JP2007138746A - Fuel supply device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fuel supply device which achieves both the further optimization of a fuel spray shape and further atomization of a sprayed fuel particle. <P>SOLUTION: A fuel spray valve 100 which can execute two types of fuel spray shown by spray 31 and spray 32 is provided in a combustion chamber 102 of a cylinder injection engine 101. The spray 31 is directed to a cavity 104 at the top of a piston 103. A widening angle of liquid droplets is increased and the fuel spray travel is shortened by enhancing turning force given to the fuel, thereby suppressing attachment onto the top of the piston 103 and implementing atomization of the liquid droplet. On the other hand, the spray 32 is directed to an ignition plug 110. A widening angle of a liquid droplet is suppressed and the fuel spray travel is expanded by weakening the turning force given to the fuel so that ignitable air-fuel mixture can be stably collected around the ignition plug 110. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a fuel supply apparatus for an internal combustion engine that directly injects fuel into a cylinder, and more particularly to a fuel supply apparatus suitable for an in-cylinder injection gasoline engine for automobiles.

  In recent years, in-cylinder injection gasoline engines (hereinafter referred to as in-cylinder injection engines) have been put into practical use as internal combustion engines aimed at low fuel consumption and high output. Depending on the shape, size, etc. of the combustion chamber formed therein, a fuel spray having a shape suitable for each is required in the combustion chamber.

  Therefore, a technique for injecting two types of fuel sprays into a cylinder using a fuel injection valve having a plurality of slit openings serving as fuel injection nozzles has been disclosed (for example, Patent Document 1). reference.).

  Here, in this prior art, the fan-shaped first spray that spreads in the width direction of the combustion chamber and the second spray that spreads in the axial direction of the combustion chamber are injected from the fuel injection valve. A method of forming a fuel spray for in-cylinder injection suitable for combustion is shown.

  In this conventional technique, the shape of the fuel spray formed in the combustion chamber is fan-shaped, so that the penetration force of the spray itself can be increased, and the fuel spray can be easily moved to the vicinity of the spark plug during stratified combustion. Can be moved to.

Further, at the time of homogeneous combustion, the intake air flowing from the intake passage collides with the fuel spray in the intake stroke, but at this time, in the conventional technology, the fuel spray is fan-shaped, so the collision surface can be narrowed, As a result, the degree to which the fuel spray is pushed by the intake air is reduced, and the fuel spray can be effectively moved in the direction of the spark plug, so that ignition is accurate and deterioration of combustion is suppressed.
JP 2003-193940 A

  The above prior art does not give consideration to the increase in the diameter of the spray particles due to the fan spray shape of the fuel spray, and has a problem in deterioration of combustion due to a delay in fuel vaporization.

  In the prior art, since the fuel spray is fan-shaped, the spatial expansion of the spray droplets is suppressed, so that the particle density of the spray increases and particle recombination occurs, resulting in a large particle size. As a result, the time required for fuel vaporization becomes longer, resulting in worsening of combustion. In a severe case, the spark plug is moistened, which may cause smoldering.

  In addition, in a cylinder injection engine, since the time from fuel injection to ignition is short, there is little time allowed for fuel vaporization, and therefore it is necessary to promote evaporation by giving the fuel particles a large surface area, Therefore, in the case of an in-cylinder injection engine, further atomization of the sprayed fuel particles is required, otherwise it is inevitable that the combustion will deteriorate.

  If the combustion deteriorates, the amount of HC (unburned fuel component) and NOx (nitrogen oxide) appearing in the exhaust of the engine increases, and the fuel consumption also deteriorates. Therefore, in the cylinder injection engine, optimization of the fuel spray shape and atomization of the sprayed fuel particles are required, but the prior art cannot sufficiently meet these requirements.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a fuel supply device that can achieve both further optimization of the fuel spray shape and further atomization of the sprayed fuel particles. It is in.

  An object of the present invention is to provide a fuel supply device for an internal combustion engine in which fuel is directly injected into a cylinder from a fuel injection valve and ignited by a spark plug, and at least a first and a plurality of fuel spray openings in the fuel injection valve. The fuel spray injected from the first fuel injection opening is extended in reach by the narrowing control of the spread angle, and the injection direction is directed in the spark plug direction in the cylinder, The fuel spray injected from the second fuel injection opening is shortened by a spread angle widening control, and the injection direction is directed toward the concave cavity provided in the piston in the cylinder. Is achieved.

