EP1749992A1 - Mehrstufiger Motor-Kompressor für die Kompression von Gasen, z. B. für Kraftfahrzeuge - Google Patents

Mehrstufiger Motor-Kompressor für die Kompression von Gasen, z. B. für Kraftfahrzeuge Download PDF

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Publication number
EP1749992A1
EP1749992A1 EP06101557A EP06101557A EP1749992A1 EP 1749992 A1 EP1749992 A1 EP 1749992A1 EP 06101557 A EP06101557 A EP 06101557A EP 06101557 A EP06101557 A EP 06101557A EP 1749992 A1 EP1749992 A1 EP 1749992A1
Authority
EP
European Patent Office
Prior art keywords
motor
compressor according
ducts
section
transfer
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.)
Granted
Application number
EP06101557A
Other languages
English (en)
French (fr)
Other versions
EP1749992B1 (de
Inventor
Fabio Pesola
Paolo Marchese
Dario Caenazzo
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.)
Centro Ricerche Fiat SCpA
Original Assignee
Centro Ricerche Fiat SCpA
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 Centro Ricerche Fiat SCpA filed Critical Centro Ricerche Fiat SCpA
Priority to US11/499,265 priority Critical patent/US20070036662A1/en
Priority to JP2006214157A priority patent/JP2007046610A/ja
Publication of EP1749992A1 publication Critical patent/EP1749992A1/de
Application granted granted Critical
Publication of EP1749992B1 publication Critical patent/EP1749992B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage 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
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet

Definitions

  • This invention refers to a multistage motor-compressor for the compression of a fluid, for motor vehicles for example.
  • the invention refers to a two-stage motor-compressor for the supply of pressurized air to fuel cell systems.
  • Motor-compressors of the above-stated type are well known, in which the first-stage scroll is connected to a tangential first section of a transfer duct, while a second axial or radial section of the transfer duct is connected to a fluid conveyor for the second-stage scroll.
  • the second section is axial, the fluid flow entering the conveyor undergoes abrupt changes of direction, giving rise to a drop in flow pressure, high operational power consumption and reduced efficiency for the motor-compressor.
  • the second section of the transfer duct is radial, it is normally shaped to create a helical flow with the same direction of rotation as that of the second-stage impeller.
  • This radial connection has the drawback of reduced efficiency and a low compression ratio at high flow rates.
  • Multistage motor-compressors are also known, in which the impellers are arranged in series on the same output side of the driving electric motor's shaft. Since the two impellers are cantilever mounted on the shaft, the latter is subject to stress, which reduces the operating speed.
  • the object of the invention is that of embodying a two-stage motor-compressor, which is highly reliable, eliminating the drawbacks and increasing the performance of motor-compressors of known art.
  • this object is achieved by a multistage motor-compressor for the compression of a fluid, as defined in claim 1.
  • the impellers of the two stages are fixed on two opposite ends of the shaft of a common driving electric motor, for which the motor-compressor is able to operate at high speeds.
  • reference 5 generically indicates a multistage motor-compressor for the compression of a fluid, for motor vehicles for example.
  • the motor-compressor 5 is of the type with two stages 6 and 7, low pressure and high pressure respectively, and is suitable for the supply of pressurized air in a fuel cell system or for supplying air to internal combustion engines, or for any system in which compressed air is required.
  • the low-pressure stage 6 comprises a low-pressure impeller, which henceforth will be called the primary impeller 8 (Figure 3).
  • the primary impeller 8 rotates around an axis A and is preceded by a fixed ogival portion 9, placed inside a low-pressure scroll, which henceforth will be called the primary scroll 10.
  • the primary impeller 8 is fixed on one end 15' of a shaft of an electric motor 15.
  • the primary impeller 8 also comprises a series of substantially radial, shaped blades 11, of known type.
  • the primary scroll 10 is composed of a shaped casing 12, connected in a removable manner, via bolts and at least one half-ring 13, to a fixed plate 20 carried on an external casing 32 of the motor 15, which has a substantially cylindrical shape.
  • the shaped casing 12 has a central air-inlet opening 14 to the low-pressure stage 6.
  • the primary scroll 10 also has at least one curved, fluid-delivery duct 16, which has a substantially spiral shape placed substantially on plane P perpendicular to axis A.
  • the primary scroll 10 is equipped with three curved ducts 16 arranged at 120° to each other, for the purpose of having a balanced load on the primary scroll 10.
  • the annular chamber 17 is in communication with the central opening 14, through an annular inlet opening 18 facing towards axis A, while on the other side it is in communication with the curved ducts 16 through corresponding outlet openings 19, facing towards the outside of the annular chamber 17.
  • the shaped blades 11 of the impeller 8 are suitable for conveying incoming air from the central opening 14 to the curved ducts 16.
  • the axial direction of the airflow to be compressed is optimized by the ogival portion 9.
  • each curved duct 16 has an increasing section from the outlet opening 19 of the annular chamber 17 to the outlet opening 25, which is defined by the terminal radial section of the curved duct 16.
  • the spiral shape of the curved duct 16 induces a fluid flow that turns in the same direction of rotation as the impeller 8.
  • the high-pressure stage 7 of the motor-compressor 5 comprises a high-pressure impeller, which henceforth will be called the secondary impeller 21 ( Figure 3), rotating around its axis.
  • This axis can advantageously coincide with axis A of the primary impeller 8.
  • the secondary impeller 21 is fixed on the end 15" of the shaft of the motor 15 opposite from that of the primary impeller 8, thereby providing a balanced load on the shaft of the motor 15 such that the group of impellers 8 and 21 can be spun at high speed.
  • the secondary impeller 21 is equipped with its own ogival portion 22, suitable for optimizing the direction of the axial flow.
  • the ogival portion 22 is placed inside a high-pressure scroll, which henceforth will be called the secondary scroll 23.
  • the secondary impeller 21 also comprises a series of substantially radial, shaped blades 24.
  • the secondary scroll 23 is composed of a shaped casing 26 connected in a removable manner, via bolts and at least one half-ring 27, to another fixed plate 33, carried on the external casing 32 of the motor 15.
  • the shaped casing 26 of the secondary scroll 23 has a sleeve 31 with a central air-inlet opening 28 to the high-pressure stage 7.
  • the secondary scroll 23 has at least one curved duct 29, substantially placed on another plane R perpendicular to axis A.
  • the secondary scroll 23 (see also Figure 7) advantageously has just one curved duct 29, which also has a substantially spiral course and terminates with a straight section 30.
  • the spiral of the curved duct 29 is such as to generate a fluid flow that also turns in the same direction as the secondary impeller 21.
  • the fixed plate 33 together with the shaped casing 26 forms an annular chamber 34, one side of which is in communication with the central opening 28, through an annular inlet opening 36 facing towards axis A.
  • the annular chamber 34 is in communication with the curved duct 29, through an opening 37 facing towards the outside, which forms the inlet opening of the curved duct 29.
  • the shaped blades 24 of the impeller 21 are suitable for conveying incoming air from the central opening 28 to the annular chamber 34.
  • the curved duct 29 has an increasing section from the portion adjacent to its inlet opening 37 to a corresponding outlet opening 38 ( Figure 5) defined by the terminal radial section of the curved duct 29, which is equal to that of the straight section 30.
