Patent Publication Number: US-10330064-B2

Title: Control device for high-pressure pump

Description:
CROSS REFERENCE TO RELATED APPLICATION 
     The application is the U.S. national phase of International Application No. PCT/JP2014/003709 filed 14 Jul. 2014, which designated the U.S. and claims priority to Japanese Patent Applications No. 2013-161052 filed on Aug. 2, 2013, the entire contents of each of which are hereby incorporated by reference. 
     TECHNICAL FIELD 
     The present disclosure relates to a control device for a high-pressure pump. 
     BACKGROUND ART 
     Conventionally, as a fuel supply system of an internal combustion engine, such as a gasoline engine or a diesel engine, a fuel supply system of an in-cylinder injection type that includes: a high-pressure pump for increasing pressure of low-pressure fuel that is pumped from a fuel tank to be high pressure; and a pressure accumulator chamber for storing high-pressure fuel that is pressure-fed from the high-pressure pump and that directly injects the high-pressure fuel in the pressure accumulator chamber from a fuel injection valve to inside of a cylinder of the internal combustion engine has been known. In addition, as the above high-pressure pump, a high-pressure pump that includes: a plunger that reciprocates within the cylinder; a pressurizing chamber into which the fuel from a low-pressure side is introduced; and a control valve of an electromagnetic drive type that adjusts a returning amount of the fuel introduced into the pressurizing chamber has been known. 
     As one example of the above high-pressure pump, the plunger is connected to a rotational shaft of an output shaft (a crankshaft) of the internal combustion engine, reciprocates within the cylinder when the rotational shaft rotates along with rotation of the crankshaft, and thus can change a volume of the pressurizing chamber. The control valve is an electromagnetic valve of a constantly open type, for example, and permits introduction of the fuel from a low-pressure side passage into the pressurizing chamber when a valve body is held at a valve opening position by a spring during non-energization of a solenoid coil. On the other hand, during energization of the coil, the valve body is displaced to a valve closing position by an electromagnetic force thereof and blocks the introduction of the fuel into the pressurizing chamber. In a state where the valve body of the control valve is at the valve opening position in a volume reduction stroke of the pressurizing chamber, a surplus of the fuel is returned from the pressurizing chamber to the low-pressure side in conjunction with movement of the plunger. Thereafter, when the valve body is controlled to be at the valve closing position by the energization of the coil, the fuel in the pressurizing chamber is pressurized by the plunger and discharged to a high-pressure side. In this way, discharge amount control of the high-pressure pump is executed. 
     During actuation of the control valve, collision sound may be produced when the valve body collides with a movement limiting member (a stopper), and the sound may give an occupant a sense of discomfort. In Patent Literature 1, various methods for reducing the collision sound between the valve body and the stopper in the discharge amount control of the high-pressure pump by the control valve are described. In Patent Literature 1, when the valve body moves to the valve closing position, the coil is energized at a minimum current value that is required to completely close the valve body. In this way, a time spent by the valve body to move to the valve closing position is extended, and a collision speed of the valve body with the stopper is reduced. Thereby, the collision sound is reduced. 
     In addition, in Patent Literature 1, in order to determine the above minimum current value, actual fuel pressure and target fuel pressure of the pressure accumulator chamber are compared, and the above minimum current value is determined on the basis of a current value at which a deviation of the actual fuel pressure from the target fuel pressure exceeds a threshold. In other words, when it is estimated that the current value applied to the coil is reduced and the actual fuel pressure of the pressure accumulator chamber falls below a lower limit value, it is estimated that complete closing of the control valve is not guaranteed. In addition, when the control valve is not completely closed, it is estimated that a fuel supply of the high-pressure pump is at least limited to such a degree that sufficiently high pressure can no longer be generated in the pressure accumulator chamber. In view of the above, in Patent Literature 1, the above minimum current value is determined on the basis of the current value at which the deviation of the actual fuel pressure from the target fuel pressure exceeds the threshold. 
     However, in the high-pressure pump, due to an individual difference or an environmental change, a variation in a fuel discharge amount with respect to the current value that is applied to the coil may be generated, and due to this variation, the fuel discharge amount may be increased or reduced from what is assumed. For this reason, when the actual fuel pressure and the target fuel pressure are compared and it is determined on the basis of a comparison result whether the fuel is discharged from the high-pressure pump (whether the pump is actuated), a relationship between the current value applied to the coil and an actuation state of the high-pressure pump at the current value may not accurately be comprehended. 
     PRIOR ART LITERATURES 
     Patent Literature 
     Patent Literature 1: JP2010-533820A 
     SUMMARY OF INVENTION 
     The present disclosure has been made to solve the above problem and therefore has a purpose of providing a control device for a high-pressure pump that can accurately comprehend an actuation state of the high-pressure pump. 
     According to an aspect of the present disclosure, the control device for a high-pressure pump is applied to a high-pressure pump including a plunger that reciprocates in conjunction with rotation of a rotational shaft so as to be able to change a volume of a pressurizing chamber, and a control valve that has a valve body disposed in a fuel suction passage that communicates with the pressurizing chamber and supplies/blocks fuel to/from the pressurizing chamber by displacing the valve body in an axial direction by energization control with respect to an electromagnetic section. The control device for the high-pressure pump adjusts a fuel discharge amount of the high-pressure pump by switching a valve opening and a valve closing of the control valve by the energization control. The control device for the high-pressure pump includes a movement detection section detecting movement of the valve body with respect to a drive command of the valve opening or the valve closing of the control valve, and an actuation determination section making an actuation determination of the high-pressure pump on the basis of a detection result of the movement detection section. 
     When the first valve body and the second valve body show the normal movement with respect to the drive command of the valve opening/valve closing of the control valve, the high-pressure pump is actuated, and the fuel is discharged from the high-pressure pump. On the other hand, when the first valve body and the second valve body do not show the normal movement with respect to the drive command, the high-pressure pump is not actuated, and the fuel is not discharged from the high-pressure pump. Attention is focused on this point. In the above configuration, the movement of the valve body with respect to the drive command of the valve opening or the valve closing of the control valve is monitored, and the actuation state of the high-pressure pump is determined from the movement of the valve body. Thus, the actuation state of the high-pressure pump can accurately be comprehended. 
     It is preferable that the movement detection section detects the movement of the valve body with respect to the drive command by detecting at least one of a change in a current flowing through the electromagnetic section, a change in a voltage applied to the electromagnetic section, a displacement amount of the valve body, and a vibration of the control valve. Therefore, the actuation state of the high-pressure pump can be directly or indirectly monitored, and the actuation state of the high-pressure pump can accurately be comprehended. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
       The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description made with reference to the accompanying drawings. In the drawings: 
         FIG. 1  is a configuration diagram of an overall outline of a fuel supply system of an engine of a first embodiment. 
         FIG. 2A  is a time chart of a behavior during actuation of a high-pressure pump. 
         FIG. 2B  is a view of an operation of the high-pressure pump indicated by IIB in  FIG. 2A . 
         FIG. 2C  is a view of the operation of the high-pressure pump indicated by IIC in  FIG. 2A . 
         FIG. 2D  is a view of the operation of the high-pressure pump indicated by IID in  FIG. 2A . 
         FIG. 2E  is a view of the operation of the high-pressure pump indicated by IIE in  FIG. 2A . 
         FIG. 3  is a time chart of a behavior during non-actuation of the high-pressure pump. 
         FIG. 4  includes time charts for depicting a method for detecting movement of a valve body on the basis of a current speed. 
         FIG. 5  is a flowchart of a pump actuation determination process of the first embodiment. 
         FIG. 6  is a time chart of an energization start timing calculation process. 
         FIG. 7  is a time chart of the energization start timing calculation process. 
         FIG. 8  is a flowchart of a pump abnormality diagnosis process of the first embodiment. 
         FIG. 9  is a view of a schematic configuration of a control valve of a second embodiment. 
         FIG. 10  is a time chart for depicting relationships between detected voltages of first to third voltage sensors and time. 
         FIG. 11  is a flowchart of a pump actuation determination process of the second embodiment. 
         FIG. 12  is a flowchart of a pump abnormality diagnosis process of the second embodiment. 
         FIG. 13  is a view of a schematic configuration of a control valve of a third embodiment. 
         FIG. 14  is a time chart of a pump actuation determination process of the third embodiment. 
         FIG. 15  is a flowchart of the pump actuation determination process of the third embodiment. 
         FIG. 16  is a view of a schematic configuration of a control valve of a fourth embodiment. 
         FIG. 17  is a time chart of a pump actuation determination process of the fourth embodiment. 
         FIG. 18  is a flowchart of the pump actuation determination process of the fourth embodiment. 
         FIG. 19  includes time charts of a pump actuation determination process of another embodiment. 
