JP5748796B2 - Fuel injection valve - Google Patents

Description

  The present invention relates to a fuel injection valve used for supplying fuel to an internal combustion engine of an automobile, and more particularly to a fuel injection valve that achieves both atomization promotion in spray characteristics and improvement in freedom of injection direction. .

  In recent years, while fuel efficiency regulations and exhaust gas regulations for automobiles and the like have been strengthened, atomization of fuel spray injected from a fuel injection valve has been demanded. For this reason, in the conventional fuel injection valve, the injection hole inlet is disposed on the inner side with respect to the main flow of the fuel flow from the valve seat, and the cavity flow path area immediately above the injection hole is rapidly reduced. As a result, fuel flow with a large entry angle at the nozzle hole inlet is promoted, and atomization of the fuel spray is achieved (for example, see Patent Document 1).

  In another conventional fuel injection valve, the length of the radially outer nozzle hole is shorter than the diameter of the radially inner nozzle hole with respect to the fuel injection valve shaft. Thereby, atomization of fuel spray is achieved with a simple structure (see, for example, Patent Document 2).

JP 2007-1000051 A JP 2004-137931 A

  In recent automobile gasoline internal combustion engines, one fuel injection valve is mounted per cylinder in order to improve controllability of fuel supply into the cylinder. In order to achieve both improved output and improved fuel efficiency, there are almost two intake ports per cylinder. In that case, the fuel injection valve directs fuel in two directions toward each intake port. It is required to be injected.

  In the fuel injection valve disclosed in Patent Document 1, in order to inject fuel in two directions, the injection holes arranged in the injection hole plate are jets that form a collective spray in two directions with a plurality of injection holes. It is necessary to make the hole direction. However, when the nozzle holes are arranged at a wide interval, the direction of the nozzle holes projected perpendicular to the plane perpendicular to the valve seat axis has a predetermined angle with respect to the radial direction from the valve seat axis. Therefore, when the main flow of the fuel flow from the valve seat to the injection hole inlet is projected perpendicularly to the plane, the injection hole direction does not face the main flow of the fuel flow.

  For this reason, after the fuel collides with the inner wall of the nozzle hole, a flow for spreading the liquid film along the inner wall of the nozzle hole is not sufficiently formed, and the fuel cannot be efficiently converted into a liquid film, There was a problem that it was difficult to atomize.

  On the other hand, in the above plane, in order to efficiently spread the fuel liquid film along the inner wall of the nozzle hole, when the nozzle hole direction is the radial direction so that the main flow of the fuel flow and the nozzle hole direction are opposed, In order to form a collective spray in two directions at the nozzle holes, it is necessary to dispose the nozzle holes in the direction of the respective collective sprays. However, in such an arrangement, there is a problem that the liquid films interfere with each other at the stage of the liquid film immediately after being sprayed and before being divided into sprays immediately after being jetted, thereby worsening atomization. . In particular, the large flow rate specification or the specification aiming at atomization spray has many injection holes, and the influence is remarkable.

  Further, since the nozzle holes are arranged so as to be offset in the direction of the respective collective sprays, the nozzle holes at the end of the nozzle hole group are more than the main flow of the fuel flow from the valve seat to the nozzle hole inlet. The side flow from the valve seat seat part to the nozzle hole inlet where the nozzle hole is not arranged on a radial straight line from the valve seat axis, and the U-turn flow from the valve seat axis once to the nozzle hole inlet Becomes stronger. For this reason, there was a problem that fuel thinning was hindered, atomization deteriorated, and the degree of freedom in the injection direction and atomization could not be made compatible.

  Furthermore, in the conventional fuel injection valve shown in Patent Document 2, a recess is formed in correspondence with the nozzle hole outlet of each nozzle hole, and straddles the radially inner surface of the valve seat axis of this recess. A nozzle hole is formed as described above. As a result, a portion of the nozzle hole on the radially outer side of the valve seat axis is cut away, and the nozzle hole length on the radially outer side than the nozzle hole length on the radially inner side with respect to the fuel injection valve shaft center. Has been shortened.

  However, in order to form a two-way collective spray while efficiently atomizing the fuel, when the main flow of the fuel flow from the valve seat portion toward the nozzle hole inlet and the nozzle hole are projected onto the plane, the fuel flow It is necessary to dispose the nozzle holes so as to be offset in the direction of the collective spray so that the nozzle holes face the main stream. For this reason, there is a problem in that the recesses having a diameter larger than that of the nozzle hole approach each other, the liquid films ejected from this interfere with each other, and the atomization is deteriorated. In particular, the effect was more prominent as the number of nozzle holes was increased aiming at atomization.

