JP2019065906A - Solenoid valve and high-pressure fuel pump - Google Patents

Abstract

To provide a solenoid valve capable of securing high movement responsiveness in valve body movement.SOLUTION: A stator 63 cooperates with an armature 64 to form a magnetic circuit C where magnetic flux M flows, thereby magnetically attracting the armature 64 to an upward direction Du of an axis direction. Consequently, the stator 63 comprises: a main core 630 arranged in the upward direction Du of the armature 64, and forming an axial gap Ga flowing the magnetic flux between itself and the armature 64, where the axial gap Ga contracts depending on movement of the armature 64 toward the upward direction Du; and a side core 631 arranged on a radial outward side of the armature 64, and forming a radial gap Gr flowing the magnetic flux M between itself and the armature 64, wherein the radial gap Gr expands depending on the movement of the armature 64 toward the upward direction Du.SELECTED DRAWING: Figure 6

Description

  The present disclosure relates to a solenoid valve and a high pressure fuel pump including the same.

  BACKGROUND Conventionally, solenoid valves provided with a valve body that reciprocates in the axial direction are widely known. This type of solenoid valve is utilized to open and close the suction passage, for example, in a high-pressure fuel pump which pressurizes the fuel sucked into the pressurizing chamber through the suction passage with a plunger and pumps the fuel to the supply destination.

  As a solenoid valve utilized by such a high pressure fuel pump etc., the thing of an indication is proposed to patent documents 1. As shown in FIG. The electromagnetic valve disclosed in Patent Document 1 includes a stationary core and a yoke together with a plunger rod, an anchor, a coil and a biasing spring.

  Specifically, in the electromagnetic valve disclosed in Patent Document 1, the magnetic circuit in which the magnetic flux generated by the coil flows when the energization is turned on under the condition that the biasing spring biases the anchor in the downward direction of the axial direction is fixed core And the yoke forms in conjunction with the anchor. As a result, the stationary core magnetically attracts the anchor in the upward direction out of the axial direction, whereby the plunger rod moves in the upward direction together with the anchor. On the other hand, the plunger rod moves in the lowering direction together with the anchor when the energization of the coil is turned off in a state where the biasing spring biases the anchor in the lowering direction.

JP, 2015-190532, A

  Now, in the electromagnetic valve disclosed in Patent Document 1, the fixed core disposed in the upward direction of the anchor is an axial gap which allows magnetic flux to flow between the anchor and the gap, and the gap decreases in response to the movement of the anchor in the upward direction. Form. On the other hand, the yoke disposed radially outward of the anchor forms a gap having a substantially constant width regardless of the movement of the anchor in the upward direction, as a radial gap through which magnetic flux flows with the anchor. doing.

  Under such a configuration, in the electromagnetic valve disclosed in Patent Document 1, the magnetic resistance decreases in the axial gap due to the reduction according to the anchor movement in the upward direction, and the magnetic flux easily flows. At this time, in the radial gap which is substantially constant regardless of the movement of the anchor in the upward direction, the change in magnetic resistance is suppressed, so the magnetic attraction force to the anchor becomes too large following the magnetic flux density in the entire magnetic circuit. In this case, at the moving end in the upward direction, the magnetic attraction force holding the anchor (hereinafter referred to as the retention suction force) becomes too large. As a result, the magnetic flux disappears from the deenergization, and a considerable delay occurs in the time for the plunger and the anchor to start to move in the downward direction. That is, the movement response deteriorates in the anchor movement in the downward direction.

  In view of the above, it is an object of the present disclosure to provide a solenoid valve and a high pressure fuel pump that ensure high movement response in valve body movement.

  Hereinafter, technical means of the present disclosure for achieving the object will be described. Note that reference numerals in parentheses in the claims and in this section indicate the correspondence with specific means described in the embodiments described in detail later, and the technical scope of the present disclosure is limited. It is not something to do.

The first aspect of the present disclosure is
A solenoid coil (670) that generates a magnetic flux (M) by turning on electricity;
An axially reciprocating valve body (62);
An armature (64, 2064) that reciprocates with the valve body,
A stator (63, 2063) that magnetically attracts the armature in the upward direction (Du) in the axial direction by forming a magnetic circuit (C) in which magnetic flux flows in cooperation with the armature;
An electromagnetic valve (60, 2060) comprising: an elastic member (65) for urging the armature in the downward direction (Dd) of the axial direction,
The stator is
A main core (630) disposed in the ascending direction of the armature, forming an axial gap (Ga) which allows magnetic flux to flow between the armature and the axial gap which is reduced according to the movement of the armature in the upward direction;
Side cores (631, 2631) which are disposed radially outside the armature and form a radial gap which is expanded according to the movement of the armature in the upward direction as a radial gap (Gr) for flowing a magnetic flux between the armature and the armature. And a solenoid valve.

  In such a first aspect, when the solenoid coil generates a magnetic flux due to the energization, the magnetic resistance decreases and the magnetic flux easily flows in the axial gap which is reduced according to the armature movement in the upward direction. At this time, in the radial gap that expands according to the armature movement in the upward direction, the magnetic resistance increases and the magnetic flux is difficult to flow, so the magnetic attraction force to the armature follows the magnetic flux density in the entire magnetic circuit and becomes large. It can be relieved that it becomes too much. Therefore, at the moving end in the upward direction, it can be mitigated that the holding suction force to the armature becomes too large. According to this, it is difficult to cause a large delay in the time until the magnetic flux disappears from the power-off and the armature and the valve start to move in the downward direction, so high movement in the valve body movement in the downward direction It becomes possible to secure responsiveness.

Moreover, the second aspect of the present disclosure is
A solenoid coil (670) that generates a magnetic flux (M) by turning on electricity;
An axially reciprocating valve body (62);
An armature (64) that reciprocates with the valve body;
A stator (3063) that magnetically attracts the armature in the upward direction (Du) in the axial direction by forming a magnetic circuit (C) in which magnetic flux flows in cooperation with the armature;
And an elastic member (65) for biasing the armature in the downward direction (Dd) of the axial direction, the electromagnetic valve (3060) comprising:
The stator is
A main core (630) disposed in the ascending direction of the armature, forming an axial gap (Ga) which allows magnetic flux to flow between the armature and the axial gap which is reduced according to the movement of the armature in the upward direction;
A side core (3631) is provided, which is disposed radially outward of the armature and forms a radial gap (Gr) for flowing a magnetic flux with the armature, and in which the magnetic resistance to the magnetic flux increases in the upward direction. Is a solenoid valve.

  In such a second aspect, when the solenoid coil generates a magnetic flux due to the energization, the magnetic resistance decreases and the magnetic flux easily flows in the axial gap which is reduced according to the armature movement in the upward direction. At this time, the magnetic resistance of the side core increases in the upward direction, and in the radial gap, it becomes difficult for the magnetic flux to flow in accordance with the movement of the armature in the upward direction Du. It can be mitigated that it becomes too large following the overall magnetic flux density. Therefore, at the moving end in the upward direction, it can be mitigated that the holding suction force to the armature becomes too large. According to this, it is difficult to cause a large delay in the time until the magnetic flux disappears from the power-off and the armature and the valve start to move in the downward direction, so high movement in the valve body movement in the downward direction It becomes possible to secure responsiveness.

Furthermore, the third aspect of the present disclosure is
A high pressure fuel pump (10, 2010, 3010) which pressurizes fuel sucked into a pressurizing chamber (202a) through a suction passage (204) by a plunger (402) and pressure-feeds it to a supply destination (6),
A pump body (20) which forms a suction passage and a pressure chamber and slidably supports a plunger;
The solenoid valve according to the first or second aspect mounted on the pump body, wherein the suction passage is opened by the movement of the valve body in the suction stroke in which the plunger is driven toward the side for sucking the fuel into the pressure chamber And a solenoid valve (60, 2060, 3060) for closing the suction passage by the movement of the valve body in the pumping stroke in which the plunger is driven toward the fuel pumping side of the pressurizing chamber. It is a high pressure fuel pump.

