JP5627743B1 - Fluid injection valve and spray generating device - Google Patents

Abstract

A fuel injection valve that achieves both atomization of fluid spray and improvement in design flexibility in spray shape, penetration force, injection amount distribution, and spray direction is obtained. In the fluid injection valve 1 of the present invention, each switching spray 32A is different in time timing and distance from the switching nozzle hole 12B in which an axis-switching phenomenon occurs. Each non-switching spray 30A from each non-switching nozzle hole 12A includes the switching spray 32A and the non-switching spray 30A adjacent to the switching spray 32A after each switching spray 32A has undergone an axis-switching phenomenon. Collective sprays 50-1 to 50-5 are formed by the Coanda effect. These collective sprays 50-1 to 50-5 are linked to form the entire spray 60. [Selection] Figure 9

Description

  The present invention relates to a fluid injection valve in which each jet is jetted from a plurality of nozzle holes to form each spray downstream to form an overall spray, and to a spray generating apparatus using the fluid injection valve. is there.

  2. Description of the Related Art In recent years, in automobile engines such as automobiles, research and development for reducing exhaust gas when the engine is cold due to atomization of fuel spray and improving fuel efficiency by improving combustibility have been actively promoted.

  For example, a fuel injection valve is known in which the arrangement is devised so that the spray from each nozzle hole does not interfere, the atomization is promoted, and the deviation of the injection amount distribution can be reduced (see Patent Document 1). .

  In addition, there is known a fuel injection valve that can prevent variation in the traveling direction of the spray because it proceeds while attracting each other due to the Coanda effect of each spray while avoiding interference between the sprays (patent) Reference 2).

  There is also known a fuel injection valve in which the spray pattern formed downstream of each spray is annular or C-shaped so that fuel spray does not collide and adhere to the center or stem of the intake valve (see Patent Document 3).

JP 2008-169766 A JP 2000-104647 A Japanese Patent Laid-Open No. 11-72067

However, in the thing of the said patent document 1, it only avoided that a spray interferes, Therefore, the spray pattern formed from a some spray and the shape of the whole spray inevitably expand if it thinks geometrically. Therefore, the degree of design freedom is small, and there are restrictions on the applicable intake port shape and intake valve arrangement.
Moreover, in order to promote atomization by promoting atomization and to reduce spray penetration force and to suppress spray adhesion in the intake port, it is necessary to expand and atomize each spray. The spray spreads.
In addition, although the injection holes are arranged on the inner side to reduce the deviation of the injection amount distribution, it can be said relatively as compared with the case where the injection holes are not arranged on the inner side. Since there is no description about a measure that causes an independent liquid column jet from the hole to be atomized while avoiding interference, resulting in an injection amount distribution with reduced bias, the applicable intake port shape, intake valve arrangement, etc. are unknown.
In other words, when the spray holes are also arranged on the inner side to bring the sprays close to each other and try to reduce the deviation of the spray amount distribution, the Coanda effect automatically acts between the sprays, and the assembly of the sprays begins. The injection amount distribution in the cross section in the downstream injection direction becomes one collective spray that has a substantially conical shape with a peak at the center, and the spray angle as a whole spray is relatively small in the market. It is clear from the characteristics of the fuel injection valve used and the known literature.
On the other hand, in order to suppress the aggregation of each spray due to the Coanda effect, it is necessary to ensure a certain distance between adjacent sprays (which varies depending on the spray conditions and atmospheric conditions). Only whole spraying can be realized.

In the thing of the said patent document 2, since it progresses while attracting each other by aiming at atomization avoiding interference of each spray and coanda effect of each spray, it is supposed that the dispersion | variation in the advancing direction of spray can be prevented.
However, it is difficult to maintain the balance of the spray direction such that the Coanda effect acts so that each spray does not spread too much, and on the other hand the Coanda effect is suppressed so that each spray does not collect, even under static atmospheric conditions, In addition, it is affected by ambient air pressure and temperature, intake air flow, spray volume (weight) flow rate, spray speed, etc. in the intake port, so it can be realized with an injection system for a gasoline engine with many unsteady states during transient operation. Is very difficult.
In other words, if the action of the Coanda effect is strengthened, the sprays gather and become compact, and the injection amount distribution in the cross section in the injection direction is usually conical with a peak at the center. If this suppression works, each spray is usually separated as it goes downstream, and as a whole, it becomes a very wide-angle spray flow.
As a result, the spray shape, spray pattern, and injection amount distribution of the entire spray are in accordance with the setting of the main axis direction of each nozzle hole or the main injection direction of each jet.

In the above-mentioned Patent Document 3, the direction of each nozzle hole (each spray) is set, and the spray pattern at the position of the intake valve is merely an annular shape or a C shape corresponding to the shape of the intake valve. It is only a scientific study.
Actually, an annular or C-shaped spray pattern is realized and maintained without considering the Coanda effect between adjacent sprays and the effect of the sag effect due to the pressure difference between the inside and outside of the entire spray. It is not possible.
In other words, the sprays gather to form one solid spray, or conversely, to avoid the spray gathering, the spray spreads to a large extent. Moreover, although it has been said that each spray does not interfere in order to realize atomization, means for simultaneously realizing the spray pattern is not clear.

As described above, the above cited documents 1, 2 and 3 do not show any measures for achieving both atomization improvement of spray and improvement of design shape of spray shape, spray pattern, spray penetration force and injection amount distribution. Therefore, in the actual situation that the shape of the intake port and the intake flow are different for each engine specification, there is a problem that it is not a guideline for determining a more optimal spray specification.
There is also an idea that the air flow in the intake port is changed by mechanical means such as an intake control valve, and the spray direction is changed only once by the air flow to suppress the adhesion of the spray to the inner wall surface of the intake port. However, since it is necessary to change the spray direction a plurality of times in the intake port having a curvature as a whole or the intake port bent in three dimensions, it has been impossible to apply this.

  The present invention aims to solve such problems, and has made both atomization of fluid spray and spray shape, penetration force, injection amount distribution, and improvement in design freedom in the spray direction compatible. It is an object of the present invention to provide a fluid injection valve and a spray generation device using the fluid injection valve.

