EP2304208B1 - Method for determining the fuel-to-air ratio of an internal combustion engine - Google Patents
Method for determining the fuel-to-air ratio of an internal combustion engine Download PDFInfo
- Publication number
- EP2304208B1 EP2304208B1 EP09765533.6A EP09765533A EP2304208B1 EP 2304208 B1 EP2304208 B1 EP 2304208B1 EP 09765533 A EP09765533 A EP 09765533A EP 2304208 B1 EP2304208 B1 EP 2304208B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel
- combustion engine
- internal combustion
- injection
- air
- 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.)
- Active
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 77
- 238000000034 method Methods 0.000 title claims description 28
- 239000000446 fuel Substances 0.000 claims description 108
- 238000002347 injection Methods 0.000 claims description 57
- 239000007924 injection Substances 0.000 claims description 57
- 230000005284 excitation Effects 0.000 claims description 31
- 238000012937 correction Methods 0.000 claims description 4
- 238000010586 diagram Methods 0.000 claims description 2
- 230000003466 anti-cipated effect Effects 0.000 claims 1
- 239000000523 sample Substances 0.000 description 7
- 239000000203 mixture Substances 0.000 description 6
- 230000006978 adaptation Effects 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 230000007613 environmental effect Effects 0.000 description 3
- 238000012545 processing Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 230000000638 stimulation Effects 0.000 description 3
- 238000012935 Averaging Methods 0.000 description 2
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000011156 evaluation Methods 0.000 description 2
- 238000009966 trimming Methods 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 239000003054 catalyst Substances 0.000 description 1
- 238000004590 computer program Methods 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 230000000875 corresponding effect Effects 0.000 description 1
- 230000001687 destabilization Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000001537 neural effect Effects 0.000 description 1
- 238000010606 normalization Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
Images
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
- F02D41/14—Introducing closed-loop corrections
- F02D41/1497—With detection of the mechanical response of the engine
- F02D41/1498—With detection of the mechanical response of the engine measuring engine roughness
-
- 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
- F02D41/008—Controlling each cylinder individually
-
- 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
- F02D41/14—Introducing closed-loop corrections
- F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
- F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
- F02D41/1454—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being an oxygen content or concentration or the air-fuel ratio
- F02D41/1458—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being an oxygen content or concentration or the air-fuel ratio with determination means using an estimation
-
- 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
- F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
-
- 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
- F02D41/064—Introducing corrections for particular operating conditions for engine starting or warming up for starting at cold start
Definitions
- the present invention relates to a method for determining the fuel-air ratio of an internal combustion engine according to the features of claim 1.
- US 2004/193360 A1 describes a method of catalyst heating wherein the internal combustion engine is run at regular lean-fat intervals. In order to suppress undesired speed fluctuations resulting therefrom, a standardized speed variance is evaluated, correlated with a stored desired course, in order to determine a correction value for the ignition angle.
- US5915359 discloses a method for determining the air-fuel ratio of an internal combustion engine wherein different levels of fuel are metered to an individual cylinder.
- the air-fuel ratio is determined by the use of a neuronal network as a function of the rotational speed fluctuations.
- the invention is based on the idea of assigning different proportions of fuel to successive work strokes of an individual cylinder of an internal combustion engine, so that the course of the rotational speed of the crankshaft or camshaft of the internal combustion engine is excited and a characteristic pattern is impressed on the course of the rotational speed, depending on This characteristic pattern of the course of the speed is determined to be an absolute value of the air-fuel ratio. In other words, the individual work cycles and thus the course of the speed targeted disturbances are switched. In accordance with the invention, further characteristics of this characteristic pattern are formed and set in relation to the torque of the internal combustion engine.
- One possible characteristic of the characteristic pattern is the rough running of the internal combustion engine.
- the relationship is used that in an internal combustion engine, a change in the proportion of fuel of a power stroke with a change in torque and a change in torque is in turn associated with a change in speed.
- the influence of the characteristic pattern or the parameter uneven running on the torque is further set according to the invention in relation to the fuel-air ratio.
- the relationship is used that a change in the air-fuel ratio is associated with a change in the torque of an internal combustion engine.
- an absolute value of the fuel-air ratio is advantageously also available when a lambda probe is not ready for operation. Furthermore, in comparison to the prior art, it is not necessary to approach safety-related limits, but an absolute value of the fuel-air ratio can be accessed directly. In this way, a correct adjustment of the air-fuel ratio is possible immediately after the start of an internal combustion engine. In the warm-up phase of an internal combustion engine, therefore, there are advantages in terms of economy and environmental compatibility.
- the inventive method can also be advantageously carried out by means of an existing device for controlling and regulating the internal combustion engine as a computer program and is therefore easy to implement.
- an internal combustion engine 1 with a plurality of cylinders 2 is shown.
- the cylinders 2 fuel is supplied by means of injection valves 3.
- the internal combustion engine 1 comprises an intake pipe 4 and an exhaust pipe 5.
- a sensor 6 for determining the current crank angle and a sensor 7 for determining the filling of the internal combustion engine 1 are provided.
- the internal combustion engine 1 preferably comprises a spark-ignition system, not shown.
- the internal combustion engine 1 can also be operated in a so-called auto-ignition mode. According to the prior art, all the sensors and actuators mentioned are connected by a control and regulating device, not shown.
- FIG. 2 is an example of a possible parameterization of a cylinder-specific excitation or trim the fuel-air ratio for a first operating point of an internal combustion engine 1 with a low load shown.
