JP2002206469A - Fuel injection valve and internal combustion engine loaded with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent deterioration of the fuel injection due to deposits adhered to a tip surface of a nozzle of a fuel injection valve. SOLUTION: This fuel injection valve 1 is provided with an injection hole 7b, a seat surface 7a positioned in the upstream of the injection hole, and a ball 6 to be brought into contact and separated with/from the seat surface to open and close a fuel passage communicated with the injection hole 7b. A recessed part 7e is provided in a tip surface 7d of the nozzle provided with a minute space from the edge of the outlet of the injection hole.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fuel injection valve and an internal combustion engine configured to inject fuel by the fuel injection valve.

[0002]

2. Description of the Related Art In-cylinder fuel injection devices for directly injecting fuel into a combustion chamber have become widespread, as opposed to in-pipe fuel injection devices for injecting fuel into an intake pipe of an engine.

An in-cylinder injection gasoline engine using such an in-cylinder fuel injection device is disclosed in JP-A-9-26896.
There is one described in Japanese Patent Publication No. In this conventional technology, the axial length of the injection port of the fuel injection valve is configured to be shorter than the diameter of the injection port, thereby reducing the reduction rate of the injection port area due to the adhesion of the deposit, and reducing the time-dependent change in the injection amount. I try to suppress it.

[0004]

However, in the prior art, as described below, when deposits adhere near the injection port, the ignitability (ignitability) and flammability (reduction of unburned gas emission) are improved. It has been difficult to generate a spray shape or fuel spray that can be maintained together.

In order to maintain ignitability and flammability even when deposits adhere, the following characteristics must be considered.

The first is a spray shape, and it is desirable that the spread angle and the reaching distance of the spray fuel be constant. Because the geometrical positional relationship between the fuel injection valve and the ignition device is fixed, the spread of the spray fuel is constant in order to always supply the appropriate concentration of the spray fuel to the ignition device. It is necessary.

[0007] The second is a spray structure, which needs to keep the spatial distribution of fuel particles to be sprayed properly.

[0008] In other words, when the deposit adheres to the spray fuel injected by the conventional fuel injection valve, the spray and the deposit interfere with each other, so that the spread angle of the spray fuel and the reach of the spray fuel tend to change. If the spread angle of the spray fuel or the range of the spray fuel changes, the spray fuel of an appropriate concentration will not reach the ignition device, or excessive spray fuel will be supplied to the piston and adhere to it, so that appropriate ignition and Combustion cannot be obtained.

It is an object of the present invention to propose a fuel injection valve and an internal combustion engine which can prevent a proper fuel spray, ignition and combustion from being hindered by deposits.

[0010]

SUMMARY OF THE INVENTION The present invention relates to an injection hole, a valve seat located upstream of the injection hole, and a valve which opens and closes a fuel passage to the injection port in contact with or separated from the valve seat. And a driving means for driving the valve, characterized in that a recess is provided in the nozzle tip surface at a small distance from the edge of the outlet of the injection hole.

The minute distance from the edge of the outlet of the injection hole to the recess is 0.01 to 0.2 of the diameter of the injection hole.
It is characterized in that it is set to 5 times.

Further, the recess is formed in an annular shape around the injection hole.

Further, the outlet opening of the injection hole is formed on a step surface, and the concave portion is formed on a lower surface.

The present invention also provides a cylinder, a piston reciprocating in the cylinder, an intake unit for introducing air into the cylinder, an exhaust unit for exhausting combustion gas from the cylinder, and the cylinder. A fuel injection valve for injecting fuel into the fuel injector, fuel supply means for supplying fuel to the fuel injection valve from a fuel tank, air introduced into the cylinder by the intake means, and injection into the cylinder by the fuel injection valve In an internal combustion engine provided with an ignition device for igniting an air-fuel mixture with the fuel, the fuel injection valve described above is used as the fuel injection valve.

