Gas injectors with damping devices, especially for short strokes

Abstract

The present invention relates to a gas injector for injecting gaseous fuel, comprising: an electromagnetic actuator (2) having an armature (20), an inner pole (21), and a coil (22); a shut-off element (3) that releases and closes a gas path (14) at a sealing seat (11), wherein the armature (20) is operatively connected to the shut-off element (3); a closed lubricant chamber (4) filled with lubricant, wherein the armature (20) is disposed in the lubricant chamber, wherein the lubricant ensures lubrication of the armature (20); and a braking device (6) disposed in the lubricant chamber (4), the braking device being configured to brake the shut-off element (3) during the reset process of the gas injector from an open state to a closed state; wherein the braking device (6) has a brake pin (60), a damping chamber (62) filled with lubricant, an elastic braking element (61), and an armature operatively connected to the armature. An armature pin and a guide plate (25) are provided. The damping chamber is fluidly connected to the lubricant chamber (4) via a first fluid path (101). The brake pin (60) and the resilient brake element (61) are capable of being brought into operative connection with the closing element (3) during the reset process. The brake pin (60) is configured during the reset process of the gas injector to discharge lubricant from the damping chamber (62) into the lubricant chamber (4) to dampen the reset of the closing element (3) to the closed state. The armature pin (24) is guided in the guide plate (25). A brake pin valve (66) for releasing and closing the second fluid path (102) is provided at a brake valve seat between the lubricant chamber (4) and the damping chamber (62). The brake pin valve (66) is configured to fill the damping chamber (62) with lubricant when the gas injector is in the open state.

Description

Technical Field

[0001] This invention relates to a gas injector for injecting gaseous fuels, particularly hydrogen or natural gas, which has reduced wear and improved damping characteristics, and is particularly suitable for internal combustion engines. The gas injector is specifically designed for direct injection into the combustion chamber of an internal combustion engine and is particularly well-dampened during short opening strokes. Background Technology

[0002] Gas injectors are known in various configurations by existing technology. The problem with gas injectors, determined by their principle, lies in the fact that lubrication through the gaseous medium is impossible, unlike in fuel injectors that inject gasoline or diesel fuel. This results in excessive wear during operation compared to fuel injectors used for liquid fuels. Therefore, it is desirable to improve the wear characteristics of gas injectors. Summary of the Invention

[0003] In contrast, the gas injector for blowing in gaseous fuel according to the present invention has the following advantages: it can significantly reduce wear on the gas injector. This can be ensured both during the long opening stroke and during the short opening stroke of the gas injector. This extends the service life of the gas injector and makes it substantially comparable to the service life of fuel injectors for liquid fuels. In particular, when closing the gas injector, the closing element can perform a significantly better damped closing process, thereby reducing or preventing wear on the seal and other components of the closing element. Especially in the case of short opening times of the gas injector, such as during internal combustion engine idling or in multiple short blowing processes, sufficient damping of the closing element returning to the initial closed position can be ensured. According to the invention, this is achieved by having a lubricant located in a closed lubricant chamber, in which the movable parts of the gas injector are arranged. The gas injector includes an electromagnetic actuator having an armature, an inner pole, and a coil. The armature is configured to enable movement for opening and / or closing the gas injector. This armature is operatively connected to a closing element that releases and seals the gas path at a sealing seat. The armature, located within the lubricant chamber, is continuously supplied with lubricant and lubricated. When the coil is energized, the armature is pulled towards the inner pole of the electromagnetic actuator by electromagnetic force. This significantly reduces wear on the armature compared to gas injectors known to date in the prior art. Furthermore, by using a closed, lubricated chamber, the service life of the gas injector can be significantly extended. Preferably, the lubricant chamber is completely filled with lubricant.

