JP2002130084A - Fuel injection valve and internal combustion engine equipped with the same - Google Patents

Abstract

[PROBLEMS] To provide a spray suitable for improving the ignition performance of an internal combustion engine and reducing the emission of unburned gas components in combustion. A fuel injection valve (1) is provided with an injection hole (8) for injecting fuel at an outlet of the injection hole (8).
To generate a flat spray. Further, the distance from the valve body axis J of the two side walls B1 and B3 forming the groove is set such that one is longer than the other, thereby forming a deflected spray deflected to the longer distance side.

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 for injecting fuel into an internal combustion engine, and more particularly to a technique for forming a fuel spray having excellent ignition performance and combustion performance.

[0002]

2. Description of the Related Art An in-cylinder fuel injection device that injects fuel directly into a combustion chamber is known, while an in-pipe fuel injection device that injects fuel into an intake pipe of an engine is known.

[0003] Such a direct injection gasoline engine is disclosed in Japanese Patent Application Laid-Open No. 6-146886. In this prior art, a consideration is given to a mounting position of a fuel injection valve, and a configuration in which an intake port (tumble flow) of a vertical vortex is formed in a combustion chamber by an intake port extending upward from an intake opening end is leaner than a theoretical air-fuel mixture. It stabilizes combustion with fuel and improves fuel efficiency.

[0004]

In the above prior art,
As described below, sufficient consideration has not always been given to a spray shape or a spray structure capable of improving both the ignitability (ignitability) and the combustibility (reduction of unburned gas emission).

To optimize the spray injected from the fuel injection valve, it is necessary to consider the following characteristics. The first is the spray shape, and the spread angle and the reach of the spray are factors. The second is the spray particle size, and it is necessary to make the particle size distribution uniform by minimizing the number of large particles as much as possible. The third is a spray structure, which needs to optimize the spatial distribution of fuel particles to be sprayed.

As a result of an experimental analysis of how these spray characteristics contribute to the combustion characteristics of an internal combustion engine, the following has been found. In order to improve the ignitability, it is effective to increase the distribution of the fuel mixture around the igniter to increase the distribution of the mixture having the flammable concentration. On the other hand, when the adhesion of the fuel particles to the piston is reduced, the unburned gas components (HC, CO) of the combustion tend to decrease, and the combustibility is improved. In consideration of these characteristics, it is desirable to directly reach the ignition device and not to cause fuel spray to adhere to the piston.

Further, in order to obtain combustion stability in a wide range from a low engine speed to a high engine speed, it is desirable that the spray shape does not change due to a pressure change in the cylinder. This is because the geometrical positional relationship between the injector and the igniter is fixed, and it is important that the spray spread is constant in order to always supply the appropriate concentration of the mist to the igniter. .

Further, when the spray directly reaches the ignition device, the control of the air flow in the cylinder is unnecessary or simplified, which is effective in terms of cost.

In particular, in the case of stratified charge combustion with a high in-cylinder pressure, if the spray can directly reach the igniter without being crushed by the pressure, it is effective in terms of ignitability, flammability and cost.

In other words, the spray injected by the conventional injector tends to spread when the in-cylinder pressure is low, and the spray tends to collapse when the in-cylinder pressure increases. in this case,
When the arrangement of the injector and the ignition device is determined based on the state where the in-cylinder pressure is relatively high, when the in-cylinder pressure is low, the fuel easily adheres to the top and side surfaces of the cylinder or the piston head. On the basis of the state where the internal pressure is relatively low, when the in-cylinder pressure becomes high, there is a tendency that it becomes difficult for the spray suitable for combustion to reach the ignition device.

SUMMARY OF THE INVENTION It is an object of the present invention to improve the ignitability of an internal combustion engine and to realize a spray suitable for reducing the amount of unburned gas components of combustion.

[0012]

In order to achieve the above-mentioned object, a spray is formed which concentrates in the vicinity of an ignition device and whose shape is hardly changed by a change in pressure in a cylinder. For this reason, when viewed on a plane including the valve element axis of the fuel injection valve and the axis in the piston linear motion direction, the spray is flattened and deflected toward the ignition device, and when viewed on a plane perpendicular to the piston linear motion direction, the spray is substantially Generates an isosceles triangular spray. At this time, the distribution of the spray as viewed in a plane perpendicular to the valve element axis is solid. As a result, the spray shape is less likely to be crushed in response to fluctuations in the in-cylinder pressure.

