WO2023061641A1 - Carter de turbocompresseur et turbocompresseur à gaz d'échappement avec carter de turbo-rotor intégré et couvercle de carter de compresseur - Google Patents

Carter de turbocompresseur et turbocompresseur à gaz d'échappement avec carter de turbo-rotor intégré et couvercle de carter de compresseur Download PDF

Info

Publication number
WO2023061641A1
WO2023061641A1 PCT/EP2022/073171 EP2022073171W WO2023061641A1 WO 2023061641 A1 WO2023061641 A1 WO 2023061641A1 EP 2022073171 W EP2022073171 W EP 2022073171W WO 2023061641 A1 WO2023061641 A1 WO 2023061641A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
compressor
turbocharger
rotor
integral
Prior art date
Application number
PCT/EP2022/073171
Other languages
German (de)
English (en)
Inventor
Ralf Böning
Timo Maier
Original Assignee
Vitesco Technologies GmbH
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 Vitesco Technologies GmbH filed Critical Vitesco Technologies GmbH
Publication of WO2023061641A1 publication Critical patent/WO2023061641A1/fr

Links

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
    • F04D29/40—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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/26—Double casings; Measures against temperature strain in casings
    • F01D25/265—Vertically split casings; Clamping arrangements therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/026—Scrolls for radial machines or engines
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/024—Units comprising pumps and their driving means the driving means being assisted by a power recovery turbine
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid 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 turbocharger housing and an exhaust gas turbocharger with an integral turbotor housing and compressor housing cover for an internal combustion engine.
  • Exhaust gas turbochargers are increasingly being used to increase the performance of internal combustion engines, for example for motor vehicles. This is done with the aim of reducing the size and weight of the combustion engine with the same or even increased performance and at the same time reducing consumption and thus CO2 emissions in view of the increasingly strict legal requirements in this regard.
  • the active principle is to use the energy contained in the exhaust gas flow to increase the pressure in the intake tract of the combustion engine and thus achieve better filling of the combustion chamber with air-oxygen in order to be able to convert more fuel, petrol or diesel, per combustion process, i.e. the to increase the power of the internal combustion engine.
  • a conventional exhaust gas turbocharger has an exhaust gas turbine arranged in the exhaust tract of the internal combustion engine, an air compressor arranged in the intake tract and a rotor bearing arranged in between.
  • the exhaust gas turbine has a turbine housing and a turbine impeller which is arranged therein and is driven by the exhaust gas mass flow.
  • the air compressor has a compressor housing and a compressor impeller which is arranged therein and builds up a boost pressure.
  • the turbine impeller and the compressor impeller are arranged in a rotationally fixed manner on the opposite ends of a common shaft, the so-called rotor shaft or rotor shaft, and thus form the so-called turbocharger rotor or turbocharger rotor.
  • the rotor shaft extends axially between the turbine impeller and the compressor impeller through the rotor bearing arranged between the exhaust gas turbine and the fresh air compressor and is rotatably mounted in it radially and axially with respect to the rotor shaft axis.
  • the turbine impeller driven by the exhaust gas mass flow drives the compressor impeller via the rotor shaft, which increases the pressure in the intake tract of the combustion engine, based on the air mass flow behind the fresh air compressor, and thus causes better filling of the combustion chamber with air-oxygen.
  • a conventional exhaust gas turbocharger has a multi-part structure.
  • a turbine housing of an exhaust gas turbine that can be arranged in the exhaust tract of the internal combustion engine, a compressor housing of an air compressor that can be arranged in the intake tract of the internal combustion engine, and a bearing housing of a bearing unit between the turbine housing and the compressor housing are arranged next to one another on a common turbocharger axis and are connected to one another in terms of assembly.
  • the turbine housing has one or more exhaust gas spiral ducts which are arranged in a ring around the turbocharger axis and the turbine impeller and taper helically towards the turbine impeller.
  • the exhaust gas spiral ducts have a respective or common, tangentially outwardly directed exhaust gas supply duct with a manifold connection flange for connection to an exhaust manifold of an internal combustion engine, through which the exhaust gas mass flow flows into the respective exhaust gas spiral duct.
  • the compressor housing has an air supply duct, which has an intake manifold connector for connection to the air intake system of the internal combustion engine and runs in the direction of the turbocharger axis toward the axial end of the compressor impeller. An air mass flow is sucked in by the compressor impeller from the air intake system via this air supply duct. Furthermore, the compressor housing generally has a compressor spiral duct, which is arranged annularly around the turbocharger axis and the compressor impeller and widens in a helical shape away from the compressor impeller 13 .
