EP3803086B1 - Method for operating an internal combustion engine, and corresponding internal combustion engine - Google Patents

Method for operating an internal combustion engine, and corresponding internal combustion engine Download PDF

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Publication number
EP3803086B1
EP3803086B1 EP19724787.7A EP19724787A EP3803086B1 EP 3803086 B1 EP3803086 B1 EP 3803086B1 EP 19724787 A EP19724787 A EP 19724787A EP 3803086 B1 EP3803086 B1 EP 3803086B1
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EP
European Patent Office
Prior art keywords
internal combustion
combustion engine
temperature
volumetric efficiency
operating
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EP19724787.7A
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German (de)
French (fr)
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EP3803086A1 (en
Inventor
Philipp Prochazka
Florian Freund
Tessen Keulertz
Michael Leihenseder
Christoph Schweitzer
Jürgen TRÜMPER
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Audi AG
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Audi AG
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    • 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
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/04—Introducing corrections for particular operating conditions
    • F02D41/06—Introducing corrections for particular operating conditions for engine starting or warming up
    • F02D41/062—Introducing corrections for particular operating conditions for engine starting or warming up for starting
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/021—Engine temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/04—Engine intake system parameters
    • F02D2200/0411—Volumetric efficiency
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D31/00—Use of speed-sensing governors to control combustion engines, not otherwise provided for
    • F02D31/001—Electric control of rotation speed
    • F02D31/002—Electric control of rotation speed controlling air supply
    • F02D31/006—Electric control of rotation speed controlling air supply for maximum speed control
    • 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