[0004] Furthermore, the gas injector includes a braking device arranged in a lubricant chamber, configured to brake and dampen the closing element during the reset process of the gas injector from an open to a closed state. The braking device includes a brake pin, a damping chamber, and a resilient braking element, particularly a spring, which is fluidly connected to the lubricant chamber via a first fluid path. Additionally, the braking device includes an armature pin and a guide disc, at which an armature is arranged and operatively connected to the closing element, the armature pin being guided within the guide disc. A brake pin valve of the braking device is configured to release and / or close a second fluid path for additionally charging the damping chamber of the braking device with lubricant. Here, charging of the damping chamber via the second fluid path occurs in the open state of the gas injector. The brake pin valve is arranged at a brake seat (Bremsventilsitz) between the armature pin and the brake pin for releasing and / or closing the second fluid path.

[0005] The brake pin and resilient braking element are operatively connected to the closing element and / or armature during the reset process. The brake pin, during reset, is also configured to allow lubricant to be discharged from the damping chamber, thus damping the reset of the brake pin and consequently the reset of the damping closing element. Since part of the braking process is also provided by hydraulic adhesion between the brake pin and the stop member, which the brake pin rests against in the open state of the gas injector, the damping chamber prevents the formation of bubbles in the liquid lubricant when overcoming hydraulic adhesion, thereby particularly preventing wear caused by cavitation.

[0006] This is further supported by the additional mass acceleration provided by the braking device. Furthermore, further braking is achieved by discharging lubricating material through the armature and brake pin. By providing two fluid paths for filling the damping chamber with lubricant, it is also possible to reliably and adequately fill the damping chamber with lubricant even when the gas injector is only briefly opened. Thus, during the subsequent closing of the gas injector, it is always possible to ensure that there is sufficient lubricant in the damping chamber to dampen the reset process of the closing element. The reset speed of the closing element can also be further reduced due to the friction between the guide elements and the brake pin. All of these factors reduce the impact force of the armature on the stop, thereby further extending the armature's lifespan.

[0007] The preferred embodiments of the present invention illustrate preferred extensions of the present invention.

[0008] Preferably, the brake pin valve includes a through-hole in the brake pin that connects the first end face of the brake pin to the damping chamber and is part of the second fluid path. The armature pin has a second end face facing the damping pin, wherein, in the closed state of the gas injector, the first end face of the brake pin abuts against the second end face of the armature pin, thus closing the second fluid path. Therefore, in the closed state, no lubricant can flow into the damping chamber through the through-hole in the brake pin. Here, the second fluid path is only open in the open state of the gas injector, allowing sufficient lubricant to enter the damping chamber through the open brake pin valve and the through-hole in the brake pin.

[0009] More preferably, the braking device includes a throttling section disposed in a first fluid path between the damping chamber and the lubricant chamber. The throttling section is preferably a stepped orifice and ensures fluid connection between the damping chamber and the lubricant chamber in every operating state of the gas injector, i.e., whether open or closed. The damping characteristics of the braking device can be set by selecting the orifice geometry, such as the orifice diameter and / or length.

[0010] The throttling section is preferably disposed in the guide body and configured as a through hole in the guide body, wherein the guide body is configured to guide the brake pin. Alternatively, a first fluid path is configured between the brake pin and the guide body, and is preferably configured as a groove in the circumferential surface of the brake pin and / or as a groove in a guide post in the guide body for the brake pin.

[0011] To ensure the damping chamber is filled with lubricant as quickly as possible, preferably, one or more channels are constructed in the side of the guide disc facing the brake pin. Alternatively or additionally, one or more channels are constructed in the first end face of the brake pin. Here, the additional channels ensure that sufficient lubricant can flow from the lubricant chamber to the damping chamber via a second fluid path in the open state. Further flow improvement is achieved when the channels are preferably fluidly connected to each other by surrounding recesses. The recesses for connecting these channels are preferably constructed in the guide disc.

[0012] Preferably, the brake valve seat between the brake pin and the armature pin is constructed as a flat sealing seat. Alternatively, the brake valve seat is a cone-ball fit seat (Kegel-Kugel-Sitz) or a cone-cone fit seat (Kegel-Kegel-Sitz).

[0013] According to another preferred embodiment of the invention, the resilient braking element of the braking device is arranged in a damping chamber. This allows for a particularly compact structure. The resilient braking element is preferably a compression spring, especially a cylindrical spring.

