WO2012072183A1 - Dispositif de suralimentation pour un moteur à combustion interne - Google Patents

Dispositif de suralimentation pour un moteur à combustion interne Download PDF

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Publication number
WO2012072183A1
WO2012072183A1 PCT/EP2011/005661 EP2011005661W WO2012072183A1 WO 2012072183 A1 WO2012072183 A1 WO 2012072183A1 EP 2011005661 W EP2011005661 W EP 2011005661W WO 2012072183 A1 WO2012072183 A1 WO 2012072183A1
Authority
WO
WIPO (PCT)
Prior art keywords
exhaust gas
turbine
turbine wheel
additional air
internal combustion
Prior art date
Application number
PCT/EP2011/005661
Other languages
German (de)
English (en)
Inventor
Michael Stiller
Kai Kanning
Siegfried Sumser
Tobias Lorenz
Original Assignee
Daimler Ag
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 Daimler Ag filed Critical Daimler Ag
Publication of WO2012072183A1 publication Critical patent/WO2012072183A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
    • F02C6/10—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output supplying working fluid to a user, e.g. a chemical process, which returns working fluid to a turbine of the plant
    • F02C6/12—Turbochargers, i.e. plants for augmenting mechanical power output of internal-combustion piston engines by increase of charge pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • 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
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
    • 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
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
    • 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
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • 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
    • F02B39/085—Non-mechanical drives, e.g. fluid drives having variable gear ratio the fluid drive using expansion of fluids other than exhaust gases, e.g. a Rankine cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • F02C6/16—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads for storing compressed air
    • 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
    • F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
    • F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
    • F01N13/08—Other arrangements or adaptations of exhaust conduits
    • F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
    • F01N13/107—More than one exhaust manifold or exhaust collector
    • 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
    • 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
    • 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
    • F02M26/40—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with timing means in the recirculation passage, e.g. cyclically operating valves or regenerators; with arrangements involving pressure pulsations
    • 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
    • F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
    • F02M26/43—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders in which exhaust from only one cylinder or only a group of cylinders is directed to the intake of the engine
    • 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
    • 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
    • F05D2240/00—Components
    • F05D2240/10—Stators
    • F05D2240/12—Fluid guiding means, e.g. vanes
    • F05D2240/128—Nozzles
    • 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
    • F05D2240/00—Components
    • F05D2240/10—Stators
    • F05D2240/12—Fluid guiding means, e.g. vanes
    • F05D2240/129—Cascades, i.e. assemblies of similar profiles acting in parallel
    • 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
    • F05D2260/00—Function
    • F05D2260/14—Preswirling
    • 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
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids
    • 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 a charging device for an internal combustion engine specified in the preamble of claim 1. Art.
  • the gas storage Has intake and a turbine in an exhaust line and a gas storage for receiving compressed gas.
  • the gas storage is charged or discharged depending on the operating state of the internal combustion engine, the gas storage is filled by the exhaust back pressure upstream of the turbine with exhaust gas, which additionally drives the exhaust gas turbocharger when unloading the gas storage.
  • exhaust gas which additionally drives the exhaust gas turbocharger when unloading the gas storage.
  • its storage contents can be fed to the exhaust gas line upstream of the turbine.
  • DE 101 58 874 A1 discloses an exhaust gas turbocharger for an internal combustion engine, with an exhaust gas turbine in the exhaust line and a compressor in the intake, wherein the compressor comprises a compressor in an inflow passage in the compressor housing, and with an additional air feeding device associated with the compressor area.
  • the additional air feed device comprises an additional air channel in the compressor housing for the supply of additional air, which is to be introduced via an injection opening in the wall of the inflow channel compressed into the inflow region of the compressor wheel.
  • Such a charging device for an internal combustion engine of a motor vehicle comprises at least one exhaust gas turbocharger which, in an exhaust tract of the
  • Internal combustion engine through-flow turbine housing comprises.
  • Turbine housing is rotatably received by the exhaust gas acted upon and thereby driven turbine wheel.
  • the charging device further comprises at least one supply device, by means of which the exhaust gas turbocharger additional air can be supplied.
  • the feed device has at least one introduction point arranged in the exhaust tract, via which the turbine wheel is connected to the
  • Driving desselbigen can be acted upon with the additional air. This can do that
  • the compressor For compressing the air, the compressor comprises, for example, a compressor wheel rotatably connected to a shaft, wherein the turbine wheel is also connected in a rotationally fixed manner to the shaft. If the turbine wheel is exposed to exhaust gas and from this
  • Internal combustion engines can compress supplied air.