Definitions

  • the invention relates to a method for operating an internal combustion engine which has at least one cylinder by introducing fresh air during a working cycle of the internal combustion engine in order to achieve a specific target delivery ratio, the target delivery ratio being limited to a maximum delivery ratio which is to a first default value when the internal combustion engine is started set and increased in the direction of a second default value after starting the internal combustion engine, and wherein the maximum delivery rate is determined depending on a temperature of the internal combustion engine, the maximum delivery rate being chosen to be smaller at a lower temperature than at a higher temperature.
  • the invention further relates to an internal combustion engine.
  • the publication is from the prior art DE 10 2012 024318 A1 known.
  • This describes a method for operating an internal combustion engine.
  • the internal combustion engine has at least one combustion chamber, an intake manifold, a compressor for generating a charge with a charge density in the intake manifold and a device for changing a degree of delivery of the charge from the intake manifold into the at least one combustion chamber.
  • part of the charge is transferred from the intake manifold into the at least one combustion chamber with a degree of delivery, the degree of delivery being set as a function of the charge density.
  • the degree of delivery is determined and adjusted depending on the air pressure prevailing in the area surrounding the internal combustion engine.
  • the publication also shows WO 2009/065541 A1 a method for controlling a stationary gas engine, in which a speed control deviation is calculated from a target speed and an actual speed, from the speed control deviation via a speed controller a target torque is determined as a manipulated variable, which is set to one via a torque limitation Air ratio limiting torque is limited, and in which a target volume flow is determined from the limited target torque for determining a mixture throttle valve angle and a gas throttle valve angle.
  • the publications also show DE 10 2005 044399 A1 , DE 10 2017112 690 A1 , DE 10 2013 202720 A1 , DE 197 58641 B4 , DE 10 2014 101817 A1 and EP 3 141 727 A1 other internal combustion engines and methods for operating them.
  • the method described is used to operate the internal combustion engine.
  • the internal combustion engine is preferably used to drive a motor vehicle, i.e. to provide a torque aimed at driving the motor vehicle.
  • the internal combustion engine has at least one cylinder, but preferably several cylinders. In the context of this description, only the at least one cylinder or the procedure relating to it will be discussed. The However, statements can always be transferred to the multiple cylinders of the internal combustion engine - if available - namely to each of the multiple cylinders. If there are several cylinders, the method described can be implemented for each of the several cylinders.
  • fresh gas is introduced into the cylinder, which consists entirely of fresh air or at least has fresh air.
  • the fresh gas is composed of fresh air and exhaust gas, namely if exhaust gas recirculation is carried out.
  • the working cycle consists of an intake cycle, a compression cycle, a work cycle and an exhaust cycle.
  • the fresh gas or fresh air is usually introduced during the intake stroke.
  • the fresh air is introduced in such a way that after it has been introduced into the cylinder there is a fresh air mass which corresponds to the target delivery level.
  • a degree of delivery is to be understood as the ratio of the fresh air mass introduced into the cylinder divided by a theoretically possible fresh air mass, the latter being achievable with very slow suction, i.e. without negative pressure in the cylinder.
  • the theoretically possible fresh air mass is determined based on an ambient pressure and an ambient temperature, which are present outside the internal combustion engine. The ambient pressure and the ambient temperature are independent of the operation of the internal combustion engine and its temperature.
  • the internal combustion engine is operated with the target delivery ratio or the target delivery ratio is set on the internal combustion engine.
  • the target delivery level is, for example, initially set to a default delivery level, which results from a specification from a driver of the motor vehicle and/or a driver assistance device of the motor vehicle.
  • the default delivery level is determined from a default torque and/or based on an accelerator pedal position.
  • the target delivery level is limited to the maximum delivery level, especially upwards, i.e. towards larger values.
  • the target delivery ratio corresponds to the maximum delivery ratio or is smaller than this.
  • the maximum delivery ratio is initially set to the first default value and is increased in the direction of the second default value after the internal combustion engine is started.
  • the second default value is greater than the first default value, so that when the internal combustion engine starts, there is initially a smaller maximum delivery ratio.
  • the maximum delivery level is increased, namely in the direction of the second specified value.
  • the maximum delivery rate is increased in such a way that the maximum delivery rate reaches the second specified value when the temperature of the internal combustion engine reaches the operating temperature.
  • Increasing the maximum delivery level starting from the first default value in the direction of the second default value, in particular up to the second default value can in principle take place according to any desired course.
  • the progression is linear, so that increasing the maximum delivery level occurs linearly depending on a reference value.
  • a temperature or time is used as a reference value.
  • the target delivery ratio is a measure of the torque generated by the internal combustion engine or the power output by the internal combustion engine, it is fundamentally also possible to set the maximum torque that can be generated by the internal combustion engine when the internal combustion engine starts to a first default torque and after the start of the Internal combustion engine to increase in the direction of a second specified torque, wherein the second specified torque is greater than the first specified torque.
  • a specified torque is preferably first determined, for example from a specification by a driver of a motor vehicle, which the internal combustion engine is used to drive, or based on the specification of a driver assistance device.
  • the default torque corresponds to the torque desired by the driver or the driver assistance device.
  • a target torque is then determined from the specified torque and set on the internal combustion engine.
  • the internal combustion engine is then operated in such a way that it provides the target torque.
  • the target torque is now a limitation to the maximum torque that can be provided as explained above.
  • the internal combustion engine is started, it is intended to limit the target torque to a smaller torque than, in terms of time, after starting.
  • the pollutant emissions of the internal combustion engine that occur when starting or after starting the internal combustion engine can be significantly reduced, namely by reducing the maximum delivery ratio or the maximum torque that can be generated when starting the internal combustion engine.
  • a spark-ignited internal combustion engine in particular a gasoline internal combustion engine, is preferably used as the internal combustion engine.
  • the maximum delivery level In addition to setting the maximum delivery level to the first default value when starting the internal combustion engine and subsequently increasing it in the direction of the second default value, it can be provided to limit the speed of the internal combustion engine to a maximum speed, with the maximum speed when starting the internal combustion engine to a first Speed value is set and increased after the internal combustion engine has started in the direction of a second speed value.
  • the second speed value preferably corresponds to a maximum permissible speed of the internal combustion engine, which when the internal combustion engine is operating as intended after reaching the operating temperature, without any damage to the internal combustion engine occurring or being expected.
  • the invention provides that the maximum delivery ratio is determined as a function of a temperature of the internal combustion engine, with the maximum delivery ratio being chosen to be smaller at a lower temperature than at a higher temperature.
  • the maximum degree of delivery is present as a function of the temperature of the internal combustion engine, the function having the temperature as an input variable and the maximum degree of delivery as an output variable.
  • a preferred further embodiment of the invention provides that a combustion chamber temperature of a combustion chamber of the cylinder is used as the temperature of the internal combustion engine.
  • the combustion chamber temperature is to be understood as meaning the temperature within the combustion chamber, i.e. the temperature of a fluid present in the combustion chamber.
  • the combustion chamber temperature can be determined, for example, by measuring using a sensor, in particular a sensor arranged in the combustion chamber, or by estimation. For the estimation, for example, a temperature model is used which determines the combustion chamber temperature from at least one other variable, in particular a measured temperature.
  • the combustion chamber temperature is decisive for the amount of pollutant emissions that occur when the internal combustion engine is operated.
  • an operating medium temperature of an operating medium of the internal combustion engine is used as the temperature of the internal combustion engine. Determining the combustion chamber temperature can be complex. For this reason, it can be provided to use the operating medium temperature instead of the combustion chamber temperature.
  • the operating fluid temperature is understood to mean the temperature of the operating fluid of the internal combustion engine. The operating fluid temperature usually lags behind the combustion chamber temperature, so that the maximum delivery rate or the target delivery rate can also be adjusted based on the operating fluid temperature in such a way that there is a significant reduction in pollutant emissions.
  • a coolant that serves to cool the internal combustion engine or a lubricant that serves to lubricate the internal combustion engine is used as operating medium.
  • the operating fluid is present as a coolant or as a lubricant.
  • the temperatures of both the coolant and the lubricant are comparatively easy to determine and are usually measured in each case.
  • Both the temperature of the coolant and the temperature of the lubricant usually lag behind the combustion chamber temperature or are related to it.
  • An increase in the combustion chamber temperature over a certain period of time usually also results in an increase in the operating fluid temperature, i.e. the temperature of the coolant or lubricant.
  • the temperature of the coolant or the temperature of the lubricant can be used in an advantageous manner to determine the maximum delivery level in such a way that there is a significant reduction in pollutant emissions.
  • a further preferred embodiment of the invention provides that the maximum delivery level depends on the first default value of the time elapsed since the start of the internal combustion engine is increased in the direction of the second default value.
  • the target degree of delivery should be determined as a function of time, namely the time that has elapsed since the internal combustion engine was started. If the maximum delivery level is determined solely as a function of time, this can be done with particularly little effort. For example, the course of the maximum delivery ratio over time is selected such that the maximum delivery ratio reaches the second specified value exactly or only when the temperature of the internal combustion engine corresponds to its operating temperature when the internal combustion engine is operating properly.
  • the maximum delivery rate is also possible to determine the maximum delivery rate as a function of both the temperature and the time, so that the maximum delivery rate is present as a function of the temperature and time.
  • the function has the temperature and time as input variables and the maximum delivery ratio as the output variable. This represents a particularly advantageous approach when determining the maximum delivery level.
  • the invention provides that the maximum delivery level reaches the second specified value when the temperature reaches the operating temperature.
  • the operating temperature is to be understood as meaning the temperature of the internal combustion engine which it has during quasi-stationary operation.
  • the internal combustion engine is therefore operated in such a way that the operating temperature is present.
  • the internal combustion engine is cooled in such a way that the temperature of the internal combustion engine corresponds to the operating temperature.
  • the fact that the maximum delivery level corresponds to the second specified value as soon as the temperature reaches the operating temperature ensures that the maximum torque or the maximum power of the internal combustion engine can be called up when the internal combustion engine is at operating temperature.
  • a further embodiment of the invention provides that the second default value has a maximum given the current ambient conditions Delivery level of the internal combustion engine corresponds.
  • the maximum degree of delivery corresponds to the degree of delivery that would exist at maximum power or at nominal power of the internal combustion engine under the current ambient conditions.
  • the maximum degree of delivery is present, for example, as a function of the ambient conditions, in particular as a function of the ambient pressure and/or the ambient temperature. Such an approach ensures that the maximum torque or maximum power can be called up when the internal combustion engine is at operating temperature.
  • the maximum degree of delivery is determined from the ambient conditions, the maximum degree of delivery being determined by subtracting a difference value from the maximum degree of delivery, the difference value starting from a first difference value present when the internal combustion engine is started is reduced in the direction of a second difference value.
  • the maximum delivery level is determined from the ambient conditions.
  • the maximum delivery rate is then determined, whereby it results from the maximum delivery rate minus the difference value.
  • the maximum degree of delivery is therefore at most as large as the maximum degree of delivery, namely when the difference value is equal to zero. If the difference value is different from zero, then the maximum delivery level is different from the maximum delivery level, in particular it is smaller than this.
  • the difference value that is used to determine the maximum delivery level is initially set to the first difference value when the internal combustion engine is started. After starting the internal combustion engine, the difference value is reduced starting from the first difference value in the direction of the second difference value.
  • the second difference value is preferably equal to zero, so that after the difference value has reached the second difference value, the maximum delivery level corresponds to the maximum delivery level.
  • the procedure described using the difference value is a special embodiment of the procedure described, according to which the target level of delivery is limited to the maximum level of delivery, which is the case Start of the internal combustion engine is set to the first default value and is increased in the direction of the second default value after the internal combustion engine has started. However, it can also be used as an alternative.
  • the invention further relates to an internal combustion engine, in particular an internal combustion engine for carrying out the method according to the statements in this description, wherein the internal combustion engine has at least one cylinder into which fresh air is introduced during a working cycle of the internal combustion engine in order to achieve a certain target delivery level. It is provided that the internal combustion engine is designed to limit the target delivery ratio to a maximum delivery ratio, which is set to a first default value when the internal combustion engine starts and is increased in the direction of a second default value after the internal combustion engine has started.
  • Figure is a schematic representation of an internal combustion engine.
  • the figure shows a schematic representation of an internal combustion engine 1, which has several cylinders 2 in the exemplary embodiment shown here.
  • Each of the cylinders 2 has at least one inlet valve 3 and at least one outlet valve 4.
  • Fresh gas from a fresh gas tract 5 can be supplied to the respective cylinder 2 via each of the inlet valves 3, whereas exhaust gas can escape from the corresponding cylinder 2 through each of the outlet valves 4, namely towards an exhaust tract 6.
  • the fresh gas is provided at the inlet valves 3 by means of a compressor 7, which is part of an exhaust gas turbocharger 8.
  • the exhaust gas turbocharger 8 has a turbine 9, which is fluidly connected to the exhaust valves 4 via an exhaust line 10, which is part of the exhaust tract 6.
  • an exhaust gas purification device 11 can be present, which has, for example, at least one catalytic converter.
  • the internal combustion engine 1 is operated by means of a method according to which fresh air is introduced into at least one of the cylinders 2, preferably into each of the cylinders 2, during a working cycle of the internal combustion engine.
  • the fresh air is introduced into the cylinder 2 or the cylinders 2 in such a way that a certain target delivery level is achieved in the respective cylinder.
  • the target delivery ratio is limited to a maximum delivery ratio, namely upwards. This means that the target delivery ratio is always less than or equal to the maximum delivery ratio.
  • the maximum delivery ratio is set to a first default value when the internal combustion engine 1 starts and is increased in the direction of a second default value after the internal combustion engine 1 is started.
  • the target delivery ratio when starting the internal combustion engine, in particular during a warm-up operation of the internal combustion engine 1 is limited to smaller values than after the internal combustion engine has reached an operating temperature due to a temperature of the internal combustion engine. Accordingly, the pollutant emissions from the internal combustion engine are significantly reduced during warm-up operation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combined Controls Of Internal Combustion Engines (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Description

