Compressor for an intake tract of an internal combustion engine, exhaust gas turbocharger for an internal combustion engine and motor vehicle

Abstract

The invention relates to a compressor (10) for an intake tract of an internal combustion engine, comprising a compressor housing (12) through which air can flow, in which a compressor wheel (14) that can be supplied with air is arranged for compressing the air, and comprising a plurality of adjusting elements (16a-c) that can be moved back and forth in the radial direction (19) of the compressor wheel (14) relative to the compressor housing (12), whereby a flow cross-section (Q) arranged upstream of the compressor wheel (14) and through which air can flow can be varied, wherein the respective adjusting element (16a-c) has at least one respective through-opening (24) via which a respective first region (B1) arranged on a respective inner side (S1) of the respective adjusting element (16a-c) facing inwards in the radial direction (19) of the compressor wheel (14) is fluidically connected to a respective first region (B1) arranged on a respective,in the radial direction (19) of the compressor wheel (14) outwardly facing and away from the respective inner side (S1) of the respective adjusting element (16a-c) is connected to the second region (B2).

Description

The invention relates to a compressor for an intake tract of an internal combustion engine according to the preamble of patent claim 1. The invention further relates to a motor vehicle.EP 3 647 601 B1 discloses a displacement mechanism for an inlet flow section of a compressor wheel of a turbocharger for defining a variable inlet diameter for an axial air flow to the compressor wheel.It is an object of the present invention to provide a compressor for an intake tract of an internal combustion engine, an exhaust gas turbocharger and a motor vehicle, so that particularly advantageous operation of the compressor can be realized.This object is achieved by a compressor having the features of patent claim 1, by an exhaust gas turbocharger having the features of patent claim 9 and by a motor vehicle having the features of patent claim 10. Advantageous embodiments with expedient developments of the invention are specified in the other claims.A first aspect of the invention relates to a compressor for an intake tract, also referred to as an intake tract, of an internal combustion engine, also referred to as an internal combustion engine or internal combustion engine, in particular of a motor vehicle. The compressor has a compressor housing through which air can flow. Furthermore, the compressor has a compressor wheel which is arranged in the compressor housing and with which air flowing through the compressor housing can be supplied, in particular via an inlet region of the compressor housing, which is also referred to as a feed region. The air can be compressed by means of the compressor wheel. In particular, the compressor wheel is rotatable about an axis of rotation relative to the compressor housing, wherein the air can be compressed by rotating the compressor wheel by means of the compressor wheel.This means that in the completely manufactured state of the internal combustion engine, the internal combustion engine has the inlet section and the compressor arranged in the inlet section. The intake tract is through which the mentioned air, which is also referred to as fresh air, can flow. By means of the intake tract, the air flowing through the intake tract can be guided to at least one combustion chamber of the internal combustion engine and in particular introduced into the combustion chamber. In particular during a fired operation of the internal combustion engine, combustion processes take place in the combustion chamber. During the respective combustion process, a respective fuel-air mixture is ignited and burned, wherein the respective fuel-air mixture comprises an in particular liquid fuel and the air, which is conducted to and into the combustion chamber by means of the intake tract. In the flow direction of the air flowing through the inlet tract, the compressor is arranged upstream of the combustion chamber in the inlet tract, such that the air which is introduced into the combustion chamber is the air compressed by means of the compressor.The compressor also has a plurality of adjustment elements, which are designed, for example, as guide blades or blades or are also referred to as guide blades or blades. The adjustment elements, i.e. at least respective parts of the adjustment elements, can be moved back and forth relative to the compressor housing in the radial direction of the compressor wheel, the axial direction of which coincides with the axis of rotation. The axial direction of the compressor wheel runs perpendicular to the radial direction of the compressor wheel. For example, the respective adjusting element, also referred to simply as an adjusting element, can be pivoted back and forth about a respective pivot axis relative to the compressor housing. In this case, the respective pivot axis runs, for example, obliquely or but preferably parallel to the axis of rotation, and therefore to the axial direction of the compressor wheel, so that, for example, by pivoting about the respective pivot axis and relative to the compressor housing, that is to say, in particular, pivoting the respective adjusting element back and forth, at least one respective region spaced apart from the respective pivot axis, in particular a respective, in particular free, end of the respective adjusting element opposite the respective pivot