  • the drive of the turbine wheel and thus the compressor wheel thus depends in particular on the mass flow of the exhaust gas, which flows through the turbine housing and the turbine wheel flows.
  • it may come to low mass flows of the exhaust gas, so that in particular the high load ranges and therefore possibly a high moment of inertia having turbine wheel can not be driven as desired.
  • This only happens an inert pressure build-up of the compressor and thus an inert power or torque buildup of the internal combustion engine. This leads to a
  • turbo lag undesirable driving behavior
  • turbo lag is thereby avoided or at least reduced.
  • the charging device according to the invention has in particular the advantage that an introduction of the additional air for driving the exhaust gas turbocharger or the turbine wheel is not provided an intake tract but in the exhaust gas tract of the internal combustion engine.
  • the introduction of additional air for driving the exhaust gas turbocharger in the intake tract has the disadvantage that in this solution, at least one
  • Valve device must be provided in the intake tract, so that it is none
  • valve device obstructs the intake tract, so that it does not come to this backflow.
  • the compressor delivers against the closed valve direction and thus against a closed system, so that the compressor exceeds its surge limit, if no additional blow-off device is provided upstream of the valve.
  • the charging device according to the invention it is possible to direct the additional air at least substantially directly to the turbine wheel and thus to be able to drive it particularly efficiently.
  • the additional air in the charging device according to the invention can be introduced into the exhaust tract at a substantially higher pressure than in the intake tract, so that the turbine wheel can be driven in a particularly advantageous manner.
  • no complex pressure control is needed.
  • the compressor reaches its pumping limit or even this
  • variable turbine used as the turbine of the exhaust gas turbocharger.
  • a variable turbine comprises an adjusting device, by means of which flow conditions in the flow direction of the exhaust gas upstream of the turbine wheel and / or stromabigen are influenced.
  • the adjusting device makes it possible, for example, at least one
  • the charging device according to the invention has the further advantage that such adjusting devices and thus additional components are not necessarily required to realize a very good instationary behavior of the internal combustion engine. As a result, the charging device according to the invention has a low number of parts, low weight and low costs.
  • the charging device according to the invention can be used in internal combustion engines for passenger cars.
  • the advantage of the low cost comes especially in internal combustion engine for commercial vehicles to fruition, since their cost-effectiveness depends in particular on the cost, which can be kept low by the charging device according to the invention.
  • the charging device allows efficient operation of the
  • Turbine pressure ratio pressure upstream of the turbine wheel in relation to the pressure downstream of the turbine wheel
  • Turbine pressure ratio pressure upstream of the turbine wheel in relation to the pressure downstream of the turbine wheel
  • the discharge point is at least partially arranged upstream of the turbine wheel.
  • the turbine can be supplied particularly well the additional air and the turbine wheel are particularly efficient driven by the additional air.
  • the discharge point is at least partially disposed in the axial direction of the turbine wheel in at least partially overlapping with a Rastructure of the turbine wheel, wherein the Raley is advantageously designed to be open.
  • the additional air can be supplied to the turbine wheel at least substantially axially and the additional air can first at least substantially axially flow from the particular open RaITA forth vanes of the turbine wheel and thereby drive the turbine wheel.
  • the turbine wheel by means of the feed device with compressed air as the additional air can be acted upon.
  • the additional air is pressurized air
  • compressed air compressed air
  • additional air is compressed, for example by means of an air compressor to a pressure of 10 to 12 bar inclusive and optionally in one Storage device, such as a pressure vessel, stored, in particular cached.
  • the storage device communicates fluidically with the point of introduction, so that the additional compressed air present as compressed air can flow from the storage device to the point of introduction and flow to the turbine wheel.
  • the high pressure of the additional air has the advantage that thereby the turbine wheel and thus the compressor wheel in particular in low load ranges of
  • Internal combustion engine can be driven particularly well, which is associated with a particularly advantageous compression of the air and thus with a particularly advantageous torque structure of the internal combustion engine.
  • the feed device comprises a valve device by means of which the additional air can be introduced as required into the exhaust tract and the
  • This valve device is, for example, a clocked valve.
  • a connecting line of the storage device and the discharge point is at least in
  • Insert intermediate position in which the connecting line is only partially fluidly released and a flow cross-section is set, which is smaller than the maximum flow cross-section.
  • a plurality of such intermediate positions are adjustable.
  • the valve means a so-called black and white valve, which completely blocks the connection line fluidically or can release completely fluid.
