JP5812517B2 - High pressure pump control device - Google Patents

Description

  The present invention relates to a control device for a high-pressure pump provided with an electromagnetic actuator for opening and closing the suction port side of the high-pressure pump.

  An in-cylinder injection engine that directly injects fuel into a cylinder has a shorter time from injection to combustion and sufficient time to atomize the injected fuel compared to an intake port injection engine that injects fuel into an intake port. Therefore, it is necessary to atomize the injected fuel by increasing the injection pressure. Therefore, in a cylinder injection engine, fuel pumped up from a fuel tank by an electric low-pressure pump is supplied to a high-pressure pump driven by engine power, and high-pressure fuel discharged from the high-pressure pump is supplied to a fuel injection valve. It is trying to pump to.

  As such a high-pressure pump, for example, a metering valve that opens and closes the suction port side of the high-pressure pump and an electromagnetic actuator that opens and closes the metering valve are provided, and the metering valve is controlled by controlling energization of the electromagnetic actuator. In some cases, the fuel pressure (fuel pressure) is controlled by controlling the fuel discharge amount of the high-pressure pump by controlling the valve closing period.

  Further, as a technique for reducing noise generated when a fuel injection valve constituted by a solenoid valve is closed, for example, as described in Patent Document 1 (Japanese Patent Laid-Open No. 4-153542), a fuel injection valve ( When the energization of the drive coil of the solenoid valve is stopped and the fuel injection valve is closed, the energization of the drive coil is temporarily re-energized after the energization of the drive coil is stopped, thereby reducing the valve closing speed of the fuel injection valve. There is something that was made to lower.

JP-A-4-153542

  In the high-pressure pump described above, when the valve opening control is performed to stop the energization of the solenoid of the electromagnetic actuator and move the movable part of the electromagnetic actuator to the open position to open the metering valve, The valve collides with the stopper or the like and vibration is generated, which may cause unpleasant noise.

  By the way, as shown in FIG. 4, in the valve opening control of the high-pressure pump, even if the energization to the solenoid is stopped, even if the fuel pressure in the pump chamber is still high, the pump does not move even if the movable part hits the metering valve. Since the metering valve is maintained in the closed state by the indoor fuel pressure, the movable part stops in a state where it hits the metering valve. Thereafter, when the fuel pressure in the pump chamber decreases, the movable portion moves to the open position and the metering valve opens.

  For this reason, using the technique of the above-mentioned Patent Document 1, as shown in FIG. 6, after the energization to the solenoid is stopped at the same timing as the normal valve opening control in the valve opening control of the high-pressure pump, Even if the power is temporarily re-energized, there is a possibility that the power is re-energized when the movable part stops against the metering valve. The moving speed when the part moves to the open position cannot be reduced, and it is difficult to reduce noise generated during valve opening control.

  Accordingly, an object of the present invention is to provide a control device for a high-pressure pump that can reduce noise generated during valve-opening control of the high-pressure pump.

In order to solve the above-mentioned problem, an invention according to claim 1 includes a pump chamber having a fuel inlet and outlet, a plunger that reciprocates in the pump chamber, a metering valve that opens and closes the inlet, In a control apparatus for a high pressure pump having an electromagnetic actuator for opening and closing the metering valve, the energization of the solenoid of the electromagnetic actuator is stopped and the movable part of the electromagnetic actuator is moved from the closed position to the open position. Valve opening control means for performing valve opening control for opening the metering valve, and the valve opening control means is configured to open the metering valve in the opening direction because the fuel pressure in the pump chamber decreases during the valve opening control . holding the movable part in the closed side position to continue the energization of the solenoid to be opened to a maximum position, the metering valve is temporarily stops energizing the solenoid after opening the maximum position of the opening direction, the movable Reaches the open position It is obtained so as to temporarily re-energizing the solenoid.

