Sato, Masahiro (Saitama-ken, JP)
Saito, Mitsunobu (Saitama-ken, JP)
Tagami, Hiroshi (Saitama-ken, JP)
Higashitani, Kosuke (Saitama-ken, JP)
Plaque It!
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| JP200173834 | March, 2001 | |||
| JP2001152929 | June, 2001 | AIR-FUEL RATIO CONTROL DEVICE FOR VARIABLE VALVE SYSTEM ENGINE | ||
| JP2001164963 | June, 2001 | INTAKE AIR AMOUNT CONTROL DEVICE FOR ENGINE | ||
| JP2002256930 | September, 2002 | INTAKE CONTROL DEVICE OF INTERNAL COMBUSTION ENGINE | ||
| JP2004100575 | April, 2004 | CONTROL UNIT OF INTERNAL COMBUSTION ENGINE |
1. A control system for an internal combustion engine, which controls an amount of intake air drawn into a cylinder of the engine by a variable intake mechanism and controls an amount of fuel to be supplied to a combustion chamber, to thereby control an air-fuel ratio of a mixture in the combustion chamber, comprising: operating condition parameter-detecting means for detecting an operating condition parameter indicative of an operating condition of the variable intake mechanism; air-fuel ratio parameter-detecting means for detecting an air-fuel ratio parameter indicative of an air-fuel ratio of exhaust gases flowing through an exhaust passage of the engine; target air-fuel ratio-calculating means for calculating a target air-fuel ratio to which the air-fuel ratio of the mixture is to be controlled; air-fuel ratio control parameter-calculating means for calculating an air-fuel ratio control parameter for controlling an air-fuel ratio of the mixture such that the air-fuel ratio becomes equal to the target air-fuel ratio, according to the air-fuel ratio parameter; correction means for correcting the operating condition parameter according to one of the air-fuel ratio control parameter and the air-fuel ratio parameter; and fuel amount-determining means for determining the amount of fuel according to the corrected operating condition parameter and the air-fuel ratio control parameter.
2. A control system as claimed in claim 1, wherein said correction means calculates a control state value indicative of a state of control of the air-fuel ratio of the mixture based on one of the air-fuel ratio control parameter and the air-fuel ratio parameter, calculates a statistically processed value by performing a predetermined sequential statistical process on the control state value, and corrects the operating condition parameter according to the statistically processed value.
3. A control system as claimed in claim 2, wherein when the statistically processed value is outside a predetermined range, said correction means corrects the operating condition parameter according to the statistically processed value such that the statistically processed value comes to be within the predetermined range, and holds an amount of correction of said operating condition parameter at a fixed value when the statistically processed value is within the predetermined range.
4. A control system as claimed in any one of claims 1 to 3, further comprising: air flow rate-detecting means for detecting a flow rate of air flowing through an intake passage of the engine; and load parameter-detecting means for detecting a load parameter indicative of load on the engine, and wherein said fuel amount-determining means determines the amount of fuel according to the corrected operating condition parameter and the air-fuel ratio control parameter when the load parameter is within a first predetermined range, and determines the amount of fuel according to the flow rate of air and the air-fuel ratio control parameter when the load parameter is within a second predetermined range different from the first predetermined range.
5. A control system for an internal combustion engine, which controls an amount of intake air drawn into a cylinder of the engine by a variable intake mechanism, and controls ignition timing and an air-fuel ratio of a mixture in a combustion chamber, comprising: operating condition parameter-detecting means for detecting an operating condition parameter indicative of an operating condition of the variable intake mechanism; air-fuel ratio parameter-detecting means for detecting an air-fuel ratio parameter indicative of an air-fuel ratio of exhaust gases flowing through an exhaust passage of the engine; target air-fuel ratio-setting means for setting a target air-fuel ratio to which the air-fuel ratio of the mixture is to be controlled; air-fuel ratio control means for controlling the air-fuel ratio of the mixture such that the air-fuel ratio becomes equal to the target air-fuel ratio, according to the air-fuel ratio parameter; correction means for correcting the operating condition parameter according to one of a state of control of the air-fuel ratio of the mixture by said air-fuel ratio control means, and the air-fuel ratio parameter; and ignition timing-determining means for determining the ignition timing according to the corrected operating condition parameter.
6. A control system as claimed in claim 5, wherein said air-fuel ratio control means calculates an air-fuel ratio control parameter for controlling the air-fuel ratio of the mixture such that the air-fuel ratio becomes equal to the target air-fuel ratio, according to the air-fuel ratio parameter, and wherein said correction means calculates a control state value indicative of a state of control of the air-fuel ratio of the mixture based on one of the air-fuel ratio control parameter and the air-fuel ratio parameter, calculates a statistically processed value by performing a predetermined sequential statistical process on the control state value, and corrects the operating condition parameter according to the statistically processed value.
7. A control system as claimed in claim 5 or 6, further comprising: air flow rate-detecting means for detecting a flow rate of air flowing through an intake passage of the engine; and load parameter-detecting means for detecting a load parameter indicative of load on the engine, and wherein said ignition timing-determining means determines the ignition timing according to the corrected operating condition parameter when the load parameter is within a first predetermined range, and determines the ignition timing according to the flow rate of air when the load parameter is within a second predetermined range different from the first predetermined range.
CROSS-REFERENCE TO RELATED APPLICATION
This application is a National Stage entry of International Application No. PCT/JP2005/010692, filed Jun. 10, 2005, the entire specification claims and drawings of which are incorporated herewith by reference.
FIELD OF THE INVENTION
The present invention relates to a control system for an internal combustion engine, which controls the amount of intake air drawn into cylinders of the engine via a variable intake mechanism and controls an air-fuel ratio and ignition timing.
BACKGROUND ART
Conventionally, a control system for an internal combustion engine, which controls the amount of intake air drawn into cylinders of the engine via a variable intake mechanism, has been proposed in Patent Literature 1. This control system is comprised of an air flow sensor that detects the flow rate of air flowing through an intake passage of the engine, a crank angle sensor that detects a state of rotation of a crankshaft, an accelerator pedal opening sensor that detects an opening of an accelerator pedal (hereinafter referred to as “the accelerator pedal opening”), and a controller to which are input detection signals from these sensors. The controller calculates an engine speed based on the detection signal from the crank angle sensor, and the amount of intake air (intake air amount) based on the detection signal from the air flow sensor. Further, the engine is provided with a throttle valve mechanism and a variable valve lift mechanism as variable intake mechanisms. The throttle valve mechanism changes the flow rate of air flowing through the intake passage as desired, and the variable valve lift mechanism changes the lift of each intake valve (hereinafter referred to as “the valve lift”) as desired.
As will be described hereinafter, in the control system, the intake air amount is controlled by the controller. First, it is determined based on the engine speed, the accelerator pedal opening, and the intake air amount, in what load region the engine is operating. Then, when it is determined that the engine is in a low-engine speed and low-load region including an idling region, the valve lift is controlled to a predetermined low lift by the variable valve lift mechanism, and the opening of the throttle valve is controlled to a value corresponding to the engine speed and the accelerator pedal opening by the throttle valve mechanism. On the other hand, when it is determined that the engine is between a medium-engine speed and medium-load region and a high-engine speed and high-load region, the throttle valve is controlled to a fully-open state, and the valve lift is controlled to a value corresponding to the engine speed and the accelerator pedal opening.
[Patent Literature 1] Japanese Laid-Open Patent Publication (Kokai) No. 2003-254100
In the control system proposed in Patent Literature 1, it is sometimes impossible to properly calculate the intake air amount, due to a low resolution of the air flow sensor. For example, some type of internal combustion engine has an intake passage whose diameter is set to a large value (i.e. which is set to a large diameter) so as to reduce flow resistance within the intake passage to enhance the charging efficiency of intake air into cylinders. When the above control system is applied to the engine configured as above, the flow velocity of intake air assumes a very low value when the engine is in a low-engine speed and low-load region, and hence the control system cannot properly calculate the intake air amount due to the low resolution of the air flow sensor, which degrades the accuracy of the intake air amount control. As a result, when the air-fuel ratio of a mixture in a combustion chamber is controlled based on the intake air amount thus calculated, there is a fear that the resulting degraded control accuracy lowers fuel economy and increases exhaust emissions.
On the other hand, in the ignition timing control of the engine, a method is conventionally employed which uses an engine speed and an intake air amount as load parameters indicative of load on the engine, and ignition timing maps having map values of ignition timing set in advance in association with the load parameters. In the above-described engine with the intake air passage having a large diameter as well, it is envisaged that ignition timing is controlled by the above method. However, as described above, in the control system proposed in Patent Literature 1, the intake air amount cannot be properly calculated in the low-load region of the engine due to the low resolution of the air flow sensor. This degrades the accuracy of the ignition timing control.
A control system for an internal combustion engine, which is capable of solving the above problems of the conventional control system, has been proposed in Japanese Patent Application No. 2004-133677 by the present assignee. This control system is comprised of an air flow sensor that detects the flow rate of air flowing through an intake passage of the engine, a pivot angle sensor that detects the valve lift, a cam angle sensor that detects the phase of a camshaft for actuating an intake valve to open and close the same with respect to a crankshaft (hereinafter referred to as “the cam phase”), and a crank angle sensor. Further, the engine includes the intake passage having a large diameter, a variable valve lift mechanism, and a variable cam phase mechanism as variable intake mechanisms. In the engine, the valve lift and the cam phase are changed by the variable valve lift mechanism and the variable cam phase mechanism as desired, respectively, whereby the intake air amount is changed as desired.
