DE102015209392B4 - Method for controlling a switching process of a valve and control unit - Google Patents

Abstract

Method for controlling a switching operation of a valve (30) of an internal combustion engine (10),
wherein before the switching operation, a first valve cross-section of the valve (30) is provided for controlling an air mass in the internal combustion engine (10),
wherein a second valve cross-section of the valve (30) to be actuated after the switching process is provided,
wherein at least one first control parameter of the internal combustion engine (10) is provided before the switching operation,
- wherein the internal combustion engine (10) is controlled before the switching operation in dependence on the first control parameter and the first valve cross section,
wherein a first torque (M1) emitted by the internal combustion engine (10) is calculated on the basis of a first parameter model, the first control parameter and the first valve cross-section,
wherein, based on the first parameter model, the first control parameter and the second valve cross-section, a second torque (M2) which can be provided by the internal combustion engine (10) after the switching operation is calculated,
wherein a difference (ΔM) is determined from the first torque (M1) and the second torque (M2),
wherein on the basis of the second valve cross-section, the difference (ΔM) of the torque, the first torque and a second parameter model, at least one second control parameter is determined such that the difference (ΔM) of the torque compared to the calculated difference (ΔM) is reduced,
wherein, after the switching operation, the internal combustion engine is controlled in dependence on the second control parameter and the second valve cross section,
- Wherein a first throttle valve position of a throttle valve (55) of the internal combustion engine (10) and a first Compressor position of a compressor (60), in particular a turbocharger or a compressor, are provided as a first control parameter,
wherein a second throttle valve position, a predefined time interval and a third throttle valve position are determined on the basis of the second parameter model,
wherein the throttle valve (55) is moved from the first throttle valve position into the second throttle valve position as a function of the time interval before the switching process of the valve (30),
wherein the throttle valve (55) is moved from the second throttle valve position to the third throttle valve position substantially at the time of the switching operation,
wherein a second compressor position is determined on the basis of the second parameter model,
- Wherein, depending on the time interval before the switching operation of the compressor (60) is moved from the first compressor position to the second compressor position.

Description

The invention relates to a method according to claim 1 and a control device according to claim 11.

From the DE 102 58 803 B4 a method for controlling a switching operation in the operation of an internal combustion engine is known in which a possibly generated by the switching operation torque jump is avoided or at least reduced.

From the DE 102 39 397 A1 For example, a method for operating an internal combustion engine of a motor vehicle is known. The internal combustion engine has a combustion chamber into which fuel can be injected and / or gas can be supplied. The method switches between a fuel injection and a gas supply.

From the 10 2010 029 749 A1 a method for controlling a torque curve of a lean-running internal combustion engine is known, wherein the internal combustion engine comprises at least one valve lift changing device for changing the lift characteristics of the intake valves, and a filling change device for changing a filling, in particular a throttle valve, and an ignition device In a switching phase, the valve lift changing device changes at least one stroke of at least one intake valve, wherein a lean running phase during which the combustion air ratio takes a value greater than one begins when an ignition angle exceeds a maximum ignition angle.

It is an object of the invention to provide an improved method and an improved control unit.

This object is achieved by means of a method according to claim 1 and by means of an improved control device according to claim 11.

• - wobei auf Grundlage des zweiten Parametermodells eine zweite Drosselventilstellung, ein vordefiniertes Zeitintervall und eine dritte Drosselventilstellung ermittelt wird,
• - wobei in Abhängigkeit des Zeitintervalls vor dem Umschaltvorgang des Ventils (30) das Drosselventil (55) von der ersten Drosselventilstellung in die zweite Drosselventilstellung verfahren wird,
• - wobei im Wesentlichen im Zeitpunkt des Umschaltvorgangs das Drosselventil (55) von der zweiten Drosselventilstellung in die dritte Drosselventilstellung verfahren wird,
• - wobei auf Grundlage des zweiten Parametermodells eine zweite Verdichterstellung ermittelt wird,
• - wobei in Abhängigkeit des Zeitintervalls vor dem Umschaltvorgang der Verdichter (60) von der ersten Verdichterstellung in die zweite Verdichterstellung verfahren wird.

