DE102021001581B4 - Burner for a motor vehicle and motor vehicle - Google Patents

Abstract

Burner (42) for an exhaust gas tract (26) through which exhaust gas from an internal combustion engine (12) of a motor vehicle can flow, with: - a combustion chamber (58), in which a mixture comprising air and a liquid fuel is to be ignited and thereby burned, - one an inner swirl chamber (62) through which a first part of the air can flow and which causes a swirl-shaped 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 removed from the inner swirl chamber (62); the outlet opening (70) can be introduced into the inner swirl chamber (62), the first outflow opening (64) of which also contains the fuel that has exited the insertion element (66, 204) via the outlet opening (70) and is thereby introduced into the inner swirl chamber (62). can be flowed through, and - an outer swirl chamber (76) which surrounds at least one length region 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 swirl-shaped flow of the second part of the air a second outflow opening which can be flowed through by the second part of the air flowing through the outer swirl chamber (76), by the fuel flowing through the first outflow opening (64) and by the first part of the air flowing through the inner swirl chamber (62) and the first outflow opening (64). (80), via which the parts of the air and the fuel can be introduced into the combustion chamber (58), the introduction element (66) being designed as a lance having a longitudinal direction of extension, in the outer peripheral surface (148) of which runs in the circumferential direction of the lance ) the outlet opening (70) is formed, the passage direction of which, along which the fuel can flow through the outlet opening (70), runs obliquely or perpendicularly to the longitudinal direction.

Description

The invention relates to a burner for an exhaust tract through which exhaust gas from an internal combustion engine of a motor vehicle can flow. The invention further relates to a motor vehicle with such a 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 known as an internal combustion engine, can flow through the respective exhaust gas tract. In some operating states or operating situations of the respective internal combustion engine, a high temperature of the exhaust gas may be desirable in order, for example, to be able to quickly heat up and/or keep warm an exhaust gas aftertreatment device arranged in the exhaust tract, although in these operating states or operating situations the temperature of the exhaust gas is only insufficiently high.

The DE 37 29 861 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 swirl-shaped flow of the first part of the air, which has a first outflow opening through which the first part of the air can be removed from the inner swirl chamber. The liquid fuel can be introduced into the inner swirl chamber using an introduction element. A second swirl chamber surrounds the inner swirl chamber in the circumferential direction at least in a length region. A second part of the air flows through the second swirl chamber and causes a swirl-shaped flow of the second part of the air. The second swirl chamber has a second outflow opening through 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 object of the present invention is therefore to create a burner for an exhaust tract of a motor vehicle and a motor vehicle with such a burner, so that at least one component of the exhaust tract can be heated particularly quickly and efficiently.

This object is achieved by a burner with the features of patent claim 1 and by a motor vehicle with the features of patent claim 5. Advantageous embodiments with useful developments of the invention are specified in the remaining claims.

A burner is provided for an exhaust gas tract through which exhaust gas from an internal combustion engine of a motor vehicle, also known as an internal combustion engine, can flow. This means that the motor vehicle, which can preferably be designed as a motor vehicle and most preferably as a passenger car, has the internal combustion engine and the exhaust tract in its fully manufactured state and can be driven by 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 from the internal combustion engine. The exhaust gas can flow out of the respective combustion chamber and flow 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 aftertreating the exhaust gas, can be arranged in the exhaust gas tract. The exhaust gas aftertreatment element is, for example, a catalytic converter, in particular an SCR catalytic converter, whereby, for example, a selective catalytic reduction (SCR) can be catalytically supported and/or brought about by means of the SCR catalytic converter. During the selective catalytic reduction, any nitrogen oxides contained in the exhaust gas are at least partially removed from the exhaust gas by reacting the nitrogen oxides 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 comprise 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 produces exhaust gas from the burner, in particular from the combustion chamber, the exhaust gas of which is also referred to as burner exhaust gas. The burner exhaust gas can, for example, flow out of the burner chamber and flow into the exhaust tract, in particular at an introduction point which is arranged, for example, upstream of the component in the flow direction of the exhaust gas of the internal combustion engine flowing through the exhaust tract. As a result, the burner exhaust gas can flow through the component, for example, whereby the component nente heated, that is, can be heated. Furthermore, it is conceivable that the burner exhaust gas flows out of the burner chamber and flows into the exhaust gas tract and is thereby mixed with the exhaust gas of the internal combustion engine flowing through the exhaust gas tract and/or with a gas flowing through the exhaust gas tract, whereby the exhaust gas of the internal combustion engine or the gas is heated. In other words, a particularly high temperature of the exhaust gas of the internal combustion engine or of the gas, also referred to as exhaust gas temperature, can be achieved in this way. Due to the high exhaust gas temperature, the component can be heated because the exhaust gas or gas flows through the component. Thus, for example, the exhaust gas from the combustion chamber is introduced into the exhaust tract at the aforementioned introduction point and thus into the exhaust gas or gas flowing through the exhaust tract. For example, an ignition device, in particular an electrically operable one, is arranged in the combustion chamber, by means of which, for example, in particular in the combustion chamber and/or using electrical energy or current, at least one ignition spark for igniting the mixture can be provided, that is to say can be generated. The ignition device is, for example, a glow plug or 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 swirl-shaped flow of the first part of the air, which is therefore preferably arranged upstream of the combustion chamber in the flow direction of the first part of the air flowing through the inner swirl chamber. The inner swirl chamber has, in particular, 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 removed 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 swirl-shaped flow of the first part of the air flowing through the inner swirl chamber is to be understood in particular as meaning that the first part of the air flows in a swirl-shaped manner in the swirl chamber, and therefore flows in a swirl-shaped manner through at least a length region of the swirl chamber and/or the first part of the air only has its swirl-shaped flow at least in a first flow region arranged downstream of the inner swirl chamber and outside the inner swirl chamber, 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 in a swirl shape via the first outflow opening and/or flows in a swirl shape into the combustion chamber, so that it is very preferably provided that the first part of the air flows in a swirl shape at least in the combustion chamber having.

The burner also has an insertion element which has at least or exactly one outlet opening through which the liquid fuel can flow. The outlet opening is arranged in the inner swirl chamber, so that the introduction element or a channel of the introduction element through which the liquid fuel can flow opens into the inner swirl chamber via the outlet opening. By means of the introduction element, the fuel flowing through the outlet opening can be introduced into the inner swirl chamber via the outlet opening, in particular directly, so that the first outflow opening is also supplied by the liquid fuel which has emerged from the introduction element via the outlet opening and is thereby introduced, in particular directly, into the inner swirl chamber can be flowed 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 thereby flow out of the inner swirl chamber.

Furthermore, the burner comprises an outer swirl chamber, which surrounds at least a length 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 circumferentially. The circumferential direction of the inner swirl chamber runs, for example, around the aforementioned first flow direction, which, for example, coincides 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 flow direction of the first part flowing through the first outflow opening and thus in the flow direction of the fuel flowing through the first outflow opening, therefore in the axial direction of the inner swirl chamber and thus 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 cause a swirl-shaped 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, and therefore flows in a swirling manner through at least a partial or length region of the outer swirl chamber, and/or the second part of the air points in a flow direction of the air flowing through the outer swirl chamber, second part of the air arranged downstream of the outer swirl chamber, second flow region, which, for example, coincides with the aforementioned first flow region, has its swirl-shaped flow, the second flow region, for example can be arranged outside the outer swirl chamber and, for example, inside the combustion chamber. Furthermore, it is conceivable that the aforementioned first flow region is arranged outside the outer swirl chamber. Expressed again in other words, it is conceivable that the second part of the air flows out of the outer swirl chamber in a swirl shape and/or flows into the combustion chamber in a swirl shape, so that it is preferably provided that the second part of the air has its swirl shape at least in the combustion chamber .

The outer swirl chamber has, in particular precisely, a 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, for example, in the flow direction of the parts and of the fuel, arranged downstream of the first outflow opening, through which the second part of the air can be removed 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, for example the second flow direction running parallel to the first flow direction or coinciding with the first flow direction. Furthermore, it is preferably provided that the second flow direction runs in the axial direction of the outer swirl chamber, and therefore coincides 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 . Expressed again 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. For example, since the second outflow opening is arranged downstream of the first outflow opening along the respective flow direction, that is in the flow direction of the respective part of the air and in the flow direction of the fuel, and since the outer swirl chamber preferably surrounds the first outflow opening, the first outflow opening is, for example, in the outer swirl chamber 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 swirl-shaped flow, for example, the respective swirl chamber can have at least one or more swirl generators, by means of which the respective swirl-shaped 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, that is, 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 swirl-shaped flow is to be understood as meaning a flow which extends in a swirl-shaped or at least essentially helical or helical shape 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. 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, whose cross section through which the respective part of the air can flow does not necessarily have to taper along the respective flow direction. Thus, for example, the second outflow opening is also referred to as an outer nozzle or second nozzle, with the first outflow opening, for example, also being referred to as an inner nozzle or first nozzle.

By effecting the respective, swirl-shaped flow, the air can be mixed with the liquid fuel particularly advantageously, in particular over only a small mixing path, in particular in the combustion chamber, so that a particularly advantageous mixture preparation is realized, that is to say the mixture can be formed particularly advantageously. In particular, the fuel can initially be mixed particularly well with the first part of the air, in particular in the inner swirl chamber, in particular due to the swirl-shaped flow of the first part, in particular in the inner swirl chamber. In addition, the fuel and, for example, the first part already mixed with the fuel can be particularly advantageously mixed 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, swirl-shaped flow having. Overall, due to the swirl-shaped flows, the parts of the air and the fuel can be mixed particularly advantageously, so that an advantageous mixture preparation can be achieved.