In the above control system, in the low-load region of the engine, as the intake air amount, a first estimated intake air amount is calculated according to the valve lift and the cam phase, and in the high-load region of the engine, a second estimated intake air amount is calculated according to the flow rate of air. In a load region between the low-load region and the high-load region of the engine, a weighted average value of the first and second estimated intake air amounts is calculated. Furthermore, air-fuel ratio control and ignition timing control are carried out using the thus calculated intake air amount. As a result, by employing the first estimated intake air amount higher in reliability in the low-load region where the reliability of the second estimated intake air amount is lower than that of the first estimated intake air amount due to the large diameter of the intake system of the engine, and employing the second estimated intake air amount higher in reliability in the high-load region in which occurs a state opposite to the above state in the low-load region, it is possible to further enhance the accuracy of the air-fuel ratio control and the ignition timing control compared with the control system proposed in Patent Literature 1.
According to the control system, however, when detection signals from the pivot angle sensor, the cam angle sensor, and the crank angle sensor drift due to changes in temperature, for example, or when the dynamic characteristics of the two variable mechanisms (i.e. the relationship between the valve lift and the cam phase with respect to control inputs) are changed by wear, contamination, play caused by aging, etc., occurring in component parts of the variable valve lift mechanism and the variable cam phase mechanism, the reliability of the results of detection by the sensors lowers. This can hinder the first estimated intake air amount from properly representing an actual intake air amount and cause the same to deviate from the actual intake air amount. When such a state occurs, if the engine is in the low-load region where the first estimated intake air amount is used as the intake air amount, it is impossible to properly calculate a fuel amount and ignition timing, which can degrade the accuracy of the air-fuel ratio control and the ignition timing control. More specifically, there is a possibility that the air-fuel ratio and the ignition timing assume improper values, which results in unstable combustion and degraded combustion efficiency.
The present invention has been made to provide a solution to the above-described problems, and an object thereof is to provide a control system for an internal combustion engine, which is capable of properly performing air-fuel ratio control and ignition timing control according to an actual intake air amount even when reliability of results of detection of an operating condition of a variable intake mechanism is low.
DISCLOSURE OF THE INVENTION
To attain the above object, in a first aspect of the present invention, there is provided a control system for an internal combustion engine, which controls an amount of intake air drawn into a cylinder of the engine by a variable intake mechanism and controls an amount of fuel to be supplied to a combustion chamber, to thereby control an air-fuel ratio of a mixture in the combustion chamber, comprising operating condition parameter-detecting means for detecting an operating condition parameter indicative of an operating condition of the variable intake mechanism, air-fuel ratio parameter-detecting means for detecting an air-fuel ratio parameter indicative of an air-fuel ratio of exhaust gases flowing through an exhaust passage of the engine, target air-fuel ratio-calculating means for calculating a target air-fuel ratio to which the air-fuel ratio of the mixture is to be controlled, air-fuel ratio control parameter-calculating means for calculating an air-fuel ratio control parameter for controlling an air-fuel ratio of the mixture such that the air-fuel ratio becomes equal to the target air-fuel ratio, according to the air-fuel ratio parameter, correction means for correcting the operating condition parameter according to one of the air-fuel ratio control parameter and the air-fuel ratio parameter, and fuel amount-determining means for determining the amount of fuel according to the corrected operating condition parameter and the air-fuel ratio control parameter.
With the configuration of this control system, an air-fuel ratio control parameter for controlling the air-fuel ratio of a mixture such that it becomes equal to a target air-fuel ratio is calculated according to an air-fuel ratio parameter indicative of the air-fuel ratio of exhaust gases flowing through an exhaust passage of the engine; an operating condition parameter indicative of an operating condition of a variable intake mechanism is corrected according to one of the air-fuel ratio control parameter and the air-fuel ratio parameter; and the amount of fuel to be supplied to a combustion chamber is determined according to the corrected operating condition parameter and the air-fuel ratio control parameter. In this case, the amount of intake air drawn into a cylinder of the engine is changed as desired by the variable intake mechanism, and hence the operating condition parameter indicative of the operating condition of the variable intake mechanism corresponds to a value indicative of the amount of the intake air drawn into the cylinder. Therefore, during execution of air-fuel ratio control, when a detection value of the operating condition parameter deviates from an actual value, an actual air-fuel ratio of the mixture deviates toward a leaner side or a richer side with respect to the target air-fuel ratio due to the deviation of the detection value. On the other hand, the air-fuel ratio control parameter is calculated as a value for controlling the air-fuel ratio of the mixture such that it becomes equal to the target air-fuel ratio, according to the air-fuel ratio parameter, in other words, a value indicative which of the leaner side and the richer side the air-fuel ratio is controlled to, so that the air-fuel ratio control parameter reflects the above-described deviation of the air-fuel ratio. Further, the air-fuel ratio parameter is a value indicative of the air-fuel ratio of exhaust gases flowing through the exhaust passage of the engine, and hence when the air-fuel ratio of the mixture is controlled such that it becomes equal to the target air-fuel ratio, the air-fuel ratio parameter as well is detected as a value reflecting the above-described deviation of the air-fuel ratio. Therefore, by correcting the operating condition parameter according to the air-fuel ratio control parameter or the air-fuel ratio parameter, thus calculated or detected, it is possible to properly correct the deviation between the detection value of the operating condition parameter and the actual value. As a result, even when the detection value of the operating condition parameter deviates from the actual value due to a drift of the detection value detected by the operating condition parameter-detecting means, and wear, contamination, play caused by aging, etc., occurring in component parts of the variable intake mechanism, it is possible to properly determine the fuel amount while compensating for the influence of the above deviation. This makes it possible to properly carry out the air-fuel ratio control, thereby making it possible to ensure a stable combustion state and excellent reduction of exhaust emissions.
Preferably, the correction means calculates a control state value indicative of a state of control of the air-fuel ratio of the mixture based on one of the air-fuel ratio control parameter and the air-fuel ratio parameter, calculates a statistically processed value by performing a predetermined sequential statistical process on the control state value, and corrects the operating condition parameter according to the statistically processed value.
With the configuration of this preferred embodiment, a control state value indicative of a state of control of the air-fuel ratio of the mixture in the air-fuel ratio control is calculated based on one of the air-fuel ratio control parameter and the air-fuel ratio parameter; a statistically processed value is calculated by performing a predetermined sequential statistical process on the control state value; and the operating condition parameter is corrected according to the statistically processed value. In the air-fuel ratio control, in general, when the operating condition or the combustion state of the engine changes, the state of control of the air-fuel ratio fluctuates with the above change in a manner oscillating between a direction toward the leaner side and a direction toward the richer side, so that the air-fuel ratio control parameter and the air-fuel ratio parameter are also changed in an oscillating manner to change the control state value in an oscillating manner as well. As a result, when the operating condition parameter is corrected using the thus changed control state value, a value obtained by correcting the operating condition parameter is also changed in an oscillating manner to reduce the accuracy of the air-fuel ratio control. This can cause occurrence of surging and fluctuation in the rotational speed of the engine, resulting in the degraded drivability. In contrast, in the present control system, the operating condition parameter is corrected according to the statistically processed value obtained by performing the predetermined sequential statistical process on the control state value, and hence even when the control state value is changed in an oscillating manner with the change in the operating condition or the combustion state of the engine, it is possible to properly correct the operating condition parameter while avoiding the influence of the oscillatory change in the control state value. As a result, it is possible to control the air-fuel ratio with excellent accuracy, thereby making it possible to ensure excellent drivability.
Preferably, when the statistically processed value is outside a predetermined range, the correction means corrects the operating condition parameter according to the statistically processed value such that the statistically processed value comes to be within the predetermined range, and holds an amount of correction of the operating condition parameter at a fixed value when the statistically processed value is within the predetermined range.
According to the first-mentioned preferred embodiment, the fuel amount is determined according to the corrected operating condition parameter and the air-fuel ratio control parameter, and hence there is a possibility that a process for correcting the operating condition parameter and an air-fuel ration control process interfere with each other. When the two processes interfere with each other, the interference can cause degradation of the accuracy of the air-fuel ration control, and an increase in exhaust emissions. In contrast, with the configuration of the control system according to the present embodiment, when the statistically processed value is outside a predetermined range, the operating condition parameter is corrected according to the statistically processed value such that the statistically processed value comes to be within the predetermined range, whereas when the statistically processed value is within the predetermined range, the amount of correction of the operating condition parameter is held at a fixed value. Therefore, by setting the predetermined range to a range of the statistically processed value which can prevent the accuracy of the air-fuel ratio control from being degraded even when the amount of correction of the operating condition parameter is held at the fixed value by reducing the deviation between the corrected operating condition parameter and the actual value through the process for correcting the operating condition parameter, it is possible to perform the air-fuel ratio control with accuracy while avoiding the interference of the two processes, described above. This makes it possible to enhance the accuracy of the air-fuel ratio control, and reduce exhaust emissions.
Preferably, the control system further comprises air flow rate-detecting means for detecting a flow rate of air flowing through an intake passage of the engine, and load parameter-detecting means for detecting a load parameter indicative of load on the engine, and the fuel amount-determining means determines the amount of fuel according to the corrected operating condition parameter and the air-fuel ratio control parameter when the load parameter is within a first predetermined range, and determines the amount of fuel according to the flow rate of air and the air-fuel ratio control parameter when the load parameter is within a second predetermined range different from the first predetermined range.