  The present invention has been made to solve the above-described problems, and an object thereof is to obtain a fuel injection valve capable of improving the degree of freedom in the injection direction while promoting atomization of the injected fuel. And

  The fuel injection valve according to the present invention has a seat surface that is inclined so that the diameter is gradually reduced toward the downstream side, and a valve seat opening provided on the downstream side of the seat surface. A valve body that abuts against the valve seat and the seat surface to prevent fuel from flowing out from the valve seat opening, and that is separated from the seat surface to allow fuel outflow from the valve seat opening, and a downstream end surface of the valve seat And a nozzle hole plate having a plurality of nozzle holes for injecting fuel that has flowed out of the valve seat opening to the outside, the nozzle hole plate being a virtual conical surface extending the seat surface downstream And the upstream end face of the nozzle hole plate are arranged so as to intersect with each other to form a virtual circle. The nozzle hole is adjacent to the nozzle hole main body and downstream of the nozzle hole main body and constitutes the outlet of the nozzle hole. The diameter of the large-diameter part is larger than the diameter of the nozzle hole body. The inlet part of the nozzle hole body is located closer to the valve seat axis than the valve seat opening, which is the smallest inner diameter of the valve seat, and the nozzle hole is projected perpendicularly to a plane perpendicular to the valve seat axis. In this case, the inlet center and the outlet center of the nozzle hole body on the plane are arranged side by side on a radial straight line passing through the valve seat axis, and the outlet center is away from the valve seat axis with respect to the inlet center. Since the center of the large diameter portion is offset with respect to the straight line, the inner wall length of the nozzle hole on the valve seat axis side of the nozzle hole body is asymmetric with respect to the straight line.

  The fuel injection valve of the present invention can improve the degree of freedom in the injection direction while promoting atomization of the injected fuel.

It is sectional drawing in alignment with the axis line of the fuel injection valve by Embodiment 1 of this invention. It is a figure which combines and shows the enlarged view of the valve seat of FIG. 1, a nozzle hole plate, and a ball | bowl, and the top view which shows the center part of a nozzle hole plate. It is sectional drawing which expands and shows the III section of FIG. It is a top view which expands and shows the IV section of FIG. It is a graph which shows the time change of the spray particle size at the time of the fuel injection by the fuel injection valve of FIG. It is a figure which combines and shows the sectional view of the valve seat of the fuel injection valve by Embodiment 2 of this invention, a nozzle hole plate, and a ball | bowl, and the top view which shows the center part of a nozzle hole plate. It is sectional drawing which expands and shows the VII part of FIG. It is a top view which expands and shows the VIII part of FIG. It is sectional drawing which expands and shows the nozzle hole of the fuel injection valve by Embodiment 3 of this invention. It is a figure which combines and shows the sectional view of the valve seat of the fuel injection valve by Embodiment 4 of this invention, a nozzle hole plate, and a ball | bowl, and the top view which shows the center part of a nozzle hole plate. It is sectional drawing which expands and shows the XI part of FIG. It is a top view which expands and shows the XII part of FIG.

Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
1 is a cross-sectional view taken along the axis of a fuel injection valve according to Embodiment 1 of the present invention. Fuel flows downward from the upper end of the fuel injection valve of FIG. In the figure, a cylindrical fixed iron core 2 is fixed to the upper end of the magnetic pipe 1. The magnetic pipe 1 and the fixed iron core 2 are arranged coaxially. Further, the magnetic pipe 1 is press-fitted and welded to the downstream end portion of the fixed iron core 2.

  A valve seat 3 and an injection hole plate 4 are fixed to the lower end portion in the magnetic pipe 1. The nozzle hole plate 4 is provided with a plurality of nozzle holes 5 for injecting fuel. The nozzle hole 5 penetrates the nozzle hole plate 4 in the thickness direction.

  The nozzle hole plate 4 is fixed to the magnetic pipe 1 by the second welded portion 4b after being inserted into the magnetic pipe 1 while being fixed to the downstream end face of the valve seat 3 by the first welded portion 4a. Has been.