  • the compressor volute duct also has a tangentially outwardly directed air discharge duct with a distributor connection flange for connection to an air distributor pipe of an internal combustion engine.
  • a so-called spiral duct tongue is formed on the side of the air discharge duct facing the diffuser running air discharge duct separates and the air flow into the air discharge channel directs. The air mass flow is then conducted through the air discharge duct under increased pressure into the air distribution pipe of the combustion engine.
  • the radial inner contour of the compressor housing follows the outer contour of the compressor impeller accommodated therein.
  • This area of the inner contour of the compressor housing is referred to as the compressor sealing contour and causes the air mass flow to flow as completely as possible through the blading of the compressor impeller and not past it.
  • the bearing housing is arranged axially between the turbine housing and the compressor housing.
  • the bearing arrangement for supporting the rotor shaft of the turbocharger rotor and the turbocharger rotor is accommodated in the bearing housing.
  • the turbocharger rotor or turbocharger rotor represents a further assembly of the exhaust gas turbocharger, which has the rotor shaft, the turbine wheel arranged in the turbine housing and the compressor wheel arranged in the compressor housing.
  • the turbine wheel and the compressor wheel are arranged on the opposite ends of the common rotor shaft and are non-rotatably connected thereto.
  • the rotor shaft extends axially through the bearing housing in the direction of the turbocharger axis and is rotatably mounted in it by means of a bearing arrangement consisting of a radial bearing and an axial bearing about its longitudinal axis, the rotor shaft axis of rotation, with the rotor shaft axis of rotation lying in the turbocharger axis, i.e. coinciding with it.
  • the turbocharger rotor and the bearing arrangement are combined to form a preassembled assembly, which is referred to as a turbocharger rotor cartridge or, in the following, as a turbo rotor cartridge for short.
  • the turbine housing, the compressor housing and the bearing housing are also combined to form a one-piece housing, referred to below as the integral turbotor housing.
  • the integral turbotor housing Such a prior art design is shown in FIG.
  • Fig. 1 shows an embodiment of an exhaust gas turbocharger 1, which essentially consists of only three structural components or component assemblies during final assembly, namely an integral turbo rotor housing 3, a turbo rotor cartridge 10 and a compressor housing cover 34.
  • the turbo rotor cartridge 10 which can be provided as a completely preassembled assembly for final assembly, has a turbine wheel 12 , a compressor wheel 13 , a rotor shaft 14 with a rotor axis of rotation 15 and a shaft bearing cartridge 40 .
  • the turbine wheel 12 is non-rotatably connected to a first shaft end of the rotor shaft 14 and the compressor wheel 13 to the second shaft end of the rotor shaft 14, and the rotor shaft 14, together with the turbine wheel 12 and the compressor wheel 13, can be rotated about the rotor axis of rotation 15 in the shaft bearing cartridge 40 stored.
  • the rotor axis of rotation 15 simultaneously specifies the turbocharger axis 6, with which it coincides when the exhaust gas turbocharger is in the installed state.
  • the integral turbotor housing 3 includes
  • the bearing housing 41 which is arranged between the turbine housing 21 and the compressor housing 31 and in which the shaft bearing cartridge 40 or the turbo rotor cartridge 10 is accommodated.
  • the integral turbo rotor housing 3 is designed as a one-piece housing part and has a rotor receiving shaft 4 extending in the direction of the turbocharger axis 6 and an internal geometry for the turbo rotor cartridge 10 .
  • the inner geometry of the rotor receiving shaft 4 of the integral turbotor housing 3 is designed in such a way that the complete turbo rotor cartridge 10 as a preassembled unit, in only one axial joining direction running in the direction of the rotor axis of rotation 15 or the turbocharger axis 6, by a front mounting opening 33, can be recorded or mounted.
  • the compressor spiral channel 32 is arranged in such a way that it overlaps the bearing housing 41 or the rotor receptacle 4 in the axial direction, which saves on axial installation space.
  • the assembly opening 33 is closed by means of a compressor housing cover 34 which has at least one compressor impeller sealing contour 35 adapted to the compressor impeller 13 and an intake manifold connection piece 37 and thus completes the turbocharger housing 2 .
  • the assembly opening is only so large that the turbo rotor cartridge 10 can be easily inserted into the rotor receiving shaft 4 in the axial direction.
  • the compressor spiral duct 32 are formed completely, including the spiral channel tongue (not visible in FIG. 1) and the diffuser gap 38, at least partially in the one-piece integral turbotortor housing 3.
  • the aforementioned configuration of the exhaust gas turbocharger advantageously reduces the total number of individual components and the required assembly processes. Furthermore, the number of housing interfaces to be sealed off from the environment is also reduced to a minimum and their overall length is also reduced to a minimum. This in turn has an advantageous effect on the production costs and on operation that is improved with regard to undesired emissions.
