JPS60113065A - Fuel injection valve for dual-intake air engine - Google Patents

Abstract

PURPOSE:To decrease the amount of fuel sticking to the wall of an intake-aid pipe as small as possible, by providing, for example, an adapter having a plurality of jetting ports for dividing the stream of fuel from a fuel injection port and by making directive the same so that air-intake valves are made directive without enlarging the width or jet fuel spray. CONSTITUTION:Fuel fed from a fuel injection port 13, is directed toward the center 20 of a fuel branch section 16, and impinges upon the latter to be branched so that the fuel is fed through jetting ports 23, 24 in an adapter 14. In this case the angle theta of wedge of the fuel branch section 16 is suitably set so that injected fuel passes through a flow dividing intake air passage sections 6a, 6b and flows directing toward the umbrella parts of intake-air valves 2a, 2b. Thereby the fuel flows into a combustion chamber 1 through the intake-air valves 2a, 2b which open.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention has a plurality of intake valves in each cylinder, and the intake passage has a plurality of branch intake passage portions that are partitioned from each other by partition walls in the vicinity of the intake valves. This invention relates to the structure of an electronically controlled fuel injection valve in a dual intake engine.

Prior Art When an electronically controlled fuel injection system is adopted in a dual intake engine that has two intake valves in one cylinder and has separate intake passages in which the intake passages are separated from each other by partition walls near the intake valves, If the intake passage is separated into two systems and the fuel injection valves of each system are installed in each branch intake passage, the number of fuel injection valves and injection systems to be installed will be twice that of a normal engine, which will significantly reduce the cost. An increase in costs is unavoidable.

To avoid this, if one fuel injector is used in each cylinder, and the fuel is to be injected evenly into multiple divided intake passages, the spray angle must be increased; however, in this case, the fuel There are problems such as a large amount of it adhering to the walls of the intake pipe, resulting in poor transient response.

Object of the Invention The present invention provides a dual intake engine having a plurality of intake valves and a plurality of divided intake passage sections for each cylinder, in which one electronically controlled fuel injection valve is provided for each cylinder. The number of fuel injection valves is minimized, and the amount of fuel adhering to the intake pipe wall is minimized by directing the fuel spray from one fuel injection valve to each intake valve without expanding the width of the spray. The purpose is to

Structure of the Invention In order to achieve this object, the fuel injection valve for a double intake engine of the present invention has the following structure. That is, the combustion chamber of each cylinder has a plurality of intake valves, and the intake passage has a plurality of branched intake passage sections that are separated from each other by partition walls near the intake valve. A valve is provided in the intake passage upstream of the divided intake passage portion. The fuel injection valve is arranged such that its center line is located within a plane that includes the center line of the partition wall, and one end of the fuel injection valve is disposed at a tip of the fuel injection valve so as to surround a fuel injection port. A cylindrical part to be attached and a wedge-shaped fuel branch part having a V-shaped concave upper end and side faces facing the opening center of the fuel injection port at the opening at the other end of the cylindrical part. Equipped with a fuel injection valve adapter.

Effect of the Invention In the fuel injection valve for a dual intake engine having such a configuration, a fuel branch portion is provided in front of the fuel injection port in the injection direction, so that fuel is divided into each branch intake passage portion,
Moreover, by setting the wedge-shaped angle to an appropriate angle, the fuel is directed to each intake valve. Moreover, since the upper end and side surfaces of the fuel branching portion are recessed in a V-shape, the injected fuel is not spread out too much but concentrated in the center and injected.

Effects of the Invention Since the fuel injection valves having the above-mentioned configuration achieve the same effect as two fuel injection valves by providing one for each cylinder, the number of fuel injection valves does not increase, and cost increases can be avoided. It will be done. Furthermore, since the injected fuel does not spread too much, the amount of fuel adhering to the wall of the intake boat is kept to a minimum, and no sloshing of the fuel or deterioration of transient response occurs.

EXAMPLE Below, a fuel injection valve for a dual intake engine according to an example of the present invention will be described with reference to the drawings.

FIGS. 1 and 2 show a four-valve engine having two intake valves and two exhaust valves as an example of a double intake engine according to the present invention. However, 2
This may also be the case for a three-valve engine with two intake valves and one exhaust valve. 1 and 2, the combustion chamber 1 has two intake valves 2a, 2b and two exhaust valves 3a.
, 3b, and has four valves 2a12b, 3a,
An intake passage is connected to the two intake valves 2a12b, in which the spark plug 4 is provided at a position that does not interfere with the ignition plug 3b.
separated from each other by the branch intake passage portions 6a, 6.
It forms b. Divided intake passage portion 5a, i3b
are combined into one intake passage section 6C in the cylinder head portion 7 upstream and connected to one intake passage section 6C of the intake pipe 8.

