Gas injector with very good damping performance during operation

Abstract

The invention relates to a gas injector for blowing in gaseous fuel, comprising: an electromagnetic actuator (2) having an armature (20), an inner pole (21) and a coil (22); a closing element (3) having a valve needle (30), the closing element (3) releasing and closing a gas path (14) on a sealing seat (11) arranged at a first end of the gas injector, the armature (20) being connected to the closing element (3); a closed lubricant chamber (4), which is filled with a lubricant and in which the armature (20) is arranged, the lubricant ensuring lubrication of the armature (20); and a restoring element (10) which resets the closing element (3) to a closed initial position, the lubricant chamber (4) having a first flexible sealing element (51) and a second flexible sealing element (52); an opening braking device (5) which reduces the load of the first flexible sealing element (51) and the second flexible sealing element (52) during opening; and a closing brake device (8) which reduces the load of the first flexible sealing element (51) and the second flexible sealing element (52) and of the sealing seat (11) during closing.

Description

Technical Field

[0001] The invention relates to a gas injector for injecting gaseous fuels, in particular hydrogen or natural gas, etc., which has a compact structure and very good damping properties during the opening and closing process of a closing element of the gas injector. The gas injector is particularly designed for direct injection into the combustion chamber of an internal combustion engine. Background Art

[0002] Gas injectors are known from the prior art in various configurations. One problem with gas injectors is that, due to the gaseous medium to be injected, lubrication cannot be achieved by this medium, as is the case with fuel injectors that inject gasoline or diesel. In order to enable the movability of the closing element, in particular the valve needle, it is known to use flexible sealing elements, such as bellows. As a result, during operation, vibration excitations may also occur due to the gaseous fuel, which may in particular have a negative impact on the actuation of the closing element during the opening or closing process. Summary of the invention

[0003] In contrast, the gas injector according to the invention for injecting gaseous fuels having the features of claim 1 has the advantage that vibration excitation of components of the gas injector can be suppressed both during the opening process and during the closing process.

[0004] As a result, a very precise compliance with the predetermined blowing amount, opening time point and closing time point is obtained when the gas injector is running. In particular, the excitation of the longitudinal vibration of the closing element can be prevented. Thus, damage to the flexible element in the gas injector, such as a metal bellows, which ensures the mobility of the closing element in the axial direction of the gas injector is avoided. According to the present invention, this is achieved by the following: the gas injector includes an electromagnetic actuator with an armature, an inner pole and a coil. In addition, the gas injector includes a closing element with a valve needle, which releases and closes the gas path for gaseous fuel at the sealing seat. The sealing seat is arranged on the first end of the gas injector, and the gas injector is preferably an injector that opens outward. Here, the armature is connected to the closing element. In addition, a closed lubricant chamber is provided, which is filled with lubricant, and the movable armature is arranged in the lubricant chamber. Here, the lubricant ensures the lubrication of the armature, so that no wear will occur on the armature during operation. Here, the lubricant chamber comprises at least one first flexible sealing element, in particular a bellows, which seals the lubricant chamber relative to the gas path and thus ensures the axial mobility of the closing element, and a second flexible sealing element which provides a compensation chamber for the lubricant chamber. In addition, the gas injector comprises a reset element, in particular a closing spring in the form of a cylindrical spring, wherein the reset element resets the closing element to a closed initial position. The gas injector also comprises an opening brake device, which reduces the load of the first flexible sealing element and the load of the second flexible sealing element during the opening process, and a closing brake device, which reduces the load of the first flexible sealing element and the load of the second flexible sealing element and the load of the sealing seat during the closing process.

[0005] The opening brake reduces the load on the valve assembly, in particular the load on the first flexible element arranged on the closing element. The opening brake also compensates for the fact that in gas injectors, compared with gasoline or diesel fuel injectors, the stroke of the closing element is very large, which tends to increase the vibration susceptibility of the components of the gas injector and leads to the opening stop surface between the armature and the inner pole. The present invention can significantly eliminate this.