  According to such a third aspect, it is possible to secure high movement responsiveness in the downward movement of the valve body according to the principle described in the first aspect or the second aspect. Therefore, according to the third aspect, since the intake passage is opened or closed by moving the valve in the downward direction in the high pressure fuel pump, high valve opening responsiveness or valve closing response is achieved by the valve moving. It will also be possible.

FIG. 1 is a block diagram showing a fuel supply system of an internal combustion engine to which a high pressure fuel pump according to a first embodiment is applied. It is a block diagram which shows the high pressure fuel pump by 1st embodiment. It is an operation figure showing operation of a high pressure fuel pump by a first embodiment. It is a sectional view expanding and showing an electromagnetic valve by a first embodiment. It is a schematic diagram which shows the solenoid valve by 1st embodiment. It is a schematic diagram which shows the operating state different from FIG. It is a schematic diagram which shows the operating state different from FIG. It is a graph for demonstrating the action | operation of the solenoid valve by 1st embodiment. It is a schematic diagram which shows the solenoid valve by 2nd embodiment. It is a schematic diagram which shows the operating state different from FIG. It is a schematic diagram which shows an operating state different from FIG. It is a schematic diagram which shows the solenoid valve by 3rd embodiment. It is a schematic diagram which shows the operating state different from FIG. It is a schematic diagram which shows the operating state different from FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG. It is a schematic diagram which shows the modification of FIG.

  Hereinafter, a plurality of embodiments will be described based on the drawings. In addition, the overlapping description may be abbreviate | omitted by attaching the same code | symbol to the corresponding component in each embodiment. When only a part of the configuration is described in each embodiment, the configuration of the other embodiments described above can be applied to other parts of the configuration. Further, not only the combination of the configurations explicitly described in the description of the respective embodiments but also the configurations of the plurality of embodiments can be partially combined with each other even if the combination is not specified unless any trouble occurs in the combination.

First Embodiment
As shown in FIGS. 1 and 2, the high pressure fuel pump 10 according to the first embodiment is applied to a fuel supply system 2 of an internal combustion engine 1 mounted on a vehicle. The fuel supply system 2 supplies a fuel oil as a fuel to a diesel engine as the internal combustion engine 1. The fuel tank 3, the low pressure fuel pump 4, the low pressure filter 5, the high pressure fuel pump 10, the common rail 6, the fuel injection valve 7 and An ECU (Electronic Control Unit) 8 is included.

  The fuel tank 3 stores fuel supplied to the internal combustion engine 1. The low pressure fuel pump 4 is an electric pump operated by energization in the present embodiment. The low pressure fuel pump 4 sucks the fuel in the fuel tank 3. The low pressure fuel pump 4 pressurizes the drawn fuel to a predetermined low pressure value (for example, about 0.4 MPa) and discharges the discharged fuel to the high pressure fuel pump 10 outside the fuel tank 3. The low pressure filter 5 filters the pressurized fuel of the low pressure fuel pump 4 at an internal filter element. Thus, the low pressure filter 5 collects foreign matter mixed in the fuel from the inside of the fuel tank 3 to itself.

  The high pressure fuel pump 10 is a mechanical pump that operates by receiving a crank torque from a crankshaft 1 a of the internal combustion engine 1. The high pressure fuel pump 10 sucks in the fuel pressure-fed from the external low pressure fuel pump 4 and filtered by the low pressure filter 5. The high pressure fuel pump 10 pressurizes the drawn fuel to a predetermined high pressure value (for example, about 250 MPa) and discharges the discharged fuel to the common rail 6 as a supply destination. The high pressure fuel pump 10 controls the adjustment operation of the fuel pumping amount (i.e., the fuel discharge amount) by energizing the built-in solenoid valve 60.

  As shown in FIG. 1, the common rail 6 holds the pressurized fuel of the high-pressure fuel pump 10 in an accumulated state in an internal pressure accumulation chamber. One fuel injection valve 7 is provided for each of the plurality of cylinders 1 b of the internal combustion engine 1. Fuel is distributed to each fuel injection valve 7 from the common rail 6. Each fuel injection valve 7 operates by energization to inject fuel into the combustion chamber in the corresponding cylinder 1 b.

  The ECU 8 is mainly composed of a microcomputer. The ECU 8 is connected to the low pressure fuel pump 4, the solenoid valve 60 of the high pressure fuel pump 10, and the fuel injection valves 7. The ECU 8 controls the operation of the connection targets 4, 60 and 7.

  The high pressure fuel pump 10 applied to such a fuel supply system 2 includes a pump body 20, a drive cam 30, a movable portion 40, a discharge valve 50, and a solenoid valve 60, as shown in detail in FIG. . The pump body 20 is formed by combining a casing 20a, a cover 20b and a cylinder 20c.

  The casing 20a is formed of a metal material in a hollow block shape. The casing 20 a forms a cam storage chamber 200 and a tappet storage chamber 201. The cam storage chamber 200 has a cylindrical hole shape. The tappet storage chamber 201 has a cylindrical hole shape substantially perpendicular to the central axis of the cam storage chamber 200. The tappet storage chamber 201 extends from the outer peripheral portion of the cam storage chamber 200 to the outer surface of the casing 20 a.

  The cover 20 b is formed in a cylindrical shape by a metal material. The cover 20 b covers the same chamber 200 by being coaxially inserted into the cam storage chamber 200. The cylinder 20c is formed of a metal material in a penetrating cylindrical shape. The cylinder 20 c is coaxially inserted into the tappet storage chamber 201 to cover the chamber 201 on the opposite side of the cam storage chamber 200.

  The cylinder 20 c forms a slide hole 202 and a mounting hole 203. The slide hole 202 and the mounting hole 203 have a cylindrical hole shape substantially perpendicular to and coaxial with the central axis of the cam housing 200. The slide hole 202 extends in the cylinder 20 c from the end surface on the cam storage chamber 200 side to the opposite side. A portion of the slide hole 202 opposite to the cam storage chamber 200 functions as a pressure chamber 202a. The mounting hole 203 extends from the sliding hole 202 to the end surface of the cylinder 20 c opposite to the cam housing 200.

  In such a pump body 20, a suction passage 204 and a discharge passage 206 are formed. The suction passage 204 penetrates at least the cylinder 20c of the pump body 20 to connect between the external low pressure filter 5 (see FIG. 1) and the internal pressure chamber 202a via the mounting hole 203. ing. The discharge passage 206 penetrates the cylinder 20c to connect the internal pressure chamber 202a and the external common rail 6 (see FIG. 1).

  The drive cam 30 is formed in a cylindrical shape by a metal material. The drive cam 30 is coaxially accommodated in the cam accommodation chamber 200. The drive cam 30 is rotationally driven around its own central axis by receiving a crank torque from the crankshaft 1a (see FIG. 1) of the internal combustion engine 1 to the drive shaft 300 penetrating the cover 20b. The drive cam 30 is formed in the shape of a plate cam having an oval-shaped contour curve on the outer peripheral surface, in consideration of, for example, the number of cylinders of the internal combustion engine 1 and the reduction ratio with the crankshaft 1a.

  The movable portion 40 includes a roller 400, a tappet 401, a plunger 402, a spring seat 403, an urging spring 404, and the like. All of the components of the movable portion 40 are formed of a metal material. Here, the plunger 402 among the components of the movable portion 40 is accommodated from the tappet accommodating chamber 201 to the sliding hole 202. On the other hand, the components other than the plunger 402 among the components of the movable portion 40 are accommodated in the tappet accommodation chamber 201.

  The roller 400 has a cylindrical shape substantially parallel to the central axis of the drive cam 30 and substantially perpendicular to the central axis of the tappet storage chamber 201. The roller 400 is in rolling contact with the outer peripheral surface of the drive cam 30 in a line contact state along the central axis of the drive cam 30.

  The tappet 401 has a generally cylindrical shape through jointing of two members. The tappet 401 is provided substantially orthogonal to the central axis of the drive cam 30. The tappet 401 is coaxially slidably supported by the inner peripheral surface of the tappet storage chamber 201, and is thus reciprocated in the axial direction. The tappet 401 holds the roller 400 so as to be able to roll and integrally reciprocate.

