JP3044876B2 - Electronically controlled fuel injection device for internal combustion engines - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electronically controlled fuel injection device for an internal combustion engine, and more particularly to an electronically controlled fuel injection device for an internal combustion engine capable of changing a spray shape according to the operating state of the engine.

[0002]

2. Description of the Related Art In recent years, a fuel supply device for a gasoline engine has been required to precisely control the fuel supply in view of measures against exhaust gas, improvement of fuel consumption and output, and the like, and electronic control fuel injection devices are rapidly increasing. . The electronic control fuel injection device
Two types of fuel injectors: a single-point fuel injection device with an electromagnetic fuel injection valve upstream of the throttle valve (single-point injection) and a multipoint fuel injection device with an electromagnetic fuel injection valve for each cylinder (multipoint injection) Can be roughly divided into Here, the single-point fuel injection system has a problem of fuel supply delay due to the mixture distribution during transition and the adhesion of injected fuel to the inner surface of the intake pipe. Requires a lot of development man-hours. For this reason, by injecting fuel near the intake valve of each cylinder, the above-mentioned problems are relatively small, and the adoption of a multipoint fuel injection device with high control accuracy is gradually increasing. However, in the multipoint fuel injection device, the responsiveness is good because the electromagnetic fuel injection valve is close to the intake valve, but there is a problem in forming a homogeneous air-fuel mixture because the fuel atomization time is short. is there. In addition, the problem of fuel supply delay due to fuel adhesion to the inner wall surface of the intake pipe is included to some extent.

In view of the above problems, it may be necessary to optimize the spray characteristics of an electromagnetic fuel injection valve for a multipoint fuel injection device. Therefore, in the electromagnetic fuel injection valve, the improvement of the single characteristic under the predetermined injection angle and the predetermined injection direction has been promoted. For example, the inventors of the present application have been studying with an emphasis on the improvement of the atomization characteristics, and a representative example thereof is disclosed in JP-A-2-256871.
(U.S. Pat. No. 5,018,501),
38164 (U.S. patent application Ser. No. 07 / 49,116).

[0004]

There have been many attempts to improve the characteristics of electromagnetic fuel injectors. In any case, however, the required characteristics are determined by the shape of the combustion chamber or the shape of the intake pipe of the engine. This has been performed based on the injection angle and the injection direction, and has not been performed to give an appropriate spray shape according to the operating state of the engine.

SUMMARY OF THE INVENTION An object of the present invention is to focus on this point. An internal combustion engine which uses an electromagnetic injection valve of a variable spray shape and which can be matched to the operation state of the engine to realize high efficiency operation of the engine. The present invention provides an electronic control fuel injection device for a vehicle.

[0006]

In order to achieve the above object, an electromagnetic fuel injection valve according to the present invention comprises a valve seat, a fuel injection hole,
Driven by an electromagnet and a nozzle forming a hollow
A valve body for opening and closing the fuel passage between the valve seat and the valve seat;
Inserted into the hollow portion of the nozzle and located upstream of the valve seat
To guide the valve body in the axial direction and to apply a turning force to the fuel.
A fuel swirling element forming a fuel passage to be provided.
The fuel passage is defined by a lower surface of the fuel swirl element and the fuel swirl element.
Fuel formed between the nozzle inner wall surface facing the lower surface
A shaft center in a chamber formed by the valve body, the valve seat and the fuel swirl element.
To the radial passage and the radial passage
And an axial passage supplying the material.
Means are provided for axially displacing the fuel swirling element.

[0007] To achieve the above object, an internal combustion engine according to the present invention is provided.
The engine electronically controlled fuel injection system has an intake valve plate for each cylinder.
Point with electromagnetic fuel injection valve that injects fuel toward
-Type electronically controlled fuel injection device for an internal combustion engine,
The magnetic fuel injection valve has a valve seat, a fuel injection hole, and a hollow part.
And a valve seat, driven by an electromagnet,
A valve body for opening and closing the fuel passage between the nozzle and the hollow of the nozzle
Inserted upstream of the valve seat and axially forward
A fuel passage that guides the valve body and imparts a turning force to the fuel
A fuel swirl element forming a passage, and
The lower surface of the fuel swirling element is opposed to the lower surface of the fuel swirling element.
The fuel formed between the nozzle inner wall surface and the valve body, the valve
Eccentric guide to the axis in the chamber formed by the seat and fuel swirl element
And a shaft for supplying fuel to the radial passage.
And the fuel swirl element is formed in the axial direction.
Displacement means for detecting the operating state of the engine.
Using the detection signal of the detection means.
Operating means for controlling the position of the engine.
The fuel swirl element is displaced in the axial direction according to the state.
It is something that has been done.