  • the clocked valve allows a very precise supply of air into the exhaust system, while the black and white valve has very low cost.
  • the feed device comprises a swirl device, by means of which the additional air which acts on the turbine wheel is to be provided with a swirl.
  • the additional air flowing to the turbine wheel has a twist and thus a high
  • the discharge point is at least partially disposed at the height of a largest diameter of the turbine wheel. This leads to a particularly efficient implementation of the energy contained in the flow of the additional air for driving the turbine wheel, whereby a particularly good transient behavior of the internal combustion engine is shown.
  • the turbine power is proportional to the inlet temperature of an incoming and acting on the turbine wheel gas for driving the turbine wheel, which is the exhaust gas of the internal combustion engine and / or the additional air in the charging device according to the invention.
  • at least one heating device is provided, by means of which the additional air can be heated upstream of the turbine wheel.
  • Compressor can be driven particularly well. This is a desired provided by the compressor boost pressure in a particularly short time to avoid the so-called turbo lag available. In addition, this prevents it at the point of introduction to icing, especially at low temperatures comes, which could adjust with a content of the storage device with ambient temperature and cold internal combustion engine.
  • the reheating device preferably comprises a heat exchanger, by means of which the additional air can be heated to the additional air as a result of heat transfer from the exhaust gas of the internal combustion engine.
  • a Laval nozzle is provided at the point of introduction, via which the turbine wheel can be acted upon by the additional air, then the turbine wheel can be acted upon by the additional air in a particularly efficient and streamlined manner and can therefore be driven.
  • the turbine housing has at least two floods which are fluidly separated from each other at least in regions by means of a partition wall of the turbine housing.
  • the turbine housing is formed at least twice.
  • the partition wall of the turbine housing is provided, wherein in this partition a fluidically connected to the inlet and by the additional air flow-through inlet channel is formed, via which the turbine wheel with the additional air can be acted upon.
  • This supply of additional air via the inlet channel not only means a particularly streamlined supply of additional air to the turbine wheel.
  • this has the turbine housing and thus the entire charging only a very small space requirement, which contributes to the avoidance and solution of package problems, especially in a space-critical area such as an engine compartment of the motor vehicle.
  • Turbine housing supplied, in particular blown, is.
  • the manufacturing costs for the turbine housing can be kept low.
  • the flood in which the additional air is optionally injected, it is a so-called lambda flood, which in particular during operation of the Charger fulfills the task of providing a desired air-fuel ratio of the internal combustion engine.
  • the other of the floods is, for example, a so-called EGR flood (EGR exhaust gas recirculation), which at least essentially fulfills the task of providing an advantageous upflow behavior of the turbine, so that an advantageous and desired large amount of exhaust gas from the exhaust gas tract can be returned to the intake of the internal combustion engine and introduced into this. This is by the EGR flood (EGR exhaust gas recirculation), which at least essentially fulfills the task of providing an advantageous upflow behavior of the turbine, so that an advantageous and desired large amount of exhaust gas from the exhaust gas tract can be returned to the intake of the internal combustion engine and introduced into this.
  • EGR flood EGR exhaust gas recirculation
  • the floods of the turbine housing may be symmetrical to each other and have at least substantially equal flow cross-sections.
  • the floods are formed asymmetrically to each other, wherein the lambda flood, for example, has a flow cross-section which is greater than a flow cross section of EGR flow.
  • an introduction channel which is fluidically connected to the introduction point and can be flowed through by the additional air is provided, which curved in the circumferential direction of the turbine wheel, kinked, bent and / or otherwise curved or oblique and at the discharge point, in particular directly, subsequent Mouth region has, via which the inlet channel opens into a receiving space of the turbine housing in which the turbine wheel is accommodated.
  • This mouth region allows the additional air to be fed obliquely to the turbine wheel in the circumferential direction of the turbine wheel over its circumference, so that the flow of additional air in the circumferential direction of the turbine wheel is already pre-aligned and the turbine wheel does not flow perpendicular to its axis of rotation.
  • the additional air for flowing into the receiving space in the circumferential direction of the turbine wheel is deflected in its direction of rotation, so that the additional air can flow the turbine wheel particularly streamlined. This leads to a particularly speed and thus boost pressure buildup of the exhaust gas turbocharger.
  • the charging device By means of the charging device, it is in particular possible to design internal combustion engines with regard to the downsizing principle. This means that by means of charging device according to the invention also in internal combustion engines with a relatively small displacement high torques and high performance can be realized while implementing the advantageous instationary behavior.
