WO2020120174A1 - Compresseur électrique présentant un dispositif de compensation de pression semiperméable - Google Patents

Compresseur électrique présentant un dispositif de compensation de pression semiperméable Download PDF

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Publication number
WO2020120174A1
WO2020120174A1 PCT/EP2019/083112 EP2019083112W WO2020120174A1 WO 2020120174 A1 WO2020120174 A1 WO 2020120174A1 EP 2019083112 W EP2019083112 W EP 2019083112W WO 2020120174 A1 WO2020120174 A1 WO 2020120174A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
compressor
pressure compensation
motor
partition
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.)
Ceased
Application number
PCT/EP2019/083112
Other languages
German (de)
English (en)
Inventor
Dominik Just
Sasa SLAVIC
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.)
Vitesco Technologies GmbH
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 WO2020120174A1 publication Critical patent/WO2020120174A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F02B39/02—Drives of pumps; Varying pump drive gear ratio
    • F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
    • F02B39/10—Non-mechanical drives, e.g. fluid drives having variable gear ratio electric
    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
    • F02B33/40—Engines with pumps other than of reciprocating-piston type with rotary pumps of non-positive-displacement type
    • 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
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • 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
    • F04D29/08—Sealings
    • F04D29/083—Sealings especially adapted for elastic fluid pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to an electric compressor designed as an electric motor-operated impeller compressor with a housing partition between
  • Compressor housing and electric motor housing in particular for arrangement and for use in a supercharging system of an internal combustion engine, in particular an internal combustion engine in a motor vehicle.
  • exhaust gas turbocharger systems are increasingly being used, with the aid of which the energy contained in the exhaust gas of the internal combustion engine is used to generate the pressure in the intake tract.
  • the turbocharger is effective due to the system only by the increasing exhaust gas pressure. For this reason and reinforced by the inertial mass of the turbocharger rotor, the pressure builds up in the
  • Intake tract is delayed, which in turn results in a delayed response of the internal combustion engine, which is generally referred to as a so-called turbo lag.
  • Another approach is to provide an alternative or additional arrangement that can be operated independently of the exhaust gas flow Compressor unit in the intake tract, which is used specifically in transient operating phases of the internal combustion engine, for the rapid build-up of pressure in the intake tract, i.e. to eliminate a performance hole.
  • Compressors operated by an electric motor which are also referred to as an e-booster or e-compressor and as an electrically driven compressor (EAV), which have been referred to above and below as an electric compressor, have proven to be advantageous for this application.
  • EAV electrically driven compressor
  • the compressor component itself is usually designed as an impeller compressor and thus has the same or a similar structure as an impeller compressor used in an exhaust gas turbocharger.
  • Such impeller compressors are designed in known designs as radial compressors, as radial-axial compressors (mixed-flow compressors) or as axial compressors and have a compressor impeller with one arranged on an impeller hub
  • Impeller blading on The compressor impeller arranged in a compressor housing on a rotor shaft is driven at high speed, in this case by an electric motor, usually draws in the medium to be compressed in the axial direction and guides the compressed medium in a through the impeller blading and the impeller hub, and that surrounding compressor housing predetermined direction.
  • the respective designation indicates the direction of the compressed medium flowing out.
  • Such an electric compressor has an impeller compressor designed as a radial compressor with one
  • Housing partition provided, which also serves as a housing cover for the
  • Compressor housing as well as for the motor housing and closes the two housings or, in other words, separates the compressor housing interior from the engine housing interior and accommodates at least one bearing of the compressor rotor. Furthermore, an electrical usually closes
  • Control unit for the electric motor to the electric motor housing which can, however, also be arranged separately.
  • the compressor rotor is usually rotatably mounted with its rotor shaft by means of two individual bearings in the electric motor housing, at least one individual bearing being accommodated in the housing cover of the motor housing or the housing partition.
  • a known weak point is the passage of the rotor shaft through the housing cover of the motor housing or the housing partition between the motor housing and the compressor housing.
  • a corresponding shaft seal must meet very high requirements with regard to temperature, shaft speed and the resulting service life. Corresponding shaft seals cause increased manufacturing costs for an electric compressor.
  • the object underlying the invention is therefore one
  • Electric compressor i.e. one connected to an electric motor and
  • the electric compressor which is particularly suitable for arrangement in a charging system of an internal combustion engine, has an impeller compressor with a compressor housing,
  • an electric motor with a motor housing and a housing partition between the compressor housing and the motor housing.
  • Compressor housing arranged and a stator and a rotor is in one
  • Motor housing interior arranged.
  • the compressor impeller and the rotor are by means of a
  • Housing partition wall guided, rotatable about a rotor axis of rotation and by means of a bearing arrangement at least in the housing partition wall-mounted rotor shaft.
  • Housing partition is arranged at least one pressure compensation device.
  • This pressure compensation device has at least one through opening that leads from the compressor housing interior to the engine housing interior and on the side of the housing partition wall facing the engine housing interior, by means of a semi-permeable pressure compensation membrane, opposite the
  • Pressure equalization membrane has the property of being permeable to air in both directions but being impermeable to water in all forms, oil in all forms and particles such as fine dust and soot.
  • Membranes are available and are known, for example, under the brand name "GoreTex".
  • the corresponding medium i.e. compressor air with low resistance, flows through the compressor compensation opening through the pressure compensation opening in the housing partition and the semi-permeable pressure compensation membrane into the motor housing and thus ensures pressure compensation, but at the same time keeps the impurities contained in the compressor air away from the electric motor components.
  • This design has the advantage that the pressure difference between the compressor housing and the motor housing can be compensated for by the pressure compensation device, and so there is no flushing of the rotor bearing due to the lack of a pressure gradient. It is therefore possible to use cheaper components for the shaft seal or to dispense with a shaft seal altogether and the manufacturing costs can be reduced as a result.
  • FIG. 1 An embodiment of an electric compressor according to the invention with the essential components, in a simplified schematic sectional view;
  • Fig. 2 shows an embodiment of an electric compressor according to the invention, using the section X marked in Figure 1.
  • Electric compressor with a pressure compensation chamber designed as an annular groove, on the basis of the section X marked in FIG. 1.