- the dashed line shows the fuel injection amount without excitation.
- the solid line shows the fuel injection amount with an excitation, that is, it is according to the invention for successive cycles the metering different proportions of fuel to a cylinder 2 of the internal combustion engine 1, for example, to cylinder 1.
- the first injection A has therefore initially a larger share and then a smaller amount of fuel, so that the amount of fuel is taken without stimulation again.
- the second injection B has only a smaller proportion and then a larger proportion of fuel, so that the amount of fuel is taken without an excitation again.
- the third injection C and the fourth injection D have neither increased nor decreased proportions of fuel.
- FIG. 3 is an example of a further possible parameterization of an individual cylinder excitation or trim the fuel-air ratio for a further operating point of an internal combustion engine 1 with a high load shown.
- the amplitude of the excitation is smaller than at the low load operating point and the duration of the excitation is the same.
- the dashed line shows the fuel injection amount without excitation.
- the solid line shows the fuel injection amount with an excitation, that is, according to the invention for successive cycles the metering of different proportions of fuel a cylinder 2 of the internal combustion engine 1, for example, to cylinders 1.
- the first injection A therefore has a smaller proportion and then a larger amount of fuel, so that the amount of fuel is taken without stimulation again.
- the second injection B has only a larger proportion and then a smaller proportion of fuel, so that the fuel quantity is taken up again without an excitation.
- the third injection C and the fourth injection D have neither increased nor decreased proportions of fuel.
- FIG. 2 and 3 clearly that according to the invention differently parameterizable consequences of changes in the fuel injection amount, which enrich the fuel air mixture in a predetermined manner or lean, can be provided.
- FIG. 2 For example, in the first injection A, an increase in the proportion of fuel and in the second injection B, a decrease in the proportion of fuel and according to FIG. 3 first a decrease in the proportion of fuel and in the second injection B an increase in the proportion of fuel.
- FIGS. 2a and 2b are still the suggestions of the speed curve of the crankshaft of the internal combustion engine 1 according to FIG. 2 shown over time.
- the first injection A with an increased proportion of fuel leads to such an excitation of the course of the rotational speed that the rotational speed decreases.
- the fuel-air ratio setpoint for this example has a value less than 1.0
- the first injection A further enriches the air-fuel ratio and thus further destabilizes combustion.
- the second injection B with a reduced proportion of fuel leads to an increase in the rotational speed, since a leaning of the air-fuel ratio and thus a stabilization of the combustion takes place.
- FIG. 2a It becomes clear that the first injection A with an increased proportion of fuel leads to such an excitation of the course of the rotational speed that the rotational speed decreases.
- the fuel-air ratio setpoint for this example has a value less than 1.0
- the second injection B with a reduced proportion of fuel leads to an increase in the rotational speed, since a leaning of the
- the forced by the changes in the fuel injection quantity according to the invention stimulation of the course of the rotational speed of the crankshaft or camshaft of the internal combustion engine 1 can be described by the parameter uneven running.
- the uneven running can, as is well known from the prior art, by reference of the current speed components of individual cycles of the cylinder of an internal combustion engine 1 on past speed components of individual cycles of these cylinders are related.
- One segment corresponds to a crank angle range of 720 degrees divided by the number of cylinders. Consequently, for a four-cylinder internal combustion engine, one segment is 180 degrees.
- the result is a so-called rough running value.
- the amplitude of the excitation within the limits of the signal resolution for the uneven running and a maximum permissible excitation, so that the amplitude is inversely proportional to the torque of the internal combustion engine 1.
- Such selection takes place, for example, via load and speed-dependent maps.
- the selection of the amplitude of the changes in the fuel injection quantity as a function of the expected torque for example represented by the load or filling, the Speed, adjusting parameters such as camshaft adjustment and setpoints for the fuel-air mixture and the ignition timing to perform.
- the running noise of each cylinder is averaged over individual cycles, for example, a dragging average or an arithmetic averaging can be used after a lead time. Furthermore, it is advantageously possible to correct the rough running values measured during the excitation according to the invention of the rotational speed of the internal combustion engine by the rough running values which are present in the respective operating point without exciting the rotational speed or targeted cylinder-individual trimming of the air-fuel ratio. Moreover, it is provided according to the invention to make corrections to the rough running values with regard to changes in rotational speed, which are caused by a dynamic driving style. Errors that are caused by the sensor 6 for determining the current crank angle and the associated encoder wheel can also be taken into account.
- the averaged uneven running is evaluated and standardized to the amplitude of the excitation and the expected torque of the internal combustion engine with completion of a pattern of targeted cylinder individual trim of the air-fuel ratio.
- the normalization parameters can be detected in operating maps specifically in characteristic maps.
- the now available standardized uneven running is converted for the underlying speed-load operating point via maps in the associated fuel-air ratio. It is still possible according to the invention to average this fuel-air ratio via various excitation or calibration patterns in order to avoid interference effects.
- FIG. 4 the change of the so-called internal engine efficiency of the air-fuel ratio is shown and how it scales with the air-fuel ratio and the amplitude of the cylinder-individual excitation or the trim of the air-fuel ratio.
- the relationship is used that the product of the change in the efficiency of the air-fuel ratio and the so-called internal torque of the internal combustion engine 1 is proportional to the forced rough running.
- the internal torque describes the torque of the internal combustion engine 1 resulting from the combustion of the fuel.
- the value of the internal torque is thus greater than the value of the effective torque that can be tapped on the crankshaft of the internal combustion engine 1, since the effective torque takes into account the torque component resulting from unavoidable losses an internal combustion engine 1 results.