[0006] Furthermore, during the closing process, the closing brake ensures that the load on the flexible sealing element remains low and that the closing element does not strike the sealing seat with excessive impact force, which could, on the one hand, lead to damage to the components and, on the other hand, could result in a so-called "bounce", in which the closing element is briefly lifted from the sealing seat again after completion of the closing process due to the impact force of the closing process, thereby briefly introducing additional unusable gas into the combustion chamber.

[0007] The dependent claims reveal preferred developments of the invention.

[0008] Further preferably, the gas injector comprises an armature column which is arranged in the lubricant chamber and / or is connected to the closing element. The opening brake and / or the closing brake are arranged on the armature column. This ensures a particularly compact design of the gas injector. By positioning the opening brake and / or the closing brake in the interior of the lubricant chamber, hydraulic damping can also be achieved during the opening and closing process.

[0009] Preferably, the opening brake device comprises a first piston, a first damping spring and a first damping chamber. Further preferably, the closing brake device comprises a second piston, a second damping spring and a second damping chamber. Further preferably, the opening brake device further comprises a stop ring, which is preferably arranged on the armature column and can firstly achieve damping in a delayed manner during the opening process. This ensures that during the opening process, damping only starts when the opening stroke is about to end.

[0010] In order to achieve a particularly compact design, the second piston is preferably arranged at least partially, preferably completely, in the first piston.

[0011] In order to achieve a more compact structure of the assembly, the armature pin preferably extends through the first piston and the second piston. Thus, the first piston and the second piston of the two brake devices are designed in an annular shape.

[0012] Further preferably, the first piston has a shoulder on the inner periphery, which serves as a stop for the second piston. This further enhances the integration of the first piston and the second piston into each other, thereby further reducing the installation space and structure of the gas injector.

[0013] Further preferably, the second piston is arranged with play on the armature column, thereby achieving a rapid onset of the damping effect, in particular during the closing process.

[0014] Preferably, the spring force of the first damping spring of the opening brake device is greater than the spring force of the second damping spring of the closing brake device. The spring force of the first damping spring is preferably at least twice the spring force of the second damping spring. Thus, it can be additionally ensured that damping only begins at the end of the entire opening stroke during the opening process.

[0015] Further preferably, the armature column has a shoulder, on which the second piston of the closing brake device is arranged. In order to provide as small a diameter of the lubricant chamber as possible, the armature preferably has a through-opening for the lubricant.

[0016] Further preferably, the armature column is guided in the guide plate. Preferably, the guide plate is also used to support the first damping spring of the opening brake device.

[0017] It is further preferred that the guide disk has an axially protruding annular shoulder which preferably protrudes at least partially into the armature which has a corresponding recess.

[0018] The first damping spring is preferably arranged between the guide plate and the first piston.The second damping spring is preferably arranged between a reservoir body arranged in the lubricant chamber and the second piston.

[0019] The first flexible element and the second flexible element are preferably bellows, in particular metal bellows. Here, preferably, the first diameter of the first flexible element is smaller than the second diameter of the second flexible element.

[0020] Further preferably, the gas injector comprises a first needle guide, a second needle guide and a third needle guide, which guide the valve needle during the opening process and the closing process. Here, the first needle guide and the second needle guide are arranged in the gas path, and the third needle guide is arranged in the lubricant chamber. The reset element is also arranged in the lubricant chamber. Therefore, the movement of the reset element and the third needle guide lubricated by the lubricant of the lubricant chamber does not produce wear or at most produces minimal, negligible wear. Therefore, the first needle guide and the second needle guide arranged in the gas path are located outside the lubricant chamber. If a tilting moment is applied to the valve needle by the reset element during operation, the tilting moment can be reliably received by the two needle guides arranged in the gas path, i.e., the first needle guide and the second needle guide. Thus, the valve needle bending that may be generated due to the tilting moment that may occur is prohibited by the two needle guides, i.e., the first needle guide and the second needle guide. Thus, under all operating conditions, the sealing seat remains closed, or the tilting of the valve needle on the sealing seat can be prevented and thus an insufficient closing process can be prevented. The valve needle is therefore reliably guided by the dual guidance outside the lubricant chamber and by the guidance in the lubricant chamber.