  In the magnetic pipe 1, there are a ball 6 as a valve body, a needle pipe 7 welded and fixed to the ball 6, and an armature fixed to the upstream end (the end opposite to the ball 6) of the needle pipe 7. (Movable iron core) 8 is inserted. The amateur 8 is press-fitted into the upstream end portion of the needle pipe 7 and welded.

  The amateur 8 can slide in the axial direction within the magnetic pipe 1. On the inner peripheral surface of the magnetic pipe 1, a guide portion 1 a that guides the sliding of the armature 8 is provided. As the amateur 8 slides, the needle pipe 7 and the armature 8 also move together in the axial direction. Thereby, the ball 6 is seated / separated from the valve seat 3. Further, the upper end surface of the armature 8 is brought into contact with and separated from the lower end surface of the fixed iron core 2. A chamfered portion 6 a is provided on the outer periphery of the ball 6.

  A compression spring 9 that presses the needle pipe 7 in the direction of pressing the ball 6 against the valve seat 3 is inserted into the fixed iron core 2. An adjuster 10 for adjusting the load of the compression spring 9 is fixed in the fixed iron core 2. Further, a filter 11 is inserted into the upper end portion of the fixed iron core 2 serving as a fuel introduction portion.

  An electromagnetic coil 12 is fixed to the outer periphery of the downstream end (the armature 8 side end) of the fixed iron core 2. The electromagnetic coil 12 has a resin bobbin 13 and a coil body 14 wound around the outer periphery thereof. Between the magnetic pipe 1 and the fixed iron core 2, a metal plate (magnetic circuit constituent member) 15 which is a yoke portion of the magnetic circuit is fixed by welding.

  The magnetic pipe 1, the fixed iron core 2, the electromagnetic coil 12, and the metal plate 15 are integrally formed in a resin housing 16. The resin housing 16 is provided with a connector portion 16a. A terminal 17 that is electrically connected to the coil body 14 is drawn into the connector portion 16a.

  2 is an enlarged view of the valve seat 3, the nozzle hole plate 4 and the ball 6 of FIG. 1, and a plan view showing the central part of the nozzle hole plate 4 (the part exposed to the fuel flow path is indicated by the arrow II from the ball 6 side). It is a figure which combines and shows the figure seen along.

  In the valve seat 3, a seat surface 3a to which the ball 6 is brought into contact with and separated from is provided. The seat surface 3a is inclined so that its diameter is gradually reduced toward the downstream side. A circular valve seat opening 3b facing the nozzle hole plate 4 is provided at the center of the downstream end of the valve seat 3 on the downstream side of the seat surface 3a.

  The ball 6 is in contact with the seat surface 3a to prevent the fuel from flowing out from the valve seat opening 3b, and is separated from the seat surface 3a to allow the fuel to flow out from the valve seat opening 3b. The nozzle hole plate 4 is arranged such that a virtual conical surface 18a that extends the sheet surface 3a downstream and an upstream end surface of the nozzle hole plate 4 intersect to form a virtual circle 18b.

  Each nozzle hole 5 includes a nozzle hole body 5a and a large-diameter portion 5b adjacent to the downstream side of the nozzle hole body 5a and constituting the outlet of the nozzle hole 5. That is, the nozzle hole main body 5a and the large diameter portion 5b are in a one-to-one correspondence. Further, the inlet portion of each nozzle hole main body 5 a is disposed on the valve seat axis 3 c side with respect to the valve seat opening 3 b which is the minimum inner diameter of the valve seat 3.

  Furthermore, each large-diameter portion 5b has a cylindrical shape centered on an axis perpendicular to the nozzle hole plate 4 (parallel to the valve seat axis 3c). Furthermore, the diameter of each large diameter part 5b is larger than the diameter of the corresponding nozzle hole main body 5a.

  Further, at the center of the nozzle hole plate 4, a convex portion 4 c is provided that is curved so as to protrude to the downstream side in parallel (or substantially parallel) to the tip portion of the ball 6. A flat nozzle hole plate flat portion 4d is provided around the convex portion 4c. The nozzle hole 5 is provided in the nozzle hole plate flat part 4d.

