JP2006329029A - Injector - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an injector which can prevent an injection timing of a fuel from coming out of place. <P>SOLUTION: The injector (1) is provided with an electromagnetic operating valve (10) to control the fuel injection. The electromagnetic operating valve is provided with a valve body (17) having passages (17a, 17b and 17c) of the fuel, an armature (16) to open and close the passages of the fuel, and an exciting coil (13) to open and close the electromagnetic operating valve by displacing the armature with excitation. The armature is provided with a plate-like wing (16e). The valve body is provided with four openings (17c) which opens to an end face (17d) of the valve body in which the passages of the fuel are opposite to the wing. Three notches (16g) are provided in the wings to able to circulate the fuel from the openings. This structure makes the area of the wings not opposed to the openings substantially stable notwithstanding the relative position of the valve body for the notches of the wing. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an injector having an electromagnetically operated valve for controlling fuel injection, and is particularly suitable for application to an injector used in a diesel engine.

In recent years, environmental pollution due to exhaust gas from vehicles has become a problem, and in order to improve the environment, reduction of CO ₂ emissions and purification of exhaust gas from vehicles are being promoted. In particular, diesel engines are required to improve techniques such as high-pressure injection fuel and multi-stage injection for the problem. An electromagnetically operated valve of an injector that realizes them is required to have high responsiveness and a short injection interval. The armature, which is the drive part inside the electromagnetically operated valve, collides with the mating member after moving a certain distance when the valve is closed, but the bounce that occurs at this time adversely affects the accuracy and stability of the injection. give. By setting a certain range between the armature wing and the mating member, it is possible to generate squeeze force (fluid drag) moderately and achieve both responsiveness when opening and bounce reduction when closing Already done, there is a problem that the opposing area and squeeze force change due to the relative position difference between the armature wing and the body leak hole, resulting in a change in response and bounce reduction effect.

  The squeeze force will be described in more detail. FIG. 2 shows a partially enlarged side sectional view of the electromagnetically operated valve 10 included in the injector 1 shown in FIG. The structure, operation, and the like of the injector 1 and the electromagnetically operated valve 10 will be described later in detail in the description of the preferred embodiment, and only the portions necessary for describing the squeeze force will be described here. When the electromagnetic valve 10 is opened and the fuel in the oil passage 17a is allowed to escape to the discharge passage 22 through the oil passage 17b, the armature 16 is attracted to the stator 14 by excitation of the excitation coil 13, and the upward direction in FIG. The direction of the stator 14). Further, when the electromagnetically actuated valve 10 is closed and the release of the fuel in the oil passage 17a to the discharge passage 22 through the oil passage 17b is terminated, the coil springs 21 installed substantially at the center of each wing portion 16e. It moves downward (in the direction of the valve body 17) in FIG. 2 by the urging force. At this time, a minute gap D is formed between the lower surface 16 d of the armature and the upper surface 17 d of the valve body 17, and (squeeze force (fluid drag)) is generated in the gap by the flow of fuel.

  Since the above-mentioned gap distance D is very small, when the seat portion 18 which is a valve member is opened, the armature increases the volume between the facing surfaces between the armature 16 and the valve body 17 due to the lift of the seat portion 18. The inflow of fuel between 16 and the valve body 17 does not follow. Therefore, a negative pressure is generated between the facing surfaces of the armature 16 and the valve body 17. As a result, energization of the exciting coil 13 is started, and even when a magnetic attractive force is generated between the stator 14 and the armature 16, the armature 16 does not move until the magnetic attractive force becomes larger than the above negative pressure. Delay in valve opening timing. When the distance D of the gap is large, the drag acting in the direction opposite to the moving direction of the armature 16 due to the fluid between the armature 16 and the valve body 17 is reduced when the seat portion 18 which is the valve member is closed. , Bounce occurs. The bounce is a reciprocating motion in the axial direction of the armature 16 that is generated when the seat portion 18 is driven against the valve seat member 19 at a high speed by the biasing force of the coil spring 21. Since the seat portion 18 is hit against the valve seat member 19 at a high speed in a short period of time, bounce is repeatedly generated by the impact. As a result, energization of the exciting coil 13 is stopped, and the opening of the valve seat member 18 is not completely closed even when the magnetic attractive force disappears between the stator 14 and the armature 16. In other words, the time during which the fuel is released to the discharge passage 22 via the oil passage 17b increases, resulting in a delay in functional valve closing timing. The squeeze force depends mainly on the shape of the facing surface between the armature 16 and the valve body 17 and the distance D of the gap. Therefore, when both the responsiveness at the time of valve opening and the bounce reduction effect at the time of valve closing are achieved. In addition, a certain gap distance D is set according to the shapes of the armature 16 and the valve body 17.

