EP4314504A1

EP4314504A1 - Burner for a motor vehicle, and motor vehicle comprising at least one such burner

Info

Publication number: EP4314504A1
Application number: EP22717562.7A
Authority: EP
Inventors: Herbert Zoeller
Original assignee: Mercedes Benz Group AG
Current assignee: Mercedes Benz Group AG
Priority date: 2021-03-25
Filing date: 2022-03-22
Publication date: 2024-02-07
Also published as: KR20230145602A; WO2022200321A1; US20240175385A1; DE102021001580A1; JP2024511153A; CN117098909A

Abstract

The invention relates to a burner (42) for an exhaust tract (26) through which exhaust of an internal combustion engine (12) of a motor vehicle can flow, comprising a combustion chamber (58) in which an air- and liquid fuel-containing mixture is to be ignited and thus combusted, an inner turbulence chamber (62) through which a first part of the air can flow and which produces a turbulent flow of the first part of the air, said inner turbulence chamber having a first outlet opening (64) through which the first part of the air flowing through the inner turbulence chamber (62) can flow and via which the first part of the air can be discharged out of the inner turbulence chamber (62), and an introduction element (66) through which the liquid fuel can flow and by means of which the fuel can be introduced into the inner turbulence chamber (62), the fuel discharged from the introduction element (66) also being able to flow through the first outlet opening (64) of the turbulence chamber.

Description

Burner for a motor vehicle and motor vehicle with at least one

burner

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.

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

To be able to heat up the exhaust aftertreatment device quickly and/or keep it warm, but in these operating states or operating situations the temperature of the exhaust gas is not sufficiently high.

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.

This object is achieved by a burner having the features of patent claim 1 or 2 and by a motor vehicle having the features of patent claim 12 . Advantageous configurations with expedient developments of the invention are specified in the remaining claims.

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. This means that 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. During fired operation 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, can be arranged in the exhaust tract. 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. In the case of 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. Furthermore, 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. As a result, 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. It is also conceivable for the burner exhaust gas to 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. In other words, 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. Thus, for example, 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. For example, 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. In particular, it is conceivable that 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. 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.

Furthermore, 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. It is preferably provided that 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. Furthermore, it is conceivable that the aforementioned first flow area is arranged outside of the outer swirl chamber. Expressed in other words, it is conceivable that 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. In particular, 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. Furthermore, it is preferably provided that 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 . In other words, it is preferably provided that 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. in the flow direction of the respective part of the air and in the flow direction of the fuel, downstream of the first outflow opening and since the outer swirl chamber preferably surrounds the first outflow opening, the first outflow opening is in the outer swirl chamber, for example arranged. In particular, it is conceivable that 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.

In order to generate the respective swirling flow, for example, 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. In particular, the respective swirl generator is arranged in the respective swirl chamber. In particular, 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. In particular, 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. In particular, the respective axial direction of the respective outflow opening runs perpendicular to a plane in which the respective outflow opening runs. In this case, for example, 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. Thus, for example, 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.

By effecting the respective swirling flow, 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. In particular, initially 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. In addition, 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. Overall, due to the swirling flows, 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.

In order to realize a particularly advantageous mixture preparation and to be able to heat up and/or keep warm the component particularly quickly and efficiently, it is provided according to the invention that 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. This means the following in particular: 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.

In order to realize a particularly advantageous mixture preparation and consequently to be able to heat up and/keep the component particularly efficiently and quickly, it is provided in a second aspect of the invention that 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. In the closed position, 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. As a result, 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.

In order to be able to heat up the component designed, for example, as an exhaust gas aftertreatment device or as an exhaust gas aftertreatment system particularly quickly and efficiently, especially when the exhaust gas from the internal combustion engine is only at a low temperature, one embodiment provides that 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. This means that 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. As a result, and in particular due to the targeted processing of the end edge, the taper or the atomizer lip is sharp-edged. To put it another way, the atomizer lip ends with a sharp edge, as a result of which a particularly advantageous preparation of the mixture can be achieved.

