How to turn on a car burner

Abstract

To provide a method for operating a burner in a motor vehicle, so that a particularly preferred operation of the burner can be realized. The present invention relates to a method of operating a burner (42), the burner (42) comprising a combustion chamber (58) in which a mixture including air and liquid fuel is ignited, and an inner swirl chamber (62) through which a first portion of the air is passed to cause a swirling flow of the first portion of the air, the inner swirl chamber having a first outlet opening (64) through which the first portion of the air passing through the inner swirl chamber (62) can pass, and through which the first portion of the air passes into the inner swirl chamber (62). The fuel injection member (66) has at least one outlet opening (70) arranged in the inner swirl chamber (62) and capable of being discharged from the inner swirl chamber (62) and through which a liquid fuel can be passed, whereby via the outlet opening (70) fuel can be injected into the inner swirl chamber (62), the first outlet opening (64) of which can also be passed through by fuel exiting the injection member (66) via the outlet opening (70) and thereby being injected into the inner swirl chamber (62).

Description

[Technical field]

[0001] The present invention relates to a method for operating a burner in a motor vehicle having an exhaust pipe through which the exhaust gases of an internal combustion engine can flow.

[0002] From the prior art in general and from the manufacture of series-produced vehicles in particular, motor vehicles are known which have an internal combustion engine and an exhaust gas system, also called exhaust pipe, through which the exhaust gases of the internal combustion engine, also called internal combustion engine, can flow. In some operating states and operating situations of the respective internal combustion engine, a high temperature of the exhaust gases may be desirable, for example in order to quickly heat up and / or to keep at a high temperature an exhaust gas aftertreatment device arranged in the exhaust pipe, but in such operating states and operating situations the temperature of the exhaust gases is insufficiently high.

[0003] The following patent document 1 discloses a burner for a motor vehicle having an exhaust pipe through which the exhaust gases of an internal combustion engine can flow. The burner has a combustion chamber in which a mixture comprising air and liquid fuel can be ignited and thereby burned. An inner swirl chamber is provided, through which a first portion of air can flow and which generates a vortex flow of the first portion of air. The inner swirl chamber is provided with an injection member having an outlet opening, by means of which fuel can be injected into the inner swirl chamber via the outlet opening. The inner swirl chamber is surrounded by an outer swirl chamber, through which a second portion of air can flow and which generates a vortex flow of the second portion of air. The inner swirl chamber has a first outlet opening and the outer swirl chamber has a second outlet opening, by means of which the air portions and the fuel can be introduced into the combustion chamber. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] German Patent No. 10 2006 015 841 B3 Summary of the Invention [Problem to be solved by the invention]

[0005] SUMMARY OF THE DISCLOSURE The object of the invention is to provide a method for operating a burner in a motor vehicle, in which a particularly preferred operation of the burner can be implemented. [Means for solving the problem]

[0006] This problem is solved by a method with the features of claim 1 as well as by a method with the features of claim 10. Advantageous embodiments according to expedient developments of the invention are defined in the further claims.

[0007] A first aspect of the invention relates to a method for operating a burner of a motor vehicle having an exhaust pipe through which exhaust gases of an internal combustion engine of the motor vehicle, also referred to as an internal combustion engine, can flow. This means that a motor vehicle, which may preferably be configured as a motor vehicle, particularly preferably as a passenger car, has an internal combustion engine and an exhaust pipe in a fully manufactured state and can be driven by the internal combustion engine. During the combustion operation of the internal combustion engine, a combustion process takes place in the internal combustion engine, particularly in at least one or more combustion chambers of the internal combustion engine, as a result of which exhaust gases of the internal combustion engine are generated. The exhaust gases flow out of the respective combustion chamber into the exhaust pipe and can subsequently flow through the exhaust pipe, also referred to as an exhaust system. At least one component, such as, for example, an exhaust gas aftertreatment element for aftertreatment of the exhaust gases, can be arranged in the exhaust pipe. The exhaust gas aftertreatment element is, for example, a catalytic device, in particular an SCR catalytic device, in which case selective catalytic reduction (SCR) can be catalytically supported and / or triggered, for example, by the SCR catalytic device. In selective catalytic reduction, nitrogen oxides possibly present in the exhaust gas are at least partially removed from the exhaust gas, which reacts with ammonia during selective catalytic reduction to form nitrogen and water. The ammonia is provided, for example, by a reducing agent, which is in particular a liquid. Furthermore, the exhaust gas aftertreatment element can be or include a particle filter, in particular a diesel particle filter, by means of which particles contained in the exhaust gas, in particular soot particles, can be filtered out of the exhaust gas.

[0008] The burner has a combustion chamber in which a mixture comprising air and liquid fuel can be ignited and thus burned. In particular, the combustion of the mixture in the combustion chamber produces burner exhaust gases, which are also called burner exhaust gases. The burner exhaust gases can, for example, leave the combustion chamber and enter the exhaust pipe, in particular at an inlet point that is arranged upstream of the respective components, for example in the direction of flow of the exhaust gases of the internal combustion engine through the exhaust pipe. As a result, the burner exhaust gases can, for example, flow through the respective components and thereby heat them, i.e. heat them up. It is also conceivable that the burner exhaust gases leave the combustion chamber and enter the exhaust pipe, thereby mixing with the exhaust gases of the internal combustion engine flowing through the exhaust pipe and / or with the gases flowing through the exhaust pipe, thereby heating the exhaust gases or gases of the internal combustion engine. In other words, a particularly high temperature of the exhaust gases or gases of the internal combustion engine, also called exhaust gas temperature, can be realized as a result. The exhaust gas or gases flow past the components, so that the components can be heated by the high exhaust gas temperatures. Thus, for example, exhaust gases from the combustion chamber are introduced into the exhaust pipe at the above-mentioned introduction points and are thus introduced into the exhaust gas or gases flowing through the exhaust pipe. For example, an ignition device, which can be activated in particular electrically, is arranged in the combustion chamber, with which at least one ignition spark can be provided, i.e. generated, for ignition of the mixture, for example, in particular in the combustion chamber and / or with the aid of electrical energy or current. The ignition device is, for example, a glow plug or a spark plug.

[0009] The burner has an inner swirl chamber through which the first portion of the air forming the mixture can flow, which generates a swirling flow of the first portion of the air, and which is therefore preferably arranged upstream of the combustion chamber as viewed in the direction of flow of the first portion of the air flowing through the inner swirl chamber. The inner swirl chamber has, in particular, exactly one first outlet opening through which the first portion of the air flowing through the inner swirl chamber can be discharged from the inner swirl chamber and, for example, can be introduced into the combustion chamber. The feature that the inner swirl chamber causes or is able to cause a vortex flow of the first part of the air flowing through the inner swirl chamber is understood in particular as meaning that the first part of the air flows vortically through the swirl chamber, i.e. flows vortically through at least one length region of the swirl chamber and / or has a vortex flow at least in a first flow region arranged downstream of the inner swirl chamber and outside the inner swirl chamber, for example arranged in a combustion chamber. In particular, it is conceivable that the first part of the air flows vortically out of the inner swirl chamber via a first outlet opening and / or flows vortically into the combustion chamber, so that the first part of the air has its vortex flow at least in the combustion chamber.

[0010] The burner further has an injection element, in particular an injection element, with at least one or just one outlet opening through which the liquid fuel can flow. The outlet opening is arranged in the inner swirl chamber, so that the injection element, in particular the injection element or the passage of the injection element, which can be penetrated by the liquid fuel, communicates with the inner swirl chamber via the outlet opening. By means of the injection element, the fuel flowing through the outlet opening can be injected, in particular injected, in particular directly through the outlet opening into the inner swirl chamber, so that the first outlet opening can also be penetrated by the liquid fuel, which exits, in particular is ejected, from the injection element via the outlet opening, thereby being injected, in particular injected, in particular directly into the inner swirl chamber. This means in particular that a first portion of the air and the fuel can flow through the first outlet opening along a common first flow direction and thereby exit the inner swirl chamber.

[0011] The burner further comprises an outer swirl chamber, which surrounds at least one length region of the inner swirl chamber, and preferably also the first outlet opening, in the circumferential direction of the inner swirl chamber, in particular completely around it. The circumferential direction of the inner swirl chamber then for example runs around the above-mentioned first flow direction, which for example coincides with the axial direction of the inner swirl chamber and thus of the first outlet opening. Preferably, the inner swirl chamber is intended to end at the first outlet opening or its end in the flow direction of the first part flowing through the first outlet opening and thus in the axial direction of the inner swirl chamber and thus of the first outlet opening. The outer swirl chamber can be passed through by the second part of air and is designed to generate a swirling flow of the second part of air. This is understood in particular to mean that the second part of the air flows in the outer swirl chamber, i.e. flows swirl-like through at least one partial region or length region of the outer swirl chamber, and / or has a swirling flow in a second flow region, which for example corresponds to the above-mentioned first flow region and is arranged downstream of the outer swirl chamber as seen in the flow direction of the second part of the air flowing through the outer swirl chamber, the second flow region for example being arranged outside the outer swirl chamber and for example inside the combustion chamber. It is further conceivable that the above-mentioned first flow region is arranged outside the outer swirl chamber. In other words, it is conceivable that the second part of the air flows swirl-like out of the outer swirl chamber and / or flows swirl-like into the combustion chamber, and it is therefore preferably intended that the second part of the air has a swirling flow at least in the combustion chamber.

[0012] The outer swirl chamber has, for example, in particular just one second outlet opening, for example arranged downstream of the first outlet opening as seen in the flow direction of the portions and the fuel, through which the second portion of air can be discharged from the outer swirl chamber and through which the portions of air and the fuel can be introduced into the combustion chamber, through which the second portion of air can be discharged from the outer swirl chamber and through which the portions of air and the fuel can be introduced into the combustion chamber. In particular, the portions of air and the fuel can flow through the second outlet opening along a second flow direction and thus enter the combustion chamber through the second outlet 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 intended that the second flow direction extends in the axial direction of the outer swirl chamber and thus coincides with the axial direction of the outer swirl chamber, such that the axial direction of the inner swirl chamber corresponds to the axial direction of the outer swirl chamber or vice versa. In other words, it is preferably intended 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 extends perpendicular to the respective axial direction of the respective swirl chamber. For example, the second outlet opening is arranged along the respective flow direction, i.e. downstream of the first outlet opening as seen from the flow direction of the respective portion of air and the flow direction of the fuel, preferably the outer swirl chamber surrounds the first outlet opening, so that for example the first outlet opening is arranged in the outer swirl chamber. In particular, it is conceivable that the outer swirl chamber terminates at the second outlet opening, in particular at its end, in particular in the flow direction of the second portion of air flowing through the second outlet opening.

[0013] For example, in order to generate a respective vortex flow, the respective vortex chamber can have at least one or a number of vortex generators, by means of which the respective vortex flow can be generated or is generated. In particular, the respective vortex generators are arranged in the respective vortex chamber. In particular, the vortex generators are, for example, guide vanes, by means of which, for example, the respective portions, i.e. the respective air forming the respective portions, are redirected at least once or exactly once, in particular by at least or exactly by 70 degrees, in particular by approximately 90 degrees, i.e. for example by 70 degrees to 90 degrees. In particular, a vortex flow is understood to be a flow that extends in a vortex-like or at least substantially vortex-like or helical manner around the respective axial direction of the respective vortex chamber or of the respective outlet opening. In particular, the respective axial direction of the respective outlet opening extends perpendicularly to the plane in which the respective outlet opening extends. In this case, for example, the respective axial direction of the respective outlet opening coincides with the respective axial direction of the respective vortex chamber. The respective outlet openings are also called, for example, respective nozzles, although their cross sections, which can be passed through by the respective portions of air, do not necessarily have to be tapered along the respective flow direction. Thus, for example, the second outlet opening is also called the outer nozzle or second nozzle, and the first outlet opening is also called, for example, the inner nozzle or first nozzle.

[0014] Due to the respective vortex flows being generated, the air can be mixed particularly favorably, especially over a very short mixing path, with the liquid fuel, especially in the combustion chamber, so that a particularly favorable mixture pretreatment is realized, i.e. the mixture can be formed particularly favorably. In particular, the fuel can first be mixed particularly well with the first portion of the air, especially in the inner vortex chamber, due to the vortex flow of the first portion in the inner vortex chamber. Furthermore, the fuel, and for example the first portion already mixed with the fuel, can be mixed particularly favorably with the second portion of the air, especially in the outer vortex chamber and / or in the combustion chamber, since the second portion of the air also has a favorable vortex flow. Overall, due to the vortex flow, the air portions can be mixed particularly favorably with the fuel, so that a favorable mixture pretreatment can be realized.

[0015] In order for a component, for example configured as an exhaust gas aftertreatment device or exhaust gas aftertreatment system, to be able to be heated particularly quickly and effectively, especially when the exhaust gases of an internal combustion engine only have a low temperature, it is preferable for the first outlet opening (first or inner nozzle) to be designed in such a way that in the flow direction of the first portion of the air flowing through the first outlet opening and thus in the flow direction of the fuel flowing through the first outlet opening, it ends with a sharp or knife-sharp end edge, which is formed by an atomizing lip, in particular configured as a solid, which ends at the end edge in such a way that in the flow direction of the first portion of the air flowing through the first outlet opening and thus in the flow direction of the fuel flowing through the first outlet opening, it tapers towards the end edge. This means that the atomizing lip has a taper that tapers in the first flow direction, and thus in particular towards the combustion chamber, and which ends in particular only at the end edge. As a result, and in particular by means of a precise machining of the end edge, the taper or atomizing lip is formed into a sharp edge, in other words the atomizing lip ends in a sharp edge, so that a particularly favorable mixture pretreatment can be achieved.