  The plunger 402 is in the shape of a small-diameter elongated cylindrical rod. The plunger 402 is provided substantially orthogonal to the central axis of the drive cam 30. The plunger 402 is coaxially slidably supported by the inner circumferential surface of the sliding hole 202, and is thus reciprocated in the axial direction. The plunger 402 is coupled to the tappet 401 via a spring seat 403 by entering into the peripheral wall portion of the tappet 401. The plunger 402 divides the pressure chamber 202 a on the opposite side of the slide hole 202 from the tappet 401.

  The spring seat 403 is held by the tappet 401 so as to be capable of integrally reciprocating. The biasing spring 404 is a compression coil spring, and is coaxially sandwiched between the cylinder 20 c and the spring seat 403. The biasing spring 404, which is in an elastically deformed state at this sandwiching point, presses the roller 400 against the outer peripheral surface of the drive cam 30 via the spring seat 403 and the tappet 401. Thus, the plunger 402 is reciprocally driven in accordance with the rotation of the crankshaft 1 a (see FIG. 1) in the internal combustion engine 1.

  Specifically, the plunger 402 in the suction stroke is driven toward the side that sucks the fuel into the pressure chamber 202a according to the rotation of the drive cam 30, thereby lowering between the top dead center and the bottom dead center. Do. On the other hand, the plunger 402 in the pumping stroke is driven toward the pressure-feeding side of the fuel in the pressurizing chamber 202a according to the rotation of the drive cam 30, and thereby rises between the bottom dead center and the top dead center.

  The discharge valve 50 is a mechanically operated check valve. The discharge valve 50 is installed in the middle of the discharge passage 206. When the pressure of the fuel in the pressurizing chamber 202 a becomes the valve opening pressure in the pressure feeding process, the discharge valve 50 is opened to discharge the fuel to the discharge passage 206, thereby pressure-feeding the discharged fuel to the common rail 6.

  The solenoid valve 60 has a cylindrical shape as a whole. The solenoid valve 60 is installed in the mounting hole 203 and thus installed in the middle of the suction passage 204. The solenoid valve 60 is a normally open control valve in the present embodiment, and operates in accordance with energization control from the ECU 8 (see FIG. 1).

  Specifically, the solenoid valve 60 incorporates a solenoid coil 670. In the solenoid valve 60, the suction passage 204 is opened by deenergizing the solenoid coil 670 from the ECU 8, thereby opening the space between the external low pressure filter 5 (see FIG. 1) and the internal pressurizing chamber 202a. On the other hand, in the solenoid valve 60, the suction passage 204 is closed by turning on the energization from the ECU 8 to the solenoid coil 670, thereby shutting off the low pressure filter 5 and the pressurizing chamber 202a.

  The operation of the high pressure fuel pump 10 configured as described above will be described. As the internal combustion engine 1 starts in the vehicle, the energization control by the ECU 8 is started for the high pressure fuel pump 10 together with the low pressure fuel pump 4 and the solenoid valve 60. The high-pressure fuel pump 10 alternately and continuously executes the suction stroke and the pumping stroke shown in FIG. 3 according to the energization control thus started.

  First, in the suction stroke shown in FIGS. 3 (a) and 3 (b), the conduction current from the ECU 8 is controlled to a zero value (see FIG. 8 (a)), so that the conduction is turned off. Continuously opens the suction passage 204. As a result, during the suction stroke, the plunger 402 is driven to move downward, whereby fuel is drawn into the pressure chamber 202a through the suction passage 204.

  Subsequently, in the pre-stroke period shown in FIG. 3C in the pressure-feeding process, the conduction current from the ECU 8 is controlled to a zero value (see FIG. 8A), so that the conduction is turned off. The solenoid valve 60 opens the suction passage 204 continuously from the previous suction stroke. At this time, in the present embodiment, the degree of valve opening is adjusted by the electromagnetic valve 60 to substantially the same degree as in the case of the suction stroke. As a result, during the pre-stroke period, the plunger 402 is driven and ascends, whereby the fuel in the pressurizing chamber 202 a is pressed by the plunger 402. At this time, the fuel pressed by the plunger 402 is returned from the pressure chamber 202a to the suction passage 204.

  Subsequently, during the pressurization period shown in FIGS. 3D and 3E in the pressure-feeding process, the energization current from the ECU 8 is controlled to the set current I (see FIG. 8A), thereby performing energization. Is turned on, the solenoid valve 60 closes the suction passage 204. As a result, during the pressurization period, the fuel return from the pressurization chamber 202a to the suction passage 204 is stopped. At this time, when the fuel pressed by the plunger 402 is pressurized to the valve opening pressure of the discharge valve 50, the fuel is discharged from the pressurizing chamber 202a to the discharge passage 206 to pressure-feed the common rail 6 (see FIG. 1). Be done. After this, the next suction stroke is performed.

(Detailed configuration of solenoid valve)
Next, the detailed configuration of the solenoid valve 60 will be described. As shown in FIG. 4, the solenoid valve 60 includes a valve body 61, a valve body 62, a stator 63, an armature 64, elastic members 65 and 66, and a valve drive unit 67.

  The valve body 61 is formed by combining the mounting member 610 and the valve seat member 611. The mounting member 610 is formed of a metal material in a penetrating cylindrical shape. The mounting member 610 is mounted on the cylinder 20 c of the pump body 20 by being screwed coaxially into the mounting hole 203. The valve seat member 611 is formed in a penetrating cylindrical shape by a metal material. The valve seat member 611 is mounted on the cylinder 20 c by coaxially fitting the mounting hole 203 between the sliding hole 202 and the mounting member 610. The valve seat member 611 has a valve seat surface 611 a exposed to the pressurizing chamber 202 a at the end on the sliding hole 202 side. At the same time, the valve seat member 611 forms an in-valve passage portion 204 a which is a part of the suction passage 204, straddling the valve seat surface 611 a from the outer peripheral surface 611 b exposed to the mounting hole 203.

  The valve body 62 is formed by combining the relay member 620, the bush member 622, and the opening / closing member 621. The relay member 620 is formed of a metal material into an elongated cylindrical rod shape. The relay member 620 is coaxially slidably supported by the inner circumferential surface of the mounting member 610, and is thus reciprocated in the axial direction. The relay member 620 reciprocates integrally with the opening / closing member 621 and the armature 64 while being coaxially held between the opening / closing member 621 and the armature 64 by the action (detailed later) of the elastic members 65 and 66. The bush member 622 is formed of a metal material in a penetrating cylindrical shape. The bush member 622 is coaxially externally fitted to the outer peripheral surface of the relay member 620, and is thereby held integrally reciprocably movable by the same member 620. The opening and closing member 621 is formed of a metal material in the shape of an elongated cylindrical rod. The opening / closing member 621 is coaxially slidably supported by the inner circumferential surface of the valve seat member 611, and is thus reciprocably disposed in the axial direction. The opening and closing member 621 has a flange-like valve portion 621 a at an end projecting from the inside of the valve seat member 611 to the pressure chamber 202 a outside.

  The opening / closing member 621 moves integrally with the relay member 620 and the bush member 622 in the upward direction Du of the axial direction to move the valve at the moving end E in the same direction Du (see FIGS. 7 and 8 described later). The portion 621a is seated on (that is, brought into contact with) the valve seat surface 611a. Thus, the suction passage 204 is closed. In the following, the movement of the open / close member 621 integrally with the relay member 620 and the bush member 622 in the upward direction Du will be described as the movement of the valve body 62 in the upward direction Du.

  On the other hand, the opening / closing member 621 moves integrally with the relay member 620 and the bush member 622 from the moving end E in the raising direction Du in the lowering direction Dd in the axial direction, as shown in FIG. Is separated from the valve seat surface 611a. Thus, the suction passage 204 is opened. In the following, the movement of the opening / closing member 621 integrally with the relay member 620 and the bush member 622 in the downward direction Dd will be described as the movement of the valve body 62 in the downward direction Dd.

  The stator 63 is fixed to the mounting member 610 of the valve body 61 outside the pump body 20. The stator 63 is provided with a main core 630, a side core 631 and a collar 632.

