Control apparatus of an internal combustion engine

Abstract: A control apparatus of an internal combustion engine which has an air-fuel ratio adjusting device for adjusting the air-fuel ratio of an air-fuel mixture, and an ignition device for igniting the air-fuel mixture. When a knock sensor detects a knocking state of the engine, it delivers a knock signal corresponding to the detected knocking state. In response to the knock signal delivered from the knock sensor, first correction data, which instantaneously prevents the knocking state by changing to a high degree, and second correction data, which corresponds to the properties of fuel used and prevents the knocking state by changing to a low degree, are calculated. The ignition timing is set in accordance with the calculated first and second correction data, whereby the operation of the ignition device is controlled. The air-fuel ratio is set in accordance with at least one of the first and second correction data, whereby the operation of the air-fuel ratio adjusting device is controlled.

Description: The present invention relates to a control apparatus of an internal combustion engine, and more particularly, to a control apparatus capable of air-fuel ratio control for fuels having different properties. In some cases, the properties of fuels used in internal combustion engines may vary in different localities or countries and depending on the season. In those countries in which leaded gasoline is being replaced by lead-free gasoline, there is a demand for the use of various fuels with different octane numbers. In engines matched to the use of low-octane fuels, the ignition timing is adjusted so as to tend to be retarded. If a high-octane fuel is used in these engines, therefore, it cannot fulfill its intrinsic potential for the engine output. In engines matched to the use of high-octane fuels, on the other hand, the ignition timing is adjusted so as to tend to advance. If a low-octane fuel is used in these engines, therefore, the engines will possible knock and be damaged. In order to avoid these awkward situations, an arrangement for ignition timing control (knock control) for the fuel used has been conventionally employed wherein an octane-number selector switch is provided which is shiftable according to the octane number of the fuel used. By shifting this switch, a basic ignition timing map is selected corresponding to the octane number of the fuel used. Also, a knock sensor is attached to the engine, whereby a retard amount is determined in accordance with a knock amount. Thus, a basic ignition timing calculated on the basis of a value read from the basic ignition timing map in accordance with the retard amount is corrected, so as to be suited to the fuel used. When a low-octane fuel is used, however, exhaust gas cannot be prevented from increasing its temperature so much that the components of an exhaust system are damaged, by only retarding the ignition timing. To eliminate this disadvantage, the octane-number selector switch shiftable according to the octane number of the fuel used can be used also for the selection of a basic injection quantity map. In this case, the basic injection quantity map is selected corresponding to the octane number of the fuel used, so that a basic injection quantity is adjusted to values corresponding to the rich and lean sides for low- and high-octane fuels, respectively. However, if the octane-number selector switch is manually operated to selected the basic ignition timing map and the basic injection quantity map, it is liable to suffer wrong operation or miss being operated. For example, if the selector switch is shifted to the low-octane side, under a misapprehension that a low-octane fuel is being used, the ignition timing is gradually switched to the advance (lead) side by knock control. Finally, the ignition timing is advanced to a point just before knocking is detected by the knock sensor. In this case, the air-fuel ratio is set on the rich side, to suit the low-octane fuel that was manually selected, so that the engine cannot be damaged. In contrast with this, if the octane-number selector switch is shifted to the high-octane side, under a misapprehension that a high-octane fuel is being used, the ignition timing is gradually retarded by knock control. Finally, the ignition timing is retarded to a point of time when knocking cannot be detected by the knock sensor. In this case, the air-fuel ratio is set on the lean side to suit the high-octane fuel that was manually selected, so that the exhaust gas may increase its temperature, thereby damaging the components of the exhaust system. If high-speed, high-load operation is continued, in particular, the possibility of such damage is high. GB-A-2 169 957 discloses a system for controlling the ignition timing of an internal combustion engine in which two ignition timings (one for high-octane fuel and one for low-octane fuel) are determined from look-up tables according to the engine speed and intake air pressure. The actual ignition timing is a weighted average of the two looked-up timings. The weighting factor is adjusted to advance or retard the ignition in response to whether or not knocking is detected, with the adjustments becoming progressively smaller until the adjustment process is terminated. EP-A-0 138 495, on which the preamble of claim 1 is based, discloses an ignition timing control apparatus in which knocking is sensed on startup and, if the knocking exceeds a certain value a setting of the engine (in one embodiment the air/fuel mixture and the initial ignition timing) is set to a value for low-octane fuel: otherwise, the setting is set to a value for high-octane fuel. Thereafter, the ignition is advanced or retarded depending on whether or not knocking is detected. A primary object of the present invention is to provide a control apparatus of an internal combustion engine permitting use of various fuels with different octane numbers and other properties. Another object of the present invention is to provide a control apparatus of an internal combustion engine, which is capable of ignition timing control and air-fuel ratio control best suited for the properties of the fuel used, thus preventing knocking of the engine and increase of the exhaust gas temperature. According to the present invention, there is provided control apparatus for an internal combustion engine which has air-fuel ratio control means for controlling the operation of an air-fuel mixture to be supplied to the engine, has ignition timing control means for controlling the timing of the ignition effected