[0021] Preferably, a first distance A1 between the first needle guide and the second needle guide in the axial direction XX of the gas injector is smaller than a second distance A2 between the second needle guide and the third needle guide in the axial direction XX. As a result, tilting moments that may occur are particularly well received by the first needle guide and the second needle guide. The second distance A2 is preferably at least twice, more preferably at least three times, the first distance A1.

[0022] It is further preferred that the first needle guide and / or the second needle guide and / or the third needle guide each have an annular guide area, which is connected to the valve needle of the closing element via a bridge portion (Steg), so that there is a through-hole for fluid circulation between the bridge portions. This is particularly advantageous at the first needle guide and the second needle guide, which are arranged in the gas guide area of ​​the gas injector so that the largest possible amount of gas can flow through the first guide area and the second guide area when the gas injector is opened. Here, the annular guide area is preferably closed along the entire periphery. In order to keep the friction as small as possible during the opening and closing processes of the closing element, the width of the annular guide area is selected to be as small as possible. Here, it is particularly preferred that three bridge portions are provided, which connect the valve needle to the annular guide area. These bridge portions are preferably arranged at the same distance along the periphery.

[0023] According to a particularly preferred embodiment of the invention, the bridge between the valve needle and the annular guide area is arranged at an acute angle to the annular guide area. As a result, the flow cross section in the area of ​​these guides can be increased, which is particularly advantageous in the case of a first needle guide and a second needle guide located in the gas guide area. Preferably, the bridge is arranged behind the guide area in the flow direction through the through-portion. Alternatively, the bridge between the valve needle and the annular guide area of ​​the needle guide is arranged at a right angle to the valve needle.

[0024] According to a particularly preferred embodiment of the present invention, a disk is further arranged on the valve needle, on which the first flexible sealing element is fixed. This enables a simple connection between the closing element and the first flexible sealing element that seals the lubricant chamber.

[0025] Preferably, the first needle guide and the second needle guide are guided on the same component. The component is preferably a cylindrical valve body, on which the sealing seat is also arranged. It is thus possible to produce the guide surfaces for the first needle guide and the second needle guide in one machining operation, which offers great advantages in terms of machining technology and also reduces manufacturing costs.

[0026] In order to further reduce the number of components, preferably, the third needle guide is also provided with a reset element for supporting the lubricant chamber. Here, the third needle guide can preferably be configured as a disk with a through-portion for lubricant during the opening process and closing process of the closing element.

[0027] Preferably, the closing element with the three needle guides is designed as a one-piece component. This makes it possible to avoid weld seams and the like, which are often sources of contamination during operation of the gas injector and which can lead to sealing problems at the sealing seat and the like. A multi-piece closing element made of individual elements welded to one another is also preferred for reducing the cutting volume and for saving manufacturing costs.

[0028] The first flexible sealing element and / or the second flexible sealing element is preferably a metal bellows. The metal bellows, on the one hand, provides very good mobility in order to enable an axial movement of the closing element, and on the other hand, the metal bellows can thereby be arranged as close as possible to the hot combustion chamber of the internal combustion engine. As a result, the axial length of the gas injector can be further reduced. Alternatively, the first flexible sealing element is a plastic bellows or a diaphragm or a rubber element.

[0029] In order to further reduce the axial length of the gas injector, the electrical attachment portion of the gas injector and / or the gas inlet of the gas injector are preferably arranged at the side of the gas injector.

[0030] It is further preferred that the gas injector has a conical sealing seat. In this case, the closing element preferably comprises a sealing disk at the end pointing toward the combustion chamber, which releases one or more through-openings at the sealing seat. In this case, the gas injector is preferably designed as an injector that opens outwards. This makes it possible to provide a sealing seat that blows the gas into the combustion chamber in the form of a hollow cone.