[0016] For example, the mixture is burned in the combustion chamber with the formation of a flame, and in particular the fuel can be mixed favorably with the air by the vortex flow, and in particular the flame in the combustion chamber can be favorably stabilized by the vortex flow. In particular the vortex flow can cause a combustion-induced vortex breakdown to occur. For this purpose, for example the air flowing into the combustion chamber is redirected in the respective vortex chamber by, for example, about 70° or about 90°, in particular within the range of 70° to 90°, which can be realized for example by a respective vortex generator. The inner vortex chamber and the outer vortex chamber form, for example, a vortex chamber, also called the overall vortex chamber, which is divided according to the invention into the inner vortex chamber and the outer vortex chamber. The inner vortex chamber and the outer vortex chamber are preferably separated from each other, in particular in the radial direction of the respective vortex chamber, by a separating wall, which is preferably formed as a solid body. It is then conceivable that the separating wall surrounds at least the aforementioned length region of the inner swirl chamber, particularly completely, in the circumferential direction of the inner swirl chamber, which runs around the axial direction of the inner swirl chamber, so that, for example, at least the length region of the inner swirl chamber is formed or defined, particularly directly, by the separating wall, radially outwardly of the inner swirl chamber. It is also conceivable that at least one second length region of the outer swirl chamber is formed or defined, particularly directly, by the separating wall, radially inwardly of the outer swirl chamber. It is then conceivable, in particular, that the length regions of the respective swirl chambers are arranged at the same height in the axial direction of the respective swirl chamber. During operation of the burner, the outer swirl chamber is traversed exclusively by air, i.e. only by the second portion of air, whereas or during this, the inner swirl chamber is traversed by air, i.e. by the first portion and by liquid fuel. In this way, a favorable mixing of the first portion of air with the fuel can already be achieved in the inner swirl chamber. The injection member, in particular the injection member, may be an injection nozzle, the outlet opening of which is arranged, for example, in or on a front or end face of the injection member, the front or end face of the injection member extending in a front or end plane that extends perpendicular to the axial direction of the respective swirl chamber.It is further conceivable that the injection element is configured as a lance, for example with a longitudinal extension coinciding with the respective axial direction of the respective swirl chamber or the respective outlet opening. The lance then has an outlet opening, which may be configured as at least one or exactly one, in particular at least two or exactly two, holes, in particular as a cross hole. The outlet opening has a through-direction along which the outlet opening can be pierced by the fuel. In particular, if the injection element is configured as an injection nozzle, the through-direction of the outlet opening runs parallel to the respective axial direction of the respective swirl chamber or the through-direction coincides with the respective axial direction of the respective swirl chamber or the respective outlet opening. In particular, if the injection element is configured as a lance, the through-direction runs obliquely or preferably perpendicularly to the axial direction of the respective swirl chamber or the respective outlet opening.

[0017] In particular, it is conceivable that at least the inner swirl chamber is constituted by a component, in particular formed as a solid, which also forms the atomizing lip and thus also the end edge. In particular, the inner circumferential outer surface of this component defines the inner swirl in the radial direction of the inner swirl chamber toward the outside. In this case, for example, this component, in particular its inner circumferential outer surface, is or functions as a film attachment between the respective swirl chambers and thus between the respective vortex-like and thus swirled flows, also called air flows. In particular, it is conceivable that the inner circumferential outer surface or the film attachment is formed by the above-mentioned separation wall or that the component forms or has the above-mentioned separation wall. In this case, the fuel, in particular ejected, which flows through the outlet opening and thus exits the injection element, is applied to the film attachment, in particular as a film, also called a fuel film, in particular on the inner circumferential outer surface, or is sprayed on the film attachment between the two swirled air flows. Due to the centrifugal force resulting from the vortex flow of the first part of air, the fuel that leaves the injection element, in particular is ejected and is thereby injected, in particular directly into the inner vortex chamber, in particular is injected, i.e. nozzle-injected, adheres to the film attachment, in particular as a film as mentioned above, in particular on the inner circumferential jacket surface, and flows or flows downstream, towards the first outlet opening, also called nozzle opening, and therewith towards the end edge, i.e. the fuel is applied to the atomizing lip and is carried or transported to the end edge. For example, the first outlet opening ends with a knife-sharp end edge, which has or does not provide a small area due to the above-mentioned taper, so that excessively large droplets of fuel are not formed at the end edge. Due to the configuration of the atomizing lip and in particular the end edge, only very small droplets of fuel are separated off at the end edge. In other words, only particularly small, i.e. minute, droplets are generated at the end edge from the fuel film mentioned above, which detach from the end edge, in particular from the atomizing lip or component, and have a correspondingly large surface area. This effect leads to a particularly soot-free combustion of the mixture in the combustion chamber.As a result, very small droplets of fuel can be produced without expensively produced high injection pressures of the fuel and without cost-intensive injection elements, so that on the one hand the costs of the burner can be kept particularly low. On the other hand, since particularly small droplets of fuel can be produced, a very low burner output can also be realized. The invention is particularly based on the finding that conventional burners have excessively high pressure losses and are therefore unsuitable for low outputs and are therefore disadvantageous in terms of fuel consumption. The problems and disadvantages mentioned above can only be avoided by the invention, so that in particular the fuel consumption can be kept particularly low. When referring below to an injection element, this is understood to mean an injection element.

[0018] If reference is made below to the gases flowing through the exhaust pipe, this is understood to mean the exhaust gases of the above-mentioned internal combustion engines or the above-mentioned gases, unless otherwise stated. The above-mentioned inlet points at which the burner exhaust gases can be introduced into the exhaust pipe or into the gases can be arranged in the exhaust pipe downstream or upstream of an oxidation catalyst device, for example configured as a diesel oxidation catalyst, seen in the flow direction of the gases flowing through the exhaust pipe. The oxidation catalyst device is configured in particular for the oxidation of unburned hydrocarbons (HC) which may be present in the exhaust gas and / or for the oxidation of carbon monoxide (CO) which may be present in the exhaust gas, in particular to carbon dioxide.

[0019] In order to operate the burner particularly favorably and thus to heat up the components particularly quickly and effectively and / or to keep them at high temperature, a first aspect of the invention provides that the power fuel is injected, particularly directly, into the inner swirl chamber by the injection member, particularly by the injection member, during a particularly definable or set time period in order to start the initially deactivated burner. The requirement that the first time period is, for example, definable or set, is understood in particular as the length of the first time period being set or definable. The feature that the burner is started and the feature that the burner is initially deactivated are understood in particular as the burner being consistently deactivated during a second time period, particularly directly preceding the first time period, whereby during the second time period, particularly consistently, no injection, particularly injection, of the power fuel into the inner swirl chamber, no active supply of air to the swirl chamber and no ignition in the combustion chamber occurs, i.e. does not take place. The feature that the second time period directly precedes the first time period is understood in particular as meaning that there is no further time period between the first and second time periods, whereby the second time period preferably ends with the start of the first time period or vice versa, the first time period starts with the end of the second time period. In particular, the first time period starts with the injection, in particular injection, of the motive fuel into the inner swirl chamber by the injection member. In particular, it is intended that during the first time period the motive fuel is injected, in particular directly, into the inner swirl chamber by the injection member in a continuous manner, i.e. without interruption. Furthermore, according to the invention, it is intended that during the first time period there is no active supply of air to the swirl chamber and no ignition in the combustion chamber.Active supply to the swirl chamber is understood as air being actively sent to the swirl chamber and thus to the burner by a delivery device also called or configured as an air pump, i.e. by active operation of the air pump, so that the swirl chamber is supplied with air and thus with air portions, but such an active supply of air and thus with air portions does not occur during the first time period and preferably also during the second time period. The feature that one or more ignitions do not occur in the swirl chamber during the first time period and preferably also during the second time period is understood in particular as an active ignition process does not take place or is not carried out in the swirl chamber, which would be able to ignite the mixture in the swirl chamber if the mixture was there, so that e.g. an ignition spark or other ignition events do not take place in the swirl chamber, in particular during the first time period and preferably also during the second time period.

[0020] It is further provided according to the invention that after the first time period, i.e. after the first time period has elapsed, air is actively supplied to the swirl chamber, in particular by the delivery device, and a power fuel is injected, in particular injected, into the inner swirl chamber by the injection device, thus generating a mixture in the combustion chamber, which is in particular actively ignited, in particular by the ignition device or the aforementioned ignition device, for example, the ignition device generates at least one ignition spark, in particular provided to the combustion chamber. In other words, the first time period is in particular directly followed by a third time period, which preferably lasts at least 10 seconds. It is thus provided that preferably the first time period ends with the start of the third time period, or vice versa, the third time period starts with the end of the first time period. In particular, the third time period is initiated by the active supply of air to the swirl chamber, in particular by the activation of a delivery device, which is, for example, initially deactivated, and which is, for example, consistently deactivated, i.e. not activated, during both the first time period and the second time period. Furthermore, for example, the third time period is initiated by the activation of an ignition device, which is, for example, configured as a glow lamp, glow pin or spark plug, and which is, for example, initially deactivated, and which is, for example, consistently deactivated during both the first time period and the second time period.

[0021] During the third time period, the swirl chamber is actively supplied with air, in particular by actively delivering air towards and into the swirl chamber by the delivery device. For example, the delivery device can be electrically actuated or is actuated. Furthermore, during the third time period, the fuel is injected, in particular injected, into the inner swirl chamber by the injection element. It is conceivable that the fuel is injected into the inner swirl chamber by the injection element continuously, i.e. without interruption, during the third time period, or that several injections, in particular injections, spaced apart in time, are carried out by the injection element during or within the third time period, in which the fuel is respectively injected, in particular directly, into the inner swirl chamber by the injection element. The air is actively supplied to the swirl chamber so that the air and therefore the parts flow through the swirl chamber, and by the active supply of air to the swirl chamber and by the injection of the motive fuel into the inner swirl chamber, in particular by injection, a mixture is formed, which is ignited and burned during or within the third time period. This means in particular that an ignition of the mixture takes place in the combustion chamber during the third time period, whereby the mixture in the combustion chamber is burned in or within the third time period, in particular without interruption. Thus, it is intended that during the first time period and during the second time period, the burner does not provide a flame or burner exhaust gases. However, during the third time period, the burner provides, in particular consistently or without interruption, burner exhaust gases resulting from the ignition and combustion of the mixture or a flame resulting from the ignition and combustion of the mixture, whereby the components can be heated and / or kept at a high temperature. During the first time period, the power fuel is injected into the inner swirl chamber, but no active supply of air to the swirl chamber and no ignition in the combustion chamber occurs, so that a sort of pre-dosing of the power fuel in the inner swirl chamber is realized or carried out. The invention is based on the following knowledge and consideration: when starting an initially deactivated burner, which is performed in particular as a cold start, neither high temperatures nor large air movements are yet present in the respective swirl chamber. This condition does not allow ignition of the mixture in the combustion chamber, or at least makes such ignition difficult.The method according to the invention thus allows the start-up of an initially deactivated burner quickly and efficiently, particularly also during operation of the internal combustion engine and / or under low ambient conditions, for which an ignitable mixture in the combustion chamber is advantageous, which can be achieved by the pre-dosing of power fuel according to the invention.

[0022] It has been found to be particularly advantageous if the first time period lasts at least 0.3 seconds, so that an ignitable mixture can be established in the combustion chamber, which allows the burner to be started quickly and efficiently.

[0023] In order to start the burner quickly, efficiently and effectively, i.e. with low fuel consumption, in another embodiment of the invention it is provided that the first time period lasts for a maximum of 6 seconds, in particular for a maximum of 4 seconds, in other words preferably for the first time period to last for 0.3 to 6 seconds, in particular for 0.3 to 4 seconds, in particular consistently or without interruption.

[0024] The fuel pre-dosing according to the invention results in the formation of a particularly rich mixture in the combustion chamber, which provides a large fuel surface suitable for ignition despite the large droplets and despite the high mass.

[0025] In order to embody a particularly effective operation of the burner, in another embodiment of the invention, it is provided that at least after the time period, i.e. for example during the third time period, a first amount of air and a second amount of fuel are determined by an electronic calculation device, also called a control device. In other words, in or during the third time period or after the first time period, a first amount of air actively supplied to the swirl chamber is determined after the time period by the electronic calculation device. In other words, after the first time period, i.e. for example during the third time period, a first amount of air supplied to the swirl chamber in a particularly active manner, i.e. for example by the operation of an air pump, is determined by the electronic calculation device. Furthermore, after the first time period, i.e. for example during the third time period, a second amount of fuel injected into the inner swirl chamber by the injection member in its interior after the first time period, i.e. during the third time period, is determined by the electronic calculation device. The first amount is also called air amount or air mass, and the second amount is also called fuel amount or fuel mass. For example the air amount is calculated in particular by the electronic calculation device and determined thereby. It is further conceivable that the air quantity is measured, in particular by a first sensor. For example, the first sensor provides a first signal, in particular electrical, characterizing at least the air quantity measured by the first sensor. The electronic computing device receives the first signal and can thereby determine, in particular, the measured air quantity. It is further conceivable that, for example, the fuel quantity is calculated, and thereby determined, by the electronic computing device. It is further conceivable that, for example, the fuel quantity is measured by a second sensor. The second sensor provides a second signal, in particular electrical, characterizing the fuel quantity measured by the second sensor. The electronic computing device receives, for example, the second signal and can thereby determine, in particular, the measured fuel quantity. It is further intended that, preferably, after the first time period, i.e. for example during a third time period, at least one actual value of the combustion air ratio of the mixture, also called lambda (Greek small letter lambda), is determined, in particular calculated, on the basis of the first quantity and on the basis of the second quantity by the electronic computing device.Furthermore, it is preferably provided that the burner is operated on the basis of the actual values ​​determined by the electronic computing device after the first time period and thus during the third time period. In this way, the lambda control preferably provides for a lambda-controlled operation of the burner, which makes it possible to ensure a particularly efficient and effective operation of the burner.

