JPH08114143A - Idle control method for engine - Google Patents

Abstract

PURPOSE: To minimize the influence of a delay of air by a method wherein a pass air quantity of an idle control valve is caculated as a total sum of an air mass accumulated in a chamber by an intake air system model and an air mass sucked in a cylinder, and based on a calculation value of a pass air qnantity, the opening of an idle control valve is controlled. CONSTITUTION: In control by an ECU, a target value Gaset of a stroke intake air quantity Ga defined by a cylinder intake air mass per a suction stroke of a cylinder considered to have a linear relation with torque, shown in a diagram, of an engine is calculated at S104. By multiplying the Gaset by a target fuel-air ratio F/A through a fuel injection quantity calculation subroutine, a fuel injection quantity Gf is calculated from the Gaset and an ISCV pass air amount Qisc is calculated according to a reverse chamber model formula at S109. Thereafter, the Qisc is corrected by temperature and converted into Gisc'. From the Qisc' and a differential pressure between the front and the rear of an ISCV(Idle Speed Control Valve), a duty ratio outputted to an idle control valve is calculated.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an engine idle control method in which an intake system model is used to calculate an air amount suitable for the fuel injection amount during idling, and the idle control valve is controlled so as to be the air amount. .

[0002]

2. Description of the Related Art Conventionally, as a method for controlling the idle speed of an engine to be constant regardless of load disturbance, as shown in FIG. 35, a PI controller (or PID control) is applied to the deviation between the engine speed and the target speed. Idle control valve (idle speed control valve; ISC) that adjusts the idle air amount as the operation amount of this PI controller.
There is a method of giving a valve opening degree of V), the air amount by ISCV is measured by an air flow meter or an intake pipe pressure sensor, the fuel injection amount is determined based on the intake air amount, and the fuel injection amount is determined according to the fuel injection amount. The engine torque is generated so that the engine speed matches the target engine speed.

However, the problem of matching the rotational speed with the target rotational speed by controlling such torque is that, in the case of a motor, the classical PI control mainly having P as a current having a linear relationship with the torque. Can be solved by doing
In the case of an engine, since there are two parameters of torque, air and fuel, a delay related to the air in the intake system and a delay in the fuel system pose a problem. It is difficult to fully satisfy the demand for sex.

Regarding the delay of the intake system, for example, as disclosed in Japanese Patent Laid-Open No. 6-185391, an attempt is generally made to improve the problem of the delay by applying a fluid dynamic model to the intake system. Further, for example, in Japanese Patent Laid-Open No. 4-136448, the rotational speed of the internal combustion engine and the intake pipe pressure are measured, and the opening of the idle control valve is determined based on these measured values, and the measured values A proposal has been made to improve the delay of air and fuel by calculating the predicted value of the intake pipe pressure from the above and calculating the fuel injection amount proportional to this predicted value.

[0005]

In the conventional idle control, there is a large follow-up delay until the engine torque increases after the operation amount (ISCV opening request) increases. That is, after the operation amount is increased to increase the valve opening (valve opening area) of the ISCV, first, there is a delay until the air flows into the cylinder (in the cylinder) of the engine, and then the There is a delay until the amount of fuel commensurate with the amount of air taken in flows into the cylinder. Therefore, a considerable delay occurs until both the air and the fuel are aligned and the engine torque increases, and the requirements for responsiveness and rotation convergence cannot be satisfied.

It is considered that the factors of these delays are that the following four items have a serial influence. (1) Mechanical response delay of ISCV (2) Since there is a time delay until the air amount passing through the ISCV becomes equal to the cylinder inflow air amount, a delay occurs until the engine torque increases (intake chamber Delay due to air filling). (3) Since the fuel injection amount is calculated after measuring the air amount, there is a measurement delay, and a delay occurs until the engine torque increases (response delay of the sensor that measures the air amount). (4) Delay in fuel transportation into the cylinder due to adhesion of fuel to the wall surface of the intake port.

The first preceding example (Japanese Patent Laid-Open No. 6-18539)
If a hydrodynamic model is applied to the intake system as in (1), the delay due to the air filling in the intake chamber in the above (2) can be minimized.
Delays due to (3) and (4) are not taken into consideration.

The second prior art example (Japanese Patent Application Laid-Open No. 4-13)
In Japanese Patent No. 6448), a predicted value of the intake pipe pressure is calculated and a fuel injection amount proportional to the predicted value is calculated. Therefore, although the measurement delay of (3) can be solved, The delays due to the above (1), (2), and (4) cannot be solved, and these mechanical ISCV response delay, intake chamber air filling delay, and fuel transport delay are added in series. However, it is impossible to sufficiently improve the response and the rotation convergence in the idle control.

In view of the above circumstances, the present invention suppresses the influence of a delay to the minimum and increases / decreases the engine torque with good followability to improve the response and rotation convergence of the idle control. The purpose is to provide a method.

[0010]

According to the first aspect of the present invention,
The target value of the physical quantity that can be regarded as having a linear relationship with the indicated torque of the engine is set according to the engine speed at the time of idling, and the passing air amount of the idle control valve that is suitable for the fuel injection amount based on the target value of the physical quantity is It is calculated as the sum of the mass of air accumulated in the chamber and the mass of air sucked into the cylinder, which is equivalently modeled from the downstream side of the throttle valve to immediately before the cylinder, and based on the calculated value of the passing air amount. It is characterized in that the opening of the idle control valve is determined and the opening signal is output to the idle control valve to control the idle speed.

According to a second aspect of the present invention, in the first aspect of the present invention, the physical quantity is a cylinder intake air mass per intake stroke of one cylinder, and the fuel injection quantity is calculated from a target value of the cylinder intake air quantity. In addition to the calculation, the amount of air passing through the idle control valve is calculated as a function of the pressure in the chamber using a gas state equation.

[0012]

According to the first aspect of the present invention, the target value of the physical quantity that can be regarded as having a linear relationship with the indicated torque of the engine is set according to the engine speed during idling, and the fuel injection amount is based on the target value of the physical quantity. The amount of air passing through the idle control valve that matches this fuel injection amount is calculated as the sum of the mass of air accumulated in the chamber by the intake system model and the mass of air sucked into the cylinder. By determining the opening degree of the idle control valve based on the calculated value of the air amount and controlling the idle speed, the fuel delay is eliminated and the influence of the air delay is minimized.

According to a second aspect of the present invention, in the first aspect of the invention, the fuel injection amount is determined by using a physical quantity that can be regarded as having a linear relationship with the indicated torque of the engine as a cylinder intake air mass per one intake stroke of one cylinder. Then, the amount of air passing through the idle control valve is calculated as a function of the pressure in the chamber that changes depending on the opening degree of the idle control valve.

[0014]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 34 relate to an embodiment of the present invention, and FIGS. 1 and 2 are flowcharts of an idle control basic routine,
FIG. 3 is a flowchart of a fuel injection amount calculation subroutine,
FIG. 4 is a flowchart of the I-minute movement amount calculation subroutine,
5 and 6 are flowcharts of the target rotation speed movement amount calculation subroutine, FIG. 7 is a flowchart of the load increase / decrease movement amount calculation subroutine, FIG. 8 is a learning value calculation subroutine flowchart, and FIG. 9 is a water temperature correction value calculation subroutine flowchart. 10 is a flowchart of the atmospheric pressure calculation subroutine, FIG. 11 is a flowchart of the temperature function calculation subroutine, FIG. 12 is a schematic configuration diagram of the engine system, and FIG.
Is a front view of the crank rotor and the crank angle sensor, and FIG.
Is a front view of the cam rotor and the cam angle sensor, FIG. 15 is a circuit configuration diagram of an electronic control system, FIG. 16 is a block diagram of idle control, FIG. 17 is a functional configuration diagram of an ECU relating to idle control, and FIG. 18 is a Ga-Ne map. FIG. 19 is an explanatory diagram of P minute control by the Ga-Ne map, FIG. 19 is an explanatory diagram of I minute control by the Ga-Ne map, FIG. FIG. 22 is an explanatory diagram showing the characteristics of the Ne map, FIG. 22 is an explanatory diagram showing the starting control in the Ga-Ne map, and FIG. 23 is a starting control and the Ga-N.
FIG. 24 is an explanatory view showing the relationship with the e-map, FIG. 24 is an explanatory view showing the relationship between the stroke intake air amount and the intake pipe pressure, FIG. 25 is an explanatory view of the chamber model, and FIG. 29 is an explanatory view showing the rotational speed convergence at the time of D range shift, FIG. 28 is an explanatory view showing the relationship between the strength of P and the rotational speed and intake pipe pressure fluctuation, FIG.
Is an explanatory view showing the rotation fluctuation at the time of starting, FIG. 30 is an explanatory view showing the target value and the actual measured value of the ISC valve passing air amount by the water temperature correction, and FIG. 31 is an illustration showing the target boost pressure and the actual boost pressure at the time of cold start. FIG. 32 is an explanatory diagram showing the rotational speed convergence at the time of turning the power steering, FIG. 33 is an explanatory diagram showing learning with respect to a characteristic change of ISCV, and FIG. 34 is a case where the value of the chamber volume in the arithmetic expression is changed. It is explanatory drawing which shows rotation fluctuation and ISCV opening change.

In FIG. 12, reference numeral 1 denotes an engine (in the figure, a horizontally opposed four-cylinder engine) main body, and an intake manifold 2 is connected to an intake port 2a of a cylinder head 2 of the engine main body 1. A throttle passage 5 is connected to the upstream side of the intake manifold 3 via an air chamber 4. An air cleaner 7 is provided on the upstream side of the throttle passage 5 via an intake pipe 6.
Is attached, and the air cleaner 7 is communicated with an air intake chamber 8 which is an intake port for intake air.

