EP3734081A1 - Dispositif de modification de flux pour compresseurs - Google Patents

Dispositif de modification de flux pour compresseurs Download PDF

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Publication number
EP3734081A1
EP3734081A1 EP19171814.7A EP19171814A EP3734081A1 EP 3734081 A1 EP3734081 A1 EP 3734081A1 EP 19171814 A EP19171814 A EP 19171814A EP 3734081 A1 EP3734081 A1 EP 3734081A1
Authority
EP
European Patent Office
Prior art keywords
compressor
pocket
section
point
projection line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP19171814.7A
Other languages
German (de)
English (en)
Inventor
Tom Heuer
Sascha KARSTADT
Thomas Lischer
Johannes Buehler
Sebastian LEICHTFUSS
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BorgWarner Inc
Original Assignee
BorgWarner Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BorgWarner Inc filed Critical BorgWarner Inc
Priority to EP19171814.7A priority Critical patent/EP3734081A1/fr
Priority to CN201920776930.4U priority patent/CN210509688U/zh
Priority to CN201910448323.XA priority patent/CN111852930A/zh
Priority to US16/862,802 priority patent/US20200347850A1/en
Publication of EP3734081A1 publication Critical patent/EP3734081A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/685—Inducing localised fluid recirculation in the stator-rotor interface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/003—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by throttling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
    • F02B37/225—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits air passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • F02B39/16—Other safety measures for, or other control of, pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0253—Surge control by throttling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer

Definitions

  • the present invention relates to a flow modifying device for a compressor of a supercharging device.
  • the invention also relates to a compressor and a charging device with such a flow modifying device.
  • Known charging devices usually have at least one compressor with a compressor wheel which is connected to a drive unit via a common shaft.
  • the compressor compresses the fresh air drawn in for the internal combustion engine or for the fuel cell. This increases the amount of air or oxygen available to the engine for combustion and the fuel cell to react. This in turn leads to an increase in the performance of the internal combustion engine or the fuel cell.
  • Charging devices can be equipped with different drive units.
  • e-chargers in which the compressor is driven by an electric motor
  • exhaust gas turbochargers in which the compressor is driven by an exhaust gas turbine, are known in particular. Combinations of both systems are also described in the prior art.
  • Each compressor has a compressor-specific compressor map, the operation of the compressor being limited to the area of the compressor map between the surge limit and the stuffing limit.
  • the compressor map the volume flow achieved on the abscissa axis is compared with the pressure ratio between the compressor inlet and outlet on the ordinate axis. Furthermore, curves are plotted for different speeds up to the maximum permissible speed between the surge limit and the stuffing limit.
  • operation at low volume flows through the compressor can be inefficient or no longer reliable because the surge limit is reached. This means that the surge limit limits the compressor map to the left, the stuffing limit to the right
  • the object of the present invention is to provide an improved flow modifying device for stabilizing the characteristic map or a compressor with an improved compressor characteristic map.
  • the present invention relates to a flow modifying device for a compressor of a charging device according to claim 1. Furthermore, the invention relates to a compressor having a charging device with such a flow modifying device according to claim 10 or 15.
  • the flow modifier for a compressor of a supercharger comprises a cylindrical housing portion and a plurality of pockets.
  • the cylindrical housing section defines an inner jacket surface. Furthermore, the cylindrical housing section comprises an end region which is downstream in the axial direction and an end region which is upstream in the axial direction. The upstream end area is arranged opposite the downstream end area in the axial direction.
  • the pockets are arranged spaced apart in the circumferential direction on the inner lateral surface. There each pocket is defined by a longitudinal projection line and a depth projection line. In an orientation plane which is formed by the longitudinal projection line and the depth projection line, a downstream opening area of the pocket is defined by a downstream entry angle ⁇ of the pocket relative to the inner surface of the jacket.
  • an upstream opening area of the pocket is defined by an upstream entry angle ⁇ of the pocket relative to the inner surface of the jacket.
  • the pockets are designed in such a way that: ⁇ ⁇ 90 ° ⁇ .
  • This special configuration of the pocket allows fluids to flow more easily into the pocket via the downstream opening region to the upstream opening region, in which the fluids can be guided again through the upstream entry angle ⁇ in the direction of the downstream end region.
  • Such a configuration of the flow modifying device can, if it is used in a compressor, achieve a significant improvement in the stability of the characteristic field. In particular, both the lower and the upper map range can be stabilized.
  • the pocket can be designed in such a way that: ⁇ ⁇ 180 ° - ⁇ . This configuration makes it possible to provide a steeper return flow from the pocket in the direction of the downstream end region.
  • the pocket can be designed such that 10 ° ⁇ ⁇ 30 °, preferably 15 ° ⁇ ⁇ 20 ° and particularly preferably 17 ° ⁇ 19 °.
  • the pocket can be designed such that 120 ° ⁇ ⁇ 165 °, preferably 130 ° ⁇ ⁇ 150 ° and particularly preferably 135 ° ⁇ 145 °.
  • the depth projection line can be inclined relative to the radial direction by an angle of incidence ⁇ .
  • the pocket can be designed such that 0 ° ⁇ ⁇ 60 °, preferably 15 ° ⁇ ⁇ 50 ° and particularly preferably 35 ° ⁇ 45 °.
  • the angle of incidence ⁇ can be inclined in a direction of rotation of a compressor wheel from the radial direction. This advantageous embodiment leads to an improved flow of fluid into the pocket. This in turn allows a larger volume flow to be recirculated through the pocket back in the direction of the downstream end region. When using the flow modifying device in a compressor, a larger volume flow can thus be directed back to the compressor wheel, whereby the efficiency can be increased again.
  • a width of the pocket orthogonal to the orientation plane can be 1mm x F D to 6mm x F D , preferably 2mm x F D to 5mm x F D and particularly preferably 3mm x F D to 4mm x F D.
  • F D D / D Ref , where D Ref is preferably 60 mm and D corresponds to an outlet diameter of a compressor wheel of the compressor for which the flow modifying device is designed.
  • D Ref is preferably 60 mm and D corresponds to an outlet diameter of a compressor wheel of the compressor for which the flow modifying device is designed.
  • the dimensions of the pocket, in particular the width of the pocket are configured as a function of the dimensions of the compressor wheel for the operation of which the flow modifying device is designed or with which it is used.
  • a length of the pocket along the longitudinal projection line can be 5mm x F D to 30mm x F D , preferably 10mm x F D to 25mm x F D and particularly preferably 15mm x F D up to 20mm x F D.