According to the invention, it has been recognized that an improved method for controlling a switching process of a valve and an improved control unit can be provided by providing a first valve cross section of the valve for controlling an air mass in the internal combustion engine before the switching operation, wherein a second valve cross section to be triggered after the switching operation the valve is provided, wherein at least a first control parameter of the internal combustion engine is provided before the switching operation, wherein the internal combustion engine is controlled before the switching operation in response to the first control parameter and the first valve cross section, based on a first parameter model, the first control parameter and the first valve cross section calculated by the internal combustion engine first torque is calculated, based on the first parameter model, the first control parameter and the second Ventilquersch a second torque which can be provided by the internal combustion engine after the switching operation is calculated, wherein a difference between the first torque and the second torque is determined, wherein at least a second one based on the second valve cross section, the difference of the torque, the first torque and a second parameter model Control parameter is determined such that the difference of the torque compared to the calculated difference is reduced, wherein after the switching operation in response to the second control parameter and the second valve cross section, the internal combustion engine is controlled. Furthermore, a first throttle valve position of a throttle valve (55) of the internal combustion engine (10) and a first compressor position of a compressor (60), in particular a turbocharger or a compressor, are provided as the first control parameter,

• wherein a second throttle valve position, a predefined time interval and a third throttle valve position are determined on the basis of the second parameter model,
• wherein the throttle valve (55) is moved from the first throttle valve position into the second throttle valve position as a function of the time interval before the switching process of the valve (30),
• wherein the throttle valve (55) is moved from the second throttle valve position to the third throttle valve position substantially at the time of the switching operation,
• wherein a second compressor position is determined on the basis of the second parameter model,
• - Wherein, depending on the time interval before the switching operation of the compressor (60) is moved from the first compressor position to the second compressor position.

In this way, a torque jump when switching the valve cross section from the first valve cross section to the second valve cross section is avoided. This leads to increased ride comfort and at the same time to a reduced load on components in the drive train of the motor vehicle.

In one embodiment, the first control parameter is a first ignition angle of the internal combustion engine and / or a first air mass. Additionally or alternatively, the second control parameter is a second ignition angle of the internal combustion engine.

In a further embodiment, a minimum firing angle and a base firing angle are provided as a first control parameter, the minimum firing angle and a base firing angle being taken into account in the determination of the second firing angle, the base firing angle being defined as the earliest permissible crank angle up to which no knocking combustion in the firing angle is defined Internal combustion engine (10) takes place, where understood by a minimum focal angle of the crankshaft angle at which still a combustion of a fuel mixture (160) in a cylinder (15) can be started.

In a further embodiment, a first valve lift of an intake valve is provided as the first valve cross-section, and a second valve lift of the intake valve of the internal combustion engine is provided as the second valve cross-section.

In a further embodiment, based on the second valve cross-section, the first control parameter and a predictive model, a second air mass is determined, wherein the second air mass is taken into account in determining the second torque.

In a further embodiment, based on the second parameter model, a third compressor position of the compressor (60) is determined, wherein the compressor is moved from the second compressor position to the third compressor position substantially at the time of switching the valve.

In a further embodiment, the second control parameter for a next combustion cylinder of the internal combustion engine, preferably at least 360 degrees crankshaft angle, before the start of ignition of fuel gas in the cylinder, is determined.

In a further embodiment, the difference of the torque is compared with a predefined threshold value, wherein a release signal for switching the first valve cross-section to the second valve cross-section is provided as a function of a result of the comparison.

In a further embodiment, the second parameter model has an optimization stage, wherein a distance of the second ignition angle to the base combustion angle and the difference is reduced by means of the optimization stage.

In a further embodiment, the first parameter model is designed as a forward model and the second parameter model at least partially as a backward model of the first parameter model and / or wherein the first and / or the second parameter model as a mathematical function and / or algorithm and / or map and / or characteristic and / or parametric model is formed, and / or wherein the second parameter model uses at least one output variable of the first parameter model as an input variable.

