JP2007023812A - Fuel injection controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fuel injection controller capable of suitably suppressing the excessive increase of fuel pressure in an accumulator when fuel is supplied into the accumulator by a fuel pump. <P>SOLUTION: In a step S6, a fuel amount to be supplied into a common rail from the fuel pump is calculated depending on the target value of the fuel pressure and the fuel injection amount. In a step S10, an overshoot amount ΔP in the common rail, which is caused by decrease in the fuel injection amount and the leakage amount followed by the fuel injection, is calculated. In a step S12, when it is judged the sum of the fuel detection value and ΔP exceeds a predetermined value, the fuel in the common rail is forcedly fed out by operating a pressure reducing valve in a step S16. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention uses a fuel injection device that includes a pressure accumulation chamber that stores fuel in a high pressure state, a fuel pump that pressurizes and supplies fuel to the pressure accumulation chamber, and a fuel injection valve that injects fuel stored in the pressure accumulation chamber. The present invention relates to a fuel injection control device that performs fuel injection control.

  As this type of fuel injection control device, a fuel injection control device for a common rail type diesel engine that stores high-pressure fuel in a common rail (pressure accumulation chamber) common to each cylinder and injects fuel in the common rail through a fuel injection valve is well known. It is. In such a fuel injection control device, the fuel pressure in the common rail is controlled to follow the target value by operating the fuel pump that pumps up the fuel in the fuel tank and supplies it to the common rail. However, during transient operation that changes the target value of the fuel pressure in the common rail, even if the fuel pressure in the common rail exceeds the target value, depending on the operation of the fuel pump, the fuel pressure in the common rail may follow the target value. I can't control it.

  Therefore, conventionally, as seen in, for example, Patent Document 1 below, when the fuel pressure in the common rail exceeds a target value by a predetermined value or more, a device that operates the pressure reducing valve to return the fuel in the common rail to the fuel tank has been proposed. ing. Thereby, even if it is a case where the target value of the fuel pressure in a common rail is changed, the fuel pressure in a common rail can be suitably made to follow a target value.

  Incidentally, in recent years, an intake metering type fuel pump has been proposed in which the amount of fuel supplied to the common rail is determined by adjusting the amount of fuel to be sucked (Patent Document 2). When this fuel pump is used, the fuel once sucked is supplied to the common rail. For this reason, there is a possibility that the fuel pressure in the common rail will greatly exceed the target value when the vehicle is suddenly decelerated.

  That is, for example, when the accelerator pedal is suddenly released from the state where it is fully depressed, until the accelerator pedal is released, a fuel amount sufficient to supplement the fuel injection amount at the time of high engine load is from the fuel pump. It is calculated as the amount of fuel supplied to the common rail, and the fuel pump is operated based on this. On the other hand, when the accelerator pedal is released, the fuel pump is operated so as to reduce the supply amount in order to supply the fuel corresponding to the accelerator pedal to the common rail. However, the fuel already sucked into the fuel pump immediately before deceleration is supplied to the common rail even after the accelerator pedal is released. At this time, when the fuel injection is stopped by releasing the accelerator pedal, the fuel pressure in the common rail is greatly increased by the fuel supplied to the common rail.

  Here, according to the control device described in Patent Document 1, when the fuel pressure in the common rail rises by a predetermined value or more than the target value, the pressure reducing valve is opened to avoid further increase in the fuel pressure. I can. However, when the target value of the fuel pressure is relatively close to the upper limit value of the common rail pressure resistance, the fuel pressure in the common rail may reach the upper limit value of the pressure resistance before the pressure reducing valve is opened. Incidentally, for example, Patent Document 3 is another example of the fuel injection control device.

The pressure control chamber is not limited to the above-described control device, and includes a pressure accumulation chamber that stores fuel in a high pressure state, a fuel pump that pressurizes and supplies fuel to the pressure accumulation chamber, and a fuel injection valve that injects fuel stored in the pressure accumulation chamber. In the case where the fuel injection control is performed using the fuel injection device, such a situation that the fuel pressure in the pressure accumulating chamber may excessively increase is generally common.
JP 2002-371940 A JP 2002-130026 JP JP 2003-307149 A

  The present invention has been made to solve the above-described problems, and has as its object to store a pressure accumulation chamber that stores fuel in a high pressure state, a fuel pump that pressurizes and supplies the fuel to the pressure accumulation chamber, and a pressure storage chamber that stores the fuel. An object of the present invention is to provide a fuel injection control device capable of suitably suppressing an excessive increase in fuel pressure in a pressure accumulating chamber when performing fuel injection control using a fuel injection device including a fuel injection valve that injects the injected fuel. is there.

  Hereinafter, means for solving the above-described problems and the effects thereof will be described.

  According to a first aspect of the present invention, there is provided a predicting means for predicting whether or not the amount of fuel supplied to the pressure accumulating chamber is greater than a predetermined amount than the amount of fuel discharged from the pressure accumulating chamber when fuel is injected by the fuel injection valve. And a correcting means for forcibly increasing the amount of fuel output from the pressure accumulating chamber when the predicting means predicts that the predetermined amount or more will be increased.

  In the above configuration, for example, when the command injection amount suddenly decreases due to a request for rapid deceleration of the vehicle, excess pressure is accumulated in the accumulator by the inertial high-pressure wave of the high-pressure fuel in the pipe connecting the fuel pump outlet and the accumulator inlet. Fuel may be supplied. Here, in the above-described configuration, the fuel output amount is forcibly increased when it is predicted that the fuel amount in the pressure accumulating chamber will exceed the fuel output amount by a predetermined amount before the fuel pressure once rises excessively. Therefore, an excessive increase in fuel pressure can be suitably suppressed.

  According to a second aspect of the present invention, in the first aspect of the invention, the fuel pump is a suction metering pump that determines the amount of fuel to be supplied to the pressure accumulating chamber by adjusting the amount of fuel to be sucked.

  In the above configuration, there is a time gap from when the fuel is sucked into the fuel pump to when the sucked fuel is supplied to the pressure accumulating chamber. During this time, for example, when the command injection amount suddenly decreases due to, for example, a sudden deceleration request of the vehicle, the amount of fuel flowing out from the pressure accumulating chamber decreases rapidly. In this case, surplus fuel is supplied to the pressure accumulation chamber by supplying the sucked fuel to the pressure accumulation chamber. For this reason, in the said structure, the excessive raise of the fuel pressure in a pressure accumulation chamber tends to arise especially. For this reason, in the said structure, it is the structure which can show | play suitably the effect of a correction | amendment means.

