Method for operating a burner of a motor vehicle and a motor vehicle

Abstract

Method for operating a burner (44) arranged in an exhaust tract (10) of an internal combustion engine (12) of a motor vehicle, wherein: - the internal combustion engine (12) comprises: o an intake tract (24) through which air can flow, by means of which the air flowing through the intake tract (24) can be introduced into at least one combustion chamber of the internal combustion engine (12); and o a compressor (31) arranged in the intake tract (24) for conveying and compressing the air flowing through the intake tract (24); - the burner (44) is arranged in the exhaust tract (10), which has a combustion chamber (51) into which a mixture comprising air and fuel is to be burned; and - a supply line (56) is provided, through which the burner (44) can be supplied with at least a part of the air flowing through the intake tract (24); characterized in that in a deactivated state of the burner (44),In its deactivated state, combustion in the combustion chamber (51) ceases, the burner (44) is supplied via the supply line (56) with air originating from the intake tract (24), which is conveyed by means of the compressor (31), and the supply line (56) is fluidically connected to the intake tract (24) at a connection point (V1) arranged downstream of the compressor (31), wherein a valve element (70) is arranged in the intake tract (24) downstream of the connection point (V1), by means of which the intake tract (24) is fluidically blocked, while in the deactivated state of the burner (44) the burner (44) is supplied via the supply line (56) with the air originating from the intake tract (24), which is conveyed by means of the compressor (31), wherein in an unfired operation of the internal combustion engine (12) the burner (44) is supplied with air via the supply line (56),while the valve element (70) is closed and thus fluidically blocks the intake tract (24).

Description

The invention relates to a method for operating a burner arranged in an exhaust system of an internal combustion engine of a motor vehicle according to the preamble of claim 1. Furthermore, the invention relates to a motor vehicle, in particular a motor car. DE 10 2019 008 965 A1 discloses an exhaust system for an internal combustion engine. DE 10 2012 200 444 A1 and DE 10 2020 126 255 A1 each disclose, considered separately, a method for operating a burner arranged in the exhaust system of an internal combustion engine of a motor vehicle. The internal combustion engine has an intake manifold through which air can flow, by means of which the air flowing through the intake manifold can be introduced into at least one combustion chamber of the internal combustion engine, and a compressor arranged in the intake manifold for conveying and compressing the air flowing through the intake manifold. The burner is arranged in the exhaust manifold, which has a combustion chamber in which a mixture comprising air and fuel is to be burned. A supply line is provided through which the burner can be supplied with at least a portion of the air flowing through the intake manifold.In a deactivated state of the burner, during which combustion in the combustion chamber ceases, the burner is supplied with air from the intake tract via the supply line. DE 10 2020 126 255 A1 further discloses valve elements that can fluidically block the intake tract, so that in the deactivated state of the burner, the burner is supplied with air from the intake tract via the supply line. The object of the present invention is to provide a method for operating a burner of a motor vehicle and a motor vehicle with at least one such burner, so that a particularly advantageous operation of the burner can be realized. This problem is solved by a method with the features of claim 1 and by a motor vehicle with the features of claim 8. Advantageous embodiments with expedient further developments of the invention are specified in the remaining claims. A first aspect of the invention relates to a method for operating a burner arranged in the exhaust system of an internal combustion engine of a motor vehicle, also referred to simply as a vehicle. The internal combustion engine is also called an internal combustion engine or motor and is preferably designed as a reciprocating engine. In its fully manufactured state, the motor vehicle comprises the internal combustion engine and thus the exhaust system and the burner, wherein the motor vehicle, preferably designed as a car, most preferably as a passenger car or commercial vehicle, can be driven by means of the internal combustion engine. The exhaust system is permeable to exhaust gas from the internal combustion engine. In this process, the internal combustion engine has an intake manifold, also referred to as the intake tract, through which fresh air (also simply called air) flows. This intake manifold allows the fresh air flowing through it to be introduced into at least one combustion chamber, and in particular, several combustion chambers, of the internal combustion engine. In other words, the at least one combustion chamber can be supplied with air flowing through it via the intake manifold. Specifically, during operation of the internal combustion engine, the fresh air flowing through the intake manifold is introduced into the at least one combustion chamber via the intake manifold. During operation of the internal combustion engine, combustion processes take place within the engine, particularly in the at least one combustion chamber.During each combustion process, a fuel-air mixture is burned, resulting in the exhaust gas of the internal combustion engine, also known as engine exhaust. The fuel-air mixture comprises the fresh air introduced into the at least one combustion chamber and a preferably liquid fuel. For example, the fuel is diesel fuel, so the internal combustion engine is preferably a diesel engine. The engine exhaust can flow out of the combustion chamber and into the exhaust system, subsequently flowing through the exhaust system. At least one component, such as an exhaust aftertreatment element, can be arranged in the exhaust system for treating the exhaust gas.The exhaust aftertreatment element is or includes, for example, a catalyst, in particular an SCR catalyst, wherein, for example, selective catalytic reduction (SCR) can be catalytically supported and / or effected by means of the SCR catalyst, such that, for example, the SCR catalyst is catalytically active for the SCR process. In selective catalytic reduction, any nitrogen oxides contained in the engine exhaust gas are at least partially removed from the exhaust gas by reacting the nitrogen oxides with ammonia to form nitrogen and water. The ammonia is provided, for example, by a reducing agent, which is particularly liquid and may be an aqueous urea solution. Furthermore, it is conceivable that the exhaust aftertreatment element is or includes a particulate filter. In particular, the particulate filter is a diesel particulate filter (DPF).The particulate filter can be used to filter out any particles, especially soot particles, that may be contained in the exhaust gas. The internal combustion engine also has at least one compressor arranged in the intake manifold, by means of which the air flowing through the intake manifold can be compressed and conveyed. For this purpose, the compressor has, for example, a compressor wheel, also referred to as an impeller, which is rotatably arranged in a compressor housing. By rotating the compressor wheel relative to the compressor housing, the air flowing through the intake manifold can be conveyed, in particular conveyed through the intake manifold, and compressed. Thus, the at least one combustion chamber is supplied with the air (fresh air) compressed by the compressor. In other words, the air (fresh air) compressed by the compressor can be directed into the at least one combustion chamber via the intake manifold. The burner is arranged in the exhaust tract, and a mixture is to be combusted by means of the burner, wherein the mixture comprises air, which is also referred to as burner air, and a preferably liquid fuel. Preferably, the aforementioned fuel is used as the fuel. For example, the burner has a combustion chamber, also called the main combustion