JP6747370B2 - Fuel injection valve - Google Patents

Description

The present invention relates to a fuel injection valve.

In a fuel injection valve that injects fuel into a combustion chamber of an internal combustion engine, various technical improvements have been made in order to optimize the form of fuel spray in the combustion chamber. For example, in the fuel injection valve described in Patent Document 1, a spiral swirl groove is provided on an outer peripheral portion of a needle that is reciprocally accommodated in a nozzle body, and thus a fuel flow that has passed through a seat portion is formed. A swirl component is applied, and by swirling the fuel, a fuel spray having high dispersion characteristics is formed.

JP, 10-176631, A

However, the fuel injection valve of Patent Document 1 is configured to uniformly provide high dispersion characteristics in any fuel injection state at the time of fuel injection. Therefore, even in a situation where it is desirable to form a spray in a strong penetration state instead of a spray in a highly dispersed state at the time of fuel injection, that cannot be realized. For example, if the spray penetration is insufficient during high-load operation of the internal combustion engine, combustion concentrates in a region near the fuel injection valve inside the combustion chamber. As a result, there is a possibility that the amount of oxygen is locally insufficient, causing problems such as a decrease in output and an increase in smoke due to a decrease in combustion speed. In addition, when the internal combustion engine is operating at low load, if the penetration of the spray is excessive, heat escape near the wall surface inside the combustion chamber increases, which may cause a problem such as deterioration of fuel efficiency due to a decrease in efficiency.

The present invention has been made in view of the above problems, and a main object thereof is to provide a fuel injection valve capable of appropriately switching fuel spray.

A fuel injection valve according to the present disclosure includes a body having a tubular shape and a sack chamber at a tip portion thereof and an injection hole extending from the sac chamber, and a valve body reciprocally provided in the body, and the valve body is A fuel injection valve for injecting fuel from the injection hole by separating from a state of being seated on the inner peripheral surface of the body, wherein the valve element has a through passage extending in an axial direction thereof. The passage inlet of the through passage is provided downstream of the seat portion of the valve body seated on the inner peripheral surface of the body and upstream of the suck chamber.

According to the above configuration, when the valve body is separated from the inner peripheral surface of the body when the fuel injection valve is opened, the fuel can flow into the suck chamber through two routes. One path is a path that passes through a gap between the inner peripheral surface of the body and the outer peripheral surface of the valve body, and the other path is a path that passes through a through passage provided in the valve body. In particular, regarding the through passage, since the passage inlet is provided downstream of the seat portion of the valve body and upstream of the suck chamber, whether fuel flows into the through passage or not Are switched according to the lift amount of the valve body. In other words, when the lift amount of the valve body is relatively small, the gap between the inner peripheral surface of the body and the outer peripheral surface of the valve body is small, so that the fuel easily flows into the through passage, and the fuel flows through the through passage to the sack. Flows into the room. In addition, when the lift amount of the valve body is relatively large, the gap between the inner peripheral surface of the body and the outer peripheral surface of the valve body is large, so that it is difficult for fuel to flow into the through passage, and the fuel is prevented from passing through the through passage. Instead, it flows into the suck chamber through the gap between the inner peripheral surface of the body and the outer peripheral surface of the valve body.

Here, when the fuel flows into the sack chamber through the through passage, the fuel is likely to collide with or stay in the sack chamber, and fuel is injected from the injection holes in the state where the fuel flow is disturbed. Therefore, the fuel spray in a highly dispersed state can be formed in the combustion chamber. On the other hand, when the fuel flows into the sack chamber through the gap between the inner peripheral surface of the body and the outer peripheral surface of the valve body without passing through the through passage, the fuel flows directly through the sac chamber. Since it flows into the injection hole, it is possible to form a fuel spray in a strong penetration state in the combustion chamber. As described above, it is possible to realize a fuel injection valve capable of appropriately switching the fuel spray.

Sectional drawing which shows the structure of the front-end|tip part of a fuel injection valve. (A) is a perspective view showing the tip configuration of the needle, and (b) is a front view of the needle as seen from the tip side. The figure for giving a supplementary explanation of the structure of a needle. (A) is a figure which shows the flow of fuel when the lift amount of a needle is small, (b) is a figure which shows a fuel flow when the lift amount of a needle is small. (A) is a figure which shows the fuel spray when the lift amount of a needle is small, (b) is a figure which shows a fuel spray when the lift amount of a needle is small. The figure which shows the structure around the combustion chamber of an engine. The figure which shows the structure of the needle in another example. The figure which shows the structure of the needle in another example. The figure which shows the structure of the needle in another example.

