JP4840240B2 - Internal combustion engine control system - Google Patents

Description

  The present invention relates to a system for controlling a spark ignition type internal combustion engine.

  When stopping the fuel supply to the combustion chamber of the internal combustion engine, such as when the accelerator of the internal combustion engine is turned off, the ignition timing is retarded in advance before stopping the fuel supply, so that the torque shock due to the stop of the fuel supply is reduced. Suppressing control may be performed.

  When such control is performed with the stop of the fuel supply, the peak value of the temperature rise in the combustion chamber decreases, and the amount of fuel remaining in the combustion chamber increases when the fuel supply stops was there. In this case, the fuel remaining in the combustion chamber may be discharged as HC as an unburned component while the fuel supply is stopped. In addition, when the internal combustion engine is returned from the fuel supply stop state, the air-fuel ratio may shift to the rich side and the HC emission amount may increase. As a result, the emission may deteriorate when or after the fuel supply to the combustion chamber of the internal combustion engine is stopped.

  In contrast, when the fuel supply is resumed from the state where the fuel supply to the combustion chamber of the internal combustion engine is stopped, the ignition timing is retarded and the intake air amount is increased to oxidize the HC catalytic converter. A technique that promotes and suppresses an increase in the amount of HC emission has been proposed (see, for example, Patent Document 1). However, in this prior art, although the HC purification efficiency in the catalytic converter is increased, the HC itself discharged from the internal combustion engine is not decreased.

On the other hand, in the conventional spark ignition type internal combustion engine, the ignition timing is advanced to the front of MBT (Minimum spark advance for Best Torque), thereby promoting the temperature rise of the cooling water, thereby increasing the warm-up property of the internal combustion engine. There is known a technique for improving the above (see, for example, Patent Document 2). However, in this prior art, the warm-up property of the internal combustion engine is considered, but the exhaust emission is not considered.
JP-A-11-101150 JP 2000-240547 A JP 11-93719 A Japanese Patent Laid-Open No. 9-32609

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a technique capable of suppressing deterioration of emissions when fuel supply to a combustion chamber of an internal combustion engine is stopped.

  In order to solve the above-described problem, the present invention provides a control system for an internal combustion engine in which the ignition timing is advanced before MBT, which is the ignition timing at which the torque can be substantially maximized. In addition, the greatest feature is that the ignition timing is advanced before MBT to increase the peak value of the temperature rise in the combustion chamber.

More specifically, an over-advance means for advancing the ignition timing of the spark ignition type internal combustion engine before MBT,
Fuel supply stop means for stopping fuel supply to the combustion chamber in the internal combustion engine;
When stopping the fuel supply to the combustion chamber in the internal combustion engine by the fuel supply stop means, the fuel advance over-advance control means for advancing the ignition timing ahead of MBT by the over-advance angle means;
It is characterized by providing.

  Here, the fuel supply to the combustion chamber of the internal combustion engine may be stopped in an operation state in which the torque is not required so much as when the accelerator is turned off. In such a case, since combustion does not occur in the combustion chamber, the fuel that has adhered to the wall surface in the cylinder or the fuel that has not adhered to the wall surface (hereinafter, these may be collectively referred to as “in-cylinder adhered fuel”). ) May be discharged unburned without being subjected to combustion.

  At that time, if the catalyst disposed in the exhaust system of the internal combustion engine is in an inactive state, the unburned fuel component described above may be released into the atmosphere without being purified by the catalyst. Alternatively, when the fuel supply stop state is released and the fuel supply to the combustion chamber of the internal combustion engine is resumed, the fuel has already adhered to the wall surface in the cylinder, so the air-fuel ratio shifts to the rich side and the combustion In some cases, the amount of HC emissions after resumption increased. Then, in any case, there is a case in which the emission is deteriorated with the stop control of the fuel supply to the combustion chamber of the internal combustion engine.

  In contrast, as a result of the inventor's earnest experiment and verification, when the ignition timing is advanced to the front of MBT (hereinafter referred to as “over-advanced angle”) in a spark ignition type internal combustion engine, the cylinder It has been found that unburned fuel components (eg HC) discharged from within are significantly reduced.