chamber, in which the mixture, also called the burner mixture, comprising the aforementioned burner air and the fuel, can be burned. For example, the mixture, also called the burner mixture, can be ignited in the combustion chamber and thereby combusted. The air forming the mixture (burner mixture) is also called burner air. In particular, the combustion chamber is bounded by a chamber element, especially one designed as a solid, and in particular by an inner circumferential surface of the chamber element, especially directly. The combustion of the burner mixture in the burner, especially in the combustion chamber, produces exhaust gas, also called burner exhaust gas.The burner exhaust gas can, for example, flow out of the burner, particularly from the combustion chamber, and into the exhaust system, that is, into an exhaust channel of the exhaust system through which the engine exhaust gas flows, particularly at an inlet point that is located upstream of the aforementioned component in the direction of flow of the engine exhaust gas through the exhaust system or exhaust channel. For example, the burner exhaust gas mixes with the engine exhaust gas. Consequently, the burner exhaust gas, especially the burner exhaust gas mixed with the engine exhaust gas, can flow through the component, thereby heating it up.In particular, it is conceivable that the burner exhaust gas can flow out of the burner, especially from the combustion chamber, and into the exhaust system or the aforementioned exhaust duct, thereby mixing with the engine exhaust gas and / or gas flowing through the exhaust system, thus heating the engine exhaust or the gas. In other words, this can result in a particularly high temperature of the engine exhaust or gas, also known as the exhaust gas temperature.In particular, the gas can be, for example, air flowing through the exhaust system or exhaust duct, especially when the internal combustion engine is off, i.e., when the engine is not firing and therefore not producing exhaust gas. In this case, the gas, especially the air, is forced through the exhaust system, particularly by means of a pump. The high exhaust gas temperature can heat and / or keep the component warm, as the burner exhaust and, for example, the engine exhaust or the gas flow through the component.Thus, for example, the burner exhaust gas from the burner, particularly from the combustion chamber, is introduced at the aforementioned inlet point into the exhaust system, specifically into the exhaust duct, and thus into the engine exhaust gas or gas flowing through the exhaust system or exhaust duct, particularly when the burner is activated and, in its activated state, provides the burner exhaust gas. This means, in particular, that when the burner is activated, the mixture is burned within the burner, specifically in the combustion chamber; in other words, combustion of the mixture takes place. In this process, the internal combustion engine also has a supply line through which the burner can be supplied with at least a portion of the air flowing through the intake manifold, specifically as burner air. This supply line is also referred to as the primary supply line. When the term "supply line" is used before and after, it refers, unless otherwise specified, to the primary supply line. For example, at least the aforementioned portion of the air flowing through the intake manifold can be diverted from the intake manifold and introduced into the supply line, and specifically directed to the burner as burner air, so that at least this portion of the air is used as burner air, and thus the burner air originates, for example, from the intake manifold. For example, the burner has at least one channel through which at least a portion of the burner air flows. The aforementioned portion of the burner air is also referred to as the first portion of the burner air. Whenever the term "part of the burner air" is used before and below, it refers, unless otherwise specified, to the first portion of the burner air. The channel is also referred to as the first channel. Whenever the term "channel" is used before and below, it refers, unless otherwise specified, to the first channel. Whenever the term "air" is used before and below, it refers, unless otherwise specified, to the burner air that forms the burner mixture. For example, the burner has a component designed as a solid body that directly delimits the channel.In particular, the channel is directly bounded by an inner circumferential surface of the component, which is preferably concave. For example, the channel has at least one or exactly one outlet opening through which the burner air flowing through the channel can be discharged from the channel and thus supplied to the combustion chamber, in particular introduced into the combustion chamber. More generally, the burner air flowing through the channel can be supplied to the combustion chamber, in particular introduced into the combustion chamber, via the channel. The aforementioned outlet opening is also referred to as the first outlet opening. When the term "outlet opening" is used before and below, it refers, unless otherwise specified, to the first outlet opening. For example, the burner also has an ignition device, particularly one that is electrically operated, by means of which the burner mixture, especially in the combustion chamber, can be ignited. It is particularly conceivable that the ignition device is at least partially located in the combustion chamber. By means of the ignition device, at least one ignition spark can be provided, i.e., generated, for igniting the mixture, particularly in the combustion chamber and / or using electrical energy with which the ignition device can be supplied or is supplied, so that the burner mixture, particularly in the combustion chamber and most preferably outside the channel, can be ignited and subsequently burned by means of the ignition spark. The ignition device can, for example, be designed as a spark plug, a glow plug, or a glow pin.In particular, the ignition device can ignite the burner mixture at at least or exactly one ignition point, for example, such that the ignition spark can be generated at the ignition point by means of the ignition device. The burner also has, for example, an injection element, also referred to as an injection element or designed as an injection element, by means of which the fuel can be introduced, at least indirectly, and in particular directly, into the channel, and in particular injected. The channel is designed, for example, to create a swirling flow, also known as the first swirling flow, of the initial portion of the burner air, i.e., the burner air flowing through the channel. For this purpose, the channel includes, for example, a swirl chamber, also referred to as the first swirl chamber, by means of which the first swirling flow of the burner air flowing through the channel is achieved. The first swirl chamber is, for example, an internal swirl chamber, which will be explained in more detail below. The first channel, and thus, for example, the first swirl chamber, is arranged upstream of the combustion chamber in the direction of flow of the burner air flowing through the first channel and thus the first swirl chamber. The aforementioned flow direction of the burner air flowing through the first channel is also referred to as the first flow direction.Thus, for example, the first swirl chamber has, as its only outlet opening, the first outlet opening through which the burner air flowing through the first channel and thus the first swirl chamber can be discharged, for example, from the first channel and thus, in particular, from the first swirl chamber, and introduced, for example, into the combustion chamber. Therefore, the combustion chamber is arranged downstream of the first channel and, in particular, downstream of the first combustion chamber in the direction of flow of the burner air flowing through the first channel and thus, in particular, the first swirl chamber.The characteristic that the first swirl chamber causes or can cause the aforementioned first swirl flow of the burner air flowing through the first channel and thus the first swirl chamber means in particular that the first part of the burner air, i.e. the burner air flowing through the first