JP5556209B2 - High-pressure fuel pump reference time calculation device - Google Patents

Description

  The present invention relates to a reference time calculation device for a high-pressure fuel pump.

  For example, a common rail system is known as a fuel supply system for a diesel engine. In this system, fuel is increased in pressure by a high-pressure fuel pump, and the high-pressure fuel is injected into a combustion chamber of the engine. As the high-pressure fuel pump, a mechanical pump that is rotationally driven by the rotation of the engine output shaft is generally used, and the plunger is reciprocated by the rotation of the engine output shaft, so that fuel suction and discharge are performed by the high-pressure fuel pump. It has become.

  Here, it is desirable that the fuel discharge timing of the high-pressure fuel pump is determined in association with the rotational phase of the engine, and Patent Document 1 is known as a technique for performing phase alignment of the high-pressure fuel pump before factory shipment. . In Patent Document 1, a protrusion is provided on the pump drive shaft, and the protrusion faces a predetermined positioning member when the rotation position of the pump drive shaft becomes a reference rotation position corresponding to the fuel discharge timing of the high-pressure fuel pump. The pump rotation position is adjusted.

JP-A-9-42100

  However, when phase alignment of the high-pressure fuel pump is performed at the time of assembling the pump to the engine before shipment from the factory, phase alignment accuracy at the time of the assembly is required, and there is a risk of complicating the pump assembly operation. Even if the phase alignment operation is performed before shipment from the factory, it is considered that a phase error or the like has occurred. Due to this phase error or the like, the fuel discharge control during engine operation or the fuel injection control by the fuel injection valve is controlled. There was a risk of lowering the sex. Further, if the phase adjustment of the high-pressure fuel pump is not performed in order to facilitate the pump assembly work, there is a concern that the controllability during the fuel discharge control or the like is lowered. For example, if the fuel discharge timing by the high-pressure fuel pump and the fuel injection timing by the engine overlap, it is considered that the accuracy of the fuel injection amount cannot be maintained.

  The main object of the present invention is to provide a reference time calculation device for a high-pressure fuel pump that can suitably calculate a reference time that is a top dead center / bottom dead center of a plunger in a high-pressure fuel pump.

  When fuel is pumped by suction and discharge of fuel in a high-pressure fuel pump, the fuel pressure rises on the downstream side of the pump as the fuel is discharged. However, when the fuel is sucked after the fuel is discharged, the fuel pressure is reduced due to various fuel leaks in the high-pressure fuel section downstream from the pump discharge section. The present invention pays attention to the repeated increase and decrease of the fuel pressure in the high-pressure fuel section every time the fuel is sucked into and discharged from the high-pressure fuel pump, and the pump reference time is calculated based on the pressure change.

In short, in the first invention, pump control means for discharging fuel by the high-pressure fuel pump in a fuel leak state in which fuel leak occurs in the high-pressure fuel portion downstream of the fuel discharge portion of the high-pressure fuel pump; Pressure detecting means for detecting the fuel pressure of the high-pressure fuel section during pump operation by the pump control means, and reference timing calculating means for calculating the pump reference time based on the fuel pressure detected by the pressure detecting means. It is characterized by providing.

  According to the present invention, the pump reference time that is the top dead center / bottom dead center is calculated by alternately repeating the increase and decrease of the fuel pressure in the process of fuel pumping by the high-pressure fuel pump. be able to. In other words, for example, when fuel discharge is terminated at the top dead center of the plunger, the fuel pressure changes from rising to falling at the top dead center of the plunger, and when fuel discharge is started at the bottom dead center of the plunger, At the bottom dead center of the plunger, the fuel pressure changes from decreasing to increasing. By determining such a pressure change, the reference time of the high-pressure fuel pump can be suitably calculated. By knowing the pump reference time, it is possible to accurately associate with the rotational phase of the internal combustion engine.

In the second invention, the pump control means controls the fuel discharge amount of the high-pressure fuel pump so that the fuel pressure of the high-pressure fuel section is maintained when calculating the pump reference time. In this case, the fuel pressure in the high-pressure fuel section is maintained by controlling the fuel discharge amount of the high-pressure fuel pump so as to compensate for the decrease in the fuel pressure due to the fuel leak. There is a correlation between the fuel pressure and the fuel leak amount, and it is considered that the fuel leak amount is constant when the fuel pressure is maintained, so that a uniform pressure change result is obtained in a series of fuel intake and discharge flows. It is done. Therefore, the calculation accuracy of the pump reference time can be increased.

