WO2004016952A1 - Roue de compresseur - Google Patents

Roue de compresseur Download PDF

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Publication number
WO2004016952A1
WO2004016952A1 PCT/DE2003/002307 DE0302307W WO2004016952A1 WO 2004016952 A1 WO2004016952 A1 WO 2004016952A1 DE 0302307 W DE0302307 W DE 0302307W WO 2004016952 A1 WO2004016952 A1 WO 2004016952A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
compressor wheel
wheel
blades
housing
Prior art date
Application number
PCT/DE2003/002307
Other languages
German (de)
English (en)
Inventor
Martin-Peter Bolz
Michael Baeuerle
Ken Zschweigert
Gunter Winkler
Bernhard Krause
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2004016952A1 publication Critical patent/WO2004016952A1/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
    • F04D29/26—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
    • 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
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials 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
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber

Definitions

  • the invention relates to a device for compressing combustion air, in particular for an automotive internal combustion engine, with the features of the preamble of claim 1, and a method for producing such a device.
  • the exhaust gas turbocharger has a turbine which is arranged in the exhaust gas flow of the internal combustion engine and operates a compressor which is arranged in the charge air supply of the internal combustion engine.
  • the design of the flow compressor for additional electrical compressors is based on the design of exhaust gas turbochargers and corresponds to this in design and
  • the object on which the present invention is based is to optimize a generic additional electric compressor to the effect that it maintains a compact response while maintaining the best possible response and, as a result, enables it to reach its maximum speed as quickly as possible.
  • the device according to the invention for compressing combustion air, in particular combustion air for a motor vehicle internal combustion engine, with the features of claim 1 has the advantage over the charge air compressors of the prior art that, owing to the low inertia of the device according to the invention
  • Compressor wheel a very fast run-up of the compressor and a correspondingly quick reaching of the optimal number of revolutions of the compressor wheel can be realized without excessive stress on the electrical system.
  • the realization of the compressor impeller in plastic leads to improved dynamic properties in the rotor due to the lower moment of inertia Comparison to the metallic compressor wheels of the prior art.
  • the use of compressor impellers made of plastic brings considerable advantages, whereby the high stability of the rotor required can be taken into account by a suitable choice of material and corresponding structural developments.
  • the device for compressing combustion air according to the invention also enables the use of cost-effective manufacturing processes, so that the material costs of a corresponding compressor are significantly reduced and its assembly can be made considerably easier.
  • Compression can be achieved. Due to the larger compressor wheel, the maximum speed of the compressor can also be reduced, which leads to a corresponding reduction in the material load and in particular that of the drive. In addition, it is possible to optimize the geometry design with a view to optimum dimensional stability and strength of the compressor wheel due to the easily formable plastic material.
  • the compressor wheel has a cover disk, which is also made of plastic and with which
  • Fuselage of the compressor wheel is installed. This measure improves the rigidity of the compressor wheel and reduces the gap losses of the compressor.
  • a further increase in the strength of the compressor wheel according to the invention results from the use of a base plate which is connected to the compressor blades and fixed it.
  • support elements can be formed in an advantageous manner which additionally increase the mechanical stability of the compressor wheel according to the invention.
  • the base plate can be ribbed in a star shape in the axial direction, and the base ribbing can be designed with a rib thickness that decreases over the impeller radius.
  • the varying material thickness of these support elements for the base plate of the compression wheel ensures an optimization between the required rigidity of the compressor wheel and the lowest possible moment of inertia of the same.
  • the compressor blades with their interior ie. H. begin their end facing the shaft exactly above a support element of the ribbing of the base plate.
  • each compressor blade can be assigned a corresponding support element on the underside of the base plate.
  • the ribbing of the base plate of the compressor wheel can advantageously be designed such that the compressor blades sweep over the corresponding support elements of the base plate at an almost right angle. In this way, it is possible to avoid or significantly reduce undesirable multi-axis stress states in the base plate of the compressor wheel.
  • the almost right-angled overlap of the compressor blades with the associated support elements of the base rib can advantageously be achieved in that the support elements of the base plate have a cranked end region in their radial alignment, which deviates from the radial preferred direction of the ribs. Multiaxial stressing of the base plate is also largely avoided in this way, with an additional, stabilizing effect for the base plate of the compressor wheel. Due to these strength-related consequences of the cranked ribbing of the base plate of the The compressor wheel can be operated with comparatively thin ribs, so that a corresponding reduction in material and thus a reduction in the moment of inertia of the compressor wheel is possible.
  • the offset of the ribs follows directly from the blending situation between the base plate and the base ribs forming the support elements for the base plate.
  • three-dimensionally curved compressor blades can be formed for the compressor wheel according to the invention, which, for example, can also be approximately T-shaped or in the form of a one-sided T-shaped.
