Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
  • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
  • F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
  • F01N3/021—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters
  • F01N3/023—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters using means for regenerating the filters, e.g. by burning trapped particles
  • F01N3/025—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters using means for regenerating the filters, e.g. by burning trapped particles using fuel burner or by adding fuel to exhaust
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
  • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
  • F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
  • F01N3/021—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters
  • F01N3/023—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters using means for regenerating the filters, e.g. by burning trapped particles
  • F01N3/025—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters using means for regenerating the filters, e.g. by burning trapped particles using fuel burner or by adding fuel to exhaust
  • F01N3/0253—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters using means for regenerating the filters, e.g. by burning trapped particles using fuel burner or by adding fuel to exhaust adding fuel to exhaust gases
  • F01N3/0256—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters using means for regenerating the filters, e.g. by burning trapped particles using fuel burner or by adding fuel to exhaust adding fuel to exhaust gases the fuel being ignited by electrical means
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
  • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
  • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
  • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
  • F01N3/18—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control
  • F01N3/20—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control specially adapted for catalytic conversion ; Methods of operation or control of catalytic converters
  • F01N3/2006—Periodically heating or cooling catalytic reactors, e.g. at cold starting or overheating
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
  • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
  • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
  • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
  • F01N3/18—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control
  • F01N3/20—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control specially adapted for catalytic conversion ; Methods of operation or control of catalytic converters
  • F01N3/2006—Periodically heating or cooling catalytic reactors, e.g. at cold starting or overheating
  • F01N3/2033—Periodically heating or cooling catalytic reactors, e.g. at cold starting or overheating using a fuel burner or introducing fuel into exhaust duct
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
  • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
  • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
  • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
  • F01N3/18—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control
  • F01N3/20—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by methods of operation; Control specially adapted for catalytic conversion ; Methods of operation or control of catalytic converters
  • F01N3/2006—Periodically heating or cooling catalytic reactors, e.g. at cold starting or overheating
  • F01N3/204—Periodically heating or cooling catalytic reactors, e.g. at cold starting or overheating using an exhaust gas igniter, e.g. a spark or glow plug, without introducing fuel into exhaust duct
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
  • F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
  • F01N2240/14—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a fuel burner
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
  • F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
  • F01N2240/20—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a flow director or deflector
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
  • F01N2470/00—Structure or shape of gas passages, pipes or tubes
  • F01N2470/24—Concentric tubes or tubes being concentric to housing, e.g. telescopically assembled

Definitions

• the invention relates to a burner for an exhaust system through which exhaust gas from an internal combustion engine of a motor vehicle can flow. Furthermore, the invention relates to a motor vehicle with at least one such burner.
• exhaust tracts Motor vehicles with internal combustion engines and exhaust systems, which are also referred to as exhaust tracts, are known from the general state of the art and in particular from series vehicle construction. Exhaust gas from the respective internal combustion engine, also referred to as an internal combustion engine, can flow through the respective exhaust tract. In some operating states or operating situations of the respective internal combustion engine, it may be desirable for the exhaust gas to have a high temperature, for example a temperature that is arranged in the exhaust gas tract
• DE 3729 861 C2 discloses a burner for an exhaust tract through which exhaust gas from an internal combustion engine of a motor vehicle can flow, with a combustion chamber in which a mixture comprising air and a liquid fuel is to be ignited and thereby burned.
• the burner has an inner swirl chamber through which a first part of the air can flow and which causes a swirling flow of the first part of the air, which has a first outflow opening via which the first part of the air can be discharged from the inner swirl chamber.
• the liquid fuel can be introduced into the inner swirl chamber by means of an introduction element.
• a second swirl chamber surrounds the inner swirl chamber in the circumferential direction, at least over a length. A second part of the air flows through the second swirl chamber and causes a swirling flow of the second part of the air.
• the second swirl chamber has a second outflow opening, via which the second part of the Air and the first part of the air and the liquid fuel can be introduced from the inner swirl chamber into the combustion chamber.
• the first outflow opening ends in the flow direction at a specifically machined end edge, which is formed by an atomizer lip and which tapers in the flow direction of the first part of the air flowing through the first outflow opening up to the end edge and ends at the end edge.
• US 2005 / 0 039456 A1 discloses a burner with an inner swirl chamber through which a first part of the air can flow and which causes a swirling flow of the first part of the air, and with an inner swirl chamber through which a second part of the air can flow and which causes a swirling flow of the second part of the Air-causing, outer swirl chamber, in which the swirling flow of a first part of the air runs counter to the swirling flow of a second part of the air.
• DE 102008 026477 A1 discloses a burner with an inner swirl chamber with a first outflow opening and an outer swirl chamber with a second outflow opening, the outer swirl chamber and thereby a second outflow opening being formed by a component and extending from the component in the radial direction of the respective outflow opening an anti-recirculation plate extends outwards and projects beyond at least a portion of the component in the radial direction of the respective outflow opening.
• the object of the present invention is therefore to create a burner for an exhaust system of a motor vehicle and a motor vehicle with such a burner, so that at least one component of the exhaust system can be heated particularly quickly and efficiently.
• a first aspect of the invention relates to a burner for an exhaust tract through which exhaust gas of an internal combustion engine of a motor vehicle, also referred to as an internal combustion engine, can flow.
• the motor vehicle which is preferably a motor vehicle and more preferably a passenger car can be formed, has the internal combustion engine and the exhaust tract in its fully manufactured state and can be driven by means of the internal combustion engine.
• combustion processes take place in the internal combustion engine, in particular in at least one or more combustion chambers of the internal combustion engine, resulting in the exhaust gas of the internal combustion engine.
• the exhaust gas can flow out of the respective combustion chamber and into the exhaust tract and subsequently flow through the exhaust tract, which is also referred to as the exhaust system.
• At least one component such as an exhaust gas aftertreatment element for aftertreatment of the exhaust gas
• the exhaust gas aftertreatment element is, for example, a catalytic converter, in particular an SCR catalytic converter, wherein, for example, a selective catalytic reduction (SCR) can be catalytically supported and/or effected by means of the SCR catalytic converter.
• SCR selective catalytic reduction
• any nitrogen oxides contained in the exhaust gas are at least partially removed from the exhaust gas by the nitrogen oxides reacting with ammonia to form nitrogen and water during the selective catalytic reduction.
• the ammonia is provided, for example, by a particularly liquid reducing agent.
• the exhaust gas aftertreatment element can be or include a particle filter, in particular a diesel particle filter, by means of which particles contained in the exhaust gas, in particular soot particles, can be filtered out of the exhaust gas.
• the burner has a combustion chamber in which a mixture comprising air and a liquid fuel can be ignited and thereby burned.
• the combustion of the mixture in particular the combustion chamber, generates exhaust gas from the burner, the exhaust gas of which is also referred to as burner exhaust gas.
• the burner exhaust gas can, for example, flow out of the combustion chamber and into the exhaust tract, in particular at an introduction point which is arranged upstream of the component, for example in the direction of flow of the exhaust gas of the internal combustion engine flowing through the exhaust tract.
• the burner exhaust gas can, for example, flow through the component, as a result of which the component can be heated, that is to say can be heated.
• the burner exhaust gas can flow out of the combustion chamber and into the exhaust tract and thereby be mixed with the exhaust gas of the internal combustion engine flowing through the exhaust tract and/or with a gas flowing through the exhaust tract, as a result of which the exhaust gas of the internal combustion engine or the gas is heated.
• this can result in a particularly high, too temperature of the exhaust gas of the internal combustion engine or of the gas, referred to as the exhaust gas temperature, can be realized.
• the component can be heated by the high exhaust gas temperature, since the exhaust gas or the gas flows through the component.
• the exhaust gas from the combustion chamber is introduced at the aforementioned introduction point into the exhaust tract and thus into the exhaust gas or gas flowing through the exhaust tract.
• an ignition device in particular one that can be operated electrically, is arranged in the combustion chamber, by means of which at least one ignition spark for igniting the mixture can be provided, i.e. generated, for example, in particular in the combustion chamber and/or using electrical energy or the current.
• the ignition device is, for example, a glow plug or else a spark plug.
• the burner has an inner swirl chamber through which a first part of the air forming the mixture can flow and which causes a swirling flow of the first part of the air, which is therefore preferably arranged upstream of the combustion chamber in the direction of flow of the first part of the air flowing through the inner swirl chamber .
• the inner swirl chamber has, in particular precisely, a first outflow opening through which the first part of the air flowing through the inner swirl chamber can flow, via which the first part of the air flowing through the first outflow opening can be discharged from the inner swirl chamber and, for example, introduced into the combustion chamber.
• the feature that the inner swirl chamber causes or can cause a swirling flow of the first part of the air flowing through the inner swirl chamber means in particular that the first part of the air in the swirl chamber flows through in a swirling manner, and therefore flows through at least a longitudinal region of the swirling chamber in a swirling manner and/or the first part of the air first develops its swirling flow at least in a first flow region which is arranged downstream of the inner swirl chamber and outside of the inner swirl chamber and which is arranged, for example, in the combustion chamber.
• the first part of the air flows out of the inner swirl chamber via the first outflow opening in a swirling manner and/or flows into the combustion chamber in a swirling manner, so that it is very preferably provided that the first part of the air has its swirling flow at least in the combustion chamber having.
• the burner also has an introduction element, in particular an injection element, which has at least or exactly one outlet opening through which the liquid fuel can flow.
• the exit port is in the inner swirl chamber arranged so that the introduction element, in particular the injection element, or a channel of the introduction element through which the liquid fuel can flow, opens out via the outlet opening into the inner swirl chamber.
• the introduction element By means of the introduction element, the fuel flowing through the outlet opening can be introduced, in particular injected, via the outlet opening, in particular directly, into the inner swirl chamber, so that the first outflow opening is also filled with the liquid that has escaped from the introduction element via the outlet opening, in particular ejected, and as a result, in particular directly , introduced into the inner swirl chamber, in particular injected, fuel can flow through.
• This means in particular that the first part of the air and the fuel can flow through the first outflow opening along a common, first flow direction and can thereby flow out of the inner swirl chamber.
• the burner comprises an outer swirl chamber, which surrounds at least one longitudinal region of the inner swirl chamber and preferably also the first outflow opening in the circumferential direction of the inner swirl chamber, in particular completely surrounding it.
• the circumferential direction of the inner swirl chamber runs, for example, around the aforementioned first flow direction, which coincides, for example, with the axial direction of the inner swirl chamber and thus the first outflow opening.
• the inner swirl chamber is in the direction of flow of the first part flowing through the first outflow opening and thus in the direction of flow of the fuel flowing through the first outflow opening, thus in the axial direction of the inner swirl chamber and thus of the first outflow opening at the first outflow opening or at its end ends.
• a second part of the air can flow through the outer swirl chamber and is designed to bring about a swirling flow of the second part of the air.
• This is to be understood in particular as meaning that the second part of the air flows in the outer swirl chamber, thus flowing through at least a partial or lengthwise region of the outer swirl chamber in a swirling manner, and/or the second part of the air has in a direction of flow of the air flowing through the outer swirl chamber, second part of the air arranged downstream of the outer swirl chamber, second flow area, which coincides, for example, with the aforementioned first flow area, its swirling flow, wherein the second flow area can be arranged, for example, outside the outer swirl chamber and, for example, inside the combustion chamber.
• the aforementioned first flow area is arranged outside of the outer swirl chamber.
• the second part of the air swirls out of the outer Swirl chamber flows out and / or swirling flows into the combustion chamber, so it is preferably provided that the second part of the air has its swirling flow at least in the combustion chamber.
• the outer swirl chamber has, in particular precisely, one of the second part of the air flowing through the outer swirl chamber, of the fuel flowing through the first outflow opening and of the first part of the air flowing through the inner swirl chamber and the first outflow opening and through which it can flow and, for example, in the flow direction of the parts and of the fuel downstream of the first outflow opening, second outflow opening, via which the second part of the air can be discharged from the outer swirl chamber and the parts of the air and the fuel can be introduced into the combustion chamber.
• the parts of the air and the fuel can flow along a second flow direction through the second outflow opening and thus flow into the combustion chamber via the second outflow opening, with the second flow direction running parallel to the first flow direction or coinciding with the first flow direction, for example.
• the second flow direction runs in the axial direction of the outer swirl chamber, thus coinciding with the axial direction of the outer swirl chamber, so that it is preferably provided that the axial direction of the inner swirl chamber corresponds to the axial direction of the outer swirl chamber or vice versa .
• the axial direction of the inner swirl chamber coincides with the axial direction of the outer swirl chamber or vice versa.
• the respective radial direction of the respective swirl chamber runs perpendicular to the respective axial direction of the respective swirl chamber. Since, for example, the second outflow opening is arranged along the respective flow direction, i.e.
• the first outflow opening is in the outer swirl chamber, for example arranged.
• the outer swirl chamber in particular in the flow direction of the second part of the air flowing through the second outflow opening, ends at the second outflow opening, in particular at its end.
• the respective swirl chamber can have at least one or more swirl generators, by means of which the respective swirling flow can be generated or is generated.
• the respective swirl generator is arranged in the respective swirl chamber.
• the swirl generator can be, for example, a guide vane, by means of which, for example, the respective part, i.e. the respective air forming the respective part, is deflected at least or exactly once, in particular by at least or exactly 70 degrees, in particular by approximately 90 degrees , that is, for example, by 70 to 90 degrees.
