JP2000073843A - Internal combustion engine control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To perform a proper control to perform a precise failure diagnosis by controlling the drive of a stepping motor by the deviation between actual opening and a target opening. SOLUTION: The actual opening of a swirl control valve opened and closed by a swirl control valve driving means 32 is measured by a swirl control valve opening sensor. The respective outputs from a target swirl control valve opening arithmetic means 31 and the swirl control valve opening sensor are detected by a target opening-to-actual opening deviation arithmetic means 35, and the swirl control valve drive control is properly corrected by a swirl control valve drive control means 32 through a zero-point calibrating control means 35 and a swirl control valve driving speed correcting means 34. The target opening and the outputs of the actual opening deviation calculating means 33, the driving speed correcting means 34 and a zero-point calibration execution frequency judging means 36 are detected by a failure judging means 37.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive control of a swirl control valve and a swirl control valve provided for the purpose of improving the exhaust gas characteristics of an internal combustion engine and improving the combustion aiming at combustion stability during lean combustion. The present invention relates to a control device for an internal combustion engine having a failure diagnosis device for diagnosing a failure, and more particularly to a drive adjustment control using an actual opening and a target opening by a valve opening sensor of a swirl control valve and a method for diagnosing an abnormality of the swirl control valve. .

[0002]

2. Description of the Related Art Conventionally, for example, in a direct injection engine, it is necessary to perform lean combustion with an air-fuel ratio A / F of 40 or more. Therefore, a gas flow called swirl or tumble is applied to a combustion chamber of a cylinder. I have. There are various means for giving the gas flow, but it is general to generate an appropriate gas flow by a combination of the shape of the intake pipe and the swirl control valve.

[0003] As such an internal combustion engine provided with a swirl control valve, for example, there is a technique described in Japanese Patent Publication No. Hei 5-31649, which discloses a technique for detecting the pressure in an intake pipe in order to prevent deterioration of drivability. It discloses that the negative pressure switching valve is controlled and the air-fuel ratio target value is changed.
However, in the prior art, when the closed state of the swirl control valve cannot be maintained, the switching valve is operated and the air-fuel ratio target value is changed, but it is determined whether or not the swirl control valve itself is normally operating. Since no diagnosis is performed, it is not always possible to say that the control is appropriate.

[0006] Here, it is generally known that swirl hardly occurs in the flow of intake air when the swirl control valve is fully open, and conversely, swirl increases near the fully closed state. When the air-fuel ratio is controlled to a target air-fuel ratio leaner than the stoichiometric air-fuel ratio, it is known that the amount of HC (hydrocarbon) in the exhaust gas changes depending on the state of swirl generated by the swirl control valve. Have been.

Therefore, when the engine is operated at the lean air-fuel ratio, the control of the swirl control has a great effect on the operability from the viewpoint of exhaust gas.
From this, diagnosis of whether the swirl control valve is operating normally is one of the important diagnosis items especially in operation control for improving combustion.

Therefore, Japanese Patent Application Laid-Open No. Hei 8-74583 proposes a technique for diagnosing the operation of the swirl control valve itself in the lean combustion operation control or the operation control for improving the exhaust characteristics. This is a signal corresponding to the actual valve opening in response to the swirl control valve opening command signal in relation to the operating state of the internal combustion engine, for example, a detection signal such as the pressure of the intake pipe near the swirl control valve by a pressure sensor, This is to diagnose that the swirl control valve is abnormal when a deviation equal to or more than a predetermined value occurs in comparison with a reference opening characteristic measured in advance.

[0007]

Generally, the magnitude of swirl swirling flow (the number of swirls) supplied to the combustion chamber of the engine naturally increases as the amount of air increases when the engine is operated at high speed and high torque. The swirl control valve must be controlled so as to decrease as the speed and torque increase. However, the swirl control valve must be controlled by other engine operating conditions and combustion conditions. Needs to be carefully controlled.

