Control device and method of controlling an internal combustion engine

A control device of an internal combustion engine includes: a target negative pressure setting section that set a target negative intake pipe pressure during cold acceleration to a negative intake pipe pressure larger than a negative intake pipe pressure prior to the cold acceleration; a throttle valve control section that controls a throttle valve so that the negative intake pipe pressure increases during cold acceleration; and an intake valve control section that controls a variable valve mechanism of an intake valve, based on the target negative intake pipe pressure, to obtain a target intake air amount.

INCORPORATION BY REFERENCE

The disclosure of Japanese Patent Application No. 2007-66914 filed on Mar. 15, 2007 including the specification, drawings and abstract is incorporated herein by reference in its entirety.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a control device and method of controlling an internal combustion engine. More specifically, the present invention relates to a control device and method of controlling a port injection type internal combustion engine in which fuel is injected to an intake port.

2. Description of the Related Art

For example, Japanese Patent Application Publication No. 08-86234 (JP-A-08-86234) describes an engine air-fuel ratio control device that calculates a fuel injection amount during cold acceleration of an internal combustion engine, based on the amount of fuel adhering to the port. More specifically, the described control device calculates a fuel shortage amount Hm obtained by subtracting a function value H(tb), that is at acceleration timing tb, from an equilibrium adhesion amount, that is immediately before the acceleration timing. Then, the transient correction amount Kathos is increased by a value corresponding to the shortage amount Hm, thereby preventing the air-fuel ratio from shifting to the lean side when accelerating immediately after a cold start.

However, if an amount of shortage in fuel that has evaporated is compensated for by an increase in fuel injection amount, during cold acceleration, the amount of fuel adhering to the port is further increased. Also, the fuel that adheres to the intake port or the like during acceleration may later be supplied into the cylinder after acceleration. Consequently, when the amount of fuel adhering to the port increases, the air-fuel ratio controllability subsequent to acceleration deteriorates.

SUMMARY OF THE INVENTION

The present invention provides a control device and method of controlling an internal combustion engine that reduces the deterioration of the air-fuel ratio controllability when executing a cold acceleration of the internal combustion engine.

A first aspect of the present invention relates to a control device of an internal combustion engine. The control device includes: a target negative pressure setting section that sets a target negative intake pipe pressure during cold acceleration to a negative intake pipe pressure larger than a negative intake pipe pressure prior to the cold acceleration; a throttle valve control section that controls a throttle valve so that the negative intake pipe pressure increases during cold acceleration; and an intake valve control section that controls a variable valve mechanism of an intake valve, based on the target negative intake pipe pressure, to obtain a target intake air amount.

A second aspect of the present invention relates to a method of controlling an internal combustion engine. The control method includes: setting a target negative intake pipe pressure during cold acceleration to a negative intake pipe pressure larger than a negative intake pipe pressure prior to the cold acceleration; controlling a throttle valve so that the negative intake pipe pressure increases during cold acceleration; and controlling a variable valve mechanism of an intake valve, based on the target negative intake pipe pressure, to obtain a target intake air amount.

In the above-described aspects, the intake pipe pressure is reduced when accelerating the internal combustion engine while cold to increase the evaporation rate of fuel. Because a reduction in port wet amount may thus be expected during cold acceleration, the amount of increase in fuel injection may be reduced, which further reduces the port wet amount. It is thus possible to prevent a deterioration of the air-fuel ratio controllability, that is caused by executing the cold acceleration, after the cold acceleration.

DETAILED DESCRIPTION OF THE EMBODIMENTS

FIG. 1is a diagram showing the configuration of a first embodiment of the present invention. The configuration of the embodiment includes an internal combustion engine10. A piston12is provided inside the cylinder of the internal combustion engine10. The piston12can reciprocate inside the cylinder. Inside the cylinder of the internal combustion engine10, a combustion chamber14is formed on the side of the top portion of the piston12. Also, an intake passage16and an exhaust passage18communicate with the combustion chamber14.

An airflow meter20that outputs a signal according to the flow rate of air sucked into the intake passage16is provided near the inlet of the intake passage16. A throttle valve22is provided downstream of the airflow meter20. The throttle valve22is an electronically controlled throttle valve whose throttle opening can be controlled independently from the accelerator displacement. Arranged near the throttle valve22is a throttle position sensor24that detects a throttle opening TA.

