JPH01159460A - Electromagnetic fuel injection valve - Google Patents

Abstract

PURPOSE:To convert pressurized fuel into a swirl one without incurring a loss as well as to secure a good atomizing characteristic all the time by specifying a ring clearance between a ball valve being formed at the time of lift of the ball valve, spraying the fuel swirled by a fuel swirl element, and a valve seat. CONSTITUTION:When a coil 15 is energized with current, a magnetic circuit is constituted by a core 2, a yoke 3 and a plunger 4, and this plunger 4 is attracted to the side of the core 2. With this magnetic attraction, a ball valve 6 is also solidly moved and comes off a valve seat 9, opening a fuel injection nozzle 8. If so, pressurized fuel passes through a lower passage 23, an outer circumference of the plunger 4, grooves 49, 50 of a fuel swirl element 37 and so on, and it is swirlingly supplied and thus sprayed out of a fuel injection valve 8. In an injection valve like this, when a groove area of the fuel swirl element 37 is set to A1, a ring clearance area at a stroke of a movable part 4A inclusive of the plunger 4 to A2 and a sectional area of the fuel injection nozzle 8 to AS, respectively, a ring clearance area A is set so as to satisfy a relationship of A1>A2>AS.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to an electromagnetic fuel injection valve for internal combustion engines, which does not particularly require static flow rate adjustment, has extremely good productivity, and has excellent atomization characteristics. Regarding electromagnetic fuel injection valves with excellent performance.

[Conventional technology]

In the conventional device, as described in Japanese Patent Application Laid-Open No. 56-75955, a swirl plate is provided in the housing, which has a guide hole for storing the balls and a swirl passage for introducing fuel into the guide hole from a direction substantially tangential to the guide hole. This configuration was supposed to improve fuel atomization.

[Problem to be solved by the invention]

The above-mentioned conventional technology does not take into account the fact that when pressurized fuel passes through the swirl passage and the four fuel passage holes that communicate with the swirl passage, it is converted into sufficient swirl velocity energy without loss. There was a problem in that the fuel could not be atomized efficiently.

SUMMARY OF THE INVENTION An object of the present invention is to provide an electromagnetic fuel injection valve that can convert pressurized fuel into swirling fuel without loss and inject fuel with excellent atomization characteristics.

[Means to solve the problem]

The first feature of the present invention for achieving the above object is that a fuel swirling element is provided upstream of the valve seat and applies swirling force to the supplied fuel, and a fuel swirling element is provided downstream of the valve seat. comprising a fuel injection hole and a ball valve that injects fuel to which a swirling force is applied by the fuel swirling element from the fuel injection hole,
In an electromagnetic fuel injection valve that controls the amount of fuel injected by controlling the opening/closing time of the ball valve, the area of an annular gap formed by the ball valve and the valve seat when the ball valve is lifted. is made smaller than the groove cross-sectional area of the fuel swirling element and larger than the cross-sectional area of the fuel injection hole.

The second feature of the present invention is that the fuel swirling element is disposed upstream of the valve seat and applies a swirling force to the supplied fuel; the fuel injection hole is disposed downstream of the valve seat; An electromagnetic fuel injection system comprising a ball valve that intermittently injects fuel to which a swirling force is applied by a fuel swirling element from the fuel injection hole, and controlling the amount of fuel injected by controlling the opening/closing time of the ball valve. In the valve, the cross-sectional area of the flow path from the inlet of the fuel swirling element to the outlet of the fuel injection hole is configured to continuously decrease.

Furthermore, a third feature of the present invention is a fuel swirling element disposed upstream of the valve seat and applying swirling force to the supplied fuel;
A fuel injection hole provided on the downstream side of a valve seat, and a ball valve that injects fuel to which a swirling force is applied by the fuel swirling element from the fuel injection hole, and the opening/closing time of the ball valve is controlled. In an electromagnetic fuel injection valve that controls the amount of fuel injected by It has a radial groove that introduces eccentricity from the center of the shaft.