by an ignition device, and has knock detecting means for detecting a knocking state of the engine, the ignition timing control means including basic ignition timing setting means for setting a basic ignition timing based on a weighted average from the two sets of data in response to the engine load and the engine speed, and first correction means arranged to set an ignition timing by adding to the basic ignition timing a first correction which is changed in the ignition-retarding direction when knocking is detected and in the ignition-advancing direction when knocking is not detected, characterised in that the ignition timing control means includes second correction means arranged to change the weighting of the basic ignition timing in the ignition-retarding direction when the value of the first correction changes in the ignition-retarding direction to get outside a preset range and to change the basic ignition timing in the ignition-advancing direction when the value of the first correction changes in the ignition-advancing direction to get outside the preset range; and in that the air-fuel ratio control means is arranged to set the air-fuel ratio in correspondence with at least one of the first correction set by the first correction means and the change in the basic ignition timing set by the second correction means. Preferably, the control apparatus comprises correction data calculating means for calculating a value of first correction data, the value of the first correction data being so calculated that it changes in an ignition-retarding direction when knocking is detected, and changes in an ignition-advancing direction opposite to the ignition-retarding direction when knocking is not detected, and the said first correction to the ignition timing being derived from the said first correction data, characterised in that the correction data calculating means is arranged to calculate a value of second correction data tending to change to a lesser extent than the first correction data, in that the value of the second correction data is so calculated that it changes in an ignition-retarding direction when the value of the first direction data changes in its said ignition-retarding direction to get beyond a preset range, and changes in an ignition-advancing direction opposite to its said ignition-retarding direction when the value of the first correction data changes in its said ignition-advancing direction to get beyond the preset range, in that the said change to the basic ignition timing is derived from the second correction data, and in that the air-fuel ratio control means is arranged to set the air-fuel ratio in accordance with at least one of the said first and second correction data. The said changes in the basic ignition timing in the ignition-retarding and ignition-advancing directions are advantageously different in magnitude, and preferably the magnitude of the change in the ignition-retarding direction is greater than the magnitude of the change in the ignition-advancing direction. The air-fuel ratio control means is advantageously arranged to enrich the air-fuel ratio when the said first correction changes in the ignition-retarding direction, and to weaken the air-fuel ratio when the first correction changes in the ignition-advancing direction. Also, the air-fuel ratio control means is advantageously arranged to enrich the air-fuel ratio when the weighting of the basic ignition timing is changed by the second correction means in its said ignition-retarding direction, and to weaken the air-fuel ratio when the weighting of the basic ignition timing is changed by the second correction means in its said ignition-advancing direction. Preferably, moreover, the air-fuel ratio control means sets basic air-fuel ratio data in accordance with the load of the engine detected by load detecting means and the speed of the engine detected by speed detecting means, so that the air-fuel ratio is set by correcting the basic air-fuel ratio data in correspondence with the first correction. The first correction is calculated to take a value between predetermined upper and lower limit values so that the basic air-fuel ratio data is corrected to take a value on the fuel-rich side in correspondence with the deviation of the first correction from a predetermined reference value between the upper and lower limit values when the value of the first correction so changes in the ignition-retarding direction that it is beyond the reference value in that direction, and that the correction of the basic air-fuel ratio data corresponding to the first correction is stopped when the value of the first correction so changes that it is beyond the reference value in the ignition-advancing direction. Preferably, furthermore, the correction of the basic air-fuel ratio data corresponding to the first correction is effected only when a predetermined high-speed, high-load operating state of the engine is detected by operating state detecting means. Preferably, moreover, the air-fuel ratio control means stores first basic air-fuel ratio data adapted for a high-octane fuel and second basic air-fuel ratio data adapted for a low-octane fuel, calculates interior division point data of the stored first and second basic air-fuel ratio data in accordance with the said change in the basic ignition timing, and sets the air-fuel ratio in accordance with the calculated interior division point data. The correction data calculating means advantageously includes non-volatile memory means which retentively stores the said change in the basic ignition timing even after the operation of the engine is stopped, so that the said change in the basic ignition timing can be used when the engine is operated thereafter. Also, the correction data calculating means advantageously includes switch means which can be selectively shifted, by manual operation, between a first shift position to provide initial correction data adapted for a high-octane fuel and a second shift position to provide initial correction data adapted for a low-octane fuel, whereby the initial value of the said change in the basic ignition timing is given depending on the shift position of the switch means. The above and other objects, features, and advantages of the invention will be more apparent from the ensuing detailed description taken in connection with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a black diagram showing an arrangement of a control apparatus of an internal combustion engine according to the present invention; Fig. 2 is a block diagram showing an arrangement of a knock detecting circuit 16a