[0026] It is indicated here as being particularly preferred if the electronic computing device controls the injection element, in particular electrically, in particular after the first time period and thus in or during the third time period on the basis of the determined actual values, so that the burner is operated on the basis of the determined actual values, whereby the injection element, for example, the fuel quantity is regulated, in particular controlled, by the electronic computing device via the injection element, so that a particularly efficient and effective operation of the burner can be achieved.

[0027] A further embodiment is characterized in that an air pump as described above is provided, by means of which air is actively pumped to the swirl chamber and thereby towards and into the burner, or in particular during the third time period. Alternatively or additionally, a fuel pump is provided, by means of which fuel is actively pumped towards and through the injection member and thereby through the injection member and thereby via the injection member to the inner swirl chamber. In particular, the fuel pump can be or is intended to be electrically operable. In other words, the fuel pump is actively operated during the third time period, by which liquid fuel is actively pumped towards and in particular through the injection member by the fuel pump, by which fuel is injected via the injection member into the inner swirl chamber. The fuel pump is then, for example, electrically operated during the third time period. Thus, with regard to the first and second time periods, it is preferably intended that during the second time period the air pump and the fuel pump are deactivated, i.e. not operating, so that during the second time period no air is pumped by the air pump into the swirl chamber. Furthermore, it is preferred that during the second time period no fuel is pumped by the fuel pump towards and through the injection member. For example, in order to pre-dosing fuel during the first time period, i.e. to inject fuel by the injection member into the inner swirl chamber, the fuel pump is in particular actively operated during or within the first time period, so that for example the first time period is started with the initially deactivated fuel pump being activated, in particular the air pump being kept deactivated during it. Furthermore, it is conceivable that during the third time period both the fuel pump and the air pump are activated, in particular in an electrically operated manner, so that for example the third time period is started with the initially deactivated air pump being activated, i.e. starting to operate.

[0028] In order to realize a particularly precise lambda control of the burner, in another embodiment of the invention, it is provided that a frequency-controlled piston pump is used as the fuel pump, which, in particular, a frequency-controlled piston pump allows the fuel to be delivered or metered in particularly precisely, so that the fuel quantity and thus also the fuel consumption can be determined, in particular calculated, particularly precisely.

[0029] The piston pump has, for example, a pump housing through which the fuel can flow and a piston, also called a delivery piston, which is accommodated at least partially, in particular at least to the majority or entirely, in the pump housing. The piston is movable, in particular translationally, relative to the pump housing along a piston direction, thereby delivering the fuel. The piston pump, in particular the pump housing, has a discharge, via which the fuel flowing through the pump housing and delivered by the piston can be discharged from the pump housing and thus delivered out of the fuel pump, for example to an injection member. It is here provided that a spring-loaded valve, for example configured or functioning as a non-return valve, is arranged in the discharge. This valve thus includes, for example, a valve body and, in particular, a mechanical spring. In particular, if the valve body is configured as a ball, this valve is configured as a ball valve. The valve body is movable, in particular translationally, for example, relative to the pump housing, between at least one closed position and at least one open position. In the closed position, the valve body completely blocks the outlet, while in the open position, the valve body opens. In this case, the valve body or valve is preferably intended to open in the direction of the injection member, i.e. to open the outlet, and to block or close the outlet in the opposite direction, and thus, for example, in the direction of the piston or in the direction of the inside of the piston housing. As a result, the piston can deliver fuel through the outlet and thus out of the piston housing towards the injection member, while the flow of fuel or other fluids, such as, for example, exhaust gas, in the opposite direction from the combustion chamber can be prevented by the valve body or valve, since the valve or valve body blocks the outlet against the flow of fluids, such as, for example, exhaust gas, from the combustion chamber coming from the injection member into the pump housing. In this way, the valve can prevent a backflow of fuel or exhaust gas.

[0030] In order to realise a particularly efficient and effective operation of the burner, in another embodiment of the invention, it is intended that the electronic computing device controls, in particular electrically, the air pump and / or the fuel pump on the basis of the determined actual value, thereby operating the air pump and / or the fuel pump on the basis of the determined actual value, and thereby operating the burner on the basis of the determined actual value, so that the combustion air ratio can be adjusted particularly accurately and quickly, in particular to a desired target value, which is preferably in the range of 0.95 to 1.05, preferably 1.03.

[0031] A further embodiment is characterized in that the actual value is compared with a setpoint value, which can in particular be set or is set by the electronic computing device, and the burner is activated on the basis of the comparison between the actual value and the setpoint value. In this case, in particular, it is conceivable for the electronic computing device to control and thereby activate the injection element and / or the fuel pump and / or the air pump on the basis of the comparison between the setpoint value and the actual value, and in this case in particular on the basis of the difference, in particular electronically, whereby the burner is activated and in particular controlled on the basis of the comparison. As a result, a particularly precise lambda control can be achieved.

[0032] In order to realise a particularly favourable, particularly effective and efficient operation of the burner, a second aspect of the invention provides that a first amount of air, also called air amount, and a second amount of fuel, also called fuel amount, are determined by the electronic calculation device, also called control device. Based on the first amount and based on the second amount, at least one actual value of the combustion air ratio of the mixture is determined, in particular calculated, by the electronic calculation device. Furthermore, the burner is operated based on the determined actual value by the electronic calculation device. A particularly favourable lambda control of the burner can thereby be realised, whereby a particularly effective and efficient, in particular low-fuel consumption, effective and efficient, in particular low-fuel consumption and emission-free operation of the burner can be realised. Advantageous and advantageous embodiments of the first aspect of the invention can be regarded as advantageous and advantageous embodiments of the second aspect of the invention and vice versa.

[0033] Further advantages, features and details of the invention will become apparent from the following description based on preferred embodiments and drawings. The features and combinations of features mentioned in the above description and in the following description of the figures and / or shown only in the figures can be used not only in the respective combinations presented, but also in other combinations or alone without departing from the scope of the invention. [Brief description of the drawings]

[0034] [Figure 1] 1 is a schematic diagram showing a drive system for a motor vehicle, comprising an internal combustion engine, an exhaust pipe and a burner according to the invention; [Diagram 2] FIG. 1 is a schematic vertical cross-sectional view showing a burner according to a first embodiment. [Diagram 3] FIG. 1 is a schematic vertical cross-sectional view partially showing a burner according to a first embodiment. [Figure 4] FIG. 2 is a schematic longitudinal sectional view showing components of the burner according to the first embodiment. [Diagram 5] FIG. 6 is a schematic vertical cross-sectional view showing a burner according to a second embodiment. [Figure 6] FIG. 11 is a schematic rear perspective view partially illustrating a burner according to a third embodiment. [Figure 7] FIG. 11 is a schematic vertical cross-sectional view showing a burner according to a third embodiment. [Figure 8] FIG. 2 is a schematic perspective cutaway view partially illustrating a swirl generating device of the burner; [Figure 9] FIG. 2 is a schematic perspective view showing a vortex generating device. [Figure 10] FIG. 2 is a schematic front view showing the closing device. [Figure 11] FIG. 10 is a schematic vertical sectional view partially showing a burner according to a fourth embodiment. [Figure 12] FIG. 10 is a schematic vertical sectional view partially showing a burner according to a fifth embodiment. [Figure 13] FIG. 13 is a schematic vertical cross-sectional view partially showing a burner according to a sixth embodiment. [Figure 14] FIG. 13 is a schematic vertical sectional view partially showing a burner according to a seventh embodiment. [Figure 15] FIG. 2 is a schematic partial cutaway side view showing an injection member of a burner. [Figure 16] FIG. 4 is a block diagram showing the operation of burner 42. [Figure 17] FIG. 2 is a schematic cross-sectional view showing a fuel pump for delivering fuel to a burner. [Figure 18] FIG. 1 is a system diagram illustrating a method for operating a burner. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0035] In the drawings, identical or functionally identical elements are provided with the same reference numbers.

[0036] FIG. 1 shows a schematic diagram of a drive 10 of a motor vehicle, which is preferably configured as a power vehicle, in particular as a passenger car. This means that a motor vehicle configured as a land vehicle has the drive 10 in the fully manufactured state and can be driven by the drive 10. The drive 10 has an internal combustion engine 12, also called internal combustion engine, which has an engine block 14, also called engine housing. The internal combustion engine 12 further has cylinders 16, which are in particular directly formed or delimited by the engine block 14. During the combustion operation of the internal combustion engine 12, the respective combustion process takes place in the cylinders 16, from which the exhaust gases of the internal combustion engine 12 are generated. For this purpose, in particular liquid power fuel is injected, in particular directly injected, into the respective cylinders 16 within the respective working stroke of the internal combustion engine 12. The internal combustion engine 12 can be configured as a diesel engine, so that the power fuel is preferably diesel fuel. A tank 18, also called a power fuel tank, is provided here, in which the power fuel can be or is contained. Each cylinder 16 is assigned, for example, a respective injector, by means of which the fuel can be injected, in particular directly injected, into the respective cylinder 16. A low-pressure pump 20 delivers the fuel from the tank 18 to a high-pressure pump 22, by means of which the fuel is delivered to the injectors or to a fuel distribution member, also called a rail or common rail, common to the injectors. The injectors can be supplied with fuel by the fuel distribution member, common to the injectors, from which the fuel can be injected, in particular directly injected, into the respective cylinder 16.

[0037] Here, the drive 10 comprises an intake manifold 24 through which the fresh air can flow, by means of which the fresh air flowing through the intake manifold 24 is guided towards and into the cylinders 16. The fresh air forms a mixture of fuel and fuel-containing air, which is ignited and thereby burned in the respective cylinder 16 within the respective working stroke. In particular, the fuel-air mixture is ignited by autoignition. The ignition and combustion of the fuel-air mixture results in the exhaust gases of the internal combustion engine 12, which are also called engine exhaust gases.

[0038] In this case, the drive 10 has an exhaust pipe 26 through which the exhaust gases from the cylinders 16 can flow. The drive 10 furthermore comprises an exhaust gas turbocharger 28 with a compressor 30 arranged in the intake pipe 24 and a turbine 32 arranged in the exhaust pipe 26. The exhaust gases can leave the cylinders 16, enter the exhaust pipe 26 and subsequently flow through the exhaust pipe 26. The turbine 32 can then be driven by the exhaust gases flowing through the exhaust pipe 26. The compressor 30 can be driven by the turbine 32, in particular via a shaft 34 of the exhaust gas turbocharger 28. When the compressor 30 is driven, the fresh air flowing through the intake pipe 24 is compressed by the compressor 30. A number of components 36a-36d are arranged in the exhaust pipe 26, which are each configured as exhaust gas aftertreatment devices, i.e. as exhaust gas aftertreatment components for aftertreatment of the exhaust gases. In the flow direction of the exhaust gases of the internal combustion engine 12 through the exhaust pipe 26, the components 36a-36d are arranged in succession and are thus connected in series or in series with one another. The 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 catalyst, also simply called 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 slip catalyst (ASC).

[0039] The motor vehicle has a structure that is configured as a monolithic body, which forms or defines an interior space of the motor vehicle, also called passenger cell or safety cell. During the respective driving of the motor vehicle, a person can be present in the interior space. For example, the structure forms or defines an engine compartment, in which the internal combustion engine 12 is arranged. For example, an exhaust gas turbocharger 28 is also arranged in the engine compartment. Furthermore, the structure has a floor, also called the main floor, by which the interior space is at least partially, in particular at least mostly or completely defined downwards in the vehicle height direction. Here, for example, the components 36a, 36b, 36c are arranged in the engine compartment, whereby for example the components 36a, 36b and 36c form a so-called hot end or form components of a so-called hot end (high temperature section). In particular, the hot end can be directly flange-connected to the turbine 32. The component 36d is arranged, for example, outside the engine compartment and below the floor as viewed in the vehicle height direction, so that, for example, the component 36d forms a so-called cold end or is a constituent element of a so-called cold end.

[0040] The drive 10 comprises a metering device 38, by means of which a reducing agent, particularly liquid, can be injected at the inlet point E1 into the exhaust pipe 26 and, for example, into the exhaust gas flowing through the exhaust pipe 26. The reducing agent is preferably an aqueous urea solution, which can react with nitrogen oxides possibly contained in the exhaust gas to give ammonia, which is reduced to water and nitrogen in a selective catalytic reduction process. The selective catalytic reduction can then be catalyzed and / or supported by an SCR catalyst. As can be seen from FIG. 1, the inlet point E1 is arranged upstream of the component 36b and downstream of the component 36a, as viewed in the direction of flow of the exhaust gas flowing through the exhaust pipe 26. The exhaust pipe 26 preferably has a mixing chamber 40, in which the reducing agent injected into the exhaust gas at the inlet point E1 can be mixed preferably with the exhaust gas.