More specifically, the flow of the spray is released in the groove direction by cutting the injection hole into a groove at the outlet of the fuel injection valve provided at the fuel injection valve and injecting the fuel. To produce a flat spray. Further, the distance from the valve body axis of the two side walls forming the groove may be set such that one is longer than the other, and a deflected spray deflected to the longer distance side may be formed. Alternatively, by providing a plurality of injection holes or a substantially arcuate injection hole connected downstream in the fuel injection direction, the spray that is flattened and deflected to the side with many injection holes or the substantially arcuate injection hole is provided. Should be generated.

In the internal combustion engine, the above-described fuel injection valve is preferably arranged so that the spray is concentrated on the ignition device side.

[0015]

1 to 4 show an embodiment of the present invention.
This will be described with reference to FIG. In the following description, a plane that includes the valve axis (valve axis) and is parallel to the valve axis is referred to as a longitudinal section,
A plane perpendicular to the valve axis is called a transverse section.

The electromagnetic fuel injection valve 1 injects fuel by opening and closing the sheet portion in accordance with a duty ON-OFF signal calculated by the control unit.
The magnetic circuit faces the core 2 including the yoke 3, the plug 2a for closing the open end of the yoke 3, and the columnar portion 2b extending to the center of the yoke 3, with a gap therebetween. Anchor 4
Consists of At the center of the columnar portion 2b, an anchor 4 made of a magnetic material, a rod 5, and a ball 6
A hole 4A for holding the spring 10 as an elastic member, which is inserted so that the valve body 40 composed of The sheet surface 9 is formed on the nozzle member 7 so as to be located together with the injection hole 8 and on the upstream side of the injection hole 8. 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 the gap facing the columnar portion 2b of the core 2 and the valve body 40 of the yoke 3, a seal ring that is mechanically fixed between the two to prevent fuel from flowing to the coil 14 side. 12 are provided. A coil 14 for exciting a magnetic circuit is wound around a bobbin 13 and its outer periphery is molded with a plastic material. The terminals 17 of the coil assembly 15 composed of these are inserted into holes 16 provided in the plug portion (collar) 2 a of the core 2. The terminal 17 is connected to a terminal of a control unit (not shown).

The yoke 3 is provided with a plunger receiving portion 18 for receiving the valve element 40, and has a diameter larger than that of the plunger receiving portion 18 and a nozzle receiving portion 19 for receiving the stopper 19 and the nozzle member 7 therein. A part 20 extends through the end of the yoke 3. A hollow portion 5A is provided on the rod 4 side of the anchor 4 to allow passage of fuel. The cavity 5A is provided with a fuel outlet 5B. The valve body 40 is the anchor 4
When the outer periphery of the ball 6 contacts the inner periphery of the seal ring 12, its axial movement is guided, and the vicinity of the ball 6 or the end of the rod 5 on the ball 6 side is moved inside the fuel swirling element 22. Guided by the peripheral surface 23. The fuel swirling element 22 is inserted into a hollow portion formed by the nozzle member 7 and positioned in contact with the inner wall 21 on the upstream side of the seat surface 9. In this embodiment, the nozzle member 7 is formed of one member so as to have a cylindrical side wall (peripheral wall) 72 and an end surface (bottom surface) 71. In this case, the nozzle member 7 forms a housing that houses a part of the fuel swirling element and the valve element.

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 in the fuel and the pipe from entering the valve sheet between the ball 6 and the seat surface 9.

Next, a nozzle member 7 having a rectangular groove structure according to this embodiment will be described with reference to FIG.

The center of the injection hole 8 coincides with the axis J (valve axis) of the valve body, and the wall surface is formed parallel to the axis J. Nozzle tip surface 7 where outlet opening of injection hole 8 is formed
A has a rectangular groove formed by planes B1 and B3 substantially parallel to the axis J and a plane B2 orthogonal to the axis J. At this time, the injection hole width of the notched portion is W1
+ W2, the injection hole length is formed to Hn ″, and the nozzle member 7
Is formed by two planes 7A and B2 perpendicular to the axis J formed so as to sandwich the injection hole 8 and planes B1 and B3 parallel to the axis J connecting these planes. Here, the distances W1 and W2 between the axis J and the planes B1 and B3 are W2> W1.
It is formed with.

According to the above configuration, the outlet opening surface of the injection hole 8 is formed with a groove on the flat surfaces 7A and 7B having steps.

In the configuration shown in FIG. 2A, the spray has the following features.

(A) On the side of the passage wall forming the injection hole 8 where the distance from the axis of the groove is long, the distribution amount of the spray (the distribution amount of the air-fuel mixture) is large. Are flattened and the spray is evenly distributed in the spray cross section.