For example, 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. For this purpose, a combustion-induced bursting of vortices can be generated in particular by the swirling flows. For example, 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. It is also conceivable that 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. During operation of the burner, only air, ie only the second part of the air, flows through the outer swirl chamber, while air, ie the first part, and the liquid fuel flow through the inner swirl chamber. Advantageous mixing of the fuel with the first part of the air can thus already take place in the inner 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. Furthermore, it is conceivable that 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.

In particular, when the introduction element is designed as an injection nozzle, 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. In particular when the introduction element is designed as a lance, the passage direction runs obliquely or preferably perpendicular to the axial direction of the respective swirl chamber or the respective outflow opening. In particular, it is conceivable that 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. In particular, 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. In this case, for example, 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. In particular, it is conceivable that 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. By means of the introduction element, the fuel flowing through the outlet opening and thus exiting, in particular ejected, from the injection element is applied, in particular as a film also referred to as fuel film, to the film applicator, in particular to the inner circumferential lateral surface, or atomized onto the film applicator between the two wired air flows. Due to the centrifugal forces resulting from the swirling flow of the first part of the air, 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. In this way, therefore, the fuel is applied to the atomizer lip and promoted or transported to the end edge. According to the invention, 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. In this way, 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. On the other hand, 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.

If 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.

In order to produce particularly small droplets of fuel by means of the end edge, 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.

In a further, particularly advantageous embodiment of the invention, it is provided that 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. In other words, the swirl chambers 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. Thus, for example, 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. In other words, for example, the first swirling flow has a first sense of rotation when viewed in the axial direction of the respective swirl chamber. 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. In other words, viewed in the axial direction of the respective swirl chamber, the second swirling flow runs in a second direction of rotation opposite to the first direction of rotation. In this way, a particularly advantageous mixture preparation can be realized, so that the component can be heated up and/or kept warm quickly and efficiently, that is to say with low fuel consumption.

In order to achieve a particularly advantageous mixture preparation and thus a particularly efficient operation of the burner, it is provided in a further embodiment of the invention that 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. To put it another way, the second outflow opening has its smallest flow cross section at the end edge.

In a further, particularly advantageous embodiment of the invention, it is provided that 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. In this context, it is particularly conceivable that the above-mentioned component, which is in particular designed in one piece, can be arranged in the component. It is preferably provided that 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. It is conceivable that 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. As a result, 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. In particular, it is conceivable that 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. For this purpose, it is preferably provided that 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.

In order to avoid excessive backflow of the mixture in the combustion chamber and thus excessive eddy formation in the combustion chamber and thus to be able to implement particularly efficient operation of the burner, it is provided in a further embodiment of the invention that 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. In this context, it has proven to be particularly advantageous if 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.

Finally, it has been shown to be particularly advantageous if 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. For example, the wall areas are formed by a perforated plate or perforated disc. The burner waste gas resulting from the combustion of the mixture can be discharged from the combustion chamber via the discharge openings and thereby introduced into the exhaust tract.

Starting the burner is described below: With a cold start of the burner, there is not yet a high temperature and therefore no high air movement in the respective swirl chamber. Usually, this state does not allow ignition or at least makes ignition more difficult. In order to start the burner particularly quickly and effectively even when the internal combustion engine is running and/or in cold ambient conditions, 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. during a predetermined or predeterminable period of time, which can for example be in a range of two seconds up to and including six seconds, 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. Only then, that is to say only after the time period has elapsed, is the ignition device switched on, that is to say activated, and an actual air and fuel supply started. In other words, it is preferably provided, for example, that the swirl chambers are not supplied with air during the period of time. Due to this pre-storage, a particularly rich mixture is formed which, despite large droplets, also offers a large fuel surface suitable for ignition due to a particularly high mass. Advantageous cooling of the ignition device designed as a spark plug, for example, 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. Alternatively or additionally, 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. As a result, the use of a check valve can be avoided and a particularly small dead volume can be created. In particular, it is conceivable that 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. In other words, 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. Alternatively or additionally, 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. As a result, particularly high gas temperatures of, for example, at least or greater than 600 degrees Celsius can be achieved, so that, for example, the component designed in particular as a particle filter can be heated to a particularly high temperature of, for example, at least or greater than 600 degrees Celsius. 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. In addition, the motor vehicle comprises a or the previously mentioned exhaust tract and at least one burner according to the first aspect of the invention. Advantages and advantageous configurations of the first aspect of the invention are to be regarded as advantages and advantageous configurations of the second aspect of the invention and vice versa.

