EP3191705A1

EP3191705A1 - Fuel injection valve

Info

Publication number: EP3191705A1
Application number: EP15759801.2A
Authority: EP
Inventors: Martin Mueller
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2014-09-10
Filing date: 2015-09-07
Publication date: 2017-07-19
Also published as: DE102014218056A1; WO2016037970A1

Abstract

A fuel injection valve (1) which serves in particular as an injector for fuel injection systems of mixture-compressing, spark-ignited internal combustion engines comprises a valve-closing body (7), which is actuable by an actuator (5), and a valve seat body (8). In this connection, the valve seat body (8) has a valve seat surface (15), wherein the valve-closing body (7) interacts with the valve seat surface (15) on an encircling seat contact line (10) to form a sealing seat (9). According to the invention, between the seat contact line (10) and a spray discharge edge (17) configured on the valve-closing body (7), at least one depression (25, 25A) is provided on the valve-closing body (7) and/or at least one depression (26, 26A) is provided in the valve seat surface (15) of the valve seat body (8). At least one depression (27, 27A) is provided here on at least the valve seat body upstream of the seat contact line (10), as viewed in the flow direction (20). Turbulences can thereby be generated in the fuel flow. By this means, especially, a greater number of smaller and larger drops can be produced than is possible in the case of fuel injection valves without such depressions.

Description

description

title

Fuel injection valve prior art

The invention relates to a fuel injection valve, in particular an injector for

Fuel injection systems of internal combustion engines. Specifically, the invention relates to the field of injectors of fuel injection systems of mixture-compression spark-ignition internal combustion engines.

From DE 10 2004 058 652 A1 a fuel injection valve is known, which serves for the direct injection of fuel into the combustion chamber of an internal combustion engine. The known fuel injection valve comprises a valve needle arranged in a nozzle body, which can be actuated by an actuator. One with the valve needle in

Active connection standing, the combustion chamber facing valve-closing body is held in the unactuated state of the actuator in sealing contact with a valve seat surface. Here, grooves are provided on one of the valve seat surface facing surface of the valve closing body. For example, eight elliptical grooves may be provided, which are arranged radially symmetrically above a Sitzberührlinie, wherein a long

Half axis of the ellipse is oriented approximately perpendicular to Sitzberührlinie.

With the configuration of a fuel injection valve, as is known from DE 10 2004 058 652 A1, it should be achieved that an asymmetric injection is realized. In this case, the flowing fuel due to the on the valve closing body

provided grooves still undergo a speed component that deviates from the predetermined by the inclination of the valve closing body direction. As a result, the flowing fuel is deflected from its original direction, so that the scattering of the exiting fuel jet increases. Specifically, laminar

Flow rates are avoided by appropriate demolition edges and increase the degree of turbulence. However, the flow of the fuel, especially in the area of the valve closing body, depends considerably on the specific configuration of the valve

Fuel injection valve, which is limited by the specific application. Above the Sitzberührlinie result in the known fuel injection valve lower flow velocities of the fuel than directly on or behind the Sitzberührlinie, as seen in the flow direction above (before) the Sitzberührlinie in the known fuel injection valve, a larger flow cross section is specified. In the concrete case of application, the desired effects for distributing the fuel in the combustion chamber may possibly not be achieved in the desired manner.

Disclosure of the invention

The fuel injection valve according to the invention with the features of claim 1 has the advantage that an improved design is made possible, in particular in the concrete application, improved injection images can be generated. The measures listed in the dependent claims are advantageous

Further developments of the fuel injection valve specified in claim 1 possible.

With a fuel injection valve, which may be developed advantageously advantageous, spray forms or injection images can be generated, which are advantageous in several respects.

By depressions, in particular grooves in Abspritzbereich, can be a turbulent

Flow can be achieved. Consequently, the injected fuel can be produced in a finely divided droplet form (spray) with a wider distribution of droplet sizes. In such a spray, there may be more smaller and larger droplets than in designs without the proposed wells. This results in a better mixing of the fuel with the air in the combustion chamber. This in turn results in a particularly low-emission combustion and a high Wrkungsgrad the

Internal combustion engine.

The thicker drops can not be easily blown by air currents in the combustion chamber. This allows the spray to be held more stably near a spark plug. The internal combustion engine thus has less engine misfire, generates less harmful exhaust gas and has a better degree of efficiency.