Die Erfindung betrifft ein Verfahren zum Betreiben einer Brennkraftmaschine, die wenigstens einen Zylinder aufweist, indem während eines Arbeitsspiels der Brennkraftmaschine Frischluft zum Erzielen eines bestimmten Sollliefergrads eingebracht wird, wobei der Sollliefergrad auf einen Maximalliefergrad begrenzt wird, der bei einem Start der Brennkraftmaschine auf einen ersten Vorgabewert gesetzt und nach dem Start der Brennkraftmaschine in Richtung eines zweiten Vorgabewerts vergrößert wird, und wobei der Maximalliefergrad in Abhängigkeit von einer Temperatur der Brennkraftmaschine bestimmt wird, wobei der Maximalliefergrad bei einer niedrigeren Temperatur kleiner gewählt wird als bei einer höheren Temperatur. Die Erfindung betrifft weiterhin eine Brennkraftmaschine.The invention relates to a method for operating an internal combustion engine which has at least one cylinder by introducing fresh air during a working cycle of the internal combustion engine in order to achieve a specific target delivery ratio, the target delivery ratio being limited to a maximum delivery ratio which is to a first default value when the internal combustion engine is started set and increased in the direction of a second default value after starting the internal combustion engine, and wherein the maximum delivery rate is determined depending on a temperature of the internal combustion engine, the maximum delivery rate being chosen to be smaller at a lower temperature than at a higher temperature. The invention further relates to an internal combustion engine.

Aus dem Stand der Technik ist beispielsweise die Druckschrift DE 10 2012 024318 A1 bekannt. Diese beschreibt ein Verfahren zum Betreiben einer Brennkraftmaschine. Die Brennkraftmaschine weist wenigstens einen Brennraum, ein Saugrohr, einen Verdichter zum Erzeugen einer Ladung mit einer Ladungsdichte im Saugrohr und eine Vorrichtung zur Veränderung eines Liefergrades der Ladung vom Saugrohr in den wenigstens einen Brennraum auf. Gemäß dem Verfahren wird ein Teil der Ladung vom Saugrohr in den wenigstens einen Brennraum mit einem Liefergrad übertragen, wobei der Liefergrad in Funktion der Ladungsdichte eingestellt ist. Der Liefergrad wird dabei in Abhängigkeit des in einer Umgebung der Brennkraftmaschine herrschenden Luftdrucks bestimmt und eingestellt.For example, the publication is from the prior art DE 10 2012 024318 A1 known. This describes a method for operating an internal combustion engine. The internal combustion engine has at least one combustion chamber, an intake manifold, a compressor for generating a charge with a charge density in the intake manifold and a device for changing a degree of delivery of the charge from the intake manifold into the at least one combustion chamber. According to the method, part of the charge is transferred from the intake manifold into the at least one combustion chamber with a degree of delivery, the degree of delivery being set as a function of the charge density. The degree of delivery is determined and adjusted depending on the air pressure prevailing in the area surrounding the internal combustion engine.

Weiterhin zeigt die Druckschrift WO 2009/065541 A1 ein Verfahren zur Regelung eines stationären Gasmotors, bei dem eine Drehzahl-Regelabweichung aus einer Soll-Drehzahl sowie einer Ist-Drehzahl berechnet wird, aus der Drehzahl-Regelabweichung über einen Drehzahlregler als Stellgröße ein Soll-Moment bestimmt wird, welches über eine Momentbegrenzung auf ein Luftverhältnis-Begrenzungsmoment begrenzt wird, und bei dem aus dem begrenzten Soll-Moment ein Soll-Volumenstrom zur Festlegung eines Gemisch-Drosselklappenwinkels sowie eines Gas-Drosselklappenwinkel bestimmt wird. Weiterhin zeigen die Druckschriften DE 10 2005 044399 A1 , DE 10 2017112 690 A1 , DE 10 2013 202720 A1 , DE 197 58641 B4 , DE 10 2014 101817 A1 und EP 3 141 727 A1 weitere Brennkraftmaschinen sowie Verfahren zu ihrem Betreiben.The publication also shows WO 2009/065541 A1 a method for controlling a stationary gas engine, in which a speed control deviation is calculated from a target speed and an actual speed, from the speed control deviation via a speed controller a target torque is determined as a manipulated variable, which is set to one via a torque limitation Air ratio limiting torque is limited, and in which a target volume flow is determined from the limited target torque for determining a mixture throttle valve angle and a gas throttle valve angle. The publications also show DE 10 2005 044399 A1 , DE 10 2017112 690 A1 , DE 10 2013 202720 A1 , DE 197 58641 B4 , DE 10 2014 101817 A1 and EP 3 141 727 A1 other internal combustion engines and methods for operating them.

Es ist Aufgabe der Erfindung ein Verfahren zum Betreiben einer Brennkraftmaschine vorzuschlagen, welches gegenüber bekannten Verfahren Vorteile aufweist, insbesondere einen Betrieb der Brennkraftmaschine mit geringen Emissionen ermöglicht, vorzugsweise während eines Aufwärmbetriebs der Brennkraftmaschine.It is the object of the invention to propose a method for operating an internal combustion engine, which has advantages over known methods, in particular enabling operation of the internal combustion engine with low emissions, preferably during warm-up operation of the internal combustion engine.

Dies wird erfindungsgemäß mit einem Verfahren zum Betreiben einer Brennkraftmaschine mit den Merkmalen des Anspruchs 1 erreicht. Dabei ist vorgesehen, dass das Vergrößern des Maximalliefergrads derart erfolgt, dass der Maximalliefergrad mit dem Erreichen einer bei einem quasistationären Betrieb der Brennkraftmaschine vorliegenden Betriebstemperatur den zweiten Vorgabewert erreicht.This is achieved according to the invention with a method for operating an internal combustion engine with the features of claim 1. It is provided that the maximum delivery ratio is increased in such a way that the maximum delivery ratio reaches the second specified value when the operating temperature present during quasi-stationary operation of the internal combustion engine is reached.

Das beschriebene Verfahren dient dem Betreiben der Brennkraftmaschine. Die Brennkraftmaschine dient vorzugsweise dem Antreiben eines Kraftfahrzeugs, also dem Bereitstellen eines auf das Antreiben des Kraftfahrzeugs gerichteten Drehmoments. Die Brennkraftmaschine verfügt über den wenigstens einen Zylinder, vorzugsweise jedoch über mehrere Zylinder. Im Rahmen dieser Beschreibung wird lediglich auf den wenigstens einen Zylinder beziehungsweise das diesen betreffende Vorgehen eingegangen. Die Ausführungen sind jedoch stets auf die mehreren Zylinder der Brennkraftmaschine - sofern vorhanden - übertragbar, nämlich auf jeden der mehreren Zylinder. Falls mehrere Zylinder vorliegen, kann das beschriebene Verfahren also für jeden der mehreren Zylinder umgesetzt sein.The method described is used to operate the internal combustion engine. The internal combustion engine is preferably used to drive a motor vehicle, i.e. to provide a torque aimed at driving the motor vehicle. The internal combustion engine has at least one cylinder, but preferably several cylinders. In the context of this description, only the at least one cylinder or the procedure relating to it will be discussed. The However, statements can always be transferred to the multiple cylinders of the internal combustion engine - if available - namely to each of the multiple cylinders. If there are several cylinders, the method described can be implemented for each of the several cylinders.