  • the charging device may also comprise at least two exhaust gas turbochargers with a respective turbine arranged in the exhaust tract of the internal combustion engine, which exhaust gas of the internal combustion engine can be flowed through and arranged in series with one another. This means that the exhaust gas flows through first a first of the turbines and then the second of the turbines. Before flowing through the first turbine, the exhaust gas has a certain pressure level. The exhaust gas is expanded by the first turbine and in particular by the turbine wheel of the first turbine and thus lowered to a contrast lower pressure level.
  • the exhaust gas flows through the second turbine, through which, in particular by the turbine wheel of the second turbine, the exhaust gas in turn expands and is lowered to a contrast lower pressure level.
  • the first turbine as a high-pressure turbine and thus the exhaust gas turbocharger comprising this high-pressure turbine is called a high-pressure exhaust gas turbocharger
  • the second turbine as a low-pressure turbine and accordingly the exhaust gas turbocharger comprising this low-pressure turbine can be referred to as a low-pressure exhaust gas turbocharger.
  • Fig. 1 is a schematic diagram of an internal combustion engine with a
  • Charging device which comprises an exhaust gas turbocharger, the additional means for driving the exhaust gas turbocharger can be fed by means of a feeding device of the charging device;
  • Fig. 2 is a schematic diagram of another embodiment of the
  • Fig. 3 is a schematic longitudinal sectional view of an exhaust gas turbocharger for a
  • FIGS. 3 and 4 shows a detail of a schematic longitudinal sectional view of a turbine of an exhaust gas turbocharger according to FIGS. 3 and 4;
  • Embodiment of the turbine according to FIG. 5 Embodiment of the turbine according to FIG. 5.
  • Fig. 1 shows an internal combustion engine 10 for a motor vehicle with six cylinders 12 and 12 '.
  • this air sucks according to a directional arrow 14 from the environment, the air is under ambient pressure p1.
  • the air flows via a corresponding intake piping of an intake tract 15 of the internal combustion engine 10 to a compressor 16 arranged in the intake manifold 15 of an exhaust gas turbocharger 18 of a charging device 19 of the internal combustion engine 10, wherein the air is compressed by the compressor 16 to a relation to the ambient pressure p1 higher boost pressure.
  • the air heated by the compression flows via a corresponding intake piping of the intake tract 15 to an intercooler 20, through which it flows and by means of which the air is cooled again to increase the degree of turbocharging.
  • Downstream of Charge air cooler 20 the air flows through a corresponding intake piping of the intake tract 15 on to an air intake manifold 22 arranged in the intake manifold 15, by means of which the standing under a pressure p2s air to the cylinders 12 and 12 'is supplied.
  • the internal combustion engine 10 is, for example, a directly injecting gasoline engine or a directly injecting diesel engine, wherein fuel is injected directly into the cylinders 12 and 12 'by means of a respective injector and thus supplied to the air in the cylinders 12 and 12' ,
  • the internal combustion engine 10 may also be a directly injecting gasoline engine or a directly injecting diesel engine, wherein fuel is injected directly into the cylinders 12 and 12 'by means of a respective injector and thus supplied to the air in the cylinders 12 and 12' ,
  • the internal combustion engine 10 may also be a
  • Internal combustion engine 10 act with intake manifold injection, wherein the air upstream of the cylinder 12 and 12 ', for example, in the air distributor 22, is supplied with fuel. Thus, a premixed air-fuel mixture flows into the cylinders 12 and 12 '.
  • an air-fuel mixture which is ignited by spark ignition or by auto-ignition and burns.
  • an exhaust gas is produced in the cylinders 12 and 12 ', which flows out of the cylinders 12 and 12' and into a corresponding exhaust gas piping via an exhaust manifold 32 arranged in an exhaust tract 31 of the internal combustion engine 10.
  • an exhaust tract 31 is a turbine 34 of the
  • Exhaust gas turbocharger 8 is arranged, which comprises, for example, two asymmetrical to each other formed floods 36 and 36 '.
  • the exhaust gas is introduced by means of the exhaust piping.
  • About these floods 36 and 36 ' is arranged in a receiving space of a turbine housing of the turbine 34
  • the turbine wheel is rotatably connected to a shaft 38 of the exhaust gas turbocharger 18, with which a compressor wheel of the compressor 16 is rotatably connected. So the compressor wheel can be driven via the turbine wheel and compress the air.
  • Combustion manifold 32 is summarized and the flood 36 'is supplied by means of the corresponding exhaust piping.