  • one leg of the compressor blades can run essentially parallel to the axis of the drive shaft of the compressor wheel and a second leg of the compressor blade can be oriented predominantly radially to this axis.
  • Dispensing with the base plate of the compressor wheel means a considerable reduction in material and thus also in mass, and advantageously enables an additionally reduced moment of inertia.
  • a metallic hub insert can be used to transmit positive force from the
  • the hub has in the axial direction at least one recess or a recess in the extruded profile, in which the plastic compressor wheel engages and is thus axially secured.
  • the device according to the invention can advantageously be driven by an electric motor integrated in the housing of the device.
  • the rotor of the electric drive is operatively connected to the shaft of the compressor wheel. Due to the low mass moment of inertia of the compressor wheel, good dynamic properties result for the electrically driven compressor.
  • a typical operating range of the compressor according to the invention is in the range between 45,000 and 80,000
  • a compressor impeller which consists of a polymer, or of a composite of several polymers, or fiber-reinforced polymers, is distinguished, among other things, by the following advantages.
  • a compressor wheel enables high stability with a low material weight. Due to the low moment of inertia of the compressor wheel, the compressor has good dynamic properties.
  • PPS polyphenylene sulfide
  • PEEK polyether ether ketone
  • These materials enable an improved dynamic of the compressor due to the lower moment of inertia, which results from the lower mass density.
  • this selection of materials also enables the use of cost-effective production methods for the compressor impeller according to the invention and thus for the device for compressing combustion air according to the invention. In this way, geometry shaping measures that are especially suitable for plastics can be carried out in the
  • the compressor wheel itself can, for example, be extrusion-coated directly around the metallic insert hub and detached from the corresponding injection mold in an axial demolding process. In this way, a mechanically stable compressor wheel can be manufactured inexpensively. Further advantages of the device for compressing combustion air according to the invention can be found in the following drawing and the associated description of some exemplary embodiments.
  • FIG. 1 shows a cross section through an electrically operated charge air compressor in a schematic representation
  • FIG. 2 shows a first exemplary embodiment of a compressor wheel according to the invention in a perspective view
  • FIG. 3 shows the compressor wheel according to the invention according to FIG. 2 in axial supervision
  • FIG. 4 shows a section through the compressor wheel according to the invention according to FIG. 3
  • FIG. 5 is a perspective view of a second exemplary embodiment of a compressor wheel according to the invention.
  • FIG. 6 shows a further embodiment of a compressor wheel according to the invention in a perspective view
  • FIG. 7 is a perspective view of the underside of the compressor wheel according to the invention according to FIG. 6, 8 the view of the underside of a further exemplary embodiment of a compression vane according to the invention in a perspective, sectional representation,
  • FIG. 9 shows a schematic illustration of the course of the support elements and of the compressor blades of a compressor wheel according to the invention according to FIG. 8,
  • Fig. 10 shows an embodiment of a hub insert according to the invention in a perspective view.
  • FIG. 1 shows an exemplary embodiment of a device according to the invention for compressing combustion air, in particular for an automotive internal combustion engine, in a simplified schematic overview.
  • Charge air compressor 10 has a housing 12 in which an electric motor 14 and a compressor part 16 are integrated.
  • the compressor part 16 is designed as a radial compressor.
  • a compressor housing 18 has a cup-shaped base part 20 with a circular bottom wall 22. Opposite the bottom wall 22, the compressor housing 18 has a funnel-shaped cover wall 24 which has a central opening 26 which represents the air inlet 28 of the charge air compressor 10.
  • the space 30 between the bottom wall 22 and the top wall 24 forms the compressor space 32 of the charge air compressor 10 and is connected to the interior 36 of a worm 38 designed as a hollow body through a lateral opening 34 which extends in the circumferential direction of the compressor housing 18.
  • the worm 38 has a diameter that increases in the circumferential direction of the compressor housing 18.
  • the end region in the section of the worm 38 has an air outlet 40 which can be connected to the combustion chamber of an engine via corresponding connecting means.
  • a compression wheel 42 is arranged in the compressor chamber 32 of the charge air compressor 10 and is driven by the electric motor 14 of the charge air compressor 10 via a shaft 44.
  • the compressor wheel 42 has an underside 46 which faces the bottom wall 22 of the compressor housing 18.
  • the shaft 44 is passed through the bottom wall 22 of the compressor housing 18 and operatively connected to the rotor 48 of the electric motor 14.
  • the upper side 50 of the compressor wheel facing away from the underside 46 of the compressor wheel 42 is provided in a manner known per se with compressor structures 52 in the form of three-dimensionally structured compressor blades 54, the outermost edge 56 of which protrudes toward the cover wall 24 is adapted to the inner contour of the funnel-shaped cover wall 24 ,
  • a flow channel 58 extends for the charge air at the
  • the section of the flow channel 58 which is formed on the inside of the cover wall 24 and extends along it up to the opening 34 forms a compressor section.
  • the electric motor 14 for driving the compressor wheel 42 comprises a stator 60 and a rotor 48, which are arranged in a motor housing 62.