contained in an electronic control unit 16 shown in Fig. 1; Fig. 3 is a timing chart for illustrating the operation of the knock detecting circuit 16a shown in Fig. 2; Figs. 4 and 5 are flow charts for illustrating a sequence of ignition timing setting operations executed by means of the electronic control unit 16 shown in Fig. 1; Fig. 6 is a graph showing a knock control operation region and a knock learning operation region of the internal combustion engine; Fig. 7 is a diagram showing a basic ignition timing map for premium-octane gasoline from which a basic ignition timing ϑ P is read in accordance with an engine speed Ne and an intake-air quantity A/N; Fig. 8 is a flow chart of a setting routine for a knock learning correction K NK ; Fig. 9 is a timing chart showing the relationship between the respective time-based transitions of a retard control amount ϑ R (t) and the knock learning correction K NK ; Fig. 10 is a graph showing the retard control amount ϑ R (t) compared with integration time intervals τ1 and τ2 and integration gains G K1 and G K2 ; Fig. 11 is a program flow chart showing a sequence of operations for setting the initial value of the knock learning correction K NK ; Fig. 12 is a flow chart for illustrating a sequence of operations for setting a valve-opening drive time T INJ of a fuel injection valve 20, executed by means of the electronic control unit 16 shown in Fig. 1; Fig. 13 is a graph showing an engine operation region in which the air-fuel ratio is to be corrected by means of a knock control amount ϑ K ; Fig. 14 is a graph showing the relationship between a retard A/F correction (Δ ϑ × K AFK ) and the knock control amount ϑ K ; and Fig. 15 is a diagram showing an A/F correction map for premium-octane gasoline from which an A/F correction factor K AFP is read in accordance with the engine speed Ne and the intake-air quantity A/N. DETAILED DESCRIPTION Referring first to Figs. 1 and 2, an arrangement of a control apparatus of an internal combustion engine according to the present invention will be described in detail. In Fig. 1, numeral 10 denotes a multi-cylinder internal combustion engine, e.g., a four-cylinder gasoline engine, and numeral 12 denotes a suction passage connected to the respective suction ports of engine cylinders. An air cleaner 13 and an air flow sensor 14 of a Ka'rman-vortex type are attached to an atmosphere-side open end portion of the suction passage 12. The air flow sensor 14, which is connected electrically to the input side of an electronic control unit (ECU) 16, supplies a Ka'rman vortex generation period signal f to the control unit 16. A throttle valve 18 is disposed in the middle of the suction passage 12, and a fuel injection valve 20 is provided at that portion of the suction passage 12 near the suction port of each engine cylinder. Each fuel injection valve 20 is connected to the output side of the electronic control unit 16, and is driven by means of a drive signal from the control unit 16. Various engine operation parameter sensors are connected to the input side of the electronic control unit 16. These sensors include a throttle sensor 19, intake-air temperature sensor 21, crank angle position sensor 22, engine-water temperature sensor 23, atmospheric pressure sensor 24, octane-number selector switch (OSS) 25, knock sensor 26, etc., for example. The throttle sensor 19 is used to detect the valve opening ϑt of the throttle valve 18. The intake-air temperature sensor 21, which is mounted in the air cleaner 13, is used to detect the intake-air temperature Ta. The position sensor 22 serves to detect a predetermined crank angle position (e.g., 75° before the top dead center of the suction stroke) of each engine cylinder. The engine-water temperature sensor 23 and the atmospheric pressure sensor 24 are used to detect the cooling-water temperature Tw of the engine 10 and the atmospheric pressure Pa, respectively. The OSS 25 is manually shiftable between two positions, e.g., a premium-octane (e.g., RON-95) position and a regular-octane (e.g., RON-91) position, depending on the octane number of fuel supplied to the engine 10. The knock sensor 26, which is attached to a cylinder block of the engine 10, is used to detect the knock level of the engine. Detection signals from these sensors are supplied to the electronic control unit 16. An ignition plug 30 is attached to each cylinder of the engine 10. The plug 30 is connected to the input side of the electronic control unit 16 through a distributor 29 and an igniter unit 28, which includes an ignition coil to generate a high secondary voltage. The igniter unit 28 produces the high secondary voltage in response to an ignition signal from the electronic control unit 16. The high secondary voltage is supplied in regular succession to the respective ignition plugs 30 of the individual cylinders by means of the distributor 29. The electronic control unit 16 comprises a central processing unit (CPU), ROM, RAM, nonvolatile RAM, I/O interface, A/D converter, knock detector circuit 16a, etc. Illustration of all these elements except the circuit 16a is omitted. The CPU calculates the ignition timing, injection quantity, etc., which will be mentioned later. The ROM stores various arithmetic programs, while the RAM temporarily stores data. The nonvolatile RAM retentively stores those data which continue to be necessary even after the operation of the engine 10 is stopped, and is backed up by a battery. The electronic control unit 16 calculates the ignition timing in the manner mentioned later, in accordance with engine operation parameter values detected by means of the various aforementioned sensors. Based on the calculated ignition timing, the control unit 16 delivers the ignition signal, calculates the injection quantity, and delivers a valve opening drive signal to the fuel injection valves 20. The knock detector circuit 16a is composed of a band-pass filter (BPF) 32, noise level detector 33, comparator 34, and integrator 35. The knock sensor 26 is connected to the input of the BPF 32, the output of which is connected to one input terminal of the comparator 34 and also to the input of the noise level detector 33. The output of the noise level detector 33 is connected to the other input terminal of the comparator 34. The output of the comparator 34 is connected to the input of the integrator 35, the output of which is connected to the input of the aforesaid A/D converter (not shown). The following is a description of the operation of the internal combustion engine constructed in this manner. Referring first to Fig. 3, a method of detecting the