DE102006014934A1 - Internal combustion engine e.g. diesel engine, has air flow adjusting device implemented as axial valve, which is arranged in flow path of air flow to compressor wheel and integrated in compressor housing of high pressure compressor - Google Patents
Internal combustion engine e.g. diesel engine, has air flow adjusting device implemented as axial valve, which is arranged in flow path of air flow to compressor wheel and integrated in compressor housing of high pressure compressor Download PDFInfo
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- DE102006014934A1 DE102006014934A1 DE102006014934A DE102006014934A DE102006014934A1 DE 102006014934 A1 DE102006014934 A1 DE 102006014934A1 DE 102006014934 A DE102006014934 A DE 102006014934A DE 102006014934 A DE102006014934 A DE 102006014934A DE 102006014934 A1 DE102006014934 A1 DE 102006014934A1
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- compressor
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- axial slide
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 55
- 238000000034 method Methods 0.000 claims abstract 3
- 238000011144 upstream manufacturing Methods 0.000 claims description 11
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 101100495769 Caenorhabditis elegans che-1 gene Proteins 0.000 claims 1
- 230000002596 correlated effect Effects 0.000 claims 1
- 239000007789 gas Substances 0.000 description 34
- 230000000694 effects Effects 0.000 description 3
- 238000005192 partition Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000009499 grossing Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000000746 purification Methods 0.000 description 1
Classifications
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- 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
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- 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
- F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
-
- 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
- F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
- F01D17/143—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path the shiftable member being a wall, or part thereof of a radial diffuser
-
- 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
- F02B29/0412—Multiple heat exchangers arranged in parallel or in series
-
- 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
- F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
-
- 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
- F02B37/013—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in series
-
- 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
- F02B37/12—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
- 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
- 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
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- 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
- F02M26/08—EGR systems specially adapted for supercharged engines for engines having two or more intake charge compressors or exhaust gas turbines, e.g. a turbocharger combined with an additional 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
- F02M26/22—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
- 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
- F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
-
- 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
Abstract
Description
Die Erfindung bezieht sich auf eine Brennkraftmaschine mit zwei in Reihe geschalteten Abgasturboladern nach dem Oberbegriff des Anspruches 1.The The invention relates to an internal combustion engine with two in series switched exhaust gas turbocharger according to the preamble of the claim 1.
In
der
Auch dem Hochdruckverdichter ist ein Bypass mit darin angeordnetem Bypassventil zugeordnet. Bei geschlossenem Verdichterbypass wirkt das Bypassventil als Rückschlagventil. Bei Undichtigkeiten im Bypassventil kann es jedoch zu unerwünschten Rezirkulationsströmungen hin zum Verdichtereintritt kommen, was mit erheblichen Wirkungsgradeinbußen verbunden ist. Ein weiteres Problem liegt in der sprunghaften Änderung des von der Brennkraftmaschine abgegebenen Drehmoments für den Fall, dass der Verdichterbypass schlagartig geöffnet wird. Diese sprunghafte Drehmomentänderung muss durch motorinterne Eingriffe kompensiert werden.Also The high pressure compressor is a bypass with bypass valve arranged therein assigned. When the compressor bypass is closed, the bypass valve acts as a check valve. In case of leaks in the bypass valve, however, it may be undesirable recirculation flows come to the compressor entry, which is associated with significant efficiency losses is. Another problem is the sudden change of the torque output by the internal combustion engine in the event that the compressor bypass is opened suddenly. This leaping torque change must be compensated by internal engine intervention.
Der Erfindung liegt die Aufgabe zugrunde, das im Abgas enthaltene Energiepotenzial zur Steigerung des Gesamtwirkungsgrades mit einfachen konstruktiven Maßnahmen in optimaler Weise zu nutzen, wobei zugleich ein effektiver Schutz gegen Bauteilüberlastungen bei hohen Lasten und Drehzahlen der Brennkraftmaschine gegeben sein soll.Of the Invention is based on the object, the energy potential contained in the exhaust gas to increase the overall efficiency with simple constructive activities in an optimal way, while at the same time providing effective protection against component overloads be given at high loads and speeds of the internal combustion engine should.
