JP2001055965A - Electromagnetic fuel injection valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To inject and supply fuel from a swinging type electromagnetic fuel injection valve by efficiently converting pressurized fuel to turning fuel with excellent atomization characteristics. SOLUTION: An electromagnetic fuel injection valve has a nozzle body provided with a valve seat 9 and a fuel injection hole 8, a valve element 6 driven by an electromagnet and opening/closing a fuel passage in-between the valve seat, a fuel turning element 37 and a plurality of fuel passages offset in respect to an axial center of the valve, arranged on an upstream side of the valve seat. In such an electromagnetic fuel injection valve, a circular fuel reservoir 52 is formed so as to communicate inlets of a plurality of fuel passages to each other, which passages are offset to the axial center of the valve.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electromagnetic fuel injection valve for an internal combustion engine, and more particularly to a swing type electromagnetic fuel injection valve.

[0002]

2. Description of the Related Art As disclosed in Japanese Patent Application Laid-Open No. 56-75955, a conventional apparatus has a swirl having a guide hole for accommodating a ball and a swirl passage for introducing fuel into the guide hole substantially from its tangential direction. The configuration in which the plate is provided in the housing can improve the atomization of fuel.

[0003]

In the above prior art, the fuel passage in the direction (axial direction) along the axis connected to the swirl passage is constituted by a vertical hole formed in the swirl plate.
Sufficient consideration has not been given to increasing the productivity of the electromagnetic fuel injection valve by facilitating work and processing around the swirl plate. Further, the above prior art does not consider that the swirl passage and the four fuel passage holes communicating with the swirl passage are converted into sufficient swirling speed energy without loss when the pressurized fuel passes. .

An object of the present invention is to provide an electromagnetic fuel injection valve which is excellent in productivity and capable of injecting and supplying fuel with excellent atomization characteristics by efficiently applying a swirling force to fuel.

[0005]

In order to achieve the above object, an electromagnetic fuel injection valve according to the present invention is provided upstream of a fuel injection hole and a valve seat, and moves a valve body in a direction along a valve axis. In an electromagnetic fuel injection valve having a plurality of fuel passages that impart a swirling force to fuel that passes through the guide member that is offset with respect to the valve axis, a guide member includes an inlet portion of the plurality of fuel passages. An electromagnetic fuel injection valve, wherein an annular fuel reservoir communicating with the fuel injection valve is formed. According to the above means, uniform distribution of the pressurized fuel is obtained at the inlets of the plurality of fuel passages offset with respect to the valve axis, and the fuel can be efficiently converted to swirl fuel.

