JP4783439B2 - Fuel injection valve - Google Patents

Description

  The present invention relates to a fuel injection valve that injects fuel into an internal combustion engine, and relates to a technique for forming a fuel spray excellent in atomization.

In general, a fuel injection valve used in an automobile engine or the like has a cylindrical nozzle portion provided with a fuel passage in the axial direction and an inner peripheral side surrounding a nozzle hole provided on the inner peripheral side of the tip portion of the nozzle portion. A valve seat member provided with a valve seat; a valve body in which a proximal end side inserted into the fuel passage of the nozzle portion is an adsorption portion and a distal end side is a valve portion; and a proximal end side of the nozzle portion And an electromagnetic actuator that attracts the adsorbing portion of the valve body and opens the valve body when energized.
In fuel injection valves, atomization of fuel is one of the important factors from the viewpoints of reducing fuel consumption, reducing emissions of unburned gas components (HC, CO) of combustion, stable engine performance, etc. .

  As an example of such a fuel injection valve of an internal combustion engine, a plate member that covers the valve seat member is provided at the tip of the nozzle portion, and at the center side, a plurality of fuels that atomize and inject outflowing fuel are provided. Some have injection holes (see Patent Document 1). In this case, it is effective to improve the atomization by reducing the nozzle hole (reducing the ratio between the hole length and the hole diameter) and speeding up the flow, but it is necessary to increase the number of nozzle holes to ensure the desired flow rate. There is. However, increasing the number of pores within a limited size will cause adjacent sprays to approach each other, causing the sprays to overlap and cause particle recombination. When the recombination of particles occurs, the particle size increases, which limits the atomization.

  On the other hand, in order to promote atomization of the spray, what controls the particle size is reduced by providing a plurality of hole sets that collide each other with the jet flow from two or more jet holes in front. Yes (see Patent Document 2). In this case, the straightness of the impinging jet flow is important, and the particle size is reduced by increasing the speed and relative angle of the jet flow.

JP 2002-534638 A JP 2002-28024 A

  As in the above prior art, in order to reduce the particle size, the collision speed and relative angle of the injected fuel flow are increased to increase the energy of the collision, but the obtained spray tends to scatter, There is a problem that this must be suppressed. The fuel injection valve is also required to be excellent in atomization performance under various flow conditions, and to have a characteristic that the spray direction is fixed without scattering of spray.

  On the other hand, the following has been found from our experimental analysis. The injection direction of the fuel spray is preferably directed on the intake valve of the internal combustion engine, and a good combustion result is obtained when the fuel spray is appropriately dispersed on the plate portion. A more preferable method is to increase the fuel spray concentration inward of the center position of the intake valve (large particles in the fuel spray may be directed), which ensures ignition of the engine and stabilizes combustion. Let As a result, it is possible to reduce the amount of fuel consumption and the amount of combustion unburned gas components (HC, CO) emitted effectively.

  The present invention solves the problem based on such a background, and its purpose is to form a spray with excellent atomization performance while ensuring a sufficient injection flow rate of the fuel injection valve, and to atomize the spray. It is an object of the present invention to provide a fuel injection valve and a fuel injection method having spray characteristics that can prevent scattering of the fuel.

The present invention includes a plate member having a plurality of injection holes penetrating in the plate thickness direction, a valve seat positioned upstream of the plate member, a valve body for opening and closing a fuel passage between the valve seat, In a fuel injection valve provided with a drive device for driving a valve body,
A first injection hole set having a plurality of injection holes (41, 45) formed in the plate member (11);
A plurality of collision injection holes (40A) formed in the plate member so that the fuel injection flows collide with each other downstream of the first injection hole set with respect to the central axis of the fuel injection valve. 40B, 42A, 42B, 44A, 44B, 46A, 46B), a plurality of second injection hole sets (40, 42, 44, 46),
A fuel injection valve comprising:
The injection directions (PP) (QQ) after the collision of the collision nozzle holes in the plurality of second injection hole groups are different from each other, and the fuel injection direction (XX) of the first injection hole group is different from each other. Is directed to the center axis side of the fuel injection valve with respect to the injection direction (PP) (QQ) after the collision of the second injection hole set,
The ratio of the plate thickness of the plate member in which the nozzle hole is formed to the hole diameter of the nozzle hole is set to be smaller than the ratio of the plate thickness of the plate member in which the collision nozzle hole is formed to the hole diameter of the collision nozzle hole. A fuel injection valve is provided.

