Compressor

Abstract

The invention relates to a compressor, in particular a gas compressor, for instance for a turbocharger, for compressing a gaseous fluid, having a compressor housing (40) in which a compressor wheel (41) is rotatably arranged, wherein the compressor housing (40) has a gas intake manifold (43), via which gas can be fed to the compressor wheel (41), a compressor duct (42) being provided, via which the compressed gas can be discharged from the compressor wheel (41), an adjustment device (60) being arranged in the area of the gas intake manifold (43), wherein the adjustment device (60) has orifice elements (70), which can be adjusted linearly between a closed position and an open position, and by means of which the opening cross-section of the gas intake manifold (43) in a duct area can be varied in order to form a minimum opening cross-section (Ömin) in the closed position and a maximum opening cross-section (Ömax) in the open position, wherein in each case two adjacent orifice elements (70) have sealing segments (73.1, 76.1) which, in the closed position, face each other, in particular rest against each other. To be able to reduce the noise emissions in such a compressor in a simple and effective manner, provision is made according to the invention that the orifice elements (70) can be adjusted into a retracted operating position, in which body areas of the orifice elements (70) at least in some areas delimit a recess, in particular a circumferential groove, in the gas intake manifold (43) to form a resonator, in particular a Helmholtz resonator, and wherein provision may in particular be made that the orifice elements (70) can be adjusted, preferably continuously, between several retracted operating positions.

Claims

1-16. (canceled)

17: A compressor for compressing a gaseous fluid, comprising: a compressor housing; a compressor wheel rotatably arranged in the compressor housing; the compressor housing including a gas intake duct configured to feed gas to the compressor wheel, and the compressor housing including a compressor duct configured to discharge compressed gas from the compressor wheel; and an adjustment device including: a plurality of orifice elements adjustable between a closed position and an open position to change an opening cross-section of the gas intake duct to form a minimum opening cross-section in the closed position and a maximum opening cross-section in the open position; and wherein each two adjacent orifice elements include respective sealing segments facing each other in the closed position; and wherein the orifice elements are further adjustable into a retracted operating position such that in at least some areas the orifice elements delimit a recess in the gas intake duct forming a resonator.

18: The compressor of claim 17, wherein: the respective sealing segments of the adjacent orifice elements rest against each other in the closed position.

19: The compressor of claim 17, wherein: the recess comprises a circumferential groove in the gas intake duct.

20: The compressor of claim 17, wherein: the resonator comprises a Helmholtz resonator.

21: The compressor of claim 17, wherein: the orifice elements are adjustable between a plurality of retracted operating positions.

22: The compressor of claim 21, wherein: the orifice elements are continuously adjustable between the plurality of retracted operating positions.

23: The compressor of claim 17, wherein: the orifice elements are arranged at a distance from each other in the open position.

24: The compressor of claim 17, wherein: the orifice elements are arranged at a distance from each other in an intermediate position between the open position and the closed position.

25: The compressor of claim 17, wherein: the respective sealing segments of adjacent orifice elements are parallel to each other during adjustment travel between the open position and the closed position.

26: The compressor of claim 17, wherein: each orifice element includes two linearly extending sealing segments arranged at an acute angle from each other, wherein in the closed position one of the two sealing segments rests against one of the sealing segments of a first adjacent orifice element and the other of the two sealing segments rests against one of the sealing segments of a second adjacent orifice element.

27: The compressor of claim 17, wherein: each orifice element includes two linearly extending sealing segments arranged at an acute angle (α) from each other, and a first one of the linear sealing elements is set perpendicular to a direction arranged at an angle (β) from a direction of motion of the orifice element, and the angle (β) is smaller than 0.5 times X, wherein: “X=360°/number of orifice elements”.

28: The compressor of claim 27, wherein: a difference between 0.5 times X and the angle (β) is less than 10°.

29: The compressor of claim 27, wherein: a difference between 0.5 times X and the angle (β) is less than 5°.

30: The compressor of claim 27, wherein: a difference between 0.5 times X and the angle (β) is less than 2°.

31: The compressor of claim 17, wherein: each orifice element includes two linearly extending sealing segments arranged at an acute angle (α) from each other, and a first one of the linear sealing elements is set perpendicular to a direction arranged at an angle (β) from the direction of motion of the orifice element, and the angle (β) is smaller than 0.5 times X, wherein X corresponds to the angle (α) formed by the two linear sealing segments of the orifice element.

