WO2007089737A1 - Combinaison de compresseur a geometrie variable, robinet d'etranglement, et robinet de recirculation - Google Patents

Combinaison de compresseur a geometrie variable, robinet d'etranglement, et robinet de recirculation Download PDF

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Publication number
WO2007089737A1
WO2007089737A1 PCT/US2007/002463 US2007002463W WO2007089737A1 WO 2007089737 A1 WO2007089737 A1 WO 2007089737A1 US 2007002463 W US2007002463 W US 2007002463W WO 2007089737 A1 WO2007089737 A1 WO 2007089737A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing
compressor
recirculation
outlet
vanes
Prior art date
Application number
PCT/US2007/002463
Other languages
English (en)
Inventor
Volker Joergl
Timm Kiener
Olaf Weber
Original Assignee
Borgwarner Inc.
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 Borgwarner Inc. filed Critical Borgwarner Inc.
Publication of WO2007089737A1 publication Critical patent/WO2007089737A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/105—Final actuators by passing part of the fluid
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/16—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes
    • F01D17/165—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of nozzle vanes for radial flow, i.e. the vanes turning around axes which are essentially parallel to the rotor centre line
    • 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
    • F02B37/12—Control of the pumps
    • F02B37/16—Control of the pumps by bypassing charging air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
    • F02B37/225—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits air passages
    • 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
    • F04D25/04—Units comprising pumps and their driving means the pump being fluid-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
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0284—Conjoint control of two or more different functions
    • 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
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/06—Low pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust downstream of the turbocharger turbine and reintroduced into the intake system upstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/14—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system
    • F02M26/15—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system in relation to engine exhaust purifying apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/28—Layout, e.g. schematics with liquid-cooled heat exchangers
    • 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
    • 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 present invention relates to an air system which has a recirculation channel in order to control the pressure ratio of an output side of a compressor and an input side of the compressor.
  • Air systems are used in vehicles in order to increase the efficiency of an engine and reduce the emissions of the vehicle by recirculating exhaust gas and compressing the intake air.
  • Air systems use a turbocharger where the exhaust gas passes through a turbine which is connected to a compressor.
  • the compressor compresses intake air which is directed towards the intake manifold of the engine.
  • the pressure ratio between the output of the compressor and the input of the compressor can be at such a high ratio that the air system is working under unstable operating conditions. These unstable operating conditions can lead to low compressor efficiency, material failure, or high emissions among other things.
  • the present invention relates to an air device having a rotatable compressor contained in a housing having an inlet and an outlet.
  • the housing also has a variable air intake mechanism within the housing for varying the flow of fluid from the inlet to the outlet.
  • a recirculation channel is also contained within the housing for recirculating at least some of the fluid to an area proximate the inlet of the housing when said variable air intake mechanism is at a closed position.
  • the variable air intake mechanism can include diffuser vanes or other suitable structures. If diffuser vanes are used then they are vanes that can be altered in order to control the air flow through the compressor housing or the recirculation channel. Thus, depending on whether a high or low flow in the recirculation channel is required, the position of the diffuser vanes can be changed accordingly. This will provide an increase in compressor efficiency.
  • the diffuser vanes can also provide a throttling function that will eliminate the need to have a throttle valve further down stream from the compressor. In another aspect the position of the diffuser vanes can be used to control the flow of fluid through the recirculation channel. Thus a single mechanism can provide increased compressor efficiency, throttling and recirculation control, or combinations thereof.
  • Figure 1 is a schematic view of an air system containing the air device
  • Figure 2 is a perspective view of an air device
  • Figure 3 is a plan view of the diffuser vanes in relation to the recirculation channel.
  • the air system 10 includes an engine 12 which has an exhaust manifold 14. Connected to the exhaust manifold 14 is a turbine 16 with variable vanes and an exhaust gas recirculation (EGR) path 18, such that the exhaust gas from the exhaust manifold 14 can enter either the turbine 16 or the EGR path 18.
  • the exhaust gas that enters the EGR path 18 first passes through an EGR cooler 20 in order to reduce the temperature of the exhaust gas, and then pass through an EGR valve 22.
  • the EGR valve 22 is a high pressure EGR valve. Next, the exhaust gas is mixed with an exhaust gas and fresh air combination and enters the engine's 12 intake manifold 24.
  • the exhaust gas that does not pass through the EGR path 18 passes through a turbine 16, which is operably connected to a compressor 28.
  • a turbocharger 30 contains the turbine 16 and the compressor 28, and the exhaust gas rotates the turbine 16 which then rotates the compressor 28.
  • the exhaust gas can pass through a diesel particulate filter 32 (DPF) which removes soot from the exhaust gas.