  • F D D / D Ref , where D Ref is preferably 60 mm and D corresponds to an outlet diameter of a compressor wheel of the compressor for which the flow modifying device is designed.
  • D Ref is preferably 60 mm and D corresponds to an outlet diameter of a compressor wheel of the compressor for which the flow modifying device is designed.
  • a depth of the pocket along the depth projection line can be 5mm x F D to 30mm x F D , preferably 10mm x F D to 25mm x F D and particularly preferably 15mm x F D to 20mm x F D.
  • F D D / D Ref , where D Ref is preferably 60 mm and D corresponds to an outlet diameter of a compressor wheel of the compressor for which the flow modifying device is designed.
  • D Ref is preferably 60 mm and D corresponds to an outlet diameter of a compressor wheel of the compressor for which the flow modifying device is designed.
  • the longitudinal projection line can be inclined relative to the axial direction by a tilt angle ⁇ .
  • the pocket can be designed such that 0 ° ⁇ ⁇ 60 °, preferably 5 ° ⁇ ⁇ 45 ° and particularly preferably 10 ° ⁇ 30 °.
  • the pocket can comprise an opening with an opening area.
  • the opening can comprise an opening length.
  • the aperture length can extend along the longitudinal projection line and 2mm x 25mm x F D to F D, preferably 5mm x F D F D up to 20mm x 10mm, and more preferably x F D to 15mm x F D.
  • the following applies to the factor F D D / D Ref , where D Ref is preferably 60 mm and D corresponds to an outlet diameter of a compressor wheel of the compressor for which the flow modifying device is designed.
  • the dimensions of the pocket are configured as a function of the dimensions of the compressor wheel for whose operation the flow modifying device is designed or with which it is used together.
  • the longitudinal projection line can lie in a plane that is defined by the opening area.
  • the longitudinal projection line can run centrally through the pocket in the circumferential direction.
  • the longitudinal projection line can run centrally through the pocket in the circumferential direction, between the downstream opening area and the upstream opening area.
  • this means that the longitudinal projection line is a kind of center line in the longitudinal orientation of the pocket.
  • the term "center” is to be understood here as a center seen in the circumferential direction.
  • the course of the longitudinal projection line is along the longitudinal extent of the pocket. In other words, the longitudinal projection line runs from the downstream end area to the upstream end area.
  • the longitudinal projection line also runs partly on the inner lateral surface.
  • the depth projection line can run centrally through the pocket in the circumferential direction.
  • the term "center” is to be understood here as a center seen in the circumferential direction.
  • the pocket can comprise a length, an opening with an opening length and a depth.
  • a contour of the pocket can be defined by an entry point at which the downstream entry angle ⁇ is present, by an exit point at which the upstream entry angle ⁇ is present and by a changeover point between the entry point and the exit point will.
  • the contour can lie in the orientation plane. This means that the contour is a kind of contour line of the pocket in a section in the orientation plane.
  • the entry point can be determined by a downstream intersection between the longitudinal projection line and an opening contour of the opening.
  • the exit point can be determined by an upstream point of intersection between the longitudinal projection line and the opening contour.
  • the change point can represent the lowest point of the contour relative to the longitudinal projection line. That means the change point can be seen as the lowest point of the contour. That is, a point in the depth of the pocket at the intersection with the depth projection line.
  • a first contour section with a variable angle ⁇ ' can be formed between the entry point and the changeover point.
  • the variable angles ⁇ 'and ⁇ ' can be seen relative to the inner surface of the jacket. This means that the variable angles ⁇ 'and ⁇ ' are to be seen analogously to the downstream entry angle ⁇ and to the upstream entry angle ⁇ .
  • the variable angles ⁇ 'and ⁇ ' can also be seen relative to a parallel line of the longitudinal projection line in the depth of the pocket according to the Z-angle analogy.
  • the course of the first contour section can be defined as differentiable, wherein alternatively or additionally, the variable angle ⁇ 'is at least not smaller in the course from the entry point to the change point.
  • the course of the second contour section can be defined as differentiable, alternatively or additionally, the variable angle ⁇ 'in the course from the change point to the exit point at least not increasing.
  • the contour between the change point and the exit point can have a reversal point.
  • the second contour section can have a reversal point.
  • the reversal point can be arranged between the change point and the exit point.
  • the reversal point can define a maximum length of the pocket.
  • the pockets can be arranged equidistantly in the circumferential direction.
  • the pockets can also be arranged unevenly distributed in the circumferential direction.
  • one or more of the pockets can also be designed differently from the other pockets.
  • one or more of the dimensions of one or more pockets that is to say a width and / or a length and / or a depth and / or an opening with an opening length different from one or more of the dimensions of the other pockets.
  • the flow modifying device can also have different numbers of pockets.
  • the invention also relates to a compressor for a charging device.
  • the compressor comprises a compressor housing, a compressor wheel and a flow modifying device according to any one of the preceding embodiments.
  • the compressor housing defines a compressor inlet with an inlet cross-section and a compressor outlet.
  • the compressor wheel is rotatably arranged in the compressor housing between the compressor inlet and the compressor outlet.
  • the special design of the flow modifying device with the pockets enables a noticeable shift of the operating points near the surge limit towards lower throughputs (or higher pressure with the same throughput). As a result, an earlier and higher torque can be provided on the internal combustion engine.
  • the flow modifying device can be incorporated into existing parts as a retrofit measure by means of machining. This means that different customer applications can be covered with identical raw parts. This results in manufacturing and financial advantages through a high degree of equality of parts.
  • the compressor can furthermore comprise an adjustment mechanism with a plurality of diaphragm elements for changing the inlet cross-section.
  • the adjustment mechanism can be actuated between a first, open position and a second, closed position. In the first position, the inlet cross-section is unchanged. In the second position, however, the inlet cross-section is reduced.
  • the compressor characteristic map can be optimized by the adjustment mechanism by moving the adjustment mechanism into the second position.
  • the cylindrical housing section can be arranged downstream of the screen elements.
  • the cylindrical housing section can be configured as a bearing ring for the diaphragm elements. In this way, a separate prefabricated module can be provided for insertion into the compressor. Furthermore, the compressor or the combination of adjusting mechanism and flow modifying device can thereby be made more compact.
  • the cylindrical housing section can be manufactured integrally with the compressor housing.
  • the cylindrical housing section can be manufactured as a separate component. If the cylindrical housing section is manufactured as a separate component, the cylindrical housing section can be inserted into the compressor housing from the compressor inlet in the axial direction to the compressor outlet or from the compressor outlet in the axial direction to the compressor inlet, i.e. in the opposite direction.
