JP2017089574A - Fuel injection valve of internal combustion engine, and internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fuel injection valve of an internal combustion engine, and the internal combustion engine, capable of sufficiently mixing fuel spray injected into a combustion chamber of the internal combustion engine with oxygen in the combustion chamber and effectively suppressing production of soot in combustion.SOLUTION: A fuel injection valve 20 of an internal combustion engine 1 is the fuel injection valve 20 for injecting fuel toward a combustion chamber 6 of the internal combustion engine 1 in which a swirl flow S is formed. The shape of fuel outlets 24 of a plurality of injection holes 22 of the fuel injection valve 20 are vertically long shape. In the vertically long shape, a major axis b is vertical to or inclined with respect to a flowing direction of the swirl flow S, and a cross-sectional area of the injection hole 22 is gradually reduced from a side of a fuel inlet 23 of the injection hole 22 toward a side of the fuel outlet 24.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a fuel injection valve for an internal combustion engine and an internal combustion engine including the same.

  Conventionally, an internal combustion engine having a fuel injection valve that directly injects fuel into a combustion chamber is known (see, for example, Patent Document 1). There is also known an internal combustion engine in which a swirl flow (a vortex rotating in a lateral direction) is formed in a combustion chamber.

JP 2004-316598 A

  By the way, in the case of an internal combustion engine that directly injects fuel into a combustion chamber and burns, in order to suppress the generation of soot during the combustion of the fuel, the sprayed fuel injected from the fuel injection valve (that is, the fuel) Adequate mixing of the spray) and oxygen in the combustion chamber is effective.

  In this regard, in the case of the prior art, the fuel spray can be easily mixed with the oxygen in the combustion chamber at its outer edge, but inside it it is difficult for oxygen to enter the fuel spray, so oxygen Full mixing with is difficult. Therefore, in the case of the prior art, a large amount of soot may be generated during combustion due to the lack of oxygen inside the fuel spray.

  The present invention has been made in view of the above, and an object of the present invention is to sufficiently mix the fuel spray injected into the combustion chamber of the internal combustion engine with oxygen in the combustion chamber. It is an object of the present invention to provide a fuel injection valve for an internal combustion engine and an internal combustion engine that can effectively suppress the occurrence of fuel.

  In order to achieve the above object, a fuel injection valve for an internal combustion engine according to the present invention is a fuel injection valve for injecting fuel toward a combustion chamber of an internal combustion engine in which a swirl flow is formed. The shape of the fuel outlet of the nozzle hole is a vertically long shape, and the vertically long shape is a shape in which the long axis of the vertically long shape is vertical or inclined with respect to the flow direction of the swirl flow, and the cross-sectional area of the nozzle hole is: The nozzle hole is reduced in size from the fuel inlet side toward the fuel outlet side.

  According to the present invention, the cross-sectional shape of the fuel spray injected from the nozzle hole having the vertically long fuel outlet is formed into a vertically long shape having a long axis perpendicular or inclined with respect to the flow direction of the swirl flow. it can. In this case, a large vortex, which is a large secondary flow due to the swirl flow, can be generated on the back side of the fuel spray, and oxygen in the combustion chamber can be effectively taken into the fuel spray by the large vortex. .

In addition, since the cross-sectional area of the nozzle hole is reduced from the fuel inlet side toward the fuel outlet side, the spread angle of the fuel spray is expanded, that is, the layer thickness of the fuel spray is prevented from being increased. can do. As a result, the distance between the adjacent fuel sprays can be increased, so that the adjacent fuel sprays overlap each other, or the oxygen present between the adjacent fuel sprays is exchanged between the adjacent fuel sprays. It is possible to suppress the shortage. As a result, the oxygen in the combustion chamber can be more effectively taken into the fuel spray.

  From the above, according to the present invention, the fuel spray injected into the combustion chamber of the internal combustion engine can be sufficiently mixed with oxygen in the combustion chamber, and the generation of soot during combustion is effectively suppressed. Can do.

  In the above configuration, the vertically long shape may be any one of an elliptical shape, a long hole shape, a shape in which a part of two ellipses are combined, or a shape in which a part of two circles are combined.