[0041] Furthermore, the drive 10, and thus the motor vehicle, comprises a burner 42, by means of which at least one of the components 36b, 36c, 36d arranged downstream of the burner 42, as seen in the flow direction of the exhaust gases through the exhaust pipe 26, can be quickly and effectively heated and / or kept at a high temperature, as will be explained in more detail below. The burner 42 combusts the mixture, in particular forming a flame 44 and in particular providing a burner exhaust gas, which can or is introduced into the exhaust pipe 26 at the introduction point E2. This means, so to speak, that the burner 42 is arranged at the introduction point E2. In the embodiment shown in FIG. 1, the introduction point E2 is arranged upstream of the components 36b, 36c and 36d and downstream of the component 36a. In other words, in the embodiment shown in FIG. 1, the burner 42 is arranged upstream of the components 36b, 36c, 36d and downstream of the component 36a. Alternatively, it is also conceivable that the burner 42 or the inlet point E2 is arranged upstream of the component 36a and in particular downstream of the turbine 32. The above-mentioned mixture to be burned in or by the burner 42 comprises air and liquid fuel. In the embodiment shown in FIG. 1, a power fuel is used as this fuel and / or at least a partial amount of air is used, which can come, for example, from the intake pipe 24, which is fed to the burner 42 and used to form the mixture. For this purpose, a power fuel supply line 46 is provided which is fluidly connected on the one hand to the burner 42 and is fluidly connected or can be connected on the other hand to a power fuel line 48. The power fuel line 48 can be passed through by the power fuel flowing from the tank 18 to the injector or to the power fuel distribution member. In particular, the power fuel supply passage 46 is fluidly connected to the power fuel pipe 48 at a first connection point V1, which is located downstream of the low pressure pump 20 and upstream of the high pressure pump 22 in the flow direction of the power fuel flowing from the tank 18 to the power fuel distribution member or the respective injectors. At the connection point V1, at least a portion of the liquid power fuel flowing through the power fuel pipe 48 can be branched off from the power fuel pipe 48 and introduced into the power fuel supply passage 46.The motive fuel introduced into the motive fuel supply line 46 can flow through the motive fuel supply line 46 and is introduced as fuel from the motive fuel supply line 46 towards and in particular into the burner 42. A first valve member 50 is arranged here in the motive fuel supply line 46, by means of which the amount of fuel to flow through the motive fuel supply line 46 and thus to be supplied to the burner 42 can be adjusted. An electronic computing device 52, also called a control device here, is provided by means of which the valve member 50 is controlled, by means of which the amount of fuel to flow through the motive fuel supply line 46 and thus to be supplied to the burner 42 can be adjusted, in particular controlled, by the control device via the valve member 50.

[0042] Furthermore, an air supply line 54 is provided, via which or by means of which air for forming the mixture can be supplied to the burner or is supplied. This means that the air for forming the mixture can flow through the air supply line 54. A pump 56, also called an air pump, is arranged in the air supply line 54 here, by means of which air can be pumped through the air supply line 54 and thus to the burner 42. For example, a low-pressure pump 20, also called a low-pressure power fuel pump, also called a fuel pump, by means of which fuel can be pumped through the power fuel supply line 46 and thus to the burner 42.

[0043] It is clear that the air supply line 54 is fluidly connected to the intake pipe 24 at the second connection point V2. In this way, for example at the connection point V2 at least a portion of the fresh air flowing through the intake pipe 24 can be branched off from the intake pipe 24 and introduced into the air supply line 54. The fresh air introduced into the air supply line 54 can flow through the air supply line 54 as air and can be introduced by the air supply line 54 towards and in particular into the burner 42. A second valve element 55 is arranged in the air supply line 54 here, by means of which the amount of air flowing through the air supply line 54 and thus through the burner 42, which is used for the formation of the mixture, can be adjusted. The control device is then designed, for example, to control the valve element 55 so that the amount of air flowing through the air supply line 54 and thus through the burner 42, which is used for the formation of the mixture, can be adjusted, in particular controlled, by the control device via the valve element 55.

[0044] 2 shows a first embodiment of the burner 42 in a schematic cross-sectional view. The burner 42 has a combustion chamber 58 in which a mixture comprising air supplied to the burner 42 and liquid fuel supplied to the burner 42 is ignited and thereby combusted, i.e. ignited and thereby combusted during operation of the burner 42. For this purpose, an ignition device 60, for example configured as a spark plug or glow plug or glow pin, is provided, by means of which at least an ignition spark can be generated in the combustion chamber 58, in particular with the aid of electrical energy or electric current. By means of the ignition spark, the mixture in the combustion chamber 58 is ignited and combusted, in particular while providing the burner exhaust gases and / or while providing the flame 44. The burner exhaust gas or flame 44 can rapidly and effectively heat, for example, the exhaust gas flowing through exhaust pipe 26 and / or keep it at a high temperature, whereby at least component 36b can rapidly and effectively heat and / or keep it at a high temperature by the heated and / or kept at a high temperature exhaust gas flowing through components 36b, 36c and 36d.

[0045] The burner 42 has an inner swirl chamber 62 through which a first portion of air can flow, which is supplied to the burner 42, and which generates a swirling first flow of the first portion of air. This is understood in particular as the first portion of air flows swirlingly through at least one first partial region of the swirl chamber 62 and / or flows swirlingly out of the swirl chamber 62 and / or flows swirlingly in the combustion chamber 58. The inner swirl chamber 62 has in particular exactly one first outlet opening 64 through which the first portion of air can flow along a first through-direction of the outlet opening 64 and thus along a first flow direction which coincides with the first through-direction. Via the first outlet opening 64, the first portion of air can be discharged from the inner swirl chamber 62. This means that the first portion of air can flow out of the inner swirl chamber 62 via the first outlet opening 64. Burner 42 further includes an injection member in the form of an injection member 66 having a passageway 68 through which liquid fuel can flow to burner 42 .

[0046] In the first embodiment, the injection member 66 is configured as a lance, also called a power fuel lance. The passage 68 and thus the injection member 66 have at least one outlet opening 70 through which the liquid fuel flowing through the passage 68 can flow. As is clear from FIG. 2, in the first embodiment, the passage 68 and thus the injection member 66 have at least two, or exactly two, outlet openings 70, which are configured, for example, as bores. The outlet openings 70 can be pierced by the fuel along the respective second through-direction, so that the fuel flowing through the injection member 66 can be ejected or discharged from the injection member 66 via the respective outlet opening 70, and in particular can be injected directly into the inner swirl chamber 62, and thus can be injected. In other words, the injection member 66 or the passage 68 communicates with the inner swirl chamber 62 via the respective outlet opening 70, so that the liquid fuel can be injected by the injection member 66 via the respective outlet opening 70, in particular directly into the inner swirl chamber 62. The respective second through-direction of the respective outlet opening 70 coincides with a respective second flow direction, in which fuel can flow through the respective outlet opening 70. It is clear that fuel can be ejected from the injection element 66 via the respective outlet opening 70 while forming a respective fuel jet 72, and thus can be injected in particular directly into the inner swirl chamber 62. For example, the respective fuel jet 72, whose longitudinal axis coincides with the respective second through-direction or with the respective second flow direction, is at least substantially conically shaped. Furthermore, for example, the injection element 66 and thus the passage 68 in this example have a longitudinal direction or longitudinal extension or longitudinal extension direction which runs parallel to the first through-direction and thus runs parallel to the first flow direction, in particular which coincides with the first through-direction and thus with the first flow direction. As is further clear from FIG. 2, the first through-direction and thus with the first flow direction coincides with the axial direction of the outlet opening 64 and with the axial direction of the inner swirl chamber 62.In this case, the respective second penetration direction or the respective second flow direction extends perpendicular to the first penetration direction and therefore the first flow direction and to the axial direction of the swirl chamber 62 and the outlet opening 64, or, as in this example, obliquely.

[0047] The swirl chamber 62 is at least partially, in particular at least in large part, and thus more than half or even entirely, formed or defined by a preferably integrally configured component 74 of the burner 42, whereby the component 74 also forms or defines the outlet opening 64.

[0048] The burner 42 furthermore has an outer swirl chamber 76 which surrounds at least one length region and in this example also the first outlet opening 64 in a circumferential direction (axial direction) of the swirl chamber 62, which runs around the axial direction of the swirl chamber 62, in particular in a completely circumferential manner. Here, the component 74 has a separation wall 78 arranged between the swirl chambers 62 and 76 in the radial direction of the swirl chamber 62, the radial direction of which runs perpendicular to the axial direction of the swirl chamber 62. The swirl chambers 62 and 76 are thereby separated from one another by the separation wall 78 in the radial direction of the swirl chamber 65. The axial direction of the swirl chamber 62 coincides with the axial direction of the swirl chamber 76, whereby 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 passed through by a second portion of the air supplied to the burner 42 and is configured to generate a swirling second flow of the second portion of the air. This means that the second part of the air flows vortex-like through the swirl chamber 76 and / or flows vortex-like out of the swirl chamber 76 and / or flows vortex-like in the combustion chamber 58. In particular, it is preferably intended that each part of the air has a vortex-like flow in the combustion chamber 58, i.e. proceeds vortex-like in the combustion chamber 58. The outer swirl chamber 76 has in particular exactly one second outlet opening 80 through which the second part of the air flowing through the outer swirl chamber 76 can flow in particular along a third flow direction, the third through-direction through which the second part of the air flowing through the swirl chamber 76 can flow through the outlet opening 80, which in this example coincides with the axial direction of the swirl chamber 76 and thus with the axial direction of the swirl chamber 62. The third through-direction coincides with the third flow direction through which the second part of the air flowing through the outer swirl chamber 76 flows or can flow through the outlet opening 80. This means in particular that the first penetration direction coincides with the third penetration direction and the first flow direction coincides with the third flow direction, so that in this example the first flow direction, the third flow direction, the first penetration direction and the third penetration direction coincide with the axial direction of the swirl chamber 62 and with the axial direction of the swirl chamber 76.Seen in the direction of flow of the air portions, the second outlet opening 80 is arranged downstream of the outlet opening 64, and here in particular in series with the outlet opening 64, so that the outlet opening 80 can be passed through by the second portion of air, the first portion of air and the fuel. In particular, the first portion of air is mixed with the fuel already in the swirl chamber 62, in particular by virtue of the vortex-like first flow, forming in particular a partial mixture. This partial mixture can flow through the outlet opening 64 and thus leave the swirl chamber 62 and subsequently flow through the outlet opening 80, in particular by virtue of the preferred vortex-like second flow, and be mixed with the second portion of air, in particular by virtue of the preferred vortex-like second flow, so that the mixture is pre-treated in a particularly preferred manner, i.e. the partial mixture is mixed in a particularly preferred manner with the second portion.

[0049] It is clear that the swirl chamber 76 is at least partially, in particular at least for the most part, and therefore at least more than half or entirely defined radially inward of the respective swirl chamber 62 to 76 by the component 74, in particular by the separating wall 78. Radially outward of the respective swirl chamber 62 to 76, the swirl chamber 76 is at least partially, in particular at least for the most part, or entirely defined by a component 82, which in this example is configured separately from the component 74. Here, the component 74 is at least partially, in particular at least for the most part, arranged in the component 82. The outlet opening 80 is defined or formed, in particular in terms of the minimum or smallest flow cross-sectional area of ​​the outlet opening 80 through which the second part of the air can flow, for example by the component 82 and partially by the component 74.

[0050] 3, the first outlet opening 64 is intended to be precisely machined, in particular mechanically, in the flow direction of the first portion of air flowing through the first outlet opening 64 and thus in the flow direction of the fuel flowing through the first outlet opening 64, so that it terminates in a knife-sharp end edge K which extends all around the outlet opening 64, for example in a circumferential direction of the outlet opening 64 which runs around the axial direction of the outlet opening 64 and coincides with the axial direction of the respective swirl chamber 62 to 76. The knife-sharp end edge K is formed by an atomizing lip 84 which is formed in this example by the component 74. The atomizing lip 84 tapers in the direction of flow of the first portion of air through the first outlet opening 64 and thus in the direction of flow of the fuel through the first outlet opening 64 up to and ends at an end edge K, which can be ground and / or turned, for example, and thus precisely machined. For example, the fuel is injected, in particular forming a fuel jet 72, towards the component 74, in particular towards the inner circumferential jacket surface 86 of the component 74, in such a way that a fuel film, also simply called a film, is formed with the fuel on the component 74, in particular on the inner circumferential jacket surface 86. It is particularly clear here that the inner swirl chamber 62 is formed radially outwards of the inner swirl chamber 62, in particular directly, by the inner circumferential jacket surface 86. The first vortex flows, and in particular the centrifugal forces resulting from the first vortex flows, carry the fuel film along the inner circumferential jacket surface 86 up to the end edge K, where the fuel separates from the end edge K, so that particularly small droplets of fuel are generated from the fuel or from the fuel film. The component 74 thus serves as a sort of film attachment between the respective vortex flows, or acts as a film attachment. The respective droplets jointly form a particularly large surface area of ​​fuel, so that a particularly effective burner operation can be realized even with low burner power, without the need for expensive pumps or expensive high-pressure generation for generating small and therefore fine droplets of fuel.In this case, the smallest flow cross section of the second outlet opening 80 through which the second partial air can flow is bounded or formed radially inwardly all over the surface by the end edge K of the respective outlet opening 64 to 80.

[0051] Furthermore, the burner 42 has a recirculation prevention plate 88, which in the first embodiment is arranged downstream of the outlet opening 80 and thus downstream of the component 82 in the flow direction of the portions flowing through the outlet opening 80 and in the flow direction of the fuel flowing through the outlet opening 80. The recirculation prevention plate 88 here has a through-flow opening 90 which is arranged correspondingly downstream of the outlet opening 80 and thus can be through-flowed by the portions of air and fuel from the swirl chambers 62 and 76. Starting from the through-flow opening 90, and in particular from the outlet opening 80 and thereby starting from the component 82, in particular from its end, the recirculation prevention plate 88 extends away outward in the axial direction of the respective swirl chamber 62 to 76. The recirculation prevention plate 88 thereby projects outward from at least one partial region T of the component 82 in the radial direction of the respective swirl chamber 62 to 76. Thereby, for example, the first part T1 of the combustion chamber 58 is at least partially separated from the second part T2 of the combustion chamber 58 by the recirculation prevention plate 88. By means of the recirculation prevention plate 88, an excessive flow of the mixture flowing through the through-flow openings 90 into the combustion chamber 58, in particular into part T2, is prevented from flowing back in the direction of the component 82 or back into part T1, so that a favorable mixture pre-treatment can be achieved.

