JP2000097030A - Direct injection type internal-combustion engine and fuel injection valve for direct injection - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a direct injection type internal combustion engine and a fuel injection valve for direct injection whereby enhancement of the output and enhancement of the fuel economy can be accomplished compatibly. SOLUTION: Atomized gas from a fuel injection valve 1 takes an atomization pattern having an approx. axis-symmetrical shape for the nozzle hole axis from the nozzle hole for a first specified distance approximately and takes an atomization pattern having an approx. point-symmetrical or line-symmetrical shape in which the section shape perpendicularly intersecting the nozzle hole axis spreads in one direction perpendicularly intersecting the nozzle hole axis after a second specified distance longer than the first specified distance from the nozzle hole. Stratified combustion is made through atomization for the first distance during the compression stroke of a piston 72, and premixed combustion is performed by conducting atomization after the second distance during the suction stroke of the piston 72.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a four-cycle direct injection type internal combustion engine for directly injecting fuel into a combustion chamber, and a direct injection type injection valve used therefor.

[0002]

2. Description of the Related Art Conventionally, at the time of high output, premix combustion is performed,
In a direct injection internal combustion engine in which stratified combustion is performed at low power and the combustion state is switched depending on the operation state of the engine, as described in the reissued patent WO 96/36808, the shape of the combustion chamber and the air flow Means have been proposed to optimize the method, the position of the fuel injection valve and the characteristics of the spray and the like, the position of the ignition plug, and the like, and simultaneously satisfy the conflicting demands of improving the output and improving the fuel efficiency.

[0003]

When an in-cylinder injection internal combustion engine is used as an automobile engine, various restrictions are imposed on the type and specifications of the engine, the layout of intake / exhaust system parts and fuel system parts, and the appearance of the vehicle. Yes, not all of the above known means can be adopted. In other words, unless the existing technology and equipment are used as much as possible while adopting a method that achieves both improvement in output and improvement in fuel efficiency, the cost will increase and the business will not be profitable. Against this background, one of the most important technical issues is compatibility between premixed combustion and stratified combustion. As described above, in order to achieve a balance between these two combustion concepts, the shape of the combustion chamber, the air flow method, the position of the fuel injection valve and the characteristics of the spray, the position of the ignition plug, and the like are related. In the premixed combustion, it is necessary to generate a homogeneous air-fuel mixture by diffusing sprays, and in the stratified combustion, it is necessary to collect converging sprays near the spark plug. In the conventional known means, since the basic shape of the spray of the fuel injection valve is changed by the difference of the injection back pressure, if the spray characteristic under a certain back pressure is defined, the spray characteristic under another back pressure will be As a result, the spray characteristics are difficult to control, and there is a problem that the spray characteristics cannot be optimized.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-described problems. In premixed combustion, the spray characteristics are relatively large in a spatially wide range with respect to the mixing of air and fuel spray. In addition, in the case of stratified combustion, in the case of stratified combustion, the spray characteristics affect the mixture of air and fuel spray in a spatially narrow range and in a short time range. Given that, in other words, the spray characteristics required in these two combustion concepts differ spatially and temporally, the spatial and temporal ranges of spray required in stratified combustion are noted. Achieves spray characteristics suitable for stratified combustion, and achieves spray characteristics suitable for premix combustion in the spatial and temporal ranges of spray required for premix combustion, achieving both improved output and improved fuel efficiency it can And to obtain a value of the direct injection type internal combustion engine and a cylinder injection type fuel injection valve used therein.

[0005]

A cylinder injection type internal combustion engine according to the present invention comprises a combustion chamber formed between an upper surface of a piston reciprocally disposed in a cylinder and a lower surface of a cylinder head. A fuel injection valve for in-cylinder injection for directly injecting fuel into the combustion chamber, a spark plug disposed on the cylinder head so as to face the combustion chamber, and a spark plug provided on the cylinder head so as to face the combustion chamber. The intake port
In a direct injection internal combustion engine provided with an exhaust port provided in the cylinder head so as to face the combustion chamber, the spray of the fuel injection valve sprays the first spray from the injection port of the fuel injection valve.
Takes a spray pattern having a substantially axially symmetrical shape with respect to the injection port axis of the fuel injection valve up to the predetermined distance, and a second predetermined distance longer than the first predetermined distance from the injection port of the fuel injection valve. Hereinafter, an operation mode in which a cross-sectional shape perpendicular to the injection port axis of the fuel injection valve adopts a spray pattern having a substantially point-symmetrical shape or a substantially line-symmetrical shape having a spread in one direction orthogonal to the injection-hole axis, and performing stratified combustion. In the operation mode in which the spray up to the first predetermined distance is sprayed during the compression stroke of the piston and premix combustion is performed,
Is sprayed during the intake stroke of the piston.

In the fuel injection valve, the injection port axis of the fuel injection valve is substantially parallel to the main flow direction of the air taken into the combustion chamber from the intake port, and the injection port of the second spray pattern is provided. The cylinder head is disposed on the cylinder head such that a short axis direction in a cross-sectional shape perpendicular to the axis is directed to a main flow of air taken into the combustion chamber from the intake port.

[0007] The spray pattern up to the first predetermined distance is substantially conical, and the spray pattern after the second predetermined distance has a substantially flat cross section orthogonal to the nozzle axis. Or it is almost glasses-like.

Further, the spraying performed during the compression stroke up to the substantially first predetermined distance has a length from the injection port of the fuel injection valve at the time of collision with the upper surface of the piston. This is performed at a timing such that the distance becomes equal to or less than a predetermined distance of 1.

The spraying performed during the intake stroke after the second predetermined distance is performed at a timing such that the spray tip does not directly interfere with the upper surface of the piston.

[0010] Further, the spray that is performed during the intake stroke after the substantially second predetermined distance does not directly interfere with the inner wall surface of the combustion chamber.

Further, the fuel injection valve has a swirl generating member for giving a swirl to the injected fuel.

The direction of spread of the spray after the second predetermined distance in the cross-sectional shape orthogonal to the injection port axis is as follows:
This is determined by setting the position of the swirl generating member in the circumferential direction.

[0013] The swirl generating member is a revolving body disposed upstream of a valve seat portion of the fuel injection valve and having two revolving grooves formed symmetrically with respect to a point. The direction of spread of the spray in the cross-sectional shape perpendicular to the injection port axis is determined by determining the position of the revolving body in the circumferential direction with respect to the valve axis of the fuel injection valve.