• the swirling flow is to be understood as a flow that extends in a swirling or at least essentially helical or helical manner around the respective axial direction of the respective swirl chamber or the respective outflow opening.
• the respective axial direction of the respective outflow opening runs perpendicular to a plane in which the respective outflow opening runs.
• the respective axial direction of the respective outflow opening coincides with the respective axis device of the respective swirl chamber.
• the respective outflow opening is also referred to, for example, as the respective nozzle, but the cross section through which the respective part of the air can flow does not necessarily have to taper along the respective direction of flow.
• the second outflow opening is also referred to as the outer nozzle or second nozzle, with the first outflow opening, for example, also being referred to as the inner nozzle or first nozzle.
• the air can be mixed with the liquid fuel in a particularly advantageous manner, in particular over only a small mixing distance, particularly in the combustion chamber, so that a particularly advantageous mixture preparation is implemented, ie the mixture can be formed particularly advantageously.
• the fuel, particularly in the inner swirl chamber can be particularly well mixed with the first part of the air, particularly due to the swirling flow of the first part, particularly in the inner swirl chamber.
• the fuel and, for example, the first part already mixed with the fuel can be mixed particularly advantageously with the second part of the air, in particular in the outer swirl chamber and/or in the combustion chamber, since the second part of the air also has an advantageous, swirling flow having.
• the parts of the air and the fuel can be mixed in a particularly advantageous manner, so that an advantageous preparation of the mixture can be achieved.
• the burner has at least or exactly one of which the air can flow through, which opens, in particular directly, into an air chamber common to the swirl chambers, through which the swirl chambers through which the parts of the air can flow along the respective flow direction flow at least partially, in particular at least predominantly and thus at least partially, in a direction opposite to the respective flow direction are more than half or fully overlapped.
• the air chamber extends uninterruptedly, ie continuously, both along a first direction running parallel to the respective flow direction and along a second direction running perpendicular to the respective flow direction.
• the air chamber is a supply chamber common to the swirl chambers, since the swirl chambers can be supplied or are supplied with the air or with the parts of the air from the air chamber.
• the air that flows through the supply channel and is directed via the air chamber that is common to the swirl chambers or by means of the supply channel is divided into parts, i.e. into the first part of the air and into the second part of the air, so that the first part of the air from the air chamber is directed into the inner swirl chamber and then flows through the inner swirl chamber, and so that the second part of the air from the air chamber is directed into the outer swirl chamber and then flows through the outer swirl chamber.
• the burner according to the first aspect of the invention is therefore a burner without a prechamber, so that a particularly advantageous mixture preparation can also be achieved in a particularly simple, space-saving, weight-saving and cost-effective manner.
• the burner has at least one closure element which, relative to the outflow openings, is between at least one at least one of the outflow openings closing and thus completely blocking the closed position and at least one of the at least one outflow opening releasing open position is movable.
• no gases and no particles, in particular from the combustion chamber can enter the at least one outflow opening or penetrate through the at least one outflow opening, so that no gases such as the burner exhaust gas or the exhaust gas of the internal combustion engine and also no particles can get into an air line for guiding the Air or in a fuel line for guiding the fuel can penetrate.
• a particularly advantageous preparation of the mixture is also possible over a particularly long service life of the burner be achieved because the mixture preparation is not affected by particles or gases that have penetrated unwanted areas of the burner.
• the first outflow opening (first or inner nozzle) ends in the direction of flow of the first part of the air flowing through the first outflow opening and thus in the direction of flow of the fuel flowing through the first outflow opening at a specifically machined and therefore sharp or razor-sharp end edge, which is formed by an atomizer lip designed in particular as a solid body, which extends in the direction of flow of the die first part of the air flowing through the first outflow opening and thus in the direction of flow of the fuel flowing through the first outflow opening tapers down to the end edge and at the E end edge ends.
• the atomizer lip has a taper which tapers in the first flow direction and thus in particular towards the combustion chamber and ends, in particular, only at the end edge.
• the taper or the atomizer lip is sharp-edged.
• the atomizer lip ends with a sharp edge, as a result of which a particularly advantageous preparation of the mixture can be achieved.
• the mixture in the combustion chamber is burned to form a flame, the fuel being able to be advantageously mixed with the air in particular due to the swirling flows, and the flame of the combustion chamber being advantageously able to be stabilized in particular due to the swirling flows.
• a combustion-induced bursting of vortices can be generated in particular by the swirling flows.
• the air flowing into the combustion chamber is first deflected in the respective swirl chamber by approximately 70 degrees or approximately 90 degrees, in particular in a range from 70 degrees to 90 degrees, which can be implemented, for example, by the respective swirl generator.
• the inner swirl chamber and the outer swirl chamber form, for example, a swirl chamber, also referred to as the overall swirl chamber, which in the invention is divided into the inner swirl chamber and the outer swirl chamber.
• the inner swirl chamber and the outer swirl chamber are preferably separated from one another by a partition wall, in particular designed as a solid body, in particular in the radial direction of the respective swirl chamber. It is conceivable that the dividing wall surrounds at least the aforementioned longitudinal region of the inner swirl chamber in the circumferential direction of the inner swirl chamber running around the axial direction of the inner swirl chamber, in particular completely circumferentially, so that, for example, at least the longitudinal region of the inner swirl chamber in the radial direction of the inner swirl chamber outside, in particular directly, formed or limited by the partition.
• At least a second longitudinal region of the outer swirl chamber is formed or delimited in the radial direction of the outer swirl chamber inwards, in particular directly, by the partition wall. It is particularly conceivable that the longitudinal areas of the swirl chambers are arranged at the same height in the axial direction of the respective swirl chamber.
• the introduction element in particular the injection element, can be an injection nozzle whose outlet opening is arranged, for example, in or on an end face or end face of the injection element, whose end face or end face runs in an end face plane or end face plane that runs perpendicular to the axial direction of the respective swirl chamber.
• the introduction element is designed as a lance, which has a longitudinal extent that coincides, for example, with the respective axial direction of the respective swirl chamber or the respective outflow opening.
• the lance has, for example, at least or exactly, in particular at least or exactly two, outlet openings, which can be designed as bores, in particular transverse bores.
• the outlet opening has a passage direction along which the fuel can flow through the outlet opening.
• the passage direction of the outlet opening runs parallel to the respective axial direction of the respective swirl chamber or the passage direction coincides with the respective axial direction of the respective swirl chamber or the respective outflow opening.
• the passage direction runs obliquely or preferably perpendicular to the axial direction of the respective swirl chamber or the respective outflow opening.
• at least the inner swirl chamber is formed by a component designed in particular as a solid body, which also forms the atomizer lip and thus the end edge.
• a lateral surface of the component on the inner peripheral side delimits the inner swirl chamber outwards in the radial direction of the inner swirl chamber.
• the component in particular its inner peripheral lateral surface, is or functions as a film layer between the swirl chambers and thus between the swirling and thus wired flows, also referred to as air flows.
• the lateral surface on the inner peripheral side or the film layer is formed by the aforementioned partition or that the component forms or has the aforementioned partition.
• the fuel that has emerged from the introduction element, in particular that has been ejected, and is thereby introduced, in particular injected, i.e. injected, in particular directly into the inner swirl chamber, is deposited in particular as the aforementioned film on the Film layer, in particular on the inner peripheral lateral surface, and flows or streams downstream to the first outflow opening, also referred to as the nozzle opening, and thus to the end edge.
• the fuel is applied to the atomizer lip and promoted or transported to the end edge.
• the first outflow opening ends at the razor-sharp end edge, which has or provides only a small area due to the tapering described above, so that no excessively large droplets of the fuel can form at the end edge.
• Due to the configuration of the atomizer lip and in particular the end edge according to the invention only tiny droplets of the fuel tear off at the end edge. In other words, only particularly small, ie tiny, droplets form from the aforementioned fuel film at the end edge, which tear off at the end edge, in particular from the atomizer lip or from the component, and have a correspondingly large surface area. This effect leads to particularly low-soot combustion of the mixture in the combustion chamber.
• tiny droplets of the fuel can also be produced without expensively generated, high injection pressures of the fuel and without expensive injection elements, so that on the one hand the costs of the burner can be kept particularly low.
• particularly small droplets of fuel can be produced, so that very low burner outputs can also be achieved.
• the invention is based in particular on the knowledge that conventional burners have an excessively high pressure loss and are unsuitable for low outputs and are therefore disadvantageous in terms of fuel consumption. The problems and disadvantages mentioned above can now be avoided by the invention, so that in particular the fuel consumption can be kept particularly low. If the injection element is mentioned below, the insertion element should be included.
• the gas flowing through the exhaust tract is mentioned below, this can be understood to mean the previously mentioned exhaust gas of the internal combustion engine or the previously mentioned gas, unless otherwise stated. It is conceivable that the above-mentioned introduction point, at which the burner exhaust gas can be introduced into the exhaust gas tract or into the gas, is arranged in the flow direction of the gas flowing through the exhaust gas tract downstream or upstream of an oxidation catalytic converter of the exhaust gas tract, embodied, for example, as a diesel oxidation catalytic converter.
• the oxidation catalytic converter is designed in particular to oxidize any unburned hydrocarbons (HC) contained in the exhaust gas and/or to oxidize any carbon monoxide (CO) contained in the exhaust gas, in particular to form carbon dioxide.
• one embodiment of the invention provides for the end edge to be machined in a targeted manner.
• the feature that the end edge is machined in a targeted manner, in particular mechanically, means in particular that the end edge does not have a randomly designed or arbitrarily provided machining, but rather the end edge is or is specifically and thus desired during the manufacture of the burner , especially mechanically processed.
• a further embodiment is distinguished by the fact that the end edge is turned, ie machined by turning, and/or ground and is thereby mechanically machined in a targeted manner. As a result, particularly small droplets of the fuel can be produced by means of the end edge.
• the swirling flow of the first part of the air, in particular in of the inner swirl chamber, in the opposite direction to the swirling flow of the second part, in particular in the outer swirl chamber are preferably designed to form the swirling flows of the parts of the air as swirling flows running in opposite directions in relation to one another.
• a first of the swirling flows runs during one or the aforementioned operation of the burner viewed along the respective axial direction of the respective swirl chamber in a first direction of rotation.
• the first swirling flow has a first sense of rotation when viewed in the axial direction of the respective swirl chamber.
• the second swirling flow has a second sense of rotation opposite to the first sense of rotation.
• the second swirling flow runs in a second direction of rotation opposite to the first direction of rotation.
• the smallest flow cross section of the second outflow opening that can be flowed through by the second part of the air is in the radial direction of the respective outflow opening and thus of the respective swirl chamber is completely delimited or formed towards the inside by the end edge.
• the second outflow opening has its smallest flow cross section at the end edge.
• the outer swirl chamber and thus the second outflow opening are formed by a component which is in particular configured in one piece and which can be configured separately from the aforementioned component, for example.
• the above-mentioned component which is in particular designed in one piece, can be arranged in the component.
• an anti-recirculation plate extends outwards from the component in the radial direction of the respective outflow opening and thus the respective swirl chamber, which anti-recirculation plate extends outwards at least a partial area of the component in the radial direction of the respective outflow opening and thus the respective swirl chamber towards.
• the partial area upstream of the anti- Recirculation plate that is, is arranged on a back side of the anti-recirculation plate, the back side of which faces the respective swirl chamber.
• at least a first region of the combustion chamber, in which the anti-recirculation plate is arranged, for example, is at least partially divided by the anti-recirculation plate from a second region of the combustion chamber.
• the anti-recirculation plate extends in the circumferential direction of the respective outflow opening running around the respective axial direction of the respective outflow opening and thus of the respective swirl chamber completely around the respective swirl chamber or around the respective outflow opening.
• the anti-recirculation plate can be used to prevent the mixture comprising the air and the fuel from flowing backwards into the combustion chamber, especially after it has exited the second outflow opening, i.e. against the respective direction of flow along which the parts and the fuel, for example, through the second outflow opening flow through, flows, so that excessive vortex formation, especially in the combustion chamber, can be avoided.
• the anti-recirculation plate runs in an imaginary plane which runs perpendicularly to the respective flow direction and thus perpendicularly to the respective axial direction of the respective outflow opening or the respective swirl chamber. A particularly efficient operation of the burner can thus be implemented.
• the second outflow opening is in the flow direction of the flow through the second outflow opening parts of the air and thus in the direction of flow of the fuel flowing through the second outflow opening in one or in the aforementioned imaginary plane running perpendicular to the flow direction of the parts of the air flowing through the second outflow opening, in which the anti-recirculation plate is arranged.
• the anti-recirculation plate is therefore not set back against the flow direction in relation to the second outflow opening, in particular in relation to its end, but it is preferably provided that the second outflow opening, in particular its end, and the anti-recirculation plate lie in the common, imaginary plane, so that excessive vortex formation can be safely avoided.
• the anti-recirculation plate is formed in one piece with the component. As a result, excessive eddy formation can be reliably avoided, as a result of which particularly efficient operation of the burner can be achieved in a particularly cost-effective manner.
• the combustion chamber has a plurality of discharge openings which are spaced apart from one another and are separated from one another by respective wall regions which are preferably embodied as solid bodies, the wall regions preferably being embodied in one piece with one another.
• the wall areas are formed by a perforated plate or perforated disc.