In order to be able to heat up and/or keep warm the component designed, for example, as an exhaust gas aftertreatment device or as an exhaust gas aftertreatment system, particularly quickly and efficiently, it is provided that the introduction element is designed to discharge the liquid fuel from the introduction element via the outlet opening in a drop shape and thus in the manner of a To provide a pipette and thereby introduce it into the inner swirl chamber in a drop shape. In other words, the introduction element is designed to pipette the fuel from the introduction element via the outlet opening, in particular directly, into the inner swirl chamber, that is to say to provide the fuel drop by drop like a pipette, that is to say drop by drop and thereby into the inner swirl chamber, in particular drop by drop, that is, to introduce drop by drop. This is to be understood in particular as meaning that the introduction element does not provide the fuel flowing through the outlet opening to form a jet, that is, it does not eject it to form a jet and thereby inject it into the swirl chamber, but rather the introduction element pipettes the fuel, thus making the fuel drop-shaped and thus Ready drop by drop. This means in particular that during operation of the burner, the fuel drips out of the introduction element drop by drop via the outlet opening and thereby drips into the inner swirl chamber and, for example, drips against an inner circumferential lateral surface, in particular a component of the burner, for example the inner circumferential lateral surface of the component directly limits the inner swirl chamber in the radial direction of the inner swirl chamber. The fuel can thus be applied or applied, in particular directly, in drop form to the inner circumferential surface, also referred to as a wall. The swirl-shaped flow of the first part of the air, which forms a twisted air flow or is formed by a wired air flow, distributes the drops of fuel provided by the introduction element via the outlet opening on the inner circumferential surface, whereupon the drops flow downstream at the first outflow opening, which is also the first nozzle is called, atomize. This eliminates the need for an injection element or a nozzle with small holes for the fuel. With regard to such small holes, there is a risk of coking of the holes, which can now be avoided. Nevertheless, a particularly advantageous mixture preparation can be realized so that the component can be heated and/or heated quickly and efficiently.

For example, the outlet opening has a passage direction along which the fuel flows through the outlet opening and can in particular flow into the inner swirl chamber. It is preferably provided that the direction of passage runs obliquely or perpendicularly to the axial direction of the respective swirl chamber and/or to the longitudinal direction of the insertion element. As a result, the fuel can be particularly advantageously dripped onto the inner circumferential surface in drop form and thus drop by drop and thus applied, so that a particularly advantageous mixture preparation can be achieved.

The introduction element can have at least one further outlet opening through which the liquid fuel can flow and arranged in the inner swirl chamber and can be designed to provide the fuel from the introduction element via the further outlet opening in a drop shape and thus drop by drop and thereby introduce it in a drop shape into the inner swirl chamber. The previous and following statements regarding the first outlet opening can therefore easily be transferred to the further outlet opening and vice versa. In other words, it is preferably provided that the insertion element has a plurality of outlet openings. This allows the fuel to be mixed with the air particularly advantageously, so that a particularly good mixture preparation can be achieved.

The outlet openings can be arranged at a distance from one another and/or evenly distributed in the circumferential direction of the insertion element extending around the longitudinal direction of the insertion element or around the axial direction of the swirl chamber. This allows the fuel to be mixed particularly advantageously with the air, which makes it possible to prepare a particularly advantageous mixture.

In order to realize a particularly advantageous mixture preparation and thus to be able to heat up the component particularly quickly and efficiently and/or keep it warm, it can be provided that the number of outlet openings is in a range from three to six inclusive.

The insertion element can have a spiral-shaped first element, through whose spiral turns at least one linear second element runs. Preferably the first element and/or the second element is a solid. Due to the fact that the first element is spiral is, the first element forms a spiral, in particular designed as a solid body, which has the aforementioned spiral turns, i.e. turns. The linear, second element is, for example, a wire or designed in the manner of a wire and extends through the spiral turns and in particular in the circumferential direction of the insertion element, in particular completely circumferentially. The second element can be supplied with the fuel from the respective outlet opening. In other words, the fuel can flow through the outlet opening and thereby flow against and/or around at least the second element, whereby the fuel can be made drop-shaped by means of the introduction element and can therefore be made available drop by drop, that is to say in the manner of a pipette and can be introduced into the inner swirl chamber, in particular dripped , is. By using the elements, a particularly uniform, thin film of the fuel can be produced, particularly on the inner circumferential surface, whereby a particularly advantageous mixture preparation can be achieved. In particular, it is conceivable that in this embodiment the fuel flows through the outlet opening itself as a jet, i.e. as a jet of fuel, with which the element designed, for example, as a wire, is sprayed, in particular from the inside, whereby the jet breaks into many small drops is divided, which finally emerge from the insertion element and hit the inner circumferential surface and are therefore dripped on. Here too, the introduction element provides the fuel in drop form and thus drop by drop. In particular, it is conceivable that the linear, second element is a wire mesh, forms a wire mesh or is part of a wire mesh, by means of which the fuel or the fuel jet can be particularly advantageously divided into drops, which then fall onto the inner circumferential surface in particular drop by drop can be applied or dripped on, whereby a particularly uniform, thin fuel film can be achieved on the inner circumferential surface.

In order to be able to heat up the component particularly efficiently and quickly and/or keep it warm, it is provided according to the invention that the insertion element is designed as a lance having a longitudinal direction of extension, in whose outer circumferential lateral surface extending in the circumferential direction of the lance running around the longitudinal direction of the lance the outlet opening is formed, the passage direction, along which the outlet opening can be flowed through by the fuel, runs obliquely or preferably perpendicular to the longitudinal direction. The longitudinal direction of the lance extends, for example, parallel to the axial direction of the respective swirl chamber or coincides with the axial direction of the respective swirl chamber. The lance can provide the fuel particularly advantageously and can thereby spray it in particular onto or against the aforementioned inner circumferential surface, whereby a particularly advantageous mixture preparation can be achieved.

In order to be able to heat the component designed, for example, as an exhaust gas aftertreatment device or as an exhaust gas aftertreatment system, particularly quickly and efficiently, in particular even when the exhaust gas from the internal combustion engine has only a low temperature, it is provided in an advantageous embodiment that the first outflow opening (first or inner nozzle ) in the flow direction of the first part of the air flowing through the first outflow opening and thus in the flow direction of the fuel flowing through the first outflow opening, ends at a specifically processed and therefore sharp or razor-sharp end edge, which is formed by an atomizer lip, in particular designed as a solid body, which is in the flow direction of the The first part of the air flowing through the first outflow opening and thus in the flow direction of the fuel flowing through the first outflow opening tapers towards the end edge and ends at the end edge. This means that the atomizer lip has a taper that tapers in the first flow direction and thus in particular towards the combustion chamber, which ends, in particular, only at the end edge. As a result of this and in particular due to the targeted processing of the end edge, the taper or the atomizer lip is sharp-edged. In other words, the atomizer lip ends with a sharp edge, which means that a particularly advantageous mixture preparation can be achieved.

For example, the mixture is burned in the combustion chamber to form a flame, whereby the fuel can be advantageously mixed with the air, in particular due to the swirl-shaped flows, and whereby the flame of the combustion chamber can be advantageously stabilized, particularly due to the swirl-shaped flows. For this purpose, a combustion-induced bursting of vortices can be generated in particular by the swirl-shaped flows. For this purpose, for example, the air flowing into the combustion chamber is initially deflected in the respective swirl chamber by approximately 70 degrees or by approximately 90 degrees, in particular in a range from 70 degrees to 90 degrees, which can be achieved, for example, by the respective swirl generator. The inner swirl chamber and the outer swirl chamber form For example, a swirl chamber, also known as a total swirl chamber, which in the invention is divided into the inner swirl chamber and the outer swirl chamber. Preferably, the inner swirl chamber and the outer swirl chamber are 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 partition wall surrounds at least the mentioned length range 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 circumferential, so that, for example, at least the length range of the inner swirl chamber follows the inner swirl chamber in the radial direction is formed or limited outside, in particular directly, by the partition. Furthermore, it is conceivable that at least a second length region of the outer swirl chamber is formed or limited in the radial direction of the outer swirl chamber inwards, in particular directly, by the partition. It is particularly conceivable that the length regions 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, that is to say only the second part of the air, flows through the outer swirl chamber, while or with the inner swirl chamber being flowed through by air, that is to say the first part, and the liquid fuel. This means that the fuel can be advantageously mixed with the first part of the air in the inner swirl chamber. The introduction element can be an injection element which can eject the fuel and thereby provide it. In particular, the insertion element can be an injection nozzle, the outlet opening of which is arranged, for example, in or on an end face or end face of the injection element, the end face or end face of which runs in an end face or end face plane that runs perpendicular to the axial direction of the respective swirl chamber. Furthermore, the introduction element, in particular the injection 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, if the insertion element is designed as an injection nozzle as an unclaimed embodiment, 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. If the insertion 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, in particular designed as a solid body, which also forms the atomizer lip and thus the end edge. In particular, an inner peripheral surface of the component delimits the inner swirl chamber in the radial direction of the inner swirl chamber to the outside. For example, the component, in particular its inner peripheral surface, is or functions as a film layer between the swirl chambers and thus between the swirl-shaped and thus twisted flows, also referred to as air flows. In particular, it is conceivable that the inner circumferential surface or the film layer is formed by the aforementioned partition or that the component forms or has the aforementioned partition. In this case, by means of the introduction element, in particular the injection element, the fuel flowing through the outlet opening and thus emerging, in particular ejected, from the injection element is applied, in particular as a film also referred to as a fuel film, to the film layer, in particular to the inner circumferential lateral surface, or to the film layer between the two wire air currents atomized. As a result of centrifugal forces resulting from the swirl-shaped flow of the first part of the air, the fuel that has emerged, in particular sprayed out, from the introduction element, in particular injection element, and is thereby introduced, in particular directly, into the inner swirl chamber, in particular injected, that is to say injected fuel, in particular than the fuel previously injected said film onto the film layer, in particular onto the inner circumferential surface, and flows or flows downstream to the first outflow opening, also referred to as a nozzle opening, and thus to the end edge. As a result, the fuel is applied to the atomizer lip and conveyed 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 fuel can form at the end edge. Due to the inventive design of the atomizer lip and in particular the end edge, only tiny droplets of fuel tear off at the end edge. In other words arise from the previously mentioned th fuel film at the end edge only contains particularly small, i.e. tiny, droplets, which break 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 fuel can be produced without complex, high injection pressures of the fuel and without costly 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 generated, so that even very low burner outputs can be achieved. The invention is based in particular on the findings 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 aforementioned problems and disadvantages can now be avoided by the invention, so that fuel consumption in particular can be kept particularly low.

When we talk below about the gas flowing through the exhaust tract, this can be understood to mean the aforementioned exhaust gas from the internal combustion engine or the aforementioned gas, unless otherwise stated. It is conceivable that the aforementioned introduction point, at which the burner exhaust gas can be introduced into the exhaust tract or into the gas, is arranged in the flow direction of the gas flowing through the exhaust tract downstream or upstream of an oxidation catalyst of the exhaust tract designed, for example, as a diesel oxidation catalyst. The oxidation catalyst is designed in particular to oxidize any unburned hydrocarbons (HC) contained in the exhaust gas and/or to oxidize any carbon monoxides (CO) contained in the exhaust gas, in particular to carbon dioxide.

