EP3835590A1 - Compresseur et boîtier de compresseur - Google Patents

Compresseur et boîtier de compresseur Download PDF

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Publication number
EP3835590A1
EP3835590A1 EP19215251.0A EP19215251A EP3835590A1 EP 3835590 A1 EP3835590 A1 EP 3835590A1 EP 19215251 A EP19215251 A EP 19215251A EP 3835590 A1 EP3835590 A1 EP 3835590A1
Authority
EP
European Patent Office
Prior art keywords
pressure
compressor
side channel
suction
channel
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Withdrawn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
EP19215251.0A
Other languages
German (de)
English (en)
Inventor
Murat Öztürk
Daniel Schulze
Michael Wendland
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.)
BMTS Technology GmbH and Co KG
Original Assignee
BMTS Technology GmbH and Co KG
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 BMTS Technology GmbH and Co KG filed Critical BMTS Technology GmbH and Co KG
Priority to EP19215251.0A priority Critical patent/EP3835590A1/fr
Priority to US17/109,274 priority patent/US20210180608A1/en
Priority to CN202011411103.9A priority patent/CN112943695A/zh
Publication of EP3835590A1 publication Critical patent/EP3835590A1/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Withdrawn legal-status Critical Current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
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F04D27/0215—Arrangements therefor, e.g. bleed or by-pass valves
    • 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
    • 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
    • F04D27/009—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by bleeding, by passing or recycling fluid
    • 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • 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
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/422—Discharge tongues
    • 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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • 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
    • 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

Definitions

  • the invention relates to a compressor for a turbocharger of a vehicle according to the preamble of claim 1.
  • the invention also relates to a compressor housing for the compressor.
  • a compressor is a part of a turbocharger that is used in a vehicle to compress air for its engine.
  • the compressor usually has a compressor housing in which a compressor wheel is received.
  • the compressor housing usually has an inlet connector, a receiving space for the compressor wheel, a spiral and a pressure connector, which are connected to one another in an air-conducting manner. Air that is sucked in is conducted via the inlet connection to the compressor wheel in the receiving space, compressed in the compressor wheel and passed on via the spiral and the pressure connection from the compressor to the engine.
  • a forced air duct can also connect the pressure side and the suction side in an air-conducting manner.
  • An electric diverter valve is then arranged in the diverter air duct, which closes or opens the diverter air duct.
  • the overrun air duct allows higher pressure ratios to be achieved at the surge limit of the compressor for a given compressor mass flow, thereby increasing the performance of the compressor.
  • the disadvantage is that the bypass valve arranged on the outside of the compressor housing and the valve flange provided for this increase the space requirement for the compressor.
  • the compressor housing is usually cast from aluminum using the lost core method.
  • relatively large wall thicknesses of the compressor housing are necessary in order to compensate for the tolerances due to the relative position of the core to the outer shape. These tolerances can be reduced when the compressor housing is manufactured using the die-casting process become.
  • the freedom of design - and in particular the freedom of design when producing the exhaust air duct and the valve flange - is restricted, since undercuts in the compressor housing can only be implemented by means of slides.
  • US 6 193 463 B1 discloses a compressor housing which is produced by the die-casting process.
  • the compressor housing comprises a total of three separate parts, which are then assembled to form the compressor housing.
  • the flow path in the compressor housing can be made very complex.
  • a further compressor housing is known which is produced in the die-casting process.
  • the compressor housing comprises a plastic part and an aluminum part, which are assembled to form the compressor housing.
  • a thermodynamically favorable spiral can be implemented in the compressor.
  • US 8 161 745 B2 discloses a compressor housing with a thrust air duct made up of a total of two ducts which are oriented at an angle to the longitudinal center axis of the inlet connection.
  • EP 2 553 275 B1 discloses a compressor housing with a forced air duct made up of a total of two ducts which are aligned parallel to one another and have no undercuts. As a result, the two channels can be represented with a single slide during manufacture.
  • the object of the invention is therefore to provide an improved or at least alternative embodiment for a compressor of the generic type and for its compressor housing, in which the disadvantages described are overcome.
  • the compressor and its compressor housing should be designed to be compact, have good fluid-mechanical properties and be producible in the die-casting process.
