Control system for internal combustion engines

Abstract: A control system for an internal combustion engine (1) estimates an amount of fuel adhering to the inner surface of the intake passage (2), as well as an amount of fuel evaporated from fuel adhering to the inner surface of the intake passage (2) and carried into the combustion chambers, determines an amount of supply fuel to be supplied to the engine (1), based upon operating conditions of the engine, the estimated adherent fuel amount, and the estimated carried-off fuel amount, and supplies the determined supply fuel amount into the intake passage (2). The control system corrects the estimated adherent fuel amount and the estimated carried-off fuel amount, in response to the valve operating characteristics of intake valves and/or exhaust valves.

Description: This invention relates to a control system for internal combustion engines, and more particularly to a control system which controls the supply of fuel injected into an intake pipe in a manner compensating for a fuel amount adhering to the inner surface of the intake pipe. In conventional internal combustion engines of the type that fuel is injected into an intake pipe, there is a problem that some of the injected fuel adheres to the inner surface of the intake pipe, so that a required amount of fuel cannot be drawn into the combustion chamber. To solve this problem, there has been proposed a fuel supply control method which estimates a fuel amount which is to adhere to the inner surface of the intake pipe and one which is to be drawn into the combustion chamber by evaporation from the fuel adhering to the intake pipe, and determines a fuel injection amount in dependence on the estimated fuel amounts (Japanese Provisional Patent Publication (Kokai) No. 61-126337). GB-A-2228592 also relates to a similar system in which an adherent fuel amount is estimated based on the quantity of fuel injected and the fuel adhesion and evaporation rates, the adhesion rate being derived from the throttle opening and coolant temperature, and the evaporation rate being derived from coolant temperature, intake air quantity and engine speed. Further, conventionally internal combustion engines are known, in which operating characteristics of intake valves and exhaust valves, i.e. valve timing (valve opening/closing timing and/or valve lift) are changeable (e.g. Japanese Provisional Patent Publication (Kokai) No. 2-50285). It is a feature of the invention to provide a control system for an internal combustion engine, which is capable of accurately controlling the air-fuel ratio of a mixture supplied to combustion chambers of the engine, by taking into consideration the amount of fuel adhering to the inner surface of the intake pipe as well as the valve timing of intake valves and/or the exhaust valves thereof. The present invention provides a control system for an internal combustion engine having at least one combustion chamber, an intake passage having an inner surface, at least one intake valve and at least one exhaust valve, the control system including supply fuel amount calculating means for calculating an amount of fuel to be supplied to the engine, based upon operating conditions of the engine, adherent fuel amount estimating means for estimating an amount of adherent fuel adhering to the inner surface of the intake passage, carried-off fuel amount estimating means for estimating an amount of carried-off fuel evaporated from fuel adhering to the inner surface of the intake passage and carried into the combustion chamber, supply fuel amount correcting means for correcting the supply fuel amount calculated by the supply fuel amount calculating means, based upon the adherent fuel amount estimated by the adherent fuel amount estimating means and the carried-off fuel amount estimated by the carried-off fuel amount estimating means, and fuel supply means for supplying the supply fuel amount corrected by the fuel amount correcting means into the intake passage, the system being characterised in that it further comprises: valve operating means for changing a valve operating characteristic of at least one of the intake valve and the exhaust valve, and estimated fuel amount correcting means for correcting the adherent fuel amount estimated by the adherent fuel amount estimating means and the carried-off fuel amount estimated by the carried-off fuel amount estimating means, in response to the valve operating characteristic of at least one of the intake valve and the exhaust valve. Preferably, the valve operating characteristic includes a low speed valve timing suitable for operation of the engine in a lower rotational speed region of the engine, and a high speed valve timing suitable for operation of the engine in a higher rotational speed region of the engine, the adherent fuel amount and the carried-off fuel amount being each corrected to different values between when the low speed valve timing is selected and when the high speed valve timing is selected. The above and other objects, features, and