  FIG. 10 is an explanatory view of the vicinity of the armature 16 of the electromagnetically operated valve 100 of the conventional example, and FIG. 10 is a view of the two parts of the armature 16 and the valve body 17 as viewed from above, and is a line A in FIG. It corresponds to a cross-sectional view along -A. Three wings 16e of the armature 16 are provided at intervals of 120 °, and a notch 16g is provided between the wings 16e. In the conventional example of FIG. 10 described above, there are three wings 16e of the armature 16 and three leak holes 17c of the valve body 17, which are symmetrical at 120 ° angular intervals. Since the armature 16 is movable in the rotational direction around the longitudinal axis of the injector 1 with respect to the fixed valve body 17, the armature blade portion 16e and the leak hole 17c have a relative positional difference. That is, the relative positional relationship between the armature wing 16e and the leak hole 17c changes. The squeeze force acts on the armature wing portion 16e, but does not occur in the portion of the wing portion 16e that is overlapped with the leak hole 17c.

  In the conventional example, an explanatory diagram when the rotatable armature 16 is rotated with respect to the valve body 17 is shown in FIG. 11, where the relative position difference is 0 ° (A) and the relative position difference is 30 ° (B). A similar view to FIG. 10 is shown. Further, in the conventional example, the change of the squeeze force (squeeze area ratio) when the relative position angle of the rotatable armature 16 with respect to the valve body 17 is changed is shown by a dotted line in FIG. In the case shown in FIG. 11A and the case shown in FIG. 11B, the squeeze force changes (the hatched portion is the squeeze force generation surface). That is, in the case of FIG. 11B (relative position difference of 30 °), the squeeze area is smaller by the area of the leak hole 17c than in the case of FIG. 11A (relative position difference of 0 °). The ratio (the ratio of the effective squeeze area at a predetermined relative position angle with respect to the valve body 17 of the rotatable armature 16 to the area when the effective squeeze area is maximum) decreases (see the dotted line in FIG. 4). This change in the squeeze area ratio causes fluctuations in the squeeze force, resulting in variations in valve opening timing and functional valve closing timing. When the electromagnetically operated valve is applied to the fuel injection device (injector 1), if the valve opening timing and the functional valve closing timing vary, the fuel injection timing deviates from the predetermined timing. There is a risk that harmful gases will be discharged from the gas or particulate matter may be discharged.

Moreover, although there exists a prior art regarding the electromagnetically operated valve of the injector for engines (for example, refer patent document 1), the proposal of this invention is not disclosed.
JP 2002-139168 A

  The present invention has been made in view of the above-described circumstances, and the above problem is that the squeeze force generation area between the armature wing and the valve body end is a relative position between the armature wing and the leak hole of the valve body. It is an object of the present invention to provide an injector capable of preventing a delay in fuel injection timing by reducing the change in the relative position difference of the squeeze generation area by paying attention to the occurrence due to the change due to the difference.