  At this time, the fuel injection valve includes a valve body that can be opened and closed to perform fuel injection and injection stop, a seat portion that is in close contact with the valve body and stops fuel injection, and a passage cross-sectional area. A fuel passage forming plate in which at least two different fuel passage portions are formed, and an injection hole having at least a first injection opening and a second injection opening having a desired inclination angle in the plate thickness direction The fuel passage forming plate is in close contact with the downstream side of the fuel introduction hole of the seat portion, and the injection hole plate is in close contact with the downstream side of the fuel passage forming plate. The objective is achieved.

  Further, at this time, the fuel passage forming plate is configured by a swirl plate, and the swirl force applied by the swirl plate to the fuel injected from the first injection opening is set to be weak. The spread angle of the spray is widened by setting the swirl force applied by the swirl plate to the fuel injected from the second injection opening. Even if control is given, the above object is achieved.

  Here, if it demonstrates according to embodiment, in the present invention, the following composition is mainly adopted.

  First, in the present invention, a fuel supply device for a direct injection internal combustion engine that directly injects fuel into the combustion chamber of the internal combustion engine, the opening of the fuel supply device is directed to the combustion chamber under the intake valve. A first injection opening directed in the direction of the spark plug and a second injection opening directed in the direction of the recessed cavity provided in the piston, and spray from the first injection opening Makes the air-fuel mixture accurately reach the spark plug by narrowing its spread and increasing its reach, while the spray from the second injection opening has a wide spread and shortens its reach Thus, the fuel adhesion to the piston concave surface is suppressed.

  Next, similarly, in the present invention, a fuel supply device for a direct injection internal combustion engine that directly injects fuel into a combustion chamber of the internal combustion engine, the fuel supply device for injecting fuel and stopping injection It has a valve body that can be opened and closed, and a seat portion that can be brought into close contact with the valve body to stop fuel injection, and includes a plurality of injection holes for injecting fuel downstream of the valve body and the seat portion. A fuel supply device for forming a fuel passage, wherein at least two fuel passage portions having different passage cross-sectional areas are formed in a recess expansion chamber downstream of a fuel introduction hole having a diameter reduced from the seat portion. A plate is inserted and fixed, and an injection hole plate having at least a first injection opening and a second injection opening having a desired inclination angle in the thickness direction is inserted and fixed following the fuel passage forming plate. Yes.

  At this time, a swirl type that imparts a swirl force to the fuel is used as the fuel supply device of the direct injection internal combustion engine, and the swirl force of the fuel injected from the first injection opening of the fuel supply device is set to be weak. Thus, the spread of the spray is narrow and the reach distance is lengthened, the turning force of the fuel injected from the second injection opening is set strong, the spread of the spray is wide and the reach distance is shortened.

  As a result, the fuel spray injected from the first injection opening has a short reach distance even when the combustion chamber is in the compression stroke (under a pressurized atmosphere), but the injection direction does not change. On the other hand, when the combustion chamber is in the intake stroke (atmospheric pressure or less) state, the fuel spray injected from the second injection opening has a short reach and promotes atomization. Fuel sticking to is avoided.

  Also, when the combustion chamber is in the compression stroke state, the fuel spray shrinks (condenses) into a compact (smallly packed) shaped spray (spray with a narrow spread and a short reach), so it is provided on the piston. The fuel adheres to other than the recessed cavity formed.

  According to the present invention, the direction of the first fuel spray injected from the fuel injection valve of the in-cylinder engine does not change depending on the pressure condition in the combustion chamber even if the arrival distance changes. Ignition combustion to the air-fuel mixture by the first fuel spray directed to the plug is stably performed.

  In addition, the second fuel spray has a short reach and promotes atomization during the intake stroke when the pressure in the combustion chamber decreases, and forms an air-fuel mixture with no fuel adhering to the piston top surface or cylinder inner wall surface. Combustion is performed.