Hereinafter, embodiments will be described with reference to the drawings. This embodiment embodies a fuel injection valve used in a diesel engine for a vehicle, and the fuel injection valve operates by opening in response to a valve opening command signal from an electronic control unit (ECU). , The high pressure fuel accumulated in the common rail is injected into the engine combustion chamber. FIG. 6 is a diagram showing the configuration around the combustion chamber of the engine.

In FIG. 6, a piston 12 is housed in a cylinder 11 of the engine, and a combustion chamber 13 is formed on the upper surface side of the piston 12. A recess 12a (cavity) is formed on the upper surface of the piston 12 so as to extend radially from the center. The fuel injection valve 20 realizes so-called center injection, and is provided at a position substantially in the center of the combustion chamber 13 in the cylinder head 14 above the piston 12. The fuel injection valve 20 has a cylindrical nozzle holder 21 and a nozzle body 22 held by the nozzle holder 21 as a configuration of the tip end portion thereof, and as shown in the drawing, the nozzle body 21 is radially formed from the tip end portion of the nozzle body 22. The fuel spray F is injected.

FIG. 1 is an enlarged cross-sectional view showing a configuration of a main part of a tip portion of the fuel injection valve 20. In the fuel injection valve 20, the nozzle body 22 is formed in a cylindrical shape with a bottom, and as the inner peripheral surface thereof, an inner wall surface 23 extending along the central axis J with the same diameter, and an inner diameter decreasing as it approaches the tip. It has a conical conical surface 24 and a concave surface 25 formed in a concave shape at the bottom of the tubular portion. The accommodating chamber 26 in the nozzle body 22 accommodates a needle 30 as a valve body, and the conical surface 24 serves as a valve seat portion that abuts the needle 30. A portion surrounded by the concave surface 25 is a suck chamber 27.

A plurality of injection holes 28, which extend from the suck chamber 27 and open to the outer surface of the nozzle body, are formed at the tip of the nozzle body 22. The injection holes 28 are provided so as to extend radially from the central axis J of the fuel injection valve 20, and are provided, for example, at several positions or at ten or more positions evenly in the circumferential direction. The concave surface 25 that surrounds the suck chamber 27 has a curved portion serving as a bottom portion, and a side wall portion other than the bottom portion and extending along the central axis J, of which each injection hole 28 is formed. ing. However, each injection hole 28 may be formed at the bottom (curved portion). Each injection hole 28 is provided so as to extend in a direction intersecting with the central axis J, and an angle θ formed by the central axis J and the extending direction of the injection hole 28 on the axial front end side of the fuel injection valve 20 is: It is in the range of 45 to 90°.

The suck chamber 27 and each injection hole 28 are always in communication with each other regardless of the lift state of the needle 30. The suck chamber 27 serves as a distribution chamber that distributes fuel to the injection holes 28 when the fuel injection valve 20 is opened.

The needle 30 is housed in the housing chamber 26 in the nozzle body 22 so as to be capable of reciprocating in the axial direction. The needle 30 is arranged coaxially with the nozzle body 22. The needle 30 has a substantially cylindrical shape, and has a shaft portion 31 having the same outer diameter dimension, and a conical cone portion 32 whose outer diameter is reduced toward the tip on the tip side of the shaft portion 31. ing.

The conical portion 32 has two tapered portions 33 and 34 having different inclination angles with respect to the central axis J. For the sake of convenience, the tapered portions 33 and 34 will be also referred to as an upper tapered portion 33 and a lower tapered portion 34 below. The lower taper portion 34 has a larger inclination angle with respect to the central axis J than the upper taper portion 33. Compared with the inclination angle of the conical surface 24 of the nozzle body 22, the inclination angle of the upper tapered portion 33 is smaller than the inclination angle of the conical surface 24, and the inclination angle of the lower tapered portion 34 is smaller than the inclination angle of the conical surface 24. Is also getting bigger. In this case, the upper end portion of the lower taper portion 34, that is, the boundary portion between the upper taper portion 33 and the lower taper portion 34 is the seat portion 34a, and in the valve closed state shown in FIG. The seat portion 34a of the above contacts.