Während jedes Arbeitsspiels der Brennkraftmaschine wird in den Zylinder Frischgas eingebracht, welches vollständig aus Frischluft besteht oder Frischluft zumindest aufweist. Beispielsweise setzt sich das Frischgas aus der Frischluft und Abgas zusammen, nämlich sofern eine Abgasrückführung durchgeführt wird. Das Arbeitsspiel setzt sich aus einem Ansaugtakt, einem Verdichtungstakt, einem Arbeitstakt und einem Ausstoßtakt zusammen. Das Einbringen des Frischgases beziehungsweise der Frischluft erfolgt üblicherweise während des Ansaugtakts. Das Einbringen der Frischluft erfolgt derart, dass nach dem Einbringen in dem Zylinder eine Frischluftmasse vorliegt, welche dem Sollliefergrad entspricht.During each working cycle of the internal combustion engine, fresh gas is introduced into the cylinder, which consists entirely of fresh air or at least has fresh air. For example, the fresh gas is composed of fresh air and exhaust gas, namely if exhaust gas recirculation is carried out. The working cycle consists of an intake cycle, a compression cycle, a work cycle and an exhaust cycle. The fresh gas or fresh air is usually introduced during the intake stroke. The fresh air is introduced in such a way that after it has been introduced into the cylinder there is a fresh air mass which corresponds to the target delivery level.

Unter einem Liefergrad ist das Verhältnis der in den Zylinder eingebrachten Frischluftmasse dividiert durch eine theoretisch mögliche Frischluftmasse zu verstehen, wobei letztere bei sehr langsamem Ansaugen, also ohne Unterdruck in dem Zylinder, erzielbar ist. Die theoretisch mögliche Frischluftmasse wird anhand eines Umgebungsdrucks und einer Umgebungstemperatur ermittelt, welche außerhalb der Brennkraftmaschine vorliegen. Der Umgebungsdruck und die Umgebungstemperatur sind insoweit unabhängig von dem Betrieb der Brennkraftmaschine und ihrer Temperatur.A degree of delivery is to be understood as the ratio of the fresh air mass introduced into the cylinder divided by a theoretically possible fresh air mass, the latter being achievable with very slow suction, i.e. without negative pressure in the cylinder. The theoretically possible fresh air mass is determined based on an ambient pressure and an ambient temperature, which are present outside the internal combustion engine. The ambient pressure and the ambient temperature are independent of the operation of the internal combustion engine and its temperature.

Die Brennkraftmaschine wird mit dem Sollliefergrad betrieben beziehungsweise der Sollliefergrad an der Brennkraftmaschine eingestellt. Der Sollliefergrad wird beispielsweise zunächst auf einen Vorgabeliefergrad gesetzt, der aus einer Vorgabe eines Fahrers des Kraftfahrzeugs und/oder einer Fahrerassistenzeinrichtung des Kraftfahrzeugs resultiert. Beispielsweise wird der Vorgabeliefergrad aus einem Vorgabedrehmoment und/oder anhand einer Fahrpedalstellung ermittelt. Bei oder nach dem Setzen des Sollliefergrads auf den Vorgabeliefergrad wird der Sollliefergrad auf den Maximalliefergrad begrenzt, insbesondere nach oben, also in Richtung größerer Werte. Der Sollliefergrad entspricht also dem Maximalliefergrad oder ist kleiner als dieser.The internal combustion engine is operated with the target delivery ratio or the target delivery ratio is set on the internal combustion engine. The target delivery level is, for example, initially set to a default delivery level, which results from a specification from a driver of the motor vehicle and/or a driver assistance device of the motor vehicle. For example, the default delivery level is determined from a default torque and/or based on an accelerator pedal position. When or after setting the target delivery level to the default delivery level, the target delivery level is limited to the maximum delivery level, especially upwards, i.e. towards larger values. The target delivery ratio corresponds to the maximum delivery ratio or is smaller than this.

Weist die Brennkraftmaschine eine Temperatur auf, welche kleiner ist als ihre Betriebstemperatur, und soll gleichzeitig ein hoher Sollliefergrad vorliegen, so erhöhen sich die Schadstoffemissionen der Brennkraftmaschine drastisch. Aus diesem Grund ist es vorgesehen, dass bei dem Start der Brennkraftmaschine der Maximalliefergrad zunächst auf den ersten Vorgabewert gesetzt und nach dem Start der Brennkraftmaschine in Richtung des zweiten Vorgabewerts vergrößert wird. Hierbei ist der zweite Vorgabewert größer als der erste Vorgabewert, sodass bei dem Start der Brennkraftmaschine zunächst ein kleinerer Maximalliefergrad vorliegt.If the internal combustion engine has a temperature that is lower than its operating temperature and at the same time a high target delivery level is to be present, the pollutant emissions from the internal combustion engine increase drastically. For this reason, it is provided that when the internal combustion engine is started, the maximum delivery ratio is initially set to the first default value and is increased in the direction of the second default value after the internal combustion engine is started. Here, the second default value is greater than the first default value, so that when the internal combustion engine starts, there is initially a smaller maximum delivery ratio.

Nach dem Start der Brennkraftmaschine wird der Maximalliefergrad vergrö-ßert, nämlich in Richtung des zweiten Vorgabewerts. Erfindungsgemäß erfolgt das Erhöhen des Maximalliefergrad derart, dass der Maximalliefergrad mit dem Erreichen der Betriebstemperatur durch die Temperatur der Brennkraftmaschine den zweiten Vorgabewert erreicht. Das Erhöhen des Maximalliefergrad ausgehend von dem ersten Vorgabewert in Richtung des zweiten Vorgabewerts, insbesondere bis auf den zweiten Vorgabewert, kann grundsätzlich gemäß einem beliebigen Verlauf erfolgen. Beispielsweise ist der Verlauf linear, sodass das Erhöhen des Maximalliefergrad in Abhängigkeit von einer Bezugsgröße linear erfolgt. Als Bezugsgröße wird beispielsweise eine Temperatur oder die Zeit herangezogen.After the internal combustion engine starts, the maximum delivery level is increased, namely in the direction of the second specified value. According to the invention, the maximum delivery rate is increased in such a way that the maximum delivery rate reaches the second specified value when the temperature of the internal combustion engine reaches the operating temperature. Increasing the maximum delivery level starting from the first default value in the direction of the second default value, in particular up to the second default value, can in principle take place according to any desired course. For example, the progression is linear, so that increasing the maximum delivery level occurs linearly depending on a reference value. For example, a temperature or time is used as a reference value.

Weil der Sollliefergrad ein Maß für das mittels der Brennkraftmaschine erzeugte Drehmoment beziehungsweise die von der Brennkraftmaschine abgegebene Leistung ist, ist es grundsätzlich auch möglich, das von der Brennkraftmaschine maximal erzeugbare Drehmoment bei dem Start der Brennkraftmaschine auf ein erstes Vorgabedrehmoment zu setzen und nach dem Start der Brennkraftmaschine in Richtung eines zweiten Vorgabedrehmoments zu vergrößern, wobei das zweite Vorgabedrehmoment größer ist als das erste Vorgabedrehmoment.Because the target delivery ratio is a measure of the torque generated by the internal combustion engine or the power output by the internal combustion engine, it is fundamentally also possible to set the maximum torque that can be generated by the internal combustion engine when the internal combustion engine starts to a first default torque and after the start of the Internal combustion engine to increase in the direction of a second specified torque, wherein the second specified torque is greater than the first specified torque.

