JP2008138650A - Solenoid valve, and fuel injection device using it - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent degradation of slidability between a guide hole of a support member slidably supporting a valve member, and the valve member. <P>SOLUTION: This solenoid valve is provided with: a valve seat member 16 equipped with a valve seat 16d having a communication passage 16a making the high-pressure side of a fuel passage communicate with the low-pressure side thereof; valve members 42b and 41 closing/opening the high-pressure side and the low-pressure side of the fuel passage by being seated/separated on/from the valve seat; the support member 17 having the guide hole 17a, supporting the valve members movably in the guide hole, and capable of adhering tightly to the valve seat member with the valve members supported thereon; a movable core 42 arranged on the side of the support member opposite to the valve seat member by facing the support member, and axially movable in cooperation with the valve members; and a fixed core 63 capable of attracting the movable core when a current is carried to a coil 61. A leak fuel passage for running a leak fuel therethrough is partitioned between the valve members 42b and 41 of the movable core 42 and the guide hole 17a of the support member 17. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a solenoid valve and a fuel injection device using the same, and is suitably applied to, for example, an accumulator fuel injection device that injects and supplies fuel to an internal combustion engine.

  2. Description of the Related Art Conventionally, there is a solenoid valve that is used for controlling a fuel pressure in a pressure control chamber of a fuel injection valve provided in each cylinder of an internal combustion engine in a pressure accumulation fuel injection device for a diesel engine (see Patent Document 1). . In the fuel injection valve, the lift movement of the nozzle needle that opens and closes the nozzle hole is controlled via the control pressure in the pressure control chamber. In this type of solenoid valve, a drive coil portion disposed in a valve housing, a movable core (also referred to as an armature) biased in the valve seat direction, and a valve member that can be integrated or cooperated with the movable core ( And an orifice member having a valve seat on which the valve member is seated and separated, and a support member that constitutes a part of the valve housing and supports the valve member in a slidable manner.

  In such an electromagnetic valve, when energization is stopped, the valve member of the movable core is guided by the support member and is provided in the valve seat of the orifice member, and the valve member closes the orifice communicating with the pressure control chamber. Yes. When energized, the movable core is attracted by the electromagnetic force generated in the drive coil portion, so that the fuel in the pressure control chamber flows into the valve housing through the orifice.

  Patent Document 1 discloses a technique in which fuel that has flowed into a valve housing is discharged to the end side of the drive coil portion opposite to the movable core side, bypassing the portion where the movable core and the drive coil portion adsorb. ing. With this technique, it is possible to prevent accumulation of foreign substances such as magnetic materials contained in the discharged fuel at the adsorption site.

  Patent Document 2 discloses a technique for returning fuel that has flowed into a valve housing to a fuel discharge passage in a fuel injection valve to which a solenoid valve is attached.

In both of Patent Document 1 and Patent Document 2, in the structure inside the valve housing, the support member and the outer peripheral side of the valve seat of the orifice member are brought into close contact with each other, and the orifice member is separated from the guide hole for supporting the valve member. A fuel communication passage for discharging the fuel flowing in from the seat into the valve housing is formed. Note that the sliding gap between the guide hole of the support member and the valve member is formed in a relatively small gap. Further, in order to secure the adhesion between the support member and the orifice member, the support member itself is screwed into the valve housing and is in close contact with the orifice member by the fastening force.
JP 2006-133297 A JP 2002-147310 A

  In the prior art, the fuel flowing in from the valve seat hardly flows into the minute sliding gap between the guide hole of the support member and the valve member regardless of the internal structure of the valve housing. The support member flows to a fuel communication path provided separately from the guide hole.

  As fuels to be used, in addition to mainstream diesel light oil, biodiesel fuel and mixed fuels obtained by mixing this fuel and light oil are becoming popular as alternative fuels. The inventor found that the above-described electromagnetic valve using or mixing biodiesel fuel was subjected to analysis investigation and endurance test evaluation, and as a result, the slidability between the guide hole of the support member and the valve member might be lowered.

  The present invention has been made in view of such circumstances, and an object of the present invention is to prevent deterioration in slidability between the guide hole of the support member that supports the valve member so as to be slidable and the valve member. .

  Another object is to prevent the sliding performance between the guide hole of the support member that slidably supports the valve member and the valve member, and to assemble the support member and the valve member into the valve housing. It is an object of the present invention to provide a solenoid valve that facilitates and a fuel injection device using the same.

    In order to achieve the above object, the present invention comprises the following technical means.

That is, in the invention described in claims 1 to 11, the solenoid valve that cuts off and distributes the fuel flow between the high pressure side and the low pressure side of the fuel passage has a communication passage that connects the high pressure side and the low pressure side of the fuel passage. A valve seat member having a valve seat, a valve member that closes and opens a high pressure side and a low pressure side of the fuel passage by being seated and separated from the valve seat, a guide hole, and the valve member by the guide hole A support member that is movably supported and that can be in close contact with the valve seat member while supporting the valve member, and is disposed on the counter valve seat member side of the support member so as to face the support member, and cooperates with the valve member. A movable core that can move in the axial direction and a fixed core that can suck the movable core when the coil is energized,
A leak fuel passage through which leak fuel flows is defined between the valve member of the movable core and the guide hole of the support member.

  According to this, since the leak fuel passage through which the leak fuel flows is defined between the valve member of the movable core and the guide hole of the support member, the coil is energized and the movable core and When the valve member is separated from the valve seat of the valve seat member, the high pressure side and the low pressure side of the fuel passage are opened, and fuel flows in through the communication passage of the valve seat. The inflowing fuel has a leak fuel passage formed between the valve member of the movable core and the guide hole of the support member because the valve seat member and the support member are in close contact with the valve member being supported. In addition, leaked fuel circulates.

  Therefore, it is possible to smoothly slide the valve member of the movable core and the guide hole of the support member by the fuel guided to the leak fuel passage each time the coil is energized.

  Here, the leak fuel passage is formed by a gap between the outer periphery of the valve member and the inner periphery of the guide hole, and the gap is set in a range of 10 μm to 20 μm. It is preferable.

  According to this, when the gap between the outer periphery of the valve member and the inner periphery of the guide hole can be enlarged, the gap in the prior art is expanded to the gap through which the leak fuel flows by expanding the gap in the prior art. Because it can be done. Therefore, according to the second aspect of the present invention, the valve member and the guide hole can be changed by a relatively slight configuration change that is larger than the gap of the prior art and the gap is set to a range of 10 μm to 20 μm. A fuel flow can be generated in the gap, and a decrease in slidability between the valve member and the guide hole can be prevented regardless of the type of fuel used as described above.