Further advantages, features and details of the invention result from the following description of preferred exemplary embodiments and from the drawing. The features and combinations of features mentioned above in the description and the features and combinations of features mentioned below in the description of the figures and/or shown alone in the figures can be used not only in the combination specified in each case, but also in other combinations or on their own, without going beyond the scope of the leave invention.

The drawing shows in:

Fig. 1 is a schematic representation of a drive device of a

Motor vehicle with an internal combustion engine, an exhaust system and a burner;

Fig. 2 is a schematic longitudinal sectional view of a first embodiment of the

burners;

3 shows a detail of a schematic longitudinal sectional view of the burner according to the first embodiment;

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;

7 is a schematic longitudinal sectional view of the burner according to the third embodiment;

8 shows a detail of a schematic and partially sectioned perspective view of a swirl generating device of the burner;

9 shows a schematic perspective view of the swirl generating device;

10 shows a schematic front view of a closure device;

11 shows a detail of a schematic longitudinal sectional view of a fourth embodiment of the burner;

12 shows a detail of a schematic sectional view of a fifth embodiment of the burner;

13 shows a detail of a schematic longitudinal sectional view of a sixth embodiment of the burner;

14 shows a detail of a schematic longitudinal sectional view of a seventh 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; and

17 shows a schematic sectional view of a fuel pump for delivering a fuel to the burner.

18 shows a schematic and sectional perspective view of a swirl generating device of the burner; 19 shows a schematic side view of an ignition device of the burner;

20 is a schematic front view of the ignition device;

21 shows a detail of a schematic longitudinal sectional view of the ignition device;

22 shows a detail of a schematic sectional view of the burner according to an eighth embodiment; and

23 shows a detail of a schematic sectional view of a ninth embodiment of the burner.

Elements that are the same or have the same function are provided with the same reference symbols in the figures.

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. This means that the motor vehicle designed as a land vehicle has the drive device 10 in its fully manufactured state and can be driven by means of the drive device 10 . 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. Furthermore, 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 . For this purpose, within a respective working cycle of the internal combustion engine 12, a fuel, in particular a liquid fuel, is introduced into the respective cylinder 16, in particular injected directly. Internal combustion engine 12 can be designed as a diesel engine, so that the fuel is preferably diesel fuel. In this case, 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 . 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. In particular, 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). Furthermore, the component 36 can be a nitrogen oxide storage catalytic converter (NSK). 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.

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. For example, the structure forms or defines an engine room in which the internal combustion engine 12 is arranged. In this case, for example, 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. Here, for example, 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). In particular, 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. It can be seen from FIG. 1 that 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 . In this case, 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. In the exemplary embodiment shown in FIG. 1, the entry point E2 is arranged upstream of the components 36b, c and d and downstream of the component 36a. In other words, in the exemplary embodiment shown in FIG. 1, the burner 42 is arranged upstream of the components 36b, c, d and downstream of the component 36a. Alternatively, it is conceivable that 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. In the exemplary embodiment shown in FIG. 1 , 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. For this purpose, 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 . In particular, 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 . In this case, 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.

Furthermore, 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. This means that the air supply path 54 can be flowed through by the air from which the mixture is formed. 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 . For example, 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 .

It can be seen that the air supply path 54 is fluidically connected to the intake tract 24 at a second connection point V2. Thus, at least part of the fresh air flowing through the intake tract 24 can be branched off from the intake tract 24 at the connection point V2 and introduced into the air supply path 54 . 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 . In this case, 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. In this case, 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. For this purpose, 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. By means of 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. This means in particular that the first part of the air flows in a swirling manner through at least a first partial region of the swirl chamber 62 and/or flows out of the swirling chamber 62 in a swirling manner and/or flows in a swirling manner in the combustion chamber 58 . 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 . This means that the first part of the air can flow out of the inner swirl chamber 62 via the first outflow opening 64 . Furthermore, 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.