Due to the effects (a) and (b), the ignitability is improved and the fuel efficiency is improved.

In the above structure, the "notch" in the notch surface A1 or the like does not limit the processing method, but means a shape with a part removed. A working method such as press working (plastic working) or casting using a mold material may be used. This is the same in the following embodiments. Further, the ball 6 does not necessarily have to be spherical.
That is, it may be a conical needle valve.

In FIG. 2B, the diameter do of the injection hole, the arrow "PLUG", the arrow "PISTON", and the lines K and M are defined. The line K passes through the center of the injection hole 8 and has a cutout surface B1,
A line parallel to B3, a line M is a line passing through the center of the injection hole 8 and orthogonal to K, and the arrow “PLUG” and the arrow “PISTO”
N ″ is parallel to the line M.

In FIG. 2, the fuel swirl element 22 is provided with an axial groove 25 and a radial groove 26 in which the outer peripheral portion of the fuel swirl element 22 is set in a plane. In the present embodiment, the axial groove 25 is formed as a plane, but may be another shape such as an annular passage. Such an axial groove 25 and a radial groove 26
Is a fuel passage introduced from above the fuel swirling element 22, and the fuel passing through the axial groove 25 is introduced eccentrically from the axial center in the radial groove 26 to impart swirling to the fuel, and the nozzle member 7 Has a function of promoting atomization at the time of injection from the injection hole 8 provided in the nozzle. Here, the swirling strength (swirl number S) provided by the fuel swirling element 22 is obtained by the following equation.

[0028]

## EQU1 ## S = (Angular momentum) / ((Momentum in injection axis direction)
× (radius of injection hole)) = (2 · do · Ls) / (n · ds ² · cos (θ / 2)) where, do: diameter of injection hole Ls: eccentricity of groove (valve shaft center and groove) (Width) distance between centers n: Number of grooves θ: Angle of valve seat ds: Rheologically equivalent diameter expressed using groove width W and groove height H = 2 · W · H / W + H is there. Increasing the swirl number promotes atomization and disperses the spray.

The operation of the fuel injection valve 1 of this embodiment will be described. When an electric signal is applied to the coil 14, a magnetic circuit is formed by the core 2, the yoke 3, and the anchor 4, and the anchor 4
Is sucked into the core 2 side. When the anchor 4 moves, the ball 6 separates from the seat surface 9 and the fuel passage is opened.

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 A provided in the anchor 4 for allowing the fuel to pass therethrough.
To the downstream through the fuel outlet 5B, and the stopper 19
The fuel is swirled and supplied to the seat through the gap between the shaft 5 and the rod 5, the axial fuel passage 25, and the radial fuel passage 26.

Next, the spray structure obtained by the fuel injection valve 1 of the present embodiment will be described with reference to FIGS.

In the internal combustion engine 60 shown in FIG.
Piston 69 provided reciprocally in cylinder 68
Moves up and down in the cylinder 68 according to the rotation of a crankshaft (not shown). A cylinder head 63 is attached to an upper portion of the cylinder 68, and forms a closed space together with the cylinder 68. An intake manifold 62 that guides external air into the cylinder via an intake air amount control device 61 having a built-in throttle valve is provided in the cylinder head 63.
And an exhaust manifold for guiding the combustion gas burned in the cylinder 68 to the exhaust device.

The intake manifold 6 of the cylinder head 63
An intake valve 64 is provided on the second side, an ignition device 65 is provided in the center, and an exhaust valve 66 is provided on the side opposite to the intake valve 64. An intake valve 64 and an exhaust valve 66 are provided in a combustion chamber 67.
It is provided to extend inside. Here, the fuel injection valve 1
Is mounted in the vicinity of the intake manifold 62 of the cylinder head 63 so that the axis J of the fuel injection valve 1 is slightly downward in the combustion chamber 67 (with the igniter 65 provided). Are set to face in opposite directions). The mounting angle θi is generally 10 ° to 50 °
It is about. 69 indicates a piston. The white arrows in the figure indicate the flow of intake air, and the hatched arrows indicate the flow of exhaust gas.

As shown in FIG. 3A, the spray injected from the fuel injection valve 1 of this embodiment is directly injected into the combustion chamber 67 at the timing of intake, and immediately before the ignition, the region 80 is injected. It is distributed as follows. The spray is flattened and deflected to the arrow “PLUG” side. Immediately before ignition, the spray angle θsv
Is larger than the angle θp between the line connecting the injection hole 8 and the ignition device 65 and the valve element axis J. That is, there is a relationship of θsv> θp.