  According to a third aspect of the present invention, in the invention according to the second aspect, the predicting means calculates a difference between the fuel output amount and the fuel input amount at the time of the intake with respect to the command injection amount immediately before the fuel intake by the fuel pump. It is characterized by comprising a balance calculation means for calculating on the basis of the subsequent change in the command injection amount.

  In the above configuration, when the command injection amount after the fuel is sucked by the fuel pump is smaller than the command injection amount until just before the suction, the sucked fuel amount is supplied to the pressure accumulation chamber, so that the fuel pressure in the pressure accumulation chamber is reduced. There is a risk of overshoot. In this regard, in the above-described configuration, it can be determined that the amount of incoming fuel is greater than the amount of outgoing fuel under such circumstances.

  According to a fourth aspect of the present invention, in the invention according to the third aspect, the predicting means calculates the difference between the fuel output amount and the fuel input amount by calculating the amount of intake by the fuel pump for the fuel supplied to the pressure accumulating chamber this time. It is characterized by comprising a balance calculation means for calculating based on a variation of the current command injection amount with respect to the command injection amount at the time of calculation.

  In the above configuration, the main factor that the fuel pressure in the pressure accumulating chamber rises excessively is that the command injection amount suddenly decreases. Here, according to the above configuration, the output fuel amount and the incoming fuel are based on the variation of the current command injection amount with respect to the command injection amount at the time of calculating the intake amount by the fuel pump for the fuel supplied this time to the pressure accumulating chamber. Calculate the difference from the quantity. For this reason, the difference is calculated based on the fluctuation amount of the current command injection with respect to the command injection amount referred to when calculating the intake amount by the fuel pump for the fuel supplied this time. For this reason, it is possible to appropriately determine whether or not the fuel pressure in the pressure accumulating chamber is excessively increased due to the decrease in the command injection amount.

  According to a fifth aspect of the present invention, in the invention according to the fourth aspect, the balance calculation means calculates the difference between the fuel output amount and the fuel amount entered from the command injection amount at the time of calculation and the fuel injection valve at the time of calculation. And a difference between the current command injection amount and the current leak amount.

  In the above configuration, at the time of sudden deceleration or the like, in addition to the sudden decrease in the command injection amount, the leak amount also sharply decreases. For this reason, surplus fuel will be supplied at the time of rapid deceleration by the control based on the command injection amount and the leak amount before sudden decrease. In this regard, according to the above configuration, even if the command injection amount and the leak amount are reduced, an excessive increase in the fuel pressure due to the excess fuel being supplied to the pressure accumulating chamber due to this is suitably suppressed. can do.

  According to a sixth aspect of the present invention, in the invention according to the fourth aspect, means for taking in a detection result of a detecting means for detecting a fuel pressure in the pressure accumulating chamber, target fuel pressure calculating means for calculating a target fuel pressure in the pressure accumulating chamber, and the detection Operating means for operating the fuel pump to control the fuel pressure to the target fuel pressure, and the amount of the entered fuel is calculated based on a difference between the detected fuel pressure and the target fuel pressure and the command injection amount. The balance calculating means calculates the difference between the fuel output amount and the amount of entered fuel by subtracting at least the current command injection amount from the amount of fuel entered at the time of the calculation. Features.

  In the above configuration, the difference between the output fuel amount and the input fuel amount is calculated by subtracting at least the current command injection amount from the input fuel amount at the time of calculation, which is the amount of fuel supplied to the current accumulator. For this reason, it is possible to suitably suppress an excessive increase in the fuel pressure in the pressure accumulating chamber due to the surplus fuel being supplied into the pressure accumulating chamber with at least a sudden decrease in the command injection amount.

  The invention according to claim 7 is the invention according to claim 4 or 6, wherein means for capturing the detection result of the detection means for detecting the fuel pressure in the pressure accumulation chamber, and target fuel pressure calculation means for calculating the target fuel pressure in the pressure accumulation chamber; And an operating means for operating the fuel pump to control the detected fuel pressure to a target fuel pressure, wherein the amount of entered fuel is a difference between the detected fuel pressure and the target fuel pressure, and the command injection amount. The balance calculation means calculates the difference between the fuel output amount and the incoming fuel amount as the difference between the value at the time of calculation of the incoming fuel amount and the current value. It is characterized by calculating.

  The amount of fuel entered includes not only the amount of fuel that has flowed out of the pressure accumulating chamber before that, but also the amount of fuel for setting the actual fuel pressure in the pressure accumulating chamber to the target fuel pressure. For this reason, the said difference about the amount of entering fuel turns into the fuel amount which raises an actual fuel pressure with respect to this target fuel pressure. For this reason, it is also possible to improve the followability with respect to the target fuel pressure by using the above difference in the amount of fuel entering.

  An eighth aspect of the invention according to any one of the first to seventh aspects further comprises fuel pressure predicting means for calculating a fuel pressure in the pressure accumulating chamber based on a difference between the fuel output amount and the fuel input amount. The predicting means performs prediction as to whether or not the fuel pressure in the pressure accumulating chamber calculated by the fuel pressure predicting means increases to a vicinity of a predetermined upper limit value. .

  According to the above configuration, when the fuel pressure predicted by the fuel pressure prediction means rises to the vicinity of the predetermined upper limit value, the amount of fuel output is forcibly increased by the correction means. An increase can be suitably suppressed.

  According to a ninth aspect of the present invention, in the invention according to any one of the first to eighth aspects, the pressure accumulating chamber is provided with a pressure reducing valve that returns the fuel in the pressure accumulating chamber to a fuel tank that stores the fuel. The fuel output is forcibly increased by forcibly opening the pressure reducing valve.

  In the said structure, the raise of the fuel pressure in a pressure accumulation chamber can be suppressed suitably because the fuel in a pressure accumulation chamber is returned to a fuel tank.

  A tenth aspect of the present invention is the invention according to any one of the first to eighth aspects, wherein the correction means injects fuel through the fuel injection valve at a timing that does not contribute to the output of the engine. Is forcibly increased.

  In the above configuration, the increase in the fuel pressure in the pressure accumulating chamber can be suitably suppressed without increasing the output of the engine.

  According to a twelfth aspect of the present invention, in the invention according to any one of the first to ninth aspects, the correction means finally adds the commanded fuel injection amount calculated based on the accelerator operation amount to the fuel amount to be discharged. The output fuel amount is forcibly increased by using the command injection amount.

  In the above configuration, the fuel that is forced to flow out of the pressure accumulating chamber can be effectively used as the driving force of the engine.

(First embodiment)
Hereinafter, a first embodiment in which a fuel injection control device according to the present invention is applied to a fuel injection control device of a diesel engine will be described with reference to the drawings.

  FIG. 1 shows the configuration of the fuel injection control device and the like.