[0015]

FIG. 1 shows a first embodiment of the present invention.
This will be described with reference to FIG. FIG. 1 is a vertical sectional side view of the fuel injection valve. 2A and 2B are enlarged views showing a nozzle portion, in which FIG. 2A is a longitudinal sectional side view, FIG. 2B is a plan view of a nozzle member viewed from an arrow N direction in FIG. 2A, and FIG. It is AA sectional drawing. In the following description, a plane including the valve axis (valve axis) and being parallel to the valve axis is referred to as a vertical section, and a plane perpendicular to the valve axis is referred to as a transverse section.

The electromagnetic fuel injection valve 1 has a duty cycle calculated by a control unit (not shown).
By driving the valve body by the electromagnetic force based on the OFF drive signal to open and close the fuel passage, the pressurized and supplied fuel is injected.

The magnetic circuit includes a core 2 having a yoke 3, a flanged 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 reciprocating operation space and an anchor 4 facing each other. A through-hole 2a, 4a is provided in the center of the columnar portion 2b of the core 2 and the anchor 4, and a valve body constituted by the anchor 4 made of a magnetic material, a rod 5, and a ball 6 as a valve joined to the rod 5 A spring 10 as an elastic member is inserted and held so as to press the nozzle 40 against a seat surface 7a serving as a valve seat of the nozzle member 7. Spring 10
Is in contact with the lower end of the spring adjuster 11 inserted through the through holes 2c and 4a in the center of the core 2 and the anchor 4 to adjust the set load. The seat surface 7a
The nozzle member 7 is formed so as to be located on the upstream side of the injection hole 7b together with the injection hole 7b.

The ball 6 constituting the valve body 40 does not necessarily have to be spherical. That is, a conical needle valve may be used.

The coil 14 for exciting the magnetic circuit is a bobbin 1
The core 2 is formed into a coil assembly 15 by being wound around the outer periphery 3 and molded with a plastic material. The coil assembly 15 is fitted around the columnar portion 2 b of the core 2, and the yoke 3 surrounds the outer periphery. Terminal 1 for supplying power to coil 14 of coil assembly 15
Numeral 7 is inserted into a hole 2d provided in the plug portion 2a of the core 2, led out, and connected to a terminal of a control unit (not shown).

A gap (outer peripheral portion of the anchor 4) facing the tip of the columnar portion 2 b of the core 2 on the valve body 40 side of the yoke 3 is provided between the two to prevent fuel from flowing out to the coil 14 side. Is provided with a seal ring 12 which is mechanically coupled thereto.

A plunger receiving portion 3a for receiving the valve body 40 is formed at the distal end of the yoke 3, and a stopper having a diameter larger than that of the plunger receiving portion 3a is provided at the distal end of the plunger receiving portion 3a. A nozzle receiving portion 3b for receiving the nozzle member 19 and the nozzle member 7 extends through to the tip of the yoke 3.

A hollow 5a is provided on the rod 4 side of the anchor 4 to allow fuel to pass therethrough, and a fuel outlet 5b communicates with the hollow 5a.

The valve element 40 guides the axial movement of the anchor 4 by contacting the outer periphery of the anchor 4 with the inner periphery of the seal ring 12, and the vicinity of the ball 6 or rod 5 side end of the fuel swirling element. 22 is guided by the inner peripheral surface of the guide hole 22a. The fuel swirling element 22 is formed in a shape cut off in the axial direction while leaving a circumferential surface on all sides of the outer periphery of the cylindrical body, and is inserted into a hollow portion 7c formed in the nozzle member 7,
The circumferential surface is brought into contact with the inner peripheral wall of the hollow portion 7c on the upstream side of the seat surface 7a of the nozzle member 7 for positioning, and the cut-out portion forms the fuel passage 25. The bottom surface is provided with a radial groove to form the fuel passage 26.

In this embodiment, the nozzle member 7 is constituted by a single cylindrical member having a bottom having a cylindrical side wall (peripheral wall) and an end surface (bottom surface) provided with an injection hole 7b. The open end is fitted in the nozzle receiving portion 3b. The nozzle member 7 forms a housing that houses the fuel swirling element 22 and a part of the valve element 40.

