Method of controlling an internal combustion engine

Abstract

A method of controlling an internal combustion engine is described; in this method, at least two operating states are differentiated, at least one operating variable of the engine being controlled, a setpoint torque being predetermined on the basis of the optimum operating point for the respective operating state and on the basis of the position of a throttle valve operated by the driver, the value of at least one operating variable to be output being determined from the setpoint torque. A cylinder-individual firing angle retardation value is predetermined by a knock control system, so that the cylinder-individual firing angle retardation value is taken into account directly in calculating the setpoint torque.

Description

BACKGROUND INFORMATION

[0001] The present invention relates to a method of controlling an internal combustion engine according to the preamble of the independent patent claim.

[0002] Such a method is already known from Unexamined German Patent 19 715 774. This publication describes a method which is used to control an internal combustion engine, at least one operating variable of the engine being controlled. An example of an operating variable here is the firing angle. The at least one operating variable is determined on the basis of a setpoint torque, which is derived from the optimum operating point for the respective operating state and from the position of the throttle valve operated by the driver. A firing angle retardation resulting from knock control is used to determine a base firing angle efficiency. In certain operating states, however, this base firing angle efficiency is not used to form a setpoint torque, but instead the setpoint torque is determined on the basis of a minimum value selection from efficiency values of other engine characteristic maps. Thus in certain operating states, e.g., idling or partial load, a knock control correction of the setpoint torque and thus also of the firing angle or other operating variables is not adequately ensured.

ADVANTAGES OF THE INVENTION

[0003] The method according to the present invention having the features of claim 1 have the advantage over the related art that a cylinder-individual firing angle adjustment value derived from knock control is taken into account directly in determining the setpoint torque and thus for all operating states.

[0004] Advantageous refinements of the method characterized in the main claim are possible through the measures characterized in the subclaims. It is especially advantageous if the firing angle adjustment value for the individual cylinder is first averaged over an engine cycle before the resulting value is used directly to determine the setpoint torque because the setpoint torque is not a cylinder-specific variable and thus the operating variables calculated from the setpoint torque do not represent cylinder-specific values.

[0005] It is also advantageous to use the setpoint torque to calculate the firing angle to be output; the firing angle is calculated on the basis of the torque and thus has a knock control correction independently of the operating state of the internal combustion engine.

[0006] It is also advantageous that the calculated firing angle is corrected by a value which includes the cylinder-individual knock control correction because in this way the requirements of each individual cylinder may be taken into account. It is advantageous that the difference between the average of the cylinder-individual firing angle retardation values and the cylinder-individual firing angle retardation value assigned to the particular cylinder is added to a calculated setpoint firing angle. In this way, the firing angle retardation for the individual cylinder may be taken into account without influencing the setpoint torque, which is not a cylinder-individual variable.

[0007] In calculating the firing angle retardation value, it is advantageous that the cylinder-individual firing angle retardation value is composed of an instantaneous firing angle retardation value and an anti-knock value, the cylinder-individual firing angle retardation value being determined on the basis of the knocking signal for the respective cylinder, and the anti-knock value being based on knock prevention in certain operating states or on knock prevention over a longer period of time.

[0008] For the starting phase, it is advantageous to take into account an additional firing angle retardation value for the calculation of the cylinder-individual firing angle retardation value because this requires the temperature of the engine in the cylinder and in the exhaust system.

DRAWINGS

[0009] The present invention is explained in greater detail below on the basis of the embodiments illustrated in the drawing. FIG. 1 shows, on the basis of a flow chart, a method of controlling an engine; FIG. 2 shows another method according to the present invention on the basis of an additional flow chart.

DESCRIPTION OF THE EXEMPLARY EMBODIMENTS

[0010] FIG. 1 shows a method according to the present invention for controlling an engine on the basis of a flow chart. The starting point for this method in step 2 is pilot control firing angle efficiency eta_zw_vst, which is described in Unexamined German Patent 197 15 774 and is determined by a minimum value selection from a predetermined firing angle efficiency and a base firing angle efficiency. In a step 4, using a characteristic curve which will not be described in greater detail here, pilot control firing angle efficiency eta_zw_vst is converted to a respective firing angle which is labeled as dzwvg. In step 6, a cylinder-individual retardation value dzwkrd is supplied by a knock control system. This cylinder-individual retardation value dzwkrd is subtracted in step 8 from firing angle value dzwvg, yielding firing angle difference dzwvgd. In a next step 10 the firing angle difference dzwvgd is averaged over an entire cycle of the engine. This yields the average of firing angle differences dzwvgdm. In a subsequent step 12, this average of firing angle differences dzwvgdm is converted to an efficiency etazwvgd by using a second characteristic curve, which is not described in greater detail here. Setpoint torque mi_fa is calculated by multiplying this efficiency etazwvgd by optimum induced torque mi_opt in a subsequent step 14. Setpoint torque mi_fa is calculated by analogy with the method described in Unexamined German Patent 197 15 774, which is described there on the basis of multiplier element 124. It is thus possible to calculate setpoint torque mi_fa for all operating states by taking into account a firing angle adjustment value from the knock control. Since this method is integrated into the torque-based method of engine control described in Unexamined German Patent 197 15 774, it was necessary to start from an efficiency, i.e., pilot control firing angle efficiency mi_zw vst, and calculate a new efficiency etazwvgd which takes into account the firing angle retardation from the knock control. The conversion to a firing angle in step 4 is necessary because only values of the same type, i.e., firing angles, may be compared. Firing angle differential values dzwvgd are averaged because setpoint torque mi_fa calculated therefrom is an average over an engine cycle and is taken into account as such in calculating other operating variables of the engine. In another embodiment, averaging may also be performed by averaging retardation value dzwkrd just before being subtracted from firing angle value dzwvg.