  This is because, when the ignition timing is over-advanced, the amount of the air-fuel mixture that burns before compression top dead center increases. In addition to the temperature effect, the pressure in the cylinder (hereinafter also referred to as “in-cylinder pressure”) and the peak value of the in-cylinder temperature are increased, and it is considered that vaporization and oxidation of the fuel adhered to the cylinder are promoted. Here, the amount of unburned fuel can be reduced by oxidizing the in-cylinder attached fuel. Further, since the in-cylinder attached fuel is vaporized, it can be more easily oxidized and can be easily purified in the exhaust purification catalyst.

  Therefore, in the control system for an internal combustion engine according to the present invention, when the fuel supply to the combustion chamber of the internal combustion engine is stopped, the unburned fuel component discharged from the cylinder is reduced by over-advancing the ignition timing. We decided to plan. According to this, it is possible to suppress the deterioration of the emission when the fuel supply to the combustion chamber of the internal combustion engine is stopped.

  In the present invention, the fuel advance over-advance control means controls the ignition timing by the over-advance means before the fuel supply stop means stops the fuel supply to the combustion chamber in the internal combustion engine. You may make it advance ahead of MBT.

  By doing so, the in-cylinder attached fuel can be oxidized or vaporized in advance by raising the peak value of the temperature rise of the combustion chamber before the fuel supply to the combustion chamber of the internal combustion engine is stopped. When the fuel supply to the combustion chamber of the internal combustion engine is stopped, the HC emission can be suppressed more reliably and the emission can be more reliably reduced.

  Further, in the present invention, when the fuel supply stop means temporarily stops the fuel supply to the combustion chamber in the internal combustion engine during operation of the internal combustion engine, the fuel stop time control means includes the internal combustion engine. In the combustion stroke immediately before the fuel supply is stopped in the cylinder of the engine, the ignition timing may be advanced to the front of MBT by the excessive advance means.

  For example, when the fuel supply to the combustion chamber of the internal combustion engine is temporarily stopped during the operation of the internal combustion engine due to the accelerator off or the maximum speed limiter of the vehicle, immediately before the fuel supply is actually stopped in each cylinder. In the combustion stroke, the ignition timing is advanced before MBT. In this case, the in-cylinder attached fuel can be oxidized or vaporized in advance before the fuel supply is stopped in the cylinder.

  Further, when the internal combustion engine has a plurality of cylinders, the ignition timing may be advanced to the front of MBT in the combustion stroke immediately before the fuel supply is stopped for all the cylinders. Further, for each cylinder, the ignition timing may be advanced before MBT in one combustion stroke immediately before the fuel supply is stopped, or in a plurality of combustion strokes including the immediately preceding combustion stroke. The ignition timing may be advanced before MBT.

  In the present invention, when the fuel supply stopping means stops the fuel supply to the combustion chamber in the internal combustion engine during the stop operation of the internal combustion engine, the fuel stop over-advance angle control means includes: The fuel supply may be stopped after the ignition timing has been advanced ahead of MBT by the over-advance means for a predetermined period after the internal combustion engine stop command has been issued.

  Here, when the internal combustion engine is stopped, since the energization to the fuel system and the ignition system has been stopped at the same time as the IG switch is turned off, the internal combustion engine is stopped in the cylinder during the stop or the next start. The remaining in-cylinder attached fuel may be discharged as HC. In particular, when the internal combustion engine is stopped before the warm-up is completed, the amount of adhering fuel remaining in the cylinder is large, and therefore the amount of HC emission at the next start of the internal combustion engine may increase. there were.

  Therefore, in the present invention, during the stop operation of the internal combustion engine, the fuel advance over-advance angle control means sets the ignition timing before the MBT by the over-advance means for a predetermined period after the stop command for the internal combustion engine is issued. The control for advancing to the left is continued to sufficiently increase the peak value of the temperature rise in the combustion chamber of each cylinder. The internal combustion engine is stopped after the in-cylinder attached fuel is sufficiently oxidized or vaporized.

  According to this, the internal combustion engine can be stopped in a state where the in-cylinder attached fuel is reduced as much as possible, and the deterioration of the emission at the next start of the internal combustion engine or during the stop of the internal combustion engine can be suppressed. it can.

  The means for solving the problems in the present invention can be used in combination as much as possible.

  According to the present invention, it is possible to more reliably suppress the deterioration of the emission when the fuel supply to the combustion chamber of the internal combustion engine is stopped.

