CN112145778A

CN112145778A - Electromagnetically actuated high-pressure gas valve

Info

Publication number: CN112145778A
Application number: CN202010604779.3A
Authority: CN
Inventors: P·布劳恩; R·温德尔; S·雷克
Original assignee: Mesa Parts GmbH
Current assignee: Mesa Parts GmbH
Priority date: 2019-06-27
Filing date: 2020-06-28
Publication date: 2020-12-29
Anticipated expiration: 2040-06-28
Also published as: CN112145778B

Abstract

The invention relates to an electromagnetically actuated high-pressure gas valve, comprising: a pilot valve seat having (a pilot opening connecting the high pressure side of the high pressure gas valve to the low pressure side and being closable by the pilot sealing element; the pilot armature is provided with a pilot armature, which is mounted movably along the longitudinal axis of the high-pressure gas valve and co-acts with the pilot sealing element and is biased in the closing direction by a first compression spring; a main valve seat is arranged on the main valve seat, it has a main opening connecting the high pressure side of the high pressure gas valve to the low pressure side and being closable by a main sealing element; the main armature is provided with a main armature, which is mounted movably along the longitudinal axis of the high-pressure gas valve and interacts with the main sealing element and is biased in the closing direction by a second compression spring; wherein a transmission device is arranged in the device, the transmission is activated when the pilot armature is moved against the closing direction, and in the activated state the pilot armature carries the main armature against the closing direction.

Description

Electromagnetically actuated high-pressure gas valve

Technical Field

The invention relates to an electromagnetically actuated high-pressure gas valve.

Background

Electromagnetically actuated high-pressure gas valves are known from the prior art, which are designed as pilot valves. This kind of high-pressure pneumatic valve includes: a pilot valve seat having a pilot opening that connects a high pressure side of the high pressure gas valve to a low pressure side and that can be closed by a pilot sealing element; and a pilot armature, which is mounted movably along the longitudinal axis of the high-pressure gas valve and acts on the pilot sealing element, and which is biased in the closing direction by a first compression spring. Furthermore, such a high-pressure gas valve has a main valve seat with a main opening which connects the high-pressure side of the high-pressure gas valve to the low-pressure side and which can be closed by a main sealing element; and a main armature, which is movably mounted along the longitudinal axis of the high-pressure gas valve and acts on the main sealing element. Depending on the application, the primary sealing element may be biased in the closing direction by a second compression spring.

For a high pressure gas valve, a pressure difference of up to +1500bar may exist between the high pressure side and the low pressure side. The pressure differential presses the pilot armature and the main armature into the respective valve seats. In order to open a high-pressure gas valve which is not designed as a pilot valve, the primary sealing element must be moved against a hydraulic or pneumatic fluid force which acts on the primary sealing element and/or on a primary armature interacting with the primary sealing element as a result of the pressure difference. If the primary sealing element is biased by a second compression spring, the primary sealing element must also move against the force of the second compression spring when opening.

The opening force necessary for opening is exerted by a magnetic field provided by a coil. Therefore, the coil must be designed to be correspondingly large, thereby increasing the total space occupied by the high pressure gas valve.

In order to open the high-pressure gas valve with the small-sized coil and thus to be able to reduce the space required, the high-pressure gas valve is designed as a pilot valve. As mentioned at the outset, the pilot valve comprises, in addition to the main armature, a pilot armature which is connected to the pilot sealing element and which, after the coil has been activated, lifts off from the pilot valve seat against the spring force of a first compression spring for closing the pilot sealing element. The pilot opening is of a much smaller cross-sectional area than the main control opening. The pilot sealing element is only opened to such an extent that pressure compensation can take place in the valve. Thus, the main armature only needs to move against the optional second compression spring to move the main sealing element and open the main valve seat, and does not need to overcome the hydraulic or pneumatic force exerted by the pressure difference, as these pressures are almost gone after opening the pilot valve seat and the pressures are substantially balanced. The required opening force is correspondingly smaller so that the solenoid coil can be dimensioned smaller or operated with a smaller ampere-turns. The ampere-turns represent the number of turns multiplied by the current flowing through the turns.