As shown in FIG. 4, the spray reaching distance Lsp in the θp direction immediately before ignition is larger than the distance Lp between the injection hole 8 and the ignition device 65. That is, Lsp>
Lp. AA cross section of the spray 80 is "PL
It is distributed flattened and deflected to the UG "side, and the density inside the spray is
Almost uniform.

That is, the fuel of the internal combustion engine 60 is directly supplied to the combustion chamber 6 by the fuel injection valve 1 in synchronization with the intake timing.
7 and is distributed like a region 80 immediately before ignition. The spray that is flattened and deflected toward the ignition device 65 can directly reach the ignition device 65. On the other hand, the adhesion of the spray to the crown surface of the piston 69 is suppressed.
Thereafter, the air-fuel mixture is compressed during the compression stroke, is stably ignited by the ignition device 65, and stable combustion in which the amount of discharged gas is suppressed is realized. Since the density inside the spray is almost uniform, the spray shape hardly changes due to the pressure fluctuation in the cylinder, and it is possible to provide a spray with good combustion stability over a wide engine speed range.

In this embodiment, the groove depth (Hn-Hn ″)
The groove widths W1, W2 and the groove length D1 are appropriately determined by the inner diameter of the cylinder, that is, the engine volume and the mounting angle of the injection valve. In order to obtain a substantial spray structure (spray angle θsv, spread angle θsh, reach distance Lsp), (1)
(Hn−Hn ″) is provided with a step larger than at least 0, (2) W1 <W2 is set,
(3) Setting W1, W2 <d0, (4) D1>
It is preferable to set d0.
(Hn−Hn ″) is 0 <(Hn−H) in a normal range of up to 3 liters and a mounting angle of the injection valve of 10 ° to 50 °.
n ″) / d0 ≦ 1 is preferably set in the range.

In the present embodiment, the projection 7A is formed at the outlet of the injection hole 8 of the nozzle member 7, but this projection 7A
Need not necessarily be provided. However, by providing the projection 7A, a large step (Hn ″ −Hn) can be formed, and the spread angle θsh can be further increased.

Further, by adjusting the injection hole widths W1 and W2, the spray angle θsv and the spread angle θsh can be adjusted. That is, θsv can be increased by increasing W2 compared to W1, and θsh can be increased by decreasing both W1 and W2.

Another embodiment will be described with reference to FIG.

In the internal combustion engine 60 shown in FIG. 5A, a cavity 69B is provided so that the spray can easily reach the ignition device 65 using the tumble flow 83. FIG. 5 (b)
Is a plan view of the piston 69. FIG. Cavity 69B
Is provided in the radial direction of the piston 69 in a range from almost immediately below the intake valve 64 to almost immediately below the exhaust valve 66. The tumble flow 82 flows through the exhaust valve 66 on the cylinder head side.
Side, turns to the piston side below the exhaust valve 66, flows along the curved surface of the cavity 69B, and
A flow toward the ignition device 65 is created so as to lift the spray from immediately below. By the tumble flow 82 induced by the cavity 69B, it is possible to enhance the convergence of the mixture 80 having the flammable concentration to the ignition device 65.

As shown in FIG. 5C, the length Li of the nozzle member 7 'is preferably made larger than the diameter Di.
In this case, the mounting angle θi can be reduced, which is effective in suppressing the amount of spray distribution on the piston side and improving the combustibility. In practice, 1 <L
It is preferable to set i / Di <5.

The nozzle member 71 may be configured as shown in FIG.

The nozzle member 71 is constituted only by the bottom surface portion 71 of the housing for accommodating a part of the fuel swirling element and the valve body, and is constituted by a member different from the side wall portion 73.
The side wall 73 forms a nozzle guide body that guides the nozzle member 71. The nozzle member 71 is welded to the side wall 73 (nozzle guide) along the joint 71D. The outlet opening of the injection hole 8 has a surface B11 substantially parallel to the axis J,
A rectangular groove formed by B13 and a surface B11 orthogonal to the axis J is formed. That is, in the present configuration, productivity can be improved by consolidating portions that are appropriately changed depending on the volume of the engine and the mounting angle of the injection valve only on the bottom surface portion 71 of the housing. Further, the nozzle member 71 of this embodiment sets W1 = W2, sets the height of the side wall B11 to (Hn−Hn ″), and sets the height of the side wall B13 to (Hn′−H).
n ''). As a result, it is possible to generate a spray with a strong deflection, so that it is effective to suppress the spray distribution amount to the piston side and improve the combustibility.

Next, another embodiment of the fuel injection valve will be described with reference to FIGS.

