EP4413247A1

EP4413247A1 - Injector for injecting fuel

Info

Publication number: EP4413247A1
Application number: EP22836076.4A
Authority: EP
Inventors: Martin Seidl; Richard Pirkl; Razvan-Sorin STINGHE; Martin Schmidt; Lydia KAPUSTA
Original assignee: Liebherr Components Deggendorf GmbH
Current assignee: Liebherr Components Deggendorf GmbH
Priority date: 2021-12-15
Filing date: 2022-12-13
Publication date: 2024-08-14
Also published as: DE102021133250A1; CN118414482A; WO2023110821A1

Abstract

The invention relates to an injector (1) for injecting fuel, preferably for injecting a gaseous fuel, in particular hydrogen, comprising a fuel supply line for introducing a highly pressurized gaseous fuel, an active valve (3) which can be actively shut off and which is designed to close or release at least one passage (A1) on a first face of a valve plate (5) in order to selectively release or interrupt a fluidic connection between the fuel supply line and a region which is downstream of the first face of the valve plate, and a passive valve (4) which is arranged downstream of the valve plate and can be passively switched to a closing or releasing state as a result of different pressure ratios upstream and downstream of the passive valve, wherein the passive valve is designed to close or release the at least one passage on a second face of the valve plate facing away from the first face by means of a tappet in order to selectively release or interrupt a fluidic connection between the second face of the valve plate and a region downstream of the passive valve.

Description

Injector for injecting fuel

The present invention relates to an injector for injecting fuel, in particular for blowing in a gas, preferably for blowing in hydrogen directly. It can be provided that the injector is designed to inject fuel into a combustion chamber of an internal combustion engine.

In the course of ever more stringent emission limits and ambitious climate protection goals, the environmental requirements for internal combustion engines are constantly increasing. In the foreseeable future, the goal is low-emission or even zero-emission drive technologies that also meet the strictest emission limits and make a significant contribution to achieving climate protection goals. In the case of technologies that work with combustion, these goals can only be achieved if climate-neutral, regeneratively produced fuels are used that do not cause any emissions along the entire value chain (so-called "zero emissions" fuels).

With current conventional petrol, diesel and gas engines, the requirements for emission-free combustion - even when using so-called e-fuels, e.g. a synthetically produced OME fuel, for the production of which only regenerative energy is required - cannot be achieved because The emission of harmful exhaust gases such as nitrogen oxides (NOx), unburned hydrocarbons (UHC) and soot cannot be completely reduced with today's technologies.

In principle, battery-powered drives meet the zero-emissions directive during operation and are v. a. on the rise in the passenger car sector. If, on the other hand, the entire value chain is considered, the production of (lithium) batteries is very expensive in terms of energy and problematic from an environmental point of view, since the mining of raw materials causes severe environmental damage and the mining of the raw materials required for the batteries cannot be carried out sustainably. In addition, with the power-to-weight ratio that can be achieved today, use in machines with a high (peak) power requirement is not possible.

Fuel cell-powered drives powered by regeneratively produced hydrogen meet the specified climate protection goals and are already in use to a very limited extent. However, this concept also has some disadvantages, e.g. a low peak power compared to today's diesel drives and low economic efficiency.

The focus has therefore shifted to hydrogen combustion engines, which represent a promising drive alternative. To date, however, these exist almost exclusively in very small numbers or as demonstrators with a low degree of maturity. Hydrogen produced by regenerative energies would meet all the requirements of "zero emissions" because it can be combusted without producing any emissions.

In the passenger car sector, for example, there are hydrogen engines with external mixture formation (PFI = port fuel injection), in which the fuel is sufficiently mixed with air before it enters the combustion chamber. Hydrogen engines with direct injection of the fuel into the combustion chamber (internal mixture formation, DI = direct injection) play practically no role nowadays, but compared to the PFI concept they have, among other things, higher efficiency and more stability Combustion and elimination of the risk of flashback in the intake tract.

In the case of direct-injection hydrogen engines, a distinction is typically made with regard to the maximum injection pressure in the injector (< 60 bar: low pressure, > 60 bar: high pressure), although the limits are not clearly defined and the transitions are fluid. Higher pressures offer the potential for reduced injection duration late in compression at higher combustion chamber pressures, resulting in increased efficiency and improved combustion stability. However, the overall efficiency drops if the hydrogen has to be compressed beforehand.