[0008]

In order to displace the fuel swirling element in the axial direction, a piezoelectric element or the like, which mechanically generates displacement when a voltage is applied, may be used as a driving source. The voltage signal is
It is conceivable to use an arithmetic operation based on a signal representative of an engine operation signal, for example, a crank angle signal (rotation speed signal), an air amount signal, or the like. Further, when controlling the shape of the spray, the operating state of the engine is continuously detected,
Alternatively, it is effective to perform detection in three stages of a low speed region, a medium speed region, and a high speed region.

[0010]

The swirling fuel component (radial direction)
Flow component) and non-swirling fuel component (axial flow component, or
Varies the ratio to the radial flow component that does not pass through the swirl path.
To produce various spray shapes. Swirling fuel component
Is offset with respect to the axis provided on the fuel swivel element.
And the non-swirl fuel component is
Fuel flowing through the gap between the bottom surface of the fuel swirl element and the inner wall surface of the nozzle
And the ratio of the fuel amount of these two fuel components
A variety of spray shapes can be controlled. And
Making the spray shape variable according to the operating state of the engine
become.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a block diagram showing an outline of the present invention. Reference numeral 100 denotes a control unit, 1 is a block to which an engine status signal from the engine 10 is input, 2 is a block to output signals indicating various control amounts to the spray shape variable fuel injection valve 16, and 3 is an input. A control block 4 for correcting the relationship between the control amount and the control amount indicates a memory in which parameters corresponding to the operating state of the engine are stored.

Before describing this element, the relationship between the operating state of the engine and the spray condition of the electromagnetic fuel injection valve will be described with reference to Table 1 and FIG.

[0014]

[Table 1]

As shown in Table 1, when the engine is started, the intake valve is closed for a long time because the engine speed is as low as several tens of revolutions per minute. Therefore, in order to effectively start the combustion of the engine, it is necessary to make the fuel droplets fine and promote the mixing with the air. In particular, when the inside of the intake pipe is cold, for example, under severe conditions such as an ambient temperature of −30 ° C., the fuel on the inner wall of the intake pipe (the surface tension and viscosity of the fuel become twice as high as those at normal temperature) Because adhesion occurs remarkably,
Mixing with air is prevented. The fuel droplets are required to be a group of fine sprays that float in the intake pipe.

On the other hand, during idling, the engine speed is higher than at startup, but the time during which the intake valve is closed is still long. For example, it is about 20 times as long as the operation time of the electromagnetic fuel injection valve. The non-uniformity of the air-fuel mixture within this time period has a negative effect such as a large amount of HC emission and misfire. It is necessary to promote mixing.

At the time of medium speed operation of the engine, the period during which the intake valve is closed becomes shorter because the engine speed is further increased as compared with the time of idling operation. Therefore, in order to evaporate the droplet in a shorter time and promote mixing with air,
In addition to the droplet diameter, it is necessary to minimize the adhesion of fuel to the inner wall of the intake pipe, which hinders this. That is,
It is necessary to prevent fuel from adhering to the inner wall surface of the intake pipe and to produce a uniform mixture in a short period of time.

At the time of high speed operation of the engine, the above points must be considered more than at the time of medium speed operation. In particular, when the intake air amount increases, the inflow speed increases, so that the spray from the electromagnetic fuel injection valve is bent, and the fuel adheres to the inner wall surface of the intake pipe. In a so-called high-speed operation of the engine, it is required that the amount of fuel attached to the inner wall surface of the intake pipe is small and the rate of direct spraying on the valve plate is high.

As described above, when the engine is operated at a medium speed to a high speed, it is possible to increase the penetration force of the spray and to quickly feed the fuel into the combustion chamber of the engine, not to mention the droplet diameter of the spray. However, this must be taken into consideration because it is good for improving the operation efficiency of the engine.

At the time of transient operation of the engine, that is, at the time of acceleration or deceleration, since the opening and closing operation of the intake valve is extremely fast, it is necessary to spray a small amount of fuel and a small droplet diameter on the inner wall surface of the intake pipe.

FIG. 2 shows the relationship between the operating state of the engine and the state of spraying. The degree of atomization indicating the size of droplets, the penetrating force indicating the magnitude of the kinetic energy of spraying, This shows the relationship with the shape.