  • a compressor for a turbocharger of a vehicle.
  • the compressor has a cast compressor housing in which a compressor wheel for compressing air is received.
  • the compressor housing has an inlet connector aligned in an axial direction, a receiving space for the compressor wheel, a diffuser that encircles the receiving space radially on the outside, a spiral and a pressure connector.
  • the inlet nozzle, the receiving space with the compressor wheel, the diffuser, the spiral and the pressure nozzle are connected in an air-conducting manner following one another.
  • the receiving space is arranged axially adjacent to the inlet connector, the spiral runs radially on the outside around the diffuser and the receiving space and the pressure connector is directed outwards tangentially from the spiral.
  • a forced air circulation duct is formed in the compressor housing, which duct has a duct on the intake side and a duct on the pressure side.
  • the pressure-side channel is at a pressure connection point downstream of the compressor wheel and the suction-side channel is connected in an air-conducting manner to the inlet connector at a suction connection point upstream of the compressor wheel.
  • the pressure connection point is formed downstream of a tongue formed by the spiral on an outer wall of the pressure connection facing the spiral.
  • the diffuser runs around the receiving space from the outside and thereby surrounds an outlet of the compressor wheel.
  • the diffuser is located radially on the outside of the receiving space.
  • the spiral surrounds the diffuser radially from the outside and the diffuser is circumferentially connected to the spiral in an air-conducting manner.
  • the diffuser lies radially between the receiving space with the compressor wheel and the spiral.
  • the dynamic pressure generated by the compressor wheel can be converted into the static pressure by the diffuser.
  • the spiral wraps around the diffuser in the circumferential direction over 360 °, with the tongue separating the beginning and the end of the spiral at 0 ° and 360 °.
  • air to be compressed flows axially into the inlet connector and on to the compressor wheel in the receiving space.
  • the air is compressed by the compressor wheel and flows on through the diffuser and the spiral into the pressure port.
  • Compressed air is fed from the pressure port to the engine of the vehicle.
  • the suction side of the compressor is arranged upstream of the compressor wheel and the pressure side of the compressor is arranged downstream of the compressor wheel in the compressor housing.
  • the suction-side channel and the pressure-side channel are inclined to the axial direction or are arranged at an angle other than 0 °.
  • the suction-side channel and the pressure-side channel can be arranged axially offset from one another.
  • the suction-side channel and the pressure-side channel can lie in planes parallel to one another, which are inclined to the axial direction or are arranged at an angle other than 0 °.
  • the suction-side channel is then aligned at a suction side angle less than or equal to 90 ° to the inlet connector.
  • the suction-side channel and the pressure-side channel are preferably arranged transversely to the axial direction.
  • the two channels or their longitudinal center axes each lie in a plane arranged transversely to the axial direction.
  • the suction-side channel is then aligned at a suction-side angle equal to 90 ° to the axial direction.
  • the terms “axial” and “radial” always relate to the axial direction.
  • a valve flange can advantageously be formed on the compressor housing in the area of the blow-off air duct.
  • the compressor can also have a diverter valve, which is fastened with its fastening flange to the valve flange. The diverter valve then engages the diverter air duct in areas and can connect the suction-side duct and the pressure-side duct to one another in an air-conducting manner or to separate them from one another in an airtight manner.
  • the diverter valve is preferably electrical.
  • the compressor housing can advantageously be cast in one piece with the suction-side channel and with the pressure-side channel in a die-casting process.
  • the compressor housing can preferably be cast from aluminum.
  • the compressor housing can be cast in one piece with the suction-side channel or with the pressure-side channel in a die-casting process.
  • the compressor housing can preferably be cast from aluminum.
  • the duct on the pressure side that is not cast at the same time or the duct on the suction side that is not cast at the same time can then be mechanically incorporated into the cast compressor housing at a later date.
  • the mechanical incorporation is preferably carried out by drilling or milling.
  • the pressure-side channel and the suction-side channel are aligned with one another at a channel angle greater than 0 ° and less than or equal to 90 °.