32: The compressor of claim 31, wherein: a difference between 0.5 times X and the angle (β) is less than 10°.

33: The compressor of claim 31, wherein: a difference between 0.5 times X and the angle (β) is less than 5°.

34: The compressor of claim 31, wherein: a difference between 0.5 times X and the angle (β) is less than 2°.

35: The compressor of claim 17, wherein: as the orifice elements move between the open position and the closed position the respective sealing segments of each two adjacent orifice elements are not more than 1 mm apart.

36: The compressor of claim 17, wherein: as the orifice elements move between the open position and the closed position the respective sealing segments of each two adjacent orifice elements are not more than 0.3 mm apart.

37: The compressor of claim 17, wherein: at least one orifice element of two adjacent orifice elements includes an overlap segment adjacent at least one of its sealing segments, and the overlap segment projects to at least partially cover, in a direction of an axis of rotation of the compressor wheel, one of the sealing segments of the adjacent orifice element in the closed position and in at least one intermediate position between the open position and the closed position.

38: The compressor of claim 37, wherein: the at least one orifice element includes first and second linearly extending sealing segments arranged at an acute angle (α) from each other and the at least one orifice element includes first and second overlap segments adjacent its first and second sealing segments, respectively; and the first overlap segment overlaps a first adjacent orifice element in the front in the direction of the axis of rotation of the compressor wheel, and the second overlap segment overlaps a second adjacent orifice element in the rear in the direction of the axis of rotation of the compressor wheel.

39: The compressor of claim 38, wherein: each of the orifice elements is identical to the other orifice elements.

40: The compressor of claim 37, wherein: at least two adjacent orifice elements include the overlapping segments at least partially overlapping each other in the direction of the axis of rotation of the compressor wheel.

41: The compressor of claim 40, wherein: the overlapping segments of the at least two adjacent orifice elements are configured to seal against each other in the closed position.

42: The compressor of claim 41, wherein: the overlapping segments are each configured as a seal attachment that can be bent relative to a base body of a respective orifice element.

43: The compressor of claim 41, wherein: the overlapping segments are each offset relative to each other such that each overlap segment is in sealing contact with an adjacent orifice element.

44: The compressor of claim 37, wherein: the overlap segment of the at least one orifice element is integrally formed on the at least one orifice element.

45: The compressor of claim 17, wherein: the adjustment device further includes a bearing ring, the bearing ring including a plurality of slide glides, each slide glide including a linear guide area, and the bearing ring including a plurality of guide surfaces; and each of the orifice elements includes a guide element movably received in the linear guide area of one of the slide glides, and each of the orifice elements includes a slideway supported on one of the guide surfaces.

46: The compressor of claim 45, wherein: the adjustment device further includes an actuator, the actuator including a plurality of actuator slide glides, each actuator slide glide including a linear guide area, each of the orifice elements including a second guide element movably received in the linear guide area of one of the actuator slide glides, such that rotation of the actuator relative to the bearing ring moves the orifice elements between the open position and the closed position.

47: The compressor of claim 17, wherein: the orifice elements each include a concave delimiting element adjoining the sealing elements, and the delimiting elements form an at least approximately circular orifice opening in the closed position of the orifice elements.

48: The compressor of claim 17, wherein: movement of the orifice elements from the open position to the closed position is limited by a stop on each orifice element resting in the closed position against a counterstop of an adjacent orifice element.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0047] The invention is explained in greater detail below based on an exemplary embodiment shown in the drawings. In the Figures:

[0048] FIG. 1 shows a side view and a full section of an exhaust gas turbocharger,

[0049] FIG. 2 shows a perspective and in partial section of a unit of the exhaust gas turbocharger as shown in FIG. 1,

[0050] FIG. 3 shows a full section of the unit of FIG. 2,

[0051] FIG. 4 shows a partial representation and front view of an adjustment device,

[0052] FIGS. 5 and 6 show two different perspective representations of an orifice element,

[0053] FIG. 7 to FIG. 9 show front views of different operating positions of the adjustment device,

[0054] FIG. 10 shows a partial representation and front view of an alternative design variant of an adjustment device,

[0055] FIG. 10a shows the design variant according to FIG. 10 along the course of the cut marked Xa-Xa in FIG. 10,

[0056] FIG. 11 shows a partial representation and front view of a further alternative design variant of an adjustment device,

[0057] FIG. 11a shows the design variant according to FIG. 11 along the course of the cut marked XIa-XIa in FIG. 11,

[0058] FIG. 12 shows a partial representation and front view of a further alternative design variant of an adjustment device,

[0059] FIG. 12a shows the design variant according to FIG. 12 along the course of the cut marked XIIa-XIIa in FIG. 12,

[0060] FIGS. 13 and 14 show a partial view and partial representation of a further alternative of an adjustment device and

[0061] FIG. 15 shows a schematic partial representation a section of a further variant of the invention.