  FIG. 3 is an enlarged cross-sectional view showing a portion III in FIG. 2, and FIG. 4 is an enlarged plan view showing a portion IV in FIG. When each nozzle hole 5 is projected perpendicularly to a plane perpendicular to the valve seat axis 3c, the inlet center (center of the upstream end) 5c and outlet center (large diameter portion 5b) of the nozzle hole body 5a on the plane are shown. The center of the side end portion 5d is arranged side by side on a radial straight line 19 passing through the valve seat axis 3c. The outlet center 5d is disposed in a direction away from the valve seat axis 3c with respect to the inlet center 5c.

  That is, the nozzle hole main body 5a is inclined so as to advance outward in the radial direction of the nozzle hole plate 4 as it goes downstream.

  When each nozzle hole 5 is projected perpendicularly to a plane orthogonal to the valve seat axis 3c, the outlet center (center of the downstream end) 5e of the large diameter part 5b is the outlet center of the nozzle hole body 5a. It is located farther from the valve seat axis 3c than 5d and offset from the straight line 19 in the desired injection direction.

  Next, the operation of the fuel injection valve will be described. When an operation signal is sent from the engine control device to the drive circuit of the fuel injection valve, a current flows through the electromagnetic coil 12 via the terminal 17, and the armature 8, the fixed iron core 2, the metal plate 15, and the magnetic pipe 1 are configured. Magnetic flux is generated in the magnetic circuit.

  Thereby, the armature 8 is attracted | sucked to the fixed iron core 2 side, and the armature 8, the needle pipe 7, and the ball | bowl 6 which are integral structures move upward of FIG. When the ball 6 is separated from the valve seat 3 and a gap is generated between the ball 6 and the valve seat 3, the fuel passes through the gap between the chamfered portion 6 a of the ball 6 and the valve seat 3 and passes through the nozzle hole 5. It is injected into the engine intake pipe.

  Next, when an operation stop signal is sent from the engine control device to the drive circuit of the fuel injection valve, energization to the electromagnetic coil 12 is stopped, the magnetic flux in the magnetic circuit is reduced, and the spring force of the compression spring 9 The amateur 8, the needle pipe 7 and the ball 6 move downward in FIG. Thereby, the clearance gap between the ball | bowl 6 and the valve seat 3 is closed, and fuel injection is complete | finished.

  In such a fuel injection valve, when the fuel flow toward the inlet of the nozzle hole 5 at the time of fuel injection is projected perpendicularly to a plane perpendicular to the valve seat axis 3c, the center of the inlet of the nozzle hole body 5a is projected from the seat surface 3a. As shown in the plan view of FIG. 2, the main flow of the fuel flow directly toward 5c is a flow 20a toward the valve seat axis 3c.

  Further, when the nozzle hole body 5a is projected perpendicularly to the plane, the nozzle hole body 5a is directed in the radial direction about the valve seat axis 3c. The direction of the nozzle hole main body 5a faces the main flow 20a of the fuel in the plane described above.

  Thereby, after the fuel collides with the nozzle hole body 5a, the flow in which the liquid film of the fuel is thinly spread along the inner wall of the nozzle hole body 5a is further strengthened. Therefore, the fuel can be thinned efficiently and atomization can be promoted.

  Further, the fuel flows from the nozzle hole body 5a into the large diameter portion 5b, so that the liquid film is further thinned while changing the flow direction along the curvature of the inner wall of the large diameter portion 5b. Thereby, atomization can be further promoted.

  Furthermore, the fuel liquid film spreading along the inner wall of the nozzle hole 5 on the valve seat axis 3c side changes the flow direction along the curvature of the inner wall of the nozzle hole 5 as it goes downstream. For this reason, the target single spray angle (= 1) is adjusted by adjusting the ratio of the inner wall length L on the valve seat axis 3c side of the nozzle hole body 5a to the diameter d of the nozzle hole body 5a (hereinafter referred to as L / d). (Spreading angle of spray sprayed from one nozzle hole 5). That is, if L / d is decreased, the single spray angle can be increased, and if L / d is increased, the single spray angle can be decreased.

  In Embodiment 1, when projected perpendicularly to the plane, the outlet center 5e of the large-diameter portion 5b is arranged farther from the valve seat axis 3c than the outlet center 5d of the nozzle hole body 5a. And offset with respect to the straight line 19 in the desired injection direction.

  For this reason, the length L is asymmetric with respect to the radial straight line 19, the L / d in the desired injection direction with respect to the radial straight line 19 is small, and the L / d in the opposite direction is large. As a result, the fuel flow becomes as indicated by the arrows 20d and 20e in FIG. 4, and the fuel can be injected in a desired injection direction.

