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WO2019233714A1 - 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
WO2019233714A1
WO2019233714A1 PCT/EP2019/062323 EP2019062323W WO2019233714A1 WO 2019233714 A1 WO2019233714 A1 WO 2019233714A1 EP 2019062323 W EP2019062323 W EP 2019062323W WO 2019233714 A1 WO2019233714 A1 WO 2019233714A1
Authority
WO
WIPO (PCT)
Prior art keywords
internal combustion
combustion engine
temperature
delivery rate
maximum delivery
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/EP2019/062323
Other languages
German (de)
French (fr)
Inventor
Philipp Prochazka
Florian Freund
Tessen Keulertz
Michael Leihenseder
Christoph Schweitzer
Jürgen TRÜMPER
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.)
Audi AG
Original Assignee
Audi 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 Audi AG filed Critical Audi AG
Priority to CN201980004619.0A priority Critical patent/CN111108282B/en
Priority to EP19724787.7A priority patent/EP3803086B1/en
Publication of WO2019233714A1 publication Critical patent/WO2019233714A1/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
    • F02D41/02—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 having at least one cylinder by fresh air is introduced during a cycle of the internal combustion engine to achieve a certain Solldauer- degree.
  • the invention further relates to an internal combustion engine.
  • the internal combustion engine has at least one combustion chamber, a suction tube, a compressor for generating a charge with a charge density in the intake manifold and a device for changing a delivery level of the charge from the intake manifold into the at least one combustion chamber.
  • a part of the charge is transferred from the intake manifold into the at least one combustion chamber with a delivery rate, wherein the delivery rate is set as a function of the charge density.
  • the degree of delivery is determined and set as a function of the air pressure prevailing in an environment of the internal combustion engine.
  • document WO 2009/065541 A1 shows a method for regulating a stationary gas engine, in which a speed control deviation is calculated from a setpoint speed and an actual speed, from the speed control deviation via a speed controller as a manipulated variable a target torque is determined which is limited to an air ratio limiting torque via a torque limitation, and at from the limited target torque, a target volume flow for determining a mixture throttle angle and a throttle throttle angle is determined.
  • the object of the invention is to propose a method for operating an internal combustion engine which has advantages over known methods, in particular allows operation of the internal combustion engine with low emissions, preferably during a warm-up operation of the internal combustion engine.
  • the desired delivery rate is limited to a maximum delivery rate, which is set to a first default value when the internal combustion engine is started and increased in the direction of a second default value after the engine has started.
  • the described method is used to operate the internal combustion engine.
  • the internal combustion engine preferably serves to drive a motor vehicle, that is to say to provide a torque directed to the driving of 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 is discussed. However, the embodiments are always transferable to the multiple cylinders of the internal combustion engine, if present, namely to each of the several cylinders. If there are several cylinders, the described method can therefore be implemented for each of the several cylinders.
  • fresh gas is introduced into the cylinder, which consists entirely of fresh air or at least fresh air.
  • the fresh gas from the fresh air and exhaust gas is composed, namely, if an exhaust gas recirculation is performed.
  • the working cycle is composed of an intake stroke, a compression stroke, a power stroke and an exhaust stroke.
  • the introduction of the fresh gas or the fresh air is usually carried out during the intake stroke.
  • the introduction of the fresh air takes place such that after introduction into the cylinder there is a fresh air mass which corresponds to the desired delivery rate.
  • 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 intake, that is to say without negative pressure in the cylinder.
  • the theoretically possible fresh air mass is determined on the basis of 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 desired delivery ratio or the target delivery rate is set on the internal combustion engine.
  • the Solllie fergrad is set, for example, first to a Vorgabearrigrad that results from a specification of a driver of the motor vehicle and / or a rerassististenz Rhein the motor vehicle.
  • the Vorgabearrigrad is determined from a default torque and / or based on an accelerator pedal position.
  • the target delivery level is limited to the maximum delivery, in particular upwards, ie in the direction of larger values.
  • the target delivery rate thus corresponds to the maximum delivery rate or is smaller than this.
  • the maximum delivery rate is initially set to the first default value and increased after the start of the internal combustion engine in the direction of the second preset value.
  • the second default value is greater than the first default value, so that at the start of the internal combustion engine initially a smaller maximum delivery rate exists.
  • the maximum delivery rate is increased, namely in the direction of the second default value.
  • the maximum delivery rate is increased such that the maximum delivery rate reaches the second preset value when the operating temperature is reached by the temperature of the internal combustion engine.
  • Increasing the maximum delivery rate starting from the first default value in the direction of the second default value, in particular to the second default value, can in principle take place according to any desired course.
  • the progression is linear, so increasing the maximum delivery rate as a function of a reference variable is linear.
  • a reference for example, a temperature or the time is used.
  • the desired delivery rate is a measure of the torque generated by the internal combustion engine or the power output by the internal combustion engine
  • a default torque is preferably first determined, for example, from a specification of a driver of a motor vehicle to whose drive the internal combustion engine is used, or based on the specification of a driver assistance device.
  • the default torque corresponds to that of the driver or the driver. rerassistenz Huawei desired torque.
  • a setpoint torque is determined from the default torque and adjusted at the internal combustion engine.
  • the internal combustion engine is operated such that it provides the target torque.
  • the setpoint torque from the default torque
  • a limitation to the maximum torque that can be provided above is now carried out. In other words, it is provided at the start of the internal combustion engine to limit the target torque to a smaller torque than in terms of time after starting.
  • the internal combustion engine is preferably a spark-ignited internal combustion engine, that is to say in particular an Otto internal combustion engine.
  • the maximum delivery rate In addition to setting the maximum delivery rate to the first default value at the start of the internal combustion engine and its subsequent enlargement in the direction of the second default value, it may be provided to limit the engine speed to a maximum speed, the maximum speed at the start of the engine Internal combustion engine is set to a first speed value and increased after the start of the internal combustion engine in the direction of a second speed value.
  • the second rotational speed value preferably corresponds to a maximum permissible rotational speed of the internal combustion engine, which may be present during normal operation of the internal combustion engine after reaching the operating temperature, without damage to the internal combustion engine occurring or to be expected.
  • a further embodiment of the invention provides that the maximum delivery rate is determined as a function of a temperature of the internal combustion engine, the maximum delivery rate being selected to be smaller at a lower temperature than at a higher temperature.
  • the maximum delivery rate is insofar as a function of the temperature of the internal combustion engine, wherein the function has the temperature as an input variable and the maximum delivery as the 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, that is to say the temperature of a fluid present in the combustion chamber.
