EP2126425A1

EP2126425A1 - Closure device for a pressure reservoir of a gas-refrigeration generator, which can be filled with a compressed gas

Info

Publication number: EP2126425A1
Application number: EP08701032A
Authority: EP
Inventors: Martin Häge; Helmut Grantz; Gunnar Helms
Original assignee: Mbb International Group AG
Current assignee: Mbb International Group AG
Priority date: 2007-01-17
Filing date: 2008-01-09
Publication date: 2009-12-02
Also published as: EA200900990A1; EA015162B1; US20100012877A1; CN101583815A; CA2673338A1; JP2010516954A; DE102007003321A1; KR20090111330A; WO2008086963A1

Abstract

The invention relates to a closure device for a pressure reservoir (14) of a gas-refrigeration generator (11), which pressure reservoir can be filled with a compressed gas. The valve body (21) is arranged so as to be displaceable inside a valve box (18). The valve body (21) has an effective compressive surface facing the main chamber (15) and an effective compressive surface facing the prechamber (52), both surfaces having identical size and being impingeable with the filling pressure of the main chamber (15). The valve body (21) is retained in a closed position by an outer effective compressive surface (64) which is subject to an atmospheric pressure in the direction of closure and by an energy storing element (47).

Description

Applicant: MBB International Group AG

Gersauerstrasse 78, CH-6440 Brunnen

Closure device for a pressurized gas-filled pressure vessel of a cold gas generator

The invention relates to a closure device for a pressurized gas-filled pressure vessel of a cold gas generator according to the preamble of claim 1.

US Pat. No. 6,068,288 discloses a closure device for a pressurized gas-filled pressure vessel of a cold gas generator. Such cold gas generators are used in particular for vehicle airbag systems. The closure device comprises a valve body which closes a container opening communicating with the environment in a rest position. For the outflow of the compressed gas, an electromagnetic drive device is provided, through which the valve body can be transferred to a drive position. The valve body is designed as a slide. By a displacement movement different flow paths are released to allow outflow of the compressed gas. This device has the disadvantage that high forces for controlling the slide are required. In addition, these increased forces make it difficult to control such. By such a closure device, the required short opening times can not be realized.

The invention is therefore an object of the invention to provide a closure device for a filled with compressed gas pressure vessel of a cold gas generator, which allows a precisely controllable and fast opening movement of a cold gas generator, so that a fast and metered delivery of high-pressure gas under pressure and a safe closing is made possible after the delivery of the compressed gas.

This object is achieved by the features of the main claim. Further advantageous embodiments and further developments are specified in the further claims.

According to the invention, the closure device has a valve body which is displaceably arranged in a valve housing and which is movable within an antechamber of the valve housing, the valve body having an effective pressure surface facing the main chamber and an effective pressure surface facing the prechamber, which are the same size or approximately the same size and an outer effective pressure surface on which acts an atmospheric pressure in the opening direction, and has a further outer effective pressure surface acts on the atmospheric pressure in the closing direction, wherein additionally acts on a force storage element on the valve body, which acts in the closing direction. To achieve a self-holding closed position of the valve body is thus provided that the outer acting in the opening direction, acted upon by atmospheric pressure surface is smaller than the outer, acting in the closing direction, acted upon by atmospheric pressure surface and the closing force of the force storage element is formed. Such a configuration makes it possible to directly control the opening and closing movement of the valve body. pers is allowed to flow out of the compressed gas. In addition, this arrangement has the advantage that a floating bearing of the valve body is provided in the valve housing, in which a pointing to the main chamber effective pressure surface and an antechamber facing effective pressure surface are equal or approximately equal in size, so that a balance of power or almost an equilibrium of forces is given and the high internal pressure of the container with respect to the forces acting on the valve body in the antechamber forces quasi quits. It is thereby achieved that the resulting closing force of the valve body is reduced to the pressure force which results from the atmospheric pressure on the pressure surfaces acting in the opening and closing direction and the closing force of the force storage element. Thus, to control an opening movement significantly reduced forces compared to the actual container internal pressure suffice to control the valve body. This results in a fast and accurate control both in the opening and in the closing direction. This also allows short timings, so that not only a single outflow, but a multiple outflow of the compressed gas is made possible from the filled pressure vessel. This embodiment according to the invention also has the advantage that pressure tolerances due to changing operating temperatures have no influence on the control and reaction times of the closure device. This is due to the fact that the filling pressure of the pressure vessel also rests in the antechamber of the valve housing and the respective effective pressure surfaces are equal or approximately equal, so that a pressure equalization occurs, regardless of the absolute pressure prevailing in the pressure vessel.