  • DPF diesel particulate filter 32
  • a portion of the exhaust gas will exit the air system 10 through the exhaust pipe 34, and a portion of the exhaust gas can pass through a low pressure EGR throttle valve 36 and into an EGR path 38.
  • the EGR throttle valve 36 can have an EGR valve portion and a throttle valve portion that are part of a single unit, or they may be separate units.
  • the amount of gas that passes through each EGR path 38 is controlled by the EGR throttle valve 36, such that when the EGR throttle valve 36 is open more gas will pass through the EGR path 38 and when the EGR throttle valve 36 is closed more gas will exit the air system 10 through the exhaust pipe 34.
  • the EGR throttle valve can work in combination so that the EGR valve portion can be opened and the throttle valve portion can be closed to allow maximum flow through the EGR path 38. Likewise, the EGR valve portion can be closed and the throttle valve portion can be opened to allow maximum flow through the exhaust pipe 34.
  • the exhaust gas that does pass through the EGR path 38 then passes through an EGR cooler 42 in order to reduce the temperature of the exhaust gas. After passing through the EGR cooler 42, the exhaust gas is mixed with fresh air and moves to an air device 33 that contains the compressor 28, where the pressure of the exhaust gas and fresh air is increased. Thus, the pressure of the air on the input side of the corn pressor 28 is lower than the pressure of the air on the output side of the compressor 28.
  • the present invention provides an air device 33 that combines a throttle valve aspect 26, variable outlet vanes aspect 27, compressor 28, a recirculation channel 44 and a recirculation valve aspect 46 into a single housing 29.
  • a variable air intake mechanism in the form of diffuser vanes 52 that provide the throttle valve aspect 26, variable outlet vanes aspect 27, and the recirculation valve aspect 46.
  • the scope of this invention is not limited to providing all three aspects in one application. It is possible for the air device to have just single aspect or any combination of the three aspects described herein.
  • the air device 33 controls the flow and pressure of fluid that flows onto a charge air cooler 48 and the intake manifold 24.
  • the air device 33 can also work with the EGR path 18 to increase the uptake of high pressure EGR from the EGR path 18 to the intake manifold 24.
  • the housing 29 has an inlet 58 for receiving fluid medium such as outside air from an air intake 61, recirculated exhaust gas from the EGR path 38 or a mixture of outside air and exhaust gas.
  • the housing 29 also has an outlet 60 that is connected to a path that leads to the intake manifold 24.
  • the compressor 28 is circumscribed by two or more diffuser vanes 52.
  • the diffuser vanes 52 can rotate between a closed position, an open position and any angular position therebetween. While diffuser vanes 52 are described it is possible for a different type of mechanism to be used. For example a butterfly valve or other valve mechanism that would be sufficient to control the flow of fluid through the air device 33 can be used.
  • Using only high pressure exhaust gas through the EGR path 18 can require higher flow which can be achieved by throttling the mass flow that flows through the compressor 28 which is typically carried out using a throttle valve located upstream of the EGR portion 18.
  • the throttle valve aspect 26 of the present invention provides this desired result.
  • the diffuser vanes 52 When the diffuser vanes 52 are closed past a certain angle they will cause throttling of the fluid medium past the vanes 52.
  • the angle that the throttling effect occurs will vary depending on several factors such as the shape of the blades on the compressor, the shape of the diffuser vanes, etc. This throttling action will lower the pressure downstream of the air device 33. This will cause increased flow from the EGR path 18.
  • variable outlet vanes aspect 27 When the diffuser vanes 52 move to an angle where they are more open and the throttling effect no longer occurs, the variable outlet vanes aspect 27 will be achieved. This occurs then the diffuser vanes are at or near a fully open position.
  • the angle of the diffuser vanes 52 can be varied to increase the pressure produced by the air device 33. Varying the angle of flow past the vanes using the variable outlet vanes aspect 27 can cause the pressure to buildup by maximizing the flow path of fluid from the compressor wheel 28.
  • the recirculation valve aspect 46 includes using the diffuser vanes 52 to open and close a recirculation channel 44.
  • the recirculation channel 44 is used to recirculate air from the output side of the compressor 28 to the input side of the compressor 28.
  • the recirculation channel 44 can be formed within the housing 29 or it can be external.
  • Recirculating the pressurized air through the recirculation channel 44 increases the internal mass flow through the compressor 28 without increasing the flow past the diffuser vanes 52.
  • the flow through the recirculation channel 44 is controlled by a recirculation valve aspect 46 of the air device 33.
  • the recirculation valve 46 aspect and the recirculation channel 44 are inside the compressor housing 29 which compacts the size of the compressor 28, the recirculation channel 44, and the recirculation valve aspect 46.
  • the recirculation channel 44 and a separate recirculation valve are outside the compressor housing 29 can be used.
  • the angle of the diffuser vanes 52 are controlled by an actuator which is designed to operate over the entire operating range of the diffuser vanes 52 and the recirculation channel 44, so long as the actuator has the necessary force to close the diffuser vanes 52 against the forces of the air flow.
  • the diffuser vanes 52 and the recirculation channel 44 are operated by separate actuators (not shown), but this embodiment requires an increase in material and space.
  • the diffuser vanes 52 can be forced balanced so that the diffuser vanes 52 are all calibrated within the same tolerances.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