Such high-pressure gas valves are known from WO 1996/15926 a1, DE 102008064409 a1, DE 1168725A, EP 2947361 a1, CN 202215826U, EP 2653763 a2 and US 3405906 a. In the high-pressure gas valves according to us 3405906 and CN 202215826U, the pilot sealing element and the main sealing element are moved by a common armature, whereas in the high-pressure gas valves in WO 1996/15926 a1, EP 2947361 a1 and DE 1168725 a, the pilot sealing element is moved with the pilot armature and the main sealing element is moved with the main armature.

Disadvantageously, in the high-pressure gas valve disclosed in said document, the pilot armature is in the core position during the pressure compensation, i.e. it is located in the core of the high-pressure gas valve. This creates a magnetic short circuit, which means that the available magnetic force acting on the main armature to overcome the residual pressure difference and to overcome the spring force of the second compression spring (if present) to open the main sealing element is small.

The high-pressure gas valve shown in EP 2947361 a1 has a core with which the pilot armature forms a first gap having a first gap height in relation to the longitudinal axis of the high-pressure valve, and with which the main armature forms a second gap having a second gap height in relation to said longitudinal axis. As described above, the magnetic field provided by the coil applies the opening force required to open the main and pilot valve seats of the high pressure gas valve. The magnetic field passes through the core, then through the first gap to the pilot armature, and through the second gap to the main armature. As the height of the gap increases, the opening force acting on the pilot armature and the main armature decreases. The maximum distance between the pilot armature and the core and the maximum first gap height can be chosen to be relatively small, since the pressure compensation requires only a small pilot stroke. The maximum first clearance height generally corresponds to the pilot stroke. Therefore, even at the maximum first gap height, a large opening force acts on the armature.

The maximum second clearance height is the clearance height at which the primary sealing element closes the primary valve seat. In practice, the height of the second gap between the main armature and the core may be chosen as small as possible in order to allow a large opening force to act on the main armature. However, due to the high pressure difference and the resulting high pressure loss in the narrow region, a throttling effect may occur in the high-pressure gas valve, which reduces the temperature in the high-pressure gas valve and adversely affects the function, in particular the sealing function of the elastomer. In addition, the minimum second clearance height may be limited by the minimum mass flow rate that the high pressure gas valve is required to flow through.

As described above, the pilot valve seat is opened to open the high pressure gas valve for pressure compensation in the high pressure gas valve. However, the pressure compensation after opening the pilot valve seat is a process that requires a certain time. Thus, the hydraulic or pneumatic force acting on the main sealing element due to the pressure difference does not suddenly disappear, but decreases over a certain time. If the opening force provided by the magnetic field and acting on the main armature (hereinafter also referred to as magnetic force) is greater than the hydraulic or pneumatic force and the spring force exerted on the main armature by the optional second pressure spring, the main armature starts to move against the closing direction. At the beginning of the movement, the pressure compensation does not have to be done, so that a certain pressure difference still exists. In the high-pressure gas valve shown in EP 2947361 a1, the pressure difference when the main armature starts to move against the closing direction is about 2.5 to 3 bar.

It is not a disadvantage to prepare the opening process of the main valve seat before the pressure compensation is completely finished. In contrast, an opening process which is started before the pressure compensation is completely ended leads to a reduction in the switching time, since there is no need to wait until the pressure compensation is completely ended. Basically, the shorter the switching time, the greater the pressure difference at which the main armature starts to move against the closing direction. Shorter switching times may, for example, improve the regulation of certain command variables or compensate for pressure fluctuations within the tank system.

Disclosure of Invention

It is an object of an exemplary embodiment of the present invention to provide an electromagnetically actuated high-pressure gas valve with which, in a simple and inexpensive manner, in a sufficient opening stroke and with maximum probability, on the main sealing element due to the pressure difference existing in the hydraulic or pneumatic force acting in the closing direction, a sufficiently high electromagnetic force can be provided for opening the main armature, the switching time of the high-pressure gas valve is shortened, and the stability against pressure fluctuations in the tank system is increased.

This object is achieved by the features of claim 1. Advantageous embodiments are the subject of the dependent claims.