According to an advantageous embodiment of the invention it is provided that the first effective pressure surface on the valve body to the main. chamber has, by a seal, in particular seat seal, and the second effective pressure surface on the valve body, which faces the prechamber, by a seal, in particular seat seal, limited, wherein a diameter of an inner circumference of the seal at the first effective, facing the main chamber Pressure area equal to a diameter of an outer circumference of the seal at the Ren effective effective for Vorkammer facing pressure surface of the valve body is provided. As a result, it can be achieved structurally in a simple manner that the pressure surfaces provided on the valve body and pointing toward the main chamber and also the prechamber can be exactly determined, so that the desired closing force is determined exactly and essentially by atmospheric pressure.

According to a preferred embodiment of the invention, it is provided that for forming the first and second effective pressure surface on the valve body, an at least two-part valve body is formed. As a result, the geometric requirements for the design of the effective pressure surfaces can be realized in a simple manner.

Between the at least two-part valve body formed a seal is provided, which is designed as a permanent seal. This makes it possible that one or more interfaces of the two- or multi-part valve body are sealed against the environment, so that a filling pressure can not escape.

The valve housing is preferably also formed in two parts. Thereby, a simple assembly can be made possible together with the valve body. Preferably, the interface of the two-part valve housing is sealed by a permanent seal. The same applies to a multipart valve housing. As a result, a secure seal to the antechamber of the valve housing can be ensured.

Furthermore, it is preferably provided that the valve body has one or more through holes extending in the displacement direction, which connect the main chamber and pre-chamber, wherein preferably a large central through-hole is provided. In particular, a large central through bore is a simple structural design to form a two-piece valve body and to allow faster compensation of the pressures between the main and prechambers. According to a further preferred embodiment of the invention, it is provided that the input and / or output of the central through-hole in the valve body have a rounded or trumpet-shaped profile. As a result, favorable flow conditions can be achieved, which also lead to the reduction of friction and thus to no delay in the opening and closing movement of the valve body.

Furthermore, it is preferably provided that the valve body has a diameter-reduced region in which a radially inwardly directed annular collar of the valve housing engages. It can thereby be achieved that the effective pressure surface facing the prechamber can be made relatively large on the valve body and adapted to the effective pressure surface facing the main chamber, so that a large container opening of the pressure container is made possible. Furthermore, this makes it possible that a force storage element is received in this undercut, which is supported on the one hand on the radially inwardly directed annular collar of the valve housing and opposite to a radially outwardly extending annular collar of the valve body and acts in the closing direction.

According to a further preferred embodiment, provision is made for the drive device to be provided adjacent to the pre-chamber and for an armature to be actuated by an actuator. By this arrangement, a structure can be made possible which is easy to install and enables a compact arrangement.

Preferably, a seal is provided between the housing of the drive device and the valve housing for producing a permanently sealed closure between the prechamber and the surroundings.

To Ansteueruπg the valve body is preferably provided that the armature is designed as an annular disc and in particular is permanently attached to the valve body. This can be done for example by a positive and / or positive connection. Furthermore, cohesive connections, such as adhesive bonds, welding bonds or the like may be provided. Furthermore, a Veπtilkörperabschnitt may be integrally formed with the armature.

The drive device preferably has a housing with a receiving space into which the actuator can be inserted, wherein a sealing plate is provided, which seals the receiving space of the actuator to the prechamber. This makes it possible that the actuator is not located in the high pressure area, but is arranged separately from the prechamber.

Furthermore, it is preferably provided that this sealing plate is designed as a stop for the damped opening movement of the valve body. Thereby, the vibration generation during the opening and closing movement of the valve body can be reduced.

According to a further preferred embodiment of the invention it is provided that a container opening closing, radially outwardly facing annular collar of the valve body on a radial outer circumferential surface has a non-sealing damping ring which engages the valve housing. This damping ring allows for improved guidance and damping of the vibration system.

To improve the Ausströmbedingungen the compressed gas is preferably provided that in the container opening of the pressure vessel, a rotationally symmetrical guide surface is arranged, which has a directed into the container interior pipe section which widens in the flow direction at the opposite end. This makes it possible that a deflection of the outflowing compressed gas is favored in the radially arranged outlet openings and the flow field is already homogenized early. As a result, defined flow conditions can be achieved.