Furthermore, a fourth feature of the present invention is a fuel swirling element disposed upstream of the valve seat and giving swirling force to the supplied fuel, a fuel injection hole disposed downstream of the valve seat, and a valve body. A ball valve that slides in the axial direction of the ball valve and injects fuel to which a swirling force is applied by the fuel swirling element from the fuel injection hole, and a means for controlling the opening and closing time of the ball valve with a stroke that maintains a constant flow rate. The reason is that it has been prepared with the following.

Furthermore, a fifth feature of the present invention is a plurality of notches disposed upstream of the valve seat to which fuel is supplied, a fuel reservoir communicating with the notches, and a fuel reservoir communicating with the fuel reservoir; A fuel swirling element having a radial groove for introducing fuel eccentrically from the axial center of the valve body, a fuel injection hole provided on the downstream side of the valve seat, and a fuel swirling force applied by the fuel swirling element to the fuel The present invention includes a ball valve that injects fuel from an injection hole, and controls the amount of fuel injected by controlling the opening/closing time of the ball valve.

[Operation] The fuel swirling element controls the fuel flow toward the subaxial force through the rapidly expanding hole of the nozzle body, the radial fuel flow toward the valve seat and the fuel injection hole, and the loss thereof. Fuel pressurized by the fuel swirling element and given swirling force flows through the annular gap formed by the ball and valve seat, which is narrower than the flow path of the fuel swirling element, and is further injected through the fuel injection hole with a small cross-sectional area. be done. Therefore, pressurized fuel can be efficiently exchanged into swirl velocity energy and guided to the fuel injection hole.
The fuel can be injected and supplied from the fuel injection hole with sufficient swirling force.

〔Example〕

An embodiment of the present invention will be described below with reference to FIGS. 1 to 9. The structure and operation of an electromagnetic fuel injection valve (hereinafter referred to as ``injection valve'') 1 will be explained with reference to FIG. The injection valve 1 injects fuel by opening and closing a seat portion in response to a duty ON-OFF signal calculated by a control unit (not shown). The magnetic circuit consists of a bottomed cylindrical yoke 3. A plug body part 2a that closes the entrance end of the yoke 3 and a columnar part 2 that extends to the center of the yoke 3
The plunger 4 is composed of a core 2 consisting of a core 2 and a plunger 4 facing the core 2 with a gap in between. A spring 10 is inserted into the center of the columnar part 2a of the core 2 as an elastic member that presses the movable part 4A consisting of the plunger 4, rod 5, and ball valve 6 against the seat surface 9 of the orifice 8 formed in the valve guide 7. It has a hole to hold it in place. The upper end of the spring 10 is in contact with the lower end of a spring adjuster 11 inserted through the center of the core 2 in order to adjust the set load. An O-ring 12 is provided between the core 2 and the adjuster 11 to prevent fuel from flowing out from the gap between the core 2 and the adjuster 11. Furthermore, an O-ring 13 is interposed between the core 2 and the yoke 3 to prevent fuel from flowing out from the gap between the core 2 and the yoke 3. A coil 15 for exciting a magnetic circuit is wound around a bobbin 14, and the outside thereof is molded with a plastic material. A terminal 18 of a coil assembly 16 made up of these is inserted into a hole 17 provided in the collar of the core 2, and an O-ring 19 is interposed between the terminal 18 and the core 2. A collar 20 is placed over the entrance of the hole 17 to prevent the mold resin 19a on the outside of the injection valve 1 (hereinafter referred to as yoke mold) from entering the inside of the injection valve 1 during molding. A gap 21 between the core 2 and the core 2 serves as a passage for fuel and fuel vapor. Upper passage 22. A lower passage 23 is provided.

An annular groove 25 is formed on the outer periphery of the yoke 3, and an O-ring 24 is held therein to prevent fuel from flowing out from a gap between the injection valve 1 and a socket (not shown) serving as a housing. An inflow passage 26 through which fuel flows and an outflow passage 27 through which excess fuel including air bubbles accumulated in the injection valve 1 flows out are opened around the yoke 3. Further, a plunger receiving portion 28 for receiving the movable portion 4A is opened in the bottomed portion of the yoke 3, and a valve guide receiving portion having a diameter larger than the diameter of the plunger receiving portion 28 and receiving the stopper 29 and the valve guide 7 therein. 30 is provided through the yoke up to the tip of the yoke. Further, a fuel inflow passage 2 is provided on the outer periphery of the yoke 3.
Fuel is running from 6.