Embodiments of the present invention relate to an electromagnetically actuated high pressure gas valve comprising:

a pilot valve seat having a pilot opening, which connects the high pressure side of the high pressure gas valve to the low pressure side, and which can be closed by a pilot sealing element,

a pilot armature mounted movably along the longitudinal axis of the high-pressure gas valve, which pilot armature interacts with a pilot sealing element, which is biased in the closing direction by a first pressure spring,

a main valve seat having a main opening connecting the high pressure side of the high pressure gas valve to the low pressure side and being closable by a main sealing element,

a main armature movably mounted along a longitudinal axis of the high pressure gas valve, interacting with the main sealing element; and

the magnet coil, the main armature and/or the pilot armature can be displaced along a longitudinal axis, wherein

A transmission is provided which is activated when the pilot armature is moved counter to the closing direction and by means of which the main armature is driven counter to the closing direction in the activated state of the pilot armature, so that the magnetic force acting on the pilot armature contributes to the opening of the main armature.

As already mentioned, in the case of the pilot valve also comprising the present high-pressure gas valve, the pilot sealing element is first opened in order to achieve pressure compensation in the high-pressure gas valve. To this end, the coil is energized, thereby generating a magnetic field that provides the opening force. The pilot armature is thus moved counter to the closing direction and against the action of the first compression spring. By means of said transmission, the pilot armature operates together with the main armature such that the main armature also moves against the closing direction. Thus, the opening force acting on the pilot armature can also be used to open the main armature. In addition, the transmission enlarges the magnetic active surface. A part of the active magnetic surface is just before the core position and therefore in a position where pneumatic or hydraulic forces acting on the primary sealing element due to the existing pressure difference have to be overcome. Therefore, a very large magnetic force acts on the main armature. Due to the use of the transmission, the main armature moves even at higher pressure differences, which may be up to 7bar, for example, than with the high pressure gas valves known from the prior art, in particular from EP 2947361 a 1. Thus, the high pressure gas valve switches earlier than the high pressure gas valves known in the prior art. According to the above-described aspect, it is possible to provide a sufficiently large stroke of the main armature and, at the same time, maximize the opening force acting on the main armature.

In order to prevent the pressure difference from impeding the movement of the pilot armature and the main armature and to prevent the high-pressure gas valve from remaining closed, the transmission is designed such that it can only be activated after the pressure compensation has started. Thus, prior to activation of the transmission, relative movement between the pilot armature and the main armature may occur in order to lift the pilot sealing element from the pilot valve seat and the pilot opening to create pressure compensation.

According to another embodiment, the high pressure gas valve comprises a core, the pilot armature forms a first gap with the core, the first gap has a first gap height associated with the longitudinal axis, the main armature forms a second gap with the core, the second gap has a second gap height associated with said longitudinal axis, and the transmission is activated when said first gap height reaches a selectable limit. The gap height represents the distance between the pilot armature or the main armature and the core.

In order to enable the pilot valve seat to open and pressure compensation to be achieved in the high-pressure gas valve, it must be ensured that the pilot armature can move sufficiently far against the closing direction and towards the core. The limit value is selected such that the main armature can be moved counter to the closing direction even at relatively high pressure differences, so that the high-pressure gas valve according to the invention switches on more quickly than known high-pressure gas valves.

In a further improved embodiment, the limit value of the first gap height can be between 0.3mm and 1.5mm, in particular between 0.4mm and 1.4 mm. It has been found that the opening force acting on the pilot armature required in the proposed high-pressure gas valve ensures a reliable and rapid opening of the high-pressure gas valve at such a first gap height.

In a further improved embodiment, the transmission device can be configured as a positive locking device. The positive locking means can be provided at a relatively small design cost and has a high degree of reliability.

In another embodiment, the positive locking means:

as a projection arranged on the leading armature and a recess arranged on the main armature, or

A groove designed to be arranged on the pilot armature and a protrusion arranged on the main armature, wherein

When the pilot armature moves, the protrusion and the groove contact each other, thereby activating the transmission.

The projections and recesses can be easily manufactured so that the manufacturing costs for providing the proposed high-pressure gas valve can be kept low.