Diese Aufgabe wird erfindungsgemäß mit den Merkmalen des Anspruches 1 gelöst. Die Unteransprüche geben zweckmäßige Weiterbildungen an.These Task is according to the invention with the Characteristics of claim 1 solved. The dependent claims give expedient further education at.
Bei der erfindungsgemäßen Brennkraftmaschine ist dem Hochdruckverdichter eine Luftstromreguliereinrichtung zur Einstellung und Beeinflussung des Luftstroms im Ansaugtrakt zugeordnet, die als in das Verdichtergehäuse des Hochdruckverdichters integriertes Stellorgan ausgeführt ist. Dieses Stellorgan befindet sich innerhalb des Verdichtergehäuses des Hochdruckverdichters im Strömungsweg des Luftstromes zum Verdichterrad. Eine Stellbewegung des Stellorgans bewirkt eine Änderung im Luftstrom, der zum Verdichterrad geführt ist, und damit auch eine Änderung des Verdichterwirkungsgrades und des vom Verdichter erzeugten Ladedrucks. Auf diese Weise ist es möglich, Einfluss auf den Wirkungsgrad des Hochdruckladers sowie auf den Gesamtwirkungsgrad der Brennkraftmaschine allein durch konstruktive Maßnahmen zu nehmen, die innerhalb des Verdichtergehäuses des Hochdruckverdichters vorgesehen sind. Ein extern am Verdichtergehäuse entlang geführter Bypass ist dagegen nicht erforderlich, so dass auch keine Probleme mit Undichtigkeiten im Bypassventil und einer hierdurch hervorgerufenen Rezirkulationsströmung oder mit einer sprunghaften Änderung des Drehmoments beim Öffnen des Bypassventils auftreten können. Vielmehr ist aufgrund der Beeinflussung der Luftströmung stromauf des Verdichterrades eine kontinuierliche, stetige Anpassung im Druckaufbau unter Vermeidung sprunghafter Änderungen möglich, da die Strömungsbeeinflussung sich aufgrund der Trägheit des Verdichterrades mit einer drehmomentglättenden Zeitverzögerung auf den Ladedruck durchsetzt. Zudem sind im Unterschied zu einer Ventilöffnung bei einer Bewegung des Stellorgans keine schlagartigen Strömungsänderungen zu befürchten. Bei der erfindungsgemäßen Lösung wird der gesamte Luftstrom im Ansaugtrakt durch den Hochdruckverdichter geführt, wobei der engste, den Luftstromdurchsatz bestimmende Querschnitt im Hochdruckverdichter den aktuellen Anforderungen entsprechend über die Einstellung des Stellorgans variiert wird.at the internal combustion engine according to the invention the high pressure compressor is a Luftstromreguliereinrichtung for Setting and influencing the air flow in the intake system assigned, as in the compressor housing the high-pressure compressor integrated actuator is executed. This actuator is located inside the compressor housing of the high pressure compressor in the flow path of the Air flow to the compressor wheel. An actuating movement of the actuator causes a change in the air flow, which is guided to the compressor wheel, and thus a change the compressor efficiency and the boost pressure generated by the compressor. In this way it is possible Influence on the efficiency of the high pressure loader as well as on the Overall efficiency of the internal combustion engine solely by constructive activities to take inside the compressor housing of the high pressure compressor are provided. An external bypass on the compressor housing is not required, so no problems with Leaks in the bypass valve and thereby caused recirculation or with a sudden change the torque when opening of the bypass valve may occur. Rather, it is due to the influence of the air flow upstream the compressor wheel a continuous, steady adjustment in pressure build-up avoiding sudden changes possible, because the flow control due to inertia the compressor wheel with a torque-smoothing time delay enforced the boost pressure. In addition, unlike a valve opening at a Movement of the actuator to fear no sudden flow changes. In the solution according to the invention is the entire air flow in the intake tract through the high pressure compressor guided, wherein the narrowest, the air flow rate determining cross-section in high pressure compressor according to the current requirements on the Adjustment of the actuator is varied.