An exhaust pipe 10 is connected to the exhaust port 2b via an exhaust manifold 9, and a catalytic converter 11 is connected to the exhaust pipe 10 and is connected to a muffler 12. On the other hand, a throttle valve 5a is provided in the throttle passage 5, and an intercooler 13 is provided in the intake pipe 6 immediately upstream of the throttle passage 5,
Further, a resonator chamber 14 is interposed downstream of the air cleaner 7 in the intake pipe 6.

Further, an idle control valve (idle speed control valve) for adjusting an idle air amount (idle speed) is provided in a bypass passage 15 which communicates the resonator chamber 14 and the intake manifold 3 and bypasses the upstream side and the downstream side of the throttle valve 5a. Control valve; ISCV) 1
6 is interposed. The ISCV 16 is a high-speed solenoid valve driven by an electronic control unit 50 (ECU; see FIG. 15) described later. In this embodiment, a rotary solenoid is used to adjust the intake air passage area of the bypass passage 15. With the configuration in which the rotary sliders are connected in series, the opening area (valve opening) of the rotary sliders is controlled by duty control.

Further, immediately downstream of the ISCV16,
When the intake pressure is negative, the valve opens and the turbocharger 18
A check valve 17 is installed which is closed when the intake pressure becomes positive by supercharging by.

In the turbocharger 18, a compressor is installed downstream of the resonator chamber 14 of the intake pipe 6, and a turbine is installed in the exhaust pipe 10. Further, a wastegate valve 19 is provided at the turbine housing inlet of the turbocharger 18, and a wastegate valve actuating actuator 20 is connected to the wastegate valve 19.

The waste gate valve actuating actuator 20 is divided into two chambers by a diaphragm, one of which forms a pressure chamber communicating with the waste gate valve controlling duty solenoid valve 21, and the other of which forms the waste gate valve 19. A spring chamber is formed that houses a spring that urges in the closing direction.

The waste solenoid valve controlling duty solenoid valve 21 is interposed in a passage that connects the resonator chamber 14 and the compressor downstream of the turbocharger 18 of the intake pipe 6, and is controlled by the ECU 50. The pressure on the side of the resonator chamber 14 and the pressure on the side of the compressor downstream are adjusted according to the duty ratio of the signal, and the pressure is supplied to the pressure chamber of the waste gate valve operating actuator 20 as control pressure.

That is, the wastegate valve controlling duty solenoid valve 21 is controlled by the ECU 50, and the wastegate valve operating actuator 20 is controlled.
Is operated to adjust the exhaust gas relief by the waste gate valve 19, so that the supercharging pressure by the turbocharger 18 is controlled.

An intake pipe pressure sensor (absolute pressure sensor) 22 is connected to the intake manifold 3 via a passage 23, and an injector 25 is provided immediately upstream of each intake port 2a of each cylinder of the intake manifold 3. Is facing. Further, an ignition plug 26 whose tip is exposed to the combustion chamber is attached to each cylinder of the cylinder head 2, and an igniter 27 is connected to an ignition coil 26 a connected to the ignition plug 26.

The injector 25 includes a fuel tank 2
Fuel is pressure-fed from an in-tank type fuel pump 29 provided inside 8 through a fuel filter 30, and a pressure regulator 31 regulates the fuel pressure to the injector 25.

Further, the air cleaner 7 of the intake pipe 6
An intake air amount sensor 32 such as a hot wire type or a hot film type is interposed immediately downstream of the throttle valve 5a, and a throttle sensor 33 including a throttle opening sensor 33a and an idle switch 33b is connected to the throttle valve 5a. ing.

Further, a knock sensor 34 is attached to the cylinder block 1a of the engine body 1, and a water temperature sensor 36 is exposed to a cooling water passage 35 which communicates the left and right banks of the cylinder block 1a, so that the exhaust pipe 10 is exposed. O at the collecting part of the above exhaust manifold 9
2 Sensor 37 is exposed.

A crank rotor 38 is rotatably mounted on the crank shaft 1b supported by the cylinder block 1a, and a crank angle sensor 39 including an electromagnetic pickup is provided on the outer periphery of the crank rotor 38. Further, a cam rotor 40 connected to the cam shaft 1c of the engine body 1 is provided with a cam angle sensor 41 for discriminating a cylinder, which is composed of an electromagnetic pickup or the like.
Incidentally, the crank angle sensor 39 and the cam angle sensor 4
1 is not limited to a magnetic sensor such as an electromagnetic pickup, but may be an optical sensor or the like.

As shown in FIG. 13, the crank rotor 38 is formed with protrusions 38a, 38b, 38c on the outer periphery thereof, and these protrusions 38a, 38b, 38c form the cylinders (# 1, # 2 and #). Before # 3, # 4 compression top dead center (BTD
C) It is formed at the positions of θ1, θ2, θ3, and in the present embodiment, θ1 = 97 ° CA, θ2 = 65 ° CA, θ3.
= 10 ° CA.

The protrusions of the crank rotor 38 are detected by the crank angle sensor 39, and the BTDC 97
Crank pulse of °, 65 °, 10 ° is 1/2 engine
It is output every rotation (every 180 ° CA). Then, the input interval time of each signal is counted by a timer, and the engine speed is calculated.

Further, as shown in FIG. 14, on the outer periphery of the cam rotor 40, there are projections 40a, 40b for cylinder discrimination,
40c is formed, and the protrusion 40a is formed at the position after compression top dead center (ATDC) θ4 of the # 3 and # 4 cylinders.
b is composed of three protrusions, and the first protrusion is A for cylinder # 1.
It is formed at the position of TDCθ5. Furthermore, the protrusion 40
c is formed by two protrusions, and the first protrusion is A for cylinder # 2.
It is formed at the position of TDC θ6. In this embodiment, θ4 = 20 ° CA, θ5 = 5 ° CA, θ6 = 20 °
It is CA.

When each projection of the cam rotor 40 is detected by the cam angle sensor 41 and the combustion stroke sequence of each cylinder is # 1 → # 3 → # 2 → # 4, this combustion stroke sequence and Cylinder discrimination is made based on the pattern of the cam pulse from the cam angle sensor 41 and the value counted by the counter.

On the other hand, in FIG. 15, reference numeral 50 is an electronic control unit (ECU) 50 for controlling the engine system,
The ECU 50 is mainly composed of two computers, a main computer 51 for performing fuel injection control, ignition timing control and the like, and a dedicated sub computer 52 for performing knock detection processing, and supplies a predetermined stabilizing power to each part. The constant voltage circuit 53 and various peripheral circuits are incorporated.

The constant voltage circuit 53 includes an ECU relay 54.
Is connected to the battery 55 via the relay contact of
A relay coil of the ECU relay 54 is connected to the battery 55 via an ignition switch 56,
When the ignition switch 56 is turned on and the relay contact of the ECU relay 54 is closed, power is supplied to each part, the constant voltage circuit 53 is directly connected to the battery 55, and the O of the ignition switch 56 is turned on.
The power supply for backup is supplied to the backup RAM 61 regardless of N or OFF. A fuel pump 29 is connected to the battery 55 via a relay contact of a fuel pump relay 57.

The main computer 51 has a CPU 5
8, the ROM 59, the RAM 60, the constant voltage circuit 53 regardless of whether the ignition switch 56 is ON or OFF.
Backup RAM 61, which is constantly supplied with backup power from
It is a microcomputer in which an SCI 63, which is a serial communication interface, and an I / O interface 64 are connected via a bus line 65.

The counter / timer group 62 includes various counters such as a free-run counter, a cam angle sensor signal input counting counter, a fuel injection timer, an ignition timer,
For convenience, various timers such as a periodic interrupt timer for generating a periodic interrupt, a timer for measuring an input interval of a crank angle sensor signal, and a watchdog timer for monitoring a system abnormality are collectively referred to for convenience. In addition, various software counters and timers are used.

The sub-computer 52, like the main computer 51, has a CPU 71 and a ROM 7.
2, RAM 73, counter / timer group 74, SCI7
5 and the I / O interface 76 is the bus line 7
7, the main computer 51 and the sub computer 52 are connected to each other by a serial communication line via the SCIs 63 and 75.

The I / O interface 64 of the main computer 51 has an intake port, an intake air amount sensor 32, a throttle opening sensor 33a, and a water temperature sensor 3 at its input ports.
6, the O2 sensor 37, the intake pipe pressure sensor 22, the vehicle speed sensor 42, the atmospheric pressure sensor 44, and the battery 55
The idle switch 33b, the crank angle sensor 39, the cam angle sensor 41, the radiator fan switch 43, the air conditioner switch 45, the shift switch 46 for detecting the shift position of the automatic transmission, etc. are connected while being connected via the / D converter 66. Further, various sensors and switches (not shown) are connected. In the case of a vehicle equipped with a manual transmission (MT vehicle), a neutral switch for detecting the neutral shift position is used instead of the shift switch 46, but the neutral switch may be omitted.

An igniter 27 is connected to the output port of the I / O interface 64, and an ISCV 16, an injector 25, a relay coil of the fuel pump relay 57, and a waste solenoid valve controlling duty solenoid valve 21 are provided as a drive circuit. 67, and various actuators (not shown) are also connected.

On the other hand, the I / O of the sub computer 52
The interface 76 has an input port to which the crank angle sensor 39 and the cam angle sensor 41 are connected, and
The knock sensor 34 is connected via the D / D converter 78, the frequency filter 79, and the amplifier 80. The knock detection signal from the knock sensor 34 is amplified to a predetermined level by the amplifier 80, and then the frequency filter 79. The necessary frequency components are extracted by the A / D converter 78.
At, it is converted into a digital signal and input.

The main computer 51 processes the detection signals from the sensors and performs fuel injection amount control, ignition timing control, idle control, etc., while the sub-computer 52 controls the engine speed and engine load. The sample section of the signal from the knock sensor 34 is set on the basis of, and the signal from the knock sensor 34 is A / D converted at high speed in this sample section to faithfully convert the vibration waveform into digital data, and based on this data Determine whether knock has occurred.

