Internal combustion engine with compressor and engine casing ventilation

Abstract

Internal combustion engine with an internal combustion engine (10), a fresh gas stream, and an engine casing ventilation system (36), wherein the fresh gas stream is provided for supplying fresh gas flowing through the fresh gas stream in a defined flow direction (72) to the internal combustion engine (10), and wherein the engine casing ventilation system (36) has a vent line which is provided for venting a casing of the internal combustion engine (10) and opens into the fresh gas stream upstream of a compressor impeller (26) of a compressor (18), wherein the opening of the vent line is formed by an outlet opening (64) of an inlet pipe (58) which projects into a guide channel (40) of the fresh gas stream, characterized in that the center of the outlet opening (64) has a distance of at least 5 mm to a wall (56) of the guide channel (40) and the outflow direction (68) of the inlet pipe (58) corresponds at least partially to the direction of flow (72),wherein an extension of the longitudinal axis (62) of the inlet pipe (58) in the outflow direction (68) starting from the center of the outlet opening (64) intersects an inlet plane (44) of the compressor impeller (26) in a central section of the compressor impeller (26).

Description

[0001] The invention relates to an internal combustion engine with compressor and engine casing ventilation and a compressor for such an internal combustion engine.

[0002] It is known to turbocharge internal combustion engines, such as those used to power motor vehicles, to increase their specific power output and reduce their specific fuel consumption. Turbocharging internal combustion engines using one or more exhaust gas turbochargers is a common method. These turbochargers comprise a turbine that is driven by exhaust gas expelled from the combustion engine. The turbine, via a shaft, drives a compressor integrated into the combustion engine's intake air stream, which compresses the intake air. Alternatively, such a compressor can also be driven by another source, such as the combustion engine itself or an electric motor. Turbocharging allows, among other things, the following improvements:The amount of fresh gas introduced into the combustion chambers of the internal combustion engine, and thus the amount of fuel that can be converted in the combustion chamber during one working cycle, is increased.

[0003] The compressors of exhaust gas turbochargers are regularly designed as flow compressors, with almost exclusively centrifugal compressor impellers being used, which are axially fed and radially discharged (radial compressors).

[0004] Modern internal combustion engines employ a closed crankcase ventilation system to meet legally mandated emission limits. This system extracts exhaust gas generated during the combustion of a fuel-air mixture in the combustion chambers of the engine. This exhaust gas, known as blow-by gas, is primarily generated by annular gaps (the gaps between the outer surfaces of the pistons and the inner surfaces of the cylinder walls in reciprocating engines) that have entered the engine's crankcase. The blow-by gas is then recirculated into the engine's intake air system. To ensure the necessary pressure differential, in turbocharged engines, the blow-by gas can be recirculated into a section of the intake air system upstream of the compressor (relative to the flow direction of the intake air).

[0005] Through such an engine casing vent, liquids, and especially water and lubricating oil, can enter the fresh air stream in significant quantities, in addition to gases. These liquids can cause problems, particularly if they initially accumulate in one section and are then carried along in larger quantities, for example, into the compressor impeller, due to changing operating conditions. It can be especially problematic if such liquid accumulations freeze due to low ambient temperatures and are consequently carried along as solids.

[0006] US Patent 2004 / 0144373A1 describes an arrangement for crankcase ventilation in which blow-by gas is introduced into the fresh air stream of an internal combustion engine via an inlet pipe. This inlet pipe is positioned within a receiving opening of a section of the fresh air stream housing, forming a circumferential gap. The gap serves to thermally insulate the inlet pipe, and thus the blow-by gas passing through it, from the fresh air stream housing. This is intended to prevent the liquids contained in the blow-by gas within the inlet pipe from freezing at low ambient temperatures. Otherwise, such freezing could lead to a blockage of the inlet pipe and consequently to a lack of or insufficient functionality of the crankcase ventilation system.The arrangement of the inlet tube in the receiving opening is such that blow-by gas exiting from an outlet opening of the inlet tube flows at a short distance and parallel to the wall of the housing section of the fresh gas stream.