• 1 eine schematische Darstellung einer Brennkraftmaschine;
• 2 ein Ablaufdiagramm eines Verfahrens zum Betrieb der in 1 gezeigten Brennkraftmaschine; und
• 3 eine Weiterbildung des in 2 gezeigten Verfahrens;

darstellt.The above-described characteristics, features, and advantages of this invention, as well as the manner in which they are achieved, will become clearer and more clearly understood in connection with the following description of the embodiments which will be described in connection with the drawings

• 1 a schematic representation of an internal combustion engine;
• 2 a flowchart of a method for operating the in 1 shown internal combustion engine; and
• 3 a further education of in 2 shown method;

represents.

1 shows a schematic representation of an internal combustion engine 10 , The internal combustion engine 10 is connected at an output side with a drive train of a motor vehicle. The internal combustion engine 10 puts on the output side 11 a torque M for driving the motor vehicle ready. The exit side 11 can be a clutch.

The internal combustion engine 10 is of the Otto type. The internal combustion engine 10 has several cylinders 15 on, of which in 1 one is indicated. Furthermore, the internal combustion engine comprises 10 an intake tract 20 , an exhaust tract 25 , an inlet valve 30 , An exhaust valve, not shown, an actuator with an adjustment 35 for discretely adjusting a valve lift of the intake valve designed as a valve cross-section 30 , an injection valve 40 for injecting fuel, a spark plug 45 with a firing angle adjustment 50 , one in the intake tract 20 arranged throttle valve 55 in the form of a throttle and one in the intake tract 20 arranged compressor 60 , Furthermore, the internal combustion engine comprises 10 a control unit 65 and an operation control device 70 ,

The control unit 65 comprises a control device 75 , a first store 80 and a first interface 85 , The control device 75 is about a first connection 90 with the first memory 80 connected. The first interface 85 is with the first control device 75 by means of a second connection 95 connected.

In the first store 80 the control device 75 is a first parameter model and a second one Parameter model of the internal combustion engine 10 stored. The first and / or the second parameter model and / or prediction model can be embodied as a mathematical function and / or algorithm and / or characteristic diagram and / or characteristic curve and / or parametric model. Further, in memory 80 stored a predefined threshold. The threshold is exemplified in the embodiment as a tolerance band.

The first and / or the second parameter model form a physical model of the internal combustion engine 10 out. In this case, the first parameter model differs from the second parameter model in that the input variables of the first parameter model are partially different from the input parameters of the second parameter model. In this case, an output variable of the first parameter model is also one of the input variables of the second parameter model.

The operating control unit 70 includes an operation control device 100 , a second memory 105 and a second interface 110 , The second memory 105 is by means of a third connection 115 with the operation control device 100 connected. The second interface 110 is by means of a fourth connection 120 with the operation control device 100 connected.

The second interface 110 is by means of a fifth connection 125 with the first interface 85 connected. Further, the second interface 110 by means of a sixth connection 130 with the spark plug 45 and by means of a seventh connection 135 with the ignition angle adjustment 50 connected. The adjusting device 35 is by means of an eighth connection 140 with the second interface 110 connected. Furthermore, the injection valve 40 by means of a ninth connection 145 and the throttle valve 55 by means of a tenth connection 150 with the second interface 110 connected.

The compressor 60 is designed in the embodiment as an adjustable compressor, in particular as a turbocharger or compressor. The compressor 60 is for controlling the operating control unit 70 by means of an eleventh connection 155 with the second interface 110 connected.

The operation control device 100 controls as a function of one in the second memory 105 stored control algorithm via the second interface 110 provided control signals the internal combustion engine 10 , It is by means of the intake 20 a fuel air mixture 160 or air in the cylinder 15 promoted.

The control or, if appropriate, the control method are known in principle to the person skilled in the art, so that this is only discussed insofar as it is necessary for the understanding of the method described below for controlling switching operations. As part of the control or regulation of the internal combustion engine is by means of the adjustment 35 based on a control signal of the operation control device 70 the valve lift between a first valve cross-section formed as the first valve and a valve formed as a second valve second valve lift of the intake valve 30 changed.

2 shows a flowchart of a method for operating the in 1 shown internal combustion engine 10 ,

In a first process step 300 represents the operation control unit 70 at the second interface 110 a first information signal ready. The first information signal is via the fifth connection 125 transferred to the first interface and detected by this. The first interface 85 represents the first information signal of the control device 75 ready.