  • the channel angle is preferably between 30 ° and 90 °, more preferably between 30 ° and 60 °. From a fluidic point of view, the channel angle should be as close as possible to 90 ° in order to reduce the deflection of the flow from the pressure-side channel into the suction-side channel. In terms of flow, this results in the optimal range between 30 ° and 90 °. From the manufacturing point of view, should however, the channel angle can be selected so that the pressure-side channel and the suction-side channel can be removed from the mold or the pressure-side channel can be produced by subsequent mechanical processing.
  • the longitudinal center axes of the two channels are not aligned parallel to one another.
  • the longitudinal center axes of the two channels can intersect or be skewed to one another. As a result, the air flow has to be deflected less at the transition between the pressure-side channel and the suction-side channel.
  • the pressure-side channel and the pressure connection can be aligned with one another at a pressure-side angle greater than 0 ° and less than or equal to 90 °.
  • the print side angle is preferably between 30 ° and 90 °, more preferably between 30 ° and 60 °.
  • the pressure side angle should be as close as possible to 0 ° in order to reduce the deflection of the flow from the pressure nozzle into the pressure-side channel. In terms of flow, this results in the optimal range between 0 ° and 60 °. From the point of view of production technology, however, the pressure side angle should be selected so that the pressure-side channel can be removed from the mold or produced by subsequent mechanical processing.
  • the longitudinal center axis of the pressure-side channel and the longitudinal center axis of the pressure port are not aligned parallel to one another.
  • the longitudinal center axis of the pressure-side channel and the longitudinal center axis of the pressure port can therefore intersect or be skewed to one another. With this arrangement of the pressure-side channel, the air flow needs to be deflected less at the transition between the pressure connection and the pressure-side channel.
  • the two longitudinal center axes intersect, so that the pressure-side channel branches off axially in the center of the pressure connection or opens axially in the center into the pressure connection.
  • negative effects of the duct on the pressure side on the flow in the pressure port can advantageously be reduced in this embodiment.
  • the suction-side channel and the pressure port are aligned parallel to one another and, as a result, the pressure-side angle and the channel angle are the same size.
  • the longitudinal center axis of the suction-side channel and the longitudinal center axis of the pressure port can be aligned parallel to one another.
  • the slide for the pressure port and the slide for the suction-side channel can move into the tool from the same direction during the manufacture of the compressor housing. If the valve flange formed on the compressor housing for the diverter valve is adapted accordingly, the two slides can be designed as one slide. This can reduce the cost of the tool.
  • the suction-side channel and the pressure connection are not aligned parallel to one another, and as a result the pressure-side angle and the channel angle differ from one another. In this embodiment, the compressor can be made more compact.
  • the suction-side channel opens radially into the inlet connector.
  • the longitudinal center axis of the suction-side channel and the longitudinal center axis of the inlet connector then intersect and are aligned perpendicular to one another.
  • a suction side angle between the inlet connector and the suction-side channel is then equal to 90 °.
  • the suction connection point of the suction-side channel can advantageously be arranged in such a way that that the flow in the inlet port experiences a pre-swirl.
  • the pre-swirl leads to an improved flow towards the compressor wheel at the surge limit of the compressor by avoiding detachment in the area of the impeller blades of the compressor wheel. As a result, the performance of the compressor can be further improved at its surge limit.
  • the sum of all deflection angles to be traversed by flowing air in the overrun air duct can be less than or equal to 360 °.
  • the air is first diverted from the pressure port into the pressure side duct by the pressure side angle defined above.
  • a first deflection angle in the overrun air duct therefore corresponds to the pressure side angle.
  • the air is then diverted from the duct on the pressure side into the duct on the suction side.
  • the two channels have the channel angle defined above to one another and the air is deflected by a second deflection angle.
  • the second deflection angle corresponds to a difference between 180 ° and the channel angle defined above.
  • a third deflection angle is therefore equal to the suction side angle.
  • the sum of these three deflection angles is therefore less than or equal to 360 °.
  • the sum of a pressure side angle between the pressure connection and the pressure-side channel, a channel angle between the suction-side channel and the pressure-side channel, and a suction side angle between the suction-side channel and the inlet connection can be less than or equal to 180 °.
  • the pressure side angle is close to 90 °, the channel angle is 35 ° and the suction side angle is 90 °, the sum of all deflection angles is approximately 325 °. If the print side angle is 45 °, the channel angle is 35 ° and the The suction side angle is 90 °, the sum of all deflection angles is 280 °. If the pressure side angle is 45 °, the duct angle is 45 ° and the suction side angle is 90 °, then the sum of all deflection angles is 270 °.