The revolving body is positioned in the circumferential direction between the revolving body and the valve body and is housed in the valve body. The valve body is positioned in the circumferential direction between the revolving body and the solenoid part to form the solenoid. It is housed in the part.

Further, the injection port axis of the fuel injection valve is inclined with respect to the axial direction of the movable shaft.

Further, the in-cylinder fuel injection valve according to the present invention is directed to an in-cylinder fuel injection valve for directly injecting fuel into a combustion chamber, wherein the fuel injection valve is located at a first predetermined distance from the injection port with respect to the injection port axis. Takes a spray pattern having a substantially axially symmetric shape,
Substantially a point-symmetric shape or a substantially line-symmetric shape in which a cross-sectional shape perpendicular to the nozzle axis extends in one direction perpendicular to the nozzle axis after a substantially second predetermined distance longer than the first predetermined distance from the nozzle hole. It is configured to adopt a spray pattern having a shape.

Further, the spray pattern up to the first predetermined distance is substantially conical, and the spray pattern after the second predetermined distance has a substantially flat cross section orthogonal to the nozzle axis. Or it is almost glasses-like.

[0018] Further, the invention has a swirl generating member for giving a swirl to the injected fuel.

The direction of spread of the spray after the second predetermined distance in the sectional shape perpendicular to the injection port axis is as follows:
This is determined by setting the position of the swirl generating member in the circumferential direction.

The swirl generating member is a revolving body arranged upstream of the valve seat portion and having two revolving grooves formed in a point-symmetric manner. The swirl generating member is configured to spray the spray after the second predetermined distance. The determination of the spreading direction in the cross-sectional shape perpendicular to the axis is performed by determining the circumferential position of the revolving structure with respect to the valve shaft.

Further, the revolving body is positioned in the circumferential direction with respect to the valve body and is accommodated in the valve body. The valve body is positioned in the circumferential direction with the solenoid portion and the solenoid is positioned. It is housed in the part.

Further, the injection port shaft is inclined with respect to the axial direction of the movable shaft.

[0023]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings. Embodiment 1 FIG. FIG. 1 is a view for explaining a fuel spray pattern under atmospheric pressure applied to stratified combustion in a direct injection internal combustion engine according to Embodiment 1 of the present invention, and FIG. FIG. 1B is a side view, and FIG. 1B is a sectional view of a fuel spray pattern. FIG. 2 is a view for explaining a fuel spray pattern under atmospheric pressure applied to premixed combustion in the direct injection internal combustion engine according to Embodiment 1 of the present invention, and FIG. FIG. 2B is a cross-sectional view of the fuel spray pattern.

In the first embodiment, the specifications of the structure of the fuel injection valve 1 are set so that the fuel spray pattern injected from the fuel injection valve 1 substantially changes depending on the time after the start of injection. That is, the fuel spray pattern is the fuel spray pattern A at the time t ≦ t1 after the start of the injection (FIG. 1).
And a time t after the start of the injection.
A fuel spray pattern B (fuel spray pattern shown in FIG. 2) at ≧ t2 (t2> t1) is adopted. This fuel spray pattern A is provided for an operation mode in which stratified combustion is performed. As shown in FIG. 1, the fuel spray pattern A includes a substantially center spray and a peripheral spray (conical shape). On the other hand, it has a substantially axially symmetric shape. The distance from the injection port of the fuel injection valve 1 to the spray tip at t = t1 has a first predetermined distance L1. On the other hand, fuel spray pattern B
Is provided in an operation mode in which premix combustion is performed. As shown in FIG. 2, the cross-sectional shape of the spray at t ≧ t2, that is, the cross-sectional shape orthogonal to the injection axis of the fuel injection valve 1 is It has a substantially flat shape. The distance from the injection port of the fuel injection valve 1 to the spray tip at t = t2 has a second predetermined distance L2 (L2> L1). As described above, in the first embodiment, the fuel spray pattern injected from the fuel injection valve 1 is substantially changed depending on the distance from the injection port of the fuel injection valve 1, that is, the distance from the injection port of the fuel injection valve 1. Has a conical shape composed of substantially central spray and peripheral spray up to a first predetermined distance L1, and has a substantially flat cross-sectional shape after the second predetermined distance L2. The specifications are set.

Here, the injection stroke in the first embodiment will be described with reference to FIGS. Note that FIG.
FIGS. 3A and 3B are views for explaining an injection stroke in a direct injection internal combustion engine according to Embodiment 1 of the present invention. FIG. 3A is a side view of a compression stroke injection, and FIG. 3B is an intake stroke injection. FIG. FIG. 4 is a view for explaining a fuel spray pattern under back pressure applied to stratified combustion in the direct injection internal combustion engine according to Embodiment 1 of the present invention, and FIG. FIG. 4B is a cross-sectional view of the fuel spray pattern.

In FIG. 3, the piston 72 is
0, slidably disposed in the cylinder 70, the piston 7
2 and a region surrounded by the cylinder head 5
Is composed. Then, two intake ports 73 (FIG. 3)
(Only one intake port 73 is shown) and an exhaust port 76 are provided in the cylinder head 5 so as to face the combustion chamber 71. The two intake ports 73 are formed on one side of a reference surface including the axis of the cylinder 70 on the lower surface of the cylinder head 5, and each intake port 73 opens and closes the opening of the intake port 73 to the combustion chamber 71. 73. Furthermore, on the upper surface of the piston 72, a vertical vortex (tumble flow) of the intake air that has entered the combustion chamber 71 from the intake port 73 is promoted at a position opposite to the intake port 73 on one side of the reference surface on the upper surface of the cylinder 70. As described above, a concave portion 72a which is depressed in a curved shape with respect to the upper surface of the cylinder 70 is formed. The ignition plug 75 is connected to the cylinder head 5.
It is arranged near the axis of the cylinder 70 on the lower surface. When the piston 72 is in a required range near the top dead center position, the injection port of the fuel injection valve 1 faces the recess 72a,
In addition, the longitudinal direction in the cross-sectional shape of the spray of the fuel spray pattern B (spreading direction of the spray in a plane passing through the fuel injection direction Y of the fuel injection valve 1 in FIG. It is arranged so as to be parallel to a plane (a plane which passes through the line X in FIG. 3B and is orthogonal to the plane of the drawing) formed by a line connecting the opening centers of the two intake ports 73 and an extension of the axis of the intake port 73. Have been. This fuel injection valve 1 is
Under the condition of in-cylinder injection, fuel injection can be performed at a significantly higher pressure (for example, 5 MPa) as compared with normal intake port injection.