In the valve closed state shown in FIG. 1, a part of the tip end side of the lower taper portion 34 of the needle 30 projects into the sac chamber 27. The tip surface 35 of the needle 30 is located closer to the tip side in the axial direction than the inner opening of the injection hole 28. The tip surface 35 is a flat surface extending in a direction orthogonal to the axial direction.

In the fuel injection valve 20, a fuel passage is formed between the inner peripheral surface of the nozzle body 22 and the outer peripheral surface of the needle 30, and the lower taper portion 34 (the seat portion) with respect to the conical surface 24 on the nozzle body 22 side is formed. (34a) is seated, fuel injection from the injection hole 28 is stopped, and fuel is injected from the injection hole 28 as the lower taper portion 34 (seat portion 34a) separates from the conical surface 24. To be done.

Further, the needle 30 has a through passage 36 extending in the axial direction thereof. That is, a plurality of (eight in this embodiment) penetrating passages 36 are formed in the lower tapered portion 34 of the needle 30 so as to penetrate the needle 30 and linearly communicate with two axially different positions. Has been formed. The through passage 36 is provided in a direction oblique to the central axis J. In this case, the injection hole 28 is provided at a position different from the extension line extending the axis of the through passage 36. The plurality of through passages 36 are respectively formed so as to face a predetermined range (tip surface 35) including the central axis J of the needle 30 in the axial direction of the needle 30.

In the needle 30, a passage inlet 36a is provided on the outer surface of the lower taper portion 34, and a passage outlet 36b is provided on the tip surface 35. A linear through passage is provided between the passage inlet 36a and the passage outlet 36b. 36 is formed. The inclination angle of the through passage 36 with respect to the central axis J is larger than the inclination angle of the outer surface of the lower taper portion 34. The passage inlets 36 a are provided in the same number as the through passages 36, while the passage outlet 36 b is provided in common in each of the through passages 36. As shown in FIG. 2, the through passages 36 are radially formed from the central axis J at equal intervals in the circumferential direction.

The diameter of the through passage 36 is, for example, about 0.1 mm. The diameter of the passage outlet 36b may be the same as the diameter of the through passage 36, but may be larger than the diameter of the through passage 36. The diameter of the passage outlet 36b is, for example, about 0.2 mm.

The passage inlet 36a of the through passage 36 is provided downstream of the seat portion 34a and upstream of the suck chamber 27. The passage inlet 36a is preferably provided such that at least a part of the passage inlet 36a is upstream of the suck chamber 27 (in the axial direction, opposite to the tip end of the suck chamber 27 in the valve closed state).

Since the passage inlet 36a is provided in the lower tapered portion 34 of the tapered portions 33 and 34 of the conical portion 32, the fuel is prevented from flowing into the through passage 36 in the valve closed state. The passage inlet 36a is provided at a position facing the conical surface 24 of the nozzle body 22. In other words, the needle 30 has a facing portion that faces the conical surface 24 of the nozzle body 22 in a close state from the seat portion 34a to a portion serving as an inlet of the suck chamber 27, and the passage inlet 36a is provided in the facing portion. Has been.

Further, as described above, the tip end portion of the needle 30 is accommodated in the sac chamber 27 in a protruding state, and the passage outlet 36b is provided at the protruding portion of the needle 30 protruding into the sac chamber 27. In this case, since the tip end surface 35 of the needle 30 is located closer to the tip end side than the inner opening of the injection hole 28 in the valve closed state, the passage outlet 36b is also more tip end than the inner opening of the injection hole 28. Located on the side. Further, in the valve closed state, the passage outlet 36b is provided on the tip side of the injection hole 28 in the axial direction of the needle 30.

The configuration relating to the through passage 36 will be further described with reference to FIG. In FIG. 3, D1 is the outer diameter dimension of the seat portion 34a of the needle 30. D2 is an outer diameter dimension of a portion connecting the outermost peripheral position of the passage inlet 36a of the through passage 36. D3 is the outer diameter dimension of the inlet of the suck chamber 27.

Here, comparing the above D1 to D3, D1>D2. Therefore, in the valve closed state, that is, in the state where the needle 30 is seated on the nozzle body 22, the inflow of fuel into the through passage 36 is blocked. Also, D2>D3. Therefore, the passage outlets 36b of the respective through passages 36 are concentrated near the central axis J of the needle 30, and fuel collision easily occurs near the central axis J.

