Gas injector for internal combustion engines

Abstract

The present invention relates to a gas injector for an internal combustion engine, comprising a housing (1) and an injector valve needle (3) slidably disposed within the housing along its longitudinal axis (2) for introducing and metering a gas flow into and into the combustion chamber of the internal combustion engine, and an electromagnet energized to actuate the injector valve needle (3), the electromagnet having a slidably disposed armature (5), characterized in that: the armature (5) can be decoupled from and reset to a deactivated position from the injector valve needle (3) in an activated position when de-energized, and at a sealing point (21), the gas flow is gas-tightly cut off by the sealing contact between the armature (5) and at least one seal (22); and the armature (5) is connected to a hollow body (30), the hollow body (30) being coaxial with the gas flow within the housing (8) and fixedly disposed with the housing, and the hollow body being airtight and elastic in the axial direction.

Description

Technical Field

[0001] The present invention relates to a gas injector for an internal combustion engine, the type of which is defined in more detail in the preamble of claim 1. Background Technology

[0002] A valve for metering fluids, particularly a fuel injection valve for an internal combustion engine, is known from DE 10 2019 205 301 A1. It includes a housing and an armature of an actuator disposed in an armature chamber of the housing, and a valve needle actuated by the armature along a longitudinal axis and overcoming a return spring.

[0003] In addition, other injectors are also known in DE 10 2021 206 186 A1 and DE 10 2021 213 023 A1. Summary of the Invention

[0004] Therefore, the objective of this invention is to provide a gas injector of the type described above, which can prevent gas leakage or reduce it to an acceptable level in a structurally simple manner when the internal combustion engine is stopped.

[0005] This task is solved by the features of claim 1. Other advantageous and claimed improvements are derived from the corresponding dependent claims, the description, and the drawings.

[0006] Therefore, a gas injector for an internal combustion engine is proposed, comprising a housing and an injector valve needle slidably disposed within the housing along its longitudinal axis for introducing and metering a gas flow into the combustion chamber of the internal combustion engine. To adjust the injector valve needle within the housing, an energized electromagnet with a slidably disposed armature is provided. To avoid or reduce gas leakage to an acceptable level in a structurally simple manner when the internal combustion engine is stopped, it is specified that: the armature, from an activated position in actuated contact with the injector valve needle, can slide relative to the injector valve needle and reset to a deactivated position in a de-energized state; and at a sealing point, the gas flow is tightly cut off through a sealing contact between the armature and at least one seal. The armature is connected to a hollow body, which is coaxial with the gas flow within the housing and fixedly disposed with the housing, and the hollow body is airtight and axially elastic.

[0007] Optionally, the hollow body has an opening leading to a valve cavity enclosed by the shell.

[0008] Therefore, at the sealing point located far from the combustion chamber and in a lower operating temperature range, the gas flow can be reliably sealed in a simple manner by at least one highly sealing seal (preferably made of plastic). This avoids the need for laborious and costly metal-to-metal contact seals that can only be manufactured in high-temperature regions.

[0009] Since the armature can be decoupled from the injector valve needle and reset to the deactivated position with a small axial gap from the injector valve needle when the power is off, the axial component tolerances between the injector valve needle and the armature can be compensated in a simple way, especially at the needle valve seat and at the sealing point.

[0010] Therefore, the injector valve needle, in particular, can be manufactured with lower precision and less mass. Due to the smaller mass, the inertia of the injector valve needle and the force generated by its impact on the needle valve seat are reduced, allowing the use of lower-strength materials. Alternatively, the permissible impact velocity of the injector valve needle can be increased.

[0011] In addition, the armature can be accelerated from the deactivated position before forming actuation contact with the injector valve needle, thereby shortening the adjustment time of the injector valve needle.

[0012] The connection between the armature and the hollow body causes a static force generated by the gas pressure present in the gas flow to act in the direction of the armature's movement to the deactivated position, thus closing and cutting off the gas flow. Since this force increases with the gas pressure in the gas inlet region, the sealing effect at the sealing seat is enhanced as the gas pressure rises. Therefore, even under very high gas pressures, especially in fault conditions, a tight seal at the sealing point can be ensured.

[0013] In a preferred embodiment of the invention, the armature can be directly coupled to the injector valve needle for actuation contact. This eliminates the need for additional components for transmitting the regulating motion. Furthermore, it reduces axial installation space.