     
    
    
     DESCRIPTION OF EMBODIMENTS 
     Hereafter, referring to drawings, an embodiment of the present invention will be described. In addition, the substantially same parts and components are indicated with the same reference numeral in following embodiments. 
     First Embodiment 
     A description will hereinafter be made on a first embodiment in which the present disclosure is embodied with reference to the drawings. In this embodiment, a fuel supply system for supplying fuel to an on-vehicle gasoline engine of an in-cylinder injection type as an internal combustion engine is constructed. The system controls a fuel discharge amount of a high-pressure pump, a fuel injection amount of an injector, and the like with an electronic control unit (ECU) being a central part. An overall schematic configuration diagram of the system is depicted in  FIG. 1 . 
     A fuel tank  11  is provided in the fuel supply system of  FIG. 1 . Fuel stored in the fuel tank  11  is pumped by a low-pressure pump  12  of an electromagnetic drive type that corresponds to a feed pump, and is introduced into a high-pressure pump  20  via a low-pressure pipe  13 . Pressure of the fuel that has been introduced in the high-pressure pump  20  is increased to be high pressure by the high-pressure pump  20  and is then pressure-fed to a pressure accumulator chamber  14 . The high-pressure fuel that has been pressure-fed is stored in a high-pressure state in the pressure accumulator chamber  14 , and is then directly injected into a cylinder from an injector  15  that is attached to each of the cylinders of the engine. 
     Next, the high-pressure pump  20  will be described. The high-pressure pump  20  of the system is configured as a plunger pump and performs suction and discharge of the fuel in conjunction with movement of a plunger. 
     More specifically, as depicted in  FIG. 1 , in the high-pressure pump  20 , a cylinder  21  is disposed in a pump main body, and a plunger  22  is inserted in the cylinder  21  in a freely reciprocating manner in an axial direction. A first end  22   a  of the plunger  22  abuts against a cam  23  by an urging force of a spring, which is not depicted. The cam  23  has multiple cam ridges and is fixed to a camshaft  24  that rotates along with rotation of an output shaft (a crankshaft  16 ) of the engine. In this embodiment, the camshaft  24  is referred to as a rotational shaft  24 . In this way, when the crankshaft  16  rotates during an operation of the engine, the plunger  22  can move within the cylinder  21  in the axial direction in conjunction with rotation of the cam  23 . 
     A pressurizing chamber  25  is provided on a second end  22   b  of the plunger  22 . The pressurizing chamber  25  communicates with a fuel suction passage  26  and a fuel discharge passage  27 , and introduction/discharge of the fuel into/from the pressurizing chamber  25  are performed via these passages  26 ,  27 . More specifically, when the plunger  22  moves in a first direction to increase a volume of the pressurizing chamber  25 , in conjunction with the movement, low-pressure fuel in the low-pressure pipe  13  is introduced into the pressurizing chamber  25  via the fuel suction passage  26 . In addition, when the plunger  22  moves in a second direction to reduce the volume of the pressurizing chamber  25 , in conjunction with the movement, the fuel in the pressurizing chamber  25  is discharged from the pressurizing chamber  25  to the fuel discharge passage  27 . 
     A control valve  30  for adjusting a fuel discharge amount of the high-pressure pump  20  is provided in a fuel entry portion of the high-pressure pump  20  that is on an upstream side of the pressurizing chamber  25 . The control valve  30  is configured as an opening/closing valve that performs supply/blockage of the fuel to/from the pressurizing chamber  25  by displacing a valve body in an axial direction by energization control of a coil  33  as an electromagnetic section. The fuel suction passage  26  is provided on the inside of the control valve  30 , and in the fuel suction passage  26 , a first valve chamber  31  and a second valve chamber  32  are sequentially formed along a flow of the fuel. 
     A first valve body  34  that is displaced by non-energization/energization of the coil  33  is accommodated in the first valve chamber  31 . The first valve body  34  is held at a valve opening position by a first spring  35  as an urging section during the non-energization of the coil  33 , and is displaced against an urging force of the first spring  35  to a position (a valve closing position) to abut against a first stopper  36  as a movement limiting member for limiting movement of the first valve body  34  during the energization of the coil  33 . A power supply  53  is connected to an input terminal side of the coil  33 , and electricity is supplied from the power supply  53  to the coil  33 . 
     A second valve body  37  that is coaxially disposed with the first valve body  34  is accommodated in the second valve chamber  32 . The second valve body  37  can be displaced along with the movement of the first valve body  34 . More specifically, when the first valve body  34  is at the valve opening position, the second valve body  37  is pressed by the first valve body  34  in the axial direction and is thereby held at a position (a valve opening position) to abut against a second stopper  39  as a movement limiting member for limiting movement of the second valve body  37  against an urging force of a second spring  38 . In this state, the second valve body  37  separates from a valve seat  40 , and the low-pressure pipe  13  and the pressurizing chamber  25  communicate with each other. Accordingly, the introduction of the low-pressure fuel into the pressurizing chamber  25  is permitted. On the other hand, when the first valve body  34  is at the valve closing position in conjunction with the energization of the coil  33 , the second valve body  37  is released from being pressed by the first valve body  34 , is thus seated on the valve seat  40  by the urging force of the second spring  38 , and is held at the valve closing position. In this state, communication between the low-pressure pipe  13  and the pressurizing chamber  25  is brought into a blocked state, and the introduction of the low-pressure fuel into the pressurizing chamber  25  is blocked. 
     The pressurizing chamber  25  is connected to the pressure accumulator chamber  14  via the fuel discharge passage  27 . In addition, a check valve  41  is provided in the middle of the fuel discharge passage  27 . The check valve  41  includes a check valve main body  42  and a check valve spring  43 , and the check valve main body  42  is displaced in an axial direction when fuel pressure in the pressurizing chamber  25  becomes at least equal to predetermined pressure. More specifically, when the fuel pressure in the pressurizing chamber  25  is lower than the predetermined pressure, the check valve main body  42  is brought into a state of being held at a valve closing position by an urging force of the check valve spring  43 , and thus discharge of the fuel from the pressurizing chamber  25  to the fuel discharge passage  27  is blocked. Meanwhile, when the fuel pressure in the pressurizing chamber  25  becomes at least equal to the predetermined pressure, the check valve main body  42  is displaced (opened) against the urging force of the check valve spring  43 , and the discharge of the fuel from the pressurizing chamber  25  to the fuel discharge passage  27  is permitted. 
     In addition to the above, the system is provided with various sensors, such as a crank angle sensor  51  for outputting a rectangular crank angle signal at every predetermined crank angle of the engine, a fuel pressure sensor  52  for detecting fuel pressure in the pressure accumulator chamber  14 , and a current sensor  54  for detecting an output current of the coil  33 . The output current of the coil  33  corresponds to a coil current that flows through the coil  33 . 
     As it has been well known, an ECU  50  is constructed of a microcomputer formed of a CPU, a ROM, a RAM, and the like as a main body, and executes various types of engine control in accordance with an operation state of the engine at the time by executing various control programs stored in the ROM. That is, the microcomputer of the ECU  50  receives detection signals from the above-described various sensors and the like, computes control amounts of various parameters related to the operation of the engine on the basis of these detection signals, and controls driving of the injector  15  and the control valve  30  on the basis of the computation values. 
     In this embodiment, in order to bring actual fuel pressure that is detected by the fuel pressure sensor  52  to target fuel pressure, as discharge amount control of the high-pressure pump  20 , feedback control that is based on a deviation of the actual fuel pressure from the target fuel pressure is executed. In this way, the fuel pressure in the pressure accumulator chamber  14  is controlled to become pressure (the target fuel pressure) that corresponds to the operation state of the engine. In addition, an energization amount of the coil  33  is adjusted by duty control. 
     The discharge amount control of the high-pressure pump  20  will further be described. The microcomputer of the ECU  50  adjusts the fuel discharge amount of the high-pressure pump  20  by controlling valve closing timing of the control valve  30 . More specifically, the ECU  50  is connected to the coil  33  of the control valve  30  via a coil drive circuit, which is not depicted, and controls an application voltage and energization timing of the coil  33  by outputting a drive command of valve opening/valve closing of the control valve  30  to the coil drive circuit. 
       FIG. 2A  is a time chart of a behavior when the high-pressure pump  20  is actuated normally with respect to the drive command by the ECU  50 . In  FIG. 2A , (a) indicates a relationship between a position of the plunger  22  that is associated with the rotation of the cam  23  and time, (b) indicates a relationship between a drive signal of the control valve  30  and time, (c) indicates a relationship between the output current of the coil  33  and time, (d) indicates a relationship between a coil voltage and the time, the coil voltage being a voltage between an input terminal and an output terminal of the coil  33 , (e) indicates relationships between displacements of the first valve body  34  and the second valve body  37  from the valve opening positions and time, (f) indicates a relationship between a vibration that is generated in the control valve  30  (for example, the valve main body) and time, and (g) indicates a relationship between the fuel pressure in the pressurizing chamber  25  and time. The position of the plunger  22  that is associated with the rotation of the cam  23  corresponds to a profile of the cam  23 . The coil voltage is also referred to as a voltage between the input/output terminals. 