- the uneven running of the internal combustion engine 1 increases with the resulting speed drop because the air-fuel ratio is shifted toward the running limit where the air-fuel ratio is too rich to burn properly, as in the Figures 2 and 2a described.
- the normalized uneven running an absolute value of the air-fuel ratio can be assigned.
- cylinder-specific reduction of the fuel-air ratio specifically, takes place That is, the running noise of the internal combustion engine 1 to values representing a speed increase, since the air-fuel ratio is shifted against the direction of the running limit, in which the fuel-air ratio is too rich to burn correctly. Rather, the fuel-air ratio is shifted in the direction of a larger moment of an internal combustion engine 1, namely in the direction of a value of the fuel-air ratio of 0.9, in which experience has shown that an internal combustion engine with otherwise the same operating parameters runs very stable and a maximum Torque provides.
- the injection A can be regarded as the starting point and the injection B as the end point of a vector.
- the direction of this vector includes the essential information as to whether the actual air-fuel ratio is in the range of less than 0.9 and thus in the increasing part of the functional relationship between the air-fuel ratio and the actual fuel-air ratio Ratio according to FIG.
- the injection A can also be regarded as the starting point and the injection B as the endpoint of a vector.
- the direction of this vector can be taken from the essential information where the actual air-fuel ratio is, namely in the range of greater than 0.9 and thus in the falling part of the functional relationship between the fuel-air ratio and the actually fuel-air ratio.
- injections C and D without a change in a preset value of the air-fuel ratio, ie without an excitation of the speed is to be expected, then arise again points on the vector.
- the actual fuel-air ratio which is in accordance with FIG. 5 can be read easily, or is available for further processing as an absolute value.
- FIG. 6 Furthermore, a block diagram for the inventive method is shown.
- the operating conditions for the inventive method for determining the air-fuel ratio of an internal combustion engine 1 are defined, that is, there is a determination of whether the inventive method is to be activated or not. If the method according to the invention is to be activated, a suitable signal from block E is transmitted via the connection to block F. Further, block E is connected to block J for the purpose of transmitting signals relating to the request of the evaluation of the rough running and the determination of the absolute value of the air-fuel ratio. In block F, a calculation of the cylinder-specific mixture excitation takes place. The multiplication point G is supplied with the parameters of the cylinder-specific mixture excitation determined in block F.
- the multiplication point G the parameters of the control and / or adaptation of the pilot control or the specification of a target value of the fuel-air ratio from block K are supplied.
- the parameters from block F and K are related to each other, so that according to the invention there is a change in the injection quantity of successive working cycles.
- a target value for a fuel injection amount at block H is output.
- Block H represents the components of the injection system of the internal combustion engine 1, as the injection valves 3.
- the answer or the reaction of the internal combustion engine 1 is indicated on the cylinder-individual trim of the fuel-air mixture.
- block I there is an evaluation of the uneven running occurring due to the cylinder-specific trimming of the air-fuel ratio and in block J the conversion of the uneven running into an absolute value of the air-fuel ratio.
- the block J is further connected to block K, so that the absolute value of the air-fuel ratio is available for the regulation and / or adaptation of the precontrol for further processing.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Description
Die vorliegende Erfindung betrifft ein Verfahren zur Bestimmung des Kraftstoff-Luft-Verhältnisses einer Verbrennungskraftmaschine gemäß den Merkmalen des Patentanspruches 1.The present invention relates to a method for determining the fuel-air ratio of an internal combustion engine according to the features of
Es ist allgemein bekannt, dass die korrekte Einstellung des Kraftstoff-Luft-Verhältnisses hinsichtlich der Wirtschaftlichkeit und die Umweltverträglichkeit einer Verbrennungskraftmaschine von großer Bedeutung ist. Zur korrekten Einstellung des Kraftstoff-Luft-Verhältnisses werden allgemein Verfahren und Vorrichtungen zur Steuerung und Regelung des Kraftstoff-Luft-Verhältnisses eingesetzt, welche auf den Einsatz von so genannten Lambdasonden aufbauen.It is well known that the correct adjustment of the air-fuel ratio in terms of economy and environmental compatibility of an internal combustion engine is of great importance. For the correct adjustment of the air-fuel ratio, methods and devices for controlling and regulating the air-fuel ratio are generally used, which build on the use of so-called lambda probes.