[0014] According to another preferred embodiment of the invention, the gas injector includes a guide disposed in a lubricant chamber, the guide being configured to guide a brake pin. Preferably, the guide has a recess, particularly at the end of the guide pointing towards the sealing seat, in which the brake pin is guided. To ensure a seal in the lubricant chamber, a flexible sealing element, such as a bellows, is preferably provided, which seals the lubricant chamber in a partial area.

[0015] Preferably, the flexible sealing element of the lubricant chamber comprises first and second flexible sealing elements. These two sealing elements are particularly preferably bellows. Thus, the lubricant chamber is sealed by two flexible sealing elements, thereby preventing the formation of unfavorable overpressure or negative pressure when the lubricating material is discharged from the lubricant chamber. Such overpressure or negative pressure could, for example, exert undesirable forces on the shut-off element of the gas injector via components of the lubricating material reservoir. By providing two flexible sealing elements, even if unfavorable forces are applied to one of the sealing elements (which could cause a pressure increase in the closed lubricant chamber), compensation can be provided by the second flexible sealing element. Therefore, undesirable pressure changes within the closed lubricant chamber can be successfully prevented.

[0016] More preferably, the reservoir spring applies a predetermined force from the outside to the lubricant in the closed lubricant chamber. Preferably, this force is 0.5 Pa to 10 × 10⁻⁶ Pa. 5 Pa, particularly preferred from 1 Pa to 5 × 10 Pa. 5 Pa of overpressure. Therefore, the lubricant in the lubricant chamber can be placed under a predetermined prestress, thereby reliably preventing undesirable deformation that may affect the stroke of the shut-off element.

[0017] The second bellows is further preferably connected to the reservoir spring via a spring disc. This allows for a simple and cost-effective structure. Furthermore, the reservoir spring allows a prestress to be directly applied to the second bellows, thereby easily increasing its rigidity compared to the first bellows.

[0018] Preferably, oil, especially mineral oil, is used as a lubricant. Alternatively, liquid fuels, especially diesel or gasoline, are used. Further alternatively, greases, PAO oils (Poly Alpha Olefine), ester oils, or polyethylene glycol oils are used as lubricants.

[0019] The gas injector is preferably an outward-opening injector. More preferably, the gas injector is pressure-balanced. Thus, the force used to open the gas injector via the electromagnetic actuator is independent of the gas pressure. Therefore, the time used to open and close the injector at the start or end of energization is also independent of the gas pressure. This, in turn, allows operation at different gas pressures. When a small blow-in volume is desired, the gas pressure can be reduced, and when a large blow-in volume is desired, the gas pressure can be increased. The injector is pressure-balanced when the average diameter of the bellows is equal to the diameter of the seat contact line between the closing element and the valve body. However, the average bellows diameter can also be implemented to be smaller or larger than the seat diameter. In the first case, at higher gas pressures, the total closing force acting on the valve needle decreases, and the injector opens faster upon energization and closes more slowly after energization. This results in an increased gas blow-in volume. In the second case, at higher gas pressures, the closing force acting on the valve needle increases. This can compensate for the increased leakage caused by higher gas pressure.

[0020] Reset is preferably performed using a return spring. In pressure-compensated injectors, especially in the closed state of the gas injector, there is no clamping force exerted on the valve needle by the gaseous fuel, which can significantly reduce the load on the closing element. Attached Figure Description

[0021] Embodiments of the present invention will now be described in detail with reference to the accompanying drawings. In the drawings: Figure 1 A schematic cross-sectional view of a gas injector according to a first preferred embodiment of the present invention is shown. Figure 2 Shown in the off state Figure 1 A schematic enlarged partial cross-sectional view of the braking device of the gas injector. Figure 3 A schematic enlarged partial cross-sectional view of the braking device of the gas injector in the open state is shown, and Figure 4 A schematic enlarged partial cross-sectional view of the braking device of a gas injector according to a second preferred embodiment of the present invention is shown. Detailed Implementation

[0022] The following is for reference. Figures 1 to 3 A gas injector 1 according to a first preferred embodiment of the present invention is described in detail.