     In (a), BDC represents bottom dead center of the plunger  22 , and TDC represents top dead center of the plunger  22 . Regarding the drive signal of (b), an OFF signal is outputted in a case of a valve opening command for keeping the control valve  30  to be in a valve opened state, and an ON signal is outputted in a case of a valve closing command for keeping the control valve  30  to be in a valve closed state. In (g), Pf represents feed pressure as fuel pressure in the low-pressure pipe  13 , and Pr represents rail pressure as the fuel pressure in the pressure accumulator chamber  14 . 
     In a volume increase stroke that corresponds to a period in which the plunger  22  moves in the first direction to increase the volume of the pressurizing chamber  25  in conjunction with the rotation of the cam  23 , as depicted in  FIG. 2E , the coil  33  is not energized, and the first valve body  34  and the second valve body  37  are set at the valve opening positions. That is, the first valve body  34  is in a state of separating from the first stopper  36  by the urging force of the first spring  35 , and the second valve body  37  is in a state of abutting against the second stopper  39  by the first valve body  34 . In this way, the pressurizing chamber  25  and the fuel suction passage  26  are brought into a communicating state, and the low-pressure fuel is introduced into the pressurizing chamber  25 . In this embodiment, a period in which the low-pressure fuel is introduced into the pressurizing chamber  25  is a suction stroke. 
     In a period in which the plunger  22  moves from the bottom dead center to the top dead center, the volume of the pressurizing chamber  25  is reduced. In a volume reduction stroke that corresponds to this period, valve closing is commanded at timing that corresponds to a requested discharge amount, and the energization of the coil  33  is started. At this time, before a start of the energization of the coil  33  (before t 12 ), the second valve body  37  is in a state of separating from the valve seat  40 . Accordingly, as depicted in  FIG. 2B , the fuel in the pressurizing chamber  25  is returned to the fuel suction passage  26  side along with the movement of the plunger  22 . In this embodiment, a period in which the fuel in the pressurizing chamber  25  is returned to the fuel suction passage  26  side is an amount adjustment stroke. 
     The first valve body  34  is attracted toward the coil  33  by the start of the energization of the coil  33 , and as depicted in  FIG. 2C , the first valve body  34  moves to a valve closing position CL 1  that is a position at which the first valve body  34  abuts against the first stopper  36 . At this time, the first valve body  34  collides with the first stopper  36 . In this way, the vibration is generated as depicted in (f) in  FIG. 2A . Once a predetermined time elapses from the start of the energization of the coil  33 , the pressurizing chamber  25  and the fuel suction passage  26  are brought into a state where the communication therebetween is blocked by the second valve body  37 . In this case, the predetermined time is a valve closing required time that corresponds to a time required for the second valve body  37  to be actually seated on the valve seat  40  and brought into the valve closed state from switching to the ON signal. When the plunger  22  moves in the second direction in this state, the fuel pressure in the pressurizing chamber  25  is increased. In this embodiment, a period in which the fuel pressure in the pressurizing chamber  25  is increased is a pressure increase stroke. High-pressure fuel, pressure of which has been increased to be high, is discharged to the fuel discharge passage  27  side. In this embodiment, a period in which the high-pressure fuel is discharged to the fuel discharge passage  27  side is a discharge stroke. Accordingly, a pump discharge amount is increased by advancing energization start timing of the coil  33 , and the pump discharge amount is reduced by delaying the timing. 
     In the pressure increase stroke, as depicted in (g) in  FIG. 2A , the fuel pressure in the pressurizing chamber  25  is increased, but the pressure increase appears after the timing t 12  at which movement of the first valve body  34  and the second valve body  37  to the valve closing positions are completed. In addition, a delay occurs to transmission of a pressure change of the pressurizing chamber  25  to the pressure accumulator chamber  14  due to presence of a fuel pipe. Thus, it takes time until the movement of the valve body appears as a change in the fuel pressure in the pressure accumulator chamber  14 . 
     When the energization of the coil  33  is stopped, as depicted in  FIG. 2D , the first valve body  34  separates from the first stopper  36 , abuts against the second valve body  37 , and is held in an abutment state for a predetermined time that corresponds to t 13  to t 14 . In the abutment state of both, the first valve body  34  and the second valve body  37  are held at a valve closing position CL 2  of the second valve body  37 . At this time, due to collision of the first valve body  34  with the second valve body  37 , the vibration is generated as depicted in (f) in  FIG. 2A . 
     Thereafter, when the plunger  22  moves from the top dead center toward the bottom dead center, the volume of the inside of the pressurizing chamber  25  is increased, and the pressure in the pressurizing chamber  25  is reduced. In this embodiment, a period in which the pressure in the pressurizing chamber  25  is reduced is a pressure reduction stroke. In this way, at t 14  onward, fuel pressure in the second valve chamber  32  is reduced. Thus, the first valve body  34  and the second valve body  37  are permitted to move and each move to the valve opening position. At timing t 15 , the second valve body  37  collides with the second stopper  39  when being pressed by the first valve body  34  in the axial direction, and the vibration is thereby generated as depicted in (f) in  FIG. 2A . 
     In the case where the first valve body  34  and the second valve body  37  move in conjunction with the energization of the coil  33 , the movement thereof appears as a change in a current that flows through the coil  33 . More specifically, due to a coil characteristic, as the first valve body  34  approaches the coil  33 , inductance of the coil  33  is increased, and the current flowing through the coil  33  is gradually reduced. Thus, in a state where a predetermined voltage is applied from the power supply  53  to the coil  33  by the duty control, as depicted in (c) in  FIG. 2A , the coil current is increased over time until the first valve body  34  starts moving. When the first valve body  34  starts moving from a valve opening position OP 1  (t 11 ), the coil current is gradually reduced as the first valve body  34  approaches the valve closing position CL 1  (an abutment position against the first stopper  36 ). When the first valve body  34  abuts against the first stopper  36  and thereby stops moving, the inductance is stabilized again, and the coil current is increased again. That is, in the case where the first valve body  34  moves in conjunction with the energization of the coil  33 , as depicted in (c) in  FIG. 2A , in an ON period of the drive signal, the coil current is switched from an increased tendency to a reduced tendency and is thereafter shifted from the reduced tendency to an increase. In this way, a bending point P 1  appears to the coil current in the ON period of the drive signal. 
     In the system, immediately after switching from ON to OFF of the drive signal, the voltage in a reverse direction is applied to the coil  33 . In this way, flyback for accelerating a reduction speed of the current that flows through the coil  33  is executed. Accordingly, as depicted in  FIG. 2A , when the drive signal is switched from ON to OFF, the coil current immediately becomes 0. Meanwhile, the voltage between the input/output terminals of the coil  33  is significantly changed in a reverse direction in conjunction with the switching of the drive signal from ON to OFF, is then shifted to a gradual increase, and is eventually converged to 0. In addition, in the system, an upper guard value is provided to the current that flows through the coil  33 . As the upper guard value, A 1  is set for a predetermined time from the energization start timing, and A 2  is set after a lapse of the predetermined time. In this embodiment, A 1  is larger than A 2 . 
     In the case where the first valve body  34  and the second valve body  37  move in conjunction with the energization of the coil  33 , the movement thereof appears as a change in a voltage that is applied to the coil  33 . In this embodiment, the voltage that is applied to the coil  33  is the voltage between the input/output terminals of the coil  33 . More specifically, in the ON period of the drive signal, as depicted in (d) in  FIG. 2A , in conjunction with a change in the inductance of the coil  33  that is caused by approaching of the first valve body  34  to the coil  33 , the voltage is changed by a predetermined value or more near the timing t 12 , and the change is apart from a voltage change by the duty control. 
     In addition, after the switching from ON to OFF of the drive signal, the voltage between the input/output terminals of the coil  33  is significantly changed in the reverse direction by the flyback, is then shifted to the increase, and is converged to 0. In a period in which the voltage is reduced toward zero, a change amount of the voltage per unit time is reduced, and a bending point P 2  appears. That is, the inductance of the coil  33  is reduced as the first valve body  34  separates from the coil  33  by the timing t 13  at which the first valve body  34  abuts against the second valve body  37 , and the inductance becomes constant when the movement of the first valve body  34  is stopped. The change in the inductance appears as the voltage change. 
     Furthermore, in a period after the voltage is converged to zero, the inductance of the coil  33  is changed by displacement of the first valve body  34  from the abutment position CL 2  that is associated with a reduction in the pressure of the second valve chamber  32 . In conjunction with this, the voltage between the input/output terminals of the coil  33  is changed. This change appears as a bending point P 3 . 