advantages of the invention will be more apparent from the following detailed description of various embodiments, given by way of example only, taken in conjunction with the accompanying drawings, in which: Fig. 1 is a block diagram showing the whole arrangement of a fuel supply control system for an internal combustion engine, according to a first embodiment of the invention; Fig. 2 is a flowchart of a program for calculating the fuel injection period Tout, according to the first embodiment; Fig. 3 is a flowchart of a program for calculating an intake pipe-adherent fuel amount TWP(N); Figs. 4(a) and (b) show tables for calculating correction coefficients for correcting the direct supply ratio A and the carry-off ratio B, according to the first embodiment; Fig. 5 is a block diagram showing the whole arrangement of a fuel supply control system for an internal combustion engine, according to a second embodiment of the invention; Fig. 6 is a cross-sectional view of an oil hydraulic valve driving unit provided in an engine in Fig. 5; Fig. 7 is a graph useful in explaining operating characteristics (valve timing) of an intake valve in the engine in Fig. 5; Fig. 8 is a flowchart of a program for calculating the fuel injection period Tout, according to the second embodiment; Figs. 9(a) and (b) show tables for use in calculating the direct supply ratio A and the carry-off ratio B; Fig. 10 shows tables for calculating correction coefficients dependent upon the direct supply ratio A and the carry-off ratio B; A first embodiment of the invention will be described in detail with reference to Figs. 1 through 4. Referring first to Fig. 1, there is illustrated the whole arrangement of a fuel supply control system of an internal combustion engine. According to a first embodiment of the invention, the intake pipe adherent fuel amount and the carried-off fuel amount are corrected in response to the valve timing of intake and exhaust valves. In the figure, reference numeral 1 designates an internal combustion engine for automotive vehicles. The engine is a DOHC four-cylinder straight-type, for instance, having a pair of intake valves and a pair of exhaust valves provided for each cylinder, none of which is shown. Connected to the cylinder block of the engine 1 is an intake pipe 2 across which is arranged a throttle body 3 accommodating a throttle valve 301 therein. A throttle valve opening ( TH ) sensor 4 is connected to the throttle valve 301 for generating an electric signal indicative of the sensed throttle valve opening and supplying same to an electronic control unit (hereinafter called "the ECU") 5. Fuel injection valves 6, only one of which is shown, are inserted into the interior of the intake pipe 2 at locations intermediate between the cylinder block of the engine 1 and the throttle valve 301 and slightly upstream of respective intake valves, not shown. The fuel injection valves 6 are connected to a fuel tank via a fuel pump (not shown), and electrically connected to the ECU 5 to have their valve opening periods controlled by signals therefrom. On the other hand, an intake pipe absolute pressure (PBA) sensor 10 is provided in communication with the interior of the intake pipe 2 via a conduit 9 at a location immediately downstream of the throttle valve 301 for supplying an electric signal indicative of the sensed absolute pressure within the intake pipe 2 to the ECU 5. An engine coolant temperature (TW) sensor 11 is mounted in the cylinder block of the engine 1, for supplying an electric signal indicative of the sensed engine coolant temperature TW to the ECU 5. An engine rotational speed (NE) sensor 12 is arranged in facing relation to a camshaft or a crankshaft of the engine 1, not shown. The engine rotational speed sensor 12 generates a pulse as a TDC signal pulse at each of predetermined crank angles whenever the crankshaft rotates through 180 degrees, the pulse being supplied to the ECU 5. An O 2 sensor 13 as an exhaust gas ingredient concentration sensor is mounted in an exhaust pipe 14 connected to the cylinder block of the engine 1, for sensing the concentration of oxygen present in exhaust gases emitted from the engine 1 and supplying an electric signal indicative of the detected value of the oxygen concentration to the ECU 5. The ECU 5 comprises an input circuit having the functions of shaping the waveforms of input signals from various sensors, shifting the voltage levels of sensor output signals to a predetermined level, converting analog signals from analog-output sensors to digital signals, and so forth, a central processing unit (hereinafter called "the CPU") which executes programs for controlling the fuel injection valves 6, etc., memory means storing maps and tables, referred to hereinafter, and various operational programs which are executed in the CPU and for storing results of calculations therefrom, etc., and an output circuit which outputs control or driving signals to the fuel injection valves 6. The CPU operates in response to the above-mentioned signals