DETAILED DESCRIPTION

[0062] FIG. 1 shows a turbocharger 10, namely an exhaust gas turbocharger, as typically used in vehicles equipped with combustion engines. The turbocharger 10 has a housing 20. A shaft 21 is rotatably mounted in this housing 20. There is a compressor wheel 41 at one end and of the shaft 21 and a turbine 31 at the other end.

[0063] The turbine 31 is housed in a turbine housing 30. The turbine housing 31 forms a spiral duct 32. It is formed like a channel. The exhaust gas flow from the combustion engine can be guided into the turbine 31 via the exhaust gas intake manifold and the spiral duct 32. The turbine housing 30 also forms an exhaust outlet 33. As the diagram shows, the exhaust gas from turbine 31 enters radially to the direction of rotation. In the exhaust gas outlet 33 the exhaust gas leaves the turbine housing 30 in the direction of the axis of rotation.

[0064] The compressor wheel 41 is surrounded by a compressor housing 40. A compressor duct 42 is arranged in the compressor housing 40. Furthermore, the compressor housing 40 has a gas intake manifold 43. The gas intake manifold 43 forms a duct wall 43.1. The gas to be compressed (e.g., air) can be routed axially to the compressor wheel 41 in the direction of its axis of rotation through the gas intake manifold 43.

[0065] As can be seen from the drawing, the gas intake manifold 43 may, for instance, also be formed at least partially by a housing part 50 of the compressor housing 40, wherein the housing part 50 is connected to the base body of the compressor housing 40. FIG. 1 shows that the housing part 50 has a flow guide 51, which transitions into the wall 43.1 as part of the gas intake manifold 43.

[0066] As FIG. 1 shows, the wall 43.1 of the gas intake manifold 43 is adapted to the contour of the compressor blades 44, resulting in an efficiency-optimized design.

[0067] FIG. 1 shows that an adjustment device 60 is held in the area between the housing part 50 and the base body of the compressor housing 40.

[0068] FIGS. 2 and 3 show the design of the adjustment device 60 in more detail. These diagrams show that the adjustment device 60 can have a bearing unit 61. The bearing unit 61 can for instance, as shown here, be formed by an annular component, wherein in particular the bearing unit 61 is manufactured from a flat component, e.g., a sheet metal blank or a plastic part. The bearing unit 61 can also be part of the housing part 50. Preferably, however, it is designed as a separate component, as shown here.

[0069] The adjustment device 60 also has an actuator 62. The actuator 62 can also be formed by an annular component. It is conceivable that the actuator 62 is also formed from a flat component, e.g., made from a sheet metal blank or a plastic part.

[0070] As shown in the diagram in FIG. 3, the inside diameters 61.6, 62.6. of the bearing unit 61 and of the actuator 62 form an opening cross-section. This opening cross-section is preferably dimensioned such that it is equal to the maximum opening cross-section Ömax of the gas intake manifold 43 in the area of the adjoining flow guide 51 of the housing part 50 or the adjoining wall 43.1 downstream of the adjustment device 60. In this way, in the operating position shown in FIG. 3, the adjustment device 60 does not constitute any obstruction of the flow in the gas intake manifold 43. However, it is also conceivable that the bearing unit 61 and/or the actuator 62 project slightly into the gas intake manifold 43 or are arranged offset radially outwards in relation to the wall 43.1.

[0071] The compressor housing 40 has a bag-shaped holder 45. The adjustment device 60 is inserted into this holder 45. The holder 45 is designed such that the bearing unit 61 is radially and axially secured at the compressor housing 40 relative to the axis of the compressor wheel 41 and the actuator 62 can be rotated in the holder 45.