An annular filter 31 is provided to prevent dust and foreign matter in the piping from entering the valve seat side. A terminal 32 for transmitting signals from the control unit to the coil 15 is connected to the terminal 18. The two-way terminal 32 is molded onto the upper end of the solenoid valve assembly using molding resin to form a molded connector 33. The movable part 4A consists of a plunger 4 made of magnetic material, a rod 5 whose one end is joined to the plunger 4, a ball joined to the other end of the rod 5, and a non-magnetic material fixed to the upper end opening of the plunger 4. Guide ring 3
It is composed of 4. The guide ring 34 is an inner wall 35 of a hollow portion opened at the tip of the core 2, and the ball valve 6 is an inner peripheral surface 38 of a cylindrical fuel swirling element 37 inserted into an inner wall 36 of a hollow portion of the valve guide 7. , a seat surface 9 for seating the ball valve 6 is formed on each of the valve guides 7 guided by the valve guides 7, which is continuous with the cylindrical fuel swirling element 37 that guides the ball valve 6, and the center of the seat surface 9 is A fuel injection hole 8 is provided in the fuel injection hole 8 . The valve guide 7 is further formed with a cylindrical portion 39 extending in a direction opposite to the seat surface 9.

An O-ring 40 for sealing fuel is interposed between the socket (not shown) and the outer peripheral surface of the valve guide 7. In the embodiment, an O-ring receiving portion 41 is formed as an annular groove on the outer periphery of the valve guide 7.

The method of assembling the injection valve and the method of adjusting the flow rate will be explained below. First, a method of assembling the electromagnet section will be explained. After attaching the O-ring 19 to the terminal 18 portion of the coil assembly 16, the terminal 18 is inserted into the hole 17 in the collar portion of the core 2, and then the collar 20 is inserted from above the terminal 18. Thereafter, an O-ring 13 is attached to the lower circumference of the plug portion of the core and inserted into the yoke 3.

In this state, the core abutting surface 42 on the upper edge of the inner periphery of the yoke 3 is pressed in the axial direction, and the material of the yoke 3 is poured radially into the groove 43 provided on the outer periphery of the plug portion of the core 2 by plastic flow, thereby tightening the material. Fix with force. Perform the so-called metal flow.

The movable part connects the ball valve 6 to the inner wall surface 3 of the fuel swirling element 37.
8, the non-magnetic ring 34 is guided by the tip inner wall surface 35 of the core 2, and in the end, the valve guide assembly housing portion 30 of the yoke 3 is guided at two places to advance and retreat in the axial direction.
It is important that the coaxiality between the inner diameter of the core 2 and the inner wall surface 35 of the core 2 is accurately obtained. Therefore, the receiving part 30 of the valve guide 7
Metal flow is performed while accurately supporting the inner diameter of the core 2 and the inner wall surface 35 of the core 2. Then, the terminal 32 is attached to the terminal 18.
The first step is to assemble the valve guide assembly, which is fixed by caulking, soldering, welding, etc., and then molded with resin. The valve guide is
It consists of a movable part 4A, a fuel swirling element 37, and a valve guide 7. In the movable part 4A, the ball valve 6 and the rod 5 made of quench-hardened stainless steel are welded together by resistance welding, laser welding, or the like.

Next, the other end of the rod 5 and the plunger 4 are connected to the plunger 4 by a metal flow in a groove 44 provided on the outer periphery of the rod 5.
It is fixed by fluid pressure bonding the inner wall of. In addition, the guide ring 34 and the plunger 4 are connected by pressing the guide ring abutting portion 46 on the inner circumferential edge of the tip of the plunger 4 in the axial direction by pressing the ball valve side surface 45 of the plunger 4 in the axial direction. This can be done with metal flow by applying a radial tension force.