First, as shown in FIG. 3A, fuel is injected from the start of injection to time t1 in the compression stroke (stratified combustion). At time t1, the distance L from the injection port of the fuel injection valve 1 to the concave portion 72a is shorter than the first predetermined distance L1 (L ≦ L1). The fuel is supplied to the fuel injection valve 1 in a fuel spray pattern A as shown in FIG.
From the combustion chamber 71. At this time, since the inside of the combustion chamber 71 is in the compression stroke, it is in a high pressure state. Therefore, since the initial velocity of the injected fuel is reduced, the fuel that has exited from the nozzle of the fuel injection valve 1 performs a spraying motion at the beginning, but stalls at an early stage, and the penetration force of the sprayed fuel is largely suppressed. Further, since the spray speed decreases, for example, the entrainment of the surrounding air into the main spray becomes relatively large, and the penetration force of the spray fuel is greatly suppressed. As a result, the fuel spray pattern is shown in FIG.
As shown in FIG. 5, a compact solid fuel spray pattern having a small spread is obtained. Note that this compact solid fuel spray pattern has a cross-sectional shape that is substantially axially symmetric with respect to the injection port axis of the fuel injection valve 1 and that the distance from the injection port of the fuel injection valve 1 to the spray tip is small. A first predetermined distance L
It is almost the same as 1. Since this compact fuel spray pattern has more directivity, the fuel reflected on the inner surface of the concave portion 72a can be easily directed to the ignition plug 75, that is, the fuel can be efficiently converged on the ignition plug 75. it can.

As shown in FIG. 3 (b), in the intake stroke (premix combustion), at the time t2 from the start of injection.
Perform fuel injection until. At time t2, the distance L from the injection port of the fuel injection valve 1 to the recess 72a is longer than the second predetermined distance L2 (L> L2). In order to increase the amount of fuel, the fuel is injected longer than the time t2. Even at the end of the injection in this case, the distance L from the injection port of the fuel injection valve 1 to the concave portion 72a is longer than the distance from the injection port of the fuel injection valve 1 to the tip of the injected fuel.
Fuel is injected from the fuel injector 1 into the combustion chamber 71 in a fuel spray pattern B as shown in FIG. At this time, since the inside of the combustion chamber 71 is in the intake stroke, the combustion chamber 71 is in a low pressure state, and the fuel injected into the combustion chamber 71 has substantially the same shape as the fuel spray pattern B. Then, the spread direction of the spray (spread direction in the cross-sectional shape of the spray) in the plane passing through the fuel injection direction Y of the fuel injection valve 1 and orthogonal to the paper surface in FIG. 3B is shown in FIG. Is parallel to a plane passing through the line X at right angles to the plane of the drawing, so that the entire spray is substantially caught in the main flow of air, and premixing of air and fuel is effectively performed. At the same time, the adhesion of the fuel to the wall surface of the cylinder 70 can be substantially eliminated.

As described above, according to the first embodiment,
Since the fuel injected from the fuel injection valve 1 adopts the fuel spray pattern A up to the first predetermined distance L1, and adopts the fuel spray pattern B after the second predetermined distance L2, the stratified combustion occurs. By applying the fuel spray pattern A to the fuel spray pattern A and the fuel spray pattern B to the premixed combustion, the spray characteristics suitable for the stratified combustion and the spray characteristics suitable for the premixed combustion can be compatible, and the output and fuel efficiency can be improved. An in-cylinder injection internal combustion engine is obtained. In the compression stroke, the fuel is sprayed to the concave portion 72a at the time when the distance L from the nozzle of the fuel injection valve 1 to the concave portion 72a becomes the first predetermined distance L1 or less in the fuel spray pattern A. Since the stratified combustion is performed, the fuel reflected on the inner surface of the concave portion 72a can be effectively converged on the ignition plug 75 by effectively utilizing the directivity of the compact spray. In the intake stroke, the fuel is sprayed in the fuel spray pattern B,
The direction of spread of the spray in a plane passing through the fuel injection direction Y of the fuel injection valve 1 and perpendicular to the plane of the drawing is parallel to a plane passing through the line X in FIG. 3B and perpendicular to the plane of the drawing. Since the premix combustion is performed while maintaining the state in which the distance L from the nozzle 1 to the concave portion 72a is longer than the spray length of the fuel spray pattern B, the entire spray substantially becomes involved in the main flow of air. , The premixing of air and fuel is effectively performed, and the fuel cylinder 7
0 can be substantially eliminated from adhering to the wall surface.

Here, in the case of an internal combustion engine utilizing a vertical vortex flow (tumble flow) of intake air, premixed combustion and stratified combustion can be established as in the above-mentioned known technique. In the case of 1, the fuel does not adhere to the cylinder wall surface or the piston upper surface, and ideal premix combustion can be performed. In addition, in the stratified combustion, if the air-fuel mixture near the spark plug becomes too rich, smoke (soot) may be generated. In such a case, in the first embodiment, the fuel distribution in the longitudinal direction of the spray after the second predetermined distance L2 is changed by changing the specifications of the fuel injection valve 1, and the first predetermined distance In a substantially axially symmetric spray pattern up to L1, a portion where the fuel distribution is dense in the same direction as the longitudinal direction of the spray after the second predetermined distance L2 is substantially formed, and the degree of convergence of the spray near the spark plug is reduced. By performing the control, generation of smoke due to combustion of the rich mixture near the spark plug can be avoided.

In the first embodiment, as shown in FIG. 2, the fuel spray pattern B used for the premix combustion has a transverse cross-sectional shape of the spray at t ≧ t2, that is, the injection port of the fuel injection valve 1. It is assumed that the cross section perpendicular to the axis has a substantially flat shape.
Is not limited to the fuel spray pattern in which the cross-sectional shape of the spray at t ≧ t2 is substantially flat, and t ≧ t2
It is only necessary that the cross-sectional shape of the spray in has a substantially point-symmetric shape or a substantially line-symmetric shape centered on the nozzle axis (spray direction). For example, the cross-section of the substantially eyeglass shape shown in FIG. The cross-sectional shape may be a surface shape, a substantially rhombic cross-sectional shape shown in FIG. 5B, or a cross-sectional shape as shown in FIG. In the first embodiment, the fuel injection valve 1 is arranged so that the direction of the spray is parallel to the direction of the main flow of the intake air. However, the direction of the spray is different from the direction of the main flow of the intake air. Therefore, the spray direction may not necessarily be parallel, and the spray direction may intersect the direction of the main intake air at an acute angle, that is, it may be substantially parallel.