  As shown in the drawing, the fuel in the fuel tank 2 that stores the fuel is pumped up by the fuel pump 10 and supplied to the common rail 30 through the supply passage 21. Here, the fuel pump 10 includes a low-pressure pump 11 that pumps fuel in the fuel tank 2, a metering control valve 12 that communicates and blocks the low-pressure pump 11 and its downstream side, and a low-pressure pump via the metering control valve 12. 11 is provided with a high-pressure pump 15 for supplying the fuel sent from 11 to the outside. Here, the high pressure pump 15 corresponds to the first passage 13 and the second passage 14 which are fuel passages branched into two on the downstream side of the metering control valve 12, and the first high pressure pump 15 sucks the fuel in these passages. A plunger portion 18 provided with a plunger 16 and a second plunger 17 is provided. The hollow portion 19 inside the plunger portion 18 is provided with a rotating body 20 connected to the output shaft of the diesel engine. The first plunger 16 and the second plunger 17 are alternately displaced from the top dead center toward the bottom dead center by the rotation of the rotating body 20, so that the fuel in the first passage 13 and the second passage 14 is transferred. It is alternately sucked into the high-pressure pump 15.

  That is, as shown in FIG. 2A, when the second plunger 17 is displaced to the bottom dead center, the fuel in the second passage 14 is sucked with the displacement of the second plunger 17. On the other hand, at this time, since the first plunger 16 is displaced toward the top dead center, the fuel is pressurized and supplied to the outside through the first passage 13. Then, as shown in FIG. 2B, when the first plunger 16 is displaced to the bottom dead center, fuel is sucked through the first passage 13. On the other hand, at this time, since the second plunger 17 is displaced toward the top dead center, fuel is pressurized and supplied to the outside through the second passage 14.

  As shown in FIG. 1, the first passage 13 and the second passage 14 join downstream and are connected to the supply passage 21. In addition, check valves 22 and 23 are provided on the upstream side of the first passage 13 and the second passage 14, respectively. Thus, the backflow of fuel when the first plunger 16 and the second plunger 17 are displaced toward the top dead center is avoided.

  The fuel supplied by the fuel pump 10 is determined by the amount of fuel sucked into the fuel pump 10 (more precisely, the amount of fuel sucked into the high-pressure pump 15). That is, fuel is drawn into the high-pressure pump 15 by opening the metering control valve 12 when the first plunger 16 or the second plunger 17 is displaced toward the bottom dead center. The intake amount is determined by the valve closing timing of the metering control valve 12. In other words, the amount of fuel supplied to the outside from the fuel pump 10 is determined by the closing timing of the metering control valve 12.

  On the other hand, the fuel supplied to the common rail 30 is supplied to the fuel injection valve 40 of each cylinder (here, four cylinders are illustrated) via the high-pressure fuel passage 32. The configuration of the fuel injection valve 40 is shown in FIG.

  A cylindrical needle storage portion 42 is provided at the tip of the fuel injection valve 40. The needle storage portion 42 stores a nozzle needle 44 that can be displaced in the axial direction. The nozzle needle 44 is seated on an annular needle seat portion 46 formed at the tip of the fuel injection valve 40, thereby blocking the needle storage portion 42 from the outside (engine combustion chamber), while the needle seat portion 46. The needle storage part 42 is communicated with the outside by separating from the position. Further, high pressure fuel is supplied from the common rail 30 to the needle storage portion 42 via the high pressure fuel passage 32.

  A back pressure chamber 50 is formed on the back side of the nozzle needle 44 (the side opposite to the side facing the needle seat portion 46). High pressure fuel is supplied from the common rail 30 to the back pressure chamber 50 via the high pressure fuel passage 32. Further, a needle spring 48 is provided at an intermediate portion of the nozzle needle 44, and the nozzle needle 44 is pushed toward the distal end side of the fuel injection valve 40 by the needle spring 48.

  On the other hand, the low pressure fuel passage 34 communicates with the fuel tank 2 as shown in FIG. 1, and the low pressure fuel passage 34 and the back pressure chamber 50 are communicated and blocked by the valve body 54. That is, the orifice 52 that connects the back pressure chamber 50 and the low pressure fuel passage 34 is closed by the valve body 54, whereby the back pressure chamber 50 and the low pressure fuel passage 34 are blocked, while the orifice 52 is opened. Thus, the back pressure chamber 50 and the low pressure fuel passage 34 are communicated with each other.

  The valve body 54 is pushed toward the distal end side of the fuel injection valve 40 by a valve spring 56. Further, the valve body 54 can be displaced to the rear side of the fuel injection valve 40 by being attracted by the electromagnetic force of the electromagnetic solenoid 58.

  In such a configuration, when the electromagnetic solenoid 58 is not energized and the attractive force by the electromagnetic solenoid 58 is not working, the valve element 54 closes the orifice 52 by the force of the valve spring 56. On the other hand, the nozzle needle 44 is pushed toward the distal end side of the fuel injection valve 40 by the needle spring 48 and is in a state of being seated on the needle seat portion 46 (the fuel injection valve 40 is closed).

  Here, when the electromagnetic solenoid 58 is energized, the valve element 54 is displaced to the rear side of the fuel injection valve 40 by the suction force of the electromagnetic solenoid 58 and opens the orifice 52. Thereby, the high pressure fuel in the back pressure chamber 50 moves to the low pressure fuel passage 34 via the orifice 52. For this reason, the pressure applied to the nozzle needle 44 by the high-pressure fuel in the back pressure chamber 50 is smaller than the pressure applied to the nozzle needle 44 by the high-pressure fuel in the needle housing portion 42. Then, when the force that pushes the nozzle needle 44 rearward of the fuel injection valve 40 due to this pressure difference becomes larger than the force that the needle spring 48 pushes the nozzle needle 44 toward the distal end side of the fuel injection valve 40, the nozzle needle 44 moves to the needle seat. In this state, the seat is separated from the portion 46 (the fuel injection valve 40 is opened).

  As shown in FIG. 1, the common rail 30 is provided with a pressure reducing valve 36 that communicates and blocks the inside of the common rail 30 and the low pressure fuel passage 34. The common rail 30 is provided with a fuel pressure sensor 38 that detects the fuel pressure inside the common rail 30.

  The detection values of various sensors such as the detection value of the fuel pressure sensor 38 and the detection value of the accelerator sensor 64 that detects the depression amount (accelerator operation amount) of the accelerator pedal 62 are taken into the electronic control unit 60. The electronic control device 60 is configured to include a central processing unit and an appropriate memory. Based on detection values of various sensors, the electronic control device 60 includes various actuators such as a metering control valve 12, a pressure reducing valve 36, and a fuel injection valve 40. Manipulate. In particular, the electronic control unit 60 performs fuel injection control by operating the fuel injection valve 40. FIG. 4 shows functional blocks related to fuel injection control.