The fuel injection valve 9 is an electronically controlled fuel injection valve, and is attached to the one intake passage section 6C. Fuel injection valve 9
is attached to the intake pipe 8 such that its central axis is located within a plane 10 that includes the center line of the partition wall 5. The fuel injection valve 9 is attached to face the upstream end 11 of the partition wall 5 .

As shown in FIGS. 3 to 5, the fuel injection valve 9 includes a valve body 12, a fuel injection port 13 formed at the lower end of the valve body 12, and an adapter 14 attached to the lower end of the valve body 12. It has The adapter 14 has a cylindrical portion 15 and a combustion/oblique branch portion 16 formed at an end opposite to the side for attachment to the valve body 12 . The fuel branch portion 16 extends between two positions on the inner circumferential surface of the cylindrical portion 15 and is formed into a wedge shape that is pointed upward. Further, the fuel branch portion 16 is formed by having a wedge-shaped upper end 17 and two side surfaces 18 and 19 recessed into a V-shape. The center 20 of the recess in the upper end 17 and the center 21 . The angle θ of the wedge formed by the center 21.22 of the side surface 18.19 is such that the branched injected fuel is connected to each intake valve 2a, 2b.
The angle is set to point the umbrella. adapter 14
The end on the fuel injection side is divided by the fuel branch 16 and formed into two injection ports 23 and 24.

Next, the operation of the fuel injection valve of the dual intake engine in the embodiment device constructed as described above will be explained.

First, the fuel injected from the fuel injection port 13 flies toward the center 20 of the fuel branch 16, collides with the fuel branch 16, branches into two holes along the side surface 18, 19, and enters the adapter 14. From the spout 23, 24 to each branch intake passage portion 6a
, 5b. In this case, the fuel branch 16
Since the wedge angle θ is set to an appropriate value,
The injected fuel flows through the divided intake passage portions 6a, 6b toward the head portions of the intake valves 2a, 2b, and flows into the combustion chamber 1 through the open intake valves 2a, 2b. In such a device, although the number of fuel @ side valves 9 itself is one for each cylinder, it achieves the same effect as if one were provided in each of the branch intake passage portions 6a and 6b.

When the fuel is branched at the fuel branch 16, the fuel branch 16 is recessed in a V-shape at the upper end 17 and side surfaces 18, 19, so that the fuel injected from the fuel injection port 13 is diverted to the fuel branch 16. The center 20, 21 of the post-collision fuel branch 16.
The fuel tends to flow so as to gather at 22, and excessive spread of the fuel is suppressed. That is, if the recess is not formed in the fuel branch part 16, the fuel will spread evenly over the entire surface of the fuel branch part 16, and the fuel will spread out too much. However, in the present invention, excessive spread of fuel is suppressed, so +1@ of fuel to the intake port can be minimized. This improves responsiveness, especially transient response. In addition, since there is no need to set a large fuel injection angle at the fuel tri injection port 13, the adapter 14
There is no possibility that a large amount of fuel will adhere to the inner wall of the fuel tank and cause smearing.

When using the apparatus of the embodiment as described above, the following effects can be obtained.

First, the reduction in adhesion of the injected fuel to the intake port wall is promoted.In order to improve drivability during transient and cold periods, conventional measures have been taken by increasing the amount of fuel. This makes it possible to reduce the increase in fuel consumption, thereby improving fuel efficiency and reducing the number of HC exhaust ports.

Further, it is possible to prevent deterioration in drivability due to lean air-fuel ratio during transient periods.

Furthermore, if the present invention is used to reduce the adhesion of fuel to the intake port wall in a dual-intake engine, the number of fuel injection valves is the same as in a normal engine, and the effect is that only one injector is installed in each branch intake passage. It is the same as having one after the other, and a significant increase in cost can be avoided.

Furthermore, since the fuel is branched after being injected, it is advantageous in terms of the difficulty level of the fuel calculation accuracy -15 in terms of machining difficulty compared to a fuel injection port in which the fuel injection port is machined into two holes.