A fuel injection valve26for injecting fuel into an intake port16aof the internal combustion engine10is provided downstream of the throttle valve22. An ignition plug28is attached for each cylinder to a cylinder head included in the internal combustion engine10so as to project into the combustion chamber14from the top portion of the combustion chamber14. An intake valve30and an exhaust valve32for establishing or cutting off communication between the combustion chamber14and the intake passage16, and between the combustion chamber14and the exhaust passage18, are provided in the intake and exhaust ports respectively.

The intake valve30is driven by a variable valve mechanism34. The variable valve mechanism34is a mechanism that can variably control the valve-open characteristics (lift, duration, opening time, closing time, and the like) of the intake valve30. An air-fuel ratio sensor36is provided in the exhaust passage18for detecting the exhaust air-fuel ratio.

The configuration shown inFIG. 1includes an electronic control unit (ECU)40. In addition to the various sensors described above, a crank angle sensor42for detecting the engine speed, an accelerator position sensor44for detecting the accelerator displacement, and a coolant temperature sensor46for detecting the engine coolant temperature are connected to the ECU40. Also, various actuators for driving the above-described throttle valve22, the variable valve mechanism34, and the like are connected to the ECU40. Based on the output of each sensor, the ECU40drives each actuator in accordance with a predetermined program, thereby controlling the operational state of the internal combustion engine10.

According to the internal combustion engine10including the variable valve mechanism34described above, by controlling the lift and the duration of the intake valve30while the throttle opening TA is sufficiently large (hereinafter, for the convenience of description, this control is referred to as “control A”), it possible to control an intake air amount Ga without reducing the intake pipe pressure significantly, that is, reducing the pump loss.

The amount of fuel adhering to the wall surface or the like of the intake port16a(port wet amount) increases as the wall surface or the like of the intake port16abecomes cooler. Accordingly, when the internal combustion engine10is cold, it is necessary to increase the fuel injection amount by taking into account a decrease in the amount of fuel injected into the cylinder due to port wet. Further, the evaporation rate of fuel is also determined by the saturation vapor pressure of fuel and the ambient pressure (the intake pipe pressure when referring to the interior of the intake port16a). More specifically, the lower the intake pipe pressure, the higher the evaporation rate of fuel.

Accordingly, because formation of a negative intake pipe pressure is suppressed under the condition in which the above-mentioned control A using the variable valve mechanism34is executed, the evaporation rate of fuel decreases. As a result, if the above-mentioned control A is executed during acceleration while the internal combustion engine10is cold, the increase in fuel injection amount required to compensate for the shortage in the evaporation amount of fuel increases, and the amount of fuel adhering to the intake port16aor the like also increases. The amount of fuel that adheres to the intake port16aor the like during acceleration may later be supplied into the combustion chamber14after acceleration. Therefore, an increase in port wet amount leads to deterioration of the air-fuel ratio controllability after the acceleration.

Accordingly, in this embodiment, as shown inFIGS. 2A to 2G, when an acceleration request is made while the engine is cold, in which the above-mentioned control A using the variable valve mechanism34is executed, the throttle valve22is closed to increase the negative intake pipe pressure, thereby promoting evaporation of fuel. At the same time, the intake air amount Ga at the cold acceleration is controlled to a requested intake air amount by regulating the lift and the duration of the intake valve30.

FIGS. 2A to 2Gare diagrams illustrating control according to this embodiment. InFIGS. 2C to 2G, each broken line indicates the execution of a commonly employed control. In the example shown inFIGS. 2A to 2G, the above-mentioned control A is performed when the internal combustion engine10is cold. Therefore, as shown inFIGS. 2C and 2D, before the acceleration request (t0), the throttle valve22is opened relatively wide, and the duration and the lift of the intake valve30are controlled to be relatively small.

As shown inFIGS. 2A and 2B, when the requested intake amount increases after the depression of an accelerator pedal during acceleration, according to the commonly employed control, as indicated by the broken lines inFIGS. 2C and 2D, the throttle valve22is widely opened, and the duration and the lift of the intake valve30are increased. Accordingly, as indicated by the broken line inFIG. 2E, the intake pipe pressure hovers around a value close to the atmospheric pressure, so fuel does not readily evaporate. Also, during acceleration, as indicated by the broken line inFIG. 2F, the fuel injection amount is increased accompanying an amount of increase that takes the port wet amount into account as indicated by the broken line inFIG. 2G. In this case, the port wet amount itself increases as the amount of fuel injection increases.

