EP0646219A1

EP0646219A1 - Device for injecting a fuel gas mixture.

Info

Publication number: EP0646219A1
Application number: EP94911833A
Authority: EP
Inventors: Ferdinand Reiter; Heinz-Martin Krause; Martin Maier; Juergen Buchholz
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 1993-04-20
Filing date: 1994-04-07
Publication date: 1995-04-05
Anticipated expiration: 2014-04-07
Also published as: US5540387A; JPH07508334A; EP0646219B1; KR100327077B1; BR9405166A; DE59401799D1; JP3523256B2; DE4312756A1; WO1994024434A1

Abstract

Devices for injecting a fuel-gas mixture are known in which there is a gas chamber partially surrounding the downstream end of the injection valve radially and axially. Various embodiments of flow dividers or deflection surfaces are also known on which sprayed fuel is deflected without the addition of gas. The novel device has a flow divider (86) with a convex divider surface (88) facing the injection port plate (21). The convex flow divider (86) acts as a flow resistor producing a dynamic flow. The dynamic flow is responsible for the maintenance of the multi-jet system, despite gas inclusion, upstream of the flow divider (86) as well and the good preparation effect of the gas inclusion by improved mixing of gas and fuel. The proposed device for injecting a fuel-gas mixture is especially suitable for injection into the intake pipe of a mixture-compression spark-ignition internal combustion engine.

Description

Device for injecting a fuel-gas mixture

State of the art

The invention is based on a device for injecting a fuel-gas mixture according to the category of the main claim.

There is already known an electromagnetically actuated valve for injecting a fuel-gas mixture into a mixture-compressing spark-ignition internal combustion engine (DE-OS 41 21 372), in which a gas encasing sleeve surrounds a nozzle body of a fuel injection valve. The gas encasing sleeve is designed in such a way that its bottom part is shaped obliquely towards the valve end of the fuel injection valve with a concentric passage opening. In this way, a gas ring gap is formed between a spray orifice plate and the bottom part of the gas encasing sleeve. The one from the gas ring gap emerging gas stream is directed radially at the individual fuel jets emerging from the spray orifice plate and leads to an approximation of the fuel jets to one another up to a possible union to a single fuel jet.

Also known is an injection valve for injecting a fuel-gas mixture (US Pat. No. 4,957,241), in which a spacer plate for influencing the air quantity is installed between a nozzle body and a protective cap. The spacer plate between the nozzle body and the protective cap has a central opening into which the downstream pin end of a valve needle is immersed. The air supply to the fuel emerging from a fuel channel takes place via air channels and air chambers. The radial air supply for tapping the valve needle is determined by the height of, for example, four spacer knobs formed on the spacer plate. Ultimately, however, the amount and the composition of the fuel-air mixture is determined by the size of the annular gap extending in the axial direction between the pin of the valve needle and the circumference of the opening in the spacer plate.

Furthermore, from DE-OS 37 16 402 injection valves with a perforated plate, into which two injection holes are made, from which fuel jets emerge, which hit specific deflection surfaces of a prismatic deflection body and are deflected there in the desired directions, The fuel is not one Gas includes so that there is no risk of the fuel jets moving towards each other.

Also known are injection valves (US Pat. No. 4,982,716), in which a baffle is provided downstream of the single spray opening, which the single sprayed fuel jet strikes and is guided in film form into two spray channels, targeting the fuel films formed after the impact an air jet is directed.

Advantages of the invention

The device according to the invention for injecting a fuel-gas mixture with the characterizing features of the main claim represents an easily mountable and easy-to-adjust option for the improved treatment of fuel by supplying a defined amount of gas while maintaining the desired double radiation. This results in the advantage that, in contrast to wedge-shaped or knife-shaped beam splitters, gas splitters with a convex splitter surface above the splitter surface are stowed, the fuel jets being pushed outward from one another by the back pressure of the gas and thus maintaining the dual radiation remains. The convex beam splitter acts as a flow resistance, which causes a backflow. The ram flow is responsible for the dual radiation that is maintained in spite of the gas containment also downstream of the beam splitter and the good treatment effect of the gas containment through an improved mixing of gas and fuel. Advantageous further developments and improvements of the device specified in the main claim are possible through the measures listed in the subclaims.