  Further, the injection direction can be optimized by adjusting the inner wall length L for each injection hole 5 by adjusting the axial length (depth) dimension L1 or the offset amount of the large diameter portion 5b. it can.

  At the start of injection, fuel in a space (dead volume) surrounded by the inner wall of the valve seat 3 downstream of the seat surface 3a, the upstream end surface of the nozzle hole plate 4, and the tip of the ball 6 is injected. Since it is discharged from the hole 5, the injection speed is lower than that at the time of steady injection after completion of the valve opening operation of the ball 6. For this reason, the initial spray at the start of injection tends to have a larger spray particle size than at the time of steady injection. It is in.

  On the other hand, in the first embodiment, the virtual conical surface 18a extending the downstream side of the seat surface 3a and the upstream end surface of the nozzle hole plate 4 intersect to form a virtual circle 18b. The dead volume is made small by arranging. For this reason, the injection amount of the initial spray having a large particle size can be reduced, and as shown in FIG. 5, the particle size of the entire spray including the initial spray and the steady spray can be reduced.

  In addition, since the dead volume is small, the amount of fuel evaporation in the dead volume during injection suspension under high temperature negative pressure is reduced, and the change in injection amount (static flow rate / dynamic flow rate) due to changes in temperature and atmospheric pressure is reduced. can do.

  Further, as shown in the plan view of FIG. 2, the fuel flow downstream from the seat surface 3a passes between the nozzle holes 5 in addition to the main flow 20a of the fuel flowing directly from the seat surface 3a to the inlet of the nozzle hole body 5a. A fuel flow 20b is included. Further, the flow 20 b collides with the fuel flowing from the opposite side at the center of the nozzle hole plate 4, and becomes a U-turn flow 20 c toward the nozzle hole 5.

  In the first embodiment, since the convex portion 4c that is curved so as to protrude downstream in parallel to the tip portion of the ball 6 is provided at the center of the nozzle hole plate 4, as shown in FIG. The flow 20c becomes a flow along the convex part 4c, and it is difficult to flow into the nozzle hole 5 provided in the nozzle hole plate flat part 4d outside the convex part 4c.

  On the other hand, the main flow 20a of the fuel sinks under the U-turn flow 20c and easily collides with the upstream side of the inner wall of the nozzle hole body 5a. Thereby, the effective length of the inner wall of the injection hole main body 5a necessary for expanding the liquid film can be increased, the fuel can be efficiently thinned, and atomization can be promoted.

  Further, as shown in the cross-sectional view of FIG. 2, the valve seat shaft on the seat surface 3 a and the upstream end surface of the nozzle hole plate 4 while avoiding interference between the tip of the ball 6 and the nozzle hole plate 4 at the time of valve closing. The distance from the vicinity of the center 3c can be shortened, and the virtual circle 18b can be enlarged.

  Thereby, the inlet center 5c of the nozzle hole body 5a arranged in the nozzle hole plate flat part 4d outside the convex part 4c can be arranged inside the virtual circle 18b, and along the inner wall of the nozzle hole body 5a. The flow for spreading the liquid film can be further strengthened. Therefore, the fuel can be thinned efficiently and atomization can be promoted.

  Furthermore, the dead volume can be further reduced while avoiding interference between the tip of the ball 6 and the nozzle hole plate 4 when the valve is closed, so that the injection amount of the initial spray having a large particle size can be further reduced, and the initial spray can be reduced. And the particle size of the entire spray combined with the steady spray can be further reduced.

Embodiment 2. FIG.
Next, FIG. 6 is a cross-sectional view of the valve seat 3, the injection hole plate 4 and the ball 6 of the fuel injection valve according to Embodiment 2 of the present invention, and a plan view showing the central part of the injection hole plate 4 FIG. 7 is an enlarged cross-sectional view of the VII portion of FIG. 6, and FIG. 8 is a VIII portion of FIG. 6. It is a top view which expands and shows.

  In the first embodiment, the projection 4c is provided at the center of the nozzle hole plate 4, but in the second embodiment, the center of the nozzle hole plate 4 is flat. Further, in the second embodiment, a flat portion 6 b parallel to (or substantially parallel to) the nozzle hole plate 4 is provided at the tip of the ball 6. The flat portion 6 b faces the center of the upstream end face of the nozzle hole plate 4. When projected perpendicularly to a plane orthogonal to the valve seat axis 3c, the flat portion 6b is provided on the inner diameter side of the inlets of all the nozzle hole main bodies 5a. Other configurations are the same as those in the first embodiment.