from the sensors to determine operating conditions in which the engine 1 is operating, such as an air-fuel ratio feedback control region in which the fuel supply is controlled in response to the detected oxygen concentration in the exhaust gases, and open-loop control regions, and calculates, based upon the determined operating conditions, the valve opening period of fuel injection period Tout over which the fuel injection valves 6 are to be opened, by the use of the program of Fig. 2 in synchronism with inputting of TDC signal pulses to the ECU 5. The CPU supplies via the output circuit the driving signals based upon the fuel injection period Tout determined as above to the fuel injection valves 6 to open same over the fuel injection period Tout. The fuel injection period Tout is proportional to the fuel injection amount, and therefore will be hereinafter referred to as the fuel injection amount. The engine 1 is provided with a valve timing changeover mechanism 100, which is capable of changing the valve timing of the intake valves and the exhaust valves between a high-speed valve timing (high speed V/T) suitable for engine operation in a higher engine rotational speed region and a low-speed valve timing (low speed V/T) suitable for engine operation in a lower engine rotational speed region. The term "valve timing" used in this specification includes the valve opening timing and/or valve closing timing, as well as the valve lift. An intake air temperature (TA) sensor 18 is mounted in the inner wall of the intake pipe 2 at a location downstream of the conduit 9 connected to the PBA sensor 10 for supplying an electric signal indicative of the sensed intake air temperature to the ECU 5. A cylinder-discriminating (CYL) sensor 15 and a crank angle (CRK) sensor 16 are arranged in facing relation to a camshaft or a crankshaft, neither of which is shown, of the engine 1 at respective predetermined locations thereof. The CYL sensor 15 generates a pulse signal (hereinafter referred to as "CYL signal pulse") at predetermined crank angles of a particular cylinder whenever the crankshaft rotates two rotations or through 720 degrees and supplies the CYL signal pulse to the ECU 5. The CRK sensor 16 generates a pulse signal (hereinafter referred to as "CRK signal pulse") whenever the crankshaft rotates through a predetermined crank angle (e.g. 45°) and supplies the CRK signal pulse to the ECU 5. The output signal pulses from the CYL sensor 15 and CRK sensor 16 are used together with the output signal from the NE sensor 12, for control of the timing of execution of fuel injection timing control, ignition timing control, etc., as well as detection of the engine rotational speed NE. The valve timing changeover mechanism 100 has a solenoid valve, not shown, for changing the valve timing and is electrically connected to the ECU 5 to have its opening and closing operation controlled by a signal from the ECU 5. The solenoid valve changes operating oil pressure for the valve timing changeover mechanism 100 from a high level to a low level or vice versa, so that the valve timing is changed over from high speed V/T to low speed V/T or vice versa. The oil pressure in the changeover mechanism 100 is detected by an oil pressure (Poil) sensor 17, and the sensed signal is supplied to the ECU 5. The output circuit of the ECU 5 is adapted to supply driving signals to the fuel injection valves 6 and the solenoid valve of the valve timing changeover mechanism 100. Fig. 2 shows a program for calculating the valve opening period of the fuel injection valves 6, i.e. the fuel injection amount Tout. This program is executed upon generation of each TDC signal pulse and in synchronism therewith. At a step S41, it is determined whether or not the high speed V/T is selected. If the answer is negative (NO), i.e. if the low speed V/T is selected, a direct supply ratio A and a carry-off ratio B for the low speed V/T are calculated at a step S42. Values of the direct supply ratio A and the carry-off ratio B are read from an A map and a B map for the low speed V/T, which are set in accordance with the coolant temperature TW and the intake pipe absolute pressure PBA, in response to detected TW and PBA values. The direct supply ratio A and the carry-off ratio B for the low speed may be calculated by interpolation, if required. At the next step S43, correction coefficients KA and KB for correcting the direct supply ratio A and the carry-off ratio B for the low speed V/T are calculated. Values of the correction coefficient KA and KB are read from a KA table and a KB table for the low speed V/T, shown in Fig. 4 (a), in response to the engine rotational speed NE. In the KA and KB tables, the correction coefficient KA for the direct supply ratio A and the correction coefficient KB for the carry-off ratio B are set such that they increase as the engine rotational speed NE increases. The reason why the correction coefficients KA and KB are thus increased as the engine rotational speed NE increases is that the direct supply ratio