The output port of the I / O interface 76 of the sub computer 52 is connected to the input port of the I / O interface 64 of the main computer 51, and the knock determination result of the sub computer 52 is I / O. It is output to the interface 76. Then, in the main computer 51, when the knocking occurrence determination result is output from the sub computer 52, knock data is read from the sub computer 52 from the serial communication line via the SCI 63, and immediately based on this knock data The ignition timing of the cylinder is delayed to avoid knock.

In such an engine control, in the main computer 51, various jobs relating to signal input processing from sensors and switches, fuel injection control, ignition timing control and idle control are executed by one operating system (OS). Performed efficiently under control. This O
S is various management functions for vehicle control, and
It has an internal strategy closely related to this management function, systematically combines various jobs, and executes various jobs efficiently by processing at equal time intervals.

The idle control by the main computer 51 will be described below. Since the sub computer 52 is a computer dedicated to knock detection processing,
The description of the operation is omitted.

In the idle control according to the present invention, as shown in FIG. 16, the target value of the physical quantity (stroke intake air quantity) which can be regarded as having a linear relationship with the indicated torque of the engine by the PI controller according to the change of the idle speed. And set the fuel injection amount based on this target value, and at the same time as the calculation of the fuel injection amount, the calculation result of the intake system model formula is obtained so as to obtain the cylinder intake air amount that matches this fuel injection amount. Is used to determine the opening degree of the ISCV 16, so that the delay of fuel injection is eliminated and the rotation convergence is improved.

Generally, in order to improve the rotational speed convergence with respect to the load disturbance at the time of idling, a method of using a higher performance controller, improving the followability of the engine torque with respect to the operation amount of the controller, or the like is considered. However, for a rotating body such as a servo motor, which has a good torque followability with respect to the manipulated variable (current), in order to improve the rotational speed convergence with respect to a load disturbance, unless a severe request is made, it is usually required. Since the PID control of 1 is sufficient, the classical PID controller is sufficient if the followability of the engine torque with respect to the operation amount of the controller can be improved.

Therefore, the classical PID is also used in the present invention.
A controller (however, in this embodiment, D control including differential calculation and not susceptible to noise is not used) is adopted, and a target value of a physical quantity, that is, an operation amount of the PI controller, one intake of one cylinder. The stroke intake air amount Ga (unit: mg / cycle) defined by the cylinder intake air mass per stroke is used. This stroke intake air amount Ga can be considered to have a linear relationship with the indicated torque of the engine, and is obtained from a map obtained experimentally using the engine speed as a parameter, as described later.

Then, at the time of idling, the fuel injection amount is calculated based on this stroke intake air amount Ga without measurement delay, and the ISCV opening is calculated using the inverse chamber model formula considering the time delay. As a result, it is possible to improve the followability of the engine torque and realize a drastic improvement in the convergence of rotation compared with the existing idle control, and to reduce the idle speed without deteriorating the feeling due to engine stall or rotation fluctuation. It is possible to reduce the rotation speed and improve fuel efficiency.

That is, as described above, the delay in the idle control is (1) mechanical ISCV response delay,
(2) Delay due to air filling in the intake chamber, (3) Response delay (measurement delay) of the sensor that measures the air amount, (4)
Four factors of the delay of fuel transportation into the cylinder due to the adhesion of fuel to the wall surface of the intake port have a serial effect, but in the present invention, the indicated torque of the engine and the indicated torque of the engine are directly obtained from the engine speed during idling. A target stroke intake air amount defined by the cylinder intake air mass per one intake stroke of one cylinder that can be regarded as having a linear relationship is set, and based on this target stroke intake air amount, the control amount for the ISCV16 along with the fuel injection amount is set. Since the setting is made, the method of measuring the air amount and determining the fuel injection amount at the time of idling is not adopted, and the response delay of the sensor for measuring the air amount in (3) can be completely eliminated. Further, based on the above target stroke intake air amount, the control amount (I
Since the SCV opening) is calculated, the delay due to the air filling in the intake chamber in (2) above can be set to a very small value.

Regarding the mechanical ISCV response delay in (1) and the transport delay in (4), even if a high-speed response ISCV and an injector with little wall fuel adhesion are adopted, these delays are zero. It is impossible to However, in the present invention, the fuel injection amount is set and the control amount for ISCV is set based on the target stroke intake air amount set according to the engine speed.
Mechanical ISCV delay and fuel transport delay will occur in parallel.

Therefore, the target stroke intake air amount is set according to the engine speed during idling, the fuel injection amount is set based on the target stroke intake air amount, and the reverse chamber model is set based on the target stroke intake air amount. IS using the formula
By setting the control amount for the CV16, the delay in the idle control becomes at least 1/4 of the delay in the idle control in which the above-mentioned four factors have a serial (additive) effect in the related art, and the engine torque is drastically reduced. In addition to improving the followability, the problem of destabilization, which is a problem in predictive control, can be completely eliminated.

On the other hand, in the non-idle state, in this embodiment,
The well-known L-Jetro fuel injection control for controlling the fuel injection amount based on the intake air amount measured by the intake air amount sensor 32 is adopted.
As the functional configuration of the (main computer 51), as shown in FIG. 17, a target stroke intake air amount setting unit corresponding to an intake air amount calculation unit 100 and a PI controller corresponding to idle time and non-idle time. 101, normal control / idle control switching unit 102, fuel injection setting unit 103, ISCV passing air amount setting unit 104 using reverse chamber model, ISC
A V opening setting unit 105 is provided as a basic configuration, and further, an engine speed calculation unit 106, a target speed / load change prediction unit 107, an intake pipe pressure detection unit 108, an atmospheric pressure detection unit 109, an ISCV drive unit 110. An injector drive unit 111 is provided.

Then, the intake air amount calculation unit 100 is selected depending on whether the engine is operating in the idle state or the non-idle state.
Calculation of the intake air amount Q based on the signal from the intake air amount sensor 32, and the target value of the stroke intake air amount Ga in the target stroke intake air amount setting unit 101 (target stroke intake air amount) Ga
The setting of set is the normal control / idle control switching unit 102.
And is output to the fuel injection setting unit 103.

In this embodiment, the idle switch 3
When 3b is OFF, various jobs of fuel injection control by the normal L-JETRO system are executed, and when the idle switch 33b is ON (throttle valve 5a is fully closed), it is determined that the engine is in the idle operation state and the idle control is performed. Various jobs are executed, and the normal control / idle control switching unit 102 is a software switch for switching jobs.

Then, the fuel injection setting unit 103 sets the fuel injection amount based on the target stroke intake air amount Gaset at the time of idling, while at the time of non-idling, the fuel injection amount is set based on the intake air amount Q measured by the intake air amount sensor 32. The injection amount is set, and the injector 25 is driven via the injector drive unit 111.

The fuel injection amount during non-idle is set by the intake air amount Q calculated by the intake air amount calculating unit 100 based on the signal from the intake air amount sensor 32 and the crank angle sensor by the engine speed calculating unit 106. The basic fuel injection amount Tp is set from the engine speed Ne calculated based on the signal input interval time from 39 (Tp = K · Q / Ne; K is an injector characteristic correction constant), and the basic fuel injection amount Tp is set.
A well-known technique for determining the final fuel injection amount Ti by correcting the fuel injection amount by various correction terms corresponding to the engine state can be applied.

On the other hand, at the time of idling, the target stroke intake air amount Gasset from the target stroke intake air amount setting unit 101 is used to calculate the fuel injection amount Gf (unit: mg / c by the following equation (1)).
Cycle) is calculated. Gf = Gaset · (F / A) (1) where F / A: target fuel-air ratio and the fuel injection amount Gf calculated by the above equation (1)
Can be converted into a normal basic fuel injection amount Tp by, for example, multiplying by an appropriate coefficient, and the final fuel injection amount Ti similar to that during non-idle can be obtained.

That is, although the amount to be manipulated by the PI control is originally the engine torque, it can be said that there is an approximately first-order relationship with this engine torque. The fuel injection amount, the stroke intake air amount, the intake pipe absolute Pressure etc. are mentioned. In the present embodiment, in the actual control calculation, the stroke intake air amount Ga is used as the operation amount of the PI controller for convenience, but the stroke intake air amount Ga is the fuel injection amount Gf and the target air-fuel ratio (A / Therefore, controlling the stroke intake air amount Ga by the equation (1) is equivalent to setting the manipulated variable for PI control to the fuel injection amount Gf,
In effect, the fuel-driven idle control is used.

In such fuel-driven idle control, even if the ISCV 16 sticks at full opening and the air amount increases, the target stroke set by the fuel injection amount Gf based on the engine speed. Since the intake air amount is given by Gaset, the air-fuel ratio becomes lean and the engine torque does not increase. That is, in the technique of calculating the fuel injection amount by measuring the air amount adjusted by the ISCV like the conventional idle control, if the ISCV 16 is fully opened and stuck, the increase in the air amount is measured. The amount of fuel injection also increases and the engine torque increases, but
The fuel-driven idle control of the present invention ensures safety without causing such a problem.

The setting of the target stroke intake air amount Gaset in the target stroke intake air amount setting unit 101 will be described below. This target stroke intake air amount Gaset is a target rotation speed based on the movement of I component (integral component) in PI control or feed forward control with respect to a map of the stroke intake air amount experimentally obtained using the engine speed as a parameter. It is set by performing movement and load increase / decrease movement. However, as will be described later, the engine speed Ne is the reference speed during cranking (cranking reference speed) N.
Below st, the map value is not used and the intake pipe pressure sensor 2
The target stroke intake air amount Gaset is calculated based on the actual intake pipe absolute pressure (boost pressure) P measured by the intake pipe pressure detection unit 108 based on the signal from 2.

First, the map of the stroke intake air amount will be described. In the idle control according to the present invention, the stroke intake air amount Ga is controlled to change the indicated torque of the engine, and the engine rotational speed Ne at which the indicated torque and the friction torque (friction) are balanced is made equal to the target rotational speed Ne0. The target value of the stroke intake air amount Ga is determined using a map (Ga-Ne map) as shown in FIG.