Here, description will be made again with reference to FIG. As an operation signal of the engine 10, a rotation speed signal, an air amount signal, a cooling water temperature, and the like are used. The control amount is determined by the controller 3 in advance from the operation signal stored in the memory 4 and the driving condition of the electromagnetic fuel injection valve 16, and a basic injection amount signal and an injection amount correction signal are output. According to the present invention, in addition to the output signal, an injection angle voltage signal is output according to the operating state of the engine. In one embodiment of the present invention, this voltage signal is continuously controlled according to the operating state of the engine, as shown in FIG. According to this embodiment, the state of the spray can be very finely changed according to the operating state, so that a highly efficient operation of the engine can be realized.

In another embodiment of the present invention, as shown in FIG. 4, the engine is controlled in a stepwise manner such as a low-speed operation range, a medium-speed operation range, and a high-speed operation range. According to this embodiment, although the control is not very fine, the load on the control unit can be reduced as compared with the above-described embodiment. In this example, depending on the state such as acceleration or deceleration, it is not controlled or is treated in the same manner as in the medium speed range.

FIG. 5 shows an electronically controlled fuel injection device of a multipoint internal combustion engine having an electromagnetic fuel injection valve for injecting fuel toward a valve plate for each cylinder. Numeral 10 is a partial sectional view of an engine using gasoline as fuel. The intake manifold 12 includes a throttle valve 11, an intake hole 13, an intake valve 14 for opening and closing the intake hole 13, a combustion chamber 15,
The valve seat 14 of the intake valve 14 is attached to the wall of the intake valve 14.
An electromagnetic fuel injection valve 16 according to the present invention, which is arranged so as to be able to inject in the a direction, is shown.

In the air system, air filtered by an air cleaner (not shown) is measured by an air flow sensor 17,
The air is distributed from the intake manifold 12 to each cylinder through the throttle body 18. In the fuel system, gasoline pumped up from a fuel tank 20 by a fuel pump 19 passes through a fuel filter 21 and is adjusted to a pressure approximately 250 kPa higher than an intake pipe pressure by a pressure regulator 22. It is distributed to each electromagnetic fuel injection valve 16. The control system determines an appropriate gasoline amount according to the operation state of the engine 10. The amount of gasoline supplied to the engine 10 is adjusted by the injection time of the electromagnetic fuel injection valve 16, and the injection time is calculated and determined by the control unit 100. The detection of the operating state of the engine 10 includes an intake air temperature sensor 7, a water temperature sensor 8, a crank position sensor 9, a throttle position sensor 25, an air flow sensor 17, an O ₂ sensor 26, and the like. Other control system components include a battery 27, an ignition switch 28, an ignition coil 29, and the like.

The operation of the engine 10 is performed by the control unit 100 processing the information of the operating state, such as the amount of intake air, the air temperature, and the engine speed. Low speed, medium speed,
High-speed state determination is mainly performed based on the engine speed. The start is determined based on, for example, the water temperature, the intake air amount, and the throttle angle. When the water temperature is low, the intake air amount is small, and the throttle angle is zero degrees, the start is determined. The determination at the time of idling is mainly performed based on whether or not the engine speed is a predetermined speed. The determination at the time of acceleration or deceleration is performed based on the throttle angle, the output of the oxygen sensor, and the engine speed.

The fuel injection electromagnetic fuel injection valve 16, the control - the signal Ruyunitto 100 is controlled have group Dzu. Here, in the present embodiment , the control unit 10
Two signals flow from 0 to the electromagnetic fuel injection valve 16. The solid line signal shown in the figure is used for the basic injection amount and the correction injection amount, and the dotted line signal is used for adjusting the injection angle.

A mixture of fuel and air is guided from an intake hole 13 of the engine 10 to a combustion chamber 15, compressed in a compression stroke, and ignited and burned by a spark plug (not shown).

Hereinafter, before describing an embodiment according to the present invention.
To, with reference to FIGS. 6 to 13, solenoid type fuel injection valve 16
Its configuration will be described for Reference Example.

FIG. 6 is a longitudinal sectional view of the electromagnetic fuel injection valve 16. The electromagnetic fuel injection valve 16 is an upstream swirling type suitable for making the shape of the spray variable. That is,
The injection angle is varied by adjusting the ratio between the swirling fuel component (radial flow component) and the non-swirl fuel component (axial flow component or radial flow component that does not pass through the swirl passage). Hereinafter, its structure and operation will be briefly described.