Das Stellorgan ist zweckmäßig als Axialschieber ausgeführt, der axial verschieblich im Verdichtereinlasskanal stromauf der Schaufeleintrittskante des Verdichterrades gelagert ist. Mithilfe des Axialschiebers wird die Anströmung auf das Verdichterrad beeinflusst. Möglich ist beispielsweise eine Ausführung des Hochdruckverdichters mit einem zusätzlich zum Verdichtereinlasskanal vorgesehenen Zusatzkanal, über den Verbrennungsluft dem Verdichterrad zuführbar ist und der radial in den Verdichtereinlasskanal einmündet, wobei der Axialschieber den Querschnitt der Mündungsöffnung des Zusatzkanals beeinflussen kann. Dies erfolgt beispielhaft dadurch, dass der Axialschieber eine Wandung des Zusatzkanals bildet und die Mündungsöffnung zwischen der Stirnseite des Axialschiebers und einem Gehäuseabschnitt des Verdichtergehäuses angeordnet ist, so dass bei einer axialen Stellbewegung des Axialschiebers der Querschnitt der Mündungsöffnung variiert wird. In dieser Ausführung verläuft der Zusatzkanal radial außerhalb des Verdichtereinlasskanals, der Axialschieber ist zweckmäßig als Schiebehülse ausgebildet und begrenzt den Zusatzkanal radial nach innen.The actuator is expediently designed as axial slide, which is mounted axially displaceable in the compressor inlet passage upstream of the blade leading edge of the compressor wheel. By means of the axial slide, the flow to the compressor wheel is influenced. It is possible, for example, an embodiment of the high-pressure compressor with an additional channel provided in addition to the compressor inlet duct, via the combustion air to the compressor is fed and opens radially into the compressor inlet passage, wherein the axial slide can influence the cross-section of the orifice of the additional channel. This is done by way of example in that the axial slide forms a wall of the additional channel and the mouth opening between the end face of the axial slide and a housing portion of the compressor housing is arranged, so that in an axial adjusting movement of the Axial slide the cross-section of the mouth opening is varied. In this embodiment, the additional channel extends radially outside of the compressor inlet channel, the axial slide is expediently designed as a sliding sleeve and limits the additional channel radially inwardly.
Die Mündungsöffnung des Zusatzkanals befindet sich vorteilhaft axial in Höhe der Verdichterradschaufeln des Verdichterrades. Aufgrund der radialen Einmündung des Zusatzkanals in den Verdichtereinlasskanal trifft die über den Zusatzkanal herangeführte Verbrennungsluft mit radialer Komponente auf die Verdichterradschaufeln, wobei zusätzlich eine Strömungskomponente in Umfangsrichtung mithilfe eines in der Mündungsöffnung platzierten Drallgitters erreicht werden kann, wodurch die Verdichterradschaufeln einen zusätzlichen Drehimpuls von der über den Zusatzkanal herangeführten Verbrennungsluft erfahren. Diese Betriebsweise kann insbesondere im so genannten Kaltluft-Turbinenbetrieb bei niedrigen Lasten und Drehzahlen der Brennkraftmaschine durchgeführt werden, bei denen in den Zylindereinlässen ein Unterdruck herrscht, so dass über der Hochdruckturbine ein Druckabfall entsteht, der für einen zusätzlichen Antrieb des Verdichterrades ausgenutzt werden kann.The Mouth opening of the Additional channel is located advantageously axially equal to the compressor wheel blades of the compressor wheel. Due to the radial opening of the additional channel in the Compressor inlet channel hits the combustion air introduced via the additional duct with radial component on the compressor wheel blades, wherein additionally a flow component achieved in the circumferential direction by means of a swirl grid placed in the mouth opening may be, whereby the compressor impeller blades an additional Angular momentum from the over introduced the additional channel Experience combustion air. This mode of operation can in particular in so-called cold air turbine operation at low loads and Speeds of the internal combustion engine are performed, in which in the cylinder inlets a negative pressure prevails, so that above the high-pressure turbine, a pressure drop arises for An additional Drive the compressor wheel can be exploited.