It is particularly advantageous to use beam splitters with convex splitter surfaces which have circular, semicircular or elliptical cross sections. For certain desired beam angles, it is advantageous if the beam splitters have waist-shaped constrictions or bulges with convex divider surfaces.

It is advantageous to clamp a sheet-metal insert with spacers, for example molded-on knobs, between a spray-perforated disk and a gas-enclosing body. With the aid of the specially shaped sheet-metal insert and the dimensionally formed knobs, the gas is metered for improved fuel preparation. The sheet-metal insert is pressed against the spray-perforated disk by a section of the gas-enclosing body tapering upstream in the shape of a truncated cone, which at least partially abuts a conical area of the sheet-metal insert. The inserted sheet-metal insert is pre-centered via tabs which lead radially outward on the sheet-metal insert. The fine adjustment is achieved by pressing the gas enclosing body. A cone difference angle formed between the sheet metal insert and the gas encasing body ensures axial tolerance compensation with respect to the sheet metal insert and the gas encasing body with respect to the spray hole disk. Because of this Jamming and the cone difference angle associated therewith a seal is achieved so that fuel cannot penetrate into gas-carrying channels and flow channels.

drawing

Embodiments of the invention are shown in simplified form in the drawing and are explained in more detail in the following description. FIG. 1 shows a partially illustrated device for injecting a fuel-gas mixture according to a first exemplary embodiment according to the invention, FIG. 2 shows an enlarged detail from FIG. 1, FIG. 3 shows an effect of a beam splitter with a convex splitter surface, FIGS. 4 to 6 Exemplary embodiments for the design of the spray chamber surrounded by the gas-enclosing body with a beam splitter having a circular cross section, FIGS. 4a to 6a top views of the spray chambers shown in FIGS. 4 to 6, FIGS. 7 to 17 as middle cross sections, design examples for the formation of convex Beam splitters and FIGS. 7a to 17a top views of the beam splitters shown in FIGS. 7 to 17.

Description of the embodiments

In FIG. 1, a valve in the form of an injection valve for fuel injection systems of mixture-compressing spark-ignition internal combustion engines is shown partially and in simplified form as an exemplary embodiment. The injection valve has a tubular valve seat support 1, in which is concentric with one Longitudinal valve axis 2, a longitudinal opening 3 is formed. In the longitudinal opening 3 there is, for example, a tubular valve needle 5 which is connected at its downstream end 6 to an, for example, spherical valve closing body 7, on the circumference of which, for example, five flats 8 are provided.

The injection valve is actuated in a known manner, for example electromagnetically. An indicated electromagnetic circuit with a magnetic coil 10, an armature 11 and a core 12 is used for the axial movement of the valve needle 5 and thus for opening against the spring force of a return spring (not shown) or closing the injection valve the valve closing body 7 facing away from the end of the valve needle 5 by, for example a weld seam is connected by means of a laser and aligned with the core 12. The magnet coil 10 surrounds the core 12, which, for example, represents the end of an inlet connection piece (not shown in more detail) which surrounds the magnet coil 10 and which serves to supply the medium to be metered by means of the valve, here fuel.

A guide opening 15 of a valve seat body 16 serves to guide the valve closing body 7 during the axial movement. In the downstream end of the valve seat carrier 1 facing away from the core, the cylinder-shaped valve seat body 16 is tightly mounted in the longitudinal opening 3, which is concentric to the valve longitudinal axis 2, by welding . The circumference of the valve seat body 16 has a slightly smaller diameter than the longitudinal opening 3 of the valve seat carrier 1. At its one, the Lower end face 17 facing away from the valve closing body 7, the valve seat body 16 is concentrically and firmly connected to a base part 20 of, for example, a cup-shaped spray orifice plate 21, so that the base part 20 rests with its upper end face 19 on the lower end face 17 of the valve seat body 16. The connection of the valve seat body 16 and the spray perforated disk 21 takes place, for example, by means of a circumferential and sealed first weld seam 22, for example formed by a laser, on the base part 20. This type of assembly means that there is at least a risk of undesired deformation of the base part 20 in the area of the base part two, for example four, injection openings 25 formed by stamping or eroding, which are located in a central region 24 of the base part 20, are avoided.