axis, can be pivoted back and forth relative to the compressor housing in the radial direction of the compressor wheel, that is to say can be pivoted inward and outward in the radial direction of the compressor wheel and thus moved. By moving the adjusting elements back and forth in the radial direction of the compressor wheel and relative to the compressor housing, a flow cross section, which is arranged upstream of the compressor wheel in the flow direction of the air flowing through the compressor housing and through which the air can flow, and via which the compressor wheel can be supplied with the air, that is, via which the air can be supplied to the compressor wheel, can be varied, that is, adjusted.The adjustment elements are formed, for example, separately from one another and separately from the compressor housing. For example, the adjustment elements are coupled by means of a coupling device, so that, for example, the adjustment elements can be moved back and forth together, i.e., simultaneously relative to the compressor housing, in the radial direction of the compressor wheel, in particular pivoted back and forth.In order to be able to ensure that the adjusting elements can be moved back and forth relative to the compressor housing, so that particularly advantageous operation of the compressor can be ensured, it is provided according to the invention that the respective adjusting element has at least or exactly one respective through opening, via which a respective first region arranged on a respective inner side of the respective adjusting element facing inward in the radial direction of the compressor wheel is fluidically connected to a respective second region arranged on a respective outer side of the respective adjusting element facing outward in the radial direction of the compressor wheel and facing away from the respective inner side. A gas such as the mentioned air can flow through the respective through-opening, so that a pressure equalization between the mentioned regions is made possible via the respective through-opening. As a result, excessively different pressures in the regions can be avoided. In other words, an excessive pressure difference between the regions and thus between the inner side and the outer side can be avoided, so that at least almost at any operating point of the compressor it can be ensured that the adjusting elements are moved relative to the compressor housing and thus the flow cross section can be varied.The respective inner side is also referred to as a respective first side or respective front side, and the respective outer side is also referred to as a respective second side or respective rear side. The invention is based on the finding that, if no corresponding countermeasure is taken, such a pressure difference can occur between the respective sides of the respective adjusting element that, for example, a higher pressure can occur in the respective second region and thus on the respective rear side than in the respective first region and thus on the respective front side. This can lead, for example, to the adjustment elements no longer being moved (any longer) outwards relative to the compressor housing in the radial direction of the compressor wheel and thus no longer being able to be retracted or retracted, for example, so that the adjustment elements can be clamped. This can now be avoided in a particularly simple and cost-effective manner by the invention. The through openings are thus channels which provide for an advantageous pressure equalization between the respective first region and the respective second region. By means of this advantageous pressure equalization, it is also possible, for example, to keep a force provided for or to be applied for moving the respective setting element and / or a torque provided for and / or to be applied for moving the respective setting element advantageously low, such that the setting elements can be moved in a particularly smooth manner. As a result, for example, an actuator which is designed or provided for moving the guide elements can be advantageously kept low with regard to its costs, its weight and its installation space requirement and its performance.In order to be able to realize a particularly advantageous pressure equalization between the respective regions, that is to say between the respective sides, and thus to be able to actuate, that is to say move, the setting elements in a particularly advantageous manner, such that particularly advantageous operation of the compressor can be achieved, it is provided in one embodiment of the invention that the respective through-openings are bounded, in particular directly, in a completely encircling manner along their respective circumferential direction and therefore over 360 degrees by the respective setting element. The respective circumferential direction of the respective through-opening runs around a respective through-direction of the respective through-opening, which is continuous along its respective through-direction and can thus be flown through by the air or the aforementioned gas, for example.A further embodiment is characterized in that the respective through-opening is elongated. This makes it possible to ensure a particularly advantageous pressure equalization between the sides or regions.In order to realize a particularly advantageous pressure equalization between the respective sides and thus to be able to bring about a particularly advantageous, in particular smooth, actuation, that is to say movement of the adjustment elements, it is provided in a further embodiment