  Hereinafter, specific embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 is a diagram illustrating a schematic configuration of an internal combustion engine control system according to the present embodiment. An internal combustion engine 1 shown in FIG. 1 is a four-stroke cycle spark ignition type internal combustion engine (gasoline engine) having a plurality of cylinders 2. The cylinder 2 of the internal combustion engine 1 is connected to the intake passage 30 through the intake port 3 and is connected to the exhaust passage 40 through the exhaust port 4.

  The intake port 3 is provided with a fuel injection valve 5 that injects fuel into the cylinder 2. The intake passage 30 is provided with a throttle valve 6 that controls the amount of air flowing through the intake passage 30. An intake pressure sensor 7 that measures the pressure (intake pressure) in the intake passage 30 is provided in the intake passage 30 downstream of the throttle valve 6. An air flow meter 8 that measures the amount of air flowing through the intake passage 30 is provided in the intake passage 30 upstream of the throttle valve 6.

  On the other hand, an exhaust purification device 9 is disposed in the exhaust passage 40. The exhaust purification device 9 includes a three-way catalyst, an NOx storage reduction catalyst, and the like, and purifies exhaust when it is in a predetermined activation temperature range.

  Further, the internal combustion engine 1 is provided with an intake valve 10 that opens and closes an open end of the intake port 3 facing the cylinder 2 and an exhaust valve 11 that opens and closes an open end of the exhaust port 4 facing the cylinder 2. The intake valve 10 and the exhaust valve 11 are driven to open and close by an intake camshaft 12 and an exhaust camshaft 13, respectively.

  A spark plug 14 for igniting the air-fuel mixture in the cylinder 2 is disposed at the upper part of the cylinder 2. A piston 15 is slidably inserted into the cylinder 2. The piston 15 is connected to the crankshaft 17 via a connecting rod 16.

  A crank position sensor 18 that detects a rotation angle of the crankshaft 17 is disposed in the vicinity of the crankshaft 17. Furthermore, a water temperature sensor 19 for measuring the temperature of the cooling water circulating through the internal combustion engine 1 is attached to the internal combustion engine 1.

  The internal combustion engine 1 configured as described above is provided with an ECU 20. The ECU 20 is an electronic control unit that includes a CPU, a ROM, a RAM, and the like. The ECU 20 is electrically connected to various sensors such as the intake pressure sensor 7, the air flow meter 8, the crank position sensor 18, and the water temperature sensor 19 described above, and can input measurement values of the various sensors.

  The ECU 20 electrically controls the fuel injection valve 5, the throttle valve 6, and the spark plug 14 based on the measured values of the various sensors described above.

  Here, the fuel cut control of the internal combustion engine 1 will be described. This fuel cut control is performed when the internal combustion engine 1 is decelerated, specifically when the accelerator is turned off, or when the maximum speed limiter of the vehicle is activated, and the engine rotation without generating torque. In order to reduce the number, the output of the fuel injection command signal from the ECU 20 to the fuel injection valve 5 is stopped and the fuel supply to the cylinder 2 is stopped.

  When this fuel cut control is performed, the fuel does not burn in the cylinder 2. Therefore, the in-cylinder adhering fuel adhering to the wall surface in the cylinder 2 at the start of the fuel cut control becomes the unburned component HC. May have been discharged from. Further, when returning from the fuel cut control, the air-fuel ratio of the air-fuel mixture shifts to the rich side due to the in-cylinder attached fuel on the wall surface in the cylinder 2, and the amount of discharged HC may increase. As a result, the emission during the fuel cut control or immediately after the end of the control may deteriorate.

  Conventionally, when the fuel cut control is performed, the torque is drastically reduced. Therefore, the torque is reduced in advance by performing a control for retarding the ignition timing of the spark plug 14 immediately before the fuel cut control. Torque shock due to fuel cut control was avoided. In this case, the peak value of the temperature rise in the cylinder 2 may decrease due to the retard of the ignition timing of the spark plug 14, and the amount of fuel adhering to the cylinder at the time when fuel cut control is started may increase. It was.

  On the other hand, according to the earnest experiment and verification by the inventors of the present application, the peak value of the in-cylinder pressure and the in-cylinder temperature of the cylinder 2 can be particularly increased by advancing the ignition timing of the spark plug 14 from the MBT. It was found that it was possible.