The stroke of the valve body 40 (the amount of upward movement in FIG. 1) is determined by the size of the gap between the receiving surface 5c of the neck of the rod 5 and the stopper 19.

The filter 24 is provided to prevent dust and foreign matter mixed in the fuel from entering the valve seat between the ball 6 and the seat surface 7a.

Next, with reference to FIG. 2, a description will be given of a concave portion provided on the nozzle member 7 in this embodiment for preventing deposits. 2A is a longitudinal side view of the nozzle member 7, FIG. 2B is a plan view of the nozzle member 7 shown in FIG. 2A as viewed from the N direction, and FIG. is there.

The center of the injection hole 7b coincides with the axis (valve axis) J of the rod 5 of the valve body 40, and the wall surface is formed parallel to the axis J. An annular concave portion 7e having a width W0 and a depth (Hn-Hn ') is formed on the nozzle tip surface 7d forming the outlet opening of the injection hole 7b at a minute distance δ from the edge of the injection hole 7b. It is formed so as to surround the hole 7b.
The concave portion 7e provided on the nozzle tip surface 7d is configured to positively adhere the deposit along the concave portion 7e so that the deposit attached near the outlet opening of the injection hole 7b is easily peeled off.

In practice, the minimum value of the minute distance δ and the width W0 of the recess 7e is 0.01 times the diameter of the injection hole 7b in consideration of the workability of the outlet opening of the injection hole 7b. The degree is appropriate. On the other hand, the maximum value of the minute distance δ is
It is determined by the method described below.

FIG. 3A is a longitudinal sectional side view showing an enlarged view of the vicinity of the injection hole 7b in the fuel injection valve 1 of this embodiment. The deposit 31 adheres as schematically shown. Here, paying attention to a portion of the deposit 31 that interferes with fuel spray, assuming that the beam has a rectangular cross section as shown in FIG. 3B, the maximum bending stress (σbmax) applied to the deposit 31 is obtained by the following equation. .

Σbmax = constant × load / second moment of area = m × W / Ij (1) where Ij: second moment of area about axis J = I + (Hd × δ) × (δ / 2 + d0 / 2 ) = (Hd × δ ³ ) / 12 + (Hd × δ) × (δ / 2 + d0 / 2) Here, the easiness of peeling of the deposit 31 is represented by δ / d0 =
It is defined as a dimensionless quantity with the maximum bending stress σbmax at 0.01 being 100.

FIG. 4 is a characteristic diagram showing the relationship between δ / d0 and the ease with which the deposit 31 can be peeled off. The deposit 31
As δ increases, peeling becomes more difficult. Therefore, δ /
The maximum value of d0 is preferably set to about 0.25 (easiness of peeling of the deposit 31 = 5). That is, practically, it is desirable to set 0.01 ≦ δ / d0 ≦ 0.25.

In FIG. 2, the fuel swirling element 22 is provided with a fuel passage 25 formed by cutting the outer peripheral portion of the fuel swirling element 22 into a plane and a fuel passage 26 formed by a radial groove. In this embodiment, the fuel passage 25 is formed as a plane, but may have another shape such as an annular passage. The fuel passages 25 and 26 serve as a passage for fuel introduced from above the fuel swirl element 22, and the fuel that has passed through the fuel passage 25 in the axial direction passes through the fuel passage 26 formed by the radial groove. The eccentricity is introduced from the center to give a swirl, and the atomization at the time of jetting from the jetting hole 7b provided in the nozzle member 7 is promoted. Here, the swirling strength (swirl number S) provided by the fuel swirling element 22 is obtained by the following equation.

S = (angular momentum) / ((momentum in injection axis direction) × (injection hole radius)) = (2 · do · Ls) / (n · ds ² · cos (θ / 2)) 2 Here, do: diameter of injection hole Ls: eccentric amount of groove (distance between valve axis and groove (width) center) n: number of grooves θ: angle of valve seat ds: groove with rheological equivalent diameter = 2 · W · H / W + H expressed using the width W and the groove height H. Increasing the swirl number promotes atomization and disperses the spray.