  In addition, in the set gap range, if the gap outside the set gap range is less than 10 μm, the fuel flow may be delayed, and there is a possibility that the leaked fuel hardly flows. On the other hand, when the gap exceeds 20 μm, the inclination of the movable core and the valve member supported by the support member exceeds the allowable inclination, which may affect the performance of the electromagnetic valve. For example, if the clearance exceeds the allowable inclination of the valve member, the valve member may not reliably close the valve seat when the valve is closed. For this reason, there exists a possibility of affecting the fuel-injection characteristic of the fuel-injection apparatus using an electromagnetic valve.

  According to a third aspect of the present invention, the leak fuel passage is formed at least from a gap between the outer periphery of the valve member and the inner periphery of the guide hole, and the peripheral wall of either the outer periphery of the valve member or the inner periphery of the guide hole It is preferable that a step portion for expanding the gap is provided in a part of the circumferential direction.

  According to this, in the case where the amount of leaked fuel flowing in the gap between the outer periphery of the valve member valve member and the inner periphery of the guide hole is increased, the peripheral wall of either the outer periphery of the valve member or the inner periphery of the guide hole is It is possible to set the gap in the wall surface of the other part other than the part of the wall surface in the direction to be equal to or smaller than the predetermined gap having the allowable inclination, and to enlarge the gap in the wall surface of the part to a predetermined gap or more by the step portion. it can. Therefore, it is possible to increase the amount of leaked fuel flowing in the gap between the valve member valve member and the guide hole while securing a support function for setting the valve member to an allowable inclination or less.

  Moreover, it is preferable that the said level | step-difference part is provided in multiple places in the circumferential direction of the surrounding wall like the invention of Claim 4. According to this, for example, when the amount of step formed in the gap expanding direction of the stepped portion is relatively small, the plurality of stepped portions are arranged in the circumferential direction of the peripheral wall, so that it is easy to secure a necessary amount of leaked fuel.

  Moreover, it is preferable that the said level | step-difference part is arrange | positioned at substantially equal intervals along the circumferential direction of a surrounding wall like the invention of Claim 5.

  According to this, the annular gap which has the gap part expanded by the level difference part arranged at substantially equal intervals along the peripheral direction of the peripheral wall is formed. As a result, the valve member is physically supported by the inner periphery of the guide hole at the outer periphery of the valve member, and is guided by the fluid force of the leak fuel flowing through the annular gap having the gap portions enlarged at substantially the same interval. It can be centered on the hole center. Therefore, the inclination of the valve member physically defined by the outer periphery of the valve member and the inner periphery of the guide hole is corrected by the fluid force of the leak fuel flowing through the annular gap having the gap portions enlarged at substantially the same interval. It is possible.

  In the annular gap in the prior art, the inclination of the valve member can be corrected by the fluid force only when the leak fuel flows evenly in the circumferential direction through the annular gap. The case where the leaked fuel is difficult to flow evenly in the circumferential direction is, for example, a state in which the valve member is arranged in an eccentric state with respect to the guide hole in the valve member closed state when the energization of the coil is stopped. .

  In addition, as described in the sixth aspect of the present invention, the opening of the guide hole has a diameter-enlarging surface in which the size of the inner periphery of the guide hole is increased, and the diameter-enlarging surface of the movable core facing the support member. The inner circumference is preferably enlarged toward the first end face.

  As a result, it is possible to mitigate the fluid collision force in which the leaked fuel flowing out from the gap between the guide hole and the valve member directly collides with the first end surface of the movable core facing the support member.

  According to the seventh aspect of the present invention, it is preferable that the support member has a groove formed on the second end surface facing the movable core, and the groove communicates with the leak fuel passage.

  According to this, when the gap between the support member and the movable core facing each other is relatively small, a groove portion communicating with the leak fuel passage is provided on the second end surface of the support member facing the movable core. When the leaked fuel flowing out from the gap flows along the gap between the support member and the movable core, it is not throttled.

  Moreover, it is preferable that the said groove part is provided in multiple places in the circumferential direction of the 2nd end surface like the invention of Claim 8.

  As a result, in the case where the flow path area where the leaked fuel flowing along the gap between the support member and the movable core is not restricted is ensured by the groove part, the necessary flow path area can be divided by the plurality of groove parts. Therefore, each groove does not significantly hinder the function of the outer shape of the support member. For example, even when the support member has a screw portion on the outer peripheral portion, it is possible to suppress a decrease in the effective screw length of the screw portion.

  Moreover, it is preferable that the said groove part is arrange | positioned at substantially equal intervals along the circumferential direction of a 2nd end surface like the invention of Claim 9.

  In general, when the air gap between the support member and the movable core facing each other is relatively small, there is a possibility that the fuel flowing between the gaps does not flow evenly in the circumferential direction between the gaps. When the air does not flow evenly in the circumferential direction between the gaps, the fluid force of the fuel does not act uniformly around the circumferential direction of the first end surface of the movable core. For example, when the movable core and the valve member are closed, the movable core In addition, the seating operation (valve closing operation) of the valve member on the valve seat may become unstable.

  On the other hand, in the invention according to claim 9, since the groove portions are arranged at substantially equal intervals along the circumferential direction of the second end surface, the fluid force caused by the fuel flowing in the groove portion is caused to flow in the circumferential direction of the first end surface of the movable core. It is made to act at equal intervals around. Thereby, for example, the seating operation (valve closing operation) of the movable core and the valve member on the valve seat can be stabilized.

  Further, as in the invention described in claim 10, it is preferable that the groove has a two-plane width extending outward from the leak fuel passage side.

  In general, as a method of bringing a support member into close contact with a valve seat member having a valve seat while supporting the valve member, for example, the support member is screwed to the housing with the valve seat member interposed therebetween. In order to screw the support member to the housing, a tightening jig for screwing the support member is required. When tightening in a state where the tightening jig is inserted and fitted into the hole using a hole defining the fuel communication path provided in the support member, There was a problem that hitting or the like was likely to occur and tightening work was not easy.

  On the other hand, in the invention described in claim 10, since the groove portion having a two-sided width extending outward from the leak fuel passage side is provided in the support member, the two-sided width of the groove portion is used for tightening. It is possible to perform the tightening operation in a state in which the attachment jig is fitted to the width of the two surfaces. In addition, since the tightening operation by fitting the two-surface width and the tightening jig is relatively easy, the tightening operation can be improved.