[0007] US Patent 4,558,681 A discloses a method of introducing blow-by gas into an intake manifold of a fresh gas stream of an internal combustion engine by means of a 90° angled pipe.

[0008] US Patent 2014 / 0366533A1 discloses an introduction of blow-by gas into a fresh gas stream of an internal combustion engine either by means of a pipe that opens in a radial orientation into a section of the fresh gas stream upstream of a compressor, or by means of a channel that is formed in the housing of the compressor and that opens into a flow space accommodating an impeller of the compressor.

[0009] US 2008 / 0314351A1 describes the introduction of blow-by gas into a fresh gas stream of an internal combustion engine upstream of a compressor of an exhaust gas turbocharger in the vicinity of and in a parallel orientation to a wall of the fresh gas stream.

[0010] US 2008 / 0314351A1 describes the introduction of blow-by gas into a fresh gas stream of an internal combustion engine with a radial orientation.

[0011] The invention was based on the objective of providing an advantageous engine casing ventilation system for an internal combustion engine and, in particular, preventing the formation of icing in a fresh gas stream of the internal combustion engine as a result of liquids introduced through the engine casing ventilation system.

[0012] This problem is solved by means of an internal combustion engine according to claim 1. A compressor for an internal combustion engine according to the invention is the subject of claim 8. Advantageous embodiments of the internal combustion engine and the compressor according to the invention are the subject of further claims and / or will become apparent from the following description of the invention.

[0013] The invention is based on the understanding that, while the introduction of blow-by gas, as known from US 2004 / 0144373 A1, can prevent icing within the inlet pipe, the exit of the blow-by gas flow from the inlet pipe in the immediate vicinity of, and parallel to, the wall of the corresponding housing section of the fresh gas line creates a risk of liquid accumulation on the housing wall due to adhering liquid droplets and / or condensation of liquid vapors. At low ambient temperatures, and consequently low wall temperatures, this can lead to icing. If larger frozen solids subsequently detach from the wall during operation of the internal combustion engine, this can cause damage, for example, to a downstream compressor.

[0014] Based on this finding, an internal combustion engine is provided, comprising at least one internal combustion engine (preferably a diesel or gasoline engine), a fresh gas train, and an engine casing ventilation system, wherein the fresh gas train is provided for supplying fresh gas to the internal combustion engine in a flow direction provided for the operation of the internal combustion engine, and wherein the engine casing ventilation system has a vent line, which is provided for venting a housing, in particular a crankcase, of the internal combustion engine and opens into the fresh gas train, wherein the opening of the vent line is formed by an opening of an inlet pipe that projects into a guide channel of the fresh gas train.In such an internal combustion engine, it is further provided that the (geometric) center of the outlet opening has a (shortest) distance of at least 5 mm, preferably at least 8 mm and particularly preferably at least 10 mm to a wall of the guide channel and that the outflow direction of the inlet pipe corresponds at least partially to the flow direction.

[0015] The "outflow direction" corresponds to the direction along an extension of the longitudinal axis of the inlet pipe, starting from the outlet opening, that leads from the inlet pipe into the guide channel. The "longitudinal axis" of the inlet pipe is understood to be the line that connects the geometric centers of all opening cross-sections of the inlet pipe. Therefore, if the outlet opening is located at the end of a curved section of the inlet pipe (or its longitudinal axis), the outflow direction runs along the tangent that originates from the center of the outlet opening, which forms a single point on the longitudinal axis.

[0016] Consequently, the design ensures that the inlet channel's outlet is positioned at a sufficient minimum distance from the guide channel wall. This helps prevent the formation of liquid accumulations originating from blow-by gas introduced into the fresh gas stream through the inlet pipe. The at least partial alignment of the outflow direction with the flow direction serves the same purpose, as it allows for the least turbulence-free mixing of the blow-by gas with the fresh gas flowing through the fresh gas stream.By combining these features, a relatively central guidance of the blow-by gas, which may still be incompletely mixed with the fresh gas, can be achieved within the guide channel, at least for a sufficiently large section of the fresh gas stream downstream of the inlet pipe's outlet, thereby preventing or minimizing the deposition of liquids contained in the blow-by gas on the wall.