[0072] FIG. 3 clearly shows that the compressor housing 40 has a holder into which the housing part 50 is inserted using a centering attachment 52. In that way the housing part 50 is oriented in the correct position relative to the compressor housing 40. Accordingly, the flow guide 51 of the housing part 50 and the part of the gas guide 43 in the compressor housing 40 can also be interaligned.

[0073] FIG. 4 shows the composition of the bearing unit 61 in more detail. As explained above, the bearing unit 61 can preferably be of annular design. Accordingly, it has a circular outer circumferential boundary 61.7 and an inner diameter 61.6. Other forms of bearing units 61 are of course also conceivable.

[0074] The bearing unit 61 has a guide surface 61.1. Slide guides 61.2 can be incorporated in the guide surface 61.1. The slide guides 61.2 are preferably designed as slotted penetrations. As FIG. 4 shows, a large number of slide guides 61.2 are provided—these slide guides 61.2 are evenly distributed around the circumference of bearing unit 61.

[0075] The slide guides 61.2 define a linear guide area 61.4. This linear guide area 61.4 can be tangential to the inner diameter 61.6, as shown in FIG. 4.

[0076] End areas 61.3, 61.5 can be used to terminate he slide guides 61.2 at the latter's longitudinal ends. This results in a stable geometry for the annular bearing unit 61. The bearing unit 61 has a flat surface facing the flat guide surface 61.1 that also extends annularly and is used for a flat contact with an associated surface area of the housing part 50.

[0077] The bearing part 61 is used to house a variety of orifice elements 70 in an adjustable manner. The orifice elements 70 can preferably all be of identical design. It is also conceivable, however, that the design of orifice elements 70 varies individually. However, for identical orifice elements 70, the parts and assembly costs are lower. In this exemplary embodiment, eight orifice elements are installed in the bearing unit 61. It is conceivable, however, that a different number of orifice elements 70 is installed in an adjustment device 60.

[0078] FIGS. 5 and 6 show the design of the orifice elements 70 in more detail. As these drawings show, the orifice element 70 has a slideway 71 on one side of the element. A further slideway 72 can be provided on the opposite side of the element of the orifice element 70. The slideways 71 and 72 can preferably be parallel to each other

[0079] The orifice element 70 can have a guide element 79.1, 79.2 in the area of the two slideways 71, 72.

[0080] The guide element 79.2 protrudes from the slideway 72. The guide element 79.2 has a rib-shaped design. The width of the guide element 79.2 has been dimensioned to fit into the slot-shaped guide area 61.4.

[0081] A conceivable design variant for realizing the invention may also be such that instead of the ribbed guide element 79.2, two projections, for instance cylindrical projections, disposed at a distance from each other are used, which engage with the guide area 61.4.

[0082] According to the invention, it is particularly preferably provided that the assignment of the orifice element 70 to the bearing unit 61 is designed such that the guide element 79.2 can be used to adjust the orifice element 70 linearly, but not rotatably, relative to the bearing unit 61 in the guide area 61.4.

[0083] The guide element 79.1 protrudes from the slideway 71. In this exemplary embodiment, the guide element 79.1 is designed as a cylindrical bevel. Other designs of the guide element 79.1 are conceivable.

[0084] As FIGS. 5 and 6 show further, the orifice element 70 has a first adjustment range 73. This first adjustment range 73 forms a sealing segment 73.1. A boundary area 74 is provided directly downstream of the sealing segment 73.1.

[0085] The boundary area 74 can preferably be concave. However, it is also conceivable that the boundary area 73 is connected to the gasket segments 63.1 rectilinearly or in some other way.

[0086] The sealing segment 73.1 can, in particular, be designed as a rectilinear surface segment 73.1. Preferably the sealing segment 73.1 is perpendicular to the slideway 71 and/or the slideway 72. The boundary area 74 can, for instance, preferably directly tangentially adjoin the sealing segment 73.1. It is also conceivable for the boundary area 74 to indirectly adjoin the sealing segment 73.1 via an intermediate segment.

[0087] The orifice element 70 has an end segment 75. In one embodiment of the invention, this end segment 75 can form a counterstop 75.1 at its free end, as will be explained later.

[0088] The end segment 75 can form the transition between the boundary area 74 and a further sealing segment 76.1. The further sealing segment 76.1 is part of a second adjustment range 76 of the orifice element.

[0089] The further sealing segment 76.1 is preferably designed as a linearly extending surface area. This sealing segment 76.1 is further preferably aligned perpendicular to the slideway 71 and/or the slideway 72.