In FIG. 18, the engine friction at the target engine speed Ne0 during idling and the engine speed N are shown.
The stroke intake air amount Ga0 at e0 is in balance with the indicated torque generated, and if the engine speed Ne deviates from the target speed Ne0, an engine torque proportional to the error is generated. That is, when the stroke intake air amount Ga0 at which the balance between the indicated torque (stroke intake air amount) of the engine and the friction reaches the target rotation speed Ne0 is experimentally obtained, the stroke is reduced from the target rotation speed Ne0. The intake air amount Ga is increased, and the stroke intake air amount Ga is decreased as the rotation becomes higher.

In this way, the stroke intake air amount Ga is given in a downward-sloping map with respect to the engine speed Ne (when the engine speed Ne increases, the stroke intake air amount Ga decreases). Increase the torque,
It is to reduce the indicated torque as the rotation increases,
For example, when the friction suddenly increases due to a sudden increase in load, the engine speed Ne is "Ne0 '" unless the stroke intake air amount Ga remains the target speed Ne0.
However, in this control, the stroke intake air amount rapidly increases to the intersection point Ga1 of the friction and the map, and the engine speed Ne drops only to "Ne1". This is P
The control is for P (proportional) in I control.

The above P component control can greatly improve the transient convergence of the rotational speed with respect to the load disturbance.
The steady-state error cannot be completely zero. Therefore, due to load changes, combustion variations, individual engine differences, etc., the stroke intake air amount (torque shown in the figure) can be obtained only by P.
It is conceivable that the rotational speed at which the friction balances with the target rotational speed does not match the target rotational speed, and it is necessary to control the I component (integral component) in order to accurately converge to the target rotational speed.

That is, as shown in FIG. 19, when the stroke intake air amount Ga indicated by the broken line is “F0” and the point of equilibrium with the friction is equal to the target rotational speed Ne0, the load is increased and fishing is performed. When the confluence point becomes "F1", the engine speed Ne becomes "Ne1". In such a case, FIG.
As shown in (a), the Ga-Ne map is plotted on the horizontal axis (Ne
By moving the balance point F1 ′ to match the target rotational speed Ne0, or, as shown in FIG. 19 (b), the Ga-Ne map is plotted on the vertical axis (G).
The I-minute control can be realized by moving the balance point F1 'in parallel with the target rotational speed Ne0 by moving it parallel to the a-axis).

Theoretically, as shown in FIG. 19B, it is correct to move the Ga-Ne map in the vertical axis direction. However, when moving the map in the vertical axis direction, it may be high depending on the conditions. Since it is necessary to take measures against the decrease in the fuel injection amount due to rotation, in the present embodiment, the map is moved in the horizontal axis direction, and this is the I minute control.

Further, in setting the target stroke intake air amount Gaset, when a known increase in friction and a known increase or decrease in target speed can be expected, such as when the water temperature is low or when the air conditioner is ON, feedforward control is added and all are fed back. I am expecting a better response than relying on it.

That is, when the target rotation speed changes, such as when the water temperature is low or when the air conditioner is on, as shown in FIG. 20, the Ga-Ne map is previously set on the horizontal axis (Ne axis) by the target rotation speed movement amount ΔNe. To move the intersection with the friction to match the target rotational speed at that time. In addition, when the increase or decrease in friction (load) can be predicted to some extent by a sensor or a switch when the water temperature is low or the air conditioner is ON, Ga-
The Ne map is moved in parallel with the vertical axis (Ga axis) by the load increase / decrease movement amount ΔGa.

The target rotational speed movement amount ΔNe and the load increase / decrease movement amount ΔGa are the signal from the water temperature sensor 36, the signal from the radiator fan switch 43, the signal from the air conditioner switch 45, the signal from the shift switch 46, and the battery voltage. Target speed / load change prediction unit 1 based on VB
It is calculated individually in 07 under the following conditions.

[0069]

For example, when the overshoot immediately after the air conditioner is turned on and the undershoot after the air conditioner is turned off are examined, in comparison with the conventional idle control shown in FIG. 26 (b), as shown in FIG. 26 (a) in this embodiment. In addition, the overshoot immediately after the air conditioner is turned on and the undershoot after the air conditioner is turned off are considerably small, and there is no fluctuation in rotation when the air conditioner is normally turned on.

Further, when the rotational fluctuation due to the shift position change of the automatic transmission is examined, when the shift from the N range to the D range, the shift from the D range to the N range, or these shifts are continuously repeated, FIG. In contrast to the rotation fluctuation caused by the conventional idling control shown in (b), in the present embodiment, the rotation fluctuation is small as shown in FIG. 27 (a), and when the shift is made from the D range to the N range, The target rotation speed can be changed gently rather than stepwise. This calculates the load fluctuation (ΔGa) and the rotation speed movement (ΔNe) individually, and changes the load movement amount ΔGa stepwise, but the rotation speed movement amount ΔNe is gently changed to display the Ga-Ne map. This is because they are moved.

Here, the Ga-Ne map basically needs only to be a map in which the stroke intake air amount Ga descends to the right, and as shown in FIG. 21, RA, RB, RC in the low, middle, and high rotation regions.
It is roughly divided into three areas. First, in the RB portion, the stroke intake air amount Ga0 that stabilizes at the target rotation speed is experimentally obtained, and the strength of the inclination of the map here is the strength of P.

The strength of the inclination at the RB portion is an important point where the rotation fluctuation amount due to the load disturbance changes due to this, and as shown in FIGS. 28 (a), (b) and (c), for example, The inclination of the RB part is 0.2 mg / 1r
pm, 0.8 mg / 1 rpm, 2.0 mg / 1 rpm, the power steering was steered, and the rotation fluctuation and the air supply pipe pressure fluctuation were examined. It is understood that the rotation fluctuation becomes smaller as the inclination becomes stronger. However, if the inclination is too strong, the intake pipe pressure fluctuates even in a steady state as shown in FIG. 28 (c), which is not preferable.
The strength of the inclination in the section is appropriately set in consideration of the rotational fluctuation and the intake pipe pressure.

In order to prevent misfire and to obtain smoothness after coasting and racing, the RC section gradually reduces Ga, and the stroke intake air intake amount is "0" in the high rotation range.
I try not to drop it. On the other hand, in the RA part, the graph is curved so as to obtain continuity with the stroke intake air amount at the time of starting (matches with the stroke intake air amount obtained at the time of cranking). Can be said.

The inclination strength of the RA portion above the cranking reference rotation speed Nst is set to be gentler than the inclination of the RB portion, and a map value is not given when the rotation speed is lower than the cranking reference rotation speed Nst. In the starting control described below, the actual stroke intake air amount Ga is calculated from the intake pipe absolute pressure (actual boost pressure; unit kPa) P measured by the intake pipe pressure sensor 22.

That is, in the present embodiment, at the time of starting at the cranking reference speed Nst or less, the execution intake air amount calculated from the actual boost pressure rather than the fuel initiative type which gives the target stroke intake air amount on the Ga-Ne map. The startup control of the D-JETRO method that determines the fuel injection amount from
The control is simplified.

First, the boost pressure P measured by the intake pipe pressure detector 108 is detected by the atmospheric pressure detector 109 by the atmospheric pressure sensor 44.
Atmospheric pressure P0 (unit: kP measured based on the signal from
Assuming that the stroke intake air amount when equal to a) is Gamax, normally, when the engine speed is 0 rpm, the intake pipe internal pressure is atmospheric pressure, so the stroke intake air amount is Gama.
x.

However, as described above, when friction increases, such as when the water temperature is low, the map is moved by the increase in friction, so a theoretically impossible stroke intake air amount is required. In this case,
As shown in 2, if the value of the stroke intake air amount is limited to Gamax, it is necessary to take measures against the occurrence of a region where the map does not fall to the right in the low transfer area, and the load due to water temperature is also a parameter of the map. , Ga-Ne
It is possible to make the map a two-dimensional map,
A large number of maps must be created depending on the water temperature, and consideration must be given so that the inclination of each map does not change and the rotation convergence does not change.

Therefore, in this embodiment, when the cranking reference rotation speed Nst or less, as shown in FIG.
In the a-Ne map, it is calculated from the actual boost pressure P without giving the stroke intake air amount Ga. The ISCV opening in this case is controlled so as to be the target stroke intake air amount at the cranking reference rotation speed Nst, and when the engine rotation speed exceeds the cranking reference rotation speed Nst, the fuel-driven type It naturally leads to idle control, and the air-fuel ratio can be controlled almost theoretically. Here, if the map is moved by the target rotation speed movement amount ΔNe when the water temperature is low, N
The stroke intake air amount is calculated from the actual boost pressure P up to st + ΔNe.

For example, as shown in FIG. 29, in the conventional idle control shown in FIG. 29 (b), a considerable overshoot occurs at the time of starting with respect to the rotation fluctuation at the time of starting.
In this embodiment, as shown in FIG. 29A, the overshoot at the time of starting can be made extremely small.

To specifically set the target stroke intake air amount Gaset from the above Ga-Ne map, Ga-Ne
Instead of actually moving the map value of the map, I am trying to move the map axis.

That is, specifically, the Ga-Ne map used in the target stroke intake air amount setting unit 101 is the actual engine speed Ne based on the signal from the crank angle sensor 39.
Is the movement amount FBN of I minute control with respect to the target rotation speed NSET
Is added, and the target rotation speed movement amount Δ by the feedforward control from the target rotation speed / load change prediction unit 107 is added.
Map instruction rotation speed IRPM (= Ne + F)
It is configured as a basic intake air amount map with BN−ΔNe) as a parameter.

When the map instruction rotational speed IRPM exceeds the cranking reference rotational speed Nst, the basic stroke intake air amount Gabase obtained by referring to this basic intake air amount map is also changed to the target rotational speed / load change. The target stroke intake air amount Gaset is set by adding the load increase / decrease movement amount ΔGa by the feedforward control from the prediction unit 107.

