JP4461947B2 - Fuel injection device for compression self-ignition internal combustion engine - Google Patents

Description

  The present invention relates to a fuel injection device for an internal combustion engine that performs compression self-ignition combustion.

Patent Document 1 discloses that in an internal combustion engine that performs compression self-ignition combustion, gasoline is separated into a high-octane fuel and a low-octane fuel, and each is stored in a tank. It is configured to supply the octane fuel separately, and the usage ratio of the high octane fuel and the low octane fuel is determined according to the engine operation area and the remaining amount in each tank, and each tank is set to have this usage ratio. Discloses an internal combustion engine configured to control the ratio of fuel supplied to the fuel injection valve.
JP 2001-050070 A

  In the conventional compression self-ignition internal combustion engine, the ignitability can be improved by the low octane number fuel. However, since the high octane number fuel and the low octane number fuel are injected by one fuel injection valve, the high octane number fuel and the low octane number fuel are The high-octane fuel and the low-octane fuel can be injected at the same time, and the reaction of the high-octane fuel can be efficiently promoted by the reaction heat of the low-octane fuel. There was a problem that the reaction rate of the high octane fuel as the main combustion could not be controlled, and as a result, the area of compression self-ignition combustion could not be expanded sufficiently.

  The present invention has been made in view of the above problems, can change the usage ratio of high-octane fuel and low-octane fuel with high accuracy and high response, and can further improve the ignitability of low-octane fuel. On the other hand, an object of the present invention is to provide a fuel injection device for a compression self-ignition internal combustion engine capable of controlling the reaction rate of high octane fuel as main combustion and maximizing the area of compression self-ignition combustion.

Therefore, the present invention separately includes a first fuel injection means for injecting low-octane fuel and a second fuel injection means for injecting high-octane fuel, and the fuel injection amount and injection of the low-octane fuel and high-octane fuel. The timing is controlled independently of each other , the second fuel injection means directly injects the high octane fuel into the cylinder, and the injection timing of the high octane fuel is set according to the engine rotational speed. When exceeding the reference speed, set the injection timing of high octane fuel during the engine valve minus overlap period, and when the engine speed falls below the reference speed, set a slower timing as the engine speed increases after the minus overlap period. It was set as the injection timing of a high octane fuel .

  According to such a configuration, since the first fuel injection means for injecting the low octane fuel and the second fuel injection means for injecting the high octane fuel are individually provided, the low octane fuel with good ignitability and the high knock resistance are high. It is possible to inject octane fuel at different timings, and by independently controlling the injection amount by each fuel injection means, it is possible to change the usage rate of each fuel with high accuracy and high response. Become.

  Accordingly, the ignitability of the low-octane fuel can be further improved, and the reaction (main combustion) of the high-octane fuel promoted by the reaction heat of the low-octane fuel can be slowed down, causing misfires and knocking. The compressed self-ignition combustion region can be expanded.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a system configuration diagram of a compression self-ignition internal combustion engine in the first embodiment.
In the internal combustion engine 1 (gasoline engine), air that has passed through the air cleaner 2 is supercharged by the supercharger 3 and then sucked into the cylinder 5 via the intake valve 4.
The intake port 6 upstream of the intake valve 4 is provided with a first fuel injection valve (first fuel injection means) 7 for injecting fuel into the intake port 6, and direct injection of fuel into the cylinder 5. A second fuel injection valve (second fuel injection means) 8 for injection is provided.

The first fuel injection valve 7 is supplied with low-octane fuel having good ignitability stored in a low-octane fuel tank 9, and the second fuel injection valve 8 is stored in a high-octane fuel tank 10. High octane fuel with good knock resistance is supplied.
A fractionator for fractionating gasoline into low-octane fuel and high-octane fuel using the difference in boiling point of gasoline components is provided, and the low-octane fuel and high-octane fuel fractionated by the fractionator are separated. It may be configured to be stored in each tank, or may be configured to be replenished with low-octane fuel and high-octane fuel from the outside.

  Here, when the low-octane fuel and the high-octane fuel are replenished from the outside, regular gasoline can be replenished as the low-octane fuel, and high-octane fuel can be replenished as the high-octane fuel. Regular gasoline can be replenished from the outside, and a special fuel having a lower octane number than regular gasoline can be replenished from the outside as a low octane fuel.