of the invention that the respective, elongate passage opening has a respective direction of longitudinal extent which runs in the circumferential direction of the compressor wheel running around the axial direction of the compressor wheel and thus around the axis of rotation.In a further, particularly advantageous embodiment of the invention, it is provided that the respective through-opening has a respective rectangular cross section through which the gas or the air can flow. Experiments and simulations have surprisingly shown that a particularly advantageous pressure equalization between the regions or sides can be realized by such a rectangular cross section of the respective passage opening. At the same time, excessive losses can be avoided, so that particularly efficient and thus advantageous operation of the compressor can be ensured.In order to be able to realize a particularly advantageous operation of the compressor, it is provided in a further embodiment of the invention that the respective adjusting element is accommodated in a recess of the compressor housing at least partially, in particular at least predominantly and thus at least more than half or even completely, in at least one position of the respective adjusting element. This makes it possible, for example, to avoid undesired and excessive flow losses when the respective adjusting element is in the at least one position, as a result of which particularly efficient operation of the compressor can be realized.In order to be able to realize particularly efficient operation of the compressor in a particularly simple manner, it is provided in a further embodiment of the invention that the recess is an annular recess common to the adjustment elements and thus running completely and preferably without interruptions in the circumferential direction of the compressor wheel, in which recess the respective adjustment element is at least partially accommodated in the respective at least one position.A further embodiment is distinguished in that the respective adjusting element is arranged completely in the recess in the respective at least one position, so that when the respective adjusting element is in the respective at least one position, the adjusting element does not project inwardly beyond the compressor housing or projects out of the compressor housing or the recess in the radial direction of the compressor wheel. This makes it possible to avoid excessive flow losses, as a result of which particularly efficient operation can be achieved.A second aspect of the invention relates to an exhaust gas turbocharger for an internal combustion engine, wherein the exhaust gas turbocharger has a compressor according to the first aspect of the invention. Advantages and advantageous configurations of the first aspect of the invention are to be regarded as advantages and advantageous configurations of the second aspect of the invention and vice versa.The exhaust gas turbocharger preferably has a turbine which can be driven by exhaust gas from the internal combustion engine and by means of which the compressor, that is to say the compressor wheel, can be driven, in particular via a shaft of the exhaust gas turbocharger. The exhaust gas results from the respective combustion process.A third aspect of the invention relates to a motor vehicle which is also referred to simply as a vehicle and is preferably designed as a motor vehicle, in particular as a passenger car, and which has an internal combustion engine and can be driven by means of the internal combustion engine. The internal combustion engine has at least or exactly one exhaust gas turbocharger according to the second aspect of the invention. Advantages and advantageous configurations of the first aspect and of the second aspect of the invention are to be regarded as advantages and advantageous configurations of the third aspect of the invention and vice versa.Further advantages, features and details of the invention are evident from the following description of preferred exemplary embodiments and with reference to the drawing. The features and combinations of features mentioned above in the description and the features and combinations of features mentioned below in the description of the figures and / or shown alone in the figures can be used not only in the respectively specified combination but also in other combinations or alone without departing from the scope of the invention.The drawing shows in: FIG. 1 shows a schematic front view of a detail of a compressor for an intake tract of an internal combustion engine; FIG. 2 shows a detail of a further schematic front view of the compressor; FIG. 3 shows a schematic longitudinal sectional view of a portion of the compressor; FIG. 4 shows a detail of a further schematic longitudinal sectional view of the compressor; FIG. 5 is a schematic front view of a first embodiment of an adjustment element of the compressor; FIG. 6 is a schematic rear view of the adjusting member according to the first embodiment; FIG. 7 is a schematic front view of a second embodiment of the adjustment element; FIG. 8 is a schematic rear view of the second embodiment of the adjusting element; FIG. 9 is a schematic rear view of a third embodiment of the adjustment element; FIG. 10 is a schematic front view of a fourth embodiment of the adjusting element; FIG. 11 is a schematic rear view of the fourth embodiment of the adjusting element; FIG. 12 is a schematic front view of a fifth embodiment of the adjusting element; FIG. 13 is another schematic front view of the fifth embodiment of the adjusting element; and