If the hydrogen is obtained 100% from renewable energies, almost climate-neutral operation can be achieved with hydrogen combustion engines. In addition, there are numerous other advantages:

• Use of well-known technologies with a high level of maturity and existing production facilities

• unlimited availability of hydrogen through electrolysis of water

• Use of the existing filling station system possible (after appropriate conversion) with fast refueling times

• (Almost) emission-free conversion of hydrogen during combustion possible, as CO2-neutral, only minimal CO, UHC, particle and soot emissions (caused solely by lubricants in the intake system, below the measurement limit) and only minimal NOx emissions Suitable combustion process (possibly with exhaust gas recirculation, SCR catalytic converter)

• Significantly lower hydrogen purity requirements compared to fuel cell drives

• no need for platinum for production as with fuel cells In addition to these numerous advantages compared to other drive concepts, there are also some challenges that have to be overcome in the development of hydrogen combustion engines:

• low molecular weight of hydrogen, resulting in a low density accompanied by a low volumetric energy density (with a high mass-specific energy density); see Table 1

• Provision of a correspondingly high volume flow when blowing in hydrogen

• Corresponding provision of large flow cross-sections in the injector and thus required significantly larger strokes of the actuator than with conventional types of drive

• Associated development of a significantly stronger actuator unit with limited space at the same time

• Tightness of the entire system / prevention of external leaks, v. a. with regard to safety aspects (risk of fire and explosion due to hydrogen escaping from the system)

• Increased risk of wear on the guides of moving components due to the practically non-existent lubricating effect of hydrogen

• Significantly greater tendency of moving components to bounce against mechanical stops in gas injectors compared to injectors with liquid fuels due to the low damping effect during gas compression

• Material resistance to hydrogen necessary with regard to the risk of hydrogen embrittlement in mechanically stressed / pressurized components (reduced strength) or due to chemical reaction of the hydrogen with oxygen present in the copper coil of the actuator (hydrogen disease of the copper)

• Mixture preparation in the combustion chamber / influencing the injection jet / ignition behavior with injection of very small quantities

Table 1 : Mass and volume specific calorific value of diesel and hydrogen

It is the object of the present invention to at least partially overcome or mitigate the disadvantages listed above. In addition, it is advantageous if the injector takes up only a small installation space and/or has a small axial length. In particular, a fuel injector is to be created that enables reliable operation even under high thermal loads. It is also advantageous if the injector is reliably sealed against the pressure in the cylinder during its compression phase, since the high cylinder pressure would otherwise press the switchable valve into the open position. Furthermore, it is advantageous if rapid and stable opening is possible with the injector, in which case the flow is not throttled. At least some or all of the above objects are achieved with an injector for injecting fuel having all the features of claim 1. Advantageous configurations of the injector are specified in the dependent claims.

An injector according to the invention for injecting fuel, preferably for blowing in a gaseous fuel, in particular hydrogen, comprises a fuel supply line for introducing a gaseous fuel under high pressure, an active valve which can be actively switched and is designed to have at least one passage at a first to close or to open a side of a valve plate to selectively open or to interrupt a flow connection from the fuel supply line to an area downstream of the first side of the valve plate, and a passive valve, which is arranged downstream of the valve plate and through upstream and downstream of the passive valve abutting different Pressure conditions can be switched passively in a closing or releasing state. The injector is characterized in that the passive valve is designed to close or open the at least one passage of the valve plate on a second side of the valve plate facing away from the first side with a tappet in order to selectively establish a flow connection from the second side of the valve plate to an area to release or interrupt downstream of the passive valve.

Because the tappet of the passive valve attaches directly to the second side (for example the underside) of the valve plate, a particularly space-saving configuration of an injector results. Typically, in the prior art, a further sealing surface was provided for the implementation of the passive valve, which is arranged downstream of the valve plate, which inevitably leads to an axial enlargement of the injector. Since, according to the invention, the first side of the valve plate can be sealed by the actively switchable armature and the side of the valve plate facing away from it can be sealed by the plunger of the passive valve, this results in a particularly space-saving configuration of an injector that is compact in the longitudinal direction and reduces the installation space required.

Another advantage of the invention is that an unintentional lifting of the armature from the valve plate due to a pressure surge or a very high pressure level, which spreads for example during a compression phase of the cylinder or during combustion from the combustion chamber in the direction of the valve plate, results in the Plunger of the passive valve is pushed into its closed position against the valve plate. The passive valve therefore ensures that the valve and needle chambers are sealed against the cylinder pressure. As a result, the spring force with which the armature has to be pressed onto the valve plate in a closed position for a secure seal can also be reduced, which has a further advantageous effect on the dimensioning and the costs of the injector.