  • the present invention is therefore based on the object of specifying a turbocharger housing and an exhaust gas turbocharger which are characterized by an integral turbotor housing which, in comparison to the prior art, is simpler and cheaper to produce in a casting process and thus further reduces the production costs contributes.
  • the turbocharger housing and the exhaust gas turbocharger are characterized in that the turbine housing, including the exhaust gas spiral duct, the bearing housing and the compressor housing, including the air spiral duct, are combined to form an integral turbotor housing, which is designed, for example, as a one-piece cast part and a Having rotor receiving shaft with an internal geometry for a turbo rotor cartridge.
  • the inside diameter of the assembly opening is enlarged at least to the outer edge area of the compressor spiral duct, and at least a part of a contour of a spiral duct tongue and a part of the housing edge of the compressor spiral duct are formed on the inside of the compressor housing cover.
  • the aforementioned configuration of the turbocharger housing and the exhaust gas turbocharger advantageously reduces the total number of individual components and the assembly processes required. Furthermore, the number of housing interfaces to be sealed off from the environment is also reduced to a minimum and their overall length is also reduced to a minimum.
  • the production of the integral turbotor housing is simplified in particular by the inventive design of the assembly opening and the compressor housing cover in that fewer undercuts have to be considered, which complicate the design of the casting molds and casting core elements and thus make the turbocharger housing and the exhaust gas turbocharger more expensive.
  • the demoulding simplified by the design according to the invention also reduces the proportion of rejects in production and extends the service life of the casting molds. All this ultimately has an advantageous effect on the production costs.
  • turbocharger housings and exhaust gas turbochargers as well as further advantageous configurations and developments of the objects according to the invention are illustrated and explained below with reference to the individual figures of the attached drawing.
  • FIG. 1 shows an exhaust gas turbocharger with the essential components, in a simplified schematic sectional representation, for representing the prior art and for explaining the terms used;
  • FIG. 2 shows an exemplary embodiment of a turbocharger housing and exhaust gas turbocharger according to the invention in a disassembled state and a simplified sectional view of the components;
  • FIG. 3 shows a front view of an opened integral turbo rotor housing with an inserted turbo rotor cartridge but without a compressor housing cover;
  • FIG. 4 shows a perspective view of an embodiment of the compressor housing cover according to the invention
  • FIG. 5 shows the design of the compressor housing cover shown in FIG. 4 in a half-section illustration.
  • FIG. 1 shows a schematic representation of an exhaust gas turbocharger 1 with a conventional integral turbotor housing 3 in a sectional representation, according to the known prior art and serves to explain the basic structure of an exhaust gas turbocharger 1 from exhaust gas turbine 20 air compressor 30, turbo rotor cartridge 10 and shaft bearing cartridge 40
  • the structure in detail has already been described in the introduction above.
  • turbocharger housing 2 for an exhaust gas turbocharger 1 of an internal combustion engine, which has an integral turbotor housing 3 and a compressor housing cover 34 .
  • the integral turbotortor housing 3 is made in one piece and has at least
  • a rotor receiving shaft 4 for a turbo rotor cartridge 10 which axially extends in the direction of a turbocharger axis 6,
  • the assembly opening 33 can be closed with the compressor housing cover 34 .
  • the compressor housing cover 34 has at least one suction pipe connecting piece 37 and a cover inner side 34a facing the rotor receiving shaft 4 with a compressor impeller sealing contour 35 .
  • the embodiment according to the invention shown is characterized in that the clear diameter D of the assembly opening 33 is expanded at least up to the outer edge region of the compressor spiral channel 32, ie at least up to the housing edge 32d of the compressor spiral channel 32 on the compressor housing 31, and on the cover Inside 34a of the compressor housing cover 34 at least a part of a contour of a spiral channel tongue 32a and the housing edge 32c of the compressor spiral channel 32 is formed.
  • turbo rotor cartridge 10 is shown outside the integral turbo rotor housing 3, in the rotor receiving shaft 4 of which it is inserted in the axial joining direction, which is symbolized by an arrow.
  • the turbo rotor cartridge 10 has a shaft bearing cartridge 40, a rotor shaft 14 which extends through the shaft bearing cartridge 40 and is rotatably mounted therein about the rotor axis of rotation 15, a turbine impeller 12 which is arranged at one end of the rotor shaft 14 and a compressor impeller 13 which is arranged at an opposite end of the rotor shaft 14.
  • turbo rotor cartridge 10 and compressor housing cover 34 When the exhaust gas turbocharger 1 is assembled with the integral turbotor housing 3, turbo rotor cartridge 10 and compressor housing cover 34, the rotor axis of rotation 15 coincides with the turbocharger axis 6; the turbine impeller 12 is arranged in the turbine housing 21.
  • the compressor impeller 13 is arranged in the compressor housing 31 and the assembly opening 33 is closed by means of the compressor housing cover 34 .