[0014] In a further preferred improvement of the invention, the hydraulically effective diameter of the hollow body is equal to or greater than the contact diameter of the sealing contact between the seal and the contact surface formed on the sealing counterpart of the armature. This ensures, in a simple manner, that the existing gas pressure always generates a closing force on the armature to cut off the gas flow. The closing force can be increased by increasing the outer diameter of the hollow body.

[0015] Furthermore, the armature can be easily reset to the deactivated position; in particular, the return spring can be set with a smaller spring force.

[0016] The hydraulically effective diameter should be understood, in particular, as the diameter of the hollow body that is hydrodynamically effective in terms of pressure drop and flow rate of the gas flow. For a circular flow cross-section, i.e., the circular cross-sectional shape of the hollow body, the outer diameter of the hollow body can be taken as the hydraulically effective diameter. For flow cross-sections that deviate from a circular shape, the hydrodynamically effective virtual diameter of the hollow body, determined as an approximation, can be taken as the hydraulically effective diameter.

[0017] A particularly simple and preferred configuration of the hollow body can be achieved by a metal bellows that is elastic in the axial direction.

[0018] Preferably, the seal is made of plastic, thereby achieving particularly high sealing performance with relatively low manufacturing precision. Furthermore, it is advantageous to use an elastic material for the seal, which can compensate for manufacturing inaccuracies in the connected components. For this purpose, an elastomer is particularly suitable for the seal, but other suitable materials can also be used.

[0019] In another preferred embodiment of the invention, the armature and the housing respectively form sealing seats at the sealing point for achieving annular sealing contact with at least one sealing element. This annular sealing contact enables a higher sealing effect.

[0020] A further improvement of the invention specifies that the seal is configured as a sealing ring, which is easy to assemble, has low manufacturing cost, and can ensure high sealing performance.

[0021] Preferably, in this case, the armature forms a circumferential concave sealing surface at the sealing point, adapted to the shape of the sealing ring, as a sealing seat, wherein the sealing element constituting the sealing ring is accommodated in a radially inward circumferential sealing contact manner. Preferably, the sealing ring is fixedly mounted on this sealing surface.

[0022] In a further improvement of the invention, the housing forms a circumferential sealing surface at the sealing point that extends radially outward along the gas flow direction, serving as a sealing seat. In the deactivated position, the seal can be airtightly abutted against this sealing surface. This achieves a sealing contact with a high sealing effect. Furthermore, in the activated position of the armature, i.e., when the gas injector is open, the sealing surface on the housing functions as a flow guide surface to guide the gas flowing between the seal and the housing at the sealing seat.

[0023] Alternatively, the seal can be injection molded onto the armature or onto the housing at the sealing seat. Furthermore, it is conceivable that the seal, as a sealing ring, is fixedly mounted onto the sealing seat on the housing.

[0024] In another preferred embodiment of the invention, the armature, on the one hand, cooperates with a return spring to reset it to a deactivated position during actuation contact, and on the other hand, is in annular sealing contact with a seal arranged in the gas flow at the sealing point. Because the armature is configured for direct actuation and sealing contact, additional components, especially those for force transmission or sealing, are avoided. Furthermore, a particularly compact configuration with high sealing performance can be achieved using a single seal.

[0025] Furthermore, it is advantageous that the return spring is preferably disposed in the electrode tube of the electromagnet in the form of a helical compression spring, and acts coaxially between the electrode tube and the armature at the outer diameter of the injector valve needle guided through the electrode tube.

[0026] Preferably, the housing has a multi-piece structure in the gas inlet region, comprising an intermediate housing forming a sealing point therein and a connector housing connected thereto, wherein the hollow body fixed to the housing is disposed in the connector housing. This simplifies, in particular, the assembly of the seal at the sealing point and the assembly of the hollow body with the armature. Attached Figure Description

[0027] Other features of the invention will be derived from the following description and from the accompanying drawings, which will further illustrate the invention.

[0028] It shows: Figure 1 According to the invention, the gas injector for an internal combustion engine in the deactivated operating state... Figure 2 Figure 1 A magnified view of the local area. Figure 3 The gas injector in its activated working state Figure 4 Figure 3 The magnified part differs in that the central flow channel is formed as a through opening rather than a blind hole. Detailed Implementation

[0029] An example of a gas injector for an internal combustion engine according to the invention is shown in the accompanying drawings. The gas injector has a multi-piece housing 1 and an injector valve needle 3 slidably disposed within the housing 1 along its longitudinal axis 2 for introducing and metering a gas flow into the combustion chamber of an internal combustion engine (not shown). This gas injector is preferably used to inject hydrogen as fuel into the combustion chamber of an internal combustion engine.