In the nozzle member 7 ″ shown in FIG. 7, a plurality of injection holes 81, 80 A, 80
The plate member 70 provided with B and 80C is connected. The injection hole 81 is a second swirl passage having a diameter larger than the diameter d0 of the injection hole 8. The fuel passes through the injection holes 80A, 80B, and 80C further downstream, and is injected as flat and deflected spray toward the “PLUG” side. FIG. 8 (a)
It is a perspective view of the plate member 70, and defines the direction of the arrow Y1. FIG. 8B is a plan view of the plate member 70 viewed from Y1, and FIG. 8C is a cross-sectional view. Assuming that the radius of the second swirl passage 81 is d1, the relationship of d1> d0 holds. The broken line Co indicates the outer shape of the injection hole 8 for convenience. The spray angle θs described earlier with reference to FIGS.
To adjust v, θsh, and reach Lsp,
A, 80B, and 80C may be adjusted by the diameter, depth Lo, distances L1, L2 from the valve body axis J, distance D2 from the line K, and the like. In particular, to obtain a spray having a large θsv, L2
> D0 / 2. Further, the number of injection holes is not necessarily three. In this embodiment, by adjusting the number and diameter of the injection holes, it is possible to control the distribution of the spray cross section with high accuracy, which is effective for improving the ignitability and the combustibility.

Further, as shown in FIG.
By providing a substantially arcuate injection hole 84 at 0 ', a shell-like spray may be generated. Using this plate member,
It is possible to generate a homogeneous spray with less concentration unevenness in the spray cross section, which is effective for improving ignitability. The plate member 70 'is preferably formed by plastic working such as press working.

Further, as shown in FIG. 10, a plurality of injection holes may be provided on the plate member 74 directly connected to the injection holes 8. In this case, the injection holes 82A, 82B, and 82C provided on the “PLUG” side with respect to the line K are parallel to the valve element axis J, and the injection holes 82D and 82 provided on the “PISTON” side.
E and 82F are preferably formed with an inclination angle of θor with respect to the valve body axis J. By using the plate member of this embodiment,
It is easy to reduce the size of the plate member, which is effective for cost reduction.

Further, the nozzle member 75 of the electromagnetic fuel injection valve 1 may be configured as shown in FIG. FIG.
1 is an enlarged view of a nozzle member 75 of the electromagnetic fuel injection valve 1, (a) is a longitudinal sectional view of the nozzle member 75,
(B) is a plan view of the nozzle member 75 of (a) viewed from the direction of the arrow N. The bottom surface of the nozzle member 75 is constituted by a surface 75B orthogonal to the axis J and a projection 75A. V-groove type notched surfaces A1, A2 of injection holes
Are the inclination angles a1, a2 of the injection hole outlet surface with respect to the axis J of the valve body (valve axis) and the central axis (injection direction) of the fuel injection hole 8.
And the length of the V-groove is formed by W1. At this time, the orifice length of the cut-out portion is L at the deepest cut-out portion and L 'at the non-cut-out (least cut-out portion) portion. It is formed of one plane perpendicular to the axis J and two inclined surfaces connecting the planes.

In the present embodiment, the projection 75A is formed at the outlet of the fuel injection hole 8 on the tip end surface of the nozzle member 7, but the projection 75A is not necessarily provided.
However, by providing the protruding portion 7A, large inclination angles a1 and a2 can be formed.

Further, the groove length W1 does not need to be stopped in the projection 75A, and the V-groove may be extended to the bottom surface 75B. In this case, the degree of flatness of the spray in the direction of arrow R can be increased.

Further, the nozzle member 76 of the electromagnetic fuel injection valve 1 may be configured as shown in FIG. FIG.
2 is an enlarged view of a nozzle member 76 of the electromagnetic fuel injection valve 1, (a) is a longitudinal sectional view of the nozzle member 76,
(B) is a plan view of the nozzle member 76 of (a) viewed from the direction of the arrow N. The difference between the nozzle member 76 of the electromagnetic fuel injection valve 1 shown in FIGS. 12A and 12B and the nozzle member 7 of the electromagnetic fuel injection valve 1 described with reference to FIG.
The thick portion 76C is provided on the outer peripheral portion of the bottom surface of the nozzle 76 portion. That is, in the present configuration, the thick portion 7
6C reduces vibration noise when the ball 6 is seated on the seat surface 9.