The air-fuel mixture in the combustion chamber is ignited and combusted by compression self-ignition or spark ignition by the spark plug 11, and the combustion exhaust is discharged via the exhaust valve 12.
The intake valve 4 and the exhaust valve 12 are provided with a variable valve mechanism 13 that makes the valve lift amount, the valve operating angle, and the center phase of the operating angle variable.
The variable valve mechanism 13 includes, for example, a variable valve event / lift mechanism (VEL) disclosed in Japanese Patent Application Laid-Open No. 2001-012262, which continuously changes the valve lift amount of the engine valve together with the operating angle, and a crankshaft. It is composed of a combination with a variable valve timing mechanism (VTC) that makes the center phase of the valve operating angle variable by changing the rotational phase of the camshaft.

The variable valve mechanism 13 may be an electromagnetically driven valve (EMV) that opens and closes the intake valve 4 and the exhaust valve 12 with a magnetic force generated by an electromagnet.
The intake port 6 upstream of the first fuel injection valve 7 partially blocks the opening of the intake port 6 so that the flow of intake air drifts and an intake control valve 14 (gas flow) generates gas flow in the cylinder. Generating means).

The gas flow may be either a swirl flow or a tumble flow, but is preferably a swirl flow in which the gas flow remains in the vicinity of the compressed TDC where the fuel reaction occurs.
In addition, each cylinder is provided with two intake ports, and either one of the intake valves is stopped or one of the intake ports is closed by the valve, so that air is introduced into the cylinder only from the other intake port (helical port, etc.). The gas flow (swirl and / or tumble) can be generated in the cylinder.

The fuel injection valves 7 and 8, the ignition plug 11, the variable valve mechanism 13 and the intake control valve 14 are controlled by an engine control unit (ECU) 20 incorporating a microcomputer.
The engine control unit 20 includes a rotation speed sensor 21 that detects the engine rotation speed, a water temperature sensor 22 that detects the cooling water temperature of the engine, and a remaining amount sensor 23 that detects the remaining amount of fuel in the fuel tanks 9 and 10. 24, a detection signal from a cylinder temperature sensor 25 for detecting the temperature in the cylinder is input.

The flowchart of FIG. 2 shows a state of control by the engine control unit 20 in the first embodiment.
In step S1, it is determined which operation mode is to be operated: compression self-ignition combustion or spark ignition combustion.
Specifically, the engine torque T is smaller than the self-ignitable maximum torque TH1, larger than the self-ignitable minimum torque TL1 (TL1 <T <TH1), and the engine speed Ne (rpm) is When it is smaller than the maximum self-ignitable rotation speed NeH1 and larger than the minimum self-ignition possible rotation speed NeL1 (NeL1 <Ne <NeH1), it is determined that it is within the region where compression self-ignition combustion is possible. When it is not satisfied, it is determined that it is within the region where spark ignition combustion is performed.

If it is determined that it is within the region where compression self-ignition combustion is possible, the process proceeds to step S3 and subsequent steps. If it is determined that it is within the region where spark ignition combustion is performed, the process proceeds to step S2.
In step S <b> 2, a spark ignition combustion operation is performed in which high octane fuel injected from the second fuel injection valve 8 is burned by spark ignition by the spark plug 11.
On the other hand, in step S3, it is determined whether or not the remaining amount of the low octane fuel stored in the low octane fuel tank 9 is equal to or greater than the minimum amount MIN.

If the remaining amount of the low octane fuel is equal to or greater than the minimum amount MIN, the process proceeds to step S4, and the compression self-ignition combustion operation using the low octane fuel and the high octane fuel is started.
In step S5, the engine coolant temperature is detected, and in the next step S6, the in-cylinder temperature at the compression top dead center (hereinafter referred to as compression TDC) is detected.
The in-cylinder temperature in the compression TDC may be estimated based on the engine operating conditions (the engine valve minus overlap period and the engine speed).