That is, the stability of engine combustion, the generation of smoke, the generation of hydrocarbons, and the like depend on the fuel injection timing and ignition timing of the fuel injection valve. It is necessary to consider the fuel injection timing and ignition timing of the valve. Particularly, the stability of combustion and the generation of hydrocarbons and the like are affected by the swirl swirling flow (the number of swirls). It is known that there is an optimum region for the stability of the carbon dioxide and a minimum region for the generation of hydrocarbon. For this reason, in controlling the opening and closing of the swirl control valve in order to adjust the swirl swirling flow, it is necessary to consider the combustion state such as combustion stability and the fuel pressure.

However, in the prior art, a signal corresponding to an actual valve opening degree, such as a pressure change in an intake pipe, is detected by a pressure sensor in response to a swirl control valve opening / closing command signal in relation to an operating state of an internal combustion engine. When the deviation of the swirl control valve exceeds a predetermined value compared with the previously measured reference opening characteristic, the swirl control valve is diagnosed as abnormal. Was not directly detected and responded to, and deterioration in drivability due to the abnormality, failure, or the like could not be accurately suppressed.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has as its object to reduce the valve drive response to a swirl control valve opening / closing command signal due to deterioration of a swirl control valve of an internal combustion engine. It is an object of the present invention to provide a failure diagnosis device for an internal combustion engine which can provide a control for performing a correction according to a change in the opening degree and a failure of the swirl control valve and can perform a reliable diagnosis by directly and quantitatively determining the failure. .

[0011]

SUMMARY OF THE INVENTION An object of the present invention is to provide an opening / closing drive control means having a swirl control valve disposed at an intake port of an internal combustion engine, and driving and controlling the swirl control valve by a stepping motor. An internal combustion engine control device comprising: a valve opening sensor for detecting a valve opening; and means for detecting a deviation between an actual opening and a target opening from the valve opening sensor. This is achieved by an internal combustion engine control device wherein the drive control of the stepping motor is performed based on the deviation from the degree.

Further, the above object is to provide a swirl control valve disposed at an intake port of an internal combustion engine, and to control the driving of the swirl control valve by a stepping motor, and to control the opening degree of the swirl control valve. In an internal combustion engine control device provided with a valve opening sensor for detecting and a failure diagnosis means for diagnosing a failure of the swirl control valve, the failure diagnosis device detects a failure of the swirl control valve itself and makes a failure determination. The present invention is also achieved by an internal combustion engine control device having means for performing the operation.

[0013]

Embodiments of the present invention will be described below in detail with reference to the drawings.

FIG. 1 shows an example of an engine system to which the present invention is applied. In the drawing, air taken into an engine 8 is taken in from an inlet 2 of an air cleaner 1 and enters a collector 7 through a throttle valve device 6 provided with a throttle valve 5 for controlling the amount of intake air. The throttle valve 5 is
The throttle valve 5 is operated by driving the motor 10. The throttle valve 5 is operated to control the amount of intake air. The intake air reaching the collector 7 is distributed to each intake air pipe 9 connected to each cylinder 23 of the engine 8 and is guided into the cylinder 23.

On the other hand, fuel such as gasoline is sucked and pressurized from a fuel tank 11 by a fuel pump 12, and then supplied to a fuel system 24 in which a fuel injection valve (injector) 13 and a variable fuel pressure regulator 14 are piped. Is done. The fuel system is adjusted to a predetermined pressure by the variable fuel pressure regulator 14 described above, and is injected into the cylinders 23 from the injectors 13 having the fuel injection ports opened in the respective cylinders 23. Further, a signal representing the intake flow rate is output from the air flow meter 3 and input to the control unit 15.

Further, a throttle sensor 18 for detecting the opening of the throttle valve 5 is attached to the throttle valve device 6, and the output thereof is also input to the control unit 15.