Further, the nozzle member 77 of the electromagnetic fuel injection valve 1 may be configured as shown in FIG. FIG.
3 is an enlarged view of the nozzle member 77 of the electromagnetic fuel injection valve 1, (a) is a longitudinal sectional view of the nozzle member 77, and (b) is an arrow of the nozzle member 77 of (a). FIG. 3 shows a plan view seen from the N direction. In this embodiment, a plane B2 parallel or substantially parallel to the axis J is provided at the outlet of the fuel injection hole 8.
1, B22, B23 and planes B24, B orthogonal to the axis J
25 are formed. Also, the orifice length L '''of the stepped rectangular groove is changed to L
By making it larger, it is possible to deflect the spray toward the “PLUG” side. Other configurations are the same as those of the first embodiment of the present invention.
This is the same as the embodiment.

[0054]

According to the present invention, the flow of the spray is opened in the groove direction by cutting the injection hole into a groove at the outlet of the injection hole provided in the fuel injection valve and injecting the fuel.
Flat spray can be generated by constraining at the side wall. further,
By setting the distance from the valve body axis of the two side walls forming the groove such that one is longer than the other, a deflected spray deflected to the longer distance side can be formed. Alternatively, by providing a plurality of injection holes or a substantially arcuate injection hole connected downstream in the fuel injection direction, the spray that is flattened and deflected to the side with many injection holes or the substantially arcuate injection hole is provided. Can be generated. In each case, the spray cross section is uniform due to the uniform spray distribution.
The flattening makes it difficult for the spray to collapse due to fluctuations in the cylinder pressure.
A deflected spray can be formed.

Further, in the internal combustion engine, the above-described fuel injection valve is arranged so that the spray is concentrated on the ignition device side, so that the ignition performance of the internal combustion engine is improved and the amount of unburned gas components emitted from the combustion is reduced. it can.

[Brief description of the drawings]

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

FIG. 2 is an enlarged view of a nozzle member 7 of the electromagnetic fuel injection valve 1; FIG. 2A is a longitudinal sectional view of a nozzle member 7;
(B) is a plan view of the nozzle member 7 of (a) viewed from the direction of the arrow N.

3A is a diagram schematically showing a state in which a fuel injection valve according to the present invention is applied to an internal combustion engine that injects fuel into a combustion chamber (cylinder), and FIG. It is the schematic diagram seen from the side.

FIG. 4 schematically shows a vertical section and a horizontal section of a spray injected from a fuel injection valve according to the present invention in relation to an ignition device.

5A and 5B show another embodiment of the internal combustion engine according to the present invention, wherein FIG. 5A is a longitudinal sectional view of the internal combustion engine, FIG. 5B is a schematic view of the piston head viewed from the intake valve side, and FIG. Is a fuel injection valve.

FIG. 6 is an enlarged view of a nozzle member 71 according to another embodiment of the present invention, and FIG.
FIG. 5B is a vertical sectional view of the nozzle member 71 shown in FIG.
FIG. 2 shows a plan view seen from a direction.

FIG. 7 shows an enlarged view of a nozzle member 7 ″ in another embodiment according to the present invention, and (a) shows a nozzle member 7 ″.
FIG. 5B is a vertical sectional view of FIG.
FIG. 2 shows a plan view seen from a direction.

FIG. 8 is an enlarged view of a plate member 70 according to another embodiment of the present invention, and FIG.
0 (b), the plate member 70 of FIG.
The plan view seen from the direction, and (c) shows a sectional view.

FIG. 9 shows a plan view of a plate member 70 in another embodiment according to the present invention.

FIG. 10 shows an enlarged view of a nozzle member 7 ″ and a plate member 74 in another embodiment according to the present invention.
(A) is a longitudinal sectional view of the nozzle member 7 ″, (b) is (a)
Is a plan view of the plate member 74 of FIG.

FIG. 11 is an enlarged view of a nozzle member 75 according to another embodiment of the present invention.
FIG. 5B is a longitudinal sectional view, and FIG. 5B is a plan view of the nozzle member 75 of FIG.

12 shows an enlarged view of a nozzle member 76 according to another embodiment of the present invention, and FIG.
6, and FIG. 6B is a plan view of the nozzle member 75 of FIG.

FIG. 13 is an enlarged view of a nozzle member 77 according to another embodiment of the present invention.
7 is a longitudinal sectional view, and FIG. 7B is a plan view of the nozzle member 77 of FIG.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Electromagnetic fuel injection valve, 40 ... Valve body, 6 ... Ball valve, 8
... Injection hole, 7 ... Nozzle, 7A ... Nozzle protrusion, B1 ... Rectangular groove cutout surface, 70 ... Plate member, 80 ... Distributed shape of deflected spray, 22 ... Fuel swirl element, 23 ... Guide hole, 32
... Axial fuel passage, 33 ... Fuel swirl chamber, 60 ... Internal combustion engine, 70 ... Electromagnetic fuel injection valve.