The present invention includes a plate member having a plurality of injection holes penetrating in the plate thickness direction, a valve seat positioned on the upstream side of the plate member, and a valve body that opens and closes a fuel passage between the valve seat, In a fuel injection valve provided with a drive device for driving the valve body,
A first injection hole set having a plurality of injection holes (41, 45) formed in the plate member (11);
A plurality of collision injection holes (40A) formed in the plate member so that the fuel injection flows collide with each other downstream of the first injection hole set with respect to the central axis of the fuel injection valve. 40B, 42A, 42B, 44A, 44B, 46A, 46B), a plurality of second injection hole sets (40, 42, 44, 46),
A fuel injection valve comprising:
The injection directions (PP) (QQ) after the collision of the collision nozzle holes in the plurality of second injection hole groups are different from each other, and the axis (XX) of the nozzle holes of the first nozzle hole group ) Is closer to the central axis side of the fuel injection valve than the injection direction (PP) (QQ) after the collision of the second injection hole set,
The ratio of the hole diameter of the nozzle hole to the plate thickness of the plate member in which the nozzle hole is formed was set to be smaller than the ratio of the plate thickness of the plate member in which the collision nozzle hole was formed to the hole diameter of the collision nozzle hole. A fuel injection valve is provided.

The present invention includes a plate member having a plurality of injection holes penetrating in the plate thickness direction, a valve seat positioned on the upstream side of the plate member, and a valve body that opens and closes a fuel passage between the valve seat, In a fuel injection valve that includes a drive device that drives the valve body and injects fuel toward the stem of the intake valve device,
A first injection hole set having a plurality of injection holes (41, 45) formed in the plate member (11);
A plurality of collision injection holes (40A) formed in the plate member so that the fuel injection flows collide with each other downstream of the first injection hole set with respect to the central axis of the fuel injection valve. 40B, 42A, 42B, 44A, 44B, 46A, 46B), a plurality of second injection hole sets (40, 42, 44, 46),
A fuel injection valve comprising:
The injection directions (PP) (QQ) after the collision of the collision nozzle holes in the plurality of second injection hole groups are different from each other, and the axis (XX) of the nozzle holes of the first nozzle hole group ) Is closer to the inside of the stem of the intake valve device than the injection direction (PP) (QQ) after the collision of the second injection hole set,
The ratio of the plate thickness of the plate member in which the nozzle hole is formed to the hole diameter of the nozzle hole is set to be smaller than the ratio of the plate thickness of the plate member in which the collision nozzle hole is formed to the hole diameter of the collision nozzle hole. A fuel injection valve is provided.

According to the fuel injection valve of the present invention, the plate member having a plurality of nozzle holes is combined such that the ratio of the hole length and the hole diameter of the nozzle holes is different from each other. Fuel injection was performed in two different directions. The resulting spray has an atomized spray on the outside and a spray having a strong penetrating force on the inside, and spraying of the spray can be suppressed by the traction effect of the spray having a strong penetrating force on the inside.
Further, the nozzle hole assembly forming such a spray structure can secure a large flow rate without impairing the atomization performance, and can enhance the performance and the degree of design freedom.

  Further, in the internal combustion engine equipped with the fuel injection valve of the present invention, the spray having a strong penetrating force on the inside is directed to the inside of the intake valve stem so that the spray having a good atomization in the periphery is contained in the intake valve plate. Therefore, the fuel can be prevented from adhering to the intake passage and the inner wall surface of the cylinder, the combustion performance is remarkably improved, and the emission of unburned gas components (HC, CO) can be greatly reduced.

  In this embodiment, a plate member having a plurality of injection holes penetrating in the plate thickness direction, a valve seat positioned on the upstream side of the plate member, and a valve body for opening and closing the fuel passage between the valve seat and In the fuel injection valve comprising the driving means for driving the valve body, the plate member has a plurality of non-collision holes directed in a desired direction downstream of the injection holes, and has an inner desired range. The ratio of the plate thickness and the hole diameter of the plurality of nozzle holes arranged in the nozzle is configured to be larger than the ratio of the plurality of nozzle holes arranged on the outside.

