JP2019007390A - Solenoid metering valve - Google Patents

Abstract

To provide an electromagnetic regulation valve suppressed in increase of current volume.SOLUTION: An electromagnetic regulation valve has a suction valve, a main spring applying downward energization force to the suction valve, an armature, a coil applying upward electromagnetic force to the armature, a connection portion for connecting the suction valve and the armature, and a fuel storage chamber partially defined by the connection portion. When a volume of a plunger chamber is reduced in a sealed state in which the fuel is sealed in the fuel storage chamber, downward drag of fuel in the fuel storage chamber is applied to the suction valve through the connection portion. In a case when electromagnetic force is not applied to the armature, a tip of the suction valve and a wall surface of the plunger chamber are separated, and the plunger chamber and a fuel supply passage are communicated by the downward drag and energization force, and in a case when electromagnetic force is applied to the armature, the sealed state of the fuel storage chamber is released by upward movement of the armature, and the tip of the suction valve and the wall surface of the plunger chamber are brought into contact with each other so that the plunger chamber and the fuel supply passage are not communicated.SELECTED DRAWING: Figure 4

Description

  The disclosure described in the present specification relates to an electromagnetic metering valve that controls communication between a plunger chamber and a fuel supply path.

  As shown in Patent Document 1, a high-pressure fuel pump having an intake valve, a plunger, a spring, an engagement member, and a solenoid is known. The intake valve restricts the flow of fuel from the fuel intake passage to the pressurizing chamber. A plunger is slidably held in the pressurizing chamber. The plunger reciprocates with a cam to change the volume in the pressure chamber.

  A biasing force of a spring is applied to the engaging member. When the solenoid is not energized, the engaging member is engaged with the intake valve by the biasing force of the spring. As a result, a biasing force of the spring is applied to the intake valve. By this urging force, the intake valve is in an open state in which the fuel intake passage and the pressurizing chamber communicate with each other.

  When the solenoid is energized, an electromagnetic force greater than the urging force is generated in the engaging member. The electromagnetic force is opposite to the biasing force. For this reason, the engaging member and the suction valve are separated. No biasing force is applied to the intake valve. In this case, the intake valve is an automatic valve that opens and closes in synchronization with the reciprocating motion of the plunger. In the compression process in which the volume of the pressurizing chamber is reduced by the plunger, the suction valve is closed by the force during the compression process. The solenoid is energized during this compression process.

Japanese Patent No. 5978249

  As described above, in the high-pressure fuel pump disclosed in Patent Document 1, the intake valve is kept open by the biasing force of the spring. In order to realize this, it is necessary to apply an urging force larger than the force in the compression process to the engaging member. In order to separate the engagement member and the suction valve against this biasing force, an electromagnetic force greater than the biasing force must be generated in the engagement member. Therefore, there is a problem that a large amount of current flows through the solenoid.

  Therefore, the disclosure described in the present specification aims to provide an electromagnetic metering valve in which an increase in current amount is suppressed.

One of the disclosures controls communication between a plunger chamber (14) whose volume is changed by a plunger (20) sliding in a cylinder (10) and a fuel supply passage (12) for supplying fuel to the plunger chamber. An electromagnetic metering valve,
A suction valve (42) provided with a tip (44) in the plunger chamber;
A main spring (32) for applying an urging force toward the plunger chamber in the sliding direction of the plunger to the suction valve;
An armature (43) connected to an end (45b) opposite the tip of the suction valve;
A coil (33) for applying an electromagnetic force in a direction away from the plunger chamber in a sliding direction to the armature by passing a magnetic field through the armature;
A connecting portion (34) for connecting the end of the intake valve and the tip (51) of the armature;
A fuel storage chamber (56) partially partitioned by the connecting portion,
When the volume of the plunger chamber decreases due to the sliding of the plunger in the sealed state in which the fuel is sealed in the fuel storage chamber, the drag of the fuel in the fuel storage chamber toward the plunger chamber in the sliding direction is caused through the connecting portion to the intake valve. Granted to
When an electromagnetic force is not applied to the armature by the coil, the tip of the suction valve and the wall surface (11b) partitioning the plunger chamber are separated in the sliding direction by the drag force and the biasing force toward the plunger chamber in the sliding direction. The plunger chamber and fuel supply passage
When electromagnetic force is applied to the armature by the coil, the armature moves in a direction away from the plunger chamber in the sliding direction, the sealed state of the fuel storage chamber is released, and the tip of the intake valve and the wall surface defining the plunger chamber Comes into contact with each other, and the plunger chamber and the fuel supply path are disconnected.

  According to this, the separation in the sliding direction between the tip (44) of the suction valve (42) and the wall surface (11b) of the plunger chamber (14) causes the drag of the fuel in the fuel storage chamber (56) and the main spring ( 32). For this reason, compared with the structure which hold | maintains the space | interval of the front-end | tip (44) of a suction valve (42), and the wall surface (11b) of a plunger chamber (14) only with the urging | biasing force of a main spring (32). The urging force of can be set weak.

  Further, when the armature (43) is moved away from the plunger chamber (14), the sealed state of the fuel storage chamber (56) is released. Therefore, the force applied to the suction valve (42) toward the plunger chamber (14) is only the urging force of the main spring (32). Thus, in order to move the suction valve (42) and bring the tip (44) of the suction valve (42) into contact with the wall surface (11b) of the plunger chamber (14), the electromagnetic force applied to the armature (43) is main. It only needs to be stronger than the biasing force of the spring (32).

  As described above, the biasing force of the main spring (32) can be set weak. Therefore, the electromagnetic force applied to the armature (43) can also be set weak. Thereby, the amount of current flowing through the coil (33) can be reduced. As a result, an increase in the amount of current of the coil (33) is suppressed.

  In addition, the code | symbol with the parenthesis is attached | subjected to the element as described in the claim as described in a claim, and each means for solving a subject. The reference numerals in parentheses are for simply indicating the correspondence with each component described in the embodiment, and do not necessarily indicate the element itself described in the embodiment. The description of the reference numerals with parentheses does not unnecessarily narrow the scope of the claims.

It is the schematic which shows a fuel supply system. It is a fragmentary sectional view for demonstrating a high pressure fuel pump. It is sectional drawing which shows the electromagnetic metering valve of a closed state. It is an expanded sectional view of the area | region A enclosed with a broken line in FIG. It is a timing chart for demonstrating operation | movement of a high pressure fuel pump. It is sectional drawing for demonstrating the high pressure fuel pump concerning 2nd Embodiment. FIG. 6 is an enlarged cross-sectional view of a region B surrounded by a broken line in FIG. 5. It is an expanded sectional view which shows the modification of an electromagnetic metering valve. It is a chart which shows the modification of an electromagnetic metering valve. It is a chart which shows the modification of an electromagnetic metering valve.

  Hereinafter, embodiments will be described with reference to the drawings.

(First embodiment)
An electromagnetic metering valve according to the present embodiment, a high-pressure fuel pump including the electromagnetic metering valve, and a fuel supply system including the high-pressure fuel pump will be described with reference to FIGS.

(Fuel supply system)
The fuel supply system 200 injects high-pressure fuel into the combustion chamber of the internal combustion engine. As shown in FIG. 1, the fuel supply system 200 includes a fuel tank 110, a low pressure fuel pump 120, a high pressure fuel pump 100, and a control device 130. In addition, the fuel supply system 200 includes a common rail and a fuel injection device (not shown).

  The fuel tank 110 stores fuel. A low pressure fuel pump 120 is provided in the fuel tank 110.

  The low-pressure fuel pump 120 is driven in conjunction with the output shaft of the internal combustion engine. The low pressure fuel pump 120 pumps the fuel in the fuel tank 110. The low pressure fuel pump 120 is connected to the high pressure fuel pump 100 via the first fuel pipe 141. The fuel pumped out by the low-pressure fuel pump 120 is supplied to the high-pressure fuel pump 100 via the first fuel pipe 141.

  The first fuel pipe 141 is connected to the fuel tank 110 via the second fuel pipe 142. The second fuel pipe 142 is provided with a return valve 142a. When the pressure in the first fuel pipe 141 increases, the return valve is opened. As a result, the fuel in the first fuel pipe 141 is returned to the fuel tank 110 via the second fuel pipe 142. The pressure in the first fuel pipe 141 decreases, and the return valve is closed. As described above, the return valve and the second fuel pipe 142 suppress an increase in the pressure of the first fuel pipe 141.

  The high pressure fuel pump 100 is driven in conjunction with the camshaft 300. The high pressure fuel pump 100 compresses the fuel supplied from the low pressure fuel pump 120 to a high pressure. The high-pressure fuel pump 100 is connected to the common rail via the third fuel pipe 143. The high pressure fuel (high pressure fuel) compressed by the high pressure fuel pump 100 is supplied to the common rail via the third fuel pipe 143.