  • the determination of the combustion chamber temperature can be effected, for example, by measuring by means of a sensor, in particular a sensor arranged in the combustion chamber, or by estimation.
  • 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 which occur during operation of the internal combustion engine.
  • the lower the combustion chamber temperature the higher the pollutant emissions.
  • it is particularly advantageous to use the combustion chamber temperature for determining the maximum delivery rate because thus a particularly significant reduction in pollutant emissions is achieved.
  • the temperature of the internal combustion engine used is an operating medium temperature of an operating medium of the internal combustion engine. Determining the combustion chamber temperature may be expensive. For this reason, it may be envisaged to use the operating medium temperature instead of the combustion chamber temperature.
  • the temperature of the operating medium of the internal combustion engine is to be understood as the temperature of the operating medium.
  • the operating medium temperature of the combustion chamber temperature runs after, so that also on the basis of the operating medium temperature, an adjustment of the maximum degree or the desired degree of delivery can be carried out in such a way that there is a significant reduction of the pollutant emissions.
  • a cooling of the internal combustion engine, the nendes coolant or a lubrication of the engine, the nendes lubricant is used as operating means a cooling of the internal combustion engine, the nendes coolant or a lubrication of the engine, the nendes lubricant.
  • the equipment is in this respect as a coolant or as a lubricant.
  • the temperatures of both the coolant and the lubricant are comparatively easily determinable and are usually measured in each case.
  • Both the temperature of the coolant and the temperature of the lubricant usually follow the combustion chamber temperature or are related to it. Increasing the combustion chamber temperature over a certain period of time usually also results in an increase in the operating medium temperature, that is to say the temperature of the coolant or of the 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 rate such that there is a significant reduction in pollutant emissions.
  • a further preferred embodiment of the invention provides that the maximum delivery rate starting from the first default value in dependence on the elapsed since the start of the internal combustion engine time in the direction of the second default value is increased.
  • the target delivery rate should therefore be determined as a function of time, namely the time elapsed since the start of the internal combustion engine. If the maximum delivery rate is determined exclusively as a function of time, this is possible with very little effort. For example, the progression of the maximum delivery rate over time is selected such that the maximum delivery rate reaches the second setpoint value exactly or only when the temperature of the internal combustion engine corresponds to its operating temperature during proper operation of the internal combustion engine.
  • the maximum delivery rate as a function of both the temperature and the time, so that the maximum delivery rate as a function of the temperature and the time is available.
  • the function has as input variables the temperature and the time and as output variable the maximum delivery rate. This represents a particularly advantageous procedure in determining the maximum level of delivery.
  • a further embodiment of the invention provides that the maximum delivery level is set by the temperature to the second preset value upon reaching an operating temperature.
  • the operating temperature is that temperature of the internal combustion engine to understand, which has this in the context of a quasi-stationary operation.
  • the internal combustion engine is thus operated such that the operating temperature is present.
  • the internal combustion engine is cooled such that the temperature of the internal combustion engine corresponds to the operating temperature.
  • a further embodiment of the invention provides that the second preset value corresponds to a max. len delivery level of the internal combustion engine corresponds.
  • the maximum delivery rate corresponds to the degree of delivery which was present at maximum power or rated power of the internal combustion engine under the current ambient conditions.
  • the maximum delivery rate is, for example, as a function of the ambient conditions, in particular as a function of the ambient pressure and / or the ambient temperature. Such a procedure ensures that the maximum torque or the maximum power can be called up when the internal combustion engine is at operating temperature.
  • the maximum delivery level is determined from the ambient conditions, wherein the maximum delivery rate is determined by subtracting a difference value from the maximum delivery rate, the differential value starting from a at the start of the internal combustion engine present first difference value in the direction of a second difference value is reduced.
  • the maximum delivery rate is determined from the ambient conditions.
  • the maximum delivery rate is determined based on the maximum delivery grade less the difference. The maximum delivery rate is thus at most as large as the maximum delivery level, namely when the difference value is equal to zero. If the difference value is different from zero, then the maximum delivery rate is different from the maximum delivery rate, in particular it is smaller than this.
  • the difference value which is used in determining the maximum delivery rate, is initially set to the first difference value when the internal combustion engine is started. After the start of 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 reaching the second difference value by the difference value, the maximum delivery rate corresponds to the maximum delivery rate.
  • the procedure described with reference to the differential value is a special embodiment of the procedure described, according to which the target delivery rate is limited to the maximum delivery rate is set at the start of the internal combustion engine to the first default value and increased after the start of the internal combustion engine in the direction of the second preset value. 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 embodiments in the context of 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 to achieve a specific target delivery level. It is provided that the internal combustion engine is designed to limit the target delivery to a maximum delivery, which is set at a start of the internal combustion engine to a first default value and increased after the start of the internal combustion engine in the direction of a second default value.
  • Figure 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 embodiment shown here.
  • Each of the cylinders 2 has at least one inlet valve 3 and at least one outlet valve 4. Via each of the inlet valves 3, fresh gas can be supplied to the respective cylinder 2 from a fresh gas tract 5, whereas exhaust gas from each of the outlet valves 4 is exhausted.
  • the exhaust gas is supplied to the intake 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 connected via an exhaust pipe 10, which is part of the exhaust gas tract 6, to the outlet valves 4 in terms of flow technology.
  • Downstream of the turbine 9 may be an exhaust gas purification device 11, 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 introduction of the fresh air into the cylinder 2 or the cylinder 2 takes place in such a way that a certain target delivery rate is achieved in the respective cylinder.
  • the desired delivery rate is limited to a maximum delivery rate, namely upwards. This means that the target delivery level is always less than or equal to the maximum delivery rate.
  • the maximum delivery rate is set at a start of the internal combustion engine 1 to a first default value and increased after the start of the internal combustion engine 1 in the direction of a second default value.
  • the desired delivery rate at the start of the internal combustion engine, in particular during a warm-up operation of the internal combustion engine 1 is limited to smaller values than after reaching an operating temperature of the internal combustion engine by a temperature of the internal combustion engine. Accordingly, the pollutant emissions of the internal combustion engine during warm-up operation are significantly reduced.