Here, the operation of the fuel injection valve 1 in this embodiment will be described. When an electric drive signal is applied to the coil 14, the magnetic circuit of the core 2, the yoke 3, and the anchor 4 is excited, and the anchor 4 is attracted to the core 2. When the anchor 4 moves, the ball 6 separates from the seat surface 7a to open a fuel passage and inject fuel.

The fuel flows from the filter 24 into the fuel injection valve 1, and passes through the internal passage of the core 2, the outer peripheral portion of the anchor 4, and the hollow portion 5 provided in the anchor 4 for allowing fuel to pass therethrough.
a through the fuel outlet 5b to the downstream, and the stopper 1
The air is swirled and supplied to the seat surface 7a through the gap between the rod 9 and the rod 5, the axial fuel passage 25, and the radial fuel passage 26.

Next, a spray structure obtained by the fuel injection valve 1 in this embodiment will be described with reference to FIG. (A) schematically shows the spray structure when no deposit is attached. In this case, the spread angle of the spray 80 is αs. On the other hand, (b) schematically shows the spray 80 and the deposit 31 with the deposit 31 attached.

In this embodiment, since the deposit 31 adhered along the concave portion 7e is easily separated, the opening angle αd of the deposit 31 can be made larger than the spread angle α's of the spray 80. . By adjusting the width W0 and the depth (Hn-Hn ') of the recess 30, interference between the spray 80 and the deposit 31 is reduced, and the spray shape and the spray structure can be kept constant. That is, α
It is possible to set s ≒ α's. As described above, even if the deposit 31 adheres, it is possible to maintain the ignitability and the combustibility.

A second embodiment of the present invention will be described with reference to FIGS. Components corresponding to the components in the above-described embodiment are denoted by the same reference numerals, and redundant description will be omitted.

FIG. 6 is an enlarged view showing a nozzle portion of the electromagnetic fuel injection valve, in which (a) is a longitudinal sectional side view, and (b).
FIG. 4 is a plan view of the nozzle member viewed from the direction of arrow N in FIG.

In the fuel injection valve of this embodiment, the nozzle tip surface 7d where the outlet opening of the injection hole 7b provided in the nozzle member 7 is formed has surfaces 7f and 7g orthogonal to the axis J.
And a notch formed by a surface 7h substantially parallel to the axis J. By providing the injection hole 7b such that the surface 7h of the cutout portion crosses the center, the length of the injection hole 7b is L at the deepest cutout portion, and is not cutout. (Least notch)
L ”at the portion. According to such a configuration, the injection hole 7
The outlet opening surface b is formed with a step on the flat surfaces 7f and 7g having the step. And the recess 7e
Is formed in a semicircular arc shape on the plane 7g.

The injection hole 7 of the fuel injection valve 1 having such a configuration is described.
By injecting fuel from b, a spray having the following characteristics can be formed. (A) The distribution amount of the spray (the distribution amount of the air-fuel mixture) can be increased on the side of the cutout flat surface 7g of the passage wall forming the injection hole 7b. That is, it is possible to form a fuel spray having a shape that increases the amount of fuel distribution directed to the ignition device side. (B) The spray fuel injected from the cut-out flat surface 7g side has a large kinetic energy, so that the particle diameter of the spray becomes small.

As a result of (a) and (b), the ignitability is improved and the fuel efficiency is improved.

In this embodiment, since the spray fuel is largely distributed on the spark plug side, the deposit 31
A large amount adheres to the spark plug side at the bottom of b. Therefore, it is sufficient to provide the concave portion 7e only in a portion where the distribution amount is large as shown in the figure. Specifically, the intended purpose can be achieved by providing only on the flat surface 7g.

In this embodiment, the nozzle tip surface 7
Steps 7f, 7g, 7h and recess 7e formed on d.
Is preferably formed by a working method such as cutting, press working (plastic working) using a mold material, or casting. This is the same in the following embodiments.