According to a third aspect of the invention, there is provided means for calculating the amount of fuel leak that occurs under the fuel leak condition, wherein the pump control means is configured to calculate the pump reference time based on the calculated fuel leak amount. The amount of fuel discharged is controlled. In this case, the fuel pressure in the high-pressure fuel section can be maintained by controlling the fuel discharge amount of the high-pressure fuel pump so that it is the same as the fuel leak amount. Can be increased.

According to a fourth aspect of the invention, there is provided a leak amount control means for controlling a fuel leak amount in the high-pressure fuel section, wherein the pump control means discharges the fuel under a state in which the fuel leak amount is controlled by the leak amount control means. Let it be done. In this case, by intentionally controlling the amount of fuel leak, the amount of increase and decrease in fuel pressure in the high-pressure fuel section can be suitably adjusted in calculating the pump reference time.

In a fifth aspect of the invention, the invention is applied to an accumulator fuel system including an accumulator that stores fuel pumped from the high-pressure fuel pump in a high-pressure state, and the pressure detection means has a withstand pressure of the accumulator or a pressure in the vicinity thereof The fuel pressure is detected in a state, and the reference time calculation means calculates the pump reference time based on the fuel pressure detected in a state where the pressure in the pressure accumulating chamber is at or near the pressure. In this case, at the pressure resistance of the pressure accumulating chamber or a pressure in the vicinity thereof, the amount of fuel leak occurring in the high pressure fuel portion increases, and the amount of pressure increase and the amount of pressure decrease during the fuel pumping process can be increased. Thereby, the calculation accuracy of the pump reference time can be increased.

In a sixth aspect of the present invention, the pressure detecting means includes means for stopping fuel injection to the internal combustion engine, the fuel pressure is detected when the fuel injection is stopped, and the reference timing calculating means is The pump reference time is calculated based on the fuel pressure detected in the resting state. In this case, in the state where the fuel injection is stopped, the cause of the fuel pressure drop is only the fuel leak, and it is not necessary to consider the fuel pressure drop due to the fuel injection. Therefore, it is possible to simplify the calculation process regarding the calculation of the pump reference time and to increase the calculation accuracy.

The block diagram which shows the outline of the common rail type fuel supply system in embodiment of invention. The time chart which shows the fuel pressure change etc. at the time of driving | operation of a high pressure pump. The flowchart which shows a plunger top dead center calculation process.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment of the invention will be described with reference to the drawings. The reference timing calculation device for a high-pressure fuel pump according to this embodiment is applied to a common rail fuel supply system that supplies high-pressure fuel to a diesel engine (internal combustion engine). First, the configuration of the fuel supply system will be described with reference to FIG.

  As shown in the drawing, the fuel in the fuel tank 20 that stores the fuel is pumped up by the fuel pump 10 and supplied to the common rail 30 (pressure accumulation chamber) via the supply pipe 21. Here, the fuel pump 10 includes a low-pressure pump 11 that pumps up fuel in the fuel tank 20 and a high-pressure pump 12 that discharges the low-pressure fuel pumped up by the low-pressure pump 11 at a high pressure. An intake metering valve (hereinafter referred to as SCV) 13 for adjusting the fuel intake amount is provided on the fuel intake side of the high-pressure pump 12.