Further, when the map instruction rotational speed IRPM is equal to or lower than the cranking reference rotational speed Nst, the intake pipe pressure detecting section 108 is based on the signal from the intake pipe pressure sensor 22.
The actual stroke intake air amount Ga is calculated from the actual boost pressure P detected in step S1, and this actual stroke intake air amount Ga is set as the target stroke intake air amount Gaset.

As shown in FIG. 24, the stroke intake air amount Ga
It has been experimentally confirmed that the boost pressure P and the boost pressure P have a simple first-order relationship, as shown in the following equation (2). In the embodiment, it is assumed to be constant during idle control. Ga = K1 · P−K2 (2) However, K1 and K2: constants In detail, if the cylinder volume is Vcy, the gas constant is R, and the intake temperature is T, the following equation (2) is It can be expressed as in equation 3).

Ga = K3 · P · Vcy / (R · T) −K2 (3) where K3: constant

By using the above equation (3), the actual intake air amount actual Ga corresponding to the actual boost pressure P can be calculated, and the ISCV passing air amount setting unit 10 described below can be calculated.
In 4, the target boost pressure Pset corresponding to the target stroke intake air amount Gaset can be calculated.

Here, although the factor of the intake air temperature T is included in the above equation (3), in this embodiment, L is set when the engine is not idle.
Since the fuel injection control by the JETRO system is adopted, the intake air temperature sensor is not provided, and the air flow rate passing through the throttle valve 5a can be regarded as 0 during idling, and the temperature of the air passing through the ISCV 16 is considered. Since the cooling water passage is right next to the air passage part of the ISCV16, the intake air temperature T is considered to be equal to the cooling water temperature TW, and the temperature function RT
Is replaced by the temperature function M shown in the following equation (4). M = R ・ TW (4)

As described above, the target stroke intake air amount Ga
When set is determined, this target stroke intake air amount Gas
As described above, et is output to the fuel injection setting unit 103 via the idle control switching unit 102 and the fuel injection amount G
f is calculated, and at the same time, the ISCV passing air amount setting unit 10
4 and the passing air amount Qisc of the ISCV 16 is set.

ISCV passing air amount setting unit 104 and IS
In the CV opening degree setting unit 105, after a very short time represented by Δt, the ISC of the intake air mass into the cylinder per actual intake stroke is made to match the target stroke intake air amount Gaset.
The opening degree of V16 (duty ratio of the drive pulse signal of ISCV16) is set, and IS is set via the ISCV drive unit 110.
Drive the CV16.

In this case, the control to the target stroke intake air amount Gaset as the instruction value of the PI controller may be considered to be the control to the target boost pressure Pset, and the stroke intake air amount Ga is set.
In order to set the target value Gaset to the target value Gaset, the opening degree of the ISCV 16 may be controlled to change the intake pipe pressure P to the target boost pressure Pset.

Therefore, the ISCV passing air amount setting unit 10
4, the ISCV passing air amount Qis such that the actual boost pressure P matches the target boost pressure Pset after the time Δt.
c is calculated using the inverse chamber model equation described below.

That is, when the inhalation system is simplified and considered,
There is a volume in the path from the downstream of the throttle valve 5a to just before the cylinder to the intake port 2a, and as shown in FIG. 25, a chamber model having this portion as a chamber is conceivable. In this chamber model, considering the input / output relationship of air into the chamber, Qisc: ISCV passing air amount (unit: g / s) Qcy: Cylinder inflow air amount (unit; g / s) Wm: Chamber air mass (Unit: g) As a result, the air flow rate through the throttle is 0 during idling.
Therefore, the air mass accumulated in the intake chamber at Δt time, that is, the air mass Wm in the chamber, is determined by the amount of air passing through the ISCV 16 and flowing into the chamber at Δt time, that is, the ISCV passing air amount Qisc, and the Δt time. It is the difference between the mass of air that flows out of the chamber and is sucked into the cylinder, that is, the cylinder inflow air amount Qcy.
It can be expressed by equation (5). (Wm (t + Δt) −Wm (t)) / Δt = Qisc−Qcy (5) where Δt is a calculation cycle (for example, 10 ms)

The above equation (5) is an equation generally called a chamber model equation. If this equation (5) is reversed, ISCV
Is the sum of the air mass accumulated in the chamber due to the pressure P in the intake chamber changing to the target boost pressure Pset in Δt time and the air mass sucked in the cylinder in Δt time. It can be considered that the gas is consumed, and the ISC valve passing air amount Qisc can be obtained by the following equation (6) (reverse chamber model equation) by applying the gas state equation. Qisc = (P (t + Δt) −P (t)) · V / (M · Δt) + Qcy (6) where V: chamber volume M: temperature function substituting R · T

Further, the cylinder inflow air flow rate Qcy is the same as the engine speed Ne described above, as shown in the following equation (7).
It can be obtained from the intake air amount Ga calculated by the equation (3). Qcy = N ・ Ga ・ (Ne / 2) ・ (1/60) (7) where N: number of cylinders

The term P (t) in the above equation (6) is the actual boost pressure P at a certain time t, and the term P (t + Δt) is the target stroke intake air amount Gaset after Δt time. The corresponding target boost pressure Pset can be given by the following equation (8) which is the inverse of the above equation (3). Pset = (Gaset + K2) · M / (K3 · Vcy) (8)

As described above, by obtaining the ISCV passing air amount Qisc by the inverse chamber model formula, the influence of the delay of the air filling into the chamber can be made minute, and the actual stroke intake after a minute time Air amount Ga is PI
It is possible to accurately match the indicated value of the controller.

In the ISCV opening setting section 105, the ISCV
ISC from the mass flow rate of the air passing through 16 at the basic temperature
The V opening (duty ratio) is set. The ISCV passing air amount Qisc calculated by the above equation (6) is a mass flow rate,
When the intake air temperature changes, it is necessary to correct the air temperature,
As described above, in this embodiment, the intake air temperature T is substituted by the cooling water temperature TW, so the basic temperature Tba during setting is set.
The ratio of the cooling water temperature TW to se is used as the water temperature correction value HIQ (HIQ = TW / Tbase), the mass flow rate ISCV passing air amount Qisc is corrected, and converted into Qisc 'as shown in the following equation (9). . Qisc '= Qisc · HIQ (9)

The target value and the actual measurement value of the passing air amount of the ISCV 16 by the water temperature correction are shown in FIG. 30A, and the target value of the passing air amount of the ISCV 16 is compared with FIG. 30B without the water temperature correction. It can be seen that the measured values are almost equal. Further, as shown in FIG. 31, the target boost pressure and the actual boost pressure are substantially the same even at the low temperature start at -10 ° C., and there is no problem even if the intake temperature T is replaced with the cooling water temperature TW, and the start is performed. Since it is stable at the target rotation speed immediately afterward, the low temperature startability is also good.

The ISCV passing air amount Qisc 'converted by the above equation (9) is the valve opening degree of ISCV16, that is, IS.
Duty ratio DUTY of pulse signal for driving CV16
And the differential pressure Pi before and after the ISCV 16 and the duty ratio DUTY can be expressed by the following equation (10) using the two-dimensional function f. DUTY = f (Pi, Qisc ') (10) where Pi = P0-P

Since the two-dimensional function f is complicatedly related to the structure of the ISCV16 and is difficult to obtain theoretically, specifically, the measured value which is the result of the characteristic experiment of the ISCV16 is calculated as the differential pressure Pi. And the ISCV passing air amount Qisc 'are used as parameters to form a two-dimensional map, and the duty ratio DUTY is obtained by referring to the two-dimensional characteristic map.

The duty ratio D set in this way
Since UTY is expected to improve responsiveness, it is not necessary to set the data quite finely as in the conventional idle control, and the number of bits of the duty ratio can be reduced (for example, 10 bits → 8 bits). . Therefore, the number of bits handled by the electronic circuit for driving the ISCV 16 is reduced, which contributes greatly to the reduction of the gate array in the ECU 50, and the cost can be reduced without increasing the equipment space.

FIG. 32 shows that when the power steering is gently rotated (see circled number 1 in the figure), and fast rotation is given near full steering (see circled number 2 in the figure), the lock is quickly released. When steering to the lock (circle number 3 in the figure)
32), the control cycle is reduced by reducing the number of bits of the duty ratio DUTY, as shown in FIG. 32A, in contrast to the conventional idle control shown in FIG. 32B. Although it is rough, it can be said that the rotational fluctuation can be suppressed to a very small value, the fluctuation of the excess air ratio λ is obviously small, and the air-fuel ratio controllability is excellent.

Further, in order to cope with the case where carbon adheres to the ISCV 16 and the characteristic of the valve changes with respect to the duty ratio DUTY obtained from the above two-dimensional map, the above two-dimensional map value is used as a basic duty ratio.
As shown in the following equation (11), the final duty ratio DUTYisc is obtained by correcting the learning value DUTYLR. DUTYisc = DUTY + DUTYLR (11)

FIG. 33 shows the effect of learning correction on the characteristic change when carbon adheres to the ISCV 16, and as shown in FIG. 33 (a), the target boost pressure and the actual boost pressure are different when carbon is not deposited. When carbon is deposited from the matched state and there is no learning correction, FIG.
As shown in (b), the target boost pressure and the actual boost pressure do not match and the excess air ratio λ shifts to the rich side, but the engine speed substantially matches the normal initial state.

When learning correction is performed in this state, the result shown in FIG.
As shown in (c), the target boost pressure and the actual boost pressure substantially match, and the excess air ratio λ also shows a value almost equal to the value in the normal initial state.

For the sake of simplicity, the ISCV characteristic map is
It is possible to make a one-dimensional map using only the ISCV passing air amount Qisc 'as a parameter, and it can be expected to simplify the processing, but the negative pressure characteristics of the ISCV16 are not hindered when operating at normal temperature and pressure. It is necessary to give sufficient consideration to changes in the.