[0017] An internal combustion engine according to the invention further comprises a compressor integrated into the fresh gas stream, wherein the vent line opens into the fresh gas stream upstream of a compressor impeller. The compressor can generate a negative pressure in the upstream section of the fresh gas stream, which can advantageously be used for drawing in blow-by gas from the housing, in particular the (cylinder) crankcase, of the internal combustion engine.In this context, introducing the blow-by gas as close as possible, or at least relatively close, to the compressor impeller can be advantageous because, on the one hand, the suction effect of the compressor tends to decrease with increasing distance, and on the other hand, because the compressor increases both the pressure and the temperature of the fresh gas mixed with the blow-by gas shortly after the introduction, which can counteract an accumulation of liquids on the walls of the fresh gas line downstream of the compressor.

[0018] The design provides that an extension of the longitudinal axis of the inlet pipe in the outflow direction, starting from the center of the outlet opening, intersects an inlet plane of the compressor impeller in a central section of the impeller (preferably encompassing a rotation axis of the impeller centrally), wherein this central section of the impeller comprises, for example, at most 50%, at most 25%, or at most 10% of the inlet area of ​​the impeller. The "inlet area" of the impeller is understood to be the area within an inlet plane of the impeller that is covered by the leading edges of the impeller blades of the impeller in total (i.e., over one complete revolution of the impeller).The "entry plane" of the compressor impeller is understood to be the plane closest to the compressor inlet, oriented perpendicular to the axis of rotation of the compressor impeller, which is defined by the impeller blades of the compressor impeller in that at least a point-like section of one, several or all of the entry edges of these impeller blades is / are arranged within this plane.

[0019] There is an interaction between the minimum distance according to the invention and the orientation of the outflow direction according to the invention, which is such that the at least partial agreement of the outflow direction with the flow direction can / should be greater or more pronounced the greater the distance of the center of the opening from the wall of the guide channel. The guidance of the blow-by gas within a central section of the guide channel, as desired according to the invention, can therefore also be advantageously achieved if the outflow direction is (approximately) parallel to the longitudinal axis of the guide channel in a section of the guide channel adjoining the opening downstream, provided that the distance of the center of the opening to the wall of the guide channel is sufficiently large (for example, 10% to 40% of the cross-sectional dimension of the guide channel).of the diameter (in the case of a circular guide channel in cross-section). If, on the other hand, the distance from the center of the outlet opening is relatively small, it can be advantageous if the outflow direction is obliquely oriented with respect to the longitudinal axis of the guide channel in the corresponding section, in order to ensure that the flow of blow-by gas exiting the inlet channel also has a component of motion towards the center of the guide channel. It can be provided that the outflow direction is oriented at an angle between 90° and 20° with respect to a radial plane of the guide channel that intersects the longitudinal axis of the inlet pipe within the outlet opening.In particular, it can also be provided that the outflow direction is oriented at an angle of less than 90° with respect to the radial plane of the guide channel intersecting the longitudinal axis of the inlet pipe within the outlet opening, and consequently obliquely with respect to the longitudinal axis in the corresponding section of the guide channel. The resulting radially directed component of the blow-by gas flow exiting the inlet channel, directed towards the center of the guide channel, allows a relatively central (initial) concentration of the blow-by gas within the guide channel to be achieved even if the inlet pipe projects only a relatively short distance into the guide channel. Such a relatively short projection of the inlet pipe into the guide channel advantageously minimizes the flow resistance generated by the inlet pipe for the flow of the fresh gas in the guide channel.For example, it may be provided that the center of the mouth opening has a (shortest) distance of no more than 20 mm to a wall of the guide channel.

[0020] An advantageous size for the muzzle opening of an internal combustion engine according to the invention can be at least 12 mm. 2 and / or at most 314 mm 2 This corresponds to a diameter of between approximately 4 mm and approximately 20 mm for a circular opening. Of course, other shapes of the opening are also possible.

