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WO2006056393A1 - Exhaust-gas turbo charger for an internal combustion engine - Google Patents

Exhaust-gas turbo charger for an internal combustion engine Download PDF

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Publication number
WO2006056393A1
WO2006056393A1 PCT/EP2005/012469 EP2005012469W WO2006056393A1 WO 2006056393 A1 WO2006056393 A1 WO 2006056393A1 EP 2005012469 W EP2005012469 W EP 2005012469W WO 2006056393 A1 WO2006056393 A1 WO 2006056393A1
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WO
WIPO (PCT)
Prior art keywords
turbine
internal combustion
combustion engine
compressor
exhaust gas
Prior art date
Application number
PCT/EP2005/012469
Other languages
German (de)
French (fr)
Inventor
Josef Günther
Alexander Kaiser
Berthold Keppeler
Detlef Scharr
Original Assignee
Daimlerchrysler 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 Daimlerchrysler Ag filed Critical Daimlerchrysler Ag
Publication of WO2006056393A1 publication Critical patent/WO2006056393A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • 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
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • F02B37/11—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump driven by other drive at starting only
    • 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
    • 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 an exhaust gas turbocharger for an internal combustion engine according to the preamble of claim 1 and of claim 6.
  • An exhaust-gas turbocharger is already known (Publication No. JP 2003254051 A, Application No. 2002058839), the turbine of which can be bypassed by means of a bypass.
  • a boost pressure control valve a so-called waste gate valve is arranged, which can open or close the bypass.
  • a bypass of the turbine of the exhaust gas turbocharger In the open position of the waste gate valve, a bypass of the turbine of the exhaust gas turbocharger, wherein the exhaust gas directly into one of the turbine downstream
  • Exhaust gas purification device in particular catalyst
  • Such waste gate valves are known to protect the exhaust gas turbocharger by bypassing the exhaust gas around the turbine at high amounts of exhaust gas.
  • This makes it possible to obtain a relatively high temperature level of the exhaust gas in the cold start phase of the internal combustion engine, which leads to a faster startup in a downstream catalytic converter.
  • By bypassing the turbine by means of the waste gate valve it follows that no operation of the from the turbine driven compressor more occurs.
  • In the critical cold start phase of the internal combustion engine so • no corresponding increase in pressure of the intake air is possible.
  • This results in a non-optimal operation of the internal combustion engine result which also causes increased hydrocarbon emissions in the exhaust gas in addition to increased fuel consumption.
  • the dynamic behavior of the exhaust gas turbocharger is not optimal, so that the ride comfort is also impaired.
  • the exhaust gas turbocharger according to the invention with the characterizing features of claim 1 and claim 6 has the advantage that in addition to the achievement of a high exhaust gas temperature in the operating range of the cold start phase of the internal combustion engine, a compression of the intake air of the internal combustion engine is ensured. This leads to an optimal operation of the internal combustion engine in the critical cold start phase, which also reduced in addition to a reduced fuel consumption
  • Hydrocarbon emissions in the exhaust gas are the result. Furthermore, the increase in the exhaust gas temperature is carried out in a fuel-efficient manner compared to conventional heating measures for the exhaust gas.
  • the dynamic behavior of the exhaust gas turbocharger is improved, so that the ride comfort in the critical cold start phase and also in the subsequent warm-up phase of the internal combustion engine is improved.
  • FIG. 1 shows a first embodiment according to the invention of the exhaust gas turbocharger for an internal combustion engine in a schematically simplified functional representation
  • Fig. 2 shows a second embodiment according to the invention of the exhaust gas turbocharger for an internal combustion engine in a schematically simplified functional representation
  • Fig. 3 shows a third embodiment of the invention the exhaust gas turbocharger for an internal combustion engine in a schematically simplified functional representation. Description of the embodiments
  • FIG. 1 shows a first embodiment of an exhaust-gas turbocharger according to the invention for an internal combustion engine 1, which has a compressor 2 and a turbine 3.
  • the compressor 2 and the turbine 3 are rotatably connected via a shaft 8 with each other.
  • the internal combustion engine 1 may be an Otto internal combustion engine or a diesel internal combustion engine.
  • the turbine 3 drives in a known manner via the shaft 8 to the compressor 2.
  • the operation of the turbine 3 is known to take place via the exhaust gases of the internal combustion engine 1, which are supplied from an exhaust line 5 of the internal combustion engine 1 of the turbine 3.
  • a bypass 12 is provided in the exhaust line 5, in which a valve, a so-called waste gate valve 10, is introduced.
  • Such valves are used for boost pressure control, in which they can control the exhaust gas quantity entering or entering the turbine 3 by more or less opening or closing the bypass 12, whereby a corresponding operation of the compressor 2 is established.
  • the bypass 12 is opened, so that the exhaust gases of the internal combustion engine 1 from the exhaust line 5, bypassing the turbine 3 directly into a downstream of the turbine 3 provided exhaust gas purification device 25, in particular a catalyst can flow.
  • Such waste gate valves 10 are used in addition to the boost pressure control and the protection of the turbine.
  • This drive can, as indicated in Figure 1, be designed as an electric drive 14, which acts for example directly to a compressor shaft of the compressor 2, not shown.
  • the electric drive 14 can be coupled for example via a coupling 16 to the compressor 2 and its compressor shaft.