  In order to achieve the above object, an internal combustion engine according to the present invention comprises the above fuel injection valve. According to the present invention, since the fuel injection valve is provided, the fuel spray injected into the combustion chamber of the internal combustion engine can be sufficiently mixed with oxygen in the combustion chamber for the same reason as described above. Thus, the generation of soot during combustion can be effectively suppressed.

  According to the present invention, the fuel spray injected into the combustion chamber of the internal combustion engine can be sufficiently mixed with oxygen in the combustion chamber, and soot generation during combustion can be effectively suppressed.

It is a schematic sectional drawing which shows typically the peripheral composition of the cylinder of the internal-combustion engine concerning an embodiment. FIG. 2A is a schematic enlarged cross-sectional view schematically showing an enlarged vicinity of the tip of the fuel injection valve. FIG. 2B is a front view schematically showing a state in which the fuel outlet of the nozzle hole in FIG. 2A is viewed from the front (A side in the drawing). FIG. 3A is a top view of the state in which fuel is injected from the fuel injection valve as viewed from above. FIG.3 (b) is a schematic sectional drawing which shows typically the cross section which cut | disconnected the fuel spray of Fig.3 (a) by the BB line. FIG. 4A to FIG. 4C are diagrams showing other shape examples of the fuel outlet of the nozzle hole. Fig.5 (a) is a front view which shows typically the state which visually recognized the fuel exit of the fuel injection valve which concerns on the modification 1 of embodiment from the A side of Fig.2 (a). FIG.5 (b) is a front view which shows typically the state which visually recognized the fuel outlet of the fuel injection valve which concerns on the modification 2 of embodiment from the A side of Fig.2 (a).

  Embodiments according to the present invention will be described below with reference to the drawings. Regarding the drawings, the dimensions are changed from the actual product so that the configuration is easy to understand, and the ratio of the thickness, width, length, etc. of each member and each component does not necessarily match the actual product ratio. Not necessarily.

  FIG. 1 is a schematic cross-sectional view schematically showing a configuration around a cylinder 4 of an internal combustion engine 1 according to the present embodiment. The internal combustion engine 1 is mounted on a vehicle. Although the specific kind of this vehicle is not specifically limited, In this embodiment, large vehicles, such as a bus and a truck, are used. A diesel engine is used as an example of the internal combustion engine 1.

  The internal combustion engine 1 includes a cylinder block 2, a cylinder head 3 disposed on the cylinder block 2, and a piston 5 disposed on a cylinder 4 (cylinder) formed on the cylinder block 2. A combustion chamber 6 is formed in a region surrounded by the top surface of the piston 5, the cylinder block 2 and the cylinder head 3. The cylinder head 3 is formed with an intake port 7 through which intake air passes and an exhaust port 8 through which exhaust passes. The internal combustion engine 1 also has an intake valve 9 that opens and closes an intake port 7 and an exhaust valve 10 that opens and closes an exhaust port 8.

  The internal combustion engine 1 is configured such that a swirl flow S is formed in the combustion chamber 6. The configuration for forming the swirl flow S in the combustion chamber 6 is not particularly limited, but in the present embodiment, as an example, the structure of the intake port 7 and the combustion chamber 6 of the internal combustion engine 1 has a swirl flow in the combustion chamber 6. The structure is such that S is formed.

  The internal combustion engine 1 also includes a fuel injection valve 20 that injects fuel toward the combustion chamber 6 where the swirl flow S is formed. Specifically, in the fuel injection valve 20 according to the present embodiment, an injection hole 22 (shown in FIG. 2 and the like described later) provided at the tip of the fuel injection valve 20 is exposed inside the combustion chamber 6. Further, the cylinder head 3 is disposed. Fuel is injected from the injection holes 22 toward the combustion chamber 6. The operation of the fuel injection valve 20 is controlled by a control device (not shown) such as an ECU.

  FIG. 2A is a schematic enlarged cross-sectional view schematically showing the vicinity of the tip of the fuel injection valve 20 in an enlarged manner. FIG. 2B is a front view schematically showing a state in which the fuel outlet 24 of the nozzle hole 22 in FIG. 2A is viewed from the front (A side in the drawing). FIG. 3A is a top view of a state in which fuel is injected from the fuel injection valve 20 as viewed from above. FIG. 3B is a schematic cross-sectional view schematically showing a cross section of the fuel spray F of FIG. 3A taken along line BB. In addition, in order to make a code | symbol easy to visually recognize, hatching is abbreviate | omitted in FIG.3 (b).