In the first embodiment, 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. It can be seen from FIG. 2 that in the first embodiment 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. In other words, 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 . For example, 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. In addition, for example, 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. It can also be seen from FIG. 2 that 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 . As a result, 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. In particular, it is preferably provided that the parts of the air have their twisted flows in the combustion chamber 58 and therefore run in a twisted manner in the combustion chamber 58 . 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 . This means in particular that 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. In the direction of flow of the parts of the air, 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. In particular, 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.

It can be seen that 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. In the radial direction of the respective swirl chamber 62 or 76 towards the outside, 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. In this 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.

In order to be able to heat at least component 36b particularly efficiently and/or keep it warm, it is provided that—as can be seen particularly well from FIG ends in the direction of flow of the fuel flowing through the first outflow opening 64 at a specifically, in particular mechanically, machined and thus or 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 Fuel up to the end edge K and ends at the end edge K. For example, the end edge K is ground and/or turned and thereby machined in a targeted manner. For example, 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. It can be seen in particular that 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.

Furthermore, 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 . Starting from the flow opening 90 and in particular starting from the outflow opening 80 and starting from the component 82, in particular starting from its end, 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. As a result, for example, 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 .

It can also be seen from FIG. 2 that, for example, 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.

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 , and 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, and 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 . In particular, 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. For example, 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.

As can be seen from FIGS. 2 to 4, the outflow openings 64 and 80, also referred to as nozzles, are both aligned in the axial direction. This means that the partial mixture flows from the inner swirl chamber 62 into the combustion chamber 58 at least essentially in the axial direction. Furthermore, 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.

It is preferably provided that the nozzles, and therefore the outflow openings 64 and 80, have the following size or area ratios: 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. In other words, provision is preferably made for the air duct LK1 to have a first annular surface and the air duct LK2 to have a second annular surface, with the annular surfaces preferably being of the same size. Fig. 5 shows a schematic sectional view of a second embodiment of the burner 42. In the first embodiment, it is provided, for example, that 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 . In the second embodiment, it is provided that the anti-recirculation plate 88 is formed in one piece with the component 82 . In the second embodiment, too, 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. In the third embodiment, 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 . In the present case, 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. As can be seen in FIG. 2, 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.

In contrast to this, in the third embodiment 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. Thus, in 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. Instead of a reduced outlet opening, it is advantageous to use 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. For example instead 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 . Also illustrated in Figure 7 is a swirling flow of the mixture and designated 106, the swirling flow 106 of the mixture in the combustion chamber 58 resulting from the respective swirling flows of the portions of the air. The swirling flows of the parts of the air and thus the swirling flow 106 of the mixture is realized in particular by the swirl generators 94 and 96 and by the tangential air supply, in particular via the air supply path 54 . 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, illustrated by the arrows 104, 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. In particular, 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 . the

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. Alternatively or additionally, 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. Thus, 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. In particular, it is conceivable that the respective air guide vane encloses a respective angle α 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. In order to realize a particularly advantageous mixture preparation, the air guide vanes of the inner and outer swirl chambers 62 and 76 can be designed in opposite directions. In other words, it is conceivable that 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. In other words, injection element 66 protrudes through through-opening 108 into inner swirl chamber 62.

10 shows, in a schematic front view, a closure device 110, which in the present case is designed as an iris diaphragm or in the manner of an iris diaphragm. If 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. It is also conceivable that 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. variably set, 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 . Alternatively or additionally, the outflow opening 80 can be closed, for example, by means of a first closure device 110 . Alternatively or additionally, 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.

In particular, it is conceivable that 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. Thus, instead of a bore in a flat closure plate, 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.