A fluid injection valve according to the present invention includes a valve seat provided in the middle of a fluid passage through which a fluid flows, a valve body that controls opening and closing of the fluid passage by separation and contact with the valve seat, A nozzle hole body provided downstream and having a plurality of nozzle holes,
A fluid injection valve in which an overall spray is formed downstream from each spray generated by each jet flow being ejected from each of the plurality of nozzle holes,
Each of the sprays includes a plurality of switching sprays in which a cross-sectional shape in a plane perpendicular to the injection direction has different major and minor axes,
Each said injection hole includes at least two switching injection hole causing said switching spraying the direction of the long axis and the short axis in the downstream to varying turned into deformation,
At least one of each of the switching sprays is different from other switching sprays in terms of time timing, distance from the nozzle hole , in which the direction of the major axis and the minor axis changes .
After the direction of the major axis and the minor axis of each of the switching sprays is changed , these switching sprays and the respective sprays adjacent to these switching sprays are aggregated by the Coanda effect to form each collective spray, These collective sprays are linked to form the entire spray.

According to the fluid injection valve according to the present invention, each nozzle hole includes at least two switching nozzle holes that generate switching sprays in which the directions of the major axis and the minor axis are changed due to the axis-switching phenomenon in the downstream, At least one of the switching sprays is different from other switching sprays in terms of time timing, distance from the nozzle hole, in which the axis-switching phenomenon occurs, and after the axis-switching phenomenon of each switching spray, these These switching sprays and each of the sprays adjacent to these switching sprays are aggregated by the Coanda effect to form each collective spray, and these collective sprays are linked to form an overall spray.
Therefore, it is possible to achieve both atomization of the fluid spray and improvement in the degree of freedom in design of the spray shape, penetration force, spray amount distribution, and spray direction.

It is sectional drawing which shows the fuel injection valve of Embodiment 1 of this invention. It is an enlarged view which shows the front-end | tip part of the fuel injection valve of FIG. It is a top view which shows the nozzle hole plate of FIG. It is an enlarged view which shows the front-end | tip part of the valve apparatus of FIG. It is an enlarged view which shows the principal part of the valve apparatus of FIG. FIG. 6A and FIG. 6B are explanatory views showing the behavior of the non-switching sprays until the collective spray is formed by the Coanda effect. FIGS. 7A and 7B show the non-switching spray and the switching spray injected from the non-switching injection hole and the switching injection hole of the fuel injection valve shown in FIG. 1 until a collective spray is formed by the Coanda effect. It is explanatory drawing which shows a behavior. It is a figure which shows one among a pair of whole spray formed with the fuel injection valve of FIG. Fig.9 (a)-FIG.9 (d) are figures which show each collective spray in time series until it reaches the whole spray. It is a block diagram which shows an example of the usage condition of the fuel injection valve of Embodiment 2 of this invention. It is a block diagram which shows the other example of the usage condition of the fuel injection valve of Embodiment 2 of this invention. It is a top view which shows the fuel injection valve of FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the drawings, the same or equivalent members and parts will be described with the same reference numerals.
Embodiment 1 FIG.
FIG. 1 is a cross-sectional view showing the fuel injection valve 1, and FIG. 2 is an enlarged view showing a tip portion of the fuel injection valve 1 of FIG.
The fuel injection valve 1 is attached to an intake pipe of an internal combustion engine, and a tip portion thereof faces an intake port of the internal combustion engine so that fuel is injected downward.
The fuel injection valve 1 includes a solenoid device 2 that generates electromagnetic force, and a valve device 7 that operates by energizing the solenoid device 2.

The solenoid device 2 includes a housing 3 that forms a yoke portion of a magnetic circuit, a core 4 that is a fixed iron core provided inside the housing 3, a coil 5 that surrounds the core 4, and an inner side of the coil 5. And an armature 6 that is a movable iron core that reciprocally moves.
The valve device 7 has a cylindrical shape, a valve body 9 that is press-fitted and welded to the outer diameter portion of the tip of the core 4, a valve seat 10 provided inside the valve body 9, and a downstream side of the valve seat 10. An injection hole plate 11 provided on the side, a cover plate 18 provided upstream of the injection hole plate 11 inside the valve seat 10, a valve body 8 provided inside the valve body 9, and a valve body 8 And a compression spring 14 provided upstream.

The valve body 8 has a hollow rod 8a that is press-fitted and welded to the inner surface of the armature 6, and a ball 13 that is fixed to the tip of the rod 8a by welding.
The ball 13 has a chamfered portion 13 a parallel to the Z-axis of the fuel injection valve 1, a planar surface portion 13 b facing the cover plate 18, and a curved surface portion 13 c in line contact with the valve seat 10.
The nozzle hole plate 11 has a peripheral edge bent downward and is welded to the front end surface of the valve seat 10 and the inner peripheral side surface of the valve body 9. A plurality of nozzle holes 12 having a circular cross section penetrating in the plate thickness direction are formed in the nozzle hole plate 11.

FIG. 3 is a plan view of the nozzle hole plate 11 as viewed in the direction of arrow J in FIG.
In the nozzle hole plate 11, a plurality of nozzle holes 12 are circularly arranged at equal intervals along the circumferential direction.
Each injection hole 12 is divided into two injection hole groups in which the central axis of the fuel injection valve 1 is directed to the intake valve of the engine and intersects with each other on the left and right in FIG. Is formed.
Each nozzle hole 12 is composed of two types of a perfect circular non-switching nozzle hole 12A and an elliptical switching nozzle hole 12B.
The switching nozzle hole 12B has a major axis of an ellipse in a direction orthogonal to a pitch circle connecting the centers of the non-switching nozzle holes 12A. The non-switching nozzle hole 12A and the switching nozzle hole 12B are separated from the switching nozzle hole 12B. And the spray from the non-switching nozzle hole 12A are set to distances in a range where they are not gathered by the Coanda effect before the later-described axis-switching phenomenon occurs.

Next, the operation of the fuel injection valve 1 will be described.
When an operation signal is sent from a control device (not shown) of the internal combustion engine to the drive circuit of the fuel injection valve 1, a current is passed through the coil 5 of the fuel injection valve 1, and the armature 6 is attracted to the core 4 side. .
As a result, the rod 8a and the ball 13 which are integral with the armature 6 move upward against the elastic force of the compression spring 14, the curved surface portion 13c of the ball 13 is separated from the valve seat surface 10a, and there is a gap between them. Thus, a fuel flow path is formed, and fuel injection directed to the intake port is started.