[0006]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to FIGS. The structure and operation of the electromagnetic fuel injection valve (hereinafter, referred to as “injection valve”) 1 will be described with reference to FIG. The injection valve 1 injects fuel by opening and closing the seat in response to a duty ON-OFF signal calculated by a control unit (not shown). The magnetic circuit includes a core 2 having a bottomed cylindrical yoke 3, a plug 2 a for closing an open end of the yoke 3, and a column 2 b extending to the center of the yoke 3, and a plunger 4 facing the core 2 with a gap therebetween. Consists of A spring 10 is inserted in the center of the columnar portion 2a of the core 2 as an elastic member for pressing a movable portion 4A composed of a plunger 4, a rod 5, and a ball valve 6 against a seat surface 9 of an orifice 8 formed in a valve guide 7. There is a hole for holding. The upper end of the spring 10 is in contact with the lower end of a spring adjuster 11 inserted into the center of the core 2 to adjust the set load. In order to prevent fuel from flowing out of the gap between the core 2 and the adjuster 11, an O-ring 12
Is provided. Also, between the core 2 and the yoke 3,
An O-ring 13 for preventing fuel from flowing out of the gap between the core 2 and the yoke 3 is provided. The coil 15 to be excited by the magnetic circuit is wound around the bobbin 14, and the outside thereof is molded with a plastic material. A terminal 18 of the coil assembly 16 composed of these is inserted into a hole 17 provided in a flange portion of the core 2, and an O-ring 1 is provided between the terminal 18 and the core 2.
9 are interposed. The collar 20 for preventing the mold resin (hereinafter referred to as yoke mold) 19a outside the injection valve 1 from entering the inside of the injection valve 1 during molding.
Over the entrance. A gap 21, an upper passage 22, and a lower passage 23 with the core 2 are provided as passages for fuel and fuel vapor. An annular groove 25 is formed on the outer periphery of the yoke 3, and an O-ring 24 for preventing fuel from flowing out from a gap between the injection valve 1 and a socket (not shown) as a housing is held therein. Around the yoke 3, an inflow passage 26 through which fuel flows and an outflow passage 27 through which excess fuel including bubbles accumulated in the injection valve 1 flows out are opened. A plunger receiving portion 28 for receiving the movable portion 4A is opened at the bottom portion of the yoke 3, and a valve guide receiving portion 30 for receiving the stopper 29 and the valve guide 7 at a diameter larger than the diameter of the plunger receiving portion 28. Extends through the end of the yoke. On the outer periphery of the yoke 3, there is provided an annular filter 31 for preventing dust and foreign matter in fuel and pipes from entering the valve seat from the fuel inflow passage 26. A terminal 32 for transmitting a signal from the control unit to the coil 15 is joined to the terminal 18. These terminals 32 are molded at the upper end of the solenoid valve assembly with a molding resin to form a molded connector 33. Movable part 4
A denotes a magnetic material plunger 4, a rod 5 having one end joined to the plunger 4, a ball joined to the other end of the rod 5, and a guide ring made of a nonmagnetic material fixed to an upper end opening of the plunger 4. 34. The guide ring 34 and the hollow inner wall 35 opened at the tip of the core 2, and the ball valve 6 is the inner peripheral surface 38 of a cylindrical fuel swirl element 37 inserted into the hollow inner wall 36 of the valve guide 7. , Each being guided by a valve guide 7
Has a cylindrical fuel swirl element 3 for guiding the ball valve 6.
7, a seat surface 9 for seating the ball valve 6.
Are formed, and a fuel injection hole 8 is provided at the center of the sealing surface 9.
Are drilled. The valve guide 7 further has a seat surface 9.
A cylindrical portion 39 extending in a direction opposite to the above is formed. An O-ring 40 for sealing fuel is interposed between a socket (not shown) and the outer peripheral surface of the valve guide 7. In the embodiment, an O-ring receiving portion 41 is formed as an annular groove on the outer periphery of the valve guide 7.

A method for assembling the injection valve and a method for adjusting the flow rate will be described below. First, a method of assembling the assembly of the electromagnet units will be described. O-ring 1 on terminal 18 of coil assembly 16
After attaching 9, the terminal 18 is inserted into the hole 17 of the collar portion of the core 2, and then the collar 20 is inserted from above the terminal 18. Then, an O-ring 13 is attached to the lower part of the outer periphery of the plug body of the core, and fitted into the yoke 3. In this state, the core contact surface 42 at the upper edge of the inner periphery of the yoke 3 is pressed in the axial direction, and the material of the yoke 3 is radially poured into the groove 43 provided on the outer periphery of the plug body of the core 2 by plastic flow. Secure with tension. A so-called metal flow is performed. The movable portion guides the ball valve 6 on the inner wall surface 38 of the fuel swirling element 37 and guides the non-magnetic ring 34 on the tip inner wall surface 35 of the core 2, thus forming the 2
In order to advance and retreat in the axial direction while guiding at two places, the inner diameter of the receiving portion 30 of the valve guide 7 of the yoke 3 and the inner
It is important that the concentricity can be accurately obtained. Therefore, metal flow is performed in a state where the inner diameter of the receiving portion 30 of the valve guide 7 and the inner wall surface 35 of the core 2 are accurately supported. Thereafter, the terminal 32 is fixed to the terminal 18 by caulking, soldering, welding, or the like, and thereafter, molding is performed with resin. Next, the assembly of the valve guide assembly will be described. The valve guide includes the movable portion 4A, the fuel swirling element 37, and the valve guide 7. The movable portion 4A welds the ball valve 6 and the quenched and hardened stainless steel rod 5 by resistance welding or laser welding. Next, the other end of the rod 5 and the plunger 4 are fixed to the groove 44 provided on the outer periphery of the rod 5 by flow-pressing the inner wall of the plunger 4 by metal flow. Further, the coupling between the guide ring 34 and the plunger 4 is carried out by receiving the surface 45 of the plunger 4 on the ball valve side and pressing the guide ring contact portion 46 at the inner peripheral edge at the tip end of the plunger 4 in the axial direction. This can be done with a metal flow by applying a radial tension.