  • the exhaust gas has the pressure p31.
  • the flood 36 ' acts as a so-called EGR flood, which has a smaller flow cross-section than the flood 36 acting as a so-called lambda flood.
  • the flood 36' provides Thus, a desired high Aufstauu ready, so that a desired high amount of exhaust gas by means of an exhaust gas recirculation device 24 of the
  • Internal combustion engine 0 is branched off from the exhaust tract 31 and to the
  • Intake tract 15 can be recycled and introduced into the intake tract 15.
  • the lambda flood at least substantially fulfills the task of setting a desired ratio of the fuel to the air in the air-fuel mixture.
  • the exhaust of the flood 36 has the pressure p32
  • the exhaust gas is supplied via the floods 36 and 36 'to the turbine wheel and expanded by the turbine 34, so that the exhaust gas downstream of the turbine wheel has a lower pressure p4 than the pressures p31 and p32. About a corresponding exhaust piping then the exhaust gas is released to the environment.
  • the exhaust gas recirculation device 24 For recirculation of the exhaust gas, the exhaust gas recirculation device 24 comprises a
  • Branch point 28 at which an exhaust gas recirculation line 26 fluidly with the
  • Exhaust piping is connected. Thus, exhaust gas from the exhaust piping into the
  • Exhaust gas recirculation line 26 are returned to the intake manifold 15. This is the
  • Exhaust gas recirculation line 26 fluidly connected to the Ansaugverrohrung at a discharge point 30 so that the exhaust gas from the exhaust gas recirculation line 26 can flow into the exhaust pipe.
  • the compressed air is exposed to exhaust gas, so that particle and nitrogen oxide emissions of the internal combustion engine 10 can be kept low.
  • the exhaust gas recirculation device 24 comprises an exhaust gas recirculation cooler 40, by means of which the exhaust gas flowing through the exhaust gas recirculation line 26 is to be cooled. Furthermore, the exhaust gas recirculation device 24 comprises an exhaust gas recirculation valve 42, by means of which a
  • desired recirculating amount of exhaust gas is adjustable.
  • the charging device 19 comprises an air compressor 44 of a feed device 45 of the charging device 19, which can be driven by the internal combustion engine 10.
  • the air compressor 44 is connected, for example via at least one belt, via at least one chain, via at least one pair of gears or the like connecting element with a crankshaft of the internal combustion engine 10.
  • the air compressor 44 sucks during its operation air from the environment according to a directional arrow 46 and compresses this air.
  • the compressed air flows to a downstream of the
  • Air compressor arranged tank 48 of the feeding device 45 in which the compressed and thus stored as compressed air is stored.
  • the air in the tank 48 has a pressure in the range of 10 to 12 bar inclusive.
  • the received in the tank 48 and present as compressed air air is used as additional air to drive the turbine of the turbine 34 of the exhaust gas turbocharger 18 and thus the compressor wheel of the compressor 6 of the exhaust gas turbocharger 18.
  • a connecting line 50 of the feed device 45 is provided, which is fluidically connected on the one hand to the tank 48. On the other hand, it flows at least indirectly into the receiving space in which the turbine wheel of the turbine 34 is received. This means that the additional air can be introduced into the turbine housing and the turbine wheel can be acted upon by this additional air in order to drive it by means of the additional air, in particular in addition to the exhaust gas.
  • This low mass flow of the exhaust gas may not be capable of higher load ranges, in particular the full load range, the
  • Internal combustion engine 10 designed and possibly a high inertia having turbine wheel to drive in a desired manner, so that it comes to only sluggish speed structure of the compressor wheel at a transition from low load ranges to the contrast higher load ranges. This can lead to an undesirable instationary behavior of the internal combustion engine 10 and to an undesired driving behavior of the same, since with the
  • Internal combustion engine can provide a desired by a driver of the motor vehicle torque or a desired performance.
  • the turbine wheel and thus the compressor can be driven by the additional air in particular at a transition from lower to higher load ranges.
  • This possibility of driving the turbine wheel both by means of the exhaust gas and by means of the additional air even at the transition from low to higher load ranges, a fast speed and thus a faster boost pressure build-up, so that the torque desired by the driver or the desired performance at least almost without delay of the
  • Internal combustion engine 10 can be provided.
  • Turbine performance increased and run-up i.
  • the so-called turbo lag is at least in the
  • Feeding device 45 is not adversely affected.
  • the feed device 45 comprises a valve device 54.