Für das Betreiben der Brennkraftmaschine wird vorzugsweise zunächst ein Vorgabedrehmoment ermittelt, beispielsweise aus einer Vorgabe eines Fahrers eines Kraftfahrzeugs, zu dessen Antrieb die Brennkraftmaschine dient, oder anhand der Vorgabe einer Fahrerassistenzeinrichtung. Das Vorgabedrehmoment entspricht dem von dem Fahrer beziehungsweise der Fahrerassistenzeinrichtung gewünschten Drehmoment. Anschließend wird aus dem Vorgabedrehmoment ein Solldrehmoment ermittelt und an der Brennkraftmaschine eingestellt.For operating the internal combustion engine, a specified torque is preferably first determined, for example from a specification by a driver of a motor vehicle, which the internal combustion engine is used to drive, or based on the specification of a driver assistance device. The default torque corresponds to the torque desired by the driver or the driver assistance device. A target torque is then determined from the specified torque and set on the internal combustion engine.

Anschließend wird die Brennkraftmaschine derart betrieben, dass sie das Solldrehmoment bereitstellt. Bei dem Ermitteln des Solldrehmoments aus dem Vorgabedrehmoment erfolgt nun eine Begrenzung auf das vorstehend erläuterte maximal bereitstellbare Drehmoment. In anderen Worten ist es vorgesehen, bei dem Start der Brennkraftmaschine das Solldrehmoment auf ein kleineres Drehmoment zu begrenzen als zeitlich gesehen nach dem Starten.The internal combustion engine is then operated in such a way that it provides the target torque. When determining the target torque from the specified torque, there is now a limitation to the maximum torque that can be provided as explained above. In other words, when the internal combustion engine is started, it is intended to limit the target torque to a smaller torque than, in terms of time, after starting.

Mit der beschriebenen Vorgehensweise können die Schadstoffemissionen der Brennkraftmaschine, die bei dem Start beziehungsweise nach dem Start der Brennkraftmaschine anfallen, deutlich reduziert werden, nämlich durch die Reduzierung des Maximalliefergrads beziehungsweise des maximal erzeugbaren Drehmoments bei dem Start der Brennkraftmaschine. Als Brennkraftmaschine kommt vorzugsweise eine fremdgezündete Brennkraftmaschine, also insbesondere eine Otto-Brennkraftmaschine zum Einsatz.With the procedure described, the pollutant emissions of the internal combustion engine that occur when starting or after starting the internal combustion engine can be significantly reduced, namely by reducing the maximum delivery ratio or the maximum torque that can be generated when starting the internal combustion engine. A spark-ignited internal combustion engine, in particular a gasoline internal combustion engine, is preferably used as the internal combustion engine.

Zusätzlich zu dem Setzen des Maximalliefergrads auf den ersten Vorgabewert bei dem Start der Brennkraftmaschine und seinem nachfolgenden Vergrößern in Richtung des zweiten Vorgabewerts kann es vorgesehen sein, die Drehzahl der Brennkraftmaschine auf eine Maximaldrehzahl zu begrenzen, wobei die Maximaldrehzahl bei dem Start der Brennkraftmaschine auf einen ersten Drehzahlwert gesetzt und nach dem Start der Brennkraftmaschine in Richtung eines zweiten Drehzahlwerts vergrößert wird. Der zweite Drehzahlwert entspricht vorzugsweise einer maximal zulässigen Drehzahl der Brennkraftmaschine, welche bei bestimmungsgemäßen Betrieb der Brennkraftmaschine nach Erreichen der Betriebstemperatur vorliegen darf, ohne dass Beschädigungen der Brennkraftmaschine auftreten beziehungsweise zu erwarten sind.In addition to setting the maximum delivery level to the first default value when starting the internal combustion engine and subsequently increasing it in the direction of the second default value, it can be provided to limit the speed of the internal combustion engine to a maximum speed, with the maximum speed when starting the internal combustion engine to a first Speed value is set and increased after the internal combustion engine has started in the direction of a second speed value. The second speed value preferably corresponds to a maximum permissible speed of the internal combustion engine, which when the internal combustion engine is operating as intended after reaching the operating temperature, without any damage to the internal combustion engine occurring or being expected.

Die Erfindung sieht vor, dass der Maximalliefergrad in Abhängigkeit von einer Temperatur der Brennkraftmaschine bestimmt wird, wobei der Maximalliefergrad bei einer niedrigeren Temperatur kleiner gewählt wird als bei einer höheren Temperatur. Der Maximalliefergrad liegt insoweit als Funktion der Temperatur der Brennkraftmaschine vor, wobei die Funktion die Temperatur als Eingangsgröße und den Maximalliefergrad als Ausgangsgröße aufweist. Die Funktion ist derart gewählt, dass der Maximalliefergrad bei der niedrigeren Temperatur kleiner ist als bei der höheren Temperatur. Das Bestimmen des Maximalliefergrads in Abhängigkeit von der Temperatur hat den Vorteil, dass eine besonders wirksame Anpassung des Maximalliefergrads an die Betriebsbedingungen und/oder die Umgebungsbedingungen der Brennkraftmaschine erfolgt, sodass eine besonders deutliche Reduzierung der Schadstoffemissionen erzielt wird.The invention provides that the maximum delivery ratio is determined as a function of a temperature of the internal combustion engine, with the maximum delivery ratio being chosen to be smaller at a lower temperature than at a higher temperature. The maximum degree of delivery is present as a function of the temperature of the internal combustion engine, the function having the temperature as an input variable and the maximum degree of delivery as an output variable. The function is selected such that the maximum delivery rate at the lower temperature is smaller than at the higher temperature. Determining the maximum delivery rate as a function of the temperature has the advantage that a particularly effective adaptation of the maximum delivery rate to the operating conditions and/or the ambient conditions of the internal combustion engine occurs, so that a particularly significant reduction in pollutant emissions is achieved.

Eine bevorzugte weitere Ausführungsform der Erfindung sieht vor, dass als Temperatur der Brennkraftmaschine eine Brennraumtemperatur eines Brennraums des Zylinders verwendet wird. Unter der Brennraumtemperatur ist die Temperatur innerhalb des Brennraums zu verstehen, also die Temperatur eines in dem Brennraum vorliegenden Fluids. Das Ermitteln der Brennraumtemperatur kann beispielsweise durch Messen mittels eines Sensors, insbesondere eines in dem Brennraum angeordneten Sensors, oder durch Abschätzen erfolgen. Für das Abschätzen kommt beispielsweise ein Temperaturmodell zum Einsatz, welches die Brennraumtemperatur aus wenigstens einer anderen Größe, insbesondere einer gemessenen Temperatur, bestimmt.A preferred further embodiment of the invention provides that a combustion chamber temperature of a combustion chamber of the cylinder is used as the temperature of the internal combustion engine. The combustion chamber temperature is to be understood as meaning the temperature within the combustion chamber, i.e. the temperature of a fluid present in the combustion chamber. The combustion chamber temperature can be determined, for example, by measuring using a sensor, in particular a sensor arranged in the combustion chamber, or by estimation. For the estimation, for example, a temperature model is used which determines the combustion chamber temperature from at least one other variable, in particular a measured temperature.

Die Brennraumtemperatur ist maßgeblich für die Menge der Schadstoffemissionen, die bei dem Betrieb der Brennkraftmaschine anfallen. So sind die Schadstoffemissionen umso höher, je geringer die Brennraumtemperatur ist. Aus diesem Grund ist es besonders vorteilhaft, die Brennraumtemperatur zum Bestimmen des Maximalliefergrads heranzuziehen, weil somit eine besonders deutliche Reduzierung der Schadstoffemissionen erzielt wird.The combustion chamber temperature is decisive for the amount of pollutant emissions that occur when the internal combustion engine is operated. The lower the combustion chamber temperature, the higher the pollutant emissions. For this reason, it is particularly advantageous to use the combustion chamber temperature to determine the maximum delivery level, because a particularly significant reduction in pollutant emissions is achieved.