  In addition, even during the compression stroke when the pressure in the combustion chamber rises, the fuel spray shrinks into a compact shaped spray, so that fuel adhesion to areas other than the recessed cavity provided in the piston is avoided, and efficient combustion is achieved. To be implemented.

  Therefore, according to the present invention, it is possible to provide a fuel supply device for an in-cylinder injection engine that is beneficial in terms of both fuel efficiency and exhaust gas purification performance.

  Hereinafter, the fuel supply device according to the present invention will be described in detail with reference to the illustrated embodiments. First, FIG. 1 is an example of an in-cylinder injection engine to which an embodiment of the present invention is applied. The reference numeral 101 represents the entire cylinder injection engine. In this figure, when the engine is in the intake stroke and fuel is injected in a state where the piston indicated by reference numeral 103 is located in the vicinity of the bottom dead center (BDC), so-called intake stroke injection is performed. One cylinder in the engine is shown as a cross-sectional view.

  Here, first, a reference numeral 100 is a fuel injection valve, which is provided in the downstream portion of the intake port 108 of the cylinder 105, and its injection opening is opened toward the piston 103 in the combustion chamber 102. Yes. At this time, a concave cavity 104 is formed in the head (top) of the piston 103. Reference numeral 106 denotes a cylinder head, which is provided with an intake valve 107, an exhaust valve 109, a spark plug 110, an intake passage 111, and the like.

  Although not shown in FIG. 1, the in-cylinder injection engine 101 is a so-called four-valve system, and therefore, the intake valve 107 and the intake port 108 are arranged side by side in a direction perpendicular to the drawing sheet. The fuel injection valve 100 is provided in the cylinder 105 so as to be positioned between the two intake valves 107. For this reason, the intake passage 111 is provided with a central partition for separating the two intake ports 108.

  In this embodiment, two types of sprays 31 and 32 are injected from the fuel injection valve 100 into the combustion chamber 102 as shown in the drawing in order to improve the quality and formation of the air-fuel mixture in the cylinder 105. It has come to be. At this time, both the spray 31 and the spray 32 have an increased degree of atomization.

  At this time, first, the spray 31 is injected toward the cavity 104 of the piston 103, and the spray 31 has a fuel particle reaching distance shortened by a method described later. Therefore, the adhesion of fuel to the top surface of the piston 103 is suppressed.

  Next, the spraying direction and shape of the spray 32 are optimized so that the fuel particles are directed in the direction of the spark plug 110 while suppressing the adhesion of fuel to the inner wall surfaces of the cylinder head 106 and the intake valve 107. . In this case, the spread of the spray 32 is narrowed and the reach distance is lengthened so that an ignitable air-fuel mixture is stably collected around the spark plug 110.

  Next, FIG. 2 shows the same in-cylinder injection engine 101 when the engine is in the compression stroke and the fuel is injected in a state where the piston 103 is located near the top dead center (TDC). One cylinder in the engine at that time is shown as a cross-sectional view. At this time, the inside of the cylinder 105 is pressurized to about several atmospheres.

  However, even at this time, the spread of the spray 31a is suppressed, and the reach distance is also suppressed, so that remarkable fuel adhesion to the piston top surface is suppressed. In addition, at this time, the fuel spray that has reached the cavity 104 of the piston 103 is deflected in the direction of the spark plug 110 along the curvature of the recess of the cavity 104, so that an air-fuel mixture that can be ignited is collected around the spark plug 110. Has been.

  The spray 32a also has a short reach at this time. However, as shown in the drawing, the spray 32a is also directed toward the spark plug 110 so that stable ignition can be obtained.

  Here, the sprays 31, 31 a, 32, and 32 a shown in FIGS. 1 and 2 are injected from the fuel injection valve 100. Therefore, next, the fuel injection valve 100 will be described in detail. This is a swirl type fuel injection valve that injects fuel by applying a swirling force. For this reason, the fuel injection valve 100 is shown in FIG. Based on the characteristics and the characteristics shown in FIG. 4, the swirl characteristics of the fuel are appropriately selected and set so that the required spray performance can be obtained.