  • the motor housing 62 is placed on the bottom wall 22 of the compressor housing 18 and has an opening 64 for the passage of the drive shaft 44 of the compressor wheel 42.
  • the rotor 48 of the electric motor 14 in the exemplary embodiment in FIG. 1 is designed as a so-called inner rotor. But it is also possible to design the rotor 48 as a bell rotor, in which case the rotor is arranged concentrically around the stator.
  • Fig. 2 shows a first embodiment of a compressor wheel according to the invention in a perspective view.
  • the compressor wheel according to the exemplary embodiment in FIG. 2 has a central hub 70 for the operative connection of the compressor wheel 42 to the drive shaft 44, not shown, of the charge air compressor 10 according to the invention.
  • a plurality of three-dimensional curved compressor blades 54 are arranged on the circumference of the hub 70 and, in the case of the exemplary embodiment according to FIG. 2, are integrally formed with the hub.
  • the radial shape of the individual compressor blades 54 produces a uniform stress distribution in the component during operation.
  • the compressor wheel consists of a polymer material.
  • the compressor blades are approximately torsionally rigid in the form of a simple T-beam.
  • the compressor blades have a flat component 72 which is designed essentially in the axial direction of the compressor wheel (radial wheel type).
  • This component 72 of the compressor blades is adjoined in the direction of the suction opening 76 of the compressor wheel by a second compressor blade component 74, which runs essentially radially to the axis of the compressor wheel, the axial wheel type.
  • the compressor wheel has a cover disk 78 which is fixedly connected to the outer ends of the flat components 72 facing away from the hub 70.
  • the cover disk 78 thus ensures increased stability of the compressor wheel according to the invention, which is made of a plastic.
  • the cover disk 78 leads to an increased outlet pressure of the compressed charge air into the interior 36 of the screw 38 of the charge air compressor.
  • the suction opening 76 of the compressor wheel 42 faces the air inlet 28 of the charge air compressor, as is shown by way of example in FIG. 1.
  • the cover plate 78 of the compressor wheel 42 is also made of a polymer material and can also be welded to the fuselage of the body
  • FIG. 5 shows a second exemplary embodiment of a compressor wheel according to the invention, made of plastic, for a charge air compressor of an internal combustion engine.
  • the compressor wheel is made of a polymer or a fiber-reinforced polymer, such as polyphenylene sulfide (PPS) or polyether ether ketone (PEEK).
  • PPS polyphenylene sulfide
  • PEEK polyether ether ketone
  • Other plastics can also be used to form the compressor wheel according to the invention.
  • carbon fiber reinforced PPS for example "Stat-CON 1006" are possible materials.
  • the compressor wheel according to the exemplary embodiment in FIG. 5 has a large number of radially arranged, three-dimensionally curved compressor blades which are arranged in a star shape around a central ring 82 central ring 82 supports via corresponding radial struts
  • the compressor wheel according to the exemplary embodiment of FIG. 5 has a base plate 88 which is closed except for a central opening for the passage of the drive shaft of the electric motor.
  • the compressor blades 80 are formed in one piece from the base plate 88.
  • a corresponding base plate can be applied to the rim of the compressor blades and can be firmly connected to these, for example by gluing, welding or other connection methods known to the person skilled in the art.
  • the compressor blades 80 have an increasingly increasing curvature in the axial direction, starting from the base plate 88, and open almost tangentially in a plane parallel to the base plate 88, which comes to rest in the air inlet of the charge air compressor in the assembled state of the compressor wheel.
  • the special shape of the curved compressor blades 80 results from an optimization routine which relates aerodynamic properties, such as the highest possible compression ratio, to mechanical properties, such as the required stability and rigidity of the plastic compressor wheel.
  • the plastic material of the compressor wheel enables the molding processes known to those skilled in the art of plastics technology (for example casting or injection molding techniques)
  • FIG. 6 shows an alternative embodiment of a compressor wheel.
  • the compressor wheel according to the embodiment in FIG. 6 has a cover plate 90, which on the side facing away from the base plate 88 axial end of the compressor blades rests and is connected to them.
  • the cover plate 90 has a central opening 92 for the suction of the air to be compressed through the compressor blades.
  • the central ring 82, the edge 94 and the end of the compressor blades facing away from the base plate lie approximately in a common plane which runs parallel to the base plate.
  • the bottom disk 88 runs parallel to the bottom wall 22 of the compressor housing.
  • the air drawn in through the central opening 26 of the charge air compressor 10 passes through the central opening 92 of the compressor wheel into the interior of the compressor wheel, which is formed by the cover plate 90, the base plate 88 and the compressor blades 80.
  • the suctioned air in the compressor wheel is accelerated and compressed.
  • the air compressed in this way emerges at the radial ends 96 of the compressor blades and is, as already described, in FIGS
  • Inner roughness 36 of the compressor screw 38 passed.
  • FIG. 7 shows the underside of the compressor wheel according to the embodiment of FIG. 6.
  • the bottom disk 88 has, on its underside 98 facing away from the compressor blades 80, rib-shaped support elements 100 which have an essentially radial profile. Starting from the central hub element 86 for receiving a drive shaft, the axial height of the support elements is reduced with their radial expansion.
  • the star-shaped support elements are formed in one piece with the base plate 88 of the compression vein. The arranged in a star shape and also connected to the hub of the compressor wheel