The fuel swirl element 37 is formed into a cylindrical shape using a sintered alloy, and is fixed to the inner wall surface 36 of the valve guide 7 by pressure.

That is, the outer circumferential surface 47 (at four locations) of the fuel swirl element 37 is fluidly pressed into the groove 48 of the valve guide 7 by metal flow. (Figure 2 and Figure 3 when looking at Figure 2 from direction A)
In this embodiment, a method of crimping and fixing with metal flow will be described as described above, but the function can be equally satisfied even if the fuel swirling element 37 is fixed from the direction A shown in FIG. 2 using an elastic member. can.

The fuel swirl rope 37 has an axial groove 49 and a radial groove 50.
is the provision. In this embodiment, the axial groove 49 forms a D-cut surface. These grooves 49° and 50 are fuel passages introduced from the axial direction, but the fuel that has passed through the grooves 49 flows into the grooves 50.
Eccentricity is introduced from the center of the shaft. A swirling force is applied to all types of fuel, which serves to promote atomization when ejected from the fuel injection hole 8 of the outlet orifice provided in the valve guide 7.

Here, the fuel swirl element 37 is designed and manufactured with the following considerations in mind, and is crimped and fixed to the inner wall surface 36 of the valve guide 7.

Factors that affect the static flow rate of fuel include the pressure drop in the flow path of the fuel swirling element 37 and the swirling force applied. The pressure loss in the flow path is mainly controlled by the cross-sectional area of the groove. The cross-sectional shape of the radial groove 50 in this embodiment is shown in FIG.
-B cross-sectional view). Using the flow equivalent diameter represented by the width W of the groove and the depth H of the groove in FIG. 4, the cross-sectional area A1 becomes as follows, where n is the number of grooves.

The cross-sectional area A1 is the cross-sectional area A3AB of the fuel injection hole 8 = d
” ...Ratio to (2) σ=
The dimensions are determined so that A 1 /A s is 1.5 x σ<6.5, and the design is such that pressure loss is prevented as much as possible. The experimental results of the authors are shown in Figures 5 and 6, which prove that the influence of loss is extremely small.

FIG. 5 shows the influence of the groove width W on the static flow rate, and the rate of change in the flow rate is a little less than 0.2% in the tolerance ±a with respect to the reference groove width Wo. Figure 6 shows the effect of groove depth H on static flow rate.

The rate of change in flow rate is a little less than 0.1% in the tolerance ±a with respect to the reference groove depth Ho. Therefore, the influence of the grooves on the static flow rate is so small that it can be ignored under the above design conditions. In addition, in FIGS. 5 and 6, the static flow rate Qo is the target flow rate, and Q+aax is Q.

Q m A n represents +3% of Qo. In addition, the tolerance ±a is 20 μm in this example.
That's about it.

Next, the influence of swirling force on static flow rate will be described.

The swirl number S given as a parameter indicating the swirl strength is given by the following equation.

(Momentum in the direction of the injection axis) x (orifice radius) where,
L: Eccentricity of the groove (see Figure 4) ds: Rheologically equivalent diameter expressed using the groove diameter W and groove depth H (Formula % Formula %): The size of this swirl number S, which is The influence of the static flow rate on the static flow rate will be explained using the following equation, and will also be described along with the authors' experimental results. First, the flow rate Q is given by equation (4).

Here, Q: flow rate co = flow coefficient ds orifice diameter γ: specific weight P: fuel pressure. The flow coefficient Go in equation (4) is expressed by the characteristic value K, which is the reciprocal of the swirl number S determined by equation (3). In this example, the flow coefficient G
The design is such that fuel is allowed to pass in a region where the rate of change of o is small.

In other words, the magnitude of the swirl number S in equation (3) can be selected by measuring the eccentricity of the groove. This eccentric scale is
It goes without saying that the dimensions are determined to reduce the rate of change in the flow rate coefficient Co, and this will be proven by FIG. 8 showing the experimental results of the authors.

In FIG. 8, the rate of change of the static flow rate is a little less than +1% in the tolerance ±a with respect to the reference eccentricity Lo.