FIG. 14 is a schematic rear view of the fifth embodiment of the adjusting member.In the figures, identical or functionally identical elements are provided with identical reference symbols.FIGS. 1 and 2 each show a detail of a schematic front view of a compressor 10 for an intake tract, also referred to as an intake tract, of an internal combustion engine, also referred to as an internal combustion engine, engine or internal combustion engine. This means that the internal combustion engine in its completely manufactured state has the intake tract and the compressor 10, which is arranged in the intake tract. Air can flow through the intake tract, which is also referred to as fresh air. By means of the intake tract, the air flowing through the intake tract can be guided to at least one combustion chamber of the internal combustion engine and introduced into the combustion chamber. During a fired operation of the internal combustion engine, combustion processes take place in the combustion chamber. In the respective combustion process, a respective fuel-air mixture is burned, resulting in exhaust gas of the internal combustion engine. The respective fuel-air mixture comprises an in particular liquid fuel and the air which is introduced into the combustion chamber by means of the inlet tract. The compressor 10 is, for example, a component of an exhaust gas turbocharger of the internal combustion engine.The compressor 10 has a compressor housing 12 through which the air can flow and a compressor wheel 14, which is arranged in the compressor housing 12 and is rotatable about an axis of rotation D relative to the compressor housing 12. The compressor wheel 14, the axial direction of which coincides with the axis of rotation D, can be supplied with the air flowing through the compressor housing 12, in particular via an inlet region of the compressor housing 12, which inlet region is also referred to as feed region, so that during operation of the internal combustion engine, such as during the fired operation of the internal combustion engine, the air flowing through the compressor housing 12 flows through the inlet region and is fed via the inlet region to the compressor wheel 14, the radial direction of which runs perpendicular to the axial direction of the compressor wheel 14. Thus, the inlet region is arranged upstream of the compressor wheel 14 in the flow direction of the air flowing through the compressor housing 12.The internal combustion engine has, for example, an exhaust tract through which the exhaust gas can flow from the combustion chamber, which exhaust tract is also referred to as an exhaust system. In this case, the exhaust gas turbocharger has, for example, a turbine which is arranged in the exhaust tract. The turbine has a turbine wheel which can be driven by the exhaust gas and is thus rotatable about the axis of rotation D relative to the compressor housing 12. The turbine wheel can drive the compressor wheel 14 via a shaft and thereby rotate about the axis of rotation D relative to the compressor housing 12, whereby the air is compressed by means of the compressor wheel 14. The compressed air is introduced into the combustion chamber by means of the inlet tract.The compressor 10 has a plurality of, in the present case at least or exactly three, actuating elements 16 a- c, which are also referred to simply as actuating elements. For example, the adjusting elements are arranged in the inlet region. The adjusting elements are formed separately from one another and separately from the compressor housing 12. The respective adjustment element 16 a- cis pivotable about a respective pivot axis S relative to the compressor housing 12. In the exemplary embodiment shown in FIGS. 1 to 4, the pivot axes S run parallel to the axis of rotation D and are spaced apart from the axis of rotation D in the radial direction of the compressor wheel 14, the radial direction of which runs perpendicular to the axis of rotation D and is illustrated by a double arrow 19. In addition, the pivot axis S are spaced apart from one another in pairs. The pivot axes S are arranged on a circle, the center of which lies on the axis of rotation D.The compressor 10 has a coupling device 18 which is in the present case designed as a ring and by means of which the setting elements 16 a- cwhich are designed separately from one another are coupled to one another. Furthermore, the compressor 10 has an actuator 20 by means of which the coupling device 18 is rotatable about the axis of rotation D relative to the compressor housing 12, namely in a first direction of rotation D 1 running about the axis of rotation D and in a second direction of rotation D 2 running about the axis of rotation D and opposite the first direction of rotation D 1. By rotating the coupling device 18 back and forth about the axis of rotation D and relative to the compressor housing 12, the adjustment elements 16 a- cmay be pivoted about their pivot axes S relative to the compressor housing 12 and thereby respectively at least partially moved back and forth in the radial direction of the compressor wheel 14 relative to the compressor housing 12. In particular, by means of the respective adjustment element 16 a- cthat is pivoted back and forth about the respective pivot axis S and relative to the compressor housing 12, at least one respective region B of the respective adjustment element 16 a- c, which region is spaced apart from the respective pivot axis S, can be moved back and forth in the radial direction of the compressor wheel 14 relative to the compressor housing 12. By this back and