According to a further preferred embodiment of the invention, it is provided that a rotationally symmetrical guide surface is provided on a region of the valve body facing the main chamber, which is aligned for the deflection of the outflowing compressed gas. These The rotationally symmetric guide surface preferably has an analogous course to the rotationally symmetric guide surface arranged in the container opening of the pressure vessel in order to calm the flow field and to achieve a favored outflow. This rotationally symmetrical guide surface on the valve body also has the advantage that when there is a flow around this guide surface, a buoyancy force for the valve body is formed, which counteracts a possible closing force due to dynamic pressure changes. This can be used to support fast opening. This rotationally symmetrical guide surface is preferably trumpet-shaped.

According to a further alternative embodiment of the invention it is provided that on a lower side of the valve body with a central through-bore a pressure-compensating supportive element is provided, which extends at least in a closed position of the valve body in a pressure and / or flow-calmed region of the pressure vessel. This arrangement has the advantage that a rapid pressure equalization between the main chamber and the prechamber is made possible during the outflow of the compressed gas and the turbulence resulting in the outflow region does not or only slightly affect the pressure equalization between the main chamber and the prechamber.

It is preferably provided that the pressure compensation element extending into the interior of the pressure vessel has a preferably cylindrical pipe section which is preferably smaller in diameter than the fastening section which can be inserted into the diameters of the central throughbore. This makes it possible, on the one hand, to provide a simple connection of the pipe section to the valve body and, on the other hand, to reduce the moving mass. In addition, this embodiment has the advantage that the pipe section in a transition region to the valve body has a widening portion, which allows a flow-favored deflection. As a result, a rotationally symmetrical guide surface for homogenizing the flow field is again achieved by the outer surface of the element. According to a further preferred embodiment of the invention it is provided that the pipe section has an intermediate portion adjacent to the widened region, which is inserted into the central through-bore of the valve body. Preferably, a press-fitting or a cohesive connection for the secure arrangement and receiving the pressure compensation element supporting the valve body.

According to a further preferred embodiment of the invention, it is provided that the guide surfaces provided in the pressure vessel, which determine the flow field of the outflowing compressed gas, have a rough surface. This makes it possible to provide a stall directly on the sliding surfaces and thus a flow profile with a high mass flow rate is possible.

According to a further preferred embodiment of the invention, provision is made for a drive device to be provided in a region of the valve body facing the container opening of the pressure vessel, which can be actuated to actuate a closing movement of the valve body. This allows a separate and adapted control of the valve body for an opening and closing movement.

Preferably, this drive device has a control chamber in which a closing body or a control element, in particular a sleeve, is inserted. This additional control element can accelerate the closing movement of the valve body in that the control essentially closes the outflow cross section and the pressure forces acting in the opening direction are considerably reduced by the outflowing compressed gas. For this purpose, it is provided that first the control element is actuated by the drive device in order to reduce the acting pressure force. Subsequently, a rapid subsequent closing of the valve body is achieved.

It is preferably provided that this control element is designed as a sleeve, which is provided in a control chamber of the valve body, which adjoins a container opening of the pressure vessel and long of the longitudinal axis of the valve body is movable. As a result, the opening cross section of the outlet opening can be reduced and thus a pressure reduction can be achieved. Due to this changed pressure situation results in an immediate closing movement of the valve body.

Furthermore, it is preferably provided that the control is arranged with radial play in the control chamber of the valve body. This allows a simple and fast control possible.

The invention and further advantageous embodiments and developments thereof are described in more detail below with reference to the examples shown in the drawings and explained. The features to be taken from the description and the drawings can be applied individually according to the invention individually or in combination in any combination. Show it:

Figure 1 is a schematic sectional view of a

Cold gas generator with a first embodiment of the closure device in a closed position,

FIG. 2 shows a schematic sectional illustration of the embodiment according to FIG. 1 in a working position,

Figure 3 is a schematic sectional view of a

Cold gas generator with a further embodiment of the closure device in a closed position,

FIG. 4 shows a schematic sectional representation of the embodiment according to FIG. 3 in a working position, FIG. 5 shows a schematic sectional illustration of an alternative embodiment according to FIG. 3 in a closed position,

FIG. 6 shows a schematic sectional view of the embodiment according to FIG. 5 in a working position,

FIGS. 7a to e show schematic sectional views of a further alternative embodiment of a closure device according to FIG. 1.