channel, flows swirlingly through the first swirl chamber, thus flowing swirlingly through at least a first sub-area of ​​the first swirl chamber, and / or the first part of the burner air, i.e. the burner air flowing through the first channel, only exhibits its first swirl flow at least in a first flow region arranged downstream of the first swirl chamber and outside the first swirl chamber, which is, for example, arranged in the combustion chamber.In particular, it is conceivable that the first part of the burner air flows out of the first swirl chamber via the first outlet opening in a swirling motion and / or flows into the combustion chamber in a swirling motion, so that it is most preferably provided that the first part of the burner air, i.e., the burner air flowing through the first channel, exhibits its first swirling flow at least in the combustion chamber. In particular, it is conceivable that the first part of the burner air already exhibits its first swirling flow in the first swirl chamber, specifically at least in the aforementioned first sub-section of the first swirl chamber. The fuel can be introduced, for example, at an injection point by means of the injection element, and in particular, injected. For example, the injection element is an injection element by means of which the fuel can be introduced, and in particular injected, at the injection point. In particular, the injection element can, for example, inject the fuel from itself at the injection point. The injection element has, for example, at least or exactly one outlet opening through which the preferably liquid fuel can flow. In particular, it is conceivable that the injection element has several, in particular more than two, outlet openings through which the preferably liquid fuel can flow. In particular, it is conceivable that the injection element has at least or exactly three outlet openings through which fuel can flow.The fuel can be introduced, particularly at the injection point, by means of the injection element. In particular, the injection element can spray the fuel flowing through it out of its respective outlet opening and thereby introduce, at least indirectly, and in particular directly, into the channel, in particular by injection. For example, the burner can have a second channel through which a second portion of the burner air forming the mixture can flow, particularly in a second flow direction. For instance, the second channel is designed to create a second swirl flow of the second portion of the burner air. For this purpose, the second channel may have a second swirl chamber, by means of which the second swirl flow of the second portion of the burner air can be achieved. If, for example, the first swirl chamber is the aforementioned inner swirl chamber, then the second swirl chamber is, for instance, an outer swirl chamber. Furthermore, it is conceivable that the first swirl chamber is the outer swirl chamber and the second swirl chamber is the inner swirl chamber.The outer swirl chamber surrounds, for example, at least a longitudinal 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. The second channel, and thus, for example, the second swirl chamber, is permeable to the second portion of the burner air in the aforementioned second flow direction, wherein, for example, the first and second flow directions coincide, or the first flow direction runs parallel to the second flow direction and vice versa. In particular, the flow directions point in the same direction. Most specifically, it is provided that the aforementioned circumferential direction of the inner swirl chamber or the first swirl chamber runs around the first flow direction.For example, it is intended that the second channel, and thus the second swirl chamber, is arranged upstream of the combustion chamber when viewed in the second flow direction, which is therefore, for example, arranged downstream of the second channel and thus, for example, the second swirl chamber when viewed in the second flow direction. When the flow direction is mentioned before and below, this refers, unless otherwise specified, to the first flow direction.The circumferential direction of the inner or first swirl chamber, for example, runs around the first flow direction, which, for instance, runs in the axial direction of the inner or first swirl chamber and thus of the first outlet opening, and therefore coincides with the axial direction of the inner or first swirl chamber, whose radial direction is perpendicular to the axial direction of the inner or first swirl chamber and thus of the first outlet opening. In particular, for example, the first flow direction runs in the axial flow direction of the first swirl chamber, whose radial direction is perpendicular to the axial direction of the swirl chamber. Furthermore, it is conceivable that the first flow direction coincides with the axial direction of the first swirl chamber.Furthermore, for example, the second flow direction runs in the axial direction of the second swirl chamber, the radial direction of which is perpendicular to the axial direction of the second swirl chamber. In particular, the second flow direction coincides with the axial direction of the second swirl chamber. Preferably, the first swirl chamber terminates at the first outlet or at its end, in the flow direction of the first portion of the burner air flowing through the first outlet opening. The second swirl chamber, whose axial direction coincides with the axial direction of the first swirl chamber, is permeable to the second portion of the burner air in the second flow direction and is designed, for example, to create the second swirl flow of the second portion of the burner air.This means, in particular, that the second part of the burner air flows in a swirling pattern in the second swirl chamber, thus flowing in a swirling pattern through at least a second sub-region of the second swirl chamber, and / or that the second part of the burner air exhibits its second swirling flow in a second flow region located downstream of the second swirl chamber in the direction of flow of the second part of the burner air flowing through the second swirl chamber, which may coincide with the aforementioned first flow region. This second flow region may, for example, be located outside the second swirl chamber and, for example, inside the combustion chamber. Furthermore, it is conceivable that the aforementioned first flow region is located outside the second swirl chamber.In other words, it is conceivable that the second part of the burner air flows out of the second swirl chamber in a swirl pattern and / or flows into the combustion chamber in a swirl pattern, so that it is preferably provided that the second part of the burner air has its second swirl-shaped flow at least in the combustion chamber. For example, the second channel, in particular the second swirl chamber, has a second outlet opening through which the second part of the burner air flows through the second channel and thus, for example, the second swirl chamber, and the first part of the burner air flows through the first swirl chamber and the first outlet, and, for example, also through which the fuel flows through the first channel, can flow, and which is arranged, for example, downstream of the first outlet opening in the direction of flow of the parts of the burner air, through which the second part of the air can be discharged from the second swirl chamber and the parts of the air, for example, also the fuel, can be supplied to the combustion chamber, in particular introduced into the combustion chamber.Since, for example, the fuel can be introduced, in particular by means of the injection element, at least indirectly, in particular directly, into the first channel, especially by bypassing the combustion chamber, the first outlet opening can be opened, in particular in the first flow direction, and can be flowed through by both the first part of the burner air, thus both by the burner air flowing through the first channel and by the fuel, so that, as a consequence, the second outlet opening can be opened, in particular in the second flow direction, by both the second part of the burner air and the first part of the burner air and also by the fuel.Thus, it is specifically provided that during or in