In the figure, the injection valve 16 has a duty ON calculated and determined by the control unit 100.
The fuel supply is performed by opening and closing the sheet portion 36 in response to the -OFF signal. The electrical signal is
As a pulse signal. When a current flows through the coil 30, a magnetic circuit is formed by the core 31, the yoke 32, and the plunger 33, and the plunger 33 is attracted to the core 31. When the plunger 33 moves, the ball valve 34 integrated with the plunger moves away from the seat surface 36 of the nozzle 35 to open a fuel injection hole 37 (hereinafter, referred to as an orifice). The ball valve 34 includes a rod 38 joined to one end of a plunger 33 made of a magnetic material, a ball 39 joined to multiple ends of the rod 38, and a plunger 33.
And a guide ring 40 made of a non-magnetic material and fixed to the upper opening. A cylindrical fuel swirling element 42 having an elastic member 41 inserted and fixed to the inner peripheral surface of the ball 39 is inserted and fixed to the inner wall of the hollow portion of the nozzle 35 at the outer peripheral portion of the ball 39. When the ball valve 34 is moved, it is firmly guided by the guide ring 40 and is slightly guided by the inner wall surface of the elastic member 41. The stroke amount during the movement is determined by the size of the gap between the receiving surface 38a at the neck of the rod 38 and the stopper 43.

Here, the fuel flow will be described with reference to FIG. 7 which is an enlarged view of the periphery of the orifice 37, and FIG. 8 and FIG. Note that, for the sake of explanation, the elastic member 41 is omitted. In the respective drawings, the same reference numerals represent the same parts.

The fuel swirling element 42 is provided with an axial groove 42a and a radial groove 42b. In this embodiment, the axial groove 4
2a is formed by a D-cut surface. Such grooves 42a, 42
b denotes a fuel passage introduced from above,
The fuel that has passed through 2a is introduced eccentrically from the axis through groove 42b. That is, a turning force is applied to the fuel. The method of adjusting the fuel turning strength includes the distance between the shaft center and the groove center, the number of grooves, the cross-sectional area of the groove, the distance between the inner wall surface 42c of the fuel turning element 42 and the outer peripheral surface of the ball 39, the fuel turning. Element 42
And the distance between the bottom surface and the surface 35a of the nozzle 35 corresponding thereto.

In the first reference example, the gap size between the inner wall surface 42c of the fuel swirl element 42 and the outer peripheral surface of the ball 39 is adjusted, and the flow speed indicated by the arrow in FIG. 7 is changed. This adjusts the turning strength. Vm is the fuel swirl element 4
2 indicates the flow velocity of the fuel of the swirling component flowing through the radial groove 42b, and Vo indicates the flow velocity of the non-swirl component fuel flowing between the inner wall surface 42c of the fuel swirling element 42 and the outer peripheral surface of the ball 39. ing. The turning intensity changes depending on the ratio (Vo / Vm) of the two, and as a result, the spread angle of the spray injected from the orifice 37 changes. FIG. 9 shows the relationship between Vo / Vm and the injection angle.

FIG. 10 is an enlarged view of a portion of the nozzle 35 having the fuel swirling element 42 in which the elastic member 41 capable of variably adjusting the flow velocity Vo of the non-swirl component fuel is inserted and fixed.
The figure shows a state where the ball valve 34 has moved upward.
The elastic member 41 has a cylindrical shape in which a large number of piezoelectric elements are mechanically displaced when a voltage is applied.

FIG. 11 shows a deformed state of the elastic member when a voltage is applied to the elastic member 41. δo indicates the gap size when the applied voltage is zero, and δi indicates the gap size when the voltage i is applied. FIG. 12 shows the relationship between the voltage signal and the displacement δ, and FIG. 13 shows the relationship between the voltage signal δ and the fuel leak amount.
Corresponds to the code in FIG. That is, as the voltage is applied, the amount of fuel leak increases, and the amount of non-swirl component fuel increases. Therefore, the spray shape has a narrow injection angle, and is suitable for high-speed operation.

[0037] Figure 14, electric shows another reference example of the magnet type fuel injection valve, the example shown in FIG. 10, the fuel swirl element 50
Are different. 6 to 11 indicate the same parts. FIG. 15 is a cross-sectional view taken along the line BB of FIG. Fuel swirl element 50
Is a flange shape made of an insulating material,
1 is fixed. The fuel swirling element 50 is provided with an axial groove 50a and a radial groove 50b eccentric with respect to the axis of the injection valve. When a voltage is applied to the elastic member 41, the size of the gap between the inner peripheral surface of the elastic member 41 and the outer peripheral surface of the ball 39 increases, and the fuel component in the axial direction (non-swirl) increases. Therefore, the spray shape has a narrow injection angle, and is suitable for high-speed operation.