  • Support elements 100 lead to an increased stability of the compression vein, which is made of a plastic, whereby stress peaks within the material are avoided.
  • the bottom rib 88 thus ribbed has an almost homogeneous stress distribution, so that the plastic compressor wheel according to the invention also in the Range of high speeds in the order of up to 100,000 rpm. can be used safely.
  • FIG. 8 shows a further embodiment of the compressor wheel according to the invention in a sectional detailed view.
  • the support elements 136 applied to the underside 134 of the base plate 132 have an essentially star-shaped or radial course.
  • the support elements 136 in accordance with the exemplary embodiment in FIG. 8 have a cranked end 130 which deviates from the main radial direction of the support elements.
  • the cranked support elements 136 according to the exemplary embodiment according to FIG. 8 provide an optimal one
  • the base plate 132 in contrast to the exemplary embodiment shown in FIG. 7, is not flat, but curved in the radial direction.
  • the support elements 136 applied to the underside 134 of the base plate 132 have an increasing axial expansion toward the center of the plate, which takes into account the curvature of the base plate 132.
  • Support elements open into a central ring 114, which functions as the hub of the compressor wheel.
  • a hub insert made of metal, in particular a light metal, is inserted into the hub of the compressor wheel in order to enable the most effective possible transmission of torque from the drive shaft of the electric motor of the charge air compressor to the compressor wheel.
  • Aluminum alloys for example, come into consideration as possible materials for the hub insert 104.
  • Some or all of the plastic compressor wheel can be molded around the metallic hub insert 104 and by an axial demolding process be formed. 8 also shows the compressor blades 106 which are connected in one piece to the base plate 132 and which have connecting pins 108 on their axial end opposite the base plate 132 for fastening a cover plate of the compressor wheel (not shown in FIG. 8).
  • the hub insert 104 allows a positive transmission of force to the drive shaft even under pretension.
  • the targeted shaping of the insert 104 enables a homogeneous introduction of force into the plastic compressor wheel. This allows high power to be transferred to the compressor wheel, which is designed, for example, as a molded component.
  • the hub insert 104 shows a detailed view of the hub insert 104.
  • the hub insert is metallic and has a strong rounding on its outer surface 108 facing the compressor wheel.
  • the hub insert 104 shows in its circumferential direction the functional mathematical course of a hypotrochoid.
  • This external shape of the hub insert according to the invention advantageously leads to a very low notch effect in the interaction with the plastic compressor wheel, but ensures reliable torque transmission of the driving shaft to the compressor wheel.
  • the metallic hub insert 104 has a central bore 110, into which the driving shaft of the electric motor of the charge air compressor is pressed. Other connection methods between the drive shaft of the electric motor and the hub insert 104 are of course also possible.
  • the hub insert 104 is obtained from a so-called extruded profile and can be produced, for example, by an extrusion process.
  • the shape of the insert according to the invention allows a homogeneous introduction of force into the injection component of the compressor wheel and thus enables high power to be transmitted to the compressor wheel by the driving electric motor.
  • the molded component on the hub insert 104 the latter has several on its circumference
  • FIG. 9 shows schematically the relative arrangement of the compressor blades with respect to the course of the support elements of the base plate.
  • the compressor blades 120 look in the axial direction through the base plate 124, which in this illustration is to be viewed as transparent, onto the support elements 126.
  • the support elements 126 extend essentially radially from the hub 128 of the compressor wheel. Deviating from this radial direction, the support elements each have a cranked end 130. In the radial direction, the support elements 126 have both a decreasing axial height and a decreasing material thickness.
  • the almost tangential compressor blades 120 begin with their interior, the end facing the hub directly above a support element of the base plate 124.
  • the projection lines of the support element and the compressor blade intersect at an angle of almost 90 °.
  • the compressor blades 126 also sweep over a further support element of the base plate 124 of the compressor wheel in the region of their cranked end 130.
  • one compressor blade each overlaps a support element of the base plate in the region of the cranked end 130 of the support element 126 such that an angle of result in almost 90 ° between the projections of the compressor blade and the cranked end of the support element.
  • the shaping of the support elements according to the invention and the relative arrangement of the support elements to the course of the compressor blades has the advantage that undesired, multi-axis stress states in the support elements or in the compressor wheel can be avoided.
  • the pairing of radially running bottom ribs with almost tangentially running compressor blades leads to a double overlap of both component groups. In this configuration, the material load or the deformation of the plastic impeller that occurs during operation is low, so that the use of a plastic compressor wheel is possible even in the area of very high revolutions of the charge air compressor according to the invention.
  • the device according to the invention for compressing combustion air is not limited to the exemplary embodiments presented in the drawings.
  • the device is not limited to the use of only a single compressor wheel.
  • the device according to the invention can be produced in an advantageous manner in that a metallic hub insert is extrusion-coated with plastic and is formed, for example, in an axial forming process.
  • the device according to the invention is not limited to a plastic compressor wheel with the materials explicitly listed in the description.