  First, FIG. 3 is a characteristic diagram showing the relationship of the spray angle to the swirl strength of the fuel. At this time, the solid line in the figure is the characteristic under atmospheric pressure, and the broken line is the characteristic under pressure. Each of them has a property of increasing according to the turning force, but the sensitivity to the pressure change is smaller in the region where the turning force is weaker.

  Next, FIG. 4 is a characteristic diagram showing the relationship of the spray reach distance with respect to the swirl strength of the fuel. Here, the broken line is the characteristic under atmospheric pressure, the solid line is the characteristic under pressure, and in the case of FIG. On the other hand, the reach distance has the property of decreasing according to the turning force. On the other hand, the sensitivity to the pressure change is similarly smaller in the region where the turning force is weaker.

  FIG. 5 schematically shows sprays 31, 31a, 32, and 32a based on a spray photograph obtained by taking a stroboscopic image of the spray with a xenon lamp or a laser. Here, first, FIG. (a) shows the case where the spray is carried out under atmospheric pressure. At this time, the spray 31 is found to be a wide-angle spray with the droplets spreading widely as a result of increasing the turning force, while the spray 32 is Since the swirl force is weakened, the spread of the droplet is small and it can be seen that the penetrating force is increased accordingly.

  Next, (b) in FIG. 5 shows a case where the spray is injected under pressure. At this time, the spray 31a is compacted by shrinking the spray having a wide angle due to an increase in the pressure of the injected atmosphere. Thus, it can be seen that the reaching distance is suppressed, and on the other hand, the spray 32a has little difference in pressure between the inside and outside, so that almost no change in the spread is seen even under pressure, and the reaching distance is slightly suppressed. It turns out that it is only done.

  The event at this time will be described in more detail. In the case of a narrow-angle spray with a small spread, the particle density of the droplets becomes high, so that the ingress of air from the periphery of the spray is suppressed, and the spray droplets accordingly. Does not replace the kinetic energy possessed by the surrounding air, and as a result, the energy of the droplet is maintained, and therefore the droplet will fly further.

  At this time, when looking at the injection direction θ1 under atmospheric pressure in FIG. 5A and the injection direction θ2 under pressure in FIG. 5B, neither of these changes. Therefore, it can be seen that the change in the atmospheric pressure does not affect the injection direction.

  Here, in FIGS. 3 and 4, the spray with a weak turning force corresponds to the sprays 32 and 32a injected in the angle θ1 direction, and the spray with a strong turning force is the sprays 31 and 31a injected in the angle θ2 direction. It corresponds to. The inclination of the sprays 32 and 32a in the direction of the angle θ1 is to make these sprays go in the direction of the spark plug 110. The inclination of the sprays 31 and 31a in the direction of the angle θ2 This is because the angles θ1 and θ2 of the inclinations are determined depending on the layout of the fuel injection valve 100 and the engine.

  Here, when a combustion test was performed on the internal combustion engine to which the present invention was applied, the exhaust gas performance and the fuel consumption were improved. Therefore, the fuel injection onto the inner wall surface of the intake pipe was caused by the spray of the fuel injection valve 100. As a result, it was confirmed that the quality of the air-fuel mixture and the formation state were improved.

  In this embodiment, the spray 31 (31a) is a symmetric spray with the same reach distance on the left and right with respect to the central axis of the fuel injection valve 100. Different so-called deflected sprays may be used. In this case, the reach distance on the piston side may be shortened or the spray density may be reduced.

  Next, in this embodiment, the fuel injection valve 100 used to form the sprays 31, 31a, 32, 32a in the combustion chamber 102 will be described in detail. First, in the cross-sectional view of FIG. As shown in detail in FIG. 7, the nozzle 13 of the fuel injection valve 100 guides the tip of the valve body 9 by the valve body 9 and the inner peripheral surface 22 at the lower end portion of the fuel injection valve 100. A ring-shaped fuel passage member 14 that functions to form a passage and a nozzle plate 1 are provided. The outer periphery of the nozzle plate 1 is fixed to the nozzle 13 by means such as welding 23.

  Here, the valve body 9 is guided to slide by a hole provided in the central portion of the guide plate 15 and the inner peripheral surface 22 of the fuel passage member 14, and is held so as to be movable in the vertical direction in the figure. And this valve body 9 is couple | bonded with the movable iron core 7 via the cylindrical member 8 by means, such as welding. At this time, the movable iron core 7, the cylindrical member 8, and the valve body 9 as a whole form the movable valve portion 6.