  • the compressor impeller sealing contour 35 comprises the blading of the compressor impeller 13 and the compressor spiral duct 32 is formed by the part of the housing edge 32c of the compressor spiral duct 32 formed on the inside of the cover 34a and by the part of the contour of the compressor volute formed on the inside of the cover 34a Spiral channel tongue 32a, completed.
  • a further feature shown in Fig. 2 corresponds to an embodiment which is characterized in that the compressor spiral channel 32 is arranged in such a way that at least a part of the compressor spiral channel 32 surrounds the rotor receiving shaft 4 in the axial direction, in relation to the turbocharger axis 6 , at least partially overlapping.
  • a part of the compressor spiral channel 32 protrudes in the direction of the turbocharger axis 6 to the right a little way over the rotor receiving shaft and encompasses the rotor receiving shaft 4 over the circumference.
  • Such an embodiment advantageously saves axial installation space due to the overlapping of the geometries.
  • a dividing plane T which is essentially perpendicular to the turbocharger axis 6, is laid between the integral turbotor housing 3 and the compressor housing cover (34) through an outer peripheral line of the compressor spiral duct (32), which, with reference to the turbocharger axis 6, runs along the radially outermost points of an inner contour of the compressor spiral channel (32) over its circumference.
  • the radially outermost points of the inner contour of the compressor volute duct 32 are the points of the inner contour of the compressor volute duct 32 which have the greatest radial distance from the turbocharger axis 6 at the respective point on its circumference.
  • the parting plane T is shown in FIG.
  • the parting plane T in this example deviates slightly from the right angle with respect to the turbocharger axis 6 .
  • an angular deviation from the perpendicular to the turbocharger axis 6 can occur, which is generally less than or equal to 22.5 degrees, which in this context is understood to be essentially perpendicular to the turbocharger axis 6 .
  • the parting plane T can optionally also be perpendicular to the turbocharger axis 6 .
  • This position of the parting plane T ensures that there are no undercuts in the direction of the turbocharger axis 6 either on the side of the compressor housing 31 or on the side of the compressor housing cover 34 due to the shaping of the respective portions of the housing edge 32c, 32d.
  • a further embodiment of the turbocharger housing 2 according to the invention is characterized in that the integral turbotortor housing 3 is an integral part of a cylinder head housing 50 or an engine housing 51 of an internal combustion engine. This is shown in FIG. 2 by a dash-dotted line encompassing the integral turbotortor housing 3 and symbolically embodying a cylinder head housing or a motor housing 51 .
  • the integration of the integral turbotortor housing 3 in the cylinder head housing 50 or the engine housing 51 of an internal combustion engine increases the complexity of the respective housing, but reduces the number of parts and the assembly effort. Furthermore, the number of interfaces between the exhaust gas turbocharger 1 and the internal combustion engine is reduced, and failure of these interfaces with regard to tightness is thus avoided.
  • FIG. 3 An integral turbo rotor housing 3 with an inserted turbo rotor cartridge 10 according to the invention is shown in FIG. 3 in a front view in the axial direction of the assembly opening 33 in the compressor housing 31 with the compressor housing cover 34 removed.
  • Compressor spiral channel 32 and the portion of spiral channel tongue 32b formed in compressor housing 31 can be seen, below which compressor spiral channel 32 begins, which in this example then runs counterclockwise around turbocharger axis 6, with its cross section permanently increasing until it in turn merges tangentially into the air discharge duct 36 in the area of the spiral duct tongue 32b, with the spiral duct tongue 32b separating the air discharge duct 36 from the compressor spiral duct 32 and representing a flow-guiding element that diverts the air flow from the compressor spiral duct 32 into the air discharge duct 36.
  • the clear diameter D of the assembly opening 33 is enlarged at least as far as the outer edge area of the compressor volute duct 32 and beyond the volute duct tongue 32b to the housing edge 32d of the compressor volute duct 32 on the compressor housing 31.
  • FIG. 4 shows an embodiment of a compressor housing cover 34 according to the invention in a perspective representation with a view of the inside 34a of the cover with the compressor impeller sealing contour 35 which merges into the air discharge duct 36 . It is also easy to see that on the inside of the cover 34a of the compressor housing sedeckels 34 at least part of a contour of a spiral channel tongue 32a and a housing edge 32c of the compressor spiral channel 32 is formed.
  • FIG. 5 shows the design of the compressor housing cover 34 shown in FIG. 4 in a half-section illustration.
  • the compressor impeller sealing contour 35 which merges into the air discharge duct 36 , is arranged on the inside 34a of the cover. It can also be clearly seen that at least part of a contour of a spiral channel tongue 32a and a housing edge 32c of the compressor spiral channel 32 is formed on the inside 34a of the compressor housing cover 34 .
  • the intake manifold connection piece 37 can be seen, via which the turbocharger housing 2 can be connected to the air supply unit of an internal combustion engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Supercharger (AREA)