In particular, 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. In the fourth embodiment, 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. It can also be seen that 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 . In the first embodiment shown in FIG. 2, 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. In the third embodiment shown in Fig. 7, however, 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. continuous, discharge opening 102 flows into the plurality of through-flow openings 98, spaced apart and separate from one another, which in the perforated disc 100 are formed, divided or divided. 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. It can be seen that 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. For this purpose, 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. In other words, 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. Since the burner exhaust gas or the flame 44 flows out of the combustion chamber 58 via the discharge opening 102, 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. Preferably, 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.

The fact that at least the longitudinal regions of chamber parts 120 and 122 are arranged one inside the other and are spaced apart from one another in the radial direction of combustion chamber 58 to form intermediate space 124, intermediate space 124 being filled with air, for example, and thus being formed as an air gap, means that 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. Thus, the combustor 58 is air gap insulated. In the following, reference is made in particular to the outer diameter Da of the film applicator, shown in Fig completely, are formed by the film layer, that is, by the component 74. With reference to FIG. 11 and the outer diameter Da, 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.

Instead of 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. With regard to the exhaust gas of the internal combustion engine 12, also referred to as engine exhaust gas, it can be advantageous to use a deflection element, in particular a deflection element and/or a perforated element, in particular a perforated plate, with 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. For example, so that the engine exhaust does not unduly negatively affect and destabilize the flame 44 in the combustion chamber 58, it is advantageous to provide a deflection element, such as a baffle, in front of the combustion chamber 58, i.e. upstream of the combustion chamber 58, so that the engine exhaust does not or only can enter the combustion chamber 58 slightly, in particular counter to the flow direction along which the flame 44 or the burner exhaust gas flows out of the combustion chamber 58 into the exhaust gas tract 26 . Provision is therefore preferably made for the deflection element to be 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.

Furthermore, it is advantageous, as described above, for the closure device 110 or another closure device to be arranged at the outlet of the combustion chamber 58 . This means in particular the following: 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°. In the fourth embodiment, the cone is designed as a fixed geometry, so that the cone, ie the cone angle, is fixed, ie cannot be varied. However, it is conceivable to design the cone to be variable, for example in an aircraft engine, in particular with regard to its cone angle, in particular using individual segments which can be folded, for example like a thrust nozzle in an aircraft engine, i.e. in particular pivoted relative to the chamber part 122. whereby the cone or the cone angle is adjustable, i.e. variable. Alternatively or additionally, it can be provided that 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 . By shifting the outlet cone in the axial direction of the combustion chamber 58 relative to the chamber element 116, 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. It can be seen that 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 .

12 shows a detail of a fifth embodiment of the burner 42 in a schematic sectional view. In particular, in FIG. 12 part of the component 74 and part of the component 82 can be seen, in particular as in FIG. 3. It is advantageous if the burner 42 is not operated , 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 . For this purpose, it is conceivable that, for example, 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. In the closed position, 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. As a result, no engine exhaust gas from the exhaust tract 26 can flow through the outflow openings 64 and 80 . In the open position, 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. In particular, it can be seen that 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. It is preferably provided that an insulating element formed separately from chamber element 116 (air-gap-insulated pipe) 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. As previously described, 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. As an alternative or in addition, 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. In order to be able to use the thermal energy of the burner 42 advantageously, 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. However, in order to ensure advantageous mixing of the engine exhaust gas with the burner exhaust gas, 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. In particular, 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. It has been shown to be particularly advantageous if 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. The feature that 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. Alternatively or additionally, 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. In particular when component 36b is a catalytic converter, in particular the aforementioned SCR catalytic converter, component 36b has a substrate. It is therefore preferably provided that 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.

It can be seen from Fig. 2 that ignition device 60, embodied, for example, as a spark plug, glow plug or glow plug, has a thread 134, embodied in particular as an external thread, by means of which ignition device 60 is screwed at least indirectly to chamber element 116 and is thereby held on chamber element 116. In order to achieve sufficient cooling of the ignition device 60, that is to say an advantageous heat dissipation from the ignition device 60, it is advantageous if 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. For example, the cooling fins have a thickness which is in a range from 2 to 4 mm inclusive. Furthermore, it is conceivable that the respective cooling rib has a diameter of 20 to 80 mm, in particular an outer diameter. In addition, it is advantageous if 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.