  As shown in FIGS. 4 to 7, the main core 630 is formed in a bottomed cylindrical shape from a metallic magnetic material. The main core 630 is made of, for example, a high BH material or the like so as to make a unique magnetic flux density appear with respect to the magnetic flux M generated by turning on the solenoid coil 670. As shown in FIG. 4, the main core 630 is indirectly and coaxially held by the mounting member 610 via the side core 631 and the collar 632. The main core 630 is provided with an opening facing the mounting member 610 side.

  As shown in FIGS. 4 to 7, the side core 631 is formed in a penetrating cylindrical shape by a metal magnetic material. The side core 631 is made of, for example, a high BH material or the like so as to cause a unique magnetic flux density to appear with respect to the magnetic flux M generated when the solenoid coil 670 is energized. The side core 631 is directly and coaxially held by the mounting member 610. As shown in FIG. 4, the side cores 631 are provided apart from the main core 630 in the lowering direction Dd on the mounting member 610 side. Here, the separation distance in the axial direction of the side core 631 from the main core 630 is set larger than the maximum width of each of the gaps Ga and Gr described later in detail.

  As shown in FIGS. 5 to 7, the side core 631 has an inner diameter changing portion 633 on the inner circumferential surface 631 a. The inner diameter changing portion 633 is provided on the inner peripheral surface 631 a of the side core 631 so as to extend between the axial end portions, and the inner diameter is expanded, ie, expanded in the rising direction Du. Here, in particular, the inner diameter changing portion 633 has a tapered shape (i.e., a conical shape) in which the diameter gradually increases toward the rising direction Du in the entire inner peripheral surface 631a of the side core 631. In the inner diameter changing portion 633, the rate of change in diameter in the axial direction is set substantially constant throughout the inner peripheral surface 631a of the side core 631.

  Thus, the inner diameter changing portion 633 is a point Po located at least radially outward of the end 64b of the lowering direction Dd of the armature 64 which reaches the moving end E (see FIG. 7) of the side cores 631 in the rising direction Du. From this point, the diameter gradually decreases in the downward direction Dd. Here, in particular, the inner diameter changing portion 633 gradually reduces the diameter in the lowering direction Dd from the end portion 631 c beyond the point Po in the rising direction Du in the side core 631. Note that the outer diameter 631 b of the side core 631 is given an outer diameter that gradually decreases in the upward direction Du. Thus, in the side cores 631, the radial thickness is reduced in the upward direction Du.

  The collar 632 is formed in a penetrating cylindrical shape by a metal nonmagnetic material. The collar 632 is coaxially sandwiched between the elements 630 and 631 by being joined to the main core 630 and the side core 631. The collar 632 regulates a short circuit between the main core 630 and the side core 631 due to the magnetic flux M generated when the solenoid coil 670 is energized. An inner diameter is given to the inner circumferential surface 632 a of the collar 632 so as to have substantially the same diameter as the maximum diameter of the inner diameter changing portion 633 of the side core 631 and a substantially constant diameter throughout the axial direction.

  The armature 64 is formed of a metallic magnetic material in a penetrating cylindrical shape (see FIG. 4). The armature 64 is made of, for example, a high BH material or the like so as to make a unique magnetic flux density appear with respect to the magnetic flux M generated by turning on the solenoid coil 670. An outer diameter is given to the outer peripheral surface 64 a of the armature 64 so as to have a substantially constant diameter less than the maximum diameter of the inner diameter changing portion 633 and in the entire axial direction. The armature 64 is disposed so as to reciprocate in the axial direction by being loosely inserted coaxially from inside the side core 631 to inside the collar 632. As shown in FIG. 4, the relay member 620 of the valve body 62 is coaxially fitted in the armature 64 so as to be capable of integral reciprocating movement. Thereby, the armature 64 which realizes the reciprocating movement to each direction Du and Dd with the valve body 62 is constructed.

  As shown in FIGS. 5 to 7, the armature 64 axially faces the main core 630 disposed in the upward direction Du of the armature 64. As a result, the main core 630 forms an axial gap Ga with the armature 64. The axial width Wa of the axial gap Ga tends to shrink in accordance with the movement of the armature 64 in the upward direction Du. As a result, at the moving end E in the upward direction Du where the valve portion 621a is seated on the valve seat surface 611a (see FIG. 7) as described above, the amount of protrusion of the armature 64 in the upward direction Du from the end 631c of the side core 631 Becomes maximum, the axial width Wa of the axial gap Ga becomes the minimum width at all movement positions. In such an axial gap Ga, a magnetic flux M generated by turning on the solenoid coil 670 flows between the armature 64 and the main core 630.

  The armature 64 axially overlaps with the side core 631 disposed radially outward of the armature 64. Thus, the side core 631 forms a radial gap Gr between the inner diameter changing portion 633 of the inner peripheral surface 631a of the side core 631 and the outer peripheral surface 64a of the armature 64. As the radial width of the radial gap Gr, the narrowest width Wr at which the end 64b in the lowering direction Dd of the armature 64 is spaced from the inner diameter changing portion 633 at each movement position follows the above-described shape of the changing portion 633. Thus, the expansion tendency is shown according to the movement of the armature 64 in the upward direction Du.

  As a result of such expansion tendency, at the moving end E in the upward direction Du (see FIG. 7), the amount of protrusion of the armature 64 in the upward direction Du is greater than that of the end 631 c of the side core 631. The narrowest width Wr at each movement position of the gap Gr is the maximum width at all the movement positions. In such a radial gap Gr, a magnetic flux M generated by turning on the solenoid coil 670 flows between the armature 64 and the side core 631.

  As shown in FIGS. 4 to 7, the first elastic member 65 is a compression coil spring formed of a metal material. The first elastic member 65 is provided straddling the radially inner side of each component 630, 631, 632 in the stator 63. The first elastic member 65 is coaxially held between the bottom wall of the main core 630 of the stator 63 and the recess of the armature 64. Thus, the first elastic member 65 biases the armature 64 in the lowering direction Dd.

  As shown in FIG. 4, the second elastic member 66 is a compression coil spring formed of a metal material. The second elastic member 66 is provided straddling the inner side in the radial direction of each component 610, 611 in the valve body 61. The second elastic member 66 is coaxially held between the recess of the valve seat member 611 of the valve body 61 and the flange portion of the bush member 622 of the valve body 62. Thereby, the second elastic member 66 biases the valve body 62 in the upward direction Du. Here, the biasing force of the armature 64 in the downward direction Dd by the first elastic member 65 is greater than the biasing force of the valve body 62 in the upward direction Du by the second elastic member 66. It is adjusted so that it always becomes large at each movement position.

  The valve driving portion 67 is fixed to the mounting member 610 of the valve body 61 via the stator 63 outside the pump body 20. The valve drive unit 67 is formed by combining a solenoid coil 670, a magnetic yoke 671 and a connector 672.

  The solenoid coil 670 is formed in a state in which a metal wire is wound around a resin bobbin 670a. The solenoid coil 670 is provided straddling the radially outer side of each component 630, 631, 632 in the stator 63. The solenoid coil 670 is disposed coaxially with each component 630, 631, 632 of the stator 63 and the armature 64.

  The magnetic yoke 671 has a penetrating cylindrical shape as a whole by the joint of two members 671a and 671b formed of a metallic magnetic material. The magnetic yoke 671 is attached to the resin bobbin 670 a to cover the solenoid coil 670 from the outer side in the radial direction.

  The connector 672 is formed in a state in which the metal terminal 672 b is embedded in the resin body 672 a. The resin body 672 a protrudes outward in the radial direction of the solenoid coil 670 by being attached to the resin bobbin 670 a. The metal terminal 672b connects between the metal wire of the solenoid coil 670 and the ECU 8 (see FIG. 1) so as to be electrically conductive through a wire harness (not shown) assembled to the resin body 672a. Thereby, the solenoid coil 670 is excited by the ECU 8 turning on the energization, while the solenoid coil 670 is demagnetized by the ECU 8 turning off the energization.