A spray lamella becomes wider due to the more turbulent flow due to the depressions perpendicular to the lamellar plane. As a result, the spray is also more Combustion chamber air detected, which also has a positive effect in terms of the aforementioned benefits.

The depressions can be advantageously by a laser processing of the

Valve-closing body or the valve seat body are generated. In particular, a laser technique based on an ultra-short-pulse laser can be used here. With such a laser technique, the wells can be introduced very precisely and with little influence of the surrounding material in the respective surface. However, the depressions may also be introduced additionally or alternatively by other methods.

It is advantageous that the valve closing body at least between the Sitzberührlinie and the Abspritzkante outside the at least one with a sealed sealing seat

Deepening of the valve closing body or the at least one recess in the valve seat surface is at least substantially on the valve seat surface. The Sitzberührlinie represents the contact point for the sealing seat. This results in a comparatively small flow area when the seal seat is open, creating a high

Flow rate is guaranteed in this area. The flow can hereby be influenced in a special way by the depressions in order to achieve the desired spray pattern and the desired droplet formation. In particular, the stochastic distribution of the droplet sizes occurring in the spray pattern can be influenced particularly effectively. The depressions can be designed here with a comparatively small depth and extent. This makes it possible, in particular, that a greater number of depressions can be realized, if necessary

For example, over a circumference of the valve closing body or the

Valve seat body are distributed. Thus, starting from an idealized laminar flow at many points, breakup of this laminar flow can be achieved to initiate turbulence in the flow at a plurality of locations defined by the wells.

It is also advantageous that at least a part of the recesses of

Valve-closing body forms a recessed space each with a closed sealing seat, which is spaced from the discharge edge of the valve-closing body. As a result, the locations for the initiation of turbulence in the flow in the direction of flow can be placed in front of the spray edge.

However, it is also advantageous that at least part of the depressions of the

Valve-closing body forms a recessed space with closed sealing seat, the extends into the discharge edge of the valve closing body. This allows points to initiate the turbulence in the flow directly to the Abspritzkante of

Valve closing body are placed. It is also advantageous that at least a part of the recesses of the valve closing body with closed sealing seat in each case forms a recessed space, which is arranged directly on the Abspritzkante the valve closing body, but does not extend into the Abspritzkante the valve closing body. Thus, the point for generating the turbulence of the flow can be placed almost at the Abspritzkante of the valve closing body, while still an uninterrupted Abspritzkante, in particular a circular

Abspritzkante, can be realized on the valve closing body. The Abspritzkante the valve closing body can also be configured as a rounded Abspritzkante.

Additionally or alternatively, at least a portion of the recesses in the valve seat surface of the valve seat body with closed sealing seat each form a recessed space, which is spaced from the discharge edge of the valve closing body. Specifically, the relevant depressions in this embodiment, viewed in the flow direction can be placed approximately in the middle between the spray edge and the Sitzberührlinie or closer to the Sitzberührlinie.

Thus, there are several ways to provide recesses on the valve closing body. By means of the generated turbulence of the flow, it is also possible to stochastically accumulate more small and larger droplets in the spray. Advantageously, the wells additionally or alternatively in the

Valve seat surface of the valve closing body may be provided.

In this case, it is advantageous that at least a part of the depressions in the valve seat surface of the valve closing body with the sealing seat closed in each case forms a depression space, which is open beyond the ejection edge of the valve closing body. Thus, when opening the sealing seat in the flow gap between the valve closing body and the

Valve seat surface in the region of the Abspritzkante over the circumference varying gap widths possible. As a result, points for generating turbulence in the sprayed fuel are generated specifically at the Abspritzkante.

Furthermore, it is advantageous that at least a part of the depressions of the valve seat surface of the valve closing body forms a recessed space when the sealing seat is closed, which immediately before the discharge edge of the valve closing body to the valve closing body adjacent, but not beyond the Abspritzkante is open. In this way, the locations for the generation of turbulence in the flow can be placed close to the injection edge, at least with respect to these recesses directly at the

Abspritzkante a constant gap width is realized at a given opening of the sealing seat.