In step S7, the intake control valve 14 is closed to generate a gas flow in the cylinder.
Here, the intake control valve 14 may be throttled to a certain opening, but it is preferable to determine the opening of the intake control valve 14 according to the in-cylinder temperature and the engine load in the compression TDC.
When determining the opening degree of the intake control valve 14 according to the in-cylinder temperature and engine load in the compression TDC, as shown in FIGS. 3 and 4, the lower the in-cylinder temperature in the compression TDC, As the engine load is larger, the opening degree of the intake control valve 14 is further reduced to further strengthen the gas flow in the cylinder.

When the gas flow in the cylinder is strengthened, the homogeneity of the fuel in the combustion chamber is increased, and the heat transfer characteristics of the self-ignition reaction molecules are improved. Can be expanded to the high load side.
When the in-cylinder temperature is the optimum high temperature for compression self-ignition combustion, the opening degree of the intake control valve 14 is determined according to the engine load.

In step S8, the minus overlap period is controlled by controlling the valve timing and the valve lift amount of the intake valve 4 and the exhaust valve 12.
In the present application, the minus overlap period is a period in which both valves are closed from when the exhaust valve 12 is closed until the intake valve 4 is opened.
In the control of the minus overlap period, as shown in FIG. 5 and FIG. 6, the in-cylinder temperature in the compression TDC needs to be increased and the in-cylinder temperature needs to be increased, and the engine rotational speed is high and the reaction speed needs to be increased. When there is, the negative overlap period is further increased and the residual gas amount (internal EGR amount) is controlled to increase.

By setting the minus overlap period, the in-cylinder temperature can be preserved by the residual gas. In this embodiment, the reaction of the high octane fuel is promoted by the reaction heat of the low-octane fuel with good ignitability. The quantity requirement, i.e., the minus overlap period requirement, is shorter.
If the minus overlap period can be shortened, the amount of fresh air flowing into the cylinder can be increased, the engine torque can be increased as shown in FIG. 7, and the engine operating region by the compression self-ignition combustion can be increased. Can be expanded.

The control of the minus overlap period is performed as shown in FIG.
FIG. 8 shows a case where a combination of a variable valve event / lift mechanism (denoted as VEL in the figure) and a variable valve timing mechanism (denoted as VTC in the figure) is used. By reducing the lift amount of the intake valve and retarding the central phase of the operating angle of the intake valve, while reducing the lift amount of the exhaust valve and advancing the central phase of the exhaust valve operating angle, The minus overlap period (-O / L period) is increased.

FIG. 9 shows a case where an electromagnetic valve (referred to as EMV in the figure) is used. During compression self-ignition combustion, the opening timing of the intake valve is greatly delayed to reduce the operating angle of the intake valve. The closing time is greatly advanced to reduce the operating angle, thereby increasing the minus overlap period (-O / L period).
In step S9, the injection amount of the low octane fuel is determined.

  Specifically, as shown in FIG. 10 and FIG. 11, the higher the engine speed and the higher the reaction speed, the lower the in-cylinder temperature at the compression TDC, and the higher octane fuel due to the reaction heat of the lower octane fuel. The more the required acceleration of the reaction is, the more the injection amount of the low octane fuel is increased, and the reaction of the high octane fuel is sufficiently promoted by the reaction heat of the low octane fuel with good ignitability.

Further, the lower the cooling water temperature, the larger the correction amount of the low octane number fuel injection is corrected to ensure the stability of the compression self-ignition combustion during cold operation.
In step S10, the injection amount of the high octane fuel is determined based on the engine speed and the engine load.
That is, the reaction of the high octane fuel becomes the main combustion, and the engine load (engine torque) is controlled by controlling the injection amount of the high octane fuel.

In step S11, the injection timing of the high octane fuel that is directly injected into the cylinder is determined.
The injection timing of the high octane number fuel is set as shown in FIG. 12 according to the engine speed Ne.
That is, when the engine rotational speed is higher than the reference rotational speed NsS and a high reaction speed is required, by setting the injection timing before the intake TDC during the minus overlap period, the high octane fuel is injected into the residual gas having a high temperature. To be.

  On the other hand, in the rotation region lower than the reference rotation NsS, if the high octane fuel is injected during the minus overlap period, the reaction is too fast to cause knocking, so that it is injected after the minus overlap period, and The injection timing is gradually delayed from the intake stroke to the compression stroke in accordance with the increase in the rotation speed in the rotation region lower than the reference rotation NsS.