With the configuration of this preferred embodiment, the fuel amount is determined according to the corrected operating condition parameter and the air-fuel ratio control parameter when a load parameter is within a first predetermined range, whereas when the load parameter is within a second predetermined range different from the first predetermined range, the fuel amount is determined according to the detected flow rate of air and the air-fuel ratio control parameter. In this case, the corrected operating condition parameter and the detection value of the flow rate of air are both indicative of the amount of intake air. Therefore, by setting the first predetermined range to a range where the corrected operating condition parameter becomes higher in reliability than the detection value of the flow rate of air, and setting the second predetermined range to a range where the detection value of the flow rate of air becomes higher in reliability than the corrected operating condition parameter, it is possible, in both of the load regions, to determine the fuel amount according to a value indicative of the amount of intake air higher in reliability, thereby making it possible to further enhance the accuracy of the air-fuel ratio control.
To attain the above object, in a second aspect of the present invention, there is provided a control system for an internal combustion engine, which controls an amount of intake air drawn into a cylinder of the engine by a variable intake mechanism, and controls ignition timing and an air-fuel ratio of a mixture in a combustion chamber, comprising operating condition parameter-detecting means for detecting an operating condition parameter indicative of an operating condition of the variable intake mechanism, air-fuel ratio parameter-detecting means for detecting an air-fuel ratio parameter indicative of an air-fuel ratio of exhaust gases flowing through an exhaust passage of the engine, target air-fuel ratio-setting means for setting a target air-fuel ratio to which the air-fuel ratio of the mixture is to be controlled, air-fuel ratio control means for controlling the air-fuel ratio of the mixture such that the air-fuel ratio becomes equal to the target air-fuel ratio, according to the air-fuel ratio parameter, correction means for correcting the operating condition parameter according to one of a state of control of the air-fuel ratio of the mixture by the air-fuel ratio control means, and the air-fuel ratio parameter, and ignition timing-determining means for determining the ignition timing according to the corrected operating condition parameter.
With the configuration of this control system, the air-fuel ratio of a mixture is controlled by air-fuel ratio control means such that it becomes equal to a target air-fuel ratio, according to an air-fuel ratio parameter indicative of an air-fuel ratio of exhaust gases flowing through an exhaust passage of the engine; an operating condition parameter indicative of an operating condition of a variable intake mechanism is corrected according to one of a state of control of the air-fuel ratio of the mixture by the air-fuel ratio control means, and the air-fuel ratio parameter; and ignition timing is determined according to the corrected operating condition parameter. As described above, the amount of intake air drawn into a cylinder of the engine is changed as desired by the variable intake mechanism, and hence the operating condition parameter indicative of the operating condition of the variable intake mechanism corresponds to a value indicative of the amount of the intake air drawn into the cylinder. Therefore during execution of air-fuel ratio control, when a detection value of the operating condition parameter deviates from an actual value, an actual air-fuel ratio of the mixture deviates toward a leaner side or a richer side with respect to the target air-fuel ratio due to the deviation of the detection value. On the other hand, the air-fuel ratio of the mixture is controlled by the air-fuel ratio control means such that it becomes equal to the target air-fuel ratio, according to the air-fuel ratio parameter, and hence a state of the air-fuel ratio control reflects the above-described deviation of the air-fuel ratio. Further, the air-fuel ratio parameter is a value indicative of the air-fuel ratio of exhaust gases flowing through the exhaust passage of the engine, and hence when the air-fuel ratio of the mixture is controlled such that it becomes equal to the target air-fuel ratio, the air-fuel ratio parameter as well is detected as a value reflecting the deviation of the air-fuel ratio as described above. Therefore, by correcting the operating condition parameter according to the state of the air-fuel ratio control or the air-fuel ratio parameter, reflecting the deviation of the air-fuel ratio, it is possible to properly correct the deviation between the detection value of the operating condition parameter and the actual value. As a result, even when the detection value of the operating condition parameter deviates from the actual value due to a drift of the detection value detected by operating condition parameter-detecting means, and wear, contamination, play caused by aging, etc., occurring in component parts of the variable intake mechanism, it is possible to properly determine the ignition timing, while compensating for the influence of the above deviation. This makes it possible to properly ensure excellent accuracy of the ignition timing control, thereby making it possible to maintain excellent combustion efficiency and fuel economy.
Preferably, the air-fuel ratio control means calculates an air-fuel ratio control parameter for controlling the air-fuel ratio of the mixture such that the air-fuel ratio becomes equal to the target air-fuel ratio, according to the air-fuel ratio parameter, and the correction means calculates a control state value indicative of a state of control of the air-fuel ratio of the mixture based on one of the air-fuel ratio control parameter and the air-fuel ratio parameter, calculates a statistically processed value by performing a predetermined sequential statistical process on the control state value, and corrects the operating condition parameter according to the statistically processed value.
With the configuration of this preferred embodiment, an air-fuel ratio control parameter for controlling the air-fuel ratio of the mixture such that it becomes equal to the target air-fuel ratio is calculated according to the air-fuel ratio parameter; a control state value indicative of a state of air-fuel ratio control of the mixture is calculated based on one of the air-fuel ratio control parameter and the air-fuel ratio parameter; a statistically processed value is calculated by performing a predetermined sequential statistical process on the control state value; and the operating condition parameter is corrected according to the statistically processed value. As described hereinabove, in the air-fuel ratio control, when the operating condition or the combustion state of the engine is changed, the state of control of the air-fuel ratio fluctuates with the above change in a manner oscillating between the leaner side and the richer side, so that the air-fuel ratio parameter is also changed in an oscillating manner to change the control state value in an oscillating manner as well. As a result, when the operating condition parameter is corrected using the thus changed control state value, a value obtained by correcting the operating condition parameter is also changed in an oscillating manner to reduce the accuracy of the ignition timing control. This can cause occurrence of surging and fluctuation in the rotational speed of the engine, resulting in the degraded drivability. In contrast, in the present control system, the operating condition parameter is corrected according to the statistically processed value obtained by performing the predetermined sequential statistical process on the control state value, and hence even when the control state value is changed in an oscillating manner with the change in the operating condition or the combustion state of the engine, it is possible to correct the operating condition parameter while avoiding the influence of the oscillatory change in the control state value. As a result, it is possible to enhance the accuracy of the ignition timing control, whereby it is possible to improve drivability.
Preferably, the control system further comprises air flow rate-detecting means for detecting a flow rate of air flowing through an intake passage of the engine, and load parameter-detecting means for detecting a load parameter indicative of load on the engine, and the ignition timing-determining means determines the ignition timing according to the corrected operating condition parameter when the load parameter is within a first predetermined range, and determines the ignition timing according to the flow rate of air when the load parameter is within a second predetermined range different from the first predetermined range.
With the configuration of this preferred embodiment, the ignition timing is determined according to the corrected operating condition parameter when the load parameter is within a first predetermined range, whereas when the load parameter is within a second predetermined range different from the first predetermined range, the ignition timing is determined according to the detected flow rate of air. In this case, the corrected operating condition parameter and the detection value of the flow rate of air are both indicative of the amount of intake air. Therefore, by setting the first predetermined range to a range where the corrected operating condition parameter becomes higher in reliability than the detection value of the flow rate of air, and setting the second predetermined range to a range where the detection value of the flow rate of air becomes higher in reliability than the corrected operating condition parameter, it is possible, in both of the load regions, to determine the ignition timing according to a value indicative of the amount of intake air, higher in reliability, whereby it is possible to further enhance the accuracy of the ignition timing control.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a diagram schematically showing the arrangement of an internal combustion engine to which is applied a control system according to a first embodiment of the present invention;
FIG. 2 is a block diagram schematically showing the arrangement of the control system;
FIG. 3 is a cross-sectional view schematically showing the arrangement of a variable intake valve-actuating mechanism and an exhaust valve-actuating mechanism of the engine;
FIG. 4 is a cross-sectional view schematically showing the arrangement of a variable valve lift mechanism of the variable intake valve-actuating mechanism;
FIG. 5( a ) is a diagram showing a lift actuator in a state in which a short arm thereof is in a maximum lift position, and FIG. 5( b ) is a diagram showing the lift actuator in a state in which the short arm thereof is in a minimum lift position;
FIG. 6( a ) is a diagram showing an intake valve placed in an open state when a lower link of the variable valve lift mechanism is in a maximum lift position, and FIG. 6( b ) is a diagram showing the intake valve placed in an open state when the lower link of the variable valve lift mechanism is in a minimum lift position;
FIG. 7 is a diagram showing a valve lift curve (solid line) which the valve lift of the intake valve assumes when the lower link of the variable valve lift mechanism is in the maximum lift position, and a valve lift curve (two-dot chain line) which the valve lift of the intake valve assumes when the lower link of the variable valve lift mechanism is in the minimum lift position;
FIG. 8 is a diagram schematically showing the arrangement of a variable cam phase mechanism;
FIG. 9 is a diagram showing a valve lift curve (solid line) which the valve lift of the intake valve assumes when a cam phase is set to a most retarded value by the variable cam phase mechanism, and a valve lift curve (two-dot chain line) which the valve lift of the intake valve assumes when the cam phase is set to a most advanced value by the variable cam phase mechanism;
FIG. 10 is a block diagram schematically showing the arrangement of an air-fuel ratio controller;
FIG. 11 is a diagram showing an example of a map for use in calculation of a basic estimated intake air amount Gcyl_vt_base;
FIG. 12 is a diagram showing an example of a map for use in calculation of a correction coefficient K_gcyl_vt;
FIG. 13 is a diagram showing an example of a table for use in calculation of a transition coefficient Kg;
FIG. 14 is a diagram showing an example of a map for use in calculation of a target air-fuel ratio KCMD;
FIG. 15 is a block diagram schematically showing the arrangement of a corrected value-calculating section;
FIG. 16 is a block diagram schematically showing the arrangement of an ignition timing controller;
FIG. 17 is a diagram showing an example of a table for use in calculation of a maximum estimated intake air amount Gcyl_max;
FIG. 18 is a diagram showing an example of a map for use in calculation of a correction coefficient K_gcyl_max;
FIG. 19 is a diagram showing an example of a basic ignition timing map for use when Cain_comp=Cainrt;
FIG. 20 is a diagram showing an example of a basic ignition timing map for use when Cain_comp=Cainad;
FIG. 21 is a flowchart showing a process for calculating an air-fuel ratio correction coefficient KSTR;
FIG. 22 is a flowchart showing an air-fuel ratio control process;
FIG. 23 is a flowchart showing a process for calculation of a basic fuel injection amount Tcyl_bs;
FIG. 24 is a flowchart showing an ignition timing control process;
FIG. 25 is a flowchart showing a normal ignition timing control process;
FIG. 26 is a flowchart showing a corrected value-calculating process;
FIG. 27 is a flowchart showing a process for calculation of a lift correction value Dliftin_comp;
FIG. 28 is a flowchart showing a process for calculation of a phase correction value Dcain_comp;
FIG. 29 is a flowchart showing a variable mechanism control process;
FIG. 30 is a diagram showing an example of a table for use in calculation of a target valve lift Liftin_cmd during starting of the engine;
FIG. 31 is a diagram showing an example of a table for use in calculation of a target cam phase Cain_cmd during starting of the engine;
FIG. 32 is a diagram showing an example of a map for use in calculation of a target valve lift Liftin_cmd during catalyst warmup control;
FIG. 33 is a diagram showing an example of a map for use in calculation of a target cam phase Cain_cmd during the catalyst warmup control;
FIG. 34 is a diagram showing an example of a map for use in calculation of a target valve lift Liftin_cmd during normal operation of the engine;
FIG. 35 is a diagram showing an example of a map for use in calculation of the target cam phase Cain_cmd during normal operation of the engine;
FIG. 36 is a timing diagram showing an example of results of air-fuel ratio control carried out by the control system according to the first embodiment;
FIG. 37 is a timing diagram showing results of the air-fuel ratio control of a comparative example;
FIG. 38 is a block diagram schematically showing the arrangement of an air-fuel ratio controller of a control system according to a second embodiment of the present invention;
FIG. 39 is a block diagram schematically showing the arrangement of an ignition timing controller of the control system according to the second embodiment;
FIG. 40 is a block diagram schematically showing the arrangement of a corrected value-calculating section according to the second embodiment; and
FIG. 41 is a timing diagram showing an example of results of air-fuel ratio control carried out by the control system according to the second embodiment.