[0011] FIG. 2 illustrates another embodiment of the method according to the present invention for controlling an engine. The method illustrated there includes steps having reference numbers that have already been explained in conjunction with FIG. 1. These steps will not be explained again here because they include the same method steps. In this embodiment, cylinder-individual retardation value dzwkrd is averaged over one engine cycle in step 16. This yields an average value dzwkrdm. In a subsequent step 18, average dzwkrdm determined in step 16 is subtracted from cylinder-individual retardation value dzwkrd, yielding differential value ddzwkrd in step 18. In addition, by analogy with the procedure described in Unexamined German Patent 197 15 774, a setpoint firing angle zw_soll is calculated from setpoint torque mi_fa determined in step 14; this procedure is denoted here as step 20. In step 22 the differential value ddzwkrd determined in step 18 is added to this setpoint firing angle, yielding firing angle zw_out to be output. The procedure described on the basis of FIG. 2 then yields the result that a cylinder-individual retardation is performed in the case of a setpoint firing angle in which an average firing angle retardation value has been taken into account. Thus, the properties of the individual cylinders may be taken into account optimally in outputting the firing angle.

[0012] In the case of the exemplary embodiments described on the basis of both FIG. 1 and FIG. 2, a cylinder-individual firing angle retardation dwkr, which depends on the operating point, and knock prevention dzwks may be taken into account in a preferred exemplary embodiment in the cylinder-individual retardation value dzwkrd supplied by knock control, in such a manner that values dwkr and dzwks are added to cylinder-individual retardation value dzwkrd. This ensures that both knock prevention and a firing angle retardation, which is determined from knock control in the respective operating point for the respective cylinder and is derived from certain operating states or a retardation extending over longer periods of time will be taken into account. In particular, a firing angle retardation dzwwl which is also added to values dwkr and dzwks may also be taken into account to yield dzwkrd (i.e., dwkr+dzwks+dzwwl=dzwkrd) so that another firing angle retardation value is taken into account in warming up the engine. This is necessary because of the temperature conditions prevailing in the cylinder and in the exhaust system of the engine.

Claims

1. A method of calculating a firing angle of an internal combustion engine in which a position of a throttle valve is preselected by a driver, a setpoint torque (mi_fa) being calculated by multiplying a firing angle efficiency (etazwvgd) by an optimum torque (mi_opt), a setpoint of the firing angle (zw_soll) being determined from the setpoint torque (mi_fa), a cylinder-individual firing angle retardation value (dzwkrd) being predetermined by a knock control system, wherein the cylinder-individual firing angle retardation value (dzwkrd) is taken into account directly in calculating the firing angle efficiency (etazwvgd).

2. The method as recited in claim 1, wherein the firing angle efficiency (etazwvgd) is determined from a resulting firing angle retardation value (dzwvgdm), the resulting firing angle retardation value (dzwvgdm) being formed as the average of the cylinder-individual firing angle retardation values (dzwvgd) over an engine cycle.

3. The method as recited in one of the preceding claims, wherein the cylinder-individual firing angle retardation value (dzwkrd) is additionally taken into account in forming the value of the firing angle (zw_out) to be output, in a manner such that the difference (ddzwkrd) between the average of the cylinder-individual firing angle retardation values (dzwkrdm) and the cylinder-individual firing angle retardation value (dzwkrd) assigned to the particular cylinder is added to a setpoint firing angle (zw_soll).

4. The method as recited in one of the preceding claims, wherein the cylinder-individual firing angle retardation value (dzwkrd) is composed of an anti-knock value (dzwks) and a firing angle retardation value (dwkr), which depends on the operating point.

5. The method as recited in claim 4, wherein a retardation value for the starting phase (dzwwl) is additionally taken into account for the cylinder-individual firing angle retardation values.