[0090] The drawings of FIGS. 5 and 6 show that the two sealing segments 73.1 and 76.1 form an angle α. The angle α in this exemplary embodiment is 45°. The angle α is calculated as follows: 360° divided by X, wherein X represents the number of orifice elements 70 of the adjustment device 60.

[0091] As FIGS. 5 and 6 further show, an end segment 78 can adjoin the first adjustment range 73. The end segment 78 transitions into an edge 77 and this in turn transitions into the second adjustment range 76.

[0092] The orifice elements 70 can preferably be designed as plastic injection molded parts. The guide elements 79.1, 79.2 are preferably integrally molded. It is also conceivable that the orifice elements 70 are manufactured as punched and bent parts from a sheet metal blank. In that case, the guide elements 79.1, 79.2 can be pressed into the orifice element, for instance.

[0093] As FIG. 4 shows, the orifice elements 70 can be inserted into the slide guide 61.2, wherein the guide element 79.2 protrudes from the slideway 72. In this way, the orifice elements in the slide guide 61.2 can be adjusted linearly along the longitudinal extension of the guide area 61.4.

[0094] As FIG. 7 shows, the preferably identical orifice elements 70 can be installed in conjunction with the bearing ring 61. The illustration in FIG. 7 is chosen to show the actuator 62 in addition to bearing unit 61. The actuator 62 is drawn transparently, rendering the arrangement of the orifice elements 70 visible.

[0095] As FIG. 7 shows, the actuator 62 has an annular geometry. Correspondingly, the actuator 62 has an inner diameter 62.6 and a circular outer circumferential boundary 62.7. This design is preferred. However, provision may also be made that the circumferential boundary 62.7 is not annular but has a different shape.

[0096] The actuator 62 forms a guide surface 62.1, which is assigned to the orifice elements 70 when the adjustment device 60 is installed. This guide surface 62.1 faces the slideways 71 of the orifice elements 70. Accordingly, the slideways 71 of the orifice elements 70 can rest against the guide surface 62.1. Slide guides 62.2 are incorporated in the actuator 62. The slide guides 62.2 can be designed as slotted openings, which are excluded from the actuator 62. The slide guides 62.2 have a linear guide area 62.4. For reasons of stability, the end ranges 62.3, 62.5 of the actuator 62 can be connected to this linear guide area 62.4.

[0097] For the installation of the adjustment device 60, the actuator 62 is placed on the orifice elements 70. The guide elements 79.1 of the orifice elements 70 each engage in one guide area 62.4 of the slide guides 62.2.

[0098] When the adjustment device 60 is installed, the bearing unit 61 is blocked against rotation in the compressor. The actuator 62 can be rotated in the peripheral direction. For this purpose, for instance, an actuating device (not shown) may be used, which acts on the actuator 62 to be able to rotate it in the peripheral direction.

[0099] FIG. 7 shows the maximum opening cross-section of the adjustment device 60. Accordingly, the orifice elements 70 are adjusted such that they are held between the actuator 62 and the bearing unit 61. Accordingly, the orifice elements 70 do not protrude beyond the inner diameter 61.6 of the bearing unit 61 or the inner diameter 62.6 of the actuator 62. For this purpose, the flanks 77 of the orifice elements 70 are designed such that they do not protrude beyond the circumferential boundaries 61.7, 62.7. In the open position the orifice elements 70 are arranged in such a way that the sealing segments 73.1 and the boundary areas 74 are almost flush with the inner diameters 61.6, 62.6 of the bearing unit 61 and the actuator 62, and thus with the opening cross-section Ömax of the gas intake manifold 43 in the area of the adjoining flow guide 51 of the housing part 50 or the adjoining wall 43.1 downstream of the adjustment device 60.

[0100] In FIG. 7, if the actuator 62 is turned clockwise in relation to the bearing unit 61, the actuator 62 uses the slide guides 62.2 to drive the guide elements 79.1 of the orifice elements 70. Accordingly, the guide elements 79.1 in the slide guides 62.2 are adjusted linearly. Because the orifice elements 70 are now also moved captive in conjunction with the second guide element 79.2 in the slide guide 61.2 of the bearing unit 61, the orifice elements 70 are adjusted linearly in the direction of the linear guide area 61.4. In this way the orifice elements 70 can be moved linearly from the open position as shown in FIG. 7 to the closed position as shown in FIG. 8.