A and the carry-off ratio B apparently increase as the air flow speed in the intake pipe increases with an increase in the engine rotational speed NE. If the answer at the step S41 is affirmative (YES), similarly to the steps S42 and S43, a direct supply ratio A, and a carry-off ratio B and correction coefficients KA, KB for the high speed V/T are calculated at steps S44 and S45, followed by the program proceeding to a step S46. At the step S44, values of the direct supply ratio A and the carry-off ratio B for the high speed V/T are read from an A map and a B map for the high speed V/T, and at the step S45, the correction coefficients KA, KB for the high speed V/T are calculated by the use of a KA table and a KB table for the high speed V/T, shown in Fig.4(b). As mentioned above, according to the present embodiment, two kinds of A maps and B maps as well as two kinds of correction coefficients KA and KB are provided, respectively, for the high speed V/T and low speed V/T. The reason for this is that the air flow speed in the vicinity of the intake valve and variation of pressure within the intake pipe 2 resulting from the variation, which are factors of fuel transportation parameters, differ depending upon the valve opening and/or closing timing and valve lift of the intake valve. Accordingly, the direct supply ratio A and the carry-off ratio B both vary depending on the valve timing of the intake valve. Therefore, the A map, B map, KA table and KB table have been set with the above-mentioned fact taken into account. At a step S46 following the step S43 or S45, a corrected direct supply ratio Ae and a corrected carry-off ratio Be are calculated by the use of the following equations (1) and (2) followed by calculating (1 - Ae) and (1 - Be) at a step S47, and then the program proceeds to a step S48: Ae = A x KA Be = B x KB The values Ae, (1 - Ae) and (1 - Be) are stored into the RAM within the ECU 5 for use in executing the program in Fig. 3 to calculate the intake pipe-adherent fuel amount TWP(N) described hereinafter, followed by the program proceeding to step S48. At step S48, it is determined whether or not the engine is being started. If the answer is affirmative (YES), the fuel injection amount Tout is calculated based upon a basic fuel amount Ti for use at the start of the engine, and then the program is terminated. If the answer to the question of the step S48 is negative (NO), i.e. if the engine is not being started, a required fuel amount TCYL(N) for each cylinder, which does not include an additive correction term Ttotal, referred to hereinafter, is calculated by the use of the following equation (3), at a step S49: Tcyl(N) = TiM x Ktotal(N) where (N) represents a number allotted to the cylinder for which the required fuel amount Tcyl is calculated. TiM represents a basic fuel amount to be applied when the engine is under normal operating conditions (other than the starting condition) and is calculated in response to the rotational speed NE and the intake pipe absolute pressure PBA. Ktotal(N) represents the product of all correction coefficients (e.g. a coolant temperature-dependent correction coefficient KTW and a leaning correction coefficient KLS) which are calculated based upon engine operating parameter signals from various sensors excluding an air-fuel ratio correction coefficient K02 which is calculated based on an output signal from the 0 2 sensor 13. At a step S50, a combustion chamber supply fuel amount TNET, which should be supplied to the corresponding combustion chamber in the present injection cycle, is calculated by the use of the following equation (4): TNET = Tcyl(N) + Ttotal - Be x TWP(N) where Ttotal is the sum of all additive correction terms (e.g. an acceleration fuel-increasing correction term TACC), which is calculated based on engine operating parameter signals from various sensors. The value Ttotal does not include an ineffective time correction term TV, referred to later. TWP(N) represents an intake pipe-adherent fuel amount (estimated value), which is calculated by the program of Fig. 3. (Be x TWP(N)) corresponds to an amount of fuel, which is evaporated from fuel adhering to the inner surface of the intake pipe 2 and carried into the combustion chamber. A fuel amount corresponding to the fuel amount carried off the intake pipe inner surface need not be injected, and, therefore, is to be subtracted from the value Tcyl(N) in the equation (4). At a step S51, it is determined whether or not the value TNET calculated by the equation (4) is larger than a value of 0. If the answer is negative (NO), i.e. if TNET ≤ 0, the fuel injection amount Tout is set to 0, followed by terminating the program. If the answer at the step 51 is affirmative (YES), i.e. if TNET > 0, the TOUT value is calculated by the use of the following equation (5): Tout = TNET(N)/Ae xK02 + TV where K02 is the aforementioned air fuel ratio correction coefficient calculated in response to the output from the 0 2 sensor 13. TV is the ineffective time correction term. Thus, a fuel