• the mixture should be ignitable, in particular in the combustion chamber, and therefore be present as an ignitable mixture. This can be achieved by so-called pre-storage of fuel or the fuel. For this purpose, for example, initially, in particular for two to six seconds, i.e.
• the fuel is conveyed by means of a fuel pump into the inner swirl chamber and in particular over the injection element is conveyed into the inner swirl chamber, in particular injected and thereby upstream, in particular while the ignition device remains deactivated, that is to say while the ignition device does not provide an ignition spark.
• the ignition device switched on, that is to say activated, and an actual air and fuel supply started.
• the swirl chambers are not supplied with air during the period of time.
• Advantageous cooling of the ignition device designed as a spark plug can be achieved, for example, by perforated, in particular drilled, ribs, in particular made of aluminum, which can be arranged or provided, for example, on a thread of the ignition device designed in particular as an external thread and also referred to as a spark plug thread.
• an in particular eccentric air supply that is to say an at least essentially eccentric supply of the respective part of the air into the respective swirl chamber or into at least one of the swirl chambers, can be provided.
• the aforesaid fuel pump may be frequency controlled and/or have a piston and spring to prevent backflow of exhaust gas.
• the film applicator or the inner swirl chamber has a Venturi nozzle, on or in whose narrowest flow cross-section, for example, the injection element is arranged.
• the injection element, in particular the lance can preferably have several, and in particular compared to two, more, particularly small outlet openings.
• the passage direction encloses a jet angle with the axial direction of the inner combustion chamber, for example.
• the fuel can flow through the outlet opening to form a fuel jet and thus flow out of the injection element via the outlet opening, with the fuel jet, in particular its longitudinal center axis, coinciding with the passage direction.
• a particularly advantageous preparation of the mixture can be achieved by appropriate selection or adjustment of the jet angle.
• an afterburner or an afterburning function is conceivable, for example in order to generate a particularly high output and in particular an output of the burner that is greater than eight kilowatts.
• the burner has, for example, a rated output of eight kilowatts, with the afterburner function being able to produce a higher output of the burner than the rated output, at least for a short period of time.
• a third aspect of the invention relates to a motor vehicle, preferably designed as a motor vehicle, in particular as a passenger car, which comprises a combustion engine or the aforementioned internal combustion engine for driving the motor vehicle.
• the motor vehicle comprises a or the previously mentioned exhaust tract and at least one burner according to the first aspect of the invention.
• Fig. 1 is a schematic representation of a drive device of a
• Fig. 2 is a schematic longitudinal sectional view of a first embodiment of the
• FIG. 3 shows a detail of a schematic longitudinal sectional view of the burner according to the first embodiment
• FIG. 4 is a schematic longitudinal sectional view of a component of the burner according to the first embodiment
• 5 shows a schematic longitudinal sectional view of a second embodiment of the burner
• 6 shows a detail of a schematic and perspective rear view of a third embodiment of the burner
• FIG. 7 is a schematic longitudinal sectional view of the burner according to the third embodiment.
• FIG. 8 shows a detail of a schematic and partially sectioned perspective view of a swirl generating device of the burner
• FIG. 10 shows a schematic front view of a closure device
• FIG. 11 shows a detail of a schematic longitudinal sectional view of a fourth embodiment of the burner
• FIG. 13 shows a detail of a schematic longitudinal sectional view of a sixth embodiment of the burner
• Fig. 15 is a schematic and partially sectioned side view of an injection element of the burner
• Fig. 16 is a block diagram showing an operation of the burner.
• FIG. 17 shows a schematic sectional view of a fuel pump for delivering a fuel to the burner.
• FIG. 21 shows a detail of a schematic longitudinal sectional view of the ignition device
• FIG. 23 shows a detail of a schematic sectional view of a ninth embodiment of the burner.
• FIG. 1 shows, in a schematic illustration, a drive device 10 of a motor vehicle which is preferably designed as a motor vehicle, in particular as a passenger car.
• the drive device 10 has an internal combustion engine 12, also referred to as an internal combustion engine, which has an engine block 14, also referred to as a motor housing.
• the internal combustion engine 12 has cylinders 16 which are formed or delimited by the engine block 14, in particular directly. During fired operation of internal combustion engine 12 , respective combustion processes take place in cylinders 16 , resulting in an exhaust gas from internal combustion engine 12 .
• a fuel in particular a liquid fuel
• Internal combustion engine 12 can be designed as a diesel engine, so that the fuel is preferably diesel fuel.
• a tank 18, also referred to as a fuel tank is provided, in which the fuel can be accommodated or accommodated.
• the respective cylinder 16 is assigned, for example, a respective injector, by means of which the fuel can be introduced, in particular directly injected, into the respective cylinder 16 .
• a low-pressure pump 20 By means of a low-pressure pump 20 the fuel is conveyed from the tank 18 to a high-pressure pump 22, by means of which the fuel is conveyed to the injectors or to a fuel distribution element common to the injectors and also referred to as a rail or common rail.
• the injectors can be supplied with fuel from the fuel distribution element common to the injectors by means of the fuel distribution element and can introduce the fuel from the fuel distribution element into the respective cylinder 16, in particular inject it directly.
• the drive device 10 includes an intake tract 24 through which fresh air can flow, by means of which the fresh air flowing through the intake tract 24 is guided to and into the cylinders 16 .
• the fresh air forms a fuel-air mixture with the fuel, which includes the fresh air and the fuel and is ignited within the respective work cycle in the respective cylinder 16 and thereby burned.
• the fuel-air mixture is ignited by self-ignition.
• the ignition and combustion of the fuel-air mixture results in exhaust gas from internal combustion engine 12, whose exhaust gas is also referred to as engine exhaust gas.
• the drive device 10 has an exhaust tract 26 through which the exhaust gas from the cylinders 16 can flow.
• the drive device 10 also includes an exhaust gas turbocharger 28 which has a compressor 30 arranged in the intake tract 24 and a turbine 32 arranged in the exhaust tract 26 .
• the exhaust gas can flow out of the cylinders 16 , flow into the exhaust tract 26 and then flow through the exhaust tract 26 .
• the turbine 32 can be driven by the exhaust gas flowing through the exhaust duct 26 .
• the compressor 30 can be driven by the turbine 32, in particular via a shaft 34 of the exhaust gas turbocharger 28. By driving the compressor 30 , the fresh air flowing through the intake tract 24 is compressed by means of the compressor 30 .
• a plurality of components 36a-d are arranged in the exhaust gas tract 26, which are designed as respective exhaust gas aftertreatment devices, that is to say exhaust gas aftertreatment components for aftertreatment of the exhaust gas.
• the components 36a-d are arranged one after the other in the flow direction of the exhaust gas of the internal combustion engine 12 flowing through the exhaust tract 26 and are therefore connected in series or in series with one another.
• the component 36a is, for example, an oxidation catalytic converter, in particular a diesel oxidation catalytic converter (DOC).
• DOC diesel oxidation catalytic converter
• NSK nitrogen oxide storage catalytic converter
• the component 36b can be an SCR catalytic converter, which is also referred to simply as an SCR.
• the component 36c can be a particle filter, in particular a a diesel particulate filter (DPF).
• Component 36d may include a second SCR catalyst and/or an ammonia slip catalyst (ASC), for example.
• ASC ammonia slip catalyst
• the motor vehicle has a structure designed, for example, as a self-supporting body, which forms or delimits an interior of the motor vehicle, also referred to as a passenger cell or safety cell. People can stay in the interior while the motor vehicle is driving.
• the structure forms or defines an engine room in which the internal combustion engine 12 is arranged.
• the exhaust gas turbocharger 28 is also arranged in the engine compartment.
• the structure also has a floor, also referred to as the main floor, through which the interior space is at least partially, in particular at least predominantly or completely, delimited downwards in the vertical direction of the vehicle.
• the components 36a, b, c are arranged in the engine compartment, so that for example the components 36a, b and c form a so-called hot end or are part of a so-called hot end (hot end).
• the hot end can be flanged directly to the turbine 32 .
• the component 36d is, for example, outside the engine compartment and is arranged below the floor in the vertical direction of the vehicle, so that the component 36d, for example, forms a so-called cold end (cold end) or is part of the so-called cold end.
• the drive device 10 includes a dosing device 38, by means of which a particularly liquid reducing agent can be introduced into the exhaust gas tract 26 and thereby, for example, into the exhaust gas flowing through the exhaust gas tract 26 at an introduction point E1.
• the reducing agent is preferably an aqueous urea solution, which can provide ammonia, which can react with any nitrogen oxides contained in the exhaust gas to form water and nitrogen during a selective catalytic reduction.
• the selective catalytic reduction can be effected and/or supported catalytically by the SCR catalytic converter.
• the introduction point E1 is arranged upstream of the component 36b and downstream of the component 36a in the direction of flow of the exhaust gas flowing through the exhaust tract 26 .
• the exhaust tract 26 preferably has a mixing chamber 40 in which the reducing agent introduced into the exhaust gas at the introduction point E1 can advantageously be mixed with the exhaust gas.
• the drive unit 10 and thus the motor vehicle also include a burner 42, by means of which - as will be explained in more detail below - at least one of the components 36b, c, d arranged downstream of the burner 42 in the direction of flow of the exhaust gas flowing through the exhaust tract 26 is heated quickly and efficiently and/or can be kept warm.
• the burner 42 can burn a mixture, in particular with the formation of a flame 44 and in particular with the provision of a burner exhaust gas, the burner exhaust gas or the flame 44 being introduced into the exhaust tract 26 at an introduction point E2. This means that, so to speak, the burner 42 is arranged at the introduction point E2.
• the burner 42 is arranged at the introduction point E2.
• the entry point E2 is arranged upstream of the components 36b, c and d and downstream of the component 36a.
• the burner 42 is arranged upstream of the components 36b, c, d and downstream of the component 36a.
• the burner 42 or the introduction point E2 is arranged upstream of the component 36a and in particular downstream of the turbine 32 .
• the aforementioned mixture to be burned in the burner 42 or by means of the burner 42 comprises air and a liquid fuel.
• the fuel is used as the fuel and/or at least a portion of the air that is supplied to the burner 42 and used to form the mixture can originate from the intake tract 24 , for example.
• a fuel supply path 46 is provided, which is or can be connected fluidically to the burner 42 on the one hand and to a fuel line 48 on the other hand.
• the fuel flowing from the tank 18 to the injectors or to the fuel distribution element can flow through the fuel line 48 .
• the fuel supply path 46 is fluidically connected to the fuel line 48 at a first connection point V1, the connection point V1 being arranged downstream of the low-pressure pump 20 and upstream of the high-pressure pump 22 in the flow direction of the fuel flowing from the tank 18 to the fuel distribution element or to the respective injector.
• At the connection point V1 at least part of the liquid fuel flowing through the fuel line 48 can be branched off from the fuel line 48 and introduced into the fuel supply path 46.
• the fuel introduced into the fuel supply path 46 is allowed to flow through the fuel supply path 46 and is guided as the fuel to, and in particular into, the combustor 42 by means of the fuel supply path 46 .
• a first valve element 50 is arranged in the fuel supply path 46, by means of which an amount of fuel flowing through the fuel supply path 46 and thus to be supplied to the burner 42 can be adjusted.
• An electronic computing device 52 also referred to as a control unit, is provided, by means of which valve element 50 can be controlled, so that the quantity of fuel flowing through fuel supply path 46 and to be supplied to burner 42 can be adjusted, in particular regulated, by means of the control unit via valve element 50.
• an air supply path 54 is provided, via which or by means of which the burner can be or is supplied with the air for forming the mixture.
• a pump 56 also referred to as an air pump, is arranged in the air supply path 54 , by means of which the air can be conveyed through the air supply path 54 and can thus be conveyed to the burner 42 .
• the low-pressure pump 20 also referred to as a low-pressure fuel pump, is referred to as a fuel pump, by means of which the fuel is conveyed through the fuel supply path 46 and is thus conveyed to the burner 42 .
• the air supply path 54 is fluidically connected to the intake tract 24 at a second connection point V2.
• the fresh air introduced into the air supply path 54 can flow through the air supply path 54 as the air and is guided to and in particular into the burner 42 by means of the air supply path 54 .
• a second valve element 55 is arranged in the air supply path 54, by means of which the quantity of air flowing through the air supply path 54 and thus the burner 42, which is used to form the mixture, can be adjusted.
• the control unit is designed, for example, to activate the valve element 55 so that, for example, the quantity of air flowing through the air supply path 54 and thus to be supplied to the burner 42 and used to form the mixture can be adjusted, in particular regulated, by means of the control unit via the valve element 55 , is.
• 2 shows a first embodiment of the burner 42 in a schematic sectional view.
• the burner 42 has a combustion chamber 58 in which the mixture comprising the air supplied to the burner 42 and the liquid fuel supplied to the burner 42 are to be ignited and thereby burned is, that is ignited during operation of the burner 42 and thereby burned.
• an ignition device 60 embodied, for example, as a spark plug or glow plug or glow plug is provided, by means of which at least one ignition spark can be generated in particular using electrical energy or electric current in combustion chamber 58 .
• the mixture in the combustion chamber 58 is ignited and burned by means of the ignition spark, in particular with the provision of the burner exhaust gas and/or with the provision of the flame 44.