[0021] It is further preferred that the inlet pipe is received in a receiving opening in the wall of the guide channel. This can result in particularly advantageous manufacturability of an internal combustion engine according to the invention. For this purpose, it can be provided that the inlet pipe is inserted into the receiving opening of the wall and secured therein against loosening. Such securing can be achieved in any manner, in particular by frictional locking (i.e., by means of a clamping fit), by positive locking (for example, by means of a threaded connection), and / or by material locking (for example, by means of an adhesive, soldered, and / or welded connection). Alternatively, however, it is also possible that the inlet pipe is integrally formed (in particular, of a single material) within the wall of the guide channel.

[0022] The invention further relates to a compressor, particularly for use in a (turbocharged) internal combustion engine according to the invention, comprising a one- or multi-part compressor housing that forms a flow chamber within which a compressor impeller is rotatably mounted, and an inlet channel extending from a compressor inlet in a predetermined flow direction to the flow chamber. Such a compressor is further characterized in that the compressor housing forms or accommodates an inlet channel for the crankcase ventilation of an internal combustion engine, the inlet pipe projecting into the inlet channel. It is provided that the center of an outlet opening of the inlet channel has a (shortest) distance of at least 2 mm to a wall of the inlet channel, and the outflow direction of the inlet pipe corresponds at least partially to the flow direction.Furthermore, it is provided that an extension of the longitudinal axis of the inlet pipe in the outflow direction starting from the center of the outlet opening intersects an inlet plane of the compressor impeller in a central section of the compressor impeller (preferably encompassing a rotation axis of the compressor impeller centrally), wherein this central section of the compressor impeller comprises, for example, at most 50%, at most 25% or at most 10% of the inlet area of ​​the compressor impeller.

[0023] Furthermore, for the design, arrangement and / or the type of integration of the inlet channel into the compressor housing, those measures can be provided which have already been described for the internal combustion engine according to the invention.

[0024] Furthermore, the invention also relates to an exhaust gas turbocharger with a compressor according to the invention and a turbine, which has a turbine impeller rotatably mounted in a turbine housing, wherein the turbine impeller is rotaryally connected to the compressor impeller. Alternatively or additionally to a drive of a compressor according to the invention by means of a turbine of an exhaust gas turbocharger, a drive by means of an output shaft of the internal combustion engine and / or by means of a separate drive motor, which may in particular be an electric motor, can also be provided.

[0025] According to a preferred embodiment of an internal combustion engine and / or a compressor according to the invention, it can be provided that the center of the opening of the inlet tube has a distance of at least 10 mm to the inlet plane of the compressor impeller.

[0026] The invention further relates to a motor vehicle, in particular a wheeled motor vehicle (preferably a passenger car or truck), with an internal combustion engine according to the invention. The internal combustion engine can be used, in particular, to provide (direct or indirect) drive power to the motor vehicle. Use in other motor vehicles, for example, rail vehicles or ships, is also possible.

[0027] The indefinite articles (“a”, “an”, “one”, and “ones”), particularly in the patent claims and in the description generally explaining the patent claims, are to be understood as such and not as numerals. Accordingly, components specified by these articles are to be understood as existing at least once and potentially existing multiple times.

[0028] The present invention will be explained in more detail below with reference to exemplary embodiments illustrated in the drawings. The drawings show: Fig. 1: A schematic representation of an internal combustion engine according to the invention, charged by means of a compressor; and Fig. 2: a longitudinal section through a section of a fresh gas stream of the internal combustion engine encompassing the compressor.

[0029] The Fig. Figure 1 shows a schematic representation of an internal combustion engine according to the invention, comprising an internal combustion engine 10 with a plurality of cylinders 12. The cylinders 12, together with pistons guided up and down within them and a cylinder head (not shown), define combustion chambers in which fresh gas (air) is combusted together with fuel. The fuel is injected directly into the combustion chambers by means of injectors 30, controlled by a control device 32 (engine control unit). The combustion of the fuel-air mixture results in cyclical upward and downward movements of the pistons, which are transmitted in a known manner via connecting rods (not shown) to a crankshaft (also not shown), thereby causing the crankshaft to rotate.