[0030] To adjust the injector valve needle 3, an energized electromagnet is installed in the housing 1. This electromagnet has a magnetic coil 4 and a slidably mounted armature 5. The latter is coaxially mounted with the injector valve needle 3 within the housing 1, sliding back and forth along a longitudinal axis 2, which also forms the sliding axis. When the magnetic coil 4 is de-energized, the armature 5 can be decoupled from the injector valve needle 3 and reset relative to it. Figure 1 and Figure 2 The indicated closing position.

[0031] At the gas inlet region 6 of the gas injector, the housing 1 is a multi-piece structure, having an intermediate housing 7 and a connector housing 8 axially connected thereto. The latter forms a gas interface 9 at its free end for connection to a gas supply system (not shown) of an internal combustion engine with a gas reservoir (especially a gas canister). This gas supply system pressurizes the gas injector at the gas interface 9 with a gas flow (preferably hydrogen) at a high pressure, preferably 40 bar.

[0032] The intermediate housing 7 is connected to the pole tube 10 of the electromagnet in the downstream axial direction of the gas flow. For this purpose, the intermediate housing 7 is axially inserted into the inner diameter of the pole tube 10 with a fixed section of its outer diameter for fixation, for example, by press-fitting or welding. The pole tube 10 serves, on the one hand, to support and guide the armature 5. On the other hand, it guides the magnetic flux generated by the electromagnet or magnetic coil 4. The magnetic coil 4 is disposed at the outer diameter of the pole tube 10 and coaxially surrounds it, and is housed in the magnet housing 11 fixed at the outer diameter of the pole tube 10.

[0033] A needle guide housing 13 is connected to the electrode tube 10 in the axial direction toward the gas outlet 12 of the gas injector, i.e. toward the combustion chamber. The needle guide housing 13 is axially inserted into the inner diameter of the free end of the electrode tube 10, for example, by press-fitting or welding.

[0034] The injector valve needle 3 is axially slidably guided in the central axial first hole 14 in the electrode tube 10 and in the needle guide housing 13 in a central axial through hole 15 coaxial with and following the first hole 14. It has a through central axial hole 41, which serves as a hollow needle for guiding gas, in this case, hydrogen. To blow the gas flow into and meter it into the combustion chamber, the injector valve needle 3 forms a valve body 16 at the gas outlet 12 of the gas injector. This valve body 16 is disposed in a valve seat 17 formed at the outlet end of the through hole 15 in the needle guide housing 13. The valve body 16 and the valve seat 17 form a needle valve. The valve body 16 is disc-shaped, where the gas flow entering the combustion chamber is metered. The needle guide housing 13 is radially inward at its outer diameter toward the combustion chamber relative to the electrode tube 10.

[0035] In electrode 10, armature 5 is axially slidably disposed relative to injector valve needle 3 in a second hole 18 axially connected to the first hole 14 toward the gas inlet region 6. In this case, the second hole 18 is expanded relative to the first hole 14 at its inner diameter by a step 39. The aforementioned holes 14 and 18 thus form a stepped hole in electrode 10.

[0036] exist Figure 3 and Figure 4 In the activated position of the armature 5 shown, the gas injector is switched to the open position, and gas is guided to the combustion chamber via a needle valve formed at the valve body 16 and valve seat 17. The armature 5 is in the activated position where it is in direct actuation contact with the injector valve needle 3 (e.g., Figure 3 and Figure 4 As shown), when the magnetic coil 4 is de-energized, it can be decoupled from the injector valve needle 3 and reset to its original position. Figure 1 and Figure 2 The deactivated position is shown, with a small axial distance 35 from the injector valve needle 3. In the deactivated position, the gas injector is in the closed position, in which the gas supply to the internal combustion engine combustion chamber is interrupted.

[0037] To reset to Figure 1 and Figure 2 In the deactivated position shown, the armature 5 engages with the return spring 19 disposed in the electrode tube 10. These return springs are coaxially disposed as helical compression springs at the outer diameter of the injector valve needle 3, in the widened section where the inner diameter of the first hole 14 of the electrode tube 10 extends radially outward through a step, and one spring end is supported at the step of the hole 14, while the other spring end is supported at the axial end face 20 of the armature 5 facing the injector valve needle 3.

