Patent Publication Number: US-11391200-B2

Title: Compressor having an adjustment mechanism

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application claims the benefit of German Patent Application No. 102019203370.9 filed Mar. 12, 2019, the disclosure of which is herein incorporated by reference in its entirety. 
     TECHNICAL FIELD 
     This invention relates to a compressor for a supercharger. The invention also relates to a supercharger having such a compressor. 
     BACKGROUND 
     More and more newer-generation vehicles are being equipped with superchargers in order to meet requirement targets and fulfill legal conditions. In the development of superchargers, the individual components as well as the system as a whole must be optimized in terms of reliability and efficiency. 
     Known superchargers usually have at least one compressor with a compressor wheel, which is connected to a drive unit by a common shaft. The compressor compresses the fresh air that is sucked in for the internal combustion engine or for the fuel cell. The volume of air or oxygen available to the engine for combustion or to the fuel cell for reaction is thus increased. This in turn leads to an increase in performance of the internal combustion engine or of the fuel cell. Superchargers can be equipped with different kinds of drive units. In particular e-chargers, in which the compressor is driven by an electric motor, and exhaust gas turbochargers, in which the compressor is driven by an exhaust gas turbine, are known to the prior art. Combinations of both systems are also described in the prior art. 
     Each compressor has a compressor-specific compressor characteristic map; the operation of the compressor being limited to the area of the compressor characteristic map between the surge line and the choke line. Depending upon the size and design of the compressor, the surge line may be reached in the event of low volumetric flows through the compressor; hence operation may be inefficient or no longer possible. 
     Known to the prior art in particular are compressors with adjustment mechanisms, which are arranged in the inlet zone of the compressor, upstream of the compressor wheel in the flow direction. The adjustment mechanisms can be used to vary the flow cross section in the compressor inlet; thus enabling, for example, the velocity and rate of the flow to the compressor wheel to be adjusted. This serves as a characteristic map-expanding measure, by which compressor surging can in turn be reduced or eliminated. Actuator devices, which must be connected to the adjustment mechanism, are required for actuating the adjustment mechanisms. This results in complex systems in terms of construction and control, and correspondingly large dimensions with increased installation space requirements, which in turn can result in design limitations. 
     The problem addressed by this invention is that of providing a compressor having an improved actuator device for an adjustment mechanism of a compressor. 
     SUMMARY OF THE INVENTION 
     This invention relates to a compressor for a supercharger according to Claim  1 . The invention also relates to a supercharger having a compressor such as the one according to Claim  15 . 
     The compressor for a supercharger comprises a compressor housing with a compressor inlet and a compressor outlet. The compressor also comprises an adjustment mechanism and an actuator device. The adjustment mechanism comprises an adjustment ring and multiple shutter elements for altering an inlet cross section of the compressor inlet. The actuator device comprises a drive unit and a coupling unit. The actuator device is coupled to the adjustment mechanism via the coupling unit for moving the adjustment mechanism between a first position and a second position. The drive unit can thus move the coupling unit, which in turn transfers the movement to the adjustment mechanism. The adjustment mechanism is designed to move in such a way that the shutter elements can reduce the inlet cross section or unblock it again. By virtue of the fact that the drive unit can move the adjustment mechanism directly via the coupling unit, a compact design is achievable. The implementation of the actuator device enables an implementation using just the drive unit and the coupling unit without the need of, for example, additional complicated transmission and/or gearbox units. In sum, it is possible to provide an improved compressor having a compact system of simple construction for stabilizing the compressor characteristic map. 
     In designs of the compressor, the coupling unit can comprise an oblong base body with a first end section and a second end section. The first end section can be coupled to the drive to unit. The second end section can be coupled to the adjustment mechanism. In other words, this means that the first end section can be coupled directly to the drive unit and that the second end section can be coupled directly to the adjustment mechanism. 
     In addition, the drive unit can be designed to move the coupling unit linearly along an axis of the oblong base body between a first position and a second position. As an alternative, the drive unit can be designed to move the coupling unit in rotation along an axis of the oblong base body between a first position and a second position. 
     In designs of the compressor which can be combined with the preceding design, the second end section can engage with the adjustment mechanism in such a way that the adjustment mechanism is in its first position in the first position of the oblong base body and that the adjustment mechanism is in its second position in the second position of the oblong base body. 
     In designs of the compressor which can be combined with any one of the preceding designs, the first position can correspond to an open position of the adjustment mechanism. The second position can correspond to a closed position of the adjustment mechanism. The inlet cross section is maximal in the open position of the adjustment mechanism. The inlet cross section is reduced in the closed position of the adjustment mechanism. In other words, this means that the inlet cross section is maximally reduced and not necessarily closed in the closed position of the adjustment mechanism. This means that the inlet cross section is minimal in the closed position of the adjustment mechanism. The inlet cross section is maximal in the open position of the adjustment mechanism. 