In this configuration, during valve opening control, energization of the solenoid is continued until the fuel pressure in the pump chamber decreases and the metering valve opens to the maximum position in the opening direction, and the movable part is held in the closed position. Then, after the metering valve is opened to the maximum position in the opening direction , the energization to the solenoid is temporarily stopped, so that the movable portion abuts against the metering valve and moves toward the open side position without stopping. Then, by temporarily re-energizing the solenoid before the movable part reaches the open side position, the electromagnetic attraction force of the solenoid is temporarily generated, and the movable part moves to the open side position by this electromagnetic attraction force. It is possible to reduce the moving speed when performing. Thereby, the vibration which generate | occur | produces when a movable part reaches | attains an open side position can be suppressed, and the noise which generate | occur | produces at the time of valve opening control can be reduced.

FIG. 1 is a diagram showing a schematic configuration of a fuel supply system for a direct injection engine according to an embodiment of the present invention. FIG. 2 is a schematic configuration diagram showing a state of the high-pressure pump during fuel suction. FIG. 3 is a schematic configuration diagram showing a state of the high-pressure pump during fuel discharge. FIG. 4 is a diagram for explaining normal valve opening control. FIG. 5 is a diagram for explaining valve-opening control for sound reduction. FIG. 6 is a diagram illustrating valve opening control of a comparative example. FIG. 7 is a diagram illustrating the relationship between the fuel pressure peak value and the metering valve opening period. FIG. 8 is a diagram showing the relationship between the fuel pressure peak value and the metering valve opening period. FIG. 9 is a diagram showing the relationship between fuel temperature and bulk modulus. FIG. 10 is a diagram showing the relationship between the fuel temperature and the metering valve opening period. FIG. 11 is a diagram for explaining the influence of the cam profile. FIG. 12 is a diagram showing the relationship between the descent speed of the cam lift amount and the metering valve opening period. FIG. 13 is a diagram for explaining a method for setting a current value during re-energization. FIG. 14 is a diagram for explaining flyback control. FIG. 15 is a schematic configuration diagram of a solenoid drive circuit. FIG. 16 is a time chart showing an execution example of flyback control. FIG. 17 is a flowchart showing the flow of processing of the valve opening control routine.

Hereinafter, an embodiment embodying a mode for carrying out the present invention will be described.
A low pressure pump 12 that pumps up the fuel is installed in the fuel tank 11 that stores the fuel. The low-pressure pump 12 is driven by an electric motor (not shown) that uses a battery (not shown) as a power source. The fuel discharged from the low pressure pump 12 is supplied to the high pressure pump 14 through the fuel pipe 13. A pressure regulator 15 is connected to the fuel pipe 13, and the pressure regulator 15 regulates the discharge pressure of the low-pressure pump 12 (fuel supply pressure to the high-pressure pump 14) to a predetermined pressure. Is returned to the fuel tank 11 by the fuel return pipe 16.

  As shown in FIGS. 2 and 3, the high-pressure pump 14 is a plunger pump that sucks / discharges fuel by reciprocating a plunger 18 in a cylindrical pump chamber 17, and the plunger 18 is a cam shaft 19 of the engine. It is driven by the rotational movement of the cam 20 fitted to the. A metering valve 23 that opens and closes the fuel passage 22 and an electromagnetic actuator 27 that opens and closes the metering valve 23 are provided on the suction port 21 side of the high-pressure pump 14.

  The electromagnetic actuator 27 electromagnetically drives the movable part 28 that can move, a spring 29 that urges the movable part 28 to the open position (see FIG. 2), and the movable part 28 to the closed position (see FIG. 3). A solenoid 30 (coil) or the like is used. The metering valve 23 includes a pressing portion 24 that is pressed in the valve opening direction by the movable portion 28 of the electromagnetic actuator 27, a valve body 25 that opens and closes the fuel passage 22, and a spring that biases the valve body 25 in the valve closing direction. 26 etc. A check valve 32 is provided on the discharge port 31 side of the high-pressure pump 14 to prevent the discharged fuel from flowing backward.

  As shown in FIG. 2, when the electromagnetic actuator 27 is not energized (when the energization of the solenoid 30 is turned off), the movable portion 28 moves to the open position by the biasing force of the spring 29 of the electromagnetic actuator 27. The pressing portion 24 of the metering valve 23 is pressed by the portion 28, the valve body 25 moves in the valve opening direction and opens, and the fuel passage 22 is opened.