The first information signal includes cylinder-dependent information from the operation control device 70 controlled internal combustion engine 10 , In this case, the first information signal includes information about the current first valve lift of the intake valve 30 (First valve cross-section) and the new, deviating from the current valve after the switching operation controlled second valve lift (second valve cross-section). For example, in the embodiment, the first valve lift should be less than the second valve lift. Of course, it is also conceivable that the second valve lift is less than the first valve lift. The operating control unit 70 controls the internal combustion engine 10 before the switching operation based on the first control parameter and the first valve lift.

Further, the first information signal includes information about a timing of switching the valve lift of the intake valve 30 and a first control parameter. In the embodiment, the first control parameter has as characteristics a first ignition angle, a base ignition angle, a minimum focal angle and a first air mass. In this case, the base ignition angle is defined as the earliest permissible crankshaft angle, up to which no knocking combustion in the internal combustion engine 10 takes place. Here, a minimum focal angle is understood to mean the crankshaft angle, to which still a combustion of the fuel-air mixture 160 is bootable. Of course, it is also conceivable that the first Control parameters further characteristics of the internal combustion engine 10 includes.

In a multi-cylinder internal combustion engine 10 determines the controller 75 based on the first information signal and a comparison of the information between the cylinders in a first method step 300 which of the cylinders 15 is ignited next. In this case, the control device leads 75 the method steps described below for the next firing cylinder, preferably in a 4-cylinder engine at least 360 degrees crankshaft angle, before igniting the cylinder by.

In a second process step 305 who is at the first procedural stage 300 follows, calculates the controller 75 on the basis of the first parameter model as well as on the basis of the first valve lift and the first control parameter on by the internal combustion engine 10 at the exit side 11 , preferably provided on a clutch first torque M1. In this case, the first valve lift and the first control parameter are input variables of the first parameter model and the first torque M1 is an output variable of the first parameter model.

In this case, losses which reduce the first torque M1 to be output can also be taken into account in the first parameter model. In particular friction losses and / or flow losses and / or pumping losses of the air and / or of the air fuel mixture and / or of an exhaust gas in the internal combustion engine may occur 10 to be taken into account.

In a third process step 310 , the second step 305 follows, the calculated first torque M1 in the first memory 80 by the control device 75 stored.

In a fourth process step 315 who is at the first procedural stage 300 follows and preferably parallel to the second process step 305 is performed, the controller determines a second air mass based on the predictive model, the first control parameter, and the second valve lift. The predictive model can also be integrated into the first parameter model.

Furthermore, the controller calculates 75 on the basis of the first parameter model, the first control parameter, the second valve lift and the second air mass by the internal combustion engine 10 after the switching operation of the intake valve 30 at the exit side 11 the internal combustion engine 10 deployable second torque M2. Here, in the first control parameter instead of the first air mass, the determined second air mass is taken into account in the calculation of the second torque M2. In this case, the second valve lift and the first control parameter and the second air mass are input variables of the first parameter model and the second torque M2 is the output variable of the first parameter model.

An example of the first valve lift enlarged second valve lift of the intake valve 30 leads to an increased filling of the cylinder 15 with fuel air mixture 160 and by the increased filling to a corresponding increase in the torque M at the output side 11 the internal combustion engine 10 ,

For example, assume that with the first valve lift the internal combustion engine 10 provides the first torque M1 of 100 Nm, for example, an increase in the first valve lift leads to the second valve lift, so that the cylinder at the second valve lift 15 compared to the first valve lift with 50 percent more fuel air mixture 160 is filled, to a corresponding increase in the torque M on the output side 11 by 50 percent. This would result in the second valve lift on the output side 11 the second torque M2 of 150 Nm.

In a fifth process step 320 , the fourth step 315 follows, the calculated second torque M2 in the first memory 80 by the control device 75 stored.

In a sixth process step 325 , the third step 310 and to the fifth process step 320 follows, determines the controller 75 based on the first memory 80 stored first torque M1 and the second torque M2, a difference ΔM of the first torque M1 and the second torque M2.

In a seventh process step 330 , the sixth procedural step 325 follows, sets the controller 75 the result of the difference ΔM in the first memory 80 from.