  • a compressor contour can be formed by the cylindrical housing section.
  • this compressor contour is formed on the separate cylindrical housing section, the geometry / surface of the compressor contour is more flexible and more easily accessible for precise machining.
  • the flow modifying device can be integrated into existing compressor geometries. Is the cylindrical housing section is designed as a separate component, compressor housings of the same type can optionally be used for different compressor applications, into which differently configured flow modifying devices can be inserted.
  • the cylindrical housing section can be constructed in several parts.
  • the cylindrical housing section can comprise several subdivision sections in the circumferential direction.
  • the cylindrical housing section can comprise a plurality of subdivision sections in the axial direction.
  • the cylindrical housing section can consist of a first subdivision section in the axial direction and a second subdivision section in the axial direction.
  • the first and the second subdivision section are designed in particular ring-shaped.
  • the first and second dividing sections can separate the pockets at their lowest point. In other words, this means that the first and the second dividing section divide the pockets at the change point.
  • one of the first and second partition portions may be made integral with the compressor housing.
  • the other of the first or the second subdivision section can be inserted into the compressor housing from the compressor inlet in the axial direction to the compressor outlet or from the compressor outlet in the axial direction to the compressor inlet.
  • a compressor contour can be formed by the cylindrical housing section. Because this compressor contour is formed on the separate cylindrical housing section, the geometry / surface of the compressor contour is more flexible and more easily accessible for precise machining.
  • the cylindrical housing section if it is designed as a separate part, can be connected to the compressor housing by a press fit, a snap-fit connection, a screw connection or another suitable coupling technology. This also applies analogously to configurations in which individual or all subdivision sections (if present) and not the entire housing section are manufactured separately.
  • the cylindrical housing section in configurations of the compressor that can be combined with any of the preceding configurations, can be made of plastic.
  • the cylindrical housing section can have an oversize in the direction of the compressor wheel, which can be reduced, in particular grinded, by the compressor wheel during operation of the compressor.
  • a contour area of the compressor ie the already mentioned compressor contour when the housing section is inserted from the compressor outlet in the axial direction to the compressor inlet, can be oversized and can be ground in by the compressor wheel. This advantageously results in a reduced necessary manufacturing tolerance. This in turn can reduce manufacturing costs and simplify the entire manufacturing process.
  • the compressor wheel can comprise a plurality of blades distributed in the circumferential direction.
  • Each blade has a leading edge, a side edge, a trailing edge, a front side and a rear side.
  • the pockets can be arranged in the axial direction in such a way that the opening of a respective pocket is located both upstream and downstream of a corner at which the leading edge and the side edge converge.
  • the pockets can be arranged in the axial direction in such a way that a center of the opening, which lies at half the opening length, is located approximately at the corner. Other arrangements are also possible in alternative configurations.
  • a ratio between a downstream opening length that is arranged downstream of the corner to an upstream opening length that is arranged upstream of the corner can also be greater or less than 1.
  • the angle of incidence ⁇ can be angled in a direction of rotation ⁇ of the compressor wheel from the radial direction. This advantageous embodiment leads to an improved flow of fluid into the pocket. As a result, a larger volume flow can in turn be directed or recirculated through the pocket back in the direction of the downstream end area, that is to say back to the compressor wheel, which in turn can increase efficiency.
  • the invention also relates to a charging device.
  • the charging device comprises a compressor and a compressor according to any one of the preceding embodiments.
  • the charging device furthermore comprises a shaft via which the compressor and the drive unit are coupled to one another in a rotationally fixed manner.
  • the drive device can comprise a turbine and / or an electric motor.
  • the invention further comprises a manufacturing method of a compressor according to any one of the preceding configurations.
  • the pockets are produced in the housing section by a milling process, an erosion process, a casting process or a combination of several manufacturing processes. It is particularly preferred to provide a plurality of basic shapes for the respective pockets in the cylindrical housing section by a casting process and the subsequent milling out of the pockets.
  • the terms axial and axial direction relate to an axis of the flow modifying device, that is to say to a cylinder axis of the cylindrical housing section or to an axis of rotation of the compressor or of the compressor wheel.
  • the axial direction of the flow modifying device or compressor is shown with the reference number 22.
  • a radial direction 24 relates to the axis 22 of the flow modifying device or of the compressor.
  • a circumference or a circumferential direction 26 relates to the axis 22 of the flow modifying device or of the compressor.
  • downstream refers to a substantially axial direction 22 from one end region of the flow modifying device (more precisely: upstream end region) to another end region of the flow modifying device (more precisely: downstream end region).
  • upstream refers to a direction substantially opposite to the downstream direction.
  • downstream and upstream are to be regarded analogously, that is to say as essentially axial directions (22) which, starting from the compressor inlet, are directed towards or away from a compressor wheel of the compressor.
  • FIGS. 1A and 1B show the flow modifying device 10 according to the invention for a compressor 100 of a charging device 400.
  • the flow modifying device 10 comprises a cylindrical housing section 150 and a plurality of pockets 200, which in the sectional view of FIG FIG. 1A is easy to see.
  • the cylindrical housing section 150 defines an inner jacket surface 152 and an outer jacket surface 158.
  • the cylindrical housing section 150 comprises an end region 154 downstream in the axial direction 22 and an end region 156 upstream in the axial direction 22.
  • the upstream end region 156 is the downstream end region 154 in the axial direction 22 arranged opposite one another.
  • the downstream end region 154 terminates in the axial direction 22 with a downstream end face 153.
  • the upstream end region 156 terminates in the axial direction 22 with an upstream end face 155.
  • the pockets 200 are arranged spaced apart in the circumferential direction 26 on the inner lateral surface 152.
  • FIG. 1B shows how the pockets 200 along the section BB from FIG. 1A are arranged on the inner lateral surface 152.
  • a respective opening 210 of a pocket 200 and the corresponding opening contour 210a can be seen. Shown in dashed lines and following the opening contour 210a of a respective pocket 200 is the course of the respective pocket 200, which is created because the respective pocket 200 has a special geometry and is oriented in a special orientation relative to the cylindrical housing section 150 or its inner lateral surface 152 is (see for example FIG. 1A ).
  • a respective longitudinal projection line 202 and a respective depth projection line 204 can be introduced for a pocket 200 (see FIGS. 2A-2C ).
  • the pocket geometry is explained below using a pocket 200 as an example. However, this should be understood analogously for all pockets 200.