  In FIG. 4, the solid line blocks indicate the inside of the electronic control device 60, and the broken line blocks indicate the outside of the electronic control device 60.

  The injection amount command value calculation unit M1 is a command for the amount of fuel injected through the fuel injection valve 40 based on the amount of depression of the accelerator pedal 62 (accelerator operation amount) by the user and the rotational speed of the output shaft of the diesel engine. A value (command injection amount) is calculated. The command injection amount calculated here is converted into the energization time of the fuel injection valve 40 (specifically, the electromagnetic solenoid 58) in the energization time calculation unit M2. Then, according to the energization time calculated here, the fuel injection valve 40 is energized by the drive circuit M3.

  On the other hand, the target pressure calculation unit M4 sets a target value (target fuel pressure) of the fuel pressure in the common rail 30 based on the command injection amount and the rotational speed. Incidentally, the target fuel pressure is low during idling, and becomes higher as the engine moves to medium to high speed rotation. Then, PID control is performed so that the detected value of the fuel pressure in the common rail 30 follows the target value. Specifically, the operation amount calculated by PID control is calculated as the duty ratio of the metering control valve 12 of the fuel pump 10. Based on this, the fuel pressure in the common rail 30 is controlled by operating the metering control valve 12 by the drive circuit M5.

  Here, the fuel injection control according to the present embodiment will be further described with reference to FIG.

  FIG. 5A shows the calculation timing of the fuel supply amount (fuel intake amount) of the fuel pump 10 by the electronic control unit 60. FIG. 5B shows the transition of the fuel intake and supply mode by the first plunger 16, and FIG. 5C shows the transition of the fuel suction and supply mode by the second plunger 17, respectively. Further, FIGS. 5D to 5G show the fuel injection timings of the first cylinder to the fourth cylinder, respectively.

  As illustrated, when either the first plunger 16 or the second plunger 17 starts to be displaced from the top dead center toward the bottom dead center, the intake amount by the fuel pump 10 is calculated. As a result, the intake amount is determined by the operation mode of the metering control valve 12 when the first plunger 16 and the second plunger 17 are displaced toward the bottom dead center.

  Further, in the present embodiment, the fuel is injected through the fuel injection valve 40 corresponding to the third cylinder or the fourth cylinder corresponding to the time when the fuel is supplied from the first plunger 16 to the common rail 30. Further, the fuel is injected through the fuel injection valve 40 corresponding to the first cylinder or the second cylinder corresponding to the time when the fuel is supplied from the second plunger 17 to the common rail 30. As described above, in the present embodiment, the fuel supply timing to the common rail 30 by the fuel pump 10 and the fuel injection timing through the fuel injection valve 40 correspond one-to-one.

  By the way, at the time of sudden deceleration when the accelerator pedal 62 is suddenly released by the user, the fuel injection through the fuel injection valve 40 is stopped. However, immediately after the rapid deceleration, the intake amount of fuel calculated immediately before the rapid deceleration is sucked into the fuel pump 10 and supplied to the common rail 30. Specifically, the supplied fuel includes the amount of fuel that has already been sucked by the fuel pump 10 before the sudden deceleration, and the amount of fuel that is supplied from the outlet of the fuel pump 10 to the common rail 30 side. It consists of the amount of fuel that is excessively supplied to the common rail 30 side due to the inertial high-pressure wave in the pipe between the pump 10 and the common rail 30 entrance. Since the fuel injection is stopped immediately after the sudden deceleration, the fuel supplied to the common rail 30 contributes to an increase in the fuel pressure in the common rail 30.

  On the other hand, when the accelerator pedal 62 is suddenly released from the state where the accelerator pedal 62 is fully depressed, the fuel pressure of the common rail 30 immediately before the sudden deceleration becomes a value relatively close to the upper limit value (the upper limit value of the pressure resistance). It is controlled. For this reason, if the fuel supplied to the common rail 30 contributes to an increase in the fuel pressure in the common rail 30, the fuel pressure in the common rail 30 may increase to near the upper limit value.

  Thus, in the present embodiment, when the amount of incoming fuel supplied to the common rail 30 is predicted to be greater than a predetermined amount than the amount of fuel that flows out from the common rail 30 when fuel is injected by the fuel injection valve 40, the fuel that flows out from the common rail 30 is predicted. Force the amount to increase. This will be described in detail below.

  FIG. 6 shows a processing procedure for forcibly increasing the amount of fuel flowing out from the common rail 30. This process is repeatedly executed by the electronic control device 60, for example, at a predetermined cycle.

  In this series of processes, first, in step S2, a command injection amount is calculated based on the accelerator operation amount and the engine speed. This process is performed by the injection amount command value calculation unit M1 shown in FIG. In the subsequent step S4, the target fuel pressure in the common rail 30 is calculated based on the command injection amount and the engine speed. This process is performed by the target pressure calculation unit M4 of FIG.

  The processes in steps S2 and S4 are performed at a predetermined time period such as “8 msec” in synchronization with the period of A / D conversion of the value of the sensor that detects the accelerator operation amount. On the other hand, the process of step S6 is performed at a predetermined crank angle cycle (here, “180 ° CA”). Incidentally, it is desirable that the processing cycle of steps S2 and S4 is shorter than the processing cycle of step S6.

In step S6, the intake amount of the fuel pump 10 is estimated and calculated based on the command injection amount calculated in step S2 and the target value of the fuel pressure calculated in step S4. Here, as shown in FIG. 4, the intake amount is estimated in view of the fact that the actual fuel pressure in the common rail 30 is feedback-controlled by the PID control to the target fuel pressure. Specifically, it is considered that the following amount of fuel is included in the intake amount of the fuel pump 10 by PID control.
a. The command injection amount (this is calculated mainly by an integral term in the steady state. That is, based on the previous outflow mode of fuel in the common rail 30 by fuel injection (the previous decrease mode of fuel pressure), (The control for compensating for this in anticipation of a decrease in the fuel pressure is performed by the integral term, so the command injection amount is included in the integral term.)
b. Amount of fuel leakage accompanying fuel injection This amount of fuel means the amount of fuel leaking to the low-pressure fuel passage 34 side with fuel injection. That is, when the nozzle needle 44 shown in FIG. 3 is separated from the needle seat portion 46 and fuel injection is performed, the fuel in the back pressure chamber 50 flows into the low pressure fuel passage 34 through the orifice 52. To do. For this reason, the fuel injection valve 40 is configured to cause fuel leakage to the low-pressure fuel passage 34 during fuel injection. Incidentally, this leak amount is also calculated mainly by an integral term in a steady state.
c. Fuel amount for controlling the actual fuel pressure in the common rail 30 to the target fuel pressure (this is mainly calculated by proportional control and differential control).
For this reason, in step S6, the intake amount is calculated as the sum of the fuel amount for compensating the differential pressure ΔPC (= target fuel pressure−actual fuel pressure) between the actual fuel pressure and the target fuel pressure, and the command injection amount and the leak amount. Estimate and calculate. Incidentally, the amount of fuel for compensating the differential pressure ΔPC is obtained by using the sum V of the volume of the fuel passage between the fuel pump 10 and the common rail 30 and the volume of the common rail 30 and the volume expansion coefficient E of the fuel. , ΔPC × V / E.