Moreover, in invention of Claim 11, the solenoid valve as described in any one of Claims 1-10 is fastened to a housing,
The support member includes a screw portion that is screwed into the housing,
The support member is in close contact with the valve seat member by sandwiching the valve seat member and fastening it in the housing.

  Further, in the invention described in claims 12 to 13, in the fuel injection device using the solenoid valve according to claim 11, a nozzle portion having a nozzle hole for injecting fuel, a nozzle needle for opening and closing the nozzle hole, and a nozzle And a nozzle body having a pressure control chamber in which high-pressure fuel for urging the needle in the nozzle hole closing direction is stored, and the housing is formed in the nozzle body.

  In a thirteenth aspect of the invention, the pressure control chamber in which high-pressure fuel is stored is on the high-pressure side of the fuel passage.

  Hereinafter, embodiments in which the electromagnetic valve of the present invention is applied to an electromagnetic valve mounted on a fuel injection valve used in an accumulator fuel injection device will be described with reference to the drawings.

(First embodiment)
FIG. 1 is a partial cross-sectional view showing a solenoid valve applied to the fuel injection device of the present embodiment. FIG. 2 is a cross-sectional view illustrating the fuel injection device according to the embodiment. FIG. 3 is a partial cross-sectional view showing the periphery of the sliding gap between the valve member and the support member in FIG. 1.

  As shown in FIG. 2, the fuel injection valve 2 used in the pressure accumulating fuel injection device 1 is a multi-cylinder (for example, four cylinders) diesel engine (not shown) mounted on a vehicle such as an automobile (hereinafter referred to as an engine). The high-pressure fuel that is provided for each cylinder of the high-pressure fuel supply pump (hereinafter referred to as supply pump) 3 and is stored in the accumulator (hereinafter referred to as common rail) 4 is accumulated in the common rail 4. This is a so-called injector that directly injects fuel into the combustion chamber.

  The fuel injection valve 2 includes a nozzle body 12 that accommodates the nozzle needle 20 so as to be movable in the axial direction, a nozzle holder 11 that houses a spring 35 as a biasing member that biases the nozzle needle 20 toward the valve closing side, and a nozzle body. A retaining nut 14 as a tightening member that fastens the nozzle 12 and the nozzle holder 11 with a predetermined tightening axial force, and an electromagnetic valve 7 are configured. The nozzle body 12, the nozzle holder 11, and the retaining nut 14 constitute a nozzle body of the fuel injection valve by fastening the nozzle body 12 and the nozzle holder 11 with the retaining nut 14. The nozzle needle 20 and the nozzle body 12 constitute a nozzle part.

  The nozzle body 12 is formed in a substantially cylindrical body, and is provided with one or a plurality of injection holes 12b for injecting high-pressure fuel into the combustion chamber on the tip end (lower end in FIG. 2) side. It is a cylindrical member.

  Inside the nozzle body 12, an accommodation hole (hereinafter referred to as a first needle accommodation hole) 12e for holding the solid cylindrical nozzle needle 20 so as to be movable in the axial direction is formed. A fuel reservoir chamber 12c having an enlarged hole diameter is provided at an intermediate portion in the drawing of the first needle housing hole 12e. Specifically, the inner periphery of the nozzle body 12 is formed in the order of the first needle accommodation hole 12e, the fuel reservoir chamber 12c, and the valve seat 12a toward the downstream side of the fuel flow, and the nozzle body 12 is formed downstream of the valve seat 12a. A nozzle hole 12b penetrating the inside and the outside of the nozzle 12 is provided.

  As shown in FIG. 2, the valve seat 12a has a truncated cone surface, the large diameter side of the truncated cone surface is continuous with the first needle accommodation hole 12e, and the small diameter side extends toward the injection hole 12b. The nozzle needle 20 is disposed on the valve seat 12a so as to be seated and separated, and the nozzle needle 20 is closed and opened by being seated and separated.

  Further, the nozzle body 12 is provided with a fuel delivery path 12d extending from a mating surface on the upper end side of the nozzle body 12 to the fuel reservoir chamber 12c. The fuel delivery path 12d communicates with a fuel supply path 11b (described later) of the nozzle holder 11 so that high-pressure fuel accumulated in the common rail 4 is sent to the valve seat 12a side via the fuel reservoir chamber 12c. The fuel delivery path 12d and the fuel supply path 11b constitute a high-pressure fuel path.

  As shown in FIG. 2, the nozzle holder 11 is formed in a substantially cylindrical body, and accommodates therein a spring 35 and a control piston 30 for driving the nozzle needle 20 so as to be movable in the axial direction. 11d (hereinafter referred to as second needle accommodation hole) 11d is provided. An inner circumference 11d2 that is wider than the middle inner circumference 11d1 is formed on the mating surface of the second needle accommodation hole 11d on the lower end side in the figure.

  Specifically, a so-called spring chamber that houses the spring 35, the annular member 31, and the needle portion 30c of the control piston 30 is formed on the inner periphery 11d2. The annular member 31 is disposed so as to be sandwiched between the spring 35 and the nozzle needle 20 and constitutes a spring receiving portion that urges the spring 35 in the valve closing direction of the nozzle needle 20. The needle portion 30 c is configured to be able to contact the nozzle needle 20 indirectly or directly via the annular member 31.

  Further, the nozzle holder 11 is provided with a joint portion (hereinafter referred to as an inlet portion) 11f to which a high pressure pipe (not shown) connected to the branch pipe of the common rail 4 is airtightly coupled. The inlet portion 11f is a fuel introduction portion that guides the high-pressure fuel supplied from the common rail to the fuel supply path 11b via the bar filter 13 mounted inside. A fuel supply path 11b is provided inside the inlet portion 11f of the nozzle holder 11 and around the spring chamber 11d2.

  Further, the nozzle holder 11 is provided with a fuel escape passage (also referred to as a leak recovery passage) (not shown) for returning the fuel guided to the spring chamber 11d2 into a low-pressure piping system such as a fuel tank (not shown). It has been. The fuel escape passage and the spring chamber 11d2 constitute a low pressure fuel passage.