     By the way, when the first valve body  34  and the second valve body  37  show normal movement in conjunction with the switching of the drive command (the switching of the ON signal/OFF signal) of the valve opening/valve closing of the control valve  30 , the high-pressure pump  20  is actuated, that is, the fuel is discharged from the high-pressure pump  20 . On the other hand, when at least one of the first valve body  34  and the second valve body  37  does not show the normal movement, the high-pressure pump  20  is not actuated, that is, the fuel is not discharged from the high-pressure pump  20 . 
     For example, in the case where the first valve body  34  is not displaced from the valve opening position regardless of output of the drive signal for switching from the valve opening to the valve closing of the control valve  30 , a state in  FIG. 2B  is retained after the output of the drive signal. In such a case, as depicted in  FIG. 3 , even when the drive signal is switched between ON/OFF, behaviors that are observed when the first valve body  34  and the second valve body  37  show the normal movement, more specifically, a change in the coil current and the change in the voltage in the ON period of the drive signal as well as the change in the voltage after the switching of the drive signal from ON to OFF are not observed. 
     For this reason, in this embodiment, a movement detection section for detecting the movement of the first valve body  34  and the second valve body  37  with respect to the drive command of the valve opening/valve closing of the control valve  30  is provided, and based on a detection result of the movement detection section, an actuation determination of the high-pressure pump  20  is made. That is, the movement of the first valve body  34  and the movement of the second valve body  37  at a time that the drive signal of the control valve  30  is switched are directly or indirectly detected, and the actuation determination of the high-pressure pump  20  is made by determining whether the first valve body  34  and the second valve body  37  have normally moved by the drive signal. 
     In this embodiment, attention is focused on the movement of the first valve body  34  with respect to the drive command of the valve closing of the control valve  30  that appears in a synchronous manner with the movement of the first valve body  34  resulted from the change in the current flowing through the coil  33 . By indirectly detecting the movement of the first valve body  34  on the basis of the change in the current, whether to permit the actuation of the high-pressure pump  20  is determined. More specifically, as the change in the current with respect to the drive command, switching of the coil current between the increased tendency and the reduced tendency is detected. In this embodiment, generation of the reduced tendency of the coil current is detected in a period in which the drive command of the valve closing of the control valve  30  is outputted. When the generation of the reduced tendency is detected, such a determination that the high-pressure pump  20  is actuated is made. 
       FIG. 4  includes time charts of specific aspects of a pump actuation determination of this embodiment. In this embodiment, the generation of the reduced tendency of the coil current in the ON period of the drive signal is detected on the basis of a current speed that corresponds to a differential value of the current. That is, when the first valve body  34  moves to the valve closing position, as depicted in  FIG. 4( a ) , a reduced tendency of a coil current value is generated in the ON period of the drive signal, and the current speed shows a negative value. On the other hand, when the movement of the first valve body  34  is not observed in conjunction with the drive command of the valve closing of the control valve  30 , as depicted in  FIG. 4( b ) , the current speed does not show the negative value in the ON period of the drive signal. In this embodiment, the current speed and a determination value THa are compared by using this, and based on a comparison result, whether to permit the actuation of the high-pressure pump  20  is determined. In this embodiment, the determination value THa is smaller than zero. 
     Next, a process procedure of a pump actuation determination process of this embodiment will be described by using a flowchart in  FIG. 5 . The pump actuation determination process is executed by the microcomputer of the ECU  50  at predetermined intervals. 
     In  FIG. 5 , the microcomputer determines in  101  whether the energization start timing for energizing the coil  33  arrives. When the energization start timing arrives, the process proceeds to  102 , and the microcomputer outputs the valve closing command of the control valve  30 . In this way, the coil  33  is energized from the power supply  53 . In  103 , the microcomputer resets a valve closing determination flag FLAG_CL to 0. The valve closing determination flag FLAG_CL is a flag for indicating that the control valve  30  is in the valve closed state. When the microcomputer determines that the control valve  30  is in the valve closed state, the valve closing determination flag FLAG_CL is set to 1. 
     In  104 , the microcomputer obtains the coil current value that is detected by the current sensor  54 . In  105 , the microcomputer computes the current speed that corresponds to a speed of the output current. In  106 , the microcomputer determines whether the computed current speed falls below the determination value THa. When the microcomputer makes a positive determination, the process proceeds to  107 , and the valve closing determination flag FLAG_CL is set to 1. In this embodiment, the processes in  103 ,  106 , and  107  correspond to the movement detection section. 
     The microcomputer determines in  108  whether energization termination timing for terminating the energization of the coil  33  arrives. When the energization termination timing arrives, the process proceeds to  109 , and the microcomputer outputs the valve opening command of the control valve  30 . In this way, the energization of the coil  33  from the power supply  53  is stopped. In  110 , the microcomputer loads the valve closing determination flag FLAG_CL and determines whether FLAG_CL is 1. When FLAG_CL is 1, the process proceeds to  111 , and the microcomputer determines that the high-pressure pump  20  is actuated normally. When FLAG_CL is 0, the process proceeds to  112 , and the microcomputer determines that the high-pressure pump  20  is not actuated. In this embodiment, the processes in  110 ,  111 , and  112  correspond to an actuation determination section. Then, the microcomputer terminates this routine. 
     The fuel discharge amount of the high-pressure pump  20  is controlled by energization start timing TIME_ON of the control valve  30  and is specifically expressed by a following equation (1).
 
TIME_ON=TIME_ Q +TIME_ P +TIME_ F/B +TIME_CL  (1)
 
In the equation (1), TIME_Q represents a discharge time that corresponds to a time required to discharge the fuel in the pressurizing chamber  25 , TIME_P represents a pressure increase time that corresponds to a time required to increase the pressure of the fuel in the pressurizing chamber  25 , TIME_F/B represents a fuel pressure feedback correction amount, and TIME_CL represents the valve closing required time.
 
     The discharge time TIME_Q is computed on the basis of the requested discharge amount of the high-pressure pump  20 , and a longer time is set therefor as the requested discharge amount is increased. The pressure increase time TIME_P is computed on the basis of the target fuel pressure, and a longer time is set therefor as the target fuel pressure is increased. The fuel pressure feedback correction amount TIME_F/B is computed on the basis of a deviation of the actual fuel pressure in the pressure accumulator chamber  14  from the target fuel pressure, and a larger value is set therefor as the deviation is increased. 
     The valve closing required time TIME_CL is a time required for the second valve body  37  to move to the valve closing position from the energization start timing (valve closing command timing) and differs by individual units, a change over time, and the like, for example. When the valve closing required time differs, the fuel discharge amount of the high-pressure pump  20  is changed, and thus fuel pressure control may be influenced by the change. 
     For the above reason, in this embodiment, the microcomputer actually measures the valve closing required time and, based on the measured time, executes an energization start timing computation process for computing the energization start timing of the control valve  30 . In this embodiment, the microcomputer computes the valve closing required time by using the detection result of the movement detection section. In this way, computation accuracy of the valve closing required time is increased. 
     The energization start timing computation process of this embodiment will be described by using a time chart in  FIG. 6 . In  FIG. 6 , (a) indicates a relationship between the drive signal of the control valve  30  and time, (b) indicates a relationship between the current flowing through the coil  33  and time, (c) indicates relationships between displacements of the first valve body  34  and the second valve body  37  from the valve opening positions and time, (d) indicates a relationship between the fuel pressure in the pressurizing chamber  25  and time, (e) indicates a relationship between the valve closing determination flag FLAG_CL and time, and (f) indicates a relationship between a valve closing time counter COUNTER and time. Regarding the valve closing time counter COUNTER, in this embodiment, a timer is provided in the ECU  50  for measurement. 
     In  FIG. 6 , in conjunction with the switching of the drive signal of the control valve  30  to ON (the valve closing command) by the microcomputer at timing t 31 , the valve closing time counter COUNTER starts counting up. In parallel with this, the microcomputer determines whether to permit the actuation of the high-pressure pump  20  by the above pump actuation determination process. When the valve closing determination flag FLAG_CL is switched from 0 to 1, the microcomputer sets the valve closing time counter COUNTER to the valve closing required time TIME_CL at switching timing t 32  and stores this in the memory. During the actuation of the pump for pressure-feeding the fuel next time, the microcomputer uses the stored valve closing required time TIME_CL to compute the energization start timing. 
     In this embodiment, the actual valve closing required time is measured by the valve closing time counter COUNTER at every actuation of the pump, and the valve closing required time TIME_CL is updated on the basis of the measured value. However, update timing of the valve closing required time TIME_CL is not limited to the above. For example, the valve closing required time TIME_CL may be updated at every predetermined time or may be updated at every predetermined travel distance. 