The fuel swirling element 37 is formed into a cylindrical shape using a sintered alloy, and is fixed to the inner wall surface 36 of the valve guide 7 by pressure bonding. That is, the outer peripheral surface 47 of the fuel swirling element 37
(4 places) are flow-bonded to the groove 48 of the valve guide 7 by metal flow (FIG. 2 and FIG. 3 when FIG. 2 is viewed from the direction A). In this embodiment, the method of press-fitting and fixing by the metal flow as described above is described. However, even if the fuel swirling element 37 is fixed in the direction A shown in FIG. 2 by an elastic member, the function can be similarly satisfied. .

The fuel swirling element 37 has an axial groove 49 and a radial groove 50. In this embodiment, the axial groove 49 is used.
Formed a D-cut surface. The grooves 49 and 50 are fuel passages that are introduced from the axial direction. The fuel that has passed through the groove 49 is eccentrically introduced into the groove 50 from the axial center. A so-called swirling force is applied to the fuel, which has the function of promoting atomization when the fuel is ejected from the fuel injection hole 8 of the outlet orifice provided in the valve guide 7.

The fuel swirling element 37 is designed and manufactured with the following considerations, and is fixed to the inner wall surface 36 of the valve guide 7 by crimping.

Factors that affect the static flow rate of fuel include pressure loss in the flow path of the fuel swirling element 37 and swirling force applied. The pressure loss of the flow path is mainly controlled by the cross-sectional area of the groove. FIG. 4 shows a sectional shape of the radial groove 50 in the present embodiment.
(B-B sectional view in FIG. 3). Using the rheological equivalent diameter represented by the groove width W and the groove depth H in FIG.

[0012]

(Equation 1)

## EQU1 ## Here, n is the number of grooves.

The sectional area A 1 is the sectional area A of the fuel injection hole 8.
Three

[0015]

(Equation 2)

The ratio σ = A1 / A3 is 1.5 <σ <6.5.
And is designed to prevent pressure loss as much as possible. The experimental results of the authors are shown in FIGS. 5 and 6, which will prove that the effect of the loss is negligible. FIG. 5 shows the effect of the groove width W on the static flow rate. The change rate of the flow rate is slightly less than 0.2% at the tolerance ± a with respect to the reference groove width W0. FIG. 6 shows the effect of the groove depth H on the static flow rate. The rate of change of the flow rate is less than 0.1% at the tolerance ± a with respect to the reference groove depth H0. Therefore, the effect of the groove on the static flow rate is so small as to be ignored in the above design conditions. 5 and 6, the static flow rate Q0 is a target flow rate, Qmax represents + 3% of Q0, and Qmin represents Q3.
This represents -3% of 0. The tolerance ± a is about 20 μm in this embodiment.

Next, the effect of the turning force on the static flow rate will be described. The swirl number S given as a parameter indicating the turning strength is given by the following equation.

[0018]

(Equation 3)

Here, L: the amount of eccentricity of the groove (see FIG. 4) dS: the rheological equivalent diameter expressed by using the groove diameter W and the groove depth H (see Equation 1) n: The number of grooves . The effect of the magnitude of the swirl number S on the static flow rate will be described by the following equation, and will be described together with the experimental results of the present inventors. First, the flow rate Q is given by Expression 4.

[0020]

(Equation 4)

Here, Q: flow rate C0: flow coefficient d: orifice diameter γ: specific weight P: fuel pressure The flow coefficient C0 in Equation 4 is represented by a characteristic value K represented by the reciprocal of the swirl number S obtained by Equation 3, and is shown in FIG. As is clear from the figure, the present embodiment is designed to allow the passage of fuel in a region where the rate of change of the flow coefficient C0 is small. In other words, the magnitude of the swirl number S in Equation 3 can be selected by the eccentric amount L of the groove. The amount of eccentricity L is, of course, determined to reduce the rate of change of the flow coefficient C0, but this will be proved by the authors' experimental results shown in FIG.

In FIG. 8, the variation rate of the static flow rate is less than ± 1% at the tolerance ± a with respect to the reference eccentricity L0. The change in the flow rate at the hatched portion in the figure corresponds to the change C0 mi in the flow coefficient C0 shown in FIG.
It can be said that this corresponds to n to C0 max.

As described above, the influence of the fuel swirling element 37 on the change in the static flow rate is relatively small, and the inexpensive fuel swirling element 37 can be provided by a simple configuration whose manufacturing accuracy is loosened. . The fuel swirling element 37 is
After being manufactured to a desired size with a loose manufacturing accuracy, it is fixed to the groove 48 of the inner wall surface 36 of the valve guide 7 by fluid pressure bonding with a metal flow.

Next, adjustment of the stroke of the movable portion 4A will be described. The stroke is the receiving surface 5 at the neck of the rod 5.
a and the size of the gap between the stopper 29.