Embodiment 2 FIG. In the first embodiment, the fuel spray pattern A used for the stratified combustion is composed of the substantially central spray and the peripheral spray, and has a substantially axially symmetric shape with respect to the injection port axis of the fuel injection valve 1. In the second embodiment, as shown in FIG. 6, the fuel spray pattern A provided for the stratified combustion has no (or almost no) center spray and only peripheral spray (hollow spray). It has a substantially axially symmetric shape with respect to one injection port axis. Also in this fuel spray pattern A, under the back pressure, the spray shape is the same as the compact spray shape shown in FIG. 4, so that the same effect as in the first embodiment can be obtained in the second embodiment. .

Embodiment 3 In the first embodiment, the fuel spray pattern A used for the stratified combustion is composed of the substantially central spray and the peripheral spray, and has a substantially axially symmetric shape with respect to the injection port axis of the fuel injection valve 1. In the third embodiment, as shown in FIG. 7, the fuel spray pattern A provided for the stratified combustion is composed of solid spray,
Have a substantially axially symmetrical shape with respect to the injection port axis. Also in this fuel spray pattern A, under the back pressure,
Since the spray shape is equivalent to the compact spray shape shown in FIG. 4, the same effect as in the first embodiment can be obtained in the third embodiment.

Embodiment 4 FIG. 8 is a sectional view showing a fuel injection valve used in a direct injection internal combustion engine according to the fourth embodiment. The in-cylinder fuel injection valve 1 includes a housing body 2 and a valve device 3 covered by a holder 35 that is caulked at one end of the housing body 2. A fuel supply pipe 4 is connected to the other end of the housing body 2.
The high-pressure fuel is supplied into the fuel injection valve 1 through 7.
The tip of the fuel injection valve 1 is inserted into the injection valve insertion hole 6 of the cylinder head 5 of the internal combustion engine, and is attached by being sealed with a wave washer 60 or the like.

The valve device 3 includes a stepped hollow cylindrical valve body 9 having a small-diameter cylindrical portion 7 and a large-diameter cylindrical portion 8, and a fuel injection hole 10 fixed to the tip of a center hole in the valve body 9 and serving as an injection hole.
, A needle valve 12 that is a valve body that opens and closes the fuel injection hole 10 by being separated from and brought into contact with the valve seat 11 by a solenoid device 50 described later, and guiding the needle valve 12 in the axial direction. A revolving body 13 is provided as a swirl generating member that gives a revolving motion to the fuel that is about to flow into the fuel injection hole 10 of the valve seat 11.
The valve body 9 of the valve device 3 cooperates with the housing body 2 to form a housing of the fuel injection valve 1.

The housing body 2 includes a first housing 30 having a flange 30a for mounting the fuel injection valve 1 to the cylinder head 5, and a second housing 40 to which a solenoid device 50 is mounted. The solenoid device 50 includes a bobbin 52 around which a coil 51 is wound, and a core 53 installed on the inner periphery of the bobbin 52, and the winding of the coil 51 is connected to a terminal 56. Core 53
Has a hollow cylindrical shape so that the inside thereof becomes a fuel passage, and a spring 55 is suspended between the sleeve 54 and the needle valve 12 in the hollow portion. A movable armature 31 is attached to the other end of the needle valve 12 so as to face the distal end side of the core 53.
2 for guiding the slide 2 along the inner peripheral surface of the valve body 9
2a and a spacer 32 installed on the first housing 30
And a needle flange 12b which is in contact with the needle flange 12b.

FIG. 9 is a sectional view showing a main part of the fuel injection valve shown in FIG. 8, and FIG. 10 is a front view of the revolving structure of the fuel injection valve shown in FIG. 8 as viewed from a valve seat side. In each figure, the revolving body 13 of the valve device 3 is a substantially hollow cylindrical member having a center hole 15 that slidably supports the needle valve 12 which is a valve body in the center in the axial direction. When assembled in the device 3, a first end face 16 in contact with the valve seat 11, a second end face 17 opposite the valve seat 11, and a valve body 9 between these end faces, which is part of a hollow housing. Inner peripheral surface 18
And a peripheral surface 19 having a portion in contact with. The second end face 17 of the revolving body 13 is supported by being in contact with a shoulder 20 of an inner peripheral face 18 of the valve body 9 at a peripheral portion thereof, and a passage groove 21 extending in the shape direction is formed. The fuel can flow from the inner peripheral portion to the outer peripheral portion of the second end face 17. A pair of flat surfaces extending in the axial direction are formed on the peripheral surface 19 of the revolving body 13 so as to face each other. As a result, the peripheral surface 19 comes into contact with the inner peripheral surface of the valve body 9 and A pair of outer peripheral surface portions 19a for defining positions and a flat surface provided between the pair of outer peripheral surface portions 19a, and a flow path portion 1 which forms an axial flow path 22 for fuel together with the inner peripheral surface 18;
9b are formed. Further, the valve seat 1 of the rotating body 13
An inner circumferential groove 24 having a U-shaped cross section of a predetermined width formed at an inner periphery adjacent to the center hole 15 of the first end face, and a circumferential face at one end is formed on an axial end face facing the first end face, that is, the first end face 16. A swivel groove 25 having a U-shaped cross section is provided which is connected to the flow path portion 19b of the surface 19 and extends substantially radially inward therefrom and is connected at the other end to the inner circumferential annular groove 24 in a tangential direction. . The two revolving grooves 25 are formed point-symmetrically about the axis of the revolving body 13.

The operation of the fuel injection valve 1 configured as described above will be described. When the coil 51 of the solenoid device 50 is energized from the outside via the terminal 56, a magnetic flux is generated in a magnetic path formed by the movable armature 31, the core 53, and the housing body 2, and the movable armature 31
5 is attracted toward the core 53 side. And
The needle valve 12 integrated with the movable armature 31 moves upward by a predetermined stroke in FIG. 1 until the needle flange 12b contacts the spacer 32. The needle valve 12 is guided and held on the inner peripheral surface of the valve body 9 by a guide 12a. When the distal end of the needle valve 12 is separated from the valve seat 11 and a gap is formed, high-pressure fuel introduced from the fuel supply pipe 4 first passes through the passage between the valve body 9 and the needle valve 12, 13 second end face 17
And flows into the axial flow path 22 on the peripheral surface through the passage groove 21. Then, it flows into the swirl groove 25 of the first end face 16 of the revolving body 13, flows radially inward, flows into the inner circumferential annular groove 24 of the first end face 16 tangentially, and forms a swirl flow to form the valve seat 11. , And is sprayed from the outlet of the tip.