  As shown in FIG. 2, pressure control chambers (hereinafter referred to as “hydraulic control chambers”) 8 and 16 c to which hydraulic pressure is supplied and discharged by the electromagnetic valve 7 are provided on the other end side of the control piston 30. The nozzle needle 20 is closed and opened by increasing or decreasing the hydraulic pressure in the hydraulic control chambers 8 and 16c. Specifically, when the hydraulic pressure is released from the hydraulic control chambers 8 and 16c and decreases, the nozzle needle 20 and the control piston 30 move upward in the axial direction in FIG. 2 against the biasing force of the spring 35, and the nozzle needle 20 Opens. On the other hand, when the hydraulic pressure is introduced into the hydraulic control chambers 8 and 16c and increases, the nozzle needle 20 and the control piston 30 are moved downward in the axial direction in FIG. 2 by the urging force of the spring 35, and the nozzle needle 20 is closed.

  The pressure control chambers 8 and 16c are formed by the outer end wall 30p of the control piston 30, the second needle housing hole 11d, and the inner wall of the pressure control chamber portion 16c.

  Next, the electromagnetic valve 7 will be described in detail. The electromagnetic valve 7 is a so-called electromagnetic two-way valve that intermittently connects the pressure control chambers 8, 16c and the low pressure passage 17d. The electromagnetic valve 7 is disposed at the end of the nozzle holder 11 as a housing on the side opposite to the injection hole. The solenoid valve 7 is fixed to the nozzle holder 11 by a retaining nut 52.

  As shown in FIG. 2, a valve seat plate (hereinafter also referred to as an orifice member) 16 as a valve seat member is provided at the end of the second needle accommodation hole 11d on the side opposite to the injection hole. Further, the outer surface of the valve seat plate 16 is formed with a two-sided width surface (left-right direction in the figure). The valve seat plate 16 is provided with high-pressure introduction passages 16a, 16b, and 16c. The high-pressure introduction passages 16a, 16b, and 16c communicate with an orifice (hereinafter referred to as an out-orifice) 16a as an outlet-side throttle portion, an orifice (hereinafter referred to as an in-orifice) 16b as an inlet-side throttle portion, and the second needle housing hole 11d. Pressure control chamber section 16c.

  As shown in FIG. 1, the out orifice 16a is disposed so as to communicate the valve seat 16d and the pressure control chamber 16c, and is closed and opened by closing and opening the movable core 42 via the valve members 42b and 41. Distributed. The in-orifice 16b is disposed so as to communicate the pressure control chamber 16c and the fuel supply path 11b.

  The valve seat plate 16 is positioned and fixed to the nozzle holder 11 via a positioning member 92 such as a pin. The through hole 16p of the valve seat plate 16 is a locking hole into which the positioning member 92 is inserted.

  As shown in FIG. 2, a support member 17 as a part of the valve housing is provided on the side opposite to the injection hole of the valve seat plate 16. The support member 17 is formed in a substantially cylindrical shape, and is provided with a through hole (hereinafter referred to as a guide hole) 17a as a guide hole. A flat plate portion 42a of the movable core 42 is disposed to face an upper end surface (hereinafter also referred to as a second end surface) 17g of the support member 17. Further, a valve chamber 17c is formed by an inner wall (hereinafter referred to as a diameter-expanded wall) 17e having a tapered diameter downward from the guide hole 17a in the drawing and the support member side end surface of the valve seat plate 16.

  The guide hole 17a slidably supports valve members 42b and 41 described later. While the movable core 42 including the valve members 42b and 41 and the flat plate portion 42b is slidably supported in the guide hole 17a, the flat plate portion 42a of the movable core 42 can approach and separate from the upper end surface 17g of the support member. It is.

  Here, a gap (hereinafter referred to as a guide hole gap) 71 between the guide hole 17a and the valve members 42b and 41 will be described with reference to FIGS. As shown in FIGS. 1 and 3, the guide hole clearance 71 is a clearance between the inner periphery of the guide hole 17a and the outer periphery of the valve members 42b and 41, that is, the outer periphery of the small diameter shaft portion (also referred to as an armature needle) 42b. .

  As shown in FIG. 3, the guide hole gap 71 includes an annular gap 72 and a step-like gap 73. The inner periphery of the guide hole 71 a is formed in the support member 17 in a circular shape. On the other hand, the outer periphery of the small-diameter shaft portion 42b of the operating core 42 is formed in a circular shape in which the first peripheral wall 42ba of the peripheral walls 42ba and 42bb is slightly smaller than the inner periphery of the guide hole 71a. Further, the second peripheral wall 42bb as the step portion forms a step with respect to the circular first peripheral wall 42ba so as to provide a flat recess in the first peripheral wall 42ba.

  The first peripheral wall 42ba forms an annular clearance 72 between the inner periphery of the guide hole 71a, and the second peripheral wall 42bb forms a step-shaped clearance 73 between the inner periphery of the guide hole 71a. . The annular clearance 72 is set to a predetermined non-zero clearance having a radial clearance δ1 of less than 10 μm. On the other hand, the step-shaped gap 73 is formed larger than the predetermined gap by using the step, and the predetermined gap is expanded to δ3max at the maximum.

  As a result, when the fuel is guided to the valve chamber 17c side of the guide hole gap portion 71, the gap is enlarged by the step-like gap portion 73 compared to the conventional configuration including only the annular gap portion 72. As a result, the leaked fuel in the guide hole gap 71 can easily flow.

  Moreover, in this embodiment, as shown in FIG. 3, it is preferable that a plurality of stepped gap portions 73 in the guide hole gap portion 71 are arranged in the circumferential direction (three in this embodiment). .

  According to this, due to the mechanical structure strength of the small-diameter shaft portion 42b of the movable core 42, restrictions on further reducing the diameter, etc., it is necessary to make the amount of step formed in the gap expansion direction of the step-like gap portion 73 relatively small. In some cases, since the plurality of stepped gap portions 73 are arranged in the circumferential direction, it is easy to secure the necessary amount of leaked fuel.

  Moreover, in this embodiment, as shown in FIG. 3, it is preferable that the said three level | step-difference gap parts 73 are arrange | positioned at substantially equal intervals along the circumferential direction.

  According to this, an annular gap portion 72 having a gap portion enlarged by the step-like gap portions 73 arranged at substantially equal intervals along the circumferential direction is formed. As a result, the outer periphery of the small-diameter shaft portion 42b of the movable core 42 is physically supported by the inner periphery of the guide hole 17a, and the annular gap portion 72 having the stepped gap portions 73 at the substantially equal intervals. The center of the guide hole 17a can be adjusted by the fluid force of the flowing leaked fuel. Therefore, the leaked fuel that flows through the annular gap 72 having the stepped gap 73 at the substantially equal intervals, the inclination of the valve member physically defined by the outer circumference of the small-diameter shaft portion 42b and the inner circumference of the guide hole 17a. It is possible to correct with the fluid force.