FIG. 9 shows an experimental result on the effect of the stroke 1 on the static flow rate. As is clear from the figure, the flow rate starts to increase rapidly with the increase of the stroke l, gradually becomes a gentle gradient, and becomes a substantially constant flow rate Q0. The area A2 of the annular gap formed between the ball 6 and the valve seat 9 by this stroke is shown in FIG.
It is given by Equation 5.

[0026]

(Equation 5)

Here, D1: lower side of trapezoid in the figure D: upper side of the number in the figure, that is, sheet diameter h: height of trapezoid in the figure.

The area A2 for obtaining a constant flow rate Q0 is:
When the ratio δ to the area A3 of the fuel injection hole 8 is represented by δ = A2 / A3, 1 <δ. In this embodiment, as shown in FIG. 9, it can be seen that the dimensions are determined to have a sufficient margin within the tolerance ± a with respect to the reference stroke l0. The ratio δ at the tolerance -a of the stroke l0 is 2 or more. The dimension a
Is about 20 μm as described above.

As described above, the stroke amount of the movable portion 4A is an absolute amount that does not affect the static flow rate, and is determined by a dimensional tolerance having a sufficient margin. Therefore, as in the conventional case, the lift amount is measured once in a state where the movable portion 4A and the valve guide 7 are combined, and the end surface of the valve guide or the receiving surface 5a of the neck portion of the rod 5 is polished to set the stroke within the target range. There is no need to make adjustments, and only the management of the part dimensions is sufficient. Therefore, the assembling operation is easy and simplified.

Next, the effect on the static flow rate of the fuel injection hole 8 as the fuel outlet provided in the valve guide 7 will be described. The static flow rate of fuel passing through a single fuel injection hole 8 is shown in FIG.
1 is shown. Tolerance ± b for reference orifice diameter d0
The rate of change of the static flow rate at is less than ± 1.5%. Here, the dimension b is about 5 μm.

As described above, the sectional area A of the fuel injection hole 8
3 represents the relationship using the annular gap area A2 of the movable portion 4A during the stroke and the groove area A1 of the fuel swirling element 37.

[0032]

A1>A2> A3 (Equation 6) In the so-called injection valve 1 in the present embodiment, the fuel is measured by the fuel injection hole 8 of the orifice.

As described above, the ratio δ of A 2 / A 3 takes a value of 2 or more. At this time, the fluid loss of the fuel injection hole 8 accounts for 95% or more of the total loss, and What is done by the injection holes 8 is supported.

Although described with reference to FIGS. 5 to 8, the flow rate change rate in consideration of the effect on the flow rate of the fuel swirl element 37 and the effect on the flow rate of the stroke described with reference to FIGS. The value of about ± 1% also means that the flow rate is adjusted by the fuel injection hole 8 in the outlet orifice.

As described above, the static flow rate is hardly affected by the stroke, and the static flow rate is
Although it varies by about 1% and about ± 1.5% depending on the orifice, the target ± 3% in the injection valve assembly can be sufficiently satisfied.

That is, it is an inexpensive injection valve which does not need to be disassembled for adjusting the static flow rate or remanufactured at high cost. Incidentally, it is needless to say that the static flow rate of the orifice provided in the valve guide 7 is measured before the fuel swirl element 37 is fixed to the valve guide 7 by press-fitting. .

As described above, the assembled valve guide assembly together with the stopper 29 is inserted into the valve guide receiving portion 30 of the yoke 3 of the electromagnet assembly to assemble them. The two are fixed by allowing the inner peripheral wall of the tip of the yoke 3 to flow into the groove 51 provided on the outer periphery of the valve guide 7 by plastic flow using a metal flow. At that time, the stopper 29 is set to have a predetermined air gap so that the tip of the plunger 4 does not directly contact the tip of the core 2 when the movable portion is sucked. Next, an adjuster 11 holding a spring 10 at the tip and having an O-ring 12 mounted on the outer periphery is inserted into a hole provided at the center of the core 2 of the electromagnet assembly from a direction opposite to the valve guide 7. The filter 31 and the O-ring 24 are attached to the outer periphery, and are temporarily stored in a hire (not shown), where the injection amount test is started. The injection amount test is
First, measurement is performed in a state where the movable part is fully stroked, and it is confirmed that the injection amount at that time becomes a specified injection amount.