  • the valve device 54 for example, only between one
  • a minimum flow cross-section for example a
  • valve device 54 has at least one intermediate position between the release position and the closed position, in which a smaller flow cross-section than in the release position but a larger
  • Valve device 54 adjustable, wherein the intermediate positions differ with respect to the enabled or blocked flow cross-section.
  • the turbine 34 of the exhaust gas turbocharger 18 is designed for example as a solid geometry turbine. That it does not include any adjusting device for influencing
  • the turbine 34 also includes such an adjusting device, by means of which the flow conditions upstream and / or downstream of the turbine wheel can be influenced.
  • Such an adjusting device allows, for example, the
  • the turbine 34 includes a bypass 56 having a bypass 58 through which exhaust gas can bypass the turbine. As a result, the turbine wheel is not acted upon by the exhaust gas and not driven by this.
  • Bypass device 58 serves to control the boost pressure.
  • Bypass device 56 an ambient valve 60, which is also referred to as waste gate.
  • the charging device 19 with the feeding device 45 also has the advantage that in addition to the thermodynamic advantages by driving the turbine by means of the additional air, the need for flaps, valve means and / or Umblaseö réelleen in or on the side of the intake tract 15 does not exist. Rather, the charging device 19 with the supply device 45 is an uncomplex
  • FIG. 2 shows an alternative embodiment of the internal combustion engine 10 comprising the cylinders 12 and 12 '. As can be seen from Fig. 2, the
  • Cylinder 12 summarized and are supplied via the functioning as an EGR flood flood 36' of the turbine 34.
  • the exhaust gas of the cylinder 12 is also by means of the exhaust manifold 32nd
  • the combined exhaust of the cylinder 12 is the as
  • lambda flood acting flood 36 supplied.
  • the flood 36 serves in
  • the turbine 34 of the exhaust gas turbocharger 18 according to FIG. 2 can also be designed as a double-flow asymmetrical solid geometry turbine with or without a bypass device 56 (waste gate).
  • the turbine 34 may be formed as shown in FIG. 2 as an asymmetric Varioturbine and include, for example, an adjusting device 62, by means of which flow conditions upstream of the turbine wheel can be acted upon.
  • the adjusting device 62 is designed for example as a tongue slide and comprises in the circumferential direction of the turbine wheel over its circumference and arranged in
  • Circumferentially displaceable tongues by means of which a flow cross-section upstream of the turbine wheel is adjustable.
  • a control device 64 is provided which controls the adjusting device 62 and the exhaust gas recirculation valve 42.
  • Storage device 66 includes, for example, a particulate filter and / or a
  • Oxidation catalyst and / or a nitrogen oxide storage catalyst and / or an SCR catalyst (SCR - selective catalytic reduction).
  • the exhaust gas recirculation device 24 comprises a damping device 68 arranged downstream of the exhaust gas recirculation cooler 40 with a damping volume 70.
  • a damping device 68 By means of the damping device 68, pressure pulsations of the recirculated exhaust gas are avoided or at least substantially reduced.
  • an air filter 72 is arranged, by means of which the intake of the internal combustion engine 10 air is to be filtered.
  • a crankshaft 74 is shown by means of which a translational movement of pistons received in the cylinders 12 and 12 'is to be converted into a rotational movement according to a directional arrow 76.
  • the feeding device 45 of the charging device 19 comprises two heat exchangers 78 and 78 '.
  • the heat exchangers 78 and 78 ' are arranged in the flow direction of the additional air from the tank 48 to the inlet 52 in the exhaust duct 31 and allow heating of the additional air before it flows into the exhaust duct 31 and the
  • the heat exchanger 78 is in operative connection with the
  • Exhaust after-treatment device 66 is of the additional air according to a
  • Directional arrow 80 can be flowed through.
  • a heat transfer from the exhaust gas aftertreatment device 66, which is hot during operation of the internal combustion engine 10, to the additional air flowing through the heat exchanger 78 is possible, as a result of which it is heated by the additional air.
  • the heat exchanger 78 works on the countercurrent principle and is in a
  • Heat exchanger 78 allows heat transfer from the hot exhaust gas to the additional air, so that heats the additional air. Thereby, a recuperation of heat energy contained in the exhaust gas as well as heat energy of the
  • Exhaust after-treatment device 66 is shown, which would otherwise be discharged unused to the environment. This contributes to a high efficiency of the internal combustion engine 10 with the charging device 19 at. Furthermore, this results in a further increase in the turbine power of the turbine 34, since the turbine power is proportional to the inlet temperature of an incoming and the turbine wheel
  • Fig. 3 shows a possible embodiment of the exhaust gas turbocharger 18 of
  • the exhaust gas turbocharger 18 includes the compressor 16, which has a compressor housing 82 in which a compressor wheel 84 is rotatably received about a rotation axis 86.