[0031] Preferably, oil, in particular synthetic oil or mineral oil, is used as lubricant. Alternatively, liquid fuel, in particular diesel or gasoline, is used. Further alternatively, grease is used as lubricant. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. The accompanying drawings show:

[0033] Figure 1 A schematic cross-sectional view showing a gas injector according to a first embodiment of the present invention, and

[0034] Figure 2 A schematic partial cross-sectional view of a gas injector is shown. DETAILED DESCRIPTION

[0035] Below, refer to Figure 1 and Figure 2 A gas injector 1 according to a first preferred embodiment of the present invention will be described in detail.

[0036] like Figure 1 As shown, a gas injector 1 for introducing gaseous fuel comprises an electromagnetic actuator 2, which moves an outwardly opening closing element 3 from a closed state to an open state. Figure 1 The closed state of the gas injector is shown.

[0037] The electromagnetic actuator 2 comprises an armature 20 which is connected to the closing element 3 by means of an armature pin 24. Furthermore, the electromagnetic actuator 2 comprises an inner pole 21, a coil 22 and a magnet housing 23 which ensures a magnetic circuit of the electromagnetic actuator.

[0038] Furthermore, the gas injector 1 comprises a body 7 having a gas inlet 70 through which gaseous fuel is supplied. The gas inlet 70 is arranged in the axial direction XX on the body 7. The body 7 is connected to a valve housing 8 in which the electromagnetic actuator 2 is arranged.

[0039] Attached to the valve housing 8 is a housing sleeve 19 , at the free end of which a sealing seat 11 is arranged on a valve seat component 93 , on which the closing element 3 releases and closes a passage for the gaseous fuel.

[0040] exist Figure 1 Schematically shown in FIG. 1 is an electric attachment portion 13 , which extends through the main body 7 up to the electromagnetic actuator 2 . The electric attachment portion 13 is arranged on a side of the main body 7 .

[0041] Reference numeral 10 denotes a reset element for the closing element 3 in order to reset the closing element to the position after the opening process. Figure 1 The closed state is shown in .

[0042] exist Figure 1 1 also shows a gas flow as a gas path 14 through the gas injector 1. Here, the gas flow starts at the gas inlet 70, is then reversed and guided through the body 7. Here, the gas flow 14 continues from the outer area of ​​the electromagnetic actuator 2 through the filter 15 until it reaches the sealing seat 11. In this case, corresponding openings are provided in the individual components, which are not all in Figure 1 Shown in.

[0043] When the gas injector 1 is opened, the gaseous fuel flows past the outer periphery of the electromagnetic actuator 2 and past the opened sealing seat 11 into the combustion chamber 100 of the internal combustion engine. Figure 1 This is indicated by arrow A.

[0044] The closing element 3 comprises a valve needle 30 with a seat disc 30a, which is arranged on the end of the closing element directed toward the combustion chamber. Here, the sealing seat 11 is configured between the seat disc 30a and the valve seat component 93, which is basically a cylindrical tube.

[0045] The closing element 3 further comprises a first needle guide 31 , a second needle guide 32 and a third needle guide 33. The two needle guides 31 , 32 are preferably constructed in one piece with the valve needle 30.

[0046] Furthermore, the gas injector 1 comprises a closed lubricant chamber 4. The closed lubricant chamber 4 is completely or partially filled with a liquid lubricant, for example oil.

[0047] like Figure 1 As shown, the lubricant chamber 4 is defined by a first flexible sealing element 51, an inner pole 21, a sleeve 18, a storage body 17 and a second flexible sealing element 52. The first and second flexible sealing elements 51, 52 are each configured as a metal bellows.

[0048] The closing element 3 also comprises a disc 34 on which the first flexible sealing element 51 is supported.