In a further possible embodiment, at least a part of the in

Viewed flow direction before the Sitzberührlinie provided recesses of the valve seat body with closed sealing seat each form a recessed space. In this way, places for generating the turbulent flow can also be placed in front of the sealing seat. Preferably, in this area also a small opening cross-section of a flow gap is realized when the sealing seat is opened in order to achieve a high flow rate. It is also advantageous that a plurality of recesses are provided on the valve closing body and a plurality of depressions in the valve seat surface of the valve seat body, which adjoin a common circumferential line when the sealing seat is closed. Specifically, the depressions of the valve closing body and the recesses in the valve seat surface viewed along the circumferential line can alternate with respect to their design on the valve closing body and in the valve seat surface. In this case, an angle of rotation mounting of the valve closing body with respect to the valve seat body is preferably predetermined.

The recesses may have suitable geometries. In this case, the depressions advantageously have a circular, triangular, oval, rhombic or slot-shaped configuration. However, there may be other embodiments for

Use come. Further, the recesses formed on the valve closing body may all have the same geometry. Further, the recesses in the valve seat surface may all have the same geometry. Specifically, the recesses in the valve closing body and the recesses in the valve seat surface can all have the same geometry, if both the valve closing body and in the

Valve seat surface such recesses are provided. However, too

different geometries are realized on the one hand on the valve closing body and on the other hand in the valve seat surface. Furthermore, combinations of different geometries can also be used on the valve closing body or in the valve seat surface.

The orientation of recesses with slot-shaped configuration can in

Be circumferential direction, which formed closed circumferentially or interrupted could be. The orientation can also be in the flow direction or obliquely to

Be flow direction.

Furthermore, advantageous arrangements result when depressions are provided both on the valve closing body and in the valve seat surface. Here, such

Wells on the valve closing body and in the valve seat surface to be aligned with each other. This possibly makes a rotation angle-dependent mounting required. Specifically, the depressions on the valve closing body and in the valve seat surface can then lie on a common circumferential line or on two closely adjacent circumferential lines. Furthermore, embodiments are also conceivable in which depressions on the

Valve-closing body opposite to a well-free part surface of the valve seat surface. Accordingly, depressions in the valve seat surface of the valve seat body can lie opposite a recess-free partial surface on the valve closing body. A rotation angle-dependent mounting of the valve closing body relative to the valve seat body is then possibly not required.

Brief description of the drawings

Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with identical reference numerals. Show it:

Fig. 1 is a fuel injection valve in an excerpt, schematic

Sectional view according to a possible embodiment of the invention;

Fig. 2 is a partial, schematic representation of the designated in Figure 1 with II section of the fuel injection valve to illustrate possible embodiments of the invention. Fig. 3 shows the detail of the fuel injection valve shown in Fig. 2 for further

Explanation of possible embodiments of the invention;

FIG. 4A shows the detail of the fuel injection valve according to a first embodiment of the invention shown in FIG. 2; FIG.

4B shows a valve seat body of FIG. 2 in excerpts

Fuel injection valve according to the first embodiment of the invention; FIG. 5A shows a valve closing body of the fuel injection valve shown in FIG. 2 in accordance with a second embodiment of the invention; FIG.

Fig. 5B is a valve seat body of Fig. 2 in excerpts

Fuel injection valve according to the second embodiment of the invention;

Fig. 6A the valve closing body shown in Fig. 5A corresponding to a third

Embodiment of the invention;

Fig. 6B the valve seat body shown in Fig. 5B according to the third

Embodiment of the invention;

7A shows the valve closing body shown in FIG. 5A according to a fourth embodiment of the invention;

Fig. 7B, the valve seat body shown in Fig. 5B according to the fourth

Embodiment of the invention and

Fig. 8 the valve closing body shown in Fig. 5A according to a fifth

Embodiment of the invention.

Embodiments of the invention

Fig. 1 shows a fuel injection valve 1 in a partial, schematic

Sectional view according to a possible embodiment of the invention. The fuel injection valve 1 can serve, in particular, as an injector for fuel injection systems of mixture-compression, spark-ignited internal combustion engines. One

preferred use of the fuel injection valve 1 is for a

Fuel injection system, in the fuel for example via a

Fuel manifold is guided to a plurality of corresponding fuel injection valves 1. However, the fuel injection valve 1 according to the invention is also suitable for other applications.