  Under such a configuration, when energization is turned on by the ECU 8 and the solenoid coil 670 is excited, as shown in FIGS. 6 and 7, the magnetic circuit C in which the generated magnetic flux M of the coil 670 flows, the stator 63 includes the armature 64 and the magnetic yoke 671 ( Form in collaboration with Figure 4). At this time, in particular, between the main core 630 and the side core 631 of the stator 63, the magnetic circuit C is formed such that the magnetic flux M passes through the radial gap Gr, the armature 64 and the axial gap Ga. As a result, the magnetic attraction force F for magnetically attracting the armature 64 by the main core 630 is, as shown in FIGS. 8A and 8B, the magnetic flux in the entire magnetic circuit C from the timing Ton at which energization is started. It will gradually increase following the density. As a result, as shown in FIGS. 8B and 8C, the armature 64 moves upward together with the valve body 62 from the timing Tu at which the gradually increased magnetic attraction force F exceeds the combined biasing force of the elastic members 65 and 66. Start moving to

  Here, as shown in FIGS. 6 and 7, in the axial gap Ga in which the axial width Wa is reduced according to the movement of the armature 64 in the upward direction Du, the magnetic resistance decreases and the magnetic flux M easily flows. On the other hand, in the radial gap Gr where the narrowest width Wr is expanded according to the movement of the armature 64 in the upward direction Du, the magnetic resistance increases and the magnetic flux M becomes difficult to flow. Therefore, although the magnetic flux density in the entire magnetic circuit C gradually increases due to the decrease in the magnetic resistance (the flowability of the magnetic flux M) in the axial gap Ga according to the movement of the armature 64 in the upward direction Du, Due to the increase in the reluctance (the difficulty of flowing the magnetic flux M) at the radial gap Gr, the time rate of increase of the magnetic flux density is reduced compared to the prior art.

  As described above, as shown in FIG. 8B, although the magnetic attraction force F gradually increases according to the movement of the armature 64 in the upward direction Du, the magnetic attraction force F does not become too large compared to the prior art. Therefore, as shown in FIGS. 8B and 8C, at the moving end E in the upward direction Du, the holding attraction force Fh as the magnetic attraction force F for holding the armature 64 is also large compared to the prior art. Not too much. Here, as shown in FIGS. 8A to 8C, from the timing Toff when the energization is turned off by the ECU 8, the solenoid coil 670 is demagnetized and the magnetic flux M disappears, so that the magnetic attraction force F is each elastic member. When the combined biasing force of 65 and 66 falls below, the armature 64 starts to move in the downward direction Dd together with the valve body 62 at timing Td. At this time, in the first embodiment in which the holding attraction force Fh is not too large, the time Δt until the timing Td when the magnetic flux M disappears from the energization and the armature 64 starts moving in the downward direction Dd is the prior art. Compared to the

  The solid line graphs in FIGS. 8A, 8B, and 8C described above indicate the case of the first embodiment. On the other hand, the double-dotted line graphs in FIGS. 8B and 8C show the case of the prior art in which the radial gap has a substantially constant width regardless of the anchor movement corresponding to the armature movement as described above. . Further, in FIG. 8C, the movement amount of the armature 64 indicates the movement amount in the upward direction Du starting from the moving end in the downward direction Dd.

(Action effect)
Hereinafter, the operation and effect according to the first embodiment will be described.

  In the first embodiment, when the solenoid coil 670 generates the magnetic flux M by turning on the energization, the magnetic resistance M decreases and the magnetic flux M flows in the axial gap Ga which is reduced according to the movement of the armature 64 in the upward direction Du. It will be easier. At this time, in the radial gap Gr that expands according to the movement of the armature 64 in the upward direction Du, the magnetic resistance increases and the magnetic flux M does not easily flow, so the magnetic attraction force F to the armature 64 in the entire magnetic circuit C. Can be mitigated to follow the magnetic flux density of Therefore, at the moving end E in the upward direction Du, it can be relaxed that the holding suction force Fh on the armature 64 becomes too large. According to this, it is difficult to cause a large delay in the time Δt until the magnetic flux M disappears from the energization and the armature 64 and the armature 64 start to move in the downward direction Dd. It is possible to ensure high movement responsiveness in the movement of the valve body 62.

  Further, according to the first embodiment, the magnetic flux density of the magnetic circuit C is increased according to the movement of the armature 64 in the upward direction Du. According to this, while maintaining the magnetic flux density necessary for the magnetic attraction of the armature 64 as the magnetic flux density in the entire magnetic circuit C, the radial gap Gr is that the magnetic attraction force F including the holding attraction force Fh becomes too large. It can be relieved by the increase in magnetic resistance at Therefore, it is possible to secure not only high movement responsiveness in movement of the valve body 62 in the downward direction Dd but also high movement responsiveness in movement of the valve body 62 in the upward direction Du.

  Furthermore, according to the first embodiment, the inner diameter changing portion 633 expanded in the rising direction Du on the inner circumferential surface 631a of the side core 631 expands in the radial direction according to the movement of the armature 64 in the rising direction Du. A gap Gr may be formed between armatures 64. According to this, it is suppressed that the magnetic attraction force F including the holding attraction force Fh becomes too large following the magnetic flux density in the entire magnetic circuit C, and a high movement response in the movement of the valve body 62 in the descent direction Dd It becomes possible to secure the

  Furthermore, according to the first embodiment, the inner diameter changing portion 633 having a tapered shape in which the diameter gradually increases toward the rising direction Du on the inner circumferential surface 631a of the side core 631 corresponds to the movement of the armature 64 in the rising direction Du. A radially expanding radial gap Gr may be formed. According to this, it is possible to gently suppress that the magnetic attraction force F including the holding attraction force Fh becomes too large following the magnetic flux density in the entire magnetic circuit C, so that the valve body 62 in the upward direction Du It is possible to secure high movement response in the movement of the valve body 62 in the downward direction Dd while facilitating the movement.

  In addition, according to the first embodiment, the side core 631 descends from a point Po located at least radially outward with respect to the end 64 b of the lowering direction Dd of the armature 64 that reaches the moving end E in the upward direction Du. The inner diameter changing portion 633 reduced in diameter toward the direction Dd can form the radial gap Gr with the maximum width at the moving end E. Thereby, at the moving end E in the upward direction Du, the movement of the valve disc 62 in the downward direction Dd can be reliably mitigated because the magnetic attraction force Fh becomes too large following the magnetic flux density in the entire magnetic circuit C. The reliability of the effect of ensuring high mobility can be improved.

  In addition, according to the first embodiment, the magnetic flux M passes through the radial gap Gr, the armature 64, and the axial gap Ga without a short circuit between the main core 630 and the side core 631 separated in the descent direction Dd. As a result, the magnetic circuit C is easily formed. According to this, while maintaining the magnetic flux density necessary for the magnetic attraction of the armature 64 as the magnetic flux density in the entire magnetic circuit C, the radial gap Gr is that the magnetic attraction force F including the holding attraction force Fh becomes too large. It can be relieved by the increase in magnetic resistance at Therefore, it is possible to secure not only high movement responsiveness in movement of the valve body 62 in the downward direction Dd but also high movement responsiveness in movement of the valve body 62 in the upward direction Du.

  Furthermore, according to the first embodiment, it is possible to ensure high movement responsiveness in the movement of the valve body 62 in the downward direction Dd according to the principle described above. Therefore, according to the first embodiment, since the suction passage 204 is opened by the movement of the valve body 62 in the downward direction Dd in the high pressure fuel pump 10, it is possible to achieve high valve opening responsiveness by the movement. It becomes. Here, in the high pressure fuel pump 10 of the first embodiment in which the plunger 402 is driven to reciprocate according to the rotation of the internal combustion engine 1, the valve body 62 is used for the needs for high rotational speed required for the internal combustion engine 1 in recent years. The high movement response of the valve and the high valve opening response accordingly are particularly effective.

Second Embodiment
As shown in FIGS. 9-11, the second embodiment discloses a solenoid valve 2060 and a high pressure fuel pump 2010, which are modifications of the first embodiment.

  In the stator 2063 of the second embodiment, an inner diameter that is substantially equal to the inner diameter of the collar 632 and substantially constant throughout the axial direction is provided on the inner circumferential surface 2631a of the side core 2631. In the same manner as in the first embodiment, the outer diameter 2631 b of the side core 2631 is also provided with an outer diameter that gradually decreases in the upward direction Du. Thus, the radial thickness of the side core 2631 is reduced in the upward direction Du.