According to this reference example, the configuration can be simplified as compared with the example of FIG. In addition, when a piezoelectric element is used as the elastic member, the temperature of the fuel can be raised by heat generation, so that atomization is easy and the startability of the engine is improved.

[0039] FIGS. 16 to 18, shows still another reference example of the solenoid type fuel injection valve, are different shapes of the valve body. 6 to 15 indicate the same parts. Figure 16 shows a fuel injection valve with a ball valve 51. Figure 17 shows a fuel injection valve using a pintle valve 52. Figure 18 is two - shows a fuel injection valve using a dollar valve 53. In each of the reference examples, FIG.
Operations and effects similar to those of the reference example described with reference to FIG . The fuel swirl element 42 may have a shape shown in FIG.

[0040] Figure 19, Figure 20 shows the real施例of the present invention. FIG. 20 is a view in the direction of arrow C in FIG. FIG.
0 is an enlargement of the nozzle portion of the electromagnetic fuel injection valve configured to make the ratio of the radial flow component (non-swirl fuel component) not passing through the swirl passage and the radial groove flow component (swirl fuel component) variable. FIG. The main change is that a fuel swirling element 54 and a spring 55 that biases the fuel swirling element 54 against the nozzle surface are interposed. The spring 55 is provided between the flange portion 54c of the fuel swirling element 54 and the stopper 43 for restricting the movement of the valve body in the axial direction. When the fuel swirling element 54 is pushed upward by an axis due to the mechanical displacement of the elastic member 41, the bottom surface of the fuel swirling element 54 and the bottom surface 35d of the nozzle 35 corresponding to this surface.
A gap is formed between the fuel cells, and a fuel leak is generated from this space. That is, a fuel flow that does not pass through the swirl groove 54b occurs,
Turning strength decreases. The groove 54b is a fuel passage extending in the axial direction. In FIG. 20, a solid arrow indicates a radial groove flow component (swirl fuel component), and a broken arrow indicates a radial flow component (non-swirl fuel component) that does not pass through the swirl passage.

As described above, the method of adjusting the fuel swirling strength includes the distance between the shaft center and the groove center, the number of grooves, the cross-sectional area of the grooves, the inner wall surface 42c of the fuel swirling element 42 and the ball 39.
, The distance between the bottom surface of the fuel swirling element 42 and the surface 35a of the nozzle 35 corresponding thereto. FIG.
0, the example of FIG. 14, the inner wall surface 42c and ball of the fuel swirl element 42 - Ru der those for varying the outer peripheral surface distance Le 39. this
Respect, the example of FIG. 19, the surface 35a distance between the bottom surface and the nozzle 35 with respect to that of the fuel swirl element 42 is intended to variably. Next, other examples will be described below. First, the number of a plurality of swirl passages provided in the fuel swirl element is switched according to the operation state, the swirl force is adjusted, and the spray shape is switched. Here, the swirl number S
Is given by the following equation. S = (2 · do · L
s) / (n · ds ² ) where n is the number of turning paths, d
s is the swirl path diameter, do is the orifice diameter, and Ls is the offset. Therefore, as described above, the spray shape can be switched by switching the number of swirl passages according to the operating state.

As can be seen from the above equation, the spray shape can be switched even if the swirl path diameter ds is changed.

Further, as another example, the fuel swirl element itself is formed of an elastic member, and the mechanical displacement of this member causes
By changing the gap between the fuel swirling element and the nozzle body, the spray shape can be switched according to the operating state.

In the above example, the spray shape is varied according to the operating state of the internal combustion engine. However, the spray shape may be varied according to the load state on the internal combustion engine. In this case, the spray shape is changed so that the spray angle is reduced when the engine is in a high load state, and is increased when the engine is in a low load state. Further, if the number of rotations is taken into account, it is preferable to change the spray shape so that the spray angle decreases as the load increases and the rotation increases, and the spray angle increases as the load decreases and the rotation decreases.

[0045]

As described above, according to the present invention, it is possible to form an appropriate mixture of fuel and air in accordance with the operating state of the engine by using the spray type variable electromagnetic fuel injection valve. In addition, high efficiency operation of the engine is enabled, and exhaust pollutants can be reduced, and fuel efficiency and output can be improved.