[0052] 2, for example, the swirl chambers 62 and 76 are supplied with air or air portions via a feed chamber 92 common to the swirl chambers 62 and 76. The feed chamber 92 is arranged upstream of the swirl chambers 62 and 76 in the direction of flow of the air portions through the swirl chambers 62 and 76. This means that the air is first introduced into the feed chamber 92 via the air feed channel 54. The air introduced into the feed chamber 92 can flow through the feed chamber 92 on its way to and into the swirl chambers 62 and 76, being divided in particular by the component 74 into a first and a second portion. The air flowing through the air feed channel 54 can flow out of the air feed channel 54 and into the feed chamber 92, for example, along a feed direction, which extends for example obliquely and / or tangentially to the axial direction of the respective swirl chambers 62 and 76 and thus to their respective longitudinal axes.

[0053] FIG. 4 shows the component 74, also called the film attachment, in a schematic longitudinal section. It is clear that at least one part TB of the outer swirl chamber 76 is formed by the component 74. Here, the component 74 comprises a first swirl generator 94 of the inner swirl chamber 62 and a second swirl generator 96 of the outer swirl chamber 76. A first vortex flow of a first part of air is generated by the swirl generator 94, and a second vortex flow of a second part of air is generated by the swirl generator 96. In particular, the inner torus surface of the inner swirl chamber 62 is designated K1 in FIG. 4, and the outer torus surface of the outer swirl chamber 76 is designated K2 in FIG. 4. The swirl generator 94 is arranged in an air passage LK1 of the swirl chamber 62, which air passage LK1 is delimited in particular over the entirety by the component 74. In particular, the air passage LK1 is delimited by the component 74 in the radial direction of the respective swirl chamber 62 to 76 towards the outside and towards the inside. The swirl generator 96 is arranged in the second air passage LK2 of the swirl chamber 76, which air passage LK2 is delimited entirely, and in particular in the axial direction of the respective swirl chamber 62 to 76 towards the outside and towards the inside, by the component 74. For example, the swirl generators 94 and 96 are also formed by the component 74. The air passage LK1 can then be traversed by a first portion of air, and the air passage LK2 can be traversed by a second portion of air, so that the swirl generator 94 generates or induces a first vortex flow and the swirl generator 96 generates a second vortex flow. In FIG. 4, the outer diameter of the air passage LK1, also called air guide, is designated Di, and the outer diameter of the air passage LK2, also called air guide, is designated Da.

[0054] As can be seen from Figures 2 to 4, the outlet openings 64 and 80, also called nozzles, are both axially oriented. This means that the partial mixture from the inner swirl chamber 62 flows at least substantially axially into the combustion chamber 58. Furthermore, a second part of the air from the outer swirl chamber 76 also flows at least substantially axially into the combustion chamber 58, and in the process flows into the combustion chamber 58 together with the finely dispersed fuel of the film deposit as small droplets at the end edge K, in particular at the separation point thereof. The smallest or narrowest flow cross section of the outer nozzle, i.e. of the outlet opening 80, is at the separation point of the inner nozzle, i.e. of the outlet opening 64, i.e. at the end edge K.

[0055] Preferably, the nozzles, i.e. the outlet openings 64 and 80, are intended to have the following size or surface ratios: preferably, the outlet opening 64 (the inner nozzle) has a diameter, in particular an inner diameter, which is 10 to 20 percent of Di. Furthermore, preferably, the outer nozzle, i.e. the outlet opening 80, is intended to have a diameter, in particular an inner diameter, which is for example 10 to 35 percent of Da. The inner and outer tori are of the same area, i.e. both are 50 percent of the total torus. In other words, it is preferably intended that the air passage LK1 has a first torus and the air passage LK2 has a second torus, which tori are preferably of equal size.

[0056] 5 shows a second embodiment of the burner 42 in a schematic cross-sectional view. In the first embodiment, for example, the component 82 and the anti-recirculation plate 88 are intended to be configured as components that are configured separately from one another and are at least indirectly, in particular directly, connected to one another. In the second embodiment, the anti-recirculation plate 88 is intended to be configured integrally with the component 82. The second embodiment has the advantage that the anti-recirculation plate 88 prevents the mixture, after leaving the outer nozzle, i.e. the outlet opening 80, and entering the combustion chamber 58, from flowing backwards towards the component 82, which could form swirls. The anti-recirculation plate 88, also simply called plate, preferably has a diameter, in particular an outer diameter, that is at least equal to Di.

[0057] FIG. 6 partially shows a third embodiment of the burner 42 in a schematic perspective view. In the third embodiment, the combustion chamber 58 has a number of through-flow openings 98 that are spaced apart from one another and are separated from one another, in particular in the radial direction of the respective swirl chamber 62 to 76, in particular by respective wall regions W that are in particular formed as solid bodies. In this example, the respective wall regions W are formed integrally with one another and are formed, for example, as integral perforated plates 100 that are formed as solid bodies. In this example, exactly eight through-flow openings 98 are provided. As can be seen from FIG. 2, it is conceivable in principle that the combustion chamber 58 has exactly one large discharge opening 102 that is not sub-divided, via which the burner exhaust gases or flames 44 can be discharged from the combustion chamber 58 and introduced into the exhaust pipe 26. In contrast to this, in the third embodiment, a number of through-flow openings 98 are provided, which are separated from one another at a distance, so that the discharge opening 102 is, as it were, subdivided or divided by the wall region W into a number of through-flow openings 98. The through-flow openings 98 are distributed uniformly in a circumferential direction running around the axial direction of the respective swirl chamber 62 to 76, and it is clear in particular that they are arranged along a circle whose centre is arranged in the axial direction of the respective swirl chamber 62 to 76. Thus, in the third embodiment, instead of one large outlet opening in the form of a large discharge opening 102, a number of outlet openings in the form of through-flow openings 98 are provided, in particular at each individual location, in order to enable a good recirculation in the combustion chamber 58. In this case, it is preferable to use a perforated plate, such as a perforated plate 100, which has a number of relatively small openings, for example in the form of the through-flow openings 98, rather than reduced outlet openings. The number of through-flow openings 98 is, for example, in the range from 3 to 9. The through-flow openings 98 have similar, or at least substantially equal, flow-through or discharge surfaces through which the burner exhaust gases or flame 44 can flow.The through-flow surface of these through-flow openings 98, or of all of them, together results in a total through-flow surface, also called the total discharge surface, which is, for example, 0.8 to 1.8 times larger than a single centrally located opening, such as the discharge opening 102. Instead of a central outlet opening, for example with a diameter of 25 millimeters and therefore an area of ​​491 square millimeters, depending on the flow conditions in the exhaust pipe 26, it may be preferable to embody six small openings, each with a diameter of 10.5 millimeters, so that a total discharge surface of 520 square millimeters is realized.

[0058] FIG. 7 shows a schematic longitudinal section of a third embodiment of the burner 42, which is provided with a perforated plate 100, also called a perforated plate. The above-mentioned preferred recirculation in the combustion chamber 58 is illustrated in FIG. 7 by an arrow 104. Furthermore, FIG. 7 shows a vortex flow of the mixture, designated by the reference number 106, which flows through the combustion chamber 58 from a respective vortex flow of the air portions. The vortex flow of the air portions, and thus the vortex flow of the mixture 106, is realized in particular by the vortex generators 94 and 96, and in particular by the tangential air supply via the air supply channel 54. The respective vortex generators 94 to 96 are preferably configured as air guide vanes, and not as, for example, a quarter-spherical sheet structure, so that the respective vortex flow can be generated or induced in a particularly preferred way. The vortex flow of the air portions and the resulting vortex flow 106 of the mixture in the combustion chamber 58 prevent the flame 44 from being extinguished in the combustion chamber 58, optimize the fuel-air mixing in the combustion chamber 58 and cause vortex breakdown in order to stabilize the flame 44. The recirculation in the combustion chamber 58, indicated by the arrows 104, can be realized in particular by the use of a perforated plate and the resulting reduction in the discharge cross section, through which the flame 44 or the burner exhaust gases can be discharged from the combustion chamber 58 and can be introduced into the exhaust pipe 26. A reduction in the discharge cross section is understood, for example, as meaning that the total discharge surface of the individual through-flow openings 98 is smaller than the area of ​​the succession of larger discharge openings 102. The preferred recirculation within the combustion chamber 58, as illustrated by arrows 104, results in improved mixing of the air and motive fuel within the combustion chamber 58 and a longer residence time of the mixture burning within the combustion chamber 58, thereby avoiding excessive emissions of unburned hydrocarbons (HC) as the flame 44 or burner exhaust gas exits the combustion chamber 58 into the exhaust 26, and enabling a particularly high temperature at the discharge of the flame 44 or burner exhaust gas. In particular, the recirculation provides a recirculation zone and vortex breakdown, thereby enabling a particularly long residence time of the flame 44 within the combustion chamber 58.

[0059] FIG. 8 shows a schematic perspective, partially cut away view of a vortex generator 107, which may be formed, for example, by components of the component 74 or by the component 74. The vortex generator 107 comprises a vortex generator 94 of the inner vortex chamber 62 and a vortex generator 96 of the outer vortex chamber 76. As can be particularly clearly seen from FIG. 8, the vortex generators 96, and preferably also the vortex generators 94, are configured as air guide vanes, which may be configured, in particular shaped, in a flow-favorable manner. This makes it possible to avoid excessive pressure losses, in particular in comparison with spherical vortex generators. The number of the outer vortex generators 94 is, for example, in the range from 6 to 11. Alternatively or additionally, the number of the outer vortex generators 96 is, for example, in the range from 8 to 14. The respective air passages LK1 to LK2 in which the vortex generators 94 to 96 are arranged have, for example, as such, a respective area, which is covered, for example, by at least 20 percent and at most 70 percent, by the respective vortex generators arranged in the air passages LK1 to LK2. In this way, a particularly preferred axial shielding of at least 20 percent and at most 70 percent of the respective area is intended. The respective radius of the respective air guide vane can extend from at least 40 percent of Di to infinity, whereby the respective air guide vane can be configured linearly. In particular, it is conceivable that the respective air guide vane forms, with the respective radial direction of the respective vortex chambers 62 and 76, a respective angle α, for example, in the range of 10 degrees to 45 degrees. The above-mentioned radius of the respective air guide vane, also simply called vane, is designated by the reference R in FIG. 8. The swirl generators 94 to 96 are preferably designed to redirect a portion of the air flowing through the respective air passage LK1 to LK2, i.e. the air flowing through the respective air passage LK1 to LK2 and thus forming the respective portion, in particular by 70° to 90° relative to the strictly or purely axial direction of the respective swirl chamber 62 to 76. In order to realise a particularly preferred mixture pre-treatment, the air guide vanes of the inner and outer swirl chambers 62 and 76 can be designed in opposite directions.In other words, the outer vortex generator 96 of the outer vortex chamber 76 and the inner vortex generator 94 of the inner vortex chamber 62 may be configured to create or induce vortical flows of the respective portions of air as opposing or counter-directional vortical flows, so that, for example, a first flow is counterclockwise and a second flow is clockwise, or vice versa.

[0060] The vortex generating device 107 has in particular a central through-opening 108, which is penetrated by the injection member 66. In other words, the injection member 66 passes through the through-opening 108 into the inner vortex chamber 62.

[0061] 10 shows a schematic front view of the closing device 110, which in this example is configured as an iris diaphragm or in the manner of an iris diaphragm. When the burner 42 is not in operation, it may be advantageous to cover the air and fuel lines, i.e. for example the air supply path 54 and / or the fuel supply path 46 and / or the swirl chambers 62 and 76, and in this case for example the outlet opening 64 and / or the outlet opening 80, in order to prevent the ingress of exhaust gases of the internal combustion engine 12 into the air supply path 54, the fuel supply path 46, the supply chamber 92, the swirl chamber 62 and / or the swirl chamber 76. It is further conceivable to cover the combustion chamber 58 or at least one length region of the combustion chamber 58 in order to prevent the ingress of exhaust gases of the internal combustion engine 12 from the exhaust pipe 26 into the combustion chamber 58 or into a part region or length region thereof. For this purpose, a closing device 110 can be used, which can be arranged for example in the combustion chamber 58 or downstream of the combustion chamber 58. The closing element 112 of the closing device 110, which is movable in the manner of an iris diaphragm, allows the opening cross section 114, which is defined in particular directly by the closing element 112 and through which, for example, the flame 44 or the burner exhaust gases can flow, to be changed, i.e. variably adjusted, so that, for example, the opening cross section 114 can be adjusted load-dependently, in particular controlled or controlled. In this way, it is conceivable to close at least one partial region of the combustion chamber 58 by the closing device 110. Alternatively or additionally, for example, the outlet opening 80 can be closed by the first closing device 110. Alternatively or additionally, for example, the outlet opening 80 can be closed by the second closing device 110. This has the advantage, in particular, that the air supply and the power fuel supply can be closed simultaneously by a small plug. In that case, an air valve downstream of the pump 56 is also not necessary, since this prevents the ingress of exhaust gases into the pump 56. A much larger exhaust gas flap after the combustion chamber 58 or after its discharge, against which the hot exhaust gases impinge, can also be dispensed with.

[0062] In particular, the opening cross section 114 is considered to be an opening cross section or a discharge cross section of the combustion chamber 58, through which the flame 44 or the burner exhaust gases can be discharged from the combustion chamber 58 and introduced into the exhaust pipe 26. The tapering of the opening cross section, which is necessary or necessary or carried out in order to increase the flow velocity of the flame 44 or the burner exhaust gases from the combustion chamber 58, in particular by a corresponding movement of the closing element 112, which is carried out in the manner of an iris diaphragm, can be embodied in a manner that is favorable for the flow. Thus, instead of a flat closing plate bore, a tapered flaring can be carried out, which has an angle of 30° to 70° to the horizontal, as is embodied, for example, in aircraft drives by segments and / or tapers. This can be carried out by means of a fixed geometry or variably, as in aircraft drives with individual segments that can be opened and closed, for example in the case of a propulsion nozzle, or by means of a slidably arranged discharge taper that can be slid in the axial direction of the respective swirl chamber 62-76.