A further developed embodiment is characterized in that the projection is designed as a washer or pin. In this embodiment, standardized washers or pins may be used to provide the protrusions, so that the associated costs may be kept low.

In another embodiment, the primary seal element is biased in the closing direction by a second compression spring. Thus, in this embodiment, the pilot armature is biased by a first compression spring, while the main armature is biased by a second compression spring. The two compression springs can be designed with different "strengths". Due to the separation into two separate springs, the pilot armature only has to work against the first compression spring acting on the pilot armature when opening it. The first compression spring can advantageously be designed "softer" compared to an embodiment of the high-pressure gas valve with only one compression spring.

A further developed embodiment is characterized in that the pilot armature is arranged at least partially within the main armature and concentric with the main armature. In this embodiment, the arrangement of both the main armature and the pilot armature is considered to be connected in parallel. Due to this arrangement the space required in the high pressure gas valve is kept small. In addition, this arrangement provides the possibility of individually adjusting the first and second gap heights in terms of stroke and required magnetic force for opening the pilot and main valve seats. Furthermore, only by this parallel arrangement it is possible to enlarge the surface acting towards the core to open the primary sealing element when the transmission is engaged. Alternatively, the pilot armature and the main armature may be arranged in series.

Drawings

Exemplary embodiments of the present invention are explained in more detail below with reference to the accompanying drawings. The following figures are based on cross-sectional views, in which

Figure 1 shows an electromagnetic high-pressure gas valve known in the prior art,

figure 2 shows a first embodiment of a high pressure gas valve according to the invention in a closed position,

fig. 3 shows the high pressure gas valve according to the invention shown in fig. 2, wherein the pilot valve seat is in an open state,

figure 4 shows the high pressure gas valve according to the invention of figure 2 in an open position,

figure 5 shows a second embodiment of a high-pressure gas valve according to the invention in the closed position,

fig. 6 shows the high pressure gas valve according to the invention shown in fig. 5, wherein the pilot valve seat is in an open state,

figure 7 shows the high pressure gas valve according to the invention of figure 5 in an open position,

FIG. 8 shows a third embodiment of a high pressure gas valve according to the invention with the pilot valve seat in an open state, and

fig. 9 shows a fourth embodiment of the high pressure gas valve according to the invention with the pilot valve seat in an open state.

Detailed Description

Fig. 1 shows a cross-sectional view of a high-pressure gas valve 10, which can be electromagnetically actuated, as can be known, for example, from EP 2947361 a 1. The high pressure gas valve 10 comprises a pilot valve seat 12 with a pilot opening 14 connecting the high pressure side H of the high pressure gas valve 10 to the low pressure side N. The pilot opening 14 can be closed by a pilot sealing element 16. Furthermore, high-pressure gas valve 10 comprises a pilot armature 18, which pilot armature 18 is mounted movably along a longitudinal axis L of high-pressure gas valve 10 and interacts with pilot sealing element 16 by means of a form fit. The pilot sealing element 16 is biased in the closing direction S by a first compression spring 20, so that the pilot sealing element 16 is pressed into the pilot valve seat 12 and closes the pilot opening 14. The form fit between the pilot sealing element 16 and the pilot armature 18 is designed such that the pilot sealing element 16 entrains (mitnehmen) the pilot armature 18 in the closing direction S. Thus, the pilot armature 18 is indirectly biased by at least the first compression spring 20. Relative movement between the pilot sealing element 16 and the pilot armature 18 in the closing direction and in the opposite direction is possible.

Furthermore, the high-pressure gas valve 10 is equipped with a main valve seat 22 having a main opening 24, the main opening 22 connecting the high-pressure side H of the high-pressure gas valve 10 with the low-pressure side N. The primary opening 24 may be closed by a primary sealing element 26. Furthermore, the high-pressure gas valve 10 has a main armature 28, which main armature 28 is mounted movably along the longitudinal axis L of the high-pressure gas valve 10 and is biased in the closing direction S by a second compression spring 30. The main armature 28 presses against the main sealing element 26, thereby closing the main opening 24. The main armature 28 is tubular and surrounds the pilot armature 18, which is arranged concentrically with the main armature 28. Thus, the main armature 28 also serves as a bearing for the pilot armature 18. Main armature 28 and pilot armature 18 may move relative to each other and independently of each other. The primary seal element 26 is connected to the primary armature 28, for example by crimping.