In order to produce particularly small droplets of fuel using the end edge, in one embodiment of the invention it is provided that the end edge is specifically mechanically processed. The feature that the end edge is processed in a targeted manner, in particular mechanically, is to be understood in particular as meaning that the end edge does not have a randomly formed or arbitrarily intended processing, but rather as part of the production of the burner, the end edge is or is targeted and thus desired , especially mechanically, processed.

A further embodiment is characterized in that the end edge is turned, that is to say machined in a rotating manner, and/or ground and thereby specifically machined mechanically. This means that particularly small droplets of fuel can be generated using the end edge.

A second aspect of the invention relates to a motor vehicle with a burner according to the first aspect and/or the second aspect of the invention. Advantages and advantageous embodiments of the first and second aspects of the invention are to be viewed as advantages and advantageous embodiments of the third aspect 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 as well as the features and combinations of features mentioned below in the description of the figures and/or shown in the figures alone can be used not only in the combination specified in each case, but also in other combinations or on their own, without the scope of to abandon invention.

• 1 eine schematische Darstellung einer Antriebseinrichtung eines Kraftfahrzeugs, mit einer Verbrennungskraftmaschine, einem Abgastrakt und einem Brenner;
• 2 eine schematische Längsschnittansicht einer ersten Ausführungsform des Brenners;
• 3 ausschnittsweise eine schematische Längsschnittansicht des Brenners gemäß der ersten Ausführungsform;
• 4 eine schematische Längsschnittansicht eines Bauteils des Brenners gemäß der ersten Ausführungsform;
• 5 eine schematische Längsschnittansicht einer zweiten Ausführungsform des Brenners;
• 6 ausschnittsweise eine schematische und perspektivische Rückansicht einer dritten Ausführungsform des Brenners;
• 7 eine schematische Längsschnittansicht des Brenners gemäß der dritten Ausführungsform;
• 8 ausschnittsweise eine schematische und teilweise geschnittene Perspektivansicht einer Drallerzeugungseinrichtung des Brenners;
• 9 eine schematische Perspektivansicht der Drallerzeugungseinrichtung;
• 10 eine schematische Vorderansicht einer Verschlusseinrichtung;
• 11 ausschnittsweise eine schematische Längsschnittansicht einer vierten Ausführungsform des Brenners;
• 12 ausschnittsweise eine schematische Schnittansicht einer fünften Ausführungsform des Brenners;
• 13 ausschnittsweise eine schematische Längsschnittansicht einer sechsten Ausführungsform des Brenners;
• 14 ausschnittsweise eine schematische Längsschnittansicht einer siebten Ausführungsform des Brenners;
• 15 eine schematische und teilweise geschnittene Seitenansicht eines Einspritzelements des Brenners;
• 16 ein Blockdiagramm zum Veranschaulichen eines Betriebs des Brenners 42;
• 17 eine schematische Schnittansicht einer Brennstoffpumpe zum Fördern eines Brennstoffes zu dem Brenner;
• 18 ausschnittsweise eine schematische Perspektivansicht einer ersten Ausführungsform eines Einbringelements des Brenners;
• 19 ausschnittsweise eine schematische Perspektivansicht einer zweiten Ausführungsform des Einbringelements;
• 20 20 ausschnittsweise eine schematische Schnittansicht einer dritten Ausführungsform des Einbringelements;
• 21 eine schematische Querschnittsansicht der dritten Ausführungsform des Einbringelements; und
• 22 ausschnittsweise und jeweils teilweise eine schematische Seitenansicht einer vierten Ausführungsform und einer fünften Ausführungsform des Einbringelements.

The drawing shows in:

• 1 a schematic representation of a drive device of a motor vehicle, with an internal combustion engine, an exhaust tract and a burner;
• 2 a schematic longitudinal sectional view of a first embodiment of the burner;
• 3 a detail of a schematic longitudinal sectional view of the burner according to the first embodiment;
• 4 a schematic longitudinal sectional view of a component of the burner according to the first embodiment;
• 5 a schematic longitudinal sectional view of a second embodiment of the burner;
• 6 a detail of a schematic and perspective rear view of a third embodiment of the burner;
• 7 a schematic longitudinal sectional view of the burner according to the third embodiment;
• 8th a detail of a schematic and partially sectioned perspective view of a swirl generating device of the burner;
• 9 a schematic perspective view of the swirl generating device;
• 10 a schematic front view of a closure device;
• 11 a detail of a schematic longitudinal sectional view of a fourth embodiment of the burner;
• 12 a detail of a schematic sectional view of a fifth embodiment of the burner;
• 13 a detail of a schematic longitudinal sectional view of a sixth embodiment of the burner;
• 14 a detail of a schematic longitudinal sectional view of a seventh embodiment of the burner;
• 15 a schematic and partially sectioned side view of an injection element of the burner;
• 16 a block diagram illustrating an operation of the burner 42;
• 17 a schematic sectional view of a fuel pump for delivering fuel to the burner;
• 18 a detail of a schematic perspective view of a first embodiment of an insertion element of the burner;
• 19 a detail of a schematic perspective view of a second embodiment of the insertion element;
• 20 20 shows a detail of a schematic sectional view of a third embodiment of the insertion element;
• 21 a schematic cross-sectional view of the third embodiment of the insertion element; and
• 22 in detail and in part a schematic side view of a fourth embodiment and a fifth embodiment of the insertion element.

In the figures, identical or functionally identical elements are provided with the same reference numerals.

1 shows a schematic representation of a drive device 10 of a motor vehicle, 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 limited by the engine block 14, in particular directly. During a fired operation of the internal combustion engine 12, respective combustion processes take place in the cylinders 16, resulting in exhaust gas from the internal combustion engine 12. For this purpose, a particularly liquid fuel is introduced into the respective cylinder 16 within a respective working cycle of the internal combustion engine 12, in particular injected directly. The internal combustion engine 12 can be designed as a diesel engine, so that the fuel is preferably a diesel fuel. A tank 18, also referred to as a fuel tank, is provided in which the fuel can be accommodated or accommodated. For example, a respective injector is assigned to the respective cylinder 16, by means of which the fuel can be introduced into the respective cylinder 16, in particular directly injected. 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 working 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 the internal combustion engine 12, the exhaust gas of which is also referred to as engine exhaust gas.

The drive device 10 has an exhaust gas 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 tract 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. Arranged in the exhaust tract 26 are several components 36a-d, which are designed as respective exhaust gas aftertreatment devices, that is, exhaust gas aftertreatment components for aftertreating the exhaust gas. In the flow direction of the exhaust gas from the internal combustion engine 12 flowing through the exhaust tract 26, the components 36a-d are arranged one after the other and are therefore connected in series or in series with one another. Component 36a is, for example, an oxidation catalyst, in particular a diesel oxidation catalyst (DOC). Furthermore, the component 36 can be a nitrogen oxide storage catalyst (NSK). The component 36b can be an SCR catalytic converter, which is also simply referred to as SCR. The component 36c can be a particulate filter, in particular a diesel particulate filter (DPF). The component 36d can, for example, have a second SCR catalyst and/or an ammonia barrier catalyst (ASC).

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 be in the interior while the motor vehicle is traveling. For example, the structure forms or delimits an engine compartment in which the internal combustion engine 12 is arranged. For example, the exhaust gas turbocharger 28 is also arranged in the engine compartment. The structure also has a floor, also referred to as a main floor, through which the interior is at least partially, in particular at least predominantly or completely, limited downwards in the vertical direction of the vehicle. 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 components of a so-called hot end. In particular, the hot end can be flanged directly to the turbine 32. The component 36d is arranged, for example, outside the engine compartment and below the floor in the vertical direction of the vehicle, so that, for example, the component 36d forms a so-called cold end or is part of the so-called cold end.

The drive device 10 comprises a metering device 38, by means of which a particularly liquid reducing agent can be introduced into the exhaust tract 26 and, for example, into the exhaust gas flowing through the exhaust 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 catalytically effected and/or supported by the SCR catalyst. Out of 1 It can be seen that in the flow direction of the exhaust gas flowing through the exhaust tract 26, the introduction point E1 is arranged upstream of the component 36b and downstream of the component 36a. 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 device 10 and thus the motor vehicle also comprise 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 flow direction 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 to form a flame 44 and in particular to provide a burner exhaust gas, wherein the burner exhaust gas or the flame 44 can be introduced or is introduced into the exhaust gas tract 26 at an introduction point E2. This means that, so to speak, the burner 42 is arranged at the introduction point E2. At the in 1 In the exemplary embodiment shown, the introduction point E2 is arranged upstream of the components 36b, c and d and downstream of the component 36a. In other words, the in 1 In the exemplary embodiment shown, 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. At the in 1 In the exemplary embodiment shown, the fuel used is 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 come from the intake tract 24, for example. For this purpose, a fuel supply path 46 is provided, which on the one hand is fluidly connected or connectable to the burner 42 and on the other hand fluidly to a fuel line 48. 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 fluid with the fuel line 48 at a first connection point V1 connected, wherein the connection point V1 is 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 can flow through the fuel supply path 46 and is guided as the fuel by means of the fuel supply path 46 to and in particular into the burner 42.

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 device, is provided, by means of which the valve element 50 can be controlled, so that the amount of fuel flowing through the fuel supply path 46 and to be supplied to the burner 42 can be adjusted, in particular regulated, by means of the control device via the valve element 50.

Furthermore, an air supply path 54 is provided, via which or by means of which the burner can be supplied or is supplied with air to form the mixture. This means that the air from which the mixture is formed can flow through the air supply path 54. A pump 56, also known 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 thus conveyed towards the burner 42. For example, the low-pressure pump 20, also known 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 thus conveyed towards the burner 42.

It can be seen that the air supply path 54 is fluidly connected to the intake tract 24 at a second connection point V2. Thus, for example, at the connection point V2, at least part of the fresh air flowing through the intake tract 24 can be branched off from the intake tract 24 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. A second valve element 55 is arranged in the air supply path 54, by means of which the amount of air that flows through the air supply path 54 and thus flows through the burner 42 and is used to form the mixture can be adjusted. In this case, for example, the control device is designed to control the valve element 55, so that, for example, by means of the control device via the valve element 55, the amount of air flowing through the air supply path 54 and thus to be supplied to the burner 42, which is used to form the mixture, can be adjusted, in particular regulated , is.

2 shows a schematic sectional view of a first embodiment of the burner 42. 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 is to be ignited and thereby burned is ignited during operation of the burner 42 and thereby burned. For this purpose, an ignition device 60 designed, 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 the combustion chamber 58, in particular using electrical energy or electrical current. By means of the ignition spark, the mixture in the combustion chamber 58 is ignited and burned, in particular by providing the burner exhaust gas and/or by providing 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 gas 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 heated up and/or kept warm quickly and efficiently.