  FIG. 2 is a graph showing how the relationship between various parameters in the cylinder 2 and the crank angle changes depending on the ignition timing in the cylinder 2. The horizontal axis represents the crank angle of the internal combustion engine 1, and the vertical axis represents each parameter in the cylinder 2. In FIG. 2, when the ignition of the spark plug 14 is performed at ST1 (to be described later) on the advance side (hereinafter referred to as “over-advance angle”) from the MBT, a solid line, and the ignition is performed at the MBT The graph when the ignition is performed at the compression top dead center (TDC) is shown by a one-dot chain line.

  When the ignition timing is over-advanced, the air-fuel mixture burned before the compression top dead center is compared to when the ignition timing is set to MBT and when the ignition timing is set to compression top dead center (TDC). The amount of increases. For this reason, the peak of heat energy generated by the combustion of the air-fuel mixture (see the heat generation rate, generated heat amount, and combustion mass ratio in FIG. 2) shifts to before the compression top dead center.

  Therefore, in-cylinder pressure during the period from the compression stroke to the expansion stroke is obtained by a synergistic effect of the temperature increase / pressure increase effect due to the combustion of the air-fuel mixture and the compression effect due to the piston ascending operation (operation from bottom dead center to top dead center) In addition, the peak value of the in-cylinder temperature increases significantly. Note that, since the excessive advance angle of the ignition timing before the MBT is executed according to a command from the ECU 20, the excessive advance means includes the ECU 20 in this embodiment.

  In the present embodiment, the above-described phenomenon is used to advance the ignition timing of the internal combustion engine 1 further than the MBT before performing the fuel cut control, thereby increasing the temperature peak in the cylinder 2 and increasing the cylinder 2 The fuel adhering to the cylinder on the inner wall surface was oxidized or vaporized. As a result, the in-cylinder attached fuel is discharged as HC during the fuel cut control or immediately after the control, and the emission is prevented from deteriorating.

  FIG. 3 shows a graph of the relationship between the ignition timing and torque in the cylinder 2 and the maximum in-cylinder temperature. The horizontal axis represents the ignition timing of the spark plug 14, and the vertical axis represents the torque and the maximum temperature in the cylinder. As can be seen from FIG. 3, the torque generated in the internal combustion engine 1 is greatest when the ignition timing is MBT. As the ignition timing is advanced to the front of MBT, the torque decreases while the in-cylinder maximum temperature increases and reaches the highest in ST1.

  In this way, by advancing the ignition timing before MBT, the torque can be reduced in advance before the fuel cut control, and the torque shock caused by the fuel cut control can be suppressed. Further, the in-cylinder maximum temperature can be raised, the in-cylinder attached fuel in the cylinder 2 can be oxidized or vaporized in advance before the fuel cut control, and unburned HC is discharged during or after the fuel cut control. Can be suppressed, and deterioration of emissions can be suppressed.

  In the present embodiment, the ignition timing when the ignition timing is over-advanced is particularly an ignition timing at which the in-cylinder pressure becomes maximum at TDC as shown in FIG. It is known that this ignition timing corresponds to ST1 that is the ignition timing at which the in-cylinder maximum temperature becomes the highest in FIG. 3, and by determining the ignition timing in this way, the fuel that adheres in-cylinder is most efficiently fueled. It can be oxidized or vaporized before cutting.

However, if the ignition timing is excessively advanced and the misfire limit ignition timing (STMF_A) determined by the operating state is exceeded, the risk of misfire increases as shown in FIG.
In an operating state in which is more advanced than STMF_A, the ignition timing is set so as not to exceed STMF_A. FIG. 5 shows the operating state of the internal combustion engine 1 and the STMF_
A map of the relationship with A is shown.

  Next, FIG. 6 shows the relationship between the timing of the fuel cut control of each cylinder 2 in the internal combustion engine 1 of the present embodiment and the timing to advance the ignition timing before MBT. In the stroke associated with each cylinder 2 in the figure, the ignition timing is advanced excessively in the combustion stroke surrounded by a thick line. Further, a fuel cut command is issued from the ECU 20 at the timing of the white arrow, and the fuel introduced from the intake port 3 to each cylinder 2 is actually cut at the timing of the black arrow.