The fuel injection valve 1 has a multi-part housing 2, wherein in FIG. 1, to simplify the illustration, only one housing part 2 designed as a nozzle body is shown. In the housing 2, in particular the nozzle body 2, a valve needle 3 is arranged and guided along an axis 4. In addition, an actuator 5 is arranged in the housing 2. The actuator 5, for example, as a magnetic actuator 5 or as be configured piezoelectric actuator 5. The valve needle 3 can be actuated by the actuator 5, which is illustrated by a double arrow 6. This operation can be done directly or indirectly. Optionally, the actuation can also take place, for example, via a hydraulic coupler or a servo valve.

The valve needle 3 has a valve closing body 7. In this embodiment, the valve closing body 7 is formed integrally with the valve needle 3. The valve closing body 7 can therefore also be actuated by the actuator 5 via the valve needle 3. On the nozzle body 2, a valve seat body 8 is formed in this

Embodiment is designed in one piece with the nozzle body 2. In a modified embodiment, however, the valve seat body 8 in a

Housing part 2, in particular the nozzle body 2, be used. The valve closing body 7 cooperates with the valve seat body 8 to form a sealing seat 9 (FIG. 2). If the fuel injection valve 1 is closed, then it is

Valve-closing body 7 on a Sitzberührlinie 10 on the valve-closing body 7, whereby the sealing seat 9 is located. Depending on the stroke of the valve needle 3 results in the open sealing seat 9, a gap over the fuel from a fuel raum 1 1 in a combustion chamber or other space of the internal combustion engine, in particular an antechamber of the combustion chamber, can be injected. Preferably, however, the fuel injection valve 1 is used for the direct injection of fuel into the combustion chamber within a cylinder of the internal combustion engine. In this direct

Injection is a targeted injection in terms of injection pattern and stochastic droplet distribution in the injection jet (spray) essential to good

Conditions for the combustion of the fuel to achieve. This affects in particular the efficiency of the internal combustion engine and the formation of pollutants in the exhaust gas or the reduction of undesirable combustion products. Fig. 2 shows a partial, schematic representation of the designated in Fig. 1 with II

Section of the fuel injection valve 1 for explaining possible embodiments of the invention. At the Sitzberührlinie 10 of the valve closing body 7 acts with a

Valve seat surface 15, which is formed on the valve seat body 8, to a closed sealing seat 19 together, when the valve closing body 7 is pressed against the valve seat surface 15. This closed position can be achieved, for example, by means of a valve spring when the actuator 5 actuates the valve closing body 7 for opening. In principle, however, a design is conceivable in which the opening via a valve spring takes place while the actuator 5 holds the valve closing body 7 against the force of the valve spring in a closed position.

Fig. 2, however, shows a position of the valve closing body 7 in the actuated state, in which the valve closing body 7 is adjusted by an opening stroke 16 from its closed position. At least the sealing seat 9 is open.

The valve closing body 7 has a discharge edge 17. Between the

Valve-closing body 7 and the valve seat surface 15, a first region 18 and a second region 19 are provided. When the sealing seat 9 is open, the fuel flows in one

Flow direction 20 from the fuel cavities 11 to the sealing seat 9, on the open sealing seat 9 and on to the Abspritzkante 17, where the fuel separates strom and injects into a combustion chamber 21 of the internal combustion engine. Viewed in the flow direction 20, the first region 18 is located in front of the sealing seat 9 or the

Sitzberührlinie 10. The second region 19 is located between the sealing seat 9 and the

Spray edge 17.

In the areas 18, 19 in this case a comparatively small opening cross-section is realized for a given opening stroke 16, so that a high fuel speed results in the areas 18, 19. Preferably, the opening cross-section in the regions 18, 19 along the flow direction 20 is at least approximately constant.