• the burner exhaust gas or by means of the flame 44 for example, the exhaust gas flowing through the exhaust tract 26 can be heated quickly and efficiently and/or or kept warm, so that by means of the heated and/or kept warm exhaust gas, which flows through the components 36b, c and d, for example at least the component 36b can be quickly and efficiently heated and/or kept warm.
• the burner 42 has an inner swirl chamber 62 through which a first part of the air that is supplied to the burner 42 can flow and causes a swirling first flow of the first part of the air.
• the inner swirl chamber 62 has, in particular precisely, a first outflow opening 64 through which the first part of the air can flow along a first passage direction of the outflow opening 64 and thus along a first flow direction coinciding with the first passage direction.
• the first part of the air can be discharged from the inner swirl chamber 62 via the first outflow opening 64 .
• the burner 42 comprises an introduction element in the form of an injection element 66 which has a channel 68 through which the liquid fuel which is supplied to the burner 42 can flow.
• the injection element 66 is designed as a lance, which is also referred to as a fuel lance.
• the channel 68 and thus the injection element 66 has at least one of the channel 68 flowing through, outlet opening 70 through which liquid fuel can flow.
• the channel 68 and thus the injection element 66 has at least or exactly two outlet openings 70 embodied, for example, as bores.
• the fuel can flow through outlet opening 70 in a respective, second passage direction, so that the fuel flowing through injection element 66 can be ejected or exit from injection element 66 via respective outlet opening 70 and can be injected, in particular directly, into inner swirl chamber 62 and thereby introduced is.
• the injection element 66 or the channel 68 opens into the inner swirl chamber 62 via the respective outlet opening 70, so that the liquid fuel can be injected via the respective outlet opening 70, in particular directly, into the inner swirl chamber 62 by means of the injection element 66.
• the respective second passage direction of the respective outlet opening 70 coincides with a respective second flow direction along which the fuel can flow through the respective outlet opening 70 . It can be seen that the fuel can be sprayed out of the injection element 66 via the respective outlet opening 70 to form a respective fuel jet 72 and can thereby be injected, in particular directly, into the inner swirl chamber 62 .
• the respective fuel jet 72 whose longitudinal center axis coincides, for example, with the respective second passage direction or with the respective second flow direction, is at least essentially conical.
• the injection element 66 and thus the channel 68 in the present case has a longitudinal direction or longitudinal extension or longitudinal extension direction, which runs parallel to the first passage direction and thus parallel to the first flow direction, in particular coincides with the first passage direction and thus with the first flow direction.
• the first passage direction and thus the first flow direction coincide with the axial direction of the outflow opening 64 and with the axial direction of the inner swirl chamber 62 .
• the respective second passage direction or the respective second flow direction runs perpendicularly or, in the present case, at an angle to the first passage direction and thus to the first flow direction and to the axial direction of swirl chamber 62 and outflow opening 64.
• Swirl chamber 62 is at least partially, in particular at least predominantly and thus more than half or completely, formed or delimited by a preferably integrally formed component 74 of burner 42, so that component 74 also forms or delimits outflow opening 64.
• the burner 42 also has an outer swirl chamber 76 which surrounds at least a longitudinal region and in the present case also the first outflow opening 64 in the circumferential direction of the swirl chamber 62 running around the axial direction of the swirl chamber 62, in particular completely surrounding it.
• the component 74 has a partition wall 78 which is arranged between the swirl chambers 62 and 76 in the radial direction of the swirl chamber 62 , the radial direction of which runs perpendicular to the axial direction of the swirl chamber 62 .
• the swirl chambers 62 and 76 are separated from one another in the radial direction of the swirl chamber 65 by the partition wall 78 .
• the axial direction of the swirl chamber 62 coincides with the axial direction of the swirl chamber 76 such that the radial direction of the swirl chamber 62 coincides with the radial direction of the swirl chamber 76 .
• a second part of the air that is supplied to the burner 42 can flow through the outer swirl chamber 76 and is designed to bring about a swirling second flow of the second part of the air. This means that the second part of the air flows through the swirl chamber 76 in a swirling manner and/or flows out of the swirl chamber 76 in a swirling manner and/or flows in the combustion chamber 58 in a swirling manner.
• Outer swirl chamber 76 has, in particular precisely, a second outflow opening 80 through which the second part of the air flowing through outer swirl chamber 76 can flow, in particular along a third flow direction; Part of the air can flow through, in this case coincides with the axial direction of the swirl chamber 76 and thus with the axial direction of the swirl chamber 62 .
• the third passage direction coincides with a third flow direction, along which the second part of the air flowing through the outer swirl chamber 76 flows or can flow through the outflow opening 80 .
• the first flow direction coincides with the third flow direction and the first flow direction with the third flow direction, so that in the present case the first flow direction, the third flow direction, the first flow direction and the third flow direction coincide with the axial direction of swirl chamber 62 and with the axial Direction of the swirl chamber 76 coincide.
• the second outflow opening 80 is arranged downstream of the outflow opening 64 and, in particular, is arranged in a row or in series with the outflow opening 64, so that the outflow opening 80 has access to the second part of the air, the first part of the air and the Fuel can flow through.
• the first part of the air is already mixed with the fuel in the swirl chamber 62, in particular due to the swirling first flow, in particular with the formation of a partial mixture.
• the partial mixture can flow through the outflow opening 64 and thus flow out of the swirl chamber 62 and then flow through the outflow opening 80 and is mixed with the second part of the air, in particular due to the advantageous swirling second flow, whereby the mixture is particularly advantageously prepared, and therefore the partial mixture is particularly advantageously mixed with the second part.
• swirl chamber 76 is delimited at least partially, in particular at least predominantly and thus at least more than half or completely, in the radial direction of the respective swirl chamber 62 or 76 inwards by component 74, in particular by partition 78 is.
• the swirl chamber 76 is at least partially, in particular at least predominantly or completely, delimited by a component 82 which is formed separately from the component 74 in the present case.
• the component 74 is at least partially, in particular at least predominantly, arranged in the component 82 .
• Outflow opening 80 is, for example, delimited or formed partially by component 82 and partially by component 74, in particular with regard to the smallest or smallest flow cross section of outflow opening 80 through which the second portion of the air can flow.
• razor-sharp end edge K which, for example, extends in the circumferential direction of the outflow opening 64 around the axial direction of the outflow opening 64, whose axial direction is aligned with the axial direction of the respective Swirl chamber 62 or 76 coincides, runs completely around the outflow opening 64.
• the razor-sharp end edge K is formed by an atomizer lip 84, which is formed by the component 74 in the present case.
• the atomizer lip 84 tapers in the flow direction of the first part of the air flowing through the first outflow opening 64 and thus in the flow direction of the first part of the air flowing through the first outflow opening 64
• the end edge K is ground and/or turned and thereby machined in a targeted manner.
• the fuel is sprayed against component 74, in particular against an inner peripheral lateral surface 86 of component 74, in particular with the formation of fuel jets 72, in particular in such a way that a film, also referred to simply as a film, forms on component 74, in particular on the inner peripheral lateral surface 86 Fuel film forms from the fuel.
• the inner swirl chamber 62 is formed in the radial direction of the inner swirl chamber 62 towards the outside, in particular directly, by the inner peripheral lateral surface 86 .
• the first swirling flow in particular the centrifugal forces resulting from the first swirling flow, transports the fuel film along the inner peripheral lateral surface 86 towards the end edge K, at which point the fuel tears away from the end edge K, causing particularly tiny Droplets of fuel are formed.
• the component 74 is therefore a so-called film layer or acts as a film bearing between the swirling flows.
• the droplets together form a particularly large surface of the fuel, so that the burner can be operated particularly efficiently even with low burner outputs, with no expensive pumps or no expensive high-pressure generation being required to generate the small and therefore fine droplets of fuel.
• the smallest flow cross-section of the second outflow opening 80 through which the second partial fan can flow is completely delimited or formed by the end edge K in the radial direction of the respective outflow opening 64 or 80 inwards.
• the burner 42 has an anti-recirculation plate 88 which, in the first embodiment, is arranged downstream of the outflow opening 80 and downstream of the component 82 in the flow direction of the parts flowing through the outflow opening 80 and of the fuel flowing through the outflow opening 80 .
• the anti-recirculation plate 88 has a flow opening 90 which is arranged correspondingly downstream of the outflow opening 80 and can therefore be flowed through by the parts of the air and the fuel from the swirl chambers 62 and 76 .
• the anti-recirculation plate 88 extends outwards in the axial direction of the respective swirl chamber 62 or 76, whereby the anti -Recirculation plate 88 at least a portion T of the component 82 protrudes in the radial direction of the respective swirl chamber 62 or 76 to the outside.
• a first part T1 of the combustion chamber 58 is at least partially separated from a second part T2 of the combustion chamber 58 by means of the anti-recirculation plate 88 .
• Anti-recirculation plate 88 can be used to prevent the mixture flowing through flow opening 90 and flowing into combustion chamber 58, in particular into part T2, from excessively flowing back in the direction of component 82 or back into part T1, so that advantageous mixture preparation can be achieved .
• the swirl chambers 62 and 76 are supplied with the air or parts of the air via a supply chamber 92 that is common to the swirl chambers 62 and 76 .
• the supply chamber 92 is arranged upstream of the swirl chambers 62 and 76 in the flow direction of the parts flowing through the swirl chambers 62 and 76 .
• This means that the air is first introduced into the supply chamber 92 via the air supply path 54 .
• the air that has been introduced into the supply chamber 92 can flow through the supply chamber 92 on its way to and into the swirl chambers 62 and 76 and is divided, in particular by means of the component 74, into the first part and into the second part.
• the air flowing through air supply path 54 can, for example, flow out of air supply path 54 along a supply direction and flow into supply chamber 92, the supply direction running, for example, obliquely and/or tangentially to the axial direction of the respective swirl chambers 62 and 76 and thus to their respective longitudinal axis.
• FIG. 4 shows the component 74, also referred to as a film applicator, in a schematic longitudinal sectional view. It can be seen that at least part TB of outer swirl chamber 76 is formed by component 74 .
• the component 74 has first swirl generators 94 of the inner swirl chamber 62 and second swirl generators 96 of the outer swirl chamber 76 .
• the first swirling flow of the first part of the air is generated by means of the swirl generator 94
• the second swirling flow of the second part of the air is generated by means of the swirl generator 96 .
• An inner annular surface, in particular of the inner swirl chamber 62 is denoted by K1 in FIG. 4
• an outer annular surface, in particular of the outer swirl chamber 76 is denoted by K2 in FIG.
• the swirl generators 94 are arranged in an air duct LK1 of the swirl chamber 62 whose air duct LK1 is delimited, in particular completely, by the component 74 .
• the air duct LK1 extends outwards and inwards through the component 74 in the radial direction of the respective swirl chamber 62 or 76 limited.
• the swirl generators 96 are arranged in a second air duct LK2 of the swirl chamber 76, the air duct LK2 of which is completely delimited by the component 74 and in particular in the axial direction of the respective swirl chamber 62 or 76 to the outside and inside.
• the swirl generators 94 and 96 are also formed by the component 74 .
• the air duct LK1 can be flowed through by the first part of the air, and the air duct LK2 can be flowed through by the second part of the air, so that the swirl generators 94 generate or effect the first swirling flow and the swirl generators 96 the second swirling flow.
• An outer diameter of the air duct LK1, also referred to as air duct, is denoted by Di, and an outer diameter of the air duct LK2, also referred to as air duct, is denoted by Da in FIG.
• the outflow openings 64 and 80 are both aligned in the axial direction.
• the partial mixture flows from the inner swirl chamber 62 into the combustion chamber 58 at least essentially in the axial direction.
• the second part of the air from the outer swirl chamber 76 also flows at least essentially in the axial direction into the combustion chamber 58 and entrains the finely distributed fuel from the film applicator in small droplets at the end edge K, in particular at its break-off point the combustion chamber 58.
• the smallest or narrowest flow cross-section of the outer nozzle, and therefore the outflow opening 80 is located at the tear-off point of the inner nozzle, therefore the outflow opening 64, i.e. the end edge K.
• the outflow opening 64 (inner nozzle) preferably has a diameter, in particular an inner diameter, which is 10 percent to 20 percent of Di having. Furthermore, it is preferably provided that the outer nozzle, and therefore the outflow opening 80, has a diameter, in particular an inner diameter, which is, for example, 10 percent to 35 percent of Da.
• a circular ring area from the inside to the outside should have the same area, i.e. both should be 50 percent of the total ring area.
• FIG. 5 shows a schematic sectional view of a second embodiment of the burner 42.
• the component 82 and the anti-recirculation plate 88 are designed as components that are designed separately from one another and are at least indirectly, in particular directly, connected to one another .
• the anti-recirculation plate 88 is formed in one piece with the component 82 .
• the anti-recirculation plate 88 advantageously prevents the mixture from flowing backwards back to the component 82 and forming a vortex after it has exited the outer nozzle, and thus out of the outflow opening 80 and into the combustion chamber 58 .
• the anti-recirculation plate 88 also referred to simply as a plate, preferably has a diameter, in particular an outer diameter, which is preferably at least as large as Di.
• Fig. 6 shows a section of a third embodiment of the burner 42 in a schematic perspective view.
• the combustion chamber 58 has a plurality of flow openings 98 which are spaced apart from one another and are formed by respective wall regions W, in particular designed as respective solid bodies, in particular in the radial direction of the respective swirl chamber 62 and 76 are separated from each other.