[0049] A plurality of connecting holes 77 are formed in the storage body 17, which connect the inner area of ​​the second flexible sealing element 52 with other areas of the lubricant chamber 4. Figure 1 As shown, the second flexible sealing element 52 has a relatively large diameter, which is greater than the diameter of the first flexible sealing element 51. Furthermore, a storage compression spring 40 supported on the body 7 is provided.

[0050] In this case, the second flexible sealing element 52 serves as a compensation chamber for the lubricant located in the lubricant chamber 4 . Pressure fluctuations in the lubricant chamber 4 can thereby be compensated.

[0051] The first flexible sealing element 51 is also fixed directly to the disk 34 at the closing element 3 and is connected at the other end to the guide sleeve 35. The third needle guide 33 is guided in the guide sleeve 35.

[0052] Therefore, the lubricant chamber 4 has two flexible sealing elements 51, 52 and a storage compression spring 40. The storage compression spring 40 applies a certain preload pressure, for example 1x10 5 If a displacement of lubricant now occurs during the opening process due to the stroke of the closing element 3 or also due to thermal expansion or cooling of the lubricant, any overpressure / negative pressure that may occur in the interior of the lubricant chamber 4 can be compensated by the deflection at the second flexible sealing element 52 in combination with the contraction of the storage compression spring 40. The first flexible sealing element 51 is therefore unable to exert undesired forces on the closing element 3 via the bellows active surface.

[0053] An armature column 24 having an armature 20 fixed thereon is also arranged in the sealed lubricant chamber 4. Since the lubricant chamber 4 is filled with a lubricant, for example, a liquid fuel such as gasoline or diesel, or grease, etc., there is continuous lubrication of the armature 20. This compensates for the following problem that occurs in the prior art when using gaseous fuels: lack of lubrication of moving parts.

[0054] The gas injector 1 further comprises an opening brake device 5 and a closing brake device 6, wherein the opening brake device reduces the load on the first and second flexible sealing elements 51, 52 and the armature stop during the opening process, and the closing brake device reduces the load on the first and second flexible sealing elements 51, 52 and the sealing seat 11 during the closing process.

[0055] More precisely, the opening brake device 5 comprises a first piston 53 , a first damping spring 54 , a first damping chamber 55 and a stop ring 56 which is arranged at the free end of the armature pin 24 facing away from the sealing seat 11 .

[0056] The closing brake device 6 comprises a second piston 63 , a second damping spring 64 and a second damping chamber 65 .

[0057] Especially from Figure 2 As can be seen in FIG. 4 , the opening brake device 5 and the closing brake device 6 are arranged in a central recess in the storage body 17 . Therefore, in the lubricant chamber 4 , the opening brake device 5 and the closing brake device 6 are arranged on the side of the armature 20 facing away from the sealing seat 11 .

[0058] If Figure 2 It can be seen that the first damping spring 54 is supported between the fixed guide disk 9 and the first piston 53 in the sleeve 18, which connects the inner pole 21 and the storage body 17 to each other. In this case, the first damping spring 54 is arranged in a first damping chamber 55. Lubricant is also present in the first damping chamber 55, because Figure 2 As shown, the armature pin 24 is guided in the guide disk 9 and the lubricant passes through this guide gap into the damping chamber 55 .

[0059] The guide disk 9 has a shoulder 91 which protrudes in the axial direction in the direction of the sealing seat 11. In this case, a correspondingly designed recess 20a is provided in the armature 20, so that the volume of lubricant in this region of the gas injector is reduced.

[0060] The closing brake device 6 is arranged on the end of the armature pin 24 facing away from the sealing seat 11. In this case, the second damping spring 64 is arranged in the second damping chamber 65. In this case, the second damping spring 64 is arranged between the storage body 17 and the second piston 63.

[0061] like Figure 2As further described, the second piston 63 is partially arranged in the first piston 64. Here, a shoulder 25 is provided on the armature column 24, which serves as a stop for the second piston 63. Figure 2 In the figure, the maximum stroke of the armature 20 is indicated by the reference symbol H1 as the first gap H1, which is equal to the maximum opening distance of the closing element 3. A second gap H2 is provided between the stop ring 56 and the second piston 63. In the closed position, a third gap H3 is provided between the second piston 63 and the first piston 53.