  On the other hand, when an operation stop signal is sent from the control device of the internal combustion engine to the drive circuit of the fuel injection valve 1, the energization to the coil 5 is stopped, and the force that the armature 6 is attracted to the core 4 side disappears. 8a is pushed to the valve seat 10 side by the elastic force of the compression spring 14, the curved surface portion 13c and the valve seat surface 10a are closed, and the fuel injection is terminated at this point.

  Here, for example, the detailed positions and structures of the nozzle hole plate 11 and the cover plate 18, the valve seat 10, and the ball 13 in which the flow in the nozzle hole 12 </ b> A and the switching nozzle hole 12 </ b> B is a liquid film flow by contraction flow are shown in FIG. 2. 4 and FIG. 5 will be used for detailed description.

From the passage parallel to the Z axis between the chamfered portion 13a of the ball 13 and the inner surface of the valve seat 10 when the valve body 8 is opened, the fuel flows downstream between the curved surface portion 13c and the valve seat surface 10a. To the sheet portion R1.
Since the fuel flows parallel to the Z-axis upstream of the seat portion R1, the fuel mainly flows along the valve seat surface 10a due to inertia after passing through the seat portion R1, and the point at the downstream end of the valve seat surface 10a. Reach P1. The point P1 is the end of the valve seat surface 10a, and the valve seat 10 has a surface extending in the vertical direction downstream from the point P1.
Therefore, the main flow of fuel is separated from the point P1. The extension line of the valve seat surface 10a intersects the peripheral side surface of the cover plate 18 at the point P2, and the fuel peeled off from the point P1 is directed to the point P2 in the annular passage C (the inner peripheral wall surface of the valve seat 10 and the cover plate 18). Between the peripheral surface of the large-diameter portion and the radial passage B (the inner peripheral wall surface of the valve seat 10 and the peripheral side surface of the small-diameter portion of the cover plate 18 without significant change in the radial direction). In between).

As described above, the main flow of the fuel passing through the seat portion R1 flows into the annular passage C, so that the inflow into the clearance passage A (between the bottom surface of the ball 13 and the top surface of the cover plate 18) is suppressed.
A line connecting the sheet portion R1 and the point R2 at the entrance of the injection hole 12 intersects with a thin portion 18b which is a large diameter portion of the cover plate 18, and the thin portion 18b is formed from the sheet portion R1 to the injection hole. The linear flow of fuel to the 12 inlets is blocked.

For this reason, at least a part of the fuel flowing into the non-switching nozzle hole 12A and the switching nozzle hole 12B flows along the radial passage B. The end face 18d of the cover plate 18 is disposed closer to the nozzle hole 12 on the inner diameter side than the nozzle hole 12. Therefore, the fuel front flow (1) (see FIG. 5) toward the inner diameter side along the radial passage B is the flow path of the return flow (see FIG. 5) flowing into the injection hole 12 from the Z axis of the fuel injection valve 1. And the speed of the return flow is reduced.
By suppressing the return flow b, the speed of the front flow a flowing into the nozzle hole 12 from the seat portion R1 side is relatively increased.
Because at least a part of the front flow a travels along the radial passage B, a large direction change is forced in the non-switching nozzle hole 12A and the switching nozzle hole 12B, and the front flow a is high speed. In the cross section of the injection hole 12, the fuel is strongly pressed against the wall surfaces of the non-switching injection hole 12A and the switching injection hole 12B on the Z-axis side of the fuel injection valve 1.
In FIG. 4, L represents the length of the non-switching nozzle hole 12A and the switching nozzle hole 12B, and D represents the diameter of the non-switching nozzle hole 12A and the switching nozzle hole 12B.

Thereafter, at the inlets of the non-switching nozzle hole 12A and the switching nozzle hole 12B, the low-speed return flow B forms a flow α along the wall surface of the nozzle hole 12, and the high-speed front flow A presses the fuel against the wall surface. A fuel stream β is formed.
Air is introduced from the outlets of the non-switching nozzle hole 12A and the switching nozzle hole 12B to the vicinity of the inlet of the non-switching nozzle hole 12A and the switching nozzle hole 12B, acts on the fuel flow β, and the point Q (the fuel inlet of the nozzle hole 12). Separation of the fuel flow β starting from the outer edge).
As the fuel flow β travels in the non-switching nozzle hole 12A and the switching nozzle hole 12B, it is pressed against the wall surface, and the direction of the liquid film is in the circumferential direction of the wall surface of the non-switching nozzle hole 12A and the switching nozzle hole 12B. While expanding, it changes in the direction along the wall surface of the non-switching nozzle hole 12A and the switching nozzle hole 12B.
When the length L of the non-switching nozzle hole 12A and the switching nozzle hole 12B is appropriate with respect to the height h of the clearance passage A, the thin liquid film flow 1a is reached in the non-switching nozzle hole 12A and the switching nozzle hole 12B. Pressed.
The liquid film flow 1a of the injected fuel starts to split after a predetermined distance, and droplets atomized by passing through the liquid yarn state are generated.

In the atomization process, in order to reduce the size of the droplet, it is effective to make the liquid yarn, which is the previous stage of the breakup, thin. For this purpose, it is effective to make the liquid film, which is the previous stage of the splitting of the liquid yarn, thinner or thinner, and the conventional knowledge is that the liquid film is more advantageous than the liquid column. I know.
In addition to this, various liquid film flow forming methods have been proposed, such as forming a liquid film flow in the nozzle hole by giving a swirling flow to the fuel flow before flowing into the nozzle hole.

By the way, the inventor of the present application has investigated and investigated the relationship between these liquid film flow forming methods and atomization processes, and the spray shape, penetration force, and injection amount distribution of the collective spray in which a plurality of sprays are gathered based on them. In the collective spray in which the single sprays are gathered, it was found that the spray can be divided into the following two forms.
That is, each single spray is identifiable and the characteristics of each single spray are almost indistinguishable (that is, a collective spray with a solid structure that is relatively homogeneous), or each single spray is identified. It has been found that it can be divided into whether or not it is a collective spray (a collective spray in which the injection amount distribution has a conical shape with a central peak).
The latter is a very characteristic and stable phenomenon in which a plurality of single sprays are aggregated and replaced with a single new collective spray that is almost different from the original form. The former can be said to be a spray that shows characteristics common to the collective spray, that is, each spray can be identified, that is, a spray that is halfway and difficult to control.
Which of these forms will depend largely on whether the spray behavior is at a certain threshold, the injection amount distribution becomes closer to axisymmetric as the aggregation of single sprays progresses, and the sharp cone shape It becomes. That is, the penetration force as a whole spray increases.
Therefore, even in the former case, the spray shape in the plane perpendicular to the spray direction and the injection amount distribution are approximately axisymmetric, and it is difficult to make the cross-sectional shape so-called irregular.
For this reason, the setting of spray targeting (injection position, injection direction, spray specification) that suppresses adhesion to the vicinity of the intake port or intake valve, in which most passage sections are so-called irregular shapes, has been insufficient.