At the valve seat body 8, an edge (further spray edge) 22 is configured, with closed sealing seat 9, the spray edge 17 of the valve closing body 7 is preferably at least approximately at the edge 22nd

In an advantageous manner, at least one depression 25 can be provided on the valve closing body 7 in the area 19, that is to say between the seat touch line 10 and the ejection edge 17 configured on the valve closing body 7. Accordingly, a recess 26 may be provided in the valve seat surface 15 of the valve seat body 8 in the second region 19. Another possibility is that, viewed in the flow direction 20 in front of the Sitzberührlinie 10, ie in the first region 18, at least one recess 27 is provided on the valve seat body 8. In the second region 19, a plurality of recesses 25, 26 on the

Valve-closing body 7 and / or the valve seat body 8 may be provided. Furthermore, a plurality of recesses 27 may be provided in the first region 18 on the valve seat body 8. Thus, the recesses 25, 26, 27 can be realized in any combination. In addition, recesses 28A, 28B, 28C viewed in the flow direction 20 may also be provided in front of the seat touch line 10 on the valve closing body 7.

A special case of depressions 25A is that such a depression 25A can also extend into the ejection edge 17. Another special case of a recess 26A is that such a recess 26A extends to the end of the second region 19, so that when the sealing seat 9 is closed, the recess 26A is located on the ejection edge 17.

Fig. 3 shows the detail of the fuel injection valve 1 shown in Fig. 2 for explaining possible embodiments of the invention. For example, you can

Recesses 25 may be provided which are provided on the valve closing body 7 and each having an elliptical shape. Here, to simplify the illustration, possible geometric modifications of the recess 25, for example the recess 25A, together with the recess 25 are shown. Here, the recess 25A, which extends into the discharge edge 17, designed in a possible embodiment in a form which is composed of a cuboid 29 and a half-cylinder 30.

The recesses 28A, 28B, 28C may each be configured, for example, groove-shaped. In this case, the recesses 28A, 28B, 28C may extend in the flow direction 20. The recesses 28A, 28B, 28C may also be perpendicular to

Flow direction 20 or obliquely to the flow direction 20 extend. For example, a partially circumferential, groove-shaped recess 28A 'and an oblique, slot-shaped

Recess 28A "shown, the possible modifications of the recess 28A

illustrate.

The recess 26 may be configured in elliptical shape in the valve seat surface 15. The recess 27 may be groove-shaped and extend in the flow direction 20. Further, an embodiment of a recess 27 A in the valve seat surface 15 is possible, which extends up to, but not in the Sitzberührlinie 10.

Such recesses 25, 25A, 26, 26A, 27, 27A may be suitably numbered and

Design in each case several times or in combination with each other and in

be provided different configurations. In addition, the

Recesses 28 A, 28 B, 28 C may be provided in a suitable number, arrangement and configuration. FIG. 4A shows the section of the fuel injection valve 1 shown in FIG. 2 in accordance with a first exemplary embodiment of the invention. The valve needle 3 has a plurality of flats 31 which are circumferentially distributed with respect to the axis 4. By the flats 31, of which in FIG. 4A, for the sake of simplicity of illustration only one flat 31 is shown, fuel passages with respect to a

Guide surface 32 formed in the interior of the nozzle body 2, via which the fuel from a suitable, connected to a fuel nozzle fuel channel can flow to the fuel chamber 1 1. At the same time, guidance of the valve needle 3 along the axis 4 can be achieved via the guide surface 32.

Is essential to the invention in this embodiment that 8 recesses 27 are provided in the first region 18 to the valve seat body. Additionally are at the

Valve-closing body 7 in the first region 18 and recesses 28 A are provided which extend over the circumference of the valve closing body 7. In this case, an angular distance is preferably predetermined between two adjacent recesses 28A, which repeats for all recesses 28A over the circumference.

FIG. 4A shows a state when the sealing seat 9 is open. Here, in the areas 18, 19 between the valve closing body 7 and the valve seat surface 15 a

Flow gap formed, which has a comparatively small flow area or is narrow. This means that an opening cross-section of the corresponding triangular geometry with the opening stroke 16 and

Tilt angle of the conical valve seat surface 15 relative to the axis 4 results.

In the area of the valve seat surface 15 and of the valve closing body 7, a conceptual peripheral line 33 can be determined when the sealing seat 9 is closed, to which reference is made in this case

Embodiment adjacent both the plurality of recesses 27 in the valve seat surface 15 and the plurality of recesses 28 A of the valve closing body 7.