[0023] As from Figure 1As can be seen, the gas injector 1 for introducing gaseous fuel includes an electromagnetic actuator 2, which moves the closing element 3 (in this embodiment, an outwardly opening valve needle) from a closed state to an open state. Figure 1 This shows the gas injector in the off state.

[0024] The electromagnetic actuator 2 includes an armature 20, which is attached to the closing element 3 by means of an armature pin 24. In addition, the electromagnetic actuator 2 includes an inner pole 21, a coil 22, and a magnetic housing 23, which ensures the magnetic reflux of the electromagnetic actuator.

[0025] Furthermore, the gas injector 1 includes a body 7 having a connecting pipe 70 through which gaseous fuel is supplied. Here, a valve housing 8 is fixed to the body 7, and an electromagnetic actuator 2 is arranged within the valve housing. A housing sleeve 19 and a valve pipe 90 are attached to the valve housing 8, and a sealing seat 11 is provided at the free end of the valve pipe, at which a shut-off element 3 releases and closes the passage for gaseous fuel.

[0026] exist Figure 1 The electrical connector 13 is schematically shown, which is guided through the body 7 to the electromagnetic actuator 2.

[0027] Reference numeral 10 indicates a reset element for closing element 3, so that the closing element can be reset again after the opening process. Figure 1 It is in the off state shown.

[0028] exist Figure 1 The diagram also shows the gas flow path 14 through the gas injector 1. Here, the gas flow begins at the connecting pipe 70 and is then redirected and guided into the annular chamber 80 between the valve housing 8 and the main body 7. Here, the gas flow 14 further passes from the outer region of the electromagnetic actuator 2 past the filter 15 until it reaches the sealing seat 11. Here, corresponding perforations are provided in the respective components, the perforations... Figure 1 Not all of them are shown.

[0029] When the gas injector 1 is opened, the gaseous fuel then flows onto the outer periphery of the electromagnetic actuator 2 and next to the opened sealing seat 11 into the combustion chamber of the internal combustion engine, which in Figure 1 It is indicated by arrow A.

[0030] Therefore, the shut-off element 3 releases and seals the gas path 14 at the sealing seat 11. For guidance, a first guide region 31 and a second guide region 32 are provided between the shut-off element 3 and the valve body 9, as from... Figure 1As can be seen in detail. The first guide region 31 is constructed directly between the closing element 3 and the valve body 9 near the sealing seat 11. The second guide region 32 is constructed between the spring plate 16 and the valve body 9. The spring plate 16 is fixedly connected to the closing element 3, wherein the reset element 10 is supported between the valve body 9 and the spring plate 16.

[0031] In addition, the gas injector 1 includes a closed lubricant chamber 4. The closed lubricant chamber 4 is completely or partially filled with a liquid lubricant, such as oil.

[0032] As from Figure 1 As can be seen, the lubricant chamber 4 is defined by a first flexible sealing element 51, an inner pole 21, a magnetic housing 23, a guide body 18, and a second flexible sealing element 52. The first and second flexible sealing elements 51 and 52 are respectively constructed as bellows. The first and second flexible sealing elements 51 and 52 are constructed identically here.

[0033] It should be noted that, instead of bellows, diaphragms or hoses can also be used as flexible sealing elements 51 and 52.

[0034] For example, further from Figure 1 As can be seen, the second flexible sealing element 52 is fixed to the reservoir spring plate 41, for example, by means of a welded connection. Furthermore, the gas injector 1 includes a reservoir pressure spring 40, which is supported on the body 7 and applies prestress to the second flexible sealing element 52 via the reservoir spring plate 41. A connection hole 18a is provided in the guide body 18 so that the lubricant in the lubricant chamber 4 is also located within the area of ​​the second flexible sealing element 52.