If the injection timing of high-octane fuel is changed during the compression stroke in response to the increase in engine rotational speed, the high-octane fuel is stratified in the combustion chamber, and a reaction speed commensurate with the increase in rotational speed can be obtained. .
In addition, the injection timing of the low octane fuel injected into the intake port is set to a constant crank angle position before the intake valve opening timing.

In step S12, fuel injection is performed at the determined injection amount and injection timing.
As described above, in the present embodiment, the injection amount of the low octane fuel, the injection amount of the high octane fuel, the injection timing of the high octane fuel, the gas flow generation, the valve according to the engine speed, the engine load, and the in-cylinder temperature. The timing (minus overlap period) is determined, and the injection of the low-octane fuel and the high-octane fuel is individually controlled, and the variable valve mechanism 13 and the intake control valve 14 are controlled (see FIG. 13).

  And according to this embodiment, the heat transfer of the reaction heat of the low octane number fuel is promoted by injecting the low octane number fuel and enhancing the gas flow, and by controlling the injection timing and the minus overlap period. Since the reaction rate of the high-octane fuel can be optimally controlled, the reaction of the high-octane fuel can be slowed down and the rotation region and the load region in which the compression self-ignition combustion can be performed can be expanded (see FIG. 14).

By the way, when it is determined in step S3 that the remaining amount of the low-octane fuel is below the minimum amount MIN, the reaction of the high-octane fuel cannot be promoted by the reaction heat of the low-octane fuel, and the compression auto-ignition combustion is not performed. The possible area becomes a narrower limited area.
Therefore, if it is determined in step S3 that the remaining amount of the low octane fuel is below the minimum amount MIN, the process proceeds to step S13, and whether or not it is within the operating range in which compression self-ignition combustion is possible with only the high octane fuel. Is determined.

  Specifically, the engine torque T is smaller than the high octane number self-ignitable maximum torque TH2 and larger than the high octane number self-ignitable minimum torque TL2 (TL2 <T <TH2), and the engine speed Ne ( rpm) is smaller than the maximum number of revolutions NeH2 capable of high-octane self-ignition and larger than the minimum number of revolutions NeL2 capable of high-octane self-ignition (NeL2 <Ne <NeH2). It is determined that it is within the possible area.

Here, as shown in FIG. 14, the compression self-ignition combustion possible region B determined in step S <b> 13 is changed to the region A with respect to the compression self-ignition combustion possible region A determined in the step S <b> 3. It is a narrower area to be included.
When it is determined that TL2 <T <TH2 and NeL2 <Ne <NeH2, it is not possible to perform compression self-ignition combustion using only high-octane fuel, so the routine proceeds to step S2 and spark ignition combustion is performed. .

On the other hand, if it is determined that TL2 <T <TH2 and NeL2 <Ne <NeH2, compression self-ignition combustion can be performed using only high-octane fuel, and the process proceeds to step S14.
In step S14, the compression self-ignition combustion operation using only the high octane fuel is started.

In step S15, the in-cylinder temperature in the compression TDC is detected.
In step S16, the opening degree (gas flow) of the intake control valve 14 is controlled in the same manner as in step S7.
In step S17, the valve timing (minus overlap period) is controlled as in step S8.

In steps S18 and 19, the injection amount and injection timing of the high octane fuel are determined in the same manner as in steps S10 and 11, and the high octane fuel injection is executed in step S20.
FIG. 15 is a system configuration diagram of a compression self-ignition internal combustion engine according to the second embodiment.
The system configuration shown in FIG. 15 is configured such that the first fuel injection valve 7 that injects the fuel directly injects the low-octane fuel into the cylinder 5 in the same manner as the second fuel injection valve 8 that injects the high-octane fuel. Only the differences are different from the system configuration shown in FIG.

The flowchart of FIG. 16 shows a state of control by the engine control unit 20 in the second embodiment.
The flowchart in FIG. 16 differs from the flowchart in FIG. 2 only in that step S11 (2) for determining the injection timing of the low octane fuel is added, and the other steps are the same as those in FIG. The same processing as in the flowchart of FIG.