Gemäß dem nachveröffentlichten Dokument
Vorbekannt aus der
Es ist jedoch bei diesem Verfahren von Nachteil, dass ohne eine betriebsbereite Lambdasonde nicht ohne weiteres festgestellt werden kann, woraus sich eine Abweichung zwischen dem Ist- und dem Soll-Laufunruhewert ergibt, also ob das Kraftstoff-Luft-Verhältnisses nicht schon zuviel oder vielleicht noch zu wenig angereichert ist. Das heißt, es ist nicht eindeutig; ob die Verbrennungskraftmaschine im Bereich einer Laufgrenze betrieben wird, bei der eine zu starke Anreicherung des Kraftstoff-Luft-Verhältnisses zu erhöhten Ist-Laufunruhewerten führt oder ob die Verbrennungskraftmaschine im Bereich einer Laufgrenze betrieben wird, bei der eine zu geringe Anreicherung des Kraftstoff-Luft-Verhältnisses zu erhöhten Ist-Laufunruhewerten führt. Eine Aussage darüber ist nur durch das Anfahren der oberen beziehungsweise unteren einstellbaren Grenzen möglich. Mit anderen Worten sind mittels dieses Verfahrens in den genannten Grenzen bestenfalls relative Aussagen möglich. Es ist weiterhin von Nachteil, dass die genannten Grenzen Sicherheiten aufweisen müssen, da während der Entwicklung einer Verbrennungskraftmaschine das Verhalten einzelner Entwicklungsexemplare auf eine gesamte Serie übertragen werden muss.However, it is disadvantageous in this method that without an operational lambda probe can not be readily determined, resulting in a deviation between the actual and the desired Laufunruhewert results, so whether the air-fuel ratio is not already too much or maybe too little is enriched. That is, it is not unique; whether the internal combustion engine is operated in the region of a running limit, in which an excessive enrichment of the air-fuel ratio leads to increased actual rough-running values or if the internal combustion engine is operated in the region of a running limit, in which an insufficient enrichment of the fuel-air ratio Ratio leads to increased actual running noise values. A statement about this is only possible by approaching the upper or lower adjustable limits. In other words, relative statements are possible at best by means of this method within the limits mentioned. It is also disadvantageous that the said limits must have collateral, because during the development of an internal combustion engine, the behavior of individual development copies must be transferred to an entire series.
Es ist daher Aufgabe der vorliegenden Erfindung, eine Möglichkeit zu schaffen, unabhängig von der Betriebsbereitschaft von Lambdasonden, einen absoluten Wert des Kraftstoff-Luft-Verhältnisses bereitzustellen.It is therefore an object of the present invention to provide a possibility, regardless of the operational readiness of lambda probes, to provide an absolute value of the air-fuel ratio.
Diese Aufgabe wird erfindungsgemäß durch die Merkmale des Patentanspruches 1 gelöst.This object is achieved by the features of
Der Erfindung liegt der Gedanke zu Grunde, aufeinanderfolgenden Arbeitstakten eines individuellen Zylinders einer Verbrennungskraftmaschine unterschiedliche Anteile an Kraftstoff zuzumessen, so dass der Verlauf der Drehzahl der Kurbel- oder Nockenwelle der Verbrennungskraftmaschine angeregt wird und dem Verlauf der Drehzahl ein charakteristisches Muster aufgeprägt wird, wobei in Abhängigkeit dieses charakteristischen Musters des Verlaufs der Drehzahl ein absoluter Wert des Kraftstoff-Luft-Verhältnisses bestimmt wird. Mit anderen Worten werden den einzelnen Arbeitstakten und somit dem Verlauf der Drehzahl gezielt Störgrößen aufgeschaltet. Erfindungsgemäß werden weiterhin Kenngrößen dieses charakteristischen Musters gebildet und in Relation zu dem Drehmoment der Verbrennungskraftmaschine gesetzt. Eine mögliche Kenngröße des charakteristischen Musters ist die Laufunruhe der Verbrennungskraftmaschine. Insbesondere wird erfindungsgemäß der Zusammenhang genutzt, dass bei einer Verbrennungskraftmaschine eine Änderung des Anteils an Kraftstoff eines Arbeitstaktes mit einer Änderung des Drehmomentes und eine Änderung des Drehmomentes wiederum mit einer Änderung der Drehzahl verbunden ist. Der Einfluss des charakteristischen Musters beziehungsweise der Kenngröße Laufunruhe auf das Drehmoment wird weiterhin erfindungsgemäß in Relation zu dem Kraftstoff-Luft-Verhältnis gesetzt. Mit anderen Worten wird erfindungsgemäß der Zusammenhang genutzt, dass eine Änderung des Kraftstoff-Luft-Verhältnisses mit einer Änderung des Drehmomentes einer Verbrennungskraftmaschine verbunden ist.The invention is based on the idea of assigning different proportions of fuel to successive work strokes of an individual cylinder of an internal combustion engine, so that the course of the rotational speed of the crankshaft or camshaft of the internal combustion engine is excited and a characteristic pattern is impressed on the course of the rotational speed, depending on This characteristic pattern of the course of the speed is determined to be an absolute value of the air-fuel ratio. In other words, the individual work cycles and thus the course of the speed targeted disturbances are switched. In accordance with the invention, further characteristics of this characteristic pattern are formed and set in relation to the torque of the internal combustion engine. One possible characteristic of the characteristic pattern is the rough running of the internal combustion engine. In particular, according to the invention, the relationship is used that in an internal combustion engine, a change in the proportion of fuel of a power stroke with a change in torque and a change in torque is in turn associated with a change in speed. The influence of the characteristic pattern or the parameter uneven running on the torque is further set according to the invention in relation to the fuel-air ratio. In other words, according to the invention, the relationship is used that a change in the air-fuel ratio is associated with a change in the torque of an internal combustion engine.