Reference numeral 16 denotes a crank angle sensor, which is driven to rotate by a cam shaft 25 and outputs a signal indicating the rotational position of the crank shaft. This signal is also input to the control unit 15.

Reference numeral 20 denotes an A / F provided in the exhaust pipe 26.
The (air-fuel ratio) sensor detects and outputs the actual operating air-fuel ratio from the components of the exhaust gas, and the signal is input to the control unit 15 in the same manner.

The control unit 15 has a processing means (CPU) 27, receives various signals for detecting the operating state of the engine, such as the above-described crank angle signal and throttle opening signal, as input signals, and performs predetermined arithmetic operations. And outputs various control signals calculated as a result of the calculation, and outputs predetermined signals to the injector 13, the ignition coil 17, and the motor 10 for operating the throttle valve to control fuel supply and ignition timing. , Execute intake air amount control.

Reference numeral 28 denotes a warning device including various warning lights.

Since these structures are well known, further description will be omitted.

FIG. 2 shows a control system in the control unit 15. In the drawings described below, the same reference numerals are given to parts common to FIG. The control unit 15 includes a CPU 15a serving as a control center, input processing means 15b for performing predetermined processing (for example, A / D conversion, etc.) on detection signals from various sensors described later, and performs data transfer. Bus 1
5c, and output processing means 15d for outputting data subjected to predetermined arithmetic processing by the CPU 15a.

The input processing means 15b includes a crank angle sensor 17, a throttle sensor 18, an accelerator sensor 10
7, detection signals from the water temperature sensor 108, the air flow meter 3, the swirl control valve angle sensor 22a, the EGR valve angle sensor 21a, and the battery voltage detection means 111 are taken in, and these signals are input to the input processing means 15b.
After the data is converted into data by a predetermined process, the data is provided to the CPU 15a via the bus 15c. Also, from the input processing 15b, the interrupt controller 1
04 is given an interrupt signal.

When the CPU 15a receives various detection data via the bus 15c, the CPU 15a performs an arithmetic operation on the various detection data based on a predetermined program stored in the ROM 101, and then performs the arithmetic operation. The data is stored in the RAM 102 and the backup RAM 106, and the warning light 28, the injectors 13a to 13d, the throttle motor 10, the motor 22b for operating the swirl control valve, and the motor 21 for operating the EGR valve.
, And outputs a control signal via the output processing means 15d.

FIG. 3 is a block diagram showing the overall configuration of the present invention.

A drive control system for the swirl control valve provided in the control unit 15, a failure detection system,
And a control block diagram of a control system based on failure detection. Detection signals from various sensors from the crank angle sensor 16, the throttle sensor 18, the air flow meter 3 and the like are taken in through the input processing means 15b, and the opening degree of the swirl control valve 22 is calculated by the target swirl control valve opening calculating means 31. Is calculated by the swirl control valve drive control means 32, the swirl control valve actuator (stepping motor, etc.)
Are driven to have the optimal opening.

The actual opening of the swirl control valve 22, which is opened and closed by the swirl control valve drive control means 32, is measured by a swirl control valve opening sensor 22a.

Target swirl control valve opening calculating means 31, swirl control valve opening sensor 22
a from the target opening degree and the actual opening degree deviation calculating means 33, and based on the calculated result, 0
Through the point calibration control means 35 (zero point calibration will be described in detail later) and the swirl control valve drive speed correction means 34, the correction is performed by the swirl control valve drive control means 32 so that the optimal drive control is performed.

The target opening and actual opening deviation calculating means 33,
Driving speed correction means 34, zero point calibration execution number determination means 36
Is detected by the failure determining means 37, and when a failure is determined, the warning light 2 is output by the failure control means 38.
Operation control such as lighting control 8 is performed.

FIG. 4 is a diagram showing a general function of the swirl control valve 22 using the stepping motor shown in FIG. 1. For example, when the number of steps of the stepping motor is small, the swirl control valve 22 is used. Is controlled to the closed side. As shown in the figure, the swirl air flow such as swirl and tumble can be variably controlled by the swirl control valve angle, so that by selecting the swirl swirl flow required from the combustion, the best control of the combustion stability of the internal combustion engine can be performed. .