  At this time, a damper plate 10 is provided inside the movable iron core 7 and is supported by the upper end surface of the cylindrical member 8. A cylindrical guide member 12 is provided on the damper plate 10 so as to pass through the movable iron core 7 and the inner fixed iron core 11, so that the movable iron core 7 is axially oriented with respect to the inner fixed iron core 11. And is slidably supported.

  At this time, the lower end of the guide member 12 in the drawing is in contact with the central portion of the damper plate 10. Therefore, since the outer peripheral portion of the damper plate 10 is supported by the cylindrical member 8, the inner peripheral portion functions as a leaf spring when the inner peripheral portion bends in the axial direction, and functions as a damper.

  Here, the nozzle 13 is inserted and fixed in a cylindrical nozzle housing 16, and a ring 17 that functions as an adjustment piece for adjusting the stroke of the valve body 9 is inserted in the upper end portion thereof. . A spring pin 20 is inserted into the inner fixed iron core 11, and the spring 21 is compressed and inserted into the inner fixed iron core 11 with the lower end of the spring pin 20 as a fixed end.

  The elastic force generated by the spring 21 at this time is transmitted from the guide member 12 to the valve body 9 via the damper plate 10, whereby the valve body 9 is set in advance in the valve seat 4 of the nozzle plate 1 as the spring 21. It is pressed by elastic force and is in a closed state. In this closed state, the fuel introduction hole 3 of the nozzle plate 1 is closed, so that the fuel remains inside the fuel injection valve 100 and fuel injection is not performed.

  At this time, an electromagnetic coil 19 is provided in the outer fixed iron core 18 so as to be wound around the outer side of the inner fixed iron core 11. Therefore, a magnetic circuit is formed by the nozzle housing 16, the movable iron core 7, the inner fixed iron core 11, and the outer fixed iron core 18 around the electromagnetic coil 19.

  Therefore, when an injection pulse generated by a fuel supply control unit (not shown) is turned on and the electromagnetic coil 19 is energized, a magnetic field is generated, and the movable iron core 7 is attracted to the inner fixed iron core 11 by the electromagnetic force. Therefore, the valve body 9 is moved against the elasticity of the spring 21, and the upper end surface thereof moves to a position where it comes into contact with the lower end surface of the inner fixed iron core 11, thereby opening the valve.

  In this open state, the valve element 9 is separated from the valve seat 2, so that a gap appears between them and the fuel passage hole 3 is opened, so that the fuel flows from the swirl plate 4 to the orifice plate 5, When the fuel is injected from the injection holes 29 and 30 and the injection pulse is turned off, no current flows through the electromagnetic coil 19 and the electromagnetic force disappears. Therefore, the valve element 9 is closed by the elasticity of the spring 21. Returning to the state, fuel injection is stopped.

  As described above, the function of the fuel injection valve 100 is to switch the position of the valve body 9 between the valve opening state and the valve closing state in accordance with the injection pulse, and to control the fuel supply amount and the supply timing. Further, in the fuel injection valve 100, by injecting fuel from the plurality of fuel injection holes 29, 30, the above-described two types of sprays 31 (31a), 32 (32a) are produced, and these sprays 31 ( 31a) and 32 (32a) serve to form a spray having a small droplet diameter, that is, a fuel spray with good atomization.

  Returning to FIG. 7, here, the nozzle plate 1, the swirl plate 4, and the orifice plate 5, which are the main portions of the fuel injection valve 100, are shown at the tip of the nozzle 13 (the lower end in this figure). And in this figure, the state which the valve body 9 is lifting upwards, ie, the valve opening state, is shown.

  As shown in the drawing, a fuel passage member 14, a nozzle plate 1, a swirl plate 4, and an orifice plate 5 are inserted into the lower end portion of the nozzle 13 in this order. The outer peripheral edge of the nozzle plate 1 is fixed to the nozzle 13 by means such as welding 23 as described above.