  That is, since the internal combustion engine 1 in this embodiment is a port injection type internal combustion engine, the end of the intake stroke or the start of the compression stroke in the cycle before the cycle in which the fuel introduced into the cylinder 2 is actually cut. At this timing, the fuel injected from the fuel injection valve 5 to the intake port 3 is cut. In the combustion stroke immediately before the timing at which the fuel actually introduced into each cylinder 2 is cut, the ignition timing is over-advanced.

  Thus, in the combustion stroke immediately before the fuel cut is performed in each cylinder 2, the ignition timing of the spark plug 14 of each cylinder 2 is over-advanced to oxidize the in-cylinder attached fuel in all the cylinders 2 or Since it can vaporize, it can suppress more reliably that HC is discharged | emitted and an emission deteriorates.

  FIG. 7 shows an ignition timing over-advance control routine in the present embodiment. This routine is a program stored in the ROM of the ECU 20, and is executed by the ECU 20 for each cylinder 2 independently for each predetermined period while the internal combustion engine 1 is in operation.

  When this routine is executed, first, in S101, it is determined whether or not the fuel cut control is performed. Specifically, for example, for fuel cut control by accelerator OFF, fuel is controlled on the condition that the accelerator OFF is detected from the output signal of an accelerator position sensor (not shown) and the engine speed is equal to or less than a predetermined value from the crank position sensor 18. It may be determined that the cutting control has not been performed. Further, for example, the fuel cut control by the operation of the maximum speed limiter may be determined to be before the fuel cut control on condition that the vehicle speed exceeds 180 km. Here, when it is determined that the fuel cut control is not being performed, the present routine is temporarily ended as it is. On the other hand, if it is determined that it is before fuel cut control, the process proceeds to S102.

  In S102, a fuel cut command is issued from the ECU 20 to the fuel injection valve 5 of the cylinder 2. That is, the fuel injection from the fuel injection valve 5 is set to be stopped at the end of the intake stroke of the cylinder 2 or the start of the compression stroke. When the process of S102 ends, the process proceeds to S103.

  In S103, the ignition timing is advanced by the combustion stroke immediately after the fuel injection from the fuel injection valve 5 is stopped in the cylinder 2. As a result, the peak value of the temperature rise in the combustion chamber is increased, and the in-cylinder attached fuel in the cylinder 2 is reliably oxidized or vaporized. When the process of S103 ends, the process proceeds to S104.

  In S104, fuel is introduced into the cylinder 2 when the intake valve 10 is opened at the end of the exhaust stroke immediately after the combustion stroke in which the ignition timing is over-advanced in the cylinder 2 or at the start of the intake stroke immediately after. Since there is no fuel, the fuel is substantially cut. When the process of S104 is completed, this routine is temporarily ended.

It should be noted that the combustion stroke in which the advance angle is performed in S103 described above substantially corresponds to the combustion stroke immediately before the fuel introduced into the combustion chamber in the cylinder 2 is cut. in this way,
In this embodiment, the ignition timing is over-advanced in the combustion stroke immediately before the fuel is cut in each cylinder 2. As a result, torque shock associated with the fuel cut is suppressed, and the fuel adhering to the wall surface of each cylinder 2 at the start of the fuel cut is prevented from being discharged as HC during or after the fuel cut. it can. As a result, it is possible to suppress the deterioration of the emission during or after the fuel cut. The ECU 20 that executes the process of S102 of the ignition timing over-advance control routine corresponds to a fuel supply stop unit in this embodiment. Further, the ECU 20 that executes the process of S103 corresponds to the fuel advance over-advance angle control means in this embodiment.

  In each cylinder 2 in the timing chart of FIG. 6, the fuel cut command to the fuel injection valve 5 of each cylinder 2 is not necessarily limited to once. That is, the fuel cut control may be continued for a plurality of consecutive cycles in each cylinder 2. In this case, the ignition timing may be advanced excessively in the combustion stroke immediately before the substantial fuel cut control is started in each cylinder 2.

  In the above description, the case where the fuel cut control is performed in the port injection type internal combustion engine has been described. Next, the case where the fuel cut control is performed in the internal combustion engine provided with the direct injection type fuel injection valve. explain.