  In the form of claim 1 of the present invention, in order to achieve the above-mentioned object, the injector (1) includes an electromagnetically operated valve (10) for controlling fuel injection, and the electromagnetically operated valve (10) A valve body (17) provided with at least one fuel passage (17a, 17b, 17c); an armature (16) for opening and closing the fuel passage (17a, 17b, 17c) of the valve body (17); An excitation coil (13) that is energized and energized and that opens and closes the electromagnetic valve (10) by displacing the armature (16) by excitation. The armature (16) includes a plate-like wing (16e), and the valve body (17) includes the fuel passage (17c) of the valve body (17) as the wing (16e). At least one opening (17c) that opens on the end surface (17d) of the valve body (17) that faces the wing (16e), and at least one notch (16g) is provided in the wing (16e). The fuel from the opening (17c) is allowed to flow. Regardless of the relative position of the opening (17c) of the valve body (17) with respect to the notch (16g) of the wing (16e), the area of the wing (16e) not facing the opening (17c) is The notch (16g) and the opening (17c) are arranged so as to be substantially constant.

  With this configuration, the squeeze force generation area between the armature wing and the end of the valve body can be reduced by changing the relative position difference between the armature wing and the opening of the valve body. Deviation of the injection timing can be prevented. As a result, the fuel is incompletely burned, and harmful gases are discharged from the internal combustion engine and particulate matter is prevented from being discharged.

  According to a first aspect of the present invention, the injector (1) comprises an electromagnetically operated valve (10) for controlling fuel injection, the electromagnetically operated valve (10) comprising at least one fuel passage (17a, A valve body (17) provided with 17b, 17c), an armature (16) for opening and closing the fuel passage (17a, 17b, 17c) of the valve body (17), and energized and energized, And an exciting coil (13) that opens and closes the electromagnetic valve (10) by displacing the armature (16) by excitation. The armature (16) includes a plate-shaped wing (16e). The valve body (17) has at least two openings in which the fuel passage (17c) of the valve body (17) opens on an end surface (17d) of the valve body (17) facing the wing (16e). (17c). The wing (16e) is provided with at least one notch (16g) to allow the fuel from the opening (17c) to flow. At least one of the openings (17c) is formed so as to be always disposed at a position overlapping the wing (16e).

  With this configuration, the opening is arranged so that the notch of the armature wing part and the opening of the valve body end part do not completely overlap, so the squeeze force generating area between the wing part and the valve body end part However, it is possible to reduce the change due to the relative position difference between the armature wing and the opening of the valve body, thereby preventing the fuel injection timing from deviating. Accordingly, it is possible to prevent harmful gas emission and particulate matter emission from the internal combustion engine due to incomplete combustion of fuel.

According to a third aspect of the present invention, in any of the first and second aspects, the wing portion (16e) is partitioned into a plurality of regions by the notches (16g), and the plurality of regions And the number of the openings (17c) of the valve body (17) are different.
According to this embodiment, by making the number of notches (that is, the number of wing regions) and the number of openings different from each other, the positions of the openings and the notches are all matched, and the squeeze area Is reduced, and the fluctuation range of the squeeze force is reduced.

In the form of Claim 4 of this invention, in the form in any one of the said Claim 1 to 3, the said notch (16g) which divides the said wing | blade part (16e) is arrange | positioned symmetrically at equal angular intervals, The openings (17c) of the valve body (17) are also arranged symmetrically at equal angular intervals.
According to this embodiment, the same effects as those of the first embodiment can be exhibited, and a balanced arrangement of the armature and the valve body can be achieved.

According to a fifth aspect of the present invention, in the third aspect, the valve body (17) is provided with three openings (17c) symmetrically at an angular interval of 120 °, and the wings (16e). The four notches (16g) are provided symmetrically at 90 ° angular intervals.
According to this form, the structure of the armature and valve body which actualize this invention more is disclosed.

According to a sixth aspect of the present invention, in any one of the first to fifth aspects, a groove is formed on the end surface (17d) of the valve body (17) on the arrangement track of the openings (17c). (17h) is provided.
According to this embodiment, another configuration of an armature and a valve body that further embodies the present invention is disclosed.