[0062] Here, the gas injector 1 functions as follows. Figure 1 and Figure 2 Starting from the closed position shown in FIG. , the coil 22 is energized, whereby the armature 20 is moved in the direction of the arrow B (see FIG. Figure 2 ) is pulled toward the inner pole 21. Since the armature 20 is firmly connected to the armature pin, the armature pin 24 also moves in the direction of the arrow B, whereby the closing element 3 is lifted from the sealing seat 11 and the blowing begins.

[0063] like Figure 2 As shown, after passing through the second gap H2, contact is established between the stop ring 56 and the second piston 63, so that the second piston 63 also moves in the direction of arrow B when the power is continued. This movement of the second piston 63 is also supported by the second damping spring 64. When the power is continued, the second piston 63 moves in the direction of arrow B, so that the third gap H3 between the second piston 63 and the first piston 53 is passed. Then, the opening brake device 5 is activated. Here, the first piston 53 continues to move in the direction of arrow B against the spring force of the first damping spring 54. Here, the lubricant must also be squeezed out of the first damping chamber 55, thereby achieving braking and damping of the opening process.

[0064] Here, the lubricant from the first damping chamber 55 flows into the second damping chamber 65 via the gap between the first piston 53 and the armature column 24 and the gap between the second piston 63 and the armature column 24, and flows into the second damping chamber 65 via the gap between the first damping piston 53 and the storage body 17 and the gap between the first damping piston 53 and the second damping piston 63. There is also flow via the gap between the armature column 24 and the guide plate 9. It should be noted that the first piston 53 and the second piston 63 are arranged on the armature column 24 with a gap here.

[0065] As soon as the blowing is to be ended, the energization of the electromagnetic actuator is terminated so that the closing element 2 and thus the armature pin 24 are moved again toward the position in which the closing element 2 is located by the reset element 10. Figure 1 and Figure 2. Since the second piston 63 abuts against the shoulder 25 on the armature column 24, the second piston 63 also moves in the direction of the arrow C during resetting. Here, the second piston 63 must move against the spring force of the second damping spring 64, and the lubricant must flow back from the second damping chamber to the first damping chamber 53 via the gap between the first piston, the second piston and the armature column 24. Damping is thus achieved during the closing process.

[0066] It should be noted that during the closing process, a damping effect is only produced when the first piston 53 abuts against the shoulder 17a of the storage body 17. Then, the second piston 63 of the closing brake device 6 is lifted from the shoulder 25 on the armature pin 24 and increases the pressure in the second damping chamber 65 to cause damping during the closing process.

[0067] The return speed of the two pistons is increased due to the gap between the two pistons and the armature pin 24. It should be noted that instead of the gap between these pistons and the armature pin 24, corresponding holes can also be constructed in the first piston and the second piston, which is, however, more complicated in terms of manufacturing technology than providing a gap with the armature pin 24.

[0068] Here, the spring force for resetting the first piston 53 is preferably twice the spring force for resetting the second piston 63. Therefore, the gas injector according to the invention can prevent the excitation of longitudinal vibrations of the first flexible sealing element 51 (first bellows) and the second flexible sealing element 52 (second bellows) both during the opening process and during the closing process. Since such longitudinal vibrations increase the number of deflections of the bellows, the service life of the flexible sealing elements can be significantly increased by the invention. The closing brake device 6 also prevents the closing element 3 from hitting the sealing seat 11 too strongly during the closing process. Therefore, the wear of the closing element and / or the sealing seat is reduced when closing the gas injector.

[0069] Here, in Figure 1 The gas injector 1 shown in FIG. 1 is compensated in terms of the pressure force. That is, the closing element 3 is connected to the guide sleeve 35 via a first flexible sealing element 51, wherein the first flexible seal 51, which is implemented as a metal bellows, has an average diameter that is equal to the diameter of the sealing seat 11 on which the closing element 3 is sealed. As a result, no pressure force acts on the closing element 3, so that the magnetic force required to open the closing element 3 can be kept very small and is in particular independent of the pressure of the gaseous fuel.