La présente invention concerne un mécanisme d'admission d'air variable qui peut comprendre des aubes de diffuseur (52) ou autres structures appropriées. Si des aubes de diffuseur (52) sont utilisées, alors ce sont des aubes qui peuvent être modifiées afin de contrôler l'écoulement d'air à travers le carter de compresseur (33) ou le canal de recirculation (44). Ainsi, suivant qu'un écoulement important ou faible est nécessaire dans le canal de recirculation (44), la position des aubes de diffuseur peut être changée en conséquence. Ceci permettra une augmentation du rendement du compresseur. Les aubes de diffuseur (52) peuvent également remplir une fonction d'étranglement qui éliminera la nécessité d'avoir un robinet d'étranglement plus en aval du compresseur (28). Dans un autre aspect, la position des aubes de diffuseur (52) peut être utilisée pour contrôler l'écoulement de fluide à travers le canal de recirculation (44). Ainsi, un mécanisme unique peut permettre de meilleurs rendement de compresseur, étranglement et contrôle de recirculation, ou combinaisons de ceux-ci.
PCT/US2007/002463 2006-01-27 2007-01-26 Combinaison de compresseur a geometrie variable, robinet d'etranglement, et robinet de recirculation WO2007089737A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US76270206P 2006-01-27 2006-01-27
US60/762,702 2006-01-27

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Publication Number Publication Date
WO2007089737A1 true WO2007089737A1 (fr) 2007-08-09

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009056391A3 (fr) * 2007-10-30 2009-08-20 Continental Automotive Gmbh Turbocompresseur et procédé de production d'un premier mouvement tourbillonnaire en amont d'un compresseur du turbocompresseur
EP2543844A1 (fr) * 2010-03-03 2013-01-09 Toyota Jidosha Kabushiki Kaisha Dispositif de commande pour moteur à combustion interne équipé d'un turbocompresseur
DE102012100339A1 (de) * 2012-01-16 2013-07-18 Universität der Bundeswehr München Verfahren und Vorrichtung zur Stabilisierung eines Verdichterstroms
CN103518048A (zh) * 2011-05-10 2014-01-15 博格华纳公司 排气涡轮增压器的压缩机
DE102015111462B3 (de) * 2015-07-15 2016-09-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Verdichter mit Rückströmkanal und verstellbaren Vorleitschaufeln
GB2557910A (en) * 2016-12-15 2018-07-04 Valeo Air Man Uk Limited Supercharger with vaned diffuser