• the burner exhaust gas or the flame 44 can be discharged from the combustion chamber 58 and introduced into the exhaust tract 26 via the through-flow openings 98 .
• the wall regions W are formed in one piece with one another and are formed by a one-piece perforated disk 100, for example, which is formed as a solid body. Precisely eight through-flow openings 98 are provided here.
• the combustion chamber 58 it is fundamentally conceivable for the combustion chamber 58 to have exactly one large and undivided discharge opening 102, through which the burner exhaust gas or the flame 44 can be discharged from the combustion chamber 58 and introduced into the exhaust gas tract 26.
• the plurality of through-flow openings 98 are provided which are spaced apart and separate from one another, so that the discharge opening 102 is subdivided or divided by the wall regions W into the plurality of through-flow openings 98 . It can be seen that the through-flow openings 98 are evenly distributed in the circumferential direction running around the axial direction of the respective swirl chamber 62 or 76 and are arranged in particular along a circle whose center point is arranged on the respective axial direction of the respective swirl chamber 62 or 76.
• the third embodiment instead of a large Outlet opening in the form of the large discharge opening 102, several outlet openings in the form of the through-flow openings 98 are provided, in particular at a particular point in each case, in order to enable advantageous recirculation in the combustion chamber 58.
• a perforated plate such as perforated disk 100 with a plurality of smaller openings in the form of flow-through opening 98 .
• the number of through-flow openings 98 is, for example, in a range from three to nine inclusive.
• the flow-through openings 98 have a similar or at least substantially the same flow-through surface or exit surface through which the burner exhaust gas or the flame 44 can flow.
• the flow-through areas of or all of the flow-through openings 98 add up to a total flow-through area, which is also referred to as the total exit area and is, for example, 0.8 times to 1.8 times larger than with a single, centrally arranged opening such as the discharge opening 102.
• a central outlet opening with a diameter of 25 millimeters and thus with an area of 491 square millimeters, depending on the flow conditions in the exhaust gas tract 26, it can be advantageous to implement six smaller openings, each with a diameter of 10.5 millimeters, so that a total outlet area of 520 square millimeters is represented is.
• FIG. 7 shows the third embodiment of the burner 42 in a schematic longitudinal sectional view, with the perforated disk 100 also referred to as perforated plate being provided.
• the aforementioned advantageous recirculation in the combustion chamber 58 is illustrated by an arrow 104 in FIG. 7 .
• a swirling flow of the mixture and designated 106 is also illustrated in Figure 7 .
• the respective swirl generator 94 or 96 is preferably designed as an air guide vane and not as a quarter-spherical sheet metal construction, so that the respective swirl-shaped flow can be generated or brought about in a particularly advantageous manner.
• the swirling flows of the parts of the air and the resulting swirling flow 106 of the mixture in the combustion chamber 58 prevents the flame 44 from being blown out in the combustion chamber 58, optimizes mixing of the air with the fuel in the combustion chamber 58 and creates vortex bursting for stabilization of the flame 44.
• the recirculation in the combustion chamber 58 illustrated by the arrows 104 can be implemented in particular by using the perforated plate and a resulting reduction in an outlet cross section, via which the flame 44 or the burner exhaust gas can be discharged from the combustion chamber 58 and introduced into the exhaust gas tract 26 is.
• the reduction in the outlet cross section means that, for example, the total outlet area of the individual flow openings 98 is smaller than the area of the large, connected discharge openings 102.
• the advantageous recirculation in the combustion chamber 58 results in improved mixing of the air and of the fuel in the combustion chamber 58 and a longer dwell time of the burning mixture in the combustion chamber 58, so that when the flame 44 or burner exhaust gas exits the combustion chamber 58 and into the exhaust tract 26, excessive emissions of unburned hydrocarbons (HC) can be avoided, and a particularly high temperature of the flame 44 or of the burner exhaust gas can be achieved at its outlet.
• the recirculation leads to recirculation areas and vortex bursts, as a result of which the flame 44 can remain in the combustion chamber 58 for a particularly long time.
• FIG. 8 shows, in a schematic and partially sectioned perspective view, a swirl generating device 107 which, for example, can be part of the component 74 or can be formed by the component 74 .
• Swirl generating device 107 comprises the swirl generators 94 of the inner swirl chamber 62 and the swirl generators 96 of the outer swirl chamber 76. It can be seen particularly well from FIG. could be. This can avoid excessive pressure drop, especially when compared to spherical swirlers.
• the number of swirl generators 94 is, for example, in a range from six to eleven inclusive.
• the number of outer swirl generators 96 is, for example, in a range from eight to 14 inclusive.
• the respective air duct LK1 or LK2, in which the swirl generators 94 or 96 are arranged has, for example, a respective surface area which, for example, is at least 20 percent and at most 70 percent is covered by the respective swirl generators arranged in the air duct LK1 or LK2.
• a particularly advantageous axial obstruction is at least 20 percent and at most 70 percent of the respective Area provided.
• a respective radius of the respective air guide vane can extend from at least 40 percent from Di to infinity, so that the respective air guide vane can be straight.
• the respective air guide vane encloses a respective angle ⁇ with the respective radial direction of the respective swirl chamber 62 and 76, which angle is, for example, in a range from ten degrees up to and including 45 degrees.
• the aforementioned radius of the respective air guide vane also referred to simply as a vane, is denoted by R in FIG.
• Swirl generators 94 and 96 are preferably designed to deflect the part of the air flowing through the respective air duct LK1 or LK2, and therefore the air flowing through the respective air duct LK1 or LK2 and thus forming the respective part, by 70 degrees to 90 degrees, in particular in relation to the strictly or purely axial direction of the respective swirl chamber 62 or 76.
• the air guide vanes of the inner and outer swirl chambers 62 and 76 can be designed in opposite directions.
• the outer swirl generators 96 of the outer swirl chamber 76 and the inner swirl generators 94 of the inner swirl chamber 62 are designed to form or cause the swirling flows of the parts of the air as opposing or oppositely directed swirling flows, so that, for example the first flow is left-handed and the second flow is right-handed, or vice versa.
• Swirl generating device 107 has a through opening 108, in particular a central through opening, through which injection element 66 passes.
• injection element 66 protrudes through through-opening 108 into inner swirl chamber 62.
• a closure device 110 which in the present case is designed as an iris diaphragm or in the manner of an iris diaphragm.
• burner 42 is not in operation, it may be advantageous to have an air line and a fuel line, that is, for example, air supply path 54 and/or fuel supply path 46 and/or swirl chambers 62 and 76 and, for example, outflow opening 64 and/or outflow opening 80 to block exhaust gas from the internal combustion engine 12 from entering the air supply path 54, the fuel supply path 46, the supply chamber 92, the swirl chamber 62 and/or the swirl chamber 76.
• the combustion chamber 58 or at least a length range of Combustion chamber 58 to block in order to prevent exhaust gas from the internal combustion engine 12 from the exhaust tract 26 penetrating into the combustion chamber 58 or in its partial area or longitudinal area.
• the closure device 110 can be used for this purpose, which can be arranged, for example, in the combustion chamber 58 or downstream of the combustion chamber 58 .
• Closing elements 112 of closing device 110 which can be moved in the manner of an iris diaphragm, can vary, i.e.
• an opening cross section 114 through which, for example, the flame 44 or the burner exhaust gas can flow and which is delimited, in particular directly, by the closing elements 112, whereby, for example, the opening cross section 114 is set depending on the load, in particular controlled or regulated, can be. It is thus conceivable to close at least a partial area of the combustion chamber 58 by means of the closing device 110 .
• the outflow opening 80 can be closed, for example, by means of a first closure device 110 .
• the outflow opening 80 can be closed, for example, by means of a second closure device 110 . In particular, this has the advantage that an air and fuel supply can be closed at the same time by means of a small plug.
• An air valve is then also not required downstream of the pump 56 since it prevents exhaust gas from entering the pump 56 . It is also possible to dispense with a much larger exhaust gas flap, which is subjected to hot exhaust gas, after the combustion chamber 58 or after its exit.
• the opening cross section 114 is an opening cross section or outlet cross section, in particular of the combustion chamber 58, with the flame 44 or the burner exhaust gas being discharged from the combustion chamber 58 via the outlet cross section and being introduced into the exhaust gas tract 26.
• a narrowing of the opening cross section that is necessary, required or implemented to increase the flow speed of the flame 44 or the burner exhaust gas from the combustion chamber 58, in particular by correspondingly moving the closure elements 112 in the manner of an iris diaphragm, should be presented in a streamlined manner.
• a conical outlet could be made at an angle of 30 degrees to 70 degrees to the horizontal, as is realized, for example, in an aircraft engine by segments and/or by a cone. This can be done with a fixed geometry or variable as in an aircraft engine with individual segments that are foldable, for example in the case of a thrust nozzle, or with a displaceable arranged outlet cone, which is displaceable, for example, in the axial direction of the respective swirl chamber 62 or 76.
• FIG. 11 shows a detail of a schematic sectional view of the burner 42 according to a fourth embodiment. It can be seen particularly well from FIG. 11, but also from FIGS. 2 and 7, that the combustion chamber 58 is formed or delimited by a chamber element 116 designed in particular as a solid body.
• combustion chamber 58 whose axial direction coincides with the axial direction of the respective swirl chamber 62 or 76, along its radial direction running parallel to the respective radial direction of the respective swirl chamber 62 or 76, in particular directly, through an inner peripheral lateral surface 118 of the chamber element 116 limited.
• the chamber element 116 can be formed in one piece.
• the chamber member 116 is formed to have two chamber parts 120 and 122 which are, for example, integrally formed with each other, or the chamber parts 120 and 122 are separately formed and interconnected components. In this case, the lateral surface 118 on the inner circumference is formed by the chamber part 122 .
• Chamber parts 120 and 122 are arranged one inside the other in such a way that at least one longitudinal region of chamber part 120 surrounds at least one longitudinal region of chamber part 122 in the circumferential direction of combustion chamber 58 running around the axial direction of combustion chamber 58, in particular completely circumferentially, with at least the longitudinal region of chamber part 120 is spaced outwards in the radial direction of the combustion chamber 58 from the longitudinal region of the chamber part 122, in particular with the formation of an intermediate space 124.
• the intermediate space 124 is arranged in the radial direction of the combustion chamber 58 between the chamber parts 120 and 122 and, for example, as an air gap, in particular between chamber parts 120 and 122.
• the continuous or uninterrupted discharge opening 102 is formed or delimited by the chamber part 122 , particularly in the circumferential direction of the combustion chamber 58 .
• the discharge opening 102 is not subdivided, that is to say free of a component dividing the discharge opening 102 into a plurality of through-flow openings that are separate and spaced apart from one another.
• the perforated disk 100 also known as the perforated plate, is arranged in the discharge opening 102, through which the per se uninterrupted, i.e.
• the flame 44 or the burner exhaust gas can flow out of the combustion chamber 58 along a fourth flow direction running in the axial direction of the combustion chamber 58, i.e. running parallel to the axial direction of the combustion chamber 58 or coinciding with the axial direction of the combustion chamber 58, and thereby through the discharge opening 102 or flow through the respective flow opening 98, with the fourth flow direction coinciding with the first, second and third flow direction.
• the discharge opening 102 tapers in the flow direction of the burner exhaust gas flowing through the discharge opening 102, ie along the fourth flow direction.
• the chamber element 116 in particular the chamber part 120, has a longitudinal region L1 that tapers in the flow direction of the burner exhaust gas flowing through the discharge opening 102 and that delimits the discharge opening 102 in the circumferential direction of the combustion chamber 58, in particular completely around it.
• the length region L1 and thus the discharge opening 102 are conical in the direction of flow of the burner exhaust gas flowing through the discharge opening 102, that is to say conical or truncated.
• the discharge opening 102 is formed at an outlet of the combustion chamber 58 or forms an outlet of the combustion chamber 58, with the combustion chamber 58 being formed conically at its outlet in the fourth embodiment , thus having a cone formed by the length region L1.
• the discharge opening 102 has an inside diameter of 34 mm. In other words, it is preferably provided that the smallest or narrowest inner diameter of the discharge opening 102 through which the burner exhaust gas can flow is 43 mm.
• intermediate space 124 is filled with air, for example, and thus being formed as an air gap
• the combustion chamber is double-walled 58 or the chamber element 116 created, whereby the combustion chamber 58 is isolated by the intermediate space 124, that is, by the air gap.
• the combustor 58 is air gap insulated.
• the combustion chamber 58 preferably has an inner diameter d1, in particular upstream of the cone or upstream of the length region L1, which is preferably 1.0 to 3.0 times Da. Furthermore, it is preferably provided that the smallest inside diameter d2 of the discharge opening 102, the smallest inside diameter d2 of the discharge opening 102 also being referred to as the outlet diameter, is 0.7 times to 2.3 times Da. A smaller outlet diameter of the discharge opening 102 maintains the outlet speed of the burner exhaust gas and reduces the influence of the flame 44, also known as the burner flame, by the exhaust gas of the internal combustion engine 12, also known as the engine exhaust gas.
• a length 11 of the combustion chamber 58 running in the axial direction of the combustion chamber 58, in particular without secondary air injection , is preferably 1.5 to 4.0 times Da. With secondary air injection, it is preferably provided that the length 11 of the combustor is 2.0 to 5.5 times Da.