In addition, there is only a very small volume of fuel with the implementation of the invention, which is in the intermediate area of the active valve and Passive valve can be located. So if there is a vacuum downstream of the passive valve (e.g. in an expansion phase or in an intake phase of a cylinder), which causes the tappet of the passive valve to lift off the valve plate, only a very small volume of fuel flows out, which may possibly be unburned in enters an exhaust tract of an engine. As a result, the delivery of the fuel is improved in terms of efficient use, since the delivery timing can be controlled more reliably and much less fuel is unintentionally delivered even in the event of a negative pressure opening the passive valve.

According to a further optional development of the invention, it can be provided that when the passive valve is in a closed state, the tappet of the passive valve that can be moved back and forth is in contact with the second side of the valve plate in order to seal the at least one passage of the valve plate. In a closed position, the ram that can be moved back and forth makes contact with the second side (underside) of the valve plate and thus seals off the at least one passage penetrating the valve plate from the second side.

Provision can preferably be made for the tappet to be in direct contact with the second side of the valve plate or to be in indirect contact via an intermediate element when the passive valve is in a closed state.

According to an advantageous modification of the present invention, it can be provided that when the active valve is in a closed state, an armature of the active valve that can be moved back and forth in the longitudinal direction of the injector is in contact with the first side of the valve plate in order to separate the at least one passage of the valve plate from the first Seal side, preferably wherein the injector further comprises a coil which is designed to move the armature from its closed position by means of magnetic force.

On the first side (for example an upper side) of the valve plate is usually lifted from a closed position with the help of a coil Armature of at least one passage of the valve plate either closed or released. In a closed position, the armature seals the at least one passage of the valve plate, so that a fluid flow guided through the valve plate along the valve plate is prevented. In this case, a coil can optionally be provided which, when energized, generates a magnetic field which leads to the armature being raised, so that the at least one passage is released.

It can preferably be provided that when the active valve is in a closed state, the armature is in direct contact with the first side of the valve plate or is in indirect contact via an intermediate element. The intermediate element can represent a sealing element that surrounds the opening contour on the circumference or completely covers it and is arranged, for example, on the end face of the valve plate facing the armature. Alternatively or additionally, however, it is also conceivable that the sealing element is arranged on the end face of the armature facing the valve plate or is arranged freely movable between the valve plate and armature.

According to an optional development of the present invention, it can be provided that the stop of the tappet contacting the valve plate is designed as a flat seal, conical seal and/or ball seal. It is clear to the person skilled in the art that a large number of possible contact pairings can lead to a desired sealing effect. However, the flat gasket is particularly advantageous because during an opening process, in which the tappet is pushed away from the valve plate from a closing position, the fuel flow originating from the fuel supply line impinges directly on a flat plate, so that a high back pressure is created and large pressure forces are exerted , which open the plunger quickly and safely.

According to an optional development of the invention, it can be provided that the injector also includes an urging device which is designed to urge the tappet of the passive valve towards the valve plate in the closed position. It can advantageously be provided that the urging device comprises a spring element, in particular the spring element being a spiral spring. The spring element can be supported on an immovable counter-stop, which also has the task of limiting the maximum stroke of the ram. The counter-stop thus defines the maximum distance that the tappet can take from the valve plate.

According to a further development of the invention, it can be provided that the counter-stop, on which the spring element is supported, is only open towards the valve plate and is otherwise closed in a fluid-tight manner. It can be provided that the counter-stop comprises a first section running radially to the longitudinal direction of the injector and an adjoining second section running parallel to the longitudinal direction of the injector, which is preferably arranged coaxially to the injection pipe. The end of a spring element remote from the valve plate can be inserted into this circular pocket-like embodiment of the counter-stop, in particular the end of a spiral spring remote from the valve plate. The advantage of this is that when the tappet is maximally deflected, in which it contacts the counter-stop, the flow of the gaseous fuel does not interact with the spring element and thus no undesirable turbulence occurs. The spring element is therefore isolated from the flow path of the gaseous fuel and cannot adversely affect it. It is advantageously provided that the opening contour of the plunger is only arranged in an area which is inside the circular contour (when viewed in cross section) when placed on the counter-stop, which is circular in cross section of the contact area with the plunger.

According to a further advantageous modification of the present invention, provision can be made for an intermediate element to be arranged between the tappet and the valve plate, which is in contact with the tappet on a first side and the valve plate on an opposite side when the passive valve is in a closed position. The intermediate element can be designed as a sealing element and enclose or cover an opening contour of the valve plate on the end face facing the tappet. If the tappet and valve plate are brought together, the intermediate element, designed as a sealing element, fluidly seals the at least one passage through the valve plate in conjunction with the tappet.