BEST MODE FOR CARRYING OUT THE INVENTION
Hereafter, a control system for an internal combustion engine, according a first embodiment of the present invention will be described with reference to the drawings. The control system 1 includes an ECU 2 , as shown in FIG. 2. As described hereinafter, the ECU 2 carries out control processes, including an air-fuel ratio control process and an ignition timing control process, depending on operating conditions of the internal combustion engine (hereinafter simply referred to as “the engine”) 3 .
Referring to FIGS. 1 and 3, the engine 3 is an in-line four-cylinder gasoline engine having a four pairs of cylinders 3 a and pistons 3 b (only one pair of which is shown), and installed on a vehicle, not shown, provided with an automatic transmission. The engine 3 includes an intake valve 4 and an exhaust valve 7 provided for each cylinder 3 a , for opening and closing an intake port and an exhaust port thereof, respectively, an intake camshaft 5 and intake cams 6 for actuating the intake valves 4 , a variable intake valve-actuating mechanism 40 that actuates the intake valves 4 to open and close the same, an exhaust camshaft 8 and exhaust cams 9 for actuating the exhaust valves 7 , an exhaust valve-actuating mechanism 30 that actuates the exhaust valves 7 to open and close the same, fuel injection valves 10 , spark plugs 11 (see FIG. 2), and so forth.
The intake valve 4 has a stem 4 a thereof slidably fitted in a guide 4 b . The guide 4 b is rigidly fixed to a cylinder head 3 c . Further, as shown in FIG. 4, the intake valve 4 includes upper and lower spring sheets 4 c and 4 d , and a valve spring 4 e disposed therebetween, and is urged by the valve spring 4 e in the valve-closing direction.
Further, the intake camshaft 5 and the exhaust camshaft 8 are rotatably mounted through the cylinder head 3 c via holders, not shown. The intake camshaft 5 has an intake sprocket (not shown) coaxially and rotatably fitted on one end thereof. The intake sprocket is connected to a crankshaft 3 d via a timing chain, not shown, and connected to the intake camshaft 5 via a variable cam phase mechanism 70 , described hereinafter. With the above configuration, the intake camshaft 5 performs one rotation per two rotations of the crankshaft 3 d . Further, the intake cam 6 is provided on the intake camshaft 5 for each cylinder 3 a such that the intake cam 6 rotates in unison with the intake camshaft 5 .
Furthermore, the variable intake valve-actuating mechanism 40 is provided for actuating the intake valve 4 of each cylinder 3 a so as to open and close the same, in accordance with rotation of the intake camshaft 5 , and continuously changing the lift and the valve timing of the intake valve 4 , which will be described in detail hereinafter. It should be noted that in the present embodiment, “the lift of the intake valve 4 ” (hereinafter referred to as “the valve lift”) represents the maximum lift of the intake valve 4 .
On the other hand, the exhaust valve 7 has a stem 7 a thereof slidably fitted in a guide 7 b . The guide 7 b is rigidly fixed to the cylinder head 3 c . Further, the exhaust valve 7 includes upper and lower spring sheets 7 c and 7 d , and a valve spring 7 e disposed therebetween, and is urged by the valve spring 7 e in the valve-closing direction.
Further, the exhaust camshaft 8 has an exhaust sprocket (not shown) integrally formed therewith, and is connected to the crankshaft 3 d by the exhaust sprocket and a timing chain, not shown, whereby the exhaust camshaft 8 performs one rotation per two rotations of the crankshaft 3 d . Further, the exhaust cam 9 is provided on the exhaust camshaft 8 for each cylinder 3 a such that the exhaust cam 9 rotates in unison with the exhaust camshaft 8 .
Further, the exhaust valve-actuating mechanism 30 includes rocker arms 31 . Each rocker arm 31 is pivotally moved in accordance with rotation of the associated exhaust cam 9 to thereby actuate the exhaust valve 7 for opening and closing the same against the urging force of the valve spring 7 e.
On the other hand, the fuel injection valve 10 is provided for each cylinder 3 a , and mounted through the cylinder head 3 c in a tilted state such that fuel is directly injected into a combustion chamber. That is, the engine 3 is configured as a direct injection engine. Further, the fuel injection valve 10 is electrically connected to the ECU 2 and the valve-opening time period and the valve-opening timing thereof are controlled by the ECU 2 , whereby the fuel injection amount is controlled.
The spark plug 11 as well is provided for each cylinder 3 a , and mounted through the cylinder head 3 c . The spark plug 11 is electrically connected to the ECU 2 , and a state of spark discharge is controlled by the ECU 2 such that a mixture in the combustion chamber is burned in timing corresponding to ignition timing, referred to hereinafter.
On the other hand, the engine 3 is provided with a crank angle sensor 20 and an engine coolant temperature sensor 21 . The crank angle sensor 20 is comprised of a magnet rotor and an MRE (magnetic resistance element) pickup, and delivers a CRK signal and a TDC signal, which are both pulse signals, to the ECU 2 in accordance with rotation of the crankshaft 3 d . Each pulse of the CRK signal is generated whenever the crankshaft 3 d rotates through a predetermined angle (e.g. 10°). The ECU 2 calculates the rotational speed NE of the engine 3 (hereinafter referred to as “the engine speed NE”) based on the CRK signal. Further, the TDC signal indicates that each piston 3 b in the associated cylinder 3 a is in a predetermined crank angle position slightly before the TDC position at the start of the intake stroke, and each pulse of the TDC signal is generated whenever the crankshaft 3 d rotates through a predetermined crank angle. In the present embodiment, the crank angle sensor 20 corresponds to operating condition parameter-detecting means and load parameter-detecting means, and the engine speed NE corresponds to a load parameter.
The engine coolant temperature sensor 12 is implemented e.g. by a thermistor, and detects an engine coolant temperature TW to deliver a signal indicative of the sensed engine coolant temperature TW to the ECU 2 . The engine coolant temperature TW is the temperature of an engine coolant circulating through a cylinder block 3 h of the engine 3 .
Furthermore, the engine 3 has an intake pipe 12 from which a throttle valve mechanism is omitted, and an intake passage 12 a which is formed to have a large diameter, whereby the engine 3 is configured such that flow resistance is smaller than in an ordinary engine. The intake pipe 12 is provided with an air flow sensor 22 and an intake air temperature sensor 23 (see FIG. 2).
The air flow sensor 22 (air flow rate-detecting means) is formed by a hot-wire air flow meter, and detects the flow rate Gin of air flowing through the intake passage 12 a (hereinafter referred to as “the air flow rate Gin”) to deliver a signal indicative of the sensed air flow rate Gin to the ECU 2 . It should be noted that the air flow rate Gin is indicated in units of g/sec. Further, the intake air temperature sensor 23 detects the temperature TA of the air flowing through the intake passage 12 a (hereinafter referred to as “the intake air temperature TA”), and delivers a signal indicative of the sensed intake air temperature TA to the ECU 2 .