Various atomization techniques as described above are being applied to fuel injection valves. Originally, there is a trend in the technology of making multiple injection holes with small diameters for atomization, and jets from adjacent injection holes Consideration is made so that the atomized state does not deteriorate due to interference.
In other words, the nozzle hole arrangement and nozzle specifications (diameter, inclination, length, etc.) or the nozzle arrangement and jet direction are made so that the nozzle hole center axis or jet direction becomes farther downstream. It has been difficult to satisfy both the requirements of compact spraying.
In addition, there is a plan to rapidly attenuate the penetration force of the spray at a predetermined distance for the purpose of reducing the spray collision near the intake valve and promoting the mixing with the air, but this is realized without greatly changing the spray form. There was no means.

In the port injection system, the fuel adhesion to the intake port has no positive influence or effect, and it is the biggest challenge to suppress this.
Therefore, even if the atomization is improved in order to reduce the rate at which the spray adheres to the intake valve or the intake port near the intake valve, the entire spray spreads, resulting in the spray side surface adhering to another intake port part. I couldn't find any merit as a port injection system.
That is, even if the direction of each liquid film flow is set to a wide angle to promote atomization, or even if the spray form is greatly changed by causing a large hoisting around the atomization spray outer periphery, the penetration force is suppressed, As a result, wide-angle spraying occurs, causing interference with the intake valve and intake port, and fuel adheres.

  On the other hand, in the case where the spread of the entire spray is suppressed, the nozzle hole center axis or jet direction is such that the nozzle hole arrangement and the nozzle hole specifications intersect with each other immediately below the nozzle hole, or the jet arrangement and jet direction. Although it is known, the relationship with the break length of the liquid film flow (the length from the nozzle hole outlet to the position where it can be regarded as a spray flow substantially through breakage and splitting of the liquid film flow) No one has taken into account the requirements for atomization.

In addition, when trying to suppress the spread of the entire spray, the angle of the central axis of the nozzle hole with respect to the vertical line (Z axis in FIG. 1) becomes relatively small, which is disadvantageous for forming a thin liquid film flow. The atomization process slowed down and the jets were likely to interfere with each other, and the atomization level could not be achieved as expected.
Further, in this case, the assembly of a plurality of sprays progresses, so-called “Academic Literature 5” (The Japan Society of Mechanical Engineers, Vol. 25, No. 156, pp 820-826 “Research on the reach of diesel engine fuel spray” (Waguri And so on), the penetration force of the collective spray was larger than the penetration force in the case of a single spray.

  Here, the inventor of the present application pays attention to the difference between the behavior of a single spray with a single nozzle hole and the behavior of a plurality of single sprays from a plurality of nozzle holes. We have found a technique to control the shape, penetration force, spray distribution, and spray direction of the entire spray by skillfully combining the switching phenomena.

Here, the knowledge about the axis-switching phenomenon is shown in the following academic literature.
[Academic Literature 1] Proceedings of the Japan Society of Mechanical Engineers (B) Vol. 55, No. 514, pp1542-1545, "Study on vortex structure in non-circular jet" (Toyota et al.)
[Academic Reference 2] ILASS-Europe 2010, “An experimental investigation of discharge coefficient and cavitation length in the elliptical nozzles” (Sung Ryoul Kim)
[Academic Reference 3] Production Research Volume 50 No.1 pp 69-72, “Numerical Simulation of Complex Turbulent Jets: Origin of Axis-Switching” (Ayodeji O. DEMUREN)
[Academic Literature 4] Jet Engineering Morikita Publishing pp41-42

In the field of jet research, this axis-switching phenomenon is not limited to the example of this embodiment in which the cross-sectional shape of the spray is an ellipse, and at least the major axis is almost line-symmetric with respect to the minor axis of the ellipse. As long as it has a shape, it is not limited to liquid but can be gas.
In the case of spray having an elliptical cross section with a long / short axis ratio, the nozzle hole specifications may be set so that the long / short axis direction changes and deforms within a range in which the long axis direction is not divided.
Therefore, in this embodiment, the angle for changing the major and minor axis directions of the spray is set to approximately 90 degrees.

The fuel injection valve 1 shown in FIG. 1 is realized by the inventor of the present invention by discovering and realizing a method for controlling the shape, penetration force, injection amount distribution, and spray direction of the entire spray, and FIG. FIG. 7 is an explanatory diagram showing a basic pattern of behavior of the non-switching spray 30A and the switching spray 32A of the fuel injection valve 1. FIG.
In this fuel injection valve 1, the collective spray 50 is formed by the Coanda effect of the non-switching spray 30A and the switching spray 32A.
In the non-switching spray 30A, the jet 30 injected from the non-switching nozzle hole 12A is generated downstream, and in the switching spray 32A, the oval jet 32 injected from the switching nozzle 12B is long downstream. The direction of the axis and the minor axis changes due to the axis-switching phenomenon.

FIG. 6A shows the behavior of the jets 30 and 31 and the non-switching sprays 30A and 31A when the non-switching nozzle holes 12A are adjacent to each other.
The cross-sectional shape of the jet flow when a break in a state in which the jet flow 30 from the non-switching nozzle hole 12A can be substantially regarded as a spray flow after breaking or splitting of the liquid film flow is the shape shown in the cross-section EE It is.
A distance a between the non-switching nozzle hole 12A and the cross section EE at this time is defined as a break length. At the position of the distance a, the gap c1 between the jets 30, 31 is already smaller than the threshold value at which the Coanda effect occurs.
Subsequently, the jets 30 and 31 are separated into single non-switching sprays 30A and 31A, and the outer diameters of the two non-switching sprays 30A and 31A start to come into contact with each other at a position b from the non-switching nozzle hole 12A ( Cross section FF).
At the same time, from the cross-section FF, the single non-switching spray 30A, 31A approaches and looks like the cross-section GG due to the Coanda effect acting between the two single non-switching sprays 30A, 31A due to the pressure distribution. Aggregation proceeds. At the same time, the ambient air is entrained in the non-switching sprays 30A and 31A, thereby inducing the air flow along the flow direction downstream of the substantially central portion in the non-switching sprays 30A and 31A.
That is, even if the jet 30 and the jet 31, or the non-switching spray 30 </ b> A and the non-switching spray 31 </ b> A each have a feature that causes an axis-switching phenomenon, before the axis-switching phenomenon occurs, the cross-section EE In this position, the Coanda effect acts between the jet 30 and the jet 31 or between the non-switching spray 30A and the non-switching spray 31A so as to start approaching.