knock level of the engine 10, by means of the knock sensor 26 and the knock detector circuit 16a, will be described. Each time the crank angle position sensor 22 detects the predetermined crank angle position (75 ° before the top dead center (BTDC) of the suction stroke), it delivers a predetermined crank angle position signal STG (see Fig. 3(a)) which maintains the high level throughout a predetermined crank angle (e.g., 70° ). An output signal from the knock sensor 26, which has detected a vibration propagated through the cylinder block of the engine 10, is filtered (see Fig. 3(c)) by means of the BPF 32. The output of the BPF 32 mixedly contains a noise signal and a knock signal. The comparator 34 separate the knock signal from the noise signal, and delivers a high-level signal (see Fig. 3(d)) while the knock signal is being inputted at a level higher than a predetermined threshold value. The integrator 35 detects the high-level signal from the comparator 34 with every predetermined period of time. Each time it detects the high-level signal, the integrator 35 delivers a knock-level signal Vn which increases by a fixed value at a time, and holds this signal level. The integrator 35 is constructed so as to be reset by means of a reset signal (see Fig. 3(f)) which is synchronous with the predetermined crank angle position signal STG. Therefore, the knock-level signal Vn of the integrator 35 corresponds to the level of a knock produced between each two adjacent BTDC-75 ° positions. On production of the predetermined crank angle position signal STG, the output level of the integrator 35 is converted into a digital signal by the A/D converter, and is read by the CPU. Referring now to Figs. 4 to 11, the sequence of ignition timing control by means of the electronic control unit 16 will be described. The program flow charts of Figs. 4 and 5 illustrate the sequence of operations for calculating the optimum ignition timing for the properties of the fuel and the operating conditions of the engine 10. Each time the crank angle position sensor 22 detects the predetermined crank angle position (BTDC-75 °), the electronic control unit 16 executes the program shown in Figs. 4 and 5. First, the electronic control unit 16 reads the signal values of the various aforementioned sensors, i.e., the Ka'rman vortex generation period signal f , throttle valve opening ϑt, intake-air temperature Ta, cooling-water temperature Tw, atmospheric pressure Pa, knock level Vn, etc. These signal values are stored in the aforementioned memories, and the on/off state of the OSS 25 is detected and stored in the memories (Step 40). The program then proceeds to Step 41, whereupon the engine speed Ne and intake-air quantity A/N are calculated. The engine speed Ne is calculated on the basis of the time interval between the point of time of the input of the preceding STG-signal and the instant that the present STG-signal is generated. The intake-air quantity A/N is obtained as a mass flow quantity per suction stroke by multiplying an intake-air volume flow rate, which is obtained according to the Ka'rman vortex generation period signal f and the engine speed Ne, by an air density obtained from the atmospheric pressure Pa and the intake-air temperature Ta. The engine speed Ne and the intake-air quantity A/N are stored in the aforementioned RAM. Subsequently, the electronic control unit 16 determines whether the engine 10 is operated within a knock-inducible operation region, i.e., knock control zone (Step 43). In Fig. 6, the knock control zone is indicated by a hatched region B, which is defined between a full-open load working line WOT of the throttle valve 18 and a load working line (indicated by the broken line), and is restricted by a predetermined engine speed N3 (e.g., 6,000 rpm). If the decision of Step 43 is NO, that is, when the engine 10 is operated outside the region B, a knock control amount ϑ K (mentioned later) is adjusted to zero (Step 45) since there is no possibility of knocking. Thereupon, the program proceeds to Step 64 of Fig. 5, as mentioned later. If the decision of Step 43 is YES, that is, when the engine 10 is operated within the knock control zone, whether the knock level Vn is high than a predetermined threshold value V RTH is determined (Step 46). If the decision of Step 46 is NO, a present retard change amount ϑn(t) is adjusted to zero (Step 48), and the program advances to Step 54, as mentioned later. If the decision of Step 46 is YES, the program proceeds to Step 50, whereupon the present retard change amount ϑn(t) is calculated as follows: ϑn(t) = (Vn - V RTH ) x K1, (1) where K1 is a predetermined coefficient. The present retard change amount ϑn(t) calculated according to equation (1) is compared with a predetermined maximum allowable value ϑ RMAX1 (Step 51). If the value ϑn(t) is smaller than the maximum allowable value ϑ RMAX1 , the program proceeds directly to Step 54. If the value ϑn(t) is greater than the value ϑ RMAX1 , the former is readjusted to the latter (Step 52), and the program proceeds to Step 54. It is not advisable, in view of drivability, to change the retard amount drastically, so that the retard amount is restricted. In Step 54, the present retard amount ϑ R (t) is calculated as follows: ϑ R (t) = ϑ R (t-1) + ϑn(t), (2) where ϑ R (t-1) is the preceding retard amount calculated during the preceding execution of the program, and the present retard amount is obtained by adding the present retard change amount ϑn(t) to the preceding retard amount ϑ R (t-1). The program then proceeds to Step 55, in which whether a predetermined time τ (e.g., 0.2 to 1.0 second) has passed after the preceding execution of Step 56 (mentioned later) is determined. If the passage of the predetermined time τ is not detected, that is, if the decision of Step 55 is NO, the program proceeds to Step 58 without changing the present retard amount ϑ R (t) set in Step 54. If the decision of Step 55 is YES, a predetermined fine retard amount ΔR R is subtracted from the present retard amount ϑ R (t) set in Step 54, and the remainder is reset as the present retard amount ϑ R (t). Thereafter, the program proceeds to Step 58. ϑ R (t) = ϑ R (t) - ΔR R . (3) In Steps 58 to 61, whether the set present retard amount ϑ R (t) is within a predetermined range is determined. More specifically, whether the amount ϑ R (t) is not greater than an upper limit value ϑ RMAX2 is determined in Step 58, and whether it is not smaller than a lower limit value (zero) is determined in Step 60. If the present retard amount ϑ R (t) is greater than the upper limit value ϑ RMAX2 or smaller