In an eighth process step 335 compares the controller 75 the difference ΔM with the predefined threshold. For example, in the embodiment, the threshold is formed as a tolerance band. The tolerance band may for example have a width of ± 5 Nm. If the difference .DELTA.M outside the tolerance band, then the control device moves 75 with a ninth procedural step 340 continued. If the difference .DELTA.M within the tolerance band, so does the controller 75 the operating control unit 70 about the fifth connection 125 a release signal ready to the valve lift switching with the second valve lift by means of the adjusting device 35 perform. The operating control unit controls this 70 after the switching operation, the internal combustion engine 10 based on the first control parameter and the first valve lift.

In the ninth step 340 determines the controller 75 based on the difference of the torque ΔM and the first torque M1, the second parameter model and the second valve lift at least a second control parameter. In this case, the control device uses the second air mass within the scope of the first control parameter. In this case, the second air mass can be determined again as described above by means of the predictive model or the control device 70 takes into account the fourth step 315 determined second air mass.

The control device 75 selects the second control parameter such that by the internal combustion engine 10 After the switching operation, essentially deliverable torque M corresponds to the first torque M1 and thus the difference .DELTA.M compared to that in the sixth method step 325 calculated difference ΔM is reduced.

It can be taken into account in the second parameter model losses that affect the output second torque M2. In particular, friction losses, flow losses and / or pumping losses of the air and / or the air fuel mixture and / or an exhaust gas in the internal combustion engine 10 to be taken into account.

Here, the second valve lift and the difference ΔM of the torque and the base firing angle and the minimum firing angle and the second air mass input variables of the second parameter model and the second control parameter, the output of the second parameter model. Thus, the second parameter model at least partially forms a kind of "backward model" with respect to the first parameter model embodied as a "forward model". In other words, at least partially, the second parameter model is the inverse first parameter model.

The second control parameter can be a second ignition angle. Alternatively, it is also conceivable that the second control parameter one or more other characteristic (s) of the internal combustion engine 10 , For example, an amount of fuel through the injector 40 is provided and / or a third amount of air that is conveyed into the cylinder is. If the second firing angle is determined as the second control parameter, the control device takes into account the minimum firing angle and the base firing angle in determining the second firing angle.

The second parameter model may have an optimization stage, so that a second ignition angle has the smallest possible distance to the base combustion angle, so that an efficiency of the internal combustion engine 10 as high as possible. At the same time, the ignition angle is selected in the optimization stage such that the difference ΔM is as small as possible. The optimization stage can be designed, for example, as Pareto optimization.

In a tenth procedural step 345 represents the controller 75 the operating control unit 70 about the fifth connection 125 a second information signal on the second control parameter, for example, the second firing angle ready.

In an eleventh process step 350 switches the operating control unit 70 from the first valve lift to the second valve lift and takes into account the second control parameter and the second valve lift in the control method of the internal combustion engine 10 ,

By the example described above 50 percent increase in the filling of the cylinder 15 determines the controller 75 a relative to the first firing angle increased second firing angle, so that the spark plug 45 later after the switching so before the switching of the valve lift the fuel gas 160 in the cylinder 15 ignites. This puts the internal combustion engine 10 at their exit 11 Both before and after the switching operation, a substantially constant torque M ready. Another advantage is that of a stoichiometrically richer operation of the internal combustion engine to a stoichiometric lean operation of the internal combustion engine 10 can be switched without jumping on the output side 11 the torque of the internal combustion engine 10 is increased. As a result, a particularly low-jerk operation of the internal combustion engine 10 guaranteed. Furthermore, faster switching can be ensured from the first to the second valve lift, so that in addition the consumption of the internal combustion engine 10 this is reduced.

In the first, second and fourth process step 300 . 305 . 315 is of course also conceivable that further characteristics of the internal combustion engine 10 through the operation control unit 70 the control unit 65 be provided as first control parameters and by the controller 65 in the determination of the first and second torque M1, M2 taken into account.

3 shows a training of in 2 described method. In addition, in the first step of the process 300 as a first control parameter in addition to the first firing angle a first Throttle valve position of the throttle valve 55 provided as a further parameter of the first control parameter. Furthermore, in the first process step 300 a first compressor position of the compressor 60 provided as a further parameter of the first control parameter.