The high-pressure pump 12 is provided with a fuel passage 14 branched into two on the downstream side of the SCV 13, and two pump chambers 15 and plungers 16 are provided corresponding to the fuel passages 14. The plungers 16 are individually reciprocated by the displacement of the cam ring 18 as the cam shaft 17 rotates, and the plungers 16 are alternately displaced from the top dead center toward the bottom dead center by the displacement of the cam ring 18. Then, the fuel in each fuel passage 14 is sucked into the pump chamber 15. Further, when each plunger 16 is displaced from the bottom dead center toward the top dead center, fuel is discharged from each pump chamber 15. Here, an eccentric cam 19 integrated with the cam shaft 17 is assembled at the center of the cam ring 18, and the cam ring 18 is displaced by the eccentric cam 19 rotating eccentrically with the rotation of the cam shaft 17. The cam shaft 17 is drivingly connected to the engine output shaft and is driven to rotate in accordance with the rotation of the engine output shaft. In the present embodiment, the engine output shaft and the cam shaft 17 rotate at a rotation ratio of 1: 1, and the fuel is discharged twice by one rotation of the engine output shaft. Incidentally, the low pressure pump 11 as well as the high pressure pump 12 is driven by the engine output shaft. Note that the number of plungers in the high-pressure pump 12 may be other than two, and may be one or three or more.

  For example, when one plunger 16 (upper plunger in the figure) is displaced from the position in FIG. 1 to the bottom dead center, the fuel in one fuel passage 14 moves into the pump chamber 15 as the plunger 16 is displaced. Inhaled. At the same time, the other plunger 16 (lower plunger in the figure) is displaced toward the top dead center, so that high-pressure fuel is discharged from the pump chamber 15 to the outside through the other fuel passage 14. In short, as the camshaft 17 rotates, the suction and discharge of fuel are repeatedly executed in each pump chamber 15 alternately. The two fuel passages 14 merge downstream and are connected to the supply pipe 21. Further, the check valves 22 and 23 provided in each of the fuel passages 14 prevent the back flow of fuel when the plunger 16 is displaced.

In the high-pressure pump 12, when the plunger 16 is displaced toward the bottom dead center, the SCV 13 is opened so that fuel is sucked into the pump chamber 15. At this time, the fuel intake amount is adjusted by closing the SCV 13 while the plunger 16 is displaced toward the bottom dead center. Then, the plunger 16 reaches the bottom dead center, the fuel ejection is performed by the closed state SCV13 when displaced for subsequent top dead center. In this case, the fuel discharge amount is determined by the fuel intake amount is adjusted by SCV13, (if brought close to the plunger bottom dead center) to lever slow closing timing increases the amount of fuel ejection, early lever closing timing The fuel discharge amount is reduced (if it approaches the top dead center of the plunger).

Incidentally, a fuel discharge end timing fixed, it is the plunger top dead center (or the immediately preceding position).

  The high-pressure fuel supplied from the high-pressure pump 12 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 pipe 32. The fuel injection valve 40 includes a body 41 having a fuel passage formed therein and an injection hole formed at a tip thereof, a needle valve 42 that opens and closes the injection hole by being displaced within a sliding hole formed in the body 41, An electromagnetic solenoid 43 that opens and closes the needle valve 42 is provided. The fuel injection valve 40 is connected to a return pipe 34 for returning high-pressure fuel to the fuel tank 20. Here, in the fuel injection valve 40, a minute gap is generated in the sliding part (valve sliding part) of the needle valve 42, and high-pressure fuel leaks through the minute gap. The fuel path from the pump chamber 15 (fuel discharge portion) of the high-pressure pump 12 to the injection hole portion of the fuel injection valve 40 corresponds to the high-pressure fuel portion.

  The common rail 30 is provided with a fuel pressure sensor 38 that detects the fuel pressure (rail pressure) inside the common rail 30. The fuel pressure sensor 38 is provided, for example, in the vicinity of the connection portion with the supply pipe 21 in the common rail 30. In addition, the present system includes a rotation sensor 39 that detects the rotational position of the engine, an accelerator sensor 52 that detects the amount of depression of the accelerator pedal 51 (accelerator operation amount), a fuel pressure sensor that detects the fuel temperature in the fuel tank, and the like. It has been. The rotation sensor 39 is, for example, an electromagnetic pickup type sensor that detects a rotation position for each predetermined rotation angle of the engine output shaft, and outputs a pulse signal (NE pulse) each time the rotation rotates at a predetermined rotation angle. In the present embodiment, the NE pulse is output every 12 ° CA.

  Detection values of various sensors such as the fuel pressure sensor 38, the rotation sensor 39, and the accelerator sensor 52 are taken into an electronic control unit (ECU 50). The ECU 50 includes a central processing unit and an appropriate memory. Based on detection values of various sensors, the ECU 50 controls fuel pressure with the SCV 13 as a control target, fuel injection control with the fuel injection valve 40 as a control target, and the like. Control of various actuators is executed.