than the lower limit value 0, it is readjusted to the limit value (Step 59 or 61), and is stored as a knock control amount ϑ K in the memories. ϑ K = ϑ R (t). (4) Using the knock control amount ϑ K set in this manner, the electronic control unit 16 calculates the ignition timing ϑ A as follows (Step 64): ϑ A = ϑ B + max( ϑ WT , ϑ AP ) + ϑ AT - ϑ k , (5) where ϑ B is a basic ignition timing. A method of setting the timing ϑ B will be mentioned later. ϑ WT and ϑ AP are a water-temperature correction and an atmospheric pressure correction, respectively. The water-temperature correction ϑ WT is set in accordance with a cooling-water temperature T W detected by the engine-water temperature sensor 23, while the atmospheric pressure correction ϑ AP is set in accordance with the atmospheric pressure Pa detected by the atmospheric pressure sensor 24. The greater one of the corrections ϑ WT and ϑ AP is added to the basic ignition timing ϑ B . ϑ AT is an intake-air temperature correction, which is set in accordance with the intake-air temperature detected by the intake-air temperature sensor 21. The basic ignition timing ϑ B is set as follows: ϑ B = K NK · ϑ P + (1 - K NK ) · ϑ R , (6) where ϑ P and ϑ R are ignition timings calculated on the basis of values read from ignition timing maps prepared for premium-octane gasoline (hereinafter referred to simply as RON-95) and regular-octane gasoline (hereinafter referred to simply as RON-91), respectively. Fig. 7 shows the ignition timing map for the RON-95 stored in the memories of the electronic control unit 16. Using the conventional 4-point interpolation method, for example, the ignition timing ϑ P , which corresponds to the engine speed Ne and the intake-air quantity A/N calculated and stored in Step 41, is read from the map of Fig. 7 and calculated. The ignition timing map (not shown) for the RON-91, which is also stored in the memories, resembles the map for the RON-95 shown in Fig. 7. Like the ignition timing ϑ P , the ignition timing ϑ R , which corresponds to the engine speed Ne and the intake-air quantity A/N, is read from the ignition timing map for the RON-91 and calculated. The values corresponding to the engine speed Ne and the intake-air quantity A/N, which are common to the ignition timing maps for the RON-95 and RON-91, are set so that the value read from the map for the RON-95 is greater than or on the advance side of the value read from the map for the RON-91. K NK is a knock learning correction, which is adjusted to a value within a range of 0 to 1.0 according to a setting routine for the knock learning correction K NK mentioned later. The greater the value of the knock learning correction K NK , the nearer to the value read from the ignition timing map for the RON-95, i.e., the deeper on the advance side, the value of the basic ignition timing ϑ B , calculated according to equation (6), will be. The knock learning correction K NK is set according to its setting routine shown in Fig. 8. In Step 80 of Fig. 8, the electronic control unit 16 first determines whether a learning condition to require the knock learning correction K NK to be updated is established. This learning condition is fulfilled when the engine 10 is operated within an operation region A shown in Fig. 6, i.e., a higher-load region of the operation region B, the engine speed Ne is not higher than a predetermined maximum speed N2 (e.g., 5,000 rpm; lower than the predetermined speed N3) , and is not lower than a predetermined minimum speed N1 (e.g., 1,800 rpm), the cooling-water temperature detected by the engine-water temperature sensor 23 is not lower than a predetermined value (e.g., 80 °C), the engine operation is stable, and the engine 10- is operated within the knock-inducible operation region. If the aforesaid learning condition is not established, the present routine is finished without any change. If the decision of Step 80 is YES, that is, if the aforementioned learning condition is established, the program proceeds to Step 81, whereupon whether the present retard amount ϑ R (t) set in Figs. 4 and 5 is not smaller than a predetermined upper limit value ϑ R2 is determined. If the decision of Step 81 is NO, the program advances to Step 83, whereupon whether the present retard amount ϑ R (t) is not greater than a predetermined lower limit value ϑ R1 , which is smaller than the upper limit value ϑ R2 , is determined. If the decision of Step 83 is NO, that is, if the present retard amount ϑ R (t) takes a value between the upper and lower limit values (before time t1 of Fig. 9(a)), the present routine is finished without changing the knock learning correction K NK at all. If the engine 10 knocks so that the present retard amount ϑ R (t) exceeds the predetermined upper limit value ϑ R2 , that is, if the decision of Step 81 is YES, the program proceeds to Step 82. Thereupon, whether a first predetermined integration time interval τ1, immediately after the start of the execution of Step 82, is terminated is determined. If the time interval τ1 is not terminated yet, the knock learning correction K NK is kept at the preceding value without being changed. If the respective decisions of Steps 80 and 81 both continue to be YES, the determination of Step 82 is repeated. Each time the predetermined time interval τ1 is terminated, the program proceeds to Step 86, whereupon a first predetermined integration gain G K1 is subtracted from the preceding value K NK (t-1) of the knock learning correction. Thus, a value smaller than the preceding value is given as a new present knock learning correction K NK (t) (between times t1 and t2 of Fig. 9(b)). If the present retard amount ϑ R (t) takes a value between the upper and lower limit values ϑ R2 and ϑ R1 again (between times t2 and t3 of Fig. 9(a)), the knock learning correction K NK is kept again at the preceding value (between times t2 and t3 of Fig. 9(b)). If the engine 10 does not continue to knock any more, the predetermined fine retard amount ΔR R is subtracted from the present retard amount ϑ R (t) with every passage of the predetermined time τ, as mentioned before. Thus, the present retard amount ϑ R (t) is gradually reduced to a value smaller than the predetermined lower limit value ϑ R1 , so that the decisions of Steps 81 and 83 become NO and YES, respectively. If the decision of Step 83 is YES, the electronic control unit 16 executes Step 84, whereupon a second predetermined integration time interval τ2, immediately after the start of the execution of Step 84, is terminated is determined. If the time interval τ2 is not terminated yet, the knock learning correction