The base part 20 of the cup-shaped spray perforated disk 21 is adjoined by a circumferential retaining edge 26 which extends in the axial direction away from the valve seat body 16 and is conically bent outwards as far as its downstream end. The holding edge 26 has a larger diameter at its end than the diameter of the longitudinal opening 3 of the valve seat carrier 1. Since the peripheral diameter of the valve seat body 16 is smaller than the diameter of the longitudinal opening 3 of the valve seat carrier 1, there is only between the Longitudinal opening 3 and the slightly tapered outwardly curved retaining edge 26 of the spray plate 21 a radial pressure. The holding edge 26 exerts a radial spring action on the wall of the longitudinal opening 3. As a result, when the valve seat body 16 consisting of the valve seat body 16 and the spray perforated disk 21 is inserted, Part of the seat in the longitudinal opening 3 of the valve seat carrier 1 prevents chip formation on the valve seat part and on the longitudinal opening 3.

The depth of insertion of the valve seat part consisting of valve seat body 16 and cup-shaped spray orifice plate 21 into the longitudinal opening 3 determines the presetting of the stroke of the valve needle 5, since the one end position of the valve needle 5 when the solenoid coil 10 is not excited due to the valve closing body 7 resting on a valve seat surface 29 of the valve seat body 16 is fixed. The other end position of the valve needle 5 is determined when the solenoid 10 is excited, for example by the armature 11 resting on the core 12. The path between these two end positions of the valve needle 5 thus represents the stroke.

At its downstream end, the holding edge 26 of the spray plate 21 is connected to the wall of the longitudinal opening 3, for example by a circumferential and tight second weld seam 30. The second weld 30 is formed like the first weld 22, for example by means of a laser. The parts to be welded are only slightly heated during laser welding and the process is safe and reliable. A tight weld of the valve seat body 16 and the spray orifice plate 21 as well as of the spray orifice plate 21 and the valve seat support 1 is necessary so that the fuel does not pass between the longitudinal opening 3 of the valve seat support 1 and the circumference of the valve seat body 16 to the spray openings 25 or between the longitudinal opening 3 of the valve seat carrier 1 and the holding edge 26 of the cup-shaped spray perforated disk 21 therethrough can flow directly into an intake line of the internal combustion engine. Because of the two weld seams 22 and 30, there are consequently two fastening points on the cup-shaped spray perforated disk 21.

The spherical valve closing body 7 interacts with the valve seat surface 29 of the valve seat body 16 tapering in the shape of a truncated cone, which is formed in the axial direction between the guide opening 15 and the lower end face 17 of the valve seat body 16. The valve seat body 16, facing the solenoid 10, has a valve seat body opening 33 which has a larger diameter than the guide opening 15 of the valve seat body 16. A section 34 which adjoins the valve seat body opening 33 in the direction of the spray orifice plate 21 is characterized by its conical frustoconical taper up to the diameter of the guide opening 15. The valve seat body opening 33 with its subsequent frustoconical section 34 serves as a flow inlet so that a flow of the medium can take place from a valve interior 35 limited in the radial direction through the longitudinal opening 3 of the valve seat carrier 1 to the guide opening 15 of the valve seat body 16.

So that the flow of the medium also reaches the spray openings 25 of the spray orifice plate 21, for example five flats 8 are introduced on the circumference of the spherical valve closing body 7. The five circular flats 8 allow the medium to flow through in the open state of the injection valve from the valve interior 35 to the spray openings 25 of the Spray hole disk 21. For the exact guidance of the valve closing body 7 and thus the valve needle 5 during the axial movement, the diameter of the guide opening 15 is designed such that the spherical valve closing body 7 projects through the guide opening 15 outside of its flattened portions 8 with a small radial distance.