[0038] In the gas inlet region 6, the armature 5 and the intermediate housing 7 are respectively connected to the sealing element 22 disposed in the gas flow. Figures 1 to 4 The sealing surfaces 23 and 26 (preferably constructed as a sealing ring) form sealing seats. For this purpose, a sealing surface 23 is formed on the axial side of the armature 5 facing the intermediate housing 7, in which the sealing element 22 is accommodated.

[0039] Preferably, the seal 22 is made of plastic, thereby achieving particularly high sealing performance with relatively low manufacturing precision. By means of an elastic material, the seal 22 can compensate for manufacturing inaccuracies in the connected components.

[0040] Elastomers are particularly suitable for this purpose, but other suitable materials can also be used.

[0041] The armature 5 tapers radially inward at its outer diameter via a step 24, forming a centrally axially protruding connecting pin 25. At the root region of the connecting pin 25, an annular concave groove adapted to the shape of the sealing ring is formed at its outer diameter as a sealing surface 23, wherein the sealing element 22 is fixedly disposed in a radially inward circumferential sealing contact manner.

[0042] Corresponding to the sealing surface 23 on the armature 5, a cylindrical circumferential sealing surface 26 is provided at the inner diameter of the intermediate housing 7, extending obliquely outward from its inner diameter. Thus, the sealing surface 26 is aligned obliquely inward relative to the longitudinal axis 2 with the sealing surface 23 on the armature 5 and the sealing element 22 disposed thereon.

[0043] In addition, Figure 3 and Figure 4 In the activated position of the armature 5 shown, that is, in the open state of the gas injector, the sealing surface 26 can act as a flow guide surface to guide the gas through the annular gap 42 at the sealing seat opened between the seal 22 on the intermediate housing 8 and the sealing surface 26.

[0044] Here, the sealing surface 26 is located at its radially outer end within a region of multiple annularly distributed gas inlet openings 27 at the steps 24 of the armature 5, the gas inlet openings 27 communicating with a flow channel 28 extending centrally in the armature 5. Therefore, in the sealing seat opened at the sealing surface 26, gas entering via the annular gap 42 is directly guided along the sealing surface 26 to the gas inlet openings 27 on the armature 5. The central flow channel 28 in the armature 5 can be configured as a blind hole (as shown) starting from the axial end face 20 on the side of the armature 5 facing the needle. Figures 1 to 3 Alternatively, the flow channel 28 can be configured as a through opening. Figure 4 ).

[0045] The advantage of the through-opening configuration is that during the operation of the injector, there is the same pressure on both sides of the connecting pin 25, so that no pressure difference needs to be overcome to open the valve during operation.

[0046] In the gas inlet region 6, the intermediate housing 7 forms a radial annular gap 29 on its radially inner side relative to the outer diameter of the connecting pin 25. Gas can flow axially toward the sealing point 21 along the annular gap 29.

[0047] By resetting armature 5 to Figure 1 and Figure 2 In the deactivated position shown, the seal 22 is pressed radially outward against the sealing surface 26 on the intermediate housing 7 to form an annular sealing contact, and the gas flow entering at the sealing point 21 is cut off. Thus, the gas injector is in a deactivated operating state.

[0048] Under the oblique orientation of the sealing surface 26 on the intermediate housing 7, the seal 22 is pressed obliquely against the step 24 at the sealing surface 23 on the armature 5 relative to the longitudinal axis 2. In this way, a particularly reliable setting of the seal 22 is achieved in the sealing seat at the sealing surfaces 23 and 26, while obtaining a high sealing effect. Therefore, in the shutdown state, gas leakage from the gas inlet area 6 to the internal combustion engine combustion chamber can be avoided or at least reduced to a harmless level.

[0049] The armature 5 is axially connected to a hollow body 30 via a connecting pin 25 extending axially into the connector housing 8. The hollow body 30 is coaxially positioned within the connector housing 8 in the gas flow and fixedly attached to the housing. The hollow body 30 is itself airtight and elastic in the axial direction, i.e., the direction of movement of the armature 5. It is preferably rotationally symmetric with respect to the longitudinal axis 2, and is here a closed hollow cylinder. Preferably, as shown in the figure, the hollow body 30 is constructed as a metal bellows, and this is particularly simple to achieve.

[0050] The hollow body 30 ensures that a surface with a pressure direction opposite to the opening direction of the injector valve needle 1 is pressurized at the same pressure as the sealing seats 23 and 26 on the intermediate housing 7. If the diameter of the hollow body 30 is equal to or larger than the diameter of the sealing seat, the pressure present in the gas inlet region 6, especially in the joint housing 8 before the sealing point 21, acts as a closing force.