Bei höheren Lasten und Drehzahlen dagegen kann der Zusatzkanal für die Ausbildung einer Rezirkulationsströmung geöffnet werden, bei der ein Teil der herangeführten Verbrennungsluft über den Zusatzkanal entgegen der Hauptströmrichtung zurückgeführt und wieder in den Verdichtereinlasskanal eingeleitet wird. Es handelt sich hierbei um eine so genannte kennfeldstabilisierende Maßnahme zur Verhinderung des Verdichterpumpens. Zugleich wird hierdurch der Luftmassenstrom reduziert, der durch den Hochdruckverdichter geschleust wird.at higher Loads and speeds, however, can be the additional channel for training a recirculation flow open in which a part of the supplied combustion air via the additional channel against the main flow direction returned and is introduced back into the compressor inlet passage. It deals this is a so-called map-stabilizing measure to prevent of the compressor pumping. At the same time thereby the air mass flow reduced, which is passed through the high-pressure compressor.
Für den Fall, dass sich keine Rezirkulationsströmung durch den Zusatzkanal ausbildet, ist bei geöffnetem Mündungsquerschnitt des Zusatzkanals eine Wirkungsgradverringerung zu erreichen, da der durch den Zusatzkanal geförderte Teilluftmassenstrom nicht die gleiche Wirkung auf das Verdichterrad entfaltet wie der axial herangeführte Luftmassenstrom. Die Öffnung des Mündungsquerschnitts zwischen Zusatzkanal und Verdichtereinlasskanal im Bereich des Verdichterrades hat daher eine Wirkungsgradreduzierung zur Folge. Damit der Hochdruckverdichter bei einer entsprechenden Anforderung einer Regel- und Steuereinheit der Brennkraftmaschine einen maximalen Ladedruck erzeugen kann, wird daher der Axialschieber in der Weise zu betätigen sein, dass die Mündungsöffnung zwischen Zusatzkanal und Verdichtereinlasskanal geschlossen wird.In the case, that no recirculation flow through the additional channel training is open Opening cross-section the additional channel to achieve a reduction in efficiency, since funded by the additional channel Partial air mass flow does not unfold the same effect on the compressor wheel as the axially introduced Air mass flow. The opening of the mouth cross-section between additional channel and compressor inlet channel in the area of the compressor wheel therefore results in a reduction in efficiency. So that the high pressure compressor with a corresponding request of a control and control unit the internal combustion engine can generate a maximum boost pressure, Therefore, the axial slide will be operated in such a way that the orifice between additional channel and compressor inlet channel is closed.
Die Stellbewegung des Axialschiebers wird vorteilhaft mithilfe eines Aktuators durchgeführt, der an einem Verstellhebel angreift, welcher fest mit dem Axialschieber verbunden ist. Die Einstellung des Aktuators erfolgt durch Stellsignale der Regel- und Steuereinheit in Abhängigkeit von Zustands- und Betriebsgrößen der Brennkraftmaschine bzw. der der Brennkraftmaschine zugeordneten Hilfsaggregate.The Actuation movement of the axial slide is advantageously using a Actuator performed, which engages an adjusting lever, which is firmly connected to the axial slide is. The adjustment of the actuator is performed by control signals of Control and control unit in dependence of state and operating variables of Internal combustion engine or the internal combustion engine assigned Auxiliary units.