  • a cross section of the pressure connection downstream of the pressure connection point is larger than a cross section of the pressure connection upstream of the pressure connection point.
  • negative effects of the duct on the pressure side on the flow in the pressure connection can be advantageously reduced in this way.
  • the cross-section at a wall part of the pressure connection, which extends outward from the pressure connection point parallel to the longitudinal center axis of the pressure connection increases more strongly.
  • a valve flange can advantageously be formed on the compressor housing in the area of the blow-off air duct.
  • the valve flange is not oriented tangentially to a radially outer wall part of the spiral.
  • the valve flange or a flange plane spanned by it and the wall part of the spiral lying radially on the outside overlap.
  • the valve flange and the pressure port can be aligned at an angle greater than 0 ° and less than or equal to 90 ° to one another.
  • the longitudinal center axis of the pressure-side channel and the valve flange or a flange plane spanned by this intersect at an angle greater than 0 ° and less than or equal to 90 °.
  • the compressor can be made more compact.
  • the diverter valve arranged on the valve flange cannot be arranged radially to the spiral and to the inlet connector, so that overall the compressor is more compact.
  • the term "not radial" means in this context, that the longitudinal center axis of the diverter valve and the longitudinal center axis of the inlet connector do not intersect.
  • valve flange is oriented perpendicular to the pressure-side channel and inclined to the suction-side channel.
  • the valve flange lies in a flange plane which is oriented perpendicular to the longitudinal center axis of the pressure-side channel and its normal at the channel angle defined above to the longitudinal center axis of the suction-side channel. If the suction-side channel and the pressure-side channel are aligned transversely to the axial direction, the valve flange and its flange plane are then arranged parallel to the axial direction.
  • the pressure-side channel branches off axially in the center of the pressure connection or opens axially centrally into the pressure connection.
  • the longitudinal center axis of the pressure port and the longitudinal center axis of the pressure-side channel intersect.
  • the angle of intersection between the two longitudinal center axes then corresponds to the pressure side angle defined above.
  • negative effects of the duct on the pressure side on the flow in the pressure port can advantageously be reduced in this embodiment.
  • the pressure-side channel can also not branch off axially centrally from the pressure connection or open into the pressure connection. In other words, the longitudinal center axis of the pressure port and the longitudinal center axis of the pressure-side channel cannot intersect.
  • the two longitudinal center axes are then arranged skewed to one another.
  • the longitudinal center axes When projecting onto one another, the longitudinal center axes then have the printing side angle defined above with respect to one another.
  • the pressure connection point is thus formed in the pressure connection axially offset from its longitudinal center axis and the pressure-side channel lies in some areas on the spiral. This allows the compressor to be constructed in a more compact manner.
  • the pressure-side channel opens axially centrally into the pressure connection.
  • negative effects of the duct on the pressure side on the flow in the pressure port can advantageously be reduced in this embodiment.
  • the suction-side channel and the pressure port are aligned parallel to one another.
  • the slide for the pressure port and the slide for the suction-side channel can move into the tool from the same direction. If the valve flange formed on the compressor housing for the diverter valve is adapted accordingly, the two slides can be designed as one slide. This can reduce the cost of the tool.
  • the suction-side channel opens radially into the inlet connector.
  • the pressure-side channel does not open axially centrally into the pressure connection.
  • the longitudinal center axis of the pressure port and the longitudinal center axis of the pressure-side channel do not intersect.
  • the two longitudinal center axes are then arranged skewed to one another.
  • the longitudinal center axes then have the printing side angle defined above with respect to one another.
  • the pressure connection point is thus formed in the pressure connection axially offset from its longitudinal center axis and the pressure-side channel lies in some areas on the spiral.
  • the pressure-side channel remains airtightly separated from the spiral in this area.
  • the pressure-side channel is facing the inlet port on the spiral.
  • the length of the suction-side channel and the length of the pressure-side channel can be reduced, which has a positive effect on the flow in the open recirculation duct.
  • the pressure-side channel does not open axially centrally into the pressure connection.