[Brief explanation of drawings]

FIG. 1 is a sectional view of the vicinity of a fuel injection valve of a dual intake engine according to an embodiment of the present invention, FIG. 2 is a plan view of the device shown in FIG. 1, and FIG. 3 is a view of the fuel injection valve of FIG. FIG. 4 is a bottom view of the fuel injection valve of FIG. 3, and FIG. 5 is a perspective view of only the fuel branch portion of the fuel injection valve of FIG. 3. 1...Combustion chambers 2a, 2b...Intake valves 3a, i3b...Exhaust valves 5...Partition walls 6a, 6b...Diversion intake Passage section 9...
Fuel injection valve 11... Bulkhead upstream end 12... Valve body 13... Fuel injection port 14... Adapter 15... Cylindrical Part 16...Fuel branch part 17...Fuel branch part upper part 18.19...Fuel branch part side surface 20...
・Top center 21.22...Side center 23.24...Spout port Figure 1? Figure 2 0 1 2.6 Figure 4 Procedural Amendment November 13, 1980 Commissioner of the Japan Patent Office Sir 1. Indication of the case 1988 Patent Application No. 219570 2. Title of the invention Fuel injection valve for a double intake engine 3. Relationship with the case of the person making the amendment Patent Applicant Address 1 Toyota-cho, Toyota City, Aichi Prefecture Name (320) Toyota Motor Corporation Representative Matsu
(Change of representative) (1 other person) 4. Agent Address: Showa Building 6, 1-7-5 Akasaka, Minato-ku, Tokyo 107
Number of inventions increased by amendment None 7, subject of amendment (
1) Full text of the specification 8, Contents of amendments (1) As shown in Attachment 9, Patent applicant address other than the above Address: 1 Fuisanko, 1-1 Kyowa-cho, Obu-shi, Aichi Prefecture (Tatsu name: Representative of Aisan Kogyo Co., Ltd. Kobayantadao) Person: Kobayashi Forgetfulness/Blindness Description Book 1, Title of the Invention Fuel Injection Valve for Dual Intake Engine 2, Claims <1) The combustion chamber of each cylinder has a plurality of intake valves, and the intake passage is formed by a partition wall near the intake valves. In a dual-intake engine that has a plurality of divided intake passage sections that are partitioned from each other, and in which an electronically controlled fuel injection valve is provided in the intake passage upstream of the divided intake passage sections, the center line of the fuel injection valve is A fuel injection valve for a dual intake engine, characterized in that it is located within a plane including a centerline of a bulkhead. 3. Detailed Description of the Invention Field of Industrial Application 1 The present invention is directed to a plurality of branched intake passages in which each cylinder has a plurality of intake valves and the intake passages are separated from each other by partition walls in the vicinity of the intake valves. This invention relates to the groove construction of an electronically controlled twisted injection valve in a dual intake engine having a multi-intake engine. bt Next technology When adopting an electronically controlled fuel injection system in a dual intake engine that has two intake valves in one cylinder and has a divided intake passage section in which the intake passage is separated from each other by a partition near the intake valve. If the intake passage can be separated into two systems and the fuel injection valves of the D system can be installed in each branch intake passage, the number of fuel injection valves and injection systems to be installed will be twice that of a normal engine. Therefore, a huge increase in costs is unavoidable. To avoid this, if you use 11 fuel injectors for each type of air, and you want to inject fuel evenly into multiple divided intake passages, you will need to increase the spray angle. One problem with this is that a large amount of fuel adheres to the intake pipe leading to poor transient response. Furthermore, if the amount of adhesion increases or fluctuates, there is a risk that even if the metering accuracy of the fuel injection valve is improved, the variation in the amount of fuel actually supplied may increase. 1. Purpose of the Invention The present invention provides a dual intake engine having a plurality of intake valves and a plurality of divided intake passage sections for each cylinder, in which one electronically controlled fuel injection valve is provided for each cylinder. The number of fuel injection valves is minimized, and the amount of fuel deposited on the intake pipe wall is reduced by directing the mist of the fuel injected from one fuel injection valve to each intake valve without increasing the width of the mist. The aim is to minimize the amount of Structure of the Invention In order to achieve this object, the fuel injection valve for a double intake engine of the present invention has the following structure. That is, the combustion seedling of each cylinder has a plurality of intake valves, and the intake passage has a plurality of branched intake passage sections that are separated from each other by partition walls near the intake valve, and an electronically controlled fuel injection system