  FIG. 8 shows the relationship between the timing of fuel cut control of each cylinder 2 in the internal combustion engine 1 and the timing of advancing the ignition timing before MBT when a direct injection type fuel injection valve is provided. In the stroke associated with each cylinder 2 in the figure, the ignition timing is advanced excessively in the combustion stroke surrounded by a thick line. In addition, a fuel cut command is issued from the ECU 20 at the timing of the black arrow. In this case, since the direct injection type fuel injection valve is used, the fuel cut command and the fuel cut are performed at the same timing.

  FIG. 9 shows a flowchart of the ignition timing over-advance control routine 2 when the internal combustion engine 1 includes a direct injection type fuel injection valve. This routine is a program stored in the ROM of the ECU 20, and is executed by the ECU 20 for each cylinder 2 independently at predetermined intervals while the internal combustion engine 1 is in operation.

  When this routine is executed, first, in S101, it is determined whether or not the fuel cut control is performed. The content of this process is the same as the content of the process of S101 in the ignition timing over-advance control routine described with reference to FIG. Here, when it is determined that the fuel cut control is not being performed, the present routine is temporarily ended as it is. On the other hand, if it is determined that it is before fuel cut control, the process proceeds to S201.

  In S201, it is determined whether or not the combustion stroke in which the ignition timing is over-advanced in the cylinder 2 is completed. Specifically, it may be determined by reading into the ECU 20 the value of each flag that is turned on when the ignition timing is excessively advanced in the combustion stroke of the cylinder 2, or the ignition plug in the cylinder 2 You may determine by reading into ECU20 the setting value of 14 operation time. If it is determined that the combustion stroke in which the ignition timing is over-advanced in the cylinder 2 is not completed, the process proceeds to S203. On the other hand, when it is determined that the combustion stroke in which the ignition timing is over-advanced in the cylinder 2 is completed, the process proceeds to S202.

  In S202, fuel cut control is executed for the cylinder 2. When the process of S202 ends, this routine ends.

In S203, the ignition timing over-advance angle is executed for the cylinder 2. Specifically, in the cylinder 2, in the combustion stroke immediately before the compression stroke in which the fuel is cut, the ignition timing is set to ST1, and ignition of the spark plug 14 is executed. When the process of S203 is completed, this routine is temporarily ended.

  As described above, in the example provided with the direct injection type fuel injection valve, the ignition timing is excessively advanced in the combustion stroke immediately before the fuel cut control is performed. While suppressing the torque shock, it is possible to suppress the deterioration of the emission due to the in-cylinder attached fuel during the fuel cut being discharged as HC.

  Next, a second embodiment of the present invention will be described. In the present embodiment, a process of stopping the internal combustion engine 1 after executing an excessive advance angle of the ignition timing when stopping the internal combustion engine will be described. Note that the internal combustion engine 1, the intake / exhaust system, and the control system in this embodiment are the same as those shown in FIG.

  Here, consider a case where the internal combustion engine 1 is stopped from an idle state, for example. In this case, the in-cylinder attached fuel adhering to the wall surface in each cylinder 2 when the internal combustion engine 1 is stopped and the operation of the spark plug 14 is stopped is discharged as HC at the next start of the internal combustion engine 1. There was a case. Alternatively, the air-fuel ratio of the air-fuel mixture at the start of the internal combustion engine 1 sometimes becomes richer than the target value. In any of these cases, there is a possibility that the emission at the start of the internal combustion engine 1 may be deteriorated. In particular, if the internal combustion engine 1 is stopped before the internal combustion engine 1 is sufficiently warmed up, the amount of in-cylinder attached fuel remaining in the cylinder 2 is large, so that the amount of HC discharged at the next start becomes larger. There was a problem.

  Therefore, in this embodiment, before the internal combustion engine 1 is stopped, the ignition timing is excessively advanced in each cylinder 2 so that the in-cylinder attached fuel in each cylinder 2 is burned more reliably.

  FIG. 10 shows the fuel cut control of each cylinder 2 in the internal combustion engine 1 and the timing of the ignition timing over-advanced angle in this embodiment. That is, when the IG switch is turned off, the ignition timing of the fuel is set to ST1 and the ignition timing is over-advanced in the next combustion stroke that is reached in each cylinder 2. Then, when combustion with an excessive advance angle of ignition timing is completed in the combustion strokes of all the cylinders 2, the energization to the fuel injection valve 5 and the spark plug 14 is turned off and the internal combustion engine 1 is stopped.