the aforementioned activated operation, i.e., during the activated operation of the burner, the burner air flowing through the first channel flows in the first flow direction through the first channel and, in particular, through the first outlet opening, and, for example, in the activated operation, the fuel flows in the first flow direction through the first channel and, in particular, through the first outlet opening. During the activated operation, i.e., in the activated operation of the burner, the second part of the burner air flows in the second flow direction through the second channel and, in particular, through the second outlet opening, and, for example, the parts of the burner air and the parts of the fuel flow in the second flow direction through the second outlet opening. In particular, the characteristic that the second swirl chamber causes or can cause the second swirl flow of the second part of the burner air flowing through the second swirl chamber or the second channel is to be understood as meaning that the second part of the burner air flows through the second swirl chamber in a swirl pattern, thus flowing through at least a second sub-area of ​​the second swirl chamber in a swirl pattern, and / or the second part of the burner air only exhibits its second swirl flow at least in a second flow area located downstream of the second swirl chamber and outside the second swirl chamber, which is, for example, located in the combustion chamber.In particular, it is conceivable that the second part of the burner air flows out of the second swirl chamber via the second outlet opening in a swirling pattern and / or flows into the combustion chamber in a swirling pattern, so that it is most preferably provided that the second part of the burner air exhibits its second swirling flow at least within the combustion chamber. In particular, it is conceivable that the second part of the burner air already exhibits its second swirling flow within the second swirl chamber, specifically at least in the aforementioned second sub-section of the second swirl chamber. In particular, it can be provided that the combustion chamber is arranged downstream of the first swirl chamber and / or downstream of the second swirl chamber in the flow direction of the respective portion of the burner air flowing through the respective swirl chamber. Specifically, the combustion chamber is arranged downstream of the respective channel in the flow direction of the respective portion of the burner air flowing through the respective channel. In particular, the portions of the burner air, and especially the fuel, from the second channel can flow through the second outlet opening along the second flow direction, particularly in the second flow direction, and thus be supplied to the combustion chamber via the second outlet opening, particularly flowing into the combustion chamber, wherein, for example, the second flow direction runs parallel to the first flow direction or coincides with the first flow direction.In particular, the first flow direction and the second flow direction run along a common straight line. Furthermore, it is preferably provided that the second flow direction runs in the axial direction of the second swirl chamber, thus coinciding with the axial direction of the second swirl chamber, whose radial direction is perpendicular to the axial direction of the second swirl chamber, so that, for example, the radial direction of the second swirl chamber coincides with the radial direction of the first swirl chamber and vice versa. Thus, it is most preferably provided that the axial direction of the first swirl chamber corresponds to the axial direction of the second swirl chamber, or vice versa. In other words, it is preferably provided that the axial direction of the first swirl chamber coincides with the axial direction of the second swirl chamber and vice versa.Furthermore, it is preferably provided that the radial direction of the second swirl chamber coincides with the radial direction of the first swirl chamber and vice versa. In other words, it is preferably provided that the radial direction of the first swirl chamber corresponds to the radial direction of the second swirl chamber and vice versa. The respective axial direction of each swirl chamber is perpendicular to the respective radial direction of the respective swirl chamber, with the radial direction of the first swirl chamber coinciding with the radial direction of the second swirl chamber and vice versa.Since, for example, the second outlet opening is arranged along the respective flow direction, that is, in the flow direction of the respective part of the burner air downstream of the first outlet opening, and since preferably the second swirl chamber or the outer swirl chamber surrounds the first outlet opening, the first outlet opening is, for example, arranged in the second swirl chamber, particularly in the outer swirl chamber. In particular, it is conceivable that the second swirl chamber terminates at the second outlet opening, especially at its end, in the flow direction of the second part of the burner air flowing through the second outlet opening. For example, in order to generate the respective swirling flow of the respective part of the air, the respective swirl chamber has a respective swirl generation device by means of which the respective swirling flow of the respective part of the burner air can be effected. In order to ensure particularly advantageous operation of the burner over a long service life, the inventive method provides that, in a deactivated state of the burner, the burner, in particular the first channel and / or the second channel, is supplied with air from the intake tract via the supply line, in particular bypassing the combustion chamber, which is conveyed by means of the compressor, in particular the compressor wheel.The characteristic that the burner, in particular the first channel and / or the second channel, is supplied with air from the intake tract bypassing the combustion chamber when the burner is deactivated, means that the air from the intake tract, which supplies the burner via the supply line when the burner is deactivated, does not flow through the combustion chamber on its way from the intake tract to and into the burner, in particular to the first channel and / or to and into the second channel. Hereinafter, the air from the intake tract, which supplies the burner, in particular the first channel and / or the second channel, via the supply line when the burner is deactivated, is also referred to as cleaning air.When the burner is deactivated, combustion does not occur in the combustion chamber. Therefore, no combustion takes place in the combustion chamber during this time. This means that the burner mixture is not combusted in the combustion chamber, and no other mixture is combusted either; consequently, the burner does not produce any exhaust gas. Preferably, in the deactivated state of the burner, the cleaning air flows through the first channel and / or the second channel. Most preferably, in the deactivated state of the burner, the cleaning air is conveyed through the first channel and / or the second channel, and thus through the first outlet opening and / or the second outlet opening, by means of the compressor, i.e., by means of the compressor wheel. In particular, in the deactivated state of the burner, the cleaning air is conveyed through the supply line by means of the compressor, especially the compressor wheel. Most particularly, in the deactivated state of the burner, the cleaning air is conveyed into the combustion chamber by means of the compressor, i.e., by means of the compressor wheel. The cleaning air can be used to remove deposits and / or other contaminants from areas of the burner, in particular by or by allowing the cleaning air to flow through, along, or around these areas while the burner is in deactivated mode. These areas include, for example, the burner's wall sections. Furthermore, it is conceivable that these areas are formed by at least one or more components of the burner, particularly those made of solid materials. The deposits include, for example, particles such as soot particles and / or other dirt, which can accumulate or settle on these areas, especially with increasing service