The burner 42 has an inner swirl chamber 62 through which a first part of the air supplied to the burner 42 can flow and causes a swirl-shaped first flow of the first part of the air. This is to be understood in particular as meaning that the first part of the air flows in a swirl shape through at least a first portion of the swirl chamber 62 and/or flows out in a swirl shape from the swirl chamber 62 and/or flows in a swirl shape in the combustion chamber 58. The inner swirl chamber 62 has, in particular, 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 removed 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 includes an introduction element in the form of an injection element 66, which has a channel 68 through which the liquid fuel supplied to the burner 42 can flow.

According to the invention, 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 outlet opening 70 through which the liquid fuel flowing through the channel 68 can flow. Out of 2 It can be seen that in the first, claimed embodiment, the channel 68 and thus the injection element 66 has at least or exactly two outlet openings 70, for example designed as bores. The outlet opening 70 can be flowed through by the fuel along a respective, second passage direction, so that the fuel flowing through the injection element 66 can be ejected or can emerge from the injection element 66 via the respective outlet opening 70 and, in particular directly, can be injected into the 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 into the inner swirl chamber 62 via the respective outlet opening 70, in particular directly, 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 ejected from the injection element 66 via the respective outlet opening 70 to form a respective fuel jet 72 and can therefore 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 in the present case the channel 68 have 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 with the first passage direction and thus coincides with the first flow direction. Further is over 2 It can be seen 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 this case, obliquely to the first passage direction and thus to the first flow direction and to the axial direction of the swirl chamber 62 and the outflow opening 64.

The swirl chamber 62 is at least partially, in particular at least predominantly and therefore more than half or completely, formed or limited by a preferably integrally formed component 74 of the burner 42, so that the component 74 also forms or delimits the outflow opening 64.

The burner 42 further has an outer swirl chamber 76, which surrounds at least one length region and, in the present case, also the first outflow opening 64 in the circumferential direction of the swirl chamber 62, which extends around the axial direction of the swirl chamber 62, in particular completely circumferentially. 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 78. The axial direction of the swirl chamber 62 coincides with the axial direction of the swirl chamber 76, so that the radial direction of the swirl chamber 62 coincides with the radial direction of the swirl chamber 76. The outer swirl chamber 76 can be flowed through by a second part of the air that is supplied to the burner 42 and is designed to cause a swirl-shaped 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 swirl pattern and/or flows out of the swirl chamber 76 in a swirl pattern and/or flows in a swirl pattern in the combustion chamber 58. In particular, it is preferably provided that the parts of the air have their swirl-shaped flows in the combustion chamber 58, and therefore run in a swirl-shaped manner in the combustion chamber 58. The outer swirl chamber 76 has, in particular precisely, a second outflow opening 80 through which the second part of the air flowing through the outer swirl chamber 76 flows, in particular along a third flow direction, the third passage direction, along which the outflow opening 80 is flowed through by the second flowing through the swirl chamber 76 Part of the air can flow through, in this case coinciding 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 through the outflow opening 80 can flow through hungrily. This means in particular that the first passage direction coincides with the third passage direction and the first flow direction coincides with the third flow direction, so that in the present case the first flow direction, the third flow direction, the first passage direction and the third passage direction coincide with the axial direction of the swirl chamber 62 and with the axial To coincide in the direction of the swirl chamber 76. 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 is arranged in particular in line or in series with the outflow opening 64, so that the outflow opening 80 is separated from the second part of the air, from the first part of the air and from the Fuel can flow through. In particular, due to the swirl-shaped first flow, the first part of the air is already mixed with the fuel in the swirl chamber 62, in particular to form 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, swirl-shaped second flow, whereby the mixture is prepared particularly advantageously, i.e. the partial mixture is particularly advantageously mixed with the second part.

It can be seen that the swirl chamber 76 is at least partially, in particular at least predominantly and therefore at least more than half or completely, limited in the radial direction of the respective swirl chamber 62 or 76 inwards by the component 74, in particular by the 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 in the present case is designed separately from the component 74. The component 74 is at least partially, in particular at least predominantly, arranged in the component 82. The outflow opening 80 is, for example, partially delimited or formed by the component 82 and partially by the component 74, in particular with regard to the smallest or smallest flow cross section of the outflow opening 80 through which the second part of the air can flow.

In order to be able to heat up at least the component 36b particularly efficiently and/or keep it warm, it is provided that - how particularly well 3 can be seen - the first outflow opening 64 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 fuel flowing through the first outflow opening 64 ends at a specifically, in particular mechanically, machined and therefore razor-sharp end edge K, which, for example, in um The circumferential direction of the outflow opening 64 extending in the axial direction of the outflow opening 64, the axial direction of which coincides with the axial direction of the respective swirl chamber 62 or 76, runs completely around the outflow opening 64. The razor-sharp end edge K is formed by an atomizer lip 84, which in the present case is formed by the component 74. 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 fuel flowing through the first outflow opening 64 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 specifically mechanically processed. For example, the fuel is sprayed against the component 74, in particular against an inner circumferential lateral surface 86 of the component 74, in particular to form the fuel jets 72, in particular in such a way that what is simply referred to as a film is formed on the component 74, in particular on the inner circumferential 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 circumferential lateral surface 86. Due to the first swirl-shaped flow, in particular due to centrifugal forces resulting from the first swirl-shaped flow, the fuel film is transported along the inner circumferential surface 86 towards the end edge K, at which the fuel tears off from the end edge K, resulting in particularly tiny ones from the fuel or from the fuel film Droplets of fuel are formed. The component 74 is therefore a so-called film layer or acts as a film bearing between the swirl-shaped flows. The droplets together form a particularly large surface area of the fuel, so that a particularly efficient operation of the burner can be achieved even with low burner outputs, with no costly pumps or no cost-intensive high-pressure generation being required to produce the small and therefore fine droplets of the 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 inwards in the radial direction of the respective outflow opening 64 or 80 by the end edge K.

Furthermore, the burner 42 has an anti-recirculation plate 88, which in the first Embodiment in the flow direction of the parts flowing through the outflow opening 80 and the fuel flowing through the outflow opening 80 is arranged downstream of the outflow opening 80 and thereby downstream of the component 82. The anti-recirculation plate 88 has a flow opening 90, which is arranged 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 projects beyond at least a portion T of the component 82 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. By means of the anti-recirculation plate 88, an excessive flow of the mixture flowing through the flow opening 90 and flowing into the combustion chamber 58, in particular into the part T2, back in the direction of the component 82 or back into the part T1 can be avoided, so that an advantageous mixture preparation can be achieved .

Out of 2 It can also be seen that, for example, the swirl chambers 62 and 76 are supplied with the air or parts of the air via a supply chamber 92 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 was 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 the second part. The air flowing through the air supply path 54 can, for example, flow out of the air supply path 54 along a supply direction and flow into the supply chamber 92, the supply direction, for example, running obliquely and/or tangentially to the axial direction of the respective swirl chamber 62 and 76 and thus to their respective longitudinal axis.

4 shows the component 74, also known as the film layer, in a schematic longitudinal section view. It can be seen that at least part TB of the outer swirl chamber 76 is formed by the 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 swirl-shaped flow of the first part of the air is generated by means of the swirl generators 94, and the second swirl-shaped flow of the second part of the air is generated by means of the swirl generators 96. An inner annular surface, in particular the inner swirl chamber 62, is in 4 designated K1, and an outer annular surface, in particular the outer swirl chamber 76, is in 4 labeled K2. The swirl generators 94 are arranged in an air duct LK1 of the swirl chamber 62, the air duct LK1 of which is delimited, in particular completely, by the component 74. In particular, the air duct LK1 is limited to the outside and inside by the component 74 in the radial direction of the respective swirl chamber 62 or 76. 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, 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 swirl-shaped flow and the swirl generators 96 generate or effect the second swirl-shaped flow. An outer diameter of the air duct LK1, also referred to as an air duct, is denoted by Di, and an outer diameter of the air duct LK2, also referred to as an air duct, is in 4 labeled Da.

How out 2 to 4 As can be seen, 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 substantially in the axial direction. Furthermore, the second part of the air from the outer swirl chamber 76 also flows at least substantially in the axial direction into the combustion chamber 58 and in doing so, at the end edge K, in particular at its break-off point, tears the finely divided fuel from the film layer into small droplets the combustion chamber 58. The smallest or narrowest flow cross section of the outer nozzle, i.e. the outflow opening 80, is located at the break-off point of the inner nozzle, i.e. the outflow opening 64, i.e. the end edge K.

It is preferably provided that the nozzles, i.e. the outflow openings 64 and 80, have the following size or area ratios: The outflow opening 64 (inner nozzle). preferably a diameter, in particular an inner diameter, which has 10 percent to 20 percent of Di. Furthermore, it is preferably provided that the outer nozzle, 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 circular ring area. In other words, it is preferably provided that the air duct LK1 has a first annular surface and the air duct LK2 has a second annular surface, the annular surfaces preferably having the same size.

5 shows a schematic sectional view of a second embodiment of the burner 42. In the first embodiment, for example, it is provided 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 can advantageously be used to prevent the mixture from flowing backwards back to the component 82 after it exits the outer nozzle, i.e. from the outflow opening 80 and into the combustion chamber 58, and forms a vortex . The anti-recirculation plate 88, also simply referred to as a plate, preferably has a diameter, in particular an outer diameter, which is preferably at least as large as Di.