The second to eighth process steps 305 - 335 correspond to the in 2 described second to eighth method steps 305 - 335 , wherein the control device 75 taken into account in the determination of the torques M1, M2, the first compressor position and the first throttle valve position as the first control parameter.

In addition, is in memory 80 filed an intake model. The intake model may be different or identical to the predictive model. Furthermore, it is conceivable that the intake model is integrated in the second parameter model. The intake model reflects a physical behavior of the intake tract 25 the internal combustion engine 10 contrary. The intake model can be designed as a mathematical function and / or algorithm and / or characteristic map and / or characteristic curve and / or parametric model.

In the ninth procedural step 340 determines the controller 75 in addition to the in 2 described ninth method step 340 after determining the second control parameter based on the second control parameter and the intake model, a second throttle valve position, a predefined time interval and a third throttle valve position. Furthermore, based on the second control parameter and the intake model, a second compressor position of the compressor 60 determined. The predefined time interval defines a time before the changeover from the first valve lift to the second valve lift.

The second throttle valve position, the predefined time interval and the third throttle valve position and the second compressor position of the second information signal are from the controller 65 to the operating control unit 70 by means of the fifth connection 125 in the tenth procedural step 340 provided in the context of the second information signal.

In an eleventh process step 350 , the tenth procedural step 345 follows, controls the operation control unit 70 the throttle valve 55 such that the first throttle valve position is moved from the first throttle valve position to the second throttle valve position at a distance from the determined predefined time interval before the switching process. Essentially, at the same time, the compressor becomes 60 through the operation control unit 70 controlled such that the compressor 60 is moved from the first compressor position to the second compressor position.

In the embodiment, for example, the second throttle valve position with respect to the first throttle valve position is selected so that the second throttle valve position of a smaller opening of the throttle valve 55 equivalent. The second compressor position is chosen such that the compressor 60 a higher pressure in the intake tract 20 provides.

In a twelfth procedural step 355 At the time of the switching operation from the first valve lift to the second valve lift, the throttle valve 55 moved to the third throttle valve position. At the same time at the time of switching the compressor 60 moved from the second compressor position in the third compressor position. Also, after the switching operation, the operation control apparatus takes into account the second control parameter in the control process of the internal combustion engine 10 ,

This causes a backlog before the throttle valve in the time interval before switching 55 the one in the cylinder 15 to be conveyed air, which occurs during the switching operation of the intake valve 30 from the first valve position to the second valve position in the cylinder 15 flows and thus to an improved filling of the cylinder 15 leads. This is particularly relevant if the second valve position has a smaller valve lift than the first valve lift and thus an inlet cross-section of the inlet valve 30 at the second valve is less than the first valve.

This embodiment has the advantage that the torque M over the switching of the valve lift away on the output side 11 the internal combustion engine 10 can be kept very good constant.

It should be noted that the operating control unit 70 and the controller 65 are integrated, and the methods described above are performed by the integrated control unit. In particular, it is conceivable that the above-described control of the internal combustion engine 10 According to the prior art and the method described above are performed on a common processor.

Although the invention has been further illustrated and described in detail by the preferred embodiment, the invention is not limited by the disclosed examples, and other variations can be derived therefrom by those skilled in the art without departing from the scope of the invention.

LIST OF REFERENCE NUMBERS

10

Internal combustion engine

11

output side

15

cylinder

20

intake system

25

exhaust tract

30

intake valve

35

adjustment

40

Injector

45

spark plug

50

Ignition angle adjustment device

55

throttle valve

60

compressor

65

control unit

70

Operational control unit

75

control device

80

first memory

85

first interface

90

first connection

95

second connection

100

Operation controller

105

second memory

110

second interface

115

third connection

120

fourth connection

125

fifth connection

130

sixth connection

135

seventh connection

140

Eighth connection

145

ninth connection

150

tenth connection

155

Eleventh connection

160

Air-fuel mixture

300

first process step

305

second process step

310

third process step

315

fourth process step

320

fifth process step

325

sixth process step

330

seventh process step

335

eighth process step

340

ninth process step

345

tenth process step

350

Eleventh process step

355

twelfth process step

Claims (11)