  The high pressure fuel pump 100 is connected to the fuel tank 110 via a fourth fuel pipe 144. Excess fuel that has not been supplied from the high-pressure fuel pump 100 to the common rail is returned to the fuel tank 110 via the fourth fuel pipe 144.

  The common rail stores high-pressure fuel supplied from a high-pressure fuel pump inside. The common rail keeps the pressure of the stored internal fuel constant. The common rail is connected to each of the plurality of fuel injection devices. The common rail distributes high-pressure fuel to each of the plurality of fuel injection devices. The fuel injection device injects high-pressure fuel supplied from the common rail into the combustion chamber of the internal combustion engine.

  The control device 130 controls the low-pressure fuel pump 120, the high-pressure fuel pump 100, the common rail, and the fuel injection device. The control device 130 controls the volume of fuel supplied from the low pressure fuel pump 120 to the high pressure fuel pump 100. The control device 130 controls the capacity of the high-pressure fuel that the high-pressure fuel pump 100 supplies to the common rail. The control device 130 controls the pressure value of the pressure held by the common rail. The control device 130 controls the timing at which the fuel injection device injects fuel and the time at which the fuel is injected.

  The control device 130 receives signals from various sensors. These various sensors are, for example, a rotation speed sensor that detects the rotation speed of the internal combustion engine, and an airflow sensor that detects the intake air intake amount. They are a supercharging pressure sensor that detects the supercharging pressure, a water temperature sensor that detects the cooling water temperature, and an oil temperature sensor that detects the oil temperature of the lubricating oil. More specifically, a fuel pressure sensor and a temperature sensor for detecting the pressure and temperature of the fuel in the fuel injection device.

  The control device 130 calculates various target values suitable for the driving situation of the vehicle based on signals from these various sensors. That is, the control device 130 calculates a target value of the volume of fuel supplied from the low pressure fuel pump 120 to the high pressure fuel pump 100. The control device 130 calculates a target value of the capacity of the high-pressure fuel supplied from the high-pressure fuel pump 100 to the common rail. The control device 130 calculates a target value of the pressure held by the common rail. The control device 130 calculates target values for the fuel injection timing and fuel injection time of the fuel injection device. Based on these calculated target values, the control device 130 controls the low pressure fuel pump 120, the high pressure fuel pump 100, the common rail, and the fuel injection device.

(High pressure fuel pump)
Next, the high pressure fuel pump 100 will be described. As shown in FIG. 1, the high-pressure fuel pump 100 includes a cylinder 10, a plunger 20, an electromagnetic metering valve 30, and a check valve 90. A pump chamber 11 in which a plunger 20 is provided is formed in the cylinder 10. As shown in FIG. 2, the cylinder 10 is formed with a fuel supply path 12 through which fuel flows. The pump chamber 11 and the fuel supply path 12 communicate with each other.

  A discharge hole 13 for discharging fuel from the pump chamber 11 is formed in the cylinder 10. The discharge hole 13 communicates with the third fuel pipe 143. Accordingly, the fuel in the pump chamber 11 can be supplied to the third fuel pipe 143 through the discharge hole 13.

  The pump chamber 11 has two openings. A plunger 20 is provided at one open end of the pump chamber 11. The plunger 20 has a column shape. In the circumferential direction around the axial direction of the plunger 20, the side wall surface of the plunger 20 and the inner wall surface constituting the pump chamber 11 are in contact over the entire circumference. As a result, the plunger 20 is slidable in its own axial direction.

  The plunger chamber 14 is defined by the inner wall surface on the other opening end side of the pump chamber 11 and the upper end surface of the plunger 20 facing the inner wall surface in the axial direction. The plunger chamber 14 has one open end. This one open end corresponds to the other open end of the pump chamber 11. As will be described later, the valve body 31 of the electromagnetic metering valve 30 is provided at the open end of the plunger chamber 14.

  The plunger 20 is interlocked with the camshaft 300 of the internal combustion engine. In response to the rotation of the camshaft 300, the plunger 20 slides in the pump chamber 11 between the two open ends. As a result, the volume of the plunger chamber 14 varies. In other words, the volume of fuel in the plunger chamber 14 varies. The direction (axial direction) in which the plunger 20 slides corresponds to the sliding direction.

  In the following, in the axial direction, one opening end side of the pump chamber 11 is indicated as a lower side. In other words, the camshaft 300 side is shown as the lower side. The other opening end side of the pump chamber 11, that is, the opening end side of the plunger chamber 14 is shown as the upper side. In other words, the stator core 38 side of the electromagnetic metering valve 30 to be described later is indicated as the upper side.

(Outline of electromagnetic metering valve)
As shown in FIG. 2, the electromagnetic metering valve 30 includes a valve body 31, a main spring 32, and a solenoid coil 33. The valve body 31 is inserted into the open end of the plunger chamber 14. Thereby, the tip of the valve body 31 is provided in the plunger chamber 14. The end opposite to the tip of the valve body 31 is provided outside the plunger chamber 14.

  The valve body 31 is biased toward the inside of the plunger chamber 14 by the biasing force of the main spring 32. Thereby, the front-end | tip of the valve body 31 and the inner wall face which comprises the plunger chamber 14 are spaced apart in the axial direction. The plunger chamber 14 and the fuel supply path 12 communicate with each other. The fuel can flow between the plunger chamber 14 and the fuel supply path 12.

  However, when a drive current is passed through the solenoid coil 33 by the control device 130, a magnetic field (magnetic circuit) passing through the end of the valve body 31 is formed by the drive current. With this magnetic circuit, the valve element 31 moves to the outside of the plunger chamber 14. At this time, the tip of the valve body 31 and the inner wall surface constituting the plunger chamber 14 come into contact with each other. As a result, the plunger chamber 14 and the fuel supply path 12 are disconnected. The flow of fuel between the plunger chamber 14 and the fuel supply path 12 is blocked.

  As shown in FIG. 2, the check valve 90 includes a closing valve 91 and a closing spring 92. The diameter of the discharge hole 13 expands locally as the distance from the plunger chamber 14 increases. A closing valve 91 and a closing spring 92 are provided in the small chamber of the discharge hole 13 formed by the expansion of the diameter.

  The small chamber of the discharge hole 13 has two communication ports. One communication port of the small chamber opens to the plunger chamber 14 side. The other communication port of the small chamber opens to the third fuel pipe 143 side. The blocking valve 91 is pressed against the communication port on the plunger chamber 14 side of the small chamber by the biasing force of the blocking spring 92. Thereby, the communication between the plunger chamber 14 and the small chamber is blocked. That is, the communication between the plunger chamber 14 and the third fuel pipe 143 through the discharge hole 13 is blocked. However, as will be described later, when the pressure in the plunger chamber 14 rises, the blocking valve 91 is thereby separated from the communication port of the small chamber against the urging force of the blocking spring 92. Thereby, the plunger chamber 14 communicates with the small chamber. That is, the plunger chamber 14 and the third fuel pipe 143 communicate with each other through the discharge hole 13.

  The opening position of the discharge hole 13 in the plunger chamber 14 is located above the upper end surface of the plunger 20 when the plunger 20 moves most upward. Thereby, obstruction | occlusion of the discharge hole 13 by the plunger 20 is avoided.

(Configuration of electromagnetic metering valve 30)
Next, the detailed configuration of the electromagnetic metering valve 30 according to the present embodiment will be described with reference to FIGS. In connection with this, elements related to the electromagnetic metering valve 30 of the high-pressure fuel pump 100 will also be described. Hereinafter, the three directions orthogonal to each other are referred to as an x direction, a y direction, and a z direction. A plane defined by the x direction and the y direction is referred to as a defined plane.

  As described above, the high-pressure fuel pump 100 includes the cylinder 10, the plunger 20, the electromagnetic metering valve 30, and the check valve 90. In the cylinder 10, in addition to the pump chamber 11, the fuel supply path 12, and the discharge hole 13, a first valve chamber 15 is formed. The electromagnetic metering valve 30 has a second valve chamber 55. In the z direction, the pump chamber 11, the fuel supply path 12, the first valve chamber 15, and the second valve chamber 55 are arranged in order from the bottom to the top. The first valve chamber 15 corresponds to a fuel storage chamber and a valve chamber. The second valve chamber 55 corresponds to an armature chamber.

  The pump chamber 11 has a pillar shape having two openings. The axial direction of the pump chamber 11 is along the z direction. The plunger 20 has a column shape. The axial direction of the plunger 20 is also along the z direction. In the circumferential direction around the axial direction of the pump chamber 11, the side wall surface 20 a of the plunger 20 and the inner wall surface 11 a constituting the pump chamber 11 contact over the entire circumference so that the plunger 20 can slide in the axial direction of the pump chamber 11. doing.