Eine Weiterbildung der Erfindung sieht vor, dass als Temperatur der Brennkraftmaschine eine Betriebsmitteltemperatur eines Betriebsmittels der Brennkraftmaschine verwendet wird. Das Bestimmen der Brennraumtemperatur ist unter Umständen aufwendig. Aus diesem Grund kann es vorgesehen sein, anstelle der Brennraumtemperatur die Betriebsmitteltemperatur heranzuziehen. Unter der Betriebsmitteltemperatur ist die Temperatur des Betriebsmittels der Brennkraftmaschine zu verstehen. Üblicherweise läuft die Betriebsmitteltemperatur der Brennraumtemperatur hinterher, sodass auch anhand der Betriebsmitteltemperatur eine Anpassung des Maximalliefergrads beziehungsweise des Sollliefergrads derart erfolgen kann, dass eine deutliche Reduzierung der Schadstoffemissionen vorliegt.A further development of the invention provides that an operating medium temperature of an operating medium of the internal combustion engine is used as the temperature of the internal combustion engine. Determining the combustion chamber temperature can be complex. For this reason, it can be provided to use the operating medium temperature instead of the combustion chamber temperature. The operating fluid temperature is understood to mean the temperature of the operating fluid of the internal combustion engine. The operating fluid temperature usually lags behind the combustion chamber temperature, so that the maximum delivery rate or the target delivery rate can also be adjusted based on the operating fluid temperature in such a way that there is a significant reduction in pollutant emissions.

Im Rahmen einer weiteren Ausführungsform der Erfindung kann vorgesehen sein, dass als Betriebsmittel ein einer Kühlung der Brennkraftmaschine dienendes Kühlmittel oder ein einer Schmierung der Brennkraftmaschine dienendes Schmiermittel verwendet wird. Das Betriebsmittel liegt insoweit als Kühlmittel oder als Schmiermittel vor. Die Temperaturen sowohl des Kühlmittels als auch des Schmiermittels sind vergleichsweise einfach bestimmbar und werden üblicherweise jeweils gemessen.As part of a further embodiment of the invention, it can be provided that a coolant that serves to cool the internal combustion engine or a lubricant that serves to lubricate the internal combustion engine is used as operating medium. The operating fluid is present as a coolant or as a lubricant. The temperatures of both the coolant and the lubricant are comparatively easy to determine and are usually measured in each case.

Sowohl die Temperatur des Kühlmittels als auch die Temperatur des Schmiermittels laufen üblicherweise der Brennraumtemperatur hinterher beziehungsweise stehen mit dieser in einem Zusammenhang. Aus einer Erhöhung der Brennraumtemperatur über eine gewisse Zeitspanne hinweg folgt üblicherweise auch eine Erhöhung der Betriebsmitteltemperatur, also der Temperatur des Kühlmittels oder des Schmiermittels. Entsprechend kann die Temperatur des Kühlmittels beziehungsweise die Temperatur des Schmiermittels auf vorteilhafte Art und Weise zur Ermittlung des Maximalliefergrads derart herangezogen werden, dass sich eine deutliche Reduzierung der Schadstoffemissionen ergibt.Both the temperature of the coolant and the temperature of the lubricant usually lag behind the combustion chamber temperature or are related to it. An increase in the combustion chamber temperature over a certain period of time usually also results in an increase in the operating fluid temperature, i.e. the temperature of the coolant or lubricant. Accordingly, the temperature of the coolant or the temperature of the lubricant can be used in an advantageous manner to determine the maximum delivery level in such a way that there is a significant reduction in pollutant emissions.

Eine weitere bevorzugte Ausführungsform der Erfindung sieht vor, dass der Maximalliefergrad ausgehend von dem ersten Vorgabewert in Abhängigkeit von der seit dem Start der Brennkraftmaschine verstrichenen Zeit in Richtung des zweiten Vorgabewerts vergrößert wird. Anstelle oder zusätzlich in Abhängigkeit der Temperatur soll also der Solliefergrad in Abhängigkeit von der Zeit bestimmt werden, nämlich von der seit dem Start der Brennkraftmaschine verstrichenen Zeit. Wird der Maximalliefergrad ausschließlich in Abhängigkeit von der Zeit ermittelt, so ist dies mit besonders geringem Aufwand möglich. Beispielsweise ist der Verlauf des Maximalliefergrads über der Zeit derart gewählt, dass der Maximalliefergrad den zweiten Vorgabewert genau dann oder erst dann erreicht, wenn die Temperatur der Brennkraftmaschine ihrer Betriebstemperatur bei ordnungsgemäßem Betrieb der Brennkraftmaschine entspricht.A further preferred embodiment of the invention provides that the maximum delivery level depends on the first default value of the time elapsed since the start of the internal combustion engine is increased in the direction of the second default value. Instead of or additionally depending on the temperature, the target degree of delivery should be determined as a function of time, namely the time that has elapsed since the internal combustion engine was started. If the maximum delivery level is determined solely as a function of time, this can be done with particularly little effort. For example, the course of the maximum delivery ratio over time is selected such that the maximum delivery ratio reaches the second specified value exactly or only when the temperature of the internal combustion engine corresponds to its operating temperature when the internal combustion engine is operating properly.

Selbstverständlich ist es auch möglich, den Maximalliefergrad in Abhängigkeit sowohl von der Temperatur als auch von der Zeit zu bestimmen, sodass also der Maximalliefergrad als Funktion von der Temperatur und der Zeit vorliegt. In anderen Worten weist die Funktion als Eingangsgrößen die Temperatur und die Zeit und als Ausgangsgröße den Maximalliefergrad auf. Dies stellt eine besonders vorteilhafte Vorgehensweise bei dem Ermitteln des Maximalliefergrads dar.Of course, it is also possible to determine the maximum delivery rate as a function of both the temperature and the time, so that the maximum delivery rate is present as a function of the temperature and time. In other words, the function has the temperature and time as input variables and the maximum delivery ratio as the output variable. This represents a particularly advantageous approach when determining the maximum delivery level.

Die Erfindung sieht vor, dass der Maximalliefergrad mit Erreichen der Betriebstemperatur durch die Temperatur den zweiten Vorgabewert erreicht. Unter der Betriebstemperatur ist diejenige Temperatur der Brennkraftmaschine zu verstehen, welche diese im Rahmen eines quasistationären Betriebs aufweist. Die Brennkraftmaschine wird also derart betrieben, dass die Betriebstemperatur vorliegt. Insbesondere erfolgt eine Kühlung der Brennkraftmaschine derart, dass die Temperatur der Brennkraftmaschine der Betriebstemperatur entspricht. Indem der Maximalliefergrad dem zweiten Vorgabewert entspricht, sobald die Temperatur die Betriebstemperatur erreicht, wird sichergestellt, dass bei betriebswarmer Brennkraftmaschine das maximale Drehmoment beziehungsweise die maximale Leistung der Brennkraftmaschine abrufbar ist.The invention provides that the maximum delivery level reaches the second specified value when the temperature reaches the operating temperature. The operating temperature is to be understood as meaning the temperature of the internal combustion engine which it has during quasi-stationary operation. The internal combustion engine is therefore operated in such a way that the operating temperature is present. In particular, the internal combustion engine is cooled in such a way that the temperature of the internal combustion engine corresponds to the operating temperature. The fact that the maximum delivery level corresponds to the second specified value as soon as the temperature reaches the operating temperature ensures that the maximum torque or the maximum power of the internal combustion engine can be called up when the internal combustion engine is at operating temperature.