4B shows the valve seat body 8 of FIG. 2 in excerpts

Fuel injection valve 1 according to the first embodiment of the invention. Here, the concealed in Fig. 4A, further recesses 27 are shown in their arrangement on the circumferential line 33. The depressions 27 in this case preferably extend over the entire circumferential line 33. Furthermore, the respectively identical angular spacing is preferably predetermined between adjacent depressions 27. Specially is the

Angular distance between two adjacent recesses 27 chosen to be the same size as the angular distance between two adjacent recesses 28 A of the valve closing body. 7 When the sealing seat 8 is closed, the depressions 28A and the depressions 27 can alternate straight. The recesses 28 A of the valve closing body 7 can thereby be assigned to the valve seat surface 15, which in each case by the

Close wells 28, 28A formed wells. To simplify the illustration, only the partial surfaces 34, 35 are marked here. Accordingly, then the recesses 27 are associated with partial surfaces 36, 37 on the valve closing body 7 in the region of the circumferential line 33, which each formed by the recesses 27

Close recessed spaces 27 when the sealing seat 9 is closed. When the sealing seat 9 is open, the fuel is then conducted past the recessed spaces 27, 28A formed by the depressions 27, 28A at high speed. These recessed spaces 27, 28A then form perturbations for the fuel flow, creating turbulence in the fuel flow. Fig. 5A shows a valve closing body 3 of the Fig. 2 in part

Fuel injection valve 1 according to a second embodiment of the

Invention. Compared with the embodiment shown in FIG. 4A, the recesses 28 A are arranged further away from the seat touch line 10 counter to the flow direction 20. As a result, they are assigned to a distal end of the ejection edge 17 38 of the valve seat 15.

FIG. 5B shows a valve seat body 8 of the nozzle body 2 of the fuel injection valve 1 shown in FIG. 2 in accordance with the second embodiment of the invention. The recesses 27 in the valve seat surface 15 are located in

Accordance with the recesses 28A of the valve closing body 7 also on the

End 38 of the valve seat surface 15. As a result, both the recesses 28A of the

Valve-closing body 7 and the recesses 27 of the valve seat body 8 at the

Circumferential line 33. Fig. 6A shows the valve closing body 7 shown in Fig. 5A corresponding to a third

Embodiment of the invention. 6B shows the valve seat body 8 according to the third embodiment of the invention shown in FIG. 5B. In this embodiment, 7 recesses 25 A are arranged on the valve closing body, which are arranged on the ejection edge 17. The circumferential line 33, along which the depressions 27A are arranged, is thus located on the ejection edge 17. The depressions 26A are assigned to the valve seat body 8 in such a way that the depression spaces 26A respectively formed by the depressions 26A extend beyond the ejection edge 17 into the cavity

Combustion chamber 21 are opened, even if the sealing seat 9 is closed. The opening The recessed spaces 26A formed by the recesses 26A are realized by the configurations of the recesses 26A. The recesses 26A may in turn be associated with partial surfaces 36, 37 on the valve closing body 7, which between

Recesses 25A of the valve closing body 7 are located.

Fig. 7A shows the valve closing body 7 shown in Fig. 5A according to a fourth embodiment of the invention. Associated with it, Fig. 7B shows that in Fig. 5B

shown valve seat body 8 according to the fourth embodiment of the

Invention. In this embodiment, recesses 25 are configured on the valve closing body 7, which lie directly in front of the discharge edge 17 of the valve closing body 7, but do not extend into the discharge edge 17. Here, an arrangement of the recesses 25 along the circumferential line 33 is provided in this embodiment. The

The circumferential line 33 is hereby spaced from the discharge edge 17 counter to the flow direction 20 of the fuel. Here, a small distance 39 between the circumferential line 33 and the Abspritzkante 17 is provided. The small distance 39 is small in relation to an axial extent 40, over which the first area 18 extends on the valve closing body 7. The axially considered small distance 39 is predetermined in a corresponding manner for the recesses 26 in the valve seat surface 15 of the valve seat body 8. As a result, the depressions 26 are also located on the circumferential line 33 when the sealing seat 9 is closed. The recessed spaces formed by the recesses 26 are closed with the sealing seat by the faces 36, 37 on the valve closing body 7 with respect to the

Combustion chamber 21 is closed when the sealing seat 9 is closed. Accordingly, the well cavities formed by the recesses 25 of the valve closing body 7 are closed by partial surfaces 34, 35 of the valve seat surface 15, so that they are not with the

Combustion chamber 21 are in communication when the sealing seat 9 is closed.