  The other opening end of the pump chamber 11 and the upper end surface 20b of the plunger 20 are opposed to each other in the z direction. The plunger chamber 14 is partitioned by the upper end surface 20b of the plunger 20 and the inner wall surface 11a of the pump chamber 11 above the upper end surface 20b.

  The cylinder 10 has a first body 16 and a second body 17. The first body 16 is located below the second body 17 in the z direction. A pump chamber 11 and a fuel supply path 12 are formed in the first body 16. The first valve chamber 15 is constituted by the first body 16 and the second body 17. A second valve chamber 55 is located above the second body 17. The second body 17 may be included in the electromagnetic metering valve 30 instead of the cylinder 10.

  As shown in FIG. 2, the first body 16 and the second body 17 are connected to each other by caulking or welding. A concave portion that is recessed downward in the z direction is formed on the side of the first body 16 that is connected to the second body 17. The concave portion is defined by an inner lower surface 16a that spreads in a prescribed plane and a first inner side surface 16b that rises annularly upward from the inner lower surface 16a. Moreover, the recessed part dented upwards in the z direction is formed in the connection part side with the 1st body 16 in the 2nd body 17. As shown in FIG. The concave portion is defined by an inner upper surface 17a facing the inner lower surface 16a in the z direction and a second inner side surface 17b standing in an annular shape downward from the inner upper surface 17a. The first valve chamber 15 is constituted by the inner lower surface 16a, the first inner side surface 16b, the second inner side surface 17b, and the inner upper surface 17a described above.

  The first body 16 is formed with a first through hole 16c penetrating in the z direction. The second body 17 is formed with a second through hole 17c penetrating in the z direction. The first through hole 16c and the second through hole 17c are arranged in the z direction. The plunger chamber 14, the fuel supply path 12, the first valve chamber 15, and the second valve chamber 55 communicate with each other through the first through hole 16c and the second through hole 17c. As described above, the cylinder 10 communicates with the plunger chamber 14, the fuel supply path 12, the first through hole 16c, the first valve chamber 15, the second through hole 17c, and the second valve chamber 55, and extends in the z direction. A communication hole is formed. A valve body 31 is provided in the communication hole. The second through hole 17c corresponds to the through hole.

  As described above, the electromagnetic metering valve 30 includes the valve body 31, the main spring 32, and the solenoid coil 33. In addition to these, the electromagnetic metering valve 30 includes a connecting portion 34, a sub spring 35, a base 36, a spacer 37, a stator core 38, a housing 39, a connector 40, and a nut 41.

  The valve body 31 includes a suction valve 42 and an armature 43. The suction valve 42 and the armature 43 each have a columnar shape extending in the z direction. The suction valve 42 and the armature 43 are separate bodies.

  The tip of the suction valve 42 is provided in the plunger chamber 14. The end of the suction valve 42 opposite to the tip is provided in the first valve chamber 15. The tip of the armature 43 is also provided in the first valve chamber 15. The end of the suction valve 42 and the tip of the armature 43 are opposed in the z direction. The end of the armature 43 opposite to the tip is provided in the second valve chamber 55.

  The suction valve 42 has a first tip portion 44 and a first column portion 45. The first tip portion 44 and the first column portion 45 are arranged in the z direction and are integrally connected to each other. The first tip portion 44 has a longer diameter on the specified plane than the first column portion 45. All of the first tip portion 44 is provided in the plunger chamber 14. The first column portion 45 is provided in the fuel supply path 12, the first through hole 16 c, and the first valve chamber 15. Due to the movement of the suction valve 42 in the z direction, the connection end of the first column portion 45 with the first tip portion 44 enters and exits the plunger chamber 14.

  The first tip portion 44 has a longer diameter on the specified plane than the open end of the plunger chamber 14. The first pillar portion 45 is integrally connected to the center of the upper surface 44 a of the first tip portion 44. Therefore, the upper surface 44a of the first tip 44 has an annular shape. The upper surface 44a of the first tip 44 is opposed to the annular upper inner surface 11b of the inner wall surface 11a on the opening end side of the plunger chamber 14 in the z direction. And this upper surface 44a has comprised the taper shape which inclined so that a diameter may become narrow gradually as it goes to the 1st pillar part 45 side from the 1st front-end | tip part 44 in the z direction. The upper inner surface 11b has a tapered shape inclined so that the diameter gradually decreases from the inside of the plunger chamber 14 toward the opening end. The tapered upper surface 44a of the intake valve 42 and the tapered upper inner surface 11b of the plunger chamber 14 are in full contact with each other. As a result, the plunger chamber 14 is closed by the suction valve 42. The upper inner surface 11b corresponds to a wall surface.

  Three first notches 45a having a cut surface extending in the z direction are formed at a portion where the first through hole 16c communicating with the fuel supply path 12 and the first valve chamber 15 in the first pillar portion 45 is communicated. Yes. The first notch 45a forms a gap extending in the z direction between the first pillar portion 45 and the wall surface forming the first through hole 16c. Due to this gap, the fuel supply path 12 and the first valve chamber 15 communicate with each other in a state in which the valve body 31 is provided in the first through hole 16c.

  A stopper 46 is provided at a portion of the first column 45 provided in the first valve chamber 15. The stopper 46 is made of a material having a lower hardness than the suction valve 42. The stopper 46 has a first tube portion 47 and a first annular portion 48. The 1st cylinder part 47 comprises cylinder shape, and the axial direction is along az direction. The first annular portion 48 is annular as the name suggests, and is open in the z direction. The axial directions of the first cylindrical portion 47 and the first annular portion 48 coincide with the axial direction of the first column portion 45 in a prescribed plane. The first tube portion 47 and the first annular portion 48 are a single piece. As shown in FIG. 4, the first cylindrical portion 47 and the first annular portion 48 are fixed to the side surface of the end portion 45 b of the portion provided in the first valve chamber 15 in the first column portion 45 by caulking.

  One end 47a of the first cylindrical portion 47 is opposed to the inner lower surface 16a of the first body 16 in the z direction. When the suction valve 42 moves to the plunger chamber 14 side in the z direction, the one end 47a of the first cylindrical portion 47 contacts the inner lower surface 16a of the first body 16. Thus, the displacement of the suction valve 42 toward the plunger chamber 14 in the z direction is restricted by the first cylindrical portion 47. As a result, the distance in the z direction between the upper surface 44a of the first tip 44 and the upper inner surface 11b of the plunger chamber 14 is restricted. Although not shown, four communication holes extending in the direction along the specified plane are formed at one end 47a of the first tube portion 47. Through this communication hole, the hollow of the first tube portion 47 communicates with the outside.

  The first annular portion 48 is connected to the other end side opposite to the one end 47 a of the first tube portion 47. The first annular portion 48 has a larger outer diameter than the first tube portion 47. Therefore, the lower surface 48a along the prescribed plane of the first annular portion 48 faces the inner lower surface 16a of the first body 16 in the z direction. A subspring 35 is provided between the first annular portion 48 and the first body 16.

  The sub spring 35 is a spring coil in which a linear elastic material is spirally wound in the z direction. A first column part 45 and a first cylinder part 47 are inserted in the hollow of the subspring 35. The subspring 35 surrounds the first column portion 45 and the first tube portion 47. The sub spring 35 is located between the first body 16 and the first annular portion 48 in the z direction. One end of the sub spring 35 is in contact with the inner lower surface 16 a of the first body 16. The other end of the sub spring 35 is in contact with the lower surface 48 a of the first annular portion 48. As will be described later, the sub spring 35 is sandwiched between the first body 16 and the first annular portion 48 by the urging force of the main spring 32. Therefore, the subspring 35 generates a biasing force in a direction away from the subspring 35 in the z direction.

  The armature 43 has a pressing portion 49 and a pedestal portion 50. The pressing portion 49 is made of a material having higher hardness than the pedestal portion 50. The pressing part 49 and the suction valve 42 are made of the same material. The pedestal 50 is made of a soft magnetic material. The pressing part 49 has a column shape, and its axial direction is along the z direction. The pedestal 50 has an annular shape and is open in the z direction. The axial directions of the pressing portion 49 and the pedestal portion 50 are coincident with each other on the prescribed plane.

  The pressing portion 49 is longer in the z direction than the pedestal portion 50. Further, the diameter of the pressing portion 49 and the inner diameter of the pedestal portion 50 are substantially equal on the specified plane. One end of the pressing portion 49 is provided in the hollow of the pedestal portion 50. The pressing part 49 and the base part 50 are connected.

  The pressing part 49 has a second tip part 51 and a second column part 52. The second tip portion 51 and the second column portion 52 are aligned in the z direction and are integrally connected to each other. All of the second tip 51 is provided in the first valve chamber 15. The second column portion 52 is provided in the first valve chamber 15, the second through hole 17 c, and the second valve chamber 55. The second column part 52 corresponds to the center part.