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55142994A (en) * 1979-04-25 1980-11-07 Hitachi Ltd Centrifugal compressor
DE3605958A1 (de) * 1986-02-25 1987-09-03 Fraunhofer Ges Forschung Vorrichtung zum erfassen und beheben von abloeseschwingungen an verdichterschaufeln
EP0526965A2 (fr) * 1991-05-01 1993-02-10 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Carters de compresseur pour turbosoufflantes
DE4213047A1 (de) * 1992-04-21 1993-10-28 Kuehnle Kopp Kausch Ag Verdichter mit einer Einrichtung zum Beeinflussen der Hauptströmung im Verdichter
DE19823274C1 (de) * 1998-05-26 1999-10-14 Daimler Chrysler Ag Abgasturbolader für eine Brennkraftmaschine
DE10049198A1 (de) * 2000-10-05 2002-04-11 Daimler Chrysler Ag Abgasturbolader für eine Brennkraftmaschine und Verfahren hierzu
EP1316699A2 (fr) * 2001-11-30 2003-06-04 DaimlerChrysler AG Turbocompresseur pour moteur à combustion interne et méthode de fonctionnement d'un moteur à combustion interne turbocompressé
DE10223876A1 (de) * 2002-05-29 2003-12-11 Daimler Chrysler Ag Verdichter für eine Brennkraftmaschine
WO2005071243A1 (fr) * 2004-01-22 2005-08-04 Daimlerchrysler Ag Compresseur installe dans la tubulure d'admission d'un moteur a combustion interne

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55142994A (en) * 1979-04-25 1980-11-07 Hitachi Ltd Centrifugal compressor
DE3605958A1 (de) * 1986-02-25 1987-09-03 Fraunhofer Ges Forschung Vorrichtung zum erfassen und beheben von abloeseschwingungen an verdichterschaufeln
EP0526965A2 (fr) * 1991-05-01 1993-02-10 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Carters de compresseur pour turbosoufflantes
DE4213047A1 (de) * 1992-04-21 1993-10-28 Kuehnle Kopp Kausch Ag Verdichter mit einer Einrichtung zum Beeinflussen der Hauptströmung im Verdichter
DE19823274C1 (de) * 1998-05-26 1999-10-14 Daimler Chrysler Ag Abgasturbolader für eine Brennkraftmaschine
DE10049198A1 (de) * 2000-10-05 2002-04-11 Daimler Chrysler Ag Abgasturbolader für eine Brennkraftmaschine und Verfahren hierzu
EP1316699A2 (fr) * 2001-11-30 2003-06-04 DaimlerChrysler AG Turbocompresseur pour moteur à combustion interne et méthode de fonctionnement d'un moteur à combustion interne turbocompressé
DE10223876A1 (de) * 2002-05-29 2003-12-11 Daimler Chrysler Ag Verdichter für eine Brennkraftmaschine
WO2005071243A1 (fr) * 2004-01-22 2005-08-04 Daimlerchrysler Ag Compresseur installe dans la tubulure d'admission d'un moteur a combustion interne

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009056391A3 (fr) * 2007-10-30 2009-08-20 Continental Automotive Gmbh Turbocompresseur et procédé de production d'un premier mouvement tourbillonnaire en amont d'un compresseur du turbocompresseur
EP2543844A1 (fr) * 2010-03-03 2013-01-09 Toyota Jidosha Kabushiki Kaisha Dispositif de commande pour moteur à combustion interne équipé d'un turbocompresseur
EP2543844A4 (fr) * 2010-03-03 2013-10-30 Toyota Motor Co Ltd Dispositif de commande pour moteur à combustion interne équipé d'un turbocompresseur
US9194308B2 (en) 2010-03-03 2015-11-24 Toyota Jidosha Kabushiki Kaisha Control apparatus for internal combustion engine equipped with turbocharger
CN103518048A (zh) * 2011-05-10 2014-01-15 博格华纳公司 排气涡轮增压器的压缩机
DE102012100339A1 (de) * 2012-01-16 2013-07-18 Universität der Bundeswehr München Verfahren und Vorrichtung zur Stabilisierung eines Verdichterstroms
DE102015111462B3 (de) * 2015-07-15 2016-09-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Verdichter mit Rückströmkanal und verstellbaren Vorleitschaufeln
GB2557910A (en) * 2016-12-15 2018-07-04 Valeo Air Man Uk Limited Supercharger with vaned diffuser
GB2557910B (en) * 2016-12-15 2021-01-20 Valeo Air Man Uk Limited Supercharger with vaned diffuser

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