Thereafter, the responsiveness of the movable portion is determined by changing the load of the spring 10 so that the injection amount at a constant period and a constant valve opening time becomes a specified injection amount.
The outer periphery of the upper protruding portion 52 is pressed in the radial direction from the hole of the mold resin, and is fixed by making the inner wall of the core into the groove 53 of the adjuster.

The operation of the injection valve configured as described above will be described. The injection valve 1 opens and closes a valve seat by operating a movable part in response to an electrical ON-OFF signal given to the electromagnetic coil 15, thereby injecting fuel.
The electric signal is given to the coil 15 as a pulse. When a current flows through the coil 15, a magnetic circuit is formed by the core 2, the yoke 3, and the plunger 4, and the plunger 4 is attracted to the core 2. When the plunger 4 moves, the ball valve 6 integrated therewith also moves to separate from the seat surface of the valve seat 9 of the valve guide 7 to open the fuel injection hole 8. The fuel is pressurized and adjusted by a fuel pump or a fuel pressure regulator (not shown), flows into the inside of the solenoid valve assembly from the inflow passage 26 through the filter 34, and the lower passage 23 of the coil assembly 16, the outer periphery of the plunger 4, and the stopper The fuel is swirled and supplied to the seat portion through the gap between the rod 29 and the rod 5 and the grooves 49 and 50 of the fuel swirling element 37, and is injected into the intake pipe through the fuel injection hole 8 when the valve is opened.

When the electromagnetic coil 15 is deenergized, the movable portion 4A
Is pushed by the spring 10 and moves to the valve seat side,
The ball valve 6 closes the seat surface of the valve seat 9.

Although it is clear from the above description that the means for adjusting the flow rate is not required, a point which contributes to atomization of the fuel will be described here.

When the fuel reaches the fuel swirling element 37, the fuel flows from the axial groove 49 provided in the swirling element and the radial groove 50 communicating therewith toward the valve seat 9 seat surface. A swirling flow occurs at the outlet of the radial groove, which is configured more eccentrically. This swirling flow proceeds downstream through a lossless annular gap formed in the seat surface 1 of the valve seat 9, but the flow is facilitated and reaches the fuel injection hole 8 while maintaining sufficient swirling energy.

The pressure drop of the fuel when flowing through the annular gap generated between the seat surfaces of the valve seat 9 when the grooves 49 and 50 and the ball 6 are lifted is very small as is apparent from the above description. . Therefore, the fuel is swirled while maintaining the supplied fuel pressure, and the fuel is injected at the fuel injection holes 8 with a sufficient injection pressure and swirling force, so that excellent atomized fuel can be obtained.

FIG. 12 shows the relationship between the fuel flow path and the flow velocity when the injection valve of the present invention is used. As is clear from FIG. 12, the flow rate is highest at the fuel injection hole from the fuel introduction part to the fuel outlet. Therefore, the flow rate can be measured only with the fuel injection hole, that is, the outlet orifice. The design means that the flow rate can be measured accurately if the outlet orifice is made accurately.

FIG. 13 shows another embodiment of the present invention, in which a fuel swirling element 37 has an axial groove 49 having a sufficient space to allow a fuel passage, a tapered shape which does not cause fuel flow loss, and the like. Due to the radial groove 50, the pressure loss at the time of passing through the groove 50 is configured to be very small, and the fuel flows into the first fuel swirl chamber 54.

FIG. 14 is a sectional view of a nozzle device according to another embodiment of the present invention. In FIG. 14, 37 is another fuel swirling element, 49 is an axial groove, and 50 is a radial groove.

In this embodiment, the same effects as in the first embodiment can be obtained, and the structure is relatively simple and can be constructed at a low cost.

The axial groove 49 and the radial groove 50 in this embodiment can have any shape as is apparent from the embodiment. That is, it is possible to adjust the injection pressure and the fuel swirl force, and it is also possible to select the pattern of the spray injected from the fuel injection holes 8. Further, it goes without saying that the same effect can be obtained by forming the axial groove 49 by chamfering.

FIG. 15 is an enlarged view of a main part of an electromagnetic fuel injection valve according to still another embodiment of the present invention, and FIG.
FIG. 5 is a sectional view taken along line BB of FIG.

In FIG. 15, reference numeral 37 denotes a fuel swirling element having a flange 51, the outer peripheral surface of which is fixed to the inner surface of the rapidly expanding hole 5 of the nozzle device 2. Numeral 52 denotes a fuel reservoir formed below the flange 51, whereby fuel is supplied to the radial groove 5 provided on the surface corresponding to the valve seat 9 surface.
0 to the first fuel swirl chamber 54. Reference numeral 55 denotes a plurality of cutouts 55 provided in the flange 51 as shown in FIG.