  The diameter of the prescribed plane of the second tip portion 51 is longer than that of the second column portion 52. The second column part 52 is integrally connected to the center of the upper surface 51 a of the second tip part 51. Therefore, the upper surface 51a of the second tip 51 has an annular shape.

  Three second notches 52a having a cut surface extending in the z direction are formed at a portion of the second pillar portion 52 where the second through hole 17c enters and exits. The second notch 52a forms a gap extending in the z direction between the second pillar portion 52 and the wall surface forming the second through hole 17c. By this gap, the first valve chamber 15 and the second valve chamber 55 communicate with each other in a state where the valve body 31 is provided in the second through hole 17c.

  The pedestal portion 50 is connected to a portion provided in the second valve chamber 55 in the second column portion 52. Therefore, all of the pedestal portion 50 is provided in the second valve chamber 55. The outer diameter of the prescribed plane of the pedestal 50 is longer than the diameter of the second through hole 17c. Therefore, the annular lower surface 50a of the pedestal 50 is opposed to the outer upper surface 17d of the second body 17 opposite to the inner upper surface 17a in the z direction. The outer upper surface 17d corresponds to the upper surface of the wall portion on the armature chamber side.

  An annular seal portion 17e is formed on the outer upper surface 17d. The seal portion 17e is formed so as to surround the opening in the outer upper surface 17d of the second through hole 17c. The height of the seal portion 17e in the z direction is the same all around. The annular upper surface of the seal portion 17e faces the lower surface 50a of the pedestal portion 50 in the z direction. Due to the movement of the valve body 31 in the z direction, the upper surface of the seal portion 17e and the lower surface 50a of the pedestal portion 50 come into full contact.

  Further, as shown in FIG. 2, the second body 17 is formed with a constant communication hole 17f that communicates the outer upper surface 17d and the second inner side surface 17b. The constant communication hole 17f is opened outside the region surrounded by the seal portion 17e on the outer upper surface 17d. Further, the constant communication hole 17f opens in a region facing the stopper 46 on the second inner side surface 17b. The second body 17 corresponds to the wall portion.

  As described above, when the entire contact between the upper surface of the seal portion 17e and the lower surface 50a of the pedestal portion 50 is released by the movement of the valve body 31 in the z direction, the second valve chamber 55 is always connected to the second valve chamber 55 via the communication hole 17f. The first valve chamber 15 communicates with the first valve chamber 15. As a result, the second valve chamber 55 is communicated with the fuel supply path 12. Conversely, when the upper surface of the seal portion 17e and the lower surface 50a of the pedestal portion 50 come into full contact, the communication between the second valve chamber 55 and the first valve chamber 15 through the continuous communication hole 17f is interrupted.

  The pedestal portion 50 is formed with a plurality of holes 50b penetrating in the z direction. Although the second valve chamber 55 is filled with fuel, the hole 50b prevents the movement of the pedestal 50 in the z direction due to the resistance of the fuel.

  The connecting portion 34 functions to indirectly connect the suction valve 42 and the armature 43. The connecting portion 34 has a second cylindrical portion 53 and a second annular portion 54. The 2nd cylinder part 53 comprises a cylinder shape, and the axial direction is along az direction. As the name suggests, the second annular portion 54 is annular and opens in the z direction. The axial direction of each of the second cylindrical portion 53 and the second annular portion 54 coincides with the axial direction of the second column portion 52 in a prescribed plane. The 2nd cylinder part 53 and the 2nd annular part 54 are an integral thing. The outer diameter of the second annular portion 54 is the same as the inner diameter of the second cylindrical portion 53. The second annular portion 54 is provided in the upper opening portion of the two opening portions of the second cylindrical portion 53. As a result, the opening area on the upper side of the second cylindrical portion 53 is narrower than the opening area on the lower side.

  As shown in FIG. 2, a pressing portion 49 is inserted into the hollow of the connecting portion 34. That is, the second tip portion 51 is provided in the hollow of the second tube portion 53. A second pillar portion 52 is provided in the hollow of the second annular portion 54. The 2nd cylinder part 53 and the 2nd front-end | tip part 51 are facing in the z direction. In the present embodiment, the second tube portion 53 and the second tip portion 51 are in contact with each other. One end 53 a of the second cylindrical portion 53 is in contact with the upper surface 48 b of the first annular portion 48 of the stopper 46. The connecting portion 34 will be described in detail later.

  The main spring 32 is a spring coil in which a linear elastic material is spirally wound in the z direction. The main spring 32 is located in the first valve chamber 15. The main spring 32 is located between the connecting portion 34 and the second body 17 in the z direction. A second pillar portion 52 is inserted into the hollow of the main spring 32. The main spring 32 surrounds the second pillar portion 52.

  An annular shim 17g is formed on the inner upper surface 17a. The shim 17g is formed so as to surround the opening in the inner upper surface 17a of the second through hole 17c. The height of the shim 17g in the z direction is the same all around. The annular lower surface of the shim 17 g faces the upper surface 54 a of the second annular portion 54 of the connecting portion 34 in the z direction.

  One end of the main spring 32 is in contact with the lower surface of the shim 17g. The other end of the main spring 32 is in contact with the upper surface 54 a of the second annular portion 54 of the connecting portion 34. As described above, the connecting portion 34 is in contact with the stopper 46. The stopper 46 is in contact with the inner and lower surfaces 16 a of the first body 16. As described above, the main spring 32 is sandwiched between the first body 16 and the second body 17 via the connecting portion 34 and the stopper 46. Therefore, the main spring 32 generates a biasing force in a direction away from the main spring 32 in the z direction.

  The height of the shim 17g is determined when the main spring 32 is assembled to the cylinder 10. As a result, the elastic deformation in the z direction of the main spring 32 is adjusted. The height of the shim 17g can be determined by preparing a plurality of shims 17g having different heights and assembling them with the second body 17 according to the desired urging force of the main spring 32. Alternatively, the height may be determined by scraping a shim 17g previously formed on the second body 17.

  As described above, the stopper 46 is connected to the suction valve 42. Accordingly, the urging force of the main spring 32 toward the inner and lower surfaces 16 a is applied to the suction valve 42 via the stopper 46.

  A subspring 35 is provided between the stopper 46 and the first body 16. The sub spring 35 is sandwiched between the first annular portion 48 of the stopper 46 and the first body 16 by the biasing force of the main spring 32 toward the inner and lower surfaces 16a. As a result, the sub spring 35 generates a biasing force in a direction away from the sub spring 35 in the z direction. As a result, the urging force toward the inner upper surface 17 a is applied from the sub spring 35 to the suction valve 42 connected to the stopper 46.

  As described above, the urging force directed downward from the main spring 32 is applied to the suction valve 42 via the connecting portion 34 and the stopper 46. A biasing force directed upward through the stopper 46 is applied to the suction valve 42 from the sub spring 35. As described above, the directions in which the main spring 32 and the sub-spring 35 are applied to the suction valve 42 are opposite to each other in the z direction. Note that the direction in which the urging force of the main spring 32 and the sub spring 35 applied to the connecting portion 34 is also opposite to each other in the z direction.

  Further, as described above, the second annular portion 54 of the connecting portion 34 and the upper surface 51 a of the second tip portion 51 of the armature 43 are in contact with each other. Therefore, the urging force of the main spring 32 toward the inner and lower surfaces 16a is applied to the armature 43.

  The main spring 32 is set to have a larger urging force than the sub-spring 35 described above. Therefore, as shown in FIG. 2, the armature 43 in contact with the connecting portion 34 is urged downward by the urging force of the main spring 32, and the lower surface 50a of the pedestal portion 50 is in contact with the seal portion 17e. The stopper 46 in contact with the connecting portion 34 is urged downward by the urging force of the main spring 32, and one end 47a of the first tube portion 47 of the stopper 46 is in contact with the inner and lower surfaces 16a. Similarly, the suction valve 42 connected to the stopper 46 is also urged downward, and the upper surface 44a of the first tip 44 and the upper inner surface 11b of the plunger chamber 14 are separated in the z direction. Thereby, the plunger chamber 14 and the fuel supply path 12 communicate with each other.

  As shown in FIG. 2, each of the solenoid coil 33, the base 36, the spacer 37, the stator core 38, the housing 39, the connector 40, and the nut 41 is provided above the second body 17.