  • the motor-compressor 5 also comprises a conveyor 39 with an outer wall 40 and a central opening 41 ( Figure 3), in which the sleeve 31 of the secondary scroll 23 engages in a sealed manner.
  • the conveyor 39 is also provided with three inlet openings 42 associated with the three outlet openings 25 of the curved ducts 16 of the primary scroll 10.
  • the three inlet openings 42 are also arranged at 120° to each other.
  • a corresponding transfer duct, generically indicated by reference 44, is placed between each outlet opening 25 of the primary scroll 10 and the corresponding inlet opening 42 of the conveyor 39.
  • each transfer duct 44 is shaped so as to create a flow entering the conveyor 39 with a substantially helical course and a direction of rotation opposite to the direction of rotation of the secondary impeller 21.
  • each transfer duct 44 comprises a first section 52 ( Figures 1, 4 and 6) connected to the corresponding curved duct 16 and substantially tangential to the primary impeller 8, a second section 56 ( Figures 2, 5 and 8) connected to the corresponding opening 42 of the conveyor 39 and substantially tangential to the secondary impeller 21, and a longitudinal intermediate section 54 and 57.
  • each transfer duct 44 comprises a first connector section 53, substantially helical in form and placed between the first tangential section 52 and the intermediate section 54 and 57.
  • Each transfer duct also comprises a second curved connector section 58 placed between the second tangential section 56 and the intermediate section 54 and 57.
  • the transfer ducts 44 are advantageously placed on the outside of the casing 32 and are each formed by two segments 46 and 47 ( Figures 1 and 2), connected in a removable manner to the primary scroll 10 and the conveyor 39 respectively.
  • the two segments 46 and 47 terminate with corresponding flanges 48 and 49, which mate together on a plane S ( Figure 3) perpendicular to axis A, and are connected to each other in a sealed and removable manner, for example by bolts 51.
  • each transfer duct 44 comprises the said first section 52, the corresponding substantially helical connection section 53, and a straight portion 54, which forms a portion 54 of the intermediate section 54 and 57.
  • segment 47 of each transfer duct 44 comprises the said second section 56, the curved connection section 58 and another straight portion 57 of the intermediate section 54 and 57.
  • All of the ducts 16, 29 and 44 of the motor-compressor 5 are outwardly sealed to support the pressurized fluid, via toroidal gaskets for example, pastes or in any other known manner.
  • the shaped casing 12 of the primary scroll 10 is provided with a series of cooling ribs or fins 59.
  • the shaped casing 26 of the secondary scroll 23 and the conveyor 39 are provided with corresponding series of cooling ribs or fins 61 and 62.
  • the fins 59, 61 and 62 serve to increase the heat-exchange surface area with the external environment, to cool the compressed fluid efficiently, increasing the density and therefore increasing the efficiency of the motor-compressor 5.
  • the transfer ducts 44 have an elliptic section to contain the radial bulk of the motor-compressor 5.
  • the two impellers 8 and 21 are coaxial and are driven by a single electric motor 15.
  • the arrows 63 and 64 represent the direction of rotation of the motor 15, while the black arrows on the transfer ducts 44 represent the flow of fluid.
  • Figure 4 clearly shows that the direction of rotation of the flow in the segments 46 is consistent with that of the motor 15 (arrow 63), while Figure 5 shows that the direction of rotation of the flow in the sections 57 of the segments 47 is opposite to that of the motor 15 (arrow 64).
  • the motor-compressor 5 comprises just one delivery duct 16 and just one transfer duct 44 to the conveyor 39.
  • the motor-compressor 5 comprises two delivery ducts 16 and two transfer ducts 44, placed diametrically opposite each other.
  • the two variants have a number of outlets 25 for the scroll 10 and inlets 42 to the conveyor 39 equal to the number of transfer ducts 44.
  • the shape of the transfer ducts 44 in Figures 9 and 10 is identical to that of the transfer ducts 44 in Figure 2.
  • Figures 9 and 10 parts that are the same or similar to those in Figure 2 are indicated with the same reference numbers, and so the two variants will not be described any further.
  • Figure 11 shows a curve 66 of the compression ratio ⁇ as a function of flow Q of the motor-compressor 5.
  • a predetermined compression curve 66 is obtained. If instead the second section 56 of each transfer duct 44 provokes an opposite helical flow to that of the motor 15, the outcome is a displacement of the curve 66 to the right in Figure 11, which indicates that a greater compression ratio is achieved at high flow-rates.
  • the functioning of the motor-compressor 5 is as follows.
  • the conveyor 39 then channels the fluid flow, via the central opening 28 of the sleeve 31, to the inlet opening 37 of the secondary scroll 23, where it undergoes a second compression imparted by the secondary impeller 21 and then passes into the curved duct 29 of the secondary scroll 23. Finally, the pressurized fluid is conveyed to where utilized by the straight section 30.
  • the advantages of the motor-compressor 5 according to the invention with respect to motor-compressors of known art are evident.
  • the transfer ducts 44 avoid energy loss in the flow and improve the efficiency of the motor-compressor 5.
  • the fixing of the two impellers 8 and 21 on the two ends 15' and 15" of the shaft of the common motor 15 renders operation of the impellers 8 and 21 well balanced, avoiding the generation of vibration and thereby allowing an increase in the speed of rotation.
  • each transfer duct 44 could be in a single piece, and be connected to the scroll 10 and to the conveyor 39 in a removable manner, via a bolted flange for example.
  • the two impellers 8 and 21 could be spun by independent electric motors and the respective axes A could be parallel, oblique or coplanar, but with a predetermined angle formed between them.
  • the two impellers 8 and 21 are preferably rotated by a common electric motor, possibly via at least one drive transmission group, of known type.
EP06101557A 2005-08-05 2006-02-10 Mehrstufiger Motor-Kompressor für die Kompression von Gasen, z. B. für Kraftfahrzeuge Not-in-force EP1749992B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US11/499,265 US20070036662A1 (en) 2005-08-05 2006-08-04 Multistage motor-compressor for the compression of a fluid
JP2006214157A JP2007046610A (ja) 2005-08-05 2006-08-07 自動車等のための流体圧縮用多段モータ−コンプレッサ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT000558A ITTO20050558A1 (it) 2005-08-05 2005-08-05 Motocompressore a piu' stadi per la compressione di fluidi, ad esempio per autoveicoli