6 shows a section of a schematic perspective view of a third embodiment of the burner 42. In the third embodiment, the combustion chamber 58 has a plurality of flow openings 98, which are spaced apart from one another and through respective wall regions W, in particular designed as respective solid bodies, in particular in the radial direction of the respective swirl chamber 62 or 76 are separated from each other. The burner exhaust gas or the flame 44 can be removed from the combustion chamber 58 via the flow openings 98 and introduced into the exhaust gas tract 26. In the present case, the wall regions W are formed in one piece with one another and are formed by, for example, a one-piece perforated disk 100, which is designed as a solid body. In the present case, exactly eight flow openings 98 are provided. As in 2 can be seen, it is fundamentally conceivable that the combustion chamber 58 has exactly one large and non-divided discharge opening 102, via which the burner exhaust gas or the flame 44 can be removed from the combustion chamber 58 and introduced into the exhaust tract 26. In contrast, in the third embodiment, the plurality of spaced-apart and separate through-flow openings 98 are provided, so that the discharge opening 102 is, so to speak, divided or divided by the wall regions W into the plurality of through-flow openings 98. It can be seen that the 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, the center of which 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 flow openings 98 are provided, in particular at a particular location, in order to enable advantageous recirculation in the combustion chamber 58. Instead of a smaller outlet opening, it is advantageous to use a perforated plate such as the perforated disk 100 with several smaller openings in the form of the flow opening 98. The number of flow openings 98 is, for example, in a range from three to nine inclusive. The flow openings 98 have a similar or at least essentially the same flow area or outlet area through which the burner exhaust gas or the flame 44 can flow. The flow areas of the or all flow openings 98 result in a total flow area, which is also referred to as the total outlet area and is, for example, 0.8 times to 1.8 times as large as 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 tract 26, it may be advantageous to realize six smaller openings with a respective diameter of 10.5 millimeters, so that a total outlet area of 520 square millimeters is represented is.

7 shows the third embodiment of the burner 42 in a schematic longitudinal section view, with the perforated disk 100, also known as a perforated plate, being provided. The previously mentioned, advantageous recirculation in the combustion chamber 58 is in 7 illustrated by an arrow 104. Furthermore, in 7 a swirl-shaped flow of the mixture is illustrated and designated 106, the swirl-shaped flow 106 of the mixture in the combustion chamber 58 resulting from the respective, swirl-shaped flows of the parts of the air. The swirling currents of the Parts of the air and thus the swirl-shaped flow 106 of the mixture are realized in particular by the swirl generators 94 and 96 as well as 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 blade and not as a quarter-spherical sheet metal construction, so that the respective swirl-shaped flow can be generated or effected particularly advantageously. The swirl-shaped flows of the parts of the air and the resulting swirl-shaped flow 106 of the mixture in the combustion chamber 58 prevents the flame 44 in the combustion chamber 58 from being blown out, optimizes mixing of the air with the fuel in the combustion chamber 58 and generates vortex bursting to stabilize the Flame 44. The recirculation in the combustion chamber 58 illustrated by the arrows 104 can be realized 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 removed from the combustion chamber 58 and introduced into the exhaust gas tract 26 . The reduction in the outlet cross section means that, for example, the total outlet area of the individual flow openings 98 is smaller than an 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 residence 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 the burner exhaust gas can be achieved at its outlet. In particular, the recirculation leads to recirculation areas and vortex bursts, whereby a particularly long residence time of the flame 44 in the combustion chamber 58 can be achieved.

8th shows a schematic and partially sectioned perspective view of a swirl generating device 107, which can be part of the component 74 or formed by the component 74, for example. The swirl generating device 107 includes the swirl generators 94 of the inner swirl chamber 62 and the swirl generators 96 of the outer swirl chamber 76. Particularly good 8th It can be seen that the swirl generators 96 and preferably also the swirl generators 94 are designed as air guide blades, which can be designed to be flow-efficient, in particular shaped. This allows excessive pressure loss to be avoided, especially compared to spherical swirl generators. 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 a maximum of 70 percent is covered by the respective swirl generators arranged in the air duct LK1 or LK2. A particularly advantageous axial blockage of at least 20 percent and at most 70 percent of the respective surface area is therefore 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 designed to be straight. In particular, it is conceivable that the respective air guide blade encloses a respective angle α with the respective radial direction of the respective swirl chamber 62 and 76, which lies, for example, in a range of ten degrees up to and including 45 degrees. The aforementioned radius of the respective air guide vane, also simply referred to as a blade, is in 8th labeled R. The swirl generators 94 and 96 are preferably designed to deflect the part of the air flowing through the respective air duct LK1 or LK2, i.e. 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 effect the swirl-shaped flows of the parts of the air as counter-rotating or opposing, swirl-shaped flows, so that, for example the first flow is left-handed and the second flow is right-handed or vice versa.

The swirl generating device 107 has a, in particular central, through opening 108, which is penetrated by the injection element 66. In other words, the injection element 66 projects through the through opening 108 into the inner swirl chamber 62.

10 shows a schematic front view of a closure device 110, which in the present case is designed as an iris diaphragm or in the manner of an iris diaphragm. If the burner 42 is not operated, it may be advantageous to have an air line and a fuel line, that is, for example, the air supply path 54 and/or the fuel supply path 46 and/or the swirl chambers 62 and 76 and, for example, the outflow opening 64 and/or the outflow opening 80 to block in order to prevent 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. Furthermore, it is conceivable to block the combustion chamber 58 or at least a length region of the combustion chamber 58 in order to prevent exhaust gas from the internal combustion engine 12 from penetrating from the exhaust tract 26 into the combustion chamber 58 or into its partial region or length region. For this purpose, the closure device 110 can be used, which can be arranged, for example, in the combustion chamber 58 or downstream of the combustion chamber 58. Closure elements 112 of the closure device 110 that can be moved in the manner of an iris diaphragm can vary, that is to say variably set, an opening cross section 114 through which the flame 44 or the burner exhaust gas can flow, for example, and which is limited by the closure elements 112, in particular directly, in particular can be controlled or regulated. It is therefore conceivable to close at least a portion of the combustion chamber 58 by means of the closure 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. This has the particular advantage that an air and fuel supply can be closed at the same time using a small plug. Then no air valve downstream of the pump 56 is necessary since it prevents exhaust gas from entering the pump 56. There is also no need for a much larger exhaust flap after the combustion chamber 58 or after its exit, which is charged with hot exhaust gas.

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, wherein the flame 44 or the burner exhaust gas can be removed from the combustion chamber 58 via the outlet cross section and introduced into the exhaust gas tract 26. A tapering of the opening cross-section that is necessary, required or carried out in order to increase a flow velocity 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 flow-efficient manner. Thus, instead of a hole in a flat closure plate, there could be a conical outlet with an angle of 30 degrees to 70 degrees to the horizontal, as is achieved, for example, in an aircraft engine using segments and/or a cone. This can be done by a fixed geometry or also variable as in an aircraft engine with individual segments that are foldable, for example in a thrust nozzle, or with a displaceably arranged outlet cone, which can be displaced, for example, in the axial direction of the respective swirl chamber 62 or 76.

11 shows a detail in a schematic sectional view of the burner 42 according to a fourth embodiment. Particularly good looking 11 , but also out 2 and 7 It can be seen that the combustion chamber 58 is formed or limited by a chamber element 116, which is designed in particular as a solid body. In particular, the combustion chamber 58, whose axial direction coincides with the axial direction of the respective swirl chamber 62 or 76, is along its radial direction, which runs parallel to the respective radial direction of the respective swirl chamber 62 or 76, in particular directly, through an inner circumferential 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 element 116 is designed such that it has two chamber parts 120 and 122, which are, for example, formed in one piece with one another, or the chamber parts 120 and 122 are components formed separately from one another and connected to one another. The inner peripheral surface 118 is formed by the chamber part 122. The chamber parts 120 and 122 are arranged one inside the other, such that at least one length region of the chamber part 120 surrounds at least one length region of the chamber part 122 in the circumferential direction of the combustion chamber 58 extending around the axial direction of the combustion chamber 58, in particular completely circumferentially, at least the length region of the 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 to form 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 the chamber parts 120 and 122. It can also be seen that the Contiguous or uninterrupted discharge opening 102 is formed or limited completely circumferentially by the chamber part 122, in particular in the circumferential direction of the combustion chamber 58. At the in 2 In the first embodiment shown, the discharge opening 102 is not divided, that is to say it is free from a component that divides the discharge opening 102 into a plurality of separate and spaced-apart flow openings. At the in 7 However, in the third embodiment shown, the perforated disk 100, also known as a perforated plate, is arranged in the discharge opening 102, through which the essentially uninterrupted, i.e. coherent, discharge opening 102 flows into the plurality of spaced-apart and separate flow openings 98 which are formed in the perforated disk 100. is divided or divided. The flame 44 or the burner exhaust gas can flow out of the combustion chamber 58 along a fourth flow direction that runs in the axial direction of the combustion chamber 58, that is, runs parallel to the axial direction of the combustion chamber 58 or coincides with the axial direction of the combustion chamber 58, and thereby through the discharge opening 102 or flow through the respective flow opening 98, the fourth flow direction coinciding with the first, second and third flow directions. 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, that is, along the fourth flow direction. For this purpose, the chamber element 116, in particular the chamber part 120, has a length region L1 which tapers in the flow direction of the burner exhaust gas flowing through the discharge opening 102 and which delimits the discharge opening 102 in the circumferential direction of the combustion chamber 58, in particular completely circumferentially. In other words, the length region L1 and thus the discharge opening 102 are conical, that is to say conical or truncated, in the flow direction of the burner exhaust gas flowing through the discharge opening 102. 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 conical at its outlet in the fourth embodiment , therefore has a cone formed by the length range L1. The discharge opening 102 preferably has an inner 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 length regions of the chamber parts 120 and 122 are arranged one inside the other and are spaced apart from one another in the radial direction of the combustion chamber 58 to form the intermediate space 124, the intermediate space 124 being filled, for example, with air and thus designed as an air gap, means that the combustion chamber is double-walled 58 or the chamber element 116, whereby the combustion chamber 58 is insulated by the gap 124, that is, by the air gap. The combustion chamber 58 is therefore air gap insulated. In the following, reference is made in particular to the in 4 shown outer diameter Da of the film layer, in particular the outer air channel LK2 of the outer swirl chamber 76, the air channel LK2, in which the outer swirl generators 96 are arranged, and thus the outer diameter Da, in particular completely, through the film layer, that is, through the component 74, are formed. Regarding 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 times 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 exit velocity of the burner exhaust gas and reduces the influence on the flame 44, also referred to as the burner flame, by the exhaust gas of the internal combustion engine 12, also referred to as engine exhaust gas. A length l1 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 times to 4.0 times Da. With secondary air injection, it is preferably provided that the length l1 of the combustion chamber is 2.0 times to 5.5 times Da.