The main armature 28 has a through-opening 32 extending perpendicularly to the longitudinal axis, through which a pressure compensation can be produced between the space enclosed by the main armature 28 and the surroundings of the main armature 28. It should be noted here that a plurality of through holes 32 may also be provided. The through-holes 32 may be omitted entirely if the gap size between the main armature 28 and the adjacent component is large enough.

Furthermore, the high-pressure gas valve 10 comprises an excitation coil 34, with which a magnetic field can be generated. The coil 34 is annular and surrounds a core 35, through which core 35 the magnetic field can be directed onto the main armature 28 and the pilot armature 18.

The high pressure gas valve 10 is designed as a "normally closed" valve. Thus, when the coil 34 is not energized, the main opening 24 and the pilot opening 14 are closed. This state is shown in fig. 1. In this state, a gap having a first gap height h is formed between the core 35 and the pilot armature 18₁And a second gap height h is formed between the core 35 and the main armature 28₂And a second gap 38. Therefore, the magnetic field must overcome the first gap 36 and the second gap 38 in order to be able to act on the pilot armature 18 or the main armature 28.

The high pressure gas valve 10 operates as follows: in the embodiment shown, the pilot opening 14 and the main opening 24 are closed. It is assumed that the inlet pressure on the high pressure side H is significantly higher than the outlet pressure on the low pressure side N. The inlet pressure reaches the interior of the high pressure gas valve 10 through the inlet 40 and through the through bore 32. The inlet pressure exerts a hydraulic or pneumatic force on the main sealing element 26 and the main armature 28, which acts in the closing direction S, thereby pressing the main sealing element 26 into the main seat 22 together with the closing force of the second compression spring 30.

To open high pressure gas valve 10, coil 34 is energized, which causes pilot armature 18 to move first toward core 35 and thus against closing direction S until pilot armature 18 rests against core 35. The pilot opening 14 is opened so that pressure compensation takes place between the high pressure side H and the low pressure side N. Due to the progressive pressure compensation, the hydraulic or pneumatic forces acting on the main sealing element 26 and the main armature 28 are reduced over time. If the pressure difference drops below a certain value (in the high-pressure gas valve 10 shown in fig. 1 between approximately 2.5bar and 3 bar), the opening force exerted by the magnetic field on the main armature 28 causes the main armature 28 to move against the closing direction S. However, it is a prerequisite that the opening force is greater than the force exerted by the second compression spring 30 on the main pivot 28 in the closing direction S, which is also the hydraulic pressure or the hydraulic force acting in the closing direction S due to the pressure difference.

As described above, during pressure compensation, the pilot armature 18 abuts against the core 35. In this position, the reluctance between the pilot armature 18 and the core 35 is lower than the reluctance between the core and the main armature 28. The magnetic lines of force preferably extend over the pilot armature 8 and do not serve to move the main armature 28 towards the core 35. Furthermore, a higher pilot stroke than is necessary for generating the pressure compensation is performed in the high-pressure gas valve 10 shown in fig. 1. The space required for high pressure gas valve 10 is correspondingly large.

Fig. 2 to 5 show a high-pressure gas valve 41 according to the invention in a sectional view₁The first embodiment of (1). In fig. 2, a high pressure gas valve 41₁In the closed position, the pilot valve seat is open in fig. 3, and the high pressure gas valve 41 is open in fig. 4₁In the open position.

The basic structure largely corresponds to the high-pressure gas valve 10 shown in fig. 1. In this regard, only the differences are discussed below.

According to the invention, a high-pressure gas valve 41₁Comprising a transmission 42, which transmission 42 acts between the first armature 18 and the main armature 28. In the embodiment shown, the transmission 42 is designed as a positive locking device 44.