This corresponds to the change in flow rate at the hatched part in the figure, and this change in flow rate is due to the change in flow coefficient Co shown in FIG.
o, 1.1, it can be said that it corresponds to Comax.

As explained above, the fuel swirl element 37 has relatively little influence on changes in the static flow rate, and the inexpensive fuel swirl element 37 can be provided by a simple configuration with loose manufacturing precision. The fuel swirl element 37 is manufactured to desired dimensions with loose manufacturing precision, and then fixed to the groove 48 of the inner wall surface 36 of the valve guide 7 by fluid pressure bonding by metal flow.

Next, adjustment of the stroke of the movable part 4A will be described. The stroke is determined by the size of the gap between the stopper 29 and the surface 5a of the neck of the rod 5.

The experimental results of the influence of this stroke ρ on the static flow rate are shown in Figure 9.As is clear from Figure 1, as the stroke value increases, the flow rate starts to rise rapidly, and then the gradient gradually becomes gentler and becomes almost constant. The flow rate is Qo. The area As of the annular gap formed between the ball 6 and the valve seat 9 due to this stroke is given by equation (5), as shown in FIG. 10.

(5) Here, Dl: Lower side of the trapezoid in the figure Dl = Upper side of the number of vehicles in the figure, that is, seat diameter h: Height of the trapezoid in the figure.

The area A2 for achieving a constant flow rate Qo is the area A2 of the fuel injection hole 8
When expressed as the ratio δ=Az/As to the area A3, 1<δ. In this embodiment, as shown in FIG. 9, it can be seen that the dimensions are determined to have a sufficient margin in the tolerance ±a with respect to the reference stroke io. Tolerance of the stroke QO -a
The ratio δ is 2 or more. As mentioned above, one dimension a is about 20 μm.

As mentioned above, the stroke amount of the movable part 4A is.

It is an absolute amount that does not affect the static flow rate, and is determined with sufficient dimensional tolerance.

Therefore, as in the past, the lift amount is measured once with the movable part 4A and the valve guide 7 combined, and the end face of the valve guide or the face 5a of the neck part of the rod 5 is polished to obtain the target range. There is no need to adjust the stroke,
Only component dimensions need to be managed, so assembly work is easy and simplified.

Next, the influence on the static flow rate of the fuel injection hole 8, which is a fuel injection port provided in the valve guide 7, will be described. The static flow rate of fuel through a single fuel injection hole 8 is shown in FIG. Reference orifice diameter d.

The rate of change of static flow rate with tolerance ±b is ±1.5
It is a little less than %. Here, the dimension b is about 5 μm.

As described above, the cross-sectional area A8 of the fuel injection hole 8 is.

If the relationship is expressed using the annular clearance area Ax during the stroke of the movable part 4A and the groove area Ax of the fuel swirling element 37, then A x > A x > A a
(6) In the so-called injection valve 1 of this embodiment, fuel is metered by the fuel injection hole 8 of the orifice.

As mentioned above, the ratio δ of Ax/Aa takes a value of 2 or more, but in this case, the fluid loss of the fuel injection hole 8 is 95% of the total loss.
% or more, which confirms that the above measurement is performed by this fuel injection hole 8.

Furthermore, the flow rate change rate takes into consideration the influence of the fuel swirling element 37 on the flow rate as explained using FIGS. 5 to 8, and the influence of the stroke on the flow rate explained using FIGS. 9 and 10. The fact that is approximately ±1% also means that the flow rate is adjusted by the fuel injection hole 8 of the outlet orifice.

As mentioned above, the static flow rate is hardly affected by the stroke, and varies by about ±1% due to the fuel swirl element 37 and about ±1.5% depending on the orifice, but the static flow rate is changed by about ±3% due to the injection valve assembly. can be fully satisfied.

In other words, the injection valve becomes an inexpensive injection valve that does not require disassembly or expensive remanufacturing for static flow rate adjustment. In addition,
The static flow rate of the orifice provided in the valve guide 7 is
It goes without saying that by measuring before crimping and fixing the fuel swirling element 37 to the valve guide 7, the accuracy can be controlled within the target accuracy.