[0063] FIG. 11 partially shows a burner 42 according to a fourth embodiment in a schematic cross-sectional view. As can be seen particularly well from FIG. 11, or also from FIGS. 2 and 7, the combustion chamber 58 is formed or delimited by a chamber part 116, which is particularly constructed as a solid body. In particular, the combustion chamber 58, whose axial direction coincides with the axial direction of the respective swirl chamber 62 to 76, is delimited, in particular directly, by an inner circumferential outer surface 118 of the chamber part 116 along a radial direction that runs parallel to the respective radial direction of the respective swirl chamber 62 to 76. The chamber part 116 can be constructed in one piece. In the fourth embodiment, the chamber part 116 is constructed, for example, in such a way that it has two chamber parts 120 and 122 that are constructed in one piece with each other, or the chamber parts 120 and 122 are components that are constructed separately from each other and are connected to each other. Here, the inner circumferential outer surface 118 is formed by the chamber part 122. The chamber parts 120 and 122 are arranged nested together such that at least one length section of the chamber part 120 surrounds at least one length section of the chamber part 122 in a circumferential direction of the combustion chamber 58 extending in the axial direction of the combustion chamber 58, in particular completely around the circumference, and the at least one length section of the chamber part 120 is understood from the at least one length section of the chamber part 122 towards the outside in the radial direction of the combustion chamber 58, in particular forming an intermediate space 124. This intermediate space 124 is arranged between the chamber parts 120 and 122 in the radial direction of the combustion chamber 58, and is formed between the chamber parts 120 and 122, for example as an air gap. It is further clear that a continuous or uninterrupted discharge opening 102 is formed or defined by the chamber part 122 in a circumferential direction of the combustion chamber 58, in particular completely around the circumference. In the first embodiment shown in FIG. 2, the discharge opening 102 is not sub-divided, i.e., there are no components that subdivide the discharge opening 102 into multiple flow-through openings that are separated and spaced apart from each other.7, a perforated plate 100, also called a perforated plate, is arranged at the discharge opening 102, by which the discharge opening 102, which is uninterrupted as such, i.e. continuous, is subdivided or divided into a number of spaced-apart, mutually separated through-flow openings 98 formed in the perforated plate 100. The flame 44 or the burner exhaust gases can flow out of the combustion chamber 58 along a fourth flow direction that runs in the axial direction of the combustion chamber 58, i.e. that runs parallel to the axial direction of the combustion chamber 58 or coincides with the axial direction of the combustion chamber 58, and in so doing can flow through the discharge opening 102 or the respective through-flow opening 98, the fourth flow direction coinciding with the first, second and third flow directions. It is clear that the discharge opening 102 tapers in the flow direction of the burner exhaust gases flowing through the discharge opening 102, i.e. along the fourth flow direction. For this purpose, the chamber part 116, in particular the chamber part 120, has a length region L1 that is defined around the discharge opening 102 in the circumferential direction of the combustion chamber 58, in particular all the way around, and that tapers in the flow direction of the burner exhaust gases flowing through the discharge opening 102. In other words, the length region L1 and therefore the discharge opening 102 are configured tapered, i.e. conically or frustoconically, in the flow direction of the burner exhaust gases flowing through the discharge opening 102. Since the burner exhaust gases or the flame 44 leave the combustion chamber 58 via the discharge opening 102, the discharge opening 102 is configured at or forms the discharge of the combustion chamber 58, which in the fourth embodiment is configured tapered at its discharge, i.e. has a taper formed by the length region L1. The discharge opening 102 preferably has an inside diameter of 34 mm. In other words, it is preferably intended that the smallest or narrowest inner diameter of the exhaust opening 102 through which the burner exhaust gas can flow is 43 mm.

[0064] At least the length regions of the chamber parts 120 and 122 are nested and spaced apart from one another in the radial direction of the combustion chamber 58 forming an intermediate space 124, which is filled, for example, with air and thus configured as an air gap, creating a double wall of the combustion chamber 58 or of the chamber part 116, whereby the combustion chamber 58 is insulated by the intermediate space 124, i.e. by an air gap. In this way, the combustion chamber 58 is air-gap insulated. In the following, with particular reference to the outer diameter Da shown in FIG. 4 of the film attachment of the outer air passage LK2 of the outer swirl chamber 76, the air passage LK2 in which the outer swirl chamber 96 is arranged and therefore the outer diameter Da is in particular formed entirely by the film attachment, i.e. by the component 74. With the aid of FIG. 11 and the outer diameter Da, the combustion chamber 58 preferably has an inner diameter d1, particularly upstream of the taper or upstream of the length region L1, which is preferably 1.0 to 3.0 times Da. Furthermore, it is preferably provided that the smallest inner diameter d2 of the discharge opening 102 is 0.7 to 2.3 times Da, where the smallest inner diameter d2 of the discharge opening 102 is also called the discharge diameter. The relatively small discharge diameter of the discharge opening 102 maintains the discharge velocity of the burner exhaust gases and reduces the influence of the exhaust gases of the internal combustion engine 12, also called the engine exhaust gases, on the flame 44, also called the burner flame. The length l1 of the combustion chamber 58, which extends in the axial direction of the combustion chamber 58, is preferably 1.5 to 4.0 times Da, particularly without the secondary air blowing section. With the secondary air blowing section, it is preferably provided that the length l1 of the combustion chamber is 2.0 to 5.5 times Da.

[0065] Instead of a continuous discharge opening 102, it is conceivable to use a plurality of through-flow openings 98 which are separated from one another. In other words, it is conceivable to divide the continuous and therefore uninterrupted discharge opening 102 into a plurality of through-flow openings 98 which are separated from one another and which are preferably in the range of 3 to 9. Each through-flow opening 98 has an area, which is also called the discharge surface or through-flow surface, and the sum of the areas of all through-flow openings 98 is preferably similar to the discharge surface of the continuous discharge opening 102, i.e. similar to the area of ​​the discharge opening 102. The sum of the areas of the individual through-flow openings 98 is also called the total discharge surface. The through-flow openings 98 are configured, for example, as bores. It is conceivable that the sum of the areas of all through-flow openings 98, i.e. the total discharge surface, is 0.8 to 1.8 times the area of ​​the continuous uninterrupted discharge openings 102 of the discharge openings 102 of the combustion chamber 58. In particular, it is conceivable that the perforated plate 100 is arranged at the discharge opening 102 or at the length region L1. From the viewpoint of the exhaust gas of the internal combustion engine 12, also called engine exhaust gas, it may be preferable to use a deflector, in particular a deflector and / or a perforated element, in particular a perforated plate, where a perforated element is understood to be an element that is particularly constructed as a solid body and has a number of holes that are spaced apart, in particular separated from one another by respective walls, through which gases, such as for example burner exhaust gas or engine exhaust gas, can flow through. In order to prevent, for example, the engine exhaust gas from excessively adversely affecting and destabilizing the flame 44 in the combustion chamber 58, it is preferable to provide a deflector, for example a deflector plate, in front of the combustion chamber 58, i.e. upstream of the combustion chamber 58, so that the engine exhaust gas cannot or only very little can enter the combustion chamber 58 in the direction opposite to the flow direction of the flame 44 or the burner exhaust gas from the combustion chamber 58 into the exhaust pipe 26. Thus, it is preferably intended that the deflector is arranged in the exhaust pipe 26 upstream of the combustion chamber 58 in the flow direction of the engine exhaust gases, ie upstream of the inlet point E2.The geometry of the deflection element can be determined depending on how the combustion chamber 58 is arranged relative to the exhaust pipe 26, i.e. relative to the exhaust gas passage of the exhaust pipe 26. Exhaust gas passage can be understood as meaning that the burner exhaust gases or flames 44 flow from the combustion chamber 58 in particular along the fourth flow direction, in particular at the inlet point E2, into the exhaust gas passage. The geometry of the deflection element is preferably adapted individually.

[0066] Furthermore, as explained above, a closure device 110 or other type of closure device is preferably arranged at the discharge of the combustion chamber 58. This can be understood in particular as follows: the closure device 110 can be arranged, for example, at the length region L1 or at the discharge opening 102, so that the flow cross section through which the burner exhaust gas or flame 44 can be discharged from the combustion chamber 58, in particular at the inlet point E2, and can be introduced into the exhaust pipe 26, in particular into the exhaust gas channel, is defined by the closure device 110, in particular by the closure element 112, and can be changed, i.e. adjusted, by the closure device 110 accordingly. Such an adjustable flow cross section is in particular the opening cross section 114.

[0067] The closing device 110 can then be arranged in the chamber section 122 and thereby in the discharge opening 102, or the closing device 110 or another closing device can be arranged downstream of the combustion chamber 58, i.e. downstream of the chamber section 122 and thereby directly following the combustion chamber 58 or the chamber section 122, i.e. downstream of the discharge opening 102 itself. In the fourth embodiment, the taper of the discharge opening 102, which is embodied by the length section L1, i.e. by the above-mentioned taper, leads to an increase in the flow velocity of the burner exhaust gases, and the taper of the discharge section of the combustion chamber 58 can be embodied in a flow-favorable manner. The taper formed by the length section L1 in this example preferably has an angle, also called the taper angle, of 30° to 70° with respect to the axial direction of the combustion chamber 58, which is particularly illustrated in FIG. 11 by the dashed line 126. In the fourth embodiment, the taper is configured as a fixed geometry, whereby the taper, i.e. the taper angle, is fixed, i.e. is not variable. However, it is also conceivable to design the taper variable, in particular with regard to its taper angle, as for example in an aircraft drive, in particular by means of individual segments which can be opened and closed, i.e. in particular pivoted relative to the chamber part 122, as for example in a propulsion nozzle in an aircraft drive, so that the taper or the taper angle is adjustable, i.e. variable. Alternatively or additionally, it may be provided that the taper or its taper angle is variable by means of a slidably arranged discharge taper and / or a discharge taper is provided whose central longitudinal axis coincides, for example, with the axial direction of the combustion chamber 58 and / or which is slidable in the axial direction of the combustion chamber 58, in particular relative to the chamber part 116, preferably arranged coaxially with the combustion chamber 58 and which tapers in the flow direction of the burner exhaust gases flowing through the discharge opening 102. The feature that the discharge taper is arranged coaxially with the combustion chamber 58 is understood in particular as meaning that the axial direction of the discharge taper, i.e. its central longitudinal axis, coincides with the axial direction of the combustion chamber 58.The sliding of the discharge taper in the axial direction of the combustion chamber 58 relative to the chamber part 116 makes it possible to change the flow cross section through which the burner exhaust gas can, for example, be discharged from the combustion chamber 58 and introduced into the exhaust gas channel. The discharge taper is particularly diagrammatically shown in FIG. 11 and is designated by the reference number 128. The direction of movement, which runs parallel to the axial direction of the combustion chamber 58 or coincides with the axial direction of the combustion chamber 58 and along which the discharge taper 128 can translate, in particular can slide, relative to the chamber part 116, is shown in FIG. 11 by a double arrow 130. It is clear that the flow cross section through which the burner exhaust gas can flow is in particular directly defined in the radial direction of the combustion chamber 58 both outwardly by the chamber part 116 and inwardly by the discharge taper 128, in which case the flow cross section is configured in the form of an annular or annular surface. The discharge taper 128 tapers in the flow direction of the burner exhaust gas flowing through the discharge opening 102 or the flow cross section, so that the flow cross section is changed by sliding the discharge taper 128 relative to the chamber member 116 along the direction of movement.

[0068] Figure 12 shows partly in a schematic cross-sectional view a fifth embodiment of the burner 42. In particular in Figure 12, partly the component 74 and partly the component 82 are evident, as in Figure 3. When the burner 42 is not in operation, the air and power fuel lines, i.e. preferably the outlet openings 64 and 68, are preferably closed to prevent the ingress of engine exhaust gases into the swirl chambers 62 and 76. For this purpose, it is conceivable to arrange a closure device 110 at the outlet opening 64 and / or at the outlet opening 80, respectively, or the closure device 110 is arranged downstream of the outlet opening 80 and thereby directly adjacent to it, so that for example a first flow cross section through which a first portion of the air and the fuel can flow, in particular the outlet opening 64, and / or a second flow cross section through which a portion of the air and the fuel can flow, in particular the outlet opening 80, or a third flow cross section through which a portion of the air and the fuel can flow and which is arranged downstream of the outlet opening 80 and directly adjacent to it, can be varied or adjusted by the closure device 110. The first, second and third flow cross sections are for example an opening cross section 114, i.e. 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 the area of ​​which can be adjusted by the closure element 112, in particular in the manner of an iris diaphragm. In this way, the first, second and third flow cross sections can be adjusted, in particular load-dependently, in particular regulated or controlled. For example, it is conceivable to close only both outlet openings 64 and 80, also called discharge nozzles, by the closing device 110 or by another further closing device, i.e. to reduce the first, second and third flow cross sections to zero.

[0069] Another closing device can be, for example, a closing element, designated by the reference number 132, also called a closing plug, which is shown in a particularly schematic way in FIG. 12. The closing element 132 is, for example, in particular in the axial direction of the respective swirl chamber 62 or 76, relative to the component 82 and relative to the component part 74, in particular translationally, between at least one closed position and at least one open position, which is shown in FIG. 12. In the closed position, the outlet openings 64 and 80 are closed by the closing element 132 and thus fluidically sealed, in particular while the burner 42 is deactivated. As a result, engine exhaust gases from the exhaust pipe 26 cannot flow through the outlet openings 64 and 80. In the open position, the closing element 132 opens the outlet openings 64 and 80, in particular while the burner 42 is in operation. It is clear that the outlet openings 64 and 80 can be closed or are closed simultaneously by the closing element 132, which is configured, for example, as a small plug, in particular when the closing element 132 is in the closed position. In that case, no air valve, such as, for example, the valve element 55, is necessary downstream of the pump 56, since the closing element 132 prevents engine exhaust gases from flowing from the exhaust pipe 26 through the air supply path 54. In other words, the closing element 132 or the closing device 110 prevents engine exhaust gases from entering the pump 56 from the exhaust pipe 26. A much larger exhaust gas flap downstream of the combustion chamber 58, i.e. after the discharge, which is loaded with hot exhaust gases, can also be omitted.