The ambient air entrainment level is not a level that greatly changes the overall shape of the collective spray 40 in which the single non-switching sprays 30A and 31A are assembled. 62) No. 599, pp. 2867-2873, “Effect of Atmospheric Viscosity on Diesel Spray Structure” (Ta et al.)). Only the 12 (a) level or the fine spray particles are at the (b) level.
If the conditions are adjusted, the assembly of two single non-switching sprays 30A and 31A proceeds from the state of the collective spray 40 in the section GG in FIG. 6A, and is substantially as shown in the section HH. Can be regarded as almost one solid collective spray 40.

In FIG. 6 (b), the surrounding air is entrained by many spiral arrows for easy understanding.
Accordingly, here, the size and number of the spiral arrows do not represent the actual state.
Further, the air flow V is induced along the flow direction downstream of the predetermined portion in the spray.
As a result, the injection amount distribution in F1-F1, G1a-G1a, G1b-G1b, and H1-H1 gradually approaches a substantially central peak as shown on the right side of FIG. 6 (b).
On the other hand, FIG. 7 shows the behavior of each jet and each spray when the non-switching nozzle hole 12A and the switching nozzle hole 12B are adjacent to each other in FIG. 3 (when viewed from the direction of arrow C in FIG. 3).

In this embodiment, assuming that the positions at which breaks occur in the jets 30 and 31 from the non-switching nozzle hole 12A and the jet 32 from the switching nozzle hole 12B are substantially the same and the break length is the distance a, these cross-sectional shapes are The shape shown in the cross-section EE of FIG.
The jet 32 is separated to become a switching spray 32A. As can be seen from FIG. 7B, the switching spray 32A having an oval cross-sectional shape has its major axis direction substantially opposite to the non-switching spray 30A. Are arranged.
While this switching spray 32A faces the non-switching spray 30A and its cross-sectional shape is slightly enlarged (both in the major and minor axes), the initial flow direction almost immediately below the switching nozzle hole 12B is maintained. Maintain and flow downstream.
And the deformation | transformation from which the major-short axis direction of switching spray 32A changes begins to arise in the position of predetermined length from the switching nozzle hole 12B (cross section JJ). At this position, the gap c2 between the switching spray 32A and the non-switching spray 30A is larger than the threshold value at which the Coanda effect occurs, and the Coanda effect does not occur.

As the cross section JJ moves downstream from the cross section KK, the deformation in which the long and short axis directions of the switching spray 32A change progresses, and the switching spray 32A and the non-switching spray 30A approach each other.
This is because the gap between the switching spray 32A and the non-switching spray 30A is reduced by switching the long and short axis directions of the switching spray 32A, and accordingly, the Coanda effect is generated between the switching spray 32A and the non-switching spray 30A. It depends.
The gap c3 between the sprays 32A and 30A at this time is smaller than the threshold value for causing the Coanda effect.
In addition, the threshold value of the gap between the switching spray 32A and the non-switching spray 30A that causes the Coanda effect varies depending on the flow rate, atomization level, particle number density, atmospheric pressure, and the like of each spray.
In the cross-section L-L, the facing ends of the switching spray 32A and the non-switching spray 30A are deformed (moved) and begin to interfere with each other.
As a result, as shown in the cross-section MM, a set of the switching spray 32A and the non-switching spray 30A gathered at a predetermined distance from the non-switching injection hole 12A and the switching injection hole 12B at a predetermined time after fuel injection. A spray 50 is formed.
By changing the characteristics of the switching spray 32A and the non-switching spray 30A, the collective spray 50 can change its shape, penetration force, injection amount distribution, and the like, and the degree of freedom thereof is improved.

Further, the switching spray 32A is deformed by changing the long and short axis directions, so that the momentum exchange with the surrounding air greatly proceeds and the penetration force becomes small, so that the non-switching spray 30A interferes with the non-switching spray 30A. The particles and the movement of the air flow dragged by the particles are suppressed, and the penetration force of the non-switching spray 30A is also suppressed.
Therefore, when the non-switching spray 30A is used alone, the tip of the non-switching spray 30A extends due to the interference with the switching spray 32A, as shown by the phantom line D in FIG. Shortened. That is, the penetration force of the non-switching spray 30A can also be suppressed.

Further, the switching spray 32A has a small penetrating force and greatly mixed with the surrounding air, so that the atomization is improved and the difference from the atomization level of the non-switching spray 30A is reduced.
That is, it is possible to form an aggregate spray 50 that is atomized and has a non-circular shape (asymmetric shape) in cross section at a predetermined position somewhat downstream from the non-switching nozzle holes 12A and 12B.

  In FIG. 7, when the switching nozzle hole 12B is not used, the adjacency of the adjacent sprays does not start unless it is further downstream, and in some cases, the assembly does not occur. Accordingly, each spray continues to spread and the penetration force does not decrease. As a result, the momentum held by the spray does not readily move to the air flow, and atomization becomes insufficient.

In FIG. 7, when the switching nozzle 12B is used in place of the non-switching nozzle 12A and both of the adjacent sprays are the switching spray 32A, the major axis direction is set to be substantially parallel, for example. By utilizing the fact that the long axes are connected in the longitudinal direction by the axis-switching phenomenon, the same behavior as in FIGS. 7A and 7B can be created.
In FIGS. 7A and 7B, the collective spray 50 is formed by a combination of one non-switching spray 30A and one switching spray 32A. However, the present invention is not limited to this combination. For example, a collective spray may be formed by a combination of two non-switching sprays 30A and one switching spray 32A, or a collective spray may be formed between two adjacent non-switching sprays 30A.