  • the pressure connection point is formed in the pressure connection axially offset to its longitudinal center axis and the pressure-side channel lies in some areas on the spiral.
  • the suction-side channel and the pressure port are not aligned parallel to one another. As a result, the print side angle defined above and the channel angle defined above are not the same.
  • the length of the intake-side channel and the length of the pressure-side channel can be reduced, which has a positive effect on the flow in the open exhaust air channel.
  • the invention also relates to a compressor housing for the compressor described above.
  • a compressor housing for the compressor described above In order to avoid repetition, reference is made at this point to the statements above.
  • Fig. 1 shows an exploded view of a compressor 1 according to the invention for a turbocharger of a vehicle.
  • the compressor 1 has a compressor housing 2 according to the invention.
  • the compressor housing 2 is in one piece and cast from aluminum in a die-casting process.
  • the compressor housing 2 comprises an inlet connector 3, a receiving space 4, a diffuser, not visible here, a spiral 5 and a pressure nozzle 6.
  • the inlet nozzle 3, the receiving space 4, the diffuser, the spiral 5 and the pressure nozzle 6 are connected in an air-conducting manner following one another .
  • the inlet connector 3 is aligned in an axial direction AR, so that its longitudinal center axis L3 and the axial direction AR are parallel.
  • the receiving space 4 is arranged downstream of the inlet connection 3 and axially adjacent to it.
  • a compressor wheel - not visible here - is accommodated in the receiving space 4.
  • the diffuser runs around the receiving space 4 radially from the outside and is arranged downstream of the receiving space 4.
  • the spiral 5 is arranged downstream of the diffuser and of the receiving space 4 and revolves around them radially from the outside.
  • the pressure port 6 is arranged downstream of the spiral 5 and is directed tangentially outwards from it.
  • a forced air duct 7 is formed, which connects the inlet connector 3 and the pressure connector 6 in an air-conducting manner.
  • a valve flange 8 is formed, to which a diverter valve 9 is then fastened with its fastening flange 10 by means of screws 11.
  • the valve flange 8 or its flange plane is not aligned tangentially to a radially outer wall part of the spiral 5. In other words, the valve flange 8 or its flange plane and the radially outer wall part of the spiral 5 intersect in an axial projection.
  • the diverter valve 9 attached to the valve flange 8 is therefore not oriented radially to the spiral 5 and to the inlet connection 3, whereby the compressor 1 is designed to be more compact overall.
  • the diverting air valve 9 separates the diverting air channel 7 into an intake-side channel 12 and a pressure-side channel 13.
  • the diverting air valve 9 can separate the two ducts 12 and 13 from one another in an airtight manner or connect them to one another in an air-conducting manner and thereby close or open the diverting air duct 7.
  • the pressure-side channel 13 is connected to the pressure connector 6 in an air-conducting manner at a pressure connection point 13a in the transition area between the spiral 5 and the pressure connector 6.
  • the suction-side channel 12 is then connected in an air-conducting manner to the inlet connector 3 at a suction connection point 12a.
  • the two channels 12 and 13 are arranged axially offset from one another and each aligned transversely to the axial direction AR or each lie in a plane aligned transversely to the axial direction AR.
  • the structure of the compressor housing 2 is based on the following Fig. 2 and Fig. 3 explained in more detail.
  • Fig. 2 shows a view of the compressor housing 2 according to the invention for the in Fig. 1 Compressor 1 according to the invention shown with an opening in the area of the blow-off air duct 7.
  • Fig. 3 shows a sectional view of the compressor housing 2 according to the invention in the area of the overrun air duct 7.
  • the pressure-side duct 13 and the pressure connection 6 are aligned with one another at a pressure-side angle ⁇ which is between 0 ° and 90 °.
  • the pressure side angle ⁇ is approximately 45 °.
  • the longitudinal center axis L13 of the pressure-side channel 13 and the longitudinal center axis L6 of the pressure port 6 are therefore not aligned parallel to one another.
  • Fig. 1 shows a view of the compressor housing 2 according to the invention for the in Fig. 1
  • Compressor 1 according to the invention shown with an opening in the area of the blow-off air duct 7.