According to a seventh aspect of the present invention, in any one of the first to fifth aspects, the end surface (16e) of the wing portion (16e) facing the end surface (17d) of the valve body (17) ( 16d), a groove (16h) is provided on a track corresponding to the array track of the openings (17c).
According to the present embodiment, still another configuration of an armature and a valve body that further embodies the present invention is disclosed.

  In an eighth aspect of the present invention, the injector (1) includes an electromagnetically operated valve (10) for controlling fuel injection, and the electromagnetically operated valve (10) includes at least one fuel passage (17a, A valve body (17) provided with 17b, 17c), an armature (16) for opening and closing the fuel passage (17a, 17b, 17c) of the valve body (17), and energized and energized, And an exciting coil (13) that opens and closes the electromagnetic valve (10) by displacing the armature (16) by excitation. The armature (16) includes a plate-shaped wing (16e). The valve body (17) has at least one opening in which the fuel passage (17c) of the valve body (17) opens on an end surface (17d) of the valve body (17) facing the wing (16e). (17c). The wing (16e) is provided with at least one notch (16g) to allow the fuel from the opening (17c) to flow. In at least one of the end surface (17d) of the valve body (17) or the end surface (16d) of the wing portion (16e) facing the end surface (17d) of the valve body (17), the opening (17c ) Is provided on the orbital arrangement track (17h, 16h).

  With this configuration, the presence of grooves on the array track where the squeeze area is reduced due to the facing of the opening causes the fluid between the wing and the end of the valve body even in the portion not facing the opening. Since the flow resistance is reduced, the squeeze force between the wing and the end of the valve body is also reduced, which can reduce the variation of the squeeze force due to the relative position difference between the armature wing and the valve body opening. This can prevent the fuel injection timing from being deviated. Accordingly, it is possible to prevent harmful gas emission and particulate matter emission from the internal combustion engine due to incomplete combustion of fuel.

According to a ninth aspect of the present invention, in any one of the first to eighth aspects, the injector (1) has a needle valve portion (42) at the tip of the injection hole (42) for injecting fuel. 30) and needles (33, 34) for controlling the fuel injection and injection stop by opening and closing the nozzle hole (42). In the electromagnetically operated valve (10), the at least one fuel passage (17a, 17b, 17c) of the valve body (17) communicates with a passage (29) through which fuel acts on the needle (33, 34). And, on the other hand, by opening the electromagnetically operated valve (10), allowing the fuel to flow through the discharge passage (22), and reducing the pressure of the fuel acting on the needles (33, 34), The needle (33, 34) is opened to inject fuel from the nozzle hole (42), and on the other hand, the electromagnetically operated valve (10) is closed to allow the fuel to flow into the discharge passage (22). By shutting off and increasing the pressure of the fuel acting on the needles (33, 34), the needles (33, 34) are closed to stop the fuel injection from the nozzle holes (42). And
According to the present embodiment, the configuration of the electromagnetically operated valve of the injector of the present invention is further embodied.

According to a tenth aspect of the present invention, in any one of the first to ninth aspects, the armature (16) is connected to the wing (16e) and protrudes therefrom. (16b, 18), and the valve body (16b, 18) is used to open and close the fuel passages (17a, 17b, 17c) of the valve body (17). .
According to this embodiment, the configuration of the armature of the electromagnetically operated valve of the injector according to the present invention is further embodied.

  Hereinafter, an injector for performing fuel injection of an engine according to an embodiment of the present invention will be described in detail based on the drawings. 1 to 3 schematically show a first embodiment of an injector according to the present invention, and FIG. 1 is a side sectional view showing an overall configuration of the injector according to the first embodiment of the present invention. 2 is a partially enlarged sectional view in the vicinity of the electromagnetically operated valve of the injector of FIG. 1, and FIG. 3 is a top view of two parts of the armature and body of the electromagnetically operated valve of FIG. 2 along line AA. It is a top view. Elements of the injector according to the first embodiment shown in FIGS. 1 to 3 are designated by the same reference numerals as those of the corresponding elements in the conventional example of FIG. The injector 1 according to the first embodiment is an injector that performs fuel injection in a diesel engine.