[0030] The fresh gas is supplied to the combustion engine 10 via a fresh gas line and is drawn in from the environment through an intake opening 14, cleaned in an air filter 16, and then fed into a compressor 18, which is part of an exhaust gas turbocharger. The fresh gas is compressed by the compressor 18, then cooled in a charge air cooler 20 and fed to the combustion chambers. The compressor 18 is driven by a turbine 22 of the exhaust gas turbocharger, which is integrated into an exhaust gas line of the combustion engine. Exhaust gas, which is produced during the combustion of the fuel-fresh gas mixture in the combustion chambers of the combustion engine 10, is discharged from the combustion engine 10 via the exhaust gas line and flows through the turbine 22. This results, in a known manner, in the rotating drive of a turbine impeller (not shown), which is connected to a compressor impeller 26 (in the Fig. (1 not shown) of the compressor 18 is connected. The rotating drive of the turbine impeller is thus transferred to the compressor impeller 26.

[0031] In order to achieve the most optimal use of the exhaust gas enthalpy for generating compression power by means of the exhaust gas turbocharger during operation of the internal combustion engine 10 with different loads and different speeds, the turbine 22 of the exhaust gas turbocharger can optionally (especially in a configuration of the internal combustion engine 10 as a diesel engine) have a device for variable turbine flow (VTG) 34, which can be controlled by the control device 32. This device can comprise, in a known manner, a plurality of guide vanes (not shown) arranged in an inlet of the turbine 22, which are individually rotatable, and which are collectively adjustable by means of an adjustment device (not shown).Depending on the rotational positions of the guide vanes, these narrow the free flow cross-section in the inlet of the turbine 22 to a greater or lesser degree and also influence the section of the primary flow to the turbine runner and the orientation of this flow.

[0032] Downstream of the compressor 18, a control flap 28, which can also be controlled by means of the control device 32, is integrated into the charge air path, i.e., into the section of the fresh gas line located between the compressor 18 and the combustion engine 10.

[0033] The internal combustion engine further comprises an engine crankcase ventilation system 36, by means of which blow-by gas can be extracted from one or more cavities, for example from a crankcase formed by a cylinder crankcase of the internal combustion engine 10, and transferred upstream of the compressor impeller 26 into the fresh gas stream. A separator device (not shown) can be integrated into the engine crankcase ventilation system 36 to largely retain liquids and solids contained in the blow-by gas.

[0034] The Fig. Figure 2 shows a longitudinal section through a section of the fresh gas stream of an internal combustion engine comprising a compressor 18 according to the Fig. 1. In addition to the compressor 18, a section of a pipeline 38 is also shown, which is connected to the compressor 18 on the inlet side. The pipeline 38 forms a guide channel 40, which, as part of the fresh gas line of the internal combustion engine, serves to supply fresh gas to the compressor 18.

[0035] The compressor 18, designed as a radial compressor, has a multi-part compressor housing 42 (for example, made of an aluminum or other light metal alloy). The compressor housing 42 forms a flow chamber within which the compressor impeller 26 is rotatably mounted. On the inlet side, the flow chamber is bounded by an inlet plane 44 of the compressor impeller 26, in which the leading edges of the impeller blades 46 of the compressor impeller 26 run or are arranged. Fresh gas can be supplied from a compressor inlet 50 to the flow chamber and thus to the compressor impeller 26 via an inlet channel 48 formed by the compressor housing 42. On the outlet side, the flow chamber is bounded by an outlet plane that surrounds the leading edges of the impeller blades 46 of the compressor impeller 26.There, a diffuser chamber 52, also encircling the exit edges of the impeller blades 46, adjoins a compressor volute 54. A compressor outlet (not visible) extends from the compressor volute 54.

[0036] The transition from the guide channel 40, which is formed by the pipe 38 connected to the compressor 18 on the inlet side, to the inlet channel 48 formed by the compressor housing 42 is essentially stepless, because the guide channel 40 and the inlet channel 48, which each have a circular cross-section, have essentially the same diameters at the transition to each other.