Publications (2)

Publication Number Publication Date
EP1749992A1 true EP1749992A1 (de) 2007-02-07
EP1749992B1 EP1749992B1 (de) 2010-02-10

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Application Number Title Priority Date Filing Date
EP06101557A Not-in-force EP1749992B1 (de) 2005-08-05 2006-02-10 Mehrstufiger Motor-Kompressor für die Kompression von Gasen, z. B. für Kraftfahrzeuge

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EP (1) EP1749992B1 (de)
AT (1) ATE457417T1 (de)
DE (1) DE602006012139D1 (de)
IT (1) ITTO20050558A1 (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010065681A (ja) * 2008-09-10 2010-03-25 Borgwarner Inc 受動的予旋回の逆方向回転のためのターボチャージャ連結
GB2490563A (en) * 2011-05-03 2012-11-07 Peter John Bayram Pre-rotating or de-rotating fluid flow with a volute
EP3112686A4 (de) * 2014-02-25 2017-01-04 Mitsubishi Heavy Industries, Ltd. Elektrischer mehrstufiger radialverdichter und aufladesystem einer brennkraftmaschine
DE102017205704A1 (de) * 2017-04-04 2018-10-04 Robert Bosch Gmbh Turbokompressor, insbesondere für ein Brennstoffzellensystem
WO2018197622A1 (de) * 2017-04-29 2018-11-01 Daimler Ag Verbrennungskraftmaschine für ein kraftfahrzeug, insbesondere für einen kraftwagen
WO2019001911A1 (de) * 2017-06-27 2019-01-03 Ebm-Papst Mulfingen Gmbh & Co. Kg Turboverdichter mit integrierten strömungskanälen
WO2022029386A1 (fr) 2020-08-05 2022-02-10 Enogia Compresseur centrifuge multi-étages
EP2821652B1 (de) * 2012-02-29 2022-08-31 Mitsubishi Heavy Industries, Ltd. Zentrifugalströmungsmaschine mit einem luftansaugrohrstruktur
WO2022214852A1 (en) * 2021-04-09 2022-10-13 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Supplying a mixture of air and exhaust gas to a compressor wheel of a compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114857043B (zh) * 2022-04-21 2023-10-24 珠海格力电器股份有限公司 空压机、燃料电池、新能源车