Fig. 8 shows the valve closing body 7 shown in Fig. 5A according to a fifth embodiment of the invention. An embodiment of recesses 28 C, the counter to the flow direction 20 even before the first region 18 at the

Valve closing body 7 are arranged, in addition to one or more arrangements of recesses 26, 26 A, 27 on the valve seat surface 15 and / or one or more arrangements of recesses 25, 25 A, 28 A, 28 B on the valve closing body. 7

be provided. In this way, an additional influencing of the fuel flow can be achieved, even before the entry of the fuel into the first region 18 of the fuel gap between the valve closing body 7 and the valve seat surface 15th

Create turbulence.

The invention is not limited to the described embodiments.

Claims

claims

1. Fuel injection valve (1), in particular injector for fuel injection systems of mixture-compressing spark-ignition internal combustion engines, with one of an actuator (5) at least indirectly operable valve closing body (7) and a valve seat body (8), wherein the valve seat body (8) has a valve seat surface (15) and wherein the

Valve-closing body (7) on a circumferential Sitzberührlinie (10) with the valve seat surface (15) to a sealing seat (9) cooperates,

characterized,

in that between the seat touch line (10) and one on the valve closing body (7)

designed Abspritzkante (17) at least one recess (25, 25A) on the

Valve closing body (7) and / or at least one recess (26, 26A) in the valve seat surface (15) of the valve seat body (8) is provided and / or that in the flow direction (20) viewed in front of Sitzberührlinie (10) at least one recess (27, 27A) is provided on at least the valve seat body (8).

2. Fuel injection valve according to claim 1,

characterized,

that the valve closing body (7) with closed sealing seat (9) at least between the Sitzberührlinie (10) and the Abspritzkante (17) outside the at least one recess (25, 25A) of the valve closing body (7) or the at least one recess

(26, 26A) in the valve seat surface (15) lies at least substantially on the valve seat surface (15).

3. Fuel injection valve according to claim 2,

characterized,

that at least one depression (25) of the valve closing body (7) forms a recessed space (25) when the sealing seat (9) is closed, said cavity being formed by the ejection edge (17) of the

Valve-closing body (7) is spaced.

4. Fuel injection valve according to claim 2 or 3,

characterized, that at least one recess (25A) of the valve closing body (7) with closed sealing seat (9) forms a recessed space (25A) which extends into the discharge edge (17) of the valve closing body (7).

5. Fuel injection valve according to one of claims 2 to 4,

characterized,

that at least one depression (25) of the valve closing body (7) forms a recessed space (25) when the sealing seat (9) is closed, which is arranged directly on the ejection edge (17) of the valve closing body (7) but does not penetrate into the ejection edge (17). of the valve closing body (7) extends.

6. Fuel injection valve according to one of claims 2 to 5,

characterized,

in that at least one depression (26, 27A) in the valve seat surface (15) of the valve seat body (8) forms a depression space (26, 27A) when the sealing seat (9) is closed, which is spaced from the ejection edge (17) of the valve closing body (7).

7. Fuel injection valve according to one of claims 2 to 6,

characterized,

in that at least one depression (26A) in the valve seat surface (15) of the valve seat body (8) with the sealing seat (9) closed forms a depression chamber (26A) which extends over the

Abspritzkante (17) of the valve closing body (7) also open.

8. Fuel injection valve according to one of claims 2 to 6,

characterized,

in that at least one depression (26) in the valve seat surface (15) of the valve seat body (8) forms a recess space (26) when the sealing seat (9) is closed, which immediately adjoins the valve closing body (7) against the valve closing body (7). adjacent, but not on the Abspritzkante (17) out is open.

9. Fuel injection valve according to one of claims 1 to 8,

characterized,

in that at least one depression (27A) of the valve seat body (8) provided in front of the seat touch line (10) in the flow direction (20) forms a depression space (27A) when the sealing seat (9) is closed.

10. Fuel injection valve according to one of claims 1 to 9,

characterized, in that a plurality of indentations (25, 25A, 28A) are provided on the valve closing body (7) and a plurality of indentations (26, 26A, 27A) are provided in the valve seat surface (15) of the valve seat body (8) which, when the sealing seat (9) is closed, adjoin a joint seat Peripheral line (33) adjoin.