  As a result, a highly directional spray obtained by the inner nozzle hole (a spray having a strong penetrating force) and a fine atomized spray obtained by the outer nozzle hole are formed, and the atomized spray is formed by the directivity. The spray structure is formed so as to surround the strong spray, and the atomized spray is pulled by the spray having a strong penetrating force so that the spray structure does not scatter the spray.

  Further, in this embodiment, a plate member having a plurality of injection holes penetrating in the plate thickness direction, a valve seat positioned on the upstream side of the plate member, and a valve body for opening and closing the fuel passage between the valve seats And a drive means for driving the valve body, wherein the plate member has a plurality of pairs of holes that collide with each other downstream of the injection holes and non-collision holes that are injected in a desired direction. The ratio of the thickness and diameter of the former collision hole is larger than that of the latter non-collision hole.

As a result, a spray with strong penetrating force obtained by the inner non-collision nozzle hole and a spray with good atomization obtained by the pair of outer nozzle holes colliding with each other are formed, and the atomization spray is passed through the penetrating nozzle. It is possible to form a spray structure that is pulled by strong spray and has no spray scattering.
In this embodiment, the plurality of injection holes provided in the plate member are arranged so as to be symmetrical, so that two sets of hole assemblies are injected downstream of the injection holes in two different directions. Configured.

  Thereby, spray with good atomization can be generated in two directions. Further, with such a nozzle hole assembly, it is possible to determine the injection direction so as not to overlap each other even if the injection amount increases.

Further, the present embodiment includes an intake valve device that opens and closes a plurality of intake ports, and a fuel injection valve that is arranged on the upstream side of the intake valve device and is driven based on a control signal from the engine control device, In the fuel injection method using the fuel injection device configured to send both the intake air controlled by the intake valve device and the fuel spray injected from the fuel injection valve into a combustion chamber, the fuel injection valve includes: A plurality of spray structures described in any one of items 1 to 3 are formed, and the fuel injection method is configured such that the spray structures are oriented so as to be accommodated in the dish portion of the intake valve device.

  This prevents fuel from adhering to the inner wall surface of the intake pipe, etc., and ensures that the engine is ignited by a spray with a strong penetration force (a spray with a high fuel concentration) injected inward from the center position of the intake valve. Thus, combustion can be stabilized, and the fuel consumption can be reduced and the emission amount of unburned gas components (HC, CO) of combustion can be effectively reduced.

  Hereinafter, the best embodiment of the present invention will be described with reference to FIGS. 1 to 4 and FIG. 1 is a longitudinal sectional view showing a structure of a fuel injection valve according to the present invention, FIG. 2 is a partially enlarged sectional view showing a nozzle portion according to Embodiment 1 of the present invention, and FIG. 3 is an enlarged central portion of a plate member 11. FIG. 4 is a partial enlarged cross-sectional view of an injection valve showing a spray structure in two directions injected from the left and right hole sets. FIG. 8 shows an example of spray characteristics indicated by the dimensional ratio between the plate thickness t of the nozzle hole and the hole diameter d.

FIG. 1 shows a normally closed electromagnetic fuel injection valve as an example of the fuel injection valve of the present invention. (However, the effect of the present invention is not limited to the electromagnetic fuel injection valve.)
The fuel injection valve 1 lifts a predetermined amount when the magnetic coil 6 surrounding the electromagnetic coil 9, the core 7 positioned at the center of the electromagnetic coil 9 and having one end in contact with the yoke 6, and the electromagnetic coil 9 is excited. A valve body 3, a seat surface 10 in contact with the valve body 3, a fuel injection chamber 2 that injects fuel flowing through a gap between the valve body 3 and the seat surface 10, and a plurality of nozzles below the fuel injection chamber 2 A plate member 11 having holes 20, 21, 23 and 24 is provided. A spring 8 is provided at the center of the core 7 as an elastic member that presses the valve body 3 against the seat surface 10. When the coil 9 is not energized, the valve body 3 and the seat surface 10 are in close contact with each other. The fuel is supplied from the fuel supply port in a state where pressure is applied by a fuel pump (not shown), and the fuel injection chamber 2 of the fuel injection valve is filled with fuel up to the contact position between the valve body 3 and the seat surface 10. When the coil 9 is energized and the valve element 3 is displaced by the magnetic force and leaves the seat surface 10 provided in the nozzle portion 4, the fuel is concentrated in the vicinity of the axial center in the fuel injection chamber 2, and then along the plate member 11. The spray structures 30A, 31A injected from a plurality of nozzle holes 20, 21, 23, 24 (described later) are injected toward an intake port of the engine or the like.