The high pressure gas valve 41 according to the invention shown in fig. 2 to 4₁In the first embodiment of (a), the positive locking means 44 is designed as a projection 48 arranged on the pilot armature 18, which projection 48 is formed by a pin 52, which pin 52 is fixedly connected to the pilot armature 18 and projects radially outwards from the pilot armature 18And (6) discharging. The pin 52 engages in an elongated hole 54 of the main armature 28. After a first movement of the pilot armature 18 counter to the closing direction S, the pin 52 abuts against the end of the elongate hole 54 which is directed toward the core 35, thereby activating the transmission 42. As can be seen from fig. 3, when the first conducting armature 18 has been moved sufficiently far in the direction of the core 35 against the closing direction S, the pin 52 of the pilot armature 18 abuts against the end of the elongate hole 54 of the main armature 28 which is directed towards the core 35, so that the pilot opening 14 is open and pressure compensation is possible. It can also be seen from fig. 3 that when the pin 52 abuts against the end of the elongated hole 54 directed toward the core 35, the pilot armature 18 does not yet abut against the core 35. This avoids a magnetic short circuit between the first conductive armature 18 and the core 35. Thus, compared to the high-pressure gas valve 10 according to the prior art shown in fig. 1, the magnetically active surface for opening the main valve seat 22 is increased, so that a greater magnetic force is present for lifting the main sealing element 26, which overcomes the spring force and the pneumatic or hydraulic force acting on the main armature 28 due to the pressure difference that is present.

A comparison of fig. 2 and 4 shows the following: if the coil 34 is energized, the pilot armature 18 is first moved toward the core 35. First gap height h of first gap 36₁Decreases while the second gap height h of the second gap 38₂Remain the same.

The first gap height h will be referred to hereinafter₁Is called the limit value, at which the pin 52 strikes the end of the elongated hole 54 directed towards the core 35, thereby activating the transmission 42. In FIG. 4, the first gap height h₁The limit value has been reached. The limit value may be, for example, between 0.3mm and 0.8mm, for example 0.4 mm. It should be noted that the transmission 42 is designed such that when the first gap height h is reached₁When decreasing, i.e. when the first armature 18 is moved against the closing direction S towards the core 35, activation takes place. After the actuation of the transmission 42, i.e. in this case when the limit value is reached, the pilot armature 18 and the main armature 28 move together. This motion will be referred to as a second motion.

The magnetic surface acting on the main armature 28 is thus enlarged and contributes completely to overcoming the fully acting spring force and the maximum possible pressure difference and the hydraulic pressure acting therebyA pneumatic force. First gap height h₁And a second gap height h₂And decreases. At the high-pressure gas valve 41₁The pilot armature 18 and the main armature 28 are dimensioned such that they strike the core 35 simultaneously, and therefore, as shown in fig. 4, the first gap height h₁And a second gap height h₂Are all zero (see figure 4). The main valve seat 22 is now fully open. It can also be seen from fig. 4 that the pilot valve seat 12 is also opened. The above-described functional principle is used when the pilot opening 14 must continue to open in the open state. However, an increased pilot stroke is required, which is higher than the stroke required for opening such a pilot opening 14.

In fig. 5 to 7, a high-pressure gas valve 41 according to the invention is shown₂The second embodiment of (1). In fig. 5, the high pressure gas valve 41₂In the closed position, in fig. 6 the pilot valve seat 12 is open, in fig. 7 the high pressure gas valve 41₂In the open position. High pressure gas valve 41 according to the second exemplary embodiment₂Corresponds largely to the high-pressure gas valve 41 according to the first exemplary embodiment₁. In the high pressure gas valve 41 according to the second exemplary embodiment₂The main sealing element 26 is biased in the closing direction S by the second compression spring 30, whereas for the high-pressure gas valve 41 according to the first exemplary embodiment₁This is not the case. The main sealing element 26 is connected to the main armature 28 in the same way as the high-pressure gas valve 10 according to the prior art shown in fig. 1. The second compression spring 30 acts on the main armature 28 and thus indirectly on the main sealing element 26.