  • Fig. 3 shows a sectional view of the compressor housing 2 according to the invention in the area
  • the longitudinal center axes L6 and L13 are arranged skewed to one another. When projecting onto one another, the longitudinal center axes L6 and L13 then intersect at the printing side angle a.
  • the pressure-side channel 13 therefore does not adjoin the pressure connection 6 in the middle and the pressure connection point 13a and the longitudinal center axis L6 of the pressure connection 6 are axially displaced relative to one another.
  • the duct on the pressure side 13 can thereby be partially arranged on the spiral 5 and the length of the channels 12 and 13 can be reduced.
  • the compressor housing 2 has a more compact design.
  • the pressure-side channel 13 and the suction-side channel 12 are also aligned with one another at a channel angle ⁇ which is between 0 ° and 90 °.
  • the channel angle ⁇ is about 40 °.
  • the longitudinal center axes L12 and L13 of the two channels 12 and 13 are not aligned parallel to one another.
  • the two channels 12 and 13 are axially offset with respect to one another, so that the longitudinal center axes L12 and L13 are skewed with respect to one another. When projecting onto one another, these then intersect at the channel angle ⁇ .
  • the suction-side channel 12 and the pressure port 6 are also not aligned parallel to one another and have an angle of less than 180 ° to one another.
  • the pressure side angle ⁇ and the channel angle ⁇ are also not equal to one another.
  • the suction-side channel 12 is also aligned at a suction side angle ⁇ equal to 90 ° to the inlet connector 3. Furthermore, the suction-side channel 12 connects radially into the inlet connector 3. In other words, the longitudinal center axis L12 of the suction-side channel 12 and the longitudinal center axis L3 of the inlet connector 3 intersect at the suction side angle ⁇ equal to 90 °.
  • the sum of the pressure side angle ⁇ , the channel angle ⁇ and the suction side angle ⁇ is less than 180 °.
  • the deflection angles in the exhaust air duct 7 are given by the pressure side angle ⁇ , the difference between 180 ° and the channel angle ⁇ and the suction side angle ⁇ . The sum of all these deflection angles is therefore less than 360 °.
  • valve flange 8 or its flange plane is aligned parallel to the axial direction AR and perpendicular to the pressure-side channel 13 or its longitudinal center axis L13. Furthermore, a normal to the valve flange 8 or to its flange plane has the channel angle ⁇ to the suction-side channel 12. Furthermore, in Fig. 2 It can be seen that a cross section of the pressure port 6 downstream of the pressure connection point 13a is larger than a cross section of the pressure connection 6 upstream of the pressure connection point 13a. In the closed overrun air duct 7, negative effects of the pressure-side duct 13 on the flow in the pressure port 6 can be reduced in this way.
  • Fig. 4 shows a view of the flow channels of the compressor housing 2 according to the invention in a first embodiment.
  • This embodiment corresponds to the compressor housing 2 shown in FIGS. 1 to 3 is shown.
  • the pressure-side channel 13 does not connect centrally into the pressure connection piece 6, so that the pressure connection point 13a in the pressure connection piece 6 is axially offset from its longitudinal center axis L6.
  • the pressure-side channel 13 is axially offset towards the inlet connector 6 and lies in some areas on the spiral 5.
  • the length of the channels 12 and 13 can be reduced, which has a positive effect on the flow in the open overrun air channel 7.
  • the pressure port 6 and the suction-side channel 12 are also not arranged parallel to one another.
  • Fig. 5 shows a view of the flow channels of the compressor housing 2 according to the invention in a second embodiment.
  • the pressure-side channel 13 is arranged offset radially outward and axially towards the spiral 5.
  • the pressure-side channel 13 adjoins the pressure connection 6 axially in the center.
  • the longitudinal center axis L6 of the pressure port 6 and the longitudinal center axis L13 of the pressure-side channel 13 intersect here.
  • the length of the suction-side channel 12 is increased here compared to the first embodiment.
  • negative effects of the pressure-side duct 13 on the second embodiment can occur Flow in the pressure port 6 can be advantageously reduced.
  • the compressor housing 2 in the second embodiment corresponds to the compressor housing 2 in the first embodiment.
  • Fig. 6 shows a view of the flow channels of the compressor housing 2 according to the invention in a third embodiment.