In contrast, according to this embodiment, when the requested intake amount increases after the depression of the accelerator pedal, as indicated by the solid line inFIG. 2C, the opening amount of the throttle valve22is reduced to a predetermined opening amount TA1that is smaller than the throttle opening amount TA immediately before the acceleration request. Thus, as indicated by the solid line inFIG. 2E, this sharply reduces the intake pipe pressure, thereby promoting evaporation of fuel. The amount by which the opening amount of the throttle valve22is reduced is determined such that a target negative intake pipe pressure defined in relation to the engine coolant temperature, as will be described later, is attained.

Also, in this embodiment, as indicated by the solid line inFIG. 2D, the duration and the lift of the intake valve30are each regulated to be a control amount X1, in order to compensate for a decrease in the intake air amount Ga following the reduction of the intake pipe pressure due to the above-mentioned closing of the throttle valve22by increasing the duration and the lift of the intake valve30.

According to the above-described control of this embodiment, during cold acceleration, the throttle valve22is controlled to form a negative intake pipe pressure, thereby making it possible to increase the evaporation rate of fuel. Therefore, as indicated by the solid line inFIG. 2G, the port wet amount is reduced. Further, as indicated by the solid line inFIG. 2F, the increase in fuel injection amount is restrained by the reduction in port wet amount. The decrease in the intake air amount Ga after the intake pipe pressure is reduced may be compensated for by regulating the duration and the lift of the intake valve30.

FIG. 3is a flowchart of an operation that is executed by the ECU40in this embodiment to realize the above-mentioned control.

First, the ECU40determines whether an acceleration request of a predetermined level or more (step100) has been made based on the output of the accelerator position sensor44.

If the ECU40determines that an acceleration request of a predetermined level or more has been made, the ECU40acquires a target negative intake pipe pressure based on the engine coolant temperature (step102).

As shown inFIG. 4, the ECU40stores a map that defines the relationship between the engine coolant temperature and the target negative intake pipe pressure. As the engine coolant temperature increases, that is, as the internal combustion engine10is warmed up, the temperature of the wall surface or the like of the intake port16aalso increases. As the temperature of the wall surface or the like of the intake port16aincreases, the port wet amount decreases. Also, as described above, as the negative intake pipe pressure increases, the port wet amount decreases because the evaporation rate of fuel increases. In the map shown inFIG. 4, the target negative intake pipe pressure is set so that the target negative intake pipe pressure is reduced (becomes closer to the atmospheric pressure) as the engine coolant temperature increases. According to this setting of the map, an appropriate target negative intake pipe pressure for reducing the port wet amount may be obtained based on the engine coolant temperature, regardless of the progress of the warm-up of the internal combustion engine10.

Next, the ECU40calculates the closing amount of the throttle valve22based on the target negative intake pipe pressure acquired in step102. Based on the above calculated closing amount of the throttle valve22and the detected requested level of acceleration, the ECU40calculates the respective target values of the duration and the lift of the intake valve30(step104).

In the ECU40, the relationship between the intake pipe pressure and the throttle opening TA is stored, and also the duration and the lift of the intake valve30required for attaining a requested intake amount according to the throttle opening TA and requested acceleration level are stored in relation to the intake pipe pressure. That is, in step104, the closing amount of the throttle valve22to obtain the target negative intake pipe pressure, and the duration and the lift of the intake valve30required to provide the requested intake amount under the negative intake pipe pressure controlled by the closing of the throttle valve22are calculated.

Then, although not illustrated in the operation shown inFIG. 3, in the subsequent step, the ECU40controls the throttle valve22, and the duration and the lift of the intake valve30based on the calculated respective target values of the closing amount of the throttle valve22, and of the duration and the lift of the intake valve30.

According to the operation shown inFIG. 3described above, when there is an acceleration request of a predetermined level or more, an appropriate target negative intake pipe pressure according to the engine coolant temperature is obtained, in which the target negative intake pipe pressure is lower than the intake pipe pressure immediately before acceleration, and based on this target negative intake pipe pressure, the target value of the throttle valve22and the target values of the duration and the lift of the intake valve30during acceleration are obtained. As a result, the throttle valve22is controlled so that the target negative intake pipe pressure is obtained, and the duration and the lift of the intake valve30are controlled so that a target intake air amount is obtained under conditions where the intake pipe pressure is controlled to the target negative intake pipe pressure.