K NK is kept at the preceding value without being changed. If the respective decisions of Steps 80 and 83 both continue to be YES, and if the decision of Step 81 continues to be NO, the determination of Step 84 is repeated. Each time the predetermined time interval τ2 is terminated, the program proceeds to Step 88, whereupon a second predetermined integration gain G K2 is added to the preceding value K NK (t-1) of the knock learning correction. Thus, a value greater than the preceding value is given as a new present knock learning correction K NK (t) (between times t3 and t4 of Fig. 9(b)). If the present retard amount ϑ R (t) takes a value between the upper and lower limit values ϑ R2 and ϑ R1 again (on and after time t4 of Fig. 9(a)), the knock learning correction K NK is kept again at the preceding value (on and after time t4 of Fig. 9(b)). The correction K NK is stored in the nonvolatile RAM contained in the electronic control unit 16, and the stored value is maintained even after the engine 10 is stopped. Fig. 10 shows the retard amount ϑ R (t) compared with the integration time intervals τ1 and τ2 and the integration gains G K1 and G K2 . In the present embodiment, the absolute values of the integration gains G K1 and G K2 are equal, the integration time interval τ2 , which is set when the retard amount ϑ R (t) is not greater than the lower limit value ϑ R1 , is greater than the integration time interval τ1, which is set when the amount ϑ R (t) is not smaller than the upper limit value ϑ R2 , and the time interval for the addition of the integration gain G K2 is longer than the time interval for the subtraction of the integration gain G K1 . The correction gain is changed by thus setting these values. Moreover, nonsensitive zones are provided in which the knock learning correction K NK is kept at the preceding value when the retard amount ϑ R (t) takes a value between the upper and lower limit values ϑ R2 and ϑ R1 . These nonsensitive zones serve to stabilize the control. The method of changing the correction gain is not limited to the embodiment described above, and the same effect as aforesaid can be obtained by setting the values so that the integration time intervals τ1 and τ2 are equivalent, and that the integration gain G K2 is smaller than G K1 . In the above embodiment, moreover, the nonsensitive zones are provided so that the knock learning correction K NK is held as it is when the present retard amount ϑ R (t) takes a value between the predetermined upper and lower limit values ϑ R2 and ϑ R1 . In some cases, however, the nonsensitive zones need not be provided. The initial value of the knock learning correction K NK is set depending on the shift position of the OSS 25 when the OSS 25 is shifted. More specifically, the electronic control unit 16 first determines whether the OSS 25 is shifted so that its output is inverted (Step 90), as shown in Fig. 11. If the decision of Step 90 is NO, the current value of the correction K NK is maintained without being updated. If the decision of Step 90 is YES, whether the OSS 25 is on is determined Step 91). If the decision of Step 91 is YES, that is, when the OSS 25 is on, the initial value of the knock learning correction K NK is set to 1, which is indicative of the use of the RON-95 (premium-octane gasoline) (Step 92). If the decision of Step 91 is NO, that is, when the OSS 25 is off, the initial value of the correction K NK is set to 0, which is indicative of the use of the RON-91 (regular-octane gasoline) (Step 94). The initial value of the knock learning correction K NK is stored in nonvolatile RAM. In the determination of Step 91, it may be concluded that the OSS 25 is on or off only when the on- or off-state continues for a predetermined period of time (e.g., one second). If a battery backup line of the nonvolatile RAM is removed during maintenance work for example, the initial value of the knock learning correction K NK may be set after the on/off state of the OSS 25 is determined, in the same manner as aforesaid, at the time of connecting the backup line. Thus, the basic ignition timing ϑ B can be adjusted to an optimum value for the properties of the fuel used, on the basis of the knock learning correction K NK . Returning to Step 64 of Fig. 5, the electronic control unit 16 delivers the ignition signal to the igniter unit 28 in accordance with the ignition timing ϑ A calculated and set in the aforementioned manner, thereby causing the igniter unit 28 to ignite an air-fuel mixture at the crank angle position corresponding to the ignition timing ϑ A . Referring now to Figs. 12 to 14, an air-fuel ratio control method according to the present invention will be described. The flow chart of Fig. 12 shows a sequence of arithmetic operations for a valve-opening drive time T INJ of the fuel injection valves 20. The electronic control unit 16 first determines whether the engine is being operated within a predetermined operation region in which the air-fuel ratio is to be corrected by means of the knock control amount ϑ K (Step 100). In this predetermined operation region, the air-fuel ratio is corrected to take a value on the rich side, in accordance with an instantaneous knock amount detected by means of the knock sensor 26. As indicated by hatching in Fig. 13, this operation region is a high-speed, high-load operation region for a predetermined engine speed Ns (e.g., approximately 3,000 rpm) or higher speed, which is defined between the full-open load working line WOT of the throttle valve 18 and a predetermined partial load working line A/N(s). If the engine 10 is not being operated within this operation region, that is, if the decision of Step 100 is NO, the program proceeds to Step 102 since there is no possibility of an exhaust system's burning or the like. Thereupon, the value of a deviation Δ ϑ (mentioned later) is adjusted to 0. If the deviation Δ ϑ is adjusted to zero, the correction of the instantaneous air-fuel ratio by means of the knock control amount ϑ K is not effected. If the decision of Step 100 is YES, the program proceeds to Step 101, whereupon the electronic control unit 16 determines whether the knock control amount ϑ K set in Step 45 of Fig. 4 and Step 63 of Fig. 5 is not smaller than a predetermined threshold value ϑ AF . If the knock control amount ϑ K is smaller than the threshold value ϑ AF , the program proceeds to Step 101, whereupon the deviation Δ ϑ is adjusted to zero. If the knock control amount ϑ K is not smaller than the threshold value ϑ AF , the program proceeds to Step 103, whereupon the deviation Δ ϑ (= ϑ K - ϑ AF ) between the knock control