  • FIG. 2A a section through the pocket 200 in an orientation plane 203 which is formed by the longitudinal projection line 202 and the depth projection line 204.
  • FIG. 2A while the section X from the FIG. 1A corresponds. That is, the section BB runs exactly along the orientation plane 203 of the pocket 200 from the section X.
  • the pocket 200 has a downstream opening area 214 and an upstream opening area 216.
  • the downstream opening area 214 is thereby through a downstream Entry angle ⁇ of pocket 200 is defined relative to inner surface 152.
  • the upstream opening region 216 is defined by an upstream entry angle ⁇ of the pocket 200 relative to the lateral inner surface 152.
  • "Relative to the inner jacket surface 152" is to be understood here relative to the solid material of the inner jacket surface 152.
  • Both the downstream entry angle ⁇ and the upstream entry angle ⁇ lie in the orientation plane 203 (see FIG FIG. 2A ).
  • the pocket 200 is designed in such a way that the following applies: ⁇ ⁇ 90 ° ⁇ .
  • This special configuration of the pocket 200 allows fluids, in particular backflowing fluids, to flow in a simplified manner into the pocket 200 via the downstream opening area 214 to the upstream opening area 216, in which the fluids can be guided again through the upstream entry angle ⁇ in the direction of the downstream end area 154 .
  • Such a configuration of the flow modifying device 10 can, if it is used in a compressor 300, achieve a significant improvement in the stability of the characteristics map. In particular, both the lower and the upper map range can be stabilized. Compared to a "ported shroud" known from the prior art, the effectiveness of even lower pressure ratios can be seen.
  • the special design of the flow modifying device 10 with the pockets 200 enables a noticeable shift of the operating points near the surge limit towards smaller throughputs (or higher pressure with the same throughput). As a result, an earlier and higher torque can be provided on the internal combustion engine. Furthermore, there are manufacturing advantages, for example compared to a "ported shroud", in which additional parts, for example a core for the recirculation cavity, are necessary, which, however, can be saved in the present flow modifying device 10 through the special design with pockets 200.
  • the longitudinal projection line 202 runs centrally through the pocket 200 in the circumferential direction 26.
  • This means that the longitudinal projection line 202 is to be understood as a kind of center line in the longitudinal orientation of the pocket 200.
  • the term “center” is to be understood here as a center seen in the circumferential direction 26.
  • the FIGS. 1A, 1B , 2B and 2C a first side wall 232 and a second side wall 234 that each pocket 200 has.
  • the side walls 232, 234 are attached to the pockets 200 from the outside, although they are formed from the inside of the pockets 200 towards the cylindrical housing section 150.
  • the longitudinal projection line 202 extends centrally between the first side wall 232 and the second side wall 234.
  • the course of the longitudinal projection line 202 is along the longitudinal extent of the pocket 200.
  • the longitudinal projection line 202 is from the downstream one End region 154 oriented towards the upstream end region 156.
  • ⁇ 0 °.
  • the longitudinal projection line 202 runs in a plane of the inner lateral surface 152. This is shown in particular in FIGS FIGS.
  • the opening 210 has an opening area 211.
  • This opening area 211 is delimited by the opening contour 210a.
  • the opening surface 211 lies in the same plane, in particular in a curved plane, as the inner lateral surface 152 (indicated in FIG FIG. 2 B ). This means that the opening area 211 lies on a lateral plane of the inner lateral surface. That is to say, the opening area 211 has a curvature or bulge.
  • the longitudinal projection line 202 this means that it lies in the right part of the illustrated pocket 200 on the opening surface 211.
  • the longitudinal projection line 202 lies in a plane which is defined by the opening area 211. In the left part of the illustrated pocket 200, the longitudinal projection line 202 also runs at least partially directly on the lateral inner surface 152.
  • the depth projection line 204 which also runs centrally through the pocket 200 in the circumferential direction 26, can be seen analogously. This means that the depth projection line 204 is a kind of center line in the depth orientation of the pocket 200.
  • a depth orientation can be understood here as an orientation of the pocket 200 which, starting from the opening 210, is centered between the side walls 232, 234, starting from the inner lateral surface 152, into the Material of the cylindrical housing section 150 extends to the lowest point of the pocket 200 (see FIGS. 2A and 2C ).
  • center is to be understood here as a center seen in the circumferential direction 26.
  • the longitudinal projection line 202 and the depth projection line 204 are to be understood as relative orientation lines of the pocket 200, which each run centrally between the side walls 232, 234 of the pocket 200.
  • the longitudinal projection line 202 and the depth projection line 204 are shown as dash-dot-lined straight lines in the respective views of the figures.
  • FIG. 1A and the FIG.1B referenced in which by way of example for a pocket 200, the depth projection line 204 or the longitudinal projection line 202 are shown (see pocket 200 on the far right in section BB).
  • the pocket 200 is designed such that the following applies: ⁇ ⁇ 180 ° - ⁇ .
  • This configuration makes it possible to provide a steeper return flow from the pocket 200 in the direction of the downstream end region 154.
  • the latter configuration can lead to simplifications in terms of manufacturing technology, since the undercut at the upstream entry angle ⁇ , that is to say at the upstream opening region 216, may be easier to manufacture.
  • the pocket 200 is formed with an upstream entry angle ⁇ of approximately 17 ° ⁇ 19 °, and with a downstream entry angle ⁇ of approximately 135 ° ⁇ 145 °. That is, the upstream entry angle ⁇ or the downstream entry angle ⁇ is an exact value from the respective interval. In principle, however, other values can also be selected for the entry angles ⁇ and ⁇ in alternative designs.
  • the upstream entry angle ⁇ can also assume a value in the range of 10 ° ⁇ ⁇ 30 °, preferably in the range of 15 ° ⁇ ⁇ 20 °.
  • the downstream entry angle ⁇ can also assume a value in the range of 120 ° ⁇ ⁇ 165 °, preferably in the range of 130 ° ⁇ ⁇ 150 °.
  • depth projection line 204 is inclined relative to the radial direction 24 by an angle of incidence ⁇ .
  • a value of 35 ° ⁇ ⁇ 45 ° particularly preferably applies to this angle of incidence ⁇ .
  • the pocket can also be designed so that 0 ° ⁇ ⁇ 60 ° and preferably 15 ° ⁇ ⁇ 50 ° applies to the angle of incidence ⁇ .
  • the angle of incidence ⁇ can be inclined in particular in a direction of rotation ⁇ of a compressor wheel 320 from the radial direction 24.