Comparing fig. 2 and 5, it is found that the high pressure gas valve 41₂First gap height h in the second exemplary embodiment of (1)₁In the closed position, is higher than the high pressure gas valve 41₁First gap height h in the first exemplary embodiment of (1)₁Is small. In a second exemplary embodiment, the first gap height h₁Is selected so that on the one hand it is as small as possible, but on the other hand it is sufficient to lift the pilot sealing element 16 from the pilot valve seat 12 to produce pressure compensation.

Thus, the first gap height h₁Is also low, at which the pin 52 strikes the end of the elongate hole 54 directed towards the core 35, as can be seen more clearly in fig. 3 and 6.

As mentioned above, the closing force that has to be overcome to open the pilot sealing element 16 results from the sum of the hydraulic or pneumatic force acting on the pilot sealing element 16 due to the pressure difference and the spring force exerted on the main sealing element 26 by the first compression spring 20. The closing force that must be overcome to open the primary sealing element 26 results from the sum of the hydraulic or pneumatic force acting on the primary sealing element 26 due to the pressure difference and the spring force applied to the primary sealing element 26 by the second compression spring 30.

As can be seen from a comparison of fig. 5 and 6, the pilot armature 18 can be moved with the pilot sealing element 16 a certain distance towards the core 35 and thus against the closing direction S. This distance can be overcome without difficulty. If the pilot armature 18 has traveled this distance along with the pilot seal 16, the closing force acting on the pilot seal 16 must be overcome in order to lift the pilot seal 16 from the pilot valve seat 12 and the pilot opening 14.

It can also be seen from a comparison of fig. 5 and 6 that the pilot opening 14 is already open when the transmission 42 enters the start-up state. As can be seen from fig. 3, this is also the case in the first embodiment of the high pressure gas valve 101. However, here, in the second exemplary embodiment of the high pressure gas valve 102, the first clearance height h₁Is smaller than the first gap height in the first exemplary embodiment, but is not equal to zero. Due to the small gap height h compared to the first exemplary embodiment₁The opening force applied to pilot armature 18 by the magnetic field is significantly higher. Nevertheless, there is a residual stroke which is used to move the main armature 28 against the closing direction S.

In the high pressure gas valve 41 according to the second exemplary embodiment₂Middle first gap height h₁And the limit value is selected such that the pilot armature 18 has hit the core 35 (first gap height h) while the main armature 28 is still arranged spaced apart from the core 35₁0), second gap height h₂And thus greater than zero. From the figure7, it can be seen that when the main armature 28 also strikes the core 35, the pin 52 no longer abuts the end of the elongate hole 54 directed toward the core 35. Therefore, the transmission 42 is deactivated, so that the main armature 28 is moved between the position where the pilot armature 18 abuts the core 35 and the position where the main armature 28 abuts the core 35 only by the opening force acting on the main armature 28, thereby moving the main sealing element 26 against the closing direction S to open the high-pressure gas element.

Here, a smaller gap height h₁Helping to overcome the hydraulic or pneumatic force acting due to the existing pressure differential, which then no longer acts on the main armature 28. Therefore, only the elastic force of the second compression spring 30 has to be overcome. As the primary sealing element 26 moves against the closing direction S, the primary sealing element 26 is in contact with the pilot sealing element 16. From this point on, the spring force of the first compression spring 20 must also be overcome. However, since the elastic force of the first compression spring 20 and the elastic force of the second compression spring 30 are both smaller than the hydraulic or pneumatic force, both the elastic forces can be easily overcome by the opening force acting on the main armature. In this state, the pilot armature 18 is already in the core position. This results in a significant reduction of the stroke and thus in a significant increase of the magnetic force. Alternatively, the installation space can be significantly reduced.

Figure 8 shows a high pressure gas valve 41 according to the invention₃In which the pilot valve seat 12 is open. In the third exemplary embodiment, the positive locking device 44 is designed as a groove 46 arranged on the pilot armature 18 and as a projection 48 arranged on the main armature 28.

In fig. 9, a high-pressure gas valve 41 according to the invention is shown₄In the fourth embodiment, the projection 48 of the main armature 28 is formed by a washer 50 fixed thereto, which abuts against the already existing high-pressure gas valve 41 when the limit value is reached₃The groove 46 of the pilot armature 18 mentioned in the third exemplary embodiment.