  Each of the base 36 and the spacer 37 has a cylindrical shape. Each of the base 36 and the spacer 37 is open in the z direction. The axial direction of each of the base 36 and the spacer 37 coincides with the axial direction of the second column part 52 in a prescribed plane. The inner diameters of the base 36 and the spacer 37 in the defined plane are the same. The base 36 is provided on the outer upper surface 17 d of the second body 17. As a result, one of the two openings of the base 36 is closed by the second body 17. The spacer 37 is provided at an end portion constituting the remaining opening of the base 36. The hollows of the base 36 and the spacer 37 communicate with each other in the z direction. The inner surfaces of the base 36 and the spacer 37 are continuous in the z direction.

  The stator core 38 has a column shape. The stator core 38 is provided at the end of the spacer 37 opposite to the connection end with the base 36. The stator core 38 closes the opening of the spacer 37. As described above, the second valve chamber 55 is constituted by the base 36, the spacer 37, and the stator core 38 above the outer upper surface 17 d of the second body 17.

  In the region surrounded by the base 36 on the outer upper surface 17d, each of the second through hole 17c and the continuous communication hole 17f is opened, and a seal portion 17e is formed. Therefore, the second through hole 17c and the constant communication hole 17f are opened in the second valve chamber 55, respectively. The seal portion 17 e is located in the second valve chamber 55. In the second valve chamber 55, the pedestal portion 50 of the armature 43 and the end of the second column portion 52 to which the pedestal portion 50 is fixed are provided.

  The solenoid coil 33 surrounds the second valve chamber 55 in the circumferential direction around the z direction. The solenoid coil 33 is fixed to the second body 17 together with the connector 40 by a housing 39 made of resin. The connector 40 functions to electrically connect the solenoid coil 33 and the control device 130. The nut 41, together with the stator core 38, fixes the connector 40 and the housing 39 to the second body 17. As described above, the solenoid coil 33, the base 36, the spacer 37, the stator core 38, the housing 39, the connector 40, and the nut 41 are provided above the second body 17.

  The base 36 and the stator core 38 are made of a soft magnetic material in the same manner as the pedestal portion 50. On the other hand, the spacer 37 is made of a nonmagnetic material. Therefore, when a drive current is supplied from the control device 130 to the solenoid coil 33 via the connector 40, a magnetic circuit passing through the base 36, the pedestal portion 50, and the stator core 38 is formed. When this magnetic circuit is formed, an upward electromagnetic force is generated in the pedestal 50.

  Due to the generation of the electromagnetic force, the armature 43 moves upward as shown in FIG. As the armature 43 moves, the connecting portion 34 also moves. Accordingly, the suction valve 42 also moves upward. As a result, the upper surface 44a of the suction valve 42 and the upper inner surface 11b of the plunger chamber 14 come into full contact. As a result, the plunger chamber 14 is closed.

  When the plunger 20 is raised by the rotation of the camshaft 300 in a state where the plunger chamber 14 is closed, the pressure in the plunger chamber 14 rises. Due to the pressure increase in the plunger chamber 14, the blocking valve 91 moves away from the communication port of the discharge hole 13 against the urging force of the blocking spring 92. As a result, the fuel in the plunger chamber 14 is discharged to the third fuel pipe 143 through the discharge hole 13.

(Connecting part)
Next, the connecting portion 34 will be described in detail based on FIG. As described above, the connecting portion 34 includes the second cylindrical portion 53 and the second annular portion 54. The outer diameter of the second cylindrical portion 53 is equal to the width of the first valve chamber 15 in the defined plane. The outer side surface 53 b of the second cylindrical portion 53 is in contact with the second inner side surface 17 b that defines a part of the first valve chamber 15. The outer side surface 53b of the second cylindrical portion 53 and the second inner side surface 17b of the second body 17 are in contact with each other to the extent that they can slide.

  The inner diameter of the second cylindrical portion 53 is longer than the diameter of the second tip portion 51. However, the inner diameter of the second annular portion 54 is shorter than the diameter of the second tip portion 51. The second tip portion 51 is inserted into the hollow of the second tube portion 53. The upper surface 51 a of the second tip portion 51 is in contact with the lower surface 54 b of the second annular portion 54.

  The inner diameter of the second annular portion 54 is equal to the diameter of the second column portion 52. The second column part 52 is inserted into the second annular part 54. The inner peripheral surface 54c of the second annular portion 54 and the side surface 52b of the second column portion 52 are in contact with each other. The inner peripheral surface 54c and the side surface 52b are in contact with each other to the extent that they can slide. However, the inner peripheral surface 54c and the side surface 52b are in contact with each other to such an extent that they are more difficult to slide than the outer side surface 53b and the second inner side surface 17b. Therefore, the flow of fuel through the gap between the inner peripheral surface 54c and the side surface 52b is suppressed.

  With the above configuration, the first valve chamber 15 defined by the first body 16 and the second body 17 is divided into two spaces with the connecting portion 34 as a boundary. That is, the first valve chamber 15 is divided into a lower valve chamber located below the connecting portion 34 and an upper valve chamber located above. The upper valve chamber is sealed when the upper surface of the seal portion 17e and the lower surface 50a of the pedestal portion 50 are in full contact with each other, and serves to store fuel. Hereinafter, the upper valve chamber is referred to as a fuel storage chamber 56. The lower valve chamber is simply referred to as a valve chamber 57.

  The fuel storage chamber 56 is partitioned by the second body 17, the connecting portion 34, and the second pillar portion 52. More specifically, the fuel storage chamber 56 includes an upper surface 34a of the connecting portion 34, a portion above the upper surface 34a of the second inner side surface 17b, an inner upper surface 17a, and a space between the upper surface 34a and the inner upper surface 17a of the side surface 52b. It is partitioned by site.

  Strictly speaking, not only the fuel storage chamber 56 is the region in which fuel is stored while the upper surface of the seal portion 17e and the lower surface 50a of the pedestal portion 50 are in full contact. A region for storing fuel is also present in the second through hole 17 c and the second valve chamber 55. In the second through hole 17c, fuel is stored in a gap (region) between the second pillar portion 52 and the wall surface constituting the second through hole 17c. In the second valve chamber 55, fuel is stored in a region surrounded by the seal portion 17 e, the second column portion 52, and the pedestal portion 50. A region in which fuel is stored in the second through hole 17c and the second valve chamber 55 is surrounded by a one-dot chain line in FIG. Hereinafter, this region is referred to as a secondary storage chamber 56a.

  As shown in FIG. 3, the valve body 31 moves in the z direction by electromagnetic force. As a result, when the full contact between the upper surface of the seal portion 17e and the lower surface 50a of the pedestal portion 50 is released, the fuel storage chamber 56 and the secondary storage chamber 56a are always communicated with the valve chamber 57 via the communication hole 17f. The The valve chamber 57 communicates with the fuel supply path 12 through the first through hole 16c. Therefore, the fuel storage chamber 56 and the secondary storage chamber 56a are always communicated with the fuel supply path 12 through the communication hole 17f, the valve chamber 57, and the first through hole 16c. As a result, the sealed state of the fuel storage chamber 56 and the secondary storage chamber 56a is released.

  As shown above, the secondary storage chamber 56a also contributes to fuel storage. However, the behavior of the secondary storage chamber 56a is the same as that of the fuel storage chamber 56. Therefore, in order to avoid complicated description, description of the secondary storage chamber 56a is omitted below.

  Next, the behavior of the electromagnetic metering valve 30 and the function of the fuel storage chamber 56 will be described with reference to FIG. As described above, the plunger 20 moves in the axial direction as the camshaft 300 rotates. At time t0 in FIG. 5, the plunger 20 is located at the uppermost position of the plunger chamber 14. Thereby, the volume of the plunger chamber 14 is the smallest. At this time, the plunger chamber 14 is closed. Therefore, the pressure in the plunger chamber 14 is still high.

  No driving current is supplied to the solenoid coil 33 at time t0. Therefore, the valve body 31 is about to move downward by the urging force of the main spring 32. However, the pressure in the plunger chamber 14 is still high. Therefore, the downward movement of the valve body 31 has not started.

  At time t0, the valve body 31 is positioned upward as shown in FIG. Therefore, the contact between the seal portion 17e and the pedestal portion 50 is released. The sealed state of the fuel storage chamber 56 is released. The volume of the fuel storage chamber 56 is the smallest. The fuel stored in the fuel storage chamber 56 is the smallest.

  When time elapses from time t0, the plunger 20 moves downward by the rotation of the camshaft 300. That is, the plunger 20 descends. As a result, the volume of the plunger chamber 14 begins to increase. The pressure in the plunger chamber 14 is reduced. As a result, the valve body 31 starts to move downward due to the urging force of the main spring 32. Contact between the suction valve 42 and the plunger chamber 14 is released, and the fuel supply path 12 and the plunger chamber 14 are communicated. Fuel begins to flow from the fuel supply path 12 into the plunger chamber 14. Fuel is sucked into the plunger chamber 14.