FIG. 6B is a plan view of the nozzle member 7 shown in FIG. 6A as viewed from the arrow N, and defines the arrows “spark plug”, the arrow “piston”, and the lines K and M. Line K indicates the injection hole 7
A line M passing through the center of b and parallel to the cutout surface 7f is a line passing through the center of the injection hole 7b and orthogonal to the line K. The arrow “spark plug” and the arrow “piston” are parallel to the line M. It is.

In the nozzle member 7 shown in FIGS. 6A and 6B, the outer peripheral portion of the bottom surface (end surface) is formed thick. That is, this configuration reduces the vibration noise when the ball 6 is seated on the seat surface 7a due to the rigidity of the thick portion.

FIG. 7 is a longitudinal side view of an internal combustion engine to which the fuel injection valve 1 described with reference to FIG. 6 is applied.

A piston 69 reciprocally provided in a cylinder 68 of the internal combustion engine 60 moves up and down in the cylinder 68 in conjunction with rotation of a crankshaft (not shown). A cylinder head 63 is mounted on the upper portion of the cylinder 68 to form a closed space together with the cylinder 68. An external intake air 81 is provided to the cylinder head 63 via an intake air amount control device 61 having a built-in throttle valve.
The intake manifold 62 that guides the combustion gas into the cylinder 68 and the exhaust manifold 84 that guides the combustion gas 83 burned in the cylinder 68 to an exhaust device (not shown).

The intake manifold 6 of the cylinder head 63
An intake valve 64 is provided on the second side, an ignition plug 65 serving as an ignition device is provided in the center, and an exhaust valve 66 is provided on the side opposite to the intake valve 64. The intake valve 64 and the exhaust valve 66
It is provided to extend into the combustion chamber 67.

Here, the fuel injection valve 1 is mounted and installed near the joint between the cylinder head 63 and the cylinder 68 such that the tip is exposed in the combustion chamber 67. The axis J of the fuel injection valve 1 is set so as to be slightly downward in the combustion chamber 67 (to face the direction opposite to the height position where the ignition plug 65 is provided). The attachment angle γ is generally about 10 ° to 50 °.

The white arrows in the drawing indicate the flow of intake air, and the hatched arrows indicate the flow of exhaust gas.

The fuel of the internal combustion engine 60 is directly injected from the fuel injection valve 1 into the combustion chamber 67 at the timing of intake, and immediately before ignition, the spray extends so as to directly hit the spark plug 65 at the spray angle θs. Form 80. On the other hand, spray 80
The component toward the direction of the piston 69 becomes lean, so that the fuel spray is not excessively sent to the piston 69 side. Therefore, the adhesion of the fuel spray to the piston 69 can be reduced. The mixture is then compressed during the compression stroke,
It is possible to realize stable combustion in which the ignition is stably performed by the ignition plug 65 and the emission of unburned gas is suppressed.

Such a direct injection gasoline engine is
There is no need to actively use the flowing air in the combustion chamber 67 to guide the spray fuel to the ignition plug 65, and lean combustion can be realized without significantly changing the cylinder head of a conventional engine.

According to the fuel injection valve 1 of this embodiment, by removing a part of the wall surface forming the injection hole 7b at the outlet of the injection hole 7b, the restriction of the flow of the spray is released and the restriction is released. The mixture having the flammable concentration is rich on the side where the mixture is applied, and the mixture having the flammable concentration is formed lean on the side where the mixture is restricted.
For this reason, the flow of the spray is less likely to be disturbed than in a configuration in which a part of the injection hole is shielded to form the deflected spray. This is because, in the fuel injection valve 1 that injects the fuel by applying a swirling force,
This is particularly effective without impairing the applied turning energy.

A third embodiment of the present invention will be described with reference to FIGS. Components corresponding to the components in the above-described embodiment are denoted by the same reference numerals, and redundant description will be omitted.

FIGS. 8A and 8B are enlarged views of the nozzle member 7 of the electromagnetic fuel injection valve 1, wherein FIG. 8A is a longitudinal sectional side view of the nozzle member 7, and FIG. FIG. 7 is a plan view when viewed from an arrow N direction.