May be connected to the high pressure gas valve 41 according to the first or second exemplary embodiment₁、41₂The high-pressure gas valve 41 according to the third and fourth exemplary embodiments is designed and operated in exactly the same manner₃、41₄。

List of reference numerals

10 high-pressure gas valve according to the prior art

12 pilot valve seat

14 pilot opening

16 pilot seal element

18 pilot armature

20 first compression spring

22 main valve seat

24 main opening

26 primary seal element

28 Main armature

30 second compression spring

32 through hole

34 coil

35 core part

36 first gap

38 second gap

40 inlet

41 high-pressure air valve

41₁-41₄High-pressure gas valve

42 transmission device

44 positive locking device

46 groove

48 projection

50 shim

52 pin

54 elongated hole

H high pressure side

L longitudinal axis

N low pressure side

S closing direction

h₁First gap height

h₂A second gap height.

Claims

1. An electromagnetically actuated high pressure gas valve (41) comprising:

-a pilot valve seat (12) having a pilot opening (14), the pilot opening (14) connecting a high pressure side (H) of the high pressure gas valve (41) to a low pressure side (N) and being closable by a pilot sealing element (16),

-a pilot armature (18) movably mounted along a longitudinal axis (L) of the high pressure gas valve (41) and interacting with a pilot sealing element (16) biased in a closing direction (S) by a first compression spring (20),

-a main valve seat (22) having a main opening (24), the main opening (24) connecting a high pressure side (H) of a high pressure gas valve (41) to a low pressure side (N) and being closable by a main sealing element (26),

-a main armature (28) mounted movably along the longitudinal axis (L) of the high-pressure gas valve (41) and interacting with the main sealing element (26); and

-a field coil (34) by means of which the main armature (28) and/or the pilot armature (18) can be moved along the longitudinal axis (L), wherein

-a transmission (42) is provided which is activated when the pilot armature (18) is moved against the closing direction (S) and in the activated state the pilot armature (18) entrains the main armature (28) against the closing direction (S) such that the magnetic force acting on the pilot armature (18) contributes to opening the main armature (28).

2. Electromagnetically actuated high-pressure gas valve (41) according to claim 1,

it is characterized in that the preparation method is characterized in that,

-the high pressure gas valve (41) comprises a core (35),

o the pilot armature (18) forming a first gap (36, 38) with the core having a first gap height (h) in relation to the longitudinal axis (L)₁) And is and

o the main armature (28) forming with the core a second gap (36, 38) having a second gap height (h) related to the longitudinal axis (L)₂) And is and

-when the first gap height (h) is reached₁) When a selectable limit value is reached, the transmission (42) is activated.

3. Electromagnetically actuated high-pressure gas valve (41) according to claim 2,

characterized in that said first gap height (h)₁) Is between 0.3mm and 0.8mm, in particular between 0.4mm and 0.7 mm.

4. Electromagnetically actuated high-pressure gas valve (41) according to any one of claims 1 to 3,

characterized in that the transmission device (42) is configured as a positive locking device (44).

5. Electromagnetically actuated high-pressure gas valve (41) according to claim 4,

characterized in that said positive locking means (44)

-a protrusion (48) configured to be arranged on the pilot armature (18) and a groove (46) arranged on the main armature, or

-a groove (46) configured to be arranged on the pilot armature (18) and a protrusion (48) arranged on the main armature, wherein

-when the pilot armature (18) moves, the protrusion (48) and the recess (46) abut each other, thereby activating the transmission (42).

6. Electromagnetically actuated high-pressure gas valve (41) according to claim 5,

characterized in that the projection (48) is designed as a washer (50) or as a pin (52).

7. Electromagnetically actuated high-pressure gas valve (41) according to any of the preceding claims,

characterized in that the primary sealing element (26) is biased in the closing direction (S) by a second compression spring (30).

8. Electromagnetically actuated high-pressure gas valve (41) according to any of the preceding claims,

characterized in that the pilot armature (18) is arranged at least partially inside the main armature (28) and concentric with the main armature.