  On the other hand, as shown in FIG. 3, when the electromagnetic actuator 27 is energized (when the solenoid 30 is energized), the movable portion 28 moves to the closed position by the electromagnetic attraction force of the solenoid 30 of the electromagnetic actuator 27. The valve body 25 moves in the valve closing direction by the urging force of the spring 26 of the metering valve 23 and closes, and the fuel passage 22 is closed.

  As shown in FIG. 2, the valve body 25 of the metering valve 23 is opened during the intake stroke of the high-pressure pump 14 (when the plunger 18 is lowered), and fuel is sucked into the pump chamber 17, as shown in FIG. The electromagnetic actuator 27 (solenoid 30) is energized so that the valve body 25 of the metering valve 23 closes and the fuel in the pump chamber 17 is discharged during the discharge stroke of the high-pressure pump 14 (when the plunger 18 is raised). Control.

  At that time, by controlling the energization start timing of the electromagnetic actuator 27 (solenoid 30) and controlling the valve closing period of the metering valve 23, the fuel discharge amount of the high-pressure pump 14 is controlled to control the fuel pressure (fuel pressure). To do. For example, when the fuel pressure is increased, the energization start timing of the electromagnetic actuator 27 is advanced to advance the valve closing start timing of the metering valve 23, thereby extending the valve closing period of the metering valve 23 and increasing the fuel pressure. 14 discharge flow rate is increased. Conversely, when reducing the fuel pressure, the energization start timing of the electromagnetic actuator 27 is retarded and the valve closing start timing of the metering valve 23 is retarded, thereby shortening the valve closing period of the metering valve 23 and increasing the pressure. The discharge flow rate of the pump 14 is decreased.

  As shown in FIG. 1, the fuel discharged from the high-pressure pump 14 is sent to a delivery pipe 34 through a high-pressure fuel pipe 33, and high-pressure fuel is supplied from the delivery pipe 34 to a fuel injection valve 35 attached to each cylinder of the engine. Is distributed. The delivery pipe 34 (or the high-pressure fuel pipe 33) is provided with a fuel pressure sensor 36 that detects the fuel pressure in the high-pressure fuel passage such as the high-pressure fuel pipe 33 and the delivery pipe 34.

  Further, the engine is provided with an air flow meter 37 for detecting the intake air amount and a crank angle sensor 38 for outputting a pulse signal at every predetermined crank angle in synchronization with rotation of a crankshaft (not shown). . Based on the output signal of the crank angle sensor 38, the crank angle and the engine speed are detected. Further, a cooling water temperature sensor 39 for detecting a cooling water temperature (cooling water temperature) is provided in the cylinder block of the engine.

  Outputs of these various sensors are input to an electronic control unit (hereinafter referred to as “ECU”) 40. The ECU 40 is mainly composed of a microcomputer, and executes various engine control programs stored in a built-in ROM (storage medium), so that the fuel injection amount and the ignition timing are determined according to the engine operating state. The throttle opening (intake air amount) and the like are controlled.

  Further, as shown in FIG. 4, the ECU 40 energizes the solenoid 30 of the electromagnetic actuator 27 to control the movable portion 28 of the electromagnetic actuator 27 during valve closing control for closing the metering valve 23 of the high-pressure pump 14. The metering valve 23 is closed by moving from the open position to the close position. Thereafter, during valve opening control for opening the metering valve 23 of the high-pressure pump 14, the energization of the solenoid 30 of the electromagnetic actuator 27 is stopped, and the movable portion 28 of the electromagnetic actuator 27 is moved from the closed position to the open position. And the metering valve 23 is opened.

However, during valve opening control of the high-pressure pump 14, the movable part 28 and the metering valve 23 collide with the stopper part 41 etc. at the maximum position in the opening direction, and vibration is generated, which can cause unpleasant noise. For example, during low-speed traveling or when the vehicle is stopped, it is easy for the driver to hear noise generated during valve opening control.