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

Abstract

The invention relates to a method for operating an internal combustion engine (1), which has at least one cylinder (2) into which fresh air is introduced during a working cycle of the internal combustion engine (1) in order to achieve a particular setpoint volumetric efficiency. Provision is made here for the setpoint volumetric efficiency to be limited to a maximum volumetric efficiency, which is set to a first preset value upon starting of the internal combustion engine (1) and is increased in the direction of a second preset value after the starting of the internal combustion engine (1). The invention furthermore relates to an internal combustion engine (1).

Description

Verfahren zum Betreiben einer Brennkraftmaschine  Method for operating an internal combustion engine

sowie entsprechende Brennkraftmaschine  as well as corresponding internal combustion engine

BESCHREIBUNG: 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 Sollliefer- grads eingebracht wird. Die Erfindung betrifft weiterhin eine Brennkraftma- schine. The invention relates to a method for operating an internal combustion engine having at least one cylinder by fresh air is introduced during a cycle of the internal combustion engine to achieve a certain Solldauer- degree. The invention further relates to an internal combustion engine.

Aus dem Stand der Technik ist beispielsweise die Druckschrift DE 10 2012 024 318 A1 bekannt. Diese beschreibt ein Verfahren zum Betreiben einer Brennkraftmaschine. Die Brennkraftmaschine weist wenigstens einen Brenn- raum, ein Saugrohr, einen Verdichter zum Erzeugen einer Ladung mit einer Ladungsdichte im Saugrohr und eine Vorrichtung zur Veränderung eines Lie- fergrades 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 herr- schenden Luftdrucks bestimmt und eingestellt. From the prior art, for example, the document DE 10 2012 024 318 A1 is known. This describes a method for operating an internal combustion engine. The internal combustion engine has at least one combustion chamber, a suction tube, a compressor for generating a charge with a charge density in the intake manifold and a device for changing a delivery level of the charge from the intake manifold into the at least one combustion chamber. According to the method, a part of the charge is transferred from the intake manifold into the at least one combustion chamber with a delivery rate, wherein the delivery rate is set as a function of the charge density. The degree of delivery is determined and set as a function of the air pressure prevailing in an environment of the internal combustion engine.

Weiterhin zeigt die Druckschrift WO 2009/065541 A1 ein Verfahren zur Re- gelung eines stationären Gasmotors, bei dem eine Drehzahl- Regelabweichung aus einer Soll-Drehzahl sowie einer Ist-Drehzahl berech- net wird, aus der Drehzahl-Regelabweichung über einen Drehzahlregler als Stellgröße ein Soll-Moment bestimmt wird, welches über eine Momentbe- grenzung auf ein Luftverhältnis-Begrenzungsmoment begrenzt wird, und bei dem aus dem begrenzten Soll-Moment ein Soll-Volumenstrom zur Festle- gung eines Gemisch-Drosselklappenwinkels sowie eines Gas- Drosselklappenwinkel bestimmt wird. Furthermore, document WO 2009/065541 A1 shows a method for regulating a stationary gas engine, in which a speed control deviation is calculated from a setpoint speed and an actual speed, from the speed control deviation via a speed controller as a manipulated variable a target torque is determined which is limited to an air ratio limiting torque via a torque limitation, and at from the limited target torque, a target volume flow for determining a mixture throttle angle and a throttle throttle angle is determined.

Weiterhin zeigen die Druckschriften DE 10 2005 044 399 A1 , DE 10 2017 112 690 A1 , DE 10 2013 202 720 A1 und DE 197 58 641 B4 weitere Brenn- kraftmaschinen sowie Verfahren zu ihrem Betreiben. Furthermore, the documents DE 10 2005 044 399 A1, DE 10 2017 112 690 A1, DE 10 2013 202 720 A1 and DE 197 58 641 B4 show further internal combustion engines and methods for their operation.

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

Dies wird erfindungsgemäß mit einem Verfahren zum Betreiben einer Brenn- kraftmaschine mit den Merkmalen des Anspruchs 1 erreicht. Dabei ist vorge- sehen, dass der Sollliefergrad auf einen Maximalliefergrad begrenzt wird, der bei einem Start der Brennkraftmaschine auf einen ersten Vorgabewert ge- setzt und nach dem Start der Brennkraftmaschine in Richtung eines zweiten Vorgabewerts vergrößert wird. This is achieved according to the invention with a method for operating an internal combustion engine having the features of claim 1. It is provided that the desired delivery rate is limited to a maximum delivery rate, which is set to a first default value when the internal combustion engine is started and increased in the direction of a second default value after the engine has started.