  In the subsequent step S8, the current command injection amount and the leak amount accompanying the injection of the command injection amount are calculated from the intake amount of the fuel pump 10 calculated in the previous previous step S6 (value at the previous previous intake). The subtracted value A is calculated. Further, a value B is calculated by subtracting the command injection amount referred to in the previous previous step S6 and the leak amount accompanying the injection of the same injection amount from the intake amount of the fuel pump 10 calculated in the previous previous step S6. To do.

  Here, the previous previous intake amount is used, as shown in FIG. 5 above, when the fuel amount supplied to the common rail 30 at the current fuel injection timing is the previous previous fuel intake by the fuel pump 10. Because it is a quantity.

  The value B is a value assumed at the time of the previous previous calculation regarding the difference between the amount of fuel flowing out from the common rail 30 and the amount of fuel supplied to the common rail 30. This is not necessarily zero. For example, when the detected value of the fuel pressure in the common rail 30 is lower than the target value, the amount of fuel supplied to the common rail 30 becomes larger than the amount of fuel flowing out from the common rail 30 by feedback control. On the other hand, the value A is the difference between the amount of fuel flowing out from the common rail 30 at the time of the current calculation of the amount of intake by the fuel pump 10 and the value that is about to be supplied to the common rail 30 now.

  In subsequent step S10, an overshoot amount ΔP of the fuel pressure in the common rail 30 is calculated. This overshoot amount ΔP is calculated as an amount resulting from the fact that the calculated value of the amount of fuel flowing out from the common rail 30 decreases during the current intake compared to the previous intake of the fuel pump 10.

  Specifically, the amount of overshoot ΔP is calculated by converting the difference “A−B” into the amount of increase in the fuel pressure in the common rail 30. Here, the reason why the difference “A−B” is used is to calculate an increase in the fuel pressure in the common rail 30 due to a decrease in the amount of fuel flowing out from the common rail 30. That is, as described above, the value B can include the amount of fuel for intentionally changing the fuel pressure in the common rail 30, and therefore, by subtracting this value B from the value A, the amount of fuel by the fuel pump 10 is reduced. The amount of decrease in the amount of fuel flowing out from the common rail 30 from the time of suction to the time of supply from the fuel pump 10 to the common rail 30 is calculated.

  This difference “A−B” is multiplied by the volume expansion coefficient E, and the sum V of the volume in the common rail 30 and the volume of the fuel passage between the fuel pump 10 and the common rail 30 is divided, thereby overshooting. The amount ΔP is calculated.

  In subsequent step S12, it is determined whether or not the value obtained by adding the overshoot amount ΔP to the detected value of the fuel pressure by the fuel pressure sensor 38 exceeds a predetermined value. Here, the predetermined value is set as a value obtained by subtracting the margin amount α from the upper limit value of the breakdown voltage of the common rail 30. Incidentally, steps S6 to S12 correspond to the predicting means, and in particular, the processing of step S12 corresponds to the fuel pressure predicting means.

  In step S12, if it is determined that the value obtained by adding the overshoot amount ΔP to the detected value of the fuel pressure by the fuel pressure sensor 38 exceeds a predetermined value, the amount of fuel flowing out from the common rail 30 is forcibly determined in steps S14 to S16. A process related to a large increase is performed (corresponding to correction means). Incidentally, the condition that the value obtained by adding the overshoot amount ΔP to the detected value of the fuel pressure by the fuel pressure sensor 38 exceeds a predetermined value is greater than the above-described “amount of fuel flowing out from the common rail 30 when fuel is injected by the fuel injection valve 40”. “When the amount of fuel supplied to the common rail 30 increases more than a predetermined amount”.

  In step S14, the forced escape amount C is set as the difference “A−B”. In the subsequent step S16, the pressure reducing valve 36 shown in FIG. 1 is operated in order to release the fuel with the escape amount C. It is desirable to set the valve opening timing and the valve opening period of the pressure reducing valve 36 based on the escape amount C and the detected value of the fuel pressure in the common rail 30. Further, it is desirable that the opening timing of the pressure reducing valve 36 is performed in synchronization with the supply of fuel from the fuel pump 10 to the common rail 30.

  When it is determined in step S12 that the predetermined value is not exceeded, or when the process of step S16 is completed, this series of processes is temporarily ended.

  Here, the effect | action of the process shown in FIG. 6 is demonstrated using FIG.

  FIG. 7A shows the change in the accelerator operation amount, and FIG. 7B shows the change in the command injection amount. 7 (c) and 7 (d) show changes in the fuel intake and supply modes by the first plunger 16 and the second plunger 17, respectively. Further, FIG. 7E shows the transition of the fuel supply amount of the fuel pump 10, and FIG. 7F shows the transition of the fuel pressure in the common rail 30.

  As shown in the figure, before the time t1 when the accelerator pedal 62 is constantly depressed to the maximum, the command injection amount is also constantly a large value. At this time, the first plunger 16 and the second plunger 17 also perform steady intake and supply of fuel. Here, in the present embodiment, integral control is particularly adopted in feedback control of the fuel pressure in the common rail 30. For this reason, the amount of fuel flowing out from the common rail 30 at each fuel injection is compensated by integral control.

  On the other hand, after the time t1 when the accelerator operation amount becomes zero by sudden release of the accelerator pedal 62, the command injection amount also becomes zero. At this time, the target fuel pressure in the common rail 30 also decreases. However, the amount of fuel supplied by the first and second fuel pumps 10 after time t1 is calculated before time t1. For this reason, if the forced fuel outflow process using the pressure reducing valve 36 is not performed, the fuel pressure in the common rail 30 becomes the predetermined value in step S12 of FIG. 6 as shown by the broken line in FIG. There is a risk of overshooting exceeding the fuel pressure indicated by the alternate long and short dash line corresponding to β. On the other hand, in this embodiment, by performing the forced outflow process by the pressure reducing valve 36, it is possible to avoid the fuel pressure of the common rail 30 from overshooting as shown by the solid line in FIG.