Here, as shown in FIG. 10, each of the turning grooves 25 is offset from the valve shaft by a predetermined amount, and the side surface far from the valve shaft is connected to the outer periphery of the inner peripheral annular groove 24 in a tangential direction. I have. Therefore, since there are two swirl grooves 25, it is difficult to mix the fuel in the inner circumferential groove 24, that is, to make the swirl fuel uniform, and the fuel flow vector in the circumferential direction of the fuel spray is not uniform. Thus, the fuel spray pattern in the first embodiment is obtained. Because, up to the first predetermined distance L1 immediately after the injection, the spread of the spray is still small, and the spray energy is not dispersed. A). Then, after the second predetermined distance L2, only a portion having a high spray density resulting from the two swirl grooves 25 forms a substantial spray structure, and a portion having a low spray density diffuses into the air. As a result, almost kinetic energy is lost, so that a substantially flat or substantially glasses-like spray structure (fuel spray pattern B) is realized.

As described above, according to the fourth embodiment,
By forming two swirl grooves 25 offset from the valve shaft, a substantially cone-shaped spray structure (fuel spray pattern A) is adopted until a first predetermined distance L1 immediately after injection, and the second
After the predetermined distance L2, the fuel injection valve 1 that can adopt a substantially flat or substantially glasses-like spray structure (fuel spray pattern B) can be realized. This revolving body 13
Can be set as one of the current product specifications,
It does not involve any cost increase. That is, the revolving unit 13 can be manufactured by diverting the existing technology and equipment, so that the inexpensive fuel injection valve 1 can be obtained. Further, since the swirl is given to the fuel spray, the atomization of the fuel is promoted and the penetration force of the spray is suppressed. Then, since the penetration force of the spray is suppressed, the force of the spray is attenuated, and the spray of the spray to the inner wall surface of the cylinder is suppressed. As a result, the adhesion of the spray to the inner wall surface of the cylinder is suppressed, so that it is possible to prevent the fuel from dissolving the lubricating film formed on the inner wall surface of the cylinder and lowering the slidability of the piston. Further, the revolving unit 1 is positioned such that the directions of the two revolving grooves 25 of the revolving unit 13 are positioned with respect to the circumferential base point of the injection valve 1.
By assembling the fuel injection valve 3, it is easy to determine the spread direction of the transverse cross-sectional shape of the fuel spray pattern B in the injection valve 1, and the mounting direction of the fuel injection valve 1 to the combustion chamber of the internal combustion engine can be easily determined.

Here, the revolving superstructure 1 according to the fourth embodiment is described.
The structure of No. 3 is similar to the structure of the revolving superstructure adopted in the conventional general fluid injection valve, but the fuel pressure is at a level (for example, 0.3M) used in the case of normal intake pipe injection.
In Pa), it is difficult to realize the spray pattern as in the present application, and in the case of the intake pipe injection, the back pressure is usually a negative pressure, which is not under the conditions where the spray pattern can be properly used as in the present application. There is no need for that. The present applicant has found that in a direct injection internal combustion engine, the spray characteristics required for the two combustion concepts of stratified combustion and premixed combustion are spatially
Focusing on the difference in time, the spray characteristics required for stratified combustion are realized in the spatial and temporal ranges required for stratified combustion, and the spatial characteristics of spray required for premixed combustion are realized. In order to achieve a fuel injection valve capable of realizing spray characteristics suitable for premixed combustion in a time range, the fuel injection valve has been intensively studied.
In other words, in the in-cylinder fuel injection valve of gasoline injection to which the present invention is applied, since the fuel is at a high pressure (5 MPa or more) and the fuel is a gasoline having a small viscosity, atomization of the fuel is extremely advanced. Formed a substantially hollow cone, and then found that the portion of the fuel particle having a small vector rapidly diffused into the air, resulting in an approximately flat or approximately glasses-like spray pattern.

Embodiment 5 FIG. In the fifth embodiment, the offset of each swivel groove 25 with respect to the valve shaft in the fourth embodiment is reduced. Embodiment 5
According to this, since the offset of each swirl groove 25 with respect to the valve shaft is set small, the swirl is weakened, and the solid fuel spray pattern in the third embodiment can be obtained.
The revolving superstructure according to the fifth embodiment can be set as one type of the current product specification similarly to the fourth embodiment, and does not involve any cost increase.

Embodiment 6 FIG. In the fourth and fifth embodiments, the first end face 16 of the revolving body 13 is formed in a plane orthogonal to the valve shaft, and the revolving groove 25 is formed in the first end face 16 of the plane. In the sixth embodiment, the first end surface 16 of the revolving body 13 is formed as a conical surface centered on the valve shaft, and the revolving groove is formed on the first end surface of the conical surface, and the same effect is obtained.

Embodiment 7 FIG. FIG. 11 is a sectional view showing a main part of a fuel injection valve according to Embodiment 7 of the present invention, and FIG. 12 is a front view of the fuel injection valve shown in FIG. 11 as viewed from a valve seat side. In the seventh embodiment, a flat surface 9a is provided on the outer peripheral surface of the distal end portion of the valve body 9 as an installation reference. The other configuration is the same as that of the fourth embodiment.

In the seventh embodiment, when the revolving body 13 is assembled, the revolving body 13 is incorporated into the valve body 9 based on the flat surface 9a while recognizing the groove direction of the revolving groove 25. Positioning in the circumferential direction with the valve body 9 can be easily performed. Therefore, it is easy to determine the longitudinal direction in the cross-sectional shape of the spray of the fuel spray pattern B on the valve body 9. Further, by attaching the fuel injection valve 1 to the cylinder head 5 on the basis of the flat surface 9a, the longitudinal direction in the cross-sectional shape of the spray of the fuel spray pattern B is determined by the line connecting the centers of the two intake valves 14 and the intake valve 1
The fuel injection valve 1 can be easily attached so as to be parallel to a plane formed by an extension of the axis 4. In addition, if a flat surface is provided on the connector portion of the solenoid device 50 or the outer diameter portion of the mold formed integrally therewith, the flat surface and the flat surface provided on the valve body 9 correspond to each other, Positioning of the valve body 9 and the solenoid device 50 in the circumferential direction can be easily performed. Therefore, it is easy to determine the longitudinal direction in the cross-sectional shape of the spray of the fuel spray pattern B on the fuel injection valve 1.