It can also be provided that the intermediate element is made of a flexible material, in particular an elastomer, in order to reduce bouncing of the tappet when it hits the valve plate. In addition to an advantageous sealing effect, this also alleviates the problem caused by the tappet bouncing on the valve plate. If the intermediate element is made of a flexible material or if it comprises a flexible material, the stop is dampened when the tappet makes contact with the valve plate, so that bouncing is reduced.

Furthermore, according to the invention, it can advantageously be provided that the intermediate element is made of a heat-insulating material, in particular comprises a ceramic material or is made of a ceramic. If the intermediate element has heat-insulating properties, this means that components arranged upstream are shielded from the high temperatures that typically occur when fuel is burned. It is then possible to use components that are specified in a lower temperature range and can therefore consist of less expensive materials and enable an overall cheaper injector.

According to an optional development of the present invention, it can be provided that the intermediate element is or comprises a coating arranged on the end face of the tappet facing the valve plate and/or comprises or is a coating arranged on the end face of the valve plate facing the tappet. The intermediate element does not necessarily have to be designed as a separate disc or film, but can also be implemented by a coating arranged either on the tappet and/or the valve plate. This is regarding Production of the injector is advantageous since, with a coating on the tappet and/or the valve plate, fewer components have to be assembled manually or in an automated manner during production of the injector.

Furthermore, according to an advantageous embodiment of the present invention, it can be provided that the intermediate element is fastened to the tappet and/or the valve plate or is arranged so that it can move freely between the tappet and the valve plate. For example, it is conceivable for the intermediate element to be implemented as a shim or shim, which is also inserted in the ram guide section surrounding the ram on the peripheral side and is guided there. This implementation is particularly advantageous with regard to future maintenance costs, since it is to be expected that the intermediate element will be subject to particularly high wear. If this is the case, a worn disc can simply be removed and replaced with a new disc, allowing the original tappet and valve plate to be used.

According to an advantageous embodiment, it can also be provided according to the invention that a counter-stop limiting the maximum stroke of the tappet from the valve plate is provided, which is preferably provided with at least one damping element in order to dampen hitting of the tappet and reduce bouncing. The damping element used here can consist of a flexible material or can include such a material and is in particular made of an elastomer.

According to the invention, it can also be provided that the tappet of the passive valve has an opening contour through which the gaseous fuel originating from the fuel supply line flows downstream. According to an optional development of the invention, it can preferably be provided that the opening contour is implemented by a single bore, preferably a single central bore, in the tappet. Furthermore, it can be provided that in a fully open position of the passive valve, in which the tappet is thus of the valve plate is maximally spaced, the orifice contour presents the only passage for the gaseous fuel through which downstream flow can occur. This is implemented, for example, when the counter-stop is designed continuously on the inner circumference of the injection pipe in such a way that a fluid does not flow in the connection area of the counter-stop and the injection pipe surrounding the counter-stop.

The invention also relates to an internal combustion engine with a fuel injection, in particular with a gas direct injection, in particular with a hydrogen direct injection, comprising an injector according to one of the preceding claims 1-14.

Further features, details and advantages of the invention can be seen from the following description of the figures. show:

1: a schematic sectional view of an injector according to the prior art,

Fig. 2: an illustration of different states of components and pressures in an injector,

3: a schematic partial sectional view of an injector according to the invention in the area of the valve plate,

4a-b: a schematic sectional view of the injector according to the invention in a closed and an open state,

5: a schematic partial sectional view of an injector according to the invention according to a second embodiment in a closed state,

6: a schematic partial sectional view of the injector according to a third embodiment in a closed state, and 7: a schematic partial sectional view of the injector according to a fourth embodiment in a closed state.

The following detailed description of the figures of FIG. 1 is explained using an injector for blowing in a gaseous fuel, although it is clear to the person skilled in the art that the invention also includes an injector for injecting a different fuel.

1 shows a longitudinal section of an injector 1 for injecting a gaseous fuel, for example hydrogen, into a combustion chamber. The injector 1 has an injector housing in which different components of the injector 1 are located. A fuel supply line 2 for introducing fuel into the injector 1 is provided on the connection side. First, the fuel or another combustible fluid (e.g. hydrogen) is fed through a hole in a cover 16 running approximately centrally in the injector housing and then through a fluid channel in an armature counterpart 19, a through-opening in the armature base 23 and the hollow interior of the armature 7, sometimes also called hollow needle or just needle, to the end of the armature 7 remote from the terminal side.