[0035] The first flexible sealing element 51 is directly fixed to the closing element 3 and connected to the valve body 9 at the other end. Here, a transverse hole 91 is provided in the valve body 9 so that there is a fluid connection between the inner chamber of the first flexible sealing element 51 and the inner chamber of the valve body 9.

[0036] Therefore, the lubricant chamber 4 has two flexible sealing elements 51 and 52 and a reservoir pressure spring 40. The reservoir pressure spring 40 applies a certain prestress, for example, 1 × 10⁻⁶. 5 A prestress of Pa is applied to the lubricant in the lubricant chamber 4. If lubricant is discharged during the opening process due to the stroke of the closing element 3 or also due to the thermal expansion or cooling of the lubricant, the overpressure / negative pressure that may be generated inside the lubricant chamber 4 can be compensated by the deflection at the second flexible sealing element 52 combined with the contraction of the reservoir pressure spring 40. Therefore, the flexible sealing element 51 can prevent undesirable forces acting on the closing element 3 via the bellows action surface.

[0037] An armature pin 24 is arranged in a closed lubricant chamber 4, and an armature 20 is fixed thereon. Because the lubrication chamber 4 is filled with a lubricant, such as liquid fuel, like gasoline or diesel or grease, continuous lubrication of the armature 20 is achieved. This compensates for the following problem that occurs in the prior art with gaseous fuel: lack of lubrication of moving parts.

[0038] As from Figure 1 As can be seen, a filling channel 17a is provided for filling the closed lubricant chamber 4. The filling channel 17a is fluid-tightly closed by means of a sealing ball 17.

[0039] A braking device 6 is also arranged in the enclosed lubricant chamber 4. The braking device 6 includes a brake pin 60, a damping chamber 62 filled with lubricant, and an elastic braking element 61 configured as a brake spring. The damping chamber 62 is in fluid contact with the lubricant chamber 4. Furthermore, the braking device 6 includes a guide disc 25 in which the armature pin 24 is guided. Here, the guide disc 25 has a plurality of through-holes 25a extending in the axial direction. Additionally, the braking device includes a brake pin valve 66.

[0040] When the brake pin valve 66 is in the open state, the armature pin 24 and the closing element 3 move together in the direction of arrow B, so that the armature pin is no longer in contact with the brake pin 60.

[0041] In the closed state of the brake pin valve 66, the first end face 60a of the brake pin 60 contacts the second end face 24a of the armature pin 24, with the first end face pointing toward the armature pin 24. Furthermore, a through hole 67 is constructed in the brake pin 60, which connects the first end face 60a to the damping chamber 62.

[0042] Figure 2 This indicates the off state of the gas injector. (See image below.) Figure 2 As can be seen in detail, a permanent connection exists between the damping chamber 62 and the lubricant chamber 4 via the throttling section 63. This permanent connection between the damping chamber 62 and the lubricant chamber 4 forms a first fluid path 101 through which lubricant can flow from the lubricant chamber 4 to the damping chamber 62, and vice versa. Figure 2 As shown, a first fluid path 101 extends through a guide body 18, in which a throttling section 63 is constructed. Here, the throttling section 63 opens into a connecting hole 18a in the guide body 18. The throttling section 63 can be constructed as a stepped straight hole and located on the central axis of the gas injector.

[0043] When the gas injector is in the open state, such as from Figure 3 As can be seen, a second fluid path 102 is generated via the opened brake pin valve 66.

[0044] exist Figure 3In the open state shown, the second end face 24a at the end of the armature pin 24 is raised from the first end face 60a via the armature path C. Because a plurality of radially extending channels 26 are provided in the guide plate 25, forming from a through-hole in the guide plate 25 to a surrounding recess 27 at the radially inner side of the guide surface for the armature pin 24, a second fluid path 102 is created when the gas injector is open. Figure 3 This is indicated by a dashed line. Thus, lubricant can flow through the channel 26 and the recess 27 into the through hole 67 and from there into the damping chamber 62. Here, the damping pin 60 is pressed against the guide plate 25 in the axial direction XX by the elastic braking element 61.