Here, the switching spray 32 </ b> A reliably suppresses the Coanda effect from acting with the non-switching spray 30 </ b> A by adopting the following method before the major and minor axis directions change and deform. Can do.
That is, at a position at the same distance in the main flow direction from the non-switching nozzle hole 12A and the switching nozzle hole 12B, a method of making the average particle diameter of the switching spray 32A larger than the average particle diameter of the non-switching spray 30A, or the switching spray 32A A method of making the break length longer than the break length of the non-switching spray 30A, and a method of setting the penetration force of the switching spray 32A larger than the penetration force of the non-switching spray 30A may be adopted.
This means that a difference is provided in the characteristics of the switching spray 32A and the non-switching spray 30A to delay the timing at which the Coanda effect occurs.

In realizing these methods, for example, it may be used to change the level and direction of the contracted flow depending on the shape of the nozzle holes of the non-switching nozzle hole 12A and the switching nozzle hole 12B.
That is, for example, when the level and direction of the contracted flow are changed, the pressure loss (jet velocity) in the nozzle hole 12, the sectional area of the jets 30 and 32, the sectional shape of the jets 30 and 32, the arrangement / direction of the jets, etc. This is because it is possible to change the threshold value of the gap between the sprays 32A and 30A in which the Coanda effect occurs.

  FIG. 8 shows one whole spray 60 out of two hollow annular whole sprays 60 formed by injection from the non-switching nozzle holes 12A and the switching nozzle holes 12B of the nozzle hole plate 11 shown in FIG. FIG.

The entire spray 60 is formed by chaining together the collective sprays 50-1 to 50-5 formed by a combination of the switching spray 32A and the non-switching spray 30A.
In forming the collective sprays 50-1, 50-2, 50-3, 50-4, and 50-5, the spray amount, the cross-sectional area, the spray direction, and the fine particles of the switching spray 32A and the non-switching spray 30A, respectively. By adjusting each of the control levels, it is possible to shift the timing at which each switching spray 32A gathers due to an Axis-switching phenomenon and the Coanda effect with the non-switching spray 30A.
Further, the switching spray 32A is deformed by changing the long and short axis directions, so that the exchange of momentum with the surrounding air greatly proceeds, the penetration force decreases, and the non-switching spray 30A also interferes with the non-switching spray 30A. The movement of the air flow dragged by each particle and each particle is suppressed, and the penetration force is suppressed.
Thereby, distribution arises in the penetration force of each collective spray 50-1,50-2,50-3,50-4,50-5. As a result, each of the collective sprays 50-1, 50-2, 50-3, 50-4, 50-5 is deflected gradually or stepwise as it proceeds downstream.

In short, the flow direction and shape change of these collective sprays 50-1, 50-2, 50-3, 50-4, 50-5 are determined by the respective momentum distributions.
That is, if there is a difference in the momentum distribution in the cross section perpendicular to the flow of the collective sprays 50-1, 50-2, 50-3, 50-4, 50-5, a difference occurs in the penetration force in the cross section. As a result, the portion where the decrease in penetration force is small, pulls the collective sprays 50-1, 50-2, 50-3, 50-4, 50-5 and changes its direction. Follows in a form where the penetrating force is lowered by a small part.

FIG. 9 is a view when the entire spray 60 is viewed from the arrow of FIG. 8, that is, when viewed in a direction perpendicular to the Z axis of the fuel injection valve 1.
FIGS. 9A to 9D show a time series of the collective sprays 50-1 to 50-5 up to the entire spray 60.
At a predetermined position from the switching nozzle hole 12B, an axis-switching phenomenon first occurs in the leftmost switching spray 32A, and then the Coanda effect acts between the closest non-switching spray 30A and both sprays 32A. , 30A further approach and interfere to form the collective spray 50-2. Since the axis-switching spray 32A and the non-switching spray 30A are arranged in the thickness direction of the paper, only one of the sprays 32A, 30A can be seen (see FIG. 9A).
Next, after a time timing delay, an axis-switching phenomenon occurs in another switching spray 32A, and the Coanda effect acts between the closest non-switching spray 30A, and both sprays 32A, 32A, 30A further approaches and interferes and gathers to form a collective spray 50-3.
During this time, the collective spray 50-2, in which a significant proportion of the momentum has moved to the air and the penetrating force has been greatly reduced, is dragged to the collective spray 50-3 that has maintained the momentum and the penetrating force has not decreased so much. Eventually, the collective spray 50-2 and the collective spray 50-3 are connected. The collective spray 50-1 that does not overlap with the collective spray 50-3 in the thickness direction of the paper is also formed in the same manner as the collective spray 50-3 (see FIG. 9B).
Subsequently, the collective sprays 50-4 and 50-5 are also formed by the behaviors of the switching sprays 32A and the non-switching sprays 30A similar to the collective sprays 50-1 to 50-3 (FIG. 9C, FIG. 9). (See (d)).

That is, the collective sprays 50-1, 50-2, 50-3, 50-4, 50-5 are generated by the non-switching spray 30A and the switching spray 32A injected from the non-switching nozzle holes 12A and the switching nozzle holes 12B. Is formed by changing the time lag, the distance from each non-switching nozzle hole 12A and the switching nozzle hole 12B, and the direction.
For the other whole spray not shown, a whole spray similar to the whole spray 60 of FIG. 8 is formed by the behavior of the non-switching spray 30A and the switching spray 32A.

Therefore, various specifications of the generally hollow overall spray 60 can be realized by setting the individual specifications of the switching spray 32A and the non-switching spray 30A and the combination and arrangement of these sprays 32A and 30A.
In other words, by skillfully utilizing the characteristic phenomena in jet engineering, it cannot be realized by a combination of the conventional circular nozzle hole-based nozzle hole diameter, nozzle hole taper degree, nozzle hole length / hole diameter ratio, etc. Spraying is possible.

In the case of port injection, the number density of spray particles downstream from the break length a is extremely low compared to gasoline in-cylinder spray or diesel spray (about 1/10 of gasoline in-cylinder spray, diesel It is considered that there is almost no collision coalescence between particles because they are basically moving in the same direction and at the same speed.
Further, at the fuel pressure level of 0.3 MPa in the case of port injection, it may be considered that no splitting from particles alone has occurred.