  Further, the volume of the fuel storage chamber 56 starts to increase. As a result, the pressure in the fuel storage chamber 56 is reduced. As shown in FIG. 5, the drag having a correlation with the pressure in the fuel storage chamber 56 is also reduced. As a result, fuel begins to flow into the fuel storage chamber 56. The capacity of the fuel in the fuel storage chamber 56 begins to increase.

  When the time t1 is reached, the volume of the fuel storage chamber 56 becomes maximum. Thereby, the decompression of the fuel storage chamber 56 stops. This has shown that the seal part 17e and the base part 50 contacted by the downward movement of the valve body 31. FIG. In addition, even if the volume of the fuel storage chamber 56 becomes maximum, the capacity of the fuel in the fuel storage chamber 56 does not become maximum. Due to flow resistance or the like, the timing at which the volume of fuel stored in the fuel storage chamber 56 is maximized is delayed from the timing at which the volume of the fuel storage chamber 56 is maximized. At time t1, the capacity of the fuel in the fuel storage chamber 56 is not maximized.

  As described above, when the seal portion 17e and the pedestal portion 50 come into contact with each other, the fuel storage chamber 56 is in a sealed state. However, because of the microscopic surface roughness such as surface irregularities, the fuel storage chamber 56 is not ideally sealed. Further, as described above, the pressure in the fuel storage chamber 56 is low. Therefore, for example, the fuel flows into the fuel storage chamber 56 through a microscopic gap between the outer side surface 53 b of the second cylindrical portion 53 and the second inner side surface 17 b of the second body 17. The fuel flows into the fuel storage chamber 56 through a microscopic gap between the inner peripheral surface 54 c of the second annular portion 54 and the side surface 52 b of the second column portion 52. Thereby, the capacity of the fuel in the fuel storage chamber 56 gradually increases. As a result, the drag of the fuel storage chamber 56 gradually increases.

  When the time t2 is reached, the fuel capacity in the fuel storage chamber 56 becomes maximum. As a result, the flow of fuel into the fuel storage chamber 56 stops, and the drag of the fuel storage chamber 56 becomes constant. The pressure in the fuel storage chamber 56 at this time is the same as the pressure in the second valve chamber 55 and the like.

  When the time t3 is reached, the plunger 20 is located at the lowest position. Thereby, the volume of the plunger chamber 14 is the largest. Therefore, the capacity of the fuel in the plunger chamber 14 is the largest.

  When time elapses from time t3, the plunger 20 starts to move upward by the rotation of the camshaft 300. That is, the plunger 20 rises. As a result, the volume in the plunger chamber 14 begins to decrease.

  At this time, no drive current is supplied to the solenoid coil 33. Therefore, the plunger chamber 14 and the fuel supply path 12 communicate with each other. Due to the upward movement of the plunger 20, the fuel is discharged from the plunger chamber 14 to the fuel supply path 12. As a result, the volume of fuel in the plunger chamber 14 is reduced.

  By discharging the fuel from the plunger chamber 14 due to the upward movement of the plunger 20, the fuel discharge pressure is applied to the suction valve 42. The direction in which this discharge pressure is applied is upward. Therefore, the suction valve 42 tends to move upward by the discharge pressure.

  The suction valve 42 is provided with a stopper 46. The stopper 46 is in contact with the connecting portion 34. A fuel storage chamber 56 is located above the connecting portion 34. At time t3, the fuel storage chamber 56 is in a sealed state and is filled with fuel. Therefore, when the connecting portion 34 moves upward together with the intake valve 42, the fuel storage chamber 56 filled with fuel is compressed. Thereby, the drag (reaction force) of the fuel storage chamber 56 is increased. This drag is applied in a direction that prevents the movement of the connecting portion 34. That is, the direction in which the drag is applied is downward. This drag is applied to the suction valve 42 via the connecting portion 34 and the stopper 46. Therefore, the urging force and the drag force of the main spring 32 are applied to the suction valve 42 downward. The separation between the suction valve 42 and the plunger chamber 14 is maintained by the biasing force and the drag force.

  When the time t4 is reached, the volume of the plunger chamber 14 reaches a target value suitable for the driving situation of the vehicle. That is, the amount of fuel discharged to the common rail reaches a target value suitable for the driving situation of the vehicle. The determination of the fuel discharge amount is performed by the control device 130. At this time, the control device 130 causes a drive current to flow through the solenoid coil 33. Thereby, a magnetic circuit is formed. An upward electromagnetic force is generated in the armature 43. Due to this electromagnetic force, the armature 43 tends to move upward.

  When the armature 43 moves upward, the seal portion 17e and the pedestal portion 50 are separated from each other. As a result, the sealed state of the fuel storage chamber 56 is released. Therefore, as shown in FIG. 5, when the time elapses from time t4, the drag of the fuel storage chamber 56 decreases.

  The armature 43 moves upward against the urging force of the main spring 32. As a result, the suction valve 42 also moves upward together with the armature 43, and the suction valve 42 and the plunger chamber 14 come into contact with each other. As a result, the communication between the plunger chamber 14 and the fuel supply path 12 is blocked.

  After time t4, the plunger 20 continues to move upward. Therefore, the pressure in the plunger chamber 14 increases. This pressure is applied to the closing valve 91. With this pressure, the blocking valve 91 moves away from the communication port on the plunger chamber 14 side of the small chamber of the discharge hole 13 against the urging force of the blocking spring 92. As a result, the plunger chamber 14 and the third fuel pipe 143 communicate with each other through the discharge hole 13. The high pressure fuel in the plunger chamber 14 is supplied to the common rail via the third fuel pipe 143.

  At time t5 in the middle of discharging fuel from the discharge hole 13 to the third fuel pipe 143, the control device 130 stops supplying drive current to the solenoid coil 33. As a result, the suction valve 42 closing the open end of the plunger chamber 14 tends to move downward. That is, the suction valve 42 tends to be separated from the wall surface of the plunger chamber 14. However, since the plunger 20 moves upward, the pressure in the plunger chamber 14 is still high. Therefore, the downward movement of the suction valve 42 does not start.

  When the time t6 is reached, the plunger 20 is located at the uppermost position. After this, the plunger 20 tries to start moving downward. Therefore, the pressure in the plunger chamber 14 decreases. Thereby, the downward movement of the suction valve 42 is started. The suction valve 42 is separated from the wall surface of the plunger chamber 14, and the plunger chamber 14 and the fuel supply path 12 are communicated with each other. Further, the closing valve 91 is pressed against the communication port on the plunger chamber 14 side of the small chamber of the discharge hole 13 by the biasing force of the closing spring 92. Thereby, the communication between the plunger chamber 14 and the third fuel pipe 143 through the discharge hole 13 is blocked. The high-pressure fuel pump 100 supplies the high-pressure fuel to the common rail by repeating the operation from the time t1 to the time t6 described above.

(Function and effect)
Next, the effect of the electromagnetic metering valve 30 of the high-pressure fuel pump 100 according to the present embodiment will be described.

  When the fuel is discharged from the plunger chamber 14 due to the upward movement of the plunger 20, the fuel discharge pressure is applied to the suction valve 42. The suction valve 42 tends to move upward by this discharge pressure. At this time, the urging force of the main spring 32 and the drag force of the fuel storage chamber 56 are applied to the suction valve 42 downward.

  For this reason, the separation in the z direction between the upper surface 44a of the suction valve 42 and the upper inner surface 11b of the plunger chamber 14 is maintained by the urging force and the drag force. Accordingly, the biasing force of the main spring 32 is set to be weaker than the configuration in which the separation in the z direction between the upper surface 44a of the suction valve 42 and the upper inner surface 11b of the plunger chamber 14 is held only by the biasing force of the main spring 32. Can do.

  In addition, an upward electromagnetic force is generated in the armature 43 by energization of the drive current to the solenoid coil 33. The armature 43 tends to move upward by this electromagnetic force. As a result, the sealed state of the fuel storage chamber 56 is released. The drag of the fuel storage chamber 56 decreases and disappears. For this reason, the downward force applied to the suction valve 42 and the armature 43 is only the urging force of the main spring 32. Therefore, in order to move the suction valve 42 and bring the upper surface 44 a of the suction valve 42 into contact with the upper inner surface 11 b of the plunger chamber 14, the electromagnetic force applied to the armature 43 is simply made stronger than the biasing force of the main spring 32. Get better.

  As described above, the biasing force of the main spring 32 can be set weak. Therefore, the electromagnetic force applied to the armature 43 can also be set weak. As a result, the amount of current flowing through the solenoid coil 33 can be reduced. As a result, an increase in the current amount of the solenoid coil 33 is suppressed.