Als Stellorgan, welches den Luftstrom hin zum Verdichterrad beeinflusst, kommt auch ein dem Verdichterrad axial unmittelbar vorgelagerter Sperrschieber im Verdichtereinlasskanal in Betracht, bei dessen axialer Stellbewegung die axial auf das Verdichterrad auftreffende Luftströmung variiert wird. Dieser Sperrschieber kann mit dem Axialschieber zusammenwirken, der eine Wandung des Zusatzkanals bildet und außerdem die Mündungsöffnung zwischen Zusatzkanal und Verdichtereinlasskanal begrenzt. Trifft der Sperrschieber auf den Axialschieber auf und verstellt diesen in Richtung auf das Verdichterrad, so wird die Mündungsöffnung zwischen Zusatzkanal und Verdichtereinlasskanal verkleinert und gegebenenfalls vollständig geschlossen. Auf diese Weise kann mit nur einem Aktuator sowohl die unmittelbar axial auf das Verdichterrad auftreffende Luftströmung als auch die über den Zusatzkanal radial auf das Verdichterrad auftreffende Luftströmung beeinflusst werden.When Actuator, which influences the air flow towards the compressor wheel, also comes the compressor immediately axially upstream Gate valve in the compressor inlet passage into consideration, in whose axial adjusting movement which impinges axially on the compressor wheel airflow is varied. This gate valve can interact with the axial slide, which forms a wall of the additional channel and also the mouth opening between additional channel and compressor inlet channel limited. Arrives the gate valve the axial slide on and adjusted in the direction of the compressor wheel, so the mouth opening is between Additional channel and compressor inlet channel reduced and, where appropriate Completely closed. In this way, with only one actuator both the directly axially impinging on the compressor wheel air flow as also the over the additional channel influenced radially on the compressor impinging air flow become.
Weitere Vorteile und zweckmäßige Ausführungen sind den weiteren Ansprüchen, der Figurenbeschreibung und den Zeichnungen zu entnehmen. Es zeigen:Further Advantages and expedient designs are the further claims, the figure description and the drawings. Show it:
In den Figuren sind gleiche Bauteile mit gleichen Bezugszeichen versehen.In The figures are the same components with the same reference numerals.
Die
in
Die
Verbrennungsluft wird über
den Ansaugtrakt
Stromab
des Hochdruckverdichters
Abgasseitig
werden die von der Brennkraftmaschine
Zur
Umgehung der Hochdruckturbine
Die
Brennkraftmaschine
Sämtliche
einstellbaren Aggregate der Brennkraftmaschine werden in Abhängigkeit
von Zustands- und Betriebsgrößen des
Motors und der Aggregate mithilfe von Stellsignalen einer Regel-
und Steuereinheit
In
Im
Verdichtereinlasskanal ist ein Axialschieber
Der
Querschnitt der Mündungsöffnung
Der
Axialschieber
In
der Darstellung nach
In
Wie
in
In
In
Etwa
parallel zur Abgasflut
Claims (13)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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DE102006014934A DE102006014934A1 (en) | 2006-03-31 | 2006-03-31 | Internal combustion engine e.g. diesel engine, has air flow adjusting device implemented as axial valve, which is arranged in flow path of air flow to compressor wheel and integrated in compressor housing of high pressure compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006014934A DE102006014934A1 (en) | 2006-03-31 | 2006-03-31 | Internal combustion engine e.g. diesel engine, has air flow adjusting device implemented as axial valve, which is arranged in flow path of air flow to compressor wheel and integrated in compressor housing of high pressure compressor |
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DE102006014934A1 true DE102006014934A1 (en) | 2007-10-04 |