forth movement of the adjusting elements 16 a- cin the radial direction of the compressor wheel 14 and relative to the compressor housing 12, a flow cross section, in particular of the inlet region, which is arranged upstream of the compressor wheel 14 and through which the air can flow in the flow direction of the air flowing through the compressor housing 12 can be varied, that is to say set to different values.It can be seen from FIGS. 1 and 2 that the respective adjusting element 16 a- cis movable, in the present case pivotable, relative to the compressor housing 12 at least between a respective first position shown in FIG. 2 and a respective second position shown in FIG. 1. The respective adjustment element 16 a- cmay thus be moved back and forth between the respective positions, namely relative to the compressor housing 12. At least in the respective second position, for example, the flow cross section defined and thus set by the adjustment elements 16 a- cis the smallest flow cross section, which is arranged upstream of the compressor wheel 14 in the compressor housing 12 and through which the air can flow or is supplied to the compressor wheel 14. By moving the adjusting elements 16 a- dto and fro relative to the compressor housing 12, an inflow to the compressor wheel can thus be adjusted as required, whereby for example the compressor 10 can be advantageously operated. The flow cross section, thus defined, set in the respective second position of the respective setting element 16 a- cby means of the setting elements 16 a- cis denoted by Q in FIG. 1.By means of the actuator 20, for example, an actuating element 22 can be moved translationally back and forth along a movement direction, namely in a first direction R 1 and in a second direction R 2. The actuating element 22 is coupled to the coupling device 18, such that by translatory movement of the actuating element 22 in the first direction R 1, the coupling device 18 is rotated in the first rotational direction D 1 about the rotational axis D relative to the compressor housing 12. As a result, the adjustment elements 16 a- care moved inward in the radial direction of the compressor wheel 14 relative to the compressor housing 12 and thus, for example, from the first position into the second position. By translatory movement of the actuating element 22 in the second direction R 2, the coupling device 18 is rotated, for example, about the axis of rotation D relative to the compressor housing 12 in the second direction of rotation D. As a result, for example, the adjusting elements 16 a- care moved, in particular pivoted, outwards in the radial direction of the compressor wheel 14 relative to the compressor housing 12 and as a result are moved, in particular pivoted, for example from the second position into the first position. By moving the adjustment elements 16 a- cfrom the first position into the second position, the flow cross section Q is reduced, such that by moving the adjustment elements 16 a- cfrom the second position into the first position, the flow cross section Q is increased. Consequently, the adjustment elements 16 a- care opened by rotating the coupling device 18 in the second rotational direction D 2 and closed by rotating the coupling device 18 in the first rotational direction D 1. FIGS. 3 and 4 each show, in a schematic longitudinal sectional view, the compressor 10. The inlet region designated EB can be seen from FIGS. 3 and 4. Furthermore, it can be seen from FIGS. 1 to 4 that the respective adjusting element 16 a- chas a respective first side S 1 and a respective second side S 2. The respective first side S 1 is a respective inner side, which is also referred to as a respective front side. The respective second side S 2 is a respective outer side, which is also referred to as the respective rear side. It can be seen that the respective side S 1 points inward in the radial direction of the compressor wheel 14 and points away from the respective second side S 2. Consequently, the respective second side S 2 points outwards in the radial direction of the compressor wheel 14 and thus away from the respective first side S 1. A respective region arranged on the respective side S 1 is denoted by B 1 and a respective region arranged on the respective second side S 2 is denoted by B 2. For example, the respective second region B 2 is arranged between the respective second side S 2 and the compressor housing 12 at least in the respective second position, shown in FIG. 1, of the respective adjustment element 16 a- cin the radial direction of the compressor wheel 14.In order to be able to ensure an advantageous actuation of the adjustment elements 16 a- c, in particular to the effect that, for example, the adjustment elements 16 a- cmay be moved relative to the compressor housing 12 in a particularly smooth manner, that is to say with only a low adjusting force, and that undesired clamping of the adjustment elements 16 a- cmay be avoided, the respective adjustment element 16 a- ccomprises at least one through opening 24, as may be seen from FIGS. 5 to 9. FIG. 5 shows a first embodiment of the respective adjustment element 16 a- c. In the first embodiment, the respective adjustment element 16 a- ccomprises a plurality of through-openings 24, via which the respective regions B 1 and B 2 are fluidically connected to one another. As a result, an advantageous pressure equalization between the respective regions B 1 and B 2 can be realized via the through-openings 24, with the result that an excessive pressure difference between the respective regions B 1 and B 2 and