[0051] The connection between the armature 5 and the hollow body 30 allows the static force of the resultant force—the static force of the gas pressure present in the gas inlet region 6, especially in the connector housing 8, acting through the hollow body 30 on the armature 5 and thus on the sealing seats 23 and 26—to act along the direction of the armature 5's movement to the deactivated position. This closes the sealing position at the sealing seats of the sealing surfaces 23 and 26, cutting off the gas flow. Since this force increases with the gas pressure in the gas inlet region 6, the sealing effect at the sealing seats 23 and 26 is enhanced as the gas pressure increases. Therefore, even under very high gas pressures, especially in fault conditions, the sealing performance at the sealing seat 26 can be ensured.

[0052] Therefore, it becomes easy to reset the armature 5 to the deactivated position; in particular, the return spring 19 can be set with a correspondingly lower spring force.

[0053] The configuration of the hollow body 30 can be optimized for the sealing seat 21 if the hydraulic diameter 31 of the metal bellows 30, i.e., the diameter that is hydraulically effective, especially in terms of pressure drop and gas flow, is at least equal to and preferably greater than the contact diameter 32 of the annular sealing contact between the seal 22 and the sealing surface 26 of the intermediate housing 7. By increasing the hydraulic diameter 31 of the hollow body 30 to a size exceeding the contact diameter 32 of the sealing contact, the resulting closing force can be increased.

[0054] The armature 5 is axially inserted into the cup-shaped first connector 33 on the hollow body 30 via the outer diameter of the free end of the connecting pin 25, and is fixed thereto, for example, by pressing or welding. On the other hand, the hollow body 30 is fixed to the inner diameter of the connector housing 8 by means of the second connector 34, preferably by welding.

[0055] To switch to Figure 3 and Figure 4 In the activated position shown, the magnetic coil 4 is energized, and the armature 5 is axially attracted by the pole tube 10. Thus, the armature 5 and the seal 22 are... Figure 1 and Figure 2 The deactivation position shown moves away from the intermediate housing 7. Therefore, the sealing seats at sealing surfaces 23 and 26 open with an annular gap 42 to allow gas passage. After a short axial displacement path 35, the armature 5 forms direct actuating contact with the opposite end face 37 of the injector valve needle 3 via its axial end face 20 facing the injector valve needle 3, thus accelerating the injector valve needle.

[0056] Following a further axial displacement path 40, the end stop 38 of the armature 5 at the widened step 39 of the second hole 18 of the electrode tube 10 reaches the activated position. During this process, the valve body 16 is lifted from the valve seat 17, and an annular gap 43 is formed between the valve body 16 and the valve seat 17, thus opening the needle valve and allowing gas (here, hydrogen) to flow into the combustion chamber of the internal combustion engine. Therefore, the gas injector is in an activated operating state.

[0057] In the activated operating state, gas flows from the gas interface 9 into the connector housing 8, toward the sealing seat 21, and enters the central flow channel 28 through the gas inlet opening 27 on the armature 5, and from its opening end into the axially opposite central hole 41 of the injector valve needle 3. In the region of the valve body 16, gas flows into the through hole 15 on the needle guide housing 13 through the gas outlet opening 44 pointing obliquely outward toward the valve body 16, and enters the combustion chamber through the annular gap 43 formed by the valve body 16 and the valve seat 17.

[0058] If the energization of the magnetic coil 4 is subsequently terminated, the injector valve needle 3, under the action of its cooperating return spring 45 and the armature 5, under the action of the return spring 19, moves toward the deactivated position, i.e., the closed direction. During this process, the valve body 16 reaches the valve seat 17 again, and the injector valve needle 3 is stopped. Therefore, the needle valve leading to the combustion chamber closes again. At the same time, the armature 5 continues to move relative to the injector valve needle 3 along the displacement path 35 until it reaches the deactivated position ( Figure 1 and Figure 2 At sealing point 21, the sealing element 22 is pressed into the sealing seat at sealing surfaces 23 and 26 in an airtight manner, and the gas supply is cut off again at sealing point 21 when the gas injector is deactivated.