Abstract

La présente invention concerne un dispositif pour comprimer de l'air de combustion, notamment dans un moteur à combustion interne d'automobile. Ce dispositif comprend un boîtier (12), au moins une entrée d'air (28) menant dans le boîtier (12), au moins une évacuation d'air (40) sortant du boîtier (12), ainsi qu'au moins une roue de compresseur (42) qui est placée dans une chambre de compresseur (32) du boîtier (12), est entraînée par un arbre (44) et présente une pluralité d'aubes (54, 80, 106, 120) placées sur la circonférence de la roue de compresseur (42). Cette roue de compresseur est montée entre ladite entrée d'air (28) et ladite évacuation d'air (40) du boîtier (12) de façon à pouvoir comprimer l'air pouvant être amené au processus de combustion, par rotation de la roue de compresseur (42). Selon cette invention, au moins une roue de compresseur (42) est principalement constituée de matière plastique.
PCT/DE2003/002307 2002-07-26 2003-07-10 Roue de compresseur WO2004016952A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10234093A DE10234093A1 (de) 2002-07-26 2002-07-26 Vorrichtung zur Verdichtung von Verbrennungsluft
DE10234093.5 2002-07-26

Publications (1)

Publication Number Publication Date
WO2004016952A1 true WO2004016952A1 (fr) 2004-02-26

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ID=30010414

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2003/002307 WO2004016952A1 (fr) 2002-07-26 2003-07-10 Roue de compresseur