  In the case of the annular gap 72 in the prior art, the inclination of the small-diameter shaft portion 42b can be corrected by the fluid force only when the leak fuel flows through the annular gap 72 evenly in the circumferential direction. . The case where the leaked fuel is difficult to flow evenly in the circumferential direction means that, for example, when the valve members 42b and 41 are closed when the coil 61 is de-energized, the valve members 42b and 41 are arranged eccentrically with respect to the guide hole 17a. It is a state such as being.

  Moreover, in this embodiment, as shown in FIG. 1, the opening part by the side of the flat plate part of the guide hole 17a has the diameter expansion wall 17e to which an inner wall expands toward the flat plate part 42a of the movable core 42. Is preferred. As a result, the fluid collision in which the leaked fuel flowing out from the guide hole clearance 71 between the guide hole 17a and the small diameter shaft portion 42b directly collides with the lower end surface (hereinafter referred to as the first end surface) of the movable core 42 facing the support member 17. Can ease the power.

  Further, as shown in FIG. 1, a screw portion (hereinafter referred to as a male screw) 17r that can be screwed into a cylindrical screw portion (hereinafter referred to as a female screw) 11r of the nozzle holder 11 is provided on the outer peripheral portion of the support member 17. .

  When the male screw 17r and the female screw portion 11r are screwed together, the support member 17 and the nozzle holder 11 are screwed together with the support member 17 sandwiching the valve seat plate 16. This is because the support member 17 can be brought into close contact with the valve seat plate 16 while the valve members 42b and 41 are supported. Specifically, the valve seat plate 16 is sandwiched between the support member 17 and the nozzle holder 11 by the support member 17 being screwed into the female screw 11 r of the nozzle holder 11. The end surfaces of the support member 17 and the valve seat plate 16 in contact with each other in the drawing are in close contact with each other.

  As shown in FIGS. 1 and 2, the coil 61 is directly wound around a resin spool 62, and the outer periphery of the spool 62 and the coil 61 is covered with a resin mold (not shown). In addition, after the outer periphery of a coil (hereinafter referred to as a winding coil) 61 wound by a winding device is coated with a resin mold, a secondary resin molding is performed on the coated winding coil 61 and the spool 62 is molded integrally. It may be done. A terminal 51 is electrically connected to the end of the coil 61.

  As shown in FIGS. 1 and 2, the fixed core 63 is formed in a substantially cylindrical shape, and includes an inner peripheral side core portion, an outer peripheral side core portion, and an upper end portion connected to both the core portions, A coil 61 is sandwiched between the inner peripheral core portion and the outer peripheral core portion. The fixed core 63 is made of a magnetic material.

  A movable core 42 as a movable member is disposed on the lower side of the fixed core 63 in FIG. 1 so as to face the fixed core 63, and the lower end surface (hereinafter referred to as a magnetic pole surface) of the fixed core 63 and the upper surface of the movable core 42. End faces (hereinafter referred to as magnetic pole faces) are disposed so as to be close to and away from each other. Using electromagnetic force generated in the coil 61 by supplying current, magnetic flux flows from the magnetic pole surfaces of the inner peripheral side core portion and the outer peripheral side core portion toward the magnetic pole surface of the flat plate portion 42a of the movable core 42, and according to the magnetic flux density. A suction force acts on the movable core 42.

  A substantially cylindrical stopper 64 is inserted and disposed inside the fixed core 63, and is sandwiched and fixed between the fixed core 63 and the upper housing 53. A biasing member 59 such as a compression spring is disposed in the stopper 64. The urging force of the urging member 59 acts on the movable core 42 and urges the air gap between the magnetic pole surface of the movable core 42 and the magnetic pole surface of the fixed core 63 so as to widen. The end surface of the stopper 64 on the movable core side regulates the lift when the movable core 42 is fully lifted.

  Inside the stopper 64 and the upper housing 52 is formed a fuel passage 37 through which the fuel that has flowed out through the valve chamber 17c and the through hole 17b flows out to the low pressure side.

  As shown in FIGS. 1 and 2, the valve housings 52, 53, 54 include an upper housing 52, a retaining nut 52, an intermediate housing 54, and a support member 17 as a lower housing. The intermediate housing 54 is formed in a substantially cylindrical shape and accommodates the fixed core 63 so as to guide it. Specifically, the fixed core 63 is formed in a substantially bottomed cylindrical shape with a step, and is inserted into the inner peripheral side of the lower end portion of the intermediate housing 54. The outer periphery of the fixed core 63 is reduced in diameter downward from the stepped portion, and the stepped portion is locked to a step formed on the inner peripheral side of the intermediate housing 54, thereby fixing the fixed core 63. Is prevented from falling off the intermediate housing 54.

  As shown in FIG. 1, the movable core 42 includes a flat plate portion 42a formed in a substantially flat plate shape, and a small diameter shaft portion 42b as a valve member having a smaller diameter than the flat plate portion 42a. A magnetic pole surface is formed on the upper end surface of the flat plate portion 42a so as to face the magnetic pole surfaces of the inner core portion and the outer core portion. The movable core 42 is made of a magnetic material, and is formed of, for example, permendur. A small diameter shaft portion 42b is formed on the lower side of the flat plate portion 42a.

  A substantially spherical valve element 41 is provided on the end surface of the small-diameter shaft portion 42 b of the movable core 42. The small-diameter shaft portion 42 b of the movable core 42 can be seated and separated from the valve seat 16 d of the valve seat plate 16 via the valve body 41. The valve body 41 is a spherical body having a flat surface portion, and the flat surface portion is disposed so as to be able to be seated and separated from the valve seat 16d. The valve body 41 closes the out-orifice 16a as a communication path when the flat portion is seated. The flat surface portion constitutes a flat surface that is seated on and separated from the valve seat.

  In addition, the valve members 42b and 41 are not limited to those in which the valve body 41 is mounted in the small-diameter shaft portion 42b and seated and separated from the valve seat 16d via the valve body 41. You may seat and separate from the valve seat 16d directly by the end surface of the small diameter shaft part 42b without having.

  Here, the high pressure introduction passages 16a, 16b, 16c, the hydraulic pressure control chamber 8, and the fuel supply passage 11b constitute the high pressure side of the fuel passage described in the claims. Further, the valve chamber 17c, the through hole 17b, and the fuel passage 37 constitute the low pressure side of the fluid passage described in the claims.