  In FIG. 5, the drive current required in the case where the suction valve 42 and the plunger chamber 14 are separated from each other in the z direction only by the urging force of the main spring 32 is indicated by a one-dot chain line. On the other hand, the solid line shows the drive current required in the present embodiment in which the suction valve 42 and the plunger chamber 14 are separated from each other in the z direction by the biasing force of the main spring 32 and the drag of the fuel storage chamber 56. . FIG. 5 schematically shows these drive currents. However, when the inventor verified by experiment, it was confirmed that the magnitude relation of the drive current shown in FIG. 5 is established. That is, it has been confirmed that the drive current is lower in this embodiment than in the comparative configuration.

  An annular seal portion 17e is formed on the outer upper surface 17d of the second body 17 so as to surround the opening in the outer upper surface 17d of the second through hole 17c. The movement of the armature 43 in the z direction controls the contact between the upper surface of the seal portion 17e and the lower surface 50a of the pedestal portion 50. Therefore, the communication between the fuel storage chamber 56 and the second valve chamber 55 is controlled by the movement of the armature 43 in the z direction.

  The second body 17 is formed with a continuous communication hole 17f that opens outside a region surrounded by the seal portion 17e on the outer upper surface 17d and opens in a region facing the stopper 46 on the second inner side surface 17b. Accordingly, when the seal portion 17e and the pedestal portion 50 are separated due to the upward movement of the armature 43, the fuel storage chamber 56 becomes the second valve chamber 55, the constant communication hole 17f, and the valve chamber 57 of the first valve chamber 15. Is communicated with the fuel supply path 12 via As a result, the sealed state of the fuel storage chamber 56 is released.

(Second Embodiment)
Next, 2nd Embodiment is described based on FIG. 6 and FIG. The electromagnetic metering valve according to the second embodiment has much in common with the above-described embodiment. Therefore, in the following description, description of common parts is omitted, and different parts are mainly described. In the following description, the same reference numerals are given to the same elements as those described in the above embodiment.

  In the first embodiment, as shown in FIG. 4, an example is shown in which the upper surface 51 a of the second tip portion 51 of the armature 43 and the lower surface 54 b of the second annular portion 54 of the connecting portion 34 are in contact. On the other hand, in the present embodiment, as shown in FIG. 7, the second tip as shown in FIG. 7 in a state where the upper surface 44a of the suction valve 42 and the upper inner surface 11b of the plunger chamber 14 are separated in the z direction. The upper surface 51a of the part 51 and the lower surface 54b of the second annular part 54 are separated in the z direction.

  In order to maintain such a gap between the armature 43 and the connecting portion 34 in the z direction, the electromagnetic metering valve 30 of this embodiment includes a guide portion 60 and an armature spring 61. As shown in FIG. 6, the stator core 38 is formed with a recess 38 a for providing the guide portion 60 and the armature spring 61. The recess 38 a is open on the surface of the stator core 38 facing the second column part 52. The recess 38a extends in the z direction.

  The guide unit 60 has a support base 62 and a guide shaft 63. The support table 62 is provided on the bottom surface side of the recess 38 a that is separated from the opposing surface of the stator core 38 in the z direction. The guide shaft 63 extends from the support base 62 toward the second column portion 52 along the z direction. The guide shaft 63 and the second column part 52 are separated from each other in the z direction. The separation distance between the guide shaft 63 and the second pillar portion 52 is designed so that the movement of the armature 43 in the z direction is not hindered by the contact between both.

  The armature spring 61 is a spring coil in which a linear elastic material is spirally wound in the z direction. A guide shaft 63 is inserted in the hollow of the armature spring 61. The armature spring 61 surrounds the guide shaft 63. The armature spring 61 is located between the support base 62 and the second column part 52 in the z direction.

  One end of the armature spring 61 is in contact with the formation surface 62 a of the guide shaft 63 in the support base 62. The other end of the armature spring 61 is in contact with the upper surface 52 c of the second column part 52 of the armature 43. The support base 62 is fixed to the recess 38 a of the stator core 38. The pedestal portion 50 of the armature 43 is in contact with the seal portion 17 e of the second body 17. As described above, the armature spring 61 is sandwiched between the stator core 38 and the second body 17 via the support base 62 and the armature 43.

  Therefore, the armature spring 61 generates a biasing force in a direction away from the armature spring 61 in the z direction. The position of the armature 43 is fixed by this urging force. That is, as shown in FIG. 7, the upper surface 51a of the second tip portion 51 of the armature 43 and the lower surface 54b of the second annular portion 54 of the connecting portion 34 are separated in the z direction. The base portion 50 of the armature 43 and the seal portion 17e are in contact with each other.

  The length (height) of the support base 62 in the z direction is determined when the armature spring 61 is assembled to the stator core 38. As a result, the elastic deformation in the z direction of the armature spring 61 is adjusted. The height of the support base 62 can be determined by preparing a plurality of support bases 62 having different heights and providing the stator core 38 with the one that matches the desired urging force of the armature spring 61. Further, the elastic deformation in the z direction of the armature spring 61 may be adjusted by changing the mounting position of the support base 62 to the stator core 38. The biasing force of the armature spring 61 can be set to be equal to or less than the biasing force of the main spring 32.

  In the present embodiment, the inner peripheral surface 54 c of the second annular portion 54 and the side surface 52 b of the second column portion 52 are the outer surface 53 b of the second cylindrical portion 53 and the second inner surface 17 b of the second body 17. They are in contact with the same degree of ease of sliding.

  Thus, in the electromagnetic metering valve 30 according to the present embodiment, the upper surface 51 a of the second tip portion 51 of the armature 43 and the lower surface 54 b of the second annular portion 54 of the connecting portion 34 are applied by the biasing force of the armature spring 61. Separated in the z direction. Further, the base portion 50 and the seal portion 17e are in contact with each other by the urging force of the armature spring 61. Thereby, the fuel storage chamber 56 is sealed. The inner peripheral surface 54 c of the second annular portion 54 of the connecting portion 34 and the side surface 52 b of the second pillar portion 52 of the armature 43 are easy to slide.

  As described above, when electromagnetic force is generated in the pedestal portion 50 by energization of the drive current to the solenoid coil 33, the upper surface 51a of the second tip portion 51 of the armature 43 and the lower surface 54b of the second annular portion 54 of the connecting portion 34 come into contact. Until then, the armature 43 moves upward alone. By the single movement of the armature 43, the sealed state of the fuel storage chamber 56 is released. Thus, the closed state of the fuel storage chamber 56 can be released faster than the configuration in which the closed state of the fuel storage chamber 56 is released by the movement of the suction valve 42 and the armature 43 together.

  The electromagnetic metering valve 30 according to the present embodiment includes components equivalent to the electromagnetic metering valve 30 described in the first embodiment. Therefore, it cannot be overemphasized that there exists an equivalent effect.

  As shown in FIG. 6, in this embodiment, the seal portion 17 e is formed on the pedestal portion 50 of the armature 43. When the armature 43 comes into contact with the outer upper surface 17d, the fuel storage chamber 56 is sealed.

  The preferred embodiments of the present disclosure have been described above. However, the present disclosure is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present disclosure. It is.

(First modification)
In the second embodiment, an example in which the armature 43 and the connecting portion 34 are separated in the z direction in a state where the upper surface 44a of the suction valve 42 and the upper inner surface 11b of the plunger chamber 14 are separated in the z direction is shown. . However, when the upper surface 44a of the intake valve 42 and the upper inner surface 11b of the plunger chamber 14 are separated in the z direction, the intake valve 42 and the connecting portion 34 are separated in the z direction as shown in FIG. Can also be adopted.

  In the modification shown in FIG. 8, the stopper 46 is not formed on the suction valve 42. Instead, the end 45b in the first valve chamber 15 of the first column 45 of the suction valve 42 has a locally longer diameter than the others. The connecting portion 34 includes a third cylindrical portion 58 and a third annular portion 59 in addition to the second cylindrical portion 53 and the second annular portion 54.

  The 3rd cylinder part 58 comprises cylinder shape, and the axial direction is along az direction. The third annular portion 59 is annular as the name suggests, and is open in the z direction. The axial directions of the third cylindrical portion 58 and the third annular portion 59 coincide with the axial direction of the first column portion 45 in the specified plane. The third cylindrical portion 58 and the third annular portion 59 are a single piece. The outer diameter of the third annular portion 59 is the same as the inner diameter of the third cylindrical portion 58. The third annular portion 59 is provided in the lower opening of the two openings of the third tube portion 58. As a result, the upper opening area of the third cylindrical portion 58 is narrower than the lower opening area.

  As shown in FIG. 8, the end 45 b of the first column part 45 is provided in the hollow of the third cylinder part 58. A first column part 45 is provided in the hollow of the third annular part 59. The third annular portion 59 and the end portion 45b face each other in the z direction. In a state where the upper surface 44a of the suction valve 42 and the upper inner surface 11b of the plunger chamber 14 are separated in the z direction, the third annular portion 59 and the end portion 45b are separated from each other in the z direction.