Further, in a system having no atmospheric pressure sensor, the differential pressure Pi before and after ISCV16 cannot be accurately obtained, but the output of the intake pipe pressure sensor is in the state before the engine is started when the system power is turned on. Since the atmospheric pressure P0 is equivalent, the atmospheric pressure P0 can be measured before the engine is started, and the boost pressure is 50 during idle.
Since it is less than or equal to kPa, it can be considered that it is not so much affected by the atmospheric pressure P0 (in the characteristic map of ISCV16, almost 50 kPa or less is almost the same value). After that, the differential pressure Pi before and after the ISCV 16 may be obtained with the atmospheric pressure kept constant.

Here, the chamber volume V in the above equation (6) (inverse chamber model equation) is a constant determined by the actual shape of the intake system in the equation, but is ISCV in control.
It is the gain of the passing air amount Qisc, the ISCV passing air amount Qisc is changed by changing the value of the chamber volume V in the arithmetic expression, and the responsiveness of the ISCV16 by the duty ratio DUTYisc determined from the equations (9) to (11). Can be determined.

For example, as shown in FIGS. 34 (a), (b), and (c), V = 250 cc, V = 1000 cc, V = 2
The change in the engine speed and the change in the swing range of the duty ratio DUTYisc when changed to 500 cc,
The larger the value of the chamber volume V, the larger the fluctuation range of the duty ratio DUTYisc. However, since the chamber volume V is the gain of Qisc, if it is set too small, the duty ratio DUTYisc becomes as shown in FIG.
Although the swing width of c is small, the responsiveness deteriorates, and the rotation convergence when the load changes is deteriorated.

Further, if the chamber volume V is made too large, it becomes too sensitive and the duty ratio DUTYisc swings widely as shown in FIG. 34 (c), which eventually causes a valve suction noise. (It should be noted that the rotation is stable even if the duty ratio DUTYisc largely fluctuates in this way). In practice, the fluctuation range of the duty ratio DUTYisc is 1 as shown in FIG.
It can be said that there is no problem if it is within 0%.

That is, by treating the chamber volume V in the above-mentioned inverse chamber type as if it were a variable,
It can be set as a setting constant that determines the responsiveness of the ISCV 16. If this is called a virtual chamber volume V ′, this virtual chamber volume V ′ is specifically a chamber volume V determined by the shape of the intake system. Can be represented by a variable (valve response coefficient) r.

Therefore, the above equation (6) for obtaining the ISCV passing air amount Qisc is replaced by the following equation (12), and the responsiveness of the ISCV 16 can be set by changing the value of the valve response coefficient r. In the present embodiment, the valve response coefficient r is, for example, a value of about r = 0.5 to 2, but it is treated as r = 1. At this time, the following equation (12) matches the ordinary reverse chamber equation To do. Qisc = (P (t + Δt) -P (t)) / Δt · r · V / M + Qcy (12)

Next, each job related to idle control will be described with reference to the flowcharts of FIGS.

In the present embodiment, the ISCV 16 is duty-controlled with a job of every 10 ms as a basic routine, and a job (for example, a crank) executed at a predetermined timing based on the target stroke intake air amount Gaset set in this basic routine. The fuel injection amount Gf is calculated by the angle signal synchronization job).

Each parameter used in the basic routine every 10 ms is calculated every 50 ms and 250 ms to obtain R.
Stored at a predetermined address of AM60, 50m
The I-minute movement amount FBN and the target rotation speed movement amount ΔNe are calculated for each job for each s, and the learning value DUTYLR and the water temperature correction value HI are calculated for each job for every 250 ms.
Q, atmospheric pressure P0, and temperature function M are calculated.

Before explaining the basic routine every 10 ms, each subroutine for calculating each parameter used in this basic routine will be described.

In the I minute movement amount calculation subroutine of FIG. 4 executed every 50 ms, the following (1) is executed in step S201.
When all the execution conditions of (4) to (4) are satisfied, that is, it is determined whether or not it is a normal idle time. (1) The engine is not stopped. (2) The engine speed Ne is higher than the target speed NSET and lower than the set speed (for example, NSET-200 rpm). (3) The shift position of the automatic transmission is in the N range or the P range (in the case of MT vehicles, the shift position is neutral). (4) The set time has elapsed after the idle switch 33b was turned on.

If at least one of the above conditions is not satisfied, the routine is exited. If all the conditions are satisfied, the process proceeds from step S201 to step S202 and subsequent steps to determine the actual engine speed Ne and the target. The error from the rotation speed NSET is integrated stepwise, and the I-minute movement amount FBN is calculated according to the amount.

Therefore, in step S202, it is checked whether the actual engine speed Ne based on the signal from the crank angle sensor 39 is equal to or higher than the target engine speed upper limit value NSET1. Ne ≧ NSE
In the case of T1 (when the actual engine speed Ne is equal to or higher than the upper limit value), the process proceeds from step S202 to step S203, and the variable IDFE for accumulating the rotational speed error is rewritten with a value obtained by subtracting the set value A (IDFE ← IDFE-A), the process proceeds to step S206.

In step S202, Ne <NSET1
If (the actual engine speed Ne has not reached the upper limit value), the process proceeds from step S202 to step S204 to check whether the actual engine speed Ne is lower than the target engine speed lower limit value NSET2, and Ne ≧ NSET2. In the case of (the actual engine speed Ne is within the upper and lower limit allowable range set in advance for the target speed NSET), the value of the variable IDFE is held and the routine is exited, and Ne <NSET2 (When the actual engine speed Ne is lower than the target engine speed lower limit value NSET2), the routine proceeds from step S204 to step S205, where the variable I
The variable IDFE is rewritten with a value obtained by adding the set value B to DFE (IDFE ← IDFE + B), and the process proceeds to step S206.

In step S206 and subsequent steps, it is checked whether or not the value of the variable IDFE, that is, the rotational speed error is within a preset range, and the I-minute movement amount FB is determined according to the value of the variable IDFE.
Calculate N. That is, in step S206, the variable IDFE
Is greater than or equal to the set value C, and if IDFE ≧ C, the amount of movement of I minutes is small and is too far from the lower limit side. Therefore, in step S207, the set value D from the previous I minute movement amount FBN is set. Is subtracted to increase the movement amount FBN by I in the negative direction (FBN ← FBN-D), the variable IDFE is reset to the initial value in step S210, and then the routine is exited.

On the other hand, if IDFE <C in step 206, the process branches from step S206 to step S208 to check whether or not the variable IDFE is smaller than the set value E, and if IDFE ≧ E, the present The routine exits from step S208 to hold the movement amount of I
In the case of E, the amount of movement of I is excessive and is too far from the upper limit side. Therefore, the process proceeds from step S208 to step S209, and the set value F is added to the previous amount of I minute movement FBN to add I amount of movement FBN. Is increased (FBN ← FBN + F), the variable IDFE is reset in step S210, and the routine exits.

Next, the target rotational speed movement amount calculation subroutine of FIGS. 5 and 6 will be described. As described above, the target rotational speed movement amount ΔNe is calculated according to the states of the cooling water temperature TW, the air conditioner switch 45, the battery voltage VB, and the shift switch 46. In this subroutine, the water temperature movement amount ΔNeTW depending on the cooling water temperature TW. Of the air conditioner movement amount ΔNeACON depending on the state of the air conditioner switch 45 and the voltage movement amount ΔNeVB depending on the battery voltage VB, the maximum one is set as the target rotation speed movement amount ΔNe, and when it is “0”, the shift switch 46 shifts the gear. Machine movement amount ΔNe
D is used as the target rotation speed movement amount ΔNe.

Therefore, first, in step S301, the map is referred to based on the cooling water temperature TW, and the water temperature movement amount ΔNeTW is calculated.
Is set, and in step S302, this water temperature movement amount ΔNeTW is set as the target rotation speed movement amount ΔNe (ΔNe ← ΔNeTW).
The map of the water temperature movement amount ΔNeTW shows that the value of the water temperature movement amount ΔNeTW increases as the water temperature decreases, and as shown in the flowchart, from the maximum value in the vicinity of TW = −30 ° C to TW = 0 ° C. The characteristic is such that it gradually decreases to TW = 80 ° C and then becomes 0 at TW = 80 ° C.

Next, in step S303, the air conditioner movement amount ΔNeACON is set according to the operating condition of the air conditioner.
That is, the air conditioner switch 45 is turned on in step S303.
Whether the air conditioner switch 45 is ON, the process proceeds to step S304, and the previous air conditioner movement amount ΔNe
Air conditioner movement amount ΔNeACON by adding the set value KS to ACON
Is increased (ΔNeACON ← ΔNeACON + KS), and it is checked in step S305 whether the air-conditioner movement amount ΔNeACON has reached the upper limit value (for example, 100 rpm), and the upper limit value or less (ΔNeACON
If NeACON ≤ 100 rpm, jump to step S309 and reach the upper limit (ΔNeACON> 100rp
m), the air conditioner movement amount ΔNeACON is set to the upper limit value in step S306, and the flow advances to step S309.

As a result, the air conditioner switch 45 is turned off.
When the air conditioner compressor drive load is applied from F to ON, the air conditioner movement amount ΔNeACON is gradually increased by the set value Ks in each calculation cycle until the upper limit value is reached, and the air conditioner movement amount ΔNeACON is gradually increased to stabilize the controllability. I am trying to change. After reaching the upper limit value, the air conditioner movement amount ΔNeACON is held at the upper limit value.

On the other hand, if it is determined in step S303 that the air conditioner switch 45 is OFF, the process proceeds to step S307 to check whether the air conditioner movement amount ΔNeACON has reached 0. If it has reached 0 (ΔNeACON ≦ 0), Jump to step S309 and when it has not reached 0 (ΔNeACON>
0), in step S308 the previous air conditioner movement amount ΔNeACON
The set value LS is subtracted from the air conditioner movement amount ΔNeACON to decrease (ΔNeACON ← ΔNeACON-LS), and step S
Proceed to 309.