  • a direction of rotation ⁇ in the is exemplary FIGS. 1A and 3A shown.
  • This advantageous embodiment leads to an improved flow of fluid into the pocket 200. This in turn allows a larger volume flow to be recirculated through the pocket 200 back in the direction of the downstream end region 154.
  • a larger volume flow can thus be directed back to the compressor wheel 320, whereby the efficiency can be increased again.
  • FIG. 3B Only in the FIG. 3B a further design option of the flow modifying device 10 is indicated schematically, which can be implemented in addition or as an alternative to one, more or all of the design options.
  • An exemplary pocket 200 is shown here relative to the axial direction 22. It can be seen here that the longitudinal projection line 202 can be inclined relative to the axial direction 22 by a tilt angle ⁇ .
  • This tilt angle ⁇ can assume a value from 0 ° ⁇ ⁇ 60 °, preferably 5 ° ⁇ ⁇ 45 ° and particularly preferably 10 ° 30 °.
  • the longitudinal projection line 202 is inclined from the axial direction 22 by the tilt angle ⁇ in such a way that the upstream opening area 216 is inclined from the axial direction 22 counter to a direction of rotation ⁇ of a compressor wheel 320.
  • This has the particular advantage that the fluids flowing out of the pocket 200 experience a movement component in the circumferential direction 26. In this way, a flow onto a compressor wheel 320 can be improved.
  • FIGS. 2A-2C further dimensions of the pocket 200 are explained. These include, for example, a width 207 of the pocket 200, a length 208 of the pocket 200, a depth 209 of the pocket 200 and an opening length 212 of the already mentioned opening 210 of the pocket 200. These dimensions are given in a factorized manner to allow for a corresponding variance for different compressor applications to cover different sizes.
  • D Ref corresponds to a reference outlet diameter of a compressor wheel 320 and is preferably 60 mm.
  • D corresponds to an outlet diameter of a compressor wheel 320 of the compressor 300 of the present application.
  • D corresponds to an outlet diameter of a compressor wheel 320 of the compressor 300 for which the Flow modifying device 10 is designed.
  • the width of the pocket 200 a value between 1 mm x F D and 6mm x F D, preferably a value between 2 mm x F D and 5mm x F D, and more preferably a value between 3mm x F D and 4mm x F D at.
  • the width 207 can be seen orthogonally to the orientation plane 203.
  • the width 207 is to be seen as the distance between the side walls 232, 234 (see FIG. 2B and 2C ).
  • the length 208 of the pocket 200 takes a value between 5mm x F D and 30mm x F D , preferably a value between 10mm x F D and 25mm x F D and particularly preferably a value between 15mm x F D and 20mm x F D at.
  • the length 208 runs along the longitudinal projection line 202. That is, the length 208 runs in the orientation plane 203. In other words, the length 208 corresponds to a maximum extent of the pocket 200 in the orientation plane 203 along the longitudinal projection line 202 (see FIG FIG. 2A and 2B ).
  • the 209 concrete increases the depth of the pocket 200 a value between 5mm x F D and 30mm x F D, preferably a value between 10mm x F D and 25mm x F D, and more preferably a value between 15mm x F D and 20mm x F D at.
  • the depth 209 runs along the depth projection line 204. That is, the depth 209 runs in the orientation plane 203. In other words, the depth 209 corresponds to a maximum extent of the pocket 200 starting from the inner lateral surface 152 or from the opening surface 211 along the Depth projection lines 204 in the material of the cylindrical housing section 150 down to the deepest point of the pocket 200 (see FIG. 2A and 2C ).
  • the opening length 212 of the pocket 200 takes a value between 2mm x F D and 25mm x F D , preferably a value between 5mm x F D and 20mm x F D and particularly preferably a value between 10mm x F D and 15mm x F D at.
  • the opening length 212 runs along the longitudinal projection line 202. That is, the opening length 212 runs in the orientation plane 203.
  • the opening length 212 in the downstream opening area 214 and in the upstream opening area 216 are each limited by the opening contour 210a (see FIG. 2A and 2B ).
  • the pocket 200 can be defined more precisely by a contour 220 which lies in the orientation plane 203. That is, the contour 220 is a type of contour line of the pocket 200 in a section in the orientation plane 203.
  • the contour 220 has an entry point 222 at which the downstream entry angle ⁇ is present, an exit point 228 at which the upstream entry angle ⁇ is present and a change point 224, which lies between the entry point 222 and the exit point 228.
  • the entry point 222 is determined by a downstream intersection between the longitudinal projection line 202 and the opening contour 210a (see FIG FIG. 2 B ).
  • the exit point 228 is determined by an upstream point of intersection between the longitudinal projection line 202 and the opening contour 210a (see FIG FIG. 2 B ).
  • the change point 224 represents the lowest point of the contour 220 relative to the longitudinal projection line 202. That is, the change point 224 can be viewed as the lowest point of the contour 220. In other words, the change point 224 can be an intersection of the depth projection line 204 with the pocket 200 at the depth 209.
  • variable angles ⁇ 'and ⁇ ' can be seen relative to the inner surface 152. This means that the variable angles ⁇ 'and ⁇ ' are to be seen analogously to the downstream entry angle ⁇ and to the upstream entry angle ⁇ . More precisely, the variable angles ⁇ 'and ⁇ ' can also be seen according to the Z-angle analogy relative to a parallel P of the longitudinal projection line 202 in the depth 209 of the pocket 200 (see FIG FIG. 4th ).
  • the first contour section 220a extends within a downstream longitudinal section 208a of the length 208 of the pocket 200.
  • the second contour section 220b extends within an upstream longitudinal section 208b of the length 208 of the pocket 200.
  • the course of the first contour section 220a can be defined as differentiable, the variable angle ⁇ 'at least not becoming smaller in the course from the entry point 222 to the changeover point 224.
  • the course of the second contour section 220b can be defined as differentiable, alternatively or additionally, the variable angle ⁇ 'in the course from the change point 224 to the exit point 228 at least not increasing.
  • the contour 220 has a reversal point 226 between the changeover point 224 and the exit point 228. More precisely, the reversal point 226 is arranged in the second contour section 220b. The reversal point 226 is arranged between the changeover point 224 and the exit point 228. The reversal point 226 limits the maximum length 208 of the pocket 200, in particular the maximum length 208 of the pocket 200 in the upstream direction.
  • FIGS. 12A-12D show various flow modifying devices 10 with different configurations and arrangements of the pockets 200 in the cylindrical housing section 150.
  • the flow modifying devices 10 of FIGS. 12A and 12B only 10 or 5 pockets 200 each.