     Next, a process procedure of the energization start timing computation process will be described by using a flowchart in  FIG. 7 . The energization start timing computation process is executed by the microcomputer of the ECU  50  at predetermined intervals. 
     In  FIG. 7 , in  201 , the microcomputer computes the requested discharge amount of the high-pressure pump  20  on the basis of the fuel injection amount of the injector  15  and also computes the discharge time TIME_Q on the basis of the computed requested discharge amount. In  202 , the microcomputer computes the target fuel pressure that is a target value of the fuel pressure in the pressure accumulator chamber  14  and also computes the pressure increase time TIME_P on the basis of the target fuel pressure. In  203 , based on the deviation of the actual fuel pressure detected by the fuel pressure sensor  52  from the target fuel pressure, the microcomputer computes the fuel pressure F/B correction amount TIME_F/B. In  204 , the microcomputer loads the valve closing required time TIME_CL from the memory. In  205 , the microcomputer computes the energization start timing TIME_ON on the basis of the above equation (1). In this embodiment, the process in  205  corresponds to a timing computation section. 
     In  206 , the microcomputer resets the valve closing time counter COUNTER to 0. In  207 , the microcomputer determines whether the energization start timing of the coil  33  arrives. When the microcomputer determines that the energization start timing arrives, the process proceeds to  208 , and the valve closing time counter COUNTER starts counting up. In  209 , the microcomputer determines whether the valve closing determination flag FLAG_CL is 1. 
     When the microcomputer determines that FLAG_CL is 0, the process proceeds to  211 , and it is determined whether the energization termination timing of the coil  33  arrives. When it is time before the energization termination timing arrives, the microcomputer repeats the processes in  208  to  211 . When the microcomputer determines that FLAG_CL is 1, the process proceeds to  210 , and a value of the valve closing time counter COUNTER is set to the valve closing required time TIME_CL. In this embodiment, the process in  210  corresponds to a time computation section. Thereafter, when the energization termination timing arrives, a positive determination is made in  211 , the process proceeds to  212 , and the microcomputer determines whether the valve closing determination flag FLAG_CL is 1. At this time, when the microcomputer determines that FLAG_CL is 0, this routine is terminated as is. When it is determined that FLAG_CL is 1, the process proceeds to  213 . The microcomputer stores the valve closing required time TIME_CL in the memory and updates the valve closing required time TIME_CL. Then, the microcomputer terminates this routine. 
     Next, a description will be made on an abnormality diagnosis section that corresponds to an abnormality diagnosis process of the high-pressure pump  20  by using the detection result of the movement detection section by using  FIG. 8 . The abnormality diagnosis process is executed by the microcomputer of the ECU  50  at predetermined intervals. 
     In  FIG. 8 , the microcomputer determines in  301  whether the energization termination timing of the coil  33  arrives. When it is the time before the energization termination timing arrives, the microcomputer terminates this routine as is. When the energization termination timing arrives, the microcomputer advances the process to  302 . The microcomputer determines in  302  whether the valve closing determination flag FLAG_CL is 1. When it is determined that FLAG_CL is 1, the process proceeds to  303 , and the microcomputer determines that the high-pressure pump  20  is normal. When it is determined that FLAG_CL is 0, the process proceeds to  304 , and the microcomputer determines that the high-pressure pump  20  is abnormal. In  305 , the microcomputer prohibits driving of the high-pressure pump  20 . In this embodiment, the processes in  301  to  305  correspond to the abnormality diagnosis section. 
     According to this embodiment that has been described in detail so far, following superior effects are obtained. 
     When the first valve body  34  and the second valve body  37  show the normal movement with respect to the drive command of the valve opening/valve closing of the control valve  30 , the high-pressure pump  20  is actuated, and the fuel is discharged from the high-pressure pump  20 . On the other hand, when the first valve body  34  and the second valve body  37  do not show the normal movement with respect to the drive command, the high-pressure pump  20  is not actuated, and the fuel is not discharged from the high-pressure pump  20 . Attention is focused on this point. In the above configuration, the movement of the valve body with respect to the drive command of the valve opening or the valve closing of the control valve  30  is monitored, and the actuation state of the high-pressure pump  20  is determined from the movement of the valve body. Thus, the actuation state of the high-pressure pump  20  can accurately be comprehended. 
     In this embodiment, the movement of the valve body with respect to the drive command of the valve opening or the valve closing of the control valve  30  is detected by detecting the change in the current that flows through the coil  33 . Accordingly, the current sensor  54  for detecting the current that flows through the coil  33  only needs to be provided, and the control device can be realized by a low-cost and relatively simple configuration. In addition, because the switching between the increased tendency and the reduced tendency of the current which is generated when the high-pressure pump  20  is actuated appears clearly, detection accuracy can also be improved. 
     In this embodiment, the valve closing required time TIME_CL that is required until the second valve body  37  is seated on the valve seat  40  from time at which the valve closing of the control valve  30  is commanded is actually measured on the basis of the change in the coil current, and the energization start timing of the control valve  30  is computed on the basis of the measured time. When the valve closing required time TIME_CL differs, the fuel discharge amount of the high-pressure pump  20  is changed, and the fuel pressure control may be influenced by the change. According to the above description, the energization start timing can be computed from the valve closing required time TIME_CL to which an individual difference, the change over time, and the like are reflected. In this way, controllability of the fuel pressure control can be increased. In addition, the actual valve closing timing is comprehended by detecting the movement of the valve body with respect to the drive command, and the valve closing required time TIME_CL is computed on the basis of this. Thus, the actual valve closing required time TIME_CL can accurately be computed. 
     Movement diagnosis of the high-pressure pump  20  is executed on the basis of the detection result of the movement of the valve body with respect to the drive command of the valve opening or the valve closing of the control valve  30 . Thus, the abnormality of the high-pressure pump  20  can accurately be comprehended, and an appropriate measure can be taken during the abnormality of the pump. 
     Second Embodiment 
     Next, a second embodiment will be described. In the above first embodiment, the movement of the valve body is detected by detecting the change in the coil current with respect to the drive command of the valve opening/valve closing of the control  30 . Meanwhile, in this embodiment, the movement of the valve body is detected by detecting a change in the voltage that is applied to the coil  33 . Hereinafter, a description will be centered on differences from the first embodiment. 
     A configuration of a fuel supply system of this embodiment is basically the same as that of the above first embodiment, but differs from the above first embodiment in a point that voltage sensors  55  to  57  are provided instead of the current sensor  54 . In detail, as depicted in  FIG. 9 , the fuel supply system includes: the first voltage sensor  55  that is disposed in a first path  61   a  for connecting a power supply  53  and a coil  33 ; the second voltage sensor  56  that is disposed in a second path  61   b  for connecting the coil  33  and a ground point; and the third voltage sensor  57  for detecting a voltage between an input terminal T 1  and an output terminal T 2  of the coil  33 . Although not depicted, a switch is provided in the middle of each of the first path  61   a  and the second path  61   b , and the energization/non-energization of the coil  33  can be switched. Detection signals of the voltage sensors  55  to  57  are each input to an ECU  50 . In this embodiment, the detection signal of the first voltage sensor  55  corresponds to a first voltage, the detection signal of the second voltage sensor  56  corresponds to a second voltage, and the detection signal of the third voltage sensor  57  corresponds to a third voltage. 
     Next, a pump actuation determination of this embodiment will be described by using a time chart in  FIG. 10 . In this embodiment, attention is focused on the movement of a first valve body  34  with respect to the switching of a drive command between the valve closing and the valve opening of a control valve  30  that appears as the change in the voltage applied to the coil  33 . By indirectly detecting the movement of the valve body on the basis of the change in the voltage, whether to permit the actuation of a high-pressure pump  20  is determined. 
     More specifically, as depicted in  FIG. 10 , in an ON period T 21  of the drive signal of the control valve  30 , a microcomputer monitors the voltage detected by the third voltage sensor  57  and determines whether a behavior V 1  in which a change amount of the voltage as a change width of the voltage becomes at least equal to a predetermined value appears separately from the voltage change by the duty control. In a period T 22  from the switching of the drive signal to OFF until a lapse of a predetermined time, the voltage detected by the third voltage sensor  57  is monitored, and, for example, bending points P 2 , P 3  of the voltage are detected as changes in the voltage that appear by the change in the inductance. In this embodiment, the bending points P 2 , P 3  respectively correspond to behaviors V 2 , V 3 . When all of the behaviors V 1  to V 3  are detected, the first valve body  34  shows the normal movement with respect to the drive command. Thus, such a determination that the high-pressure pump  20  is actuated is made. On the other hand, when at least one of the behaviors V 1  to V 3  is not detected, the first valve body  34  does not show the normal movement with respect to the drive command. Thus, such a determination that the high-pressure pump  20  is not actuated normally is made. 