A LAF sensor 24 (air-fuel ratio parameter-detecting means) is inserted into an exhaust pipe 13 of the engine 3 at a location upstream of a catalytic device, not shown. The LAF sensor 24 is comprised of a zirconia layer and platinum electrodes, and linearly detects the concentration of oxygen in exhaust gases flowing through an exhaust passage of the exhaust pipe 13 , in a broad air-fuel ratio range from a rich region richer than the stoichiometric ratio to a very lean region, to deliver a signal indicative of the sensed oxygen concentration to the ECU 2 . The ECU 2 calculates a detected air-fuel ratio KACT indicative of an air-fuel ratio in the exhaust gases, based on a value of the signal output from the LAF sensor 24 . The detected air-fuel ratio KACT (air-fuel ratio parameter) is expressed as an equivalent ratio.
Next, a description will be given of the aforementioned variable intake valve-actuating mechanism 40 . As shown in FIG. 4, the variable intake valve-actuating mechanism 40 is comprised of the intake camshaft 5 , the intake cams 6 , a variable valve lift mechanism 50 , and the variable cam phase mechanism 70 .
The variable valve lift mechanism 50 (variable intake mechanism) is provided for actuating the intake valves 4 to open and close the same, in accordance with rotation of the intake camshaft 5 , and continuously changing the valve lift Liftin between a predetermined maximum value Liftinmax and a predetermined minimum value Liftinmin. The variable valve lift mechanism 50 is comprised of rocker arm mechanisms 51 of a four joint link type, provided for the respective cylinders 3 a , and a lift actuator 60 (see FIGS. 5( a ) and 5 ( b )) simultaneously actuating these rocker arm mechanisms 51 .
Each rocker arm mechanism 51 is comprised of a rocker arm 52 , and upper and lower links 53 and 54 . The upper link 53 has one end pivotally mounted to an upper end of the rocker arm 52 by an upper pin 55 , and the other end pivotally mounted to a rocker arm shaft 56 . The rocker arm shaft 56 is mounted through the cylinder head 3 c via holders, not shown.
Further, a roller 57 is pivotally disposed on the upper pin 55 of the rocker arm 52 . The roller 57 is in contact with a cam surface of the intake cam 6 . As the intake cam 6 rotates, the roller 57 rolls on the intake cam 6 while being guided by the cam surface of the intake cam 6 . As a result, the rocker arm 52 is vertically driven, and the upper link 53 is pivotally moved about the rocker arm shaft 56 .
Furthermore, an adjusting bolt 52 a is mounted to an end of the rocker arm 52 toward the intake valve 4 . When the rocker arm 52 is vertically moved in accordance with rotation of the intake cam 6 , the adjusting bolt 52 a vertically drives the stem 4 a to open and close the intake valve 4 , against the urging force of the valve spring 4 e.
Further, the lower link 54 has one end pivotally mounted to a lower end of the rocker arm 52 by a lower pin 58 , and the other end of the lower link 54 has a connection shaft 59 pivotally mounted thereto. The lower link 54 is connected to a short arm 65 , described hereinafter, of the lift actuator 60 by the connection shaft 59 .
On the other hand, as shown in FIGS. 5( a ) and 5 ( b ), the lift actuator 60 is comprised of a motor 61 , a nut 62 , a link 63 , a long arm 64 , and the short arm 65 . The motor 61 is connected to the ECU 2 , and disposed outside a head cover 3 g of the engine 3 . The rotational shaft of the motor 61 is a screw shaft 61 a formed with a male screw and the nut 62 is screwed onto the screw shaft 61 a . The nut 62 is connected to the long arm 64 by the link 63 . The link 63 has one end pivotally mounted to the nut 62 by a pin 63 a , and the other end pivotally mounted to one end of the long arm 64 by a pin 63 b.
Further, the other end of the long arm 64 is attached to one end of the short arm 65 by a pivot shaft 66 . The pivot shaft 66 is circular in cross section, and extends through the head cover 3 g of the engine 3 such that it is pivotally supported by the head cover 3 g . The long arm 64 and the short arm 65 are pivotally moved in unison with the pivot shaft 66 in accordance with pivotal motion of the pivot shaft 66 .
Furthermore, the aforementioned connection shaft 59 pivotally extends through the other end of the short arm 65 , whereby the short arm 65 is connected to the lower link 54 by the connection shaft 59 .
Next, a description will be given of the operation of the variable valve lift mechanism 50 configured as above. In the variable valve lift mechanism 50 , when a lift control input U_Liftin, described hereinafter, is input from the ECU 2 to the lift actuator 60 , the screw shaft 61 a rotates, and the nut 62 is moved in accordance with the rotation of the screw shaft 61 a , whereby the long arm 64 and the short arm 65 are pivotally moved about the pivot shaft 66 , and in accordance with the pivotal motion of the short arm 65 , the lower link 54 of the rocker arm mechanism 51 is pivotally moved about the lower pin 58 . That is, the lower link 54 is driven by the lift actuator 60 .
In the process, under the control of the ECU 2 , the range of pivotal motion of the short arm 65 is restricted between a maximum lift position shown in FIG. 5( a ) and a minimum lift position shown in FIG. 5( b ), whereby the range of pivotal motion of the lower link 54 is also restricted between a maximum lift position indicated by a solid line in FIG. 4 and a minimum lift position indicated by a two-dot chain line in FIG. 4.
The four joint link formed by the rocker arm shaft 56 , the upper and lower pins 55 and 58 , and the connection shaft 59 is configured such that when the lower link 54 is in the maximum lift position, the distance between the center of the upper pin 55 and the center of the lower pin 58 becomes longer than the distance between the center of the rocker arm shaft 56 and the center of the connection shaft 59 , whereby as shown in FIG. 6( a ), when the intake cam 6 rotates, the amount of movement of the adjusting bolt 52 a becomes larger than the amount of movement of a contact point where the intake cam 6 and the roller 57 are in contact with each other.
On the other hand, the four joint link is configured such that when the lower link 54 is in the minimum lift position, the distance between the center of the upper pin 55 and the center of the lower pin 58 becomes shorter than the distance between the center of the rocker arm shaft 56 and the center of the connection shaft 59 , whereby as shown in FIG. 6( b ), when the intake cam 6 rotates, the amount of movement of the adjusting bolt 52 a becomes smaller than the amount of movement of the contact point where the intake cam 6 and the roller 57 are in contact with each other.
For the above reason, when the lower link 54 is in the maximum lift position, the intake valve 4 is opened with a larger valve lift Liftin than when the lower link 54 is in the minimum lift position. More specifically, during rotation of the intake cam 6 , when the lower link 54 is in the maximum lift position, the intake valve 4 is opened according to a valve lift curve indicated by a solid line in FIG. 7, and the valve lift Liftin assumes its maximum value Liftinmax. On the other hand, when the lower link 54 is in the minimum lift position, the intake valve 4 is opened according to a valve lift curve indicated by a two-dot chain line in FIG. 7, and the valve lift Liftin assumes its minimum value Liftinmin.
Therefore, in the variable valve lift mechanism 50 , the lower link 54 is pivotally moved by the lift actuator 60 between the maximum lift position and the minimum lift position, whereby it is possible to continuously change the valve lift Liftin between the maximum value Liftinmax and the minimum value Liftinmin.
It should be noted that the variable valve lift mechanism 50 is provided with a lock mechanism, not shown, which locks operation of the variable valve lift mechanism 50 when the lift control input U_Liftin is set to a failure time value U_Liftin_fs, referred to hereinafter, and when the lift control input U_Liftin is not input from the ECU 2 to the lift actuator 60 e.g. due to a disconnection. More specifically, the variable valve lift mechanism 50 is inhibited from changing the valve lift Liftin, whereby the valve lift Liftin is held at the minimum value Liftinmin. It should be noted that when a cam phase Cain is held at a locking value, described hereinafter, the minimum value Liftinmin is set to a value which is capable of ensuring a predetermined failure time value Gcyl_fs, referred to hereinafter, as the intake air amount. The predetermined failure time value Gcyl_fs (predetermined value) is set to a value which is capable of suitably carrying out idling or starting of the engine 3 during stoppage of the vehicle, and at the same time holding the vehicle in a state of low-speed traveling when the vehicle is traveling.
The engine 3 is provided with a pivot angle sensor 25 (see FIG. 2). The pivot angle sensor 25 detects a pivot angle of the pivot shaft 66 , i.e. the short arm 65 , and delivers a signal indicative of the sensed pivot angle to the ECU 2 . The ECU 2 calculates the valve lift Liftin based on the signal output from pivot angle sensor 25 . In the present embodiment, the pivot angle sensor 25 corresponds to the operating condition parameter-detecting means and the load parameter-detecting means, and the valve lift Liftin corresponds to an operating condition parameter and the load parameter.
Next, a description will be given of the aforementioned variable cam phase mechanism 70 (variable intake mechanism). The variable cam phase mechanism 70 is provided for continuously advancing or retarding the relative phase Cain of the intake camshaft 5 with respect to the crankshaft 3 d (hereinafter referred to as “the cam phase Cain”), and mounted on an intake sprocket-side end of the intake camshaft 5 . As shown in FIG. 8, the variable cam phase mechanism 70 includes a housing 71 , a three-bladed vane 72 , an oil pressure pump 73 , and a solenoid valve mechanism 74 .