  First, referring to FIG. 1, the injector 1 according to the present embodiment includes an electromagnetically operated valve 10 and a needle valve portion 30. By opening and closing the electromagnetically operated valve 10, the tip of the needle valve portion 30 is opened. Fuel is injected from the injection hole 42. The injector has a configuration as shown in FIGS. 1 and 2 so that fuel can be injected at a high speed and a high pressure. Since the configuration of such an injector 1 is known, the general configuration is as follows. Only the operation will be described.

  The injector 1 includes a fuel supply unit 25, and fuel is supplied from a fuel pump (not shown) to the fuel supply unit 25, passes through the fuel passage 27, and on the other hand, the fuel at the tip of the needle valve unit 30 through the fuel passage 28. It reaches the reservoir 32b and, on the other hand, reaches the top surface of the control pin 33 via the fuel passage 29. The control pin 33 is connected to a needle 34 provided at a lower portion thereof, and the needle 34 closes the injection hole 42 by the fuel pressure acting on the top surface of the control pin 33. At this time, the other end portion of the fuel passage 29 reaches the lower surface of the shaft portion 16b of the armature 16 of the electromagnetic valve 10 via an oil passage 17a formed in the valve body 17, as shown in FIG. When the electromagnetically operated valve 10 is closed, the high pressure of the fuel acting on the top of the control pin 33 is maintained because the shaft 16b and the seat 18 are closed.

  Fuel injection by opening the electromagnetically operated valve 10 will be described. When the exciting coil 13 is excited, the attracting surface 16a of the armature 16 opposes the exciting coil 13 against the urging force of the coil spring 21 that urges the armature 16 in the axial downward direction of the injector 1 (the direction of the control pin 33). Since it is attracted to the surrounding stator 14, the armature 16 rises and a gap is formed between the shaft portion 16 b and the seat portion 18 and the valve body 17. Since the fuel in the oil passage 17a communicates with the discharge passage 22 through the oil passage 17b and the leak hole 17c, the pressures in the oil passage 17a and the fuel passage 29 are reduced. Thus, the pressure for pushing up the needle 34 via the fuel passage 28 exceeds the pressure on the top surface of the control pin 33 and the needle 34 rises, so that the fuel in the fuel passage 28 is discharged from the nozzle hole 42.

  FIG. 3 is a cross-sectional view taken along line AA in FIG. 2 and is a view of the two parts of the armature 16 and the valve body 17 as seen from above. Four wings 16e of the armature 16 are provided at 90 ° intervals, and a notch 16g is provided between the wings 16e. An armature hole 16f is formed substantially in the center of each wing portion 16e, and the flow of oil from the leak hole 17c can be passed therethrough. In the conventional example of FIG. 10 described above, there are three wings 16e of the armature 16 and three leak holes 17c of the valve body 17, which are symmetrical at 120 °. Since the armature 16 is movable in the rotational direction around the longitudinal axis of the injector 1 with respect to the fixed valve body 17, the armature blade portion 16e and the leak hole 17c have a relative positional difference. That is, since the relative positional relationship between the armature wing 16e and the leak hole 17c changes, the squeeze force (fluid drag) varies as described above in the conventional example of FIG.

  In the present embodiment of FIG. 3, there are four armature wings 16e and three leak holes 17c, which are symmetrical with an angular interval of 90 ° and 120 °, respectively. As a result, the armature blade 16e and the leak hole 17c wrap regardless of the position of the armature 16 in the rotational direction around the axis. FIG. 4 shows the transition of the area where the squeeze force is generated (squeeze area ratio) with respect to the relative position difference between the armature blade 16e and the body leak hole 17c in the case of the present embodiment by a solid line. It can be seen that the change in the area to be suppressed is substantially suppressed. The wings 16e are preferably provided with one armature hole 16f at substantially the center of the wing, but the armature holes 16f may not be provided. Since the armature hole 16f is formed so as to allow the oil flow from the leak hole 17c to pass therethrough, no squeeze force is generated in the portion of the armature hole 16f. Further, the armature hole 16f and all the leak holes 17c do not overlap.