[Brief description of the drawings]

FIG. 1 is a block diagram showing an outline of the present invention.

FIG. 2 is a diagram showing a relationship between an operating state and a spray state of an engine according to an embodiment of the present invention.

FIG. 3 is a diagram illustrating a relationship between an operating state of an engine and a voltage signal according to an embodiment of the present invention.

FIG. 4 is a diagram illustrating a relationship between an operating state of an engine and a voltage signal according to an embodiment of the present invention.

FIG. 5 is a diagram showing an electronic control fuel injection device having the electromagnetic fuel injection valve of the present invention.

Figure 6 is a longitudinal sectional view of a reference example of the electromagnetic fuel injection valve having a mists shape varying means

FIG. 7 is an enlarged view of a portion around the orifice 37 in FIG. 6;

8 is a sectional view taken along line AA of FIG. 7;

FIG. 9 is a diagram showing the relationship between the ratio between the axial flow velocity Vo and the radial flow velocity Vm and the injection angle.

Figure 10 is an enlarged view of Roh <br/> nozzle portion in the reference example of inserting the elastic members 41

11 is a diagram showing a deformation state when a voltage is applied to the elastic member 41

12 is a diagram showing the relationship between the voltage signals of the elastic member 41 and the displacement

[13] input signal (voltage signal) and fuel Li - shows the click of relationships

Enlarged view of the nozzle portion showing another reference example of FIG. 14 solenoid type fuel injection valve

FIG. 15 is a sectional view taken along line BB of FIG. 14;

FIG. 16 is a sectional view of a reference example in which a valve body is a spherical valve.

FIG. 17 is a sectional view of a reference example in which a valve body is a pintle valve.

FIG. 18 is a sectional view of a reference example in which the valve body is a needle valve.

FIG. 19 shows an embodiment of an electromagnetic fuel injection valve according to the present invention.
There is an enlarged view of the nozzle part that controls the fuel that does not go through the swirl groove passage

20 is a sectional view taken along line CC of FIG. 19;

[Explanation of symbols]

1 ... input 2 ... control amount 3 ... controller 4.
..Memory 10 ・ ・ ・ Engine 16 ・ ・ ・ Electromagnetic fuel injection valve 34 ・ ・ ・ Ball valve 3
7 ... fuel injection hole 41 ... elastic member 42, 50, 54 ... fuel swirl element 42a, 50a. 54a: axial groove 42b, 50
b, 54b ... radial groove 51 ... spherical valve 52 ... pintle valve 53 ... needle valve 55 ... spring 100 ... control unit

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-3-70863 (JP, A) JP-A-60-95186 (JP, A) JP-A-2-238164 (JP, A) JP-A-60-95186 81273 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) F02M 51/08 F02M 61/04 F02M 61/18 310

Claims (2)

(57) [Claims] A valve that is driven by an electromagnet to open and close a fuel passage between the valve seat, a fuel injection hole, and a nozzle that forms a hollow portion; A fuel swirling element inserted upstream of the valve seat to guide the valve body in the axial direction and form a fuel passage for imparting a swirling force to fuel, the fuel swirling element comprising: A radial passage formed between a lower surface and the inner wall surface of the nozzle opposed to the lower surface of the fuel swirling element, for introducing fuel eccentrically with respect to an axis into a chamber formed by the valve element, the valve seat and the fuel swirling element; An electromagnetic fuel injection valve formed by using an axial passage for supplying fuel to a radial passage, and having means for axially displacing the fuel swirling element. 2. A multi-point electronically controlled fuel injection device for an internal combustion engine having an electromagnetic fuel injection valve for injecting fuel toward an intake valve plate for each cylinder. ,
A valve seat, a fuel injection hole, a nozzle forming a hollow portion, a valve element driven by an electromagnet to open and close a fuel passage between the valve seat, and the valve inserted into the hollow portion of the nozzle. A fuel swirling element that is located upstream of the seat and guides the valve body in the axial direction and forms a fuel passage that imparts a swirling force to the fuel. The fuel is formed between a radial passage formed between the nozzle inner wall surface opposed to the lower surface of the element and introducing fuel eccentrically with respect to an axis into a chamber formed by the valve element, the valve seat, and the fuel swirl element. A displacement means for forming the fuel swirling element in the axial direction, a detection means for detecting an operating state of the engine, and the displacement means using a detection signal of the detection means. Control means for controlling the An internal combustion engine electronic control fuel injection device for displacing in the axial direction of the fuel swirl element in accordance with the operating condition of the engine.