     The behavior V 1  can also be detected by the first voltage sensor  55 , and the behaviors V 2  and V 3  can also be detected by the second voltage sensor  56 . Accordingly, such a configuration may be adopted that all of sensor detection values of the first voltage sensor  55  to the third voltage sensor  57  are used to determine that all of the behaviors V 1  to V 3  are detected. In this case, determination accuracy can be increased by confirming the behaviors V 1  to V 3  by the multiple sensors. 
     Next, a process procedure of a pump actuation determination process of this embodiment will be described by using a flowchart in  FIG. 11 . The pump actuation determination process is executed by the microcomputer of the ECU  50  at predetermined intervals. 
     In  FIG. 11 , the microcomputer determines in  401  whether the energization start timing of the coil  33  arrives. When the energization start timing arrives, the process proceeds to  402 , and the microcomputer commands the valve closing of the control valve  30  and energizes the coil  33 . In  403 , the microcomputer resets a valve closing determination flag FLAG_CL and a valve opening determination flag FLAG_OP to 0. The valve opening determination flag FLAG_OP is a flag for indicating that the control valve  30  is in the valve opened state. When the microcomputer determines that the control valve  30  is in the valve opened state, the valve opening determination flag FLAG_OP is set to 1. 
     In  404 , the microcomputer obtains the voltage value that is detected by the third voltage sensor  57 . In  405 , the microcomputer determines whether the change width of the voltage from which a pulse change is eliminated is at least equal to the predetermined value. The microcomputer computes the change width of the voltage as the change amount of the voltage from a time point at which a change of the voltage detected by the third voltage sensor  57  to an increased side or a reduced side is observed, for example. When the change width of the voltage is smaller than the predetermined value, the microcomputer does not execute the process in  406  and advances the process to  407 . When the change width of the voltage is at least equal to the predetermined value, the process proceeds to  406 , the microcomputer sets the valve closing determination flag FLAG_CL to 1, and the process proceeds to  407 . 
     The microcomputer determines in  407  whether the energization termination timing for terminating the energization of the coil  33  arrives. When the energization termination timing arrives, the process proceeds to  408 . The microcomputer outputs the valve opening command of the control valve  30  and stops the energization of the coil  33 . 
     In  409 , the microcomputer obtains the voltage that is detected by the third voltage sensor  57 . The microcomputer determines in  410  whether the bending point of the voltage is generated. When the microcomputer determines that the bending point of the voltage is not generated, the process in  411  is not executed, and the process proceeds to  412 . When the microcomputer determines that the bending point of the voltage is generated, the process proceeds to  411 , the valve opening determination flag FLAG_OP is set to 1, and the process proceeds to  412 . In this embodiment, a positive determination is made in  410  when both of the bending points P 2 , P 3  are detected. However, it may be configured that the positive determination is made in  410  when either one of the bending points P 2 , P 3  is detected. In this embodiment, the processes in  403 ,  405 ,  406 ,  410 , and  411  correspond to a movement detection section. 
     The microcomputer determines in  412  whether the predetermined time T 22  has elapsed since the energization termination timing of the coil  33 . When a negative determination is made, the microcomputer executes the processes in  409  to  412 . When the predetermined time T 22  has elapsed since the energization termination timing of the coil  33  and thus the positive determination is made in  412 , the process proceeds to  413 , and the microcomputer loads the valve closing determination flag FLAG_CL and the valve opening determination flag FLAG_OP and determines whether both of these flags FLAG_CL, FLAG_OP are 1. When it is determined that both of FLAG_CL and FLAG_OP are 1, the process proceeds to  414 , and the microcomputer determines that the high-pressure pump  20  is actuated normally. When at least either one of FLAG_CL and FLAG_OP is 0, the process proceeds to  415 , and the microcomputer determines that the high-pressure pump  20  is not actuated. In this embodiment, the processes in  413 ,  414 , and  415  correspond to an actuation determination section. Then, the microcomputer terminates this routine. 
     Next, a description will be made on an abnormality diagnosis process of the high-pressure pump  20  by using the detection result of the movement detection section by using  FIG. 12 . The abnormality diagnosis process is executed by the microcomputer of the ECU  50  at predetermined intervals. 
     In  FIG. 12 , the microcomputer determines in  501  whether the predetermined time T 22  has elapsed since the energization termination timing of the coil  33 . When it is time before a lapse of the predetermined time T 22  from the energization termination timing, the microcomputer terminates this routine as is. When it is time after the lapse of the predetermined time T 22  from the energization termination timing, the microcomputer advances the process to  502 . The microcomputer determines in  502  whether the valve closing determination flag FLAG_CL is 1. The microcomputer determines in  503  whether the valve opening determination flag FLAG_OP is 1. When a positive determination is made in  502  and a positive determination is made in  503 , the process proceeds to  504 , and the microcomputer determines that the high-pressure pump  20  is normal. 
     When a negative determination is made in  502  or a negative determination is made in  503 , the process proceeds to  505 , and the microcomputer determines that the high-pressure pump  20  is abnormal. In  506 , the microcomputer prohibits the driving of the high-pressure pump  20 . In this embodiment, the processes in  501  to  506  correspond to an abnormality diagnosis section. 
     In the second embodiment that has been described in detail so far, the movement of the valve body with respect to the drive command of the valve opening or the valve closing of the control valve  30  is detected by detecting the change in the voltage that is applied to the coil  33 . Thus, the voltage sensor (the third voltage sensor  57 ) only needs to be provided. Therefore, the control device can be realized by a low-cost and relatively simple configuration. 
     Third Embodiment 
     Next, a third embodiment will be described. In this embodiment, a displacement sensor for detecting displacement of a valve body of a control valve  30  is provided. By detecting the displacement of the valve body by the displacement sensor, the movement of the valve body with respect to a drive command of the valve opening or the valve closing is detected. In addition, an actuation determination of a high-pressure pump  20  is made on the basis of a detection result. Hereinafter, a description will be centered on differences from the first embodiment and the second embodiment. 
     A configuration of a fuel supply system of this embodiment is basically the same as that of the above first embodiment but, as depicted in  FIG. 13 , differs from the above first embodiment in a point that a displacement sensor  58  for detecting displacement of a first valve body  34  is provided instead of the current sensor  54 . That is, in this embodiment, the movement of the first valve body  34  with respect to the switching of the drive command between the valve closing and the valve opening of the control valve  30  is directly detected, and a determination of whether to permit the actuation of the high-pressure pump  20  is made on the basis of the detected displacement. The displacement sensor  58  is provided at a position to oppose an end of the first valve body  34  and can detect a separation distance with respect to the valve closing position (the abutment position against a first stopper  36 ). A detection signal of the displacement sensor  58  is input to an ECU  50 . 
     A pump actuation determination of this embodiment will be described by using a time chart in  FIG. 14 . In this embodiment, the movement of the first valve body  34  at a time that the high-pressure pump  20  is actuated normally is taken into consideration. In an ON period T 31  of the drive signal of the control valve  30 , displacement X of the first valve body  34  is monitored by the displacement sensor  58 , and it is determined whether the displacement X of the first valve body  34  falls within a predetermined range that includes a valve closing position CL 1 . In a period T 32  from the switching of the drive signal to OFF until a lapse of a predetermined time, the displacement X of the first valve body  34  is monitored by the displacement sensor  58 , and it is determined whether the displacement X of the first valve body  34  falls within a predetermined range that includes a valve opening position OP 1 . When both of a determination result of the period T 31  and a determination result of the period T 32  are positive, such a determination that the high-pressure pump  20  is actuated is made. On the other hand, when at least either one of the determination result of the period T 31  and the determination result of the period T 32  is negative, such a determination that the high-pressure pump  20  is not actuated is made. 
     Next, a process procedure of a pump actuation determination process of this embodiment will be described by using a flowchart in  FIG. 15 . The pump actuation determination process is executed by a microcomputer of the ECU  50  at predetermined intervals. In the description of  FIG. 15 , the description of the processes that are the same as those in above  FIG. 11  is not made. 
     In  FIG. 15 , in  601  to  603 , the microcomputer executes the same processes as  401  to  403  in above  FIG. 11 . In  604 , the microcomputer obtains the displacement X of the first valve body  34  that is detected by the displacement sensor  58 . The microcomputer determines in  605  whether the displacement X is within a valve closing determination region that is a region between the valve closing position CL 1  (the abutment position against the first stopper  36 ) and a position CL 3  that is separated from the first stopper  36  by a predetermined distance. When the microcomputer determines that the displacement X is not within the valve closing determination region, the process in  606  is not executed, and the process proceeds to  607 . When the microcomputer determines that the displacement X is within the valve closing determination region, the process proceeds to  606 , a valve closing determination flag FLAG_CL is set to 1, and the process proceeds to  607 . 