is used. A valve is provided in the intake passage upstream of the divided intake passage portion. The fuel injection valve is arranged such that its center line is located within a plane that includes the center line of the partition wall, and the injection part of the fuel injection valve is a single-hole fuel injector that measures and injects the sent fuel. It consists of an injection port and an adapter having a plurality of injection ports that divides the flow of fuel from the fuel injection port and directs it toward each intake valve. Effect of the Invention In the fuel injection valve for a dual intake engine having such a configuration, fuel is metered and delivered through the single-hole fuel injection port, and this fuel is divided by the injection port of the adapter. By setting the angle of the jet nozzle at an appropriate angle, the fuel is directed to each intake valve. Therefore, even if the injected fuel is not particularly spread, the fuel is appropriately directed toward each intake valve, and fuel adhesion to the intake pipe wall is suppressed. Furthermore, the fuel is metered at the fuel injection port before branching, and the metered fuel is divided appropriately and sent toward the intake valves without sticking to the intake pipe wall. Supply accuracy is also improved. Effects of the Invention The above (n-component fuel injection valves) can achieve the same effect as two fuel injection valves by simply providing one for each cylinder.
The number of fuel injection valves does not increase, and cost increases can be avoided. In addition, since the injected fuel does not spread too much, the amount of fuel adhering to the intake port 1 to the wall is kept to a minimum.
There is no occurrence of fuel flapping or deterioration of transient response. Furthermore, since the measuring section and the fuel dividing section are separate parts arranged in series, a decrease in the total ff1lf degree can also be avoided. EXAMPLE Below, a fuel injection valve for a dual intake engine according to an example of the present invention will be described with reference to the drawings. FIG. 1 and FIG. 2 show a four-valve engine having two intake valves and two exhaust valves as an example of a reduced intake engine according to the present invention. However, 2
This may also be the case for a three-valve engine with two intake valves and one exhaust valve. 1 and 2, the combustion chamber 1 has two intake valves 2a, 2b and two exhaust valves 3a.
, 3b, and has four valves 2a12b, 3a,
An intake passage is connected to the two intake valves 2a and 2b, in which a spark plug 4 is provided in a position that does not interfere with the spark plug 3b, but the intake passages are separated from each other by a partition wall 5 near the intake valves 2a and 2b. , branch intake passage portions 6a, 6b
is formed. Upstream, the divided intake passage sections 6a, 6b are combined into one intake passage section 6C in the cylinder head section 7 and connected to one intake passage section 6C of the intake pipe 8. The fuel injection valve 9 is an electronically controlled fuel injection valve, and is attached to the one intake passage section 6C. Fuel injection valve 9
is attached to the intake pipe 8 such that its center line is located within a plane 10 that includes the center line of the partition wall 5. The fuel valve 9 is attached to the upstream end 11 of the partition wall 5 so as to face it. As shown in FIGS. 3 to 5, the fuel injection valve 9 includes a valve body 12, a fuel injection port 13 formed at the lower end of the valve body 12, and a fuel injection port 13 for metering and injecting fuel. It has an adapter 14 attached to the lower end. The adapter 14 includes a cylindrical portion 15, a fuel branch portion 16 formed at an end opposite to the side for attachment to the valve body 12,
That is, it has a fuel branch part 16 that divides the flow of fuel from the fuel injection port 13. In this embodiment, the fuel branch portion 16 extends between two positions on the inner circumferential surface of the cylindrical portion 15 and is formed in a wedge shape that is pointed upward. The fuel branch 16 also has a wedge-shaped upper end 17 and two side faces 18.1.
9 is recessed into a V-shape. Center 20 of the recess on the top end 17 and center 21 of the recess on the side surfaces 18.19.
22 is located in a plane that includes the center line of the fuel injection port 13 and is perpendicular to the longitudinal direction of the fuel branch portion 16 . Also side 1
The angle θ of the wedge formed by the centers 21 and 22 of 8.19 is set to an angle at which the branched injected fuel is directed toward the umbrella portion of each intake valve 2a, 2b. The end of the adapter 14 on the fuel injection side is divided by the fuel branch 16 and formed into two injection ports 23 and 24. Next, the operation of the fuel injection valve of the dual intake engine in the embodiment device constructed as described above will be explained. First, the fuel sent is injected at the single-hole fuel injection port 13 while being accurately measured. The fuel injected from the fuel injection port 13 is transferred to the fuel branch 16