Das beschriebene Verfahren dient dem Betreiben der Brennkraftmaschine. Die Brennkraftmaschine dient vorzugsweise dem Antreiben eines Kraftfahr- zeugs, also dem Bereitstellen eines auf das Antreiben des Kraftfahrzeugs gerichteten Drehmoments. Die Brennkraftmaschine verfügt über den wenigs- tens einen Zylinder, vorzugsweise jedoch über mehrere Zylinder. Im Rahmen dieser Beschreibung wird lediglich auf den wenigstens einen Zylinder bezie- hungsweise das diesen betreffende Vorgehen eingegangen. Die Ausführun- gen 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. 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 üblicher weise während des Ansaugtakts. Das Einbringen der Frischluft erfolgt derart, dass nach dem Einbringen in dem Zylinder eine Frischluftmasse vorliegt, welche dem Sollliefergrad entspricht. The described method is used to operate the internal combustion engine. The internal combustion engine preferably serves to drive a motor vehicle, that is to say to provide a torque directed to the driving of 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 is discussed. However, the embodiments are always transferable to the multiple cylinders of the internal combustion engine, if present, namely to each of the several cylinders. If there are several cylinders, the described method can therefore be implemented for each of the several cylinders. During each cycle of the internal combustion engine fresh gas is introduced into the cylinder, which consists entirely of fresh air or at least fresh air. For example, the fresh gas from the fresh air and exhaust gas is composed, namely, if an exhaust gas recirculation is performed. The working cycle is composed of an intake stroke, a compression stroke, a power stroke and an exhaust stroke. The introduction of the fresh gas or the fresh air is usually carried out during the intake stroke. The introduction of the fresh air takes place such that after introduction into the cylinder there is a fresh air mass which corresponds to the desired delivery rate.

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 Unter- druck in dem Zylinder, erzielbar ist. Die theoretisch mögliche Frischluftmasse wird anhand eines Umgebungsdrucks und einer Umgebungstemperatur er- mittelt, welche außerhalb der Brennkraftmaschine vorliegen. Der Umge- bungsdruck 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 intake, that is to say without negative pressure in the cylinder. The theoretically possible fresh air mass is determined on the basis of 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 beziehungs- weise der Sollliefergrad an der Brennkraftmaschine eingestellt. Der Solllie fergrad wird beispielsweise zunächst auf einen Vorgabeliefergrad gesetzt, der aus einer Vorgabe eines Fahrers des Kraftfahrzeugs und/oder einer Fah- rerassistenzeinrichtung 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 die- ser. The internal combustion engine is operated with the desired delivery ratio or the target delivery rate is set on the internal combustion engine. The Solllie fergrad is set, for example, first to a Vorgabeliefergrad that results from a specification of a driver of the motor vehicle and / or a rerassististenzeinrichtung the motor vehicle. For example, the Vorgabeliefergrad is determined from a default torque and / or based on an accelerator pedal position. During or after setting the target delivery level to the Vorgabeliefergrad the target delivery level is limited to the maximum delivery, in particular upwards, ie in the direction of larger values. The target delivery rate thus corresponds to the maximum delivery rate or is smaller than this.

Weist die Brennkraftmaschine eine Temperatur auf, welche kleiner ist als ihre Betriebstemperatur, und soll gleichzeitig ein hoher Sollliefergrad vorlie- gen, 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 Vorga- bewert 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 Brennkraftma- schine zunächst ein kleinerer Maximalliefergrad vorliegt. If the internal combustion engine has a temperature which is lower than its operating temperature, and at the same time a high desired delivery rate should be present. conditions, the pollutant emissions of the internal combustion engine increase drastically. For this reason, it is provided that at the start of the internal combustion engine, the maximum delivery rate is initially set to the first default value and increased after the start of the internal combustion engine in the direction of the second preset value. Here, the second default value is greater than the first default value, so that at the start of the internal combustion engine initially a smaller maximum delivery rate exists.

Nach dem Start der Brennkraftmaschine wird der Maximalliefergrad vergrö- ßert, nämlich in Richtung des zweiten Vorgabewerts. Beispielsweise erfolgt das Erhöhen des Maximalliefergrad derart, dass der Maximalliefergrad mit dem Erreichen der Betriebstemperatur durch die Temperatur der Brenn- kraftmaschine den zweiten Vorgabewert erreicht. Das Erhöhen des Maximal- liefergrad ausgehend von dem ersten Vorgabewert in Richtung des zweiten Vorgabewerts, insbesondere bis auf den zweiten Vorgabewert, kann grund- sätzlich gemäß einem beliebigen Verlauf erfolgen. Beispielsweise ist der Ver- lauf linear, sodass das Erhöhen des Maximalliefergrad in Abhängigkeit von einer Bezugsgröße linear erfolgt. Als Bezugsgröße wird beispielsweise eine Temperatur oder die Zeit herangezogen. After starting the internal combustion engine, the maximum delivery rate is increased, namely in the direction of the second default value. By way of example, the maximum delivery rate is increased such that the maximum delivery rate reaches the second preset value when the operating temperature is reached by the temperature of the internal combustion engine. Increasing the maximum delivery rate starting from the first default value in the direction of the second default value, in particular to the second default value, can in principle take place according to any desired course. For example, the progression is linear, so increasing the maximum delivery rate as a function of a reference variable is linear. As a reference, for example, a temperature or the time is used.