  • the flow modifying devices 10 in use in a compressor 300 and / or different configurations of the pockets 200 e.g.
  • the flow modifying device 10 have different numbers of pockets 200, also more than 19, less than 5 or other numbers between 5 and 19.
  • FIG. 12D an example of a flow modifying device 10 in which differently configured pockets 200 are present.
  • FIG. 12D Only two different types of configurations of pockets 200 are shown, several of the pockets can also be configured differently from other pockets 200 (for example 3, 4, 5, etc. different types of configurations of pockets 200).
  • one or more of the dimensions of one or more pockets 200 i.e.
  • a width 207 and / or a length 208 and / or a depth 209 and / or an opening 210 with an opening length 212 and / or one or more of the angles ⁇ , ⁇ ', ⁇ , ⁇ ' can be designed differently from one or more of the dimensions of the other pockets 200.
  • the pockets 200 are arranged equidistantly in the circumferential direction 26.
  • the pockets 200 can also be arranged unevenly distributed in the circumferential direction 26 (see FIG FIG. 12C ). In particular, combinations of different arrangements with different designs of pockets 200 are also possible.
  • the invention further relates to a compressor 300 for a charging device 400, which is shown schematically in a side sectional view in FIG FIG. 5 and the corresponding detail section Y is shown.
  • the detail section Y is in area Y of the FIG. 5 to be located, but runs in the area of the pocket 200 through a section along the orientation plane 203 of the pocket 200. That is, the FIG. 5 and the corresponding detail section Y are basically in section CC of FIG. 1 shown, but the upper pocket 200, which is explained in detail in detail Y, is shown in a section along the orientation plane 203 of the pocket 200 in order to be able to describe the opening length 212 accordingly.
  • the FIG. 6th and the associated detail section Z completely in section CC of FIG. 1 shown.
  • the compressor 300 comprises a compressor housing 310, a compressor wheel 320 and the flow modifying device 10.
  • the compressor housing 310 defines a compressor inlet 312 with an inlet cross section 312a and a compressor outlet 314.
  • the compressor wheel 320 is rotatably arranged in the compressor housing 310 between the compressor inlet 312 and the compressor outlet 314 .
  • the use of the flow modifying device 10 in a compressor 300 can result in a significant improvement the map stability can be achieved. In particular, both the lower and the upper map range can be stabilized. Compared to a "ported shroud" known from the prior art, the effectiveness can be seen even at lower pressure ratios.
  • the special design of the flow modifying device 10 with the pockets 200 enables a noticeable shift of the operating points near the surge limit towards lower throughputs (or higher pressure with the same throughput). As a result, an earlier and higher torque can be provided on the internal combustion engine.
  • the flow modifying device 10 can be incorporated as a retrofit measure into existing parts by means of machining. This means that different customer applications can be covered with identical raw parts. This results in manufacturing and financial advantages through a high degree of equality of parts.
  • the cylindrical housing section 150 of the flow modifying device 10 is manufactured integrally with the compressor housing 310.
  • the cylindrical housing section 150 can also be manufactured as a separate component.
  • FIGS. 8A-8C Simplified compressor housing 310 with a flow modifying device 10 shown in a greatly simplified manner and without a turbine wheel 320.
  • FIG. 8A a cylindrical housing section 150 manufactured integrally with the compressor housing 310, a cylindrical housing section 150, which is manufactured as a separate component from the FIGS. 8B and 8C juxtaposed.
  • the flow modifying device 10 or the cylindrical housing section 150 can be configured from the compressor inlet 312 in the axial direction 22 to the compressor outlet 314 (see FIG FIG.
  • a compressor contour 316 can be formed by the cylindrical housing section 150. Because this compressor contour 316 is formed on the separate cylindrical housing section 150, the geometry / surface of the compressor contour 316 is more flexible and more easily accessible for precise machining.
  • compressor housings 310 of the same type can optionally be used for different compressor applications, into which differently configured flow modifying devices 10 can be inserted. Furthermore, there may be manufacturing and / or material advantages if the cylindrical housing section 150 is designed as a separate component. In sum, these configurations can result in manufacturing and financial advantages due to a high degree of equality of parts.
  • FIG. 6th and the associated detail section Z show a further embodiment of the compressor 300, in which the compressor 300 comprises an adjusting mechanism 100 with a plurality of diaphragm elements 110 for changing the inlet cross section 312a. All of the previously explained possible variations of the compressor 300 and / or the flow modifying device 10 also apply to this embodiment of the compressor 300.
  • the flow modifying device 10 is arranged downstream of the adjustment mechanism 100 or downstream of the screen elements 110. More precisely, the cylindrical housing section 150 is arranged downstream of the adjustment mechanism 100 or downstream of the screen elements 110. Regardless of whether the cylindrical housing section 150 is manufactured integrally with the bearing housing 310 or as a separate component, the cylindrical housing section 150 can be configured as a bearing ring 130 for the diaphragm elements 110 (see FIG FIG.
  • the adjusting mechanism 100 comprises an adjusting ring 120 for adjusting the panel elements 110 (see detail section Z of FIG. 6th ).
  • the adjustment mechanism 100 can be actuated between a first, open position and a second, closed position. In the first position, the inlet cross section 312a is unchanged. In the second position, however, the inlet cross section 312a is reduced (see FIG FIG. 6th ).
  • the compressor map can be optimized by the adjustment mechanism 100 by moving the adjustment mechanism 100 into the second position.
  • FIG. 7A shows a compressor map in which the pressure ratio p 1 / p 2 is plotted over the volume flow V ⁇ for a compressor which comprises only one adjusting mechanism 100 and no flow modifying device 10.
  • the two map areas K 1 (closed) and K 2 (open) and the gap area L are plotted.
  • the compressor map of a compressor 300 comprises both the adjusting mechanism 100 and the flow modifying device 10.
  • the map area K 1 open position
  • the map area K ⁇ shown in dashed lines
  • This can be achieved by combining the adjustment mechanism 100 with the special design of the flow modifying device 10, whereby the gap area L is made FIG. 7A can be reduced significantly.
  • a considerably improved compressor 300 can be provided with a compressor map or map areas improved in both positions of the adjusting mechanism 100.
  • FIGS. 9A-9D and 11B show exemplary configurations in which the cylindrical housing section 150 is constructed in several parts.
  • the cylindrical housing section 150 may comprise a plurality of subdivision sections 157 in the circumferential direction 26. These subdivision sections 157 in the circumferential direction 26 may also be referred to as circumferential partition sections 157.