Method for controlling a switching operation of a valve (30) of an internal combustion engine (10), wherein before the switching operation, a first valve cross-section of the valve (30) for controlling an air mass in the internal combustion engine (10) is provided, - wherein a second to be controlled after the switching operation Valve cross section of the valve (30) is provided, - wherein at least a first control parameter of the internal combustion engine (10) is provided before the switching operation, - wherein the internal combustion engine (10) is controlled before the switching operation in response to the first control parameter and the first valve cross section, - on the basis of a first parameter model, the first control parameter and the first valve cross section, a first torque (M1) output by the internal combustion engine (10) is calculated, - based on the first parameter model, the first control parameter and the second valve cross section, a first torque (M1) generated by the internal combustion engine (10 ) wherein a difference (ΔM) from the first torque (M1) and the second torque (M2) is determined, - wherein based on the second valve cross-section, the difference (.DELTA.M) of the Torque, the first torque and a second parameter model at least a second control parameter is determined such that the difference (.DELTA.M) of the torque compared to the calculated difference (.DELTA.M) is reduced, - wherein after the switching operation in dependence on the second control parameter and the second valve cross-section Wherein a first throttle valve position of a throttle valve (55) of the internal combustion engine (10) and a first compressor position of a compressor (60), in particular a turbocharger or a compressor, are provided as the first control parameter, - based on the second parameter model, a second throttle valve position , one predefined time interval and a third throttle valve position is determined, - wherein the throttle valve (55) is moved from the first throttle valve position to the second throttle valve position as a function of the time interval before the switching operation of the valve (30), - wherein substantially at the time of the switching operation, the throttle valve ( 55) is moved from the second throttle valve position to the third throttle valve position, - wherein a second compressor position is determined on the basis of the second parameter model, - being moved depending on the time interval before the switching operation of the compressor (60) from the first compressor position to the second compressor position , Method according to Claim 1 - wherein the first control parameter is a first ignition angle of the internal combustion engine (10) and / or a first air mass, - and / or wherein the second control parameter is a second ignition angle of the internal combustion engine (10). Method according to Claim 2 in which a minimum firing angle and a base firing angle are provided as the first control parameter, wherein in the determination of the second firing angle the minimum firing angle and a base firing angle are taken into account, wherein the base firing angle is defined as the earliest permissible crankshaft angle up to which no knocking combustion in the internal combustion engine (10) takes place, - is understood by a minimum focal angle of the crankshaft angle, to which even a combustion of a fuel mixture (160) in a cylinder (15) can be started. Method according to one of Claims 1 to 3 , wherein a first valve lift of an intake valve (30) is provided as the first valve cross-section and a second valve lift of the intake valve (30) of the internal combustion engine (10) is provided as the second valve cross-section. Method according to one of Claims 1 to 4 in which a second air mass is determined on the basis of the second valve cross section, the first control parameter and a predictive model, wherein the second air mass is taken into account in the determination of the second torque. Method according to one of Claims 1 to 5 wherein - based on the second parameter model, a third compressor position of the compressor (60) is determined, - wherein the compressor (60) is moved from the second compressor position to the third compressor position substantially at the time of the switching operation of the valve (30). Method according to one of Claims 1 to 6 wherein the second control parameter for a next burning cylinder (15) of the internal combustion engine (10), preferably at least 360 degrees crankshaft angle before the start of igniting fuel gas (160) in the cylinder (15) is determined. Method according to one of Claims 1 to 7 , - wherein the difference (ΔM) of the torque is compared with a predefined threshold value, - is provided depending on a result of the comparison, a release signal for switching the first valve cross section on the second valve cross section. Method according to one of Claims 3 to 8th , wherein the second parameter model has an optimization stage, wherein by means of the optimization stage, a distance of the second ignition angle to the base combustion angle and the difference (ΔM) are reduced. Method according to one of Claims 1 to 9 , wherein the first parameter model is designed as a forward model and the second parameter is at least partially designed as a backward model of the first parameter model, and / or wherein the first and / or the second parameter model is a mathematical function and / or algorithm and / or characteristic map and / or or characteristic curve and / or parametric model is formed, - and / or wherein the second parameter model uses at least one output variable of the first parameter model as an input variable. Control unit (65) which is adapted to a method according to one of Claims 1 to 10 perform.

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