The housing 71 is integrally formed with the intake sprocket on the intake camshaft 5 d , and divided by three partition walls 71 a formed at equal intervals. The vane 72 is coaxially mounted on the intake sprocket-side end of the intake camshaft 5 , such that the vane 72 radially extends outward from the intake camshaft 5 , and rotatably housed in the housing 71 . Further, the housing 71 has three advance chambers 75 and three retard chambers 76 each formed between one of the partition walls 71 a and one of the three blades of the vane 72 .
The oil pressure pump 73 is of a mechanical type which is connected to the crankshaft 3 d . As the crankshaft 3 d rotates, the oil pressure pump 73 draws lubricating oil stored in an oil pan 3 e of the engine 3 via a lower part of an oil passage 77 c , for pressurization, and supplies the pressurized oil to the solenoid valve mechanism 74 via the remaining part of the oil passage 77 c.
The solenoid valve mechanism 74 is formed by combining a spool valve mechanism 74 a and a solenoid 74 b , and connected to the advance chambers 75 and the retard chambers 76 via an advance oil passage 77 a and a retard oil passage 77 b such that oil pressure supplied from the oil pressure pump 73 is output to the advance chambers 75 and the retard chambers 76 as advance oil pressure Pad and retard oil pressure Prt. The solenoid 74 b of the solenoid valve mechanism 74 is electrically connected to the ECU 2 . When a phase control input U_Cain, referred to hereinafter, is input from the ECU 2 , the solenoid 74 b moves a spool valve element of the spool valve mechanism 74 a within a predetermined range of motion according to the phase control input U_Cain to thereby change both the advance oil pressure Pad and the retard oil pressure Prt.
In the variable cam phase mechanism 70 constructed as above, during operation of the oil pressure pump 73 , the solenoid valve mechanism 74 is operated according to the phase control input U_Cain, to supply the advance oil pressure Pad to the advance chambers 75 and the retard oil pressure Prt to the retard chambers 76 , whereby the relative phase between the vane 72 and the housing 71 is changed toward an advanced side or a retarded side. As a result, the cam phase Cain described above is continuously changed between a most retarded value Cainrt (e.g. a value corresponding to a cam angle of 0°) and a most advanced value Cainad (e.g. a value corresponding to a cam angle of 55°), whereby valve timing of the intake valve 4 is continuously changed between a most retarded timing indicated by a solid line in FIG. 9 and a most advanced timing indicated by a two-dot chain line in FIG. 9.
It should be noted that the variable cam phase mechanism 70 is provided with a lock mechanism, not shown, which locks operation of the variable cam phase mechanism 70 when oil pressure supplied from the oil pressure pump 73 is low, when the phase control input U_Cain is set to a failure time value U_Cain_fs, referred to hereinafter, or when the phase control input U_Cain is not input to the solenoid valve mechanism 74 e.g. due to a disconnection. More specifically, the variable cam phase mechanism 70 is inhibited from changing the cam phase Cain, whereby the cam phase Cain is held at a predetermined locking value. As described hereinabove, the predetermined locking value is set to a value which is capable of ensuring the predetermined failure time value Gcyl_fs as the intake air amount when the valve lift Liftin is held at the minimum value Liftinmin, as described above.
As described above, in the variable intake valve-actuating mechanism 40 used in the present embodiment, the valve lift Liftin is continuously changed by the variable valve lift mechanism 50 , and the cam phase Cain, i.e. the valve timing of the intake valve 4 is continuously changed by the variable cam phase mechanism 70 between the most retarded timing and the most advanced timing, described hereinabove. Further, as described hereinafter, the valve lift Liftin and the cam phase Cain are controlled by the ECU 2 via the variable valve lift mechanism 50 and the variable cam phase mechanism 70 , respectively, whereby the intake air amount is controlled.
On the other hand, a cam angle sensor 26 (see FIG. 2) is disposed at an end of the intake camshaft 5 opposite from the variable cam phase mechanism 70 . The cam angle sensor 26 is implemented e.g. by a magnet rotor and an MRE pickup, for delivering a CAM signal, which is a pulse signal, to the ECU 2 along with rotation of the intake camshaft 5 . Each pulse of the CAM signal is generated whenever the intake camshaft 5 rotates through a predetermined cam angle (e.g. one degree). The ECU 2 calculates the cam phase Cain based on the CAM signal and the CRK signal, described above. In the present embodiment, the cam angle sensor 26 corresponds to the operating condition parameter-detecting means and the load parameter-detecting means, and the cam phase Cain corresponds to the operating condition parameter and the load parameter.
Next, as shown in FIG. 2, connected to the ECU 2 are an accelerator pedal opening sensor 27 , and an ignition switch (hereinafter referred to as “the IG•SW”) 28 . The accelerator pedal opening sensor 27 detects a stepped-on amount AP of an accelerator pedal, not shown, of the vehicle (hereinafter referred to as “the accelerator pedal opening AP”) and delivers a signal indicative of the sensed accelerator pedal opening AP to the ECU 2 . Further, the IG•SW 28 is turned on or off by operation of an ignition key, not shown, and delivers a signal indicative of the ON/OFF state thereof to the ECU 2 .
The ECU 2 is implemented by a microcomputer including a CPU, a RAM, a ROM, and an I/O interface (none of which are shown). The ECU 2 determines operating conditions of the engine 3 , based on the detection signals delivered from the above-mentioned sensors 20 to 27 , the ON/OFF signal from the IG•SW 28 , and the like, and executes control processes. More specifically, as will be described in detail hereinafter, the ECU 2 executes the air-fuel ratio control process and the ignition timing control process according to the operating conditions of the engine 3 . Furthermore, the ECU 2 calculates a corrected valve lift Liftin_comp and a corrected cam phase Cain_comp, and controls the valve lift Liftin and the cam phase Cain via the variable valve lift mechanism 50 and the variable cam phase mechanism 70 , respectively, to thereby control the intake air amount.
It should be noted that in the present embodiment, the ECU 2 corresponds to the operating condition parameter-detecting means, air-fuel ratio parameter-detecting means, target air-fuel ratio-calculating means, air-fuel ratio control parameter-calculating means, correction means, fuel amount-determining means, the load parameter-detecting means, air-fuel ratio control means, and ignition timing-determining means.
Next, a description will be given of the control system 1 according to the present embodiment. The control system 1 includes an air-fuel ratio controller 100 (see FIG. 10) for carrying out the air-fuel ratio control, and an ignition timing controller 130 (see FIG. 16) for carrying out ignition timing control, both of which are implemented by the ECU 2 . In the present embodiment, the air-fuel ratio controller 100 corresponds to the fuel amount-determining means and the air-fuel ratio control means, and the ignition timing controller 130 corresponds to the ignition timing-determining means.
First, a description will be given of the air-fuel ratio controller 100 . As will be described hereinafter, the fuel injection controller 100 is provided for calculating a fuel injection amount TOUT (fuel amount) for each fuel injection valve 10 , and as shown in FIG. 10, includes first and second estimated intake air amount-calculating sections 101 and 102 , a transition coefficient-calculating section 103 , amplification elements 104 and 105 , an addition element 106 , an amplification element 107 , a target air-fuel ratio-calculating section 108 , an air-fuel ratio correction coefficient-calculating section 109 , a total correction coefficient-calculating section 110 , a multiplication element 111 , a fuel attachment-dependent correction section 112 , and a corrected value-calculating section 113 .
The first estimated intake air amount-calculating section 101 calculates, as described hereinafter, a first estimated intake air amount Gcyl_vt. More specifically, a basic estimated intake air amount Gcyl_vt_base is calculated by searching a map shown in FIG. 11 according to the engine speed NE and the corrected valve lift Liftin_comp. The corrected valve lift Liftin_comp is a value obtained by correcting the valve lift Liftin, and calculated by the corrected value-calculating section 113 , as described hereinafter. Further, in FIG. 11, NE 1 to NE 3 represent predetermined values of the engine speed NE, between which the relationship of NE 1 <NE 2 <NE 3 holds. This also applies to the following description.
In this map, when NE=NE 1 or NE 2 holds, in a region where the corrected valve lift Liftin_comp is small, the basic estimated intake air amount Gcyl_vt_base is set to a larger value as the corrected valve lift Liftin_comp is larger, whereas in a region where the corrected valve lift Liftin_comp is close to the maximum value Liftinmax, the basic estimated intake air amount Gcyl_vt_base is set to a smaller value as corrected valve lift Liftin_comp is larger. This is because in a low-to-medium engine speed region, as the corrected valve lift Liftin_comp is larger in the region where the corrected valve lift Liftin_comp is close to the maximum value Liftinmax, the valve-opening time period of the intake valve 4 becomes longer, whereby charging efficiency is reduced by blow-back of intake air. Further, when NE=NE 3 holds, the basic estimated intake air amount Gcyl_vt_base is set to a larger value as the corrected valve lift Liftin_comp is larger. This is because in a high engine speed region, the above-described blow-back of intake air is made difficult to occur even in a region where the corrected valve lift Liftin_comp is large, due to the inertia force of intake air, so that the charging efficiency becomes higher as the corrected valve lift Liftin_comp is larger.
Further, a correction coefficient K_gcyl_vt is calculated by searching a map shown in FIG. 12 according to the engine speed NE and the corrected cam phase Cain_comp. The corrected cam phase Cain_comp is a value obtained by correcting the cam phase Cain, and calculated by the corrected value-calculating section 113 , as described hereinafter.