  • the exhaust gas turbocharger 18 further includes a bearing housing 88, in which the shaft 38 is rotatably mounted.
  • the turbine 34 of the exhaust gas turbocharger 18 includes a turbine housing 90 with the two floods 36 and 36 '. As can be seen from FIG. 3, the floods 36 and 36 'are at least substantially symmetrical to each other and at least in the
  • a receiving space 92 is formed, in which a turbine wheel 94 of the turbine 34 is rotatably received about the axis of rotation 86.
  • the turbine wheel 94 is non-rotatably connected to the shaft 38.
  • the introduction point 52 is integrated in the turbine housing 90 of the turbine 34, wherein the introduction point 52 is rotated in the circumferential direction and rotational direction of the turbine wheel 94 in the image plane of FIG. 3.
  • a Laval nozzle 96 connects, via which the additional air upstream of the turbine wheel 94 to flow into the turbine housing 90 and the turbine wheel 94 can flow streamlined to drive.
  • the Laval nozzle 96 opens via the introduction point 52 into an annular nozzle 98 formed by walls of the turbine housing 90, which is arranged upstream of the turbine wheel 94.
  • the exhaust gas and optionally the additional air flow to the turbine wheel 94 at least substantially in the radial direction.
  • the turbines 34 of the charging devices 19 according to FIGS. 1 and 2 as well as other embodiments of the charging device 19 may thus be radial turbines.
  • a corresponding number of discharge points such as the discharge point 52 and a corresponding number of nozzles such as the Laval Nozzle 96 fixed.
  • more than one introduction point 52 and / or Laval nozzle 96 can be provided in order to introduce the additional air into the exhaust gas tract 31 for, in particular, additional driving of the turbine wheel 94.
  • the Laval nozzle 96 represents a swirl nozzle, by means of which the additional air flowing into the exhaust tract 31 or into the turbine housing 90 can be imparted with a swirl.
  • Other swirl generating devices are also possible.
  • Such a twist is a particularly spiral-shaped rotational movement about an axis parallel to the flow direction.
  • FIG. 4 shows a further embodiment of the turbine designed as a double-flow symmetrical turbine 34 according to FIG. 3. As shown in FIG. 4, are
  • Einleitstellen 52 arranged in overlap with an open trained wheel back 100 of the turbine wheel 94 and formed in a heat shield 102 as passages.
  • the heat shield 102 serves that bearing housing 88 in front of a
  • the passage openings are formed as swirl openings, so that the additional air, the turbine wheel 94 with a high
  • Flow energy from Ratile 100 at least substantially initially flow in the axial direction and thus can drive very efficient.
  • a space 104 at least partially limited by the bearing housing 88, the turbine housing 90 and the heat shield 102 acts as a collecting space, wherein high gas forces must be taken into account when dimensioning and fastening the heat shield 102.
  • the introduction points 52 in the form of the swirl openings are located in very close proximity to the turbine wheel 94 or its wheel back 100, so that an at least substantially direct admission of the turbine wheel 94 by the additional air is made possible. This favors a particularly efficient driving of the
  • Turbine wheel 94 and thus the compressor wheel 84 to illustrate a fast
  • FIG. 5 shows a further embodiment of the double-flow symmetrical turbine 34 according to FIGS. 3 and 4.
  • the turbine housing 90 has a partition wall 106, through which the floods 36 and 36 'At least partially fluidly separated from each other.
  • an introduction channel 108 is now formed, which adjoins the inlet 52 and is fluidly connected thereto.
  • an exit of the additional air from the inlet channel 08 advantageously takes place at least almost centrally into the annular nozzle 98 upstream of the turbine wheel 94. This provides a streamlined application and thus an efficient driving of the turbine wheel 94.
  • FIG. 6 shows a further embodiment of the introduction channel 108.
  • the introduction channel 108 has an opening region 112, via which the introduction channel 108 opens into the ring nozzle 98 or into the receiving space 92.
  • the mouth region 102 in this case adjoins directly at the introduction point 52 and is fluidically connected thereto. 6, the mouth region 112 in the circumferential direction of the turbine wheel 94 of the receiving space 92 and thus the annular nozzle 98 according to a directional arrow 114 in the direction of rotation according to a directional arrow 116, in which the Turbine wheel 94 during operation of the exhaust gas turbocharger 18 rotates, curved.