  • Fig. 5 shows an example of a pressure compensation membrane in a membrane carrier for mounting on the housing partition of another embodiment of the
  • FIG. 6 Another example of a pressure compensation membrane in one
  • the electric motor 20 also has a stator 23 connected to the cup wall 21 c of the motor housing 21 and a rotor 12 arranged on the rotor shaft 14.
  • a housing partition 22 is arranged between the compressor housing 31 and the motor housing 21, but connects the two housings to one another, but at the same time separates the compressor housing interior 31 a from the motor housing interior 21 a.
  • Rotor axis of rotation 15 of the rotor shaft 14 rotates.
  • the rotor axis of rotation 15 and the electric compressor axis 2 coincide and are represented by the center line drawn in, which characterizes the axial orientation of the electric compressor 1.
  • the rotor shaft 14 is guided through the housing partition 22 and rotatably supported at least in the housing partition 22 by means of a bearing arrangement 40.
  • a shaft seal 16 is provided which separates the interior of the motor housing 21 a and the interior of the compressor housing 31 a.
  • Motor control unit 50 for the electric motor in a control housing 51 to the motor housing 21, which could, however, also be arranged separately. To simplify matters, the electronic components are not shown here.
  • the electrical compressor 1 according to the invention shown is primarily characterized in that at least one in the housing partition 22
  • Pressure compensation device 24 is arranged, the at least one
  • the through opening 25, which is designed as a simple bore, opens into a recess in the
  • FIG. 1 a section X is marked, which is shown in an enlarged representation, in two sectional planes in the following figures.
  • Fig. 2 shows a further embodiment of an inventive
  • Design is characterized, inter alia, in that at least one through opening 25 is arranged in the housing partition 22 at a radial distance R from the rotor axis of rotation 15. Nevertheless, a plurality of pressure equalization devices of the same design and distributed over a circumference, as indicated by dashed lines in sectional view A-A of FIG. 2, can also be arranged in the housing partition wall 22.
  • the through openings 25 are each simple
  • the pressure compensation membrane 27 is surrounded by an edge 22d formed on the housing partition 22 and is, for example, within this edge 22d in FIG.
  • the pressure compensation membrane 26 has a larger surface area than the embodiment shown in FIG. 1 and a correspondingly increased “permeability”, which enables faster pressure compensation.
  • FIG. 3 shows a further embodiment of the electric compressor 1 according to the invention, in the same representation as FIG. 2, only the reference numbers to be emphasized being entered here for a better overview.
  • the recess forming the pressure compensation chamber 27 is designed as an annular groove 27 'which extends concentrically around the rotor axis of rotation 15 and the bearing receiving dome 22a and is covered by a pressure compensation membrane 26 which runs around the entire circumference of the annular groove 27'. This ensures a further enlarged surface of the pressure compensation membrane 26 and
  • the pressure compensation membrane 26 which runs around the entire circumference of the annular groove 27 ', has an outer clamping ring 28 in its radial outer region, that is to say in the region of the connecting flange 22b, and an inner clamping ring in its radially inner region, that is to say in the region of the bearing receiving dome 22a 29 attached to the housing partition 22. It goes without saying that the pressure compensation membrane 26 can also be fastened, for example glued, to the housing partition wall 22 or, if appropriate, also to the pot wall 21c in any other suitable manner.
  • the radius R on which the respective through openings 25 are arranged in the above-mentioned embodiments shown in FIGS. 1 to 3 is advantageously to be selected such that the through openings 25 lie in a radial area in which a pressure difference between
  • Compressor housing interior 31 a and engine housing interior 21 a has a maximum during operation.
  • Pressure level can be achieved, whereby a flushing of contaminated air from the compressor housing interior 31 a in the bearing arrangement 40 is effectively prevented.
  • FIG. 4 shows a further embodiment of the electric compressor 1 according to the invention, in the same representation as FIGS. 2 and 3, but here too, for the better
  • the structure of this embodiment differs from that shown in FIGS. 1 to 3 Example in particular in that the pressure compensation device 24 has a plurality of through openings 25, which are formed as flat openings 25 'in the
  • Housing partition 22 are designed radially between a bearing receiving dome 22a for the bearing arrangement 40 and the connecting flange 22b for a cup wall 21c of the motor housing 21.
  • the bearing receiving dome 22a thus only stands with the housing partition over a plurality of spoke-like webs 22c
  • Pressure compensation membrane 26 and represents a large one
  • Pressure compensation membrane 26 which are received in a membrane carrier 60.
  • a corresponding further exemplary embodiment of the electric compressor is accordingly distinguished in particular by the fact that the pressure compensation membrane 26 is received in the membrane carrier 60 and by means of this on the
  • the example of the membrane carrier 60 specifically shown in FIG. 5 has a round carrier disk 61 with a plurality of membrane windows, similar to the flat openings shown in FIG. 4, and a central rotor shaft bore 62.
  • the pressure compensation membrane 26 is arranged in the membrane windows and the rotor shaft 14 is guided through the rotor shaft bore 62 in the assembled state.
  • the carrier disk has screw receiving bores 63, through which, in the assembled state, fastening screws are guided, with which the membrane carrier 60 is fastened to the housing partition wall 22.
  • the example of the membrane carrier 60 shown in FIG. 6, on the other hand, has only one carrier ring with a pressure compensation membrane 26 stretched therein.
  • Such an embodiment would be for example in combination with the
  • Embodiment of FIG. 2 suitable.
  • FIGS. 5 and 6 have the advantage that a
  • Membrane carriers are available at low cost as a prefabricated solid component and can be easily and automatically mounted or attached to the housing partition or in the motor housing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un compresseur électrique (1) conçu comme un compresseur à hélice actionné par un moteur électrique, en particulier destiné à être disposé dans un système de chargement d'un moteur à combustion interne, qui présente un compresseur à hélice (30) pourvu d'un carter de compresseur (31), un moteur électrique (20) présentant un carter de moteur (21) et une paroi de séparation des carters (22) entre le carter de compresseur (31) et le carter du moteur (21). L'hélice du compresseur (13) dans l'espace interne (31a) du carter de compresseur et un rotor (12) dans l'espace interne (21a) du carter de moteur sont reliés au moyen d'un arbre de rotor (14) guidé à travers la paroi de séparation des carters (22) et logé rotatif au moyen d'une disposition de palier (40) au moins dans la paroi de séparation de carters (22). Au moins un dispositif de compensation de pression (24) est disposé dans la paroi de séparation des carters et présente au moins une ouverture de passage (25) qui est recouverte au moyen d'une membrane de compensation de pression (26) semiperméable par rapport à l'espace interne (21a) du carter de moteur.
PCT/EP2019/083112 2018-12-12 2019-11-29 Compresseur électrique présentant un dispositif de compensation de pression semiperméable Ceased WO2020120174A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018221556.1A DE102018221556A1 (de) 2018-12-12 2018-12-12 Elektro-Verdichter mit einer semipermeablen Druckausgleichseinrichtung
DE102018221556.1 2018-12-12