[0045] Therefore, with the gas injector open, two fluid paths 101 and 102 are provided to adequately supply lubricant to the damping chamber 62. This is particularly important because achieving the rapid reset of the closing element and thus the armature 20 and armature pin 24, given the very short opening time of the gas injector, requires sufficient damping. Such short injection times are achieved, for example, during internal combustion engine idling or during multiple injections.

[0046] Therefore, it can prevent the absence of damping via braking device 6 despite the short opening time of the gas injector. (As from...) Figure 3 It becomes clear that when the gas injector is opened, the armature pin 24 is lifted from the mating surface (Sitzfläche) at its brake pin 60. Therefore, the brake pin valve 66 is opened directly after this lifting, allowing lubricant to flow through the channel 26, the recess 27, and the through-hole 67 into the damping chamber 62. The flow of lubricant via the second fluid path 102 is also supported by the resilient braking element 61, which ensures that the brake pin 60 is pressed against the guide disc 25 in the axial direction and remains in this position. Here, the brake pin 60 is guided within the guide body 18.

[0047] In order to fill the damping chamber 62, flow is also generated via the first fluid path 101 through the always-open throttling section 63.

[0048] In this embodiment, a flat sealing seat is constructed between the first end face 60a of the brake pin 60 and the second end face 24a of the armature pin 24. However, it is also possible to provide a cone-ball fit sealing seat or a cone-cone fit sealing seat.

[0049] Furthermore, the damping process during gas injector closure is supported by the hydraulic adhesion of the brake spring 61 and brake pin 60 to the guide disc 25. Here, the damping chamber 62 prevents cavitation from occurring in the region between the guide disc 25 and the first end face 60a of the brake pin 60 during gas injector closure.

[0050] By selecting the diameter and / or length of the throttling section 63, the damping characteristics can be additionally and individually set for the corresponding gas injector.

[0051] Figure 1 The gas injector 1 shown here is pressure-balanced. That is, the shut-off element 3 is connected to the valve body 9 via a first flexible sealing element 51, wherein the first flexible sealing element 51, implemented as a metal bellows, has an average diameter equal to the following diameter on the sealing seat 11: the shut-off element 3 seals at the sealing seat 11 on this diameter. Thus, no pressure force is generated acting on the shut-off element 3, so the magnetic force required to open the shut-off element 3 can be kept very small and, in particular, independent of the pressure of the gaseous fuel.

[0052] Therefore, using the present invention, when the closing element 3 is placed in the open state by manipulating the electromagnetic actuator 2 (in... Figure 1 When the closing element 3 moves to the left and gas is blown in, reliable damping can be applied during the reset of the closing element 3 before it is pressed into the sealing seat 11. Therefore, the closing speed of the closing element 3 is significantly and effectively braked before it impacts the sealing seat 11. This effectively reduces wear at the sealing seat 11 and the closing element 3, and the braking device 6 also enables quieter operation of the gas injector. It also effectively prevents so-called "closing rebound," in which the element hard-impacts the valve seat and bounces back.

[0053] Therefore, the gas injector 1 can provide reduced wear on moving parts (especially on the seal 11, armature 20, and armature pin 24), and ensures sufficient damping even with a short stroke through the damping chamber 62, which is always fully filled via the two fluid paths 101, 102. Furthermore, the closed lubricant chamber 4 with liquid lubricant significantly improves heat conduction from the electromagnetic actuator 2. Additionally, the two flexible sealing elements 51, 52 prevent unwanted forces from acting on the closing element 3.

[0054] Figure 4 An enlarged partial cross-sectional view of the braking device of a gas injector according to a second preferred embodiment of the present invention is shown. Identical or functionally identical components are indicated by the same reference numerals as in the first embodiment.