  FIG. 2 is a partially enlarged cross-sectional view showing the nozzle portion according to the first embodiment of the present invention. The feature of the present invention is that, as shown in FIG. 3, the plate member 11 in the fuel passage has a plurality of nozzle hole sets 20 and 21 and nozzle holes 23 which are nozzle holes directed in a desired direction downstream of the injection holes. 24 (all non-collision holes for a single nozzle hole). In this embodiment, the ratio of the hole length t ′ and the hole diameter d of at least one nozzle hole among the plurality of nozzle holes is different from that of the other nozzle holes. The inclination of the nozzle hole is slight, and the hole length t ′ can be approximated to the plate thickness t. Therefore, hereinafter, t / d is handled as a hole diameter with respect to the plate thickness t. Therefore, the plate thickness can be read as the length of the hole. The nozzle hole sets 23 and 24 formed in the convex portion 22 of the plate member 11 have a large t / d, and the nozzle hole sets 20 and 21 having the same ratio are arranged in the periphery. These nozzle hole sets are formed symmetrically across the Y axis. The nozzle hole sets 20 and 23 are inclined to the left in the figure, and the nozzle hole sets 21 and 24 are inclined to the right in the figure. It is a hole.

  Next, the spray form produced | generated by these nozzle hole groups is demonstrated using FIG. FIG. 4 is a partial enlarged cross-sectional view of an injection valve showing a spray structure in two directions injected from the left and right hole sets across the Y axis, and schematically shows the spray form immediately below the injection hole. .

  The sprays generated by the nozzle hole sets 20 and 21 are sprays 30a and 31a with good atomization with a large spray energy and relatively wide spread because of a small t / d. Moreover, since the spray produced | generated in the nozzle hole groups 23 and 24 is arrange | positioned at the convex part 22, t / d is large and, therefore, injection energy becomes small. However, the sprays 30b and 31b have a small spread and a strong penetration force. FIG. 8A shows the relationship between the t / d of the non-collision type nozzle hole and the spray characteristics (particle size). When the t / d is increased, the particle size is increased. That is, it becomes a spray form with a strong penetration force.

  The point of this embodiment is that the sprays 30a and 31a atomized so as to cover both sides of the sprays 30b and 31b having a strong penetrating force are formed. It can be prevented. As they flow down, the sprays are combined to form spray structures 30A, 31A, thereby forming a two-way spray. Note that another feature of the spray structures 30A and 31A is that the narrow-angle spray (0 ° in the present embodiment) having a strong penetrating force determines the injection direction. That is, the best spray performance can be provided for various injection direction requirements that differ depending on the engine.

FIG. 5 is a partially enlarged cross-sectional view showing a nozzle portion according to Embodiment 2 of the present invention. In the present invention, as shown in FIG. 6, the plate member 11 in the fuel passage has a pair of holes 40A and 40B that collide downstream of the injection holes, and a single hole set 41 (non-collision) directed in a desired direction. Is installed.
In the case of this embodiment, the nozzle hole set 40 is formed symmetrically across the straight line PP, and is composed of two holes 40A and 40B inclined to the left in the drawing. The nozzle hole set 42 is formed at a symmetrical position with the X axis in between, and the two holes 42A and 42B are formed symmetrically with the straight QQ line in the same manner and tilted to the left in the figure. Is configured to do. Further, the nozzle hole set 41 is formed on the X-axis and is similarly inclined to the left in the drawing.

  The point of this embodiment is that the ratio t / d between the plate thickness t and the hole diameter d of the nozzle hole sets 40 and 42 is larger than the same ratio of the nozzle hole set 41. Specifically, a recess 48 is formed in the vicinity of the center of the plate member 11, and the nozzle hole sets 40 and 42 are provided at locations where the plate thickness outside the portion is thicker.