     In designs of the compressor which can be combined with any one of the preceding designs, at least one stop can be provided on the compressor housing. The stop can limit a movement of the coupling unit and/or a movement of the adjustment mechanism in the first position and/or in the second position. In particular, the stop can limit a movement of the adjustment ring and/or a movement of one or more of the shutter elements in the first position and/or in the second position. As an alternative, the adjustment mechanism can comprise at least one stop, which limits a movement of the shutter elements and/or of the adjustment ring in the first position and/or in the second position. The shutter elements comprise respective coupling elements, which are operatively coupled to corresponding shutter recesses in the adjustment ring so that the shutter elements can be moved via the adjustment ring. For example, the shutter recesses and/or the coupling elements can be configured in such a way that only maximum relative movement is possible, beyond which a type of tilting occurs which prevents a further relative movement of the shutter elements relative to the adjustment ring, in particular in the open position of the adjustment mechanism. The shutter elements can be configured and/or dimensioned in such a way that they, particularly in a closed position of the adjustment mechanism, touchingly contact the respective adjacent shutter elements. The adjacent shutter elements can come into touching contact, particularly in a circumferential direction, such that a further movement is prevented. A movement of the shutter elements and thus also a movement of the adjustment ring can thus be limited in the closed position of the adjustment ring. As an alternative, a limitation of the movement in the closed position can also be implemented by the aforementioned physical stop or by suitably designing the coupling elements and shutter recesses. 
     In designs of the compressor which can be combined with any one of the preceding designs, the drive unit can be a pneumatic, a hydraulic or an electric drive unit. In addition, the drive unit, if it is pneumatic, can be fluidically coupled to a line section downstream of the compressor outlet. 
     In designs of the compressor which can be combined with any one of the preceding designs, the compressor can furthermore comprise a fail-safe device. The fail-safe device is designed to move the adjustment mechanism into a safety position and hold it therein. For example, the fail-safe device can be configured to operate in the event that a (correct) functioning of the drive unit is impaired or if the latter is not working. For example, the fail-safe device can be activated by an interruption of the power supply and/or of the compressed air supply and/or an overload of the compressor. The safety position can correspond to the first position of the adjustment mechanism or to the second position of the adjustment mechanism. The fail-safe device is preferably designed to move the adjustment mechanism into its first position in which the inlet cross section is maximal. In other words, the safety position preferably corresponds to the first position of the adjustment mechanism and/or to the open position of the adjustment mechanism. The fail-safe device can comprise a spring element, for example. 
     In designs of the compressor which can be combined with the preceding design, the fail-safe device can be coupled to the drive unit. As an alternative, the fail-safe device can be coupled to the adjustment mechanism, in particular to the adjustment ring. A combined coupling to the drive unit and to the adjustment mechanism is also possible. If the fail-safe device is coupled to the drive unit, the fail-safe device can be designed to move the coupling unit in such a way that the coupling unit in turn moves the adjustment mechanism into the safety position. If the fail-safe device is coupled to the adjustment mechanism, the adjustment mechanism can also be moved into the safety position independently of the coupling unit and/or the drive unit in the event of, say, a defect in the coupling unit, in particular a breakage of the coupling unit. 
     In designs of the compressor which can be combined with any one of the preceding designs, the second end section can be in direct operative engagement with the adjustment ring. As an alternative, the second end section can be in direct operative engagement with one or a plurality of the shutter elements. 
     In designs of the compressor which can be combined with any one of the preceding designs in which the coupling unit is movable linearly along the axis of the oblong base body, the second end section can comprise one of either a recess or a protrusion. The adjustment ring can comprise the other of either a recess or a protrusion. The recess and the protrusion are in operative engagement with each other. In addition, and if the second end section comprises the recess, the recess can extend orthogonally to the axis of the oblong base body and orthogonally to the compressor axis. As an alternative and if the adjustment ring comprises a recess, the recess can extend in a radial direction. It is thus possible to compensate the radial offset between the coupling unit and the adjustment ring during the movement, since the coupling unit is moved tangentially to the adjustment ring. The coupling unit, in particular the oblong base body, is arranged in a direction tangential to the adjustment mechanism, in particular in a direction tangential to the adjustment ring. More precisely, the coupling unit or the oblong base body is arranged in a tangential direction of the compressor and offset radially inwards so that it can be coupled to the adjustment ring. A linear movement of the coupling unit can thus be converted to a rotary movement of the adjustment ring. The protrusion can extend substantially in an axial direction of the compressor into the recess. Additionally, the protrusion can extend substantially in an axial direction into the recess. The protrusion can be pin-shaped or bolt-shaped for example. As an alternative, the recess can be configured simply as a depression, e.g., as a groove. The first end section can be configured as, say, an extension of the oblong base body and coupled directly to the drive unit in order to receive a linear movement or absorb linear forces. 
     As an alternative to the preceding design, the second end section can comprise a three-joint mechanism. The three-joint mechanism is operatively coupled to the adjustment ring and designed to convert a linear movement of the coupling unit into a rotary movement of the adjustment ring. It is thus possible to compensate the radial offset between the coupling unit and the adjustment ring during the movement, since the coupling unit is moved tangentially to the adjustment ring. 
     In designs of the compressor which can be combined with any one of the preceding designs in which the coupling unit is movable linearly along the axis of the oblong base body, the compressor housing can comprise a drilled hole. The oblong base body can enter the compressor housing through the drilled hole. A bushing, in which the oblong base body is slidingly arranged, can also be arranged in the drilled hole. The drilled hole can also be arranged in a tangential direction (of the adjustment mechanism or of the adjustment ring). More precisely, the drilled hole is arranged in a tangential direction of the compressor and offset radially inwards. 