Embodiment 8 FIG. In the above fourth to seventh embodiments, the center of the injection hole 10 (injection axis) is the needle valve 1.
In the eighth embodiment, the center of the injection hole 10 is inclined with respect to the axis of the needle valve 12. That is, in the eighth embodiment, the spray direction of the fuel sprayed from the injection hole 10 has a predetermined angle with respect to the axis of the needle valve 12. In the cylinder injection type internal combustion engine, there is a great restriction on the mounting position of the fuel injection valve 1 due to space and other problems. In the case of a fuel injection valve whose spray direction coincides with the axial direction of the needle valve 12, the fuel injection valve 1 May not be able to direct the spray direction to a predetermined direction. In the eighth embodiment, by inclining the center of the injection hole 10 with respect to the axis of the needle valve 12, the spray direction with respect to the axis of the fuel injection valve (the axis of the needle valve 12) can be arbitrarily set. Therefore, even if the mounting position of the fuel injection valve is restricted, the spray direction of the fuel can be easily directed in a predetermined direction. In this case, it is necessary to adjust the direction of the density of the spray.

In the fourth to eighth embodiments, the turning groove 25 has a U-shaped cross section.
The cross-sectional shape of 5 is not limited to a U-shape, and may be a triangle or a part of a circle. Also, the cross-sectional area of the swirl groove 25 does not need to be uniform over its length direction, but is gradually reduced toward the downstream so that the inflow portion into the inner peripheral annular groove 24 has a predetermined cross-sectional area. It is also possible to set.
Furthermore, the turning groove 25 does not necessarily need to be formed linearly. Further, the revolving body 13 forming the swirling flow is provided with the valve body 9.
And may be formed integrally with the valve seat 11. Further, the revolving groove 25 is connected to the first end face 16 of the revolving body 13.
But the inner peripheral surface of the valve body 9 or the valve seat 11
The same effect can be obtained by forming a diagonal groove on the tapered surface and using the diagonal groove as a turning groove. Further, an oblique groove is formed on the outer peripheral surface of the needle valve 12, and the needle valve 12
May also be used as the revolving superstructure. In addition, the first
Although the groove provided to be open in the end face 16 is the turning groove 25, the turning groove may be an offset hole 25a penetrating the turning body 13 as shown in FIG. The oblique hole 25b penetrating the revolving unit 13 as shown in FIG.

Further, in each of the above embodiments, the case where the main flow of the air flow in the combustion chamber is a vertical vortex flow (tumble flow) is described as an example. The same effect can be achieved by setting flat spray directed to the optimum point of the spiral flow as the piston descends, and setting the piston cavity etc. so that the compression stroke spray is also optimal for stratified combustion in that state. Obtainable.

[0049]

Since the present invention is configured as described above, it has the following effects.

According to the present invention, the combustion chamber formed between the upper surface of the piston and the lower surface of the cylinder head arranged reciprocally in the cylinder, and the cylinder for directly injecting fuel into the combustion chamber An injection fuel injection valve, a spark plug disposed in the cylinder head so as to face the combustion chamber,
In a direct injection internal combustion engine having an intake port provided in the cylinder head so as to face the combustion chamber and an exhaust port provided in the cylinder head so as to face the combustion chamber, The spray takes a spray pattern having a substantially axially symmetrical shape with respect to the injection port axis of the fuel injection valve up to a substantially first predetermined distance from the injection port of the fuel injection valve. After the second predetermined distance that is longer than the predetermined distance, the cross-sectional shape orthogonal to the injection port axis of the fuel injection valve has a substantially point symmetric shape or a substantially line symmetric shape having a spread in one direction orthogonal to the injection port axis. In an operation mode in which a spray pattern is adopted and stratified combustion is performed, spray up to the substantially first predetermined distance is sprayed during the compression stroke of the piston, and in an operation mode in which premix combustion is performed, the second mode is used. Since the spray after a predetermined distance is sprayed during the intake stroke of the piston, spray characteristics suitable for each of stratified combustion and premixed combustion can be realized, and a cylinder that achieves both improved output and improved fuel efficiency can be achieved. An internal injection type internal combustion engine is obtained.

In the fuel injection valve, the injection port axis of the fuel injection valve is substantially parallel to the main flow direction of the air taken into the combustion chamber from the intake port, and the injection port of the second spray pattern is provided. The cylinder head is disposed in the cylinder head such that a short axis direction in a cross-sectional shape perpendicular to the axis is directed to a main flow of air taken into the combustion chamber from the intake port. Substantially the entire spray after the distance is entrained in the main stream of air, a uniform mixture is generated, and effective premixed combustion can be realized.

The spray pattern up to the substantially first predetermined distance is substantially conical, and the spray pattern after the second predetermined distance has a substantially flat cross section orthogonal to the nozzle axis. Alternatively, since it is substantially glasses-like, a spray pattern suitable for each of stratified combustion and premix combustion can be realized.

The spraying performed during the compression stroke up to the substantially first predetermined distance may have a length from the injection port of the fuel injection valve at the time of collision with the upper surface of the piston. Since the spraying is performed at a timing that is equal to or less than the predetermined distance of 1, the spray collides with the upper surface of the piston and is carried in the direction of the spark plug, so that effective stratified combustion can be realized.

The spraying performed during the intake stroke after the substantially second predetermined distance is performed at a timing such that the spray tip does not directly interfere with the upper surface of the piston. Adhesion is eliminated, and ideal premix combustion can be realized.

Further, since the spray that is performed during the intake stroke after the second predetermined distance does not directly interfere with the inner wall surface of the combustion chamber, the spray is prevented from adhering to the inner wall surface of the combustion chamber. Ideal premix combustion can be realized.

Further, since the fuel injection valve has a swirl generating member for giving a swirl to the injected fuel, the penetration force of the spray is suppressed, and the fuel is prevented from flying to the inner wall surface of the cylinder.

Further, the spread direction of the spray after the second predetermined distance in the sectional shape perpendicular to the injection port axis is as follows:
Since it is determined by the circumferential position of the swirl generating member, it is easy to determine the spreading direction in the cross-sectional shape.