FIG. 5 shows the drive system of the swirl control valve using the stepping motor shown in FIG. 4, and the two intake ports 9a and 9b of the intake pipe 9 communicating with each cylinder 23 of the engine 8. One of the 9b
The swirl control valve 22 is provided so as to close the passage 9b, and the exciting coils 22b1-2 are opened and closed so as to open and close the swirl control valve 22.
Swirl control valve motor 22 having 2b4
b (hereinafter referred to as stepping motor for simplicity)
Is attached. The stepping motor 22b
Are driven by the driving power from the battery power supply VB. The CPU 15a in the control unit 15
Thus, for example, four transistors Tr1, Tr2,
Tr3 and Tr4 are driven. For example, when the transistors Tr1, Tr2, Tr3 and Tr4 are driven in the order of transistor Tr1, Tr2, Tr3 and Tr4, the stepping motor 22b is driven to rotate in the forward direction. , Transistors Tr4 → Tr3 → Tr2 →
The transistors Tr1, Tr2, Tr3, in the order of Tr1
When Tr4 is driven, the stepping motor 22b
Are rotated in the opposite direction (the driving principle will be described later in detail). Thereby, the swirl control valve 2
2 is performed. Further, the angle of the swirl control valve 22 whose opening has been actually adjusted is measured by the swirl control valve angle sensor 22a, detected by the input processing 15b, and
Predetermined arithmetic processing is performed by 5a.

FIG. 6 shows a swirl control valve 22.
The principle of the operation of the stepping motor 22b for driving the motor to open and close will be described. The stepping motor 22b has a permanent magnet 81 magnetized alternately with NS poles around the circumference, and a permanent magnet 81 surrounding the magnet.
A layered electromagnetic coil 82 (here, the coil 82 is the same as the exciting coils 22b1 to 22b4, but is collectively described below with another reference numeral 82 for convenience of explanation).
In the figure, only one set of NS is shown for convenience of explanation of the permanent magnet 81, and a part of the circumference of the permanent magnet 81 and the electromagnetic coil 82 is projected and shown on a plane. Here, when the electromagnetic coil 82 is excited as shown in FIG.
By the force balance of 2, the position is stabilized at the position shown in FIG. Next, as shown in (b), when the N and S poles are reversed by reversing the energizing direction of the phase of the lower electromagnetic coil,
It is stabilized at the next position as shown in FIG. That is, the permanent magnet is displaced by the operation shown in FIG. By repeating this operation, the operation of the stepping motor 22b can be realized in the circumferential direction. If this circumferential motion is converted to linear motion, accurate position control can be performed.
Also, as shown in FIG. 3C, when only one of the two excitation phases is excited, in this case, only the upper phase is excited following the operation of FIG. Can be realized. As described above, by performing the control of repeating one phase → two phases → one phase, the control accuracy of the operation amount can be doubled as compared with the case where the control of only two phases or only one phase is performed.

Here, for example, an external force is applied to the stepping motor 22b, and the stepping motor 22b is forcibly operated in the rotation direction.
If the stable phase is shifted by one rotation, the stepping motor 22b
It is stable in a deviated position and does not return to the original position by a simple phase excitation operation. This is called step-out. If the step-out occurs, the control accuracy of the control using the stepping motor 22b is disadvantageously deteriorated. Therefore, a mechanical restriction (stopper) is provided in the operation range of the stepping motor 22b, and the operation of applying the stepping motor 22b to this is provided. It is generally known that the control is repeatedly performed to absorb a step-out deviation and to make the position recognition value on the control coincide with the actual stepping motor position. This is called zero-point calibration.