[0101] FIG. 8 shows that in the closed position of the orifice elements 70, the concave boundary areas 74 of the individual orifice elements 70 are interaligned such that a minimum opening cross-section Ömin results, which is approximately circular.

[0102] In the closed position as shown in FIG. 8, the sealing segments 73.1 of the orifice elements 70 rest against the sealing segments 76.1 of the adjacent orifice elements 70. In this way, the slideways 71 and/or the slideways 72 of the orifice elements 70 contribute to a closed orifice surface in the closed position, which only opens the minimum opening cross-section Ömin.

[0103] According to the invention, it is now provided that, starting from the closed position, in which the sealing segments 73.1, 76.1 are in contact, the orifice elements 70 can be continuously adjusted to the open position (see FIG. 7). To this end, provision is made that starting from the closed position, when the actuator 62 is turned (counterclockwise in FIG. 8), the sealing segments 73.1, 76.2 of the adjacent orifice elements 70 are slightly spaced apart so as not to impede the motion of the orifice elements 70 into the open position. Preferably, in any position between the closed position and the open position, the sealing segments 73.1, 76.1 are aligned in parallel to each other. Especially preferably, the first linear sealing segment 73.1 of the orifice element 70 is set at an angle of 90°+β to the direction of motion of orifice element 70. This angle β is smaller than 0.5*X, wherein: “X=360°/(number of orifice elements (70))”. In this case X=45°. Therefore, β has to be selected smaller than 22.5°.

[0104] In this exemplary embodiment α=X. Thus, the angle α between the two linear sealing segments 73.1, 76.1 of the orifice element 70 also has to be selected smaller than β (in this case therefore smaller than 22.5°).

[0105] Furthermore, it may preferably be according to the invention that:

[0106] “(0.5*X−β)<10°, preferably smaller than 5°, especially preferred smaller than 2°”, applies.

[0107] In this exemplary embodiment “(0.5*45°−β)<2°”, i.e., β is >20.5°.

[0108] When dimensioning, it is particularly important to select β<0.5 α or β<0.5 X. In this exemplary embodiment, this limit would be chosen accordingly as β<0.5 X, i.e., β<22.5°.

[0109] The above-mentioned angular ratios ensure that the sealing segments 73.1, 76.1 lift off from each other immediately after turning the actuator 62 from the closed position.

[0110] If the orifice elements 70 are adjusted further, the sealing segments 73.1, 76.1 remain in parallel to each other in every intermediate position and are only slightly spaced apart from each other. This ensures a particularly good sealing effect of the orifice area even in the intermediate position.

[0111] FIG. 10 shows a further design variant of the invention. Identical reference numerals refer to identical component areas. To avoid repetition, reference can be made to the explanations above. Only the changes made to the alternative embodiment shall be explained below.

[0112] As FIG. 10 shows, the orifice elements 70 have overlap segments 73.3, 76.3 both in the first adjustment range 73 and in the second adjustment range 76. The overlap segments 73.3, 76.3 are formed as steps. The adjacent orifice elements 70 also have overlap segments 73.1, 76.1, which are stepped to match.

[0113] FIG. 10 shows that the overlap segments 73.3, 76.3 of adjacent orifice elements 70 overlap. The assignment is made in such a way that the projections of the overlap segments 73.3, 76.3 overlap in the direction of flow in the gas intake manifold 43, i.e., in the direction of the axis of rotation of the compressor wheel 41. Thus, the overlap segments 73.3, 76.3 of the adjacent orifice elements form 70 labyrinth-like seals, which form a flow resistance in the area of the orifice surface. This flow resistance prevents or reduces the risk of unintentional air flow through the gap areas between the adjacent sealing segments 73.1, 76.2.

[0114] FIG. 10a shows a sectional view along the section line Xa-Xa marked in FIG. 10. As this illustration shows, the steps of the orifice element 70, which form the sealing segments 73.1 and 76.1, are each oriented towards one side of the orifice element 70. The sealing segments 73.1, 76.1 of the orifice element 70 at the right in FIG. 10a are located at the rear end. Accordingly, the sealing segments 73.1, 76.1 of the left-hand orifice element 70 are arranged at the front end.