  According to the embodiment described in detail above, the following effects can be obtained.

  (1) It is determined that the fuel pressure in the common rail 30 predicted based on the amount of fuel flowing out from the common rail 30 and the amount of entering fuel supplied to the common rail 30 when fuel is injected by the fuel injection valve 40 is greater than or equal to a predetermined value. The fuel in the common rail 30 was forced to flow out. For this reason, it can suppress suitably that the fuel pressure in the common rail 30 exceeds predetermined value (beta).

  (2) Based on the difference “A−B”, in other words, the amount of overshoot was calculated based on the difference between the amount of fuel flowing out from the common rail 30 and the amount of fuel supplied to the common rail 30. For this reason, even if the amount of fuel flowing out from the common rail 30 after the fuel is sucked by the fuel pump 10 is suddenly reduced, it is possible to accurately predict the increase in the fuel pressure in the common rail 30, and as a result, the fuel pressure is predetermined. Exceeding the value can be suitably suppressed.

  (3) The amount of fuel forcibly flowing out from the common rail 30 is defined as a decrease between the command injection amount and the leak amount. Thereby, the raise of the fuel pressure in the common rail 30 can be suppressed more suitably.

  (4) When it is determined by the overshoot amount ΔP that the fuel pressure exceeds a predetermined value, the amount of fuel flowing out is forcibly increased by forcibly opening the pressure reducing valve 36. Thereby, the raise of the fuel pressure in the common rail 30 can be suppressed suitably.

(Second Embodiment)
Hereinafter, the second embodiment will be described with reference to the drawings with a focus on differences from the first embodiment.

  In the present embodiment, the fuel having the escape amount C is injected through the fuel injection valve 40 at a timing that does not contribute to the engine torque. This injection timing is a period between the latter half of the expansion stroke and the exhaust stroke.

  FIG. 8 illustrates a process related to forced outflow of fuel in the common rail 30 according to the present embodiment. FIG. 8A shows the transition of the accelerator operation amount, and FIG. 8B shows the transition of the operation mode of the fuel injection valve 40.

  As shown in the figure, fuel injection is performed at a timing that does not contribute to the torque of the diesel engine after time t11 when the accelerator operation amount decreases rapidly. In contrast, at time t11, the timing at which the injected fuel is subjected to combustion in the combustion chamber of the diesel engine and converted into torque is indicated by a broken line.

  Also according to the present embodiment described above, the effects (1) to (4) of the first embodiment can be obtained.

(Third embodiment)
Hereinafter, the third embodiment will be described with reference to the drawings with a focus on differences from the first embodiment.

  In the present embodiment, an amount obtained by adding the escape amount C to the command injection amount calculated based on the accelerator operation amount is set as a final command injection amount, and the fuel injection valve 40 is operated based on the final command injection amount. Injects a commanded amount of fuel.

  FIG. 9 illustrates a process related to forced outflow of fuel in the common rail 30 according to the present embodiment. FIG. 9A shows the transition of the accelerator operation amount, and FIG. 9B shows the transition of the operation mode of the fuel injection valve 40.

  As shown in the figure, even after the time t21 when the accelerator operation amount sharply decreases, even if the command injection amount calculated based on the accelerator operation amount becomes zero, fuel of the escape amount C is injected through the fuel injection valve 40. . Thus, fuel injection is performed twice even after time t21.

  Also according to the present embodiment described above, the effects (1) to (4) of the first embodiment can be obtained.

(Fourth embodiment)
Hereinafter, the fourth embodiment will be described with reference to the drawings with a focus on differences from the first embodiment.

  In the first embodiment, the difference between the amount of fuel that flows out from the common rail 30 and the amount of fuel that is supplied to the common rail 30 is calculated as the amount of intake by the fuel pump 10 for the fuel that is supplied to the common rail 30 this time. It was calculated as the difference between the command injection amount and leak amount at the time and the current command injection amount and leak amount. Thus, if the actual fuel pressure in the common rail 30 is substantially equal to the target fuel pressure immediately before the sudden deceleration, an increase in the fuel pressure in the common rail 30 can be accurately predicted. However, when the actual fuel pressure in the common rail 30 is lower than the target fuel pressure immediately before the sudden deceleration, the fuel pressure calculated in the previous step S12 in FIG. 6 (“detected value of fuel pressure + ΔP”) is stored in the common rail 30. It becomes lower than the true value of the fuel pressure realized by supplying surplus fuel. Further, since the target fuel pressure also decreases at the time of sudden deceleration, it is not sufficient to make the actual fuel pressure follow the target fuel pressure if the decrease amount of the command injection amount and the leak amount is set as the release amount C.

  Therefore, in this embodiment, the escape amount C is set based on the difference between the estimated intake amount when the fuel pump 10 calculates the intake amount of the fuel supplied to the common rail 30 this time and the estimated intake amount this time. Hereinafter, this will be described in detail with reference to FIG.

  FIG. 10 shows a processing procedure for forcibly increasing the amount of fuel flowing out from the common rail 30 according to the present embodiment. This process is repeatedly executed by the electronic control device 60, for example, at a predetermined cycle.

  In this series of processes, first, in steps S22 to S26, the same processes as in steps S2 to S6 of FIG. 6 are performed. In step S28, the value A at the time of the previous previous suction and the value B at the time of the current suction for the estimated value of the suction amount by the fuel pump 10 calculated in step S26 are acquired. In step S30, the amount of overshoot is calculated using value A and value B as in step S10 of FIG. In a succeeding step S32, it is determined whether or not the overshoot amount ΔP is larger than a predetermined value γ. The predetermined value γ may be a value at which the fuel pressure of the common rail 30 does not exceed the predetermined value β. In addition, the predetermined value γ may be an allowable upper limit value at which the actual fuel pressure exceeds the target fuel pressure. Further, in steps S34 to S36, processing similar to that in steps S14 to S16 of FIG. 6 is performed.

  Since the value obtained by inverting the sign of the difference “A−B” calculated in step S8 is the fuel amount for setting the actual fuel pressure as the target fuel pressure, the overshoot amount ΔP calculated from this difference is the target amount. This value represents the amount of overshoot with respect to the fuel pressure. For this reason, by escaping the fuel of the escape amount C in step S36, the actual fuel pressure can quickly follow the target fuel pressure even during sudden deceleration.

  According to this embodiment described above, the following effects can be obtained in addition to the effects (1) to (4) of the first embodiment.