FIG. 7 shows an operation diagram of the zero-point calibration. If the switching of the excitation phase of the stepping motor 22b that drives the opening and closing of the swirl control valve 22 continues to be driven toward the stopper, the position of the stepping motor repeats collision → reflection → collision with the stopper as shown by the dotted line in the drawing. . After performing this operation a predetermined number of times, if the stepping motor position on the control is corrected to the stopper position, the stepping motor position shift due to the step-out can be absorbed. The number of times of the zero-point calibration and the repetition control are referred to as margin times and margin control. Here, during the zero-point calibration, the original control cannot be performed because the stepping motor 22b is fixed at the position of the stopper.
Further, since the zero-point calibration operation collides with the mechanical stopper as described above, a sound is generated due to the collision. Therefore, in a swirl control valve using a stepping motor, it is desirable to minimize the stopper collision period performed in the zero-point calibration. Therefore, by comparing the swirl control valve angle sensor 22a with the control recognition swirl control valve step position, the amount of step-out which is the difference between the dotted line and the solid line shown in FIG. 7 is measured, and the measured step-out amount is calculated. If the zero-point calibration is performed based on this, it is possible to minimize the stopper collision period performed in the zero-point calibration.

FIG. 10 shows the flow of the above-mentioned zero-point calibration control. In step 1001, the swirl control valve step position STPM and the output value STP of the swirl control valve angle sensor 22a are determined.
Find the deviation DELSTP of O.

Next, at step 1002, a margin is added to the deviation DELSRP to the previously evaluated characteristic variation of the swirl control valve angle sensor 22a (this characteristic variation will be described later with reference to FIGS. 16, 17, and 20). The minimum number of zero-point calibration steps MRG0 to which MRGSTP is added is calculated. In step 1003, a zero-point calibration permission determination is performed based on the operating state of the internal combustion engine, the battery voltage, and other conditions. If it is determined that the zero-point calibration permission condition is satisfied, zero-point calibration control is performed in step 1004. .

Here, regarding the control contents of the zero-point calibration,
It has been described with reference to FIG. 7, and the detailed description is omitted here.

FIG. 12 shows the relationship between the excitation switching cycle of the stepping motor 22b for opening and closing the swirl control valve 22, the so-called control speed, and the step-out of the stepping motor 22b described with reference to FIG. As shown in (a), when the control speed is increased, the stepping motor 22b cannot follow the control speed, causing a step-out. If the high-speed control is continued as it is, the step-out amount increases in proportion to the duration, and it becomes impossible to secure the swirl control valve control accuracy. The cause of this step-out occurs when the control speed is set too high or when the operating friction of the stepping motor 22b increases. Such a step-out can be prevented by reducing the control speed as shown in FIG.

FIG. 11 shows a control flow for preventing the step-out amount from increasing due to the control speed shown in FIG. 12. In step 1101, the control speed of the stepping motor 22b for driving the swirl control valve 22 to open and close is determined. Calculation is performed, and drive control of the stepping motor 22b is performed. Next, in step 1001, the deviation DELSTP is obtained as described with reference to FIG. In step 1102, the DELSTP obtained in step 1001
Is determined based on the result of the above. The step-out determination method will be described later with reference to FIGS. Then
In step 1103, when step-out is determined in step 1102, SPLOW is added to the control speed STPSP to perform low-speed control of the control speed.

FIG. 16 is a diagram showing the relationship between the control swirl control valve step position STPM and the output value STPO of the swirl control valve angle sensor 22a. With respect to the basic characteristics shown in the figure, the characteristic variation of the swirl control valve angle sensor 22a is the upper limit and the lower limit. If the relationship between the STPM and STPO deviates from the upper and lower limit lines in the figure, STPM and STPO
The relationship of PO becomes unmatched, and the stepping motor 22 for opening and closing the swirl control valve 22 is opened.
This means that b is out of step.