  The operation of the fuel injection valve 2 having the above-described configuration will be described below. High pressure fuel is supplied from the common rail 4 as a high pressure source to the fuel reservoir chamber 12c through the high pressure pipe, the fuel supply path 11b, and the fuel delivery path 12d, and the hydraulic control chamber 8 through the fuel supply path 11b and the in-orifice 16a. , 16c is supplied with high pressure fuel.

  When the coil 61 is not energized, the movable core 42 and the valve members 42b and 41 are pressed against the valve seat 16d (downward in FIG. 1) by the biasing force of the biasing member 59, and the valve member 41 is pressed against the valve seat 16d. Sit down. The out orifice 16 d is closed by the seating of the valve members 42 b and 41, and the fuel flow from the hydraulic control chambers 8 and 16 c to the valve chamber 17 c, the guide hole gap 71, and the fuel passage 37 is blocked.

  At this time, the fuel pressure (hereinafter referred to as back pressure) stored in the hydraulic control chambers 8 and 16c is maintained at the same pressure as the fuel pressure inside the common rail 4 (hereinafter referred to as common rail pressure). Due to the back pressure stored in the hydraulic control chambers 8 and 16c, the acting force that urges the nozzle needle 20 in the nozzle hole closing direction via the control piston 30 (hereinafter referred to as the first acting force) and the urging force of the spring 35 The sum of the acting force that urges the nozzle needle 20 in the nozzle hole closing direction (hereinafter referred to as the second acting force) is received by the nozzle needle 20 in the nozzle hole opening direction by the common rail pressure in the vicinity of the fuel reservoir chamber 12c and the valve seat 12a. It is larger than the acting force (hereinafter referred to as third acting force). Therefore, the nozzle needle 20 is seated on the valve seat 12a, and the nozzle hole 12b is closed. Fuel is not injected from the nozzle hole 12b. The fuel pressure (back pressure) in the closed out orifice 16b (specifically, the outlet side inner periphery 16l) acts on the valve members 42b and 41 seated on the valve seat 16d.

  When energization of the coil 61 is started (hereinafter, when the fuel injection valve 2 is opened), an electromagnetic force is generated in the coil 61, and the magnetic attraction force generated between both magnetic pole surfaces of the fixed core 63 and the movable core 42 is generated. The movable core 42 is sucked in the direction of the fixed core 63. At this time, the valve members 42b and 41 are acted upon by the back pressure of the out-orifice 16b in the seating direction (hereinafter referred to as fourth acting force). It is separated from the seat 16d. When the valve members 42b and 41 are separated from each other, the valve members 42a and 41 move toward the fixed core 63 along the guide hole 17a.

  At this time, since the movable core 42 and the valve members 42b and 41 are separated from the valve seat 16d, the fuel flow that flows from the hydraulic control chambers 8 and 16c to the valve chamber 17c and the low-pressure passage 17d through the out orifice 16b flows. To do. Since the fuel in the hydraulic control chambers 8 and 16c is released to the low pressure side, the back pressure in the hydraulic control chambers 8 and 16c decreases. When the back pressure decreases, the first acting force gradually decreases. When the third acting force acting in the nozzle hole opening direction of the nozzle needle 20 becomes larger than the first acting force and the second acting force acting in the nozzle hole closing direction of the nozzle needle 20, the nozzle needle 20 moves to the valve seat 12a. It is further separated and lifts upward in FIG. When the nozzle needle 20 is lifted, the nozzle hole 12b is opened and fuel is injected from the nozzle hole 12b.

  Further, when energization of the coil 61 is stopped (hereinafter, when the fuel injection valve 2 is closed), the electromagnetic force of the coil 61 disappears, so that the urging force of the urging member 59 causes the movable core 42 and the valve member 42b, 41 moves in the direction of the valve seat 16d. When the flat surface portion 42b of the valve members 42b and 41 is seated on the valve seat 16d, the outflow of fuel from the hydraulic control chambers 8 and 16c to the valve chamber 17c and the guide hole gap portion 71 is stopped. Then, when the back pressure in the hydraulic control chambers 8 and 16c increases and the first acting force and the second acting force are greater than the third acting force, the nozzle needle 20 starts to move downward in FIG. When the nozzle needle 20 is seated on the valve seat 12a, the fuel injection is finished.

  Here, in order to reduce the bounce that occurs when the movable core 42 and the valve members 42b and 41 are valve seat 16d by the urging force of the urging member 59 when the fuel injection valve 2 is closed, A gap L between the facing surfaces 42ad and 18d with the fixing members 17 and 18 is set to a predetermined distance. As a result, when the movable core 42 moves in the direction of the valve seat 16d, a drag force in a direction opposite to the direction in which the movable core 42 and the valve members 42b and 41 move is formed by using the fluid resistance of the fuel existing in the gap L. And reduce bounce.

  In the present embodiment described above, a guide including an annular gap 72 and a stepped gap 73 that further enlarges the gap of the annular gap 72 between the guide hole 17a and the valve members 42b and 41. Since the hole clearance portion 71 is provided, a leak fuel passage through which leak fuel flows is formed between the guide hole 17a and the valve members 42b and 41.

  Thereby, when the coil 61 is energized and the movable core 42 and the valve members 42b and 41 are separated from the valve seat 16d by the suction force of the fixed core 63, the high pressure side and the low pressure side of the fuel passage are opened, and the valve Fuel flows through the out orifice 16a of the seat 16d. The inflowing fuel is in close contact with the valve seat plate 16 and the support member 17 in a state where the valve members 42b and 41 are supported. Therefore, the valve members 42b and 41 of the movable core 42 and the guide holes of the support member 17 are in contact with each other. Leakage fuel flows through the leak fuel passage formed between 17a and 17a.

  Therefore, each time the coil 61 is energized, the fuel guided to the leak fuel passage can smoothly slide between the valve members 42 b and 41 of the movable core 42 and the guide hole 17 a of the support member 17.

(Second Embodiment)
Hereinafter, other embodiments to which the present invention is applied will be described. In the following embodiments, the same or equivalent components as those in the first embodiment are denoted by the same reference numerals, and description thereof will not be repeated.

  A second embodiment is shown in FIG. In the second embodiment, a groove portion 17 d is formed on the second end surface (upper end surface) 17 g of the support member 17. FIG. 4 is a plan view showing a support member according to this embodiment. FIG. 5 is a cross-sectional view of the support member of FIG. 4 as viewed from the V direction.