  • the electrical energy must within engine, for example, over a generator of the internal combustion engine 1 are provided.
  • This additional exhaust gas temperature increase is desirable in the cold start phase of the internal combustion engine 1, as it leads to an improved effect of the catalyst 25 or to a faster popping thereof due to the increase in the exhaust gas temperature.
  • the exhaust gas temperature increase can be further enhanced by other, not shown, further electrical consumers of the internal combustion engine or of a motor vehicle are switched on.
  • the electric heaters of a urea metering device not shown in detail for the exhaust gas purification device 25 can be used for this purpose.
  • the wastegate valve 10 is brought into its closed position or boost pressure control position, so that the exhaust gases essentially pass back to the catalyst 25 via the turbine 3.
  • the exhaust turbine 3 In this state when acted upon by exhaust turbine 3 is a conventional drive of the compressor 2 via the shaft 8, so that it is possible to turn off the additional drive 14 again.
  • the electric drive 14 is, as stated, provided only in the cold start phase of the internal combustion engine 1. But it is also possible to use the additional electric drive 14 for short-term increase in boost pressure during normal operation of the internal combustion engine 1 or to activate for a short time.
  • FIG. 2 shows a second exemplary embodiment of the exhaust-gas turbocharger according to the invention, which via the additional drive 15 independent of the turbine 3 features.
  • the same or equivalent components are identified by the same reference numerals of the first embodiment.
  • the drive 15 may be a mechanical drive, for example in the form of a crankshaft 15, which is coupled via the coupling 16 to a compressor shaft of the compressor 2, not shown.
  • the mechanical drive 15, 16 of the compressor 2 is as in the first embodiment of the
  • the mechanical drive 15 can be decoupled from the compressor 2 again via the coupling 16. But it is also possible to use the additional mechanical drive 15 for short-term increase in boost pressure during normal operation of the internal combustion engine 1 or to activate for a short time.
  • FIG. 3 shows a third exemplary embodiment according to the invention, in which the same or equivalent components have been identified by the same reference numerals of the first and second exemplary embodiments.
  • a second compressor 20 is provided instead of an additional electric or mechanical drive of the compressor 2.
  • the second compressor 20 is housed downstream of the first compressor 2 in the intake tract 4 of the internal combustion engine 1 and serves as a substitute for the first, in the cold start phase of the internal combustion engine 1 non-driven compressor 2. In the cold start phase takes place via the waste gate valve 10 bridging the Turbine 3, which therefore fails as a drive for the first compressor 2.
  • the second compressor 20 has a second bypass 22, which bypasses the second compressor 20.
  • a second valve 30 in the manner of the waste gate valve 10th housed, which opens the second bypass 22 in an open position and closes the second bypass 22 in a closed position.
  • a bypass of the second compressor 20 which is then ineffective.
  • Only in the closed position of the second valve 30 is an admission of the second compressor 20 with the first, in the cold start phase of the internal combustion engine 1 not active compressor 2 ago flowing air.
  • the loading or closed position of the second valve 30 is inventively provided in particular in the cold start phase of the internal combustion engine 1.
  • a dashed line in Figure 3 indicated electric drive 14 may be provided, which is optionally connected via a clutch 16 as in the first embodiment.
  • electric drive 14 it is also possible, as shown in FIG. 3 by a solid line, to mechanically drive the second compressor 20, for example via a crankshaft 15, which can be connected to the second compressor 20 via a coupling 16.
  • control of the first valve 10, the second valve 30 and the electric Drive 14 and / or the clutch 16 are taken over by an electrical control unit 40.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Exhaust Gas After Treatment (AREA)

Abstract

The invention relates to an exhaust-gas turbo charger for an internal combustion engine, comprising a compressor (2) which is arranged in the intake section (4) and a turbine which is arranged in the exhaust gas line (5). The turbine (3) and the compressor (2) are connected together in a rotationally secure manner by means of a common shaft (8). The turbine (3) is surrounded by a bypass (12) wherein a valve (10) is provided. The compressor (2) comprises a drive (14, 15) which is independent from the turbine (3), said drive being activated in the cold start operation of the internal combustion engine (1) for maintaining the compression in the intake section (4).

Description

Abgasturbolader für eine Brennkraftmaschine Exhaust gas turbocharger for an internal combustion engine
Die Erfindung geht aus von einem Abgasturbolader für eine Brennkraftmaschine nach der Gattung des Anspruchs 1 bzw. des Anspruchs 6.The invention relates to an exhaust gas turbocharger for an internal combustion engine according to the preamble of claim 1 and of claim 6.
Es ist bereits ein Abgasturbolader bekannt (Publication-No. JP 2003254051 A, Application-No. 2002058839), dessen Turbine mittels eines Bypasses umgangen werden kann. In dem Bypass ist ein Ladedruck-Regelventil, ein sogenanntes Waste-Gate- Ventil, angeordnet, welches den Bypass öffnen oder schließen kann. In Offenstellung des Waste-Gate-Ventils erfolgt eine Umgehung der Turbine des Abgasturboladers, wobei das Abgas direkt in eine der Turbine nachgeschalteteAn exhaust-gas turbocharger is already known (Publication No. JP 2003254051 A, Application No. 2002058839), the turbine of which can be bypassed by means of a bypass. In the bypass, a boost pressure control valve, a so-called waste gate valve is arranged, which can open or close the bypass. In the open position of the waste gate valve, a bypass of the turbine of the exhaust gas turbocharger, wherein the exhaust gas directly into one of the turbine downstream
Abgasreinigungseinrichtung, insbesondere Katalysator, strömen kann. Derartige Waste-Gate-Ventile sind bekannt, um den Abgasturbolader durch bypassieren des Abgases um die Turbine herum bei hohen Abgasmengen zu schützen. Es ist aber auch bekannt, das Waste-Gate-Ventil in einem Kaltstartbetrieb der Brennkraftmaschine zu öffnen, um so eine Temperaturerniedrigung des Abgases durch eine ansonsten stattfindende Expansion in der Turbine zu vermeiden. Damit lässt sich in der Kaltstartphase der Brennkraftmaschine ein relativ hohes Temperaturniveau des Abgases erhalten, welches in einem nachgeschalteten Katalysator zu einem schnelleren Anspringen führt. Durch die Umgehung der Turbine mittels des Waste-Gate-Ventils ergibt sich jedoch, dass kein Betrieb des von der Turbine angetriebenen Verdichters mehr erfolgt. In der kritischen Kaltstartphase der Brennkraftmaschine ist so • keine entsprechende Druckerhöhung der angesaugten Luft möglich. Dies hat eine nicht optimale Betriebsweise der Brennkraftmaschine zur Folge, welche neben einem erhöhten Kraftstoffverbrauch auch erhöhte Kohlenwasserstoffemissionen im Abgas bewirkt. Des Weiteren ist das dynamische Verhalten des Abgasturboladers nicht optimal, so dass der Fahrkomfort ebenfalls beeinträchtigt wird.Exhaust gas purification device, in particular catalyst, can flow. Such waste gate valves are known to protect the exhaust gas turbocharger by bypassing the exhaust gas around the turbine at high amounts of exhaust gas. However, it is also known to open the wastegate valve in a cold start operation of the internal combustion engine, so as to avoid a decrease in temperature of the exhaust gas by an otherwise occurring expansion in the turbine. This makes it possible to obtain a relatively high temperature level of the exhaust gas in the cold start phase of the internal combustion engine, which leads to a faster startup in a downstream catalytic converter. By bypassing the turbine by means of the waste gate valve, however, it follows that no operation of the from the turbine driven compressor more occurs. In the critical cold start phase of the internal combustion engine so • no corresponding increase in pressure of the intake air is possible. This results in a non-optimal operation of the internal combustion engine result, which also causes increased hydrocarbon emissions in the exhaust gas in addition to increased fuel consumption. Furthermore, the dynamic behavior of the exhaust gas turbocharger is not optimal, so that the ride comfort is also impaired.
Vorteile der ErfindungAdvantages of the invention
Der erfindungsgemäße Abgasturbolader mit den kennzeichnenden Merkmalen des Anspruchs 1 bzw. des Anspruchs 6 hat demgegenüber den Vorteil, dass neben der Erzielung einer hohen Abgastemperatur im Betriebsbereich der Kaltstartphase der Brennkraftmaschine auch eine Verdichtung der angesaugten Luft der Brennkraftmaschine gewährleistet wird. Dies führt zu einer optimalen Betriebsweise der Brennkraftmaschine in der kritischen Kaltstartphase, wodurch neben einem verringerten Kraftstoffverbrauch auch verringerteThe exhaust gas turbocharger according to the invention with the characterizing features of claim 1 and claim 6 has the advantage that in addition to the achievement of a high exhaust gas temperature in the operating range of the cold start phase of the internal combustion engine, a compression of the intake air of the internal combustion engine is ensured. This leads to an optimal operation of the internal combustion engine in the critical cold start phase, which also reduced in addition to a reduced fuel consumption
Kohlenwasserstoffemissionen im Abgas die Folge sind. Des Weiteren erfolgt die Erhöhung der Abgastemperatur in verbrauchsgünstiger Weise im Vergleich zu herkömmlichen Aufheizmaßnahmen für das Abgas. Vorteilhafterweise wird dabei auch das dynamische Verhalten des Abgasturboladers verbessert, so dass auch der Fahrkomfort in der kritischen Kaltstartphase und auch in der nachfolgenden Warmlaufphase der Brennkraftmaschine verbessert ist.Hydrocarbon emissions in the exhaust gas are the result. Furthermore, the increase in the exhaust gas temperature is carried out in a fuel-efficient manner compared to conventional heating measures for the exhaust gas. Advantageously, while the dynamic behavior of the exhaust gas turbocharger is improved, so that the ride comfort in the critical cold start phase and also in the subsequent warm-up phase of the internal combustion engine is improved.
Besonders vorteilhaft ist gemäß Anspruch 6 das Vorsehen eines zweiten, separat angetriebenen Verdichters, wodurch neben der Aufrechterhaltung der Verdichtung in der Kaltstartphase der Brennkraftmaschine auch die Durchführung einer zweistufigen Aufladung der angesaugten Verbrennungsluft in den anderen Betriebsbereichen der Brennkraftmaschine möglich ist.It is particularly advantageous according to claim 6, the provision of a second, separately driven compressor, which in addition to maintaining the compression in the cold start phase of the Internal combustion engine, the implementation of a two-stage supercharging of the intake combustion air in the other operating ranges of the internal combustion engine is possible.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 bzw. Anspruch 6 angegebenen Abgasturboladers für eine Brennkraftmaschine möglich.The measures listed in the dependent claims advantageous refinements and improvements of claim 1 or claim 6 exhaust gas turbocharger for an internal combustion engine are possible.
Zeichnungdrawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert.Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description.
Es zeigen:Show it:
Fig. 1 ein erstes erfindungsgemäßes Ausführungsbeispiel des Abgasturboladers für eine Brennkraftmaschine in schematisch vereinfachter Funktionsdarstellung,1 shows a first embodiment according to the invention of the exhaust gas turbocharger for an internal combustion engine in a schematically simplified functional representation,
Fig. 2 ein zweites erfindungsgemäßes Ausführungsbeispiel des Abgasturboladers für eine Brennkraftmaschine in schematisch vereinfachter Funktionsdarstellung undFig. 2 shows a second embodiment according to the invention of the exhaust gas turbocharger for an internal combustion engine in a schematically simplified functional representation and
Fig. 3 ein drittes erfindungsgemäßes Ausführungsbeispiel des Abgasturboladers für eine Brennkraftmaschine in schematisch vereinfachter Funktionsdarstellung. Beschreibung der AusführungsbeispieleFig. 3 shows a third embodiment of the invention the exhaust gas turbocharger for an internal combustion engine in a schematically simplified functional representation. Description of the embodiments
In Figur 1 ist ein erstes erfindungsgemäßes Ausführungsbeispiel eines Abgasturboladers für eine Brennkraftmaschine 1 gezeigt, der über einen Verdichter 2 und eine Turbine 3 verfügt. Der Verdichter 2 und die Turbine 3 sind drehfest über eine Welle 8 miteinander verbunden. Bei der Brennkraftmaschine 1 kann es sich um eine Otto- Brennkraftmaschine oder um eine Diesel-Brennkraftmaschine handeln. Die Turbine 3 treibt in bekannter Weise über die Welle 8 den Verdichter 2 an. Der Verdichter 2 fördert Ansaugluft aus einem nicht näher dargestellten Luftfilter in einen Ansaugtrakt 4 der Brennkraftmaschine 1. Der Betrieb der Turbine 3 erfolgt bekanntermaßen über die Abgase der Brennkraftmaschine 1, welche aus einem Abgasstrang 5 der Brennkraftmaschine 1 der Turbine 3 zugeführt werden.FIG. 1 shows a first embodiment of an exhaust-gas turbocharger according to the invention for an internal combustion engine 1, which has a compressor 2 and a turbine 3. The compressor 2 and the turbine 3 are rotatably connected via a shaft 8 with each other. The internal combustion engine 1 may be an Otto internal combustion engine or a diesel internal combustion engine. The turbine 3 drives in a known manner via the shaft 8 to the compressor 2. The operation of the turbine 3 is known to take place via the exhaust gases of the internal combustion engine 1, which are supplied from an exhaust line 5 of the internal combustion engine 1 of the turbine 3.
Zum Umgehen der Abgase um die Turbine 3 herum, ist ein Bypass 12 im Abgasstrang 5 vorgesehen, in welchem ein Ventil, ein sogenanntes Waste-Gate-Ventil 10, eingebracht ist. Derartige Ventile dienen zur Ladedruckregelung, in dem sie die in die Turbine 3 eintretende bzw. um die Turbine 3 herumgeführte Abgasmenge durch mehr oder weniger öffnen bzw. schließen des Bypasses 12 steuern können, wodurch sich ein entsprechender Betrieb des Verdichters 2 einstellt. In einer Offenstellung des Waste-Gate-Ventils 10 ist der Bypass 12 geöffnet, so dass die Abgase der Brennkraftmaschine 1 aus dem Abgasstrang 5 unter Umgehung der Turbine 3 direkt in eine stromab der Turbine 3 vorgesehene Abgasreinigungseinrichtung 25, insbesondere einem Katalysator, strömen können. Derartige Waste-Gate-Ventile 10 dienen neben der Ladedruckregelung auch dem Schutz der Turbine. Sie werden beispielsweise geöffnet, wenn ein Überangebot an Abgas vorliegt, das zu einem Überdrehen der Turbine führen könnte. Es ist nun vorgesehen, auch in der Kaltstartphase und ggf. kurzzeitig auch in der nachfolgenden Warmlaufphase der Brennkraftmaschine 1 die Turbine 3 zu umgehen, wozu hierzu das Waste-Gate-Ventil 10 in seine Offenstellung gebracht wird. Damit wird die Turbine 3 außer Funktion gestellt und das Abgas gelangt ohne eine Expansion in der Turbine 3 direkt in den Katalysator 25. Damit ergibt sich eine hohe Abgastemperatur, da eine Temperaturerniedrigung durch die Expansion der Abgase in der Turbine 3 nicht erfolgt. Dies führt zu einem schnelleren Anspringen des Katalysators 25. Weitere, nicht näher dargestellte emissionsmindernde Maßnahmen die auf einer Zudosierung eines zusätzlichen Reduktionsmittels im Abgas, wie z. B. eine wässrige Harnstofflösung, sind in ihrer Funktionalität auf eine Mindesttemperatur im Abgas angewiesen. Durch Umgehen der Turbine 3 im Kaltstart können diese Maßnahmen eingesetzt werden, da die Mindestabgastemperatur schnell erreicht wird.To bypass the exhaust gases around the turbine 3 around, a bypass 12 is provided in the exhaust line 5, in which a valve, a so-called waste gate valve 10, is introduced. Such valves are used for boost pressure control, in which they can control the exhaust gas quantity entering or entering the turbine 3 by more or less opening or closing the bypass 12, whereby a corresponding operation of the compressor 2 is established. In an open position of the waste gate valve 10, the bypass 12 is opened, so that the exhaust gases of the internal combustion engine 1 from the exhaust line 5, bypassing the turbine 3 directly into a downstream of the turbine 3 provided exhaust gas purification device 25, in particular a catalyst can flow. Such waste gate valves 10 are used in addition to the boost pressure control and the protection of the turbine. They are opened, for example, if there is an oversupply of exhaust gas that could lead to overspeeding of the turbine. It is now planned to bypass the turbine 3 even in the cold start phase and possibly also briefly in the subsequent warm-up phase of the internal combustion engine 1, for which purpose the wastegate valve 10 is brought into its open position. Thus, the turbine 3 is put out of action and the exhaust gas passes without an expansion in the turbine 3 directly into the catalyst 25. This results in a high exhaust gas temperature, since a decrease in temperature due to the expansion of the exhaust gases in the turbine 3 does not occur. This leads to a faster onset of the catalyst 25. Further, not shown in detail emission-reducing measures on a metered addition of an additional reducing agent in the exhaust gas, such as. As an aqueous urea solution, are dependent in their functionality on a minimum temperature in the exhaust gas. By bypassing the turbine 3 in cold start these measures can be used, since the minimum exhaust gas temperature is reached quickly.
Bei Umgehung der Turbine 3 erfolgt kein Antrieb des mit der Turbine 3 gekoppelten Verdichters 2. Um die Aufladung der von der Brennkraftmaschine 1 angesaugten Luft in diesem Zustand dennoch gewährleisten zu können, ist nun erfindungsgemäß vorgesehen, den Verdichter 2 über einen zusätzlichen Antrieb 14 anzutreiben. Dieser Antrieb kann, wie in Figur 1 angedeutet, als elektrischer Antrieb 14 ausgestaltet sein, welcher beispielsweise direkt auf eine nicht näher dargestellte Verdichterwelle des Verdichters 2 wirkt. Der elektrische Antrieb 14 kann beispielsweise über eine Kupplung 16 an den Verdichter 2 bzw. dessen Verdichterwelle angekoppelt werden.When bypassing the turbine 3, no drive of the coupled to the turbine 3 compressor 2. In order to ensure the charging of the sucked in by the internal combustion engine 1 air in this state, it is now provided according to the invention to drive the compressor 2 via an additional drive 14. This drive can, as indicated in Figure 1, be designed as an electric drive 14, which acts for example directly to a compressor shaft of the compressor 2, not shown. The electric drive 14 can be coupled for example via a coupling 16 to the compressor 2 and its compressor shaft.
Zum Betrieb des elektrisch angetriebenen Verdichters 2 muss die elektrische Energie innermotorisch, zum Beispiel über einen Generator der Brennkraftmaschine 1 zur Verfügung gestellt werden. Dies hat eine Lasterhöhung für die Brennkraftmaschine 1 zur Folge, die wiederum zu einer zusätzlichen Temperaturerhöhung im Abgas führt. Diese zusätzliche Abgastemperaturerhöhung ist in der Kaltstartphase der Brennkraftmaschine 1 erwünscht, da sie aufgrund der Erhöhung der Abgastemperatur zu einer verbesserten Wirkung des Katalysators 25 bzw. zu einem schnelleren Anspringen desselben führt. Die Abgastemperaturerhöhung kann noch verstärkt werden, indem andere, nicht näher dargestellte, weitere elektrische Verbraucher der Brennkraftmaschine bzw. eines Kraftfahrzeugs zugeschaltet werden. Beispielsweise können hierzu die elektrischen Heizeinrichtungen einer nicht näher dargestellten Harnstoff-Dosiereinrichtung für die Abgasreinigungseinrichtung 25 Verwendung finden.For the operation of the electrically driven compressor 2, the electrical energy must within engine, for example, over a generator of the internal combustion engine 1 are provided. This has a load increase for the internal combustion engine 1 result, which in turn leads to an additional increase in temperature in the exhaust gas. This additional exhaust gas temperature increase is desirable in the cold start phase of the internal combustion engine 1, as it leads to an improved effect of the catalyst 25 or to a faster popping thereof due to the increase in the exhaust gas temperature. The exhaust gas temperature increase can be further enhanced by other, not shown, further electrical consumers of the internal combustion engine or of a motor vehicle are switched on. For example, the electric heaters of a urea metering device not shown in detail for the exhaust gas purification device 25 can be used for this purpose.
Nach der Kaltstartphase der Brennkraftmaschine 1 in der nachfolgenden Warmlaufphase, wird das Waste-Gate-Ventil 10 in seine Schließstellung bzw. Ladedruck-Regelstellung gebracht, so dass die Abgase im Wesentlichen wieder über die Turbine 3 zum Katalysator 25 gelangen. In diesem Zustand bei von Abgas beaufschlagter Turbine 3 erfolgt ein herkömmlicher Antrieb des Verdichters 2 über die Welle 8, so dass es möglich ist, den zusätzlichen Antrieb 14 wieder abzuschalten. Der elektrische Antrieb 14 ist, wie ausgeführt, nur in der Kaltstartphase der Brennkraftmaschine 1 vorgesehen. Möglich ist aber auch, den zusätzlichen elektrischen Antrieb 14 zur kurzfristigen Ladedruckerhöhung im Normalbetrieb der Brennkraftmaschine 1 einzusetzen bzw. kurzzeitig zu aktivieren.After the cold start phase of the internal combustion engine 1 in the subsequent warm-up phase, the wastegate valve 10 is brought into its closed position or boost pressure control position, so that the exhaust gases essentially pass back to the catalyst 25 via the turbine 3. In this state when acted upon by exhaust turbine 3 is a conventional drive of the compressor 2 via the shaft 8, so that it is possible to turn off the additional drive 14 again. The electric drive 14 is, as stated, provided only in the cold start phase of the internal combustion engine 1. But it is also possible to use the additional electric drive 14 for short-term increase in boost pressure during normal operation of the internal combustion engine 1 or to activate for a short time.
Die Figur 2 zeigt ein zweites erfindungsgemäßes Ausführungsbeispiel des Abgasturboladers, der über den zusätzlichen, von der Turbine 3 unabhängigen Antrieb 15 verfügt. Gleiche oder gleichwirkende Bauteile sind dabei mit denselben Bezugszeichen des ersten Ausführungsbeispiels gekennzeichnet. Bei dem Antrieb 15 kann es sich um einen mechanischen Antrieb handeln, beispielsweise in Form einer Kurbelwelle 15, die über die Kupplung 16 an eine nicht näher dargestellte Verdichterwelle des Verdichters 2 angekoppelt wird. Der mechanische Antrieb 15, 16 des Verdichters 2 ist wie im ersten Ausführungsbeispiel auf denFIG. 2 shows a second exemplary embodiment of the exhaust-gas turbocharger according to the invention, which via the additional drive 15 independent of the turbine 3 features. The same or equivalent components are identified by the same reference numerals of the first embodiment. The drive 15 may be a mechanical drive, for example in the form of a crankshaft 15, which is coupled via the coupling 16 to a compressor shaft of the compressor 2, not shown. The mechanical drive 15, 16 of the compressor 2 is as in the first embodiment of the
Betriebsbereich der Kaltstartphase der Brennkraftmaschine 1 beschränkt. In der nachfolgenden Warmlaufphase der Brennkraftmaschine 1 kann der mechanische Antrieb 15 über die Kupplung 16 wieder vom Verdichter 2 abgekoppelt werden. Möglich ist aber auch, den zusätzlichen mechanischen Antrieb 15 zur kurzfristigen Ladedruckerhöhung im Normalbetrieb der Brennkraftmaschine 1 einzusetzen bzw. kurzzeitig zu aktivieren.Operating range of the cold start phase of the internal combustion engine 1 limited. In the subsequent warm-up phase of the internal combustion engine 1, the mechanical drive 15 can be decoupled from the compressor 2 again via the coupling 16. But it is also possible to use the additional mechanical drive 15 for short-term increase in boost pressure during normal operation of the internal combustion engine 1 or to activate for a short time.
Die Figur 3 zeigt ein drittes erfindungsgemäßes Ausführungsbeispiel, bei dem gleiche oder gleichwirkende Bauteile mit denselben Bezugszeichen des ersten bzw. zweiten Ausführungsbeispiels gekennzeichnet worden sind. Anstelle eines zusätzlichen elektrischen oder mechanischen Antriebs des Verdichters 2 ist ein zweiter Verdichter 20 vorgesehen. Der zweite Verdichter 20 ist stromab des ersten Verdichters 2 im Ansaugtrakt 4 der Brennkraftmaschine 1 untergebracht und dient quasi als Ersatz des ersten, in der Kaltstartphase der Brennkraftmaschine 1 antriebslosen Verdichters 2. In der Kaltstartphase erfolgt über das Waste-Gate-Ventil 10 ein Überbrücken der Turbine 3, die daher als Antrieb für den ersten Verdichter 2 ausfällt. Der zweite Verdichter 20 verfügt über einen zweiten Bypass 22, welcher den zweiten Verdichter 20 umgeht. In dem zweiten Bypass 22 ist ein zweites Ventil 30 nach Art des Waste-Gate-Ventils 10 untergebracht, welches in einer Offenstellung den zweiten Bypass 22 öffnet und in einer Schließstellung den zweiten Bypass 22 schließt. In der Offenstellung des zweiten Ventils 30 erfolgt eine Umgehung des zweiten Verdichters 20, der dann wirkungslos ist. Nur in der Schließstellung des zweiten Ventils 30 erfolgt eine Beaufschlagung des zweiten Verdichters 20 mit der über den ersten, in der Kaltstartphase der Brennkraftmaschine 1 nicht aktiven Verdichter 2 her strömenden Luft. Die Beaufschlagung bzw. Schließstellung des zweiten Ventils 30 ist erfindungsgemäß insbesondere in der Kaltstartphase der Brennkraftmaschine 1 vorgesehen.FIG. 3 shows a third exemplary embodiment according to the invention, in which the same or equivalent components have been identified by the same reference numerals of the first and second exemplary embodiments. Instead of an additional electric or mechanical drive of the compressor 2, a second compressor 20 is provided. The second compressor 20 is housed downstream of the first compressor 2 in the intake tract 4 of the internal combustion engine 1 and serves as a substitute for the first, in the cold start phase of the internal combustion engine 1 non-driven compressor 2. In the cold start phase takes place via the waste gate valve 10 bridging the Turbine 3, which therefore fails as a drive for the first compressor 2. The second compressor 20 has a second bypass 22, which bypasses the second compressor 20. In the second bypass 22 is a second valve 30 in the manner of the waste gate valve 10th housed, which opens the second bypass 22 in an open position and closes the second bypass 22 in a closed position. In the open position of the second valve 30, a bypass of the second compressor 20, which is then ineffective. Only in the closed position of the second valve 30 is an admission of the second compressor 20 with the first, in the cold start phase of the internal combustion engine 1 not active compressor 2 ago flowing air. The loading or closed position of the second valve 30 is inventively provided in particular in the cold start phase of the internal combustion engine 1.
Zum Antrieb des zweiten Verdichters 20 kann ein in Figur 3 gestrichelt angedeuteter elektrischer Antrieb 14 vorgesehen sein, der wie im ersten Ausführungsbeispiel ggf. über eine Kupplung 16 zuschaltbar ist. Möglich ist aber auch, wie in Figur 3 mit durchgezogener Linie dargestellt ist, den zweiten Verdichter 20 mechanisch anzutreiben, beispielsweise über eine Kurbelwelle 15, die über eine Kupplung 16 dem zweiten Verdichter 20 zuschaltbar ist.For driving the second compressor 20, a dashed line in Figure 3 indicated electric drive 14 may be provided, which is optionally connected via a clutch 16 as in the first embodiment. However, it is also possible, as shown in FIG. 3 by a solid line, to mechanically drive the second compressor 20, for example via a crankshaft 15, which can be connected to the second compressor 20 via a coupling 16.
Selbstverständlich ist es mit dieser Anordnung auch möglich, außerhalb der Kaltstartphase der Brennkraftmaschine eine herkömmliche zweistufige Verdichtung der von der Brennkraftmaschine 1 angesaugten Luft durchzuführen. Das zweite Ventil 30 befindet sich dabei in seiner Schließstellung. Der zweite Verdichter 20 verdichtet dann die vom ersten, aktiven Verdichter 2 zugeführte, vorverdichtete Luft weiter, die dann über den Ansaugtrakt 4 in die Brennkraftmaschine 1 gelangt.Of course, it is also possible with this arrangement, outside the cold start phase of the internal combustion engine to perform a conventional two-stage compression of the sucked by the internal combustion engine 1 air. The second valve 30 is in its closed position. The second compressor 20 then further compresses the pre-compressed air supplied by the first active compressor 2, which then passes into the internal combustion engine 1 via the intake tract 4.
Wie in den Figuren 1 bis 3 angedeutet, kann in den beschriebenen Ausführungsbeispielen die Steuerung des ersten Ventils 10, des zweiten Ventils 30 sowie des elektrischen Antriebs 14 und/oder der Kupplung 16 von einem elektrischen Steuergerät 40 übernommen werden. As indicated in Figures 1 to 3, in the described embodiments, the control of the first valve 10, the second valve 30 and the electric Drive 14 and / or the clutch 16 are taken over by an electrical control unit 40.

Claims

Patentansprüche claims
Abgasturbolader für eine Brennkraftmaschine, der einen in einem Ansaugtrakt der Brennkraftmaschine eingebrachten Verdichter und eine in einem Abgasstrang der Brennkraftmaschine eingebrachte Turbine aufweist, wobei zum Antrieb des Verdichters über die Turbine der Verdichter und die Turbine über eine gemeinsame Welle drehfest miteinander verbunden sind, mit einem die Turbine umgehenden Bypass, in welchem ein Ventil vorgesehen ist, das eine Offenstellung oder eine Schließstellung einnehmen kann und in der Offenstellung eine Umgehung der Abgase um die Turbine herum im Bypass ermöglicht, welches dann weiter in eine der Turbine nachgeschaltete Abgasreinigungseinrichtung strömt, dadurch gekennzeichnet, dass der Verdichter (2) einen von der Turbine (3) unabhängigen Antrieb (14, 15) aufweist, welcher im Kaltstartbetrieb der Brennkraftmaschine (1) zur Aufrechterhaltung der Verdichtung im Ansaugtrakt (4) aktiviert ist, wobei das Ventil (10) in einer Offenstellung ein Umgehen der Abgase um die Turbine (3) herum in dem Bypass (12) zur Abgasreinigungseinrichtung (25) ermöglicht. Exhaust gas turbocharger for an internal combustion engine which has a compressor introduced in an intake tract of the internal combustion engine and a turbine introduced in an exhaust line of the internal combustion engine, wherein for driving the compressor via the turbine of the compressor and the turbine are rotatably connected to each other via a common shaft, with a the Turbine bypass, in which a valve is provided, which can take an open position or a closed position and in the open position allows bypassing the exhaust gases around the turbine in the bypass, which then flows further into a turbine downstream exhaust purification device, characterized in that the compressor (2) has a drive (14, 15) which is independent of the turbine (3) and is activated during cold start operation of the internal combustion engine (1) to maintain the compression in the intake tract (4), the valve (10) being in an open position bypassing the exhaust gases around allows the turbine (3) in the bypass (12) to the exhaust gas purification device (25).
2. Abgasturbolader nach Anspruch 1, dadurch gekennzeichnet, dass der Antrieb ein elektrischer Antrieb (14) ist.2. Exhaust gas turbocharger according to claim 1, characterized in that the drive is an electric drive (14).
3. Abgasturbolader nach Anspruch 1, dadurch gekennzeichnet, dass der Antrieb ein mechanischer Antrieb (15) ist.3. Exhaust gas turbocharger according to claim 1, characterized in that the drive is a mechanical drive (15).
4. Abgasturbolader nach Anspruch 3, dadurch gekennzeichnet, dass der mechanische Antrieb in Form einer von der Brennkraftmaschine (1) angetriebenen Kurbelwelle (15) gestaltet ist.4. Exhaust gas turbocharger according to claim 3, characterized in that the mechanical drive in the form of one of the internal combustion engine (1) driven crankshaft (15) is designed.
5. Abgasturbolader nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass der Antrieb (14; 15) über eine Kupplung (16) an den Verdichter (2) ankoppelbar ist.5. Exhaust gas turbocharger according to claim 2 or 3, characterized in that the drive (14; 15) via a coupling (16) to the compressor (2) can be coupled.
6. Abgasturbolader für eine Brennkraftmaschine, der einen in einem Ansaugtrakt der Brennkraftmaschine eingebrachten ersten Verdichter und eine in einem Abgasstrang der Brennkraftmaschine eingebrachte Turbine aufweist, wobei zum Antrieb des ersten Verdichters über die Turbine der erste Verdichter und die Turbine eine gemeinsame Welle drehfest miteinander verbunden sind, mit einem die Turbine umgehenden Bypass, in welchem ein erstes Ventil vorgesehen ist, das eine Offenstellung oder eine Schließstellung einnehmen kann und in der Offenstellung eine Umgehung der Abgase um die Turbine herum im Bypass ermöglicht, welches dann weiter in eine der Turbine nachgeschaltete Abgasreinigungseinrichtung strömt, dadurch gekennzeichnet, dass dem ersten Verdichter (2) ein zweiter Verdichter (20) nachgeschaltet ist, der über einen zweiten Bypass (22) umgehbar ist, in welchem ein zweites Ventil (30) untergebracht ist, wobei im Kaltstartbetrieb der Brennkraftmaschine (1) zur Aufrechterhaltung der Verdichtung im Ansaugtrakt (4) das zweite Ventil (30) eine Schließstellung einnimmt und der zweite Verdichter (20) über einen Antrieb (14; 15) betrieben ist.6. Exhaust gas turbocharger for an internal combustion engine having a first compressor introduced in an intake tract of the internal combustion engine and a turbine introduced in an exhaust line of the internal combustion engine, wherein for driving the first compressor via the turbine of the first compressor and the turbine, a common shaft are rotatably connected to each other with a turbine bypass bypass, in which a first valve is provided, which can assume an open position or a closed position and in the open position allows bypassing of the exhaust gases around the turbine in the bypass, which then flows further into a turbine downstream exhaust gas purification device , characterized in that the first compressor (2) has a second compressor (20) is connected, which is bypassed via a second bypass (22), in which a second valve (30) is housed, wherein in the cold start operation of the internal combustion engine (1) for maintaining the compression in the intake tract (4), the second valve (30 ) assumes a closed position and the second compressor (20) via a drive (14, 15) is operated.
7. Abgasturbolader nach Anspruch 6, dadurch gekennzeichnet, dass der Antrieb ein elektrischer Antrieb (14) ist.7. Exhaust gas turbocharger according to claim 6, characterized in that the drive is an electric drive (14).
8. Abgasturbolader nach Anspruch 8, dadurch gekennzeichnet, dass es der Antrieb ein mechanischer Antrieb (15) ist.8. Exhaust gas turbocharger according to claim 8, characterized in that it is the drive, a mechanical drive (15).
9. Abgasturbolader nach Anspruch 6, dadurch gekennzeichnet, dass der mechanische Antrieb in Form einer von der Brennkraftmaschine (1) angetriebenen Kurbelwelle (15) gestaltet ist.9. Exhaust gas turbocharger according to claim 6, characterized in that the mechanical drive in the form of one of the internal combustion engine (1) driven crankshaft (15) is designed.
10. Abgasturbolader nach Anspruch 7 oder 8, dadurch gekennzeichnet, dass der Antrieb (14; 15) über eine Kupplung (16) an den zweiten Verdichter (20) ankoppelbar ist. 10. Exhaust gas turbocharger according to claim 7 or 8, characterized in that the drive (14; 15) via a coupling (16) to the second compressor (20) can be coupled.
PCT/EP2005/012469 2004-11-27 2005-11-22 Exhaust-gas turbo charger for an internal combustion engine WO2006056393A1 (en)

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