[0055] Compared with the first embodiment Figure 2 Same, Figure 4The gas injector is shown in its closed state. Here, in the second embodiment, the first fluid path 101 is not configured as a throttling section in the guide body 18, but rather the fluid connection between the damping chamber 62 and the lubricant chamber 4 is configured between the brake pin 62 and the cylindrical receiving chamber for the brake pin 62 in the guide body 18. As in Figure 4 As shown, here, one or more grooves 60a are formed in the brake pin 60 on the circumferential surface region of the brake pin 60. Alternatively, the first fluid path 101 can also be defined by a gap between the brake pin 60 and the cylindrical region of the guide 18, in which the brake pin 60 is received. Further alternatively or additionally, one or more grooves may also be provided in the cylindrical region of the guide 18. Thus, throttling is achieved in the first fluid path in the region between the brake pin 60 and the cylindrical portion region of the guide 18. In other respects, this embodiment corresponds to the previous embodiment, and reference can be made thereto to the description given there.

Claims

1. A gas injector for blowing in gaseous fuel, comprising: - Electromagnetic actuator (2), which has an armature (20), an inner pole (21) and a coil (22). - A shut-off element (3) that releases and seals the gas path (14) at a sealing seat (11), wherein the armature (20) is operatively connected to the shut-off element (3). - A closed lubricant chamber (4), the lubricant chamber being filled with lubricant and the armature (20) being arranged in the lubricant chamber, wherein the lubricant ensures the lubrication of the armature (20), and - A braking device (6) arranged in the lubricant chamber (4), the braking device being configured to brake the closing element (3) during the reset process of the gas injector from the open state to the closed state. - The braking device (6) includes a brake pin (60), a damping chamber (62) filled with lubricant, an elastic braking element (61), an armature pin operatively connected to the armature, and a guide disc (25). The damping chamber is fluidly connected to the lubricant chamber (4) via a first fluid path (101). The brake pin (60) and the elastic braking element (61) can be brought into operative connection with the closing element (3) during the reset process. Furthermore, the brake pin (60) is configured during the reset process of the gas injector to transfer lubricant. The lubricant is discharged from the damping chamber (62) into the lubricant chamber (4) to dampen the reset of the closing element (3) to the closed state, and wherein the armature pin (24) is guided in the guide plate (25), and a brake pin valve (66) for releasing and closing the second fluid path (102) at the brake valve seat is provided between the lubricant chamber (4) and the damping chamber (62), wherein the brake pin valve (66) is configured to fill the damping chamber (62) with lubricant when the gas injector is in the open state.

2. The gas injector according to claim 1, wherein, A through hole (67) is constructed in the brake pin (60) to connect the first end face (60a) of the brake pin (60) to the damping chamber (62). The armature pin (24) has a second end face (24a). In the closed state of the gas injector, the first end face (60a) of the brake pin (60) abuts against the second end face (24a) of the armature pin (24), thereby closing the second fluid path (102) and preventing lubricant from flowing into the damping chamber (62) through the through hole (67).

3. The gas injector according to claim 1 or 2, wherein, The braking device (6) also has a throttling section (63) arranged in the first fluid path (101) between the damping chamber (62) and the lubricant chamber (4).

4. The gas injector according to claim 3, wherein, The throttling section (63) is configured to be open in both the open and closed states of the gas injector.

5. The gas injector according to claim 2, wherein, One or more channels are constructed in the side of the guide disc (25) pointing toward the brake pin (60), and / or, one or more channels are constructed in the first end face (60a) of the brake pin (60).

6. The gas injector according to claim 5, wherein, The channels are fluidly connected to each other through the surrounding recesses (27).

7. The gas injector according to claim 6, wherein, The recess (27) is constructed in the guide plate (25).

8. The gas injector according to any one of claims 1, 2, 4 to 7, wherein, The brake valve seat of the brake pin valve (66) is constructed as a flat sealing seat, a cone-ball fit seat, or a cone-cone fit seat.

9. The gas injector according to any one of claims 1, 2, 4 to 7, wherein, The elastic braking element (61) is arranged in the damping chamber (62).

10. The gas injector according to any one of claims 1, 2, 4 to 7, further comprising a guide (18) disposed in the lubricant chamber (4), the guide being configured to guide the brake pin (60).

11. The gas injector according to claim 4, wherein, The throttling section (63) is constructed as a stepped orifice.

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