That is, when the air conditioner switch 45 is switched from ON to OFF and the air conditioner compressor drive load is released, the air conditioner movement amount ΔNeACON is gradually decreased by the set value LS until it reaches 0, thereby gradually reducing the air conditioner movement amount ΔNeACON. In the same way, the controllability is stabilized.

In step S309, the air conditioner movement amount ΔNe
ACON is compared with the target rotation speed movement amount ΔNe depending on the cooling water temperature TW in step S302 to check the magnitude relationship. If ΔNe ≧ ΔNeACON, the process jumps to step S311, and if ΔNe <ΔNeACON, step S310.
Then, the air conditioner movement amount ΔNeACON is set to the target rotation speed movement amount ΔN.
As e (ΔNe ← ΔNeACON), the process proceeds to step S311.

In step S311, the voltage shift amount ΔNeVB is set by referring to the map based on the battery voltage VB.
As shown in the figure, the voltage shift amount ΔNeVB increases as the battery voltage VB decreases, and becomes ΔNeVB = 0 when VB = 13V or higher. This voltage transfer amount ΔNeVB
After setting, proceed to step S312 and proceed to step S3 above.
Comparing the voltage movement amount ΔNeVB at 11 and the target rotation speed ΔNe set in the previous step (the larger one of the water temperature movement amount ΔNeTW and the air conditioner movement amount ΔNeACON),
If ΔNe ≧ ΔNeVB, jump to step S314,
If ΔNe <ΔNeVB, in step S313, the voltage movement amount ΔNeVB is set as the target rotation speed movement amount ΔNe (ΔNe
← ΔNeVB), and proceeds to step S314.

At step S314, the target rotational speed movement amount ΔN
Whether e is "0", that is, the cooling water temperature TW is 80 ° C.
With the above, the air conditioner switch 45 is OFF, the battery voltage VB is 13 V or more, and the water temperature moving amount ΔNeTW, the air conditioner moving amount ΔNeACON, and the voltage moving amount ΔNeVB are all 0.
If ΔNe ≠ 0, the water temperature transfer amount ΔNeT
The routine exits with the maximum value of W, air conditioner movement amount ΔNeACON, and voltage movement amount ΔNeVB set as the target rotation speed movement amount ΔNe.

On the other hand, if ΔNe = 0 in step S314, the process proceeds from step S314 to step S315 to set the transmission movement amount ΔNeD based on the signal from the shift switch 46 (neutral switch in the case of MT vehicle). To do. That is, in step S315, the shift position of the transmission is N
Whether the range (including the P range) is checked, and if it is the N range, the process proceeds to step S316, and the previous transmission movement amount ΔNe
The set value MS is subtracted from D to decrease the transmission movement amount ΔNeD (ΔNeD ← ΔNeD-MS), and in step S317, the transmission movement amount ΔNeD is set to a lower limit value (for example, -100rp).
m) is checked, and the value is lower than the lower limit (ΔNeD ≧ -1
00 rpm), jump to step S321. If the lower limit is reached (ΔNeD <-100 rpm), step S3
At 18, the transmission movement amount ΔNeD is set to the lower limit value, and the process proceeds to step S321.

As a result, when the shift position of the transmission is shifted from the D range (including 1, 2, and R range) to the N range and the drive load is released, the transmission movement amount ΔNeD is set to the lower limit value (-100 rpm). ) Is gradually decreased by the set value MS until the transmission amount ΔNeD is gradually decreased to stabilize the controllability. Then, at this time, each movement amount ΔNeTW, ΔNeACON, ΔNe
VB is all 0, and the transmission movement amount ΔNeD for setting the rotation speed movement amount ΔNe reaches the lower limit value and then is held at the lower limit value.

On the other hand, if the shift position of the transmission is in the D range in step S315, the process proceeds to step S319 to check whether the transmission movement amount ΔNeD has reached 0, and when it has reached 0 ( ΔNeD ≧ 0), jump to step S321, and when it does not reach 0 (ΔNeD <0), in step S320, the set value NS is added to the previous transmission movement amount ΔNeD to increase the transmission movement amount ΔNeD ( ΔNeD ← ΔN
eD + NS), and proceeds to step S31.

That is, when the shift position of the transmission is shifted from the N range to the D range and a driving load is applied, the transmission movement amount ΔNeD is gradually increased by the set value NS until it reaches 0, whereby the transmission movement is changed. The amount ΔNeD is gradually increased to similarly stabilize the controllability.

Then, in step S321, the transmission movement amount Δ
Let NeD be the target rotational speed movement amount ΔNe (ΔNe ← ΔN
e) Exit the routine.

In the load increase / decrease movement amount calculation subroutine of FIG. 7, in step S401, the water temperature load movement amount ΔGaTW (map value) based on the cooling water temperature TW and the air conditioner load movement amount based on the air conditioner operation (air conditioner switch 45 is ON). ΔGaACON, automatic transmission load (1, 2, D, R range)
Transmission load movement amount ΔGaD based on, voltage load movement amount ΔGaVB (map value) based on battery voltage VB, radiator fan operation (radiator fan switch 43 is ON)
Radiator fan load movement amount ΔGaRAD based on the above is added to increase / decrease load movement amount ΔGa (ΔGa ← ΔGaTW + Δ
GaACON + ΔGaD + ΔGaVB + ΔGaRAD), exit the routine.

On the other hand, FIG. 8 is a learning value calculation subroutine executed every 250 ms. In step S501, it is determined whether all the following conditions (1) to (6) are satisfied and the learning condition is satisfied. To determine. (1) The engine is not stopped. (2) The shift position of the automatic transmission is the N range or the P range. (3) The set time has elapsed after the idle switch 33b was turned off. (4) Load increase / decrease movement amount ΔGa = 0 (5) The engine speed Ne falls within the upper and lower limit allowable range (NSET1 ≧ Ne ≧ N) preset with respect to the target speed NSET.
SET2). (6) Learning has not been completed (learning flag F is not set).

If any of the conditions is not satisfied, the routine is exited. If it is determined that all conditions are satisfied and learning is possible, the process proceeds to step S502, and the target boost pressure Pset and the actual boost pressure are set. Difference from P (Pse
t-P) is compared with a set value G (plus value) that is an allowable value on the lower limit side, and if (Pset-P) ≧ G, then IS
Since the valve opening may be smaller than the indicated value of the duty ratio DUTYisc due to carbon or the like adhering to the CV 16, the process proceeds from step S502 to step S503 to count the number of times the allowable value is exceeded. The counter DTYCT (a counter that takes a positive or negative value) is incremented (DTYCT ← DTYCT + 1), and the process proceeds to step S506.

On the other hand, in step S502, (Pset-
If P) <G, the above steps S502 to S5
After branching to 04, the difference (Pset-P) between the target boost pressure Pset and the actual boost pressure P is compared with a set value H (minus value) that is an allowable value on the upper limit side, and (Pset-P) ≧ H In this case, the routine is exited to maintain the current learning value DUTYLR because of the allowable range (Pset-P) <H, and the duty ratio DUTYisc is indicated due to variations in the valve opening area of ISCV16 during production. Since it may be larger than the value, the counter DTYCT is counted down (DTYCT ← DT) in step S505.
YCT-1), and proceeds to step S506.

At step S506, the target boost pressure Pse
The set value I (plus value) and the value of the counter DTYCT for determining whether the number of times the difference between t and the actual boost pressure P (Pset-P) exceeds the lower limit allowable value is equal to or more than the set number. Compare. Then, when DTYCT ≧ I,
It is determined that the actual boost pressure P has deviated from the lower limit control range to the target boost pressure Pset because the valve opening (valve opening area) of the ISCV 16 has become smaller than the instruction value of the duty ratio DUTYisc due to carbon deposition or the like. Then, in step S507, the current learning value DUTYLR stored in the backup RAM 61 is increased by the set value D1 (DUTYLR to correct the duty ratio DUTYisc in the direction of increasing the valve opening of the ISCV16). ← DUTYLR + D1), step S5
At 10, the learning flag F for indicating that the learning value DUTYLR has been rewritten is set (F ← 1) and the routine exits.

In step S506, DTYCT <
In the case of I, whether the number of times the difference (Pset-P) between the target boost pressure Pset and the actual boost pressure P exceeds the allowable value on the upper limit side is equal to or more than the set number of times by branching from step S506 to step S508. The set value J (minus value) for discriminating is compared with the value of the counter DTYCT, and the DTY
If CT ≧ J, exit the routine to hold the current learning value DUTYLR, and if DTYCT <J, ISC.
It is determined that the actual boost pressure P has deviated from the control range on the upper limit side to the target boost pressure Pset because the valve opening of V16 becomes larger than the instruction value of the duty ratio DUTYisc, and the duty ratio is determined in step S509. DUTYis
The current learning value DUTYLR is decreased by the set value D1 in order to correct c in the direction of decreasing (direction of decreasing the ISCV16 valve opening) (DUTYLR ← DUTYLR-
D1) Exit the routine through step S510 described above.

The counter DTYCT and the learning flag F are initially set to "0" at the time of system initialization, and as described above, the learning flag F is referred to at the beginning of this learning value calculation subroutine.
The rewriting of LR is rewritten only once after the ignition switch 56 is turned on until it is turned off.

Further, in the water temperature correction value calculation subroutine of FIG. 9, in step S601, the cooling water temperature TW detected based on the signal from the water temperature sensor 36 at every predetermined timing.
Is divided by the basic temperature Tbase, the water temperature correction value HIQ is calculated (HIQ ← TW / Tbase), and the routine is exited.

Further, in the atmospheric pressure calculation subroutine of FIG. 10, in step S701, the atmospheric pressure P0 is measured based on the signal from the atmospheric pressure sensor 44, and the routine is exited.
In the temperature function calculation subroutine of step S801, the gas constant R is multiplied by the cooling water temperature TW from the water temperature sensor 36 to calculate the temperature function M (M ← R · TW), and the routine is exited.