Weil der Sollliefergrad ein Maß für das mittels der Brennkraftmaschine er- zeugte Drehmoment beziehungsweise die von der Brennkraftmaschine ab- gegebene 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 Vorgabedreh- moments zu vergrößern, wobei das zweite Vorgabedrehmoment größer ist als das erste Vorgabedrehmoment. Because the desired delivery rate is a measure of the torque generated by the internal combustion engine or the power output by the internal combustion engine, it is also possible in principle to set the maximum torque that can be generated by the internal combustion engine at the start of the internal combustion engine to a first default torque and after the start of the internal combustion engine in the direction of a second preset torque to increase, wherein the second predetermined torque is greater than the first predetermined torque.

Für das Betreiben der Brennkraftmaschine wird vorzugsweise zunächst ein Vorgabedrehmoment ermittelt, beispielsweise aus einer Vorgabe eines Fah- rers eines Kraftfahrzeugs, zu dessen Antrieb die Brennkraftmaschine dient, oder anhand der Vorgabe einer Fahrerassistenzeinrichtung. Das Vorga- bedrehmoment entspricht dem von dem Fahrer beziehungsweise der Fah- rerassistenzeinrichtung gewünschten Drehmoment. Anschließend wird aus dem Vorgabedrehmoment ein Solldrehmoment ermittelt und an der Brenn- kraftmaschine eingestellt. For the operation of the internal combustion engine, a default torque is preferably first determined, for example, from a specification of a driver of a motor vehicle to whose drive the internal combustion engine is used, or based on the specification of a driver assistance device. The default torque corresponds to that of the driver or the driver. rerassistenzeinrichtung desired torque. Subsequently, a setpoint torque is determined from the default torque and adjusted at 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 Star- ten. Subsequently, the internal combustion engine is operated such that it provides the target torque. When determining the setpoint torque from the default torque, a limitation to the maximum torque that can be provided above is now carried out. In other words, it is provided at the start of the internal combustion engine 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 er- zeugbaren Drehmoments bei dem Start der Brennkraftmaschine. Als Brenn- kraftmaschine kommt vorzugsweise eine fremdgezündete Brenn kraftmaschi- ne, also insbesondere eine Otto-Brennkraftmaschine zum Einsatz. With the procedure described, the pollutant emissions of the internal combustion engine, which occur at the start or after the start of the internal combustion engine can be significantly reduced, namely by reducing the maximum delivery or the maximum producible torque at the start of the internal combustion engine. The internal combustion engine is preferably a spark-ignited internal combustion engine, that is to say in particular an Otto internal combustion engine.

Zusätzlich zu dem Setzen des Maximalliefergrads auf den ersten Vorgabe- wert bei dem Start der Brennkraftmaschine und seinem nachfolgenden Ver- größern 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 Dreh- zahlwert entspricht vorzugsweise einer maximal zulässigen Drehzahl der Brennkraftmaschine, welche bei bestimmungsgemäßen Betrieb der Brenn- kraftmaschine nach Erreichen der Betriebstemperatur vorliegen darf, ohne dass Beschädigungen der Brennkraftmaschine auftreten beziehungsweise zu erwarten sind. Eine weitere Ausgestaltung der Erfindung sieht vor, dass der Maximal liefer- grad 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 Maximal- liefergrad 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 Umgebungs- bedingungen der Brennkraftmaschine erfolgt, sodass eine besonders deutli- che Reduzierung der Schadstoffemissionen erzielt wird. In addition to setting the maximum delivery rate to the first default value at the start of the internal combustion engine and its subsequent enlargement in the direction of the second default value, it may be provided to limit the engine speed to a maximum speed, the maximum speed at the start of the engine Internal combustion engine is set to a first speed value and increased after the start of the internal combustion engine in the direction of a second speed value. The second rotational speed value preferably corresponds to a maximum permissible rotational speed of the internal combustion engine, which may be present during normal operation of the internal combustion engine after reaching the operating temperature, without damage to the internal combustion engine occurring or to be expected. A further embodiment of the invention provides that the maximum delivery rate is determined as a function of a temperature of the internal combustion engine, the maximum delivery rate being selected to be smaller at a lower temperature than at a higher temperature. The maximum delivery rate is insofar as a function of the temperature of the internal combustion engine, wherein the function has the temperature as an input variable and the maximum delivery as the output variable. The function is chosen such that the maximum delivery rate is lower at the lower temperature 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 takes place, 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 Tempe- ratur eines in dem Brennraum vorliegenden Fluids. Das Ermitteln der Brenn- raumtemperatur kann beispielsweise durch Messen mittels eines Sensors, insbesondere eines in dem Brennraum angeordneten Sensors, oder durch Abschätzen erfolgen. Für das Abschätzen kommt beispielsweise ein Tempe- raturmodell zum Einsatz, welches die Brennraumtemperatur aus wenigstens einer anderen Größe, insbesondere einer gemessenen Temperatur, be- stimmt. 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, that is to say the temperature of a fluid present in the combustion chamber. The determination of the combustion chamber temperature can be effected, for example, by measuring by means of a sensor, in particular a sensor arranged in the combustion chamber, or by estimation. For 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 Schadstoffemis- sionen, 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 be- sonders deutliche Reduzierung der Schadstoffemissionen erzielt wird. Eine Weiterbildung der Erfindung sieht vor, dass als Temperatur der Brenn- kraftmaschine eine Betriebsmitteltemperatur eines Betriebsmittels der Brennkraftmaschine verwendet wird. Das Bestimmen der Brennraumtempe- ratur ist unter Umständen aufwendig. Aus diesem Grund kann es vorgese- hen 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 Maximall iefer- grads beziehungsweise des Sollliefergrads derart erfolgen kann, dass eine deutliche Reduzierung der Schadstoffemissionen vorliegt. The combustion chamber temperature is decisive for the amount of pollutant emissions which occur during operation of the internal combustion engine. Thus, the lower the combustion chamber temperature, the higher the pollutant emissions. For this reason, it is particularly advantageous to use the combustion chamber temperature for determining the maximum delivery rate, because thus a particularly significant reduction in pollutant emissions is achieved. A further development of the invention provides that the temperature of the internal combustion engine used is an operating medium temperature of an operating medium of the internal combustion engine. Determining the combustion chamber temperature may be expensive. For this reason, it may be envisaged to use the operating medium temperature instead of the combustion chamber temperature. The temperature of the operating medium of the internal combustion engine is to be understood as the temperature of the operating medium. Usually, the operating medium temperature of the combustion chamber temperature runs after, so that also on the basis of the operating medium temperature, an adjustment of the maximum degree or the desired degree of delivery can be carried out in such a way that there is a significant reduction of the pollutant emissions.