Abstract

L'invention concerne un carter de turbocompresseur (2) pour un turbocompresseur à gaz d'échappement (1) d'un moteur à combustion interne, et un turbocompresseur à gaz d'échappement comprenant un tel carter de turbocompresseur (2). Le carter de turbocompresseur (2) comprend un carter intégré de turbo-rotor (3) conçu sous forme d'une seule pièce et un couvercle de carter de compresseur (34), le carter intégré de turbo-rotor (3) comprenant un arbre de réception de rotor (4) pour une cartouche de turbo-rotor (10), un carter de turbine (21) ayant au moins un canal en spirale de turbine (22) et un carter de compresseur (31) ayant un canal en spirale de compresseur (32) et un canal d'évacuation d'air (36) adjacent à celui-ci. Le carter intégré de turbo-rotor (3) comprend, sur le côté du carter de compresseur (31), une ouverture d'assemblage de face d'extrémité (33) à travers laquelle la cartouche de turbo-rotor (10) peut être insérée dans l'arbre de réception de rotor (4) du carter intégré de turbo-rotor (3) dans une direction de jonction axiale s'étendant parallèlement à l'axe de turbocompresseur (6). L'ouverture d'assemblage (33) peut être fermée avec le couvercle de carter de compresseur (34), ce dernier comprenant au moins une pièce de raccordement de tuyau d'aspiration (37) et un côté interne de couvercle (34a) faisant face à l'arbre de réception de rotor (4), sur lequel est formé un contour d'étanchéité d'hélice de compresseur (35) et au moins une partie d'un contour d'une languette de canal en spirale (32a) et un bord de carter (32b) du canal en spirale de compresseur (32).
PCT/EP2022/073171 2021-10-14 2022-08-19 Carter de turbocompresseur et turbocompresseur à gaz d'échappement avec carter de turbo-rotor intégré et couvercle de carter de compresseur WO2023061641A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021211624.8A DE102021211624A1 (de) 2021-10-14 2021-10-14 Turboladergehäuse und Abgasturbolader mit Integral-Turborotorgehäuse und Verdichtergehäusedeckel
DE102021211624.8 2021-10-14

Publications (1)

Publication Number Publication Date
WO2023061641A1 true WO2023061641A1 (fr) 2023-04-20

Family

ID=83271428

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2022/073171 WO2023061641A1 (fr) 2021-10-14 2022-08-19 Carter de turbocompresseur et turbocompresseur à gaz d'échappement avec carter de turbo-rotor intégré et couvercle de carter de compresseur

Country Status (2)