Durch das erfindungsgemäße Verfahren steht vorteilhaft auch dann ein absoluter Wert des Kraftstoff-Luft-Verhältnisses bereit, Wenn eine Lambdasonde nicht betriebsbereit ist. Im Vergleich zum Stand der Technik ist es des Weiteren nicht erforderlich, sicherheitsbehaftete Grenzen anzufahren, sondern es kann unmittelbar auf einen absoluten Wert des Kraftstoff-Luft-Verhältnisses zugegriffen werden. Auf diese Weise ist unmittelbar nach dem Start einer Verbrennungskraftmaschine eine korrekte Einstellung des Kraftstoff-Luft-Verhältnisses möglich. In der Warmlaufphase einer Verbrennungskraftmaschine ergeben sich daher hinsichtlich der Wirtschaftlichkeit und der Umweltverträglichkeit Vorteile. Insbesondere ist es möglich, nach der Neubetankung eines Fahrzeuges mit einem Kraftstoff, der im Vergleich zu dem vorherigen Kraftstoff abweichende Eigenschaften aufweist, beispielsweise die Neubetankung mit einem ethanolhaltigen Kraftstoff, nach einer Betankung mit herkömmlichen Ottokraftstoff, eine unzulässige Abweichung zwischen dem Soll- und dem Ist-Kraftstoff-Luft-Verhältnis zu vermeiden, da mittels des erfindungsgemäßen Verfahrens, auch ohne Bereitschaft der Lambdasonde, schnell, einfach und prozesssicher das Ist-Kraftstoff-Luft-Verhältnis bestimmt werden kann und eine Ausregelung auf ein Soll-Kraftstoff-Luft-Verhältnis möglich ist.By the method according to the invention, an absolute value of the fuel-air ratio is advantageously also available when a lambda probe is not ready for operation. Furthermore, in comparison to the prior art, it is not necessary to approach safety-related limits, but an absolute value of the fuel-air ratio can be accessed directly. In this way, a correct adjustment of the air-fuel ratio is possible immediately after the start of an internal combustion engine. In the warm-up phase of an internal combustion engine, therefore, there are advantages in terms of economy and environmental compatibility. In particular, it is possible, after the refueling of a vehicle with a fuel that has different properties compared to the previous fuel, such as refueling with an ethanol-containing fuel, after refueling with conventional gasoline, an impermissible deviation between the target and the actual Fuel-to-air ratio too avoid, because by means of the method according to the invention, even without readiness of the lambda probe, the actual air-fuel ratio can be determined quickly, easily and reliably and a compensation to a desired fuel-air ratio is possible.
Das erfindungsgemäße Verfahren kann ferner vorteilhaft mittels einer vorhandenen Vorrichtung zur Steuerung und Regelung der Verbrennungskraftmaschine als Computerprogramm ausgeführt werden und ist daher leicht umsetzbar.The inventive method can also be advantageously carried out by means of an existing device for controlling and regulating the internal combustion engine as a computer program and is therefore easy to implement.
Weitere vorteilhafte Ausgestaltungen der vorliegenden Erfindung sind dem nachfolgenden Ausführungsbeispiel sowie den abhängigen Patentansprüchen zu entnehmen.Further advantageous embodiments of the present invention will become apparent from the following embodiment and the dependent claims.
Gemäß
In
In
Gemäß
Außerdem wird gemäß
Grundsätzlich kann erfindungsgemäß sowohl gemäß
Gemäß den
Die durch die Änderungen der Kraftstoffeinspritzmenge erfindungsgemäß erzwungene Anregung des Verlaufes der Drehzahl der Kurbel- oder Nockenwelle der Verbrennungskraftmaschine 1 kann durch die Kenngröße Laufunruhe beschrieben werden. Die Laufunruhe kann, wie aus dem Stand der Technik allgemein bekannt, durch einen Bezug der aktuellen Drehzahlanteile einzelner Arbeitsspiele der Zylinder einer Verbrennungskraftmaschine 1 auf vergangene Drehzahlanteile einzelner Arbeitsspiele dieser Zylinder bezogen werden. Insbesondere ist es bekannt, so genannte Segmentzeiten aufeinanderfolgender Arbeitsspiele zueinander in das Verhältnis zu setzen. Ein Segment entspricht dabei einem Kurbelwinkelbereich von 720 Grad geteilt durch die Anzahl der Zylinder. Für eine Vierzylinder-Verbrennungskraftmaschine beträgt ein Segment folglich 180 Grad. Resultat ist dabei ein so genannter Laufunruhewert. Es erfolgt nun bevorzugt eine Auswahl der Amplitude der Anregung innerhalb der Grenzen der Signalauflösung für die Laufunruhe und einer zulässigen maximalen Anregung, so dass die Amplitude umgekehrt proportional zum Drehmoment der Verbrennungskraftmaschine 1 ist. Eine solche Auswahl erfolgt beispielsweise über last- und drehzahlabhängige Kennfelder. Außerdem ist es erfindungsgemäß vorgesehen, die Auswahl der Amplitude der Änderungen der Kraftstoffeinspritzmenge in Abhängigkeit des zu erwartenden Drehmomentes, beispielsweise repräsentiert durch die Last oder Füllung, die Drehzahl, Stellparameter wie Nockenwellenverstellung und Sollwerten für das Kraftstoff-Luft-Gemisch und dem Zündzeitpunkt, durchzuführen.The forced by the changes in the fuel injection quantity according to the invention stimulation of the course of the rotational speed of the crankshaft or camshaft of the