  As shown in FIGS. 4 and 5, a groove portion 17 d is provided on the second end surface (upper end surface) 17 g of the support member 17, and the bottom portion of the groove portion 17 d is the tip of the external screw 17 r on the outer peripheral portion of the support member 17. Thus, a step 17f on the outer peripheral side of the second end face (upper end face) 17g is formed.

  In general, when the gap between the support member and the movable core facing each other (the space corresponding to the dimension L in FIG. 2) is relatively small, the fuel flowing between the gaps is relatively relatively distributed in the circumferential direction between the gaps. It may be difficult to flow.

  On the other hand, as in the present embodiment, it is preferable to provide a groove portion 17d on the second end surface (upper end surface) 17g of the support member 17 and arrange the groove portion 17d so as to communicate with the leak fuel passage. In the present embodiment, one end of the groove portion 17d is connected to a diameter-expanding wall on the opening side of the guide hole 17a. Thereby, the leak fuel flowing out from the leak fuel passage is not restricted when flowing along the gap between the support member 17 and the flat plate portion 42a of the movable core 42.

  Moreover, it is preferable that the said groove part 17d is provided in multiple places in the circumferential direction of the 2nd end surface (upper end surface) 17g.

  As a result, when the groove portion 17d secures a flow passage area where the leaked fuel flowing along the gap between the support member 17 and the movable core 42 is not restricted, the necessary flow passage area is reduced by the plurality of groove portions 17d. Since it can be divided, each groove portion 17d does not significantly hinder the function of the outer shape of the support member 17. For example, even when the support member 17 has the external thread 17r on the outer peripheral portion, it is possible to suppress a decrease in the effective thread length of the external thread 17r.

  Moreover, it is preferable that the said groove part 17d is arrange | positioned at substantially equal intervals along the circumferential direction of the 2nd end surface (upper end surface) 17g.

  In general, when the air gap between the support member 17 and the movable core 42 facing each other is relatively small, the fuel flowing into the gap may not flow evenly in the circumferential direction between the gaps. . When the air does not flow evenly in the circumferential direction between the gaps, the fluid force of the fuel does not act uniformly around the circumferential direction of the first end face (magnetic pole surface) of the movable core 42. For example, the movable core 42 and the valve member 42b , 41, the seating operation (valve closing operation) on the valve seat 16d of the movable core 42 and the valve members 42b, 41 may become unstable.

  On the other hand, since the groove portion 16d is arranged at substantially equal intervals along the circumferential direction of the second end surface (upper end surface) 17g, the fluid force caused by the fuel flowing in the groove portion 16d is changed in the circumferential direction of the first end surface (magnetic pole surface). It is made to act at equal intervals around. As a result, the seating operation (valve closing operation) of the movable core 42 and the valve members 42b and 41 on the valve seat can be stabilized.

  The groove 17d preferably has a two-sided width W extending outward from the leak fuel passage side.

  In general, as a method of bringing the support member 42 into close contact with the valve seat plate 16 having the valve seat 16d while supporting the valve members 42b and 41, for example, the support member 17 is screwed into the housing (nozzle holder) with the valve seat plate interposed therebetween. It is concluded. In order to screw the support member to the housing, a tightening jig for screwing the support member is required. When tightening in a state where the tightening jig is inserted and fitted into the hole using a hole defining the fuel communication path provided in the support member, There was a problem that hitting or the like was likely to occur and tightening work was not easy.

  In contrast, in the present embodiment, the support member 17 is provided with the groove portion 17d having a two-sided width W extending outward from the leak fuel passage side. Therefore, the two-sided width W of the groove portion 17d is used. It is possible to perform the tightening operation in a state where the tightening jig is fitted to the width W of the two surfaces. In addition, since the tightening operation by fitting the two-surface width W and the tightening jig is relatively easy, the tightening operation can be improved.

(Third embodiment)
A third embodiment is shown in FIG. The third embodiment is an expansion to the radial clearance δ2 when the guide hole gap in the prior art is only an annular gap. FIG. 6 is a partial cross-sectional view showing the valve member and the support member according to the present embodiment.

  It is preferable that δ2 of the annular clearance 172 with the enlarged radial clearance δ2 is set in a range of 10 μm to 20 μm.

  Thereby, the guide hole between the valve members 42b and 41 and the guide hole 17a can be enlarged by a relatively slight change in configuration so as to enlarge the gap compared to the conventional annular gap and set the gap in the range of 10 μm to 20 μm. A fuel flow can be generated in the gap, and it is possible to prevent a decrease in slidability between the valve members 42b and 41 and the guide hole 17a regardless of the type of fuel used.

  In addition, in the set gap range, if the gap outside the set gap range is less than 10 μm, the fuel flow may be delayed, and there is a possibility that the leaked fuel hardly flows. On the other hand, when the gap exceeds 20 μm, the inclination of the movable core 42 and the valve members 42b and 41 supported by the support member 17 exceeds the allowable inclination, which may affect the performance of the electromagnetic valve 7. is there. For example, if the clearance exceeds the allowable inclination of the valve members 42b and 41, the valve members 42b and 41 may not reliably close the valve seat 16d when the valve is closed. For this reason, the fuel injection characteristics of the fuel injection valve 2 using the electromagnetic valve 7 may be affected.

(Fourth embodiment)
A fourth embodiment is shown in FIG. The fourth embodiment is an example in which the stepped gap portion 74 is formed by the step of the guide hole 17 in the case where the guide hole gap portion 71 includes the annular gap portion 72 having the stepped gap portion. FIG. 7 is a partial cross-sectional view showing a valve member and a support member according to the embodiment.

  The guide hole gap portion 71 includes an annular gap portion 72 and a step-like gap portion 74, and the inner periphery of the guide hole 271a is formed with a step having a portion 217b of the peripheral wall recessed outward. The step-shaped gap 73 is formed to be larger than the predetermined gap δ1 by using the step, and the annular gap 72 is expanded to at least δ4 mim at least.

(Fifth embodiment)
A fifth embodiment is shown in FIG. The fifth embodiment is an example in which the low-pressure fuel passage of the electromagnetic valve 7 is applied to the fuel injection valve 2 that returns to the nozzle holder 11 that is a housing. FIG. 8 is a partial cross-sectional view showing the electromagnetic valve of the present embodiment.

  As shown in FIG. 8, the support member 17 is provided with a second through-hole 317p, in addition to the guide hole 17a and the guide hole 17a.