Claims

1. A gas injector for blowing gaseous fuel, the gas injector comprising: - an electromagnetic actuator (2) having an armature (20), an inner pole (21) and a coil (22); a closing element (3) having a valve needle (30), wherein the closing element (3) releases and closes the gas path (14) at a sealing seat (11) arranged at a first end of the gas injector, wherein the armature (20) is connected to the closing element (3); a closed lubricant chamber (4), which is filled with lubricant and in which the armature (20) is arranged, wherein the lubricant ensures lubrication of the armature (20); and - a reset element (10) which resets the closing element (3) to a closed initial position, wherein the lubricant chamber (4) has a first flexible sealing element (51) and a second flexible sealing element (52), wherein the first flexible sealing element (51) is arranged on the closing element (3) and seals the lubricant chamber (4) relative to the gas path (14), and the second flexible sealing element (52) is arranged on a region of the gas injector opposite to the sealing seat (11); - an opening brake device (5) which reduces the load on the first flexible sealing element (51) and the second flexible sealing element (52) during the opening process; and A closing brake (8) which reduces the load on the first flexible sealing element (51) and the second flexible sealing element (52) as well as the sealing seat (11) during the closing process.

2. The gas injector according to claim 1, further comprising an armature pin (24), which is arranged in the lubricant chamber (4) and connected to the closing element (3), wherein: The opening brake device (5) and / or the closing brake device (6) are arranged on the armature pin (24).

3. The gas injector according to claim 2, -in, The opening brake device comprises a first piston (53), a first damping spring (54), a first damping chamber (55), and a stop ring (56) on the armature column (24), and - wherein said The closing brake device (6) has a second piston (63), a second damping spring (64) and a second damping chamber (65).

4. The gas injector according to claim 3, wherein: The second piston (63) is at least partially arranged in the first piston (53).

5. The gas injector according to claim 3 or 4, wherein: The armature pin (24) extends through the first piston (53) and the second piston (63).

6. The gas injector according to claim 4 or 5, wherein: The first piston (53) has a shoulder on the inner circumference, which serves as a stop for the second piston (63).

7. The gas injector according to any one of claims 3 to 6, wherein: The first piston (53) and / or the second piston (63) are arranged with play on the armature pin (24).

8. The gas injector according to any one of claims 3 to 7, wherein: The spring force of the first damping spring (54) is greater than the spring force of the second damping spring (64).

9. The gas injector according to any one of claims 3 to 8, wherein: The armature pin (24) has a shoulder (25) which serves as a stop for the opening brake device (5).

10. The gas injector according to any one of claims 3 to 9, further comprising a guide disk (9), wherein: The armature pin (24) is guided in the guide disk (9).

11. The gas injector according to claim 10, wherein: The first damping spring (54) is arranged between the guide plate (9) and the first piston (63), and wherein the second damping spring (64) is arranged between the storage body (17) and the second piston (63).

12. The gas injector according to any one of the preceding claims, further comprising: a first needle guide (31), a second needle guide (32) and a third needle guide (33) arranged to guide the valve needle (30), - wherein the first needle guide (31) and the second needle guide (32) are arranged in the gas path (14), and the third needle guide (33) is arranged in the lubricant chamber (4).

13. The gas injector according to claim 12, wherein: A first distance (A1) between the first needle guide (31) and the second needle guide (32) in the axial direction (XX) is smaller than a second distance (A2) between the second needle guide (32) and the third needle guide (33) in the axial direction (XX).

14. The gas injector according to claim 12 or 13, wherein: The first needle guide (31) and / or the second needle guide (32) and / or the third needle guide (33) each have an annular guide area, which is connected to the valve needle (30) via a bridge portion so that a passage is present for fluid flow between the bridge portions.

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