At its downstream end, the valve seat carrier 1 is at least partially radially and axially enclosed by a stepped concentric gas-enclosing body 41. The gas encasing body 41 made of a plastic includes, for example, both the actual gas encasing at the downstream end of the valve seat support 1 and a gas inlet channel (not shown), which serves to supply the gas into the gas encasing body 41 and, for example, is formed in one piece with the gas enclosing body 41 is. To an axially extending, tubular section 43 of the gas encasing body 41, which is connected, for example, to a plastic encapsulation of the injection valve in the axial direction between the magnet coil 10 and the valve closing body 7 by ultrasonic welding, is followed by a section 44 tapering downstream. This conical section 44 is, for example, also stepped. The formation of the gas enclosing body 41 in this area can be varied in accordance with the spatial conditions of a valve receptacle, not shown. The section 44 is followed downstream by an axially extending tubular section 45 of the gas enclosing body 41, which, however, is distinguished by a much smaller diameter than in the section 43. The axial section 45 surrounds this downstream end of the valve seat support 1 both directly adjacent and at a radial distance from the supply of the gas up to the fuel emerging from the spray openings 25 of the orifice plate 21. In, for example, three to six areas of section 45 of the gas-enclosing body 41, the walls are therefore formed less strongly than in the entire other peripheral area. The reduction in the wall thickness of the gas containment body 41 in section 45 has the result that, for example, three to six gas inlet channels 48 are formed between the valve seat support 1 and the gas containment body 41, which for example regularly run axially at equal intervals on the circumference of the valve seat support 1, for example at three gas inlet channels 48 offset by 120 ° each or six gas inlet channels 48 offset by 60 ° each.

The section 45 of the gas enclosing body 41 is designed in such a way that first chamfers 49 are formed in the areas of the gas inlet channels 48 and extend axially over the entire length of the gas inlet channels 48. In addition, the section 45 of the gas enclosing body 41 has second chamfers 50 at its upstream end, which are only formed on the circumference outside the gas inlet channels 48 and which simplify assembly when the gas enclosing body 41 is pushed on from the downstream side onto the valve seat carrier 1 and thus enable the injector. The axially extending section 45 has at its upstream and downstream ends a radially outward-facing circumferential shoulder 52, 53, which together with the outer wall of section 45 form an annular groove 55. A sealing ring 56 is arranged in the annular groove 55, the Side surfaces are formed by the downstream side of the shoulder 52 and the upstream side of the shoulder 53 and the groove base 58 thereof by the outer wall of the section 45 of the gas encasing body 41. The sealing ring 56 serves to seal between the circumference of the injection valve with the gas encasing body 41 and a valve receptacle (not shown), for example the intake line of the internal combustion engine or a so-called fuel and / or gas distribution line.

At its downstream end, the valve seat carrier 1 has an outer circumferential taper 60 and an inner circumferential taper 61, against which no other components are in contact and which are intended to improve the assembly of the gas encasing body 41 on the injection valve, while on a downstream end face 62 of the valve seat carrier 1, the gas encasing body 41 with a radially extending section 63 in the areas outside the gas inlet channels 48. In order to ensure that the gas flows into a metering cross section, the axially extending gas inlet channels 48 are followed, for example, by as many, for example three to six, radially extending flow channels 64 between the radially extending section 63 of the gas encasing body 41 and the downstream end face 62 of the valve seat carrier 1 arise after the assembly of the gas enclosing body 41 and the gas flows radially through it. The gas then flows axially upstream into an annular channel 65 between a last concentric section 68 of the gas enclosing body 41 which tapers in the shape of a truncated cone upstream and the wall of the longitudinal opening 3 in the valve seat support 1 until it is deflected Kung the flow at a lower end face 69 of the bottom part 20 of the spray plate 21 in the radial direction.