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3171353A (en) * 1962-02-27 1965-03-02 Kenton D Mcmahan Centrifugal fluid pump
US4969803A (en) * 1987-09-03 1990-11-13 Man Gutehoffnungshutte Gmbh Compressor unit
EP1041289A2 (de) * 1999-03-31 2000-10-04 Cooper Cameron Corporation Direktangetriebene Verdichtereinheit
US20040179947A1 (en) * 2002-12-19 2004-09-16 R & D Dynamics Corporation Motor driven two-stage centrifugal air-conditioning compressor
US20040247461A1 (en) * 2001-11-08 2004-12-09 Frank Pflueger Two stage electrically powered compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3171353A (en) * 1962-02-27 1965-03-02 Kenton D Mcmahan Centrifugal fluid pump
US4969803A (en) * 1987-09-03 1990-11-13 Man Gutehoffnungshutte Gmbh Compressor unit
EP1041289A2 (de) * 1999-03-31 2000-10-04 Cooper Cameron Corporation Direktangetriebene Verdichtereinheit
US20040247461A1 (en) * 2001-11-08 2004-12-09 Frank Pflueger Two stage electrically powered compressor
US20040179947A1 (en) * 2002-12-19 2004-09-16 R & D Dynamics Corporation Motor driven two-stage centrifugal air-conditioning compressor

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010065681A (ja) * 2008-09-10 2010-03-25 Borgwarner Inc 受動的予旋回の逆方向回転のためのターボチャージャ連結
EP2163746A3 (de) * 2008-09-10 2010-04-21 BorgWarner Inc. Kopplung von Turboladern für den passiven Vordrall-Gegenlauf
US8388302B2 (en) 2008-09-10 2013-03-05 Borgwarner Inc. Coupling turbochargers for passive pre-swirl counter-rotation
GB2490563A (en) * 2011-05-03 2012-11-07 Peter John Bayram Pre-rotating or de-rotating fluid flow with a volute
GB2490563B (en) * 2011-05-03 2015-07-22 Peter John Bayram Spiral energy recovery and flow pre-rotation for turbochargers, turbo-expansion valves, turbojets and marine propellers, etc
EP2821652B1 (de) * 2012-02-29 2022-08-31 Mitsubishi Heavy Industries, Ltd. Zentrifugalströmungsmaschine mit einem luftansaugrohrstruktur
US10174670B2 (en) 2014-02-25 2019-01-08 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Multi-stage electric centrifugal compressor and supercharging system for internal combustion engine
EP3112686A4 (de) * 2014-02-25 2017-01-04 Mitsubishi Heavy Industries, Ltd. Elektrischer mehrstufiger radialverdichter und aufladesystem einer brennkraftmaschine
DE102017205704A1 (de) * 2017-04-04 2018-10-04 Robert Bosch Gmbh Turbokompressor, insbesondere für ein Brennstoffzellensystem
WO2018197622A1 (de) * 2017-04-29 2018-11-01 Daimler Ag Verbrennungskraftmaschine für ein kraftfahrzeug, insbesondere für einen kraftwagen
WO2019001911A1 (de) * 2017-06-27 2019-01-03 Ebm-Papst Mulfingen Gmbh & Co. Kg Turboverdichter mit integrierten strömungskanälen
WO2022029386A1 (fr) 2020-08-05 2022-02-10 Enogia Compresseur centrifuge multi-étages
FR3113303A1 (fr) 2020-08-05 2022-02-11 Enogia Compresseur centrifuge multi-étages
WO2022214852A1 (en) * 2021-04-09 2022-10-13 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Supplying a mixture of air and exhaust gas to a compressor wheel of a compressor

Also Published As

Publication number Publication date
DE602006012139D1 (de) 2010-03-25
ATE457417T1 (de) 2010-02-15
ITTO20050558A1 (it) 2007-02-06
EP1749992B1 (de) 2010-02-10

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