When each parameter is calculated as described above, in the basic routine every 10 ms, step S101
Then, from the ROM 59, constants K3, K2, cylinder volume Vc
A known fixed value such as y is read out and the RAM 60
Value of the temperature function M calculated in the 250 ms job is read from the above, and the actual intake air amount Ga is calculated by the above equation (3) using these values and the actual boost pressure P measured by the intake pipe pressure sensor 22. Do (Ga ← (K3 ・ Vcy / M)
-P-K2).

Next, in step S102, the actual engine speed Ne calculated based on the signal input interval time from the crank angle sensor 39 is added to the I-minute movement amount FBN calculated in the 50 ms job, and further, Also 50ms
The target rotation speed movement amount ΔNe calculated in the job is subtracted to calculate the map instruction rotation speed IRPM (IRPM ← Ne
+ FBN-ΔNe).

In a succeeding step S103, the basic stroke intake air amount Gabase is set by referring to the map of the basic stroke intake air amount using the map instruction rotational speed IRPM as a parameter. Next, in step S104, the target stroke intake air amount Gase is added to the basic stroke intake air amount Gbase by adding the load increase / decrease movement amount ΔGa calculated in the 50 ms job.
t is calculated (Gaset ← Gabase + ΔGa), and the process proceeds to step S105.

Then, when the routine proceeds to step S105, the target boost pressure Pset is calculated by the aforementioned equation (8) using the target stroke intake air amount Gaset and the fixed values K2, K3 and Vcy read from the ROM 59 ( Pset ←
(Gaset + K2) * M / (K3 * Vcy)).

In the following step S106, the above step S102
The map instruction rotational speed IRPM calculated in step 1 is compared with the cranking reference rotational speed Nst to determine whether to perform normal idle control or startup control in an extremely low rotational speed range during cranking. Then, if IRPM ≦ Nst and it is determined that the control is at the start in the extremely low rotation speed range, the process proceeds to step S107,
The execution stroke intake air amount Ga calculated in step S101 is set as the target stroke intake air amount Gaset (Gaset ← G
a), the process proceeds to step S108. On the other hand, the above step S106
If it is determined that IRPM> Nst (normal idle control), the process jumps to step S108.

At the time of starting control in the extremely low speed range, the above step S107 is carried out, and at the time of normal idle control, the above step S104 is carried out.
The target stroke intake air amount Gaset calculated by
3 is stored in 60 and is executed at a predetermined timing.
Is referred to in the fuel injection amount calculation subroutine. In this fuel injection amount subroutine, in step S151, the target stroke intake air amount Gaset is multiplied by the target fuel air ratio F / A to calculate the fuel injection amount Gf (Gf ← Gaset · (F /
A)), exit the routine.

Then, in the basic routine, the above steps
When the process proceeds from step S106 or step S107 to step S108, the cylinder inflow air amount Qcy required to calculate the ISCV passing air amount Qisc is calculated from the above equation (7) (Qcy ← N.Ga.Ne / 2). , Go to step S109.

In step S109, the target boost pressure Pset calculated in step S105, the cylinder inflow air amount Qcy calculated in step S108, the temperature function M calculated in the 250 ms job and stored in the predetermined address of the RAM 60, the ROM 59. By using the value of the chamber volume V stored in the and the actual boost pressure P measured by the intake pipe pressure sensor 22, the ISCV passing air amount Qisc is calculated from the above equation (6) (Qisc ← (Pset-P )
・ V / (Δt · M) + Qcy).

Then, the process proceeds to step S110, and the above step is executed.
The ISCV passing air amount Qisc calculated in S109 is set to 250
When the temperature is corrected by the water temperature correction value HIQ calculated by the ms job and stored in the RAM 60 and converted into Qisc ′ (Qisc ′ ← Qisc · HIQ), in step S111,
RAM calculated by this Qisc 'and 250ms job
A basic duty ratio DUTY is set by referring to the basic duty ratio map using the differential pressure Pi before and after the ISCV 16 stored in 60 as a parameter.

After setting the basic duty ratio DUTY in step S111, the process proceeds to step S112, in which the learning value DUTYLR calculated in the 250 ms job is added to the basic duty ratio DUTY and the final duty ratio is output to the ISCV16. Set to DUTYisc, step S1
At 13, the duty ratio DUTYisc is set and the routine exits.

[0157]

As described above, according to the present invention, the target value of the physical quantity that can be regarded as having a linear relationship with the indicated torque of the engine is set according to the engine speed during idling, and the target value of this physical quantity is set to the target value. Based on this, the fuel injection amount is determined, and the amount of air passing through the idle control valve that matches this fuel injection amount is calculated as the sum of the mass of air accumulated in the chamber and the mass of air sucked into the cylinder according to the intake system model. Calculate and determine the opening degree of the idle control valve based on the calculated value of the passing air amount to control the idle speed, eliminate the fuel delay, minimize the influence of the air delay, and reduce the engine torque. The response can be increased and decreased with good followability, and the response and rotation convergence in idle control can be significantly improved.

Further, the physical quantity that can be regarded as having a linear relationship with the indicated torque of the engine is taken as the cylinder intake air mass per one intake stroke of one cylinder, and the target value of this cylinder intake air mass is immediately multiplied by, for example, the fuel-air ratio. The amount of fuel injection can be determined, and the amount of air passing through the idle control valve can be calculated as a function of the pressure in the chamber that changes depending on the opening of the idle control valve to obtain the target value of the cylinder intake air mass. An excellent effect is obtained such that the control of the idle control valve can be facilitated by controlling the control to the target pressure.

[Brief description of drawings]

FIG. 1 is a flowchart of an idle control basic routine.

FIG. 2 is a flowchart of a basic idle control routine (continued)

FIG. 3 is a flowchart of a fuel injection amount calculation subroutine.

FIG. 4 is a flowchart of an I-minute movement amount calculation subroutine.

FIG. 5 is a flowchart of a target rotation speed movement amount calculation subroutine.

FIG. 6 is a flowchart of a target rotation speed movement amount calculation subroutine (continued)

FIG. 7 is a flowchart of a load increase / decrease movement amount calculation subroutine.

FIG. 8 is a flowchart of a learning value calculation subroutine.

FIG. 9 is a flowchart of a water temperature correction value calculation subroutine.

FIG. 10 is a flowchart of an atmospheric pressure calculation subroutine.

FIG. 11 is a flowchart of a temperature function calculation subroutine.

FIG. 12 is a schematic configuration diagram of an engine system.

FIG. 13 is a front view of a crank rotor and a crank angle sensor.

FIG. 14 is a front view of a cam rotor and a cam angle sensor.

FIG. 15 is a circuit configuration diagram of an electronic control system.

FIG. 16 is a block diagram of idle control.

FIG. 17 is a functional configuration diagram of an ECU relating to idle control.

FIG. 18 is an explanatory diagram of P minute control by a Ga-Ne map.

FIG. 19 is an explanatory diagram of I minute control by a Ga-Ne map.

FIG. 20 is an explanatory diagram showing the movement of the Ga-Ne map when the water temperature is low and when the load changes.

FIG. 21 is an explanatory diagram showing the characteristics of a Ga-Ne map.

FIG. 22 is an explanatory diagram showing control at the time of starting in the Ga-Ne map.

FIG. 23 is an explanatory diagram showing the relationship between start-up control and a Ga-Ne map.

FIG. 24 is an explanatory diagram showing the relationship between the stroke intake air amount and the intake pipe pressure.

FIG. 25 is an explanatory diagram of a chamber model.

FIG. 26 is an explanatory diagram showing the rotational speed convergence when the air conditioner is on and off.

FIG. 27 is an explanatory diagram showing the rotational speed convergence during D range shift.

FIG. 28 is an explanatory diagram showing the relationship between the strength of P, the rotational speed, and the intake pipe pressure fluctuation.

FIG. 29 is an explanatory diagram showing rotation fluctuation at the time of starting.

FIG. 30 is an explanatory diagram showing target values and actually measured values of the ISC valve passing air amount by water temperature correction.

FIG. 31 is an explanatory diagram showing a target boost pressure and an actual boost pressure at the time of cold start.

FIG. 32 is an explanatory diagram showing the rotational speed convergence when the power steering is turned.

FIG. 33 is an explanatory diagram showing learning with respect to a characteristic change of ISCV.

FIG. 34 is an explanatory diagram showing rotation fluctuation and ISCV opening change when the value of the chamber volume in the arithmetic expression is changed.

FIG. 35 is a block diagram of conventional idle control by PI control.

[Explanation of symbols]

1 engine 5a throttle valve 16 ISCV (idle control valve) Ne engine speed Ga stroke intake air amount (physical quantity that can be regarded as having a linear relationship with the indicated torque of the engine) Gaset target stroke intake air amount (with a linear relationship with the indicated torque of the engine Target value of physical quantity that can be considered to be) Gf Fuel injection amount Qisc ISCV Passing air amount (passing air amount of idle control valve) Wm Chamber air mass (air mass accumulated in chamber) Qcy Cylinder inflow air amount (in cylinder) Intake air mass) DUTYisc duty ratio (opening of idle control valve)

Claims (2)

[Claims] 1. A target value of a physical quantity that can be regarded as having a linear relationship with an indicated torque of an engine is set according to an engine speed at idle, and an idle control valve suitable for a fuel injection amount based on the target value of the physical quantity is set. The amount of passing air is calculated as the sum of the mass of air accumulated in the chamber, which is equivalently modeled from the downstream of the throttle valve to immediately before the cylinder, and the mass of air sucked into the cylinder, and the amount of passing air is calculated. An idle control method for an engine, comprising: determining an opening of the idle control valve based on a value and outputting the opening signal to the idle control valve to control an idle speed. 2. The physical quantity is defined as a cylinder intake air mass per one intake stroke of one cylinder, the fuel injection quantity is calculated from a target value of the cylinder intake air quantity, and the air quantity passing through the idle control valve is gas. 2. The engine idle control method according to claim 1, wherein the calculation is performed as a function of the pressure in the chamber by using the state equation of.