therefore between the respective sides S 1 and S 2 can be avoided. As a result, the respective adjustment element 16 a- cmay be moved, in particular pivoted, both easily and in particular smoothly in the radial direction of the compressor wheel 14 outwards and thus in the direction of the compressor housing 12 and also in the radial direction of the compressor wheel 14 inwards and thus away from the compressor housing 12, in particular in at least almost any position of the respective adjustment element 16 a- c. In the first embodiment shown in FIG. 5, the through openings 24 are, for example, spaced apart from one another by the same distance in pairs. It can also be seen from FIG. 5 that the respective through-opening 24 is directly bounded along its respective circumferential direction in a completely encircling manner by the respective setting element 16 a- c. In the first embodiment, the respective through-opening 24 is circular. Thus, for example, the respective through-opening 24 has a circular, continuous cross-section through which a gas, such as the mentioned air, can flow. While FIG. 5 shows the first embodiment of the adjustment element 16 a- cin a schematic front view, FIG. 6 shows the first embodiment of the adjustment element 16 a- cin a schematic rear view.FIG. 7 shows a schematic front view of a second embodiment of the respective adjustment element 16 a- c, wherein the respective adjustment element 16 a- cis shown in FIG. 8 in a schematic rear view. In the second embodiment as well, the through-openings 24 are circular, and consequently the respective through-opening 24 has a respective, circular cross section. For example, the respective through-opening 24 is designed as a respective bore. In the second embodiment, the through-openings 24 are arranged in an unevenly distributed manner such that a first number of through-openings 24 is arranged in a first region and a second number of through-openings 24 is arranged in a second region, wherein the second region is the same size as the first region and wherein the second number is less than the first number. In the present case, the first number is 3 and the second number is 1.FIG. 9 shows a schematic rear view of a third embodiment of the respective adjustment element 16 a- c. In the third embodiment, the respective through-opening 24 is configured to be elongate, as a result of which the respective through-opening has a respective direction of longitudinal extent. Along the respective longitudinal extension direction, the respective through opening 24 extends in an elongate manner. Thus, for example, the respective through-opening 24 is designed as a respective slot. The direction of longitudinal extent runs, for example, in the circumferential direction of the compressor wheel 14 running around the axis of rotation D, wherein the circumferential direction is shown by a double arrow 26 in FIGS. 3 and 4. In particular, for example, the respective through-opening 24 in the third embodiment has a rectangular cross section, in particular with regard to a projection of the respective through-opening 24 into a plane. In the third embodiment, the respective adjusting element 16 a- ccomprises exactly two through-openings 24, which are embodied in a rectangular manner, and therefore have a rectangular cross section. This makes it possible to avoid excessive losses, so that particularly efficient operation of the compressor 10 can be achieved.It can be seen from FIGS. 3 and 4 that the respective adjusting element 16 a- cin the respective first position is received in the present case completely in a recess 28 of the compressor housing 12. The recess 28 is set back outwards in the radial direction of the compressor wheel 14 with respect to respective wall regions W of the compressor housing 12 which directly adjoin the respective recess 28 in the axial direction of the compressor wheel 14. This means that the recess 28 is bounded towards the outside in the radial direction of the compressor wheel 14 by a base BO, which is a further wall region of the compressor housing 12. The bottom BO is set back outwards in the radial direction of the compressor wheel 14 with respect to the wall regions W of the compressor housing 12 adjoining the recess 28 on both sides in the axial direction of the compressor wheel 14. In the exemplary embodiment shown in FIGS. 1 to 4, the recess 28 is an annular recess common to the exactly three setting elements 16 a- cin the present case and thus running completely closed and without interruptions in the circumferential direction of the compressor wheel 14 running around the axis of rotation D and thus the axial direction of the compressor wheel 14, which is also referred to as a groove. As a result, the recess 28 can be produced particularly easily.In particular, the feature that the respective adjusting element 16 a- cis arranged completely in the recess 28 in the respective first position is to be understood to mean that, in the respective first position, the respective adjusting element 16 a- cdoes not project inwardly from the recess 28 in the radial direction of the compressor wheel 14, and therefore does not project inwardly beyond the wall regions W in the radial direction of the compressor wheel 14. Thus, in the respective first position, the respective adjustment element 16 a- cis arranged at most flush with the wall regions W when viewed inwards in the radial direction of the compressor wheel 14 or is set back outwards in the radial direction of the compressor wheel 14 with respect to the wall regions W.FIG. 10 shows a schematic front view of