Next, the manner of fuel injection when the fuel injection valve 20 is opened will be described with reference to FIGS. 4 and 5. In the fuel injection valve 20 of the present embodiment, when fuel injection is performed with the valve opening operation of the needle 30, two fuels, a through passage 36 of the needle 30 and a clearance passage between the nozzle body 22 and the needle 30, are used. Fuel injection is performed using the passage, and which of the two fuel passages the fuel passes through can be switched according to the lift amount of the needle 30. 4 and 5, (a) shows a state where the lift amount of the needle 30 is relatively small, and (b) shows a state where the lift amount of the needle 30 is relatively large. In other words, (a) of FIGS. 4 and 5 shows the state in the initial period of the start of fuel injection, and (b) shows the state after the initial period of the start of fuel injection.

In FIG. 4A, since the lift amount of the needle 30 is small, the separation distance of the lower tapered portion 34 of the needle 30 from the conical surface 24 of the nozzle body 22, that is, the nozzle body 22 and the needle 30 closely oppose each other. The gap distance between parts is small. Therefore, the fuel flowing from the upstream side of the fuel injection valve 20 preferentially flows into the through passage 36. Then, the fuel that has passed through the through passage 36 enters the suck chamber 27, and is injected from the injection hole 28 via the suck chamber 27.

In this case, since the fuel enters the suck chamber 27 from the tip end surface 35 of the needle 30, the fuel does not flow directly into the injection hole 28, but once circulates inside the suck chamber 27, and then the injection hole 28. Flow into. Therefore, the fuel collides or stays in the sac chamber 27, which causes turbulence in the fuel flow. In particular, the passage outlet 36b is provided on the tip side of the injection hole 28 in the axial direction of the needle 30, and the injection hole 28 is provided at a position different from the extension of the extension of the axis of the through passage 36. Since each through passage 36 is formed so as to face a predetermined range including the central axis J of the needle 30, a situation in which the turbulence of the fuel flow in the suck chamber 27 is likely to occur is suitably created. It is like this.

In such a situation, as shown in FIG. 5A, a highly dispersed spray is formed in the combustion chamber. In this case, the fuel spray can be separated from the wall surface (for example, the recess wall surface of the piston 12) in the combustion chamber, and it is possible to suppress the heat escape to the wall surface during the combustion of the fuel.

Further, in FIG. 4B, since the lift amount of the needle 30 is large, the distance between the lower tapered portion 34 of the needle 30 and the conical surface 24 of the nozzle body 22, that is, the nozzle body 22 and the needle 30 are close to each other. The gap distance between the facing parts is large. Therefore, the fuel flowing from the upstream side in the fuel injection valve 20 does not flow into the through passage 36 and passes through the clearance passage between the nozzle body 22 and the needle 30. Then, the fuel directly flows into the injection hole 28 from the clearance passage and is injected from the injection hole 28. In this case, the turbulence of the fuel flow is less likely to occur in the suck chamber 27.

In such a situation, as shown in FIG. 5(b), a spray in a strong penetration state is formed in the combustion chamber. In this case, the fuel spray can reach the wall surface (for example, the wall surface of the concave portion of the piston 12) in the combustion chamber, and the air (oxygen) in the combustion chamber including the air (oxygen) near the wall surface can be effectively used when the fuel is burned. It can be used up.

Comparing FIGS. 4(a) and 4(b), the ratio of the amount of fuel passing through the through passage 36 in the amount of injected fuel is different, and thus the amount of lift of the needle 30 is smaller in FIG. 4(a). However, the proportion of fuel passing through the through passage 36 increases. In short, in the fuel injection valve 20 configured as described above, the smaller the lift amount of the needle 30, the larger the proportion of the fuel passing through the through passage 36, and the larger the lift amount of the needle 30, the more the fuel passing through the through passage 36. The ratio becomes smaller.

In the fuel injection control executed by the ECU, the fuel injection amount is controlled based on the engine rotation speed and the load, and the fuel injection amount is increased as the engine rotation speed increases or the load increases. In consideration of such fuel injection control, it is conceivable that the injection pulse becomes long in the high rotation state or the high load state, so that the hard penetration injection is performed. Further, in the low rotation state or the low load state, since the injection pulse becomes short, it is considered that the high dispersion injection is performed.

According to this embodiment described in detail above, the following excellent effects are obtained.