amount corresponding to TNET(N) X K02 + Be x TWP(N) is supplied to the combustion chamber by opening the fuel injection valve 6 over the time period Tout calculated by the equation (5). Fig. 3 shows the program for calculating the intake-pipe adherent fuel amount TWP(N), which is executed upon generation of each crank angle pulse which is generated whenever the crankshaft rotates through a predetermined angle (e.g. 30 degrees). At a step S21, it is determined whether or not the present loop of execution of this program falls within a time period after the start of the calculation of the fuel injection amount Tout and before the fuel injection is completed (hereinafter referred to as the injection control period). If the answer is affirmative (YES), a first flag FCTWP(N) is set to a value of 0 at a step S32, followed by terminating the program. If the answer at the step S21 is negative (NO); i.e. if the present loop is not within the injection control period, it is determined at a step S22 whether or not the first flag FCTWP(N) is equal to 1. If the answer is affirmative (YES), that is, if FCTWP(N) = 1, the program jumps to a step S31, whereas if the answer is negative (NO), i.e. if FCTWP(N) = 0, it is determined at a step S23 whether or not the engine is under fuel cut (the fuel supply is interrupted). If the engine is not under fuel cut, the intake pipe-adherent fuel amount TWP(N) is calculated at step S24 by the use of the following equation (3), then a second flag FTWPR(N) is set to a value of 0, and the first flag FCTWP(N) is set to a value of 1 at steps S30 and S31, followed by terminating the program: TWP(N) = (1 - Be) x TWP(N) (n - 1) + (1 - Ae) x (Tout(N) - TV) where TWP(N)(n - 1) represents a value of TWP(N) obtained on the last occasion, and Tout(N) an updated or new value of the fuel injection amount Tout which has been calculated by the program of Fig 2. The first term on the right side corresponds to a fuel amount remaining on the inner surface of the intake pipe 2 without being carried into the combustion chamber, out of the fuel previously adhering to the inner surface of the intake pipe 2, and the second term on the right side corresponds to a fuel amount newly adhering to the inner surface of the intake pipe 2 out of newly injected fuel. If the answer at the step S23 is affirmative (YES), i.e. if the engine is under fuel cut, it is determined at a step S25 whether or not the second flag FTWPR(N) has been set to a value of 1. If the answer is affirmative (YES), i.e. if FTWPR(N) = the program jumps to the step S31. If the answer is negative (NO), i.e. if FTWPR(N) = 0, the adherent fuel amount TWP(N) is calculated by the use of the following equation (7) at a step S26, and then the program proceeds to a step S27: TWP(N) = (1 - Be) x TWP(N)(n -1) The equation (7) is identical with the equation (6) except that the second term on the right side is omitted. The reason for the omission is that there is no fuel newly adhering to the intake pipe inner surface, due to fuel cut. At the step 27, it is determined whether or not the calculated TWP(N) value is larger than a very small predetermined value TWPLG. If the answer is affirmative (YES), i.e. if TWP(N) > TWPLG, the program proceeds to the next step S30. If the answer at the step S27 is negative (NO), i.e. if TWP(N) ≤ TWPLG, the TWP(N) value is set to a value of 0 at a step S28, and then the second flag FTWPR(N) is set to a value of 1 at a step S29, followed by the program proceeding to the step S31. According to the program of Fig. 3 described above, the intake pipe-adherent fuel amount TWP(N) can be accurately calculated. Moreover, an appropriate fuel amount can be supplied to the combustion chamber of each cylinder, which reflects the fuel amount adhering to the inner surface of the intake pipe 2 as well as the fuel amount carried off the adherent amount. According to the first embodiment described above, the direct supply ratio A and the carry-off ratio B are calculated and corrected in response to valve timing selected, whereby it is possible to accurately estimate the intake pipe-adherent fuel amount, irrespective of valve timing selected and hence control the air-fuel ratio of a mixture supplied to the combustion chamber to a desired value. Fig. 5 shows the whole arrangement of a fuel supply control system for an internal combustion engine, according to a second embodiment of the invention. As shown in the figure, according to this embodiment, the engine 1 is provided with an oil hydraulic driving valve unit 200 for each cylinder, in place of the valve timing changeover mechanism 100 employed in the arrangement of Fig. 1. The ECU 5 is connected to a solenoid of the oil hydraulic driving valve unit 200, and supplies control signals (OFF and ON) thereto. A motor 3a is coupled to the throttle valve 301 for driving it in response to a control signal from the ECU 5 so as to control its valve opening. The throttle valve 301 is held at almost the maximum opening when the engine 1 is operating in normal operating