  2 (a), 2 (b), and 3 (a), a plurality of injection holes 22 that are holes for injecting fuel are provided at the tip of the body 21 of the fuel injection valve 20 ( In this embodiment, four are formed as an example). The number of the injection holes 22 need not be plural. For example, the fuel injection valve 20 may include only one injection hole 22. In addition, although the needle which opens and closes the nozzle hole 22 is also arrange | positioned inside the body 21, illustration of this needle is abbreviate | omitted. This needle is a valve body that opens and closes the nozzle hole 22 by sliding in the body 21 along the axis 100 of the body 21.

  As shown in FIG. 3A, each nozzle hole 22 has a predetermined angle (90 degrees in the present embodiment) with the adjacent nozzle hole 22, while surrounding the tip of the fuel injection valve 20. Arranged in the direction.

  As shown in FIG. 2A, each nozzle hole 22 is constituted by a fuel flow path extending from the fuel inlet 23 to the fuel outlet 24 by a predetermined distance. Further, as shown in FIG. 2B, the shape of the fuel outlet 24 of the injection hole 22 has a vertically long shape having a short axis a and a long axis b longer than the short axis a. As an example of the vertically long shape, an elliptical shape is illustrated in FIG. In this embodiment, the short axis a is the shortest axis in the vertically long shape, and the long axis b is the longest axis.

  As can be seen from FIG. 2B and FIG. 3A, when the fuel outlet 24 of the nozzle hole 22 is viewed from the front, the long axis b is in the flow direction of the swirl flow S. It is a vertical axis. Specifically, in this embodiment, the axial direction (extending direction) of the long axis b is the vertical direction when viewed from the front, and the swirl flow S is flowing in the lateral direction. The direction is perpendicular to the flow direction of the swirl flow S flowing in the direction. In this embodiment, since the axial direction of the short axis a of the fuel outlet 24 of the nozzle hole 22 is a lateral direction, the axial direction of the short axis a is parallel to the flow direction of the swirl flow S.

In this embodiment, each nozzle hole 22 has the same shape of the fuel inlet 23 as that of the fuel outlet 24, and the cross-sectional shape of the flow path portion between the fuel inlet 23 and the fuel outlet 24 is also the same. The shape is the same as that of the fuel outlet 24. However, the shape of the nozzle hole 22 is sufficient if at least the shape of the fuel outlet 24 is vertically long, and the portion other than the fuel outlet 24 does not necessarily have to be vertically long.

  In addition, the vertically long shape of the fuel outlet 24 of the nozzle hole 22 is not limited to the shape of FIG. FIG. 4A to FIG. 4C are diagrams showing other shape examples of the fuel outlet 24 of the nozzle hole 22. For example, as shown in FIG. 4A, the shape of the fuel outlet 24 of the injection hole 22 may be a long hole shape having a long axis b perpendicular to the flow direction of the swirl flow S. Specifically, the elongated hole shape of FIG. 4A is an elongated hole shape in which the upper end and the lower end of the rectangular long axis b direction (longitudinal direction) are formed in an arc shape.

  Or as shown in FIG.4 (b), the shape of the fuel outlet 24 of the nozzle hole 22 can also be made into the vertically long shape which a part of two ellipse couple | bonded. Specifically, the shape of the fuel outlet 24 in FIG. 4B is a shape in which the second ellipse is coupled to the lower side of the first ellipse, and more specifically, the length of the first ellipse. The first ellipse and the second ellipse are combined such that the end of the shaft and the end of the major axis of the second ellipse partially overlap. Note that the size of the first ellipse and the size of the second ellipse may be the same or different.

  Or as shown in FIG.4 (c), the shape of the fuel outlet 24 of the nozzle hole 22 can also be made into the vertically long shape where a part of two circles couple | bonded. Specifically, the shape of the fuel outlet 24 in FIG. 4C is such that the second circle is coupled to the lower side of the first circle. Note that the size of the first circle and the size of the second circle may be the same or different.

  In addition, although the specific value of the ratio (b / a) of the long axis b with respect to the vertically long short axis a is not specifically limited, in this embodiment, it is 1.2-5.0 as an example. A value within the range is used.