As a result, if acceleration is requested while the internal combustion engine10is cold, the intake pipe pressure is significantly reduced, thereby increasing the evaporation rate of fuel. Therefore, during cold acceleration, the port wet amount is reduced, thereby making it possible to reduce the increase in the fuel injection amount. Further, such a reduction in the amount of increase in fuel injection leads to a further reduction in port wet amount. It is thus possible to improve the air-fuel ratio controllability subsequent to cold acceleration.

Further, because the target negative intake pipe pressure during cold acceleration is set to an appropriate value according to the engine coolant temperature, the air-fuel ratio controllability subsequent to cold acceleration is improved, and also an operation that reduces pump loss, that is, a reduction in fuel consumption by the above-mentioned control A, may be executed as much as possible.

It should be noted that in the first embodiment described above, the ECU40that acquires the target negative intake pipe pressure based on the engine coolant temperature in step102may be regarded as a “target negative pressure setting section” of the present invention. In addition, the ECU40that controls the opening of the throttle valve22based on the target value calculated in the process of step104may be regarded as a “throttle valve control section” of the present invention. The ECU40that controls the duration and the lift of the intake valve30based on the target value calculated in the process of step104may be regarded as the “intake valve control section” of the present invention.

Next, a second embodiment of the present invention will be described with reference toFIGS. 5A to 8. In this embodiment, the configuration shown inFIG. 1is employed, and the ECU40executes the operation shown inFIG. 6, described later, instead of the operation shown inFIG. 3.

In this embodiment as well, basically in the same manner as in the first embodiment described above, the ECU40closes the throttle valve22during cold acceleration to generate a negative intake pipe pressure according to the engine coolant temperature, and also controls the duration and the lift of the intake valve30so that the intake air amount Ga becomes the requested intake amount.

However, if cold acceleration is sudden, the requested intake amount changes abruptly. In that case, there may be times when the requested intake amount cannot be provided due to restriction on the operating speed of the variable valve mechanism34, that is the actuator that varies the duration and the lift of the intake valve30.

Accordingly, in this embodiment, the limit value of a target negative intake pipe pressure during cold acceleration is derived based on the limit value of the operating speed of the duration and the lift of the intake valve30by the variable valve mechanism34, and a negative intake pipe pressure is formed within a range of values that allow a requested intake amount to be provided by the variable valve mechanism34. Below, a more detailed description will be given in this regard with reference toFIGS. 5A to 5G.

FIGS. 5A to 5Gare diagrams illustrating control according to the second embodiment. The broken line inFIG. 5Dindicates a change in the duration and the lift of the intake valve30required when an intake air amount Ga that exceeds the operating limit of the variable valve mechanism34is requested during cold acceleration. On the other hand, the solid line inFIG. 5Dindicates a change in the duration and the lift of the intake valve30when the variable valve mechanism34is at its operating limit.

In this embodiment, in view of such restriction on the operating speed of the variable valve mechanism34, as indicated by the solid line inFIG. 5E, a restriction is placed on how much the intake pipe pressure may be reduced. To ensure that such restriction on the negative intake pipe pressure is reflected, the closing amount of the throttle valve22is restricted as indicated by the solid line inFIG. 5C.

FIG. 6is a flowchart of an operation executed by the ECU40in this embodiment in order to realize the above-mentioned function. It should be noted that inFIG. 6, the steps that are the same as those shown inFIG. 3in the first embodiment are denoted by the same symbols and description thereof is omitted or simplified.

In the operation shown inFIG. 6, if the ECU40determines in step100that there is an acceleration request of a predetermined level or more, the ECU40acquires the limit value of a target negative intake pipe pressure based on the limit value of the operating speed of the variable valve mechanism34(step200). As shown inFIG. 7, the ECU40stores a map that defines the relationship between the accelerator pedal depression speed and the change in negative intake pipe pressure during acceleration. In the map shown inFIG. 7, based on the operating limit of the variable valve mechanism34, the target negative intake pipe pressure is set so that as the depression speed increases (that is, as the requested acceleration increases), the change in negative intake pipe pressure relative to that before acceleration decreases (that is, a greater restriction is placed on the formation of a negative intake pipe pressure). In this step200, the ECU40acquires the limit value of a target negative intake pipe pressure by referencing the map stored in the ECU40.

Next, as shown inFIG. 8, the ECU40acquires a target negative intake pipe pressure based on the engine coolant temperature, according to the limit value of a target negative intake pipe pressure acquired in step200(step202). In this step202, referring to a map shown inFIG. 8, which is set to have a similar characteristic as the map shown inFIG. 4, the ECU40acquires the target negative intake pipe pressure within the range of restriction as imposed by the limit value of a target negative intake pipe pressure.