life and / or operating time of the burner.This can be achieved in particular as follows: As described above, for example, during operation of the burner, in an activated state, where the mixture is burned in the combustion chamber, and the burner provides the exhaust gas, the exhaust gas can flow out of the combustion chamber and into the exhaust system, in particular into the exhaust duct. For this purpose, the aforementioned chamber element has, for example, at least one or more through-openings through which, in the activated state, i.e., during operation of the burner, which is in the activated state during its operation, the exhaust gas flows, causing the burner gas to flow out of the combustion chamber and into the exhaust system, in particular into the exhaust duct.If the burner is deactivated, meaning it is not supplying exhaust gas, and the internal combustion engine is in operation, the engine exhaust can flow through the exhaust system. For example, it can flow from the exhaust system through the through-opening and thus into the combustion chamber. From the combustion chamber, the engine exhaust can flow through the first and / or second outlet opening and thus into the first and / or second channel. In other words, the engine exhaust can flow to, and thus reach, the aforementioned area of ​​the burner. This engine exhaust can contain the aforementioned particles, particularly soot particles, and / or other contaminants, which can then accumulate or be deposited in these areas. The invention now makes it possible to remove the aforementioned deposits from these areas using cleaning air. Since the cleaning air is supplied by the compressor, it can have an advantageously high pressure, which is achieved by the compressor, in particular by the compressor supplying the cleaning air. Thus, even deposits that are firmly adhered to the aforementioned areas of the burner can be removed. In particular, the compressor can generate a higher pressure for the cleaning air than, for example, an air pump specifically designed for the burner and for supplying it with combustion air, so that the invention enables a particularly advantageous cleaning of the burner areas.In particular, the deposits or impurities consist of coking components such as soot and / or compounds that include unburned hydrocarbons (HC). It has been shown that the aforementioned deposits can clog and thus reduce the first channel and / or the second channel, in particular the first outlet opening and / or the second outlet opening, and / or at least one other, further flow cross-section of the burner through which the burner air flows, which can impair efficient burner operation. The invention now makes it possible to avoid excessive clogging of the first channel and / or the second channel, in particular the first outlet opening and / or the second outlet opening and / or the flow cross-section, so that particularly efficient burner operation can be ensured even over a long burner service life. In particular, for example, the swirl chambers can be cleaned and / or kept clean by means of the cleaning air.For example, each swirl chamber has swirl channels by means of which the respective swirl flow is created. In particular, the swirl channels can be cleaned of impurities using the cleaning air. This prevents excessive clogging of the swirl chambers, ensuring that the swirl chambers can maintain a beneficial swirl of the burner air even over a long burner service life. This allows the burner to be operated efficiently and effectively over a long service life. In particular, the cleaning air is compressed air, since the compressor that supplies the cleaning air can generate a particularly high pressure, also referred to as air pressure, by supplying and, for example, compressing the cleaning air. The method according to the invention thus enables the realization of a compressed air cleaning mechanism that uses the cleaning air as compressed air supplied by the compressor. Deposits can be advantageously removed from the aforementioned areas of the burner by means of this compressed air. Preferably, the compressor is a component of an exhaust gas turbocharger, which has a turbine arranged in the exhaust tract. The turbine can be driven by the engine exhaust gas. For example, the compressor can be driven by the turbine, in particular via a shaft. Preferably, the turbine is arranged upstream of the burner or the inlet point in the flow direction of the engine exhaust gas flowing through the exhaust tract. Since the invention allows contaminants such as deposits, i.e., coatings, to be advantageously removed from the burner areas, especially from the swirl chambers, reliable and advantageous burner operation can be achieved, particularly with regard to mixture preparation. Mixture preparation refers to the formation of the mixture, also known as conditioning.In other words, the burner mixture can be advantageously formed even over a long service life, since the respective swirl chamber can generate a beneficial swirl of the burner air throughout the burner's long lifespan. Consequently, the burner air can be efficiently mixed with the fuel, resulting in a particularly advantageous mixture formation, also known as mixture formation or mixture preparation. The supply line is fluidically connected to the intake tract at a connection point, also referred to as the first connection point, located downstream of the compressor, particularly the compressor wheel, in the direction of flow of the fresh air passing through the intake tract. When the term "connection point" is used before and after, it refers to the first connection point unless otherwise specified. A valve element is arranged in the intake tract downstream of the first connection point, by means of which the intake tract is fluidically closed. When the burner is deactivated, the burner is supplied via the supply line (first supply line) with the air (cleaning air) from the intake tract, which is conveyed by the compressor.This allows for an effective and efficient supply of cleaning air to the burner, so that even particularly stubborn contaminants adhering to the burner can be removed. In order to clean the burner, especially the aforementioned areas, particularly effectively and efficiently from contaminants such as deposits, one embodiment of the invention provides that an air path extending continuously from the compressor to the burner, encompassing the entire supply line and, for example, a portion of the intake tract, through which the burner is supplied with air (cleaning air) originating from the intake tract and conveyed by the compressor when in the deactivated state, is free of an air pump provided in addition to the compressor for conveying the cleaning air.This prevents excessive pressure loss of the cleaning air on its way from the intake tract to the burner, so that the cleaning air builds up a suitably high pressure when it flows through the burner, especially through the first channel and / or the second channel. This also allows even particularly stubborn deposits to be removed from the burner. Another embodiment is characterized by a second supply line, provided in addition to the first and at least partially separated from it, particularly fluidically. This second supply line provides the burner with combustion air from the intake tract during its activated state, i.e., during the aforementioned burner operation, when the mixture is combusted in the combustion chamber. This provides a functional separation. On the one hand, the first supply line is used to supply the burner with cleaning air and subsequently to clean the burner in its deactivated state. On the other hand, the second supply line is used to supply the burner with combustion air in its activated state. This ensures effective and efficient burner operation. In order to achieve the particularly advantageous operation of the burner, it has proven especially advantageous if an air pump is arranged in the second supply line in addition to the compressor and also in addition to the internal combustion engine, by means of which, in the activated state of the burner, the burner air is conveyed through the second supply line and thereby conveyed to the burner, so that the burner is supplied with the burner air. It has