The gas-enclosing body 41 presses at least partially with an outer surface 70 of its section 68, which projects into the injection valve and thus into the valve seat support 1 in the direction of the orifice plate 21, against an inner surface 72 of a tapered and circumferential region 73 of a sheet metal insert 74, which in turn abuts on the lower end face 69 of the base part 20 of the spray plate 21 with spacers, for example knobs 75. With the aid of the specially shaped sheet-metal insert 74 and the knobs 75 molded onto it with dimensional accuracy, the gas is ultimately metered for improved preparation of the fuel emerging from the spray openings 25 of the spray plate 21. The sheet metal insert 74 is formed by a radial region 77 with a mixture spray opening 78 running in it centrally and concentrically to the longitudinal axis 2 of the valve, the region 73 which is conical and thus oblique to the longitudinal axis 2 and, for example, three radially outward and conical Area 73 formed downstream tabs 80. On the radial region 77 of the sheet-metal insert 74, the knobs 75 are formed at at least three, then offset by 120 °, which have an axial expansion in the direction of the spray-perforated disk 21, and these are provided on their lower end face 69 after the gas-encasing body 41 has been installed touch point.

With the knobs 75 of the sheet-metal insert 74, an axial distance between the lower end face 69 of the spray hole Washer 21 and an upper end face 81 of the radial region 77 of the sheet metal insert 74 facing the spray orifice disk 21, which corresponds to the axial height of the knobs 75 and thus the axial expansion of a gas ring gap 83 formed thereby. The knobs 75 of the sheet metal insert 74 are introduced, for example, by embossing processes, since this allows the desired, very small tolerances of the axial extent to be maintained. The axial dimension of the extent of the gas ring gap 83 forms the metering cross section for the gas flowing in from the ring channel 65, for example treatment air. The gas ring gap 83 serves to supply the gas to the fuel discharged through the spray openings 25 of the spray orifice plate 21 and to meter the gas. The gas supplied through the gas inlet ducts 48, the flow ducts 64 and the ring ducts 65 flows through the narrow gas ring gap 83 to the mixture spray opening 78 and meets the fuel emitted through the two or four spray openings 25, for example. Due to the small axial extent of the gas ring gap 83 predetermined by the knobs 75, the gas supplied is greatly accelerated and atomizes the fuel particularly finely. For example, the suction air branched off by a bypass in front of a throttle valve in the intake manifold of the internal combustion engine, air conveyed by an additional blower, but also recirculated exhaust gas from the internal combustion engine or a mixture of air and exhaust gas can be used as the gas.

The mixture spray opening 78 in the radial region 77 of the sheet metal insert 74 has such a large diameter that it flows upstream from the spray openings 75 of the spray orifice plate 21 Escaping fuel, which the gas comes vertically from the gas ring gap 83 for better processing, can exit unhindered through the mixture spray opening 78 of the sheet metal insert 74.

The sheet metal insert 74 is pressed against the spray orifice plate 21 by the upstream frustoconical section 68 of the gas encasing body 41, which at least partially abuts the inner surface 72 of the conical area 73 of the sheet metal insert 74. FIG. 2 clearly illustrates this clamping area as an enlarged detail from FIG. 1. The sheet metal insert 74 is designed in such a way that, for example, three tabs 80 (FIG. 1) adjoin the area 73 downstream, which serve to precenter the sheet metal insert 74 in the valve seat support 1. The tabs 80 have radial end surfaces 85, which are achieved, for example, by smooth stamping and are of good quality with regard to their surface roughness. This ensures that the tabs 80 with their radial end faces 85 can rest as precisely as possible on the wall of the longitudinal opening 3 in the valve seat support 1. With the help of the gas encasing body 41 pressing against the conical area 73 of the sheet-metal insert 74, the pre-centered sheet-metal insert 74 is finely adjusted. There is a line contact between the gas encasing body 41 and the sheet-metal insert 74, which leads to the frusto-conical section 68 of the gas encasing body 41 when it is pushed further upstream a surface contact. Between the outer surface 70 of the portion 68 of the gas containment body 41 and the inner surface 72 of the area 73 of the sheet metal insert 74 inevitably results in a cone difference angle α. This cone difference angle α ensures an axial tolerance compensation with respect to the sheet metal insert

74 and the gas containment body 41 with respect to the spray orifice plate 21. By clamping the two components sheet metal insert 74 and gas containment body 41 and the associated cone difference angle α, a seal is achieved so that fuel cannot enter the gas-carrying ring channels 65 and flow channels 64.