  • the additional air is deflected before entering the annular nozzle 98 in the circumferential direction according to the directional arrow 116, which is represented by a directional arrow 110 in FIG. 6.
  • the additional air flows the turbine wheel 94 obliquely to its real direction, whereby the turbine wheel is particularly streamlined and efficiently driven.

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

Abstract

L'invention concerne un dispositif de suralimentation (19) pour un moteur à combustion interne (10) d'un véhicule automobile, comprenant au moins un turbocompresseur à gaz d'échappement (18) qui comprend un carter de turbine (90) disposé dans une conduite de gaz d'échappement (31) du moteur à combustion interne (10) et pouvant être parcouru par le gaz d'échappement du moteur à combustion interne (10). Une roue de turbine (94) pouvant être sollicitée par le gaz d'échappement est reçue à rotation dans le carter de turbine. Le dispositif de suralimentation (19) selon l'invention comprend aussi au moins un dispositif d'alimentation (45) au moyen duquel le turbocompresseur à gaz d'échappement (18) peut être alimenté en air supplémentaire, le dispositif d'alimentation (45) présentant au moins un point d'introduction (52) disposé dans la conduite de gaz d'échappement (31), par le biais duquel la roue de turbine (94) peut être sollicitée en air supplémentaire.
PCT/EP2011/005661 2010-12-01 2011-11-11 Dispositif de suralimentation pour un moteur à combustion interne WO2012072183A1 (fr)

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Cited By (3)

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GB2523855A (en) * 2014-03-07 2015-09-09 Cummins Ltd Turbomachine arrangement
US10151256B2 (en) 2016-12-15 2018-12-11 Caterpillar Inc. Systems and methods to control cold transient response via air assist
EP4008887A1 (fr) * 2020-12-07 2022-06-08 BMTS Technology GmbH & Co. KG Système d'échappement pour un moteur à combustion interne

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DE102012100339A1 (de) * 2012-01-16 2013-07-18 Universität der Bundeswehr München Verfahren und Vorrichtung zur Stabilisierung eines Verdichterstroms
EP2749751B1 (fr) * 2012-12-28 2016-07-27 Volvo Car Corporation Turbocompresseur amélioré
EP2960458A1 (fr) 2014-06-27 2015-12-30 Volvo Car Corporation Moteur turbochargé avec un réservoir d'air comprimé pour alimenter la turbine des gaz d'échappement en air additionnel quand la charge moteur requise est suffisamment grande
DE102014223306A1 (de) * 2014-11-14 2016-05-19 Bosch Mahle Turbo Systems Gmbh & Co. Kg Abgasturbolader
EP3051098B1 (fr) 2015-02-02 2018-04-11 Volvo Car Corporation Dispositif de turbocompresseur à volutes jumelées avec une meilleure réponse turbo
EP3095982B1 (fr) * 2015-05-20 2018-12-05 Volvo Car Corporation Système de turbocompresseur amélioré
FR3114125A1 (fr) * 2020-09-17 2022-03-18 Psa Automobiles Sa Moteur a injection d’air a l’echappement
DE102020007366B4 (de) 2020-12-03 2023-12-14 Mercedes-Benz Group AG Verbrennungskraftmaschine für ein Kraftfahrzeug, insbesondere für einen Kraftwagen, sowie Kraftfahrzeug

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GB620376A (en) * 1946-01-16 1949-03-23 British Thomson Houston Co Ltd Improvements in and relating to exhaust driven turbo-superchargers of internal combustion engines
DE8023061U1 (de) * 1980-08-29 1981-02-26 Nova-Werke Ag, Effretikon (Schweiz) Vorrichtung zum aufladen eines verbrennungsmotors mit einem turbolader
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EP0821147A1 (fr) * 1996-07-26 1998-01-28 Daimler-Benz Aktiengesellschaft Dispositif de frein moteur pour un moteur à combustion interne avec turbocompresseur
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GB2523855A (en) * 2014-03-07 2015-09-09 Cummins Ltd Turbomachine arrangement
GB2523855B (en) * 2014-03-07 2020-04-01 Cummins Ltd Turbomachine arrangement
US10151256B2 (en) 2016-12-15 2018-12-11 Caterpillar Inc. Systems and methods to control cold transient response via air assist
EP4008887A1 (fr) * 2020-12-07 2022-06-08 BMTS Technology GmbH & Co. KG Système d'échappement pour un moteur à combustion interne

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