  By the way, as shown in FIG. 4, in the valve opening control of the high pressure pump 14, even when the energization to the solenoid 30 is stopped, the movable portion 28 is controlled by the metering valve when the fuel pressure in the pump chamber 17 is still high. Even if it hits 23 (pressing part 24), the metering valve 23 is maintained in the closed state by the fuel pressure in the pump chamber 17, so the movable part 28 stops in the state of hitting the metering valve 23 (pressing part 24). . Thereafter, when the fuel pressure in the pump chamber 17 decreases, the movable portion 28 moves to the open position and the metering valve 23 opens.

  For this reason, using the conventional technology, as in the comparative example shown in FIG. 6, after the energization of the solenoid 30 is stopped at the same timing as the normal valve opening control during the valve opening control of the high pressure pump 14, Even if the solenoid 30 is temporarily re-energized, there is a possibility that re-energization may occur when the movable part 28 stops against the metering valve 23 (pressing part 24). The fuel pressure in the pump chamber 17 decreases and the moving speed when the movable part 28 moves to the open position cannot be reduced, and it is difficult to reduce noise generated during valve opening control.

Therefore, in this embodiment, the ECU 40 executes a valve opening control routine shown in FIG. 17 to be described later, thereby stopping the energization of the solenoid 30 of the electromagnetic actuator 27 and closing the movable portion 28 during the valve opening control. When the predetermined sound reduction control execution condition is satisfied when the metering valve 23 is moved from the position to the open position and the metering valve 23 is opened), it is assumed that the noise generated during the valve opening control is easily heard by the driver. In order to reduce the noise generated during the valve opening control, sound reduction valve opening control is executed as shown in FIG. In this valve opening control for reducing sound, the solenoid 30 is continuously energized until the fuel pressure in the pump chamber 17 decreases and the metering valve 23 opens to the maximum position in the opening direction, and the movable portion 28 is closed. The solenoid valve 30 is temporarily deenergized after the metering valve 23 is opened to the maximum position in the opening direction . Thereby, the movable part 28 contacts the metering valve 23 and moves toward the open position without stopping. And before the movable part 28 reaches | attains an open side position, it re-energizes the solenoid 30 temporarily. Thereby, the electromagnetic attraction force of the solenoid 30 is temporarily generated, and the moving speed when the movable part 28 moves to the open side position is reduced by this electromagnetic attraction force.

In this valve-opening control for reducing noise, the fuel pressure in the pump chamber 17 decreases to a predetermined value (fuel pressure at which the metering valve 23 opens ) or lower and the metering valve 23 opens to the maximum position in the opening direction. It is necessary to continue energization of the solenoid 30 and hold the movable portion 28 in the closed position.

Here, the relationship between the cam lift amount L (the lift amount of the plunger 18) and the fuel pressure P in the pump chamber 17 uses the volume V of the pump chamber 17, the volume elastic modulus E of the fuel, and the area S of the plunger 18. Then, it can be expressed by the following formula (1).
L = P × V / (E × S) (1)
From the above equation (1), as the fuel pressure P in the pump chamber 17 increases, the amount of decrease in the cam lift amount L required to reduce the fuel pressure P to a predetermined value or less increases, so the fuel pressure P decreases to a predetermined value or less. The period until it decreases becomes longer.

  For this reason, as shown in FIG. 7, as the fuel pressure peak value in the pump chamber 17 increases, the period until the fuel pressure drops below a predetermined value (fuel pressure at which the metering valve 23 opens) becomes longer. The amount valve opening period (the period from when the fuel pressure starts to drop until the metering valve 23 opens) becomes longer. That is, as shown in FIG. 8, there is a characteristic that the metering valve opening period becomes longer as the fuel pressure peak value in the pump chamber 17 becomes higher.