amount ϑ K and the predetermined threshold value ϑ AF is calculated. A retard A/F correction is the product of the deviation Δ ϑ, calculated in Steps 100 to 103, and a retard A/F correction factor K AFK . Fig. 14 shows the relationship between the retard A/F correction ( Δ ϑ x K AFK ) and the knock control amount ϑ K . As seen from Fig. 14, the range between 0 and ϑ AF , with respect to the knock control amount ϑ K , is a nonsensitive zone in which the deviation Δ ϑ is set to zero. If the knock control amount ϑ K takes a value within this nonsensitive zone, enrichment (mentioned later) of the air-fuel ratio corresponding to the amount ϑ K is not effected. Subsequently, electronic control unit 16 calculates an A/F correction factor K AF as follows: K AF = K NK · K AFP + (1 - K NK ) x K AFR + Δ ϑ · K AFK . (7) Here K NK is the same knock learning correction as the one set in Step 86 or 88 and used for the calculation of the basic ignition timing ϑ B , and K AFP and K AFR are A/F correction factors calculated on the basis of values read from A/F correction maps prepared for the RON-95 (premium-octane gasoline) and the RON-91 (regular-octane gasoline), respectively. Fig. 15 shows the A/F correction map for the RON-95 stored in the memories of the electronic control unit 16. Using the conventional 4-point interpolation method, the A/F correction factor K AFP , which corresponds to the engine speed Ne and the intake-air quantity A/N calculated and stored in Step 41 of Fig. 4, is read from the map of Fig. 15 and calculated. The A/F correction map (not shown) for the RON-91, which is also stored in the memories, resembles the correction map for the RON-95 shown in Fig. 15. Like the A/F correction factor K AFP , the A/F correction factor K AFR , which corresponds to the engine speed Ne and the intake-air quantity A/N, is read from the A/F correction map for the RON-91 and calculated. The values corresponding to the engine speed Ne and the intake-air quantity A/N, which are common to the A/F correction maps for the RON-95 and RON-91, are set so that the value read from the correction map for the RON-95 is smaller than or on the fuel-lean side of the value read from the correction map for the RON-91. The A/F correction factor K AF calculated according to equation (7) is checked for its upper limit value in Step 106. More specifically, whether the value of the A/F correction factor K AF is not smaller than a predetermined upper limit value K AFMAX is determined in Step 106. If the value of the factor K AF is smaller than the upper limit value K AFMAX , the program proceeds to Step 108 without changing the value K AF . If the value K AF is not smaller than the upper limit value K AFMAX , the A/F correction factor is readjusted to the value K AFMAX in Step 107, whereupon the program proceeds to Step 108. Using the A/F correction factor K AF set in this manner, the valve-opening drive time T INJ of the fuel injection valves 20 is calculated in Step 108 as follows: T INJ = T B · K AF · K2 · K3 + Tb, (8) where T B is a basic drive time, which is calculated on the basis of a value read from a basic drive time map stored in the ROM of the electronic control unit 16, in accordance with the engine speed Ne and the intake-air quantity A/N. K2 is an A/N learning correction factor, and K3 is another correction factor for cooling-water temperature correction, acceleration correction, etc. The A/N learning correction factor K2 is set in accordance with a detection value of the O₂ concentration of exhaust gas, and is obtained as a time mean value of an O₂ feedback correction factor for the feedback control of the air-fuel ratio to a predetermined value (theoretical air-fuel ratio). Tb is an injection valve operation dead time correction set corresponding to the battery voltage and the like. Based on the valve-opening drive time T INJ set in this manner, the electronic control unit 16 can deliver a drive signal to the fuel injection valve 20, thereby causing the engine 10 to be supplied with a quantity of fuel corresponding to the optimum air-fuel ratio for the retard amount of the ignition timing. In the embodiment described above, the valve-opening drive time T INJ is obtained by multiplying the basic drive time T B by the A/F correction factor K AF which is set in accordance with the knock learning correction K NK and the knock control amount ϑ K . The present invention is not, however, limited to this embodiment, and various modifications may be applied to the method for correcting the quantity of fuel injection into the engine 10 by means of the knock amount. For example, the basic drive time T B may be calculated according to the following equation (9) similar to equation (6) which is used to calculate the basic ignition timing ϑ R . T B = K NK · T P + (1 - K NK ) · T R , (9) where T P and T R are basic drive times calculated on the basis of values read from basic drive time maps prepared for the RON-95 and RON-91, respectively, in accordance with the engine speed Ne and the intake-air quantity A/N. In this case, the A/F correction factor K AF may be calculated as follows: K AF = 1 + Δ ϑ · K AFK . (10) Moreover, the output of the knock sensor 26 may be connected to a knock detector circuit formed of an analog circuit, in place of the knock detector circuit 16a. This analog circuit may, for example, be a charge and discharge circuit, which is quickly charged when a knock is produced, and is gradually discharged when no knock is produced, without being reset by means of the reset signal every time the predetermined crank angle position signal STG is generated. In the embodiment described above, the ignition device is provided with an electronic advance unit. Alternatively, however, it may be provided with a knock retard unit as well as an advance unit which includes a so-called vacuum advancer and a governor. The vacuum advancer serves to advance the ignition timing as a negative suction-passage pressure increases, while the governor advances the ignition timing with the increase of the engine speed. Furthermore, the air-fuel ratio adjusting device may be a fuel injection device, as in the case of the aforementioned embodiment, or an electronically-controlled carburetor which is provided with an electromagnetic solenoid valve for opening/closing the main jet (orifice) in accordance with a duty factor. Alternatively, the air-fuel ratio adjusting device may be constructed so that a by-pass valve is attached to an air passage which by-passes a carburetor, whereby the air-fuel ratio can be variably adjusted by controlling the opening of the by-pass valve.