  On the outer wall of the valve seat plate 16, as described above, a two-sided width surface (see FIG. 8) is formed. A gap formed between the width across the two surfaces and the inner wall of the nozzle holder 11 is disposed in the second through hole 317p, and the second end surface (upper end surface) 17g side of the support member 17 and the opposite surface thereof. The side communicates with the inside and outside. The nozzle holder 11 is provided with a low-pressure fuel passage 11c so as to communicate with the second through hole 317p.

  Even with such a configuration, the same effect as in the first embodiment can be obtained.

(Other embodiments)
(1) In the present embodiment described above, the valve members 42b and 41 are mounted on the valve seat 16d via the valve body 41, and the valve body 41 is mounted in the small-diameter shaft portion 42b as described above. As explained. The valve member is not limited to the valve member 41 mounted in the small-diameter shaft portion 42b and seated on and away from the valve seat 16d via the valve body 41, but the small-diameter shaft without the valve body. It may be seated and separated directly from the valve seat 16d at the end face of the part.

  (2) In the first, second, fourth, and fifth embodiments described above, the radial clearance δ1 of the annular gap portion 72 of the guide hole gap portion 71 is less than 10 μm, which is equivalent to the conventional technology. It has been described that it is set with a predetermined non-zero gap. Not limited to this, it may be set in the range of 10 μm to 20 μm as in the third embodiment.

It is a fragmentary sectional view which shows the solenoid valve applied to the fuel-injection apparatus of the 1st Embodiment of this invention. It is sectional drawing which shows the fuel-injection apparatus of 1st Embodiment. FIG. 2 is a partial cross-sectional view showing the periphery of a sliding gap between the valve member and the support member in FIG. 1. It is a top view which shows the supporting member concerning 2nd Embodiment. It is sectional drawing which looked at the supporting member of FIG. 4 from the V direction. It is a fragmentary sectional view showing a valve member and a support member concerning a 3rd embodiment. It is a fragmentary sectional view showing a valve member and a supporting member concerning a 4th embodiment. It is a fragmentary sectional view which shows the solenoid valve of 5th Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Fuel injection apparatus 2 Fuel injection valve 11 Nozzle holder (housing)
11b Fuel supply passage (high pressure fuel passage)
11c Fuel escape passage (leak recovery passage)
11d 2nd needle accommodation hole (accommodation hole)
11r Female thread (thread part)
12 Nozzle body 12b Injection hole 12c Fuel reservoir 12d Fuel delivery path (high pressure fuel path)
12e 1st needle accommodation hole (accommodation hole)
16 Valve seat plate (valve seat member)
16a Out orifice (orifice, communication path)
16b In-orifice (orifice)
16c Pressure control chamber (pressure control chamber)
16d Valve seat 17 Support member 17a Guide hole (through hole)
17e Expanded wall 17f Step 17r Male thread (threaded part)
17g Upper end surface (second end surface)
20 Nozzle needle 30 Control piston 30c Needle part 31 Annular member 35 Spring (biasing member)
41 valve body 41b plane part 42 movable core (movable member)
42a Flat plate part 42ad Opposing surface 42b Small diameter shaft part (valve member)
42ba 1st peripheral wall 42bb 2nd peripheral wall 59 Energizing member 61 Coil 63 Fixed core 7 Electromagnetic valve 71 Guide hole clearance part 72 Annular clearance part 73 Step-shaped clearance part 8 Hydraulic control chamber (pressure control chamber)

Claims (13)

In a solenoid valve that shuts off and circulates the fuel flow between the high pressure side and the low pressure side of the fuel passage,
A valve seat member comprising a valve seat having a communication passage communicating the high pressure side and the low pressure side of the fuel passage;
A valve member that closes and opens the high-pressure side and the low-pressure side of the fuel passage by being seated and separated from the valve seat;
A support member having a guide hole, movably supporting the valve member in the guide hole, and capable of closely contacting the valve seat member in a state of supporting the valve member;
A movable core that is disposed on the side of the support member opposite to the valve seat member and is opposed to the support member, and is movable in the axial direction in cooperation with the valve member;
A stationary core capable of attracting the movable core when the coil is energized,
An electromagnetic valve characterized in that a leak fuel passage for flowing leak fuel is defined between the valve member of the movable core and the guide hole of the support member. The leak fuel passage is formed by a gap between the outer periphery of the valve member and the inner periphery of the guide hole,
The electromagnetic valve according to claim 1, wherein the gap is set in a range of 10 μm to 20 μm. The leak fuel passage is formed at least from a gap between the outer periphery of the valve member and the inner periphery of the guide hole,
The step part which expands the said clearance gap is provided in a part of circumferential direction of either the outer periphery of the said valve member, or the inner periphery of the said guide hole, The Claim 1 or Claim 2 characterized by the above-mentioned. The solenoid valve described in 1.   The electromagnetic valve according to claim 3, wherein the step portion is provided at a plurality of locations in a circumferential direction of the peripheral wall.   The electromagnetic valve according to claim 4, wherein the stepped portions are arranged at substantially equal intervals along a circumferential direction of the peripheral wall. The opening of the guide hole has a diameter-enlarging surface that increases the size of the inner periphery of the guide hole,
6. The diameter expansion surface according to claim 1, wherein the inner diameter is increased toward the first end surface of the movable core facing the support member. Solenoid valve. The support member has a groove formed on a second end surface facing the movable core,
The electromagnetic valve according to any one of claims 1 to 6, wherein the groove portion communicates with the leak fuel passage.   The electromagnetic valve according to claim 7, wherein the groove is provided at a plurality of locations in a circumferential direction of the second end surface.   The electromagnetic valve according to claim 8, wherein the groove portions are arranged at substantially equal intervals along a circumferential direction of the second end surface.   10. The electromagnetic valve according to claim 7, wherein the groove portion has a two-surface width extending outward from the leak fuel passage side. 11. The solenoid valve according to any one of claims 1 to 10 is fastened to a housing,
The support member includes a screw portion that is screwed into the housing,
The electromagnetic valve according to claim 1, wherein the support member is in close contact with the valve seat member by sandwiching the valve seat member and fastening it in the housing. The fuel injection device using the solenoid valve according to claim 11,
An injection hole for injecting fuel, and a nozzle part having a nozzle needle for opening and closing the injection hole,
A nozzle body having a pressure control chamber in which high-pressure fuel for urging the nozzle needle in the nozzle hole closing direction is stored;
The fuel injection device according to claim 1, wherein the housing is formed in the nozzle body.   The fuel injection device according to claim 12, wherein the pressure control chamber in which the high-pressure fuel is stored is on a high-pressure side of the fuel passage.

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