Further, the swirl generating member is a revolving body which is disposed upstream of the valve seat portion of the fuel injection valve and has two revolving grooves formed symmetrically with respect to the point. The direction of spread of the spray of the spray in the cross-sectional shape perpendicular to the injection port axis is determined by determining the position of the revolving body in the circumferential direction with respect to the valve axis of the fuel injection valve. In addition, the apparatus can be manufactured by diverting the equipment, the cost can be reduced, and the spread direction in the sectional shape can be easily determined.

The revolving body is positioned in the circumferential direction with respect to the valve body and accommodated in the valve body, and the valve body is positioned in the circumferential direction with the solenoid portion to form the solenoid. Since it is accommodated in the fuel injection valve, the direction of spread of the spray in the fuel injection valve after the second predetermined distance in the cross-sectional shape orthogonal to the injection port axis can be easily determined, and the main air flow sucked into the combustion chamber and the cross-sectional shape The attachment of the fuel injection valve in consideration of the relationship with the spreading direction in the above becomes easy.

Further, since the injection port axis is inclined with respect to the axial direction of the movable axis of the fuel injection valve, the spray direction can be shifted with respect to the axial direction of the movable axis of the fuel injection valve. The spray direction can be easily set to a predetermined direction even if there is a restriction on the mounting position of.

According to the present invention, the in-cylinder fuel injection valve for directly injecting fuel into the combustion chamber has a substantially axially symmetrical shape with respect to the injection port axis up to a substantially first predetermined distance from the injection port. A substantially symmetrical shape in which a cross-sectional shape perpendicular to the nozzle axis extends in one direction perpendicular to the nozzle axis after a substantially second predetermined distance longer than the first predetermined distance from the nozzle hole, taking a spray pattern. Since it is configured to adopt a spray pattern having a shape or a substantially line-symmetric shape, an in-cylinder fuel injection valve capable of realizing a spray pattern suitable for each of stratified combustion and premixed combustion is obtained.

The spray pattern up to the first predetermined distance is substantially conical, and the spray pattern after the second predetermined distance has a substantially flat cross section orthogonal to the nozzle axis. Alternatively, since it is substantially glasses-like, a spray pattern suitable for each of stratified combustion and premix combustion can be realized.

Further, since a swirl generating member for giving a swirl to the injected fuel is provided, the atomization of the fuel is promoted and the penetration force of the spray is suppressed.

The direction of spread of the spray after the second predetermined distance in the cross-sectional shape perpendicular to the injection port axis is as follows:
Since it is determined by the circumferential position of the swirl generating member, it is easy to determine the spreading direction in the cross-sectional shape.

The swirl generating member is a revolving body provided upstream of the valve seat portion and having two revolving grooves formed symmetrically with respect to a point, and the spout of the spray after the second predetermined distance. Since the determination of the spreading direction in the cross-sectional shape perpendicular to the axis is performed by determining the position of the revolving structure in the circumferential direction with respect to the valve shaft, the revolving structure can be manufactured by diverting existing technology and equipment. The cost is increased, and the spread direction in the cross-sectional shape is easily determined.

The revolving body is positioned in the circumferential direction with respect to the valve body and is accommodated in the valve body, and the valve body is positioned in the circumferential direction with the solenoid portion to form the solenoid. Since it is accommodated in the portion, it becomes easy to determine the direction of spread of the spray of the fuel injection valve in the cross-sectional shape orthogonal to the injection port axis after the second predetermined distance.

Further, since the injection shaft is inclined with respect to the axial direction of the movable shaft, the spray direction can be shifted with respect to the axial direction of the movable shaft, and even if the mounting position of the fuel injection valve is restricted. The spray direction can be easily set to a predetermined direction.

[Brief description of the drawings]

FIG. 1 is a diagram illustrating a fuel spray pattern under atmospheric pressure applied to stratified combustion in a direct injection internal combustion engine according to Embodiment 1 of the present invention.

FIG. 2 is a diagram illustrating a fuel spray pattern under atmospheric pressure applied to premixed combustion in a direct injection internal combustion engine according to Embodiment 1 of the present invention.

FIG. 3 is a diagram illustrating an injection stroke in a direct injection internal combustion engine according to Embodiment 1 of the present invention.

FIG. 4 is a diagram illustrating a fuel spray pattern under back pressure applied to stratified combustion in the direct injection internal combustion engine according to Embodiment 1 of the present invention.

FIG. 5 is a diagram illustrating another fuel spray pattern under atmospheric pressure applied to premixed combustion in the in-cylinder injection internal combustion engine according to Embodiment 1 of the present invention.

FIG. 6 is a diagram illustrating a fuel spray pattern under atmospheric pressure applied to stratified combustion in a direct injection internal combustion engine according to Embodiment 2 of the present invention.

FIG. 7 is a diagram illustrating a fuel spray pattern under atmospheric pressure applied to stratified combustion in a direct injection internal combustion engine according to Embodiment 3 of the present invention.

FIG. 8 is a sectional view showing an in-cylinder fuel injection valve according to Embodiment 4 of the present invention;

FIG. 9 is a cross-sectional view showing a main part of an in-cylinder injection fuel injection valve according to Embodiment 4 of the present invention.

FIG. 10 is a front view of a revolving structure of an in-cylinder fuel injection valve according to Embodiment 4 of the present invention as viewed from a valve seat side.

FIG. 11 is a cross-sectional view showing a main part of a direct injection fuel injection valve according to Embodiment 7 of the present invention.

FIG. 12 is a front view of a revolving structure of an in-cylinder injection fuel injection valve according to Embodiment 7 of the present invention, as viewed from a valve seat side.

FIG. 13 is a sectional view showing a main part of another in-cylinder fuel injection valve applied to the present invention.

[Explanation of symbols]

1. In-cylinder fuel injection valve, 5 cylinder head, 9
Valve body, 9a Flat surface (positioning reference), 10 injection hole (injection hole), 13 revolving body (swirl generating member), 25
Swivel groove, 50 solenoid device, 70 cylinder, 71
Combustion chamber, 72 piston, 73 intake port, 75 spark plug, 76 exhaust port, L1 first predetermined distance,
L2 The second predetermined distance.