  The reason for this will be described again with reference to FIG. FIG. 4B shows the spray characteristics of the collision type nozzle. In the collision type nozzle, when t / d is increased, the atomization performance is improved. This is because when t / d is increased, a fuel flow having a fixed injection direction is injected, and a collision occurs reliably at a desired downstream position. When the collision of the injected fuel is accurately performed, the atomization degree is increased.

Reference numeral 43 denotes a nozzle hole set assembly constituted by three nozzle hole sets 40 , 41 , and 42 , and is arranged on the left side of the Y axis.

  On the other hand, 44, 45 and 46 are three nozzle hole groups formed symmetrically with respect to the left nozzle hole group 40, 41 and 42 across the Y axis, and the central nozzle hole group 45 is located on the X axis. The arranged single hole is inclined rightward, and the upper nozzle hole set 44 is constituted by two holes 44A and 44B. The lower nozzle hole set 46 is constituted by two holes 46A and 46B, which are formed so as to collide with each other downstream of the injection holes.

  Reference numeral 47 denotes the other nozzle hole set assembly constituted by three nozzle hole sets 44, 45, and 46, which is arranged on the right side of the Y axis.

Next, the spray form produced | generated by these nozzle hole assembly aggregates 43 and 47 is demonstrated using FIG. FIG. 7 is a partial enlarged cross-sectional view of an injection valve showing a spray structure in two directions injected from the left and right hole sets across the Y axis, and schematically shows the spray form immediately below the injection hole. . The spray generated by the nozzle hole sets 40 and 42 becomes a spray 42a having a relatively wide spread and good atomization due to a collision effect. On the other hand, since the spray generated by the nozzle hole set 41 is formed by a single hole, it becomes a spray 41a having a small spread and a strong penetration force. The point of this embodiment is that the atomized spray 42a is formed so as to cover the outer side of the spray 41a having a strong penetrating force, so that the spray can be prevented by being pulled by the spray having a strong penetrating force. It is. As they flow down, the sprays are combined to form a spray structure 43a. As shown in the drawing, this one spray structure 43a is jetted toward a desired position in the left direction.

  Another spray structure 47a formed across the Y axis is generated in the center of the spray hole 46a with good atomization corresponding to the nozzle hole set 44 and the nozzle hole set 46 by the action as described above. The spray 45a has a small spread and a strong penetration force. Similarly atomized spray is pulled to form another spray structure 47a which is sprayed toward the desired position in the right direction as shown.

  As a result, a two-way spray having two spray structures 43a and 47a is formed. Another feature of the spray structures 43a and 47a is that the spray having a strong penetrating force determines the spray direction of the spray.

  FIG. 9 shows an enlarged cross-sectional view of a main part showing an enlarged central part of the plate member 50 of Example 3 according to the present invention. In this embodiment, the hole arrangement of the plate member 11 of the second embodiment is configured as a separate type, and the plate member 50 includes a plate member 51 having a small plate thickness and a plate member 53 having a large plate thickness.

In the plate member 53, a hole set 55 that collides downstream of the injection holes and a single hole set 54 (non-collision) directed in a desired direction are inclined leftward, and at least one is formed. On the other hand, similarly, the hole set 57 colliding with the downstream side of the injection hole and the single hole set 56 (non-collision) directed in the desired direction are formed so as to incline to the right.
The plate member 51 is formed with a hole set 55a, 57a corresponding to the colliding hole set 55, 57 and a large diameter hole 52 communicating with the single hole set 54, 56.

  The point of this embodiment is that hole processing is facilitated by reducing the plate thickness, which can reduce the cost. The obtained spray is the same as that of Example 1, and the effect is also the same. Note that the thickness relationship between the plate member 51 and the plate member 53 may be a combination opposite to that described in the present embodiment, and the degree of design freedom in performing spray formation is high. . Further, by separating, the upstream plate member becomes the plate member 51 in this case, but it is possible to make the shape convenient for atomization, and the degree of freedom of design is increased. For example, the surface accuracy is roughened, the turbulence is added to the fuel flow, and atomization is promoted. Such a design event can be easily performed by those skilled in the art.

  In FIG. 10, the principal part expanded sectional view which expands and shows the center part of the plate member 61 of Example 4 which concerns on this invention is shown. In this embodiment, the holes 41 and 45 of the plate member 11 of Example 2 are press-press formed to form the recess 62, and the partial plate thickness is reduced. Specifically, a dent of several tens of microns in depth is provided.