proven particularly advantageous if the second supply line is fluidically connected to the intake tract at a second connection point, with the first connection point located upstream of the second connection point. This ensures effective and efficient cleaning of the burner in the deactivated state, as the burner can then be advantageously supplied with cleaning air. In the activated state, an advantageous supply of combustion air to the burner can be achieved via the second supply line. In principle, the invention enables the burner to be supplied with cleaning air via the supply line, for example, when the combustion engine is not operating under fire and / or when a change from fired to unfired operation occurs, and in particular when an electronic computing device determines the situation, whereby combustion processes cease in the combustion engine, and thus in particular in the combustion chamber(s) or all combustion chambers of the combustion engine, particularly while the valve element is closed and thus fluidically blocks the intake tract. Thus, for example, a path for the air flowing through the intake tract to the second supply line is blocked, and therefore, for example, without the need for an air pump.The invention can, for example, exploit the fact that during a certain period of time following the start of unfired operation of the internal combustion engine, the compressor wheel continues to rotate, in particular continues to rotate, even though the combustion engine is not operating under fire during this period. This period begins, for example, with the start of unfired operation, and in particular, at the end of fired operation. This period can extend over several seconds. During the period in which the compressor wheel continues to rotate, it draws air through the intake manifold. This air, drawn by the compressor wheel during this period, is excess air that is used, or can be used, as cleaning air.It was found that, particularly in the case described above, the cleaning air has an air pressure of 2 bar and higher, this pressure being caused by the compressor wheel continuing to rotate, especially after it has finished rotating, during the cleaning process. The invention now makes it possible to blow the excess air out of the intake tract as cleaning air and direct it to the burner, specifically through the burner. To enable particularly efficient and effective cleaning of the burner, a further embodiment of the invention provides for the compressor to be designed as an electric compressor. The compressor comprises a compressor wheel for compressing and conveying the air and an electric motor. When the burner is deactivated, the electric motor drives the compressor wheel, thereby supplying the burner with cleaning air from the intake manifold via the supply line. For example, the exhaust gas turbocharger is designed as an electrically assisted exhaust gas turbocharger, also known as an E-ATL. The electric compressor allows for a particularly high pressure of the cleaning air, specifically 1.5 bar or more.Further advantages, features, and details of the invention will become apparent from the following description of a preferred embodiment and from the drawing. The features and combinations of features mentioned above in the description, as well as those mentioned below in the figure description and / or shown in the single figure 1, can be used not only in the combinations specified, but also in other combinations or individually, without departing from the scope of the invention. The drawing shows in the single figure 1 a schematic representation of an internal combustion engine of a motor vehicle. Fig. 1 shows a schematic representation of an exhaust system 10, also referred to as an exhaust tract, for an internal combustion engine (also referred to as an engine, combustion engine, or internal combustion power unit) of a motor vehicle, preferably a car, which is also simply referred to as a vehicle and is, for example, a passenger car or a commercial vehicle. The following describes a method for operating a burner 44 arranged in the exhaust system 10 with reference to Fig. 1. The motor vehicle is powered by the internal combustion engine 12, which is preferably a reciprocating engine. Preferably, the internal combustion engine 12 is a diesel engine. It would also be conceivable for the internal combustion engine 12 to be a gasoline engine.The internal combustion engine 12 is associated with a tank 14, also referred to as a fuel tank, in which a fuel, in particular a liquid fuel, is stored for operating the internal combustion engine 12 during its combustion operation. If the internal combustion engine 12 is, for example, a diesel engine, the fuel is diesel fuel. A low-pressure pump 16 can pump the fuel from the tank 14 to a high-pressure pump 18. The high-pressure pump 18 pressurizes the fuel and pumps it, for example, to a fuel distribution element, also referred to as a rail. The fuel is temporarily stored at high pressure in the fuel distribution element.The high-pressure fuel is distributed from the fuel distribution element to individual injectors 20, by means of which the high-pressure fuel is injected directly into the cylinder 22 of the internal combustion engine 12. Each cylinder 22 partially defines a combustion chamber of the internal combustion engine 12. The internal combustion engine 12 has an intake manifold 24, also referred to as the intake tract, through which air, also called fresh air, can flow. The intake manifold 24 supplies or directs the fresh air flowing through it to, and in particular into, the combustion chambers, and thus to, and in particular into, the cylinders 22. In other words, the intake manifold 24 allows or directs the fresh air flowing through it into the combustion chambers. Thus, a fuel-air mixture is formed in the respective combustion chamber, and therefore in the respective cylinder 22, which is ignited, in particular by auto-ignition, and thereby combusted. This results in exhaust gas from the internal combustion engine 12, the exhaust gas of which is also referred to as engine exhaust.The internal combustion engine 12 has an exhaust tract 10, through which the engine exhaust gas from the combustion chambers, i.e., from the cylinders, can flow. The internal combustion engine 12 also has a charging device 28, which includes at least or exactly one exhaust gas turbocharger 30. The exhaust gas turbocharger 30 has a compressor 31 arranged in the intake tract 24 with a compressor wheel 32, also referred to as an impeller, whereby the fresh air flowing through the intake tract 24 can be compressed by means of the compressor wheel 32, and thus by means of the compressor 31. The exhaust gas turbocharger 30 also has a turbine 33 arranged in the exhaust tract 10 with a turbine wheel 34. The turbine wheel 34, and thus the turbine 33, can be driven by the engine exhaust gas. The compressor wheel 32 can be driven by the turbine wheel 34, in particular via a shaft of the exhaust gas turbocharger 30. An exhaust aftertreatment device 36 is arranged in the exhaust tract 10, positioned downstream of the turbine 33, i.e., downstream of the turbine wheel 34, in the direction of flow of the engine exhaust gas through the exhaust tract 10. The exhaust aftertreatment device 36 comprises an oxidation catalyst 38, a particulate filter 40, and an SCR catalyst 42. Since the exhaust tract 10 is open to flowing exhaust gas, the oxidation catalyst 38, the particulate filter 40, and the SCR catalyst 42 are also open to flowing exhaust gas. The oxidation catalyst 38, the particulate filter 40, and the SCR catalyst 42 are therefore components open to flowing engine exhaust gas, which are preferably designed as exhaust aftertreatment elements for treating the engine exhaust gas. For example, the oxidation catalyst 38 is designed as a diesel oxidation catalyst (DEC). In this case, the oxidation catalyst 38 is arranged downstream of the turbine 33 and upstream of the particle filter 40.The particulate filter 40 is arranged downstream of the oxidation catalyst 38 and upstream of the SCR catalyst 42. The particulate filter 40 filters out any particles, especially soot particles, that may be present in the engine exhaust. Furthermore, a metering device 45 is arranged in the exhaust tract 