The determination of the injection timing of the low octane fuel in step S11 (2) is performed according to the engine speed as shown in FIG.
That is, similarly to the injection timing of the high octane fuel, in the high engine speed range where the engine speed is higher than the reference rotation NsS, the injection timing before the intake TDC during the minus overlap period is set as the injection timing of the low octane fuel.

On the other hand, in the low speed range where the engine speed is lower than the reference speed NsS, the intake stroke after the minus overlap period is set as the injection timing of the low octane fuel, but in the low speed range lower than the reference speed NsS. As the rotational speed increases, the injection timing of the low-octane fuel is gradually advanced to approach the intake TDC.
The closer to the intake TDC, the higher the pressure in the cylinder, the faster the reaction of the low-octane fuel, and it is possible to meet the demand for increasing the reaction speed due to the increase in the rotational speed.

FIG. 18 is a system configuration diagram of a compression self-ignition internal combustion engine according to the third embodiment.
In the configuration shown in FIG. 18, the first fuel injection valve 7 is configured to inject low-octane fuel into the intake collector 19.
In this configuration, the injection amount is controlled in the same manner as the flowchart of FIG. 2 described in the first embodiment in which the first fuel injection valve 7 injects fuel into the intake port.

FIG. 19 is a system configuration diagram of a compression self-ignition internal combustion engine according to the fourth embodiment. In this embodiment, an exhaust gas recirculation device 31 is provided, and an exhaust amount recirculated by the exhaust gas recirculation device 31 and heating of the recirculated exhaust gas by a heater. The in-cylinder temperature in the compressed TDC is controlled by the temperature.
The exhaust gas recirculation device 31 includes an exhaust gas recirculation pipe 32, a heater 33 interposed in the exhaust gas recirculation pipe 32, and an exhaust gas recirculation control valve 34 that controls an exhaust gas recirculation amount by the exhaust gas recirculation pipe 32.

The in-cylinder temperature is controlled by controlling the exhaust gas recirculation amount and the heating temperature by the heater 33 instead of controlling the above-described minus overlap period.
Specifically, when an increase in the minus overlap period is requested, that is, in response to a request to increase the in-cylinder temperature, the exhaust gas recirculation amount is increased and the heating temperature by the heater 33 is increased to increase the heat of the exhaust gas being recirculated. To increase the in-cylinder temperature.

  The in-cylinder temperature can be controlled by combining the control of the minus overlap period and the control of the exhaust gas recirculation amount and / or the heating temperature of the recirculated exhaust gas.

The system block diagram of the internal combustion engine in 1st Embodiment. The flowchart which shows the injection control in 1st Embodiment. The diagram which shows the correlation with compression TDC in-cylinder temperature and the opening degree of an intake control valve. The diagram which shows the correlation with an engine load and the opening degree of an intake control valve. The diagram which shows the correlation with compression TDC in-cylinder temperature and a minus overlap period. The diagram which shows the correlation with an engine speed and a minus overlap period. The diagram which shows the change of the intake air amount and engine torque by the reduction | decrease of a minus overlap period. The figure which shows control of the minus overlap period by the combination of a variable valve event lift mechanism and a variable valve timing mechanism. The figure which shows control of the minus overlap period by an electromagnetic valve. The diagram which shows the correlation with an engine speed and the low-octane fuel injection quantity. The diagram which shows the correlation with compression TDC in-cylinder temperature and low octane number fuel injection amount. The diagram which shows the correlation with the injection timing of high octane fuel and the engine speed. The time chart which shows roughly the control characteristic of 1st Embodiment. The diagram which shows the compression self-ignition combustion area with respect to engine rotational speed and engine load. The system block diagram of the internal combustion engine in 2nd Embodiment. The flowchart which shows the injection control in 2nd Embodiment. The diagram which shows the correlation with the injection timing of low octane number fuel and an engine speed. The system block diagram of the internal combustion engine in 3rd Embodiment. The system block diagram of the internal combustion engine in 4th Embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Internal combustion engine, 2 ... Air cleaner, 3 ... Supercharger, 4 ... Intake valve, 5 ... Cylinder, 6 ... Intake port, 7 ... 1st fuel injection valve, 8 ... 2nd fuel injection valve, 9 ... Low octane number fuel Tank 10, high octane fuel tank 11, spark plug, 12 exhaust valve, 13 variable valve mechanism, 14 intake control valve, 20 engine control unit, 21 rotational speed sensor, 22 water temperature sensor, 23 , 24 ... Remaining sensor 23, 24, 25 ... Cylinder temperature sensor