  In the plan view of FIG. 6, the flow path cross-sectional area of the fuel flow 20 b passing between the nozzle holes 5 and going to the center of the nozzle hole plate 4 is rapidly reduced when passing through a portion facing the flat portion 6 b. For this reason, a pressure loss increases and the speed of the flow 20b falls in the part facing the flat part 6b.

  Along with this, the speed of the U-turn flow 20c also decreases, so that the U-turn flow 20c hardly flows into the nozzle hole 5. For this reason, as shown in FIG. 7, at the inlet of the nozzle hole body 5a, the main flow 20a of the fuel can overcome the U-turn flow 20c and collide with the upstream side of the inner wall of the nozzle hole body 5a.

  As a result, the effective length of the inner wall of the nozzle hole body 5a necessary for widening the liquid film can be increased, the fuel can be efficiently thinned, and atomization can be further promoted. .

  6, the valve seat between the seat surface 3a and the upstream end surface of the nozzle hole plate 4 while avoiding interference between the tip of the ball 6 and the nozzle hole plate 4 when the valve is closed. The distance in the direction of the axis 3c can be shortened. Thereby, the virtual circle 18b can be enlarged and the inlet center 5c of the nozzle hole body 5a can be arranged inside the virtual circle 18b. Therefore, the flow for expanding the liquid film along the inner wall of the nozzle hole main body 5a is further strengthened, and the fuel can be effectively thinned and atomization can be promoted.

  Furthermore, the dead volume can be further reduced while avoiding interference between the tip of the ball 6 and the nozzle hole plate 4 when the valve is closed. Thereby, the injection amount of the initial spray having a large particle size can be further reduced, and the particle size of the entire spray including the initial spray and the steady spray can be further reduced.

Embodiment 3 FIG.
Next, FIG. 9 is an enlarged sectional view showing the injection hole 5 of the fuel injection valve according to Embodiment 3 of the present invention. In Embodiment 3, in the flow path of the nozzle hole body 5a, a cylindrical portion 5f having a minimum cross-sectional area is provided between the inlet and the outlet of the nozzle hole body 5a. Other configurations are the same as those in the first embodiment.

  In such a fuel injection valve, since the flow rate of the fuel in the nozzle hole 5 is determined by the cross-sectional area of the cylindrical portion 5f, the flow rate variation due to the variation in the position of the nozzle hole body 5a and the large diameter portion 5b can be suppressed.

  A cylindrical portion 5f may be provided on the nozzle hole body 5a of the second embodiment. That is, Embodiments 2 and 3 may be combined.

Embodiment 4 FIG.
Next, FIG. 10 is a cross-sectional view of the valve seat 3, the nozzle hole plate 4 and the ball 6 of the fuel injection valve according to Embodiment 4 of the present invention, and a plan view showing the central part of the nozzle hole plate 4 FIG. 11 is an enlarged cross-sectional view of the XI portion of FIG. 10, and FIG. 12 is a XII portion of FIG. 10. It is a top view which expands and shows.

  The nozzle hole plate 4 of the fourth embodiment is configured by laminating a first nozzle hole plate 21 provided on the upstream side and a second nozzle hole plate 22 provided on the downstream side.

  The first nozzle hole plate 21 includes a thick portion 21a and a thin portion 21b that is located at the center of the thick portion 21a and has a thickness dimension smaller than that of the thick portion 21a. The thin portion 21b is provided in a portion facing the inner side (the valve seat axis 3c side) of the valve seat opening 3b, that is, a portion in contact with the fuel.

  Moreover, the thin part 21b is formed by pressing the upstream end surface of the first nozzle hole plate 21 to the downstream side and denting it. A tapered portion 21c is formed between the thin portion 21b and the thick portion 21a.

  A plurality of positioning holes 21d are press-molded in the thick portion 21a. The second injection hole plate 22 is press-molded with a half punched portion 22a fitted into the positioning hole 21d. The second injection hole plate 22 is positioned with respect to the first injection hole plate 21 by fitting the half punching portion 22a into the positioning hole 21d. Other configurations are the same as those in the second embodiment.