Im Rahmen einer weiteren Ausführungsform der Erfindung kann vorgesehen sein, dass als Betriebsmittel ein einer Kühlung der Brennkraftmaschine die nendes Kühlmittel oder ein einer Schmierung der Brennkraftmaschine die nendes Schmiermittel verwendet wird. Das Betriebsmittel liegt insoweit als Kühlmittel oder als Schmiermittel vor. Die Temperaturen sowohl des Kühlmit- tels als auch des Schmiermittels sind vergleichsweise einfach bestimmbar und werden üblicherweise jeweils gemessen. In the context of a further embodiment of the invention can be provided that is used as operating means a cooling of the internal combustion engine, the nendes coolant or a lubrication of the engine, the nendes lubricant. The equipment is in this respect as a coolant or as a lubricant. The temperatures of both the coolant and the lubricant are comparatively easily determinable and are usually measured in each case.

Sowohl die Temperatur des Kühlmittels als auch die Temperatur des Schmiermittels laufen üblicherweise der Brennraumtemperatur hinterher be- ziehungsweise stehen mit dieser in einem Zusammenhang. Aus einer Erhö- hung 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 Schmier- mittels 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 follow the combustion chamber temperature or are related to it. Increasing the combustion chamber temperature over a certain period of time usually also results in an increase in the operating medium temperature, that is to say the temperature of the coolant or of the 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 rate such 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 Ab- hängigkeit der Temperatur soll also der Solliefergrad in Abhängigkeit von der Zeit bestimmt werden, nämlich von der seit dem Start der Brenn kraftmaschi- ne verstrichenen Zeit. Wird der Maximalliefergrad ausschließlich in Abhän- gigkeit 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 Brenn kraftma- schine entspricht. A further preferred embodiment of the invention provides that the maximum delivery rate starting from the first default value in dependence on the elapsed since the start of the internal combustion engine time in the direction of the second default value is increased. Instead of or additionally as a function of the temperature, the target delivery rate should therefore be determined as a function of time, namely the time elapsed since the start of the internal combustion engine. If the maximum delivery rate is determined exclusively as a function of time, this is possible with very little effort. For example, the progression of the maximum delivery rate over time is selected such that the maximum delivery rate reaches the second setpoint value exactly or only when the temperature of the internal combustion engine corresponds to its operating temperature during proper operation of the internal combustion engine.

Selbstverständlich ist es auch möglich, den Maximalliefergrad in Abhängig- keit sowohl von der Temperatur als auch von der Zeit zu bestimmen, sodass also der Maximalliefergrad als Funktion von der Temperatur und der Zeit vor- liegt. In anderen Worten weist die Funktion als Eingangsgrößen die Tempe- ratur und die Zeit und als Ausgangsgröße den Maximalliefergrad auf. Dies stellt eine besonders vorteilhafte Vorgehensweise bei dem Ermitteln des Ma- ximalliefergrads 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 as a function of the temperature and the time is available. In other words, the function has as input variables the temperature and the time and as output variable the maximum delivery rate. This represents a particularly advantageous procedure in determining the maximum level of delivery.

Eine weitere Ausgestaltung der Erfindung sieht vor, dass der Maximal liefer- grad mit Erreichen einer Betriebstemperatur durch die Temperatur auf den zweiten Vorgabewert gesetzt wird. 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. Durch das Setzen des Maximalliefergrads auf den zweiten Vorgabewert, sobald die Temperatur die Betriebstemperatur erreicht, wird sichergestellt, dass bei betriebswarmer Brennkraftmaschine das maximale Drehmoment beziehungsweise die maxi- male Leistung der Brennkraftmaschine abrufbar ist. A further embodiment of the invention provides that the maximum delivery level is set by the temperature to the second preset value upon reaching an operating temperature. Under the operating temperature is that temperature of the internal combustion engine to understand, which has this in the context of a quasi-stationary operation. The internal combustion engine is thus operated such that the operating temperature is present. In particular, the internal combustion engine is cooled such that the temperature of the internal combustion engine corresponds to the operating temperature. By setting the maximum delivery rate to the second preset value, as soon as the temperature reaches the operating temperature, it is ensured 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 Vor- gabewert einem bei aktuell vorliegenden Umgebungsbedingungen maxima- len Liefergrad der Brennkraftmaschine entspricht. Der maximale Liefergrad entspricht demjenigen Liefergrad, welcher bei maximaler Leistung bezie- hungsweise bei Nennleistung der Brennkraftmaschine unter den momenta- nen Umgebungsbedingungen vorläge. Der maximale Liefergrad liegt bei- spielsweise 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 maxi- male Leistung abrufbar ist. A further embodiment of the invention provides that the second preset value corresponds to a max. len delivery level of the internal combustion engine corresponds. The maximum delivery rate corresponds to the degree of delivery which was present at maximum power or rated power of the internal combustion engine under the current ambient conditions. The maximum delivery rate is, for example, as a function of the ambient conditions, in particular as a function of the ambient pressure and / or the ambient temperature. Such a procedure ensures that the maximum torque or the 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 Lie fergrad ermittelt wird, wobei der Maximalliefergrad durch Subtraktion eines Differenzwerts von dem maximalen Liefergrad bestimmt wird, wobei der Dif- ferenzwert ausgehend von einem bei dem Start der Brennkraftmaschine vor- I legenden ersten Differenzwert in Richtung eines zweiten Differenzwerts ver- kleinert wird. Zunächst wird also der maximale Liefergrad aus den Umge- bungsbedingungen bestimmt. Anschließend wird der Maximalliefergrad fest- gelegt, wobei er sich aus dem maximalen Liefergrad abzüglich des Diffe- renzwerts 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, it can be provided within the scope of a further embodiment of the invention that the maximum delivery level is determined from the ambient conditions, wherein the maximum delivery rate is determined by subtracting a difference value from the maximum delivery rate, the differential value starting from a at the start of the internal combustion engine present first difference value in the direction of a second difference value is reduced. First of all, the maximum delivery rate is determined from the ambient conditions. Subsequently, the maximum delivery rate is determined based on the maximum delivery grade less the difference. The maximum delivery rate is thus at most as large as the maximum delivery level, namely when the difference value is equal to zero. If the difference value is different from zero, then the maximum delivery rate is different from the maximum delivery rate, in particular it is smaller than this.