In the FIG. 12 map, when NE=NE 1 or NE 2 holds, in a region where the corrected cam phase Cain_comp is close to the most retarded value Cainrt, the correction coefficient K_gcyl_vt is set to a smaller value as the corrected cam phase Cain_comp is closer to the most retarded value Cainrt, and in the other regions, the correction coefficient K_gcyl_vt is set to a smaller value as the corrected cam phase Cain_comp assumes a value closer to the most advanced value Cainad. This is because in the low-to-medium engine speed region, as the corrected cam phase Cain_comp is closer to the most retarded value Cainrt in the region where the corrected cam phase Cain_comp is close to the most retarded value Cainrt, the valve-closing timing of the intake valve 4 is retarded, whereby the charging efficiency is degraded by the blow-back of intake air, and in the other regions, as the corrected cam phase Cain_comp assumes a value closer to the most advanced value Cainad, the valve overlap is increased to increase the internal EGR amount, whereby the charging efficiency is degraded. Further, when NE=NE 3 holds, in the region where the corrected cam phase Cain_comp is close to the most retarded value Cainrt, the correction coefficient K_gcyl_vt is set to a fixed value (a value of 1), and in the other regions, the correction coefficient K_gcyl_vt is set to a smaller value as the corrected cam phase Cain_comp assumes a value closer to the most advanced value Cainad. This is because in the high engine speed region, the blow-back of intake air is made difficult to occur even in a region where the corrected cam phase Cain_comp is close to the most advanced value Cainad, due to the above-mentioned inertia force of intake air.
Then, the first estimated intake air amount Gcyl_vt is calculated using the basic estimated intake air amount Gcyl_vt_base and the correction coefficient K_gcyl_vt, calculated as above, by the following equation (1):
Gcyl — vt=K — gcyl — vt·Gcyl — vt _base (1)
Further, the transition coefficient-calculating section 103 calculates a transition coefficient Kg as follows: First, an estimated flow rate Gin_vt (unit: g/sec) is calculated by the following equation (2), using the first estimated intake air amount Gcyl_vt calculated by the first estimated intake air amount-calculating sections 101 , and the engine speed NE.
Gin — vt= 2· Gcyl — vt·NE/ 60 (2)
Subsequently, the transition coefficient Kg is calculated by searching a table shown in FIG. 13 according to the estimated flow rate Gin_vt. In FIG. 13, Gin 1 and Gin 2 represent predetermined values between which the relationship of Gin 1 <Gin 2 holds. Since the flow rate of air flowing through the intake passage 12 a is small when the estimated flow rate Gin_vt is within the Gin_vt≦Gin 1 , the predetermined value Gin 1 is set to such a value as will cause the reliability of the first estimated intake air amount Gcyl_vt to exceed that of a second estimated intake air amount Gcyl_afm, described hereinafter, due to the resolution of the air flow sensor 22 . Further, since the flow rate of air flowing through the intake passage 12 a is large when the estimated flow rate Gin_vt is within the range of Gin 2 ≦Gin_vt, the predetermined value Gin 2 is set to such a value as will cause the reliability of the second estimated intake air amount Gcyl_afm to exceed that of the first estimated intake air amount Gcyl_vt. Furthermore, in this table, the transition coefficient Kg is set to a value of 0 when the first estimated intake air amount Gcyl_vt is in the range of Gin_vt≦Gin 1 , and to a value of 1 when the same is within the range of Gin 2 ≦Gin_vt. When the estimated flow rate Gin_vt is within the range of Gin 1 <Gin_vt<Gin 2 , the transition coefficient Kg is set to a value which is between 0 and 1, and at the same time larger as the estimated flow rate Gin_vt is larger.
On the other hand, the second estimated intake air amount-calculating section 102 calculates the second estimated intake air amount Gcyl_afm (unit: g) based on the air flow rate Gin and the engine speed NE, by the following equation (3):
Gcyl — afm=Gin· 60/(2· NE ) (3)
The amplification elements 104 and 105 amplifies the first and second estimated intake air amounts Gcyl_vt and Gcyl_afm, calculated as above, to a (1−Kg)-fold and a Kg-fold, respectively. The addition element 106 calculates a calculated intake air amount Gcyl based on the values thus amplified, by a weighted average arithmetic operation expressed by the following equation (4):
Gcyl=Kg·Gcyl — afm +(1− Kg )· Gcyl — vt (4)
As is clear from the equation (4), when Kg=0, i.e. within the aforementioned range of Gin_vt≦Gin 1 , Gcyl=Gcyl_vt holds, and when Kg=1, i.e. within the aforementioned range of Gin 2 ≦Gin_vt, Gcyl=Gcyl_afm holds. When 0<Kg<1, i.e. when the estimated flow rate Gin_vt is within the range of Gin 1 <Gin_vt<Gin 2 , the degrees of weighting the first and second estimated intake air amounts Gcyl_vt and Gcyl_afm in the calculated intake air amount Gcyl are determined by the value of the transition coefficient Kg.
Furthermore, the amplification element 107 calculates a basic fuel injection amount Tcyl_bs based on the calculated intake air amount Gcyl (intake air amount), by the following equation (5):
Tcyl — bs=Kgt·Gcyl (5)
wherein Kgt represents a conversion coefficient set in advance for each fuel injection valve 10 .
Further, the target air-fuel ratio-calculating section 108 (target air-fuel ratio-calculating means) calculates a target air-fuel ratio KCMD by searching a map shown in FIG. 14 according to the calculated intake air amount Gcyl and the accelerator pedal opening AP. In this map, the value of the target air-fuel ratio KCMD is set as an equivalent ratio, and basically, it is set to a value corresponding to a stoichiometric air-fuel ratio (14.5) so as to maintain excellent emission-reducing performance of the catalytic converter.
On the other hand, the air-fuel ratio correction coefficient-calculating section 109 is formed as an STR (Self Tuning Regulator) including an onboard identifier (not shown). The air-fuel ratio correction coefficient-calculating section 109 calculates an air-fuel ratio correction coefficient KSTR according to the detected air-fuel ratio KACT and the target air-fuel ratio KCMD. More specifically, the air-fuel ratio correction coefficient KSTR is calculated with an algorithm expressed by the following equations (6) to (13) such that the air-fuel ratio of the mixture, i.e. the detected air-fuel ratio KACT is caused to converge to the target air-fuel ratio KCMD, and as a value in terms of the equivalent ratio. It should be noted that in the present embodiment, the air-fuel ratio correction coefficient-calculating section 109 corresponds to air-fuel ratio control parameter-calculating means, and the air-fuel ratio correction coefficient KSTR corresponds to an air-fuel ratio control parameter and a value indicative of the state of control of the air-fuel ratio.
In the above equations (6) to (13), each portion with (n) represents discrete data sampled or calculated every combustion cycle, i.e. whenever a total of four successive pulses of the TDC signal are generated. The symbol n indicates a position in the sequence of sampling cycles of respective discrete data. For example, the symbol n indicates that discrete data therewith is a value sampled in the current control timing, and a symbol n−1 indicates that discrete data therewith is a value sampled in the immediately preceding control timing. It should be noted that in the following description, the symbol (n) and the like provided for the discrete data are omitted as deemed appropriate.
In the equation (6), kstr(n) represents a basic value of the air-fuel ratio correction coefficient (hereinafter simply referred to as “the basic value”), and is calculated by the equation (7). Further, Lim(kstr(n)) represents a value obtained by performing a limiting process on the basic value kstr(n), and is calculated specifically as a value obtained by limiting the basic value kstr(n) within a range defined by a predetermined lower limit value KSTRmin (e.g. a value of 0.6) and a predetermined upper limit value KSTRmax (e.g. a value of 1.4). More specifically, when kstr(n)<KSTRmin, Lim(kstr(n))=KSTRmin holds, when KSTRmin≦kstr(n)≦KSTRmax, Lim(kstr(n))=kstr(n) is set, and when kstr(n)>KSTRmax, Lim(kstr(n))=KSTRmax is set.
The air-fuel ratio correction coefficient KSTR is calculated, as described above, as a value obtained by performing the limiting process on the basic value kstr so as to avoid the engine speed NE from becoming unstable or an engine stall from occurring due to an excessively rich or excessively lean air-fuel ratio of the mixture brought about by failure of the LAF sensor 24 during execution of feedback control of the air-fuel ratio using the air-fuel ratio correction coefficient KSTR.
Further, the equation (7) is derived as follows: When one of the four cylinders 3 a is regarded as a controlled object to which is input the air-fuel ratio correction coefficient KSTR, and from which is output the detected air-fuel ratio KACT, and the controlled object is modeled into a discrete-time system model, the following equation (14) is obtained. It should be noted that in the equation (14), b0, r1, r2, r3, and s0 represent model parameters.
KACT ( n )= b 0 ·KSTR ( n )+ r 1( n )· KSTR ( n− 4) +r 2( n )· KSTR ( n− 5)+ r 3( n )· KSTR ( n− 6) +s 0( n )· KCMD ( n ) (14)
In the above equation, in the dead time of the detected air-fuel ratio KACT with respect to the target air-fuel ratio KCMD is estimated to correspond to approximately three combustion cycles, and therefore, the relationship of KCMD(n)=KACT (n+3) holds. When this relationship is applied to the equation (14), and KSTR(n) is replaced by kstr(n), the aforementioned equation (7) is derived.
Further, the model parameter vector θ of the model parameters b0, r1, r2, r3, and s0 in the equation (7) is identified with an identification algorithm expressed by the equations (8) to (13). In the equation (8), KΓ represents a vector of a gain coefficient, and e_str an identification error.
The identification error e_str is calculated by the equations (9) to (13). In the equation (9), θ T represents a transposed matrix of θ, and is defined by the equation (11). Further, the vector KΓ of the gain coefficient is determined by the equation (10). In equation (10), ζ represents that the transposed matrix is a vector defined by the equation (12), and Γ represents a square matrix of order 5 defined by the equation (13). In the equation (13), γ represents an adaptive gain which is set such that 0<γ holds.