  When the injection hole main body 5a and the large diameter part 5b are press-molded in one injection hole plate, the large diameter part 5b is forged, so there is a limit in the size and depth of the large diameter part 5b, and the fuel There is a limit to the direction in which the liquid film pops out.

  On the other hand, in Embodiment 4, since the nozzle hole plate 4 has a stacked structure of the first nozzle hole plate 21 and the second nozzle hole plate 22, the second nozzle hole plate 22 has a large diameter. The part 5b can be formed by press punching. For this reason, the depth of the large diameter portion 5b can be easily changed by changing the thickness of the second injection hole plate 22. Thereby, the freedom degree of the magnitude | size and depth of the large diameter part 5b improves, and the liquid film of a fuel can be made to jump out in the desired injection direction.

  As a specific method of providing the nozzle holes 5 in the first and second nozzle holes plates 21 and 22, first, the large-diameter portion 5b is provided in the second nozzle hole plate 22 by press punching. Thereafter, the first nozzle hole plate 21 and the second nozzle hole plate 22 are stacked in a state of being aligned. Then, from the downstream side of the second nozzle hole plate 22, a part of the inner wall of the large-diameter portion 5 b is extracted while being punched so as to penetrate to the upstream side of the first nozzle hole plate 21. The nozzle hole main body 5 a is provided in the first and second nozzle hole plates 21 and 22. Thereby, position shift with the corresponding nozzle hole main body 5a and the large diameter part 5b can be suppressed.

  Here, as a processing method of the first and second nozzle holes plates 21 and 22, a method of progressively pressing a belt-like hoop material is used in order to accurately process at low cost. At that time, a pilot hole for positioning with a press mold is provided in the band-shaped hoop material, and the injection hole main body 5a and the large diameter portion 5b are press-molded with reference to the pilot hole. The positional accuracy of the large diameter portion 5b is ensured.

  In the fourth embodiment, a positioning hole 21d is press-molded in the first nozzle hole plate 21 with the pilot hole as a reference, and a half punching portion 22a protruding upstream is pressed in the second nozzle hole plate 22. Mold.

  In this way, the nozzle hole body 5a and the positioning hole 21d are processed with the same pilot hole as a reference, the large diameter portion 5b and the half punched portion 22a are processed with the same pilot hole as a reference, and further positioning is performed. It is also possible to press-fit the half punched portion 22a into the hole 21d. Thereby, the positioning accuracy of the 1st nozzle hole plate 21 and the 2nd nozzle hole plate 22 can be improved, and the dispersion | variation in spray shape can be made small.

  Further, the first injection hole plate 21 and the second injection hole plate 22 can be joined in a stacked state by press-fitting and fitting the half punched portion 22a into the positioning hole 21d within the pressing process. Therefore, the manufacturing cost can be reduced as compared with the case where the nozzle hole plates 21 and 22 are welded and aligned.

  Further, in the fourth embodiment, since the first welded portion 4a is provided on the valve seat shaft center 3c side with respect to the positioning fitting portion (the positioning hole 21d and the half punched portion 22a), the fuel is discharged to the outside. It has a structure that does not leak.

  Further, when the first and second injection hole plates 21 and 22 are processed by the progressive press method, if the plate thickness of the injection hole plates 21 and 22, that is, the thickness of the hoop material is thin, the rigidity becomes insufficient. When the hoop material is fed forward, the hoop material is wrinkled, and there is a problem in that it is not possible to feed the hoop material to the correct position, causing a problem in the process. It is desirable that the thickness of the nozzle holes 21 and 22 is thicker.

  On the other hand, the injection hole main body 5a is processed while the first and second injection hole plates 21 and 22 are stacked, while a part 5g of the inner wall of the large-diameter portion 5b is extracted by press punching. It is necessary to penetrate to the upstream side of the nozzle hole plate 21. For this reason, considering the ease of press punching, it is desirable that the first nozzle hole plate 21 is thin.

  On the other hand, in Embodiment 4, the thin-walled portion 21b is provided in the first nozzle hole plate 21, and the inlet of the nozzle hole main body 5a is provided in the thin-walled portion 21b. For this reason, the thickness of the hoop material of the first nozzle hole plate 21 can be increased, and the punching ability of the nozzle hole body 5a to be pressed into the thin wall portion 21b is improved while preventing a process failure in the progressive feeding. be able to.