  (5) With respect to the intake amount of the fuel pump 10, the escape amount C is set based on the difference between the intake amount calculated by the fuel pump 10 and the current intake value for the fuel supplied to the common rail 30 this time. Thereby, the followability with respect to a target fuel pressure can be improved.

(Fifth embodiment)
Hereinafter, the fifth embodiment will be described with reference to the drawings with a focus on differences from the fourth embodiment.

  FIG. 11 shows a processing procedure for forcibly increasing the amount of fuel flowing out from the common rail 30 according to the present embodiment. This process is repeatedly executed by the electronic control device 60, for example, at a predetermined cycle.

  Also in this series of processing, first, in steps S42 and 44, processing similar to that in steps S22 and 24 of FIG. 10 is performed. In step S46, the amount of fuel supplied from the fuel pump 10 to the common rail 30 due to the differential pressure ΔPC between the detected actual fuel pressure and the target fuel pressure is calculated. Here, the fuel amount “ΔPC × V / E” corresponding to the differential pressure ΔPC is calculated as the fuel amount supplied to the common rail 30. Further, in step S48, the sum of the previous and previous intake values for the fuel amount calculated in step S46 and the previous and previous command injection amount is set as a value A, and the fuel amount calculated in step S46 and the current intake time. The value B is the difference between the current injection amount and the current command injection amount.

  In subsequent steps S50 to S56, processing similar to the processing shown in steps S30 to S36 of FIG. 10 is performed.

  As described above, in the present embodiment, the amount of fuel sucked by the fuel pump 10 is determined by the amount of fuel supplied from the fuel pump 10 to the common rail 30 due to the differential pressure ΔPC between the detected actual fuel pressure and the target fuel pressure. It was calculated as the sum of the command injection amount. This means that a calculation result that is smaller by the amount of leakage than that shown in FIG. 10 is output. However, at the time of sudden deceleration, the amount of leak can be ignored as compared with other factors. Therefore, according to the present embodiment, the same control as in FIG. 10 can be easily performed.

(Other embodiments)
The above embodiments may be implemented with the following modifications.

  -The forced outflow amount is not limited to the above-mentioned escape amount C. For example, in the first to third embodiments, “{(detected value of fuel pressure) + ΔP− (predetermined value β)} × V / E” may be used.

  The method for controlling the fuel pressure in the common rail 30 to the target value is not limited to the PID control. Here, in the case of performing feedback control by classical control, by performing integral control, the amount of fuel outflow from the common rail 30 at the time of fuel injection through the fuel injection valve 40 is compensated. In this integral control, regardless of whether or not the difference between the detected value of the fuel pressure of the common rail 30 and the target value is detected during the current control, the steady deviation amount between the previous detected value and the target value is calculated. Compensation control is performed. For this reason, while there is a merit of compensating for the decrease in the fuel pressure in the common rail 30 during steady operation, it is likely to cause a fuel pressure overshoot during sudden deceleration. For this reason, the application of the present invention is particularly effective when performing integral control in classical control.

  In addition to the feedback control, for example, the amount of fuel flowing out from the common rail 30 may be calculated based on the command injection amount, and the fuel pressure in the common rail 30 may be feedforward controlled so as to compensate for this outflow amount. Even in this case, at the time of sudden deceleration or the like, the amount of fuel sucked into the fuel pump 10 by feedforward control with reference to the command injection amount immediately before the sudden deceleration is supplied to the common rail 30 as surplus fuel after the sudden deceleration. The Rukoto. Therefore, also in this case, since overshoot of the fuel pressure is likely to occur, the application of the present invention is effective.

  In short, the application of the present invention is particularly effective in the case where control is performed in anticipation of a decrease in the fuel pressure in the common rail 30 based on the previous fuel outflow mode. However, for example, even when the fuel pressure in the common rail 30 is controlled only by proportional control, an overshoot of the fuel pressure may occur due to a sudden decrease in the injection amount after the intake of fuel.

  In the processing shown in FIGS. 10 and 11, the value A may be set as the current command injection amount in step S48. This also makes it possible to perform control that does not increase by more than the predetermined value γ from the current actual fuel pressure. At this time, in step S32 or step S52, “detection value of fuel pressure + ΔP” may be used as a predicted value of fuel pressure and compared with the predetermined value β shown in FIG.

  In step S36 in FIG. 10 and step S56 in FIG. 1, the processing exemplified in the second and third embodiments may be performed.

  In the first to third embodiments, when the fuel pressure is predicted to exceed the predetermined value, the forced fuel outflow process from the common rail 30 is performed, but the present invention is not limited to this. For example, it may be performed when the amount of fuel supplied to the common rail 30 is larger than the amount of fuel flowing out from the common rail 30 and when the detected value of the fuel pressure is not below the target value.

  The fuel injection control mode is not limited to that shown in FIG. For example, the fuel pump 10 may include only one plunger, and the rotating body 20 shown in FIG. 1 may rotate twice while the output shaft of the diesel engine rotates once.

  Also, the number of plungers may be any number N. In this case, N plungers that are displaced from the top dead center toward the bottom dead center at different timings are provided, and fuel that sucks fuel when any of these plungers is displaced from the top dead center toward the bottom dead center. In the case of using a pump, the processing shown in FIGS. 6, 10, and 11 may be appropriately changed in consideration that the amount of fuel sucked N times before the fuel pump becomes the current supply amount. desirable.

  Furthermore, an asynchronous system in which the fuel supply to the common rail 30 and the fuel injection from the fuel injection valve 40 do not correspond one-to-one may be used. Even in this case, the difference between the output fuel amount and the input fuel amount is calculated based on the variation of the command injection amount after the intake to the command injection amount immediately before the fuel intake by the fuel pump 10. It is effective to provide a calculation means. In such an asynchronous system, the amount of fuel discharged by a plurality of fuel injections may be compensated by the amount of fuel discharged by the fuel pump 10 once. In this case, when the command injection amount suddenly decreases (becomes zero) after the fuel is sucked by the fuel pump 10, the surplus fuel amount is determined for all or part of these multiple command injections according to the sudden decrease timing. The command injection amount and the leak amount associated with the fuel injection are obtained. For this reason, it is desirable to calculate the variation according to the sudden decrease timing. In each of the above embodiments, for convenience of explanation, only the main injection is dealt with in particular. However, for the small injections such as pilot injection, pre-injection, and after injection, the injection amount is zero when the main injection amount becomes zero. Can be. For this reason, these micro-injections can also become surplus fuel during sudden deceleration. For this reason, it is desirable that the balance calculation means includes the command injection amount for minute injection in the command injection amount immediately before inhalation and the command injection amount after inhalation.