  The armature 2064 according to the second embodiment has an outer diameter changing portion 2643 on the outer peripheral surface 2064 a. The outer diameter changing portion 2643 is provided across the axial end portions of the outer peripheral surface 2064a of the armature 2064, and the outer diameter is enlarged, ie, the diameter is increased in the rising direction Du. Here, in particular, the outer diameter changing portion 2643 has a tapered shape (i.e., a conical shape) that gradually increases in diameter toward the rising direction Du in the entire outer peripheral surface 2064 a of the armature 2064. The rate of change in diameter in the axial direction of the outer diameter changing portion 2643 is set substantially constant in the entire outer peripheral surface 2064 a of the armature 2064.

  Thus, the outer diameter changing portion 2643 is a portion of the armature 2064 that has reached the moving end E (see FIG. 11) in the upward direction Du, at least radially inward with respect to the end 2631c in the upward direction Du of the side core 2631. From Pi, the diameter gradually increases in the upward direction Du. Here, in particular, the outer diameter changing portion 2643 is gradually diameter-expanded toward the rising direction Du from an end 2064 b which exceeds the point Pi in the lowering direction Dd in the side core 2631.

  The armature 2064 axially overlaps the side core 2631 disposed radially outward of the armature 2064. Thus, the side core 2631 forms a radial gap Gr between its own inner peripheral surface 2631 a and the outer diameter changing portion 2643 of the outer peripheral surface 2064 a of the armature 2064. As the radial width of the radial gap Gr, the narrowest width Wr at which the end 2631 c in the rising direction Du in the side core 2631 is spaced apart from the outer diameter changing portion 2643 at each movement position is the above-described shape of the changing portion 2643 In accordance with, the expansion tendency is shown according to the movement of the armature 2064 in the upward direction Du.

  As a result of such an expansion tendency, at the moving end E (see FIG. 11) in which the valve portion 621a is seated on the valve seat surface 611a as in the first embodiment, the rising direction is higher than the end 2631c of the side core 2631. When the amount of protrusion of the armature 2064 is maximized at Du, the narrowest width Wr at each movement position of the radial gap Gr becomes the maximum width at all movement positions. In the radial gap Gr, a magnetic flux M generated by turning on the solenoid coil 670 flows between the armature 2064 and the side core 2631. In addition, the armature 2064 and the side core 2631 have the structure according to the armature 64 and the side core 631 of 1st embodiment by points other than having demonstrated so far.

  In the second embodiment under such a configuration, when the solenoid coil 670 is energized as in the first embodiment, as shown in FIGS. 10 and 11, the magnetic circuit C in which the generated magnetic flux M flows is a stator 2063. Form in cooperation with the armature 2064 and the magnetic yoke 671 (not shown). At this time, the magnetic circuit C is formed so that the magnetic flux M passes through the radial gap Gr, the armature 2064 and the axial gap Ga between the main core 630 and the side core 2631 in the stator 2063 in particular. As a result, the magnetic attraction force F that magnetically attracts the armature 2064 by the main core 630 gradually increases following the magnetic flux density in the entire magnetic circuit C from the start timing Ton of the energization. Thus, the armature 2064 starts to move in the upward direction Du together with the valve body 62.

  Here, as in the first embodiment, under the situation where the axial width Wa of the axial gap Ga decreases in accordance with the movement of the armature 2064 in the upward direction Du, the diameter of the narrowest width Wr increases in accordance with the movement. In the direction gap Gr, the magnetic resistance increases and the magnetic flux M becomes difficult to flow. Therefore, although the magnetic flux density in the entire magnetic circuit C gradually increases due to the decrease in the magnetic resistance (the easiness of flow of the magnetic flux M) in the axial gap Ga according to the movement of the armature 2064 in the upward direction Du, Due to the increase in the reluctance (the difficulty of flowing the magnetic flux M) at the radial gap Gr, the time rate of increase of the magnetic flux density is reduced with respect to the prior art.

  As described above, although the magnetic attraction force F gradually increases in accordance with the movement of the armature 2064 in the upward direction Du, the magnetic attraction force F does not become too large as compared with the prior art described above. Therefore, at the moving end E in the upward direction Du, the holding suction force Fh holding the armature 2064 is also not too large compared to the prior art. As a result, as in the first embodiment, the time Δt from the power off timing Toff to the disappearance of the magnetic flux M and the movement of the armature 2064 with the valve body 62 in the downward direction Dd is the same as in the first embodiment. To be shortened.

(Action effect)
Hereinafter, the special effects according to the second embodiment, that is, the effects according to the features different from the first embodiment will be described. In addition, about the effect similar to 1st embodiment, description is abbreviate | omitted as an effect which read the armature 64 and the side core 631 as the armature 2064 and the side core 2631 respectively is exhibited.

  According to the second embodiment, the outer diameter changing portion 2643 expanded in the rising direction Du at the outer peripheral surface 2064a of the armature 2064 is a radial gap that expands in response to the movement of the armature 2064 in the rising direction Du. Gr may be formed between the side cores 2631. According to this, it is suppressed that the magnetic attraction force F including the holding attraction force Fh becomes too large following the magnetic flux density in the entire magnetic circuit C, and a high movement response in the movement of the valve body 62 in the descent direction Dd It becomes possible to secure the

  Further, according to the second embodiment, the outer diameter changing portion 2643 in the outer peripheral surface 2064a of the armature 2064 in the tapered shape gradually diameter-expanded toward the rising direction Du corresponds to the movement of the armature 2064 in the rising direction Du. A progressively expanding radial gap Gr may be formed. According to this, it is possible to gently suppress that the magnetic attraction force F including the holding attraction force Fh becomes too large following the magnetic flux density in the entire magnetic circuit C, so that the valve body 62 in the upward direction Du It is possible to secure high movement response in the movement of the valve body 62 in the downward direction Dd while facilitating the movement.

  Furthermore, according to the second embodiment, in the armature 2064 that has reached the moving end E in the upward direction Du, the elevation direction is from the point Pi located at least radially inward with respect to the end 2631 c of the side core 2631 in the upward direction Du. The outer diameter changing portion 2643 which is expanded toward Du can form the radial gap Gr with the maximum width at the moving end E. Thereby, at the moving end E in the upward direction Du, the movement of the valve disc 62 in the downward direction Dd can be reliably mitigated because the magnetic attraction force Fh becomes too large following the magnetic flux density in the entire magnetic circuit C. The reliability of the effect of ensuring high mobility can be improved.

Third Embodiment
As shown in FIGS. 12-14, the third embodiment discloses a solenoid valve 3060 and a high pressure fuel pump 3010 which are modifications of the first embodiment.

  In the stator 3063 of the third embodiment, the inner circumferential surface 3631 a of the side core 3631 is provided with an inner diameter that is substantially equal to the inner diameter of the collar 632 and substantially constant throughout the axial direction. In the same manner as in the first embodiment, the outer diameter 3631 b of the side core 3631 is also provided with an outer diameter that gradually decreases in the upward direction Du. Thus, in the side cores 3631, the radial thickness is reduced in the upward direction Du.

  Under this configuration, in the side core 3631 of the third embodiment, the internal magnetic resistance is adjusted to increase in the upward direction Du with respect to the magnetic flux M generated by turning on the solenoid coil 670. Therefore, the side cores 3631 are formed by axially combining metal magnetic materials of different types (here, two types) different in magnetic resistance with respect to the generated magnetic flux M.

  Specifically, a plurality of side cores 3631 have different magnetic resistances of metal magnetic materials as constituent materials with respect to the generated magnetic flux M of the solenoid coil 670 excited according to the set current I supplied by the ECU 8 at the time of energization. (1) magnetoresistive portion 3634, 3635. Here, the first magnetic resistance portion 3634 exhibiting a penetrating cylindrical shape is coaxially adjacent to the second magnetic resistance portion 3635 exhibiting a penetrating cylindrical shape having substantially the same inner diameter in the downward direction Dd. The magnetic resistance to the generated magnetic flux M according to the setting current I appears more largely in the metal magnetic material constituting the second magnetic resistance portion 3635 than in the metal magnetic material constituting the first magnetic resistance portion 3634 It is set to. Thus, for example, the first magnetic resistance portion 3634 is formed of a high BH material or the like, while the second magnetic resistance portion 3635 is formed of a low BH material or the like. As described above, the side core 3631 of the third embodiment has a structure in which the magnetic resistance to the generated magnetic flux M is gradually increased in the upward direction Du.