Der Differenzwert, der bei dem Bestimmen des Maximalliefergrads herange- zogen 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 ent- spricht. Die beschriebene Vorgehensweise unter Heranziehung des Diffe- renzwerts ist eine spezielle Ausgestaltung der beschriebenen Vorgehens- weise, 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 herangezo- gen werden. The difference value, which is used in determining the maximum delivery rate, is initially set to the first difference value when the internal combustion engine is started. After the start of 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 reaching the second difference value by the difference value, the maximum delivery rate corresponds to the maximum delivery rate. The procedure described with reference to the differential value is a special embodiment of the procedure described, according to which the target delivery rate is limited to the maximum delivery rate is set at the start of the internal combustion engine to the first default value and increased after the start of the internal combustion engine in the direction of the second preset value. However, it can also be used as an alternative.

Die Erfindung betrifft weiterhin eine Brennkraftmaschine, insbesondere eine Brennkraftmaschine zur Durchführung des Verfahrens gemäß den Ausfüh- rungen im Rahmen dieser Beschreibung, wobei die Brennkraftmaschine we- nigstens 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 zwei- ten 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 embodiments in the context of 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 to achieve a specific target delivery level. It is provided that the internal combustion engine is designed to limit the target delivery to a maximum delivery, which is set at a start of the internal combustion engine to a first default value and increased after the start of the internal combustion engine in the direction of a second default value.

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

Die Erfindung wird nachfolgend anhand der in der Zeichnung dargestellten Ausführungsbeispiele näher erläutert, ohne dass eine Beschränkung der Er- findung erfolgt. Dabei zeigt die einzige The invention will be explained in more detail with reference to the embodiments illustrated in the drawings, without any limitation of the invention takes place. The only one shows

Figur eine schematische Darstellung einer Brennkraftmaschine. Figure 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 auf- weist. 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 wer- den, wohingegen durch jedes der Auslassventile 4 Abgas aus dem entspre- chenden 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 Auslass- ventile 4 strömungstechnisch angeschlossen ist. Stromabwärts der Turbine 9 kann eine Abgasreinigungseinrichtung 11 vorliegen, welche beispielsweise über wenigstens einen Katalysator verfügt. 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, ein- gebracht wird. Das Einbringen der Frischluft in den Zylinder 2 beziehungs- weise die Zylinder 2 erfolgt derart, dass ein bestimmter Sollliefergrad in dem jeweiligen Zylinder erzielt ist. Vor dem Einbringen des Frischgases bezie- hungsweise 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. Der Maximalliefergrad wird bei einem Start der Brennkraftmaschine 1 auf einen ersten Vorgabewert gesetzt und nach dem Start der Brenn kraftma- schine 1 in Richtung eines zweiten Vorgabewerts vergrößert. Auf diese Art und Weise wird der Sollliefergrad bei dem Start der Brennkraftmaschine, ins- besondere 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 figure shows a schematic representation of an internal combustion engine 1, which has several cylinders 2 in the embodiment shown here. Each of the cylinders 2 has at least one inlet valve 3 and at least one outlet valve 4. Via each of the inlet valves 3, fresh gas can be supplied to the respective cylinder 2 from a fresh gas tract 5, whereas exhaust gas from each of the outlet valves 4 is exhausted. The exhaust gas is supplied to the intake 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 connected via an exhaust pipe 10, which is part of the exhaust gas tract 6, to the outlet valves 4 in terms of flow technology. Downstream of the turbine 9 may be an exhaust gas purification device 11, 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 introduction of the fresh air into the cylinder 2 or the cylinder 2 takes place in such a way that a certain target delivery rate is achieved in the respective cylinder. Before introduction of the fresh gas or the fresh air in the respective cylinder 2, the desired delivery rate is limited to a maximum delivery rate, namely upwards. This means that the target delivery level is always less than or equal to the maximum delivery rate. The maximum delivery rate is set at a start of the internal combustion engine 1 to a first default value and increased after the start of the internal combustion engine 1 in the direction of a second default value. In this way, the desired delivery rate at the start of the internal combustion engine, in particular during a warm-up operation of the internal combustion engine 1, is limited to smaller values than after reaching an operating temperature of the internal combustion engine by a temperature of the internal combustion engine. Accordingly, the pollutant emissions of the internal combustion engine during warm-up operation are significantly reduced.