[0037] At a relatively short distance upstream of the compressor inlet 50, a receiving opening is provided in the wall 56 of the pipe 38, in which an inlet pipe 58 is sealed and immovably held. The inlet pipe 58 is part of an engine crankcase ventilation system 36 of an internal combustion engine, for example, according to the Fig. 1. The positioning of the receiving opening, and thus of the inlet pipe 58, can be provided in a section of the pipeline 38 that is located as high as possible in the installation position intended for the operation of the internal combustion engine, with respect to the circumferential direction. The inlet pipe 58 can be made of (at least) one metal, for example, (an) aluminum (alloy), copper, or steel, while the wall 56 of the pipeline can also be made of (at least) one metal or, preferably, of plastic.

[0038] The receiving opening (longitudinal axis 62) has a radial orientation with respect to the longitudinal axis 60 of the pipeline 38 or the guide channel 40. This also results in a corresponding radial orientation (of the longitudinal axis 62) of the inlet pipe 58 in the section received in the receiving opening. The section of the inlet pipe 58 that projects into the guide channel 40 formed by the pipeline 38, however, is formed with a semicircular curve, the curvature being oriented such that an outlet opening 64, which is bounded by the end of the inlet pipe 64 located within the guide channel 40, points towards the compressor inlet 50.The curved section of the inlet pipe 58, located within the guide channel 40, is dimensioned such that the outlet opening 64 lies in a plane that is inclined at an angle to 90° with respect to the axis of rotation 66 of the compressor impeller 26. This results in an outflow direction 68 of the inlet pipe 58 that is inclined with respect to a radial plane 70 intersecting the longitudinal axis 62 of the inlet pipe 58 at the outlet opening 64 and simultaneously partially (i.e., with a directional component) corresponds to the flow direction 72 and thus points towards the compressor 18. The flow direction 72 is the direction in which the fresh gas is intended to flow through the fresh gas stream and thus also through the compressor 18.

[0039] For the in the Fig. The following dimensions and design details can be provided for in the two illustrated design examples: - Distance between the center of the opening 64 of the inlet tube 58 and the wall 56 of the guide channel 40 (A): 10 mm ± 3 mm; - Diameter of the circular muzzle opening 64 (B): 10 mm ± 2 mm; - Distance between the center of the outlet opening 64 and the compressor inlet 50 (C): 15 mm ± 3 mm; - Distance between the center of the outlet opening 64 and the inlet plane of the compressor impeller (D): 57 mm ± 3 mm; - Diameter of the compressor inlet 50 and the guide channel 48 in the area between the receiving opening for the inlet pipe 58 and the end (E) connected to the compressor inlet 50: 54 mm ± 2 mm; and - Angle enclosed by the outflow direction 68 with the radial plane 70 of the guide channel 40 intersecting the longitudinal axis 62 of the inlet tube 58 in the outlet opening 64 (α): 65° +10° / -15°.

[0040] Because the inlet pipe 58 extends relatively far into the guide channel 40 of the pipeline 38 and also has an obliquely oriented (at an angle of less than 90°) outflow direction with respect to the radial plane 70, it can be ensured that blow-by gas, which escapes via an engine crankcase ventilation 36 of an internal combustion engine according to the Fig.1 and is thus introduced into the guide channel 40 via the inlet pipe 58, which forms part of such an engine housing ventilation 38, until it reaches the compressor impeller 26 in central sections of the guide channel 40 and the inlet channel 48. This prevents liquids contained in the blow-by gas (especially water and lubricating oil) from accumulating in relevant quantities on the wall of the compressor housing 42, particularly the wall bordering the inlet channel 48. Consequently, this also largely prevents accumulations of liquids from freezing at very low ambient temperatures due to contact with the correspondingly cold wall of the compressor housing 42, which would pose a risk of damage, especially to the compressor 18, because such ice deposits could detach from the wall of the inlet channel and enter the compressor impeller. Reference symbol list 10 Internal combustion engine 12 cylinders 14 Intake nozzle 16 air filters 18 compressors 20 intercoolers 22 Turbine 24 wave 26 Compressor impeller 28 Control valve 30 injectors 32 Control device 34 Device for variable turbine flow 36 Engine housing ventilation 38 Pipeline 40 guide channel 42 compressor housings 44 Inlet level of the compressor impeller 46 wheel blades 48 Inlet channel 50 compressor inlet 52 Diffuser space 54 compressor volume 56 Wall of the guide channel 58 Inlet pipe 60 Longitudinal axis of the guide channel 62 Longitudinal axis of the inlet pipe 64 Discharge opening of the inlet pipe 66 Rotation axis of the compressor impeller 68 Outflow direction of the inlet pipe 70 Radial plane that intersects the longitudinal axis of the inlet tube within the muzzle opening 72 Flow direction