In the fuel injection valve 20, when the valve is opened, the fuel is circulated through two routes to inject the fuel. In this case, one path is a path that passes through the gap between the inner peripheral surface of the body and the outer peripheral surface of the needle, and the other path is a path that passes through the through passage 36 of the needle 30. As for the through passage 36, since the passage inlet 36a is provided on the downstream side of the seat portion 34a of the needle 30 and on the upstream side of the suck chamber 27, fuel flows into the through passage 36 or does not flow into the through passage 36. It is possible to switch between them depending on the lift amount of the needle 30. When the fuel flows into the suck chamber 27 via the through passage 36, the fuel spray in the highly dispersed state can be formed due to the disturbance of the fuel flow in the suck chamber 27. Further, when the fuel flows into the suck chamber 27 through the gap between the inner peripheral surface of the body and the outer peripheral surface of the needle without passing through the through passage 36, the fuel spray in the strong penetration state is formed. be able to. As described above, the fuel injection valve 20 capable of appropriately switching the fuel spray can be realized.

In the needle 30, since the passage inlet 36a of the through passage 36 is provided in the facing portion that closely faces the inner peripheral surface (conical surface 24) of the nozzle body 22, the through passage is provided in a situation where the lift amount of the needle 30 is relatively small. It is possible to preferably realize the inflow of the fuel into 36.

Since the passage outlet 36b of the through passage 36 is provided at the protruding portion of the needle 30 that protrudes into the sac chamber 27, when the fuel flows into the sac chamber 27 through the through passage 36, the fuel is supplied to the inner peripheral surface of the body. The fuel flows in at a position on the inner side of the suck chamber 27 as compared with the case where the fuel flows into the suck chamber 27 through the gap between the needle and the outer peripheral surface of the needle. Therefore, it is possible to preferably create a situation in which the turbulence of the fuel flow in the suck chamber 27 is likely to occur.

Since the passage outlet 36b of the through passage 36 is provided on the tip side of the injection hole 28 in the axial direction of the needle 30, the fuel flowing to the sac chamber 27 side through the through passage 36 flows to the tip side of the fuel injection valve 20. After flowing toward the injection hole 28, the flow returns (U-turn) to the injection hole 28. Therefore, it is possible to preferably create a situation in which the fuel flow in the suck chamber 27 is likely to be disturbed.

Since the injection hole 28 is provided at a position different from the extension of the extension of the axis of the through passage 36, the fuel passing through the through passage 36 does not directly reach the injection hole 28 but undergoes collision or retention and is injected into the injection hole. 28, and is injected from the injection hole 28 into the combustion chamber. As a result, a desired highly dispersed spray can be realized.

Since each of the through passages 36 is formed so as to face a predetermined range including the central axis J of the needle 30 in the axial direction of the needle 30, the fuel flowing to the sack chamber 27 side via each of the through passages 36 flows into the needle 30. Collisions easily occur near the central axis J. Therefore, the turbulence of the fuel flow is likely to occur in the suck chamber 27, and the fuel spray in a highly dispersed state can be preferably formed.

In the engine using the fuel injection valve 20 configured as described above, both high dispersion characteristic spray and strong penetration characteristic spray can be realized according to the operating state of the engine and the like. As a result, it is possible to improve the fuel consumption and the exhaust of the engine.

(Other embodiments)
The above embodiment may be modified as follows, for example.

A modified example of the through passage 36 in the needle 30 will be shown below. For example, in the configuration shown in FIG. 7, as a difference from the configuration of FIG. 2 described above, a passage outlet 36b is provided for each through passage 36. Also in this case, the plurality of through passages 36 are respectively formed so as to face a predetermined range (tip surface 35) including the central axis J of the needle 30 in the axial direction of the needle 30. Further, the tip end surface 35 of the needle 30 is not a flat surface but a conical circle. The tip surface 35 of the needle 30 may be a flat surface.

Further, the configuration shown in FIG. 8 is different from the configuration in FIG. 7 in that the through passages 36 are not provided at equal intervals in the circumferential direction but are provided at unequal intervals. In FIG. 8, each through passage 36 is provided by grouping two together.

Further, in the configuration shown in FIG. 9, the difference from the configuration of FIG. 7 is that the plurality of through passages 36 are provided so that extension lines extending the axis of each through passage 36 do not pass through the central axis J of the needle 30. Has been. However, the passage outlets 36b are all provided on the tip surface 35. In this case, the fuel flowing through the through passages 36 to the sac chamber 27 is swirled in the sac chamber 27 in a predetermined direction (clockwise in FIG. 9B). Therefore, the turbulence of the fuel flow is likely to occur in the suck chamber 27, and the fuel spray in a highly dispersed state can be preferably formed.