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DE102006014934A Withdrawn DE102006014934A1 (en) | 2006-03-31 | 2006-03-31 | Internal combustion engine e.g. diesel engine, has air flow adjusting device implemented as axial valve, which is arranged in flow path of air flow to compressor wheel and integrated in compressor housing of high pressure compressor |
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Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2009095632A1 (en) * | 2008-02-01 | 2009-08-06 | Cummins Turbo Technologies Limited | A variable geometry turbine with wastegate |
DE102009010310A1 (en) * | 2009-02-24 | 2010-09-02 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Loading device, particularly turbo-supercharger for motor vehicle, has turbine housing and compressor housing, where compressor housing is formed by inner shell and outer shell |
EP2687676A3 (en) * | 2012-07-20 | 2014-09-10 | Pratt & Whitney Canada Corp. | Compound cycle engine |
US9512721B2 (en) | 2012-07-20 | 2016-12-06 | Pratt & Whitney Canada Corp. | Compound cycle engine |
US9926843B2 (en) | 2012-07-20 | 2018-03-27 | Pratt & Whitney Canada Corp. | Compound cycle engine |
US10107195B2 (en) | 2012-07-20 | 2018-10-23 | Pratt & Whitney Canada Corp. | Compound cycle engine |
DE102010035085B4 (en) | 2010-08-21 | 2019-08-08 | Audi Ag | Motor vehicle with an internal combustion engine and method for operating an internal combustion engine |
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2006
- 2006-03-31 DE DE102006014934A patent/DE102006014934A1/en not_active Withdrawn
Cited By (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009095632A1 (en) * | 2008-02-01 | 2009-08-06 | Cummins Turbo Technologies Limited | A variable geometry turbine with wastegate |
GB2469423A (en) * | 2008-02-01 | 2010-10-13 | Cummins Turbo Tech Ltd | A variable geometry turbine with wastegate |
US8191368B2 (en) | 2008-02-01 | 2012-06-05 | Cummins Turbo Technologies Limited | Variable geometry turbine with wastegate |
GB2469423B (en) * | 2008-02-01 | 2012-09-05 | Cummins Turbo Tech Ltd | A variable geometry turbine with wastegate |
DE102009010310A1 (en) * | 2009-02-24 | 2010-09-02 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Loading device, particularly turbo-supercharger for motor vehicle, has turbine housing and compressor housing, where compressor housing is formed by inner shell and outer shell |
DE102010035085B4 (en) | 2010-08-21 | 2019-08-08 | Audi Ag | Motor vehicle with an internal combustion engine and method for operating an internal combustion engine |
US9194232B2 (en) | 2012-07-20 | 2015-11-24 | Pratt & Whitney Canada Corp. | Compound cycle engine |
US9512721B2 (en) | 2012-07-20 | 2016-12-06 | Pratt & Whitney Canada Corp. | Compound cycle engine |
US9856789B2 (en) | 2012-07-20 | 2018-01-02 | Pratt & Whitney Canada Corp. | Compound cycle engine |
US9926843B2 (en) | 2012-07-20 | 2018-03-27 | Pratt & Whitney Canada Corp. | Compound cycle engine |
US10107195B2 (en) | 2012-07-20 | 2018-10-23 | Pratt & Whitney Canada Corp. | Compound cycle engine |
US10196971B2 (en) | 2012-07-20 | 2019-02-05 | Pratt & Whitney Canada Corp. | Compound cycle engine |
EP2687676A3 (en) * | 2012-07-20 | 2014-09-10 | Pratt & Whitney Canada Corp. | Compound cycle engine |
US10920662B2 (en) | 2012-07-20 | 2021-02-16 | Pratt & Whitney Canada Corp. | Compound cycle engine |
US10968824B2 (en) | 2012-07-20 | 2021-04-06 | Pratt & Whitney Canada Corp. | Compound cycle engine |
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Owner name: DAIMLER AG, 70327 STUTTGART, DE |
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R005 | Application deemed withdrawn due to failure to request examination |
Effective date: 20130403 |