Country Link
DE (1) DE102021211624A1 (fr)
WO (1) WO2023061641A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3734650A (en) * 1970-05-02 1973-05-22 Kuehnle Kopp Kausch Ag Exhaust-gas driven turbochargers
DE102007055617A1 (de) * 2007-11-20 2009-05-28 Inprosim Gmbh Gehäuse für einen Radialverdichter
DE102014214226A1 (de) * 2014-07-22 2016-01-28 Continental Automotive Gmbh Verbundverdichtergehäuse
US9683482B2 (en) * 2010-12-09 2017-06-20 Continental Automotive Gmbh Turbocharger which is integrated into the cylinder head of an engine
DE102020202967A1 (de) 2020-03-09 2021-09-09 Vitesco Technologies GmbH Abgasturbolader mit Integralgehäuse

Family Cites Families (3)

* 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
DE102010030516A1 (de) 2010-06-25 2011-12-29 Bayerische Motoren Werke Aktiengesellschaft Abgasturbolader für eine Brennkraftmaschine
US9091200B2 (en) 2012-03-21 2015-07-28 Honeywell International Inc. Turbocharger and engine cylinder head assembly

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3734650A (en) * 1970-05-02 1973-05-22 Kuehnle Kopp Kausch Ag Exhaust-gas driven turbochargers
DE102007055617A1 (de) * 2007-11-20 2009-05-28 Inprosim Gmbh Gehäuse für einen Radialverdichter
US9683482B2 (en) * 2010-12-09 2017-06-20 Continental Automotive Gmbh Turbocharger which is integrated into the cylinder head of an engine
DE102014214226A1 (de) * 2014-07-22 2016-01-28 Continental Automotive Gmbh Verbundverdichtergehäuse
DE102020202967A1 (de) 2020-03-09 2021-09-09 Vitesco Technologies GmbH Abgasturbolader mit Integralgehäuse

Also Published As

Publication number Publication date
DE102021211624A1 (de) 2023-04-20

Similar Documents

Publication Publication Date Title
DE60022044T2 (de) Druckgussgehäuse für kreiselkompressoren mit echter spiralform
EP2242931B1 (fr) Structure d'écoulement pour turbocompresseur
DE112015001237B4 (de) Abgasturbolader
DE102018221812B4 (de) Abgasturbine mit einer Abgasleiteinrichtung für einen Abgasturbolader und Abgasturbolader
EP2859190B1 (fr) Carter de turbine pour turbocompresseur à gaz d'echappement
DE102017201468A1 (de) Turbolader für eine Brennkraftmaschine
EP3183079B1 (fr) Modèle de coulée de boîtier, série de boîtier et procédé de fabrication d'un boîtier coulé d'une turbomachine à énergie fluidique radiale
EP2112332B1 (fr) Anneau support de distributeur avec canal pressurisé
DE102020202967A1 (de) Abgasturbolader mit Integralgehäuse
DE102012205198A1 (de) Turbolader für eine Brennkraftmaschine
DE112011102809T5 (de) Lagergehäuse eines Abgasturboladers
EP1500788A1 (fr) Volute à double flux
DE102012022647A1 (de) Abgasturbolader für eine Verbrennungskraftmaschine
WO2023061641A1 (fr) Carter de turbocompresseur et turbocompresseur à gaz d'échappement avec carter de turbo-rotor intégré et couvercle de carter de compresseur
DE102015012225A1 (de) Leiteinrichtung für einen Verdichter eines Abgasturboladers
DE60115025T2 (de) Gegossenes spiralgehäuse für einen turbolader
EP3601739B1 (fr) Turbocompresseur pour un moteur à combustion interne ainsi que roue de turbine
DE102011111702A1 (de) Turbine für einen Abgasturbolader
DE102018222289B3 (de) Radialverdichter mit Kennfeldstabilisierung für eine Aufladevorrichtung einer Brennkraftmaschine und Aufladevorrichtung
DE102020005110A1 (de) Abgasrückführungseinrichtung für eine Verbrennungskraftmaschine insbesondere eines Kraftfahrzeugs
WO2016184549A1 (fr) Compresseur centrifuge, en particulier pour un turbocompresseur à gaz d'échappement d'un moteur à combustion interne
DE102012212738A1 (de) Diffusorbaugruppe für einen Abgasturbolader
DE102009058102A1 (de) Verdichter für eine Aufladeeinrichtung
WO2021032711A1 (fr) Compresseur électrique doté d'un manchon de réception de palier
WO2021032714A1 (fr) Compresseur électrique comprenant un manchon de réception de palier séparé

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22768354

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE