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WO2011054407A1 - Internal combustion engine - Google Patents

Internal combustion engine Download PDF

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Publication number
WO2011054407A1
WO2011054407A1 PCT/EP2010/005439 EP2010005439W WO2011054407A1 WO 2011054407 A1 WO2011054407 A1 WO 2011054407A1 EP 2010005439 W EP2010005439 W EP 2010005439W WO 2011054407 A1 WO2011054407 A1 WO 2011054407A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
internal combustion
combustion engine
compressed
exhaust gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2010/005439
Other languages
German (de)
French (fr)
Inventor
Thomas Kuhn
Siegfried Weber
Eberhard Berger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mercedes Benz Group AG
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 WO2011054407A1 publication Critical patent/WO2011054407A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002—Controlling intake air
    • F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/001—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel
    • 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
    • F02B37/001—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel
    • F02B37/002—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel the exhaust supply to one of the exhaust drives can be interrupted
    • 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
    • F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
    • F02B37/225—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits air passages
    • 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 internal combustion engine according to claim 1.
  • Exhaust gas turbocharger designed as a smaller exhaust gas turbocharger that is, it has in relation to the second exhaust gas turbocharger a lower inertia and consequently a particularly faster startup or run-up behavior, which is why this smaller exhaust gas turbocharger is mainly used in low speed ranges of the internal combustion engine. From a certain speed of the second turbocharger is switched on, so that the exhaust gas flow rate to two
  • Exhaust gas turbocharger is divided according to their throughputs.
  • the two exhaust gas turbochargers are matched to their respective range of action, with predominantly the smaller exhaust gas turbocharger reduces the so-called turbo lag.
  • turbo lag it is not absolutely necessary to start up with the aid of the smaller exhaust-gas turbocharger; it can also be started up with the aid of the larger exhaust-gas turbocharger, so that the smaller turbocharger is switched on in a higher speed and / or load range.
  • the larger exhaust gas turbocharger is dependent on its design in low
  • Speed ranges are unable to reach a certain speed fast enough and thus build up an overpressure in the intake area.
  • An internal combustion engine comprises a first and at least one second, each having a compressor charging device, in particular exhaust gas turbocharger whose compressor output side are fluidly coupled to each other, wherein upstream of the compressor of the second charging device, a valve device is provided, by means of which the compressor of the second charging device feedable current a compressed by this compressor medium, in particular air, is adjustable and which can be actuated by a negative pressure generated by this compressor.
  • a compressor charging device in particular exhaust gas turbocharger whose compressor output side are fluidly coupled to each other, wherein upstream of the compressor of the second charging device, a valve device is provided, by means of which the compressor of the second charging device feedable current a compressed by this compressor medium, in particular air, is adjustable and which can be actuated by a negative pressure generated by this compressor.
  • the internal combustion engine according to the invention thus has a register charging with two charging devices connected in parallel, which can be used optimally in specific speed and power ranges of the internal combustion engine and compress the said medium to be supplied to the internal combustion engine.
  • This medium is, for example, air, which is announced by the environment of the internal combustion engine.
  • the medium to be supplied to the internal combustion engine is compressed by this or by its compressor. Since the compressors of the two charging devices are, for example, fluidically coupled to one another on the input side, the valve device prevents overflow from the compressor of the charging device in operation to the compressor of the second charging device that is not in operation, which enables efficient operation of the charging device in operation and therefore the whole
  • valve device prevents a false flow of the compressed medium via the compressor is not in Operated charging device to the environment, which would severely negatively affect an efficient operation of the charging device.
  • the entire medium to be supplied to the internal combustion engine is compressible by means of the first charging device, and there is no fault or
  • valve device of the internal combustion engine according to the invention can now be actuated by the negative pressure generated or generated by this compressor, additional control and / or actuating means for controlling
  • Actuation of the valve device is not required. This keeps both the cost and the weight of the internal combustion engine within limits, which is a small
  • Energy consumption for operation of the internal combustion engine benefits, in particular in connection with mobile applications, for example for
  • the compressors are fluidically coupled to one another on the output side, the undesired flow of the medium compressed by the first charging device or by the compressor of the first charging device through the compressor of the second charging device to the environment, whereby the compressed air does not the internal combustion engine could be supplied.
  • the internal combustion engine according to the invention may be a
  • the mentioned, input side, fluidic coupling or couplability of the compressor is for example designed such that the compressor relate to the medium to be compressed, for example air, from at least one common line and / or at least from a common collection volume, wherein the valve means in the one common Line fluidly seen between the compressors upstream of the
  • Compressor of the second charging device is arranged. This reduces the number of parts and thus the cost and weight of the internal combustion engine, resulting in the advantages already described in this context.
  • the second charging device is switched on or off, which, for example, by means of a second valve means on the side of a turbine, by means of which the compressor is driven, is shown.
  • the said first valve means is operable, for example, between a closed position interrupting the flow of the medium to be compressed and at least one open position releasing the flow of the medium to be compressed, wherein the first valve means is actuable into an open position releasing the flow of the medium to be compressed, when the Compressor of the second charging device compresses the medium to be compressed at least substantially to the same pressure as the compressor of the first charging device.
  • At least one spring element is provided which ensures a defined position, in particular the closed position, of the first valve device as a result of a force applied to the valve device by a spring force of the spring element.
  • This spring force is to be tuned with the opening time of the valve device, wherein the valve device in connection with the speed of the compressor of the second charging device may open neither too late nor too early to realize a smooth and efficient operation of the charging devices.
  • a second aspect of the invention relates to a method for operating a
  • Fig. 1 is a schematic representation of an embodiment of the
  • Valve device of the internal combustion engine according to the invention shown in FIG. 1 in two a current of a medium to be compressed interrupting closed positions and in a stream of the medium to be compressed releasing open position.
  • Fig. 1 shows an internal combustion engine 10 with six working spaces in the form of cylinders 12, 14, 16, 18, 20, 22, in which a fuel-air mixture is compressed by a respective piston and then ignited by external or auto-ignition.
  • Internal combustion engine 10 this has a first charging device in the form of a first exhaust gas turbocharger 24, which in turn has a compressor 26 and a turbine 28. Furthermore, a second charging device in the form of the second exhaust gas turbocharger 30 is provided, which likewise has a compressor 32 and a turbine 34.
  • the exhaust gas turbochargers 24 and 30 are connected in parallel to each other, whereby a Registeraufladung the internal combustion engine 10 is shown.
  • the compressors 26 and 32 are coupled on the output side fluidly with each other, that is, they promote the air to be compressed in a common volume.
  • the turbines 28 and 34 can be acted upon by exhaust gas of the internal combustion engine 10 via corresponding pipelines 36 on an exhaust gas side 38 of the internal combustion engine 10.
  • the energy of the exhaust gas is used to drive the respective turbine 28 and 34, which in turn the
  • Compressor 26 and 32 are driven.
  • the exhaust gas flows through further piping 40 to an exhaust gas purification system 42, for example, a
  • an exhaust gas recirculation device 46 is provided, by means of which exhaust gas of the internal combustion engine 10 from the exhaust gas side 38 to the intake side 48 of the internal combustion engine 10 is traceable.
  • an amount of recirculated exhaust gas is adjustable by means of an exhaust gas recirculation valve 50, so that one of the internal combustion engine 10 according to directional arrows 52 and 54 on the
  • Exhaust gas recirculation by means of the exhaust gas recirculation device 46 thereby allows a reduction of emissions, in particular nitrogen oxide emissions, the
  • the air sucked in according to the directional arrows 52 and 54 first flows through air filters 56 and 58 and then through
  • Air mass meter in the form of H preciselyfileinuftmassenmessern 60 and 62, before being fed to the compressors 26 and 32 and compressed.
  • the air heated as a result of this compression then flows first through an air cooling intercooler 64, whereupon they optionally with the
  • the exhaust gas turbocharger 24 is in operation, with the turbine 28, which has, for example, an adjusting device 66 for influencing flow parameters, for example, at the turbine inlet, with exhaust gas
  • the second exhaust gas turbocharger 30 is not in operation, which is realized in such a way that the actuation of the turbine 34 is prevented by a controllable or controllable valve device 68, which prevents the turbine 34 from being exposed to the exhaust gas of the internal combustion engine 10 by providing an inflow cross section blocked at the turbine inlet of the turbine 34.
  • Internal combustion engine 10 may be the case, wherein the first exhaust gas turbocharger 24 has an operating strategy adapted to the desired performance and this
  • Operating strategy requires a connection of the second exhaust gas turbocharger 32 only at higher speeds and / or loads.
  • valve device 70 Upstream of the compressor 32 of the exhaust gas turbocharger 30 is now a valve device 70 is provided, by means of which a compressor 32 feedable flow of the sucked and compressed air is adjustable and which can be actuated by a negative pressure generated by the compressor 32. If the compressor 32 is stationary, as in the present case, so it is not in operation, the determined by the compressor 26 pressure through the stationary compressor 32 passes through to the valve device 70 at.
  • the turbocharger 30 or its turbine 34 is switched to realize high mass flow rates of the exhaust gas of the internal combustion engine 10.
  • the valve device 68 thus releases the inflow cross section upstream of the turbine 34, whereupon the turbine 34 and thus the compressor 32 start and run up. Since the compressor 32 is not yet in operation, it still does not absorb any power and does not yet decelerate the turbine 34. If the valve means 70 were located downstream of the compressor 32, a massive pumping of the compressor 32 would occur during this start-up and run-up because the compressor 32 wants to build the pressure into a closed volume which in turn wants to relax, resulting in the known pumps would lead. This is prevented by the valve device 70 upstream of the compressor 32
  • Compressor 32 a negative pressure upstream of the compressor 32 is constructed.
  • the valve device 70 is also advantageously self-regulating and opens at exactly the right speed of the compressor 32, which is the case when the compressor 32 rotates at a speed, so that the pressure ratio with which he is a volume upstream of itself, ie between the Valve device 70 and the
  • Compressor 32 biases, is just as large that the valve means 70 is actuated by means of this negative pressure in their air flow releasing open position. This is the case when the pressure upstream of the compressor, ie between valve device 70 and compressor 32 has dropped to 1 bar and thus the valve device 70 is acted upon both from upstream of itself with 1 bar ambient pressure and downstream of itself with 1 bar. In this case, the compressor 32 compresses to the same pressure as the first compressor 26, the, as described, the pressure on the output side of
  • Compressor 32 pretends.
  • valve device 70 This exact opening of the valve device 70 thus enables on the one hand a
  • valve device 70 By this self-regulating design of the valve device 70 are cost and weight-intensive, additional control device for operating or regulating the valve device 70 is not required, which on the one hand keeps the cost and on the other hand, the weight of the internal combustion engine 10 low.
  • valve device 70 shows in a detailed schematic view of the valve device 70, wherein in the uppermost representation of the exhaust gas turbocharger 30 and thus the compressor 32 is stationary. This is for example at partial load and / or full load of
  • the overpressure generated by the compressor 26 is via piping 72 through the compressor 32 to the valve means 70th and presses together with a spring force of a spring element 76, a valve 74 of the valve device 70 on the seat to illustrate the closed position of the
  • Valve means 70 whereby the flow of air to be compressed is interrupted. Upstream of the valve device 70 and thus of the valve 74 is ambient pressure.
  • the middle diagram indicates a connection operation of the second exhaust gas turbocharger 30 and thus of the second compressor 32, in which case the exhaust gas turbocharger 30 and thus the compressor 32 starts and runs up.
  • the rotational speed of the compressor 32 increases in the volume upstream of the compressor 32 and downstream of the valve 74, between the valve device 70 and the compressor 32, the pressure in the negative pressure range, the valve 74 only by the spring force of the spring element 76 on its seat is pressed, which is the case until the negative pressure is high enough to absorb the valve 74 of the valve means 70, whereupon the valve means 70 releases the flow of air to be compressed, which is shown in the lowermost representation and by directional arrows 78th and 80 is indicated. The air now flows through the
  • Valve means 70 according to the directional arrows 78 and 80 and further according to a directional arrow 82, the compressor 32, which compresses the air and according to another directional arrow 84 in a compressor 32 and the compressor 26 common volume, whereupon the air, as already described, the Charge air cooler 64 flows through, optionally applied by means of the exhaust gas recirculation device 46 with exhaust gas and finally the internal combustion engine 10 is supplied. 2 clearly shows the self-regulating design of the valve device 70, which avoids additional, weight and cost-intensive control device.

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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)

Abstract

The invention relates to an internal combustion engine (10), comprising a first and at least one second supercharging device (24, 30), in particular an exhaust gas turbocharger (24, 30), each having a compressor (26, 32), the compressors (26, 32) of the supercharging devices being coupled to each other on the outlet side so as to permit fluid flow, wherein a valve device (70) is provided upstream of the compressor (32) of the second supercharging device (30). A flow of a medium to be compressed by the compressor (32) of the second supercharging device (30), which flow can be fed to said compressor (32), can be adjusted by means of the valve device, and the valve device can be activated by means of a vacuum produced by said compressor (32).

Description

Verbrennungskraftmaschine  Internal combustion engine

Die Erfindung betrifft eine Verbrennungskraftmaschine gemäß Patentanspruch 1. The invention relates to an internal combustion engine according to claim 1.

Aus dem Serienbau von Verbrennungskraftmaschinen ist die so genannte From the mass production of internal combustion engines is the so-called

Registeraufladung bekannt, bei welcher zwei parallel geschaltete, abwechselnd betreibbare Abgasturbolader vorgesehen sind. Dabei ist einer der beiden Register charging known in which two parallel, alternately operable exhaust gas turbocharger are provided. It is one of the two

Abgasturbolader als kleinerer Abgasturbolader ausgebildet, das heißt, dass er im Verhältnis zu dem zweiten Abgasturbolader eine geringere Massenträgheit und infolge dessen ein besonders schnelleres Anlauf- bzw. Hochlaufverhalten aufweist, weswegen dieser kleinere Abgasturbolader überwiegend in niedrigen Drehzahlbereichen der Verbrennungskraftmaschine eingesetzt wird. Ab einer bestimmten Drehzahl wird der zweite Turbolader zugeschaltet, so dass der Abgasvolumenstrom auf zwei Exhaust gas turbocharger designed as a smaller exhaust gas turbocharger, that is, it has in relation to the second exhaust gas turbocharger a lower inertia and consequently a particularly faster startup or run-up behavior, which is why this smaller exhaust gas turbocharger is mainly used in low speed ranges of the internal combustion engine. From a certain speed of the second turbocharger is switched on, so that the exhaust gas flow rate to two

Abgasturbolader ihren Durchsätzen gemäß aufgeteilt wird. Die beiden Abgasturbolader sind dabei auf ihren jeweiligen Wirkungsbereich abgestimmt, wobei überwiegend der kleinere Abgasturbolader das so genannte Turboloch reduziert. Allerdings ist es nicht zwingend notwendig, dass mit Hilfe des kleineren Abgasturboladers angefahren wird, es kann ebenso mit Hilfe des größeren Abgasturboladers angefahren werden, so dass in einem höheren Drehzahl- und/oder Lastbereich der kleinere Abgasturbolader zugeschaltet wird. Exhaust gas turbocharger is divided according to their throughputs. The two exhaust gas turbochargers are matched to their respective range of action, with predominantly the smaller exhaust gas turbocharger reduces the so-called turbo lag. However, it is not absolutely necessary to start up with the aid of the smaller exhaust-gas turbocharger; it can also be started up with the aid of the larger exhaust-gas turbocharger, so that the smaller turbocharger is switched on in a higher speed and / or load range.

Der größere Abgasturbolader ist abhängig von seiner Auslegung in niedrigen The larger exhaust gas turbocharger is dependent on its design in low

Drehzahlbereichen nicht in der Lage, eine bestimmte Drehzahl schnell genug zu erreichen und damit einen Überdruck im Ansaugbereich aufzubauen. Speed ranges are unable to reach a certain speed fast enough and thus build up an overpressure in the intake area.

Welcher der beiden Abgasturbolader zugeschaltet wird hängt grundsätzlich von der gewünschten Betriebsstrategie ab. Bei bekannten Konzepten sind aufwendige Ventileinrichtungen vonnöten, die die Kosten für die bekannten Konzepte unerwünschter Weise ansteigen lassen. Which of the two exhaust gas turbochargers is switched depends basically on the desired operating strategy. In known concepts, expensive valve devices are required, which increase the costs of the known concepts undesirably.

Es ist daher Aufgabe der vorliegenden Erfindung, eine Verbrennungskraftmaschine der eingangs genannten Art bereitzustellen, sodass eine Kostenreduzierung ermöglicht ist. It is therefore an object of the present invention to provide an internal combustion engine of the type mentioned, so that a cost reduction is made possible.

Diese Aufgabe wird von einer Verbrennungskraftmaschine mit den Merkmalen des Patentanspruchs 1 gelöst. Vorteilhafte Ausgestaltungen mit zweckmäßigen und nichttrivialen Weiterbildungen der Erfindung sind in den abhängigen Ansprüchen angegeben. This object is achieved by an internal combustion engine having the features of patent claim 1. Advantageous embodiments with expedient and non-trivial developments of the invention are specified in the dependent claims.

Eine erfindungsgemäße Verbrennungskraftmaschine umfasst eine erste und zumindest eine zweite, jeweils einen Verdichter aufweisende Aufladeeinrichtung, insbesondere Abgasturbolader, deren Verdichter ausgangsseitig fluidisch miteinander gekoppelt sind, wobei stromauf des Verdichters der zweiten Aufladeeinrichtung eine Ventileinrichtung vorgesehen ist, mittels welcher ein dem Verdichter der zweiten Aufladeeinrichtung zuführbarer Strom eines durch diesen Verdichter zu verdichteten Mediums, insbesondere Luft, einstellbar ist und welches von einem durch diesen Verdichter erzeugten Unterdruck betätigbar ist. An internal combustion engine according to the invention comprises a first and at least one second, each having a compressor charging device, in particular exhaust gas turbocharger whose compressor output side are fluidly coupled to each other, wherein upstream of the compressor of the second charging device, a valve device is provided, by means of which the compressor of the second charging device feedable current a compressed by this compressor medium, in particular air, is adjustable and which can be actuated by a negative pressure generated by this compressor.

Die erfindungsgemäße Verbrennungskraftmaschine weist somit eine Registeraufladung mit zwei parallel geschalteten Aufladeeinrichtungen auf, die in bestimmten Drehzahl- und Leistungsbereichen der Verbrennungskraftmaschine, jeweils optimal darauf abgestimmt, einsetzbar sind und das besagte, der Verbrennungskraftmaschine zuzuführende Medium verdichten. Bei diesem Medium handelt es sich, beispielsweise um Luft, die von der Umgebung der Verbrennungskraftmaschine angesagt wird. The internal combustion engine according to the invention thus has a register charging with two charging devices connected in parallel, which can be used optimally in specific speed and power ranges of the internal combustion engine and compress the said medium to be supplied to the internal combustion engine. This medium is, for example, air, which is announced by the environment of the internal combustion engine.

Ist nun eine Aufladeeinrichtung in Betrieb, so wird das der Verbrennungskraftmaschine zuzuführende Medium von dieser bzw. von deren Verdichter verdichtet. Da die Verdichter der beiden Aufladeeinrichtungen beispielsweise eingangsseitig fluidisch miteinander gekoppelt sind, verhindert die Ventileinrichtung ein Überströmen von dem Verdichter der sich im Betrieb befindlichen Aufladeeinrichtung zu dem Verdichter der sich nicht im Betrieb befindlichen, zweiten Aufladeeinrichtung, was einen effizienten Betrieb der sich im Betrieb befindlichen Aufladeeinrichtung und damit der gesamten If a charging device is now in operation, then the medium to be supplied to the internal combustion engine is compressed by this or by its compressor. Since the compressors of the two charging devices are, for example, fluidically coupled to one another on the input side, the valve device prevents overflow from the compressor of the charging device in operation to the compressor of the second charging device that is not in operation, which enables efficient operation of the charging device in operation and therefore the whole

Verbrennungskraftmaschine ermöglicht. Internal combustion engine allows.

Aufgrund der ausgangsseitigen Kopplung der Verdichter verhindert die Ventileinrichtung eine Fehlströmung des verdichteten Mediums über den Verdichter der sich nicht in Betrieb befindlichen Aufladeeinrichtung an die Umgebung, was einen effizienten Betrieb der Aufladeeinrichtung stark negativ beeinflussen würde. Due to the output side coupling of the compressor, the valve device prevents a false flow of the compressed medium via the compressor is not in Operated charging device to the environment, which would severely negatively affect an efficient operation of the charging device.

Dadurch ist das gesamte der Verbrennungskraftmaschine zuzuführende Medium mittels der ersten Aufladeeinrichtung verdichtbar, und es kommt zu keinem Fehl- bzw. As a result, the entire medium to be supplied to the internal combustion engine is compressible by means of the first charging device, and there is no fault or

Leckagestrom des zu verdichteten sowie des verdichteten Medium über die sich nicht in Betrieb befindliche Aufladeeinrichtung bzw. deren Verdichter. Leakage flow of the compressed and the compressed medium on the non-operating charging device or its compressor.

Dadurch, dass die Ventileinrichtung der erfindungsgemäßen Verbrennungskraftmaschine nun von dem durch diesen Verdichter erzeugten bzw. erzeugbaren Unterdruck betätigbar ist, sind zusätzliche Regel- und/oder Betätigungseinrichtungen zur Regelung bzw. The fact that the valve device of the internal combustion engine according to the invention can now be actuated by the negative pressure generated or generated by this compressor, additional control and / or actuating means for controlling

Betätigung der Ventileinrichtung nicht vonnöten. Dies hält sowohl die Kosten als auch das Gewicht der Verbrennungskraftmaschine in Grenzen, was einem geringen Actuation of the valve device is not required. This keeps both the cost and the weight of the internal combustion engine within limits, which is a small

Energieverbrauch zum Betrieb der Verbrennungskraftmaschine zugute kommt, insbesondere in Zusammenhang mit mobilen Anwendungen, beispielsweise zum Energy consumption for operation of the internal combustion engine benefits, in particular in connection with mobile applications, for example for

Antreiben eines Kraftwagens. Dies bedeutet somit eine Kostenreduzierung für die Verbrennungskraftmaschine als auch einen geringen Kraftstoffverbrauch und damit geringe C02-Emissionen. Driving a motor car. This therefore means a cost reduction for the internal combustion engine as well as a low fuel consumption and thus low C0 2 emissions.

An dieser Stelle sei angemerkt, dass die Verdichter eingangsseitig nicht It should be noted at this point that the compressor is not on the input side

notwendigerweise gekoppelt sein müssen. In diesem Falle erlaubt die Ventileinrichtung dadurch, dass die Verdichter ausgangsseitig fluidisch miteinander gekoppelt sind, eine unerwünschtes Fehlströmung des von der ersten Aufladeeinrichtung bzw. von dem Verdichter der ersten Aufladeeinrichtung verdichteten Mediums über den Verdichter der zweiten Aufladeeinrichtung an die Umgebung, wodurch die verdichtete Luft nicht der Verbrennungskraftmaschine zugeführt werden könnte. necessarily be coupled. In this case, by virtue of the fact that the compressors are fluidically coupled to one another on the output side, the undesired flow of the medium compressed by the first charging device or by the compressor of the first charging device through the compressor of the second charging device to the environment, whereby the compressed air does not the internal combustion engine could be supplied.

Die Vermeidung dieses Fehlstromes erlaubt ebenso einen besonders effizienten Betrieb der Aufladeeinrichtung damit der gesamten Verbrennungskraftmaschine, womit ebenso die Vorteile eines niedrigen Kraftstoffverbrauchs sowie geringer C02-Emissionen einhergehen. The avoidance of this fault current also allows a particularly efficient operation of the supercharger so that the entire internal combustion engine, which also goes along with the benefits of low fuel consumption and low C0 2 emissions.

Bei der erfindungsgemäßen Verbrennungskraftmaschine kann es sich um einen In the internal combustion engine according to the invention may be a

Dieselmotor oder um einen Ottomotor oder um jedwede anderweitige Art von Diesel engine or a gasoline engine or any other kind of

Verbrennungskraftmaschine handeln, die mittels der beschriebenen Aufladeeinrichtungen aufgeladen ist. Die erwähnte, eingangsseitige, fluidische Kopplung bzw. Koppelbarkeit der Verdichter ist beispielsweise derart ausgebildet, dass die Verdichter das zu verdichtende Medium, beispielsweise Luft, aus zumindest einer gemeinsamen Leitung und/oder zumindest aus einem gemeinsamen Sammelvolumen beziehen, wobei die Ventileinrichtung in der einen gemeinsamen Leitung fluidisch gesehen zwischen den Verdichtern stromauf des Internal combustion engine, which is charged by means of the described charging devices. The mentioned, input side, fluidic coupling or couplability of the compressor is for example designed such that the compressor relate to the medium to be compressed, for example air, from at least one common line and / or at least from a common collection volume, wherein the valve means in the one common Line fluidly seen between the compressors upstream of the

Verdichters der zweiten Aufladeinrichtung angeordnet ist. Dies reduziert die Teileanzahl und damit die Kosten sowie das Gewicht der Verbrennungskraftmaschine, woraus die in diesem Zusammenhang bereits beschriebenen Vorteile resultieren. Compressor of the second charging device is arranged. This reduces the number of parts and thus the cost and weight of the internal combustion engine, resulting in the advantages already described in this context.

In einer vorteilhaften Ausführungsform der Erfindung ist die zweite Aufladeeinrichtung zu- bzw. abschaltbar, was beispielsweise mittels einer zweiten Ventileinrichtung auf Seiten einer Turbine, mittels welcher der Verdichter antreibbar ist, dargestellt ist. In an advantageous embodiment of the invention, the second charging device is switched on or off, which, for example, by means of a second valve means on the side of a turbine, by means of which the compressor is driven, is shown.

Die besagte, erste Ventileinrichtung ist dabei beispielsweise zwischen einer den Strom des zu verdichteten Mediums unterbrechenden Schließstellung und zumindest einer den Strom des zu verdichteten Mediums freigebenden Offenstellung betätigbar, wobei die erste Ventileinrichtung in eine den Strom des zu verdichteten Mediums freigebende Offenstellung betätigbar ist, wenn der Verdichter der zweiten Aufladeeinrichtung das zu verdichtende Medium zumindest im Wesentlichen auf den gleichen Druck verdichtet wie der Verdichter der ersten Aufladeeinrichtung. The said first valve means is operable, for example, between a closed position interrupting the flow of the medium to be compressed and at least one open position releasing the flow of the medium to be compressed, wherein the first valve means is actuable into an open position releasing the flow of the medium to be compressed, when the Compressor of the second charging device compresses the medium to be compressed at least substantially to the same pressure as the compressor of the first charging device.

Vorteilhafterweise ist zumindest ein Federelement vorgesehen, welches eine definierte Lage, insbesondere die Schließstellung, der ersten Ventileinrichtung infolge einer Kraftbeaufschlagung der Ventileinrichtung durch eine Federkraft des Federelements gewährleistet. Diese Federkraft ist dabei mit dem Öffnungszeitpunkt der Ventileinrichtung abzustimmen, wobei die Ventileinrichtung in Zusammenhang mit der Drehzahl des Verdichters der zweiten Aufladeeinrichtung weder zu spät noch zu früh öffnen darf um einen reibungslosen und effizienten Betrieb der Aufladeeinrichtungen zu realisieren. Advantageously, at least one spring element is provided which ensures a defined position, in particular the closed position, of the first valve device as a result of a force applied to the valve device by a spring force of the spring element. This spring force is to be tuned with the opening time of the valve device, wherein the valve device in connection with the speed of the compressor of the second charging device may open neither too late nor too early to realize a smooth and efficient operation of the charging devices.

Ein zweiter Aspekt der Erfindung betrifft ein Verfahren zum Betreiben einer A second aspect of the invention relates to a method for operating a

Verbrennungskraftmaschine mit einer ersten und zumindest einer zweiten, jeweils einen Verdichter aufweisenden Aufladeeinrichtung, insbesondere Abgasturbolader, deren Verdichter ausgangsseitig fluidisch miteinander gekoppelt sind, wobei stromauf des Verdichters der zweiten Aufladeeinrichtung eine Ventileinrichtung vorgesehen ist, mittels welcher ein dem Verdichter der zweiten Aufladeeinrichtung zuführbarer Strom eines durch diesen Verdichter zu verdichtenden Mediums eingestellt wird und welches von einem durch diesen Verdichter erzeugten Unterdruck betätigt wird. Vorteilhafte Ausgestaltungen des zweiten Aspekt der Erfindung sind als vorteilhafte Ausgestaltungen der erfindungsgemäßen Verbrennungskraftmaschine und umgekehrt anzusehen. Somit ermöglicht auch das Verfahren eine kostengünstige Darstellung sowie einen Internal combustion engine with a first and at least one second, each having a compressor charging device, in particular exhaust gas turbocharger whose compressor output side are fluidly coupled to each other, wherein upstream of the compressor of the second charging device, a valve means is provided, by means of which the compressor of the second charging device feedable current through This compressor is set to be compressed medium and which is actuated by a negative pressure generated by this compressor. advantageous Embodiments of the second aspect of the invention are to be regarded as advantageous embodiments of the internal combustion engine according to the invention and vice versa. Thus, the method also allows a cost-effective representation and a

kostengünstigen und gleichzeitig effizienten Betrieb der Verbrennungskraftmaschine ohne aufwendige Betätigungs- bzw. Regeleinrichtungen zur Betätigung der Ventileinrichtung. inexpensive and at the same time efficient operation of the internal combustion engine without complex operating or regulating devices for actuating the valve device.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines bevorzugten Ausführungsbeispiels sowie anhand der Zeichnungen. Die vorstehend in der Beschreibung genannten Merkmale und Further advantages, features and details of the invention will become apparent from the following description of a preferred embodiment and from the drawings. The features mentioned above in the description and

Merkmalskombinationen sowie die nachfolgend in der Figurenbeschreibung genannten und/oder in den Figuren alleine gezeigten Merkmale und Merkmalskombinationen sind nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Feature combinations as well as the features and feature combinations mentioned below in the description of the figures and / or shown alone in the figures are not only in the respectively indicated combination but also in others

Kombinationen oder in Alleinstellung verwendbar, ohne den Rahmen der Erfindung zu verlassen. Combinations or alone, without departing from the scope of the invention.

Die Zeichnungen zeigen in: The drawings show in:

Fig. 1 eine schematische Darstellung einer Ausführungsform der Fig. 1 is a schematic representation of an embodiment of the

erfindungsgemäßen Verbrennungskraftmaschine; und  internal combustion engine according to the invention; and

Fig. 2 jeweils eine schematische Darstellung einer Ausführungsform einer 2 each a schematic representation of an embodiment of a

Ventileinrichtung der erfindungsgemäßen Verbrennungskraftmaschine gemäß Fig. 1 in zwei einen Strom eines zu verdichtenden Mediums unterbrechenden Schließstellungen sowie in einer den Strom des zu verdichtenden Mediums freigebenden Offenstellung.  Valve device of the internal combustion engine according to the invention shown in FIG. 1 in two a current of a medium to be compressed interrupting closed positions and in a stream of the medium to be compressed releasing open position.

Die Fig. 1 zeigt eine Verbrennungskraftmaschine 10 mit sechs Arbeitsräumen in Form von Zylindern 12, 14, 16, 18, 20, 22, in welchen ein Kraftstoff-Luft-Gemisch von jeweils einem Kolben verdichtet und anschließend durch Fremd- oder Selbstzündung entzündet wird. Fig. 1 shows an internal combustion engine 10 with six working spaces in the form of cylinders 12, 14, 16, 18, 20, 22, in which a fuel-air mixture is compressed by a respective piston and then ignited by external or auto-ignition.

Zur Darstellung hoher spezifischer Leistungen und Drehmomente der For the representation of high specific performances and torques of the

Verbrennungskraftmaschine 10 weist diese eine erste Aufladeeinrichtung in Form eines ersten Abgasturboladers 24 auf, der wiederum einen Verdichter 26 sowie eine Turbine 28 aufweist. Des Weiteren ist eine zweite Aufladeeinrichtung in Form des zweiten Abgasturboladers 30 vorgesehen, der ebenso einen Verdichter 32 sowie eine Turbine 34 aufweist. Die Abgasturbolader 24 und 30 sind dabei parallel zueinander geschaltet, wodurch eine Registeraufladung der Verbrennungskraftmaschine 10 dargestellt ist. Die Verdichter 26 und 32 sind dabei ausgangsseitig fluidisch miteinander gekoppelt, das heißt sie fördern die zu verdichtende Luft in ein gemeinsames Volumen. Internal combustion engine 10, this has a first charging device in the form of a first exhaust gas turbocharger 24, which in turn has a compressor 26 and a turbine 28. Furthermore, a second charging device in the form of the second exhaust gas turbocharger 30 is provided, which likewise has a compressor 32 and a turbine 34. The exhaust gas turbochargers 24 and 30 are connected in parallel to each other, whereby a Registeraufladung the internal combustion engine 10 is shown. The compressors 26 and 32 are coupled on the output side fluidly with each other, that is, they promote the air to be compressed in a common volume.

Wie der Fig. 1 zu entnehmen ist, sind die Turbinen 28 und 34 über entsprechende Verrohrungen 36 auf einer Abgasseite 38 der Verbrennungskraftmaschine 10 mit Abgas der Verbrennungskraftmaschine 10 beaufschlagbar. Dabei wird die Energie des Abgases genutzt, um die jeweilige Turbine 28 und 34 anzutreiben, worüber wiederum die As can be seen from FIG. 1, the turbines 28 and 34 can be acted upon by exhaust gas of the internal combustion engine 10 via corresponding pipelines 36 on an exhaust gas side 38 of the internal combustion engine 10. In this case, the energy of the exhaust gas is used to drive the respective turbine 28 and 34, which in turn the

Verdichter 26 bzw. 32 angetrieben werden. Compressor 26 and 32 are driven.

Nach erfolgter Beaufschlagung der Turbinen 28 und 34 strömt das Abgas durch weitere Verrohrungen 40 zu einer Abgasreinigungsanlage 42, die beispielsweise einen After the loading of the turbines 28 and 34, the exhaust gas flows through further piping 40 to an exhaust gas purification system 42, for example, a

Oxidationskatalysator sowie einen Partikelfilter umfasst, woraufhin das Abgas gemäß einem Richtungspfeil 44 an die Umwelt strömt. Includes oxidation catalyst and a particulate filter, whereupon the exhaust flows according to a directional arrow 44 to the environment.

Außerdem ist eine Abgasrückführeinrichtung 46 vorgesehen, mittels welcher Abgas der Verbrennungskraftmaschine 10 von der Abgasseite 38 auf die Ansaugseite 48 der Verbrennungskraftmaschine 10 rückführbar ist. Eine Menge des rückzuführenden Abgases ist aber mittels eines Abgasrückführventils 50 einstellbar, wobei also eine von der Verbrennungskraftmaschine 10 gemäß Richtungspfeilen 52 und 54 auf der In addition, an exhaust gas recirculation device 46 is provided, by means of which exhaust gas of the internal combustion engine 10 from the exhaust gas side 38 to the intake side 48 of the internal combustion engine 10 is traceable. However, an amount of recirculated exhaust gas is adjustable by means of an exhaust gas recirculation valve 50, so that one of the internal combustion engine 10 according to directional arrows 52 and 54 on the

Ansaugseite 48 angesaugte Luft mit diesem Abgas beaufschlag bar ist. Diese Intake side 48 sucked air with this exhaust gas is bar. These

Abgasrückführung mittels der Abgasrückführungseinrichtung 46 erlaubt dabei eine Reduzierung von Emissionen, insbesondere Stickoxidemissionen, der Exhaust gas recirculation by means of the exhaust gas recirculation device 46 thereby allows a reduction of emissions, in particular nitrogen oxide emissions, the

Verbrennungskraftmaschine 10. Internal combustion engine 10.

Wie der Fig. 1 zu entnehmen ist, strömt die gemäß den Richtungspfeilen 52 und 54 angesaugte Luft zunächst durch Luftfilter 56 und 58 und anschließend durch As can be seen from FIG. 1, the air sucked in according to the directional arrows 52 and 54 first flows through air filters 56 and 58 and then through

Luftmassenmesser in Form von Heißfilmluftmassenmessern 60 und 62, bevor sie den Verdichtern 26 und 32 zugeführt und verdichtet wird. Air mass meter in the form of Heißfileinuftmassenmessern 60 and 62, before being fed to the compressors 26 and 32 and compressed.

Die infolge dieser Verdichtung erwärmte Luft strömt anschließend zunächst durch einen die Luft kühlenden Ladeluftkühler 64, woraufhin sie gegebenenfalls mit dem The air heated as a result of this compression then flows first through an air cooling intercooler 64, whereupon they optionally with the

rückgeführten Abgas aufschlagt und der Verbrennungskraftmaschine zugeführt wird. Die Regelung der durch die Abgasturbolader 24 und 32 dargestellten Registeraufladung erfolgt dabei folgender Maßen: der Abgasturbolader 24 befindet sich in Betrieb, wobei dessen Turbine 28, die beispielsweise eine VerStelleinrichtung 66 zur Beeinflussung von Strömungsparametern beispielsweise am Turbineneintritt aufweist, mit Abgas recirculated exhaust gas aufschlagt and the internal combustion engine is supplied. The regulation of the charging by the turbochargers 24 and 32 shown register charging takes place as follows: the exhaust gas turbocharger 24 is in operation, with the turbine 28, which has, for example, an adjusting device 66 for influencing flow parameters, for example, at the turbine inlet, with exhaust gas

beaufschlagt wird und somit den Verdichter 26 antreibt. Der zweite Abgasturbolader 30 befindet sich dabei nicht in Betrieb, was derart realisiert ist, dass die Beaufschlagung der Turbine 34 durch eine steuerbare bzw. regelbare Ventileinrichtung 68 verhindert ist, die eine Beaufschlagung der Turbine 34 vom Abgas der Verbrennungskraftmaschine 10 verhindert, indem sie einen Einströmquerschnitt am Turbineneintritt der Turbine 34 versperrt. is acted upon and thus drives the compressor 26. The second exhaust gas turbocharger 30 is not in operation, which is realized in such a way that the actuation of the turbine 34 is prevented by a controllable or controllable valve device 68, which prevents the turbine 34 from being exposed to the exhaust gas of the internal combustion engine 10 by providing an inflow cross section blocked at the turbine inlet of the turbine 34.

Dies kann beispielsweise bei niedrigen Drehzahlen und Lasten der This can, for example, at low speeds and loads of

Verbrennungskraftmaschine 10 der Fall sein, wobei der erste Abgasturbolader 24 ein der Betriebsstrategie angepasst gewünschtes Betriebsverhalten aufweist und diese Internal combustion engine 10 may be the case, wherein the first exhaust gas turbocharger 24 has an operating strategy adapted to the desired performance and this

Betriebsstrategie ein Zuschalten des zweiten Abgasturbolader 32 erst bei höheren Drehzahlen und/oder Lasten erfordert. Operating strategy requires a connection of the second exhaust gas turbocharger 32 only at higher speeds and / or loads.

Bei sich im Betrieb befindlichem Verdichter 26 und sich nicht im Betrieb befindlichem Verdichter 32 auf Grund der Vermeidung der Umströmung der Turbine 34 durch die entsprechende Sperrstellung der Ventileinrichtung 68 bestimmt der Verdichter 26 den Druck, der ausgangsseitig am Verdichter 32 anliegt. Stromauf des Verdichters 32 des Abgasturboladers 30 ist nun eine Ventileinrichtung 70 vorgesehen, mittels welcher ein dem Verdichter 32 zuführbarer Strom der angesaugten und zu verdichtenden Luft einstellbar ist und welches von einem durch den Verdichter 32 erzeugten Unterdruck betätigbar ist. Steht der Verdichter 32 wie im vorliegenden Fall still, also befindet er sich nicht im Betrieb, so liegt der durch den Verdichter 26 bestimmte Druck durch den stehenden Verdichter 32 hindurch bis an die Ventileinrichtung 70 an. When in operation befindlichem compressor 26 and not in operation befindlichem compressor 32 due to the avoidance of the flow around the turbine 34 by the corresponding blocking position of the valve means 68, the compressor 26 determines the pressure on the output side of the compressor 32 abuts. Upstream of the compressor 32 of the exhaust gas turbocharger 30 is now a valve device 70 is provided, by means of which a compressor 32 feedable flow of the sucked and compressed air is adjustable and which can be actuated by a negative pressure generated by the compressor 32. If the compressor 32 is stationary, as in the present case, so it is not in operation, the determined by the compressor 26 pressure through the stationary compressor 32 passes through to the valve device 70 at.

Bei Bedarf, das heißt beispielsweise bei steigenden Drehzahlen und Leistungen der Verbrennungskraftmaschine 10, wird der Turbolader 30 bzw. dessen Turbine 34 zur Realisierung hoher Massendurchsätze des Abgases der Verbrennungskraftmaschine 10 zugeschaltet. Das bedeutet, dass also die Ventileinrichtung 68 den Einströmquerschnitt stromauf der Turbine 34 frei gibt, woraufhin also die Turbine 34 und damit der Verdichter 32 an- und hochläuft. Da der Verdichter 32 noch nicht in Betrieb ist, nimmt er noch keine Leistung auf und bremst die Turbine 34 noch nicht ab. Wäre die Ventileinrichtung 70 stromab des Verdichters 32 angeordnet, würde während dieses An- und Hochlaufs ein massives Pumpen des Verdichters 32 auftreten, da der Verdichter 32 den Druck in ein geschlossenes Volumen hinein aufbauen will, welches sich wiederum entspannen will, was zu den bekannten Pumpen führen würde. Dies ist dadurch verhindert, dass die Ventileinrichtung 70 stromauf des Verdichters 32 If necessary, that is, for example, at increasing speeds and powers of the internal combustion engine 10, the turbocharger 30 or its turbine 34 is switched to realize high mass flow rates of the exhaust gas of the internal combustion engine 10. This means that the valve device 68 thus releases the inflow cross section upstream of the turbine 34, whereupon the turbine 34 and thus the compressor 32 start and run up. Since the compressor 32 is not yet in operation, it still does not absorb any power and does not yet decelerate the turbine 34. If the valve means 70 were located downstream of the compressor 32, a massive pumping of the compressor 32 would occur during this start-up and run-up because the compressor 32 wants to build the pressure into a closed volume which in turn wants to relax, resulting in the known pumps would lead. This is prevented by the valve device 70 upstream of the compressor 32

angeordnet ist, was das Pumpen vermeidet, da bei einem An- bzw. Hochlauf des is arranged, which avoids pumping, as at a startup or run-up of the

Verdichters 32 ein Unterdruck stromauf des Verdichters 32 aufgebaut wird. Compressor 32, a negative pressure upstream of the compressor 32 is constructed.

Die Ventileinrichtung 70 ist des Weiteren vorteilhafterweise selbstregelnd und öffnet bei genau der richtigen Drehzahl des Verdichters 32, was dann der Fall ist, wenn der Verdichter 32 mit einer Drehzahl dreht, sodass das Druckverhältnis, mit dem er ein Volumen stromauf seiner selbst, also zwischen der Ventileinrichtung 70 und dem The valve device 70 is also advantageously self-regulating and opens at exactly the right speed of the compressor 32, which is the case when the compressor 32 rotates at a speed, so that the pressure ratio with which he is a volume upstream of itself, ie between the Valve device 70 and the

Verdichter 32 vorspannt, genauso groß ist, dass die Ventileinrichtung 70 mittels dieses Unterdrucks in ihre den Luftstrom freigebende Offenstellung betätigt wird. Dies ist dann der Fall, wenn der Druck stromauf des Verdichters, also zwischen Ventileinrichtung 70 und Verdichter 32 auf 1 bar abgesunken ist und somit die Ventileinrichtung 70 sowohl von stromauf ihrer selbst mit 1 bar Umgebungsdruck als auch stromab ihrer selbst mit 1 bar beaufschlagt wird. In diesem Falle verdichtet der Verdichter 32 auf den gleichen Druck wie der erste Verdichter 26, der, wie beschrieben, den Druck ausgangsseitig des Compressor 32 biases, is just as large that the valve means 70 is actuated by means of this negative pressure in their air flow releasing open position. This is the case when the pressure upstream of the compressor, ie between valve device 70 and compressor 32 has dropped to 1 bar and thus the valve device 70 is acted upon both from upstream of itself with 1 bar ambient pressure and downstream of itself with 1 bar. In this case, the compressor 32 compresses to the same pressure as the first compressor 26, the, as described, the pressure on the output side of

Verdichters 32 vorgibt. Compressor 32 pretends.

Dieses exakte Öffnen der Ventileinrichtung 70 ermöglicht somit einerseits eine This exact opening of the valve device 70 thus enables on the one hand a

Darstellung eines Druckverhältnisses, um eine Luftförderung zur Representation of a pressure ratio to an air transport to

Verbrennungskraftmaschine 10 zu ermöglichen sowie die Vermeidung einer Internal combustion engine 10 to allow and avoid a

Überdrehzahl des Abgasturboladers 30 was zu einer Zerstörung desselbigen führen würde. Overspeed of the exhaust gas turbocharger 30 which would lead to a destruction desselbigen.

Durch diese selbst regelende Ausbildung der Ventileinrichtung 70 sind kosten- und gewichtsintensive, zusätzliche Regelungseinrichtung zur Betätigung bzw. Regelung der Ventileinrichtung 70 nicht vonnöten, was einerseits die Kosten und andererseits das Gewicht der Verbrennungskraftmaschine 10 gering hält. By this self-regulating design of the valve device 70 are cost and weight-intensive, additional control device for operating or regulating the valve device 70 is not required, which on the one hand keeps the cost and on the other hand, the weight of the internal combustion engine 10 low.

Die Fig. 2 zeigt in einer detaillierten schematischen Ansicht die Ventileinrichtung 70, wobei in der obersten Darstellung der Abgasturbolader 30 und damit dessen Verdichter 32 still steht. Dies ist beispielsweise bei Teillast- und/oder Volllast der 2 shows in a detailed schematic view of the valve device 70, wherein in the uppermost representation of the exhaust gas turbocharger 30 and thus the compressor 32 is stationary. This is for example at partial load and / or full load of

Verbrennungskraftmaschine 10 der Fall. Der von dem Verdichter 26 erzeugte Überdruck liegt über Verrohrungen 72 durch den Verdichter 32 hindurch an der Ventileinrichtung 70 an und drückt zusammen mit einer Federkraft eines Federelements 76 ein Ventil 74 der Ventileinrichtung 70 auf dessen Sitz zur Darstellung der Schließstellung der Internal combustion engine 10 the case. The overpressure generated by the compressor 26 is via piping 72 through the compressor 32 to the valve means 70th and presses together with a spring force of a spring element 76, a valve 74 of the valve device 70 on the seat to illustrate the closed position of the

Ventileinrichtung 70, wodurch der Strom der zu verdichtenden Luft unterbrochen ist. Stromauf der Ventileinrichtung 70 und damit des Ventils 74 liegt Umgebungsdruck an. Valve means 70, whereby the flow of air to be compressed is interrupted. Upstream of the valve device 70 and thus of the valve 74 is ambient pressure.

Die mittlere Darstellung deutet einen Zuschaltvorgang des zweiten Abgasturboladers 30 und damit des zweiten Verdichters 32 an, wobei also der Abgasturbolader 30 und damit der Verdichter 32 an- und hochläuft. Mit steigender Drehzahl des Verdichters 32 sinkt in dem Volumen stromauf des Verdichters 32 und stromab des Ventils 74, zwischen der Ventileinrichtung 70 und dem Verdichter 32, der Druck bis in den Unterdruckbereich ab, wobei das Ventil 74 lediglich noch durch die Federkraft des Federelements 76 auf dessen Sitz gedrückt wird, was so lange der Fall ist, bis der Unterdruck groß genug ist, um das Ventil 74 der Ventileinrichtung 70 aufzusaugen, woraufhin die Ventileinrichtung 70 den Strom der zu verdichtenden Luft freigibt, was in der untersten Darstellung dargestellt und durch Richtungspfeile 78 und 80 angedeutet ist. Die Luft durchströmt nun die The middle diagram indicates a connection operation of the second exhaust gas turbocharger 30 and thus of the second compressor 32, in which case the exhaust gas turbocharger 30 and thus the compressor 32 starts and runs up. As the rotational speed of the compressor 32 increases in the volume upstream of the compressor 32 and downstream of the valve 74, between the valve device 70 and the compressor 32, the pressure in the negative pressure range, the valve 74 only by the spring force of the spring element 76 on its seat is pressed, which is the case until the negative pressure is high enough to absorb the valve 74 of the valve means 70, whereupon the valve means 70 releases the flow of air to be compressed, which is shown in the lowermost representation and by directional arrows 78th and 80 is indicated. The air now flows through the

Ventileinrichtung 70 gemäß den Richtungspfeilen 78 und 80 und weiter gemäß einem Richtungspfeil 82 den Verdichter 32, der die Luft verdichtet und gemäß einem weiteren Richtungspfeil 84 in ein dem Verdichter 32 sowie dem Verdichter 26 gemeinsames Volumen fördert, woraufhin die Luft, wie bereits beschrieben, den Ladeluftkühler 64 durchströmt, gegebenenfalls mittels der Abgasrückführeinrichtung 46 mit Abgas beaufschlagt und schließlich der Verbrennungskraftmaschine 10 zugeführt wird. Der Fig. 2 deutlich zu entnehmen ist die selbstregelnde Ausbildung der Ventileinrichtung 70, welche zusätzliche, gewichts- und kostenintensive Regelungseinrichtung vermeidet. Valve means 70 according to the directional arrows 78 and 80 and further according to a directional arrow 82, the compressor 32, which compresses the air and according to another directional arrow 84 in a compressor 32 and the compressor 26 common volume, whereupon the air, as already described, the Charge air cooler 64 flows through, optionally applied by means of the exhaust gas recirculation device 46 with exhaust gas and finally the internal combustion engine 10 is supplied. 2 clearly shows the self-regulating design of the valve device 70, which avoids additional, weight and cost-intensive control device.

Claims

Patentansprüche claims 1. Verbrennungskraftmaschine (10) mit einer ersten und mit zumindest einer zweiten, jeweils einen Verdichter (26, 32) aufweisenden Aufladeeinrichtung (24, 30), insbesondere Abgasturbolader (24, 30), deren Verdichter (26, 32) ausgangsseitig fluidisch miteinander gekoppelt sind, wobei stromauf des Verdichters (32) der zweiten Aufladeeinrichtung (30) eine Ventileinrichtung (70) vorgesehen ist, mittels welcher ein dem Verdichter (32) der zweiten Aufladeeinrichtung (30) zuführbarer Strom eines durch diesen Verdichter (32) zu verdichtenden Mediums einstellbar ist und welches von einem durch diesen Verdichter (32) erzeugten Unterdruck betätigbar ist. 1. internal combustion engine (10) having a first and at least one second, each having a compressor (26, 32) having charging means (24, 30), in particular exhaust gas turbocharger (24, 30), the compressor (26, 32) coupled on the output side fluidly with each other in which upstream of the compressor (32) of the second charging device (30) a valve device (70) is provided by means of which a compressor (32) of the second charging device (30) feedable stream of a through this compressor (32) to be compressed medium adjustable is and which of a by this compressor (32) generated negative pressure is actuated. 2. Verbrennungskraftmaschine (10) nach Anspruch 1 , 2. internal combustion engine (10) according to claim 1, dadurch gekennzeichnet, dass  characterized in that die erste und die zweiten Aufladeeinrichtung (24, 30) parallel zueinander geschaltet sind.  the first and second charging means (24, 30) are connected in parallel with each other. 3. Verbrennungskraftmaschine (10) nach einem der Ansprüche 1 oder 2, 3. internal combustion engine (10) according to any one of claims 1 or 2, dadurch gekennzeichnet, dass  characterized in that das durch den jeweiligen Verdichter (26, 32) zu verdichtende Medium in ein den Verdichtern (26, 32) gemeinsames Sammelvolumen führbar ist.  the medium to be compressed by the respective compressor (26, 32) can be guided into a collecting volume common to the compressors (26, 32). 4. Verbrennungskraftmaschine (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass 4. internal combustion engine (10) according to one of the preceding claims, characterized in that die Verdichter (26, 32) eingangsseitig fluidisch miteinander gekoppelt sind. the compressors (26, 32) are fluidically coupled together on the input side. 5. Verbrennungskraftmaschine (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass 5. internal combustion engine (10) according to one of the preceding claims, characterized in that die zweite Aufladeeinrichtung (30) zu- und abschaltbar ist.  the second charging device (30) is switched on and off. 6. Verbrennungskraftmaschine (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass 6. internal combustion engine (10) according to one of the preceding claims, characterized in that die Ventileinrichtung (70) zwischen einer den Strom des zu verdichtenden Mediums unterbrechenden Schließstellung und zumindest einer den Strom des zu verdichtenden Mediums freigebenden Offenstellung betätigbar ist.  the valve device (70) is operable between a closed position interrupting the flow of the medium to be compressed and at least one open position releasing the flow of the medium to be compressed. 7. Verbrennungskraftmaschine (10) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass 7. internal combustion engine (10) according to one of the preceding claims, characterized in that die Ventileinrichtung (70) in eine den Strom des zu verdichtenden Mediums freigebende Offenstellung betätigbar ist, wenn der Verdichter (32) der zweiten Aufladeeinrichtung (30) das zu verdichtende Medium zumindest im Wesentlichen auf den gleichen Druck verdichtet wie der Verdichter (26) der ersten  the valve means (70) is actuatable into an open position releasing the flow of the medium to be compressed when the compressor (32) of the second charging means (30) compresses the medium to be compressed at least substantially to the same pressure as the compressor (26) of the first one Aufladeeinrichtung (24).  Charging device (24). 8. Verfahren zum Betreiben einer Verbrennungskraftmaschine (10) mit einer ersten und mit zumindest einer zweiten, jeweils einen Verdichter (26, 32) aufweisenden Aufladeeinrichtung (24, 30), insbesondere Abgasturbolader (24, 30), deren 8. A method for operating an internal combustion engine (10) having a first and at least one second, each having a compressor (26, 32) having charging means (24, 30), in particular exhaust gas turbocharger (24, 30) whose Verdichter (26, 32) ausgangsseitig fluidisch miteinander gekoppelt sind, wobei stromauf des Verdichters (32) der zweiten Aufladeeinrichtung (30) eine  Compressors (26, 32) are fluidically coupled together on the output side, wherein upstream of the compressor (32) of the second charging device (30) has a Ventileinrichtung (70) vorgesehen ist, mittels welcher ein dem Verdichter (32) der zweiten Aufladeeinrichtung (30) zuführbarer Strom eines durch diesen Verdichter (32) zu verdichtenden Mediums eingestellt wird und welches von einem durch diesen Verdichter (32) erzeugten Unterdruck betätigt wird.  Valve device (70) is provided, by means of which a compressor (32) of the second charging device (30) can be supplied flow of a by this compressor (32) to be compressed medium and which is actuated by a by this compressor (32) generated negative pressure.
PCT/EP2010/005439 2009-11-05 2010-09-04 Internal combustion engine Ceased WO2011054407A1 (en)

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