• the continuous discharge opening 102 it is conceivable to use the plurality of through-flow openings 98 that are separate and spaced apart from one another. In other words, it is conceivable to divide the continuous and therefore uninterrupted discharge opening 102 into the plurality of throughflow openings 98 which are spaced apart and separate from one another, the number of which is preferably in a range from 3 to 9 inclusive.
• the respective through-flow opening 98 has a surface area, also referred to as the exit area or through-flow area, with the sum of the surface areas of all through-flow openings 98 preferably being similar to the exit area of the connected discharge openings 102, i.e. similar to the surface area of the discharge opening 102.
• the sum of the surface areas of the through-flow openings 98 is also referred to as the total exit area.
• the through-flow openings 98 are designed as bores, for example. It is conceivable that the sum of the surface areas of all flow openings 98, i.e. the total outlet surface, is 0.8 to 1.8 times the surface area of the or an uninterrupted, connected discharge opening of the discharge opening 102 of the combustion chamber 58. In particular, it is conceivable that the perforated disk 100 is arranged in the discharge opening 102 or in the length region L1.
• the exhaust gas of the internal combustion engine 12 also referred to as engine exhaust gas
• a deflection element in particular a deflection element and/or a perforated element, in particular a perforated plate
• the perforated element an element designed in particular as a solid body can be understood, which has a plurality of holes spaced apart from one another and in particular separated from one another by respective walls, through which a gas, such as the burner exhaust gas or the engine exhaust gas, can flow.
• a deflection element such as a baffle
• the deflection element is arranged in the direction of flow of the engine exhaust gas upstream of the combustion chamber 58, that is to say upstream of the introduction point E2, in the exhaust tract 26.
• a geometry of the deflection element can depend on how the combustion chamber 58 is arranged in relation to the exhaust gas tract 26 , that is to say in relation to an exhaust gas duct of the exhaust gas tract 26 .
• the exhaust gas duct means that the burner exhaust gas or the flame 44 flows out of the combustion chamber 58, in particular along the fourth flow direction, into the exhaust gas duct, in particular at the inlet point E2. Individual adjustment of the geometry of the deflection element is advantageous.
• closure device 110 or another closure device can be arranged at the outlet of the combustion chamber 58 .
• the closure device 110 can be arranged, for example, in the length region L1 or in the discharge opening 102, so that a flow cross section through which the burner exhaust gas or the flame 44 can flow, over which the burner exhaust gas or the flame 44, in particular at the Inlet point E2, can be removed from combustion chamber 58 and introduced into exhaust gas tract 26, in particular into the exhaust gas duct, is delimited by closure device 110, in particular by closure elements 112, and can therefore be varied, i.e. adjusted, by means of closure device 110.
• This adjustable flow cross section is in particular the opening cross section 114.
• the closure device 110 can be arranged in the chamber part 122 and in the discharge opening 102, or the closure device 110 or a Another closure device is arranged downstream of the combustion chamber 58, that is to say downstream of the chamber part 122 and directly adjoining the combustion chamber 58 or the chamber part 122, and therefore arranged downstream of the discharge opening 102 per se.
• a narrowing of the discharge opening 102 as is realized in the fourth embodiment by the length region L1, i.e. by the cone described, leads to an increase in the flow velocity of the burner exhaust gas, with the narrowing of the outlet of the combustion chamber 58 being designed to be streamlined.
• the cone formed here by the length region L1 preferably has an angle, also referred to as a cone angle, in particular to the axial direction of the combustion chamber 58 illustrated by a dashed line 126 in FIG. 11 of 30° to 70°.
• the cone is designed as a fixed geometry, so that the cone, ie the cone angle, is fixed, ie cannot be varied.
• the cone or its cone angle can be varied by means of a displaceably arranged outlet cone and/or that an outlet cone is provided whose longitudinal center axis coincides, for example, with the axial direction of combustion chamber 58 and/or which extends in the axial direction of combustion chamber 58 is displaceable, in particular relative to the chamber element 116, with the outlet cone, which is preferably arranged coaxially to the combustion chamber 58, preferably tapering in the direction of flow of the burner exhaust gas flowing through the discharge opening 102.
• the feature that the outlet cone is arranged coaxially to the combustion chamber 58 means in particular that the axial direction of the outlet cone, and therefore its longitudinal center axis, coincides with the axial direction of the combustion chamber 58 .
• the flow cross section through which the burner exhaust gas can flow can be varied, for example, via which the burner exhaust gas can be discharged from the combustion chamber 58 and introduced into the exhaust gas duct.
• the exit cone is shown particularly schematically in FIG. 11 and is denoted by 128 .
• a movement direction running parallel to the axial direction of combustion chamber 58 or coinciding with the axial direction of combustion chamber 58, along which the outlet cone 128 can be moved, in particular displaced, translationally relative to the chamber element 116 is shown in FIG a double arrow 130 is illustrated.
• the flow cross-section through which the burner exhaust gas flows in the radial direction of the combustion chamber 58 is also limited to the outside by the chamber element 116 and to the inside by the outlet cone 128, in particular directly, with the flow cross-section being annular or ring-shaped . Since the outlet cone 128 tapers in the direction of flow of the burner exhaust gas flowing through the discharge opening 102 or the flow cross section, the flow cross section is varied by displacing the outlet cone 128 along the direction of movement and relative to the chamber element 116 .
• FIG. 12 shows a detail of a fifth embodiment of the burner 42 in a schematic sectional view.
• part of the component 74 and part of the component 82 can be seen, in particular as in FIG. 3.
• an air and fuel line that is, preferably to close the outflow openings 64 and 68 in order to prevent the engine exhaust gas from entering the swirl chambers 62 and 76 .
• a closure device 110 is arranged in outflow opening 64 and/or in outflow opening 80, or closure device 110 is arranged downstream of outflow opening 80 and directly adjoining outflow opening 80, so that, for example, one of the first part of the air and the fuel through which a first flow cross-section can flow, in particular outflow opening 64, and/or a second flow cross-section through which the parts of the air and fuel can flow, in particular outflow opening 80, or one of the parts of the air and of
• the third flow cross section through which the fuel can flow and which is arranged downstream of the outflow opening 80 and directly or directly adjoins the outflow opening 80 is variable or adjustable by means of the closure device 110 .
• the first, second or third flow cross section is, for example, opening cross section 114, i.e. in particular opening cross section 114 of an opening having opening cross section 114, whose flow cross section (opening cross section 114) and thus surface area can be adjusted, in particular in the manner of an iris diaphragm, by means of closure elements 112.
• the respective first, second or third flow cross section can thus be adjusted, in particular controlled or regulated, in particular as a function of the load. For example, it is conceivable to close only the two outflow openings 64 and 80, also referred to as outlet nozzles, by means of the closure device 110 or by means of another, additional closure device close, thus reducing the first, second or third flow cross section to zero.
• the further closure device can be, for example, a closure element which is shown particularly schematically in FIG. 12 and is designated by 132, which is also designated as a closure plug.
• the closure element 132 can be moved, for example, in particular in the axial direction of the respective swirl chamber 62 or 76, relative to the component 82 and relative to the component 74, in particular translationally, in particular between at least one closed position and at least one open position shown in FIG.
• the outflow openings 64 and 80 are closed by the closure element 132 and are thus fluidically blocked, in particular while the burner 42 is deactivated.
• no engine exhaust gas from the exhaust tract 26 can flow through the outflow openings 64 and 80 .
• the closure element 132 releases the outflow openings 64 and 80, in particular while the burner 42 is being operated. It can be seen that the outflow openings 64 and 80 can be closed or are closed at the same time by means of the closure element 132, which is designed as a small plug, for example, particularly when the closure element 132 is in the closed position.
• An air valve such as the valve element 55, for example, is then not required downstream of the pump 56 , since it can be avoided by means of the closure element 132 that engine exhaust gas from the exhaust tract 26 flows through the air supply path 54. In other words, it can be avoided by means of the closure element 132 or by means of the closure device 110 that engine exhaust gas from the exhaust tract 26 penetrates into the pump 56 . It is also possible to dispense with a much larger exhaust gas flap, which is subjected to hot exhaust gas, downstream of the combustion chamber 58, that is to say after its outlet.
• the above-mentioned air gap insulation of the combustion chamber 58 is explained in more detail below: Since the combustion chamber 58 is very hot on its outer wall, especially during full-load operation, and possibly glows, the air gap insulation can ensure particularly reliable operation. In addition, heat losses can be kept particularly low thanks to the air gap insulation. It is preferably provided that thermal insulation, in particular, surrounds the combustion chamber 58 in the circumferential direction running around the axial direction of the combustion chamber 58, in particular completely circumferentially. In the present case, the air gap insulation, and therefore the air gap, is provided as this insulation.
• the intermediate space designed here as an air gap 124 preferably has a width running in the radial direction of the combustion chamber 58, in particular a gap width, the width, in particular the gap width, preferably being 6% to 25% of Da. In particular, it is conceivable that the width is in a range from 1.5 mm up to and including 6 mm.
• the chamber element 116 is a double-walled and therefore air-gap insulated tube. In other words, the chamber parts 120 and 122 form a double-walled and therefore air-gap insulated tube.
• an insulating element formed separately from chamber element 116 surrounds the air-gap-insulated pipe (chamber element 116), i.e. at least a longitudinal region of chamber element 116 running in the axial direction of combustion chamber 58, in particular completely surrounding it surrounds.
• the insulating element is preferably an insulating mat.
• the insulating element is preferably formed at least from mineral wool and/or sheet metal, as a result of which the combustion chamber 58 can be insulated in a particularly advantageous manner.
• a possible installation position of the combustion chamber 58 or the burner 42 is described below.
• the mixture in the combustion chamber 58 is too thin to burn, releasing heat or thermal energy.
• At least component 36b for example, can be effectively and efficiently heated and/or kept warm by means of thermal energy.
• component 36c embodied as a particle filter, for example, can be heated. By heating up the particle filter, regeneration of the particle filter can be brought about or carried out, for example.
• it or the introduction point E2 should be arranged as close as possible to the component to be heated or kept warm, such as the component 36b and/or 36c. As a result, heat losses can also be kept low.
• a minimum distance for mixing the burner exhaust gas with the engine exhaust gas should be provided, with this minimum distance extending in particular continuously in the direction of flow of the engine exhaust gas flowing through the exhaust tract 26 from the burner 42 or from the introduction point E2 up to the component to be heated or kept warm, such as component 36b, in particular up to its inlet.
• the minimum distance is a minimum distance of the mixing chamber 40. Therefore, the Do not approach the entry point E2 directly to the entry point of component 36b.
• a distance, particularly in the flow direction of the exhaust gas flowing through the exhaust gas tract 26, between the inlet point E2 and the component 36b, in particular in the flow direction of the component 36b immediately following the exhaust gas tract 26, is at least 5 times to 8 times Da and at most 30 times Da.
• component 36b in the direction of flow of the exhaust gas (engine exhaust) flowing through exhaust tract 26 directly adjoins inlet point E2 means that in the direction of flow of the exhaust gas flowing through exhaust tract 26 between inlet point E2 and component 36b no other, further exhaust gas aftertreatment component is arranged.
• a diameter, in particular an inner diameter, of the exhaust gas duct in which the introduction point E2 is arranged, in particular after exiting the combustion chamber 58 should expand conically to at least 6 times Da, in particular before the exhaust gas enters component 36b entry.
• component 36b is a catalytic converter, in particular the aforementioned SCR catalytic converter
• component 36b has a substrate.
• the aforementioned distance is a distance running in particular in the flow direction of the exhaust gas flowing through the exhaust gas tract 26 between the introduction point E2 and the substrate of the catalytic converter. It is therefore advantageous if the inner diameter of the exhaust gas duct expands to at least 6 times Da after exiting the combustion chamber 58, i.e. starting from the introduction point E2, for example, before the exhaust gas (engine exhaust gas or burner exhaust gas) hits the substrate.
• ignition device 60 embodied, for example, as a spark plug, glow plug or glow plug
• cooling ribs are applied to the thread 134 of the ignition device 60, which is also referred to as the spark plug thread.
• the number of cooling fins is preferably in a range from 1 to 7 inclusive.
• the cooling fins have a thickness which is in a range from 2 to 4 mm inclusive.
• the respective cooling rib has a diameter of 20 to 80 mm, in particular an outer diameter.
• the individual cooling ribs have openings in the form of bores, in particular through-openings, the number of which is in a range from 3 to 8 inclusive, in order to implement advantageous heat dissipation to an environment of ignition device 60, i.e. ambient air .
• the respective passage opening of the respective cooling rib has, for example, a diameter, in particular an inner diameter, which is at least 5 mm and at most 15 mm.
• An electrode spacing between electrodes of the ignition device 60 is at least 0.7 mm and at most 10 mm.
• the electrodes can be seen in FIG. 2 and are denoted there by 136 and 138, the ignition spark for igniting the mixture in the combustion chamber 58 being generated by means of the electrodes 136 and 138, in particular between the electrodes 136 and 138.
• the air should not be introduced into the respective swirl chamber 62 or 76 strictly radially, i.e. in the radial direction of the respective swirl chambers 62 or 76, but instead tangentially or obliquely to the respective axial direction of the respective swirl chamber 62 or 76, as illustrated in FIG.
• an impulse of the incoming air can already be directed in the direction of the swirl, which leads to a particularly high level of effectiveness in the generation of the swirl.
• a fuel pump such as a fuel pump, is used to deliver the fuel from the tank 18 .