In this embodiment, the nozzle member 7
The housing that houses the fuel swirling element 22 and a part of the valve body 40 is a separate member, a side wall member 71 and a bottom wall member 72.
Are combined. Side wall member 71
Is provided with a fitting window 71a for fitting the bottom wall member 72 at the tip thereof, the seat surface 7a, the injection hole 7b, and the step surfaces 7i, 7j,
The bottom wall member 72 provided with 7k, 7m, 7n and the concave portion 7e is fitted into the fitting window 71a and the joint portion 73 is welded to integrate them.

According to the fuel injection valve 1 having such a configuration,
Since the portion appropriately set according to the engine volume and the mounting angle of the fuel injection valve can be concentrated on the bottom wall member 72 of the nozzle member 7, it is possible to share the components constituting the various fuel injection valves 1. , And productivity can be improved.

The concave portion 7e for regulating the adhesion of the deposit is
It is provided on the nozzle tip surface 7d of the bottom wall member 72. On the nozzle tip surface 7d where the outlet opening of the injection hole 7b provided in the bottom wall member 72 is formed, the surfaces 7j, 7 orthogonal to the axis J are provided.
A stepped rectangular groove formed by the surfaces 7i, 7k, 7n substantially parallel to m and the axis J is formed.

In this embodiment, the degree of opening to the fuel flow is increased by removing the wall surface of the fuel injection hole 7b for restraining the fuel flow into a rectangular shape. Therefore, it is effective for generating a spray having a strong flatness. It is also effective to form a relatively solid spray in order to promote the diffusion and dispersion of the spray. Further, by generating a relatively solid spray, it is possible to generate a spray that is hardly affected by fluctuations in the in-cylinder pressure, and it is easy to specify the spread angle and the reach of the spray. The spray particle size is the same as in the first embodiment.

The orifice length H of the stepped rectangular groove
By making n 'larger than Hn ", it is possible to deflect the spray toward the" plug "side. The other configuration is the same as that of the first embodiment.

FIG. 9 is a diagram in which the fuel injection valve 1 in this embodiment is adapted to an internal combustion engine. 9A is a longitudinal side view of the internal combustion engine, FIG. 9B is a plan view of a piston,
(C) is a side view of the fuel injection valve.

The internal combustion engine 60 in this embodiment is
The piston 69 is provided with a cavity 69a so that the spray can easily reach the ignition plug 65 using the tumble flow 83. The cavity 69 a is provided in a range from substantially directly below the intake valve 64 to almost directly below the exhaust valve 66 in the radial direction of the piston 69. The tumble flow 83 flows on the cylinder head side to the exhaust valve 66 side, turns to the piston 69 side below the exhaust valve 66, flows along the curved surface of the cavity 69a, and lifts the spray from immediately below the intake valve 64. , A flow toward the spark plug 65 is created. By the tumble flow 83 guided by the cavity 69a, it is possible to enhance the convergence of the combustible mixture (spray) 80 to the ignition plug 65.

Further, as shown in FIG.
The length Li of the nozzle member 7 should be larger than the diameter Di. The fuel injection valve 1 having such a configuration includes an internal combustion engine 60 that can easily avoid interference between the fuel injection valve 1 and other components (for example, the cylinder head 63 and the intake manifold 62 shown in FIG. 5). Make it easy to realize.
Thereby, for example, it is possible to reduce the mounting angle θi of the fuel injection valve 1, and it is effective to suppress the amount of spray distribution to the piston 69 side and improve the combustibility. In addition, practically, 1 <
Used with Li / Di <5.

[0066]

According to the present invention, by providing a recess at a very small distance from the outlet edge of the injection hole of the fuel injection valve, a deposit that is easily peeled off is formed, and the fuel spray shape due to the growth of the deposit is formed. And a change in the spray structure can be suppressed. Further, by setting the minute distance from the edge of the outlet of the injection hole to the concave portion to be 0.01 to 0.25 times the diameter of the injection hole, it is possible to secure a favorable spray shape and structure.