conditions. With the throttle valve 301 thus held at almost the maximum opening, the valve opening period of the intake valve is changed by the oil hydraulic driving unit 200 to control an intake air amount supplied to the cylinder of the engine 1. Connected to the ECU 5 is an oil pressure sensor 17' which detects the pressure (Poil) of operating oil in the hydraulic driving valve unit 200, in place of the oil pressure sensor 17 in the first embodiment. Further connected to the ECU 5 are an oil temperature sensor 19 which senses the oil temperature Toil of the operating oil, a lift sensor 18 which senses the lift of the intake valve, and an accelerator pedal opening sensor 4' which senses a stepping amount (ACC) of an accelerator pedal, not shown, of a vehicle on which the engine is installed. Output signals from these sensors are supplied to the ECU 5. Elements and parts other than those mentioned above are identical in construction and arrangement with those employed in the first embodiment of Fig. 1 and designated by identical reference numerals, and description thereof is omitted. Fig. 6 shows the internal construction of the oil hydraulic driving valve unit 200 which is provided in each cylinder head 21 of the engine 1. The cylinder head 21 is formed therein with an intake valve port 23, one end of which opens into an upper space within a combustion chamber, not shown, of the engine 1 and the other end is in communication with an intake port 24. An intake valve 22 is slidably mounted in the cylinder head 21 arranged for vertical reciprocating motion as viewed in the figure to close and open the intake valve port 23. A valve spring 26 is tautly mounted between a collar 25 of the intake valve 22 and a spring seat 21a in the cylinder head 21 and urges the intake valve 22 upward as viewed in the figure or in a valve closing direction. On the other hand, a camshaft 28 having a cam 27 formed integrally thereon is rotatably mounted in the cylinder head 21 at a left side of the intake valve 22. The camshaft 28 is coupled to a crankshaft, not shown, via a timing belt, not shown. The oil hydraulic driving unit 200 is interposed between the intake valve 22 and the cam 27 formed on the camshaft 28. The oil hydraulic driving valve unit 200 is comprised of an oil hydraulic driving mechanism 30 disposed to downwardly urge the intake valve 22 against the force of the valve spring 26 to close or open same in response to the profile of the cam 27, and an oil pressure release mechanism 31 disposed to cancel the urging force of the oil hydraulic driving mechanism 30 while the intake valve 22 is being opened to thereby close the intake valve 22 irrespective of the cam profile. The oil hydraulic driving mechanism 30 is mainly comprised of a first cylinder body 33 secured to a block 32 mounted on or formed integrally with the cylinder head 21, a valve-side piston (valve driving piston) 34 slidably fitted in a cylinder bore 33a in the first cylinder body 33, with a lower end thereof resting against an upper end of the intake valve 22, an operating oil pressure chamber 38 defined by the first cylinder body 33 and the valve-side piston 34, a second cylinder body 36 secured to the block 32, a lifter 35 disposed in sliding contact with the cam 27, a cam-side piston 37 slidably fitted in a lower portion of the second cylinder body 36, with a lower end thereof resting against a bottom surface of the lifter 35, an oil hydraulic pressure creating chamber 39 defined by the second cylinder body 36 and the cam-side piston 37, and an oil passage 40 extending between the oil hydraulic pressure creating chamber 39 and the operating oil pressure chamber 38. The oil hydraulic driving mechanism 30 thus constructed operates according to the profile of the cam 27 to selectively open or close the intake valve 22 when the oil pressure in the operating oil pressure chamber 38 is above a predetermined value. The lift sensor 18 is arranged in the block 32 at a location opposite the collar 25 of the intake valve 22 to sense its lift. The lift sensor 18 is electrically connected to the ECU 5 to supply same with a signal indicative of the sensed lift. On the other hand, the oil pressure release mechanism 31 is mainly comprised of an oil passage 41 connecting between the oil passage 40 and an oil supply gallery 42, a spill valve 45 disposed to allow oil pressure to escape from the oil passage 41, a feed valve 43 and a check valve 44 both arranged in the oil passage 41, and an accumulator 46 disposed to maintain oil pressure within an accumulator circuit 41a formed by the valves 43, 44 and the spill valve 45 at a predetermined value. The oil supply gallery 42 is connected to an oil pump 47 to supply oil pressure created by the oil pump 47 to the oil hydraulic driving valve units 200 of the engine cylinders. The oil pump 47 pressurizes operating oil in an auxiliary oil pan 48 provided in the cylinder head 21 and supplies the pressurized oil to the oil supply gallery 42. It may be so arranged that the oil supply gallery 42 is