• the fuel pump can thus be the low-pressure pump 20, for example.
• the burner is operated stoichiometrically, which means that the mixture is a stoichiometric mixture.
• a first portion of the air in the mixture and a second portion of the fuel in the mixture are set or regulated as precisely as possible.
• a first quantity of the air in the mixture also referred to as combustion air
• a second quantity of the fuel in the mixture are set and/or calculated at least essentially exactly and fed into the respective corresponding swirl chamber 62 or 76 be initiated. Therefore, it is advantageous to use a frequency-controlled piston pump as the fuel pump for delivering the fuel to the combustor 42 . At its outlet, this should be provided with a spring-loaded valve, such as a ball valve, in order to prevent fuel or exhaust gas from flowing back, in particular into the fuel pump.
• FIG. 17 Such a fuel pump is shown in FIG. 17 in a schematic longitudinal sectional view and is denoted by 137 .
• the fuel pump 137 is designed as a piston pump, the piston of which is denoted by 138 for conveying the fuel.
• the spring-loaded valve which is designed as a spring-loaded ball valve in the exemplary embodiment shown in FIG. 17, is designated 140 in FIG. 17 and includes a spring unit 142, in particular mechanical, and a ball 144.
• the spring-loaded valve 140 is designed or functions as a check valve as a non-return valve, so that the fuel can be conveyed to burner 42 by means of fuel pump 137, so that valve 140 opens in the direction of the burner but blocks in the opposite direction, so that no exhaust gas and no air from burner 42 back in the fuel pump 137 can flow.
• FIG. 13 shows a detail of a sixth embodiment of the burner 42 in a schematic longitudinal sectional view, with the outflow openings 64 and 80 and thus the component 82 and the component 74 being recognizable in particular in FIG. 6 as well as in FIG.
• the injection element 66 can also be seen in FIG. 13, which in the exemplary embodiment shown in FIG. 13 is designed as a lance according to FIGS.
• the outlet openings are not arranged or formed on an axial end face 146 of the injection element 66 oriented in the axial direction of the swirl chambers 62 or 76, but rather the outlet openings 70 are oriented in the radial direction of the swirl chambers 62 or 76 and in this case in an outer circumferential lateral surface 148 of the injection element 66 is formed, whose outer circumferential lateral surface 148 extends around the axial direction of the respective swirl chamber 62 or 76 running circumferential direction.
• the respective fuel jet 72 does not exit from the injection element 66 at the end face 146 and not in the axial direction or not parallel to the axial direction of the respective swirl chamber 62 or 76, but rather the fuel jet 72 exits perpendicularly or, in the present case, obliquely 13 by a dashed line 150, of the respective swirl chamber 62 or 76 out of the injection element 66.
• the inner peripheral lateral surface 86 of the component 74 is also referred to as the film wall, since the fuel that is ejected through the outlet openings 70 from the injection element 66 and brought or injected against the film wall forms the aforementioned film or fuel film on the film wall (inner peripheral lateral surface 86). forms.
• a simple lance such as the injection element 66 shown in FIG. 13, can be used, for example, instead of an atomizer nozzle.
• the lance comprises a small tube 152, in the end area of which the at least two outlet openings 70, designed for example as transverse bores, are attached.
• the fuel does not exit the lance or tube 152 in the axial direction of the respective swirl chamber 62 or 76, but rather in the radial direction or at an angle to the radial direction of the respective swirl chamber 62 or 76 on the film applicator and in particular on or against the film wall, it is advantageous if the fuel is atomized.
• a Venturi nozzle 154 is arranged on or on the film wall, also referred to as the film layer wall, which is particularly in the axial direction of the respective swirl chamber 62 or 76, its respective axial direction with the axial direction and with the longitudinal direction of the injection element 66, in particular the tube 152, is arranged at the level of the outlet openings 70, which are preferably arranged at the same level in the axial direction.
• the venturi nozzle 154 is preferably provided in the swirl chamber 62, in which the outlet openings 70 are also arranged of injection element 66 is arranged in such a way that the narrowest or smallest or smallest flow cross section of Venturi nozzle 154 and the respective outlet opening 70 are arranged at the same height in the axial direction of the respective swirl chamber 62 or 76 and thus in the axial direction of injection element 66.
• the venturi nozzle 154 and the injection element 66 can function in the manner of a jet pump. The first part of the air flows through the venturi nozzle 154, ie through its narrowest flow cross section.
• the outlet openings 70 are each arranged at least partially in the narrowest flow cross section of the Venturi nozzle 154, that is, since the narrowest Flow cross-section of the Venturi nozzle 154 and the outlet openings 70 are arranged at the same height in the axial direction of the injection element 66 and thus in the direction of flow of the first part of the air flowing through the Venturi nozzle 154, the first part of the air acts or functions as a propellant medium that Fuel sucks in as a suction medium, so to speak, in particular via the outlet openings 70, so that so to speak the propellant medium sucks the suction medium (fuel) through the outlet openings 70.
• the fuel in the swirl chamber 62 is atomized in a particularly advantageous manner.
• FIG. 14 shows a detail of a seventh embodiment of the burner in a schematic longitudinal sectional view.
• the injection element 66 is formed as a lance, for example.
• the respective fuel jet 72 in particular its longitudinal axis or longitudinal center axis, with an imaginary perpendicular to the axial direction of the respective swirl chamber 62 or 76 and thus perpendicular to the respective flow direction of the respective part of the fluid flowing through the respective swirl chamber 62 or 76
• the plane EB running in the air includes an angle ß, also referred to as the jet angle.
• the axial direction of the respective swirl chamber 62 or 76 coincides with the direction of longitudinal extent or longitudinal extent of the injection element 66 and thus with its axial direction.
• the outlet openings 70 are distributed, in particular uniformly, in the circumferential direction running around the axial direction of the injection element 66 and are spaced apart from one another.
• the number of outlet openings 70 is preferably at least 2 and at most 10. In other words, it is provided, for example, that the number of outlet openings 70 in a range from 2 to 10 inclusive.
• the angle ⁇ is in a range from 10° to 60° inclusive, in particular in order to direct an impulse of the fuel in the direction of flow.
• the respective, preferably circular outlet opening 70 which is designed as a bore, for example, has a diameter, in particular an inner diameter, which is in a range from 50 mm to 3 mm inclusive.
• FIG. 15 shows a possible, further embodiment of the injection element 66 in a schematic and partially sectioned side view.
• the injection element 66 is in the form of an injection nozzle formed, as used in fuel oil burners.
• the injection element 66 has a head 155, a swirl slot 156, a swirl body 158, a secondary filter 160 and a primary filter 162.
• the injection element 66 according to FIG. 15 has at least or precisely one outlet opening 70, the outlet opening 70 of the injection element 66 being arranged or formed on its axial end face 146, which is also referred to as the axial end face.
• the fuel jet 72 flowing through the outlet opening 70 emerges in the axial direction of the injection element 66 and thus of the respective swirl chamber 62 or 76 from the outlet opening 70 and thus out of the injection element 66 .
• the fuel jet 72 or its longitudinal axis or longitudinal center axis runs at least essentially in the axial direction, i.e. parallel to the axial direction of the respective swirl chamber 62 or 76.
• T5 A temperature of the exhaust gas at inlet point E2 or downstream of inlet point E2 and in particular upstream of component 36b is denoted by T5.
• T5 A temperature of the exhaust gas at inlet point E2 or downstream of inlet point E2 and in particular upstream of component 36b is denoted by T5.
• the temperature T5 is measured, in particular by means of a temperature sensor, so that, for example, a value, also referred to as the T5 value, which characterizes the temperature T5, is measured.
• the T5 value is illustrated by a block 164 in FIG.
• the T5 value is transmitted to a block 166, in particular as an input variable.
• the block 166 illustrates an initial state in which, for example, an air supply in the burner 42 is closed, the fuel pump is deactivated, so that a fuel supply in the burner 42 is also deactivated and the ignition device 60 is deactivated.
• An arrow 168 illustrates a so-called burner release, ie a release of the burner.
• the ignition device 60 is switched on at a block 170, ie activated.
• a block 172 for example, a combustion air ratio of the mixture of 0.9 is set in order to implement start-up operation of the burner 42 in this way.
• the air pump is activated and the fuel pump is activated.
• the air/fuel ratio of the mixture is adjusted to 1.03 with the fuel pump operating at a low frequency.
• the ignition device 60 is deactivated.
• a block 178 illustrates an operational state of the combustor 42. In the operational state, an air supply to the combustor 42 is open and the fuel pump is on turned on and the igniter 60 is deactivated so that the burner 42 is supplied with the air and fuel.
• An arrow 180 illustrates that the burner release is revoked, in particular when the temperature T5 is greater than a limit value, which is 400° C., for example.
• a comparison takes place in which an actual value of the temperature T5 is compared with a target value of the temperature T5.
• the actual value of the temperature T5 is, for example, the aforementioned T5 value and/or, for example, the actual value of the temperature T5 is measured, in particular by means of the aforementioned temperature sensor, in particular at the introduction point E2 or at a downstream of the introduction point E2 and in particular upstream of component 36b in exhaust tract 26. If, for example, the comparison shows that the actual value is less than or equal to the setpoint value, a state set in block 174 in particular is retained, in particular with regard to the operation of the fuel pump and the air pump, the fuel pump being illustrated in FIG.
• the fuel pump is activated in block 188, in particular by means of an electronic computing device also referred to as a control unit, and/or in block 190, in particular by the control unit, a Activation of the air pump, in particular to the effect that the fuel pump or the air pump is changed with regard to its respective operation, in particular in such a way that the actual value is reduced until, for example, the actual value corresponds to the setpoint value or is less than the setpoint value .
• the quantity of air in the mixture is determined, in particular measured, in particular by means of an air flow measurement.
• an arrow 194 illustrates that the amount of fuel is determined, in particular measured.
• the combustion air ratio (g) is determined, in particular calculated, as a function of the determined, in particular measured, amount of air and as a function of the determined, in particular measured or else calculated, amount of fuel.
• an actual value of the combustion air ratio of the mixture is determined, in particular calculated.
• the actual air-fuel ratio is compared to a second target air-fuel ratio, the second target being, for example, 1.03.
• a block 202 illustrates that the target value of the temperature T5 is specified from or by the control unit, in particular to block 182. Alternatively or additionally, the control unit can specify or output the target value of the air/fuel ratio, in particular to block 198.
• FIG. 18 shows the swirl generation device 107 of the burner 42 in a schematic and partially sectioned perspective view.
• the air ducts LK1 and LK2 can be seen particularly well in FIG.
• the outer air duct LK2 is outwardly delimited in the radial direction of the respective swirl chamber 62 or 76 by a first wall 109 of the swirl generating device 107, which is designed in particular as a solid body, the wall 109 of which completely runs around the respective swirl chamber 62 or 76, for example in the circumferential direction, and thus the air duct LK2 completely surrounds.
• the outer air duct LK2 is delimited by a second wall 111 of the swirl generating device 107, which is designed in particular as a solid body, the wall 111 of which preferably runs completely around the respective swirl chamber 62 or 76 in the circumferential direction, and thus the air duct LK1 completely surrounds.
• the respective air duct LK1 or LK2 is at least essentially ring-shaped, and is therefore designed as a ring duct.
• the air duct LK1 is delimited by a body 113 of the swirl generating device 107 designed in particular as a solid body, with the body 113 being an air guide body, as will be explained in more detail below.
• the Swirl generating device 107 is formed in one piece, so that it is conceivable that the walls 109 and 111 are formed in one piece with one another and/or the wall 109 and/or 111 is formed in one piece with the body 113 .
• the swirl generating device 107 comprises an inner, first
• Swirl generating device 115 which includes the first, inner swirl generating elements 94.
• swirl-generating elements 94 are designed as guide vanes that are at least partially curved or arc-shaped, with the air flowing through air duct LK1, i.e. the first part of the air, being guided, deflected or deflected in this way by means of swirl-generating elements 94 is that the swirling, first flow of the first part of the air can be brought about or is brought about by means of the swirl generating elements 94, and consequently by means of the swirl generating device 115.
• the respective swirl generation element 94 is formed in one piece with the wall 109 and/or 111 and/or in one piece with the body 113 . It can be seen that the swirl-generating elements 94 are arranged in the air duct LK1, the swirl-generating elements 94 being arranged in succession and, in particular, spaced apart from one another in the circumferential direction of the respective swirl chamber 62 or 76 and thus in the circumferential direction of the swirl-generating device 107.
• the swirl generation device 107 comprises the swirl generation device 115 arranged in the air duct LK1 with the swirl generation elements 94 and an outer, second swirl generation device 117 arranged in the air duct LK2, which has the second, outer swirl generation elements 96 .
• the swirl-generating elements 96 are thus arranged in the air duct LK2, the swirl-generating elements 96 being arranged one after the other and in particular spaced apart from one another in the circumferential direction of the respective swirl chamber 62 or 76 and thus in the circumferential direction of the swirl-generating device 107 .
• the part of the air flowing through the air duct LK2 is or is deflected, deflected or guided by means of the swirl generation elements 96, ie by means of the swirl generation device 117, in such a way that the second swirling flow of the second part of the air is brought about.
• the respective swirl generation element 96 is preferably formed in one piece with the wall 109 and/or 111 and/or in one piece with the body 113 and/or in one piece with the respective swirl generation element 94, so that the swirl generation device 107 is preferably formed in one piece overall. In the case of the one in Fig.