  The armature 64 axially overlaps the side core 3631 disposed radially outward of the armature 64. Thus, the side core 3631 forms a radial gap Gr between its own inner peripheral surface 3631 a and the outer peripheral surface 64 a of the armature 64. The radial width of the radial gap Gr is substantially constant in design over the entire axial direction of the side core 3631 at each movement position. In addition, the side core 3631 is equipped with the structure according to the side core 631 of 1st embodiment by the point except having demonstrated so far.

  In the third embodiment under such a configuration, when the solenoid coil 670 is energized as in the first embodiment, the magnetic circuit C in which the generated magnetic flux M flows, as shown in FIGS. Form in cooperation with the armature 64 and the magnetic yoke 671 (not shown). At this time, the magnetic circuit C is formed so that the magnetic flux M passes through the radial gap Gr, the armature 64 and the axial gap Ga between the main core 630 and the side core 3631 in the stator 3063 in particular. As a result, the magnetic attraction force F that magnetically attracts the armature 64 by the main core 630 gradually increases following the magnetic flux density in the entire magnetic circuit C from the start timing Ton of the energization. Thereby, the armature 64 starts to move in the upward direction Du together with the valve body 62.

  Here, in the third embodiment, under the condition that the axial width Wa of the axial gap Ga is reduced according to the movement of the armature 64 in the upward direction Du as in the first embodiment, the magnetoresistance in the upward direction Du is obtained. The increasing side cores 3631 make it difficult for the magnetic flux M to flow to the radial gap Gr in response to the movement. Therefore, although the magnetic flux density in the entire magnetic circuit C gradually increases due to the flowability of the magnetic flux M in the axial gap Ga according to the movement of the armature 64 in the upward direction Du, the radial gap Gr corresponding to the movement Due to the difficulty of the flow of the magnetic flux M, the rate of time increase of the magnetic flux density is reduced compared to the prior art.

  As described above, although the magnetic attraction force F gradually increases in accordance with the movement of the armature 64 in the upward direction Du, the magnetic attraction force F does not become too large as compared with the prior art described above. Therefore, at the moving end E in the upward direction Du, the holding suction force Fh holding the armature 64 is not too large as compared with the prior art. As a result, as in the first embodiment, the time Δt from the power off timing Toff to the disappearance of the magnetic flux M and the movement of the armature 64 together with the valve body 62 in the downward direction Dd is the same as in the first embodiment. To be shortened.

(Action effect)
Hereinafter, the special effects according to the third embodiment, that is, the effects according to the features different from the first embodiment will be described. In addition, about the effect similar to 1st embodiment, description is abbreviate | omitted as what the effect of having read the side core 631 as the side core 3631 each is exhibited.

  In the third embodiment, when the solenoid coil 670 generates the magnetic flux M by turning on the energization, the magnetic resistance M decreases and the magnetic flux M flows in the axial gap Ga which is reduced according to the movement of the armature 64 in the upward direction Du. It will be easier. At this time, the magnetic resistance M of the side core 3631 increases in the upward direction Du, so that the magnetic flux M does not easily flow in the radial gap Gr according to the movement of the armature 64 in the upward direction Du. It can be mitigated that the magnetic attraction force F becomes too large following the magnetic flux density in the entire magnetic circuit C. Therefore, at the moving end E in the upward direction Du, it can be relaxed that the holding suction force Fh on the armature 64 becomes too large. According to this, it is difficult to cause a large delay in the time Δt until the magnetic flux M disappears from the energization and the armature 64 and the armature 64 start to move in the downward direction Dd. It is possible to ensure high movement responsiveness in the movement of the valve body 62.

  Further, according to the third embodiment, in order to suppress the magnetic attraction force F from becoming too large, the side core 3631 in which the magnetic resistance to the magnetic flux M is gradually increased in the rising direction Du is the axial direction The combination of the constituent materials can form a relatively simple structure. According to this, the structure for securing high movement responsiveness in the movement of the valve body 62 in the descent direction Dd can be obtained by suppressing the holding suction force Fh as the magnetic suction force F from becoming too large. It becomes possible to build well.

(Other embodiments)
As mentioned above, although a plurality of embodiments were described, the present disclosure should not be construed as being limited to these embodiments, and applied to various embodiments and combinations within the scope of the gist of the present disclosure. Can.

  In the first modification to the first to third embodiments, the solenoid valves 60, 2060, and 3060 may be normally closed control valves. That is, in the first modification, the armatures 64 and 2064 and the valve body 62 are moved in the upward direction Du by turning on the solenoid coil 670 to open the suction passage 204 in the prestroke period of the suction stroke and the pressure feed stroke. On the other hand, in the first modification, the armatures 64 and 2064 and the valve body 62 are moved in the downward direction Dd by turning off the solenoid coil 670 so that the suction passage 204 is closed during the pressurization period of the pumping stroke. According to the first modification, since the suction passage 204 is closed by the movement of the valve body 62 in the downward direction Dd in the high pressure fuel pump 10, it is possible to achieve high valve closing responsiveness due to the movement. . Here, in the high-pressure fuel pump 10 in which the plunger 402 is reciprocated according to the rotation of the internal combustion engine 1 even in the first modification, the valve for the high rotational speed needs of the internal combustion engine 1 recently required. The high valve closing response of the body 62 is particularly effective.

  In the pumping stroke of Modification 2 of the first to third embodiments, only the pressurization period may be performed without the pre-stroke period being performed. That is, the solenoid valve 60 always closes the suction passage 204 during the pressure-feeding process of the second modification. In the third modification related to the first to third embodiments, the side cores 631, 2631 and 3631 are not provided from the main core 630 via space portions that are longer in the axial direction than the maximum widths of the gaps Ga and Gr without providing the collar 632. It may be separated.

  In Modification 4 of the first and second embodiments, at least one of the main core 630 and the side cores 631 and 2631 has a magnetic diaphragm 1635 instead of the collar 632 not provided in the stator 63 as shown in FIGS. And may be integrally formed. The magnetic diaphragm 1635 according to the fourth modification is formed thinner than the radial thickness of the side cores 631 and 2631 by the recess of at least one of the inner peripheral surface and the outer peripheral surface with respect to the side cores 631 and 263. In addition, as a fourth modification related to the first embodiment, FIG. 15 representatively shows a magnetic diaphragm 1635 in which an inner peripheral surface integrally formed with the main core 630 is recessed relative to the side core 631. Further, as a fourth modification related to the second embodiment, FIG. 16 representatively shows a magnetic diaphragm 1635 in which the outer peripheral surface integrally formed with the main core 630 is recessed relative to the side core 2631.

  In Modification 5 of the third embodiment, at least one of the main core 630 and the second magnetoresistance portion 3635 is integrally formed with the magnetic diaphragm 1635 instead of providing the collar 632 in the stator 63, 2063 as shown in FIG. It may be done. The magnetic diaphragm 1635 of the fifth modification is formed thinner than the radial thickness of the second magnetoresistance portion 3635 by the recess of at least one of the inner circumferential surface and the outer circumferential surface with respect to the second magnetoresistance portion 3635. As a fifth modification of the third embodiment, FIG. 17 representatively shows a magnetic diaphragm 1635 in which the outer peripheral surface integrally formed with the second magnetic resistance portion 3635 is recessed relative to the resistance portion 3635. .

  In the sixth modification related to the first embodiment, as shown in FIG. 18, the armature 64 may be changed to the armature 2064 of the second embodiment. In the sixth modification, the inner diameter changing portion 633 of the side core 631 is formed with a taper angle larger or smaller than the outer diameter changing portion 2643 of the armature 2064. Thus, in the sixth modification, the narrowest width Wr of the radial gap Gr between the inner diameter changing portion 633 and the outer diameter changing portion 2643 is expanded according to the movement of the armature 2064 in the rising direction Du. As a sixth modification of the first embodiment, FIG. 18 representatively shows an inner diameter changing portion 633 having a taper angle larger than the outer diameter changing portion 2643.