  FIG. 5 shows a second embodiment of the present invention, which is a modification of the first embodiment. In the present embodiment, the valve body 17 is provided with four leak holes 17c symmetrically at an angular interval of 90 °. The shape of the wing portion 16e of the armature 16 is the same as that of the conventional example, and it is preferable that three armature holes 16f are provided, one at the substantial center of each wing portion 16e.

  FIG. 6 shows a third embodiment of the present invention, which is a modification of the first or second embodiment. In the present embodiment, the three leak holes 17c of the valve body 17 are elongated in the circumferential direction in an elliptical shape, and are provided symmetrically at an angular interval of 120 °. The shape of the wing portion 16e of the armature 16 and the number of the armature holes 16f are the same as those in the second embodiment.

  FIG. 7 shows a fourth embodiment of the present invention, which is also a modification of the first or second embodiment. In the present embodiment, the three leak holes 17c of the valve body 17 are the same as in the first embodiment, but the number of the wings 16e of the armature 16 is three, but the width of the notch 16g is Therefore, the area of one wing portion 16e is wide. It is preferable that six armature holes 16f, two for each wing portion 16e, are provided symmetrically at an angular interval of 60 °.

  FIG. 8 shows a fifth embodiment of the present invention. In the present embodiment, the shape, quantity, arrangement, etc. of the wing portion 16e of the armature 16 and the three leak holes 17c of the valve body 17 are the same as in the conventional example shown in FIG. However, in the radial direction of the armature 16, a groove 16h having a predetermined depth is formed along the circumferential direction at the position of the three armature holes 16f (the position corresponding to the position of the leak hole 17c). The groove 16h facilitates fuel flow, the squeeze force in the groove portion is reduced, and fluctuations in the squeeze area ratio are also reduced.

FIG. 9 shows a sixth embodiment of the present invention. In the present embodiment, the shape, quantity, arrangement, etc. of the wing portion 16e of the armature 16 and the three leak holes 17c of the valve body 17 are the same as in the conventional example shown in FIG. However, in the radial direction of the valve body 17, a groove 17h having a predetermined depth is formed along the circumferential direction so as to connect them to the positions of the three leak holes. The groove 17h facilitates the flow of fuel, the squeeze force in the groove portion is reduced, and the fluctuation of the squeeze area ratio is also reduced.
The configurations of the second to sixth embodiments are the same as those of the first embodiment except for the above.

Next, effects and operations of the above embodiment will be described.
The following effects can be expected from the injector according to the first embodiment of the present invention.
Focusing on the fact that the squeeze force generation area between the armature wing and the end of the valve body changes due to the relative position difference between the armature wing and the leak hole of the valve body, the squeeze generation area is the wing By reducing the change due to the relative position difference between the leak hole and the leak hole, it is possible to prevent a delay in the fuel injection timing.
-This prevents incomplete combustion of the fuel and emission of harmful gases and particulate matter from the internal combustion engine.

  The injectors according to the second to sixth embodiments of the present invention can exhibit the same effects as those of the first embodiment.

In the above description, the injector of the present invention has been described for a diesel engine, but may be used for other engines.
Further, in the embodiment described above or shown in the accompanying drawings, various examples are shown for the number, arrangement, shape, etc. of the wings and leak holes, but the present invention is not limited to this. Configurations other than these examples may be adopted in the present invention, and may be a combination of the number, arrangement, shape, and the like of the wings and leak holes that reduce the fluctuation range of the squeeze area that is the principle of the present invention. .

  The above-described embodiment is an example of the present invention, and the present invention is not limited by the embodiment, but is defined only by matters described in the claims, and other embodiments than the above are also possible. It can be implemented.