Depending on the position of the armature 7 relative to the valve plate 5, the openings A1 penetrating the valve plate 5 are closed or opened. In the state shown in FIG. 1, the passages A1 are closed by the armature 7 being pressed against the valve plate 5, since the end face of the armature 7 covers the opening contours of the passages A1. To improve the tightness, sealing elements 25 can be provided, which run around the opening contours of the passages A1 and contact the end face of the armature 7 in a sealing state. If the passages A1 are closed by the face of the armature 7, the fluid flow of the fuel at this point of the injector 1 is stopped and there is no downstream flow of fuel beyond the valve plate 5. On the other hand, when the passages A1 are opened, which is implemented by lifting the armature 7 away from the valve plate 5 , the fuel introduced into the injector 1 with a certain pressure flows out and passes through the plurality of passages A1 on the side spaced apart from the armature 7 the valve plate 5. After flowing through a passive valve 4 provided in the injector 1, the pressurized fuel flows out of the injector through the injection cap 28. After flowing through the injection cap 28, the fuel delivered by the injector 1 is then typically located outside the injector 1 in a combustion chamber. In addition, the fuel is typically compressed in the combustion chamber 16, where the fuel then ignites or is ignited.

The passive valve 4, which is located on the side of the valve plate 5 facing away from the armature 7, serves to keep a very high pressure in the combustion chamber away from the armature 7. Otherwise it could happen that the very high pressure prevailing in the combustion chamber acts on the armature 7 and moves it away from its position closing the at least one passage A1. In a subsequent work step of the injector 1, the fuel required for combustion would then no longer be introduced into the combustion chamber, but an already at least partially burned mixture, which can lead to an interruption of the combustion process or, at best, to a lower performance of the combustion process.

The passive valve 4 has a valve tappet 6, a valve guide 27 and a valve spring 10, which urges the valve tappet 6 in a closing direction, so that fuel flows out via the opening contour A2 of the passive valve 4 only when on the valve plate 5 facing Side of the passive valve 4 there is a pressure which is greater than the pressure on the side facing away from the passive valve 4 to the valve plate 5 by at least the restoring force of the valve tappet 6 exerted by the valve spring 10 . This prevents a fluid from flowing in from the side of the passive valve 4 facing the combustion chamber. Deviating from the drawings, it can be provided that the opening contour is implemented by a single bore, preferably a single central bore, through which the flow of the gaseous fuel is guided through the passive valve. The provision of only one bore in the passive valve can be advantageous with regard to the required manufacturing costs of the passive valve and any turbulence that occurs in the flow guidance.

The armature 7 is reciprocally movable in the longitudinal direction of the injector 1 . The movement of the armature 7, which can consist of one piece or an armature base 23 and an armature tip (also called a needle or hollow needle), is controlled via an active valve 3, which is a solenoid valve in the present representation of FIG. The armature 7 is designed in such a way that it reacts to the magnetic force generated by a coil 8 . Current can optionally flow through the coil 8 in such a way that the resulting magnetic force moves the armature 7 in the direction of the fuel connection 2 . This movement causes the armature 7 to be raised relative to the valve plate 5. This opens up the passages A1 in the valve plate 5, so that fuel can flow through the valve plate 5.

For a precise guidance of the armature 7 along the longitudinal axis of the injector 10, an armature guide 24 can be provided which encloses an outer side of the armature 7 on the peripheral side.

An air gap 22 is provided between the armature 7 and the armature counterpart 19 and is closed or reduced when the coil 8 is energized.

In order to improve the magnetic flux 12 when the active valve 3 is implemented as a solenoid valve, the coil 8 can be surrounded on its peripheral outside by an iron yoke 21 in which the magnetic field can propagate particularly well. The situation is similar with the housing component directly surrounding the anchor element 5 and the anchor counterpart 27. which also preferably consists of a magnetizable material. So it can be advantageous if the pole tube 18, which is a part of the injector housing 2, is also made of iron or another ferromagnetic material. The same also applies to the armature counterpart 19, which advantageously also consists of a magnetizable material.

A visualized representation of the magnetic field lines 12 is illustrated in each case by the dotted, closed line that runs in a circle around the coil. The magnetic force pulls the armature element 7 (together with the armature base 23) towards the armature counterpart 19 and thus lifts it off the valve plate 5 or from the passages A1 breaking through the valve plate 5, so that fuel can flow towards the passive valve. from where fuel is ultimately introduced into the combustion chamber via the injection cap 28 .