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F02D 41/02 325 F02D 41/02 325G 41/34 41/34 E F02M 61/14 310 F02M 61/14 310A 61/18 310 61/18 310B 360 360J F term (reference) 3G023 AA02 AA04 AB03 AC05 AD02 AD03 AD06 AD09 AG01 3G066 AA02 AA03 AB02 AD12 BA16 BA17 BA24 BA65 CC14 CC34 CC43 CC48 CD04 3G301 HA01 HA04 HA16 HA17 JA11 MA02 JA24

Claims (18)

[Claims] 1. A combustion chamber formed between an upper surface of a piston reciprocally disposed in a cylinder and a lower surface of a cylinder head, and in-cylinder fuel injection for directly injecting fuel into the combustion chamber. A valve, a spark plug disposed in the cylinder head so as to face the combustion chamber, and an intake port provided in the cylinder head so as to face the combustion chamber;
In a direct injection internal combustion engine having an exhaust port provided in the cylinder head so as to face the combustion chamber, the spray of the fuel injection valve is sprayed from the injection port of the fuel injection valve to a substantially first predetermined distance. Adopts a spray pattern having a substantially axially symmetrical shape with respect to the injection port axis of the fuel injection valve, and the fuel injection from a second predetermined distance longer than the first predetermined distance from the injection port of the fuel injection valve. In the operation mode in which the cross-sectional shape perpendicular to the nozzle axis of the valve has a substantially point-symmetrical shape or a substantially line-symmetrical shape in which the cross-sectional shape extends in one direction perpendicular to the nozzle axis, and in the operation mode in which stratified combustion is performed, In the operation mode in which the spray up to the first predetermined distance is sprayed during the compression stroke of the piston and premix combustion is performed, the spray after the second predetermined distance is sprayed during the intake stroke of the piston. Like Cylinder injection internal combustion engine, characterized in that it has. 2. The fuel injection valve according to claim 2, wherein an injection port axis of the fuel injection valve is substantially parallel to a main flow direction of air taken into the combustion chamber from the intake port, and the injection port has the second spray pattern. 2. The cylinder according to claim 1, wherein the cylinder head is arranged so that a short axis direction in a cross-sectional shape orthogonal to an axis is directed to a main flow of air taken into the combustion chamber from the intake port. Injection type internal combustion engine. 3. The spray pattern up to the substantially first predetermined distance is substantially conical, and the spray pattern after the second predetermined distance has a substantially flat cross section orthogonal to the nozzle axis. 3. The direct injection internal combustion engine according to claim 1, wherein the internal combustion engine is substantially shaped like glasses. 4. The spraying performed during the compression stroke up to the substantially first predetermined distance has a length from the injection port of the fuel injection valve at the time of collision with the upper surface of the piston. The cylinder injection type internal combustion engine according to any one of claims 1 to 3, wherein the operation is performed at a timing that is equal to or less than a predetermined distance of 1. 5. The spraying performed after the substantially second predetermined distance during the intake stroke is performed at a timing such that the spray tip does not directly interfere with the upper surface of the piston. An in-cylinder injection internal combustion engine according to any one of claims 1 to 3. 6. The in-cylinder injection system according to claim 5, wherein the spray sprayed during the intake stroke after the second predetermined distance does not directly interfere with the inner wall surface of the combustion chamber. Internal combustion engine. 7. The direct injection internal combustion engine according to claim 1, wherein the fuel injection valve has a swirl generating member for giving a swirl to the injected fuel. 8. The spread direction of the spray after the second predetermined distance in the cross-sectional shape orthogonal to the injection port axis is determined by setting the circumferential position of the swirl generating member. 7. A direct injection internal combustion engine according to claim 7. 9. The swirl generating member is a revolving body arranged upstream of a valve seat portion of the fuel injection valve and having two revolving grooves formed in point symmetry. 9. The method according to claim 8, wherein the determination of the direction of spread of the spray of the spray in a cross-sectional shape perpendicular to the injection port axis is performed by determining the position of the revolving structure in the circumferential direction with respect to the valve axis of the fuel injection valve. The direct injection internal combustion engine according to claim 1. 10. The revolving structure is positioned in the circumferential direction between the revolving body and the valve body, and is housed in the valve body. The valve body is positioned in the circumferential direction between the revolving body and the solenoid portion to form the solenoid. 10. The direct injection internal combustion engine according to claim 9, wherein the internal combustion engine is housed in a portion. 11. The direct injection internal combustion engine according to claim 1, wherein an injection port axis of the fuel injection valve is inclined with respect to an axial direction of a movable shaft. 12. An in-cylinder fuel injection valve for injecting fuel directly into a combustion chamber, wherein a spray pattern having a substantially axially symmetrical shape with respect to an injection port axis is employed up to a first predetermined distance from the injection port. A substantially point symmetric shape or a substantially line symmetric shape having a cross-sectional shape perpendicular to the nozzle axis extending in one direction perpendicular to the nozzle axis after a substantially second predetermined distance longer than the first predetermined distance from the nozzle. A fuel injection valve for in-cylinder injection, wherein the fuel injection valve is configured to adopt a spray pattern having: 13. A spray pattern substantially up to the first predetermined distance is substantially conical, and a spray pattern after the second predetermined distance has a substantially flat cross section orthogonal to the nozzle axis. 13. The fuel injection valve for in-cylinder injection according to claim 12, wherein the fuel injection valve is substantially shaped like glasses. 14. The in-cylinder fuel injection valve according to claim 12, further comprising a swirl generating member for giving a swirl to the injected fuel. 15. The spread direction of the spray after the second predetermined distance in a cross-sectional shape orthogonal to the injection port axis is determined by setting a circumferential position of the swirl generating member. 15. The fuel injection valve for in-cylinder injection according to claim 14. 16. The swirl generating member is a revolving body arranged upstream of the valve seat portion and having two revolving grooves formed symmetrically with respect to a point. The spout of the spray after the second predetermined distance is provided. 16. The fuel injection valve for in-cylinder injection according to claim 15, wherein the determination of the spreading direction in the cross-sectional shape perpendicular to the axis is made by determining the circumferential position of the revolving structure with respect to the valve shaft. 17. The revolving structure is positioned in a circumferential direction with respect to a valve body and accommodated in the valve body, and the valve body is positioned in a circumferential direction with a solenoid portion to form the solenoid. 17. The fuel injection valve for in-cylinder injection according to claim 16, wherein the fuel injection valve is housed in a portion. 18. The direct injection internal combustion engine according to claim 12, wherein the injection port shaft is inclined with respect to the axial direction of the movable shaft.