Claims

[1] Internal combustion engine with an internal combustion engine (10), a fresh gas stream and an engine casing ventilation (36), wherein the fresh gas stream is provided for supplying fresh gas flowing through the fresh gas stream in a provided flow direction (72) to the internal combustion engine (10) and wherein the engine casing ventilation (36) has a vent line which is provided for venting a casing of the internal combustion engine (10) and opens into the fresh gas stream upstream of a compressor impeller (26) of a compressor (18), wherein the opening of the vent line is formed by an opening (64) of an inlet pipe (58) which projects into a guide channel (40) of the fresh gas stream, characterized by, that the center of the outlet opening (64) has a distance of at least 5 mm to a wall (56) of the guide channel (40) and the outflow direction (68) of the inlet pipe (58) corresponds at least partially to the flow direction (72), wherein an extension of the longitudinal axis (62) of the inlet pipe (58) in the outflow direction (68) starting from the center of the outlet opening (64) intersects an inlet plane (44) of the compressor impeller (26) in a central section of the compressor impeller (26). [2] Internal combustion engine according to claim 1, characterized by , that the outflow direction (68) is aligned at an angle (α) between 90° and 20° with respect to a radial plane (70) of the guide channel (40) intersecting the longitudinal axis (62) of the inlet tube (58) within the outlet opening (64). [3] Internal combustion engine according to claim 1 or 2, characterized by, that the longitudinal axis (62) of the inlet tube (58) in the outlet opening (64) is aligned at an angle (α) less than 90° with respect to a radial plane (70) of the guide channel (40) intersecting the longitudinal axis (62) of the inlet tube (58) in the outlet opening (64). [4] Internal combustion engine according to any one of the preceding claims, characterized by , that the center of the opening (64) has a distance (A) of no more than 20 mm to a wall (56) of the guide channel (40). [5] Internal combustion engine according to any one of the preceding claims, characterized by , that the muzzle opening (64) has a size of at least 12 mm 2 and / or of no more than 314 mm 2 exhibits. [6] Internal combustion engine according to any one of the preceding claims, characterized by , that the inlet tube (58) is received in a receiving opening of a / the wall (56) of the guide channel (40). [7] Internal combustion engine according to any one of the preceding claims, characterized by , that the center of the outlet opening (64) has a distance of at least 10 mm to the inlet plane (44) of the compressor impeller (26). [8] Compressor (18) with a compressor housing (42) forming a flow chamber within which a compressor impeller (26) is rotatably mounted and an inlet channel (48) extending from a compressor inlet (50) in a flow direction (72) to the flow chamber, characterized by, that the compressor housing (42) forms or accommodates an inlet pipe (58) for an engine housing ventilation (36) of an internal combustion engine (10), wherein the center of an outlet opening (64) of the inlet pipe (58) has a distance of at least 2 mm to a wall of the inlet channel (48) and the inlet pipe (58) projects into the inlet channel (48) and the outflow direction (68) of the inlet pipe (58) corresponds at least partially to the flow direction (72), wherein an extension of the longitudinal axis (62) of the inlet pipe (58) in the outflow direction (68) starting from the center of the outlet opening (64) intersects an inlet plane (44) of the compressor impeller (26) in a central section of the compressor impeller (26).

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