2 shows the basic behavior of the injector 1 during an injection. In the starting position at time t ₀ at the bottom dead center (BDC) of the cylinder piston, the armature 7 and valve tappet 6 are pressed into their respective stops by the prestressed armature spring 17 or passive valve spring 10 and close the throttle points A1 or A2, which connect the needle chamber with the valve chamber or Connect the valve chamber to the injection chamber when armature 7 or valve tappet 6 is open. The pressure in the injector 1 corresponds to the pressure in the supply line, the pressure in the combustion chamber and in the injection chamber corresponds to the charge pressure during the intake phase of the cylinder piston, in which fresh air is sucked into the combustion chamber via the intake valves. The pressure in the valve chamber corresponds approximately to the combustion chamber pressure and depends, among other things, on the armature spring 17, the pressure in the combustion chamber during the phase in which the hot combustion gases are ejected via the outlet valves of the combustion chamber and any preceding injections. The functional representation is simplified below and does not take into account the gas exchange by opening and closing the intake and exhaust valves of the combustion chamber. At this point, the control device applies a voltage signal via the electrical contacts to the coil 8 of the actuator, so that the current F1 in the electrical circuit increases to a defined end level. The current-carrying coil 8 induces a magnetic field 12 in the actuator, the magnetic field lines of which propagate in a toroidal shape around the coil (see FIG. 1 ). The magnetic field 12 builds up a magnetic force F2 in the air gap between the armature 7 and the armature counterpart 19, whereby at the time t ₂ the armature 7 is attracted to the armature counterpart 19 as soon as the magnetic force F2 exceeds the closing force (sum of the prestressing force of the armature spring 17 and the pressure forces on the anchor 7) surpasses. The build-up of the magnetic field and thus the magnetic force F2 is delayed by eddy currents in the iron parts of the magnetic circuit. The armature 7 is integrally or firmly connected to the armature base 23, so that the armature 7 moves uniformly with the armature stroke (or also: needle stroke) F3. As soon as the sealing element 25 on the valve plate 5 is no longer in contact with the end face of the armature 7 at time t ₃ , the connection between the needle chamber and the valve chamber is released, so that the fuel flows from the needle chamber into the valve chamber. This increases the pressure in the valve chamber. As soon as the pressure difference from the valve chamber to the injection chamber corresponds to a force difference on the valve tappet 6 of the same magnitude as the prestressing force of the valve spring 10, the passive valve 4 opens, i.e. the valve tappet 6 moves away from the seat along a valve tappet stroke F4 and establishes the connection between the valve chamber and the injection chamber freely, so that fuel flows from the valve chamber into the injection chamber. This leads to an increase in pressure in the injection space (cf. F8: pressure in the injection space). Fuel continues to flow downstream through orifice(s) A3 in injection cap 28 into the combustion chamber. The injection cap 28 is designed in such a way that the flow can be introduced into the combustion chamber in a defined state (jet orientation, inlet impulse, jet pattern, etc.). The open state of armature 7 and valve tappet 6 is maintained throughout the rest of the energization phase. The current level can be reduced (eg by a PWM voltage signal) as soon as the armature 7 is fully open and possible bouncing does not lead to the armature 7 closing. During blow-in the cylinder of the engine is in the compression phase, so that the combustion chamber pressure F5 increases steadily.

In order to end the injection process, the power supply is terminated by the control unit, so that the current F1 through the coil 8 is reduced to zero (time t ₄ ). Due to the eddy currents, the magnetic force F2 also decreases with a time delay. As soon as the magnetic force F2 is less than the sum of the closing force of the armature spring 17 and the hydraulic forces on the armature 7, the armature 7 begins to close uniformly (time t ₅ ); see also F3, F4. If the end face of the armature 7 hits the sealing element 25 of the valve plate 5, the connection between the needle chamber and the valve chamber is broken and the flow of fuel from the needle chamber into the valve chamber is interrupted (time t ₆ ). This reduces the pressure in valve chamber F7. If the pressure difference from valve chamber F7 to injection chamber F8 corresponds to a force difference on valve tappet 6 of the same magnitude as the valve spring force, valve tappet 6 moves back into its closed position on valve seat 27 and is pushed against the Seat 27 pressed, so that the fuel connection between the valve chamber and injection chamber (possibly after a phase of bouncing of the tappet on the valve seat 27) is interrupted (times t ₆ - t ₇ ). This completes the blowing-in process. During the further compression phase of the combustion chamber up to top dead center (TDC) in the period t ₇ - t _s , the air-fuel mixture in the injection chamber is compressed, while it expands in the subsequent expansion phase (period t ₈ - t ₉ ), with the further interim increase of the combustion chamber pressure F5 due to combustion is not shown here for the sake of simplicity. If the pressure in the combustion chamber falls so far that the difference between the pressure forces on the valve tappet 6 corresponds to the prestressing force of the armature spring 17 (time t ₉ ), the valve tappet 6 opens again briefly, so that part of the fuel in the valve chamber flows into the combustion chamber escapes. This process depends on the spring force and can occur repeatedly (period t ₉ - 1 ₁₀ ). The respective mass flow of the fuel via the passages A1 of the valve plate 5, the passages A2 of the tappet 6 and the passages A3 of the injection cap 28 is given as F9, F10 and F11.