A beam splitter 86 is provided in the gas containment body 41 downstream of the mixture spray opening 78 of the sheet metal insert 74. The jet expensive 86 runs transversely through the longitudinal axis 2 of the valve and symmetrically divides a spray chamber 87 formed by the gas-enclosing body 41 downstream of the mixture spray opening 78. The spray chamber 87 can first be cylindrical in accordance with the design of the gas encasing body 41 in the flow direction and then be conical or continuously cylindrical or elliptical. Viewed in the axial direction, the beam splitter 86 is located, for example, at the same height as the radially extending section 63 of the gas enclosing body 41, which therefore also represents the connection of two points of the section 63 which are 180 ° apart. The beam splitter 86 can both be part of the gas enclosing body 41 made of plastic as a web, and can also be installed, for example, as a pin made of another material. Crucial in the design of the beam splitter 86 is the formation of an upper, upstream, convex splitter surface 88. FIG. 3 is intended to illustrate the effect of the beam splitter 86 with its convex splitter surface 88 in the case of two-jet valves with gas enclosures. Two or four fuel jets are generated by the two or four spray openings 25 in the spray orifice plate 21 and are sprayed into the spraying space 87 in areas formed on both sides of the beam splitter 86. The inventive design of the beam splitter 86 is useful not only in the case of individual fuel jets directed onto the beam splitter 86, but also when the fuel jets run past the beam splitter 86 or when they also move away from one another with increasing distance from the spray openings 25 . The fuel jets are hit vertically by the gas flowing out of the gas ring gap 83 immediately after they emerge from the spray openings 25. The consequence of this is that the dual radiation of the fuel jets is endangered by the gas enclosure and the two fuel jets can even merge, since the gas moves the fuel jets towards one another, as indicated by the dotted lines 90. In contrast to wedge-shaped or knife-shaped beam splitters, gas is jammed in the beam splitters 86 with a convex splitter surface 88 above the splitter surface 88, the fuel jets being pushed apart outward again by the back pressure of the gas, and thus a clear dual radiation is retained. This effect of the back pressure of the gas only occurs in the case of a beam splitter 86 with a conventional dividing surface 88, while in the case of a wedge-shaped or cutting-shaped beam splitter a back pressure which may form is negligibly small. The convex beam splitter 86 works as flow resistance, which causes a ram flow. The ram flow is responsible for the very compact beam splitting in the area of the beam splitter 86 and the good treatment effect of the gas enclosure due to an improved mixing of gas and fuel. With wedge-shaped or knife-shaped beam splitters, no proper two-jet radiation is achieved when surrounding the gas, since the fuel jets move towards one another again downstream of the beam splitter. Only in the direction of flow very long beam splitters with a wedge-shaped or cutting-shaped cross section achieve the same effect as the convex beam splitters 86 which have a small extension in the axial direction. The dash-dotted lines 91 show fuel jet profiles in two-jet valves without gas containment. The convex splitter surface 88 of the beam splitter 86 ensures that an equally good double radiation is created in the axial direction downstream from the beam splitter 86, despite the gas enclosure. The transition from the dotted line 90 to the dash-dotted line 91 is intended to illustrate this.

By using gas enclosing bodies 41 with different geometry of the spraying chamber 87 and the jet splitter 86, the most varied jet angles of the injection valves can be achieved. Only through variations of the gas enclosing body 41 or the jet part 86 are there a multitude of possibilities for the geometry of the sprayed-off fuel-gas mixture. FIGS. 4 to 6 and 4a to 6a schematically show exemplary embodiments for the design of the spraying chamber 87 surrounded by the gas-enclosing body 41 with a beam splitter 86, which has a circular cross section. The execution Example in FIG. 4 illustrates a cylindrical spraying space 87 in the area of the beam splitter 86, FIG. 5 shows a conical spraying space 87, as can also be seen in FIGS. 1 and 3, and FIG. 6 shows an elliptical spraying space 87. FIGS. 4a to 6a represent top views of the spraying chambers 87 shown in FIGS. 4 to 6.