As described above, according to the fuel injection valve 1 of the first embodiment of the present invention, each switching spray 32A is different in the time timing at which the axis-switching phenomenon occurs and the distance from the switching nozzle 12B. After the occurrence of the 32A axis-switching phenomenon, the switching sprays 32A are aggregated by the Coanda effect with the non-switching sprays 30A adjacent to the switching sprays 32A to form the collective sprays 50-1 to 50-5. The collective sprays 50-1 to 50-5 are linked to form the entire spray 60.
Therefore, it is possible to realize the spray shape, penetration force, injection amount distribution, and spray direction, which cannot be obtained with the whole spray formed by ordinary multi-hole spray, and greatly improve the design freedom of spray specifications. be able to.
Thereby, it can suppress significantly that the whole spray 60 collides with an intake valve or an intake port wall surface downstream compared with the conventional one.
In addition, by providing a distribution of momentum in each of the collective sprays 50-1 to 50-5, the collective sprays 50-1, 50-2, 50-3, 50-4, and 50-5 are easy as they progress downstream. Are gradually or stepwise deflected.

Furthermore, the shape, penetration force, injection amount distribution, and direction of the entire spray 60 suitable for promoting the formation of a homogeneous mixture by matching the air flow in the intake port with the intake valve closed are easily set. Can do.
In addition, for example, in the intake stroke injection, it becomes easier to follow the intake flow flowing into the cylinder from the intake valve, and the entire spray 60 may flow into the cylinder without interfering with the intake valve and the intake port wall surface in the vicinity thereof. This makes it possible to improve the charging efficiency by the intake air cooling effect in the cylinder.
In this case as well, if interference with the intake valve wall surface in the vicinity of the intake valve cannot be avoided by only the shape of the overall spray 60, the direction of the overall spray 60 is set to change midway to follow the intake flow. It becomes possible to make it.
Therefore, controlling the penetration force without widening the non-switching spray 30A increases the degree of freedom of the entire injection system and improves the engine performance.

In the first embodiment, the so-called two-spray spray mode divided into the nozzle holes extending in two directions has been described. However, the fuel injection valve 1 according to the present embodiment is often an engine for a four-wheeled vehicle. It can correspond to the two intake valves used.
Also, in the case of so-called one-spray spraying mode and corresponding to two intake valves, each fuel injection valve is inclinedly attached to each intake port, and each injection hole of the fuel injection valve is connected to the intake valve. If the distances are not the same, a fuel injection valve having an optimum spray form may be attached to each intake port. The same applies to the three intake valves.

Further, in the first embodiment, the combination in which the switching spray 32A and the non-switching spray 30A are paired one by one is described as the five collective sprays 50-1 to 50-5, but the same effect can be exhibited. As long as the combination of both the sprays 32A and 30A, the number of sprays therein, and the total number of collective sprays forming the entire spray are not limited to those of the first embodiment.
For example, for example, the combination spray 50 may be formed by forming a combination of three non-switching sprays 30 </ b> A and one switching spray 32 </ b> A on both sides thereof.
Then, by setting the characteristics of the collective spray 50 that can be realized by each of these combinations as desired, the momentum distribution of each collective spray 50, that is, the penetration force distribution, can be formed. Can be deflected three-dimensionally.

Further, in the first embodiment, the entire spray 60 has been described as having a hollow shape. However, the present invention is not limited to this shape, and a solid shape, a C shape, or a U shape can be freely formed. Can do.
In general, since a hollow spray has a pressure difference between the inside and the outside of the umbrella shape, a change in shape such as the spraying withering occurs depending on the atmospheric pressure. In this embodiment, the switching spray 32A or the non-switching spray is used. Regardless of which of 30A, adjacent sprays are arranged so that the Coanda effect does not act until the axis-switching phenomenon occurs. Are communicating, and there is no pressure difference between the inside and outside of the umbrella shape.
Therefore, it is possible to realize the same behavior as the C-shaped or U-shaped whole spray 60.

Further, since the switching spray 32A has an oval shape in which the major axis is axisymmetric with respect to the minor axis, the switching spray 32A and the non-switching adjacent to the switching spray 32A are generated after the occurrence of the axis-switching phenomenon. The distance between the spray 30A is rapidly approached, and the Coanda effect can be generated quickly.
Moreover, since the switching spray 32A faces the non-switching spray 30A, the Coanda effect can be generated more quickly.
In addition, the switching spray 32A may have a flat shape, for example.

Embodiment 2. FIG.
Hereinafter, an example in which the fuel injection valve 1 is attached to the intake port 20 will be described.
FIG. 10 is a configuration diagram showing an example in which the fuel injection valve 1 having the above configuration is attached to the throttle body 21 of the intake port 20. In addition, although a pair of whole spray 60 is formed from the fuel injection valve 1, about one of the whole sprays is abbreviate | omitted in FIG.
In this example, the fuel injection valve 1 is provided downstream of the throttle valve 22. The tip of the fuel injection valve 1 is directed to inject fuel toward the upstream side of the intake flow.
The non-switching sprays 30A and the switching sprays 32A generated by the fuel injection from the fuel injection valve 1 are entirely passed through the collective sprays 50-1, 50-2, 50-3, 50-4, and 50-5. The spray 60 is formed, and the penetration force of the entire spray 60 is suddenly suppressed immediately before the throttle valve 22 and the wall surface of the throttle body 21.
Therefore, once the fuel is injected toward the throttle valve 22 in the upstream direction, a space in which the air-fuel mixture is generated by the fuel and air between the intake valve 23 and the entire spray 60 can be increased.

As a result, when fuel is injected in the downstream direction of the intake flow when the intake port 20 is extremely short or the like, the injection amount distribution between the cylinders becomes unbalanced, or the ratio of spray adhesion to the inner wall surface of the intake port 20 increases. As a result, the inconvenience that the air-fuel mixture formation state deteriorates and the engine performance does not improve can be solved.
In particular, since the fuel injection valve 1 must be attached with an angle with respect to the intake port central axis, the distance from the injection hole 12 to the throttle valve 22 is uneven.
Therefore, in the case of a fuel injection valve in which fuel is ejected from the nozzle hole symmetrically about the axis, it is difficult to achieve both the setting of the injection direction suitable for the mixture formation and the prevention of sprayed fuel adhesion to the throttle valve.
On the other hand, the above-described compatibility can be achieved by using the fuel injection valve 1 of the first embodiment.

FIG. 11 is a configuration diagram showing an example in which the fuel injection valve 1 is attached to the intake pipe collecting portion 25 of the intake port 20, and FIG. 12 is a plan view of FIG.
In this example, the fuel injection valve 1 is attached to the intake pipe collecting portion 25. The intake pipe collecting portion 25 is connected to the branch portion 26 at the downstream side. Each branch portion 26 is connected to a cylinder (not shown). An intake valve 23 is attached to each branch portion 26. The tip of the fuel injection valve 1 is directed so as to inject fuel toward each intake valve 23.