  For details on the fuel pressure control, the target fuel pressure is set based on the engine operating state (specifically, the fuel injection amount and the engine speed), and the actual fuel pressure detected by the fuel pressure sensor 38 matches the target fuel pressure. Thus, the fuel pressure feedback control is executed. At this time, the target fuel pressure is set to a relatively low pressure value in a low load state such as during idle operation, and to a relatively high pressure value in a high load state such as full load.

  In this embodiment, the rotation position of the plunger top dead center as the pump reference time in the high-pressure pump 12 is calculated. Here, in particular, when fuel suction and discharge are repeatedly performed in the high-pressure pump 12, the fuel pressure (fuel pressure on the downstream side of the pump) increases during fuel discharge, and the fuel injection valve 40 during other fuel suction, for example. Focus on the fact that fuel pressure drops due to fuel leaks, etc., and the end timing of fuel discharge is the plunger top dead center, and calculate the rotation position of the plunger top dead center based on the pressure change during fuel discharge To do.

  Such calculation of the pump reference time is performed, for example, in a process before factory shipment. At this time, an engine test operation is performed in a state where the fuel pump 10 is assembled to the engine, and under this state, the ECU 50 is set to the reference position calculation mode and the pump reference time is calculated. However, in addition to calculating the pump reference time at the time prior to shipment, the pump reference time may be calculated after shipment. For example, it is possible to calculate the pump reference time at a vehicle dealer that sells vehicles, and to calculate the pump reference time after delivery of the vehicle to the user.

FIG. 2 is a time chart showing changes in fuel pressure during operation of the high-pressure pump 12. In Figure 2, the plunger 16 reciprocates 180 ° CA as 1 cycle, the top dead center of the plunger 16 (T DC) → SCV13 in fuel suction period in the displacement process of the bottom dead center (B DC) is closed . Then, during the fuel discharge period, the fuel pressure rises due to the fuel discharge according to the fuel intake amount . Further, the fuel pressure is reduced except during the fuel discharge period, which is caused by fuel leak in the fuel injection valve 40 and the like. As a result, the fuel pressure has become that alternates and decreases with Noboru Ue. At this time, the fuel discharge amount of the high-pressure pump 12 is feedback-controlled so as to compensate for the decrease in fuel pressure due to fuel leak, and the fuel pressure is maintained substantially constant. If the number of plungers in the high-pressure pump 12 is two, the SCV 13 is opened twice within the 180 ° CA period (see the operation of the one-dot chain line in FIG. 2).

  Here, the NE pulse is generated at a 12 ° CA cycle, and the fuel pressure P is detected each time, and the fuel pressure change amount ΔP is calculated from the current value Pi of the fuel pressure and the previous value Pi−1 (ΔP = Pi−). Pi-1). In this case, when it is determined that the fuel pressure change amount ΔP is smaller than the predetermined determination value Th (Th≈0 and Th> 0), the fuel pressure has changed from increasing to decreasing, that is, the pump rotational position is changed to the plunger. It can be determined that the top dead center has been reached.

  FIG. 3 is a flowchart showing the plunger top dead center calculation process. This process is executed for each rising edge of the NE pulse after the ECU 50 is powered on.

  First, in step S11, it is determined whether or not it is currently in the reference position calculation mode for calculating the rotation position (pump reference time) of the plunger top dead center. If it is in the same calculation mode, the process proceeds to the subsequent step S12 to determine whether or not the fuel is being cut, that is, whether or not the fuel injection by the fuel injection valve 40 is stopped. The start of this process is before the execution of fuel cut, step S12 becomes NO, and the process proceeds to step S13.

  In step S13, it is determined whether or not the engine operation state is a fuel leak operation state in which a desired amount of fuel leak occurs. Specifically, it is determined whether the engine speed NE is in a predetermined high rotation state (for example, 2200 rpm or more) and the engine load is in a predetermined high load state (for example, full load state). If the condition is satisfied, it is determined that the fuel leak operation state is set. At this time, it may be added to the determination condition that the fuel leak operation state continues for a predetermined time. The fuel leak operation state may be determined as long as the fuel pressure (rail pressure) is determined to be in a predetermined maximum value (rail withstand pressure 180 MPa) or in the vicinity thereof, and the fuel pressure is the maximum value. It may be determined whether or not the value is equal to or greater than a predetermined predetermined determination value (for example, 170 MPa).