  • a separate, circumferential dividing section 157 can be provided for each pocket 200 (see FIG FIG. 11B ).
  • a circumferential dividing section 157 can also accommodate a plurality of pockets 200.
  • the cylindrical housing section 150 can also comprise more or less circumferential subdivision sections 157.
  • a circumferential dividing section 157 can be designed to be essentially T-shaped in cross-section in order to be secured against slipping out in the radial direction 24 (see also FIG. 11B ).
  • the cylindrical housing section 150 can also, as in FIG. 11A shown, consist of a single component in the circumferential direction 26.
  • FIGS. 9A-9D , 11A and 11B show greatly simplified compressor housings 310 with likewise greatly simplified flow modifying devices 10.
  • FIGS. 9A-9D show how the cylindrical housing section 150 can comprise a plurality of subdivision sections 159 in the axial direction 22.
  • These dividing sections 159 in the axial direction 22 can also be referred to as axial dividing sections 159.
  • the cylindrical housing section 150 can consist of a first dividing section 159a in the axial direction 22 and a second dividing section 159a in the axial direction 22 (see FIGS. 9C and 9D ).
  • the first axial subdivision section 159a and the second axial subdivision section 159b are designed in particular in the form of a ring.
  • the first axial dividing section 159a and the second axial dividing section 159b are designed in such a way that they separate the pockets 200 at their lowest point. In other words, this means that the first axial subdivision section 159a and the second axial subdivision section 159b subdivide the pockets 200 at the change point 224.
  • This has advantages in terms of manufacturing technology in particular, such as simplified accessibility to the pocket 200.
  • one of the first axial dividing portion 159 a and the second axial dividing portion 159 b can be manufactured integrally with the compressor housing 310.
  • the other of the first axial dividing portion 159a and the second axial dividing portion 159b from the compressor inlet 312 in the axial direction 22 to the Compressor outlet 314 or from the compressor outlet 314 in the axial direction 22 to the compressor inlet 312 in the compressor housing 310.
  • This also applies in an analogous manner to a cylindrical housing section 150 with a first axial subdivision section 159a and a second axial subdivision section 159b, none of which is manufactured integrally with the compressor housing 310.
  • both the first axial dividing section 159a and the second axial dividing section 159b can be inserted into the compressor housing 310 from the compressor inlet 312 in the axial direction 22 to the compressor outlet 314 (see FIG FIG. 9C ).
  • the first axial subdivision section 159a and also the second axial subdivision section 159b can be inserted into the compressor housing 310 from the compressor outlet 314 in the axial direction 22 to the compressor inlet 312.
  • a corresponding adaptation of the compressor housing 310 according to the respective direction of insertion of the cylindrical housing section 150 is of course and, for example, from the FIGS. 9A-9D evident.
  • the compressor contour 316 can be formed by the cylindrical housing section 150. Because this compressor contour 316 is formed on the separate cylindrical housing section 150, the geometry / surface of the compressor contour 316 is more flexible and more easily accessible for precise machining.
  • circumferential subdivision sections 157 and axial subdivision sections 159 are also possible.
  • first axial subdivision section 159a and / or the second axial subdivision section 159b also have two or more circumferential subdivision sections 157.
  • FIGS. 10A-10D show, by way of example, various fastening devices 330 of the cylindrical housing section 150 of the flow modifying device 10 in a highly simplified form.
  • the flow modifying device 10 can be fastened in the compressor housing 310 via its cylindrical housing section 150, if this is designed as a separate part.
  • Various coupling technologies such as a press fit, a snap hook connection, a screw connection or other suitable ones, are used as the fastening device 330 Technologies in question. They show FIGS. 10A and 10B Two different configurations of fastening devices 330 in the form of snap-hook connections between the cylindrical housing section 150 and the compressor housing 310.
  • the snap-hook connection is arranged on the outer jacket surface 158.
  • the snap hook connection can be arranged at different positions of the cylindrical housing section 150.
  • the snap hook connection in the upstream end region 156 (not shown), in the downstream end region 154 (see FIG FIG. 10B ) or axially between the upstream end region 156 and the downstream end region 154 (see FIG. 10A ).
  • FIG. 10C shows an embodiment of the fastening devices 330 as a screw connection in which the cylindrical housing section 150 is screwed via a thread on its outer jacket surface 158 with a thread on an inner jacket surface of the compressor housing 310.
  • FIG. 10D shows an embodiment of the fastening devices 330 as a press connection, in which the cylindrical housing section 150 is held in the compressor housing 310 with a friction fit between its outer jacket surface 158 and an inner jacket surface of the compressor housing 310.
  • the configurations just explained also apply analogously to configurations of the flow modifying device 10 in which individual or all subdivision sections 157, 159 (if present) and not the entire cylindrical housing section 150 are manufactured separately.
  • the cylindrical housing section 150 can have an oversize 160 in the direction of the compressor wheel 320 (see FIGS. 13D and 13E ).
  • the FIGS. 13D and 13E only the outer contours of the compressor wheel 320 are shown in dashed lines.
  • the cylindrical housing section 150 has an oversize 160.
  • the flow modifying device 10 or the cylindrical housing section 150 is designed to be inserted into the compressor housing 310 from the compressor inlet 312 in the axial direction 22 to the compressor outlet 314.
  • the oversize 160 is formed inward in the radial direction 24.
  • the oversize 160 is only present in a partial area of the compressor contour 316.
  • the flow modifier 10 or the cylindrical housing section 150 is designed to be inserted into the compressor housing 310 from the compressor outlet 314 in the axial direction 22 to the compressor inlet 312.
  • the oversize 160 is formed in the area of the compressor contour 316. In other words, this means that the oversize 160 is formed downstream in the axial direction 22 and inward in the radial direction 24.
  • the oversize 160 can be reduced, in particular grinded in or ground off, by the compressor wheel 320. This means that the compressor wheel 320, which is made of a metallic material, can remove or grind the softer and unnecessary plastic material of the cylindrical housing section 150 in the area of the oversize 160.
  • the invention further comprises a manufacturing method of the compressor 300 or the flow modifying device 10.
  • the cylindrical housing section 150 can be provided integrally with the compressor housing 310 or as a separate component. It is also possible for only individual, several or all of the subdivision sections 157, 159 (if present) to be provided integrally with the compressor housing 310 or as separate components. If the cylindrical housing section 150 or the subdivision sections 157, 159 are provided as separate components, the pockets 200 can be produced directly with the cylindrical housing section 150 or the subdivision sections 157, 159, for example in an injection molding process. Alternatively, the pockets 200 can subsequently be introduced into the cylindrical housing section 150 or into the subdivision sections 157, 159 by removing processes.