Instead of the contiguous discharge opening 102, it is conceivable to use the multiple, separate and spaced-apart flow openings 98. In other words, it is conceivable to divide the inherently connected and therefore uninterrupted discharge opening 102 into the plurality of spaced-apart and separate flow openings 98, the number of which is preferably in a range from 3 to 9 inclusive. The respective flow opening 98 has an area also referred to as an exit area or flow area, the sum of the areas of all flow openings 98 preferably being similar to the exit area of the connected discharge openings 102, that is is similar to the area of the discharge opening 102. The sum of the areas of the flow openings 98 is also referred to as the total exit area. The flow openings 98 are designed, for example, as bores. It is conceivable that the sum of the surface areas of all flow openings 98, that is to say the total outlet area, is 0.8 times 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 range L1. With regard to the exhaust gas from 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, whereby the perforated element can be understood to mean an element designed in particular as a solid body, which has several 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. So that, for example, the engine exhaust does not have an excessively negative influence and destabilizes 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, that is, upstream of the combustion chamber 58, so that the engine exhaust does not or only can enter slightly into the combustion chamber 58, in particular against the flow direction along which the flame 44 or the burner exhaust gas flows from the combustion chamber 58 into the exhaust gas tract 26. It is therefore preferably provided that the deflection element is arranged in the exhaust gas tract 26 upstream of the combustion chamber 58 in the flow direction of the engine exhaust gas, that is to say upstream of the introduction point E2. A geometry of the deflection element can depend on how the combustion chamber 58 is arranged in relation to the exhaust tract 26, that is to say to an exhaust duct of the exhaust tract 26. The exhaust gas duct is to be understood as meaning that the burner exhaust gas or the flame 44 flows from the combustion chamber 58, in particular along the fourth flow direction, into the exhaust gas duct, in particular at the introduction point E2. An individual adjustment of the geometry of the deflection element is advantageous.

Furthermore, it is advantageous, as described above, that the closure device 110 or another closure device is arranged at the exit of the combustion chamber 58. This is to be understood in particular as follows: The closure device 110 can be arranged, for example, in the length range 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 Introductory point E2, which can be removed from the combustion chamber 58 and introduced into the exhaust tract 26, in particular into the exhaust duct, is limited by the closure device 110, in particular by the closure elements 112, and can therefore be varied, that is to say adjustable, by means of the 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 another closure device is downstream of the combustion chamber 58, that is, downstream of the chamber part 122 and directly on the combustion chamber 58 or on the chamber part 122 subsequently arranged, therefore arranged downstream of the discharge opening 102 itself. A taper of the discharge opening 102, as is realized in the fourth embodiment by the length range L1, i.e. by the cone described, leads to an increase in the flow velocity of the burner exhaust gas, whereby the taper of the outlet of the combustion chamber 58 should be represented in a flow-efficient manner. The cone formed in the present case by the length range L1 preferably has an angle, also referred to as a cone angle, in particular to the in 11 axial direction of the combustion chamber 58, illustrated by a dashed line 126, from 30° to 70°. In the fourth embodiment, the cone is designed as a fixed geometry, so that the cone, i.e. the cone angle, is fixed, i.e. cannot be varied. However, it is conceivable to design the cone, such as in an aircraft engine, to be variable, in particular with regard to its cone angle, in particular by individual segments which, for example, can be folded like a thrust nozzle in an aircraft engine, that is to say can be pivoted in particular relative to the chamber part 122. whereby the cone or the cone angle is adjustable, that is, variable. Alternatively or additionally, it can be provided that the cone or its cone angle can be varied by a displaceably arranged outlet cone and/or that an outlet cone is provided whose longitudinal central axis coincides, for example, with the axial direction of the combustion chamber 58 and/or in the axial direction of the combustion chamber 58 is displaceable, in particular relative to the chamber element 116, wherein preferably the outlet cone, which is preferably arranged coaxially to the combustion chamber 58, tapers in the flow direction of the burner exhaust gas flowing through the discharge opening 102. Under the feature, that the outlet cone is arranged coaxially with the combustion chamber 58, it is to be understood in particular that the axial direction of the outlet cone, hence its longitudinal central axis, coincides with the axial direction of the combustion chamber 58. By moving the outlet cone in the axial direction of the combustion chamber 58 relative to the chamber element 116, for example, the flow cross section through which the burner exhaust gas can flow, via which the burner exhaust gas can be removed from the combustion chamber 58 and introduced into the exhaust gas duct, can be varied. The exit cone is in 11 shown particularly schematically and designated 128. A direction of movement running parallel to the axial direction of the combustion chamber 58 or coinciding with the axial direction of the combustion chamber 58, along which the outlet cone 128 is translationally movable, in particular displaceable, relative to the chamber element 116 is shown in 11 illustrated by a double arrow 130. It can be seen that the flow cross section through which the burner exhaust gas can flow in the radial direction of the combustion chamber 58 is limited to the outside by the chamber element 116 and inwards by the outlet cone 128, in particular directly, the flow cross section being annular or annular surface-shaped. Since the outlet cone 128 tapers in the flow direction of the burner exhaust gas flowing through the discharge opening 102 or the flow cross section, the flow cross section is varied by moving the outlet cone 128 along the direction of movement and relative to the chamber element 116.

12 shows a detail in a schematic sectional view of a fifth embodiment of the burner 42. In particular, in 12 partly the component 74 and partly the component 82 can be seen, in particular as in 3 . If the burner 42 is not operated, it is advantageous to close an air and fuel line, i.e. preferably the outflow openings 64 and 68, in order to prevent the engine exhaust gas from penetrating into the swirl chambers 62 and 76. For this purpose, it is conceivable that, for example, a closure device 110 is arranged in the outflow opening 64 and / or in the outflow opening 80, or the closure device 110 is arranged downstream of the outflow opening 80 and directly adjacent to the outflow opening 80, so that, for example, one of the first part of the air and the fuel can flow through, in particular the outflow opening 64, and / or a second flow cross section through which the parts of the air and the fuel can flow, in particular the outflow opening 80, or one of the parts of the air and the fuel A third flow cross-section which can flow through and is arranged downstream of the outflow opening 80 and which 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, the opening cross section 114, that is in particular the opening cross section 114 of an opening having the opening cross section 114, the flow cross section (opening cross section 114) and thus surface area of which can be adjusted in particular in the manner of an iris diaphragm by means of the closure elements 112. Thus, the respective first, second or third flow cross section can be adjusted, in particular controlled or regulated, in particular depending on 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, further closure device, thus reducing the first, second and third flow cross sections to zero.

The further closure device can be, for example, an in 12 Particularly schematically shown closure element designated 132, which is also referred to as a closure plug. The closure element 132 is, for example, movable, 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 in 12 open position shown. In the closed position, the outflow openings 64 and 80 are closed by the closure element 132 and are therefore fluidly 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, for example, as a small stopper, in particular in the closed position of the closure element 132. Then no air valve such as the valve element 55 downstream of the pump 56 is required , since by means of the closure element 132 it can be prevented that engine exhaust gas from the exhaust tract 26 flows through the air supply path 54. In other words, by means of the closure element 132 or by means of the closure device 110, it can be avoided that engine exhaust gas from the exhaust tract 26 into the pump 56 penetrates. There is also no need for a much larger exhaust flap downstream of the combustion chamber 58, i.e. after its exit, which is charged with hot exhaust gas.

The previously mentioned air gap insulation of the combustion chamber 58 is explained in more detail below: Since the combustion chamber 58 becomes very hot on its outer wall and possibly glows, especially in full-load operation, the air gap insulation can ensure particularly safe operation. In addition, heat losses can be kept particularly low thanks to the air gap insulation. It is preferably provided that an in particular thermal insulation surrounds the combustion chamber 58 in a circumferential direction running around the axial direction of the combustion chamber 58, in particular completely. In the present case, the air gap insulation, i.e. the air gap, is provided as this insulation. The intermediate space 124, which in the present case is designed as an air gap, preferably has a width, in particular gap width, which extends in the radial direction of the combustion chamber 58, the width, in particular 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 to 6 mm inclusive. 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 the chamber element 116 (air-gap-insulated tube) surrounds the air-gap-insulated tube (chamber element 116), that is, at least a length region of the chamber element 116 running in the axial direction of the combustion chamber 58, in particular completely circumferentially in the circumferential direction of the combustion chamber 58 surrounds. The insulating element is preferably an insulating mat. The insulating element is preferably formed at least from mineral wool and/or sheet metal, whereby the combustion chamber 58 can be insulated particularly advantageously.

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. Using the thermal energy, for example, at least the component 36b can be effectively and efficiently heated and/or kept warm. Alternatively or additionally, the component 36c, designed for example as a particle filter, can be heated. By heating the particle filter, for example, a regeneration of the particle filter can be brought about or carried out. 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 component 36b and/or 36c. This also allows heat losses to be kept low. However, in order to ensure an advantageous mixing of the engine exhaust gas with the burner exhaust gas, a minimum distance should be provided for mixing the burner exhaust gas with the engine exhaust gas, this minimum distance being particularly continuous in the flow direction of the engine exhaust gas flowing through the exhaust tract 26 from the burner 42 or from the introduction point E2 extends up to the component to be heated or kept warm, such as component 36b, in particular up to its entrance. In particular, the minimum distance is a minimum distance of the mixing chamber 40. Therefore, the introduction point E2 cannot move directly to the entry of the component 36b. It has proven to be particularly advantageous if a distance, particularly in the flow direction of the exhaust gas flowing through the exhaust tract 26, between the introduction point E2 and the component 36b, particularly in the flow direction of the exhaust tract 26 immediately following the introduction point E2, is at least 5-fold to 8-fold. times of Da and at most 30 times of Da. The feature that the component 36b adjoins the introduction point E2 in the flow direction of the exhaust gas (engine exhaust gas) flowing through the exhaust tract 26 is to be understood as meaning that in the flow direction of the exhaust gas flowing through the exhaust tract 26 between the introduction point E2 and the component 36b no other additional 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 the component 36b entry. In particular, when component 36b is a catalyst, in particular the aforementioned SCR catalyst, component 36b has a substrate. It is therefore preferably provided that the aforementioned distance is a distance that runs in particular in the flow direction of the exhaust gas flowing through the exhaust 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 duct expands to at least 6 times Da after exiting the combustion chamber 58, that is, for example, starting from the introduction point E2, before the exhaust gas (engine exhaust or burner exhaust) hits the substrate.