  When step S13 is NO, it progresses to step S14 and control is performed so that the engine operation state becomes the fuel leak operation state. Specifically, the engine load is increased until, for example, a full load state is reached. As a result, the engine speed increases and the target fuel pressure is set to a high fuel pressure value. In addition, the process of step S14 is also a process for raising a fuel pressure.

  When step S13 becomes YES by engine control in step S14, the process proceeds to step S15, and fuel cut of the engine is started. Specifically, the fuel injection by the fuel injection valve 40 is stopped for all the engine cylinders. However, at this time, load reduction and NE reduction occur with fuel cut, but the target fuel pressure is maintained at the start of fuel cut, and fuel pressure feedback control is also continued.

After the start of fuel cut, step S12 becomes YES and the process proceeds to step S16. In step S16, it is determined whether or not an execution condition for calculating the plunger top dead center is satisfied. This execution condition includes
・ Various sensors such as the fuel pressure sensor 38 and the rotation sensor 39 are normal.
・ The fuel temperature is within the specified temperature range.
The engine rotational speed NE is within a predetermined rotational speed range (for example, 1800 to 2200 rpm),
If all of these conditions are satisfied, it is determined that the execution condition for calculating the plunger top dead center is satisfied.

  When step S16 is YES, the process proceeds to step S17, and the fuel pressure change amount ΔP is calculated from the current value and the previous value of the fuel pressure P (ΔP = Pi−Pi−1). In subsequent step S18, the fuel pressure change amount ΔP is compared with a predetermined determination value Th to determine whether ΔP ≧ Th at the previous NE edge and ΔP <Th at the current NE edge. And if step S18 is NO, this process will be complete | finished as it is, and if it is YES, it will progress to subsequent step S19. In this case, ΔP ≧ Th because fuel pressure rises when fuel is being discharged, and ΔP <Th when fuel is not being discharged. Therefore, it is determined that ΔP ≧ Th last time and ΔP <Th this time is that the fuel discharge has ended, that is, the pump rotation position becomes the top dead center of the plunger, and the fuel pressure increases accordingly. It means that it has started to fall.

  In step S19, it is temporarily determined that the current rotational position is the plunger top dead center. At this time, an NE pulse number is assigned to each NE pulse with one combustion cycle (= 720 ° CA) of the engine as one cycle, and the rotational position of the plunger top dead center is associated with the NE pulse number. Temporarily determined. Specifically, in this embodiment, NE pulse numbers of “1 to 58” are assigned (two pulses are subtracted due to missing teeth within 720 ° CA), and at the top dead center of the plunger. When it is temporarily determined that there is, the current NE pulse number is read and temporarily stored.

  In subsequent step S20, it is determined whether or not the provisional determination of the plunger top dead center has been performed a predetermined number of times. If YES, the process proceeds to step S21. In step S21, the rotational position of the plunger top dead center is determined (this determination) based on a plurality of determination results relating to the plunger top dead center. For example, an average value of a plurality of determination results regarding the plunger top dead center is determined as the rotation position of the plunger top dead center. Thereafter, in step S22, the rotation position of the plunger top dead center determined as described above is written in a memory such as an EEPROM in the ECU 50, and then this process is terminated. When the rotation position (pump reference time) of the plunger top dead center is already stored in the EEPROM, the past value may be updated (learned) with a new value.

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

  The fuel pressure rises when the fuel is discharged by the high-pressure pump 12, and otherwise the fuel pressure decreases due to fuel leak. Based on the change in the fuel pressure rise and fall, the rotation position of the plunger top dead center as the pump reference time Therefore, calculation of the rotational position of the plunger top dead center can be suitably performed. By knowing the rotational position of the top dead center of the plunger, it is possible to accurately associate with the engine rotational phase.