  Referring to FIG. 2A again, the nozzle hole 22 according to the present embodiment has a tapered shape in which the cross-sectional area decreases from the fuel inlet 23 side toward the fuel outlet 24 side. Specifically, the lengths of the short axis a and the long axis b of the injection hole 22 are reduced from the fuel inlet 23 side toward the fuel outlet 24 side, whereby the cross-sectional area of the injection hole 22 is reduced. The size is reduced from the side toward the fuel outlet 24 side. That is, in this case, the cross-sectional area of the fuel inlet 23 is the largest in one nozzle hole 22, and the cross-sectional area of the fuel outlet 24 is the smallest. This is the same not only when the shape of the fuel outlet 24 of the nozzle hole 22 is the shape shown in FIG. 2B but also when the shape is the shape shown in FIGS. 4A to 4C.

  The operational effects of the present embodiment described above are as follows. First, according to the present embodiment, as described above with reference to FIG. 2B and FIGS. 4A to 4C, the shape of the fuel outlets 24 of the plurality of injection holes 22 of the fuel injection valve 20 is as follows. The longitudinal shape is a shape in which the long axis b is perpendicular to the flow direction of the swirl flow S. As a result, as shown in FIG. 3B, the cross-sectional shape of the fuel spray F injected from the injection hole 22 is changed to a vertically long shape having a long axis b perpendicular to the flow direction of the swirl flow S. it can.

  Specifically, when the shape of the fuel outlet 24 of the nozzle hole 22 is the elliptical shape of FIG. 2B, as shown in FIG. 3B, the cross-sectional shape of the fuel spray F injected from the nozzle hole 22 Also, the elliptical shape having a long axis b perpendicular to the flow direction of the swirl flow S can be obtained. Further, when the shape of the fuel outlet 24 of the nozzle hole 22 is the shape shown in FIGS. 4A to 4C, the cross-sectional shape of the fuel spray F injected from the nozzle hole 22 is also the swirl flow S. It can be made into the vertically long shape of Fig.4 (a)-FIG.4 (c) which has the long axis b perpendicular | vertical with respect to a flow direction.

In this case, as shown in FIG. 3B, a large vortex that is a large secondary flow due to the swirl flow S on the back side of the fuel spray F (on the downstream side of the fuel spray F in the flow direction of the swirl flow S). Can be generated. As a result, oxygen in the combustion chamber 6 can be effectively taken into the fuel spray F by the large vortex.

  Further, according to the present embodiment, as described above with reference to FIG. 2A, the cross-sectional area of the injection hole 22 is reduced from the fuel inlet 23 side toward the fuel outlet 24 side, so that the fuel spray F spreads. The angle θ (this is an angle formed by the lateral direction (short axis a direction) of the fuel spray F and is illustrated in FIG. 3A), that is, the layer thickness of the fuel spray F is thick. It can be suppressed. As a result, the distance between the adjacent fuel sprays F can be increased, so that the adjacent fuel sprays F overlap each other, and the oxygen present between the adjacent fuel sprays F is exchanged between the adjacent fuel sprays F. Therefore, it is possible to suppress oxygen shortage. As a result, oxygen in the combustion chamber 6 can be more effectively taken into the fuel spray F.

  From the above, according to the present embodiment, the fuel spray F injected into the combustion chamber 6 can be sufficiently mixed with the oxygen in the combustion chamber 6 to effectively suppress the generation of soot during combustion. can do.

  In the present embodiment, the injection pressure when the fuel injection valve 20 injects fuel is not particularly limited, but the higher the injection pressure, the more stably the shape of the injected fuel spray F is maintained. It is preferable in that it can be performed.

  Moreover, the larger vortex by the swirl flow S formed on the back side of the fuel spray F can be generated more stably as the swirl ratio of the swirl flow S is higher. Therefore, it is preferable that the swirl ratio of the swirl flow S is as high as possible. The swirl ratio can be increased by adjusting the shape of the intake port 7 and the shape of the combustion chamber 6. Alternatively, when the internal combustion engine 1 includes a variable swirl device that can change the swirl ratio of the swirl flow S, the swirl ratio can also be increased by using this variable swirl device.