supplied with operating oil from an oil pan provided at a bottom portion of a crankcase, not shown. The spill valve 45 is comprised of a control valve section 45A, and a solenoid driving section 45B for driving the control valve section 45A. In the spill valve 45, when a solenoid 202 of the solenoid driving section 45B is deenergized, the spill valve 45 is open, whereas when the solenoid 202 is energized, the spill valve 45 is closed. The solenoid is electrically connected to the ECU 5 to be energized or deenergized by a control signal from the ECU 5. The accumulator 46 is arranged in the accumulator circuit 41a to maintain oil pressure within the accumulator circuit 41a at a predetermined value. The accumulator 46 is comprised of a cylinder bore 461 formed in the block 32, a cap 463 having an air hole 462 formed therein, a piston 464 slidably fitted in the cylinder bore 461, and a spring 465 tautly interposed between the cap 463 and the piston 464. The operation of the oil hydraulic driving mechanism 30 and the oil pressure release mechanism 31 constructed as above will now be described. When the solenoid 202 of the spill valve 45 is energized by the control signal from the ECU 5, the spill valve 45 is closed so that the oil pressure within the oil pressure creating chamber 39, the oil passage 40 and the operating oil pressure chamber 38 of the oil hydraulic driving mechanism 30 is maintained at a high level (at a predetermined pressure value or more), whereby the intake valve 22 is alternately opened and closed in response to the profile of the cam 27. The valve operating characteristic (the relationship between the crank angle and the valve lift) in this case is shown, by way of example, by the solid line in Fig. 7. On the other hand, when the solenoid 202 of the spill valve 45 is deenergized by the control signal from the ECU 5 while the intake valve is open, the spill valve 45 becomes open. As a result, the oil pressure within the operating oil pressure creating chamber 39, the oil passage 40 and the oil pressure chamber 38 decreases, whereby the intake valve 22 starts its closing motion, irrespective of the profile of the cam 27. Then, the valve operating characteristic is such as shown by the broken line in Fig 7. That is, in the figure, when the solenoid 202 is deenergized at a crank angle OFF, the intake valve 22 begins to make a closing motion at a crank angle ST after a slight time delay from the crank angle OFF and becomes completely closed at a crank angle IC (hereinafter referred to as "the intake valve closing timing"). In this way, the intake valve 22 is controlled by the control signal from the ECU 5 such that it begins to make a closing motion when it is on the opening stroke, by rendering the oil hydraulic driving mechanism 30 inoperative. Therefore, the timing of valve closing start can be set to any desired timing, whereby it is possible to control the intake air amount supplied to the engine cylinders by the control signal from the ECU 5. A similar oil hydraulic driving unit, not shown, is provided on the side of exhaust valves in this or second embodiment. Alternatively, there may be provided an ordinary type valve operating mechanism in which the exhaust valve is closed at a constant timing according to a cam profile, or a variable valve timing mechanism in which the valve opening/closing timing can be set to a plurality of different timings, similarly to the valve timing changeover mechanism employed in this embodiment. In the following description, the valve closing timing on the exhaust valve side will be referred to as "exhaust valve closing timing EC", as corresponding to the intake valve timing IC on the intake valve side. Fig. 8 shows a program for calculating the fuel injection amount Tout according to the second embodiment, which program corresponds to the one shown in Fig. 2. At a step S61, valve timing parameters, i.e. intake valve closing timing IC and exhaust valve closing timing EC are read. At a step S62, the direct supply ratio A and the carry-off ratio B are calculated by the use of an A table and a B table shown in Fig. 9(a) in response to the detected engine rotational speed Ne. Then, coolant temperature correction coefficients KATW and KBTW are calculated-in response to the detected engine coolant temperature by the use of a KATW table and a KBTW table set in accordance with the engine coolant temperature TW as shown in Fig. 9(b). The values of the A and B tables shown in Fig. 9(a) are set to values to be obtained when the engine output assumes 50% of its maximum value at each value of the engine rotational speed. At the step S62, reference values Abase and Bbase of the direct supply ratio and the carry-off ratio are also calculated by the use of the following equations 8 and 9: Abase = A x KATW Bbase = B x KBTW At a step S63, intake side correction coefficients KAIC and KBIC for the direct supply ratio and the carry-off ratio are calculated by the use of a KAIC table and a KBIC table set in accordance with the closing timing IC of the