  The plate member 61 is formed with at least one or more hole sets 64 that collide downstream of the injection holes and a single hole set 63 (non-collision) that heads in a desired direction and is inclined leftward. On the other hand, the hole set 66 colliding downstream of the injection holes and the single hole set 65 (non-collision) heading in the desired direction are formed so as to incline to the right.

  The point of the present embodiment is that, as in the previous example, the hole processing is facilitated by the reduction of the plate thickness, which can reduce the cost. The obtained spray is the same as that of Example 1, and the effect is also the same. In addition, since it is necessary to generate various spray shapes, the press molding site is not limited to the scope of the present embodiment, and the installation may be at a desired position or a plurality of locations. Such a design event can be easily performed by a person skilled in the art.

  In the previous embodiment, a nozzle hole in which the spray is non-cross-collision by a single nozzle hole was used. However, even if the nozzle hole set has a shape in which the spray cross-collises, the angle of cross-collision is narrow. Thus, the same effect as that of a single nozzle hole can be obtained, and further the effect of atomizing the fuel can be obtained. In this embodiment, the generation of the lead spray is not formed by a single nozzle hole but is formed by two nozzle hole sets that form a colliding spray, and the atomization performance is superior to the former and the penetrating force is improved. It has the characteristic of maintaining the formation of a strong spray. In this example, the lead spray is formed by two sprays that collide with each other at a narrow angle.

  FIG. 11 shows an example in which the fuel injection valve 1 according to the present invention shown in FIG. 1 is mounted on an internal combustion engine, and shows the relationship between two spray structures obtained from the fuel injection valve and the intake valve device. Therefore, it is the schematic seen from the engine upper part.

  In the internal combustion engine shown in the figure, 100 indicates one of the cylinders of the multi-cylinder internal combustion engine, 101 is a valve plate portion of an intake valve device that opens and closes an intake port, 102 is an intake valve stem of the intake valve device, 103 Is an intake passage having a central partition 104 separating the intake ports and communicating on the upstream side. Reference numeral 105 denotes a combustion chamber, 106 denotes an exhaust valve device, and 107 denotes an ignition device. Reference numerals 30 </ b> A and 31 </ b> A schematically show spray structures injected from the fuel injection valve 1. Two intake valve devices are juxtaposed as shown in the figure. A so-called double intake type internal combustion engine is shown. Therefore, the spray structures 30A and 31A from the fuel injection valve 1 are injected toward the dish portion 101 of each intake valve device. As described above, the fuel injection valve 1 employs a fuel injection system that is arranged as a multi-point injection (MPI) system, one disposed upstream of the intake valve device.

  What is characteristic in this embodiment is that the atomized sprays 30A and 31A injected from the fuel injection valve are injected into the dish portion 101 of the intake valve device, and the spray 30b having a strong penetrating force inside is provided. 31b is directed inward from the stem 102 of the intake valve device. As a result, the adhesion of fuel droplets to the intake passage and the inner wall surface of the cylinder head is suppressed. In particular, the sprays 30b and 31b having a strong penetrating force are effective in forming a combustible air-fuel mixture around the ignition device 107. Further, the peripheral sprays 30a and 31a having good atomization performance effectively act to improve the quality and formation state of the air-fuel mixture.

  From the above, in the internal combustion engine provided with the fuel injection valve of the present invention, since the adhesion of the fuel spray injected from the fuel injection valve to the excessive portion is suppressed, the unburned gas component of combustion (HC, CO) emissions can be greatly reduced.

  As described above, a plate member having a plurality of injection holes penetrating in the plate thickness direction, a valve seat positioned on the upstream side of the plate member, and a valve body that opens and closes the fuel passage between the valve seat and In a fuel injection method using a fuel injection valve provided with a driving device for driving the valve body, an injection hole having a hole axis extension line of non-crossing collision is disposed inside the plate member and in proximity to the injection hole. And a hole diameter with respect to the plate thickness at the position of the injection hole arranged on the inside compared to the ratio of the hole diameter with respect to the plate thickness at the position of the injection hole arranged on the outside The spray is made from the injection hole having the hole axis extension line of the non-crossing collision, and the single spraying which is the non-crossing collision is made from the other single injection hole. The latter spray, and the latter spray, attracts the surrounding spray and leads Fuel injection method as inward from the stem center of the intake valve device, so as to direct each to form a spray structure as is formed.