(Modification 1 of embodiment)
Fig.5 (a) is a front view which shows typically the state which visually recognized the fuel exit 24a of the fuel injection valve 20a which concerns on the modification 1 of the said embodiment from the A side of Fig.2 (a). Here, in the case of the combustion chamber 6 of the internal combustion engine 1 to which the fuel injection valve 20a according to the present modification is applied, the flow rate of the swirl flow S has a flow velocity distribution that is faster on the upper side of the combustion chamber 6 than on the lower side. Have. The fuel injection valve 20a according to the present modification has a shape in which the upper side of the longitudinal long axis b of the fuel outlet 24a is inclined to the upstream side in the flow direction of the swirl flow S from the lower side. This is different from the fuel injection valve 20 shown in FIG. Since the other structure of the fuel injection valve 20a is the same as that of the fuel injection valve 20, description of this other structure is abbreviate | omitted.

  According to the fuel injection valve 20a, the cross-sectional shape of the fuel spray F injected from the fuel outlet 24a is formed into a vertically long shape in which the upper side of the long axis b is inclined to the upstream side in the flow direction of the swirl flow S from the lower side. it can.

  In addition, although the specific value of the inclination angle with respect to the axis 100 of the major axis b of the fuel outlet 24a is not specifically limited, in this modification, as an example, it is 45 with respect to the axis 100 of the fuel injection valve 20a. An angle selected from the range below ° is used. The specific value of the inclination angle of the major axis b with respect to the axis 100 is preferably set to an appropriate value in consideration of the vertical flow velocity difference of the swirl flow S in the fuel chamber 6.

Also in this modification, a large vortex that is a large secondary flow due to the swirl flow S can be generated on the back side of the fuel spray F. As a result, the fuel spray F injected into the combustion chamber 6 can be sufficiently mixed with the oxygen in the combustion chamber 6 by the large vortex, so that the oxygen in the combustion chamber 6 is effectively contained in the fuel spray F. Can be imported.

  Also in the fuel injection valve 20a, since the cross-sectional area of the injection hole 22 is reduced from the fuel inlet 23 side toward the fuel outlet 24a side, the spread angle θ of the fuel spray F can be suppressed from increasing. Thereby, since the oxygen in the combustion chamber 6 can be more effectively taken into the inside of the fuel spray F, the fuel spray F can be sufficiently mixed with the oxygen in the combustion chamber 6, so Can be effectively suppressed.

  Moreover, according to this modification, the following effects can also be produced. Specifically, in the case of this modification, the flow rate of the swirl flow S has a higher flow velocity distribution on the upper side of the combustion chamber 6 than on the lower side, so that the upper side of the fuel spray F is on the lower side. The moving speed by the swirl flow S becomes faster than that. That is, in the case of this modification, the upper side of the fuel spray F has a longer moving distance in the flow direction of the swirl flow S than the lower side. In this regard, according to this modification, the cross-sectional shape of the fuel spray F can be a vertically long shape in which the upper side of the long axis b is inclined upstream in the flow direction of the swirl flow S from the lower side. Compared to the case where the cross-sectional shape of F is not this shape, the shape of the fuel spray F can be prevented from being broken from the vertically long shape under the influence of the flow velocity distribution of the swirl flow S. Therefore, according to this configuration, a beautiful large vortex can be generated, and oxygen in the combustion chamber 6 can be more effectively taken into the fuel spray F by the large vortex. Thereby, the fuel spray F injected into the combustion chamber 6 can be sufficiently mixed with the oxygen in the combustion chamber 6, and soot generation during combustion can be more effectively suppressed.

(Modification 2 of embodiment)
FIG.5 (b) is a front view which shows typically the state which visually recognized the fuel exit 24b of the fuel injection valve 20b which concerns on the modification 2 of the said embodiment from the A side of Fig.2 (a). In the case of the combustion chamber 6 of the internal combustion engine 1 to which the fuel injection valve 20b according to this modification is applied, the flow velocity of the swirl flow S has a flow velocity distribution that is faster on the lower side of the combustion chamber 6 than on the upper side. Yes.

  The fuel injection valve 20b according to the present modification has a shape in which the lower side of the longitudinal long axis b of the fuel outlet 24b is inclined to the upstream side in the flow direction of the swirl flow S from the upper side. This is different from the fuel injection valve 20 shown in FIG. Since the other structure of the fuel injection valve 20b is the same as that of the fuel injection valve 20, description of this other structure is abbreviate | omitted.