Claims (11)

A first fuel injection means for injecting a low octane fuel and a second fuel injection means for injecting a high octane fuel are separately provided, and the fuel injection amount and the injection timing of the low octane fuel and the high octane fuel are mutually independent. In a fuel injection device for a compression self-ignition internal combustion engine to be controlled ,
The second fuel injection means directly injects the high-octane fuel into the cylinder and sets the injection timing of the high-octane fuel according to the engine rotational speed. When the engine rotational speed exceeds the reference speed, The injection timing of the high octane fuel is set during the negative overlap period of the engine valve, and when the engine rotational speed is lower than the reference speed, the higher the engine rotational speed after the negative overlap period, the slower the timing is A fuel injection device for a compression self-ignition internal combustion engine, characterized by: A first fuel injection means for injecting a low octane fuel and a second fuel injection means for injecting a high octane fuel are separately provided, and the fuel injection amount and the injection timing of the low octane fuel and the high octane fuel are mutually independent. In a fuel injection device for a compression self-ignition internal combustion engine to be controlled,
The first fuel injection means injects the low octane fuel directly into the cylinder, and the injection timing of the low octane fuel is set according to the engine rotational speed. When the engine rotational speed exceeds the reference speed, The low-octane fuel injection timing is set during the engine valve minus overlap period, and when the engine speed falls below the reference speed, the low-octane fuel injection timing approaches the intake TDC as the engine speed increases. A fuel injection device for a compression self-ignition internal combustion engine, characterized in that A first fuel injection means for injecting a low octane fuel and a second fuel injection means for injecting a high octane fuel are separately provided, and the fuel injection amount and the injection timing of the low octane fuel and the high octane fuel are mutually independent. In a fuel injection device for a compression self-ignition internal combustion engine to be controlled,
A fuel injection device for a compression self-ignition internal combustion engine, wherein an exhaust gas recirculation amount and / or a heating temperature of the recirculated exhaust gas is set according to an in-cylinder temperature and / or an engine speed . The second fuel injection unit injects the high octane fuel directly into the cylinder, and the first fuel injection unit injects the low octane fuel into the upstream side of the intake valve or directly into the cylinder. A fuel injection device for a compression self-ignition internal combustion engine according to any one of claims 1 to 3. The compression self-ignition internal combustion engine according to any one of claims 1 to 4, wherein the injection amount and the injection timing of the low octane number fuel and the high octane number fuel are set according to the engine load and / or the engine rotational speed. Engine fuel injection device.   The fuel injection device for a compression self-ignition internal combustion engine according to any one of claims 1 to 5, wherein the injection amount of the low octane fuel is set according to the in-cylinder temperature and / or the engine rotational speed.   The fuel injection device for a compression self-ignition internal combustion engine according to any one of claims 1 to 6, wherein the injection amount of the high octane fuel is set according to the engine load and the engine speed.   The fuel injection device for a compression self-ignition internal combustion engine according to any one of claims 1 to 7, wherein a minus overlap period of the engine valve is set in accordance with an in-cylinder temperature and / or an engine speed. . The fuel injection device for a compression self-ignition internal combustion engine according to any one of claims 1 to 8, further comprising gas flow generation means for generating a gas flow in the cylinder. The fuel injection device for a compression self-ignition internal combustion engine according to claim 9, wherein the gas flow generation means is controlled in accordance with an in-cylinder temperature and / or an engine speed. The engine's operating range is divided into a compression self-ignition combustion region and a spark ignition combustion region, and when the remaining amount in the fuel tank that stores the low-octane fuel falls below the minimum amount, the compression self-fuel only by the high-octane fuel The fuel injection device for a compression self-ignition internal combustion engine according to any one of claims 1 to 10, wherein the ignition combustion is performed only in a narrower operating region.

Images