  Since the plunger top dead center can be calculated in this manner, the rotational phase error for the engine can be eliminated even if the pump assembly accuracy at the manufacturing plant is not good. Further, it is possible to eliminate the process of aligning the key grooves for phase alignment between the engine and the high pressure pump 12. At this time, it is possible to associate with the engine rotation phase by calculating the pump reference time in the ECU 50 without performing phase matching at the time of assembling the pump.

  Since the fuel discharge amount of the high-pressure pump 12 is controlled so that the fuel pressure (rail pressure) is maintained when calculating the plunger top dead center, the fuel leak amount can be kept constant, and a series of fuel suction and discharge pumps A uniform pressure change result can be obtained each time in operation. Therefore, the calculation accuracy of the plunger top dead center can be increased.

  The engine is determined to be in the fuel leak operation state when the engine operation state is a high rotation and high load state, and the plunger top dead center is calculated on the condition that the engine is in the leak operation state. That is, using the fact that there is a correlation between the fuel pressure and the amount of fuel leak, the condition that the fuel pressure has risen to near the rail pressure resistance is used as the calculation condition for the plunger top dead center. In this case, the fuel leak amount increases at the pressure near the rail pressure resistance, and the pressure increase amount and the pressure decrease amount in the fuel pumping process can be increased. Thereby, the calculation precision of a plunger top dead center can be raised.

  Before calculating the top dead center of the plunger, the fuel leakage amount is adjusted by controlling the engine operating state to a high rotation and high load state. Therefore, the fuel leakage amount is suitable for calculating the plunger top dead center. The amount of leakage can be adjusted intentionally.

  Since the fuel pressure change is detected in the fuel cut state and the rotation position of the plunger top dead center is calculated based on the detection result, the fuel pressure drop is the only factor causing the fuel pressure drop when calculating the plunger top dead center. It is not necessary to consider the fuel pressure drop due to. Therefore, it is possible to simplify the calculation process regarding the calculation of the plunger top dead center and to increase the calculation accuracy.

(Other embodiments)
The present invention is not limited to the description of the above embodiment, and may be implemented as follows, for example.

  A means for calculating the amount of fuel leak that occurs under a fuel leak condition may be provided, and the fuel discharge amount of the high-pressure pump 12 may be controlled based on the calculated fuel leak amount when calculating the plunger top dead center. In this case, the fuel pressure of the common rail or the like can be maintained by controlling the fuel discharge amount of the high-pressure pump 12 so as to be the same as the fuel leak amount. Again, by maintaining the fuel pressure, the accuracy of calculating the plunger top dead center can be increased as described above. The fuel leak amount may be calculated based on the fuel pressure (rail pressure) at each time.

  The pump chamber 15 of the high-pressure pump 12 and the fuel pressure detection position are separated by at least the length of the supply pipe 21. Therefore, the plunger top dead center (pump reference time) may be calculated in consideration of the transport delay when high-pressure fuel flows through the supply pipe 21. In this case, a delay time required for transport delay may be determined in advance, and the calculation result of the plunger top dead center may be corrected accordingly. Note that the delay time may be set according to the fuel pressure. In addition, in order to eliminate the transport delay at the fuel pressure detection point, it is possible to operate a configuration for detecting the fuel pressure in the supply pipe 21.

  In the above embodiment, the rotation position of the plunger top dead center is calculated based on the change in the fuel pressure. Instead, the rotation position of the plunger bottom dead center may be calculated. Specifically, in the high-pressure pump 12, the fuel discharge start timing is fixed at the plunger bottom dead center in the process in which the plunger 16 is displaced toward the top dead center, and the fuel discharge is terminated in accordance with the fuel discharge control amount at each time. The timing is variably controlled. In this case, since the fuel pressure of the common rail or the like changes from a decrease to an increase at the plunger bottom dead center, the plunger bottom dead center can be calculated by detecting this change in fuel pressure.

  -When it is possible to switch between a state where fuel leak occurs and a state where it does not occur according to the fuel pressure in the high pressure fuel section (common rail, etc.), a leak execution means for shifting to a state where fuel leak occurs It is set as the structure provided. For example, if the fuel pressure does not occur when the fuel pressure is relatively low and the fuel leak occurs when the fuel pressure is relatively high, the fuel pressure is positively increased to the pressure at which the fuel leak occurs when calculating the pump reference time. A means for raising the temperature may be provided.