The flat portion 6b may not be provided on the ball 6 of the fourth embodiment, and the convex portion 4c may be provided at the center of the nozzle hole plate 4. That is, Embodiments 1 and 4 may be combined.
In the fourth embodiment, the positioning hole 21d is provided in the first injection hole plate 21 and the half punching portion 22a is provided in the second injection hole plate 22. However, the reverse may be possible.

  3 valve seat, 3a seat surface, 3b valve seat opening, 4 injection hole plate, 4c convex part, 4d injection hole plate flat part, 5 injection hole, 5a injection hole body, 5b large diameter part, 5c inlet center, 5d outlet center 5f Cylindrical portion, 6 balls (valve element), 6b flat part, 18a virtual conical surface, 18b virtual circle, 19 straight line, 21 first injection hole plate, 21b thin part, 21d positioning hole, 22 second injection hole Plate, 22a Half punching part.

Claims (7)

A valve seat having a seat surface inclined such that the diameter is gradually reduced toward the downstream side, and a valve seat opening provided on the downstream side of the seat surface;
A valve body that abuts against the seat surface to prevent fuel from flowing out of the valve seat opening and is separated from the seat surface to allow fuel outflow from the valve seat opening; and downstream of the valve seat An injection hole plate that is fixed to a side end surface and has a plurality of injection holes for injecting fuel that has flowed out of the valve seat opening to the outside;
The nozzle hole plate is arranged so that a virtual conical surface extending the sheet surface downstream and an upstream end surface of the nozzle hole plate intersect to form a virtual circle,
The nozzle hole is composed of a nozzle hole main body and a large-diameter portion adjacent to the downstream of the nozzle hole main body and constituting the outlet of the nozzle hole,
The diameter of the large diameter portion is larger than the diameter of the nozzle hole body,
The inlet portion of the nozzle hole body is disposed closer to the valve seat axis than the valve seat opening which is the minimum inner diameter of the valve seat,
When projected perpendicularly to the plane perpendicular to the injection hole in the valve seat axis, an inlet center and the outlet center of the injection hole body on the plane, radial same through the pre SL valve seat axis Arranged on a straight line, and the outlet center is arranged in a direction away from the valve seat axis with respect to the inlet center,
The center of the large-diameter portion is offset in a desired injection direction with respect to the radial straight line passing through the inlet center and the outlet center of the nozzle hole body on the plane. A fuel injection valve in which the inner wall length of the injection hole on the valve seat axis side is asymmetric with respect to the straight line. The nozzle hole plate is provided with a convex portion projecting downstream in order to avoid interference with the tip of the valve body when the valve is closed,
Around the projection of the nozzle hole plate, a flat nozzle hole plate flat part is provided,
The fuel injection valve according to claim 1, wherein the injection hole is provided in a flat part of the injection hole plate. In order to avoid interference with the nozzle hole plate when the valve is closed, a flat part parallel to or substantially parallel to the nozzle hole plate is provided at the tip of the valve body,
2. The fuel injection valve according to claim 1, wherein the flat portion is provided on an inner diameter side with respect to an inlet of the nozzle hole body when projected perpendicularly to the plane.   The fuel according to any one of claims 1 to 3, wherein a cylindrical portion having a minimum cross-sectional area is provided between an inlet and an outlet of the nozzle hole body in the flow path of the nozzle hole body. Injection valve. The nozzle hole plate is configured by stacking a first nozzle hole plate provided on the upstream side and a second nozzle hole plate provided on the downstream side,
After the large-diameter portion is formed in the second nozzle plate by press punching, the first nozzle plate and the second nozzle plate are stacked in a aligned state, and the nozzle body 5. The method according to claim 1, wherein the first injection hole plate is formed by press punching so as to penetrate from the downstream side of the second injection hole plate to the upstream side of the first injection hole plate. Fuel injection valve.   Either one of the first nozzle hole plate and the second nozzle hole plate is provided with a positioning hole, and the other of the first nozzle hole plate and the second nozzle hole plate has the positioning hole. The fuel injection valve according to claim 5, wherein a half punching portion to be fitted into the hole is provided. A portion facing the inside of the valve seat opening of the first nozzle hole plate is provided with a thin-walled portion formed by denting the upstream end face of the first nozzle hole plate to the downstream side,
The fuel injection valve according to claim 5 or 6, wherein an inlet of the nozzle hole body is provided in the thin portion.

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