Eine weitere Ausführungsform der Erfindung sieht vor, dass der zweite Vorgabewert einem bei aktuell vorliegenden Umgebungsbedingungen maximalen Liefergrad der Brennkraftmaschine entspricht. Der maximale Liefergrad entspricht demjenigen Liefergrad, welcher bei maximaler Leistung beziehungsweise bei Nennleistung der Brennkraftmaschine unter den momentanen Umgebungsbedingungen vorläge. Der maximale Liefergrad liegt beispielsweise als Funktion von den Umgebungsbedingungen, insbesondere als Funktion von dem Umgebungsdruck und/oder der Umgebungstemperatur, vor. Eine derartige Vorgehensweise stellt sicher, dass bei betriebswarmer Brennkraftmaschine das maximale Drehmoment beziehungsweise die maximale Leistung abrufbar ist.A further embodiment of the invention provides that the second default value has a maximum given the current ambient conditions Delivery level of the internal combustion engine corresponds. The maximum degree of delivery corresponds to the degree of delivery that would exist at maximum power or at nominal power of the internal combustion engine under the current ambient conditions. The maximum degree of delivery is present, for example, as a function of the ambient conditions, in particular as a function of the ambient pressure and/or the ambient temperature. Such an approach ensures that the maximum torque or maximum power can be called up when the internal combustion engine is at operating temperature.

Schließlich kann im Rahmen einer weiteren Ausgestaltung der Erfindung vorgesehen sein, dass aus den Umgebungsbedingungen der maximale Liefergrad ermittelt wird, wobei der Maximalliefergrad durch Subtraktion eines Differenzwerts von dem maximalen Liefergrad bestimmt wird, wobei der Differenzwert ausgehend von einem bei dem Start der Brennkraftmaschine vorliegenden ersten Differenzwert in Richtung eines zweiten Differenzwerts verkleinert wird. Zunächst wird also der maximale Liefergrad aus den Umgebungsbedingungen bestimmt. Anschließend wird der Maximalliefergrad festgelegt, wobei er sich aus dem maximalen Liefergrad abzüglich des Differenzwerts ergibt. Der Maximalliefergrad ist also höchstens so groß wie der maximale Liefergrad, nämlich wenn der Differenzwert gleich Null ist. Ist der Differenzwert von Null verschieden, so ist der Maximalliefergrad von dem maximalen Liefergrad verschieden, insbesondere ist er kleiner als dieser.Finally, as part of a further embodiment of the invention, it can be provided that the maximum degree of delivery is determined from the ambient conditions, the maximum degree of delivery being determined by subtracting a difference value from the maximum degree of delivery, the difference value starting from a first difference value present when the internal combustion engine is started is reduced in the direction of a second difference value. First of all, the maximum delivery level is determined from the ambient conditions. The maximum delivery rate is then determined, whereby it results from the maximum delivery rate minus the difference value. The maximum degree of delivery is therefore at most as large as the maximum degree of delivery, namely when the difference value is equal to zero. If the difference value is different from zero, then the maximum delivery level is different from the maximum delivery level, in particular it is smaller than this.

Der Differenzwert, der bei dem Bestimmen des Maximalliefergrads herangezogen wird, wird bei dem Start der Brennkraftmaschine zunächst auf den ersten Differenzwert gesetzt. Nach dem Start der Brennkraftmaschine wird der Differenzwert ausgehend von dem ersten Differenzwert in Richtung des zweiten Differenzwerts verkleinert. Der zweite Differenzwert ist vorzugsweise gleich Null, sodass nach dem Erreichen des zweiten Differenzwerts durch den Differenzwert der Maximalliefergrad dem maximalen Liefergrad entspricht. Die beschriebene Vorgehensweise unter Heranziehung des Differenzwerts ist eine spezielle Ausgestaltung der beschriebenen Vorgehensweise, gemäß welcher der Sollliefergrad auf den Maximalliefergrad begrenzt wird, der bei dem Start der Brennkraftmaschine auf den ersten Vorgabewert gesetzt und nach dem Start der Brennkraftmaschine in Richtung des zweiten Vorgabewerts vergrößert wird. Sie kann jedoch auch alternativ herangezogen werden.The difference value that is used to determine the maximum delivery level is initially set to the first difference value when the internal combustion engine is started. After starting the internal combustion engine, the difference value is reduced starting from the first difference value in the direction of the second difference value. The second difference value is preferably equal to zero, so that after the difference value has reached the second difference value, the maximum delivery level corresponds to the maximum delivery level. The procedure described using the difference value is a special embodiment of the procedure described, according to which the target level of delivery is limited to the maximum level of delivery, which is the case Start of the internal combustion engine is set to the first default value and is increased in the direction of the second default value after the internal combustion engine has started. However, it can also be used as an alternative.

Die Erfindung betrifft weiterhin eine Brennkraftmaschine, insbesondere eine Brennkraftmaschine zur Durchführung des Verfahrens gemäß den Ausführungen im Rahmen dieser Beschreibung, wobei die Brennkraftmaschine wenigstens einen Zylinder aufweist, in den während eines Arbeitsspiels der Brennkraftmaschine Frischluft zum Erzielen eines bestimmten Sollliefergrads eingebracht wird. Dabei ist vorgesehen, dass die Brennkraftmaschine dazu ausgebildet ist, den Sollliefergrad auf einen Maximalliefergrad zu begrenzen, der bei einem Start der Brennkraftmaschine auf einen ersten Vorgabewert gesetzt und nach dem Start der Brennkraftmaschine in Richtung eines zweiten Vorgabewerts vergrößert wird.The invention further relates to an internal combustion engine, in particular an internal combustion engine for carrying out the method according to the statements in this description, wherein the internal combustion engine has at least one cylinder into which fresh air is introduced during a working cycle of the internal combustion engine in order to achieve a certain target delivery level. It is provided that the internal combustion engine is designed to limit the target delivery ratio to a maximum delivery ratio, which is set to a first default value when the internal combustion engine starts and is increased in the direction of a second default value after the internal combustion engine has started.

Auf die Vorteile einer derartigen Vorgehensweise beziehungsweise einer derartigen Ausgestaltung der Brennkraftmaschine wurde bereits hingewiesen. Sowohl die Brennkraftmaschine als auch das Verfahren zu ihrem Betreiben können gemäß den Ausführungen im Rahmen dieser Beschreibung weitergebildet sein, sodass insoweit auf diese verwiesen wird.The advantages of such an approach or such a design of the internal combustion engine have already been pointed out. Both the internal combustion engine and the method for operating it can be further developed according to the statements in this description, so that reference is made to this.

Die Erfindung wird nachfolgend anhand der in der Zeichnung dargestellten Ausführungsbeispiele näher erläutert, ohne dass eine Beschränkung der Erfindung erfolgt. Dabei zeigt die einzigeThe invention is explained in more detail below with reference to the exemplary embodiments shown in the drawing, without restricting the invention. The only one shows

Figur eine schematische Darstellung einer Brennkraftmaschine.Figure is a schematic representation of an internal combustion engine.