The non-switching sprays 30A and the switching sprays 32A generated by the fuel injection from the fuel injection valve 1 finally become the entire spray 60, and as described above, the penetration force of the entire spray 60 is set to the intake valve 23. And immediately before the inner wall surface of the branch part 26, it is suppressed suddenly.
Further, since the spray collects due to the Coanda effect between the non-switching spray 30 </ b> A and the switching spray 32 </ b> A, it is possible to suppress the direct adhesion of the spray to the inner wall surface of the intake port 20 as indicated by the dotted line in FIG. 12. it can.
Further, as can be seen from FIGS. 11 and 12, the shape of the entire spray 60 is such that the shape does not directly interfere with the inner wall surface of the branch portion 26 and the intake valve 23.

  As described above, in this example, only one fuel injection valve 1 is arranged in the intake pipe collecting portion 25, and the intake valve is suppressed from adhering to the intake port 20 to the vicinity of the intake valve 23 of each cylinder. It is possible to perform wide-angle spraying while suppressing the penetration force of the entire spray 60 near 23.

Such a system (so-called single point injection) that uses only one fuel injection valve 1 in a multi-cylinder engine improves the cost performance of the engine and is very useful.
In other words, in general-purpose engines and small-sized engines, the current carburetor is changing to a fuel injection system. However, since it is difficult to increase the cost significantly, it is difficult to use the single point injection shown in FIGS. Very useful.

  As described above, the fuel spray can be prevented from directly adhering to the intake port 20 in the intake port 20 in the vicinity of the intake valve 23 in which the cross section of the normal fluid passage has a so-called three-dimensionally deformed shape.

  11 and 12 show an example in which one cylinder has one intake valve 23 and one fuel injection valve 1 covers two cylinders. However, two intake valves 23 are provided for one cylinder. Thus, the present invention can be applied to an example in which one fuel injection valve 1 covers one cylinder.

In the case of a gasoline engine having two intake valves 23, the use of the fuel injection valve 1 of this embodiment that constitutes two general sprays 60 corresponding to the respective intake valves 23 allows freedom of each spray form of two sprays. The degree is greatly improved.
The specifications of the entire spray 60 according to the purpose, such as the suppression of the adhesion of the spray to the inner wall surface of the intake port 20, the formation of a homogeneous air-fuel mixture by matching the spray and the air flow, and the direct entry into the cylinder by following the intake air flow of the spray. You can decide.

  As for the spray pattern, it is possible to provide fuel injection valves having different specifications for the shape of the overall spray 60 in not only two sprays but also multi-sprays such as one spray and three sprays.

In addition, although the fuel injection valve 1 of each embodiment demonstrated the electromagnetic fuel injection valve, the drive source may be another system, may be other systems, such as a piezo system and a mechanical system, and it is an intermittent injection valve. It is obvious that the present invention can be applied to a continuous injection valve instead.
In addition to the fuel injection valve 1, it can be used for general industrial purposes such as painting / coating, spraying of agricultural chemicals, cleaning, humidification, sprinklers, sprays for sterilization, cooling, etc., agriculture, equipment, home use, personal use, etc. -There are a wide variety of required functions.
Therefore, regardless of the drive source, the nozzle form, and the spray fluid, it is possible to incorporate the fluid injection valve of the present invention in these spray generation apparatuses to realize an unprecedented spray form.

  1 fuel injection valve (fluid injection valve), 1a liquid film flow, 2 solenoid device, 3 housing, 4 core, 5 coil, 6 amateur, 7 valve device, 8 valve body, 8a rod, 9 valve body, 10 valve seat, 10a valve seat surface, 11 injection hole plate (nozzle body), 12A non-switching injection hole, 12B switching injection hole, 13 ball, 13a chamfering part, 13b flat part, 13c curved part, 14 compression spring, 18 cover plate, 18d End face, 18b Thin part, 20 Intake port, 21 Throttle body, 22 Throttle valve, 23 Intake valve, 24 Intake port, 25 Intake pipe collection part, 26 Branch part, 30, 31, 32 Jet, 30A, 31A Non-switching Spray, 32A switching spray, 40,50 collective spray, 60 whole spray, R1 seat, V air flow, β fuel , A clearance passage, B radial passages, C annular passage C, Lee front flow, b return flow.

Claims (6)

A valve seat provided in the middle of a fluid passage through which a fluid flows, a valve body that controls opening and closing of the fluid passage by separation and contact with the valve seat, and a plurality of nozzle holes provided downstream of the valve seat An injection hole body having
A fluid injection valve in which an overall spray is formed downstream from each spray generated by each jet flow being ejected from each of the plurality of nozzle holes,
Each of the sprays includes a plurality of switching sprays in which a cross-sectional shape in a plane perpendicular to the injection direction has different major and minor axes,
Each said injection hole includes at least two switching injection hole causing said switching spraying the direction of the long axis and the short axis in the downstream to varying turned into deformation,
At least one of each of the switching sprays is different from other switching sprays in terms of time timing, distance from the nozzle hole , in which the direction of the major axis and the minor axis changes .
After the direction of the major axis and the minor axis of each of the switching sprays is changed , these switching sprays and the respective sprays adjacent to these switching sprays are aggregated by the Coanda effect to form each collective spray, A fluid injection valve in which these collective sprays are linked to form the entire spray.   2. The fluid injection valve according to claim 1, wherein the switching spray has a line symmetry of at least the major axis with respect to the minor axis.   The fluid injection valve according to claim 1, wherein the switching spray is opposed to a non-switching spray excluding the switching spray in the spray.   The fuel injection valve is attached to the intake port at the downstream side of the intake flow of the throttle valve and the tip is directed to the throttle valve, and the penetration force of the entire spray is suppressed before the throttle valve The fluid injection valve according to claim 1, wherein adhesion of the spray to the throttle valve is suppressed.   The fuel injection valve is attached to the intake port with a tip portion directed toward the intake valve, and the whole spray is oriented by forming a penetration force distribution in a plane perpendicular to the traveling direction. The fluid injection valve according to any one of claims 1 to 4, wherein the direction is deflected and adhesion of the spray to the inner wall surface of the intake port and the intake valve is suppressed.   The spray production | generation apparatus containing the fluid injection valve of any one of Claims 1-5.

Images