  • the pockets 200 can be made into the cylindrical housing section 150 or the subdivision sections 157, 159 or into the Compressor housing 310 be introduced.
  • FIG. 13A exemplary pockets 200 that are in an erosion process in the compressor housing 310 were introduced.
  • FIGS. 13B and 13C show a combination of a casting process in which a basic shape of the pockets 200 is already provided in the compressor housing 310 (see FIG FIG. 13B ), followed by a removal process, in particular a milling process, by means of which the final geometry of the pocket 200 (as described above) is generated (see FIG FIG. 13C ). That is to say, the pockets 200 can be produced by an erosion process, a casting process, an abrasive process or any combination of two or more of the above-mentioned and / or other suitable processes.
  • the relative position of the pockets 200 to the compressor wheel 320 is based on FIG. 5 and the detail section Y.
  • the compressor wheel 320 comprises a plurality of blades 322 distributed in the circumferential direction 26, as is also known from the prior art. In the FIG. 5 two blades 322 are shown in this regard. Each blade 322 has a leading edge 324, a side edge 325, a trailing edge 326, a front side 327 and a rear side 328.
  • This can be seen in detail Y, in which the compressor housing 310 or the pocket 200 is not shown along the section CC, but along a section through the orientation plane of the pocket 20. For perspective reasons, only the rear side is for one vane 322 328 and for the other blade only the front side 327 can be seen.
  • the front side 327 and the rear side 328 can be seen relative to the direction of rotation ⁇ of the compressor wheel 320.
  • the pockets 200 are arranged in the axial direction 22 or at an axial position in such a way that the opening 210 of a respective pocket 200 is located both upstream and downstream of a corner 329 at which the leading edge 324 and the side edge 325 converge.
  • the pockets 200 are arranged in the axial direction 22 or at an axial position in such a way that a center of the opening 210, which lies at half the opening length 212, is located approximately at the corner 329.
  • a ratio between a downstream opening length 212 a, which is arranged downstream of the corner 329, to an upstream opening length 212 b, which is arranged upstream of the corner 329 can also be greater or less than 1.
  • the angle of incidence ⁇ is angled in a direction of rotation ⁇ of the compressor wheel 320 from the radial direction 24.
  • This advantageous embodiment leads to an improved fluid flow into the pocket 200.
  • a larger volume flow can in turn be directed or recirculated through the pocket 200 back in the direction of the downstream end region 154, i.e. back to the compressor wheel 320, which in turn can increase efficiency .
  • the invention also relates to a charging device 400 (see FIG. 14th ).
  • the charging device 400 includes and the compressor 300.
  • the compressor 300 shown comprises a flow modifying device 10 and an adjusting mechanism 100.
  • the cylindrical housing section 150 is formed integrally with the compressor housing 310.
  • the cylindrical housing section 150 can also be designed as a separate component.
  • all of the configuration variants mentioned above can be transferred to the charging device 400.
  • the compressor 300 can also only comprise a flow modifying device 10 and no adjusting mechanism 100.
  • the compressor 300 further comprises a compressor inlet connection 340 which is arranged in the axial direction 220 upstream of the compressor housing 310 and is fastened to the latter.
  • the adjustment mechanism 100 is arranged axially between the compressor inlet connection 340 and the compressor housing 310.
  • the charging device 400 further comprises a shaft 420 via which the compressor 300 and the drive unit 410 are coupled to one another in a rotationally fixed manner.
  • the drive device 410 is a turbine.
  • the drive unit 410 can also comprise an electric motor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP19171814.7A 2019-04-30 2019-04-30 Dispositif de modification de flux pour compresseurs Withdrawn EP3734081A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP19171814.7A EP3734081A1 (fr) 2019-04-30 2019-04-30 Dispositif de modification de flux pour compresseurs
CN201920776930.4U CN210509688U (zh) 2019-04-30 2019-05-28 流动改变装置、压缩机和增压设备
CN201910448323.XA CN111852930A (zh) 2019-04-30 2019-05-28 用于压缩机的流动改变装置
US16/862,802 US20200347850A1 (en) 2019-04-30 2020-04-30 Flow-modifying device for compressors

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Application Number Priority Date Filing Date Title
EP19171814.7A EP3734081A1 (fr) 2019-04-30 2019-04-30 Dispositif de modification de flux pour compresseurs

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JP2021124069A (ja) * 2020-02-06 2021-08-30 三菱重工業株式会社 コンプレッサハウジング、該コンプレッサハウジングを備えるコンプレッサ、および該コンプレッサを備えるターボチャージャ
CN114738320B (zh) * 2022-03-25 2024-06-18 潍柴动力股份有限公司 一种导流环及压气机

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US4212585A (en) * 1978-01-20 1980-07-15 Northern Research And Engineering Corporation Centrifugal compressor
US20020004004A1 (en) * 2000-06-16 2002-01-10 Peter Fledersbacher Exhaust turbocharger for an internal combustion engine
US20050111968A1 (en) * 2003-11-25 2005-05-26 Lapworth Bryan L. Compressor having casing treatment slots
US20090041576A1 (en) * 2007-08-10 2009-02-12 Volker Guemmer Fluid flow machine featuring an annulus duct wall recess
US20100014956A1 (en) * 2008-07-07 2010-01-21 Rolls-Royce Deutschland Ltd & Co Kg Fluid flow machine featuring a groove on a running gap of a blade end
US20160195109A1 (en) * 2013-08-09 2016-07-07 Aeristech Limited Attachment arrangement for turbo compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4212585A (en) * 1978-01-20 1980-07-15 Northern Research And Engineering Corporation Centrifugal compressor
US20020004004A1 (en) * 2000-06-16 2002-01-10 Peter Fledersbacher Exhaust turbocharger for an internal combustion engine
US20050111968A1 (en) * 2003-11-25 2005-05-26 Lapworth Bryan L. Compressor having casing treatment slots
US20090041576A1 (en) * 2007-08-10 2009-02-12 Volker Guemmer Fluid flow machine featuring an annulus duct wall recess
US20100014956A1 (en) * 2008-07-07 2010-01-21 Rolls-Royce Deutschland Ltd & Co Kg Fluid flow machine featuring a groove on a running gap of a blade end
US20160195109A1 (en) * 2013-08-09 2016-07-07 Aeristech Limited Attachment arrangement for turbo compressor

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