Fig. 3 shows a partial sectional view of an injector 1 according to the present invention with a focus on the passive valve 4 and the valve plate 5. It can be seen that the tappet 6 of the passive valve 4 is provided on an underside of the valve plate 5 and the passages provided in the valve plate 5 A1 seals by direct contact. On the other side of the valve plate 5, depending on the position of the armature 7 (or also: armature needle or just needle), the at least one passage A1 through the valve plate 5 is optionally closed or opened. Since the valve plate 5 can come into contact with the respective valve inserts, namely the tappet 6 and the armature 7, from two sides, a two-sided valve is disclosed which is only open when both valve inserts (piston 6 and armature 7) are in the open position. It can thus be seen that one end of the at least one passage A1 through the valve plate 5 can be closed by the armature 7 and the other end of the at least one passage A1 can be closed by the tappet 6 . The closing forces of the two valve inserts act antiparallel to one another, so that a force for lifting a respective valve insert (armature 7 and tappet 6) must be directed away from the valve plate 5.

In this case, the tappet 6 is urged into its closed position by a spring element 10 , the spring element 10 being supported on a counter-stop arranged downstream, which is arranged rigidly in the injector 1 . It can also be seen that the seal created by the tappet 6 on the underside of the valve plate 5 is a flat seal or a flat seat 13 .

The armature 7 is also urged onto the valve plate 5 with a certain force, which is typically exerted via an armature spring 17. The force exerted by the armature spring 17 on the armature 7 acts in the opposite direction to the force which is exerted by the spring element 10 to urge the plunger 6 into its closed position. The configuration shown with a direct seal on the underside of the valve plate 5 is very space-saving and allows very short injectors 1 in the longitudinal direction.

4a and 4b show a closed state (FIG. 4a) and an open state (FIG. 4b) of the injector. In FIG. 4b, the flow of fuel is shown with arrows, starting from the fuel supply line and towards the injection cap. Furthermore, the movement of the components required from their respective closed position, which is required to create the fluid connection between the fuel supply line and the injection cap, is also highlighted by arrows. It can be seen that the armature is lifted out of its closed position due to energization of the coil, which means that the fuel, which is under high pressure, forces the tappet of the passive valve out of its closed position. If the components have moved accordingly, the fuel, which is under high pressure, can flow from the fuel supply line to the injection cap out of the injector

flow out.

5 shows a schematic partial sectional view of an injector according to a second embodiment of the invention in a closed state. A corresponding shaping of the tappet 6 and the underside of the valve plate 5 can be seen, so that the seal produced by the tappet 6 being pressed against the underside of the valve plate 5 is implemented by a conical sealing seat or a ball sealing seat. The advantage here is that this type of sealing seat enables reliable sealing and is low-wear.

Fig. 6 shows a further embodiment of the present invention, in which in the intermediate region between the tappet 6 and the valve plate 5 an intermediate element

II is arranged, which preferably covers or encloses a contour of the at least one passage A1 of the valve plate 5 which is directed towards the plunger 6 . Provision can be made here for the intermediate element 11 to be made of a flexible material in order to avoid a stop of the plunger 6 during a movement dampen in the direction of the valve plate 5. An elastomer with very good damping properties can be used as an example for the flexible material.

As an alternative or in addition to the design as a flexible material, it can also be provided that the intermediate element 11 has a heat-insulating property or comprises or consists of a heat-insulating material. Furthermore, the intermediate element can also be a coating applied to the tappet 6 and/or the valve plate 5 , but alternatively it is also possible for the intermediate element 11 to be arranged freely movable in the space between the tappet 6 and the valve plate 5 .

The provision of the intermediate element 11 is particularly advantageous with regard to the fatigue strength of the sealing connection between the tappet 6 and the valve plate 5 and protects the components that are typically heavily stressed when the tappet 6 and the valve plate 5 hit.

7 shows a further modification of the idea according to the invention, in which the counter-stop 9, which defines the maximum stroke of the tappet 6 away from the valve plate 5, has a damping element 15. This damping element 15 is arranged on the counter-stop 9 in such a way that a ram 6 moving toward the counter-stop 9 is damped by the damping element 15 before its movement is completely stopped. This reduces the bouncing of the tappet 6 when the passive valve 4 opens, with the high material stresses associated with the bouncing also being reduced due to the damping element 15 .