  -The method of forcibly letting out the fuel in the common rail 30 is not limited to those exemplified in the above embodiments. For example, the fuel pressure in the common rail 30 may be controlled by performing idle driving of the fuel injection valve 40. Here, in the idle driving, the electromagnetic solenoid 58 is energized to connect the back pressure chamber 50 and the low pressure fuel passage 34, and the nozzle needle 44 is separated from the needle seat portion 46 (fuel injection valve). This is done by stopping the energization control to the electromagnetic solenoid 58 before the valve 40 opens). Thereby, the fuel supplied from the common rail 30 can be returned to the fuel tank 2 without being injected.

  The fuel pump 10 is not limited to a suction metering pump that determines the amount of fuel to be supplied to the pressure accumulating chamber by adjusting the amount of fuel to be sucked. Even if it is other than this, at the time of sudden deceleration, surplus fuel is supplied to the common rail 30 side by the inertia high-pressure wave of the high-pressure fuel in the fuel passage connecting the outlet of the fuel pump 10 to the inlet of the common rail 30. Since the fuel pressure inside the fuel may rise excessively, the application of the present invention is effective.

  Other than the fuel injection control device of the common rail type diesel engine, the main points are a pressure accumulating chamber for storing fuel in a high pressure state, a fuel pump for pressurizing fuel to the pressure accumulating chamber, and a pressure accumulating chamber. Any fuel injection device including a fuel injection valve that injects the injected fuel may be used. At this time, the number of cylinders of the internal combustion engine may be arbitrary.

The figure which shows the structure of 1st Embodiment of a fuel-injection control apparatus. Sectional drawing explaining operation | movement of a fuel pump. Sectional drawing which shows the cross-sectional structure of a fuel injection valve. The functional block diagram of fuel-injection control. The time chart which shows a fuel-injection control aspect. The flowchart which shows the procedure of the forced outflow process of the fuel in a common rail. The time chart which shows the forced outflow processing aspect of a fuel. The time chart which shows the forced outflow processing aspect of the fuel concerning 2nd Embodiment. The time chart which shows the forced outflow processing aspect of the fuel concerning 3rd Embodiment. The flowchart which shows the procedure of the forced outflow process of the fuel in the common rail concerning 4th Embodiment. The flowchart which shows the procedure of the forced outflow process of the fuel in the common rail concerning 5th Embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 2 ... Fuel tank, 10 ... Fuel pump, 11 ... Low pressure pump, 12 ... Metering control valve, 15 ... High pressure pump, 30 ... Common rail, 40 ... Fuel injection valve, 60 ... Electronic control device (one of prediction means, correction means) Embodiment).

Claims (11)

Fuel injection control using a fuel injection device comprising a pressure accumulating chamber for storing fuel in a high pressure state, a fuel pump for pressurizing and supplying fuel to the pressure accumulating chamber, and a fuel injection valve for injecting fuel stored in the pressure accumulating chamber In the fuel injection control device for performing
Predicting means for predicting whether or not the amount of fuel supplied to the pressure accumulating chamber is greater than a predetermined amount than the amount of fuel flowing out from the pressure accumulating chamber when fuel is injected by the fuel injection valve;
A fuel injection control device, comprising: a correcting means for forcibly increasing the amount of fuel output from the pressure accumulating chamber when the predicting means predicts that the predetermined amount or more will be increased.   2. The fuel injection control device according to claim 1, wherein the fuel pump is a suction metering type pump that determines a fuel amount to be supplied to the pressure accumulating chamber by adjusting a fuel amount to be sucked.   The predicting means calculates the difference between the fuel output amount and the fuel input amount based on a variation in the command injection amount after the intake time with respect to the command injection amount immediately before the fuel intake by the fuel pump. The fuel injection control device according to claim 2, further comprising a calculation unit.   The balance calculation means calculates the difference between the fuel output amount and the fuel amount that has entered the current command injection amount with respect to the command injection amount at the time of calculating the intake amount by the fuel pump for the fuel supplied to the accumulator chamber this time The fuel injection control device according to claim 3, wherein the fuel injection control device is calculated based on a fluctuation amount of   The balance calculating means calculates the difference between the fuel output amount and the fuel amount entered, the command injection amount at the time of calculation, the leak amount from the fuel injection valve at the time of calculation, the current command injection amount, and the current fuel injection amount. The fuel injection control device according to claim 4, wherein the fuel injection control device calculates the difference from the leak amount. Means for capturing the detection result of the detection means for detecting the fuel pressure in the pressure accumulation chamber;
Target fuel pressure calculating means for calculating a target fuel pressure in the pressure accumulation chamber;
Operating means for operating the fuel pump to control the detected fuel pressure to a target fuel pressure;
The entering fuel amount is calculated based on the difference between the detected fuel pressure and the target fuel pressure, and the command injection amount,
5. The balance calculating means calculates the difference between the fuel output amount and the amount of entering fuel by subtracting at least the current command injection amount from the amount of entering fuel at the time of the calculation. The fuel injection control device described. Means for capturing the detection result of the detection means for detecting the fuel pressure in the pressure accumulation chamber;
Target fuel pressure calculating means for calculating a target fuel pressure in the pressure accumulation chamber;
Operating means for operating the fuel pump to control the detected fuel pressure to a target fuel pressure;
The entering fuel amount is calculated based on the difference between the detected fuel pressure and the target fuel pressure, and the command injection amount,
The balance calculation means calculates the difference between the fuel output amount and the amount of incoming fuel as the difference between the value at the time of calculation and the current value for the amount of fuel input. 7. The fuel injection control device according to 6. Fuel pressure predicting means for calculating a fuel pressure in the pressure accumulating chamber based on a difference between the fuel output amount and the fuel input amount;
The prediction means performs prediction as to whether or not the fuel pressure in the pressure accumulating chamber calculated by the fuel pressure prediction means rises to a vicinity of a predetermined upper limit value. The fuel injection control device according to any one of claims 1 to 7. The pressure accumulating chamber is provided with a pressure reducing valve that returns the fuel in the pressure accumulating chamber to a fuel tank that stores fuel;
The fuel injection control device according to any one of claims 1 to 8, wherein the correction means forcibly increases the fuel output amount by forcibly opening the pressure reducing valve.   The said correction | amendment means forcibly increases the said fuel output amount by injecting a fuel through the said fuel injection valve at the timing which does not contribute to the output of the said engine. A fuel injection control device according to claim 1.   The correction means forcibly increases the output fuel amount by setting a final command injection amount obtained by adding the fuel amount to be discharged to the command injection amount calculated based on an accelerator operation amount. The fuel injection control device according to claim 1, wherein the fuel injection control device is a fuel injection control device.

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