10, by means of which a reducing agent, in particular a liquid reducing agent and, more specifically, an aqueous urea solution, can be introduced into the engine exhaust at a location S1 downstream of the oxidation catalyst 38 and upstream of the SCR catalyst 42. Furthermore, the burner 44, which has a combustion chamber 51, is arranged in the exhaust tract 10. The burner 44 can be supplied with air, also referred to as burner air, and a fuel, in particular a liquid fuel. Preferably, the fuel with which the burner 44 can be supplied, or is supplied, particularly when the burner 44 is activated, is the fuel that can be stored or has been stored in the tank 14. By supplying the burner 44 with the burner air and the fuel, a burner mixture, also simply referred to as a mixture, can be formed, particularly in the burner 44, which comprises the fuel and the burner air with which the burner 44 is or was supplied.Particularly during the activated state of the burner 44, the burner mixture is combusted in the combustion chamber 51, especially also with the formation of a flame 46, resulting, for example, in burner exhaust gas. The flame 46 and / or the burner exhaust gas can be introduced into the exhaust tract 10 at a second point S2, also referred to as the inlet point, thereby heating the engine exhaust gas. The engine exhaust gas, heated particularly at point S2, can flow through the particulate filter 40 and the SCR catalyst 42, thereby heating the particulate filter 40 and / or the SCR catalyst 42. It can be seen that point S2 is located upstream of the particulate filter 40 and upstream of the SCR catalyst 42, and particularly downstream of point S1. In the exhaust tract 10, a mixing chamber 47 is arranged downstream of the oxidation catalyst 38 and upstream of the particulate filter 40. The flame 46 can be generated in this chamber by means of the burner 44 and / or introduced into it. This allows the engine exhaust gas to be heated, for example, in the mixing chamber 47. In particular, the burner exhaust gas, which flows into the engine exhaust gas, for example, at point S2, and especially flows out of the combustion chamber 51 and into the engine exhaust gas, can be mixed particularly advantageously with the engine exhaust gas in and / or by means of the mixing chamber 47. This heats the engine exhaust gas from the combustion chambers, i.e., from the cylinders 22, which in turn allows the particulate filter 40 and / or the SCR catalyst 42 to be advantageously heated. Figure 1 also shows that a fuel line 48, through which fuel from the tank 14 flows, is provided.The fuel line 48 can supply the burner 44, in particular its feed element, with fuel from the tank 14, so that the fuel is used as the aforementioned fuel. For example, the fuel from the tank 14 can be pumped through the fuel line 48 by means of the low-pressure pump 16 and thus conveyed to the burner 44, in particular to its feed element. An electronic computing device 52, also referred to as a control unit, is also provided. For example, the aforementioned procedure is carried out using the electronic computing device 52. A valve element 54 is arranged in the fuel line 48, by means of which the quantity of fuel supplied to the burner 44 can be adjusted. The valve element 54 can be controlled, in particular controlled or regulated, by the electronic computing device 52, so that the control unit (electronic computing device 52) can adjust, in particular regulate, the quantity of fuel supplied to the burner 44 by controlling the valve element 54. A first supply line 56 is also provided, via which the burner 44 can be supplied with at least part of the air flowing through the intake tract 24. To ensure particularly effective and efficient operation of the burner 44, especially over a long service life, the method provides that, when the burner 44 is deactivated, it is supplied with cleaning air from the intake tract 24 via the supply line 56. This cleaning air is conveyed by the compressor 31, specifically by the compressor wheel 32. The cleaning air can flow through at least a portion of the burner 44, and in particular into the combustion chamber 51, so that the cleaning air flows directly onto and / or around areas such as the burner walls, and / or along these areas of the burner 44.Since the cleaning air is supplied by the compressor 31, it has a suitably high pressure, also referred to as atmospheric pressure, which is, for example, at least 1.5 bar. This allows the cleaning air to remove deposits, also referred to as contaminants, that have accumulated on and adhere to the areas of the burner 44, thus effectively cleaning the burner 44. In the aforementioned deactivated state of the burner 44, combustion does not occur in the combustion chamber 51. This means that, in the deactivated state of the burner 44, combustion does not take place in the combustion chamber 51, and therefore, in the deactivated state, the burner 44 does not produce any exhaust gas. Consequently, in the deactivated state, the burner 44 also does not provide the flame 46. It is evident that an air path L, extending continuously and thus without interruption from the compressor 31, i.e., from the compressor wheel 32, to the burner 44, in particular to the combustion chamber 51, and encompassing, in particular, the entire supply line 56, through which the burner 44 is supplied with cleaning air originating from the intake tract 24 and conveyed by the compressor 31 when the burner 44 is deactivated, is free of an additional air pump provided for conveying the cleaning air. The supply line 56 is, for example, fluidically connected to the intake tract 24 at a first connection point V1. The cleaning air from the intake tract 24 can, for example, be diverted at connection point V1 via the supply line 56 and introduced into the supply line 56.The diverted cleaning air can flow through the supply line 56 and is directed to the burner 44 via the supply line 56. For example, the supply line 56 is fluidically connected to the burner 44 at a second connection point V2. A second supply line 64 is also provided, through which air from the intake tract 24 can flow. The second supply line 64 is fluidically connected to the intake tract 24 at a third connection point V3. For example, the supply line 64 is fluidically connected to the burner 44 at a fourth connection point V4. The connection points V2 and V4 are, for example, spaced apart from each other and separated from each other, in particular by at least or exactly one wall of the burner 44, which is designed as a solid. In the activated state of the burner 44, that is, while the burner 44 is activated and thus the mixture is being burned in the combustion chamber 51, the burner 44 is supplied with burner air from the intake tract 24 via the supply line 64.For this purpose, at connection point V3, at least a portion of the fresh air flowing through the intake tract 24 is diverted as burner air from the intake tract 24 via supply line 56 and introduced into the second supply line 64. The diverted burner air introduced into supply line 64 can be routed to the burner 44 via supply line 64, thus supplying the burner 44 with burner air. It is evident that supply line 64 is at least partially separated from supply line 56, particularly fluidically. Furthermore, connection points V1 and V3 are spaced apart from each other in the direction of flow of the fresh air flowing through the intake tract 24, such that connection point V3 is located downstream of connection point V1. Connection point V1 is located downstream of the compressor wheel 32, specifically downstream of the compressor 31. In the second supply line 64, an air pump 66, provided in addition to the compressor 31 and the internal combustion engine 12, is arranged, in particular an electrically operated air pump 66, by means of which, in the activated state of the burner 44, the burner air is conveyed through the second supply line 64 and conveyed to the burner 44. In particular, the air pump is electrically operated by supplying the air pump 66 with electrical energy and being operated by means of this electrical energy. In particular, a valve element is arranged in the supply line 64 by means of which the quantity of burner air supplied to the burner 44 can be adjusted. It is conceivable