As described above, the assembled valve guide assembly is inserted together with the stopper 29 into the valve guide receiving portion 30 of the yoke 3 of the electromagnet assembly, and both are assembled. Both are fixed by flowing the inner circumferential wall of the tip end of the yoke 3 into the groove 51 provided on the outer periphery of the valve guide 7 by plastic flow using a metal flow. At this time, the stopper 29 is set to have a thickness that provides a predetermined air gap so that the tip of the plunger 4 and the tip of the core 2 do not come into direct contact when the movable part is sucked.
Next, the adjuster 11 holding the spring 10 at the tip and the O-ring 12 attached to the outer periphery is inserted into the hole provided in the center of the core 2 of the electromagnet assembly from the opposite direction to the valve guide 7. A filter 31 and an O-ring 24 are attached to the outer periphery, and the device is temporarily stored in a storage space (not shown), where an injection amount test is started. For injection and quantity tests, first measure with the movable part at full stroke, and confirm that the injection quantity at that time is the specified injection quantity.

Thereafter, the responsiveness of the movable part is determined by changing the load of the spring 10 so that the injection amount at a certain period and a certain amount of valve time becomes a specified injection amount, and then the outer circumference of the upper protrusion 52 of the core 2 is radially from the hole in the mold resin,
It is fixed by biting the inner wall of the core into the groove 53 of the adjuster.

The operation of the present injection valve configured as above will be explained. The injection valve 1 has an electrical 0N-O applied to the electromagnetic coil 15.
The FF signal operates the movable part to open and close the valve seat, thereby injecting fuel. An electric signal is given to the coil 15 as a pulse. When a current is passed through the coil 15, the core 2. York 3. A magnetic circuit is formed by the plunger 4, and the plunger 4 is attracted to the core 2 side.

When the plunger 4 moves, the ball valve 6 integrated therewith also moves and separates from the seat surface of the valve seat 9 of the valve guide 7 to open the fuel injection hole 8.

The fuel is pressurized by a fuel pump or a fuel pressure regulator (not shown), flows into the electromagnetic valve assembly from the inlet passage 26 via the filter 34, and flows into the lower passage 23 of the coil assembly 16. The fuel is supplied to the seat through the outer periphery of the plunger 4, the gap between the stopper 29 and the rod 5, and the grooves 49 and 50 of the fuel swirl element 37, and is injected into the intake pipe through the fuel injection hole 8 when the valve is opened.

When the electromagnetic coil 15 is deenergized, the movable portion 4A is pushed by the spring 10 and moves toward the valve seat, and the ball valve 6 closes the seat surface of the valve seat 9.

From the above explanation, it has become clear that a flow rate adjustment means is not required, but here we will describe the points that contribute to atomization of the fuel.

When the fuel reaches the fuel swirling element 37, it flows from the axial groove 49 provided in the swirling element and the radial groove 50 communicating with the radial groove 50 toward the seat surface of the valve seat 9. A swirling flow occurs at the outlet of the eccentrically configured radial groove. This swirling flow passes downstream through a lossless annular gap formed in the seat surface 1 of the valve seat 9, but the flow is encouraged and reaches the fuel injection hole 8 while retaining sufficient swirling energy.

Incidentally, as is clear from the above description, the pressure drop of the fuel when it flows through the annular gap created between the seat surfaces of the valve seat 9 when the grooves 49, 50 and the ball 6 are lifted is extremely small. Therefore, the swirling supply of fuel is performed while maintaining the supplied fuel pressure, and the fuel is injected at the fuel injection hole 8 with sufficient injection pressure and swirling force, so that excellent atomized fuel can be obtained.

Here, FIG. 12 shows the relationship between the fuel flow path and the flow velocity when the injection valve of the present invention is used. As is clear from FIG. 12, the flow velocity is highest in the area of the fuel injection hole from the fuel inlet to the outlet. Therefore, the flow rate can be measured only at the fuel injection hole, that is, the outlet orifice. In terms of design, if the exit orifice is made accurately, the flow rate can be measured accurately.