Claims

PATENTANSPRÜCHE: CLAIMS: 1. Verfahren zum Betreiben einer Brennkraftmaschine (1 ), die wenigstens einen Zylinder (2) aufweist, in den während eines Arbeitsspiels der Brennkraftmaschine (1 ) Frischluft zum Erzielen eines bestimmten Soll- liefergrads eingebracht wird, dadurch gekennzeichnet, dass der Soll- liefergrad auf einen Maximalliefergrad begrenzt wird, der bei einem Start der Brennkraftmaschine (1 ) auf einen ersten Vorgabewert gesetzt und nach dem Start der Brennkraftmaschine (1 ) in Richtung eines zwei- ten Vorgabewerts vergrößert wird. 1. A method for operating an internal combustion engine (1), which has at least one cylinder (2) into which during a cycle of the internal combustion engine (1) fresh air is introduced to achieve a certain target delivery level, characterized in that the target delivery level a maximum delivery rate is limited, which is set at a start of the internal combustion engine (1) to a first default value and after the start of the internal combustion engine (1) in the direction of a second default value is increased. 2. Verfahren nach Anspruch 1 , dadurch gekennzeichnet, dass der Ma- ximalliefergrad in Abhängigkeit von einer Temperatur der Brennkraft- maschine (1 ) bestimmt wird, wobei der Maximalliefergrad bei einer niedrigeren Temperatur kleiner gewählt wird als bei einer höheren2. Method according to claim 1, characterized in that the maximum delivery rate is determined as a function of a temperature of the internal combustion engine (1), wherein the maximum delivery rate is selected smaller at a lower temperature than at a higher one Temperatur. Temperature. 3. Verfahren nach Anspruch 2, dadurch gekennzeichnet, dass als Tem- peratur der Brennkraftmaschine (1 ) eine Brennraumtemperatur eines Brennraums des Zylinders (2) verwendet wird. 3. The method according to claim 2, characterized in that as the temperature of the internal combustion engine (1) a combustion chamber temperature of a combustion chamber of the cylinder (2) is used. 4. Verfahren nach Anspruch 2, dadurch gekennzeichnet, dass als Tem- peratur der Brennkraftmaschine (1 ) eine Betriebsmitteltemperatur eines Betriebsmittels der Brennkraftmaschine (1 ) verwendet wird. 4. The method according to claim 2, characterized in that the temperature of an internal combustion engine (1) is used as the temperature of the internal combustion engine (1). 5. Verfahren nach Anspruch 4, dadurch gekennzeichnet, dass als Be- triebsmittel ein einer Kühlung der Brennkraftmaschine (1 ) dienendes Kühlmittel oder ein einer Schmierung der Brennkraftmaschine (1 ) die nendes Schmiermittel verwendet wird. 5. The method according to claim 4, characterized in that as an operating means for cooling the internal combustion engine (1) serving coolant or a lubrication of the internal combustion engine (1) the nendes lubricant is used. 6. Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Maximalliefergrad ausgehend von dem ersten Vorgabewert in Abhängigkeit von der seit dem Start der Brenn kraftma- schine (1 ) verstrichenen Zeit in Richtung des zweiten Vorgabewerts vergrößert wird. 6. The method according to any one of the preceding claims, characterized in that the maximum delivery rate, starting from the first default value in dependence on the since the start of the combustion kraftma- (1) elapsed time is increased in the direction of the second default value. 7. Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Maximalliefergrad mit Erreichen einer Betriebs- temperatur durch die Temperatur auf den zweiten Vorgabewert gesetzt wird. 7. The method according to any one of the preceding claims, characterized in that the maximum delivery rate is set with reaching an operating temperature by the temperature to the second preset value. 8. Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der zweite Vorgabewert einem bei aktuell vorlie- genden Umgebungsbedingungen maximalen Liefergrad der Brenn- kraftmaschine (1 ) entspricht. 8. The method according to any one of the preceding claims, characterized in that the second predetermined value corresponds to a present at maximum present environmental conditions maximum delivery of the internal combustion engine (1). 9. Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, 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 (1 ) vorliegenden ersten Differenzwert in Richtung eines zweiten Differenzwerts verkleinert wird. 9. The method according to any one of the preceding claims, characterized in that the maximum delivery rate is determined from the environmental conditions, wherein the maximum delivery rate is determined by subtracting a difference value from the maximum delivery, said difference value starting from a at the start of the internal combustion engine (1). decreasing present first difference value in the direction of a second difference value. 10. Brennkraftmaschine (1 ), insbesondere zur Durchführung des Verfah- rens nach einem oder mehreren der vorhergehenden Ansprüche, wobei die Brennkraftmaschine (1 ) wenigstens einen Zylinder (2) aufweist, in den während eines Arbeitsspiels der Brennkraftmaschine (1 ) Frischluft zum Erzielen eines bestimmten Sollliefergrads eingebracht wird, dadurch gekennzeichnet, dass die Brenn kraftmasch ine (1 ) dazu aus- gebildet ist, den Sollliefergrad auf einen Maximalliefergrad zu begren- zen, der bei einem Start der Brennkraftmaschine auf einen ersten Vor- gabewert gesetzt und nach dem Start der Brennkraftmaschine (1 ) in Richtung eines zweiten Vorgabewerts vergrößert wird. 10. internal combustion engine (1), in particular for carrying out the method according to one or more of the preceding claims, wherein the internal combustion engine (1) has at least one cylinder (2), in the during a working cycle of the internal combustion engine (1) fresh air to achieve a certain internal delivery level is introduced, characterized in that the internal combustion engine (1) is designed to limit the target delivery to a maximum delivery, set at a start of the internal combustion engine to a first Vorgabewert and after the start of Internal combustion engine (1) is increased in the direction of a second default value.
PCT/EP2019/062323 2018-06-07 2019-05-14 Method for operating an internal combustion engine, and corresponding internal combustion engine Ceased WO2019233714A1 (en)

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