  -It is good also as a structure which provides the leak adjustment mechanism by a throttle | throttle or an on-off valve in a fuel high pressure part (common rail etc.). In this case, the amount of fuel leak at the time of calculating the pump reference time can be arbitrarily adjusted by controlling the amount of leak by the leak adjustment mechanism by the ECU.

  In the above embodiment, the case where the present invention is applied to a fuel supply system for a diesel engine has been described. However, for example, a fuel supply system such as a spark ignition gasoline engine (especially a cylinder injection engine) is basically used. Similarly, the present invention can be applied. The fuel supply system of the direct injection gasoline engine is equipped with a delivery pipe that stores fuel (gasoline) in a high-pressure state. Fuel is pumped from the high-pressure pump to the delivery pipe, and the high-pressure inside the delivery pipe Fuel is injected and supplied from the fuel injection valve into the engine combustion chamber.

  DESCRIPTION OF SYMBOLS 10 ... Fuel pump, 12 ... High pressure pump (high pressure fuel pump), 15 ... Pump chamber (fuel discharge part), 16 ... Plunger, 30 ... Common rail (pressure accumulation chamber), 40 ... Fuel injection valve, 50 ... ECU (pump control means) Pressure detection means, reference time calculation means, leak amount control means).

Claims (6)

A high-pressure fuel pump that is driven to rotate in accordance with the rotation of the output shaft of the internal combustion engine, and the plunger reciprocates in accordance with the rotation drive, and repeatedly performs fuel suction and discharge by the plunger reciprocation. This is a reference timing calculation device for a high-pressure fuel pump that calculates a pump reference timing that is a point,
Pausing means for suspending fuel injection to the internal combustion engine;
A pump control means for causing the high-pressure fuel pump to discharge fuel under a fuel leak state in which a fuel leak occurs in a high-pressure fuel portion downstream of the fuel discharge portion of the high-pressure fuel pump;
Pressure detecting means for detecting the fuel pressure of the high pressure fuel section during pump operation by the pump control means;
Reference time calculation means for calculating the pump reference time based on the fuel pressure detected by the pressure detection means in a resting state in which the fuel injection is stopped ;
An apparatus for calculating a reference time for a high-pressure fuel pump. The reference time calculation means includes
Means for determining whether or not a predetermined amount of fuel leakage occurs in the high-pressure fuel section before fuel injection is stopped by the stopping means;
Means for performing control to increase the amount of fuel leakage when it is determined that the predetermined amount of fuel leakage is not in a state;
The pump reference time is calculated on the basis of the fuel pressure detected by the pressure detecting means in a state where the control for increasing the fuel leak amount is performed and the fuel injection is stopped. Reference time calculation device for high-pressure fuel pumps. 3. The high-pressure fuel pump according to claim 1, wherein the pump control unit controls a fuel discharge amount of the high-pressure fuel pump so that a fuel pressure of the high-pressure fuel portion is maintained when the pump reference time is calculated. Reference time calculation device. Means for calculating the amount of fuel leakage that occurs under the fuel leakage condition;
The high-pressure fuel pump according to any one of claims 1 to 3, wherein the pump control unit controls a fuel discharge amount of the high-pressure fuel pump based on the calculated fuel leak amount when calculating the pump reference time. Reference time calculation device. Leak amount control means for controlling the amount of fuel leak in the high pressure fuel part,
The reference timing calculation apparatus for a high-pressure fuel pump according to any one of claims 1 to 4 , wherein the pump control means causes the fuel discharge to be performed in a state where the fuel leak amount is controlled by the leak amount control means. Applied to an accumulator fuel system including an accumulator that stores fuel pumped from the high-pressure fuel pump in a high-pressure state;
The pressure detecting means detects the fuel pressure in a state where the pressure in the pressure accumulating chamber is at or near the pressure, and the reference time calculating means is a fuel detected in a state where the pressure is in the pressure accumulating chamber or near the pressure. The reference time calculation device for a high-pressure fuel pump according to any one of claims 1 to 5 , wherein the pump reference time is calculated based on pressure.

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