Die Figur zeigt eine schematische Darstellung einer Brennkraftmaschine 1, die in dem hier dargestellten Ausführungsbeispiel mehrere Zylinder 2 aufweist. Jeder der Zylinder 2 verfügt über wenigstens ein Einlassventil 3 und wenigstens ein Auslassventil 4. Über jedes der Einlassventile 3 kann dem jeweiligen Zylinder 2 Frischgas aus einem Frischgastrakt 5 zugeführt werden, wohingegen durch jedes der Auslassventile 4 Abgas aus dem entsprechenden Zylinder 2 entweichen kann, nämlich in Richtung eines Abgastrakts 6. Das Frischgas wird an den Einlassventilen 3 mittels eines Verdichters 7 bereitgestellt, welcher Teil eines Abgasturboladers 8 ist. Zusätzlich zu dem Verdichter 7 weist der Abgasturbolader 8 eine Turbine 9 auf, welche über eine Abgasleitung 10, die Bestandteil des Abgastrakts 6 ist, an die Auslassventile 4 strömungstechnisch angeschlossen ist. Stromabwärts der Turbine 9 kann eine Abgasreinigungseinrichtung 11 vorliegen, welche beispielsweise über wenigstens einen Katalysator verfügt.The figure shows a schematic representation of an internal combustion engine 1, which has several cylinders 2 in the exemplary embodiment shown here. Each of the cylinders 2 has at least one inlet valve 3 and at least one outlet valve 4. Fresh gas from a fresh gas tract 5 can be supplied to the respective cylinder 2 via each of the inlet valves 3, whereas exhaust gas can escape from the corresponding cylinder 2 through each of the outlet valves 4, namely towards an exhaust tract 6. The fresh gas is provided at the inlet valves 3 by means of a compressor 7, which is part of an exhaust gas turbocharger 8. In addition to the compressor 7, the exhaust gas turbocharger 8 has a turbine 9, which is fluidly connected to the exhaust valves 4 via an exhaust line 10, which is part of the exhaust tract 6. Downstream of the turbine 9, an exhaust gas purification device 11 can be present, which has, for example, at least one catalytic converter.

Die Brennkraftmaschine 1 wird mittels eines Verfahrens betrieben, gemäß welchem während eines Arbeitsspiels der Brennkraftmaschine Frischluft in wenigstens einen der Zylinder 2, vorzugsweise in jeden der Zylinder 2, eingebracht wird. Das Einbringen der Frischluft in den Zylinder 2 beziehungsweise die Zylinder 2 erfolgt derart, dass ein bestimmter Sollliefergrad in dem jeweiligen Zylinder erzielt ist. Vor dem Einbringen des Frischgases beziehungsweise der Frischluft in dem jeweiligen Zylinder 2 wird der Sollliefergrad auf einen Maximalliefergrad begrenzt, nämlich nach oben. Das bedeutet, dass der Sollliefergrad stets kleiner oder gleich dem Maximalliefergrad ist.The internal combustion engine 1 is operated by means of a method according to which fresh air is introduced into at least one of the cylinders 2, preferably into each of the cylinders 2, during a working cycle of the internal combustion engine. The fresh air is introduced into the cylinder 2 or the cylinders 2 in such a way that a certain target delivery level is achieved in the respective cylinder. Before the fresh gas or fresh air is introduced into the respective cylinder 2, the target delivery ratio is limited to a maximum delivery ratio, namely upwards. This means that the target delivery ratio is always less than or equal to the maximum delivery ratio.

Der Maximalliefergrad wird bei einem Start der Brennkraftmaschine 1 auf einen ersten Vorgabewert gesetzt und nach dem Start der Brennkraftmaschine 1 in Richtung eines zweiten Vorgabewerts vergrößert. Auf diese Art und Weise wird der Sollliefergrad bei dem Start der Brennkraftmaschine, insbesondere während eines Aufwärmbetriebs der Brennkraftmaschine 1, auf kleinere Werte begrenzt als nach dem Erreichen einer Betriebstemperatur der Brennkraftmaschine durch eine Temperatur der Brennkraftmaschine. Entsprechend werden die Schadstoffemissionen der Brennkraftmaschine während des Warmlaufbetriebs deutlich reduziert.The maximum delivery ratio is set to a first default value when the internal combustion engine 1 starts and is increased in the direction of a second default value after the internal combustion engine 1 is started. In this way, the target delivery ratio when starting the internal combustion engine, in particular during a warm-up operation of the internal combustion engine 1, is limited to smaller values than after the internal combustion engine has reached an operating temperature due to a temperature of the internal combustion engine. Accordingly, the pollutant emissions from the internal combustion engine are significantly reduced during warm-up operation.

Claims (8)

  1. Method for operating an internal combustion engine (1), which comprises at least one cylinder (2) into which fresh air is introduced during an operating cycle of the internal combustion engine (1) in order to achieve a specific desired volumetric efficiency, wherein the desired volumetric efficiency is limited to a maximal volumetric efficiency, which is set to a first set value at a start of the internal combustion engine (1) and is increased in the direction of a second set value after the start of the internal combustion engine (1), and wherein the maximal volumetric efficiency is determined as a function of a temperature of the internal combustion engine (1), wherein the maximal volumetric efficiency is selected to be smaller at a lower temperature than at a higher temperature, characterized in that the maximal volumetric efficiency is increased in such a way that the maximal volumetric efficiency reaches the second set value when an operating temperature is reached, which is present during quasi-stationary operation of the internal combustion engine (1).
  2. The method according to claim 1, characterised in that a combustion chamber temperature of a combustion chamber of the cylinder (2) is used as the temperature of the internal combustion engine (1).
  3. Method according to one of the preceding claims, characterised in that an operating medium temperature of an operating medium of the internal combustion engine (1) is used as the temperature of the internal combustion engine (1).
  4. Method according to claim 3, characterised in that a coolant used for cooling of the internal combustion engine (1) or a lubricant used for lubrication of the internal combustion engine (1) is used as the operating medium.
  5. Method according to one of the preceding claims, characterized in that the maximal delivery rate is increased from the first set value towards the second set value as a function of the time elapsed since the start of the internal combustion engine (1).
  6. Method according to one of the preceding claims, characterised in that the second set value corresponds to a maximum volumetric efficiency of the internal combustion engine (1) under currently present ambient conditions.
  7. Method according to claim 6, characterized in that the maximum delivery rate is determined from the ambient conditions, wherein the maximal delivery rate is determined by subtracting a difference value from the maximum delivery rate, wherein the difference value is decreased in the direction of a second difference value starting from a first difference value present at the start of the internal combustion engine (1).
  8. Internal combustion engine (1) for carrying out the method according to one or more of the preceding claims, wherein the internal combustion engine (1) comprises at least one cylinder (2) into which fresh air is introduced during an operating cycle of the internal combustion engine (1) in order to achieve a specific desired volumetric efficiency, wherein internal combustion engine (1) is configured to limit the desired volumetric efficiency to a maximal volumetric efficiency, which is set to a first set value at a start of the internal combustion engine (1) and is increased in the direction of a second set value after the start of the internal combustion engine (1), and wherein the maximal volumetric efficiency is determined as a function of a temperature of the internal combustion engine (1), wherein the maximal volumetric efficiency is selected to be smaller at a lower temperature than at a higher temperature, characterized in that the maximal volumetric efficiency is increased in such a way that the maximal volumetric efficiency reaches the second set value when an operating temperature is reached, which is present during quasi-stationary operation of the internal combustion engine (1).
EP19724787.7A 2018-06-07 2019-05-14 Method for operating an internal combustion engine, and corresponding internal combustion engine Active EP3803086B1 (en)

Applications Claiming Priority (2)

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DE102018209080.7A DE102018209080B3 (en) 2018-06-07 2018-06-07 Method for operating an internal combustion engine and corresponding internal combustion engine
PCT/EP2019/062323 WO2019233714A1 (en) 2018-06-07 2019-05-14 Method for operating an internal combustion engine, and corresponding internal combustion engine

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CN111108282B (en) 2022-07-22
WO2019233714A1 (en) 2019-12-12
DE102018209080B3 (en) 2019-03-28
EP3803086A1 (en) 2021-04-14

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