Publications (1)

Publication Number Publication Date
WO2020120174A1 true WO2020120174A1 (fr) 2020-06-18

Family

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Family Applications (1)

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PCT/EP2019/083112 Ceased WO2020120174A1 (fr) 2018-12-12 2019-11-29 Compresseur électrique présentant un dispositif de compensation de pression semiperméable

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DE (1) DE102018221556A1 (fr)
WO (1) WO2020120174A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024217662A1 (fr) * 2023-04-18 2024-10-24 Pierburg Pump Technology Gmbh Pompe à flux de gaz électrique

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2952748A1 (fr) * 2014-06-06 2015-12-09 BorgWarner, Inc. Dispositif de chargement pour un moteur à combustion interne
FR3045722A1 (fr) * 2015-12-17 2017-06-23 Valeo Systemes De Controle Moteur Compresseur electrique avec systeme d'etancheite dynamique ameliore

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1257580B (de) * 1962-01-05 1967-12-28 Poul Due Jensen Abdichtungseinrichtung zwischen Motor und Pumpe eines Spaltrohrmotorpumpenaggregats
DE2550201A1 (de) * 1975-11-08 1977-05-18 Hermetic Pumpen Gmbh Hermetisch abgekapselter elektrischer pumpen-antrieb

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2952748A1 (fr) * 2014-06-06 2015-12-09 BorgWarner, Inc. Dispositif de chargement pour un moteur à combustion interne
FR3045722A1 (fr) * 2015-12-17 2017-06-23 Valeo Systemes De Controle Moteur Compresseur electrique avec systeme d'etancheite dynamique ameliore

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024217662A1 (fr) * 2023-04-18 2024-10-24 Pierburg Pump Technology Gmbh Pompe à flux de gaz électrique

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DE102018221556A1 (de) 2020-06-18

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