     In designs of the compressor which can be combined with any one of the preceding designs in which the coupling unit is movable in rotation along the axis of the oblong base body, the second end section can be fork-shaped or pin-shaped and project radially away from the axis of the oblong base body. The second end section can engage operatively with a corresponding depression in the adjustment ring or with a corresponding protrusion of the adjustment ring. In particular if the second end section is fork-shaped, it can engage operatively with a corresponding protrusion of the adjustment ring. The second end section can extend, in particular in an axial direction of the adjustment ring, into the depression of the adjustment ring. In particular, the second end section can engage operatively in an axial direction with the adjustment ring, i.e., with the depression or protrusion thereof. In the case of a depression, the latter can have a tangential gradient in order to compensate for a radial offset between the coupling unit and the adjustment ring during the movement. As an alternative or in addition, the second end section can also be configured as correspondingly smaller than the recess for the same purpose. 
     In designs of the compressor which can be combined with any one of the preceding designs in which the coupling unit is movable in rotation along the axis of the oblong base body, the first end section can comprise a lever and a rod coupled to the same. The lever can project radially away from the axis of the oblong base body. The rod can be coupled directly to the drive unit in such a way that the rod is movable linearly along its axis by the drive unit. A conversion of the linear movement of the rod into a pivot movement or rotation of the lever about the axis of the oblong base body is possible because the rod is arranged tangentially to the axis of the oblong base body (and offset radially outward from the axis of the oblong base body). 
     As an alternative to the preceding design, the drive unit can be designed to generate a rotary movement. For this purpose, the first end section can be coupled directly to the drive unit and designed to receive a rotary movement. For example, the first end section can be configured as an extension of the oblong base body and coupled directly to the rotary drive unit in order to receive a rotary movement or absorb rotary forces. 
     In designs of the compressor which can be combined with any one of the preceding designs in which the coupling unit is movable in rotation along the axis of the oblong base body, the compressor housing can comprise a drilled hole. The oblong body can enter the compressor housing through the drilled hole. In addition, a bushing in which the oblong body is rotatably mounted can be arranged in the drilled hole. In addition, the drilled hole can be arranged in a radial direction of the compressor or in an axial direction of the compressor. 
     In designs of the compressor which can be combined with any one of the preceding designs, the drive unit can be arranged directly on, in particular fastened to, the compressor housing. 
     In designs of the compressor which can be combined with any one of the preceding designs, the actuator device can furthermore comprise a control unit. The control unit can be designed to control the drive unit according to various operating modes of the compressor. 
     The invention furthermore relates to a supercharger comprising a drive device and a shaft. The supercharger furthermore comprises a compressor according to any one of the preceding designs. The compressor is coupled to the drive device, for conjoint rotation therewith, via the shaft. More precisely, the compressor wheel of the compressor is coupled to the drive device via the shaft. The drive device can comprise a turbine and/or an electric motor. 
    
    
     
       BRIEF DESCRIPTION OF THE FIGURES 
         FIG. 1A  shows a perspective view of a compressor with the actuator device; 
         FIG. 1B  shows a top view of the compressor from  FIG. 1A  without inlet nozzles, with the adjustment mechanism visible; 
         FIGS. 2A-2B  show a view from above and a detailed view of the adjustment mechanism, from which the stop is discernible; 
         FIG. 3  shows, in a perspective view, how the actuator device and the adjustment mechanism according to a first design of a linearly movable coupling unit are intercoupled; 
         FIG. 4  shows, in a perspective view, how the actuator device and the adjustment mechanism according to a second design of a linearly movable coupling unit are intercoupled; 
         FIGS. 5A-5B  show, in perspective views, how the actuator device and the adjustment mechanism according to a first design of a rotationally movable coupling unit are intercoupled when the adjustment mechanism is in a closed position ( FIG. 5A ) and in an open position ( FIG. 5B ); 
         FIG. 5C  shows the design of the adjustment ring for a rotationally movable coupling unit in a view from above; 
         FIG. 6A  shows, in a perspective view, how the actuator device and the adjustment ring according to a second design of a rotationally movable coupling unit are intercoupled; 
         FIG. 6B  shows the coupling according to  FIG. 6A  installed in a compressor; 
         FIG. 7  shows the compressor housing in a perspective view, with a flange and gasket for coupling to the actuator device; 
         FIG. 8  shows a schematic representation of a supercharger. 
     
    
    
     DETAILED DESCRIPTION 
     In the context of this application, the expressions axial and axial direction relate to a rotation axis of the compressor  100  or of the adjustment ring  210 . With reference to the figures (see for example  FIG. 1A  or  FIG. 3 ), the axial direction of the compressor  100  or of the adjustment ring  210  is represented with the reference sign  22 . A radial direction  24  relates to the axis  22  of the compressor  100  or of the adjustment ring  210 . A circumference or a circumferential direction  26  likewise relates to the axis  22  of the compressor  100  or of the adjustment ring  210 . A tangential direction  28  relates to an orientation substantially orthogonal to the radial direction  24 . In principle, orientations and directions are to be interpreted according to these explanations, except when an axial/linear/radial/circumferential/tangential or other orientation/direction relates explicitly to another object (e.g., oblong base body). 
       FIGS. 1A and 1B  show the compressor  100  according to the invention for a supercharger  10 . The compressor  100  comprises a compressor housing  110  having a compressor inlet  112  and a compressor outlet  114 . The compressor  100  furthermore comprises an adjustment mechanism  200  and an actuator device  300 . In  FIG. 1A , an inlet nozzle  130  is mounted on the compressor housing  110 , in the zone of the compressor inlet  112 , which is why the adjustment mechanism  200  is only visible in  FIG. 1B . The adjustment mechanism  200  comprises an adjustment ring  210  and multiple shutter elements  220  for changing an inlet cross section  112   a  of the compressor inlet  112 . The actuator device  300  comprises a drive unit  310  and a coupling unit  320 . The actuator device  300  is coupled to the adjustment mechanism  200  via the coupling unit  320  in order to move the adjustment mechanism  200  between a first position and a second position. In this process, the drive unit  310  can move the coupling unit  320 , which in turn transmits the movement to the adjustment mechanism  200 . The adjustment mechanism  200  is designed to move in such a way that the shutter elements  220  can reduce the inlet cross section  112   a  or unblock it again. This becomes clear upon examination of  FIGS. 5A and 5B , which show a closed position and an open position, respectively, of the adjustment mechanism  200 . The first position ( FIG. 5B ) corresponds to an open position of the adjustment mechanism  200  and the second position ( FIG. 5A ) corresponds to a closed position of the adjustment mechanism  200 . The inlet cross section  112   a  is maximal in the open position of the adjustment mechanism  200 . In contrast, the inlet cross section  112   a  is reduced in the closed position of the adjustment mechanism  200 . In other words, this means that the inlet cross section  112   a  is maximally reduced but not necessarily closed in the closed position of the adjustment mechanism  200 . This means that there is a minimal inlet cross section  112   a  in the closed position of the adjustment mechanism  200 . The inlet cross section  112   a  is maximal in the open position of the adjustment mechanism  200 . Various intermediate positions such as those illustrated in  FIGS. 3 and 6B  are also settable. The surge behavior of the compressor  100  can be improved by changing the inlet cross section  112   a . In other words, a characteristic map-stabilizing measure (kennfeldstabilisierende Maßnahme (KSM)) or characteristic map-expanding measure can be implemented, which in turn improves the operational properties and operational range of the compressor. The fact that the drive unit  310  can move the adjustment mechanism  200  directly via the coupling unit  320  permits a compact design. Furthermore, the implementation of the actuator  300  enables an implementation solely by the drive unit  310  and the coupling unit  320  without the need of, for example, additional complicated transmission and/or gearbox units. In sum, provision can be made of an improved compressor  100  with a compact system with simple construction for stabilizing the characteristic map of the compressor  100 . 
     The coupling unit  320  shall be explained in more detail with reference to  FIGS. 3 and 5A . Basically, the coupling unit  320  comprises an oblong base body  322  with a first end section  324  and a second end section  326 . The first end section  324  is coupled to the drive unit  310 . The second end section  326  is coupled to the adjustment mechanism  200 . In other words, this means that the first end section  324  can be coupled directly to the drive unit  310  (see for example  FIG. 3 ) and that the second end section  326  can be coupled directly to the adjustment mechanism  200  (see for example  FIGS. 5A and 5B ). The second end section  326  is preferably in direct operative engagement with the adjustment ring  210 . As an alternative or in addition, the second end section  326  can be in direct operative engagement with one or a plurality of the shutter elements  220 . As an alternative to direct coupling, the first end section  324  can also be connected to the drive unit  310  via further elements (e.g.,  325 ), as explained in detail further below with reference to  FIG. 6A . The second end section  326  can likewise be connected to the adjustment mechanism  200  via further elements (e.g.,  327 ), as explained in detail further below with reference to  FIG. 4 . 
     The adjustment mechanism  200  further comprises multiple stops  116  (see  FIGS. 2A and 2B ). The stops are designed to limit a movement of the shutter elements  220  and of the adjustment ring  210  in the first position and in the second position. Accordingly, the shutter elements  220  each comprise a coupling element  222 . The adjustment ring  210  comprises corresponding shutter recesses  216 , one for each coupling element  222 . The coupling elements  222  are operatively coupled to the shutter recesses  216  so that the shutter elements  220  can be moved via the adjustment ring  210 . The stops  116  are implemented by a suitable geometric designing and dimensioning of the coupling elements  222  and of the shutter recesses  216 . For example, the shutter recesses  216  and/or the coupling elements  222  can be configured in such a way that only a maximum relative movement is possible, beyond which a type of tilting occurs that prevents any further relative movement of the shutter elements  220  relative to the adjustment ring  210 , particularly in the open position of the adjustment mechanism  200  (see  FIG. 2B ). The shutter elements  220  can be configured and/or dimensioned in such a way that they, particularly in an open position of the adjustment mechanism  200 , can touchingly contact the respective adjacent shutter elements  220 . The adjacent shutter elements  220  can come into touching contact, particularly in the circumferential direction  26 , such that any further movement is prevented (see  FIG. 5A ). A movement of the shutter elements  220  and consequently also a movement of the adjustment ring  210  in the closed position can thus be limited. This means that the stops  116  are implemented in the open position of the adjustment mechanism  200  by a corresponding geometric coordination of the coupling elements  222  and of the shutter recesses  216 , and in the closed position of the adjustment mechanism  200  by a corresponding geometric designing of the shutter elements  220  or mutually abutting edges of the shutter elements  220 . As an alternative to this, at least one (not illustrated) physical stop can be provided on the compressor housing  110 . This can be implemented in the form of, for example, a projection or a protrusion, which protrudes from the compressor housing  110 . The stop can limit a movement of the coupling unit  320  and/or a movement of the adjustment mechanism  200  in the first position and/or in the second position. In particular, the stop can limit a movement of the adjustment ring  210  and/or a movement of one or a plurality of the shutter elements  220  in the first position and/or in the second position. 
     In principle, a distinction can be made between two different designs of the coupling unit  320 . The drive unit  310  can also be configured in correspondingly different ways. One of these designs is a linearly movable coupling unit  320  (see  FIGS. 1A, 1B, 3, 4 ) and the other is a rotationally movable coupling unit  320  (see  FIGS. 5A, 5B, 6A, 6B ). This means that the drive unit  310  can be designed to move the coupling unit  320  linearly along an axis  322   a  of the oblong base body  322  between a first position and a second position. As an alternative, the drive unit  310  can be designed to move the coupling unit  320  in rotation along an axis  322   a  of the oblong base body  322  between a first position and a second position. In both embodiments, the second end section  326  engages with the adjustment mechanism  200  in such a way that, in the first position of the oblong base body  322 , the adjustment mechanism  200  is situated in its first position. The second end section  326  furthermore engages with the adjustment mechanism  200  in such a way that, in the second position of the oblong base body  322 , the adjustment mechanism  200  is situated in its second position. 
     The following embodiments relate to designs in which the coupling unit  320  is movable linearly along the axis  322   a  of the oblong base body  322 . In the design according to  FIG. 3 , the second end section  326  comprises a recess  212  and the adjustment ring  210  comprises a protrusion  214 . As an alternative, the second end section  326  can also comprise a protrusion  214  and the adjustment ring  210  a recess  212 . The recess  212  and the protrusion  214  are in operative engagement with each other. In the example shown in  FIG. 3 , the recess  212  has an extension oriented orthogonally to the axis  322   a  of the oblong base body  322  and orthogonally to the compressor axis  22 . As an alternative and if the adjustment ring  210  comprises the recess  212 , the recess  212  can extend in a radial direction  24 . A compensation of the radial offset between the coupling unit  320  and the adjustment ring  210  during the movement is thus achievable, since the coupling unit  320  is moved in a tangential direction  28  with respect to the adjustment ring  210 . The coupling unit  320 , in particular the oblong base body  322 , is thus arranged in a tangential direction  28  with respect to the adjustment mechanism  200 , particularly in a tangential direction  28  with respect to the adjustment ring  210 . More precisely, the coupling unit  320  or the oblong base body  322  is arranged in a tangential direction  28  of the compressor  100  and offset inwardly in a radial direction  24  so that it can be coupled to the adjustment ring  210 . A linear movement of the coupling unit  320  can thus be converted to a rotary movement of the adjustment ring  210 . The protrusion  214  can extend substantially in an axial direction  22  of the compressor  100 . The protrusion  214  can furthermore extend in a substantially axial direction  22  into the recess  212 . The protrusion  214  can be bolt-shaped or pin-shaped, for example. As an alternative, the recess  212  can be configured simply as a depression, e.g., as a groove. The first end section  324 , for example, can be configured as an extension of the oblong base body  322  and coupled directly to the drive unit  310  (indicated by dashed lines in  FIG. 3 ), in order to receive a linear movement or absorb linear forces. 
     As an alternative to the preceding design, the second end section  326  can comprise a three-joint mechanism  327  (see  FIG. 4 ). The three-joint mechanism  327  is operatively coupled to the adjustment ring  210  and designed to convert a linear movement of the coupling unit  320  into a rotary movement of the adjustment ring  210 . A compensation of the radial offset between the coupling unit  320  and the adjustment ring  210  during the movement is thus achievable, since the coupling unit  320  is moved tangentially with respect to the adjustment ring  210 . The compressor housing  110  comprises a drilled hole  117  (see  FIG. 7 ). The oblong base body  322  can enter the compressor housing  110  through the drilled hole  117 . A bushing, in which the oblong base body  322  is slidingly arranged, can also be arranged in the drilled hole  117  (shown only in the context of a rotationally movable coupling unit  320 ). In addition, the drilled hole  117  can be arranged in a tangential direction  28  (of the adjustment mechanism  200  or of the adjustment ring  210 ). More precisely, the drilled hole  117  is arranged in a tangential direction  28  of the compressor  100  and offset inwardly in a radial direction  24 . 
     The following embodiments relate to designs in which the coupling unit  320  is movable in rotation along the axis  322   a  of the oblong base body  322 , and in which the second end section  326  is fork-shaped (see  FIGS. 6A and 6B ) or pin-shaped (see  FIGS. 5A and 5B ). The second end section  326  projects radially away from the axis  322   a  of the oblong base body  322 . The second end section  326  is in operative engagement with a corresponding recess  212  in the adjustment ring  210 . As an alternative or in addition, the second end section  326  can be coupled to a corresponding protrusion  214  of the adjustment ring  210 . In particular, this is the case if the second end section  326  is fork-shaped (see  FIGS. 6A and 6B ). The second end section  326  can extend, in particular in an axial direction  22  of the adjustment ring  210 , into the depression  212  of the adjustment ring  210 . In particular, the second end section  326  can engage operatively, in the axial direction  22 , with the adjustment ring  210 , i.e., engage operatively with the depression  212  and/or protrusion  214  thereof. In the case of a depression  212 , the latter can have an extension in a tangential direction  28  in order to compensate for a radial offset between the coupling unit  320  and the adjustment ring  210  during the movement. As an alternative or in addition, for the same purpose the second end section  326  can be configured, at least in a region which engages with the recess, as correspondingly smaller than the recess  212 , as shown in  FIGS. 5A and 5B . As can be inferred from  FIG. 5C  in particular, the recess  212  can also have an extension in a radial direction  24  and optionally be open to the outside in a radial direction  24 . As an alternative, the recess  212  can also be configured simply as a depression, e.g., as a groove. 
     As shown in the example of  FIG. 6A , the first end section  324  can comprise a lever  324   a  and a rod  325  coupled thereto. In a manner similar to the coupling of the second end section  326  and the adjustment ring  210  from  FIG. 3 , the lever  324   a  can have a groove-like recess (not illustrated) in order to compensate for a radial offset relative to the axis  322   a  of the oblong base body  322 . The lever  324   a  projects radially away from the axis  322   a  of the oblong base body  322 . The rod  325  is coupled directly to the drive unit  310  in such a way that the rod  325  is movable linearly along its axis  325   a  by the drive unit  310 . A conversion of the linear movement of the rod  325  into a pivot movement or a rotation of the lever  324   a  about the axis  322   a  of the oblong base body  322  is possible because the rod  325  is arranged tangentially with respect to the axis  322   a  of the oblong base body  322  (and offset radially outwards from the axis  322   a  of the oblong base body  322 ). Although this example is shown only in the context of a fork-shaped second end section  326 , it is equally applicable in a design with a pin-shaped second end section  326  and should therefore not be construed as a limitation to such a design. 
     As an alternative to the preceding design, the drive unit  310  can be designed to generate a rotary movement (see  FIG. 6B ). For this purpose, the first end section  324  is coupled directly to the drive unit  310  and designed to receive a rotary movement. The first end section  324  is configured as an extension of the oblong base body  322  and is coupled directly to the rotary drive unit  310  in order to receive a rotary movement or absorb rotary forces. Although this example is shown only in the context of a fork-shaped second end section  326 , it is equally applicable in a design with a pin-shaped second end section  326  and should therefore not be construed as a limitation to such a design. 
     As illustrated by way of example in  FIG. 6B , the compressor housing  110  comprises a drilled hole  117 . The oblong base body  322  can enter the compressor housing  110  through the drilled hole  117 . A bushing  118  (not visible), in which the oblong base body  322  is rotatably mounted, is also arranged in the drilled hole  117 . The drilled hole  117  is arranged in the compressor housing  110  in a radial direction  24  of the compressor  100 . As an alternative, the drilled hole  117  can be arranged in the compressor housing  110  in an axial direction  22  of the compressor  100 . 
     The following statements again relate to both designs of the coupling unit  320 —i.e., to both linearly movable and rotationally movable coupling units  320 . 
     In the examples shown, the drive unit is configured as a pneumatic drive unit  310  (e.g.,  FIG. 1A ) or as an electric drive unit  310  (e.g.,  FIG. 6B ). As an alternative, the drive unit could also be configured as, say, a hydraulic drive unit  310 . In designs in which the drive unit  310  is pneumatic, the drive unit  310  can be fluidically coupled with a line section  318  downstream of or in the area of the compressor outlet  114 , as indicated schematically in  FIG. 1B . What is essential here is that the line section  318  is arranged or coupled in the high-pressure range of the compressor  100 . This means that the line section  318  can be arranged downstream of the compressor wheel  120 . The advantage of this is that the drive unit  310  can be controlled in a self-regulating manner directly via the high-pressure range of the compressor  100 . 
     The compressor  100  furthermore comprises a fail-safe device  312 . This fail-safe device  312  is illustrated schematically in  FIGS. 3 and 6B . The fail-safe device  312  is designed to move the adjustment mechanism  200  into a safety position and hold it therein. For example, the fail-safe device  312  can be configured to operate in the event that a (correct) functioning of the drive unit  310  is impaired or if the drive unit  310  is not working. For example, the fail-safe device  312  can be activated by an interruption of the power supply and/or of the compressed air supply and/or by an overload of the compressor  100 . The safety position can correspond to the first position of the adjustment mechanism  200  or to the second position of the adjustment mechanism. The fail-safe device  312  is preferably designed to move the adjustment mechanism  200  into the first position in which the inlet cross section  112   a  is maximal. In other words, the safety position preferably corresponds to the first position of the adjustment mechanism  200  or rather the open position of the adjustment mechanism  200 . The fail-safe device  312  can comprise, for example, a spring element, which pretensions the adjustment mechanism  200  and/or the drive unit  310  in a position. In the example of  FIG. 3 , the fail-safe device  312  is coupled to the drive unit  310 . 
     In the example of  FIG. 6B , the fail-safe device  312  is coupled to the adjustment mechanism  200  or to the adjustment ring  210 . A combined coupling to the drive unit  310  and to the adjustment mechanism  200  is also possible. If the fail-safe device  312  is coupled to the drive unit  310 , the fail-safe device  312  can be designed to move the coupling unit  320  in such a way that the coupling unit  320  in turn moves the adjustment mechanism  200  into the safety position. If the fail-safe device  312  is coupled to the adjustment mechanism  200 , the adjustment mechanism  200  can also be moved into the safety position independently of the coupling unit  320  and/or the drive unit  310  in the event of, say, a defect in the coupling unit  320 , in particular a breakage of the coupling unit  320 . 
     The drive unit  310  can be arranged directly on, in particular fastened to, the compressor housing  110 . To this end, the compressor housing  110  can be provided with a corresponding flange  119  (see  FIG. 7 ), on which the drive unit  310  can be mounted. Optionally, the flange  119  can comprise a gasket groove  119   a  with an O-ring  119   b . Leakage can thus be prevented or at least limited. 
     The actuator device furthermore comprises a (not illustrated) control unit. The control unit can be designed to control the drive unit  310  according to various operation modes of the compressor  100 . 
     The invention furthermore relates to a supercharger  10 , which comprises a drive device  410  and a shaft  420  (see  FIG. 8 ). The supercharger  10  furthermore comprises the compressor  100  described further above. The compressor  100  is coupled to the drive device  410 , for conjoint rotation therewith, via the shaft  420 . More precisely, the compressor wheel  120  of the compressor  100  is coupled to the drive unit  410  via the shaft  420 . The drive device  410  comprises a turbine. As an alternative or in addition, the drive device  410  can comprise an electric motor. Even though this is simply not illustrated in  FIG. 8 , the compressor  100  comprises the adjustment mechanism  200  and the actuator device  300 . 
     Although this invention has been described above and is defined in the appended claims, it should be understood that as an alternative, the invention can also be defined according to the following embodiments:
     1. A compressor ( 100 ) for a supercharger ( 10 ), comprising:
       a compressor housing ( 110 ) with a compressor inlet ( 112 ) and a compressor outlet ( 114 ),   an adjustment mechanism ( 200 ) having an adjustment ring ( 210 ) and multiple shutter elements ( 220 ) for changing an inlet cross section ( 112   a ) of the compressor inlet ( 112 ), and   an actuator device ( 300 ) having a drive unit ( 310 ) and a coupling unit ( 320 ), wherein the actuator device ( 300 ) is coupled, via the coupling unit ( 320 ), to the adjustment mechanism ( 200 ) in order to move the adjustment mechanism ( 200 ) between a first position and a second position.   
       2. The compressor ( 100 ) according to Embodiment 1, wherein the coupling unit ( 320 ) comprises an oblong base body ( 322 ) with a first end section ( 324 ) and a second end section ( 326 ), wherein the first end section ( 324 ) is coupled to the drive unit ( 310 ) and the second end section ( 326 ) is coupled to the adjustment mechanism ( 200 ).   3. The compressor ( 100 ) according to Embodiment 2, wherein the drive unit ( 310 ) is designed to move the coupling unit ( 320 ) linearly along an axis ( 322   a ) of the oblong base body ( 322 ) between a first position and a second position.   4. The compressor ( 100 ) according to Embodiment 2, wherein the drive unit ( 310 ) is designed to move the coupling unit ( 320 ) rotationally along an axis ( 322   a ) of the oblong base body ( 322 ) between a first position and a second position.   5. The compressor ( 100 ) according to either one of Embodiments 3 or 4, wherein the second end section ( 326 ) engages with the adjustment mechanism ( 200 ) in such a way that the adjustment mechanism ( 200 ) is in its first position in the first position of the oblong base body ( 322 ) and that the adjustment mechanism ( 200 ) is in its second position in the second position of the oblong base body ( 322 ).   6. The compressor ( 100 ) according to any one of Embodiments 2 to 5, wherein at least one stop ( 116 ) is provided on the compressor housing ( 110 ), which limits a movement of the coupling unit ( 320 ) and/or a movement of the adjustment mechanism ( 200 ), in particular a movement of the adjustment ring ( 210 ), in the first position and/or in the second position.   7. The compressor ( 100 ) according to any one of Embodiments 1 to 5, wherein the adjustment mechanism ( 200 ) comprises at least one stop ( 116 ), which limits a movement of the shutter elements ( 220 ) and/or of the adjustment ring ( 210 ) in the first position and/or in the second position.   8. The compressor ( 100 ) according to any one of the preceding embodiments, wherein the first position corresponds to an open position of the adjustment mechanism ( 200 ) in which the inlet cross section ( 112   a ) is maximal and wherein the second position corresponds to a closed position of the adjustment mechanism ( 200 ) in which the inlet cross section ( 112   a ) is reduced.   