Therefore, in this embodiment, during the valve opening control for sound reduction, the period during which the movable portion 28 is held at the closed position is changed according to the fuel pressure peak value in the pump chamber 17. Specifically, as the fuel pressure peak value in the pump chamber 17 becomes higher, the energization extension period (period in which energization to the solenoid 30 is extended with respect to the energization stop timing of normal valve opening control) is lengthened, and the movable part The period for holding 28 in the closed position is lengthened. In this way, according to the fuel pressure peak value in the pump chamber 17, the period during which the movable portion 28 is held at the closed position can be changed corresponding to the change in the metering valve opening period. . Thus, even if the metering valve opening period changes due to the change in the fuel pressure peak value, the movable portion 28 is reliably held at the closed position until the metering valve 23 opens to the maximum position in the opening direction. it can.

  Moreover, as shown in FIG. 9, the higher the fuel temperature, the smaller the volume elastic modulus of the fuel. Furthermore, from the above equation (1), as the volume elastic modulus E of the fuel decreases, the amount of decrease in the cam lift amount L required to lower the fuel pressure P to a predetermined value or greater increases, so the fuel pressure P decreases to a predetermined value or less. The period until it decreases becomes longer (that is, the metering valve opening period becomes longer). For this reason, as shown in FIG. 10, there is a characteristic that the metering valve opening period becomes longer as the fuel temperature becomes higher.

Therefore, in the present embodiment, during valve opening control for sound reduction, the period during which the movable portion 28 is held at the closed position is changed according to the fuel temperature. Specifically, as the fuel temperature increases, the energization extension period is lengthened, and the period for holding the movable portion 28 in the closed position is lengthened. In this way, the period during which the movable portion 28 is held at the closed position can be changed in accordance with the change in the metering valve opening period according to the fuel temperature. As a result, even if the metering valve opening period changes due to a change in fuel temperature, the movable portion 28 can be reliably held at the closed position until the metering valve 23 opens to the maximum position in the opening direction. . The fuel temperature may be detected by a temperature sensor, but the coolant temperature, the oil temperature, or the like may be used as fuel temperature substitute information. Alternatively, the fuel temperature may be estimated based on the cooling water temperature, the oil temperature, or the like.

  Moreover, as shown in FIG. 11, the descending speed of the cam lift amount varies depending on the cam profile (the shape of the cam 20). Furthermore, as shown in FIG. 12, the metering valve opening period is shortened as the cam lift amount descending speed increases. That is, the metering valve opening period changes according to the cam profile.

Therefore, in this embodiment, the period during which the movable portion 28 is held at the closed position is changed according to the cam profile. Specifically, the energization extension period is shortened and the period during which the movable portion 28 is held in the closed position is shortened as the cam lift amount descending speed increases due to the difference in the cam profile. In this way, according to the cam profile, the period during which the movable portion 28 is held at the closed position can be changed in response to the change in the metering valve opening period. Thereby, even if the metering valve opening period changes due to the difference in the cam profile, the movable portion 28 can be reliably held at the closed position until the metering valve 23 opens to the maximum position in the opening direction. .

Further, when the “energization extension period” is set as “time”, the metering valve opening period (time) changes according to the rotation speed of the cam 20. By changing the period (time), the period (time) for holding the movable part 28 in the closed position is changed. In this way, the period (time) for holding the movable portion 28 in the closed position is changed in accordance with the change in the metering valve opening period (time) according to the rotational speed of the cam 20. be able to. Thus, even if the metering valve opening period (time) changes due to the change in the rotational speed of the cam 20, the movable portion 28 is reliably closed until the metering valve 23 opens to the maximum position in the opening direction. Can be held in.
When the “energization extension period” is set as “cam angle or crank angle”, it is not affected by the rotational speed of the cam 20, so there is no need to make a change according to the rotational speed of the cam 20.

  Further, in this embodiment, during the valve opening control for sound reduction, the solenoid 30 is temporarily re-energized before the movable portion 28 reaches the open position, but FIG. As shown in FIG. 6, if the current value when the current is re-energized is too large, the electromagnetic attraction force of the solenoid 30 becomes too large, and the movable portion 28 may be returned to the closed position direction.