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DE (1) DE10234093A1 (fr)
WO (1) WO2004016952A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008055948A1 (de) * 2008-11-05 2010-05-06 Bosch Mahle Turbo Systems Gmbh & Co. Kg Ladeeinrichtung
DE102009001095A1 (de) 2009-02-24 2010-08-26 Bfa Anlagen + System Gmbh Lüfterrad
WO2016207288A1 (fr) * 2015-06-24 2016-12-29 Basf Se Roue de compresseur et utilisation de la roue de compresseur
US20180238339A1 (en) * 2017-02-22 2018-08-23 Borgwarner Inc. Compressor Wheel With Supports

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7452187B2 (en) * 2005-08-09 2008-11-18 Praxair Technology, Inc. Compressor with large diameter shrouded three dimensional impeller
DE102007062152A1 (de) 2007-12-21 2009-06-25 Bosch Mahle Turbo Systems Gmbh & Co. Kg Welle
DE102009013372B4 (de) * 2009-03-07 2020-06-25 Ziehl-Abegg Se Ventilatoreinheit
DE102014014169A1 (de) * 2014-09-24 2016-03-24 Linde Aktiengesellschaft Carbonfaserverstärktes PEEK Verdichterrad
FR3060672A1 (fr) * 2016-12-21 2018-06-22 Valeo Systemes De Controle Moteur Compresseur electrique avec roue amelioree

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Publication number Priority date Publication date Assignee Title
GB2090338A (en) * 1980-12-31 1982-07-07 Birmid Qualcast Home & Garden Centrifugal fan
DE3307386A1 (de) * 1983-03-02 1984-09-06 Wilden Kg, 8473 Pfreimd Laufrad fuer pumpen, verdichter, geblaese und dgl.
EP0575763A1 (fr) * 1992-06-20 1993-12-29 Robert Bosch Gmbh Roue pour un ventilateur radial
DE4418051A1 (de) * 1994-05-24 1995-12-07 Abb Research Ltd Verdichterrad
EP0737814A1 (fr) * 1995-04-10 1996-10-16 Abb Research Ltd. Compresseur
US5904471A (en) * 1996-12-20 1999-05-18 Turbodyne Systems, Inc. Cooling means for a motor-driven centrifugal air compressor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2090338A (en) * 1980-12-31 1982-07-07 Birmid Qualcast Home & Garden Centrifugal fan
DE3307386A1 (de) * 1983-03-02 1984-09-06 Wilden Kg, 8473 Pfreimd Laufrad fuer pumpen, verdichter, geblaese und dgl.
EP0575763A1 (fr) * 1992-06-20 1993-12-29 Robert Bosch Gmbh Roue pour un ventilateur radial
DE4418051A1 (de) * 1994-05-24 1995-12-07 Abb Research Ltd Verdichterrad
EP0737814A1 (fr) * 1995-04-10 1996-10-16 Abb Research Ltd. Compresseur
US5904471A (en) * 1996-12-20 1999-05-18 Turbodyne Systems, Inc. Cooling means for a motor-driven centrifugal air compressor

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008055948A1 (de) * 2008-11-05 2010-05-06 Bosch Mahle Turbo Systems Gmbh & Co. Kg Ladeeinrichtung
DE102009001095A1 (de) 2009-02-24 2010-08-26 Bfa Anlagen + System Gmbh Lüfterrad
WO2016207288A1 (fr) * 2015-06-24 2016-12-29 Basf Se Roue de compresseur et utilisation de la roue de compresseur
KR20180019738A (ko) * 2015-06-24 2018-02-26 바스프 에스이 컴프레서 휠 및 컴프레서 휠의 용도
JP2018518630A (ja) * 2015-06-24 2018-07-12 ビーエーエスエフ ソシエタス・ヨーロピアＢａｓｆ Ｓｅ 圧縮機ホイール及びその圧縮機ホイールの使用
KR102582856B1 (ko) 2015-06-24 2023-09-25 바스프 에스이 컴프레서 휠 및 컴프레서 휠의 용도
US20180238339A1 (en) * 2017-02-22 2018-08-23 Borgwarner Inc. Compressor Wheel With Supports
CN108457896A (zh) * 2017-02-22 2018-08-28 博格华纳公司 具有支撑件的压缩机叶轮
EP3366926A1 (fr) * 2017-02-22 2018-08-29 Borgwarner Inc. Rouet de compresseur avec nervures courbées sur la face arrière du disque du rouet

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