FIG. 13 shows another embodiment of the present invention, in which the fuel swirl element 37 has an axial groove 49 with a sufficient gap to allow passage of fuel, and a core with a constricted shape that does not cause fuel flow loss. The radial groove 50 is configured so that the pressure loss during passage through the radial groove 50 is negligible, and the fuel flows into the first fuel swirling chamber 54 .

FIG. 14 is a sectional view of a nozzle device according to another embodiment of the present invention. In FIG. 14, 37 is another fuel swirling element, 49 is an axial groove, and 50 is a radial groove.

This embodiment also provides the same effects as the first embodiment, and has a relatively simple structure and can be constructed at low cost.

Note that the axial groove 49 and the radial groove 5 in this embodiment
0 can take any shape as is clear from the embodiments. That is, it is possible to adjust the injection pressure and the fuel swirling force, and it is also possible to select the pattern of the spray injected from the fuel injection hole 8. Furthermore, it goes without saying that the same effect can be obtained by forming the axial groove 49 by chamfering it.

Next, FIG. 15 is an enlarged view of main parts of an electromagnetic fuel injection valve according to still another embodiment of the present invention, and FIG. 16 is a B of FIG. 15.
-B is a sectional view taken along the arrow.

In FIG. 15, 37 is a fuel swirling element having a flange 51, and the outer peripheral surface of this flange 51 is
It is fixed to the inner surface of the rapidly expanding hole 5 of No. 2. 52 is flange 5
1, from which fuel flows from the radial groove 50 provided on the surface corresponding to the valve seat 9 to the first fuel swirling chamber 54. - 55 communicates with the fuel reservoir 52 through a plurality of notches 55 provided in the flange 51 as shown in FIG.

A second fuel swirling chamber 57 is formed by a conical valve seat 9 below the ball 6, and promotes the swirling flow of the fuel flowing from the first fuel swirling chamber 54.

Reference numeral 56 denotes a spacer member inserted between the support surface 1a of the yoke 3 and the support surface 2a of the nozzle device 7, and this spacer member 56 regulates the gap with the protrusion surface 8a of the valve device. , to ensure the upward movement of the valve device, that is, the amount of lift.

In this embodiment, the same effects as in the first embodiment can be obtained, but in particular, the pressurized fuel can be uniformly distributed immediately before the radial groove 50, and can be efficiently replaced with swirling fuel. be.

【Effect of the invention〕

According to the present invention, the configuration is simple and does not require flow rate adjustment after assembly, and efficient swirling fuel can be obtained by supplying fuel without pressure drop, and excellent atomized fuel can be obtained.

[Brief explanation of the drawing]

FIG. 1 is a vertical cross-sectional view of an electromagnetic fuel injection valve according to an embodiment of the present invention, FIG. 2 is a vertical cross-sectional view for explaining the fuel swirl element and valve guide assembly structure, and FIG. Figure 4 is a sectional view taken along line B-B in Figure 3, Figure 5 is an experimental example showing the relationship between groove width and flow rate, and Figure 6 is an experiment showing the relationship between groove depth and flow rate. For example, FIG. 7 is a diagram showing the relationship between fuel swirl strength and flow rate coefficient according to an embodiment of the present invention, FIG. 8 is a diagram showing the relationship between groove eccentricity and flow rate, and FIG. 9 is a diagram showing the relationship between valve stroke and flow rate. Figure 10 is a diagram to explain the annular gap created between the ball and valve seat, Figure 11 is a diagram to illustrate the relationship between orifice diameter and flow rate, and Figure 12 is a diagram to explain the relationship between fuel flow path and flow velocity. 13 and 14 are cross-sectional views of the ball valve body portion of another embodiment of the present invention, and FIG. 15 is an enlarged cross-sectional view of essential parts of another embodiment of the present invention, and FIG. 16 is a diagram showing the relationship. is B in Figure 15.
-B sectional view. 1... Injection valve, 2... Core, 3... Yoke, 4a
...Movable valve, 4...Plunger, 5...Rod,
6... Ball valve, 8... Fuel injection hole, 9. ...Valve seat, 15... Coil, 37... Fuel swirl element, 49
...Axial groove, 50...Radial groove. Agent: Patent attorney Katsuo Ogawa. ~ Tsubo Pa, -- 3rd eye Qin, 5 Rozohata W (m ki) Groove depth - 5t - IC deposit cape collar property tk (=%) 8th diagram Two-dimensional rotation to I island of the groove η 1. ) No. 9 Concave No. 70 Orifice 1 Article (Msu No. 12 Mouth 51 L Road 1 (Staying No. 13 Fist 74 Fast Mouth 1.!5 Prisoner No. 76 Mouth