In order to support the effecting or generating of the swirling flows of the parts of the air in the swirl chambers 62 and 76, 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. In other words, it is advantageous if the air or the respective part of the air flows tangentially into the respective swirl chamber 62 or 76 . As a result, 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.

In order to supply the combustor 42 with the fuel, 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. It is advantageous to operate the burner 42 in a lambda-controlled manner so that, for example, the mixture has a combustion air ratio (g) of at least essentially 1.0. In other words, it is preferably provided that the burner is operated stoichiometrically, which means that the mixture is a stoichiometric mixture. In other words, it is advantageously provided that 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. It is therefore advantageous if a first quantity of the air in the mixture, also referred to as combustion air, and 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.

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. In particular, 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.

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. In other words, 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. In order to bring the fuel onto or against the film wall in a particularly advantageous manner, 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. For this purpose, it is preferably provided if 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. In other words, 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. In this way, a particularly advantageous atomization of the fuel flowing through the outlet openings 70 can be realized. In particular, 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. Since 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. As a result, 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. In the seventh embodiment, the injection element 66 is formed as a lance, for example. It can be seen that 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. In order to produce a fuel film that is as thin and uniform as possible on the film applicator, i.e. on the inner peripheral lateral surface 86, 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. For example, it is preferably provided that the angle β 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. It is also provided that 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. In the exemplary embodiment shown in FIG. 15, the injection element 66 is in the form of an injection nozzle formed, as used in fuel oil burners. In the exemplary embodiment shown in FIG. 15, 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. This means that 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 . In other words, according to FIG. 15, 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.

16 shows a block diagram to illustrate operation, in particular regulation of burner 42. 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. For example, 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. As a result of the burner release, the ignition device 60 is switched on at a block 170, ie activated. In 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. Also, for example at block 172, the air pump is activated and the fuel pump is activated. Then, for example, at a block 174, the air/fuel ratio of the mixture is adjusted to 1.03 with the fuel pump operating at a low frequency. At a block 176, for example, 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.

In a block 182, 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. 16 by a block 184 and the air pump being illustrated by a block 186 . If, for example, the actual value is greater than the setpoint value, 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 .

In a block 192, the quantity of air in the mixture is determined, in particular measured, in particular by means of an air flow measurement. In addition, an arrow 194 illustrates that the amount of fuel is determined, in particular measured. In a block 196, 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. In particular, in block 196 an actual value of the combustion air ratio of the mixture is determined, in particular calculated. At a block 198, the actual air-fuel ratio is compared to a second target air-fuel ratio, the second target being, for example, 1.03. Does the actual value of the combustion air ratio correspond to the target value of the combustion air ratio, or does the actual value of the If the combustion air ratio only deviates from the setpoint value of the combustion air ratio in such a way that a difference between the actual value of the combustion air ratio and the setpoint value of the combustion air ratio is greater than or equal to a limit, in particular in terms of amount, then current operation of burner 42, in particular the fuel pump and the air pump. However, if the actual value of the combustion air ratio deviates excessively from the setpoint value of the combustion air ratio, then, as shown in particular by arrow 200, the air pump and/or the fuel pump, for example, are changed with regard to their respective operation, in particular by actuating the fuel pump or Air pump, in particular such that the difference between the actual value of the combustion air ratio and the target value of the combustion air ratio is at least reduced or eliminated. Finally, 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. Inward in the radial direction of the respective swirl chamber 62 or 76, 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. In particular, it can be seen that the respective air duct LK1 or LK2 is at least essentially ring-shaped, and is therefore designed as a ring duct. In the radial direction of the respective swirl chamber 62 or 76 inwards, 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. For example, 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. In the exemplary embodiment shown in Fig. 18, too, 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. In particular, it is conceivable that 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. 18 shown embodiment, 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. It is preferably provided that 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. In addition, 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 . In particular, in the present case 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 β, 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. In order to achieve a particularly advantageous mixture formation, provision is preferably made for swirl-generating device 115, in particular swirl-generating elements 94, to run or be designed in the opposite direction to swirl-generating device 117, in particular swirl-generating elements 96, so that 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, wherein 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.