  At this time, the nozzle plate 1 has a conical valve seat 2, a fuel introduction hole 3 with a reduced diameter (reduced diameter), and a disk connected downstream of the fuel introduction hole 3. An enlarged-diameter portion made of a concave portion is formed. And the swirl plate 4 and the orifice plate 5 are inserted in this enlarged diameter part, and are fixed by the outer periphery part by means, such as welding 24. FIG.

  Here, the fuel passes through the lower passage from the outer peripheral passage of the fuel passage member 14 to the fuel introduction hole 3 of the nozzle plate 1 and flows into the orifice plate 5 further downstream through the swirl plate 4. The fuel injection holes 29 and 30 are opened, and the fuel is injected after its shape is controlled in a desired direction.

  Here, FIG. 8 shows a state in which the swirl plate 4 and the orifice plate 5 are combined, and FIG. 9 is a view of FIG. 8 viewed from the direction of arrow A. As shown in FIG. The swirl plate 4 includes a fuel passage 25 having a width W1, a swirl chamber 26 having a relatively large diameter D1 communicating with the fuel passage 25, and a fuel passage 27 having a width W2 and a relatively communicating passage therewith. A swirl chamber 28 having a small diameter D2 is provided.

  The orifice plate 5 is provided with fuel injection holes 29 and 30 communicating with the swirl chambers 26 and 27, respectively. At this time, first, the fuel injection hole 29 is connected to the fuel passage 25 having the width W1. The fuel injection hole 30 is opened at a position shifted by the offset L2 with respect to the fuel passage 27 having the width W2, and is formed with a desired inclination angle. Yes.

  With such an arrangement, the fuel injection holes 29 and the fuel injection valves 30 can be supplied with fuels having different turning forces, respectively, and as a result, each can obtain a spray controlled to have a desired shape. Control and narrowing control can be provided, and directivity control in the flight direction in which the fuel is injected in a desired direction can be provided, and as described above, injection useful for combustion of the internal combustion engine can be obtained.

  At this time, as for the setting of the number of fuel injection holes, as a result of various examinations from the viewpoint of processing surface and spray performance, in the above embodiment, the two fuel injection holes 29 and 30 are selected as the optimum design values. The number of the pistons 103 can be changed depending on the cavity shape or the like. In this case, the number of fuel passages can be easily increased.

  Next, the injection mode in the fuel injection valve 100 having the nozzle configuration as described above will be described in detail. When the valve is open, the fuel flows from the fuel introduction hole 3 with a reduced diameter and flows into the swirl plate 4. After that, the fuel flow is divided into the fuel passage 25 and the fuel passage 27 in different directions, and flows into the respective fuel injection holes 29 and 30 formed in the orifice plate 5 from the respective fuel swirl chambers 26 and 28.

  At this time, the fuel diverted into the fuel passage 25 and flows into the fuel swirl chamber 26 is given a sufficient swirl force because the fuel swirl chamber 26 has a large diameter D1 and a large offset L1, and as a result, fuel injection From the hole 29, a spray 31 (31a) having a wide angle, a short reach, and good atomization can be obtained.

  On the other hand, the fuel diverted into the fuel passage 27 and flows into the fuel swirl chamber 28 is given only a slight swirl force because the fuel swirl chamber 28 has a small diameter D2 and a small offset L21. From the hole 30, a spray 32 (32 a) having a narrow angle, a long reach, and a strong penetrating force is obtained.

  At this time, the spray 31 (31a) having a wide angle, a short reach, and good atomization is directed toward the piston 103 as described with reference to FIGS. Therefore, the adhesion of fuel to the top surface of the piston 103 can be effectively suppressed.

  On the other hand, the spray 32 (32a) having a narrow angle, a long reach, and a strong penetrating force is directed toward the spark plug 110. For this reason, the combustible air-fuel mixture which can be ignited around the plug can be effectively formed.

At this time, the swirl force applied to the fuel injected by the swirl plate 4 and the orifice plate 5 includes the thickness H of the swirl plate 4 and the thickness S of the orifice plate 5, and the diameters d ₂₉ and d _{30 of the} fuel injection holes ₂₉ and _30. Since it can be arbitrarily determined by selecting the above dimensions L1, L2, D1, D2, W1, W2 and the distance L3 from the nozzle center of each fuel injection hole 29, 30, it is required for the fuel injection valve 100. It is easy to meet the characteristics.