Reference numeral 57 denotes a conical valve seat 9 below the ball 6.
The second fuel swirl chamber formed by the first fuel swirl chamber 5
4 promotes the swirling flow of the fuel flowing in from the side.

Reference numeral 56 denotes a spacer member inserted between the bearing surface 1a of the yoke 3 and the bearing surface 2a of the nozzle device 7, and the spacer member 56 serves to remove a gap between the projection surface 8a of the valve device. This restricts the upward movement of the valve device, that is, the lift amount.

In this embodiment, the same effects as those of the first embodiment can be obtained. However, in particular, just before the radial groove 50, a uniform distribution of the pressurized fuel is obtained, and the fuel is efficiently replaced with the swirling fuel. It is possible.

[0054]

According to the present invention, uniform distribution of the pressurized fuel can be obtained at the inlets of the plurality of fuel passages offset with respect to the valve shaft center, the fuel can be efficiently converted to swirl fuel, and excellent atomization can be achieved. It is possible to provide an electromagnetic fuel injection valve capable of performing fuel injection and supply with characteristics and having excellent productivity.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of an electromagnetic fuel injection valve according to one embodiment of the present invention.

FIG. 2 is a longitudinal sectional view for explaining a fuel swivel element and valve guide assembly structure.

FIG. 3 is a view from the direction A in FIG. 2;

FIG. 4 is a sectional view taken along line BB of FIG. 3;

FIG. 5 is an experimental example showing the relationship between groove width and flow rate.

FIG. 6 is an experimental example showing the relationship between groove depth and flow rate.

FIG. 7 is a diagram showing a relationship between a fuel swirling strength and a flow coefficient according to the embodiment of the present invention.

FIG. 8 is a diagram showing the relationship between the amount of eccentricity of a groove and the flow rate.

FIG. 9 is a diagram showing a relationship between a valve stroke and a flow rate.

FIG. 10 is a diagram for explaining an annular gap generated between a ball and a valve seat.

FIG. 11 is a diagram showing a relationship between an orifice diameter and a flow rate.

FIG. 12 is a diagram showing a relationship between a fuel flow path and a flow velocity.

FIG. 13 is a sectional view of a ball valve body according to another embodiment of the present invention.

FIG. 14 is a sectional view of a ball valve body according to another embodiment of the present invention.

FIG. 15 is an enlarged sectional view of a main part of another embodiment of the present invention.

FIG. 16 is a sectional view taken along line BB of FIG. 15;

[Explanation of symbols]

Reference Signs List 1 injection valve, 2 core, 3 yoke, 4a movable valve, 4
... plunger, 5 rod, 6 ... ball valve, 8 ... fuel injection hole, 9 ... valve seat, 15 ... coil, 37 ... fuel swirl element
49: axial groove, 50: radial groove.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Yoh Nakamura ▲ Kura ▼ 502 Kandate-cho, Tsuchiura-city, Ibaraki Pref. Machinery Research Laboratories, Ltd. Hitachi Machinery Laboratory (72) Inventor Haruo Watanabe 502 Kandachi-cho, Tsuchiura-shi, Ibaraki Prefecture Machinery Research Laboratory, Hitachi Ltd. (72) Inventor Tokuo Kosuge 2520 Odaiba, Hitachinaka-shi, Ibaraki Hitachi, Ltd. Inside the Sawa Plant (72) Inventor Akira Onishi 2520 Oji Takaba, Hitachinaka City, Ibaraki Prefecture Inside Hitachi Ltd.Sawa Plant (72) Inventor Terasaki ▲ Akane ▼ Hitachi Ltd. 2520 Oaza Takaba, Hitachinaka City, Ibaraki Prefecture Inside the Sawa Plant (72) Inventor Hiroyuki Ando 2520 Takada, Hitachinaka-shi, Ibaraki Pref. (72) Eiji Hamajima, Inventor 3085-5 Nishikouchi, Higashiishikawa, Hitachinaka, Ibaraki Prefecture Hitachi Automotive Engineering, Ltd.

Claims (1)

[Claims] 1. A fuel injection system comprising: a fuel injection hole;
A guide member for guiding a valve body in a direction along a valve axis, an electromagnetic fuel injection valve having a plurality of fuel passages for imparting a swirling force to fuel passing offset from the valve axis. An annular fuel reservoir communicating with inlets of the plurality of fuel passages.