From Fig. 20 it can be seen that 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. In the closed position, 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. In the exemplary embodiment shown in FIG. 23 , the closure element 132 penetrates the outflow opening 80 and protrudes into the outflow opening 64 . Since 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 . As a result, 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 .

According to FIG. 12, 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 . According to FIG. 22, 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. For this purpose, the actuator 234 is coupled to the closure element 132 via a lever arrangement 236, in particular in an articulated manner. For example, 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. As a result, for example, 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.

In particular, it can be seen that 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. It can be seen from FIG. 7 that 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. 7 by a double arrow 250 and along a direction perpendicular to the respective flow direction illustrated by the arrow 246 and thus perpendicular to the second direction, third direction illustrated in FIG. 7 by a double arrow 252 without interruption, that is to say uninterrupted. 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.

Finally, FIG. 23 shows, as an exception, a further embodiment of the burner 42 in a schematic sectional view. In the further embodiment according to FIG is. In this case, 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. In other words, for example, the exit opening 70 is formed in the insertion element housing 254 . In this case, 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 .

In the embodiment shown in Fig. 23, 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. 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. In the loading position, however, 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 .

In the exemplary embodiment shown in FIG. 23, 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. In the present case, 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 .

For example, the 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. By moving the valve element 256 from the blocking position into the insertion position, the spring element 270 is tensioned, in particular compressed, as a result of which the spring element 270 provides a spring force at least in the insertion position. 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. In the exemplary embodiment shown in Fig. 23, the 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.

In combination with FIG. 14, for example, it can be seen that the 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.

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 .

Reference List

10 drive device

12 internal combustion engine

14 engine block

16 cylinders

18 tanks

20 low pressure pump

22 high pressure pump

24 intake tract

26 exhaust tract

28 exhaust gas turbocharger

30 compressors

32 turbines

34 wave

36a-d component

38 dosing device

40 mixing chamber

42 burners

44 flame

46 fuel supply path

48 fuel line

50 valve member

52 electronic computing device

54 air supply path

55 valve element

56 pump 58 combustion chamber 60 ignition device 62 inner swirl chamber 64 first outflow opening 66 injection element 68 channel 70 outlet opening 72 fuel jet 74 component outer swirl chamber partition wall second outflow opening

component

Atomizer lip inner peripheral lateral surface

anti-recirculation plate

F ow opening

supply chamber

swirl generator

F ow opening

perforated disc

discharge opening

Arrow swirling flow swirl generating device passage opening wall

locking device

wall

closure element

Body

opening cross-section

twist generating device

chamber element

Swirl generating device on the inner peripheral lateral surface

chamber part

space dashed line

exit cone

double arrow

closure element

thread

electrode fuel pump

Pistons

Valve

Feather

Bullet

face

lateral surface dashed line

tube

venturi nozzle

head

twist slot

vertebrae

secondary filter

primary filter

block

Arrow

block

Arrow

block

Arrow

block

Arrow

block

body

double arrow 228 double arrow

230 cooling fin

232 through hole

234 actuator

236 lever arrangement

238 lever element

240 lever element

241 feed channel

242 double arrow 244 outlet opening 246 arrow 248 arrow 250 double arrow 252 double arrow 254 insertion element housing 256 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

K trailing edge

LK1 air duct

LK2 air duct

K1 circular ring area

K2 circular ring area

TB part

The outside diameter Because outside diameter

W wall area

R radius a angle

11 length d1 inner diameter d2 inner diameter

L1 length range ß angle

EB level

LW length range

TBK section

LBE length range

Claims

patent claims

1. Burner (42) for an exhaust gas of an internal combustion engine (12) of a

Motor vehicle through-flow exhaust system (26), with:

- a combustion chamber (58) in which a mixture comprising air and a liquid fuel is to be ignited and thereby burned,

- an inner swirl chamber (62) 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 (64) through which the first part of the air flowing through the inner swirl chamber (62) can flow, via which the first part of the air can be discharged from the inner swirl chamber (62),