  Therefore, according to this embodiment, since the combustion stability is improved, it is possible to give a degree of freedom in setting the ignition timing and the injection timing, and it is possible to perform ignition at a timing with higher thermal efficiency. And by this improvement in combustion efficiency, both improvement in fuel consumption and suppression of exhaust deterioration can be achieved.

  Further, if the stability of combustion is improved in this way, effective combustion can be performed over a wide range of engine load and rotation speed, so that further improvement in fuel consumption and suppression of exhaust deterioration can be achieved. Can do.

1 is a cross-sectional view showing an example of a direct injection internal combustion engine to which an embodiment of a fuel supply device according to the present invention is applied. 1 is a cross-sectional view showing an example of a direct injection internal combustion engine to which an embodiment of a fuel supply device according to the present invention is applied. It is a characteristic view for demonstrating the spray characteristic of a fuel injection valve. It is a characteristic view for demonstrating the spray characteristic of a fuel injection valve. It is a schematic diagram which shows an example of the spray injected from the fuel injection valve by one Embodiment of the fuel supply apparatus by this invention. It is sectional drawing which shows an example of the fuel injection valve currently used in one Embodiment of this invention. It is the elements on larger scale in an example of the fuel injection valve currently used in one Embodiment of this invention. It is an enlarged view which shows the relative positional relationship of the swirl plate and orifice plate which forms a fuel injection hole in an example of the fuel injection valve used in one Embodiment of this invention. It is explanatory drawing of the swirl plate in an example of the fuel injection valve currently used in one Embodiment of this invention.

Explanation of symbols

1: Nozzle plate 2: Valve seat 3: Fuel introduction hole 4: Swirl plate 5: Orifice plate 6: Movable valve part 7: Movable iron core 8: Tubular member 8
9: Valve body 10: Damper plate 11: Inner fixed iron core 12: Guide member 13: Nozzle 14: Fuel passage member 19: Electromagnetic coil 25, 27: Fuel passage 26, 28: Fuel swirl chamber 29, 30: Fuel injection hole 31, 31a: Spray toward the piston recess 32, 32a: Spray toward the spark plug 100: Fuel injection valve 101: In-cylinder injection engine (in-cylinder injection internal combustion engine)
102: Combustion chamber 103: Piston 104: Cavity 105: Cylinder 106: Cylinder head 107: Intake valve 108: Intake port 109: Exhaust valve 110: Spark plug 111: Intake passage (intake manifold)

Claims (3)

In a fuel supply device for an internal combustion engine in which fuel is directly injected into a cylinder from a fuel injection valve and ignited by a spark plug,
Providing at least first and second plurality of fuel spray openings in the fuel injection valve;
The fuel spray injected from the first fuel injection opening is extended in reach by the narrowing control of the spread angle, and the injection direction is directed toward the spark plug in the cylinder,
The reach of the fuel spray injected from the second fuel injection opening is shortened by the widening control of the spread angle, and the injection direction is directed toward the concave cavity provided in the piston in the cylinder. A fuel supply device for an internal combustion engine. The fuel supply device according to claim 1,
The fuel injection valve is
A valve body that can be opened and closed to inject and stop fuel injection;
A seat for closely contacting the valve body to stop fuel injection;
A fuel passage forming plate in which at least two fuel passage portions each having a different passage cross-sectional area are formed;
An injection hole plate having at least a first injection opening and a second injection opening having a desired inclination angle in the plate thickness direction;
The fuel supply of the internal combustion engine, wherein the fuel passage forming plate is in close contact with the downstream side of the fuel introduction hole of the seat portion, and the injection hole plate is in close contact with the downstream side of the fuel passage forming plate. apparatus. The fuel supply device according to claim 2,
The fuel passage forming plate is composed of a swirl plate,
By setting the swirl force applied by the swirl plate to the fuel injected from the first injection opening to be weak, the spray spread angle is controlled to be narrowed, and the second injection opening A fuel supply device for an internal combustion engine, characterized in that a widening control of the spread angle of the spray is given by strongly setting a turning force applied by the swirl plate to the fuel injected from the section.

Images