The plurality of through passages 36 provided in the needle 30 may not all have the same diameter, and a large diameter through passage 36 and a small diameter through passage 36 may be provided in a mixed manner. For example, in the needle 30, it is preferable to provide a large diameter through passage 36 and a small diameter through passage 36 alternately in the circumferential direction.

In the above-described embodiment, the passage outlet 36b of the through passage 36 in the needle 30 is provided closer to the tip side than the injection hole 28 in the needle axial direction, but this is changed so that the passage outlet 36b is formed in the needle axial direction. It may be provided at the same position as 28 or on the side of the tip opposite to the injection hole 28. In short, the passage outlet 36b is preferably provided in the vicinity of the injection hole 28 or on the tip side of the injection hole 28 in the axial direction of the needle 30.

In the fuel injection valve 20 of the above-described embodiment, the conical portion 32 of the needle 30 is configured by the two tapered portions 33 and 34 having different inclination angles with respect to the central axis J. The inclination angle may be constant over the entire area.

In the above embodiment, the fuel injection valve 20 is arranged in the center of the combustion chamber 13 in the engine to perform the center injection, but this may be changed. For example, the fuel injection valve 20 may be arranged at a position deviated from the center position of the combustion chamber 13, and the fuel injection may be performed from an oblique position of the combustion chamber 13. In such a case, in the fuel injection valve 20, the position and size of the injection hole 28 may be appropriately changed according to the direction of the spray for each injection hole 28, while the configuration regarding the through passage 36 of the needle 30 is the same.

The fuel injection valve 20 having the above configuration can be applied to, for example, a direct injection type gasoline engine in addition to the diesel engine.

20... Fuel injection valve, 22... Nozzle body, 27... Suck chamber, 28... Injection hole, 30... Needle (valve body), 34a... Seat part, 36... Through passage, 36a... Passage inlet.

Claims (7)

A body (22) having a tubular shape and a sack chamber (27) and an injection hole (28) extending from the sac chamber at a tip portion; and a valve body (30) reciprocally provided in the body When the valve body is separated from the seated state on the inner peripheral surface of the body, the fuel is caused to flow into the suck chamber through the gap between the inner peripheral surface of the body and the valve body, and the fuel is injected. A fuel injection valve (20) capable of being injected from a hole,
The valve body has a through passage (36) extending axially and radially inward thereof,
The passage inlet (36a) of the through passage is provided downstream of the seat portion (34a) seated on the inner peripheral surface of the body in the valve body and upstream of the suck chamber. and,
In a state where the valve body is separated, the fuel is supplied from the first flow path passing through the through passage to the injection hole side, and passes through a gap between the inner peripheral surface of the body and the valve body and A fuel injection valve capable of supplying fuel to the injection hole side from a second flow path that does not pass through a through passage . The valve body has a facing portion that faces the inner peripheral surface of the body in a close state from the seat portion to a portion that becomes the inlet of the suck chamber,
The fuel injection valve according to claim 1, wherein the passage inlet is provided in the facing portion. The tip portion of the valve body is accommodated in the sac chamber in a protruding state,
The fuel injection valve according to claim 1 or 2, wherein a passage outlet (36b) of the through passage is provided at a protruding portion of the valve body protruding into the suck chamber. The fuel injection valve according to claim 3, wherein the passage outlet is provided in the vicinity of the injection hole or on the tip side of the injection hole in the axial direction of the valve body. The fuel injection valve according to any one of claims 1 to 4, wherein the injection hole is provided at a position different from the extension line extending the axis of the through passage. As the through passage, the valve body has a plurality of through passages arranged at predetermined intervals in the circumferential direction,
The fuel injection valve according to claim 1, wherein each of the plurality of through passages is formed so as to face a predetermined range including a central axis of the valve body in an axial direction of the valve body. As the through passage, the valve body has a plurality of through passages arranged at predetermined intervals in the circumferential direction,
The plurality of through passages have passage outlets (36b) for each passage, and extension lines extending the axial lines of the through passages are provided so as not to pass through the central axis of the valve body. 5. The fuel injection valve according to any one of 5 above.

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