     In  607  and S 608 , the microcomputer executes the same processes as  407  and  408 . In  609 , the microcomputer obtains the displacement X of the first valve body  34  that is detected by the displacement sensor  58 . The microcomputer determines in  610  whether the displacement X is within a valve opening determination region that is a region between the valve opening position OP 1  (a maximum displaceable position in a direction to separate from the first stopper  36 ) and a position OP 2  that is displaced from the valve opening position OP 1  to the first stopper  36  side by a predetermined distance. In this embodiment, the valve opening position OP 1  is the maximum displaceable position in the direction to separate from the first stopper  36 . When the microcomputer determines that the displacement X is not within the valve opening determination region, the process in  611  is not executed, and the process proceeds to  612 . On the other hand, when the microcomputer determines that the displacement X is within the valve opening determination region, a valve opening determination flag FLAG_OP is set to 1 in  611 , and the process proceeds to  612 . In this embodiment, the processes in  603 ,  605 ,  606 ,  610 , and  611  correspond to a movement detection section. 
     The microcomputer determines in  612  whether the predetermined time T 32  has elapsed since the energization termination timing of a coil  33 . When it is determined that it is time before a lapse of the predetermined time T 32 , the processes in  609  to  612  are executed. When the predetermined time T 32  has elapsed since the energization termination timing of the coil  33  and thus the microcomputer makes a positive determination in  612 , the process proceeds to  613 , the same processes as  413  to  415  are executed in  613  to  615 , and this routine is terminated. In this embodiment, the processes in  613 ,  614 , and  615  correspond to an actuation determination section. 
     In the third embodiment that has been described in detail so far, the movement of the valve body with respect to the drive command of the valve opening or the valve closing of the control valve  30  is detected by detecting the displacement of the first valve body  34 . Thus, the movement of the first valve body  34  with respect to the drive command can directly be monitored, and detection accuracy is high. 
     Fourth Embodiment 
     Next, a fourth embodiment will be described. In this embodiment, a vibration sensor for detecting vibrations that are generated when a first valve body  34  and a second valve body  37  of a control valve  30  respectively collide with a first stopper  36  and a second stopper  39  is provided. By detecting the vibrations during collision of the first valve body  34  with the first stopper  36  and collision of the second valve body  37  with the second stopper  39  by the vibration sensor, the movement of the valve body with respect to a drive command of the control valve  30  is detected. In addition, an actuation determination of a high-pressure pump  20  is made on the basis of a detection result. Hereinafter, a description will be centered on differences from the first embodiment to the third embodiment. 
     A configuration of a fuel supply system of this embodiment is basically the same as the above first embodiment but, as depicted in  FIG. 16 , differs from the above first embodiment in a point that a vibration sensor  59  is attached to a main body of the control valve  30  instead of the current sensor  54 . That is, in this embodiment, the movement of the first valve body  34  and the movement of the second valve body  37  with respect to the switching of the drive command between the valve closing and the valve opening of the control valve  30  are indirectly detected by the vibration sensor  59 , and a determination of whether to permit the actuation of the high-pressure pump  20  is made on the basis of a detection result. A detection signal of the vibration sensor  59  is input to an ECU  50 . 
     A pump actuation determination of this embodiment will be described by using a time chart in  FIG. 17 . In this embodiment, a standard deviation σ of a detection value (amplitude) of the vibration sensor  59  is computed, and an actuation determination of the high-pressure pump  20  is made by a comparison between the computed standard deviation σ and a determination value. That is, when the high-pressure pump  20  can be actuated, the first valve body  34  and the second valve body  37  are displaced in conjunction with the drive command of the control valve  30 . Accordingly, vibrations are generated at timing t 61  at which the first valve body  34  collides with the first stopper  36  in conjunction with the valve closing command, at timing t 62  at which the first valve body  34  collides with the second valve body  37  in conjunction with the valve opening command, and timing t 63  at which the second valve body  37  collides with the second stopper  39 , and the standard deviation σ of the amplitude becomes larger than the determination value. On the other hand, the vibration is not generated when the high-pressure pump  20  is not actuated. Accordingly, the standard deviation σ of the amplitude becomes substantially 0. By using this event, the actuation determination of the high-pressure pump  20  is made. 
     Next, a process procedure of a pump actuation determination process of this embodiment will be described by using a flowchart in  FIG. 18 . The pump actuation determination process is executed by a microcomputer of the ECU  50  at predetermined intervals. In the description of  FIG. 18 , the description of the processes that are the same as those in above  FIG. 11  is not made. 
     In  FIG. 18 , in  701  to  703 , the microcomputer executes the same processes as  401  to  403  in above  FIG. 11 . In  704 , the microcomputer computes the standard deviation σ of the amplitude of the vibration that is detected by the vibration sensor  59 . The microcomputer determines in  705  whether the standard deviation σ exceeds the determination value. When the microcomputer determines that the standard deviation σ does not exceed the determination value, the process in  706  is not executed, and the process proceeds to  707 . When the microcomputer determines that the standard deviation σ exceeds the determination value, the process proceeds to  706 , a valve closing determination flag FLAG_CL is set to 1, and the process proceeds to  707 . 
     In  707  and  708 , the microcomputer executes the same processes as  407  to  408 . In  709 , the microcomputer computes the standard deviation σ of the amplitude that is detected by the vibration sensor  59 . The microcomputer determines in  710  whether the standard deviation σ exceeds the determination value. When the microcomputer determines that the standard deviation σ does not exceed the determination value, the process in  711  is not executed, and the process proceeds to  712 . When the microcomputer determines that the standard deviation σ exceeds the determination value, the process proceeds to  711 , a valve opening determination flag FLAG_OP is set to 1, and the process proceeds to  712 . In this embodiment, the processes in  703 ,  705 ,  706 ,  710 , and  711  correspond to a movement detection section. 
     The microcomputer determines in  712  whether a predetermined time has elapsed since the energization termination timing of a coil  33 . When the microcomputer determines it is time before a lapse of the predetermined time, the processes in  709  to  712  are executed. As the predetermined time, a time from the energization termination timing to timing between t 62  and t 63  in  FIG. 17  may be set. In this case, the movement of the valve body can be detected on the basis of the vibration at the abutment position. In addition, as the predetermined time, a time from the energization termination timing to timing after t 63  may be set. In this case, the movement of the valve body can be detected on the basis of the vibration at the abutment position and the vibration during the collision of the second valve body  37  with the second stopper  39 . 
     When the predetermined time has elapsed since the energization termination timing of the coil  33  and thus the microcomputer makes a positive determination in  712 , the process proceeds to  713 , the same processes as  413  to  415  are executed in  713  to  715 , and this routine is terminated. In this embodiment, the processes in  713 ,  714 , and  715  correspond to an actuation determination section. 
     In the fourth embodiment that has been described in detail so far, the movement of the valve body with respect to the drive command of the valve opening or the valve closing of the control valve  30  is detected by detecting the vibrations that are generated when the first valve body  34  and the second valve body  37  are displaced. Sound and the vibrations during the collisions of the valve bodies with the first stopper  36  and the second stopper  39  are relatively large, and detection accuracy is high. 
     Other Embodiments 
     The present disclosure is not limited to the described contents of the above embodiments but may be implemented as follows, for example. 
     (a) In the above first embodiment, the change in the current with respect to the drive command of the control valve  30  is detected on the basis of the current speed. However, the configuration for detecting the change in the current is not limited thereto. For example, in the ON period of the drive signal, a maximum value of the measured value of the current is held, and a change amount of a measurement value of this time with respect to the held value is computed. Then, the change in the current is detected on the basis of the computed change amount. 
     More specifically, when the high-pressure pump  20  is actuated, the reduced tendency of the coil current is generated in the ON period of the drive signal. Accordingly, as depicted in  FIG. 19( a ) , the change amount of the measurement value of this time with respect to the held value is gradually increased in a period in which the reduced tendency of the coil current is generated. On the other hand, when the high-pressure pump  20  is not actuated, the reduced tendency of the coil current is not generated in the ON period of the drive signal. Thus, the change amount of the measurement value of this time with respect to the held value is substantially zero. In consideration of this point, in this embodiment, the change amount of the measurement value of this time with respect to the held value is compared to the determination value. When the change amount is detected to be larger than the determination value, the valve closing determination flag FLAG_CL is set to 1. 
     (b) In the above first embodiment, the actuation determination of the high-pressure pump  20  is made by detecting the generation of the reduced tendency of the coil current in the ON period of the drive signal. However, in view of a fact that the switching between the increased tendency and the reduced tendency of the current clearly appears as the bending point P 1 , a configuration for making the actuation determination of the high-pressure pump  20  by detecting shifting of the coil current from the reduced tendency to the increase in the period may be adopted. More specifically, the presence or the absence of the bending point P 1  of the current is detected on the basis of the current value that is monitored in the ON period of the drive signal, for example. When the bending point is present, it is determined that the high-pressure pump  20  is in the actuated state. In this configuration, not only the reduced tendency of the coil current, but further shifting to the increased tendency is also detected. Thus, determination accuracy of the movement of the valve body can be increased, and furthermore, accuracy of the actuation determination of the high-pressure pump  20  can be increased. 