  Furthermore, a plate member having a plurality of injection holes penetrating in the plate thickness direction, a valve seat located upstream of the plate member, a valve body for opening and closing a fuel passage between the valve seat, and the valve In a fuel injection method using a fuel injection valve provided with a drive device for driving a body, a pair of injection holes each having a hole axis extension line intersecting at a wide angle downstream of the injection hole and an inner side of the plate member, And an injection hole having a hole axis extension line of non-crossing collision, which is disposed in the vicinity of the injection hole, and is disposed on the inner side as compared with the ratio of the hole diameter to the plate thickness at the position of the injection hole disposed on the outer side. The ratio of the hole diameter to the plate thickness at the hole position is the same or larger, and spray is performed so that each hole axis extension line crosses and collides at a wide angle downstream from the pair of injection holes, and the other single injection A single shot that is non-crossing collision from the hole, wide angle A spray structure is formed so that the spray is directed to the tray portion of the intake valve device, and the narrow-angle spray is directed toward the inside of the stem center of the intake valve device as a lead spray by attracting the surrounding spray. The fuel injection method is configured.

  From the above, in the internal combustion engine provided with the fuel injection valve of the present invention, since the adhesion of the fuel spray injected from the fuel injection valve to the excessive portion is suppressed, the unburned gas component of combustion (HC, CO) emissions can be greatly reduced.

It is a longitudinal cross-sectional view which shows the structure of the fuel injection valve of this invention. It is a principal part expanded sectional view which shows the nozzle part which concerns on the Example of this invention. It is a principal part enlarged view which expands and shows the center part of the plate member which concerns on Example 1. FIG. It is a principal part expanded sectional view of the fuel injection valve which shows the spray structure of 2 directions injected from a hole set on either side. FIG. 6 is an enlarged cross-sectional view showing a main part of a nozzle part according to a second embodiment. It is a principal part enlarged view which expands and shows the center part of the plate member which concerns on Example 2. FIG. It is a principal part expanded sectional view of the fuel injection valve which shows the spray structure of 2 directions injected from a hole set on either side. It is a figure for demonstrating an example of the spray characteristic shown by the dimension ratio of the board thickness t of an injection hole, and the hole diameter d. FIG. 9 is an enlarged cross-sectional view of a main part showing an enlarged central part of a separate plate member according to Example 3; It is a principal part expanded sectional view which expands and shows the center part of the plate member with a recessed part which concerns on Example 4. FIG. It is a figure which shows the mode of the spray structure injected toward the intake valve apparatus.

  DESCRIPTION OF SYMBOLS 1 ... Fuel injection valve, 2 ... Fuel injection chamber, 3 ... Valve body, 4 ... Nozzle part, 5 ... Fuel passage, 6 ... Yoke, 7 ... Core, 8 ... Spring, 9 ... Coil, 10 ... Seat surface, 11 ... Plate member, 20, 21, 23, 24 ... Nozzle hole set, 22 ... Projection of plate member, 30A, 31A, 43a, 47a ... Spray structure, 40, 41, 42, 44, 45, 46 ... Nozzle hole set 43, 47 ... Nozzle hole assembly, 62 ... Depression, 101 ... Intake valve device, 102 ... Intake valve device stem, 103 ... Intake passage, 104 ... Central partition, 105 ... Combustion chamber, 106 ... Exhaust valve device, 107: Ignition device.

Claims (3)