  • the pressure-side channel 13 does not connect centrally into the pressure connection piece 6, so that the pressure connection point 13a in the pressure connection piece 6 is axially offset.
  • the pressure-side channel 13 is axially offset towards the inlet connector 6 and lies in some areas on the spiral 5.
  • the suction-side channel 12 and the pressure connector 6 are not aligned parallel to one another here.
  • the pressure side angle ⁇ is higher than in the first embodiment, so that the length of the suction-side channel 12 is reduced.
  • the suction-side channel 12 is offset towards the inlet connector 3 and the pressure-side channel 13 is rotated around the pressure connection point 13a to the inlet connector 3 by approximately 5 °.
  • the length of the channels 12 and 13 compared to the first embodiment can according to Fig. 4 can be further reduced, which has a positive effect on the flow in the open overrun air duct 7.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP19215251.0A 2019-12-11 2019-12-11 Compresseur et boîtier de compresseur Withdrawn EP3835590A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP19215251.0A EP3835590A1 (fr) 2019-12-11 2019-12-11 Compresseur et boîtier de compresseur
US17/109,274 US20210180608A1 (en) 2019-12-11 2020-12-02 Compressor and compressor casing
CN202011411103.9A CN112943695A (zh) 2019-12-11 2020-12-03 压缩机和压缩机壳体

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19215251.0A EP3835590A1 (fr) 2019-12-11 2019-12-11 Compresseur et boîtier de compresseur

Publications (1)

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EP3835590A1 true EP3835590A1 (fr) 2021-06-16

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US (1) US20210180608A1 (fr)
EP (1) EP3835590A1 (fr)
CN (1) CN112943695A (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6193463B1 (en) 1999-06-30 2001-02-27 Alliedsignal, Inc. Die cast compressor housing for centrifugal compressors with a true volute shape
US8161745B2 (en) 2006-11-09 2012-04-24 Borgwarner Inc. Turbocharger
EP2553275A1 (fr) * 2010-03-29 2013-02-06 Continental Automotive GmbH Carter de turbocompresseur doté d'un dispositif à soupape et procédé de production d'un tel carter de turbocompresseur
DE102014214226A1 (de) 2014-07-22 2016-01-28 Continental Automotive Gmbh Verbundverdichtergehäuse
US20170211465A1 (en) * 2016-01-22 2017-07-27 Honeywell International Inc. Compressor recirculation system having compressor inlet recirculation duct configured to reduce noise from rossiter excitation and cavity acoustic resonance
DE102017201922A1 (de) * 2017-02-08 2018-08-09 Bayerische Motoren Werke Aktiengesellschaft Verdichter für einen Verbrennungsmotor-Turbolader und Verbrennungsmotor-Turbolader
US10132324B2 (en) * 2010-09-02 2018-11-20 Borgwarner Inc. Compressor recirculation into annular volume

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6193463B1 (en) 1999-06-30 2001-02-27 Alliedsignal, Inc. Die cast compressor housing for centrifugal compressors with a true volute shape
US8161745B2 (en) 2006-11-09 2012-04-24 Borgwarner Inc. Turbocharger
EP2553275A1 (fr) * 2010-03-29 2013-02-06 Continental Automotive GmbH Carter de turbocompresseur doté d'un dispositif à soupape et procédé de production d'un tel carter de turbocompresseur
EP2553275B1 (fr) 2010-03-29 2018-01-24 Continental Automotive GmbH Carter de turbochargeur incluant un carter de soupape et procédé de fabrication d'un tel carter
US10132324B2 (en) * 2010-09-02 2018-11-20 Borgwarner Inc. Compressor recirculation into annular volume
DE102014214226A1 (de) 2014-07-22 2016-01-28 Continental Automotive Gmbh Verbundverdichtergehäuse
US20170211465A1 (en) * 2016-01-22 2017-07-27 Honeywell International Inc. Compressor recirculation system having compressor inlet recirculation duct configured to reduce noise from rossiter excitation and cavity acoustic resonance
DE102017201922A1 (de) * 2017-02-08 2018-08-09 Bayerische Motoren Werke Aktiengesellschaft Verdichter für einen Verbrennungsmotor-Turbolader und Verbrennungsmotor-Turbolader

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US20210180608A1 (en) 2021-06-17

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