     (c) As a configuration for detecting the shifting of the coil current from the reduced tendency to the increase in the ON period of the drive signal, a configuration for detecting that both conditions including that the current speed falls below the determination value THa (&lt;0) and that the current speed exceeds a determination value THb (&lt;0) are satisfied may be adopted. At this time, the determination value THa and the determination value THb may be the same or differ from each other. 
     (d) As the configuration for detecting the shifting of the coil current from the reduced tendency to the increase in the ON period of the drive signal, in  FIG. 19 , a configuration for detecting on the basis of a comparison result between the change amount of the measurement value of this time with respect to the held value as the maximum value and a determination value may be adopted. More specifically, a configuration for detecting that both conditions including that the change amount of the measurement value of this time with respect to the held value exceeds the determination value and that the change amount falls below the determination value are satisfied may be adopted. 
     (e) In the above second embodiment, the movement of the valve body is detected by using the detection value of the third voltage sensor  57 . However, a configuration for detecting the movement of the valve body not by using the detection value of the third voltage sensor  57  but by using at least either one of the detection value of the first voltage sensor  55  and the detection value of the second voltage sensor  56  may be adopted. 
     (f) In the above second embodiment, the presence or the absence of the behavior V 1  is detected in the ON period T 21  of the drive signal, and the presence or the absence of the behaviors V 2 , V 3  is detected in the period T 22  from the switching from ON to OFF of the drive signal to the lapse of the predetermined time. However, a configuration for making the actuation determination of the high-pressure pump  20  on the basis of the detection result in either one of the period T 21  and the period T 22  may be adopted. 
     (g) In the above third embodiment, the displacement of the first valve body  34  is detected by the displacement sensor  58 . However, the sensor for detecting the displacement of the valve body is not limited thereto. For example, a contact point sensor is attached to the first stopper  36 , an ON signal is outputted when the first valve body  34  abuts against the first stopper  36 , and an OFF signal is outputted when the first valve body  34  separates from the first stopper  36 . A configuration for detecting the displacement of the valve body by the ON/OFF signal of the contact point sensor may be adopted. Alternatively, a conduction sensor is attached to the valve opening position of the first valve body  34 , an ON signal is outputted when the first valve body  34  is held at the valve opening position, and an OFF signal is outputted when the first valve body  34  is displaced from the valve opening position. A configuration for detecting the displacement of the valve body by the ON/OFF signal of the conduction sensor may be adopted. 
     (h) In the above third embodiment, the sensor for detecting the displacement of the first valve body  34  is provided, and the actuation determination of the high-pressure pump  20  is made on the basis of the displacement detected by the sensor. However, a configuration for providing a sensor for detecting the displacement of the second valve body  37  and making the actuation determination of the high-pressure pump  20  on the basis of the displacement detected by the sensor may be adopted. 
     (i) In the above third embodiment, a configuration for detecting the displacement of the first valve body  34  to the abutment position after the switching from ON to OFF of the drive signal, so as to detect the movement of the valve body with respect to the drive signal may be adopted. More specifically, in the period T 32  in  FIG. 14 , it is determined whether the displacement X of the first valve body  34  detected by the displacement sensor  58  enters a predetermined region including the abutment position. When it is determined that the displacement X is within the predetermined region, or under a condition that it is determined that the displacement X is within the predetermined region, the valve opening determination flag FLAG_OP is set to 1. 
     In  607  and  608 , the same processes as  407  and  408  are executed. In  609 , the displacement X of the first valve body  34  that is detected by the displacement sensor  58  is obtained, and it is determined in  610  whether the displacement X is within the region (the valve opening determination region) between the valve opening position OP 1  (the maximum displaceable position in the direction to separate from the first stopper  36 ) and the position OP 2  that is displaced from the valve opening position OP 1  to the first stopper  36  side by the predetermined distance. When it is determined that the displacement X is not within the valve opening determination region, the process in  611  is not executed, and the process proceeds to  612 . On the other hand, when it is determined that the displacement X is within the valve opening determination region, the valve opening determination flag FLAG_OP is set to 1 in  611 , and the process proceeds to  612 . 
     (j) In the above fourth embodiment, the movement of the valve body with respect to the drive command is detected on the basis of the standard deviation σ of the amplitude of the vibration that is detected by the vibration sensor  59 . However, a configuration for detecting the movement of the valve body with respect to the drive command on the basis of a comparison result between the amplitude and a determination value may be adopted. At this time, when the amplitude (&gt;0) is larger than the determination value, the valve closing determination flag FLAG_CL or the valve opening determination flag FLAG_OP is switched to 1. Alternatively, a configuration for computing an integral value of the amplitude per vibration and detecting the movement of the valve body with respect to the drive command on the basis of the computed integral value may be adopted. At this time, the integral value and the determination value are compared. When the integral value is larger than the determination value, the valve closing determination flag FLAG_CL or the valve opening determination flag FLAG_OP is switched to 1. 
     (k) In the above embodiments, the reduction speed of the current that flows through the coil  33  is accelerated by applying the voltage in the reverse direction to the coil  33  immediately after the switching from ON to OFF of the drive signal of the control valve  30 . However, when a circuit (a flyback circuit) for executing such a process is not provided, the actuation determination of the pump  20  can be made on the basis of the change in the coil current after the switching from ON to OFF of the drive signal. More specifically, in the case where the flyback circuit is not provided, a projected bending point appears to the coil current when the first valve body  34  abuts against the second valve body  37  and when the second valve body  37  abuts against the second stopper  39 . Thus, a configuration for making the actuation determination of the high-pressure pump  20  by detecting presence or absence of these bending points may be adopted. 
     (l) In the above embodiments, the movement of the valve body with respect to the drive command is detected by detecting any one of the change in the current flowing through the coil  33 , the change in the voltage applied to the coil  33 , the displacement amount of the valve body, and the vibration of the control valve  30 . However, a configuration for detecting the movement of the valve body with respect to the drive command by detecting two or more of these may be adopted. For example, in the case where it is detected that a speed (a differential value) of the current value detected by the current sensor  54  falls below the determination value THa and that the change width of the voltage value detected by the voltage sensor  57  is at least equal to a predetermined value in the ON period of the drive signal of the control valve  30 , the valve closing determination flag FLAG_CL is set to 1. On the other hand, in the case where either that the speed (the differential value) of the current value detected by the current sensor  54  falls below the determination value THa or that the change width of the voltage value detected by the voltage sensor  57  is at least equal to a predetermined value is not detected, the valve closing determination flag FLAG_CL remains 0. 
     (m) In the above second embodiment, the above third embodiment, and the above fourth embodiment, similar to the above first embodiment, the energization start timing computation process may be executed by using the valve closing determination flag FLAG_CL that is set in the pump actuation determination process. In addition, in the above third embodiment and the above fourth embodiment, similar to the above first embodiment or the above second embodiment, the abnormality diagnosis process may be executed by using the valve closing determination flag FLAG_CL and the valve opening determination flag FLAG_OP that are set in the pump actuation determination process. 
     (n) In the above embodiments, a case where the present disclosure is applied to the fuel supply system that includes the control valve  30  having the two valve bodies (the first valve body  34  and the second valve body  37 ) has been described. However, the present disclosure may be applied to a fuel supply system that includes a control valve having only one valve body. More specifically, the present disclosure is applied to a system having a valve body configured that the control valve is disposed as the valve body in a fuel suction passage that communicates with a pressurizing chamber, can be displaced in an axial direction by switching between energization and non-energization of the coil  33 , and supplies/blocks fuel to/from the pressurizing chamber in conjunction with displacement. Also in this configuration, the movement of the valve body with respect to the drive command can be detected on the basis of at least one of the change in the current flowing through the coil  33 , the change in the voltage applied to the coil  33 , the displacement amount of the valve body, and the vibration of the control valve  30 . Thus, the actuation determination of the high-pressure pump  20  can be made on the basis of the movement. 
     (o) In the above embodiments, the gasoline engine is used as the internal combustion engine. However, a configuration for using a diesel engine may be adopted. That is, the present disclosure may be embodied as a control device for a common rail type fuel supply system of the diesel engine. 
     While the present disclosure has been described with reference to embodiments thereof, it is to be understood that the disclosure is not limited to the embodiments and constructions. The present disclosure is intended to cover various modification and equivalent arrangements. In addition, while the various combinations and configurations, other combinations and configurations, including more, less or only a single element, are also within the spirit and scope of the present disclosure.