FIG. 1 is a side sectional view schematically showing the overall configuration of the injector according to the first embodiment of the present invention. FIG. 2 is a partially enlarged cross-sectional view of the vicinity of the electromagnetically operated valve of the injector of FIG. FIG. 3 is a top view (A) along line A-A and a top view (B) of the armature wing portion when two parts of the armature and valve body of the electromagnetically operated valve of FIG. 2 are viewed from above. FIG. 4 shows a first embodiment (solid line) of the present invention and a conventional example regarding a change in squeeze force (squeeze area ratio) when a predetermined relative position angle of the rotatable armature 16 with respect to the valve body 17 changes. It is a graph which shows a comparison (dotted line). FIG. 5 shows a top view (A) similar to FIG. 3 and a top view of the valve body, in which two parts of the armature and valve body of the electromagnetically operated valve of the injector according to the second embodiment of the present invention are viewed from above. (B). FIG. 6 shows a top view (A) similar to FIG. 3 and two top views of a valve body (B), in which two parts of an armature and a valve body of an electromagnetically operated valve according to a third embodiment of the present invention are viewed from above. ). FIG. 7 is a top view (A) similar to FIG. 3 and two top views (B) of the armature and valve body of the electromagnetically operated valve according to the fourth embodiment of the present invention viewed from above. ). FIG. 8 is a top view (A) similar to FIG. 3 and two top views (B) of the armature and valve body of the electromagnetically operated valve according to the fifth embodiment of the present invention viewed from above. ). FIG. 9 shows a top view (A) similar to FIG. 3 and two top views of a valve body (B) in which two parts of an armature and a valve body of an electromagnetically operated valve according to a sixth embodiment of the present invention are viewed from above. ). FIG. 10 is a top view (A) similar to FIG. 3 in which two parts of the armature and valve body of the electromagnetically operated valve of the conventional injector are viewed from above, and the wing (B) and valve body (C). It is a top view. FIG. 11 is an explanatory view when the rotatable armature 16 rotates with respect to the valve body 17 in the conventional example shown in FIG. 10, and the relative position difference is 0 ° (A) and the relative position difference is 30 ° (B). This case is shown in the same diagram as FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Injector 10 Electromagnetically operated valve 13 Excitation coil 14 Stator 16 Armature 16b Shaft part 16e Wing | wing part 16f Armature hole 16g Notch 17 Valve body 17a, 17b Oil passage 17c Leak hole 18 Seat part 19 Valve seat member 21 Coil spring 22 Exhaust passage 25 Fuel Supply portion 27 Fuel passage 28 Fuel passage 29 Fuel passage 30 Needle valve portion 33 Control pin 32b Fuel reservoir portion 34 Needle 42 Injection hole

Claims (10)