- an introduction element (66) through which the liquid fuel can flow, by means of which the fuel can be introduced into the inner swirl chamber (62), the first outflow opening (64) of which can also be flowed through by the fuel discharged from the introduction element (66), and

- an outer swirl chamber (76), which surrounds at least a length of the inner swirl chamber (62) in the circumferential direction of the inner swirl chamber (62), through which a second part of the air can flow and which causes a swirling flow of the second part of the air, which second part of the air flowing through the outer swirl chamber (76), of the fuel flowing through the first outflow opening (64) and of the first part of the air flowing through the inner swirl chamber (62) and the first outflow opening (64) through which the second outflow opening (80) can flow , via which the parts of the air and the fuel can be introduced into the combustion chamber (58), and

- A through-flow of the air supply channel (240), which in a swirl chambers (62, 76) common air chamber (92) opens, through which the along a respective flow direction (246) of the parts of the swirl chambers (62, 76) through which air can flow in a direction (248) opposite the respective flow direction (246), the air chamber (92) extending both along a parallel to the respective first direction (250) running in the respective flow direction (246) and without interruption along a second direction (252) running perpendicular to the respective flow direction (246), and

- the combustion chamber (58) has a plurality of through-flow openings (98), which are spaced apart from one another and wall regions (W) formed by respective solid bodies are separated from one another, in particular in the radial direction of the respective swirl chamber (62) or (76), with the through-flow openings (98) Burner exhaust gas (44) can be removed from the combustion chamber (58) and introduced into the exhaust tract (26).

2. Burner (42) for one of the exhaust gas of an internal combustion engine (12).

Motor vehicle through-flow exhaust system (26), with:

- an outer swirl chamber (76), which surrounds at least a length of the inner swirl chamber (62) in the circumferential direction of the inner swirl chamber (62), through which a second part of the air can flow and which causes a swirling flow of the second part of the air, which second part of the air flowing through the outer swirl chamber (76), of the fuel flowing through the first outflow opening (64) and of the fuel flowing through the inner swirl chamber (62) and the first outflow opening (64) first part of the air flowing through, second outflow opening (80) through which the parts of the air and the fuel can be introduced into the combustion chamber (58), and - at least one closure element (132) which is positioned relative to the

outflow openings (64, 80) between at least one closed position fluidically blocking at least one of the outflow openings (64, 80) and at least one open position releasing the at least one outflow opening (64, 80).

3. Burner (42) according to claim 1 or 2, characterized in that the first outflow opening (64) ends in the flow direction (246) of the first part of the air flowing through the first outflow opening (64) at a specifically machined end edge (K), which is formed by an atomizer lip (84) which tapers in the flow direction (246) of the first part of the air flowing through the first outflow opening (64) up to the end edge (K) and ends at the end edge (K).

4. Burner (42) according to claim 3, characterized in that the end edge (K) is machined in a targeted manner.

5. Burner (42) according to claim 4, characterized in that the end edge (K) is turned and/or ground and thereby machined in a targeted manner.

6. Burner (42) according to one of the preceding claims, characterized in that the swirling flow of the first part is in the opposite direction to the swirling flow of the second part.

7. Burner (42) according to one of the preceding claims, characterized in that the smallest flow cross-section through which the second part of the air can flow of the second outflow opening (80) in the radial direction of the respective outflow opening (64, 80) inwards is completely delimited by the end edge (K).

8. Burner (42) according to claim 1, characterized in that the wall regions (W) are formed in one piece with one another and are formed by a one-piece perforated disk (100).

9. Burner (42) according to Claim 8, characterized in that the flow openings (98) are distributed uniformly in a circumferential direction running around an axial direction of the respective swirl chamber (62) or (76) and are arranged along a circle whose center point is on the respective axial direction of the respective swirl chamber (62) or (76) is arranged.

10. Burner (42) according to claim 8 or 9, characterized in that

Number of flow openings (98) is in a range from three to nine inclusive

11. Burner (42) according to claim 8 or 9, characterized in that eight flow openings (98) are provided.

12. Motor vehicle with a burner (42) according to any one of the preceding claims.