[0070] In the following, the air gap insulation of the combustion chamber 58 mentioned above will be explained in more detail. The air gap insulation can ensure a particularly safe operation of the combustion chamber 58, since the outer wall of the combustion chamber 58 becomes very hot, and even glows, especially during full load operation. Furthermore, the air gap insulation can keep heat losses particularly low. In this case, it is particularly intended that the thermal insulation surrounds the combustion chamber 58 in a circumferential direction extending around the axial direction of the combustion chamber 58, in particular all around. As such an insulation, an air gap insulation, i.e. an air gap, is provided in this example. The intermediate space 124, which is formed as an air gap in this example, preferably has a width extending in the radial direction of the combustion chamber 58, in particular a gap width, which is preferably 6% to 25% of Da. In particular, this width can be in the range of 1.5 mm to 6 mm. It is particularly clear that the chamber part 116 is a tube that is air gap insulated by having a double wall. In other words, the chamber parts 120 and 122 are double-walled and thus form an air-gap insulated tube. It is then intended that an insulating element, preferably constructed separately from the chamber member 116 (air-gap insulated tube), surrounds the air-gap insulated tube (chamber member 116), i.e. at least one length region of the chamber member 116 extending in the axial direction of the combustion chamber 58, particularly all around in the circumferential direction of the combustion chamber 58. This insulating element is preferably an insulating mat. The insulating element is preferably formed at least from mineral wool and / or sheet metal, which allows a particularly favorable insulation of the combustion chamber 58.

[0071] In the following, possible mounting positions of the combustion chamber 58 or the burner 42 are described. As explained above, the mixture in the combustion chamber 58 is too lean to burn under the release of heat or thermal energy. With the thermal energy, for example at least the component 36b can be efficiently and effectively heated and / or kept at a high temperature. Alternatively or additionally, the component 36c, which is configured as a particle filter, can be heated. The particle filter can be heated, for example, so that a regeneration of the particle filter can be initiated or carried out. In order to be able to favorably utilize the thermal energy of the burner 42, the inlet E2 should be arranged as close as possible to the components to be heated or kept at a high temperature, for example the components 36b and / or 36c. This also keeps heat losses to a minimum. However, in order to ensure a favorable mixture of the burner exhaust gas and the engine exhaust gas, a minimum section for mixing the engine exhaust gas and the burner exhaust gas should be provided, which in particular extends all the way in the flow direction of the engine exhaust gas through the exhaust pipe 26 from the burner 42 or the inlet point E2 to the component to be heated or to be kept hot, such as the component 36b, in particular to its inlet. In particular, this minimum section is the minimum section of the mixing chamber 40. The inlet point E2 cannot therefore be brought so close as to immediately precede the inlet point of the component 36b. It has been shown to be particularly preferred if the distance between the inlet point E2 and the component 36b, in particular the component 36b which directly follows the inlet point E2 in the flow direction of the exhaust gas through the exhaust pipe 26, in the flow direction of the exhaust gas through the exhaust pipe 26, is at least 5 to 8 times Da and at most 30 times Da. The feature that component 36b immediately follows inlet point E2 in the flow direction of the exhaust gas (engine exhaust gas) flowing through the exhaust pipe 26 is understood to mean that no other exhaust gas aftertreatment components are arranged between inlet point E2 and component 36b in the flow direction of the exhaust gas flowing through the exhaust pipe 26.Alternatively or additionally, the diameter, in particular the inner diameter, of the exhaust gas passage in which the inlet point E2 is located preferably expands conically, in particular before the exhaust gas enters the component 36b, in particular after the discharge from the combustion chamber 58, to at least six times Da. In particular, if the component 36b is a catalyst, in particular the above-mentioned SCR catalyst, the component 36b has a substrate. Accordingly, the above-mentioned distances are preferably intended to be distances that extend between the inlet point E2 and the substrate of the catalyst, in particular in the flow direction of the exhaust gas through the exhaust pipe 26. Accordingly, it is preferred that the inner diameter of the exhaust gas passage expands, in particular after the discharge from the combustion chamber 58, i.e. starting from the inlet point E2, to at least six times Da, before the exhaust gas (engine exhaust gas or burner exhaust gas) hits the substrate.

[0072] As is evident from FIG. 2, the ignition device 60, which is configured, for example, as a spark plug, glow plug or glow pin, has a thread 134, in particular configured as an external thread, by means of which the ignition device 60 is at least indirectly screwed into the chamber part 116 and thereby held therein. In order to realize a sufficient cooling of the ignition device 60, i.e. a good heat dissipation from the ignition device 60, the thread 134 of the ignition device 60, also called the spark plug thread, is preferably equipped with cooling ribs. The number of cooling ribs is preferably in the range from 1 to 7. For example, the cooling ribs have a thickness in the range from 2 to 4 mm. Furthermore, it is conceivable for each cooling rib to have a diameter, in particular an outer diameter, of 20 to 80 mm. In addition to this, in order to realize a good heat dissipation, the individual cooling ribs preferably have openings, in particular configured as bores, in particular through openings, in the periphery of the ignition device 60, i.e. to the surrounding air, the number of which is preferably in the range from 3 to 8. Each through-opening of each cooling rib has a diameter, in particular an inner diameter, which is for example at least 5 mm and at most 15 mm. The electrode spacing between the respective electrodes of the ignition device 60 is at least 0.7 mm and at most 10 mm. The electrodes are apparent from Fig. 2, where they are designated by the reference numerals 136 and 138, by means of which, in particular between the electrodes 136 and 138, an ignition spark for igniting the mixture is generated in the combustion chamber 58.

[0073] In order to support the initiation or creation of a vortex-like flow of the air portions in the swirl chambers 62 and 76, the air is not introduced strictly radially into the respective swirl chamber 62 to 76, i.e. in the radial direction of the respective swirl chamber 62 to 76, but tangentially or obliquely to the respective axial direction of the respective swirl chamber 62 to 76, as shown in Fig. 2. In other words, the air or the respective portions of air preferably enter the respective swirl chamber 62 to 76 tangentially, so that the impulse of the incoming air can already be directed in the vortex direction, which leads to a particularly high efficiency of vortex generation.

[0074] A fuel pump is used to supply fuel to the burner 42, in particular a power fuel pump for delivering power fuel from the tank 18. Thus, the fuel pump can be, for example, the low-pressure pump 20. The burner 42 is preferably operated with lambda control, so that, for example, the mixture has a combustion air ratio (γ) of at least substantially 1.0. In other words, it is preferably intended that the burner is operated stoichiometrically, i.e. that the mixture is a stoichiometric mixture. Expressed again in other words, it is preferably intended that the first proportion of air in the mixture and the second proportion of fuel in the mixture are adjusted or controlled as precisely as possible. It is therefore preferred that the first amount of air in the mixture, also called combustion air, and the second amount of fuel in the mixture are adjusted and / or calculated at least substantially precisely and introduced into the corresponding swirl chambers 62-76. Thus, it is preferred to use a frequency-controlled piston pump as a fuel pump for delivering fuel towards or into the burner 42. Such piston pumps may include a spring biased valve, such as a ball valve, at the discharge, particularly to prevent backflow of motive fuel or exhaust gases into the fuel pump.

[0075] Such a fuel pump is shown in a schematic longitudinal section in Fig. 17 and is designated by reference 137. Here, the fuel pump 137 is configured as a piston pump, the piston for delivering fuel being designated by reference 138. The spring-loaded valve, configured in the embodiment shown in Fig. 17 as a spring-loaded ball valve, is designated by reference 140 in Fig. 17 and includes, among other things, a mechanical spring unit 142 and a ball 144. In particular, the spring-loaded valve 140 is configured as or functions as a check valve, so that fuel can be delivered by the fuel pump 137 to the burner 42, whereby the valve 140 opens in the direction of the burner, but is closed in the opposite direction, whereby exhaust gases and air cannot flow back from the burner 42 to the fuel pump 137.

[0076] Figure 13 partially shows a sixth embodiment of the burner 42 in a schematic longitudinal section, in which, in particular like Figures 6 and 12, the outlet openings 64 and 80 and thus the element 82 and the component 74 are evident. Figure 13 also reveals the injection element 66, which in the embodiment shown in Figure 13 is configured as a lance, as in Figures 2 and 7. Here, the outlet openings are not arranged or configured on an axial end face 146 of the injection element 66 facing in the axial direction of the swirl chambers 62 to 76, but rather the outlet openings 70 face in the radial direction of the swirl chambers 62 to 76 and are formed in an outer circumferential jacket surface 148 of the injection element 66, which runs around a circumferential direction extending around the axial direction of the respective swirl chamber 62 to 76. In other words, rather than each fuel jet 72 exiting the injection member 66 at end face 146 in the direction of, or parallel to, the axis of its respective swirl chamber 62-76, the fuel jets 72 exit the injection member 66 perpendicular, or in this example obliquely, to the axial direction of its respective swirl chamber 62-76, as illustrated by dashed lines 150 in FIG. 13.

[0077] The inner circumferential jacket surface 86 of the component 74 is also called the membrane wall, because the fuel that is ejected from the injection element 66 and transferred or injected through the outlet openings 70 onto the membrane wall forms the aforementioned membrane or fuel film at the membrane wall (inner circumferential jacket surface 86). For example, instead of an atomizing nozzle, a simple lance can be used, for example an injection element 66 as shown in FIG. 13, in order to particularly favorably transfer or direct the fuel onto the membrane wall. The lance comprises a small tube 152, in the end region of which at least two outlet openings 70 are provided, which are configured, for example, as cross holes. Here, the fuel does not leave the lance or small tube 152 in the axial direction of the respective swirl chamber 62 to 76, but in the radial direction of the respective swirl chamber 62 to 76 or at an angle to the radial direction. In order that the fuel leaving the outlet opening 70 can be transferred or directed particularly efficiently to the membrane attachment and in this case in particular to the membrane wall, it is preferred that the fuel is atomized. For this purpose, it is provided that a Venturi nozzle 154 is arranged on or above the surface of the membrane wall, also called the membrane attachment wall, in particular in the axial direction of the respective swirl chambers 62 to 76, the axial direction of which coincides with the axial and longitudinal extension direction of the injection member 66, in particular of the small tube 152, at the level of the outlet openings 70, which are preferably arranged at the same axial level in each case. In other words, the venturi nozzle 154 is preferably provided in the swirl chamber 62, in which the outlet opening 70 is also arranged, and the narrowest flow cross section through which the first part of the air can flow is preferably arranged in the axial direction of the respective swirl chamber 62-76 and thus of the injection member 66, in such a way that the narrowest or smallest or minimum 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 62-76 and thus of the injection member 66. This allows a particularly favorable atomization of the fuel flowing through the outlet opening 70 to be realized. In particular, the venturi nozzle 154 and the injection member 66 function in the manner of a jet pump.The first part of the air flows through the Venturi nozzle 154, i.e. through its narrowest flow cross section. Since the outlet openings 70 are here at least partially arranged in the narrowest flow cross section of the Venturi nozzle 154, i.e. the narrowest flow cross section of the Venturi nozzle 154 and the outlet openings 70 are arranged at the same height in the axial direction of the injection element 66 and thus in the flow direction of the first part of the air flowing through the Venturi nozzle 154, the first part of the air acts or functions as a driving medium, which as it were sucks in the fuel as suction medium, in particular through the outlet openings 70, so that the driving medium as it were sucks in the suction medium (fuel) through the outlet openings 70. As a result, the fuel is atomized particularly preferably in the swirl chamber 62.

[0078] 14 partially shows a seventh embodiment of the burner in a schematic longitudinal section. In the seventh embodiment, the injection element 66 is exemplarily configured as a lance. It is clear that each fuel jet 72, in particular its major or central longitudinal axis, forms an angle β, also called jet angle, with an imaginary plane EB, which extends perpendicular to the axial direction of the respective swirl chamber 62-76 and thus perpendicular to the respective flow direction of the respective portion of air flowing through the respective swirl chamber 62-76. The axial direction of the respective swirl chamber 62-76 then coincides with the longitudinal extension or longitudinal extension of the injection element 66 and thus with its axial direction. The outlet openings 70 are arranged and spaced apart from one another, in particular evenly distributed, in a circumferential direction extending around the axial direction of the injection element 66. In order to generate a fuel film that is as thin and uniform as possible on the film attachment, i.e. on the inner circumferential outer jacket surface 86, the number of outlet openings 70 is preferably at least 2 and at most 10. In other words, it is intended, for example, that the number of outlet openings 70 is in the range from 2 to 10. For example, it is preferably intended that the angle β is in the range from 10° to 60° in order to already guide the impingement of the fuel in the flow direction. Furthermore, it is intended that each outlet opening 70, which is preferably circular and configured, for example, as a bore, has a diameter, in particular an inner diameter, in the range from 3 mm to 50 mm.

[0079] Fig. 15 shows another possible embodiment of the injection member 66 in a schematic, partially cutaway side view. In the embodiment shown in Fig. 15, the injection member 66 is configured as an injection nozzle, as used in heating oil burners. In the embodiment shown in Fig. 15, the injection member 66 has a head 155, a swirl slit 156, a volute 158, a secondary filter 160 and a primary filter 162. The injection member 66 in Fig. 15 has at least one, or exactly one, outlet opening 70, which is arranged or formed on its axial end face 146, also called the axial end face. This means that the fuel jet 72 flowing through the outlet opening 70 exits the injection member 66, and thus the respective swirl chamber 62 to 76, axially from the outlet opening 70 and thus from the injection member 66. In other words, in FIG. 15, the injection jet 72 or its major or central longitudinal axis extends at least substantially axially, i.e., parallel to the axial direction of the respective swirl chamber 62-76.