Here, as the characteristic variation of the swirl control valve angle sensor 22a is larger, the upper and lower limit lines are broader with respect to the basic characteristics, and the accuracy of the step-out determination is deteriorated. When such a case is allowed, the determination control in FIG. 10 and step 1001 adversely affects the zero-point calibration control and the stepping motor drive speed control.

FIG. 17 is a diagram showing a method for absorbing the characteristic variation of the swirl control valve angle sensor 22a. As shown in FIG.
Point calibration control is performed, and then drive control is performed to the initial position. Since the initial position is immediately after the zero point calibration is performed, the angle of the swirl control valve is an accurate position. By correcting the angle of the swirl control valve angle sensor 22a based on the initial position, it is possible to correct the characteristic variation of the swirl control valve angle sensor 22a.

FIG. 4B shows the characteristics before and after the characteristic variation correction of the swirl control valve angle sensor 22a. By correcting the characteristic variation of the swirl control valve angle sensor 22a, FIG.
It is possible to accurately measure the angle of the swirl control valve, and to perform optimal zero-point calibration control and stepping motor drive speed control.

FIG. 20 shows a control flow for absorbing the characteristic variation of the swirl control valve angle sensor 22a described in FIG. 17. In step 2001, it is determined whether the zero-point calibration control of the stepping motor has been completed. Is determined. If it is determined in step 2001 that the zero-point calibration has been completed, in step 2002, the stepping motor is driven to the initial position.

Next, at step 2003, the output value STPOmin of the swirl control valve angle sensor 22a at the initial position is read. Step 20
04, the STPOmin obtained in step 2003
Is multiplied by the update gain WT and added to the output value STPOV of the swirl control valve angle sensor 22a.
Obtain the swirl control valve STPO. Here, by giving the update gain WT, the learning update amount at one time is suppressed, thereby preventing erroneous learning due to noise or the like.

Next, during the zero-point calibration of the stepping motor 22b for driving the swirl control valve 22 to open and close, there is a problem that control cannot be performed originally and a sound is generated. As mentioned. FIG. 10 shows that the problem is dealt with by optimizing the number of drives (the number of margins) during the zero-point calibration. However, the stepping motor 22b for opening and closing the swirl control valve 22 loses synchronism. Whether or not
Determine the zero-point calibration start condition, and if there is no step-out,
The above problem can also be dealt with by not performing zero-point calibration.

FIG. 18 shows a flow chart for determining the zero-point calibration condition. In step 1801, a zero-point calibration start condition is determined based on the operating state of the internal combustion engine. FIG. 19 shows an example of operating conditions of the internal combustion engine. FIG. 19 shows the setting of the angle of the swirl control valve according to the operating state of the internal combustion engine. In the idle state, the valve is fully closed. If the zero-point calibration is performed on the swirl control valve fully closed side, the zero-point calibration may be permitted during the idling.

FIG. 13 shows a swirl control valve 2
2 is a control flow for determining the failure of the swirl control valve based on the control speed of the stepping motor 22b that drives the opening and closing of the motor 2. As described above with reference to FIG. 11, the control speed STPSP of the stepping motor 22b abnormally decreases. If corrected, the stepping motor 2
2b does not secure a normal function and can be regarded as a failure. In step 1103, as described in FIG. 11, the control speed STPSP by the deviation DELSTP is used.
Is corrected. In step 1301, the control speed STP
It is determined whether or not SP is equal to or greater than a predetermined value SPNG.
Here, the SPNG value may be set according to the power supply voltage that is the driving force of the stepping motor. In this case, the driving force of the stepping motor is more likely to be reduced on the low voltage side, However, the SPNG value becomes a large value. In step 1302, control speed ST
When it is determined that the PSP is equal to or greater than the predetermined value SPNG, it is determined that the swirl control valve has failed.