Next, based on the target negative intake pipe pressure acquired in step202, the ECU40calculates the respective target values of the closing amount of the throttle valve22and of the duration and the lift of the intake valve30(step104).

Then, although not illustrated in the operation shown inFIG. 6, in the subsequent step, the ECU40controls the throttle valve22, and the duration and the lift of the intake valve30on the basis of the calculated respective target values of the closing amount of the throttle valve22, and of the duration and the lift of the intake valve30.

According to the operation shown inFIG. 6described above, the negative intake pipe pressure to be formed during acceleration is restricted based on the operating limit of the variable vale mechanism34, thereby making it possible to reduce the port wet amount and provide the requested intake amount during cold acceleration.

Next, a third embodiment of the present invention will be described with reference toFIGS. 9A to 9GandFIG. 10. In this embodiment, the configuration shown inFIG. 1is employed, and the ECU40executed the operation shown inFIG. 10, described later, instead of the operation shown inFIG. 3.

In this embodiment as well, basically in the same manner as in the first embodiment described above, the ECU40closes the throttle valve22during cold acceleration to produce a negative intake pipe pressure according to the engine coolant temperature, and also controls the duration and the lift of the intake valve30so that the intake air amount Ga becomes the requested intake amount.

However, when the level of a requested negative intake pipe pressure to be produced by closing the throttle valve22during cold acceleration is high, there may be times when the requested negative intake pipe pressure cannot be provided due to the restriction on the operating speed of the throttle valve22, so an intake amount supplied into the cylinder may exceed the requested intake amount as a result.

Accordingly, in this embodiment, the limit value of a target negative intake pipe pressure during cold acceleration is derived on the basis of the limit value of the operating speed at the time of closing operation of the throttle valve22. Then, by controlling the variable valve mechanism34in accordance with the negative intake pipe pressure that is restricted by the limit value of the operating speed at the closing operation of the throttle valve22, the intake air amount Ga is controlled to be the requested intake amount.

FIGS. 9A to 9Gare diagrams illustrating control according to the third embodiment. The broken line inFIG. 9Cindicates a change in the opening of the throttle valve22required when an intake air amount Ga that exceeds the operating limit of the variable valve mechanism34is requested during cold acceleration. On the other hand, the solid line inFIG. 9Cindicates a change in the opening amount when the throttle valve22is at its operating limit.

In this embodiment, in view of such restriction on the operating speed of the throttle valve22, as indicated by the solid line inFIG. 9E, a restriction is placed on how much the intake pipe pressure may be lowered. To ensure that a requested intake amount is attained in accordance with such restriction on the negative intake pipe pressure, the duration and the lift of the intake valve30are controlled by the variable valve mechanism34as indicated by the solid line inFIG. 9D.

FIG. 10is a flowchart of an operation executed by the ECU40to realize the above-described function. It should be noted that inFIG. 10, the steps that are the same as those shown inFIG. 3are denoted by the same symbols and description thereof is omitted or simplified.

In the operation shown inFIG. 10, if the ECU40determines in step100that there is an acceleration request of a predetermined level or more, the ECU40acquires the limit value of a target negative intake pipe pressure based on the limit value of the operating speed of the throttle valve22when closing the throttle valve22(step300). The ECU40stores a map (a map similar to the map shown inFIG. 7) that defines the relationship between the accelerator pedal depression speed and the change in negative intake pipe pressure during acceleration. In step300, the ECU40acquires the limit value of a target negative intake pipe pressure by referring to this map.

Next, the ECU40acquires a target negative intake pipe pressure based on the engine coolant temperature, according to the limit value of a target negative intake pipe pressure acquired in step300(step302). In this step302, the ECU40acquires a target negative intake pipe pressure by referencing a map similar to the map shown inFIG. 8.

Next, based on the target negative intake pipe pressure acquired in step302, the ECU40calculates the respective target values of the closing amount of the throttle valve22and of the duration and the lift of the intake valve30(step104).

Then, although not illustrated in the operation shown inFIG. 10, in the subsequent step, the ECU40controls the throttle valve22, and the duration and the lift of the intake valve30in accordance with the calculated respective target values of the closing amount of the throttle valve22, and of the duration and the lift of the intake valve30.