  By doing so, after the internal combustion engine 1 is stopped, the in-cylinder attached fuel does not remain in each cylinder 2 of the internal combustion engine 1, and the emission at the next start of the internal combustion engine 1 can be improved.

  FIG. 11 shows the ignition timing over-advance control routine 3 in the present embodiment. This routine is a program stored in the ROM of the ECU 20 and is executed by the ECU 20 at predetermined intervals while the internal combustion engine 1 is in operation. This routine need not be executed independently for each cylinder.

  When this routine is executed, it is first determined in S301 whether or not the IG switch has been turned off. Here, if it is determined that the IG switch continues to be in the ON state, this routine is temporarily terminated as it is. On the other hand, if it is determined that the IG switch has been turned off, the process proceeds to S302.

In S302, it is determined whether or not the cooling water temperature is equal to or higher than a predetermined value. Specifically, it is determined by reading the output signal of the coolant temperature sensor 19 into the ECU 20 and comparing the coolant temperature obtained from this value with a predetermined value. Here, if it is determined that the cooling water temperature is equal to or higher than the predetermined value, since the internal combustion engine 1 is sufficiently warmed up, even if the engine is stopped as it is, the in-cylinder attached fuel in the cylinder 2 is sufficiently large. Since it is determined that the emission is not affected at the next start-up of the internal combustion engine 1, the process proceeds to S304, which will be described later. On the other hand, when it is determined that the cooling water temperature is lower than the predetermined value, the process proceeds to S303. Here, the predetermined value means that if the cooling water temperature is higher than this, the internal combustion engine 1 is sufficiently warmed up, and even if the engine is stopped as it is, the in-cylinder adhered fuel in the cylinder 2 is sufficiently small, and the next time This is the cooling water temperature as a threshold value at which it is determined that the emission does not deteriorate when the internal combustion engine 1 is started, and is obtained in advance through experiments or the like.

  In S303, it is determined whether or not the ignition timing over-advanced angle has been completed in all the cylinders 2 of the internal combustion engine 1. Specifically, the determination may be made by reading into the ECU 20 the value of a flag that is turned on when the ignition timing over-advanced angle is completed in all the cylinders 2, or the operation timing of the ignition plug 14 in each cylinder 2. It may be determined by reading the set value into the ECU 20. If it is determined that the ignition timing over-advance angle has not yet been completed in all the cylinders 2, the process proceeds to S305. On the other hand, if it is determined that the over-advanced ignition timing has already been completed in all the cylinders 2, the process proceeds to S304.

  In S304, energization to the fuel injection valve 5 and the spark plug 14 is stopped, and the internal combustion engine 1 is stopped. When the process of S304 ends, this routine ends once.

  In S305, the over advance angle of the ignition timing is executed in each cylinder 2. Specifically, in the combustion stroke of each cylinder 2, the ignition plug 14 is ignited after the ignition timing is set to ST1. Here, the ignition timing over-advance angle may be performed once in each cylinder 2 in order so that the over-advance angle of the ignition timing is completed in all the cylinders 2. When the processing of S305 ends, this routine is temporarily ended.

  As described above, in this embodiment, before the internal combustion engine 1 is stopped, the ignition timing is excessively advanced in each cylinder 2. As a result, the in-cylinder attached fuel in each cylinder 2 when the internal combustion engine 1 is stopped can be prevented from being discharged as HC at the next start of the internal combustion engine 1 or during the stop of the internal combustion engine 1, thereby reducing the deterioration of emissions. Can be suppressed.