[0115] FIG. 10 shows an intermediate position between the closed position and the open position. As can be seen from this diagram, in this position the sealing segments 73.1, 76.1 are arranged in parallel to each other, resulting in only a narrow gap area. This gap area is covered by the overlap segment 73.3, 76.3.

[0116] FIGS. 11 and 11a show a further development of the design variant according to FIGS. 10 and 10a. In contrast to the design variant according to FIGS. 10/10a, in the design according to FIGS. 11/11a, the sealing segments 73.1, 76.1 of each orifice element 70 are arranged alternating at the front end and the rear end of the orifice element 70. This is clearly shown in FIG. 11a. In this way, all orifice elements can be designed identically.

[0117] FIGS. 12 and 12a show a further design variant of the invention. This design variant generally matches the design of the adjustment device 61 as shown in the preceding FIGS. 10 to 11a. Therefore, only the differences will be discussed below. In the invention variant according to FIGS. 12 and 12a, the orifice elements 70 have several overlap segments 73.3, 76.3 at their sealing segments 73.1, 76.1. In this case, two protruding overlap segments 73.3, 76.3 are provided at each of the sealing segments 73.1 and 76.1 of an orifice element 70. FIG. 11 then shows that when using identical orifice elements 70, the adjacent sealing segments 73.1, 76.1 of two orifice elements 70 interlock in a comb-like manner, wherein the projections of the overlap segments 73.3, 76.3 overlap in the direction of the axis of rotation of the compressor wheel 41 to form a labyrinth seal.

[0118] FIGS. 13 and 14 show a further development of the design of the invention as shown in FIGS. 4 to 9. To avoid repetition, reference is made to the explanations above. Only the differences shall be explained below.

[0119] Whereas in the embodiment shown in FIGS. 4 to 9 in the closed position of the orifice elements 70, the travel of the orifice elements 70 is limited either by the guide elements 79.1, 79.2, which stop at the associated end areas 62.3, 61.5 of the slide guides 62, 61, or by the sealing segments 73.1, 76.1 of two adjacent orifice elements coming into contact, the orifice elements 70 as shown in FIG. 13 have stops 73.2 and matching counterstops 75.1. In the closed position, the stops 75.1 of the orifice elements 70 abut the associated counterstops 75.1 of the adjacent orifice elements 70 to delimit the closing motion of the orifice elements 70.

[0120] As FIGS. 13 and 14 show, the stops 73.2 can preferably be formed in the transition area between the sealing segments 73.1 and the boundary areas 74. The counterstop 75.1 can then be formed by the end segment 75, for instance.

[0121] As FIGS. 13 and 14 show, the orifice elements 70 can be equipped with overlap segments 73.3.

[0122] FIG. 15 shows as various operating states of the adjustment device 60 an invention variant. Longitudinal sections through the compressor when the orifice elements 70 in the open position (maximum opening cross-section Ömax) according to FIG. 7, in the closed position (minimum opening cross-section Ömin) according to FIG. 8 or in a retracted position are shown schematically.

[0123] In the retracted position, the orifice elements 70 are moved such that their opening cross-section is larger than the opening cross-section Ömax of the open position. In this way the sealing segments 73.1 and the boundary areas 74 of the orifice elements 70 in conjunction with the guide surfaces 61.1, 62.1 of the bearing unit 61 and the actuator 62 form a circumferential groove in the flow guide 51. The circumferential groove acts as a Helmholtz resonator, and can thus be used to cancel out certain frequencies of the compressor. In principle, the orifice elements 70 can be continuously moved between the neutral (Ömax) and the retracted position and thus to adjust the Helmholtz resonator to the frequency to be canceled.

[0124] It goes without saying that the shape of the groove can be designed by designing the guide surfaces 61.1, 62.1 of the bearing unit 61 and the actuator 62 in the transition area to the wall 43.1 and to the flow guide 51 according to the measures known from the state of the art.

[0125] The invention is not limited to the exemplary embodiment described. Rather, provision may also be made in the invention in that the compressor is used as a support for an exhaust gas turbocharger or is arranged decoupled from an exhaust gas turbocharger. It is also conceivable that the compressor is an electrically driven compressor, wherein the compressor wheel is driven by an electric motor. Such an electrically driven compressor can also be part of a turbocharger for a combustion engine. Furthermore, provision may also be made that the compressor according to the invention is used, for instance, in connection with an air supply for a fuel cell. In this case, the compressor wheel 41 can also be driven by an electric motor.