  Therefore, in this embodiment, as shown in FIG. 13A, the current value at the time of re-energization is set within a range in which the backward movement of the movable portion 28 toward the closed position does not occur. In this way, when the solenoid 30 is temporarily re-energized before the movable part 28 reaches the open position, it is possible to prevent the movable part 28 from returning back to the closed position.

Further, in the present embodiment, during valve opening control for sound reduction, energization to the solenoid 30 is temporarily stopped after the metering valve 23 is opened to the maximum position in the opening direction . As shown in (b), when the flyback control to be described later is not executed, when the energization to the solenoid 30 is temporarily stopped, the current flowing through the solenoid 30 is slowly reduced by the counter electromotive force. For this reason, the electromagnetic attraction force of the solenoid 30 is generated even after the energization of the solenoid 30 is stopped, and the behavior when the movable part 28 moves to the open side position varies due to the influence of the electromagnetic attraction force. It becomes difficult.

  Therefore, in this embodiment, as shown in FIG. 14A, the flyback circuit 46 (see FIG. 15) removes the current flowing through the solenoid 30 by the back electromotive force when the energization to the solenoid 30 is temporarily stopped. Perform back control. By doing so, the electromagnetic attraction force of the solenoid 30 hardly occurs after the energization of the solenoid 30 is stopped, and the behavior when the movable portion 28 moves to the open side position is stabilized. Can be set.

  Specifically, as shown in FIG. 15, in the drive circuit 42 of the solenoid 30, the solenoid 30 and the diode 44 are connected in parallel to the battery 43, and the switch S <b> 1 is connected between the battery 43 and the diode 44. The switch S2 and the resistor 45 are connected between the diode 44 and the solenoid 30. Further, a flyback circuit 46 is connected in parallel with the switch S2 and the resistor 45, and the flyback circuit 46 includes a Zener diode 47 and a switch S3.

  Normally (when the flyback control is not executed), as shown in FIGS. 15A and 15B, the solenoid 30 is energized by turning on / off the switch S1 with the switch S2 turned on. Turn on / off (execute / stop).

  On the other hand, when the flyback control is executed when the energization to the solenoid 30 is stopped, as shown in FIG. 15C, the switch S2 is turned off and the switch S3 is turned on simultaneously. Thereby, the energy accumulated in the solenoid 30 is converted into a counter electromotive force while being limited by the Zener diode 47, and flyback control is performed to quickly reduce the current flowing through the solenoid 30 and remove the current (see FIG. 16).

The valve opening control of the high pressure pump 14 of the present embodiment described above is executed by the ECU 40 according to the valve opening control routine of FIG. The processing contents of this routine will be described below.
The valve opening control routine shown in FIG. 17 is repeatedly executed at a predetermined period during the power-on period of the ECU 40 (while the ignition switch is on), and serves as valve opening control means in the claims. When this routine is started, first, in step 101, it is determined whether or not a predetermined sound reduction control execution condition is satisfied, for example, depending on whether or not all of the following conditions (1) to (5) are satisfied. judge.

(1) Battery voltage is stable (battery voltage> predetermined value)
(2) Running at low speed or stopping (vehicle speed ≤ predetermined value)
(3) Accelerator off (accelerator opening = 0)
(4) The engine rotation speed is in a stable state (| target rotation speed−engine rotation speed | ≦ predetermined value)
(5) The fuel pressure is in a stable state (| target fuel pressure – fuel pressure | ≦ predetermined value)

Here, the above conditions (2) and (3) are conditions for determining whether or not the noise generated during the valve opening control is easily heard by the driver.
If all of the above conditions (1) to (5) are satisfied, the sound reduction control execution condition is satisfied, but if there is a condition that does not satisfy any one of the above conditions (1) to (5), The sound reduction control execution condition is not satisfied.

  If it is determined in step 101 that the sound reduction control execution condition is not satisfied, the routine proceeds to step 102 where normal valve opening control (see FIG. 4) is executed. In this normal valve opening control, energization to the solenoid 30 of the electromagnetic actuator 27 is stopped when the fuel pressure in the pump chamber 17 becomes high. In this case, since the metering valve 23 is maintained in the closed state by the fuel pressure in the pump chamber 17, the movable portion 28 stops in contact with the metering valve 23 (pressing portion 24). When the internal fuel pressure decreases, the movable portion 28 moves to the open position and the metering valve 23 opens.