[0059] The return spring 45, which mates with the injector valve needle 3, is preferably disposed in the region of the through hole 15 in the needle guide housing 13 facing the end of the electrode tube 10. It is coaxially disposed at the outer diameter of the injector valve needle 3 within a stepped groove 46 arranged radially outward from the inner diameter of the through hole 15. The return spring 45 is supported at one end in the groove 46 of the needle guide housing 13 and at the other end on a spring support 47 fixedly connected to the injector valve needle 3.

[0060] Explanation of reference numerals in the attached figures 1. Shell 2. Longitudinal axis 3. Injector valve needle 4. Electromagnetic coil, electromagnet 5. Armature, electromagnet 6. Gas Inlet Area 7. Intermediate shell 8. Connector housing 9 Gas Interface 10-pole transistor, electromagnet 11. Magnet casing, electromagnet 12 Gas outlet 13 Needle housing 14 First Hole 15 Through Holes 16 Valve body 17 Valve seat 18 Second Hole 19 Return spring components, helical compression springs 20. Axial end face of the armature 21 Sealing point, sealing seat 22. Seals, sealing rings 23. Sealing surface on the armature, sealing seat 24. Steps on the armature 25 Connecting pins 26. Sealing surface and sealing seat on the intermediate housing. 27. Gas inlet opening on the armature 28 Flow Channel 29 Radial annular gap 30 Hollow body, metal bellows 31. Hollow body outer diameter, hydraulic diameter 32. Contact diameter of the sealed contact 33 First Connector 34 Second connector 35 Axial displacement stroke, spacing 37. Axial end face of the injector valve needle 38 End stop 39 steps 40 Axial displacement stroke 41. Central hole in the injector valve needle 42 Annular Gap 43 Annular Gap 44 Gas outlet opening 45 Groove 46 Return spring components 47 Spring Support

Claims

1. A gas injector for an internal combustion engine, comprising: A housing (1) and an injector valve needle (3) slidably disposed within the housing along its longitudinal axis (2) for introducing and metering a gas flow into and into the combustion chamber of the internal combustion engine; And an electromagnet energized to actuate the injector valve needle (3), the electromagnet having a slidably disposed armature (5), characterized in that: the armature (5) can be decoupled from and reset to the deactivated position when de-energized from the activated position in actuated contact with the injector valve needle (3); and at a sealing point (21), the gas flow is gas-tightly cut off by the sealing contact between the armature (5) and at least one seal (22); and the armature (5) is connected to a hollow body (30), the hollow body (30) being coaxial in the gas flow within the housing (1) and fixedly disposed with the housing, and the hollow body being airtight and having axial elasticity.

2. The gas injector according to claim 1, characterized in that, The armature (5) can be directly coupled to the injector valve needle (3) for actuation contact.

3. The gas injector according to claim 1 or 2, characterized in that, The hydraulically effective diameter (31) of the hollow body (30) is equal to or greater than the contact diameter (32) of the sealing contact between the seal (22) and the sealing contact surface (26) formed on the sealing counterpart of the armature (5).

4. The gas injector according to any one of claims 1 to 3, characterized in that, The hollow body (30) is designed as a metal bellows.

5. The gas injector according to any one of claims 1 to 4, characterized in that, The seal (22) is made of plastic.

6. The gas injector according to any one of claims 1 to 5, characterized in that, The armature (5) and the housing (1) respectively form sealing seats (23, 26) at the sealing point (21) for achieving annular sealing contact with at least one sealing element (22).

7. The gas injector according to any one of claims 1 to 6, characterized in that, At the sealing point (21), the armature (5) forms a circumferential concave sealing surface (23) as a sealing seat for the sealing element (22), wherein the sealing element (22), which is formed as a sealing ring, is accommodated in a radially inward circumferential sealing contact manner.

8. The gas injector according to any one of claims 1 to 7, characterized in that, The housing (1) forms a circumferential sealing surface (26) at the sealing point (21) that extends radially outward along the gas flow direction as a sealing seat. In the deactivated position, the sealing element (22) can be airtightly attached to the sealing surface.

9. The gas injector according to claim 1 or 8, characterized in that, The armature (5) cooperates with the return spring (19) to reset it to the deactivated position in the actuation contact, and is in annular sealing contact with the seal (22) arranged in the gas flow at the sealing point (21).

10. The gas injector according to any one of claims 1 to 9, characterized in that, The housing (1) has a multi-piece structure in the gas inlet region (6), having an intermediate housing (7) in which the sealing point (21) is formed and a connector housing (8) connected thereto, wherein the hollow body (27) is fixedly disposed in the connector housing (8) and fixed to the housing.

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