According to the operation shown inFIG. 10described above, the duration and the lift of the intake valve30during cold acceleration are controlled by the variable valve mechanism34so that the intake air amount Ga according to a negative intake pipe pressure that is restricted in relation to the operating limit of the throttle valve22is obtained. Therefore, it is possible to reduce the port wet amount and provide the requested intake amount during cold acceleration.

Next, a fourth embodiment of the present invention will be described with reference toFIGS. 11 and 12. In this embodiment, the configuration shown inFIG. 1is employed, and an operation shown inFIG. 11, described later, is executed by the ECU40instead of the operation shown inFIG. 3.

This embodiment has a configuration in which a plurality of fuel types, for example, gasoline and ethanol, are supplied, and the internal combustion engine10may be operated by using any one of these fuel types (a system mounted in a vehicle that is a so-called flexible-fuel vehicle (FFV)). In this configuration, the fuel that is ultimately supplied to the internal combustion engine10varies depending on such factors as the fuel type selected by the user of the vehicle, the amount added during refueling, and the amount of fuel that remains within the fuel tank at that time.

The evaporation characteristics of fuel vary depends on the property of the fuel. More specifically, when a fuel with poor evaporation characteristics such as ethanol is used, when accelerating during cold, the amount of fuel injected needs to be greatly increased, which also leads to an increase in port wet amount. Also, because a fuel with poor evaporation characteristics has a low evaporation rate, the evaporation amount of fuel from the intake port16aor the like is not sufficient relative to the increase in the intake air amount Ga during acceleration. As a result, the air-fuel ratio during acceleration becomes lean, which may cause misfire.

Therefore, when a fuel with poor evaporation characteristics is used, it is desirable to sharply lower the intake pipe pressure during cold acceleration. However, when a fuel with good evaporation characteristics is used, application of an excessive negative intake pipe pressure increases pump loss, which may cause deterioration of fuel economy. Accordingly, in this embodiment, the target negative intake pipe pressure during cold acceleration varies depending on fuel property.

FIG. 11is a flowchart of an operation executed by the ECU40in this embodiment in order to implement the above-described function. It should be noted that inFIG. 11, the steps that are the same as those shown inFIG. 3are denoted by the same symbols and description thereof is omitted or simplified.

In the operation shown inFIG. 11, if the ECU40determines in step100that there is an acceleration request of a predetermined level or more, the ECU40then determines the properties of the fuel supplied to the internal combustion engine10(step400). Because the theoretical air-fuel ratio varies depending on the fuel, the air-fuel ratio changes sharply upon switching the fuel supplied to the internal combustion engine10. Such a change in air-fuel ratio manifests itself as a change in the amount of feedback correction to the fuel injection amount in the air-fuel ratio feedback control executed by the ECU40. In this step400, the ECU40performs the fuel property determination based on the air-fuel ratio feedback correction amount.

Next, the ECU40acquires a target negative intake pipe pressure based on the engine coolant temperature and fuel property (step402). As shown inFIG. 12, the ECU40stores a map that defines the relationship between the engine coolant temperature, the fuel property, and the target negative intake pipe pressure. In the map shown inFIG. 12, the target negative intake pipe pressure is set so that the target negative intake pipe pressure increases (the pressure decreases) as the evaporation characteristics of fuel become poorer.

Next, based on the target negative intake pipe pressure acquired in step402, the ECU40calculates the respective target values of the closing amount of the throttle valve22and of the duration and the lift of the intake valve30(step104).

Then, although not illustrated in the operation shown inFIG. 11, in the subsequent step, the ECU40controls the throttle valve22, and the duration and the lift of the intake valve30based on the calculated respective target values of the closing amount of the throttle valve22, and of the duration and the lift of the intake valve30.

According to the operation shown inFIG. 11described above, the negative intake pipe pressure during acceleration is controlled so as to attain a target negative intake pipe pressure that appropriately takes the property of fuel supplied to the internal combustion engine10into consideration. Therefore, during cold acceleration, the amount of increase in fuel injection may be reduced irrespective of the evaporation characteristics of fuel, and also such a reduction in the amount of increase in fuel injection enables a further reduction in port wet amount. Further, when a fuel with relatively good evaporation characteristics is used, it is possible to prevent an excessive negative intake pipe pressure from being applied, thereby preventing a deterioration of fuel economy due to an increase in pump loss.

It should be noted that the ECU40in the fourth embodiment described above that executes the determination of the property of fuel supplied to the internal combustion engine10in step400may be regarded as the “fuel property determining section” of the present invention.