  On the other hand, if it is determined in step 101 that the sound reduction control execution condition is satisfied, it is determined that the noise generated during the valve opening control is easily heard by the driver, and the sound reduction control is performed. The valve opening control is executed as follows. First, in step 103, an “energization extension period (see FIG. 5)” that is a period for extending the energization to the solenoid 30 with respect to the energization stop timing of the normal valve opening control is set as the “cam angle or crank angle”. .

  In this case, first, the energization extension period corresponding to the fuel pressure peak value in the pump chamber 17 is calculated by a map or a mathematical expression. As a result, the higher the fuel pressure peak value in the pump chamber 17 is, the longer the energization extension period and the longer the period for holding the movable part 28 in the closed position. The energization extension period map or mathematical expression is created in advance based on test data, design data, etc., and stored in the ROM of the ECU 40.

  Further, a correction value corresponding to the fuel temperature is calculated using a map or a mathematical formula, and the energization extension period is corrected using this correction value. As a result, the higher the fuel temperature, the longer the energization extension period and the longer the period for holding the movable portion 28 in the closed position. Furthermore, a correction value corresponding to the cam profile may be calculated using a map or a mathematical formula, and the energization extension period may be corrected using this correction value. Thereby, the energization extension period is shortened and the period during which the movable portion 28 is held in the closed position is shortened as the cam lift amount descending speed increases due to the difference in the cam profile. A map or mathematical expression of the correction value for the energization extension period is created in advance based on test data, design data, and the like, and is stored in the ROM of the ECU 40.

  When the “energization extension period” is set as “time”, the metering valve opening period (time) changes according to the rotation speed of the cam 20, and accordingly, according to the rotation speed of the cam 20, The energization extension period (time) is changed, and the period (time) for holding the movable portion 28 in the closed position is changed.

  Thereafter, the routine proceeds to step 104, where the “energization stop time (see FIG. 5)”, which is the time from when power supply to the solenoid 30 is temporarily stopped to when power is supplied again, is set to a predetermined time T1 (eg, 0.5 ms). The “re-energization time (see FIG. 5)”, which is the time for which the solenoid 30 is continuously energized, is set to a predetermined time T2 (for example, 1 ms), and the current value when the solenoid 30 is energized again is “re-energized”. The “energization current value (see FIG. 5)” is set to a predetermined current value (eg, 3 A). The predetermined time T1, the predetermined time T2, and the predetermined current value are set in advance based on test data, design data, and the like, and are stored in the ROM of the ECU 40.

Thereafter, the process proceeds to step 105, and energization to the solenoid 30 is continued until the energization extension period ends, so that the fuel pressure in the pump chamber 17 decreases and the metering valve 23 opens to the maximum position in the opening direction. Until the solenoid 30 is energized, the movable portion 28 is held at the closed position.

Thereafter, the process proceeds to step 106, and when the energization extension period set in step 103 is completed, the energization of the solenoid 30 is temporarily stopped, so that the metering valve 23 is opened to the maximum position in the opening direction. While the energization of the solenoid 30 is temporarily stopped, the flyback control for removing the current flowing through the solenoid 30 by the flyback circuit 46 is performed by simultaneously turning off the drive circuit 42 switch S2 and the switch S3 of the solenoid 30. To do.

  Thereafter, the process proceeds to step 107, and when the energization stop time set in step 104 has elapsed, the solenoid 30 is re-energized with the re-energization time and re-energization current value set in step 104, whereby the movable portion 28. The solenoid 30 is temporarily energized before reaching the open position. Thereby, the electromagnetic attraction force of the solenoid 30 is temporarily generated, and the moving speed when the movable part 28 moves to the open side position is reduced by this electromagnetic attraction force.