──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F02M 61/18 340 F02M 61/18 340C 360 360J F02B 23/10 F02B 23/10 DM F02M 61/14 310 F02M 61/14 310S (72) Inventor Yuzo Kadokomu 502 Kandate-cho, Tsuchiura-shi, Ibaraki Pref. Machinery Research Laboratories, Hitachi, Ltd. Inside the research laboratory (72) Inventor Hiromasa Kubo 2520 Ojitakaba, Hitachinaka-shi, Ibaraki Pref.Hitachi, Ltd.Automotive equipment group (72) Inventor Toru Ishikawa 2520 Odaitakaba, Hitachinaka-shi, Ibaraki Automobile equipment Hitachi, Ltd. F-term within the group (reference) 3G023 AA00 AA01 AA04 AB01 AC05 AD01 AD08 AD29 3G066 AA02 AA03 AB02 AD12 BA14 BA26 CC06U CC14 CC15 CC24 CC26 CC32 CC37 CC41 CC48 CD29 CE22

Claims (18)

[Claims] 1. A fuel comprising: an injection hole; a valve seat upstream of the injection hole; a valve body for opening and closing a fuel passage between the valve seat; and driving means for driving the valve body. In the injection valve, at an outlet of the injection hole, a part of a wall surface forming the injection hole is cut out in a groove shape, and a distance between two side walls forming the groove and a valve body axis is longer than one of the other. A fuel injection valve characterized by being provided as described above. 2. A fuel system comprising: an injection hole; a valve seat upstream of the injection hole; a valve body for opening and closing a fuel passage between the valve seat; and driving means for driving the valve body. A fuel injection valve, wherein a plurality of injection holes are connected to the injection holes downstream in a fuel injection direction. 3. A fuel comprising: an injection hole; a valve seat upstream of the injection hole; a valve body for opening and closing a fuel passage between the valve seat; and driving means for driving the valve body. In the injection valve, a fuel swirl passage having a different inner diameter is connected to the injection hole downstream in a fuel injection direction, and a plurality of injection holes are connected further downstream. 4. The fuel injection valve according to claim 3, wherein the plurality of injection holes are arranged asymmetrically with respect to a valve body axis. 5. The fuel injection valve according to claim 3, wherein a center position of the plurality of injection holes is located outside of a valve body axis with respect to an edge of the most upstream injection hole. valve. 6. A fuel comprising: an injection hole; a valve seat upstream of the injection hole; a valve body for opening and closing a fuel passage between the valve seat; and driving means for driving the valve body. In the injection valve, a fuel swirl passage having a different inside diameter is connected to the injection hole downstream in a fuel injection direction, and a substantially arcuate injection hole is provided further downstream. 7. The fuel injection valve according to claim 1, wherein at a fuel inlet to the fuel injection valve,
A fuel injection valve which applies a pressure of 0.5 to 25 MPa to fuel and injects the same. 8. The fuel injection valve according to claim 1, wherein the spray injected from the injection hole includes a center axis of the injection hole and is parallel to the center axis. A cross-section that is flat and deflected to one side with respect to the valve body axis, includes a central axis of the injection hole, and has a substantially isosceles triangular shape with the injection hole as a vertex in a cross-section orthogonal to the cross-section; A fuel injection valve characterized in that a spray cross section taken perpendicularly to a central axis of the injection hole injects a spray that is distributed almost uniformly in a range where the spray reaches. 9. A fuel comprising: an injection hole; a valve seat upstream of the injection hole; a valve body for opening and closing a fuel passage between the valve seat; and driving means for driving the valve body. In the injection valve, a groove-shaped notch is provided in the injection hole, and the spray is flattened and deflected to the side of the two side walls forming the groove that has a longer distance to the valve body. A fuel injection valve characterized in that a spray cross section taken perpendicularly to a central axis of the injection hole injects spray that is substantially uniformly distributed. 10. An injection hole, a valve seat upstream of the injection hole,
In a fuel injection valve including a valve body that opens and closes a fuel passage between the valve seat and a driving unit that drives the valve body, a plurality of injection holes are provided downstream of the injection holes, and the number of the injection holes is large. A fuel injection valve characterized in that the spray is flattened and deflected to the side, and in a range where the spray reaches, the spray cross section taken perpendicularly to the central axis of the injection hole injects the spray with a substantially uniform distribution. 11. An injection hole, a valve seat upstream of the injection hole,