Claims: Control apparatus (16) for an internal combustion engine (10) which has air-fuel ratio control means (18) for controlling the operation of an air-fuel ratio adjusting device (20) for adjusting the air-fuel ratio of an air-fuel mixture to be supplied to the engine, has ignition timing control means (16) for controlling the timing of the ignition effected by an ignition device (28, 29), and has knock detecting means (26, 16a) for detecting a knocking state of the engine, the ignition timing control means (16) including basic ignition timing setting means (16) for setting a basic ignition timing (ϑ B ) based on a weighted average from the two sets of data in response to the engine load and the engine speed, and first correction means (16) arranged to set an ignition timing (ϑ A ) by adding to the basic ignition timing a first correction (ϑ K ) which is changed in the ignition-retarding direction when knocking is detected (step 54) and in the ignition-advancing direction when knocking is not detected (step 56), characterised in that the ignition timing control means includes second correction means (16) arranged to change the weighting of the basic ignition timing (ϑ B ) in the ignition-retarding direction when the value of the first correction changes in the ignition-retarding direction to get outside a preset range (step 86) and to change the basic ignition timing (ϑ B ) in the ignition-advancing direction when the value of the first correction changes in the ignition-advancing direction to get outside the preset range (step 88); and in that the air-fuel ratio control means (16) is arranged to set the air-fuel ratio in correspondence with at least one of the first correction set by the first correction means and the change in the basic ignition timing set by the second correction means. Control apparatus according to claim 1, which comprises correction data calculating means (16) for calculating a value of first correction data (ϑ R (t), ϑ K ), the value of the first correction data (ϑ R (t), ϑ K ) being so calculated that it changes in an ignition-retarding direction (ϑ R (t) increasing) when knocking is detected, and changes in an ignition-advancing direction (ϑ R (t) decreasing) opposite to the ignition-retarding direction when knocking is not detected, and the said first correction to the ignition timing being derived from the said first correction data, characterised in that the correction data calculating means (16) is arranged to calculate a value of second correction data (K NK ) tending to change to a lesser extent than the first correction data (ϑ R (t), ϑ K ), in that the value of the second correction data (K NK ) is so calculated that it changes in an ignition-retarding direction (K NK decreasing) when the value of the first correction data changes in its said ignition-retarding direction to get beyond a preset range, and changes in an ignition-advancing direction (K NK increasing) opposite to its said ignition-retarding direction when the value of the first correction data changes in its said ignition-advancing direction to get beyond the preset range, in that the said change to the basic ignition timing is derived from the second correction data, and in that the air-fuel ratio control means is arranged to set the air-fuel ratio in accordance with at least one of the said first and second correction data. Control apparatus according to claim 1 or claim 2, wherein the air-fuel ratio control means is arranged to enrich the air-fuel ratio when the said first correction changes in the said ignition-retarding direction, and to weaken the air-fuel ratio when the said first correction changes in the said ignition-advancing direction. Control apparatus according to any one of claims 1 to 3, wherein the air-fuel ratio control means is arranged to enrich the air-fuel ratio when the weighting of the basic ignition timing is changed by the second correction means in its said ignition-retarding direction, and to weaken the air-fuel ratio when the weighting of the basic ignition timing is changed by the second correction means in its said ignition-advancing direction. Control apparatus according to any one of claims 1 to 4, wherein the air-fuel ratio control means is arranged to store first basic air-fuel ratio data appropriate for a high-octane fuel and second basic air-fuel ratio data appropriate for a low-octane fuel, calculate an interior division point of the stored first and second basic air-fuel ratio data in accordance with the said change in the weighting of the basic ignition timing, and set the air-fuel ratio in accordance with the calculated interior division point. Control apparatus according to claim 5, wherein the calculated interior division point serves as modified basic air-fuel ratio data, the said first correction being so calculated as to take a value between predetermined upper and lower limit values so that the modified basic air-fuel ratio data is corrected to take a value on the fuel-rich side in accordance with the deviation of the first correction from a predetermined reference value between the upper and lower limit values when the said first correction so changes in its said ignition-retarding direction that it is beyond the reference value in that direction, and that the correction of the modified basic air-fuel ratio data corresponding to the said first correction is stopped when the said first correction so changes in its said ignition-advancing direction that it is beyond the reference value in the latter direction. Control apparatus according to any one of claims 1 to 6, which comprises load detecting means for detecting the load of the engine, speed detecting means for detecting the speed of the engine, and operating state detecting means for detecting a predetermined high-speed, high-load operating state of the engine; and wherein the air-fuel ratio control means is arranged to set basic air-fuel ratio data in accordance with the engine load detected by the load detecting means and the engine speed detected by the speed detecting means, so that the air-fuel ratio is set by correcting the basic air-fuel ratio data in correspondence with the said first correction, the correction of the basic air-fuel ratio data corresponding to the said first correction being effected only when the predetermined high-speed, high-load operating state is detected by the operating state detecting means. Control apparatus according to any one of claims 1 to 7, which comprises load detecting means for detecting the load of the engine and speed detecting means for detecting the speed of the engine; and wherein the air-fuel ratio control means is arranged to set basic air-fuel ratio data in accordance with the engine load detected by the load detecting means and the engine speed detected by the speed detecting means, so that the air-fuel ratio is set by correcting the basic air-fuel ratio data in correspondence with the said first correction, the first correction being calculated to take a value between predetermined upper and lower limit values so that the basic air-fuel ratio data is corrected to take a value on the fuel-rich side in correspondence with the deviation of the first correction from a predetermined reference value between the upper and lower limit values when the value of the first correction so changes in its said ignition-retarding direction that it is beyond the reference value in that direction, and that the correction of the basic air-fuel ratio data corresponding to the first correction is stopped when the value of the first correction so changes that it is beyond the reference value in its said ignition-advancing direction. Control apparatus according to any one of claims 1 to 8, wherein the said change in the basic ignition timing is maintained unchanged during any period in which the first correction remains within the preset range. Control apparatus according to any one of claims 1 to 9, wherein the said changes in the basic ignition timing in the ignition-retarding and ignition-advancing directions are different in magnitude. Control apparatus according to claim 10, wherein the magnitude of the said change in the basic ignition timing in the ignition-retarding direction is higher than that in the ignition-advancing direction. Control apparatus according to any one of claims 2 to 11, wherein the correction data calculating means includes nonvolatile memory means for retentively storing the second correction data even after the operation of the engine is stopped, the second correction data stored in the memory means being used when the engine is operated thereafter. Control apparatus according to any one of claims 2 to 12, wherein the correction data calculating means includes switch means capable of being moved, by manual operation, between a first position to provide initial correction data appropriate for a high-octane fuel and a second position to provide initial correction data appropriate for a low-octane fuel, and wherein the initial value of the second correction data depends on the position of the switch means. An internal combustion engine equipped with control apparatus according to any one of claims 1 to 13. A motor vehicle powered by an internal combustion engine as claimed in claim 14.

Inventors: HASHIMOTO TORU, SUGIURA MAMORU, TAKAHASHI AKIRA, HASHIMOTO, TORU, SUGIURA, MAMORU, TAKAHASHI, AKIRA
Applicants: MITSUBISHI MOTORS CORP, MITSUBISHI JIDOSHA KOGYO KABUSHIKI KAISHA
Application year: 1988
Main classification: F02P5
IPC codes: F02B1, F02P5, F02D37, F02D41