  Also in this modified example, a large vortex, which is a large secondary flow due to the swirl flow S, can be generated on the back side of the fuel spray F, so that the fuel spray F injected into the combustion chamber 6 is caused by the large vortex. The oxygen in the combustion chamber 6 can be sufficiently mixed with the oxygen, and the oxygen in the combustion chamber 6 can be effectively taken into the fuel spray F.

  Also in the fuel injection valve 20b, since the cross-sectional area of the injection hole 22 is reduced from the fuel inlet 23 side toward the fuel outlet 24b side, the spread angle θ of the fuel spray F can be suppressed from increasing. Thereby, since the oxygen in the combustion chamber 6 can be more effectively taken into the inside of the fuel spray F, the fuel spray F can be sufficiently mixed with the oxygen in the combustion chamber 6, so Can be effectively suppressed.

  Further, according to this modification, the flow rate of the swirl flow S has a faster flow velocity distribution on the lower side of the combustion chamber 6 than on the upper side, so that the lower side of the fuel spray F is higher than the upper side. Also, the moving speed due to the swirl flow S increases. That is, in the case of this modification, the lower side of the fuel spray F has a longer moving distance in the flow direction of the swirl flow S than the upper side.

In this regard, according to this modification, the cross-sectional shape of the fuel spray F can be a vertically long shape in which the lower side of the long axis b is inclined to the upstream side in the flow direction of the swirl flow S from the upper side. Compared to the case where the cross-sectional shape of F is not this shape, the shape of the fuel spray F can be prevented from being broken from the vertically long shape under the influence of the flow velocity distribution of the swirl flow S. Therefore, according to this configuration, a beautiful large vortex can be generated, and oxygen in the combustion chamber 6 can be more effectively taken into the fuel spray F by the large vortex. Thereby, the fuel spray F injected into the combustion chamber 6 can be sufficiently mixed with the oxygen in the combustion chamber 6, and soot generation during combustion can be more effectively suppressed.

  In this modification as well, the specific value of the inclination angle of the long axis b with respect to the axis 100 is set to an appropriate value in consideration of the vertical flow velocity difference of the swirl flow S in the fuel chamber 6. Is preferred.

(Modification 3 of embodiment)
In addition, in the said embodiment and the modifications 1 and 2 of embodiment, the fuel injection valve 20, 20a, 20b may divide | segment and inject a fuel twice or more. For example, a detailed description will be given by taking, for example, a case where two split injections are executed. The fuel injection valves 20, 20a, 20b receive pilot instructions or pre-injections as the first fuel injection in response to an instruction from the control device. And main injection that is the second fuel injection.

  According to this modified example, not only the oxygen in the combustion chamber 6 but also the fuel injected by pilot injection or pre-injection by the large swirl of the swirl flow S formed on the back surface of the fuel spray F injected by main injection. OH radicals generated by the combustion of the spray F can also be taken into the fuel spray F injected by the main injection. As a result, the fuel spray F injected by the main injection can be burned more effectively, and the generation of soot during the combustion of the main injection can be more effectively suppressed.

  Although the preferred embodiments of the present invention have been described above, the present invention is not limited to such specific embodiments, and various modifications and changes can be made within the scope of the gist of the present invention described in the claims. Is possible.

1 Internal combustion engine 6 Combustion chamber 20, 20a, 20b Fuel injection valve 22 Injection hole 23 Fuel inlet 24, 24a, 24b Fuel outlet

Claims (3)

In a fuel injection valve that injects fuel toward a combustion chamber of an internal combustion engine where a swirl flow is formed,
The shape of the fuel outlet of the plurality of nozzle holes of the fuel injection valve is a vertically long shape,
The vertically long shape is a shape in which the long axis of the vertically long shape is perpendicular or inclined with respect to the flow direction of the swirl flow,
The fuel injection valve for an internal combustion engine, wherein the cross-sectional area of the nozzle hole is reduced from the fuel inlet side to the fuel outlet side of the nozzle hole.   2. The fuel injection valve for an internal combustion engine according to claim 1, wherein the vertically long shape is any one of an elliptical shape, a long hole shape, a shape in which a part of two ellipses are combined, or a shape in which a part of two circles are combined. .   An internal combustion engine comprising the fuel injection valve according to claim 1.

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