A plate member having a plurality of injection holes penetrating in the plate thickness direction, a valve seat located upstream of the plate member, a valve body for opening and closing a fuel passage between the valve seat, and driving the valve body In a fuel injection valve equipped with a drive device
A first injection hole set having a plurality of injection holes (41, 45) formed in the plate member (11);
A plurality of collision injection holes (40A) formed in the plate member so that the fuel injection flows collide with each other downstream of the first injection hole set with respect to the central axis of the fuel injection valve. 40B, 42A, 42B, 44A, 44B, 46A, 46B), a plurality of second injection hole sets (40, 42, 44, 46),
A fuel injection valve comprising:
The injection directions (PP) (QQ) after the collision of the collision nozzle holes in the plurality of second injection hole groups are different from each other, and the fuel injection direction (XX) of the first injection hole group is different from each other. Is directed to the center axis side of the fuel injection valve with respect to the injection direction (PP) (QQ) after the collision of the second injection hole set,
The thickness of the plate member in which the nozzle hole is formed is smaller than the plate thickness of the plate member in which the collision nozzle hole is formed, and the plate member in which the nozzle hole is formed with respect to the hole diameter d of the nozzle hole. The ratio t / d of the plate thickness t is set to be smaller than the plate thickness / hole diameter, which is the ratio of the plate thickness of the plate member on which the collision injection hole is formed to the hole diameter of the collision injection hole , The injection after the collision from the collision nozzle forms a highly atomized spray, and the injection from the nozzle hole generates a spray having a strong penetrating force compared to the spray having a high atomization due to the collision. A fuel injection valve formed inside a high spray. A plate member having a plurality of injection holes penetrating in the plate thickness direction, a valve seat located upstream of the plate member, a valve body for opening and closing a fuel passage between the valve seat, and the valve body In a fuel injection valve provided with a driving device for driving,
A first injection hole set having a plurality of injection holes (41, 45) formed in the plate member (11);
A plurality of collision injection holes (40A) formed in the plate member so that the fuel injection flows collide with each other downstream of the first injection hole set with respect to the central axis of the fuel injection valve. 40B, 42A, 42B, 44A, 44B, 46A, 46B), a plurality of second injection hole sets (40, 42, 44, 46),
A fuel injection valve comprising:
The injection directions (PP) (QQ) after the collision of the collision nozzle holes in the plurality of second injection hole groups are different from each other, and the axis (XX) of the nozzle holes of the first nozzle hole group ) Is closer to the central axis side of the fuel injection valve than the injection direction (PP) (QQ) after the collision of the second injection hole set,
The thickness of the plate member in which the nozzle hole is formed is smaller than the plate thickness of the plate member in which the collision nozzle hole is formed, and the plate member in which the nozzle hole is formed with respect to the hole diameter d of the nozzle hole. the ratio t / d of the thickness t is set to be smaller than the plate thickness / hole diameter is the ratio of the plate thickness of the collision nozzle hole formed plate member relative to the hole diameter of the impingement injection hole, The injection after the collision from the collision nozzle forms a highly atomized spray, and the injection from the nozzle hole atomizes the spray having a strong penetrating force compared to the spray that is highly atomized by the collision. A fuel injection valve characterized by being formed inside a high spray. A plate member having a plurality of injection holes penetrating in the plate thickness direction, a valve seat located upstream of the plate member, a valve body for opening and closing a fuel passage between the valve seat, and the valve body In a fuel injection valve that includes a drive device for driving and injects fuel toward the stem of the intake valve device,
A first injection hole set having a plurality of injection holes (41, 45) formed in the plate member (11);
A plurality of collision injection holes (40A) formed in the plate member so that the fuel injection flows collide with each other downstream of the first injection hole set with respect to the central axis of the fuel injection valve. 40B, 42A, 42B, 44A, 44B, 46A, 46B), a plurality of second injection hole sets (40, 42, 44, 46),
A fuel injection valve comprising:
The injection directions (PP) (QQ) after the collision of the collision nozzle holes in the plurality of second injection hole groups are different from each other, and the axis (XX) of the nozzle holes of the first nozzle hole group ) Is closer to the inside of the stem of the intake valve device than the injection direction (PP) (QQ) after the collision of the second injection hole set,
The thickness of the plate member in which the nozzle hole is formed is smaller than the plate thickness of the plate member in which the collision nozzle hole is formed, and the plate member in which the nozzle hole is formed with respect to the hole diameter d of the nozzle hole. the ratio t / d of the thickness t is set to be smaller than the plate thickness / hole diameter is the ratio of the plate thickness of the collision nozzle hole formed plate member relative to the hole diameter of the impingement injection hole, The injection after the collision from the collision nozzle forms a highly atomized spray, and the injection from the nozzle hole atomizes the spray having a strong penetrating force compared to the spray that is highly atomized by the collision. A fuel injection valve characterized by being formed inside a high spray.

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