Die Laufunruhe jedes Zylinders wird über einzelne Arbeitsspiele gemittelt, beispielsweise kann ein schleppendes Mittel oder eine arithmetische Mittelung nach einer Vorlaufzeit verwendet werden. Weiterhin ist es vorteilhaft möglich, die während der erfindungsgemäßen Anregung der Drehzahl der Verbrennungskraftmaschine 1 gemessenen Laufunruhewerte um die Laufunruhewerte zu korrigieren, die in dem jeweiligen Betriebspunkt ohne Anregung der Drehzahl beziehungsweise gezielte zylinderindividuelle Vertrimmung des Kraftstoff-Luft-Verhältnisses vorliegen. Außerdem ist es erfindungsgemäß vorgesehen, Korrekturen der Laufunruhewerte hinsichtlich Drehzahländerungen vorzunehmen, die durch eine dynamische Fahrweise bedingt sind. Auch Fehler, die durch den Sensor 6 zur Bestimmung des aktuellen Kurbelwinkels und das damit zusammenwirkende Geberrad bedingt sind, können mit berücksichtigt werden.The running noise of each cylinder is averaged over individual cycles, for example, a dragging average or an arithmetic averaging can be used after a lead time. Furthermore, it is advantageously possible to correct the rough running values measured during the excitation according to the invention of the rotational speed of the internal combustion engine by the rough running values which are present in the respective operating point without exciting the rotational speed or targeted cylinder-individual trimming of the air-fuel ratio. Moreover, it is provided according to the invention to make corrections to the rough running values with regard to changes in rotational speed, which are caused by a dynamic driving style. Errors that are caused by the
Erfindungsgemäß wird mit Abschluss eines Musters der gezielten zylinderindividuellen Vertrimmung des Kraftstoff-Luft-Verhältnisses die gemittelte Laufunruhe ausgewertet und auf die Amplitude der Anregung und das erwartete Drehmoment der Verbrennungskraftmaschine normiert. Alternativ können die Normierungsparameter betriebspunktspezifisch in Kennfeldern erfasst werden. Die nunmehr bereitstehende normierte Laufunruhe wird für den zu Grunde liegenden Drehzahl-Last-Betriebspunkt über Kennfelder in das zugehörige Kraftstoff-Luft-Verhältnis umgerechnet. Es ist erfindungsgemäß weiterhin möglich, dieses Kraftstoff-Luft-Verhältnis über verschiedene Anregungs- oder Vertrimmungsmuster zu mitteln, um Störeffekte zu vermeiden.According to the invention, the averaged uneven running is evaluated and standardized to the amplitude of the excitation and the expected torque of the internal combustion engine with completion of a pattern of targeted cylinder individual trim of the air-fuel ratio. Alternatively, the normalization parameters can be detected in operating maps specifically in characteristic maps. The now available standardized uneven running is converted for the underlying speed-load operating point via maps in the associated fuel-air ratio. It is still possible according to the invention to average this fuel-air ratio via various excitation or calibration patterns in order to avoid interference effects.
In
Analog kann eine Bestimmung des tatsächlichen Kraftstoff-Luft-Verhältnisses gemäß
In
- 11
- VerbrennungskraftmaschineInternal combustion engine
- 22
- Zylindercylinder
- 33
- EinspritzventilInjector
- 44
- Ansaugleitungsuction
- 55
- Abgasleitungexhaust pipe
- 66
- Sensor zur Bestimmung des aktuellen KurbelwinkelsSensor for determining the current crank angle
- 77
- Sensor zur Bestimmung der FĂĽllungSensor for determining the filling
- AA
- erste Einspritzungfirst injection
- BB
- zweite Einspritzungsecond injection
- CC
- dritte Einspritzungthird injection
- DD
- vierte Einspritzungfourth injection
- Ee
- Block zur Definition der BetriebsbedingungenBlock for defining the operating conditions
- FF
- Block zur Berechnung der zylinderindividuellen GemischanregungBlock for calculating the cylinder-specific mixture excitation
- GG
- Multiplikationsstellemultiplication point
- HH
- Blockblock
- H'H'
-
Antwort, Reaktion der Verbrennungskraftmaschine 1Answer, reaction of the
internal combustion engine 1 - II
- Block zur Auswertung der LaufunruheBlock for evaluating the rough running
- JJ
- Block zur Umrechnung der LaufunruheBlock for converting the rough running
- KK
- Block mit Parametern der Vorsteuerung des Kraftstoff-Luft-VerhältnissesBlock with parameters of the pilot control of the air-fuel ratio
Claims (12)
- Method for determining the fuel-to-air ratio of an internal combustion engine (1) with one or more cylinders (2), wherein fuel is fed to the cylinders (2) by means of injection valves (3), characterized in that different proportions of fuel are metered to successive working cycles of an individual cylinder (2) of the internal combustion engine (1), with the result that the profile of the rotational speed of the crankshaft or camshaft of the internal combustion engine (1) is excited, and a characteristic pattern is impressed on the profile of the rotational speed, wherein an absolute value of the fuel-to-air ratio is determined as a function of this characteristic pattern of the profile of the rotational speed.
- Method according to Claim 1, wherein a characteristic variable of the characteristic pattern of the profile of the rotational speed is formed and is placed in relation to the torque of the internal combustion engine (1).
- Method according to Claim 2, wherein the characteristic variable of the characteristic pattern is the unsmoothed running of the internal combustion engine (1).
- Method according to Claim 1 or 3, wherein a ratio is formed between the influence of the characteristic pattern or the characteristic variable and the torque in relation to the fuel-to-air ratio.
- Method according to Claim 3 or 4, wherein the characteristic variable of the unsmoothed running is standardized to the amplitude of the excitation, and the anticipated torque of the internal combustion engine (1), and the standardized unsmoothed running is converted into the associated fuel-to-air ratio by means of characteristic diagrams.
- Method according to one of Claims 3 to 5, wherein the unsmoothed running is averaged over individual operating cycles.
- Method according to one of Claims 3 to 6, wherein the corrections of the unsmoothed running values are made with respect to changes in rotation speed which are caused by dynamic driving style, and errors which are caused by a sensor (6) for determining the current crank angle and by a signal generator which interacts with said sensor (6) are taken into account.