It is a figure which shows schematic structure of the internal combustion engine, the intake / exhaust system, and the control system in the Example of this invention. It is a graph which shows the relationship between the ignition timing in the cylinder which concerns on the Example of this invention, and the state in a cylinder. It is a graph which shows the relationship between the ignition timing in the cylinder which concerns on the Example of this invention, the torque of an internal combustion engine, and the highest in-cylinder temperature. It is a graph for demonstrating the difference by the ignition timing of the relationship between the crank angle and cylinder pressure in the cylinder which concerns on the Example of this invention. It is an example of the graph used as the standard of the map which shows the relationship between the driving | running state of the internal combustion engine which concerns on the Example of this invention, and the ignition timing of a misfire limit. It is a figure shown about the fuel cut control of each cylinder in the internal combustion engine which concerns on Example 1 of this invention, and the timing of ignition timing over-advance. It is a flowchart which shows the ignition timing over-advance control routine in Example 1 of this invention. It is a figure shown about the fuel cut control of each cylinder in the internal combustion engine which concerns on Example 1 of this invention, and another example of the timing of ignition timing over-advance. It is a flowchart which shows the ignition timing over-advance control routine 2 in Example 1 of this invention. It is a figure shown about the engine stop control in the internal combustion engine in Example 2 of this invention, and the timing of an ignition timing excessive advance angle. It is a flowchart which shows the ignition timing over-advance control routine 3 in Example 2 of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Internal combustion engine 2 ... Cylinder 3 ... Intake port 4 ... Exhaust port 5 ... Fuel injection valve 6 ... Throttle valve 7.・ ・ ・ ・ Intake pressure sensor 8 ・ Air flow meter 9 ・ Exhaust gas purification device 10 ・ ・ ・ ・ Intake valve 11 ・ ・ ・ ・ Exhaust valve 12 ・ ・ ・ ・ Intake side camshaft 13 ・ ・・ ・ Exhaust camshaft 14 ・ ・ ・ ・ Spark plug 15 ・ ・ ・ ・ Piston 16 ・ ・ ・ ・ Connecting rod 17 ・ ・ ・ ・ Crankshaft 18 ・ ・ ・ ・ Crank position sensor 19 ・ ・ ・ ・ Water temperature sensor 20 ・... ECU
30 ... Intake passage 40 ... Exhaust passage

Claims (5)

Over-advance means for advancing the ignition timing of the spark ignition type internal combustion engine before MBT;
Fuel supply stop means for stopping fuel supply to the combustion chamber in the internal combustion engine;
When stopping the fuel supply to the combustion chamber in the internal combustion engine by the fuel supply stop means, the fuel advance over-advance control means for advancing the ignition timing ahead of MBT by the over-advance angle means;
Equipped with a,
The fuel advance over-advance angle control means advances the ignition timing ahead of MBT by the over-advance angle means before the fuel supply stop means stops the fuel supply to the combustion chamber in the internal combustion engine. ,
When the fuel supply stop means temporarily stops the fuel supply to the combustion chamber in the internal combustion engine during operation of the internal combustion engine, the fuel stop over-advance angle control means is provided in the cylinder of the internal combustion engine. wherein in a combustion stroke immediately before the fuel supply is stopped, the control system of an internal combustion engine, characterized in Rukoto advance is angularly to prior MBT ignition timing by the over-advanced means. When stopping the fuel supply to the combustion chamber in the internal combustion engine by the fuel supply stop means during the stop operation of the internal combustion engine, the over-advance angle control means at the time of fuel stop is instructed to stop the internal combustion engine. 2. The control system for an internal combustion engine according to claim 1 , wherein the fuel supply is stopped after the ignition timing is advanced to the front of MBT by the over-advance angle means for a predetermined period thereafter. The over-advancement means, the ignition timing of the internal combustion engine even before than MBT, claim 1, the pressure in the cylinder of the internal combustion engine is equal to or to advance up to become the ignition timing in the vicinity of TDC Or the control system of the internal combustion engine of 2 . The internal combustion engine is a port injection internal combustion engine;
The fuel supply stop means stops the supply of fuel injected from the fuel injection valve to the intake port at the end of the intake stroke or the start of the compression stroke in the cycle before the cycle in which the fuel supply into the cylinder is actually stopped. Command
The fuel advance over-advance angle control means advances the ignition timing ahead of MBT by the over-advance angle means in a cycle before the cycle in which the fuel supply into the cylinder is actually stopped.
The control system for an internal combustion engine according to any one of claims 1 to 3, wherein: The internal combustion engine is a direct injection internal combustion engine,
The fuel supply stop means issues a stop command for fuel supply injected into the cylinder from the fuel injection valve at the same timing as when the fuel supply into the cylinder is actually stopped,
The fuel stop over-advance angle control means advances the ignition timing ahead of MBT by the over-advance angle means in a cycle before a cycle in which the fuel supply into the cylinder is actually stopped. The control system for an internal combustion engine according to any one of claims 1 to 3.

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