  In the seventh modification related to the first and second embodiments, according to the side core 3631 of the third embodiment, by combining a plurality of types of metal magnetic materials having different magnetic resistances with respect to the generated magnetic flux M in the axial direction, the side core 631 , 2631 may be formed. In the seventh modification, the side cores 631 and 2631 have a plurality of magnetic resistance portions 3634 and 3635 as shown in FIGS. 19 and 20, respectively, resulting in a structure in which the magnetic resistance increases in the upward direction Du.

  In Modification 8 of the third embodiment, the side core 3631 may be configured by combining three or more types of metal magnetic materials having different magnetic resistances so as to increase the magnetic resistance in the upward direction Du. In the eighth modification, the side core 3631 has three or more magnetoresistive portions in which magnetic reluctances of metal magnetic materials as constituent materials are different from each other.

  In the ninth modification related to the first and second embodiments, as long as the diameter is increased in the upward direction Du, the change portions 633 and 2643 may be formed in a shape other than the tapered shape. In the specific example shown in FIGS. 21 and 22 as the modified example 9, the diameter change rate of the change parts 633 and 2643 in the axial direction gradually decreases as it goes in the rising direction Du. Further, in the specific example shown in FIGS. 23 and 24 as the ninth modification, the diameter change rate of the change parts 633 and 2643 in the axial direction gradually increases in the upward direction Du. Furthermore, in the specific example shown in FIGS. 25 and 26 as the ninth modification, the changing portions 633 and 2643 are gradually enlarged in diameter in the upward direction Du.

  In Modification 10 of the first embodiment, starting from a point Po located radially outward with respect to the end 64 b of the lowering direction Dd of the armature 64 which has reached the moving end E of the raising direction Du in the side core 631. An inner diameter changing portion 633 may be provided in the downward direction Dd. In the modification 10, the inner circumferential surface 631a may be formed to have a substantially constant inner diameter from the end portion 631c of the side core 631 in the rising direction Du to the point Po.

  In the eleventh modification of the second embodiment, a starting point Pi of the armature 2064 that has reached the moving end E in the upward direction Du with respect to the end 2631 c in the upward direction Du in the side core 2631 is the starting point, An outer diameter changing portion 2643 heading in the upward direction Du may be provided. In this modification 11, the outer peripheral surface 2064a may be formed to have a substantially constant outer diameter from the end 2064b in the lowering direction Dd of the armature 2064 to the place Pi.

  In a modification 12 relating to the first to third embodiments, in the fuel supply system 2 for supplying gasoline as a fuel to a gasoline engine as the internal combustion engine 1, the solenoid valves 60, 2060, 3060 and the high pressure fuel pump 10, 2010 , 3010 may be applied. In Modification 13 of the first to third embodiments, the solenoid valves 60, 2060, and 3060 may be applied to various systems or devices other than the high-pressure fuel pump 10, 2010, and 3010.

10, 2010, 3010 High-pressure fuel pump, 20 pump body, 60, 2060, 3060 solenoid valve, 61 valve body, 62 valve body, 63, 2063, 3063 stator, 64, 2064 armature, 65 first elastic member, 66 second Elastic member, 202a pressure chamber, 204 suction passage, 630 main core, 631,2631, 3631 side core, 631a inner circumferential surface, 633 inner diameter changing portion, 670 solenoid coil, 2064a outer circumferential surface, 2631c end, 2643 outer diameter changing portion , 3634 first magnetoresistance part, 3635 second magnetoresistance part, C magnetic circuit, Dd downward direction, Du upward direction, E moving end, F magnetic attraction force, Fh holding attraction force, Ga axial direction gap, Gr radial direction gap , M magnetic flux, Pi, Po point

Claims (13)

A solenoid coil (670) that generates a magnetic flux (M) by turning on electricity;
An axially reciprocating valve body (62);
An armature (64, 2064) that reciprocates with the valve body;
A stator (63, 2063) which magnetically attracts the armature in the upward direction (Du) in the axial direction by forming a magnetic circuit (C) through which the magnetic flux flows in cooperation with the armature;
An electromagnetic valve (60, 2060) comprising: an elastic member (65) for urging the armature in the downward direction (Dd) of the axial direction,
The stator is
An axial gap (Ga) disposed in the ascending direction of the armature and flowing the magnetic flux between the armature and the armature, which forms an axial gap which is reduced according to the movement of the armature in the ascending direction With the core (630)
A side core which is disposed radially outside the armature and which forms a radial gap which is expanded according to the movement of the armature in the ascending direction as a radial gap (Gr) for flowing the magnetic flux between the armature and the armature. A solenoid valve provided with (631, 2631).   The electromagnetic valve according to claim 1, wherein the magnetic flux density of the magnetic circuit increases in response to the movement of the armature in the upward direction. The side core (631) is
The internal diameter change part (633) which is diameter-expanded toward the said raise direction in the internal peripheral surface (631a) which forms the said radial direction gap between the said armature (64), The claim 1 or 2 Description solenoid valve. The inner diameter changer is
The solenoid valve according to claim 3, which exhibits a tapered shape in which the diameter is gradually increased toward the rising direction on the inner peripheral surface of the side core. The inner diameter changer is
From the portion (Po) located at least radially outward of the end (64b) in the descending direction of the armature reaching the moving end (E) in the upward direction in the side core, in the downward direction 5. The solenoid valve according to claim 3, wherein the diameter is reduced. The armature (2064) is
The method according to any one of claims 1 to 5, further comprising an outer diameter changing portion (2643) whose diameter is increased in the ascending direction on the outer peripheral surface (2064a) forming the radial gap with the side core (2631). The solenoid valve according to any one of the preceding claims. The outer diameter changing portion is
The solenoid valve according to claim 6, which exhibits a tapered shape in which the diameter is gradually increased in the rising direction on the outer peripheral surface of the armature. The outer diameter changing portion is
Of the armature reaching the moving end in the upward direction, the armature is expanded in the upward direction from a point (Pi) located at least radially inward with respect to the end (2631c) in the upward direction of the side core The solenoid valve according to claim 6 or 7, wherein the solenoid valve has a diameter. The magnetic resistance of the side core to the magnetic flux is
The solenoid valve according to any one of claims 1 to 8, which increases in the upward direction. A solenoid coil (670) that generates a magnetic flux (M) by turning on electricity;
An axially reciprocating valve body (62);
An armature (64) that reciprocates with the valve body;
A stator (3063) which magnetically attracts the armature in the upward direction (Du) in the axial direction by forming a magnetic circuit (C) through which the magnetic flux flows in cooperation with the armature;
An electromagnetic valve (3060) comprising: an elastic member (65) for urging the armature in the downward direction (Dd) of the axial direction,
The stator is
An axial gap (Ga) disposed in the ascending direction of the armature and flowing the magnetic flux between the armature and the armature, which forms an axial gap which is reduced according to the movement of the armature in the ascending direction With the core (630)
A side core (3631) disposed radially outward of the armature, forming a radial gap (Gr) for flowing the magnetic flux with the armature, and increasing the magnetic resistance to the magnetic flux in the upward direction. ) And a solenoid valve. The magnetic resistance of the side core to the magnetic flux is
The electromagnetic valve according to claim 9 or 10, wherein the electromagnetic valve gradually increases in the upward direction. The side cores (631, 2631 and 3631) are
The solenoid valve as described in any one of Claims 1-11 spaced apart and provided in the said descent | fall direction from the said main core. A high pressure fuel pump (10, 2010, 3010) which pressurizes fuel sucked into a pressurizing chamber (202a) through a suction passage (204) by a plunger (402) and pressure-feeds it to a supply destination (6),
A pump body (20) which forms the suction passage and the pressure chamber and slidably supports the plunger;
The solenoid valve according to any one of claims 1 to 12, mounted on the pump body, in the suction stroke in which the plunger is driven toward the side where the fuel is sucked into the pressure chamber. The solenoid valve opens the suction passage by the movement of the body, and closes the suction passage by the movement of the valve body in the pumping stroke in which the plunger is driven toward the pressure feeding side of the pressurizing chamber. 60, 2060, 3060), and the high pressure fuel pump comprised.

Images