that the valve element 58 can be controlled, or is controlled, by the electronic control unit 52, in particular that it can be controlled or regulated. This allows, for example, the control unit to adjust, in particular control or regulate, the quantity of burner air supplied to the burner 44 by means of the valve element 58. Furthermore, alternatively or additionally, the control unit can, for example, control the air pump 66 and thus, for example, control or regulate it in order to adjust, in particular regulate or control, the quantity of burner air supplied to the burner 44. In the embodiment shown in Fig. 1, a further air line 60 is provided, which is, for example, at least partially separated from the supply line 56 and the supply line 56, particularly fluidically. The air line 60 is, for example, fluidically connected to the supply line 64 at a fifth connection point V5, particularly via the valve element 58, wherein, for example, the connection point V5 is arranged upstream of the burner 44 and downstream of the air pump 66 in the flow direction of the burner air flowing through the supply line 64. In particular, the air line 60 is fluidically connected to the supply line 64 via the valve element 58, such that, for example, the valve element 58 is arranged at the connection point V5.On the other hand, the air line 60 is fluidically connected at a sixth connection point V6 to an exhaust pipe 62 of the exhaust system 10 through which the engine exhaust gas flows, wherein, for example, the particulate filter 40 and / or the SCR catalyst 42 is arranged in the exhaust pipe 62. The connection point V6 is located upstream of the SCR catalyst 42 and preferably downstream of the particulate filter 40. Thus, for example, at connection point V5, at least a portion of the air supplied by the air pump 66 and flowing through the supply line 64 can be diverted from the supply line 64 and introduced into the air line 60. The air introduced into the air line 60 can be guided to connection point V6 via the air line 60 and introduced into the exhaust pipe 62 at connection point V6. For example, the amount of air flowing through the air line 60 can be adjusted by actuating the valve element 58. In the embodiment shown in Fig. 1, the compressor 31 is designed as an electric compressor, and the exhaust gas turbocharger 30 is also designed as an electric exhaust gas turbocharger, which is also referred to as an electrically assisted exhaust gas turbocharger. An electric motor 68 is provided, by means of which, in the deactivated state of the burner 44, the compressor wheel 32 is driven, thereby conveying the cleaning air through the supply line 56 and supplying the burner 44 with the cleaning air via the supply line 56. A valve element 70 is also provided, which is arranged in the intake tract 24 downstream of the compressor 31, in particular downstream of the compressor wheel 32, and downstream of connection point V1 and upstream of connection point V3. The intake tract 24 is fluidically blocked by means of the valve element 70 while the compressor 31 delivers the cleaning air through the supply line 56 and to the burner 44, i.e., while the burner 44 is supplied with the cleaning air and while the burner 44 is deactivated, i.e., in its deactivated state. This allows the air delivered by the compressor 31 to be used particularly effectively and efficiently as cleaning air, since the air delivered by the compressor 31 flows, in particular completely, through the supply line 56 and thus to the burner 44 and, in particular, through the burner 44. Reference symbol list 10 Exhaust system 12 Internal combustion engine 14 Tank 16 Low-pressure pump 18 High-pressure pump 20 Injector 22 Cylinder 24 Intake system 28 Charging unit 30 Exhaust turbocharger 31 Compressor 32 Compressor wheel 33 Turbine 34 Turbine wheel 36 Exhaust aftertreatment system 38 Oxidation catalyst 40 Particulate filter 42 SCR catalyst 44 Burner 45 Metering device 46 Flame 47 Mixing chamber 48 Fuel line 51 Combustion chamber 52 Electronic control unit 54 Valve element 56 First supply line 58 Valve element 60 Air line 62 Exhaust pipe 64 Second supply line 66 Air pump 68 Electric motor 70 Valve element L Air path S1 Position S2 Position V1 Connection point V2 Connection point V3 Connection point V4 Connection point V5 Connection point V6 Connection point

Claims

Method for operating a burner (44) arranged in an exhaust tract (10) of an internal combustion engine (12) of a motor vehicle, wherein: - the internal combustion engine (12) comprises: o an intake tract (24) through which air can flow, by means of which the air flowing through the intake tract (24) can be introduced into at least one combustion chamber of the internal combustion engine (12); and o a compressor (31) arranged in the intake tract (24) for conveying and compressing the air flowing through the intake tract (24); - the burner (44) is arranged in the exhaust tract (10), which has a combustion chamber (51) into which a mixture comprising air and fuel is to be burned; and - a supply line (56) is provided, via which the burner (44) can be supplied with at least a part of the air flowing through the intake tract (24); characterized in that in a deactivated state of the burner (44),In its deactivated state, combustion in the combustion chamber (51) ceases, the burner (44) is supplied via the supply line (56) with air originating from the intake tract (24), which is conveyed by means of the compressor (31), and the supply line (56) is fluidically connected to the intake tract (24) at a connection point (V1) arranged downstream of the compressor (31), wherein a valve element (70) is arranged in the intake tract (24) downstream of the connection point (V1), by means of which the intake tract (24) is fluidically blocked, while in the deactivated state of the burner (44) the burner (44) is supplied via the supply line (56) with the air originating from the intake tract (24), which is conveyed by means of the compressor (31), wherein in an unfired operation of the internal combustion engine (12) the burner (44) is supplied with air via the supply line (56),while the valve element (70) is closed and thus fluidically blocks the intake tract (24). Method according to claim 1, characterized in that an air path (L) extending continuously from the compressor (31) to the burner (44) and comprising the supply line (56), through which the burner (44) is supplied with air originating from the intake tract (24) and conveyed by means of the compressor (31) in the deactivated state of the burner (44), is free of an air pump provided in addition to the compressor (31) for conveying the air. Method according to claim 1 or 2, characterized by a second supply line (64) provided in addition to the supply line (56) and at least partially separated from the supply line (56), through which the burner (44) is supplied with air from the intake tract (24) in an activated state of the burner (44), in whose activated state the mixture is burned in the combustion chamber (51). Method according to claim 3, characterized in that an air pump is arranged in the second supply line (64) in addition to the compressor (31), by means of which, in the activated state of the burner, the air is conveyed through the second supply line and conveyed to the burner. Method according to one of the preceding claims, characterized in that the second supply line (64) is fluidically connected to the intake tract (24) at a second connection point (V3), wherein the first connection point (V1) is arranged upstream of the second connection point (V3). Method according to one of the preceding claims, characterized in that the compressor (31) is an electric compressor (31) which has a compressor wheel (32) for compressing and conveying the air and an electric motor (68) by means of which, in the deactivated state of the burner (44), the compressor wheel (32) is driven, whereby the burner (44) in the deactivated state is supplied with the air from the intake tract (24) via the supply line (56). Motor vehicle, with an internal combustion engine (12) by means of which the motor vehicle can be driven, wherein the internal combustion engine (12) is designed to carry out a method according to one of the preceding claims.

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