Out of 2 It can be seen that the ignition device 60, designed for example as a spark plug, glow plug or glow plug, has a thread 134, in particular designed as an external thread, by means of which the ignition device 60 is at least indirectly screwed to the chamber element 116 and thereby held on the 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 fins are applied to the thread 134 of the ignition device 60, also known 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 fin has a diameter of 20 to 80 mm, in particular an outer diameter. In addition, it is advantageous if the individual cooling fins have openings, in particular through openings, designed as bores, the number of which is in a range from 3 to 8 inclusive, in order to realize an advantageous heat dissipation to an environment of the ignition device 60, that is to say an ambient air . The respective through opening of the respective cooling fin has, for example, a diameter, in particular an inner diameter, which is at least 5 mm and at most 15 mm. An electrode gap between electrodes of the ignition device 60 is at least 0.7 mm and at most 10 mm. The electrodes are off 2 recognizable and designated 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 effect or generation of the swirl-shaped flows of the parts of the air in the swirl chambers 62 and 76, the air should not be introduced into the respective swirl chambers 62 and 76 strictly radially, that is, in the radial direction of the respective swirl chambers 62 and 76, but rather tangential or oblique to the respective axial direction of the respective swirl chamber 62 or 76, as shown in 2 is illustrated. 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 be directed in the direction of swirl, which leads to a particularly high effectiveness of swirl generation.

In order to supply the burner 42 with the fuel, a fuel pump, such as a fuel pump for delivering the fuel from the tank 18, is used. The fuel pump can therefore 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 (γ) of at least substantially 1.0. In other words, it is preferably provided that the burner is operated stoichiometrically, and therefore the mixture is a stoichiometric mixture. Expressed again in other words, it is advantageously provided if a first proportion of the air in the mixture and a second proportion of the fuel in the mixture are set or regulated as precisely as possible. It is therefore advantageous if a first amount of the air of the mixture, also referred to as combustion air, and a second amount of the fuel of the mixture are set and/or calculated at least substantially exactly and introduced into the respective, corresponding swirl chamber 62 or 76. It is therefore advantageous to use a frequency-controlled piston pump as the fuel pump for conveying the fuel to or into the burner 42. This should be provided at its outlet with a spring-loaded valve, such as a ball valve, to prevent fuel or exhaust gas from flowing back, especially into the fuel pump.

Such a fuel pump is in 17 shown in a schematic longitudinal section view and designated 137. The fuel pump 137 is designed as a piston pump, the piston of which is designated 139 for conveying the fuel. The spring-loaded valve, which is in 17 The exemplary embodiment shown is designed as a spring-loaded ball valve 17 denoted by 140 and includes a particularly mechanical spring unit 142 and a ball 144. In particular, the spring-loaded valve 140 is designed as a check valve or functions as a check valve, so that the fuel can be conveyed to the burner 42 by means of the fuel pump 137, so that the valve 140 opens in the direction of the burner, but blocks in the opposite direction, so that no exhaust gas and no air can flow from the burner 42 back into the fuel pump 137.

13 shows a detail in a schematic longitudinal section view of a sixth embodiment of the burner 42, in particular in 6 as well as in 12 the outflow openings 64 and 80 and thus the component 82 and the component 74 can be seen. Also recognizable is from 13 the injection element 66, which is in 13 However, according to the exemplary embodiment shown 2 and 7 designed as a lance. The outlet openings are not arranged or formed on an axial end face 146 of the injection element 66 that is aligned in the axial direction of the swirl chambers 62 or 76, but rather the outlet openings 70 are aligned in the radial direction of the swirl chambers 62 or 76 and in an outer circumferential lateral surface 148 of the injection element 66 is formed, the outer peripheral surface 148 of which extends around the axial direction of the respective swirl chamber 62 or 76 extending circumferential direction. In other words, the respective fuel jet 72 does not emerge 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 emerges perpendicularly or, in this case, obliquely to the in 13 axial direction of the respective swirl chamber 62 or 76 from the injection element 66, illustrated by a dashed line 150.

The inner peripheral lateral surface 86 of the component 74 is also referred to as a film wall, since the fuel, which is sprayed out of the injection element 66 via the outlet openings 70 and brought or sprayed 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 particularly advantageously onto or against the film wall, according to the invention, instead of an atomizer nozzle, a simple lance is used, such as the one in 13 Injection element 66 shown is used. The lance comprises a tube 152, in the end region of which the at least two outlet openings 70, designed for example as transverse bores, are attached. The fuel does not emerge from the lance or from the tube 152 in the axial direction of the respective swirl chamber 62 or 76, but in the radial direction or obliquely to the radial direction of the respective swirl chamber 62 or 76. The fuel emerging from the outlet openings 70 is particularly effective In order to be able to bring it onto the film layer and in particular onto 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 known as the film layer wall, which in particular in the axial direction of the respective swirl chamber 62 or 76, the respective axial direction of which corresponds to the axial direction and to the longitudinal direction of the injection element 66, in particular the tube 152, coincides, is arranged at the level of the outlet openings 70, which are preferably arranged at the same height 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, the narrowest flow cross section through which the first part of the air can flow, preferably in the axial direction of the respective swirl chamber 62 or 76 and thus of the injection element 66 is arranged such that the narrowest or smallest or lowest flow cross section of the 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 the injection element 66. In this way, a particularly advantageous atomization of the fuel flowing through the outlet openings 70 can be achieved. 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, that is, 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 in the axial direction of the injection element 66 and thus in the flow direction of the Venturi nozzle 154 flowing through the first part of the air are arranged at the same height, the first part of the air acts or functions as a propellant medium that sucks in the fuel as a suction medium, so to speak, in particular via the outlet openings 70, so that the propellant medium, so to speak, pushes the suction medium (fuel) through the Exhaust openings 70 sucks through. As a result, the fuel in the swirl chamber 62 is atomized particularly advantageously.

14 shows a section of a claimed, seventh embodiment of the burner in a schematic longitudinal section view. In the seventh embodiment, the injection element 66 is designed according to the invention as a lance. It can be seen that the respective fuel jet 72, in particular its longitudinal axis or longitudinal central axis, runs with an imaginary part of the air flowing through the respective swirl chamber 62 or 76, 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 air flowing through the respective swirl chamber 62 or 76 Plane EB includes an angle β, also known as the beam angle. The axial direction of the respective swirl chamber 62 or 76 coincides with the longitudinal direction or longitudinal extent of the injection element 66 and thus with its axial direction. The outlet openings 70 are in the axial direction of the input Spray element 66 extending circumferential direction, in particular evenly, distributed and spaced apart from each other. In order to produce a fuel film that is as thin and uniform as possible on the film layer, that is to say on the inner circumferential 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, for example, as a bore, has a diameter, in particular an inner diameter, which is in a range from 50 mm to 3 mm inclusive.

15 shows a schematic and partially sectioned side view of a possible, unclaimed, further embodiment of the injection element 66. In the in 15 In the exemplary embodiment shown, the injection element 66 is designed as an injection nozzle, as used in heating oil burners. At the in 15 In the exemplary embodiment shown, the injection element 66 has a head 155, a swirl slot 156, a vortex body 158, a secondary filter 160 and a primary filter 162. The injection element 66 according to 15 has at least or exactly 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 from the outlet opening 70 and thus from the injection element 66 in the axial direction of the injection element 66 and thus the respective swirl chamber 62 or 76. In other words, proceeds accordingly 15 the fuel jet 72 or its longitudinal axis or longitudinal central axis at least substantially in the axial direction, that is, parallel to the axial direction of the respective swirl chamber 62 or 76.

16 shows a block diagram to illustrate an operation, in particular a control of the burner 42. A temperature of the exhaust gas at the introduction point E2 or downstream of the introduction point E2 and in particular upstream of the 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 a T5 value, which characterizes the temperature T5, is measured. The T5 value is in 16 illustrated by a block 164. The T5 value is transmitted to a block 166, in particular as an input variable. 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, that is, a release of the burner. As a result of the burner release, the ignition device 60 is switched on, i.e. activated, at a block 170. In a block 172, for example, a combustion air ratio of the mixture of 0.9 is set in order to realize start operation of the burner 42. Additionally, at block 172, for example, the air pump is activated and the fuel pump is activated. Then, for example, at block 174, the combustion air ratio of the mixture is set to 1.03, with the fuel pump operating at a low frequency. At block 176, for example, the ignition device 60 is deactivated. A block 178 illustrates an operating state of the burner 42. In the operating state, an air supply to or in the burner 42 is opened and the fuel pump is switched on and the igniter 60 is deactivated so that the burner 42 is supplied with the air and fuel becomes. An arrow 180 illustrates that the burner release is revoked, especially when the temperature T5 is greater than a limit value, which is, for example, 400 ° C.

At block 182, a comparison is made 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 the component 36b in the exhaust tract 26. If, for example, the comparison shows that the actual value is less than or equal to the target value, a state set in particular in block 174 is maintained, in particular with regard to the operation of the fuel pump and the air pump, with the fuel pump in 16 is illustrated by a block 184 and the air pump by a block 186. For example, if the actual value is greater than the target value, the fuel pump is activated in block 188, in particular by means of an electronic computing device, also known as a control device, and/or in block 190, in particular by the control device Control of the air pump, in particular in such a way that the fuel pump or the air pump is changed with regard to their respective operation, in particular in such a way that the actual value is reduced until, for example, the actual value corresponds to the target value or is smaller than the target value .

In a block 192, the amount of air in the mixture is determined, in particular measured, in particular by 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 (γ) 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 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 value of the combustion air ratio is compared with a second target value of the combustion air ratio, the second target value 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 combustion air ratio only deviate from the target value of the combustion air ratio in such a way that there is a difference between the actual value of the combustion air ratio and the target value of the combustion air ratio In particular, the amount is greater than or equal to a limit, then current operation of the burner 42, in particular the fuel pump and the air pump, is maintained. However, if the actual value of the combustion air ratio deviates excessively from the target value of the combustion air ratio, then, as shown in particular by an arrow 200, for example the air pump and / or the fuel pump is changed with regard to their respective operation, in particular by controlling the fuel pump respectively Air pump, in particular in such a way 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 combustion air ratio, in particular to block 198.

It can be seen that in the 1 to 17 illustrated embodiments, the insertion element is designed as the described injection element 66. According to the invention it is provided that - as for example in 13 can be seen - the insertion element is designed as a lance having a longitudinal extension direction, in whose outer circumferential lateral surface 148 extending around the longitudinal extension direction of the lance the respective outlet opening 70 is formed, the passage direction along which the outlet opening 70 can be flowed through by the fuel is, runs obliquely or preferably perpendicular to the longitudinal direction of the lance. The longitudinal direction of the lance is in 13 illustrated by the dashed line 150 and in the present case coincides with the axial direction of the swirl chambers 62 and 76. For example, the direction of passage of the outlet opening 70 coincides with, for example, in 14 particularly easily recognizable fuel jet 72, in particular with its longitudinal axis or longitudinal central axis, so that it is, for example, according to 14 It is provided that the direction of passage of the outlet opening 70 includes the angle β with the imaginary plane EB. So it is according to 14 it is provided that the passage direction of the respective outlet opening 70, also referred to as the flow direction, runs obliquely to the longitudinal direction of the lance and thus obliquely to the axial direction of the respective swirl chamber 62 or 76.