FIG. 14 shows a control flow for judging the failure of the swirl control valve by comparing the control swirl control valve step position STPM with the change width of the output value STPO of the swirl control valve angle sensor 22a. In step 1401, a change width ΔSTPM of the STPM at every predetermined time is calculated. In step 1402, a change width ΔSTPO of the STPO at predetermined time intervals is calculated. Here, ΔSTPM and ΔS
The predetermined time for obtaining the TPO is the same time interval.
Next, in step 1403, the ΔSTPM and ΔS
It is determined whether or not the difference between TPO is greater than a predetermined value DELNG. If either the whirl control valve step or the swirl control valve angle sensor has failed, the relative relationship between ΔSTPM and ΔSTPO is broken, and the absolute value of the difference between ΔSTPM and ΔSTPO becomes a predetermined value DE.
This is a value larger than LNG.

In step 1302, step 1403
And the difference between ΔSTPM and ΔSTPO is a predetermined value DELNG
If it is determined that the value is larger than the threshold value, it is determined that the swirl control valve has failed.

FIG. 15 shows that the swirl control valve step position STPM and the swirl control valve angle sensor 2 on the above-mentioned control were obtained even though the zero-point calibration was performed.
This shows a control flow for determining a failure of the swirl control valve based on the fact that the difference between the output values STPO of 2a is not improved. In step 1501, it is determined whether or not the zero-point calibration control has been executed. In step 1502, when the zero-point calibration is executed in step 1501,
The zero point calibration execution counter 0CNT is incremented.
In step 1503, the 0CNT is a predetermined value 0CNT.
It is determined whether or not NG has been performed. By this judgment,
It is determined whether the zero-point calibration has been sufficiently performed. Where 0C
The NTNG value may be set to a value that can correct even the maximum possible step-out. In step 1001, as described with reference to FIG. 10, the absolute value DELSTP of the deviation between the control swirl control valve step position STPM and the output value STPO of the swirl control valve angle sensor 22a is determined. Next, in step 1504, the DELSTP is set to a predetermined value S
It is determined whether or not the value is equal to or more than the CVNG value. In step 1302, when it is determined in step 1504 that the DELSTP is equal to or greater than the SCVNG value, it is determined that the swirl control valve is faulty.

If any one of the swirl control valve failure determinations described above is determined to be a failure, the lighting control of the warning lamp 28 in FIG. 2 is performed to notify the driver of the failure state. .

Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above-described embodiments, and may be designed in a manner not departing from the spirit of the invention described in the appended claims. Various changes can be made.

[0054]

As can be understood from the above description, according to the swirl control valve control and failure diagnosis apparatus for an internal combustion engine according to the present invention, when the deviation calculation means outputs a step-out determination output, the appropriate Control of the stepping motor can be performed, and a highly accurate failure diagnosis can be performed.

[Brief description of the drawings]

FIG. 1 is an example of an engine system to which the present invention is applied.

FIG. 2 is a configuration diagram of a control unit to which the present invention is applied.

FIG. 3 is a basic configuration diagram of a control block according to the present invention.

FIG. 4 is a characteristic diagram of a swirl control valve to which the present invention is applied.

FIG. 5 is a drive system of a swirl control valve to which the present invention is applied.

FIG. 6 shows a driving principle of a stepping motor to which the present invention is applied.

FIG. 7 is a zero-point calibration control diagram of a stepping motor to which the present invention is applied.

FIG. 8 is an abnormal state diagram of the swirl control valve to which the present invention is applied.

FIG. 9 is an abnormal state diagram of a swirl control valve to which the present invention is applied.

FIG. 10 is a flowchart of zero-point calibration control to which the present invention is applied.

FIG. 11 is a control flowchart for correcting a driving speed to which the present invention is applied.

FIG. 12 is a view for explaining the effect of the effect of FIG. 11;

FIG. 13 is a control flow chart for judging a failure by control speed correction applied to the present invention.

FIG. 14 is a control flow chart for determining a failure by performing a change width comparison to which the present invention is applied.

FIG. 15 is a control flowchart for determining a failure based on an angle deviation applied to the present invention.