In the present embodiment described above, during valve opening control (that is, energization of the solenoid 30 of the electromagnetic actuator 27 is stopped, the movable portion 28 is moved from the closed position to the open position, and the metering valve 23 is opened). When a predetermined sound reduction control execution condition is satisfied, it is determined that the noise generated during the valve opening control is easily heard by the driver, and the sound reduction valve opening control is executed. In this valve opening control for reducing sound, the solenoid 30 is continuously energized until the fuel pressure in the pump chamber 17 decreases and the metering valve 23 opens to the maximum position in the opening direction, and the movable portion 28 is closed. The solenoid valve 30 is temporarily deenergized after the metering valve 23 is opened to the maximum position in the opening direction . Thereby, the movable part 28 contacts the metering valve 23 and moves toward the open position without stopping. And before the movable part 28 reaches | attains an open side position, it re-energizes the solenoid 30 temporarily. Thereby, the electromagnetic attraction force of the solenoid 30 can be temporarily generated, and the moving speed when the movable portion 28 moves to the open position by this electromagnetic attraction force can be reduced. Thereby, the vibration which generate | occur | produces when the movable part 28 reaches | attains an open side position can be suppressed, and the noise which generate | occur | produces at the time of valve opening control can be reduced.

  In the above embodiment, the period during which the movable portion 28 is held at the closed position is changed according to the fuel pressure peak value in the pump chamber 17, the fuel temperature, and the like. You may make it fix the period which hold | maintains 28 in a closed position in the predetermined period (period beyond the maximum value of a metering valve opening period) set beforehand.

  In addition, the present invention can be implemented with various modifications without departing from the gist, such as appropriately changing the configuration of the high-pressure pump and the configuration of the fuel supply system.

  DESCRIPTION OF SYMBOLS 14 ... High pressure pump, 17 ... Pump chamber, 18 ... Plunger, 20 ... Cam, 21 ... Suction port, 23 ... Metering valve, 27 ... Electromagnetic actuator, 28 ... Movable part, 30 ... Solenoid, 31 ... Discharge port, 40 ... ECU (valve opening control means), 46... Flyback circuit

Claims (7)

A pump chamber (17) having a fuel suction port (21) and a discharge port (31), a plunger (18) reciprocating in the pump chamber, a metering valve (23) for opening and closing the suction port side, In a control device for a high pressure pump (14) comprising an electromagnetic actuator (27) for opening and closing the metering valve,
The energization of the solenoid (30) of the electromagnetic actuator is stopped, the movable part (28) of the electromagnetic actuator is moved from the closed position to the open position, and valve opening control is performed to open the metering valve. Comprising valve opening control means (40),
In the valve opening control, the valve opening control means continues to energize the solenoid until the fuel pressure in the pump chamber decreases and the metering valve opens to the maximum position in the opening direction. After the movable part is held at the closed position, the energization to the solenoid is temporarily stopped after the metering valve is opened to the maximum position in the opening direction, and before the movable part reaches the open position. A control apparatus for a high-pressure pump, wherein the solenoid is temporarily re-energized.   The high-pressure pump control device according to claim 1, wherein the valve-opening control unit changes a period during which the movable portion is held at the closed position according to fuel pressure.   The control apparatus for a high-pressure pump according to claim 1 or 2, wherein the valve-opening control means changes a period during which the movable part is held at the closed position according to a fuel temperature.   The valve opening control means changes a period during which the movable part is held at the closed position in accordance with a rotational speed of a cam (20) that drives the plunger. A control device for a high pressure pump according to claim 1.   5. The valve opening control means changes a period during which the movable portion is held at the closed position in accordance with a shape of a cam that drives the plunger. 6. High pressure pump control device.   The valve-opening control means does not cause a reversal of the current value when the solenoid is temporarily energized to the solenoid before the movable part reaches the open side position in the direction toward the closed side of the movable part. The high pressure pump control device according to any one of claims 1 to 5, wherein the control device is set within a range. The valve-opening control means is a flyback control in which a current flowing through the solenoid is removed by a flyback circuit (46) when energization of the solenoid is temporarily stopped after the metering valve is opened to the maximum position in the opening direction. The high pressure pump control device according to any one of claims 1 to 6, wherein:

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