On the other hand, the total correction coefficient-calculating section 110 calculates various correction coefficients by searching maps and tables, none of which are shown, according to parameters, such as the engine coolant temperature TW and the intake air temperature TA, indicative of the operating conditions of the engine 3 , and calculates a total correction coefficient KTOTAL by multiplying the thus calculated correction coefficients by each other.
Further, the multiplication element 111 calculates a required fuel injection amount Tcyl by the following equation (15):
Tcyl=Tcyl — bs·KSTR·KTOTAL (15)
Furthermore, the fuel attachment-dependent correction section 112 calculates the fuel injection amount TOUT by performing a predetermined fuel attachment-dependent correction process on the required fuel injection amount Tcyl calculated as above. Then, the fuel injection valve 10 is controlled such that the fuel injection timing and the valve-opening time period thereof are determined based on the fuel injection amount TOUT.
As expressed by the above equations (5) and (15), the air-fuel ratio controller 100 calculates the fuel injection amount TOUT based on the calculated intake air amount Gcyl, and as expressed by the equation (4), when Kg=0, Gcyl=Gcyl_vt holds, and when Kg=1, Gcyl=Gcyl_afm holds. This is because of the following reasons: As described hereinabove, within the range of Gin_vt≦Gin 1 , the reliability of the first estimated intake air amount Gcyl_vt exceeds that of the second estimated intake air amount Gcyl_afm, and hence within the above range, the fuel injection amount TOUT is calculated based on the first estimated intake air amount Gcyl_vt higher in reliability, to thereby ensure an excellent accuracy of calculation. Further, within the range of Gin 2 ≦Gin_vt, the flow rate of air flowing through the intake passage 12 a is large, and the reliability of the second estimated intake air amount Gcyl_afm exceeds that of the first estimated intake air amount Gcyl_vt, so that in the above range, the fuel injection amount TOUT is calculated based on the second estimated intake air amount Gcyl_afm higher in reliability, to thereby ensure an excellent accuracy of calculation.
Further, when 0<Kg<1 holds, the degrees of weighting the first and second estimated intake air amounts Gcyl_vt and Gcyl_afm in the calculated intake air amount Gcyl are determined by the value of the transition coefficient Kg. This is to avoid the occurrence of a torque step because it is considered that when one of Gcyl_vt and Gcyl_afm is directly switched to the other thereof, the torque step is caused by a large difference between the values of the first and second estimated intake air amounts Gcyl_vt and Gcyl_afm. In other words, as described hereinbefore, within the range of Gin 1 <Gin_vt<Gin 2 in which the transition coefficient Kg satisfies the relationship of 0<Kg<1, the transition coefficient Kg is set such that it assumes a value proportional to the estimated flow rate Gin_vt, so that when the estimated flow rate Gin_vt is varied between Gin 1 and Gin 2 , the transition coefficient Kg is progressively changed with the variation in the estimated flow rate Gin_vt. This causes the calculated intake air amount Gcyl to progressively change from a value of one of the first and second estimated intake air amounts Gcyl_vt and Gcyl_afm to a value of the other thereof. As a result, it is possible to avoid occurrence of the torque step.
Next, a description will be given of the corrected value-calculating section 113 . As described hereinafter, the corrected value-calculating section 113 is provided for correcting the valve lift Liftin and the cam phase Cain, respectively, to thereby calculate the corrected valve lift Liftin_comp and the corrected cam phase Cain_comp. In the present embodiment, the corrected value-calculating section 113 corresponds to correction means, and the corrected valve lift Liftin_comp and the corrected cam phase Cain_comp correspond to corrected operating condition parameters.
Referring to FIG. 15, the corrected value-calculating section 113 is comprised of an air-fuel ratio index value-calculating section 114 , a least-squares method filter 115 , nonlinear processing filters 116 and 117 , and addition elements 118 and 119 . First, the air-fuel ratio index value-calculating section 114 calculates an air-fuel ratio index value KAF (=KSTR/KCMD) by dividing the air-fuel ratio correction coefficient KSTR by the target air-fuel ratio KCMD. In the present embodiment, the air-fuel ratio index value KAF corresponds to a control state value and a value indicative of a control state of the air-fuel ratio.
Then, the least-squares method filter 115 calculates a statistically processed value KAF_LS of the air-fuel ratio index value (hereinafter simply referred to as “the statistically processed value KAF_LS”) with a fixed-gain sequential least-squares method algorithm expressed by the following equations (16) and (17):
In the above equation (16), e_ls represents the difference calculated by the equation (17), and P_ls a predetermined gain (fixed value). Further, in the equations (16) and (17), each portion with (k) represents discrete data sampled (or calculated) in synchronism with a predetermined control period ΔT (e.g. 5 msec in the present embodiment). The symbol k indicates a position in the sequence of sampling cycles of respective discrete data. For example, the symbol k indicates that discrete data therewith is a value sampled in the current control timing, and a symbol k−1 indicates that discrete data therewith is a value sampled in the immediately preceding control timing. This applies to the following discrete data. It should be noted that in the following description, the symbol (k) and the like provided for the discrete data are omitted as deemed appropriate.
Further, the nonlinear processing filter 116 calculates a lift correction value Dliftin_comp (correction amount of the operating condition parameter) by one of the following equations (18) to (20) based on the result of comparison between the above statistically processed value KAF_LS and predetermined upper and lower limit values KAF_LSH and KAF_LSL. It should be noted that in the equations (18) and (20), Dinc and Ddec both represent positive predetermined values.
When KAF_LS(k)≧KAF_LSH holds,
Dliftin — comp ( k )= Dliftin — comp ( k− 1)+ Dinc (18)
When KAF_LSL<KAF_LS(k)<KAF_LSH holds,
Dliftin — comp ( k )= Dliftin — comp ( k −1) (19)
When KAF_LS(k)≦KAF_LSL holds,
Dliftin — comp ( k )= Dliftin — comp ( k− 1)− Ddec (20)
Then, the addition element 118 calculates the corrected valve lift Liftin_comp by the following equation (21):
Liftin — comp ( k )= Liftin ( k )+ Dliftin — comp ( k ) (21)
The corrected value-calculating section 113 calculates the corrected valve lift Liftin_comp and the lift correction value Dliftin_comp, as described above. This is for the following reason: When the valve lift Liftin is controlled using the aforementioned variable valve lift mechanism 50 and pivot angle sensor 25 , the mounting angle of the pivot angle sensor 25 can be changed e.g. due to a change in temperature or an impact thereon, which will cause occurrence of a drift of the signal output from the pivot angle sensor 25 , or the tappet clearance can be changed due to wear of the adjusting bolt 52 a . In such a case, the valve lift Liftin calculated based on the signal output from the pivot angle sensor 25 deviates from an actual valve lift (hereinafter also referred to as “the actual value”).
When the above deviation of the valve lift Liftin from the actual value is occurring, if feedback control of the air-fuel ratio by the air-fuel ratio correction coefficient KSTR is performed during a stable operating condition of the engine 3 , e.g. during idling of the engine 3 , the detected air-fuel ratio KACT cannot converge to the target air-fuel ratio KCMD due to the deviation, and the air-fuel ratio continues to be made leaner or richer. For example, when the valve lift Liftin assumes a smaller value than the actual value, an actual intake air amount assumes a larger value than that of the calculated intake air amount Gcyl, whereby the detected air-fuel ratio KACT deviates toward the leaner side with respect to the target air-fuel ratio KCMD. As a result, the air-fuel ratio continues to be made richer, and the air-fuel ratio correction coefficient KSTR is set to a larger value than the target air-fuel ratio KCMD, which causes the air-fuel ratio index value KAF (=KSTR/KCMD) to assume a larger value than a value of 1. Inversely, when the valve lift Liftin assumes a larger value than the actual value, the air-fuel ratio index value KAF assumes a smaller value than a value of 1.
The above-described correlation exists between the deviation of the valve lift Liftin from the actual value and the air-fuel ratio index value KAF, and in the present embodiment, the air-fuel ratio control is carried out using the calculated intake air amount Gcyl calculated according to the corrected valve lift Liftin_comp, so that the deviation of the corrected valve lift Liftin_comp from the actual value is reflected on the air-fuel ratio index value KAF.
Therefore, when KAF_LS(k)≧KAF_LSH holds, since the corrected valve lift Liftin_comp used for calculation of the calculated intake air amount Gcyl deviates from the actual value toward the smaller side, the air-fuel ratio is controlled to be richer, so that by increasing the lift correction value Dliftin_comp, as expressed by the equation (18), it is possible to make the corrected valve lift Liftin_comp closer to the actual valve lift (see FIG. 36, referred to hereinafter). On the other hand, when KAF_LS(k)≦KAF_LSL holds, since the corrected valve lift Liftin_comp deviates from the actual value toward the larger side, the air-fuel ratio is controlled to be leaner, so that by decreasing the lift correction value Dliftin_comp as expressed by the equation (20), it is possible to make the corrected valve lift Liftin_comp closer to the actual valve lift.
Further, when KAF_LSL<KAF_LS(k)<KAF_LSH holds, the lift correction value Dliftin_comp is held at a fixed value without being updated. This is to avoid a process for calculating the corrected valve lift Liftin_comp and the feedback control of the air-fuel ratio from interfering with each other by holding the lift correction value Dliftin_comp at the fixed value and stopping update of the corrected valve lift Liftin_comp. Further, since deviation between the corrected v