- Method according to one of Claims 1 to 7, wherein a parametrization of a cylinder-specific excitation/detuning of the fuel-to-air ratio is carried out on a cylinder-specific basis for various operating points of the internal combustion engine (1) as a function of the state of load of the internal combustion engine (1).
- Method according to Claim 8, wherein in the case of low loading of the internal combustion engine (1) relatively high amplitudes of the excitation are provided, and in the case of relatively high loading of the internal combustion engine (1) relatively low amplitudes of the excitation are provided.
- Method according to one of Claims 1 to 8, wherein differently parameterizable sequences of changes in the fuel injection quantity, which changes make the fuel-to-air ratio richer or leaner in a predefined fashion, are provided.
- Method according to one of Claims 1 to 10, wherein in a first injection a relatively high proportion of fuel and in a subsequent second injection a relatively low proportion of fuel are metered to the individual cylinder (2) compared to a setpoint value prescription of the fuel-to-air ratio, or in a first injection a relatively low proportion of fuel and in a subsequent second injection a relatively high proportion of fuel are metered to the individual cylinder (2) compared to the setpoint value prescription.
- Method according to Claim 11, wherein subsequent to the second injection, a proportion of fuel corresponding to the setpoint value prescription of the fuel-to-air ratio is metered to the individual cylinder (2) in at least one injection.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200810028769 DE102008028769A1 (en) | 2008-06-17 | 2008-06-17 | Method for determining the fuel-air ratio of an internal combustion engine |
PCT/EP2009/003954 WO2009152953A1 (en) | 2008-06-17 | 2009-06-03 | Method for determining the fuel-to-air ratio of an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2304208A1 EP2304208A1 (en) | 2011-04-06 |
EP2304208B1 true EP2304208B1 (en) | 2016-03-23 |
Family
ID=40964984
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09765533.6A Active EP2304208B1 (en) | 2008-06-17 | 2009-06-03 | Method for determining the fuel-to-air ratio of an internal combustion engine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2304208B1 (en) |
DE (1) | DE102008028769A1 (en) |
WO (1) | WO2009152953A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012101607A1 (en) | 2012-02-28 | 2013-08-29 | Zylum Beteiligungsgesellschaft Mbh & Co. Patente Ii Kg | Method for separating nitrogen oxide e.g. nitrite and nitrate for fertilizers, involves performing gas liquid sorption and gas solid sorption of nitrogen oxide using sorbent containing hydroxides and/or oxides of alkaline earth metal |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2739142A1 (en) | 1995-09-27 | 1997-03-28 | Siemens Automotive Sa | Control of richness of air=fuel mixture fed to internal combustion engine used in e.g. garden tool |
US5690072A (en) | 1996-12-13 | 1997-11-25 | Ford Global Technologies, Inc. | Method and system for determining and controlling a/f ratio in lean engines |
EP0715686B1 (en) | 1993-08-27 | 1999-02-17 | Aktiebolaget Electrolux | Engine control |
US5915359A (en) | 1996-12-13 | 1999-06-29 | Ford Global Technologies, Inc. | Method and system for determining and controlling A/F ratio during cold start engine operation |
DE4305206C2 (en) | 1992-02-20 | 2003-04-30 | Electrolux Ab | Method and device for controlling a carburetor |
DE102004013613A1 (en) | 2003-03-27 | 2004-10-07 | Honda Motor Co., Ltd. | Control system for correcting a torque fluctuation of an engine |
WO2008135312A1 (en) | 2007-05-07 | 2008-11-13 | Continental Automotive Gmbh | Method and device for determining the combustion lambda value of an internal combustion engine |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000130225A (en) * | 1998-10-21 | 2000-05-09 | Sanshin Ind Co Ltd | Engine and outboard engine provided with engine |
DE10231951A1 (en) * | 2001-07-16 | 2003-04-24 | Denso Corp | Control device for an internal combustion engine |
DE10252423A1 (en) | 2002-11-12 | 2004-05-19 | Robert Bosch Gmbh | Procedure for correcting the enrichment of a fuel / air mixture |
DE102004045154A1 (en) * | 2004-09-17 | 2006-03-23 | Volkswagen Ag | Air-fuel ratio determining method for e.g. gasoline engine, involves determining air-fuel ratio of engine based on ratio of total turnover of cylinder to fuel mass supplied to cylinder |
DE102007044614B3 (en) * | 2007-09-19 | 2009-04-09 | Continental Automotive Gmbh | Internal combustion engine i.e. diesel internal combustion engine, operating method for motor vehicle, involves detecting combustion misfire when time difference is larger than preset threshold value that is larger than another value |
-
2008
- 2008-06-17 DE DE200810028769 patent/DE102008028769A1/en not_active Withdrawn
-
2009
- 2009-06-03 WO PCT/EP2009/003954 patent/WO2009152953A1/en active Application Filing
- 2009-06-03 EP EP09765533.6A patent/EP2304208B1/en active Active
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4305206C2 (en) | 1992-02-20 | 2003-04-30 | Electrolux Ab | Method and device for controlling a carburetor |
EP0715686B1 (en) | 1993-08-27 | 1999-02-17 | Aktiebolaget Electrolux | Engine control |
FR2739142A1 (en) | 1995-09-27 | 1997-03-28 | Siemens Automotive Sa | Control of richness of air=fuel mixture fed to internal combustion engine used in e.g. garden tool |
US5690072A (en) | 1996-12-13 | 1997-11-25 | Ford Global Technologies, Inc. | Method and system for determining and controlling a/f ratio in lean engines |
US5915359A (en) | 1996-12-13 | 1999-06-29 | Ford Global Technologies, Inc. | Method and system for determining and controlling A/F ratio during cold start engine operation |
DE102004013613A1 (en) | 2003-03-27 | 2004-10-07 | Honda Motor Co., Ltd. | Control system for correcting a torque fluctuation of an engine |
WO2008135312A1 (en) | 2007-05-07 | 2008-11-13 | Continental Automotive Gmbh | Method and device for determining the combustion lambda value of an internal combustion engine |
EP2156039A1 (en) * | 2007-05-07 | 2010-02-24 | Continental Automotive GmbH | Method and device for determining the combustion lambda value of an internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
DE102008028769A1 (en) | 2009-12-24 |