7 to 17 and 7a to 17a, some possible design variants of the convex beam splitters 86 are simplified and shown schematically as cross sections or top views. The convex splitter surface 88 is decisive in the formation of the beam splitter 86. The variants shown allow different beam angles of the fuel-gas mixture. In addition to beam splitters 86 with circular (FIGS. 7, 7a), semicircular (FIGS. 8, 8a), elliptical (FIGS. 12, 12a) or semi-elliptical (FIGS. 11, 11a) or other rounded cross sections (FIGS. 9, 9a, 13, 13a, 15, 15a), beam splitters 86 are also conceivable which have, for example in their central region, waist-shaped constrictions (FIGS. 9, 9a, 10, 10a, 14, 14a, 15, 15a) for small beam angles or bulges (FIG. 16, 16a, 17, 17a) for larger beam inke1.

Claims

Expectations

1. Device for injecting a fuel-gas mixture, with an injection valve, in particular an electromagnetically actuated fuel injection valve, for fuel injection systems of internal combustion engines, with a longitudinal valve axis, with a movable valve closing body, with a valve provided at the downstream end of the injection valve. Seat body, which has a valve seat surface interacting with the valve closing body, with a spray-perforated disc arranged downstream of the valve seat surface and having at least two spray orifices, with a gas-encasing body which at least partially axially and at least partially radially surrounds the downstream end of the injection valve with the spray-orifice disc, with one Mixture spray opening for the exit of the fuel-gas mixture, characterized in that a jet splitter (86) is provided downstream of the mixture spray opening (78), said beam splitter (86) transversely to the valve longitudinal axis (2 ) and running through this to the spray perforated disc (21) has a convex divider surface (88), which causes a ram flow, whereby a multi-jet of the fuel jets sprayed from the spray openings (25) is maintained downstream of the jet splitter (86) despite the gas enclosure.

2. Device according to claim 1, characterized in that the mixture spray opening (78) in a sheet metal insert (74) is introduced, which is a separate from the gas enclosing body (41) component.

3. Apparatus according to claim 2, characterized in that the sheet metal insert (74) is frustoconical, the mixture spray opening (78) being arranged in a radial region (77) and a conically tapering region (73) which tapers towards the spray orifice plate (21) ) connects downstream to the radial region (77).

4. The device according to claim 2, characterized in that the sheet metal insert (74) in the axial direction of the spray orifice plate

(21) facing knobs (75), through the axial height of which a gas ring gap (83) is formed between the spray orifice plate (21) and the sheet metal insert (74), which serves as a metering cross-section for the supplied gas.

5. The device according to claim 3, characterized in that the sheet-metal insert (74) between the gas enclosing body (41) and the spray perforated disc (21) is clamped.

6. The device according to claim 5, characterized in that the clamping of the sheet metal insert (74) in the tapered region (73) by the gas enclosing body (41).

7. The device according to claim 1, characterized in that the beam splitter (86) as a web is part of the gas enclosing body (41).

8. The device according to claim 1, characterized in that the beam splitter (86) is a separate component and is fixed in the Gasum¬ socket body (41).

9. The device according to claim 1, characterized in that the beam splitter (86) has a circular cross section.

10. The device according to claim 1, characterized in that the beam splitter (86) has a semicircular cross section.

11. The device according to claim 1, characterized in that the beam splitter (86) has an elliptical cross section.

12. The apparatus according to claim 1, characterized in that the beam splitter (86) has a semi-elliptical cross section.

13. The apparatus according to claim 1, characterized in that the beam splitter (86) has at least one waist-shaped constriction.

14. The apparatus according to claim 1, characterized in that the beam splitter (86) has at least one bulge.

15. The apparatus according to claim 1, characterized in that downstream of the mixture spray opening (78) is a spray chamber (87) which is cylindrical in the direction of flow and in which the beam splitter (86) is arranged.

16. The apparatus according to claim 1, characterized in that downstream of the mixture spray opening (78) is a spray chamber (87) which is designed to widen in the direction of flow and in which the beam splitter (86) is arranged.

17. The apparatus according to claim 1, characterized in that downstream of the mixture spray opening (78) is a spray chamber (87) which is elliptical in the direction of flow and in which the beam splitter (86) is arranged.

18. The apparatus according to claim 1, characterized in that downstream of the mixture spray opening (78) is a spray chamber (87) which is enclosed by the gas enclosing body (41).