[0080] FIG. 16 shows a block diagram for illustrating the operation, in particular the control, of the burner 42. The temperature of the exhaust gases at the inlet point E2 or downstream of the inlet point E2 and in particular upstream of the component 36b is designated here by the reference T5. For example, the temperature T5 is measured in particular by a temperature sensor, whereby a value, also called the T5 value, which characterizes the temperature T5, is measured. The T5 value is illustrated in FIG. 16 by a block 164. The T5 value is transmitted in particular as an input quantity to a block 166. Block 166 shows an initial state, in which, for example, the air supply at the burner 42 is closed, the fuel pump is deactivated, whereby the fuel supply at the burner 42 is also deactivated, and the ignition device 60 is deactivated. An arrow 168 shows the so-called burner release, i.e. the release of the burner. As a result of the burner release, the ignition device 60 is switched on, i.e. activated, in a block 170. In block 172, a combustion air ratio of the mixture of, for example, 0.9 is set, thus realizing the starting operation of the burner 42. Furthermore, for example, in block 172, the air pump is activated and the fuel pump is activated. Subsequently, for example, in block 174, the combustion air ratio of the mixture is set to 1.03 and the fuel pump is operated at a low frequency. In block 176, for example, the ignition device 60 is deactivated. Block 178 shows the operating state of the burner 42. In this operating state, the air supply to and into the burner 42 is opened, the fuel pump is switched on and the ignition device 60 is deactivated, so that the burner 42 is supplied with air and fuel. Arrow 180 indicates that the burner release is revoked, in particular if the temperature T5 is higher than a limit value, for example 400° C.

[0081] In block 182, a comparison is made in which the actual value of the temperature T5 is compared with a setpoint value of the temperature T5. The actual value of the temperature T5 is, for example, the T5 value mentioned above and / or is, for example, measured by a temperature sensor, for example, as mentioned above, in particular at the inlet point E2 or downstream of the inlet point E2, in particular at the exhaust pipe 26 arranged upstream of the component 36b. If, for example, the comparison shows that the actual value is lower than or equal to the setpoint, then the state remains regulated, in particular in block 174, with respect to the operation of the fuel pump and the air pump being represented in FIG. 16 by block 184 and by block 186, respectively. If, for example, the actual value is higher than the setpoint value, then in block 188, the fuel pump is controlled, in particular by an electronic computing device, also referred to as a control device, and / or in block 190, the air pump is controlled, in particular by a control device, and in particular the fuel pump or the air pump is altered in respect of their respective operation, in particular the actual value is reduced, for example, until the actual value corresponds to the setpoint value or is lower than the setpoint value.

[0082] In block 192, the amount of air in the mixture is determined, in particular measured, in particular by air flow measurement. Furthermore, the arrow 194 indicates that the amount of fuel is determined, in particular measured. In block 196, depending on the determined, in particular measured, amount of air and depending on the determined, in particular measured or calculated amount of fuel, the combustion air ratio (γ) is determined, in particular calculated. In particular, in block 196, the actual value of the combustion air ratio of the mixture is determined, in particular calculated. In block 198, the actual value of the combustion air ratio is compared with a second setpoint value of the combustion air ratio, the second setpoint value being, for example, 1.03. If the actual value of the combustion air ratio corresponds to the setpoint value of the combustion air ratio or if the actual value of the combustion air ratio differs only slightly from the setpoint value of the combustion air ratio and the difference between the actual value of the combustion air ratio and the setpoint value of the combustion air ratio is, in particular, numerically greater than or equal to a limit value, the current operation of the burner 42, in particular the fuel pump and the air pump, is maintained. However, if the actual combustion air ratio differs too much from the target combustion air ratio, then, as shown by arrow 200, for example, the air pump and / or the fuel pump are altered in their respective operation, in particular by controlling the fuel pump or the air pump, in order to at least reduce or eliminate the difference between the actual combustion air ratio and the target combustion air ratio.

[0083] Finally, block 202 indicates that a setpoint value for the temperature T5 is set from or by the control device, in particular in block 182. Alternatively or additionally, the control device can set or output a setpoint value for the combustion air ratio, in particular in block 198.

[0084] It is clear that the low-pressure pump 20 is used as a fuel pump, by means of which fuel is delivered in particular actively towards and in particular through the injection member 66, so as to inject the power fuel through the injection member 66 in particular directly into the inner swirl chamber 62. Here, the low-pressure pump 20 is given a double function, for example, on the one hand, it is used to deliver the power fuel as fuel to the injection member 66, and on the other hand, it is used to deliver the power fuel from the tank 18 to the high-pressure pump 22. Alternatively, it is also conceivable to use a fuel pump provided only for the burner 42, i.e. a fuel pump which in particular can or is capable of delivering fuel in particular as power fuel from the tank 18 to the burner 42 in an active manner, but which does not deliver the power fuel from the tank 18 to the high-pressure pump 22 by means of this own fuel pump. In this way, for example, a fuel pump 137 can be used which is configured as a piston pump, by means of which fuel can also be delivered in particular through the injection member 66.

[0085] FIG. 18 shows a system diagram for illustrating the burner 42 and in particular for illustrating a method of operating the burner 42. In FIG. 18, arrow 204 indicates that the electronic calculation device 52, the air pump 56, the injection member 66 and the ignition device 60 can be controlled, in particular electrically. Alternatively or additionally, the electronic calculation device 52 can control, in particular electrically, the fuel pump. Arrow 206 indicates the above-mentioned air line or air supply path 54. In other words, the air supply path 54 is or includes at least one air line, by means of which air can be introduced, in particular tangentially or obliquely to the axial direction of the respective swirl chamber 62-76 or to the air chamber 92. Furthermore, arrow 208 indicates a power fuel line, also called a fuel line, or the above-mentioned power fuel line, by means of which fuel can be supplied to the injection member 66. Thus, arrow 208 indicates in particular the power fuel supply path 46 and / or the passage 68.

[0086] Control of the valve member of the injection member 66 is understood, for example, to mean that the valve member of the injection member 66 can be or is adjusted between at least one closed position and at least one open position by controlling the injection member 66. In the closed position, the valve member blocks, for example, the outlet opening 70, and in the open position, the valve member opens, for example, the outlet opening 70. Alternatively or additionally, control of the injection member 66 can be understood, for example, to mean control of a fuel pump, in particular the electrically operable piston pump 136 or the control described above.

[0087] In order to realise a particularly effective and efficient operation of the burner 42, as already alluded to in connection with Fig. 16, the electronic calculation device 52 (control device) determines a first amount of air, also called air amount, which is in particular actively supplied to the swirl chambers 62 and 76 or to which the swirl chambers 62 and 76 are in particular actively supplied. By active supply of air to the swirl chambers 62 and 76 is understood air being actively pumped by the air pump 56, in particular by electrical operation of the air pump 56, and thereby towards and into the swirl chambers 62 and 76. Furthermore, the electronic calculation device 52 determines a second amount of fuel, also called fuel amount, which is in particular actively supplied to the injection member 66 or to which the injection member 66 is in particular actively supplied. Active supply of fuel to the injection member 66 is understood in particular as meaning that the fuel is delivered by a fuel pump, in particular by electrical operation of the fuel pump, and is then delivered further through the injection member 66 and is injected in particular through the injection member 66 into the inner swirl chamber 62.

[0088] At least one actual value of the combustion air ratio is determined, in particular calculated, by the electronic calculation device 52 as a function of the air amount and as a function of the fuel amount. Furthermore, the burner 42 is activated by the electronic calculation device 52 as a function of the determined actual value, in particular the electronic calculation device 52 controls the air pump 56 and / or the injection element 66 and / or the fuel pump and / or the ignition device 60, in particular electrically and / or in dependence on the determined actual value. This is performed in particular in such a way that the actual value is compared with a setpoint value by the electronic calculation device 52. The electronic calculation device 52 activates the burner 42 as a function of the comparison of the setpoint and actual values ​​of the combustion air ratio, whereby a particularly preferred lambda control of the burner 42 can be realized.

[0089] Alternatively or additionally, it may be provided that for starting the initially deactivated burner 42, the power fuel is injected by the injection element 66, in particular directly, into the inner swirl chamber 62 during a first time period, during which there is no active supply of air, i.e. of each line, into the swirl chambers 62 and 76 and no ignition in the combustion chamber 58. After the first time period, i.e. for example during a second time period directly following the first time period, air is actively supplied to the swirl chambers 62 and 76, fuel is injected by the injection element 66 into the inner swirl chamber 62 during or within the second time period, and the mixture is ignited and burned in the combustion chamber 58 during or within the second time period. This allows a particularly fast and effective start-up of the initially deactivated burner 42, in particular within the framework of a cold start and / or under low ambient conditions.

Claims

1. 1. A method for operating a burner (42) of a motor vehicle having an exhaust pipe (26) through which exhaust gases of an internal combustion engine (12) can flow, comprising: The burner (42) a combustion chamber (58) in which a mixture including air and liquid fuel is ignited and thereby combusted; An ignition device (60) is provided, and the ignition is performed by the ignition device; The device has an inner swirl chamber (62) through which a first portion of air can flow and which generates a swirling flow of the first portion of air, the inner swirl chamber having a first outlet opening (64) through which the first portion of air can flow through the inner swirl chamber (62), and through which the first portion of air can be discharged from the inner swirl chamber (62); at least one injection member (66) having an outlet opening (70) arranged in the inner swirl chamber (62) through which a liquid fuel can be passed, by means of which fuel can be injected into the inner swirl chamber (62) via the outlet opening (70), the first outlet opening (64) also being through which fuel exits the injection member (66) via the outlet opening (70) and is thereby injected into the inner swirl chamber (62); an outer swirl chamber (76) surrounding at least one length region of the inner swirl chamber (62) in the circumferential direction of the inner swirl chamber (62) and capable of being passed through by a second portion of the air, generating a vortex-like flow of the second portion of the air, the outer swirl chamber having a second outlet opening (80) capable of being passed through by the second portion of the air passing through the outer swirl chamber (76), the fuel passing through the first outlet opening (64), and the first portion of the air passing through the inner swirl chamber (62) and the first outlet opening (64), through which the portions of the air and the fuel can be introduced into the combustion chamber (58); To start the burner (42), Fuel is injected into the inner swirl chamber (62) by the injection member (66) during a predetermined period of time; during said time period, no active supply of air to said swirl chamber and no ignition in said combustion chamber occurs; After the time period, air is actively supplied to the swirl chamber and fuel is injected into the inner swirl chamber by the injector, and the mixture is ignited and combusted in the combustion chamber. method.

2. The time period lasts at least 0.3 seconds 2. The method of claim 1 .

3. The period lasts at most 6 seconds, and preferably at most 4 seconds.

3. The method according to claim 1 or 2.

4. by an electronic computing device (52) at least after said time period; A first amount of air and a second amount of fuel are determined; determining at least one actual value of a combustion air ratio of the mixture based on the first amount and the second amount; The burner (42) is operated based on the determined actual value. The method according to any one of claims 1 to 3.

5. The electronic computing device (52) controls the injection member (66) based on the determined actual value, thereby operating the burner (42) based on the determined actual value.

5. The method of claim 4.

6. an air pump (56) by means of which air is actively pumped towards the swirl chamber (62, 76) and thereby towards and into the burner (42); and / or A fuel pump (136) is provided by which fuel is actively pumped toward and through the injector member (66) and thereby through the injector member (66) and into the inner swirl chamber (62). The method according to any one of claims 1 to 5.

7. A piston pump (136) is used as the fuel pump (136).

7. The method of claim 6.

8. The electronic computing device (52) controls the air pump (56) and / or the fuel pump (136) based on the determined actual value, thereby operating the burner (42) based on the determined actual value.

8. The method according to claim 6, which depends on claim 4 or claim 5, or claim 7, which depends on claim 6.

9. The electronic computing device (52) compares the actual value with a target value and activates the burner (42) based on the comparison.

10. A method according to claim 4, according to claim 5, according to claim 6 which depends on claim 4 or claim 5, according to claim 7 which depends on claim 6, or according to claim 8.

10. 1. A method for operating a burner (42) of a motor vehicle having an exhaust pipe (26) through which exhaust gases of an internal combustion engine (12) can flow, comprising: The burner (42) a combustion chamber (58) in which a mixture including air and liquid fuel is ignited and thereby combusted; An ignition device (60) is provided, and the ignition is performed by the ignition device; The invention comprises an inner swirl chamber (62) through which a first portion of air can flow and which generates a swirling flow of the first portion of air, the inner swirl chamber having a first outlet opening (64) through which the first portion of air flows through the inner swirl chamber (62), the first portion of air being discharged from the inner swirl chamber (62) via the first outlet opening, at least one injection member (66) having an outlet opening (70) arranged in the inner swirl chamber (62) through which a liquid fuel can flow, by means of which fuel is injected into the inner swirl chamber (62) via the outlet opening (70), the first outlet opening (64) also being pierced by the fuel which leaves the injection member (66) via the outlet opening (70) and is thereby injected into the inner swirl chamber (62); an outer swirl chamber (76) surrounding at least one length region of the inner swirl chamber (62) in the circumferential direction of the inner swirl chamber (62) and passing through it by a second portion of the air, the outer swirl chamber having a second outlet opening (80) passed through by the second portion of the air passing through the outer swirl chamber (76), the fuel passing through the first outlet opening (64) and the first portion of the air passing through the inner swirl chamber (62) and the first outlet opening (64), the air portions and the fuel being introduced into the combustion chamber (58) via the second outlet opening; By an electronic computing device (52), A first amount of air and a second amount of fuel are determined; determining at least one actual value of a combustion air ratio of the mixture based on the first amount and the second amount; The burner (42) is operated based on the determined actual value. A method comprising:

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