EP2304208A1 (en) | 2011-04-06 |
WO2009152953A1 (en) | 2009-12-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE102015209665B4 (en) | Method for identifying valve timing of an internal combustion engine | |
DE102006056708B4 (en) | Method, device and computer program for determining cylinder-specific Verbrennugsmerkmale an internal combustion engine | |
DE69426039T2 (en) | Air-fuel ratio control device for an internal combustion engine | |
DE102006035310B4 (en) | A fuel injection control device with interpolation between a plurality of learned values | |
EP0152604A1 (en) | Control and regulation method for the operating parameters of an internal-combustion engine | |
DE3408223A1 (en) | CONTROL AND REGULATING METHOD FOR THE OPERATING CHARACTERISTICS OF AN INTERNAL COMBUSTION ENGINE | |
EP2148070A2 (en) | Method for determining the injected fuel mass of a single injection and device for carrying out the method | |
WO2010057738A1 (en) | Device for operating an internal combustion engine | |
EP0151768B1 (en) | Measuring system for the fuel-air mixture of a combustion engine | |
DE102005057975A1 (en) | Method for controlling fuel or air flow to individual cylinder of internal-combustion engine, involves evaluation of signal which is influenced by combustion or affects value which has influence on combustion | |
DE102005010029B4 (en) | Engine control system for a multi-cylinder internal combustion engine | |
DE102008037634A1 (en) | System for controlling an air / fuel ratio for internal combustion engines | |
EP2550443B1 (en) | Method and apparatus for adapting adaptation values for actuating injection valves in an engine system having a plurality of injection types | |
EP1409865B1 (en) | Method for compensating injection quantity in each individual cylinder in internal combustion engines | |
DE10001274A1 (en) | Internal combustion motor management system measures the piston movements in time segments during the rotation of the crankshaft to establish irregular running for correction of fuel injection/ignition times | |
DE60102503T2 (en) | Method for controlling the air-fuel ratio in an internal combustion engine | |
WO2015049073A1 (en) | Device for operating an internal combustion engine | |
EP2304208B1 (en) | Method for determining the fuel-to-air ratio of an internal combustion engine | |
AT516669B1 (en) | Method for controlling an internal combustion engine | |
DE102015219362B3 (en) | Method and device for operating an internal combustion engine | |
DE102015200898B3 (en) | Pilot control of an internal combustion engine | |
DE10051974A1 (en) | Regulating knock of IC engine with which using adaptable performance graph value for retard setting of ignition angle are prepared and values are assigned operating parameter | |
DE102011086064B4 (en) | Method for determining a filling difference in the cylinders of an internal combustion engine, operating method and computing unit | |
DE102019207252B4 (en) | Recording of cylinder-specific combustion process parameter values for an internal combustion engine | |
EP0150437A2 (en) | Measuring system for the fuel-air mixture in a combustion engine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20110117 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA RS |
|
DAX | Request for extension of the european patent (deleted) | ||
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: VOLKSWAGEN AKTIENGESELLSCHAFT |
|
17Q | First examination report despatched |
Effective date: 20150529 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20151127 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 783412 Country of ref document: AT Kind code of ref document: T Effective date: 20160415 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502009012309 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 8 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20160323 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160623 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160624 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160723 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160725 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R026 Ref document number: 502009012309 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160630 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 |
|
PLBI | Opposition filed |
Free format text: ORIGINAL CODE: 0009260 |
|
PLAX | Notice of opposition and request to file observation + time limit sent |
Free format text: ORIGINAL CODE: EPIDOSNOBS2 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
26 | Opposition filed |
Opponent name: PRUEFREX ENGINEERING E MOTION GMBH & CO. KG Effective date: 20161222 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160623 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160630 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160630 |
|
PLBB | Reply of patent proprietor to notice(s) of opposition received |
Free format text: ORIGINAL CODE: EPIDOSNOBS3 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160603 Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 9 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 783412 Country of ref document: AT Kind code of ref document: T Effective date: 20160603 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160603 |
|
PLBP | Opposition withdrawn |
Free format text: ORIGINAL CODE: 0009264 |
|
PLBD | Termination of opposition procedure: decision despatched |
Free format text: ORIGINAL CODE: EPIDOSNOPC1 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R100 Ref document number: 502009012309 Country of ref document: DE |
|
PLBM | Termination of opposition procedure: date of legal effect published |
Free format text: ORIGINAL CODE: 0009276 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: OPPOSITION PROCEDURE CLOSED |
|
27C | Opposition proceedings terminated |
Effective date: 20171216 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20090603 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160603 Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160323 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 10 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230523 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20240618 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240630 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20240625 Year of fee payment: 16 |