a fourth embodiment of the respective adjustment element 16 a- c, wherein the fourth embodiment is shown in FIG. 11 in a schematic rear view. It can be seen that in the fourth embodiment, the respective adjustment element 16 a- chas, in particular exactly, four through-openings 24, wherein the respective through-opening 24 is circular and has a diameter of 2 millimeters. In particular, the respective through-opening 24 is formed as a respective bore, that is to say is produced by drilling by machining. Three of the four through-openings 24, i.e. in the present case all through-openings 24 except one form a group which is spaced further from the fourth or a through-opening 24 than the through-openings 24 of the group viewed between one another and in pairs. In particular, the through openings 24 of the group are spaced apart from one another in pairs in the same way.Finally, FIGS. 12 to 14 show a fifth embodiment, which is shown in FIGS. 12 and 13 in a respective schematic front view and in FIG. 14 in a schematic rear view. In the fifth embodiment, the respective through-opening 24 is formed as a respective elongate slot. In this case, the respective setting element 16 a- chas, in particular exactly, fifth passage openings 24. Four of the five through-openings 24 and thus all but one of the through-openings 24 form a group which is spaced further from the fifth or one through-opening 24 than the through-openings 24 of the group viewed between one another and in pairs. In particular, the through openings 24 of the group are spaced apart from one another in pairs in the same way.List of reference characters10 Compressor 12 Compressor housing 14 Compressor wheel 16 a- c Setting element 18 Double arrow 19 Double arrow 20 Actuator 22 Actuating element 24 Through opening 26 Double arrow 28 Recess B Region BO Base B 1 First region B 2 Second region D Axis of rotation D 1 First direction of rotation D 2 Second direction of rotation EB Inlet region Q Flow cross section S Axis of rotation S 1 First side S 2 Second side W Wall region R 1 First direction R 2 Second directionReferences included in the specificationThis list of documents cited by the applicant has been produced in an automated manner and is only included for the better information of the reader. The list is not part of the German patent application or utility model application. The DPMA does not take any adhesion for any faults or omissions.Patent Literature citedEP 3 647 601 B1

[0002]

Claims

Compressor (10) for an intake tract of an internal combustion engine, having a compressor housing (12) through which air can flow, in which a compressor wheel (14), which can be supplied with the air, is arranged for compressing the air, and having a plurality of adjusting elements (16a-c), which can be moved back and forth relative to the compressor housing (12) in the radial direction (19) of the compressor wheel (14), as a result of which a flow cross section (Q) which is arranged upstream of the compressor wheel (14) and through which the air can flow can be varied, characterized in that the respective adjusting element (16a-c) has at least one respective through opening (24), via which a respective first region (B1), which is arranged on a respective inner side (S1) of the respective adjusting element (16a-c) which points inwards in the radial direction (19) of the compressor wheel (14), is fluidically connected to a respective first region (B1), which is arranged in the radial direction (19) of the respective adjusting element (16a-c), on a respective second region (B2) facing outwards in the radial direction (19) of the compressor wheel (14) and arranged away from the respective inner side (S1) of the respective adjusting element (16a-c).Compressor (10) according to Claim 1, characterized in that the respective through-opening (24) is bounded in a completely encircling manner along its respective circumferential direction by the respective setting element (16a-c).Compressor (10) according to Claim 1 or 2, characterized in that the respective through-opening (24) is of elongate configuration.Compressor according to Claim 3, characterized in that the respective, elongate through-opening (24) has a respective direction of longitudinal extent which runs in the circumferential direction of the compressor wheel (14).Compressor (10) according to one of the preceding claims, characterized in that the respective through-opening (24) has a rectangular cross section.Compressor (10) according to one of the preceding claims, characterized in that the respective adjusting element (16a-c) is at least partially accommodated in a recess of the compressor housing in at least one position of the respective adjusting element (16a-c).Compressor (10) according to Claim 6, characterized in that the recess (28) is an annular recess (28) which is common to the adjusting elements (16a-c) and which is thus completely circumferential in the circumferential direction (26) of the compressor wheel (14), in which recess the respective adjusting element (16a-c) is at least partially accommodated in the respective at least one position.Compressor (10) according to Claim 6 or 7, characterized in that the respective adjusting element (16a-c) is arranged completely in the recess (28) in the respective at least one position.Exhaust gas turbocharger for an internal combustion engine, having a compressor (10) according to one of the preceding claims.Motor vehicle, having an internal combustion engine which has at least one exhaust gas turbocharger according to Claim 9.

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