• the respective swirl-generating element 96 is designed as a vane or air vane, which is at least partially bent or arcuate, and therefore has an arcuate course.
• the number of first, inner swirl-generating elements 94 is preferably in a range from six to eleven inclusive.
• the number of second, outer swirl-generating elements 96 is preferably in a range from eight to 14 inclusive.
• the respective air duct LK1 or LK2 itself i.e. when considering the respective air duct LK1 or LK2 without the swirl-generating elements 94 or 96, has a surface area also referred to as the passage cross section, in particular upstream of the respective swirl-generating device 115 or 117 and/or downstream of the respective swirl-generating device 115 or 117. Since the respective air duct LK1 or LK2 is ring-shaped in the present case, the respective surface area is a respective surface area of an annular surface.
• the respective swirl-generating elements 94 or 96 cover or block at least 20 percent and at most 60 percent of the surface area of the respective air duct LK1 or LK2 arranged upstream and/or downstream of the respective swirl-generating device 115 or 117, as a result of which a particularly advantageous Twist generation can be realized.
• the body 113 which is a central body, is closed and therefore cannot be traversed by air.
• the body 113 itself is rotationally symmetrical with respect to its longitudinal axis or longitudinal center axis, which coincides with the axial direction of the respective swirl chamber 62 or 76 and thus with the axial direction of the swirl generating device 107 .
• the body 113 is designed as a profile, in particular a central and/or closed profile.
• the respective twist-generating element 94 or 96 encloses the angle ⁇ , for example, with the aforementioned imaginary plane EB, which is preferably in a range from 10 degrees to 45 degrees inclusive. Provision is also preferably made for the respective swirl-generating element 94 or 96 to cause the part of the air flowing through the respective air duct LK1 or LK2 to be deflected by a deflection angle, which is preferably in a range from 70 degrees up to and including 90 degrees.
• swirl-generating device 115 in particular swirl-generating elements 94
• swirl-generating device 117 in particular swirl-generating elements 96
• the first swirling flow of the first part of the air merges first direction of rotation, in particular about the respective axial direction of the respective swirl chamber 62 or 76
• the second swirling flow of the second part of the air preferably has a second direction of rotation, in particular about the axial direction of the respective swirl chamber 62 or 76, and wherein the first direction of rotation corresponds to the second Direction of rotation is opposite or vice versa.
• Fig. 19 shows a schematic side view of a possible embodiment of ignition device 60, which is designed as a spark plug, for example. It can be seen from Fig. 19 that ignition device 60 has a plurality of radial direction in Fig. 19 is illustrated by a double arrow 226 and runs perpendicularly to the direction of longitudinal extent of ignition device 60, protruding and in the direction of longitudinal extent of base body 224, the direction of longitudinal extent of which is illustrated in Fig. 19 by a double arrow 228 and coincides overall with the direction of longitudinal extent of ignition device 60, has cooling fins 230 spaced apart from one another, by means of which the ignition device 60 can be cooled in a particularly advantageous manner.
• At least one of the cooling ribs 230 preferably the respective cooling rib 230, has through-openings 232 which, for example, can be in the form of bores and/or can be circular.
• the cooling ribs and in particular their spacing can be seen particularly well in FIG.
• Fig. 23 shows a detail of a further embodiment of the burner 42 in a schematic sectional view.
• the burner 42 has the closure element 132, which relative to the outflow openings 64 and 80 and thereby relative to the component 74 and relative to the component 82 between the in The open position shown in FIG. 12 and the closed position shown in FIG. 23 can be moved.
• the outflow opening 80 is closed by means of the closure element 132 , that is to say it is fluidically blocked, with the closure element 132 being at least partially arranged in the outflow opening 80 in the closed position.
• the closure element 132 penetrates the outflow opening 80 and protrudes into the outflow opening 64 .
• the outflow opening 80 is closed by means of the closing element 132 in the closed position, and since the outflow opening 80 is arranged downstream of the outflow opening 64 in the flow direction of the air, i.e. the flow direction of the respective part of the air, no particles and no gases can escape from the combustion chamber 58 flow through the outflow opening 80 when the closure element 132 is in its closed position, so that no particles and no gases from the combustion chamber 58 can flow through the outflow opening 64 .
• both the air supply path 54 and the fuel supply path 46 can be protected from contamination by gases and/or particles from the combustion chamber 58 .
• the closure element 132 can be moved between the closed position and the open position, for example, along an element direction that runs parallel to the axial direction of the respective swirl chamber 62 or 76 or coincides with the respective axial direction of the respective swirl chamber 62 or 76 .
• the closure element 132 can be pivoted about a pivot axis SA running through a pivot point between the closed position and the open position relative to the outflow openings 64 and 80 and thus relative to the component 74 and relative to the component 82.
• the closure element 132 is assigned an actuator 234 that can be operated electrically and/or pneumatically and/or hydraulically, for example, by means of which the closure element 232 can be moved, in particular pivoted, between the closed position and the open position.
• the actuator 234 is coupled to the closure element 132 via a lever arrangement 236, in particular in an articulated manner.
• the actuator 234 can move lever elements 238 and 240 of the lever arrangement 236 at least in a translatory manner, i.e. shift them, wherein the lever elements 238 and 240 can be coupled to the closure element 132 at least indirectly or directly in an articulated manner.
• translational movements of the lever elements 238 and 240 are converted into a pivoting movement of the closure element 132, as a result of which the closure element 132 can be pivoted between the closed position and the open position.
• the air chamber 92 is a supply chamber that is common to both swirl chambers 62 and 76 and is also referred to as an air supply chamber, which will be explained in more detail below.
• the burner 42 has a supply channel 241 through which the air and thus the parts can flow, which is around the components of the air supply path 54 .
• the air can flow through the air duct 241 in a flow direction illustrated in Fig. 7 by a double arrow 242 and opens out along the flow direction, in particular directly, into the air chamber 92 242 can be flowed through by the air and thus by both parts.
• the air flowing through the supply duct 241 along the flow direction can flow through the outlet opening 244 along the flow direction and thus flow via the outlet opening 244 along the chamber flow direction illustrated by the double arrow 242 and also simply referred to as the flow direction into the air chamber 92, so that the supply duct 241 flows directly into the air chamber 92 via the outlet opening 244 along the chamber flow direction.
• the air introduced into the air chamber 92 via the supply duct 241 can flow through the air chamber 92 along the respective axial direction of the respective swirl chamber 62 or 76 and can thus flow out of the air chamber 92 along the respective axial direction of the respective swirl chamber 62 or 76 and into the respective swirl chamber 62 or 76 flow in.
• the air chamber 92 is thus an air supply chamber common to the swirl chambers 62 and 76, through which the swirl chambers 62 and 76 can be supplied with the parts of the air. That is, the first portion of air may exit air chamber 92, enter inner swirl chamber 62, and then flow through swirl chambers 62, and the second portion of air may exit air chamber 92, enter outer swirl chamber 76, and then flow through the outer swirl chamber 76 .
• the respective part of the air flows in the aforementioned flow direction through the respective swirl chamber 62 or 76, with this respective flow direction being illustrated in FIG. 7 by an arrow 246.
• the respective flow direction, illustrated by arrow 246, in which the respective part of the air flows through the respective swirl chamber 62 or 76, runs parallel to the respective axial direction of the respective swirl chamber 62 or 76 or coincides with the respective axial direction of the respective swirl chamber 62 or 76 together.
• a first direction opposite to the direction of flow illustrated by arrow 246 and running parallel to the respective axial direction of the respective swirl chamber 62 or 76 or coinciding with the respective axial direction of the respective swirl chamber 62 or 76 is shown in Fig. 7 illustrated by arrow 248 .
• Both swirl chambers 62 and 76 are in each case at least partially, in particular at least predominantly at least more than half or in the present case completely overlapped in the first direction illustrated by arrow 248 by air chamber 92 common to swirl chambers 62 and 76.
• the air chamber 92 extends both along a second direction running parallel to the respective flow direction illustrated by the arrow 246 and illustrated in Fig.
• the burner 42 is thus a burner without an antechamber, without a central antechamber, as a result of which a particularly advantageous preparation of the mixture is possible in terms of space, weight and cost, which can be presented in terms of its particularly advantageous mixture preparation.
• FIG. 23 shows, as an exception, a further embodiment of the burner 42 in a schematic sectional view.
• the injection element 66 has an introduction element housing 254 embodied in particular as a solid body, through which the outlet opening 70 is formed or delimited, or completely.
• the exit opening 70 is formed in the insertion element housing 254 .
• the introduction element housing 254 can be flowed through by the fuel which can be made available via the outlet opening 70 by the injection element 66 , in particular can be sprayed out of the injection element 66 .
• injection element 66 has valve element 256, in the present case designed as an umbrella valve, which, in particular along a direction of movement illustrated in Fig. 23 by a double arrow 258, relative to insertion element housing 254, in particular translationally, between at least one insertion position and at least one blocking pitch is movable.
• valve element 256 In the locking position shown in FIG. 23, the outlet opening 70 is completely blocked by the valve element 256, which is closed so that the injection element 66 does not provide any fuel or the outlet opening 70 cannot be flowed through by the fuel.
• the valve element 256 gives the Outlet opening 70 free, whereby the outlet opening 70 can be flowed through by the fuel and the injection element 66 provides the fuel, in particular ejects it from the outlet opening 70 .
• the insertion element housing 254 has two housing parts 260 and 266, which are preferably designed as components which are configured separately from one another and are connected to one another.
• the outlet opening 70 is formed or delimited, in particular completely, by the housing part 266 , in particular formed in the housing part 266 .
• a support element 268 is provided on the valve element 256 and can be moved with the valve element 256 relative to the insertion housing in 254 .
• valve element 256 and the closing element 268 are designed as components that are designed separately from one another and are connected to one another.
• the injection element 66 also has a spring element 270 designed here as a mechanical spring, in particular as a compression spring.
• Spring element 270 can be or is supported, in particular along the direction of movement illustrated by double arrow 258, on insertion element housing 254, in particular on housing part 266, on the one hand, and on support element 268, in particular directly, on the other hand.
• valve element 256 By means of the spring force, the valve element 256 can be moved out of the insertion position into the blocking position and, in particular, is held in the blocking position.
• a particularly advantageous metering of the fuel also referred to as fuel metering, can thus be implemented by means of the valve element 256, which is designed here as an umbrella valve. Since the spring force that can be provided or is provided by spring element 270 acts at least indirectly, in particular directly, on valve element 56, which can be moved from the insertion position into the blocking position by means of the spring force, valve element 256 is a spring-loaded valve element, which in the present case is embodied as a spring-loaded umbrella valve .
• the injection element 66 has a valve seat 272, which in the present case is formed, in particular directly, by the insertion element housing 254, in particular by the housing part 266.
• the valve element 256 has a seat surface 274 corresponding to the valve seat 272, which is also referred to as a sealing surface and is formed here, in particular directly, by the valve in 256. In the lockdown the valve element 256 sits via its seat surface 274, in particular directly, on the corresponding valve seat 272, so that the seat surface 274 touches the corresponding valve seat 272, in particular directly.
• valve seat 272 or the sealing surface 274 is conical or truncated and thus has the shape of a cone, the longitudinal center axis of which runs parallel to the direction of movement illustrated by the double arrow 258 or with the direction of movement illustrated by the double arrow 258 coincides.
• outlet opening 70 is arranged downstream of the swirl-generating elements 96, so that the fuel can be metered, in particular metered, by means of the valve element 256 downstream of the swirl-generating devices 115 and 117 as required.
• valve element 56 When burner 42 is inactive and internal combustion engine 12 is running, valve element 56 is in the blocking position, so that no gas, such as engine exhaust gas or burner exhaust gas, in particular from combustion chamber 58, and dirt particles contained therein, cannot penetrate outlet opening 60 and thus penetrate fuel supply path 46 there could lead to deposits and, as a result, to throttling losses in the fuel metering, so that a particularly advantageous mixture preparation can also be ensured over a particularly long service life of the burner 42 .
• gas such as engine exhaust gas or burner exhaust gas, in particular from combustion chamber 58, and dirt particles contained therein
• valve element 258 double arrow 260 housing part 266 housing part 268 section element 270 spring element 272 valve seat 274 sealing surface E1 inlet point E2 inlet point V1 connection point V2 connection point T1 part T2 part T part

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Chemical Kinetics & Catalysis (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Combustion & Propulsion (AREA)
• Toxicology (AREA)
• Health & Medical Sciences (AREA)
• Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
• Processes For Solid Components From Exhaust (AREA)
• Exhaust Gas After Treatment (AREA)
• Air Supply (AREA)
• Incineration Of Waste (AREA)

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• 2021
  • 2021-03-25 DE DE102021001580.0A patent/DE102021001580A1/de active Pending
• 2022
  • 2022-03-22 EP EP22717562.7A patent/EP4314504A1/de active Pending
  • 2022-03-22 JP JP2023558679A patent/JP2024511153A/ja active Pending
  • 2022-03-22 KR KR1020237032102A patent/KR20230145602A/ko unknown
  • 2022-03-22 US US18/551,795 patent/US20240175385A1/en active Pending
  • 2022-03-22 CN CN202280024622.0A patent/CN117098909A/zh active Pending
  • 2022-03-22 WO PCT/EP2022/057444 patent/WO2022200321A1/de active Application Filing

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