Claims (7)

[Claims] 1. A fuel swirling element is provided upstream of the valve seat and applies a swirling force to the supplied fuel, a fuel injection hole is provided downstream of the valve seat, and the fuel swirling element provides the swirling force. In the electromagnetic fuel injection valve, the electromagnetic fuel injection valve is equipped with a ball valve that injects fuel from the fuel injection hole, and controls the amount of fuel injected by controlling the opening and closing time of the ball valve, when the ball valve lifts. The area of the annular gap formed by the ball valve and the valve seat is smaller than the cross-sectional area of the groove of the fuel swirling element and larger than the cross-sectional area of the fuel injection hole. Electromagnetic fuel injection valve. 2. A fuel swirling element is provided upstream of the valve seat and applies a swirling force to the supplied fuel, a fuel injection hole is provided downstream of the valve seat, and the fuel swirling element provides the swirling force. and a ball valve that injects fuel from the fuel injection hole, and the electromagnetic fuel injection valve is controlled by the fuel injection amount by controlling the opening/closing time of the ball valve, from the inlet of the fuel swirl element. A fuel injection valve characterized in that the cross-sectional area of the flow path from the fuel injection hole to the outlet is configured to decrease continuously. 3. A fuel swirling element is provided upstream of the valve seat and applies a swirling force to the supplied fuel, a fuel injection hole is provided downstream of the valve seat, and the fuel swirling element provides the swirling force. In the electromagnetic fuel injection valve, the electromagnetic fuel injection valve includes a ball valve that injects fuel from the fuel injection hole, and controls the amount of fuel to be injected by controlling the opening/closing time of the ball valve, wherein the fuel swirl element is attached to the valve body. 1. An electromagnetic fuel injection valve characterized by having an axial groove into which fuel is introduced from the axial direction of the valve body, and a radial groove which has a tapered shape and introduces fuel eccentrically from the axial center of the valve body into a fuel swirling chamber. 4. In claim 3, the axial groove is D.
An electromagnetic fuel injection valve characterized by a cylindrical groove with a cut surface. 5. A fuel swirling element is disposed upstream of the valve seat and applies swirling force to the supplied fuel, and a fuel injection hole is disposed downstream of the valve seat. A ball valve that injects fuel to which a swirling force is applied by a swirling element from the fuel injection hole, and a means for controlling the opening and closing time of the ball valve with a stroke that makes the flow rate constant. Electromagnetic fuel injection valve. 6. In claim 5, the stroke of the ball valve is such that the ratio of the area of an annular gap formed by the ball valve and the valve seat to the cross-sectional area of the flow path of the fuel injection hole is 1 or more. An electromagnetic fuel injection valve, characterized in that the ratio of the groove cross-sectional area of the fuel swirling element to the flow passage cross-sectional area of the fuel injection hole is 1.5 or more. 7. A plurality of notches arranged on the upstream side of the valve seat to which fuel is supplied, a fuel reservoir communicating with the notches, and a fuel reservoir communicating with the fuel reservoir, introducing fuel eccentrically from the axial center of the valve body. A fuel swirling element having a radial groove, a fuel injection hole provided on the downstream side of a valve seat, and a ball valve that injects fuel to which swirling force is applied by the fuel swirling element from the fuel injection hole. An electromagnetic fuel injection valve, characterized in that the amount of fuel injected is controlled by controlling the opening/closing time of the ball valve.