Further, according to the internal combustion engine of the present invention, it is possible to prevent the shape of the fuel spray injected from the fuel injection valve so as to extend toward the spark plug from being hindered by the deposit, and to improve the ignition and combustion characteristics. Degradation can be prevented.

[Brief description of the drawings]

FIG. 1 is a vertical sectional side view of an electromagnetic fuel injection valve according to a first embodiment of the present invention.

2 is an enlarged view showing a nozzle portion of the electromagnetic fuel injection valve shown in FIG. 1, (a) is a longitudinal side view, (b)
3A is a plan view of the nozzle member viewed from the direction of the arrow N in FIG. 3A, and FIG. 3C is a cross-sectional view taken along line AA in FIG.

FIG. 3 is a drawing schematically showing a recess and a deposit provided at the tip of an injection hole of a fuel injection valve according to the present invention.

FIG. 4 is a graph showing the separability of the deposit in the fuel injection valve according to the present invention.

FIG. 5 is a drawing schematically showing a longitudinal section of spray injected from a fuel injection valve in relation to a deposit in the first embodiment of the present invention.

FIG. 6 is an enlarged view showing a nozzle portion according to a second embodiment of the present invention, in which FIG.
(B) is a plan view of the nozzle member viewed from the direction of arrow N in (a).

FIG. 7 is a vertical sectional side view of an internal combustion engine according to a second embodiment of the present invention.

FIG. 8 is an enlarged view showing a nozzle portion according to a second embodiment of the present invention, wherein FIG.
(B) is a plan view of the nozzle member viewed from the direction of arrow N in (a).

FIG. 9 is a vertical sectional side view of an internal combustion engine according to a third embodiment of the present invention.

[Description of Signs] 1 ... Electromagnetic fuel injection valve, 40 ... Valve, 6 ... Ball, 7 ...
Nozzle member, 7a: seat surface, 7b: injection hole, 7e: concave portion, 60: internal combustion engine.

Continued on the front page (72) Inventor Yuzo Kadokomu 502 Kandate-cho, Tsuchiura-shi, Ibaraki Pref. Machinery Research Laboratories, Hitachi, Ltd. In-house (72) Inventor Hiromasa Kubo 2520 Oji Takaba, Hitachinaka City, Ibaraki Pref.Hitachi, Ltd.Automotive Equipment Group (72) Inventor Toru Ishikawa 2520 Oji Takaba, Hitachinaka City, Ibaraki Automobile Equipment Group (72) Inventor Yasuo Ikuizawa 2520, Odaiba, Hitachinaka-shi, Ibaraki F-term in the automotive equipment group of Hitachi, Ltd. (reference) 3G066 AA02 AD12 BA32 CC06U CC15 CC32 CC34 CC48 CE22

Claims (5)

[Claims] An injection hole, a valve seat located upstream of the injection hole, a valve for opening and closing a fuel passage to the injection port in contact with or separated from the valve seat, and driving means for driving the valve The fuel injection valve according to claim 1, wherein a concave portion is provided on a tip end surface of the nozzle at a minute distance from an edge of an outlet of the injection hole. 2. The injection hole according to claim 1, wherein the minute distance from the edge of the outlet of the injection hole to the concave portion is 0.00 of the diameter of the injection hole.
A fuel injection valve characterized by being set to 1 to 0.25 times. 3. The method according to claim 1, wherein the recess is
A fuel injection valve formed annularly around the injection hole. 4. The fuel injection valve according to claim 1, wherein an outlet opening of the injection hole is formed on a step surface, and the recess is formed on a lower surface. 5. A cylinder, a piston reciprocating in the cylinder, intake means for introducing air into the cylinder, exhaust means for exhausting combustion gas from the cylinder, and fuel in the cylinder. A fuel injection valve for injecting,
A fuel supply means for supplying fuel from a fuel tank to the fuel injection valve; and an ignition device for igniting a mixture of air introduced into the cylinder by the intake means and fuel injected into the cylinder by the fuel injection valve. An internal combustion engine comprising: the fuel injection valve according to any one of claims 1 to 4 as the fuel injection valve.