FIG. 16 is a diagram illustrating a relationship between control and an actual opening degree.

FIG. 17 is a diagram illustrating a method of absorbing variation in the opening degree sensor.

FIG. 18 is a flowchart of setting a zero-point calibration condition to which the present invention is applied.

FIG. 19 is a relationship diagram between operating conditions and a target opening.

FIG. 20 is a control flowchart of FIG. 17 to which the present invention is applied;

[Explanation of symbols]

13: injector, 15: control unit, 1
5b: input processing, 22a: swirl control valve opening sensor, 22b: swirl control valve motor, 28: warning light.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Toshio Hori 2520 Oita Takaba, Hitachinaka-shi, Ibaraki F-term in the Automotive Equipment Division of Hitachi, Ltd. (Reference) 3G065 CA27 CA34 CA39 DA06 FA04 FA07 FA09 FA13 GA00 KA33 3G084 BA21 DA22 DA27 EA09 EA11 EB08 EB22 EC04 EC07 FA00 FA03 3G301 HA01 HA04 JA15 JB01 JB02 JB09 LA05 NB06 NC02 ND25 NE20 NE21 PA00Z

Claims (12)

[Claims] An opening / closing drive control means having a swirl control valve disposed at an intake port of an internal combustion engine, and driving and controlling the swirl control valve by a stepping motor, and a valve for detecting an opening degree of the swirl control valve An internal combustion engine control device comprising an opening sensor and a means for detecting a deviation between the actual opening and the target opening from the valve opening sensor, wherein the stepping is performed by a deviation between the actual opening and the target opening. An internal combustion engine control device that performs drive control of a motor. 2. The internal combustion engine according to claim 1, wherein the drive control of the stepping motor determines the number of times of zero point calibration driving of the stepping motor based on a deviation between the actual opening and the target opening. Engine control device. 3. The internal combustion engine control device according to claim 1, wherein the drive control of the stepping motor changes the drive speed of the stepping motor according to a deviation between the actual opening and the target opening. 4. The method according to claim 3, wherein the drive speed of the stepping motor is controlled to be slow when a deviation between the actual opening and the target opening is larger than a predetermined threshold value. Internal combustion engine control device. 5. The driving control of the stepping motor according to claim 1, further comprising means for judging permission of zero-point calibration control of the stepping motor based on a difference between the actual opening and the target opening. An internal combustion engine control device characterized by the above-mentioned. 6. The method according to claim 5, wherein the permission of the zero-point calibration control of the stepping motor is determined when the deviation between the actual opening and the target opening becomes a value larger than a preset threshold value. An internal combustion engine control device, which determines permission. 7. The internal combustion engine control device according to claim 6, wherein said zero-point calibration permission determination threshold value is variable based on a power supply voltage. 8. An internal combustion engine control system according to claim 1, further comprising means for learning an angle recognition value of said swirl control valve at an initial position after completion of said zero point calibration. 9. An opening / closing drive control means having a swirl control valve disposed at an intake port of an internal combustion engine, and driving and controlling the swirl control valve by a stepping motor, and a valve for detecting an opening degree of the swirl control valve In an internal combustion engine control device including an opening sensor and a failure diagnosis unit that diagnoses a failure of the swirl control valve, the failure diagnosis unit includes a unit that detects a failure of the swirl control valve itself and performs a failure determination. An internal combustion engine control device, comprising: 10. The internal combustion engine control device according to claim 9, wherein the failure determination is performed by comparing a control change amount of the swirl control valve with a change amount of the actual valve opening. 11. The failure determination according to claim 9, wherein the failure is determined when a deviation between the actual opening and the target opening after the zero-point calibration becomes larger than a predetermined threshold value. An internal combustion engine control device characterized by determining that: 12. The method according to claim 9, wherein the failure is determined to be a failure when the control speed of the swirl control valve is corrected to be lower than a preset threshold value. An internal combustion engine control device according to any one of the preceding claims.