In an injector (1) comprising an electromagnetically operated valve (10) for controlling fuel injection,
The electromagnetic valve (10) is
A valve body (17) provided with at least one fuel passage (17a, 17b, 17c);
An armature (16) for opening and closing the fuel passage (17a, 17b, 17c) of the valve body (17);
An excitation coil (13) that is energized and energized, and that displaces the armature (16) by excitation to open and close the electromagnetic valve (10);
It has
The armature (16) has a plate-like wing (16e),
The valve body (17) has at least one opening in which the fuel passage (17c) of the valve body (17) opens on an end surface (17d) of the valve body (17) facing the wing (16e). (17c)
The wing (16e) is provided with at least one notch (16g) to allow the fuel from the opening (17c) to flow,
Regardless of the relative position of the opening (17c) of the valve body (17) with respect to the notch (16g) of the wing (16e), the area of the wing (16e) not facing the opening (17c) is The injector, wherein the notch (16g) and the opening (17c) are arranged so as to be substantially constant. In an injector (1) comprising an electromagnetically operated valve (10) for controlling fuel injection,
The electromagnetic valve (10) is
A valve body (17) provided with at least one fuel passage (17a, 17b, 17c);
An armature (16) for opening and closing the fuel passage (17a, 17b, 17c) of the valve body (17);
An excitation coil (13) that is energized and energized, and that displaces the armature (16) by excitation to open and close the electromagnetic valve (10);
It has
The armature (16) has a plate-like wing (16e),
The valve body (17) has at least two openings in which the fuel passage (17c) of the valve body (17) opens on an end surface (17d) of the valve body (17) facing the wing (16e). (17c)
The wing (16e) is provided with at least one notch (16g) to allow the fuel from the opening (17c) to flow,
The injector is characterized in that at least one of the openings (17c) is always disposed at a position overlapping the wing (16e).   The wing (16e) is partitioned into a plurality of regions by the notches (16g), and the number of the plurality of regions and the number of the openings (17c) of the valve body (17) are different. The injector according to claim 1 or 2.   The notches (16g) defining the wings (16e) are symmetrically arranged at equal angular intervals, and the openings (17c) of the valve body (17) are also symmetrically arranged at equal angular intervals. The injector according to any one of claims 1 to 3.   In the valve body (17), three openings (17c) are provided symmetrically at 120 ° angular intervals, and four notches (16g) are provided at 90 ° angular intervals in the wing portion (16e). 4. The injector according to claim 3, wherein the injector is provided symmetrically.   The injector according to any one of claims 1 to 5, wherein a groove (17h) is provided on an arrangement track of the opening (17c) on the end face (17d) of the valve body (17).   In the end surface (16d) of the wing portion (16e) facing the end surface (17d) of the valve body (17), a groove (16h) is provided on a track corresponding to the arrangement track of the openings (17c). The injector according to any one of claims 1 to 5, characterized in that: In an injector (1) comprising an electromagnetically operated valve (10) for controlling fuel injection,
The electromagnetic valve (10) is
A valve body (17) provided with at least one fuel passage (17a, 17b, 17c);
An armature (16) for opening and closing the fuel passage (17a, 17b, 17c) of the valve body (17);
An excitation coil (13) that is energized and energized, and that displaces the armature (16) by excitation to open and close the electromagnetic valve (10);
It has
The armature (16) has a plate-like wing (16e),
The valve body (17) has at least one opening in which the fuel passage (17c) of the valve body (17) opens on an end surface (17d) of the valve body (17) facing the wing (16e). (17c)
The wing (16e) is provided with at least one notch (16g) to allow the fuel from the opening (17c) to flow,
In at least one of the end surface (17d) of the valve body (17) or the end surface (16d) of the wing portion (16e) facing the end surface (17d) of the valve body (17), the opening (17c ), And the grooves (17h, 16h) are provided on the orbit. The injector (1)
A needle valve portion (30) having a nozzle hole (42) for injecting fuel at its tip;
Needles (33, 34) for opening and closing the nozzle hole (42) to control fuel injection and injection stop;
Further comprising
In the electromagnetically operated valve (10), the fuel passages (17a, 17b, 17c) of the valve body (17) communicate with a passage (29) where fuel acts on the needles (33, 34). On the other hand, by opening the electromagnetically operated valve (10), the fuel flows into the discharge passage (22), and the pressure of the fuel acting on the needles (33, 34) is reduced, whereby the needle ( 33, 34) is opened to inject fuel from the nozzle hole (42), and on the other hand, the electromagnetically operated valve (10) is closed to shut off the flow of fuel to the discharge passage (22). The pressure of the fuel acting on the needles (33, 34) is increased to close the needles (33, 34) and stop the injection of fuel from the nozzle holes (42). Any one of claims 1 to 8 The injector as described in.   The armature (16) further includes a rod-shaped valve body portion (16b, 18) connected to the wing portion (16e) and protruding therefrom, and the valve body portion (16b, 18) The injector according to any one of claims 1 to 9, wherein the fuel passage (17a, 17b, 17c) of the valve body (17) is opened and closed.

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