18 shows a detail in a schematic perspective view of a first embodiment of the in 18 with 204 designated insertion element, which in the first embodiment according to 18 - as will be explained in more detail - is designed as a pipette or in the manner of a pipette. The insertion element 204 has several and according to 18 exactly three outlet openings 70, which are arranged spaced apart and evenly distributed in the circumferential direction of the insertion element 204, which extends around the longitudinal direction and thus around the axial direction of the insertion element 204, the circumferential direction of which extends around the respective axial direction of the respective swirl chamber 62 or 76. The respective outlet opening 70 is formed by an elongated tube 206, which extends elongated away from a base body 208 of the insertion element 204 which has a longitudinal extension direction. The longitudinal extension direction of the base body 208 is the longitudinal extension direction of the insertion element 204 as a whole, with the longitudinal extension direction of the respective tube 206 running obliquely or, in this case, perpendicular to the longitudinal extension direction of the base body 208 and thus of the insertion element 204 as a whole. This is to be understood in particular as meaning that the respective tube 206 itself or its longitudinal extension direction is oblique or perpendicular to the axial Direction of the respective swirl chamber 62 or 76 runs. In particular, the tubes 206 are arranged around the base body 208, in particular evenly distributed, in the circumferential direction of the insertion element 204 and thus of the base body 208. For example, the respective longitudinal extension direction of the respective tube 206 coincides with the respective direction of passage of the respective outlet opening 70. In particular, the respective tube 206 delimits a respective outlet channel, which has the respective outlet opening 70 and thus opens via the respective outlet opening 70 to an environment of the insertion element 204 and thereby into the inner swirl chamber 62. The introduction element 204 is now designed to provide the liquid fuel from the introduction element 204 via the respective outlet opening 70 in a drop shape and thus drop by drop and thereby introduce it in a drop shape and thus drop by drop into the inner swirl chamber 62, in particular to drip it into the inner swirl chamber 62 and in particular drip directly onto the inner circumferential surface 86 of the component 74. As a result, a particularly thin and uniform film of the fuel can be formed on the inner peripheral surface 68, so that particularly good mixture preparation can be achieved. It can be seen that the introduction element 204 functions in the manner of a pipette, and therefore provides the fuel in the manner of a pipette, i.e. drop by drop, so that the introduction element 204 is also referred to as a pipetting nozzle.

19 shows a detail in a schematic perspective view of a second embodiment of the pipette-like or pipette-like insertion element 204. In the second embodiment according to 19 the insertion element 204 is lasered or designed as a lasered nozzle.

20 and 21 each show a section of a third embodiment of the insertion element 204, which functions as a pipette or works in the manner of a pipette 3 It can be seen that the insertion element 204, in particular on its head 208, has several and preferably or in the present case at least or exactly three outlet openings 70, which are arranged at a distance from one another and/or evenly distributed, in particular in the circumferential direction of the insertion element 204. The outlet openings 70 are supplied with fuel via a supply channel 210 common to the outlet openings 70. This is illustrated in 20 an arrow 212 shows the fuel or its flow through the supply channel 210 and to the outlet openings 70. Fluidically connected to the supply channel 210 are respective channels 214 through which the fuel can flow, which have the respective outlet openings 70 and thus into the inner swirl chamber via the outlet openings 70 62 mouths.

Finally shows 22 a fourth and fifth embodiment, each in part, in particular in half. In 22 The fourth embodiment of the insertion element 204 is shown on the left. In the fourth embodiment, the introduction element 204 has a drop-forming device 216, which has at least one spiral-shaped and thus forming a spiral first element and at least one, in particular several and, for example, or exactly three second elements. The respective second element is, for example, an at least essentially linear element. The respective second element or elements form, for example, a braid. In particular, the respective second element can be designed as a wire, so that the mesh is, for example, a wire mesh. The respective second element or the second elements run through spiral turns of the spiral, also known as turns. The device 216, in particular the respective second element, can be sprayed with the fuel flowing through the respective outlet opening 70. By means of the device 216, drops are formed from the fuel that is sprayed against the device 216, in particular against the respective second element, which are provided by the introduction element 204, in particular drop by drop, and in particular are dripped against the inner circumferential lateral surface 86.

In 22 The fifth embodiment is illustrated on the right. In the fifth embodiment, the insertion element 204 has a large number of outlet openings 70 designed as small holes, which are arranged in succession in the circumferential direction of the insertion element 204 extending around the longitudinal extension direction or around the axial direction of the insertion element 204 and are in particular spaced apart from one another and / or evenly distributed are arranged. As a result, the fuel can, so to speak, be dripped from the outside through the outlet openings 70 onto or against the inner peripheral surface 86 formed, for example, by an inner wall of the film layer (component 74), whereby a particularly uniform and thin film can be formed from the fuel. This allows a particularly advantageous mixture preparation to be achieved.

It is conceivable that the introduction element 66 or 204, particularly when it is designed as an injection element, forms a through which the fuel can flow and, for example, the outlet opening 70, in particular directly ndes or limiting element housing and an element valve, which is also referred to as an injection valve. The element valve is, for example, movable relative to the element housing, in particular translationally, between at least one closed position and at least one open position. In the closed position, the outlet opening is fluidically blocked by the element valve so that no fuel can flow through the outlet opening. In the open position, the element valve releases the outlet opening, whereby fuel can flow through the outlet opening and thus be provided, in particular sprayed out, by the introduction element. In the closed position, for example, the element valve, in particular a sealing surface of the element valve, sits on a corresponding valve seat, which is formed, for example, in particular directly, by the element housing. It is conceivable that the element valve is designed as a cone valve. This is to be understood in particular as meaning that the element valve has at least one at least essentially conical or cone-flow-shaped partial area through which the sealing surface is formed. In other words, it is conceivable that the sealing surface and preferably also the corresponding valve seat are conical or cone-flow shaped. Furthermore, it is conceivable that the element valve is a ball valve. This is to be understood in particular as meaning that the element valve is designed to be spherical or spherical segment-shaped, at least in a partial area, through which the sealing surface is formed, in particular directly. Expressed again in other words, it is conceivable that the sealing surface is spherical or spherical segment-shaped, and the corresponding valve seat can preferably also be spherical or spherical segment-shaped.

Reference symbol list

10

Drive device

12

Internal combustion engine

14

Engine block

16

cylinder

18

tank

20

Low pressure pump

22

high pressure pump

24

intake tract

26

Exhaust tract

28

Exhaust gas turbocharger

30

compressor

32

turbine

34

Wave

36a-d

component

38

Dosing device

40

Mixing chamber

42

burner

44

flame

46

Fuel supply path

48

Fuel line

50

Valve element

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

Exit opening

72

Fuel jet

74

Component

76

outer swirl chamber

78

partition wall

80

second outflow opening

82

Component

84

atomizer lip

86

inner circumferential surface

88

Anti-recirculation plate

90

Flow opening

92

Supply chamber

94

Swirl generator

96

Swirl generator

98

Flow opening

100

Perforated disc

102

discharge opening

104

Arrow

106

swirling flow

107

Swirl generating device

108

Passage opening

110

Closure device

112

Closure element

114

Opening cross section

116

Chamber element

118

inner circumferential surface

120

Chamber part

122

Chamber part

124

space

126

dashed line

128

exit cone

130

Double arrow

132

Closure element

134

thread

136

electrode

137

Fuel pump

138

electrode

139

Pistons

140

Valve

142

Feather

144

Bullet

146

front side

148

Lateral surface

150

dashed line

152

tube

154

Venturi nozzle

155

Head

156

Swirl slot

158

Vertebral body

160

Secondary filter

162

Primary filter

164

block

166

block

168

Arrow

170

block

172

block

174

block

176

block

178

block

180

Arrow

182

block

184

block

186

block

188

block

190

block

192

block

194

Arrow

196

block

198

block

200

Arrow

204

Insertion element

206

tube

208

Basic body

210

supply channel

212

Arrow

214

channel

216

Furnishings

E1

Induction point

E2

Induction point

V1

connection point

V2

connection point

T1

Part

T2

Part

T

Part

K

end edge

LK1

Air duct

LK2

Air duct

K1

Circular surface

K2

Circular surface

TB

Part

Tue

outer diameter

There

outer diameter

W

Wall areas

R

radius

α

angle

11

length

d1

Inner diameter

d2

Inner diameter

L1

Length range

β

angle

E.B

level

Claims (5)

Burner (42) for an exhaust gas tract (26) through which exhaust gas from an internal combustion engine (12) of a motor vehicle can flow, 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 flows and which causes a swirl-shaped 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), via which the first part of the air can be removed from the inner swirl chamber (62), - an introduction element (66, 204) having at least one outlet opening (70) through which the liquid fuel can flow and arranged in the inner swirl chamber (62), by means of which the fuel can be introduced into the inner swirl chamber (62) via the outlet opening (70), the first outflow opening (64) of which can also be flowed through by the fuel that has exited the introduction element (66, 204) via the outlet opening (70) and is thereby introduced into the inner swirl chamber (62), and - an outer swirl chamber (76) which surrounds at least one length region 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 swirl-shaped flow of the second part of the air, which is one of the second part of the air flowing through the outer swirl chamber (76), from which fuel flows through the first outflow opening (64) and from which the first part of the air flowing through the inner swirl chamber (62) and the first outflow opening (64) has a second outflow opening (80). , via which the parts of the air and the fuel can be introduced into the combustion chamber (58), the introduction element (66) being designed as a lance having a longitudinal direction of extension, in whose outer peripheral surface (148) running in the circumferential direction of the lance the outlet opening ( 70), the passage direction of which, along which the fuel can flow through the outlet opening (70), runs obliquely or perpendicularly to the longitudinal direction. Burner (42) after Claim 1 , characterized in that the first outflow opening (64) ends in the flow direction of the first part of the air flowing through the first outflow opening (64) at a specifically processed end edge (K), which is formed by an atomizer lip (84) which is in the flow direction of the The first part of the air flowing through the first outflow opening (64) tapers towards the end edge (K) and ends at the end edge (K). Burner (42) after Claim 2 , characterized in that the end edge (K) is specifically mechanically processed. Burner (42) after Claim 3 , characterized in that the end edge (K) is turned and/or ground and thereby specifically mechanically processed. Motor vehicle, with a burner (42) according to one of the preceding claims.

Images