intake valve, as shown in Fig. 10(a), then, exhaust-side correction coefficients KAEC and KBEC are calculated by the use of a KAEC table and a KBEC table set in accordance with the closing timing EC of the exhaust valve, as shown in Fig. 10(b), followed by calculating reference value correction coefficients KA and KB by the use of the following equations (10) and (11). In this embodiment, as the IC value or EC value increases in Fig. 10 (the IC value moves leftward in Fig. 10 for instance), the valve opening period of the intake valve or the exhaust valve decreases: KA = KAIC x KAEC KB = KBIC x KBEC At the next step S64, a corrected direct supply ratio Ae and a corrected carry-off ratio Be are calculated by the use of the following equations (12) and (13), and then the programs proceeds to a step S47: Ae = Abase x KA Be = Bbase x KB The steps S47 - S54 in Fig. 8 are identical with the steps S47 - S54 in Fig. 2, description of which is therefore omitted. The intake pipe-adherent fuel amount TWP(N) is calculated by the aforedescribed program in Fig. 3, also in this embodiment. According to the present embodiment, the direct supply ratio A and the carry-off ratio B are corrected in response to the closing timing of the intake and exhaust valves. Therefore, it is possible to accurately estimate the intake pipe-adherent fuel amount and the carried-off fuel amount, irrespective of the closing timing of the intake and exhaust valves and hence accurately control the air-fuel ratio of a mixture supplied to the combustion chambers. The method of calculating the direct supply ratio A and the carry-off ratio B employed in the first and second embodiments described above is applicable to a valve control system in which part of the intake valves and/or part of the exhaust valves are rendered inoperative when the engine is operating in a low load condition. In this way, according to the second embodiment described above, estimated values of the intake pipe-adherent fuel amount and the carried-off fuel amount are corrected in dependence on the valve operating characteristics of the intake valves and/or the exhaust valves, to thereby enable to accurately estimate the intake pipe-adherent fuel amount, irrespective of the valve operating characteristics and hence accurately control the air-fuel ratio of a mixture supplied to the combustion chambers.

Claims: A control system for an internal combustion engine (1) having at least one combustion chamber, an intake passage (2) having an inner surface, at least one intake valve, and at least one exhaust valve, said control system including supply fuel amount calculating means for calculating an amount of fuel to be supplied to said engine (1), based upon operating conditions of said engine, adherent fuel amount estimating means for estimating an amount of adherent fuel adhering to said inner surface of said intake passage (2), carried-off fuel amount estimating means for estimating an amount of carried-off fuel evaporated from fuel adhering to said inner surface of said intake passage (2) and carried into said combustion chamber (1), supply fuel amount correcting means for correcting said supply fuel amount calculated by said supply fuel amount calculating means, based upon said adherent fuel amount estimated by said adherent fuel amount estimating means and said carried-off fuel amount estimated by said carried-off fuel amount estimating means, and fuel supply means for supplying said supply fuel amount corrected by said fuel amount correcting means into said intake passage (2), characterised in that the control system further comprises: valve operating means for changing a valve operating characteristic of at least one of said intake valve and said exhaust valve, and estimated fuel amount correcting means for correcting said adherent fuel amount estimated by said adherent fuel amount estimating means and said carried-off fuel amount estimated by said carried-off fuel amount estimating means, in response to said valve operating characteristic of said at least one said intake valve and said exhaust valve. A control system as claimed in claim 1, wherein said valve operating characteristic includes a low speed valve timing suitable for operation of said engine (1) in a lower rotational speed region of said engine (1), and a high speed valve timing suitable for operation of said engine (1) in a higher rotational speed region of said engine (1), said adherent fuel amount and said carried-off fuel amount being each corrected to different values between when said low speed valve timing is selected and when said high speed valve timing is selected.

Inventors: HARA YOSHIHISA, MIYASHITA KOTARO, OGAWA KEN, HARA, YOSHIHISA, MIYASHITA, KOTARO, OGAWA, KEN, Hara, Yoshihisa, c/o Honda R &amp; D, Co., Ltd., Miyashita, Kotaro, c/o Honda R &amp; D, Co., Ltd., Ogawa, Ken, c/o Honda R &amp; D, Co., Ltd.
Applicants: HONDA MOTOR CO LTD, HONDA GIKEN KOGYO KABUSHIKI KAISHA
Application year: 1992
Main classification: F02D35
IPC codes: F02M25, F02D43, F02D13, F01L9, F02D41