A fuel injection valve comprising a valve body for opening and closing a fuel passage between the valve seat and a driving unit for driving the valve body, wherein a substantially arcuate injection hole is provided downstream of the injection hole. Fuel injection, wherein the spray is flattened and deflected to the side of the injection hole, and in a range where the spray reaches, the spray cross section taken perpendicularly to the central axis of the injection hole injects the spray with a substantially uniform distribution. valve. 12. A fuel injection valve according to any one of claims 1 to 3, 6 and 9 to 11, wherein a fuel passage for imparting a swirling force to fuel is formed upstream of said valve seat. Fuel injection valve. 13. 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 directly in the cylinder. A fuel supply valve for injecting fuel from a fuel tank to the fuel injection valve, air introduced into the cylinder by the intake means, and fuel injected into the cylinder by the fuel injection valve And an ignition device for igniting an air-fuel mixture with the fuel injection valve, wherein the fuel injection valve according to claim 1 is provided as the fuel injection valve, and the groove is formed by providing the groove. The part where the distance from the valve body axis of the side wall that becomes
An internal combustion engine, wherein the fuel injection valve is arranged so as to face the ignition device. 14. 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 directly in the cylinder. A fuel supply valve for injecting fuel from a fuel tank to the fuel injection valve, air introduced into the cylinder by the intake means, and fuel injected into the cylinder by the fuel injection valve And an ignition device for igniting an air-fuel mixture with the fuel injection valve, wherein, as the fuel injection valve, the fuel injection valve according to claim 2, 3 or 10, and the side provided with a large number of the plurality of injection holes is provided. An internal combustion engine, wherein the fuel injection valve is disposed so as to face the ignition device. 15. 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 directly in the cylinder. A fuel supply valve for injecting fuel from a fuel tank to the fuel injection valve, air introduced into the cylinder by the intake means, and fuel injected into the cylinder by the fuel injection valve And an ignition device for igniting an air-fuel mixture with the fuel injection valve, wherein the fuel injection valve includes the fuel injection valve according to claim 6, and the side provided with the substantially arcuate injection hole includes:
An internal combustion engine, wherein the fuel injection valve is arranged so as to face the ignition device. 16. 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 directly in the cylinder. A fuel supply valve for injecting fuel from a fuel tank to the fuel injection valve, air introduced into the cylinder by the intake means, and fuel injected into the cylinder by the fuel injection valve An ignition device for igniting an air-fuel mixture of the fuel injection valve, the fuel injection valve, an injection hole, a valve seat upstream of the injection hole, and a valve body that opens and closes a fuel passage between the valve seat. An internal combustion engine comprising: a driving unit for driving the valve element; wherein the fuel injection valve includes the fuel injection valve according to claim 1, wherein a flat and deflected spray is formed on the ignition device side. Sa An internal combustion engine characterized by arranging the fuel injection valve so that the fuel injection valve is disposed. 17. 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 directly in the cylinder. A fuel supply valve for injecting fuel from a fuel tank to the fuel injection valve, air introduced into the cylinder by the intake means, and fuel injected into the cylinder by the fuel injection valve An ignition device for igniting an air-fuel mixture of the fuel injection valve, the fuel injection valve, an injection hole, a valve seat upstream of the injection hole, and a valve body that opens and closes a fuel passage between the valve seat. An internal combustion engine comprising: a driving unit that drives the valve body. The fuel injection valve includes the fuel injection valve according to claim 1, wherein at the time of ignition, a valve body axis of the fuel injection valve and The ignition The internal combustion engine according to claim 1, wherein the fuel injection valve is arranged such that a spread angle of the spray is larger than an angle between the fuel injection device and the spray device and the spray reaches the ignition device. 18. 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 directly in the cylinder. A fuel supply valve for injecting fuel from a fuel tank to the fuel injection valve, air introduced into the cylinder by the intake means, and fuel injected into the cylinder by the fuel injection valve An ignition device for igniting an air-fuel mixture of the fuel injection valve, the fuel injection valve, an injection hole, a valve seat upstream of the injection hole, and a valve body that opens and closes a fuel passage between the valve seat. An internal combustion engine provided with a driving means for driving the valve body, comprising: a fuel injection valve for injecting spray that is substantially uniformly distributed when a spray section is viewed by deflecting and spraying the spray toward the ignition device. , At the time of ignition, the fuel injection valve is set so that the spread angle of the spray is larger than the angle between the valve body axis of the fuel injection valve and the ignition device, and so that the spray reaches the ignition device. An internal combustion engine, which is arranged.