It flew towards the center 20 of
The adapter 14 is branched into two holes along the sides 18 and 19.
Each branch intake passage portion 6a, 61 from the spout 23, 24 of
] is sprayed towards. In this case, since the wedge angle θ of the fuel branching portion 16 is set to an appropriate value, the injected fuel passes through the branched intake passage portions 6a and 6b and is directed toward the umbrella portion of the intake valve 2a12b. and flows into the combustion chamber 1 through the same intake valves 2a, 2b. In such a device, the number of fuel injection valves 9 itself is one for each cylinder, but one for each branch intake passage portion 6a, 6b.
It achieves the same effect as if it were provided individually. When the fuel is divided at the fuel branch i isthmus part 16, since the upper end 17 and side surfaces 18 and 19 of the fuel branch part 1G are recessed in a V-shape, the fuel injected from the fuel vn tip 13 is
The center 20.2 of the collision penetrating branch 16 on the fuel branch 16
The fuel tends to flow so that it gathers at 1.22, preventing the fuel from spreading too much. In other words, the dent is the fuel branch part 1G.
If the fuel branch portion 16 is not formed, the fuel will spread evenly over the entire surface of the fuel branch portion 16, and the fuel will spread out too much. However, in the present invention, excessive spread of fuel is suppressed, so that adhesion of fuel to the intake port is minimized. This improves responsiveness, especially transient response. Further, since there is no need to set a large fuel injection angle at the fuel injection port 13, there is no possibility that a large amount of fuel will adhere to the inner wall of the adapter 14 and cause sagging. When using the apparatus of the embodiment as described above, the following effects can be obtained. First, by promoting the reduction of adhesion of injected fuel to the intake port wall, the conventional method was to increase the amount of fuel in order to improve the convertibility of the selector when it is overheated or cold.
The increased amount can be reduced, improving fuel efficiency and HC.
It is possible to reduce the number of people discharging. Still, it is possible to prevent deterioration of drivability due to the lean air-fuel ratio during overtemperature. Furthermore, if the present invention is used to reduce the adhesion of fuel to the intake port wall in a dual-intake engine, the number of fuel injection valves is the same as in a normal engine, and the effect is that only one injector is installed in each branch intake passage. It is the same as having one after the other, and a significant increase in cost can be avoided. Furthermore, since Shimotsuki is branched after being ejected, the single-hole metering part and the branching part are arranged in series in the fuel flow direction, so the fuel injection port is simply machined into two holes. Compared to the conventional method, it is possible to improve fuel measurement accuracy, and it is also advantageous in terms of processing difficulty. 4. Brief description of the drawings FIG. 1 is a cross-sectional view of the vicinity of a fuel injection valve of a dual-intake engine according to an embodiment of the present invention, FIG. 2 is a plan view of the device shown in FIG. 1, and FIG. FIG. 4 is a bottom view of the fuel injector shown in FIG. 3, and FIG. 5 shows only the fuel branch part of the fuel injector shown in FIG. 3. This is a perspective view. 1... Combustion plan 2a, 2b... Intake valve 3a, 31+... Exhaust valve 5... Bulkhead 5a, +3b... Diversion punch Air passage section 9...
... Fuel injection valve 11 ... Bulkhead upstream end 12 ... Valve body 13 ... Fuel injection port 14 ... Adapter 15 ... Cylinder Shaped portion 1G...Fuel branch part 17...Fuel branch part side surface 18.19...Fuel branch part side surface 20...
・Top center 21.22...Side center 23.24...Spout port Patent applicant Toyota Motor Corporation

Claims (1)

[Claims] (1) The combustion chamber of each cylinder has a plurality of intake valves, the intake passage has a plurality of branch intake passage sections separated from each other by partition walls near the intake valve, and the electronically controlled fuel injection valve has a branch intake passage. In a dual intake engine provided in an intake passage upstream of an intake passage portion, the fuel injection valve is arranged so that its center line lies within a plane that meets the center line of a partition wall, and the fuel injection valve , a cylindrical part attached to the tip of the fuel injection valve at one end so as to surround the fuel injection port, and an upper end facing the opening center of the fuel injection port at the opening at the other end of the cylindrical part. 1. A fuel injection valve for a dual intake engine, comprising: a fuel injection valve adapter having a wedge-shaped fuel branch portion having a V-shaped concave side surface and a wedge-shaped fuel branch portion formed in a V-shaped concave shape.