It is clear to a person skilled in the art that the various embodiments of the present invention explained in the figures can be partially or fully combined with one another. Reference character list:

1 injector

2 fuel line

3 active valve

4 passive valve

5 valve plate

6 tappets / valve core

7 anchors

8 coil

9 counter stop

10 spring element

11 intermediate element

12 magnetic field lines

13 flat gasket/flat seat

14 cone seal seat/ball seal seat

15 damping element

16 housing cover

17 anchor spring

18 pole tube

19 anchor counterpart

20 by-pass

21 iron inference

22 air gap

23 anchor base

24 Anchor Guide/Needle Guide

25 sealing element

26 injection tube

27 valve guide

28 blow cap

A1 Passage of the valve plate

A2 Plunger passage

A3 Passage of the blowing cap

Claims

Expectations

1. Injector (1) for injecting fuel, preferably for blowing in a gaseous fuel, in particular hydrogen, comprising: a fuel supply line (2) for introducing a particularly gaseous fuel which is under high pressure, an active valve (3) which can be actively switched and is designed to close or open at least one passage (A1) on a first side of a valve plate (5) in order to selectively open or close a flow connection from the fuel supply line (2) to an area downstream of the first side of the valve plate (5). and a passive valve (4), which is arranged downstream of the valve plate (5) and can be passively switched into a closing or releasing state by the different pressure conditions present upstream and downstream of the passive valve (4), characterized in that the passive valve (4) is designed to close or open the at least one passage (A1) on a second side of the valve plate (5) facing away from the first side with a tappet (6) in order to selectively establish a flow connection from the second side of the valve plate (5) to a To release or interrupt the area downstream of the passive valve (4).

2. injector (1) according to the preceding claim 1, wherein in a closed state of the passive valve (4) of the reciprocating tappet (6) of the passive valve (4) with the second side of the valve plate (5) is in contact to seal the at least one passage (A1) of the valve plate (5).

3. injector (1) according to the preceding claim 2, wherein in a closed state of the passive valve (4) of the tappet (6) with the second side of the valve plate (5) is in direct contact or indirectly via an intermediate element (11) in contact stands.

4. injector (1) according to any one of the preceding claims, wherein in a closed state of the active valve (3) a reciprocating armature (7) of the active valve (3) with the first side of the valve plate (5) is in contact to sealing the at least one passage (A1) of the valve plate (5), preferably wherein the injector also has a coil (8) which is designed to move the armature (7) out of its closed position by means of magnetic force.

5. injector (1) according to the preceding claim 4, wherein in a closed state of the active valve (3) the armature (7) with the first side of the valve plate (5) is in direct contact or indirectly via an intermediate element (25) in contact stands.

6. Injector (1) according to one of the preceding claims, wherein the valve plate (5) contacting stop of the tappet (6) together with the second side of the valve plate (5) as a flat seal (13), conical seal (14) and / or ball seal is trained.

7. injector (1) according to any one of the preceding claims, further comprising an urging device which is designed to urge the tappet (6) of the passive valve (4) towards the valve plate (5) in the closed position.

8. injector (1) according to the preceding claim 7, wherein the urging device comprises a spring element (10), preferably wherein the spring element (10) is a spiral spring.

9. The injector (1) according to any one of the preceding claims, wherein an intermediate element (11) is arranged between the tappet (6) and the valve plate (5), which in a closed position of the passive valve (4) can be pushed from one side by the tappet (6 ) and is contacted by the valve plate (5) from a side opposite thereto.

10. injector (1) according to the preceding claim 9, wherein the intermediate element (11) is made of a flexible material, in particular an elastomer, in order to reduce bouncing of the tappet (6) when it hits the valve plate (5).

11. The injector (1) according to any one of the preceding claims 9 or 10, wherein the intermediate element (11) is made of a heat-insulating material, in particular comprises a ceramic or is made of a ceramic.

12. The injector (1) according to any one of the preceding claims 9-11, wherein the intermediate element (11) comprises or is a coating arranged on the end face of the tappet (6) facing the valve plate (5) and/or a coating on the tappet ( 6) facing end face of the valve plate (5) comprises or is arranged coating.

13. injector (1) according to any one of the preceding claims 9-12, wherein the intermediate element (11) on the plunger (6) and / or the valve plate (5) is fixed or freely between the plunger (6) and the valve plate (5). is movably arranged.

14. injector (1) according to any one of the preceding claims, wherein a maximum stroke of the plunger (6) of the valve plate (5) limiting counter-stop (9) is provided, which is preferably provided with at least one 26

Damping element (15) is provided in order to dampen impacts of the plunger (6) and to reduce bouncing.

15. Internal combustion engine with a fuel injection, in particular with a gas direct injection, in particular with a hydrogen direct injection, comprising an injector (1) according to any one of the preceding claims 1-14.