  As described above, when electromagnetic force is generated in the pedestal portion 50 by energization of the drive current to the solenoid coil 33, the armature 43 moves upward alone until the third annular portion 59 and the end portion 45b come into contact with each other. By the single movement of the armature 43, the sealed state of the fuel storage chamber 56 is released. For this reason, similarly to the electromagnetic metering valve 30 described in the second embodiment, the sealed state of the fuel storage chamber 56 can be quickly released.

(Second modification)
As shown in FIG. 9, a configuration in which an auxiliary communication hole 17 h that assists communication between the fuel storage chamber 56 and the second valve chamber 55 is formed in the second body 17 may be employed. The auxiliary communication hole 17h promotes the fuel flow between the fuel storage chamber 56 and the second valve chamber 55. In the case of this modification, it is not necessary to form the second notch 52 a in the second pillar portion 52.

  The auxiliary communication hole 17h of the modified example shown in FIG. 9A is opened outside the region surrounded by the seal portion 17e on the outer upper surface 17d. The opening on the outer upper surface 17d of the auxiliary communication hole 17h is located between the seal portion 17e and the opening of the constant communication hole 17f. The auxiliary communication hole 17 h is provided with a check valve 64 that allows fuel to flow in one direction from the second valve chamber 55 to the fuel storage chamber 56. The check valve 64 is opened when the volume of the fuel storage chamber 56 is increased by the downward movement of the plunger 20 due to the rotation of the camshaft 300. Thereby, the inflow of the fuel to the fuel storage chamber 56 through the auxiliary communication hole 17h is promoted.

  The auxiliary communication hole 17h of the modified example shown in FIG. 9B opens on the upper surface of the seal portion 17e on the outer upper surface 17d. This also promotes the inflow of fuel into the fuel storage chamber 56 via the auxiliary communication hole 17h.

(Third Modification)
In the first embodiment, an example is shown in which three first notches 45a are formed in a portion where the first through hole 16c communicating with the fuel supply path 12 and the first valve chamber 15 in the first pillar portion 45 enters and exits. It was. Moreover, the example in which the 3rd notch 52a was formed in the site | part which enters / exits the 2nd through-hole 17c in the 2nd pillar part 52 was shown. However, the number of the first notches 45a and the second notches 52a is not limited to the above example. For example, a configuration in which four first cutouts 45a and four second cutouts 52a are formed may be employed. FIG. 10A shows a configuration in which four notches are formed at equal intervals in the circumferential direction around the z direction.

(Fourth modification)
As shown in FIG. 10B, a configuration in which a communication hole 16 d that connects the valve chamber 57 of the first valve chamber 15 and the fuel supply path 12 is formed in the first body 16 may be employed. This communication hole 16d eliminates the need to form the first notch 45a in the first pillar portion 45. In the modification shown in the column (b) of FIG. 10, four communication holes 16d are formed at equal intervals in the circumferential direction around the z direction.

DESCRIPTION OF SYMBOLS 10 ... Cylinder, 11b ... Upper inner surface, 12 ... Fuel supply path, 14 ... Plunger chamber, 15 ... 1st valve chamber, 16 ... 1st body, 16c ... 1st through-hole, 17 ... 2nd body, 17c ... 2nd Through hole, 17d ... outer upper surface, 17e ... seal part, 17f ... normal communication hole, 17h ... auxiliary communication hole, 20 ... plunger, 30 ... electromagnetic metering valve, 32 ... main spring, 33 ... solenoid coil, 34 ... connecting part , 35 ... sub spring, 42 ... suction valve, 43 ... armature, 44 ... first tip, 45 ... first pillar, 45b ... end, 50 ... pedestal, 51 ... second tip, 52 ... second. Column part, 55 ... 2nd valve chamber, 56 ... Fuel storage chamber, 57 ... Valve chamber, 61 ... Armature spring, 64 ... Check valve, 100 ... High-pressure fuel pump, 200 ... Fuel supply system

Claims (8)

An electromagnetic metering valve that controls communication between a plunger chamber (14) whose volume is changed by a plunger (20) sliding in the cylinder (10) and a fuel supply passage (12) for supplying fuel into the plunger chamber. There,
A suction valve (42) provided with a tip (44) in the plunger chamber;
A main spring (32) for applying an urging force toward the plunger chamber in the sliding direction of the plunger to the suction valve;
An armature (43) connected to an end (45b) opposite to the tip of the suction valve;
A coil (33) for applying an electromagnetic force in a direction away from the plunger chamber in the sliding direction to the armature by passing a magnetic field through the armature;
A connecting portion (34) for connecting an end portion of the suction valve and a tip (51) of the armature;
A fuel storage chamber (56) partially partitioned by the connecting portion,
In the sealed state in which the fuel is sealed in the fuel storage chamber, when the volume of the plunger chamber decreases due to the sliding of the plunger, the drag of the fuel in the fuel storage chamber toward the plunger chamber in the sliding direction Is provided to the suction valve via the connecting portion,
When the electromagnetic force is not applied to the armature by the coil, a wall surface (11b) that separates the tip of the intake valve and the plunger chamber by the drag force and the biasing force toward the plunger chamber in the sliding direction. ) Are separated in the sliding direction so that the plunger chamber and the fuel supply path communicate with each other,
When the electromagnetic force is applied to the armature by the coil, the sealed state of the fuel storage chamber is released by moving the armature in a direction away from the plunger chamber in the sliding direction, and the intake valve An electromagnetic metering valve in which a tip end and the wall surface defining the plunger chamber come into contact with each other so that the plunger chamber and the fuel supply path are not in communication. The connecting portion and the tip of the armature face each other in the sliding direction,
When the tip of the suction valve and the wall surface defining the plunger chamber are separated in the sliding direction, the connecting portion and the tip of the armature are separated in the sliding direction,
The electromagnetic force is applied to the armature by the coil, and the sealed state of the fuel storage chamber is released by the armature moving in a direction away from the plunger chamber in the sliding direction, and the connecting portion and the armature The electromagnetic metering valve according to claim 1, wherein the suction valve moves together with the armature in a direction away from the plunger chamber in the sliding direction.   The electromagnetic metering valve according to claim 2, further comprising an armature spring (61) that applies a force toward the plunger chamber in the sliding direction to the armature. The connecting portion and the end of the suction valve face each other in the sliding direction;
When the tip of the suction valve and the wall surface defining the plunger chamber are separated in the sliding direction, the connecting portion and the end of the suction valve are separated in the sliding direction,
The electromagnetic force is applied to the armature by the coil, and the sealed state of the fuel storage chamber is released by moving the armature in a direction away from the plunger chamber in the sliding direction, and the connection portion and the suction portion 2. The electromagnetic metering valve according to claim 1, wherein the suction valve moves in a direction away from the plunger chamber in the sliding direction together with the armature by contact with an end of the valve. An armature chamber (55) for accommodating the end (50) of the armature;
A wall (17) separating the armature chamber and the fuel storage chamber;
A through-hole (17c) formed in the wall portion for communicating the armature chamber and the fuel storage chamber and into which the central portion (52) of the armature is inserted;
An annular seal portion (17e) formed around the opening of the through hole in the upper surface (17d) of the wall portion on the armature chamber side,
The contact between the seal portion and the end portion of the armature is cut off from communication between the fuel storage chamber and the armature chamber via the through hole, and the end portion of the armature is separated from the seal portion. The electromagnetic metering valve according to claim 1, wherein the fuel storage chamber and the armature chamber communicate with each other through a through hole. An auxiliary communication hole (17h) for communicating the armature chamber and the fuel storage chamber is formed in the wall portion,
The auxiliary communication hole opens in the seal portion on the upper surface of the wall portion,
Communication between the fuel storage chamber and the armature chamber through the through hole and the auxiliary communication hole is blocked by contact between the seal portion and the end portion of the armature, and the end portion of the armature is separated from the seal portion. The electromagnetic metering valve according to claim 5, wherein the fuel storage chamber and the armature chamber are communicated with each other through the through hole and the auxiliary communication hole. An auxiliary communication hole (17h) for communicating the armature chamber and the fuel storage chamber is formed in the wall portion,
The auxiliary communication hole is provided with a check valve (64) for flowing the fuel in one direction from the armature chamber to the fuel storage chamber,
The electromagnetic metering valve according to claim 5, wherein the auxiliary communication hole is opened outside a region surrounded by the seal portion on the upper surface of the wall portion. A valve chamber (57) that houses an end of the intake valve and communicates with the fuel supply path;
A continuous communication hole (17f) for always communicating the armature chamber and the valve chamber;
The electromagnetic metering valve according to claim 5, wherein the constantly communicating hole is opened outside a region surrounded by the seal portion on the upper surface of the wall portion.

Images