9. The compressor ( 100 ) according to any one of the preceding embodiments, wherein the drive unit ( 310 ) is a pneumatic, a hydraulic or an electric drive unit ( 310 ) and optionally, if the drive unit ( 310 ) is pneumatic, wherein the drive unit ( 310 ) is fluidically coupled to a line section ( 318 ) downstream of the compressor outlet ( 314 ).   10. The compressor ( 100 ) according to any one of the preceding embodiments, further comprising a fail-safe device ( 312 ) which is designed to move the adjustment mechanism ( 200 ) into a safety position and hold it therein.   11. The compressor ( 100 ) according to Embodiment 10, wherein the safety position corresponds to the first position of the adjustment mechanism ( 200 ) or to the second position of the adjustment mechanism ( 200 ).   12. The compressor ( 100 ) according to either one of Embodiments 10 or 11, wherein the fail-safe device ( 312 ) is coupled to the drive unit ( 310 ) and/or to the adjustment mechanism ( 200 ), in particular to the adjustment ring ( 210 ).   13. The compressor ( 100 ) according to any one of the preceding embodiments if dependent on Embodiment 2, wherein the second end section ( 326 ) is in direct operative engagement with the adjustment ring ( 210 ) or in direct operative engagement with one of the shutter elements ( 220 ).   14. The compressor ( 100 ) according to any one of the preceding embodiments if dependent on Embodiment 3, wherein the second end section ( 326 ) comprises one of a recess ( 212 ) or a protrusion ( 214 ) and the adjustment ring ( 210 ) comprises the other of the recess ( 212 ) or protrusion ( 214 ), wherein the recess and the protrusion are in operative engagement with each other.   15. The compressor ( 100 ) according to Embodiment 14, wherein the recess ( 212 ) extends orthogonally to the axis ( 322   a ) of the oblong base body and orthogonally to the compressor axis ( 22 ) if the second end section ( 326 ) comprises the recess ( 212 ), or the recess extends in a radial direction ( 24 ) if the adjustment ring ( 210 ) comprises the recess ( 212 ).   16. The compressor ( 100 ) according to any one of the preceding embodiments if dependent on Embodiment 3, wherein the second end section ( 326 ) comprises a three-joint mechanism ( 327 ), which is operatively coupled to the adjustment ring ( 210 ) and designed to convert a linear movement of the coupling unit ( 320 ) into a rotary movement of the adjustment ring ( 210 ).   17. The compressor ( 100 ) according to any one of the preceding embodiments if dependent on Embodiment 3, wherein the compressor housing ( 110 ) comprises a drilled hole ( 117 ) through which the oblong base body ( 322 ) enters the compressor housing ( 110 ), and optionally wherein a bushing ( 118 ), in which the oblong base body slides ( 322 ), is arranged in the drilled hole ( 117 ).   18. The compressor ( 100 ) according to Embodiment 17, wherein the drilled hole ( 117 ) is arranged in a tangential direction ( 28 ).   19. The compressor ( 100 ) according to any one of the preceding embodiments if dependent on Embodiment 4, wherein the second end section ( 326 ) is fork-shaped or pin-shaped and projects radially away from the axis ( 322   a ) of the oblong base body ( 322 ), and wherein the second end section ( 326 ) operatively engages with a corresponding recess ( 212 ) in the adjustment ring ( 210 ) or with a corresponding protrusion ( 214 ) of the adjustment ring ( 210 ).   20. The compressor ( 100 ) according to any one of the preceding embodiments if dependent on Embodiment 4, wherein the first end section ( 324 ) comprises a lever ( 324   a ) and a rod ( 325 ) coupled thereto, wherein the lever ( 324   a ) projects radially away from the axis ( 322   a ) of the oblong base body ( 322 ) and wherein the rod ( 325 ) is coupled directly to the drive unit ( 310 ) in such a way that the rod ( 325 ) is moved linearly along its axis ( 325   a ) by the drive unit ( 310 ).   21. The compressor ( 100 ) according to any one of Embodiments 1 to 18 if dependent on Embodiment 4, wherein the drive unit ( 310 ) is designed to generate a rotary movement and wherein the first end section ( 324 ) is coupled directly to the drive unit ( 310 ) and is designed to receive a rotary movement.   22. The compressor ( 100 ) according to any one of the preceding embodiments if dependent on Embodiment 4, wherein the compressor housing ( 110 ) comprises a drilled hole ( 117 ) through which the oblong base body ( 312 ) enters the compressor housing ( 110 ), and optionally wherein a bushing ( 118 ), in which the oblong base body ( 312 ) is rotatably mounted, is arranged in the drilled hole ( 117 ).   23. The compressor ( 100 ) according to Embodiment 22, wherein the drilled hole ( 117 ) is arranged in a radial direction ( 24 ) or in an axial direction ( 22 ).   24. The compressor ( 100 ) according to any one of the preceding embodiments, wherein the drive unit ( 310 ) is arranged directly on, in particular fastened to, the compressor housing ( 110 ).   25. The compressor ( 100 ) according to any one of the preceding embodiments, wherein the actuator device ( 300 ) furthermore comprises a control unit ( 330 ), which controls the drive unit ( 310 ) in accordance with various operating modes of the compressor ( 300 ).   26. A supercharger ( 10 ) comprising:   a drive device ( 410 ) and a compressor ( 100 ) according to any one of the preceding embodiments, wherein the compressor ( 100 ) is coupled via a shaft ( 420 ) to the drive device ( 410 ) for conjoint rotation therewith.   27. The supercharger ( 10 ) according to Embodiment 26, wherein the drive device ( 410 ) comprises a turbine and/or an electric motor.