1 shows a schematic sectional view of a cold gas generator 11 with a first embodiment of a closure device 12, which is provided on a pressure vessel 14. The pressure vessel 14 has a container opening 16 at the upper end. In this container opening 16, a valve housing 18 is inserted, which is formed in two parts according to the embodiment. The valve housing 18 may also be multi-part. A lower portion 19 of the valve housing 18 engages the container opening 16 and protrudes into an interior of the pressure vessel 14, which forms a main chamber 15, and extends in an opposite direction outside of the pressure vessel 14. The valve housing 18 receives a valve body 21 and a Antriebsvorrich- 22 on which form the closing device 12 together with the valve housing.

On an outer periphery of the pressure vessel 14, a pressure bag 24 is attached, which is only partially shown in FIG, but is provided in all pressure vessels 14. As soon as a signal is detected by a controller not shown, which triggers the use of a pressure bag 24, the valve body 21 is transferred from a closed position shown in Figure 1 by the drive device 22 in a working position of the open position shown in Figure 2, so that in the pressure vessel 14 located pressure gas can flow through the radially aligned outlet openings 26 in the valve housing 18 in the pressure bag 24. At a lower portion 19 of the valve housing 18, a valve seat 28 is provided, on which a valve seat surface 29 of the valve body 21 rests in a closed position. In this valve seat surface 29, a seal 31 is provided, which rests on the valve seat 28 and an outlet region 32 between the container opening 16 and the outlet openings 26 closes.

The valve body 21 is preferably formed in two parts and has a first valve body portion 34 and a second valve body portion 35 which are fastened to each other. Preferably, a screw connection is provided for easy installation. Further alternative embodiments for the permanent and fixed connection of the two valve body sections 34, 35 are also possible. In a separation point between the first valve body portion 34 and the second valve body portion 35, a seal 36 is preferably provided, which ensures a permanent tightness of the separation point. The first valve body portion 34 is formed sleeve-shaped with a radially outwardly directed Rbngbund 38, at its pointing to the container opening 16 axial end face, the valve seat surface 29 is formed. Through the sleeve-shaped configuration of the first valve body portion 34, a central through-hole 39 is provided, which also extends along the second valve body portion 35.

The second valve body portion 35 is also formed sleeve-shaped and has a container opening 16 directed to the second valve seat surface 41, which bears against a valve seat 42 of an upper portion 20 of the valve housing 18. In this valve seat surface 41 of the valve body 21, a seal 43 is provided, which is preferably the same as the seal 31 is formed. In particular, a seat seal can be provided for this purpose.

Between the lower and upper portions 19, 20 of the valve housing 18, an undercut region or a taper 46 is formed, in which a Kraftspeicherelemeπt 47 is arranged. Such a force storage element 47 may be a coil spring, plate spring or the like. Likewise, other types of energy storage elements be used. The force storage element 47 engages on one side on an outer pressure surface 48, which is the valve seat surface 29 opposite to the Riπgbund 38 of the valve body 21 is provided. Opposite the force storage element 47 engages a Rflächengfläche 51 of a radially inwardly facing annular collar 50, which is formed at the upper portion 20 of the valve housing 18.

The valve body 21 is slidably guided in a pre-chamber 52 in the valve housing 18, in particular in the upper portion 20 of the valve housing 18. For this purpose, for example, guide surfaces between an outer periphery 53 of the valve body portion 35 and an inner periphery 54 of the upper portion 20 are provided. The lifting movement of the valve body 21 is limited by the drive device 22, which acts on the upper portion 20 of the valve housing 18. The drive device 22 comprises a ferrite core 57 inserted in a housing 56 and an actuator 59 arranged in a receiving space 58. The receiving space 58 is closed by a sealing plate 61. This sealing plate 61 preferably extends completely over the receiving space 58, so that in the receiving space 58 no internal container pressure acts on the actuator 59. The lifting movement of the valve body 21 can be limited by the core 57 or in particular by the sealing plate 61. The sealing plate 61 preferably also has damping properties. The drive device 22 further comprises an annular armature 60 which is fixedly connected to the valve body 21. This armature 60 can additionally be guided by an inner guide section on the core 57 and / or housing 56. The pre-chamber 52 is permanently sealed in the transition region from the housing 56 of the drive device 22 to the upper portion 20 of the valve housing 18 by a seal 63. This seal 63 may also be provided at the upper end of the upper portion 20 of the valve housing 18 to the housing 56 of the drive device 22.

For the above-described embodiment, a closure device 12 is achieved with a floating valve body 21, wherein the pressure in the main chamber 15, ie in the pressure vessel 14, is equal to that in the pre-chamber 52. Due to the large central Gangsbohrung 39, such pressure equalization is achieved quickly and can be maintained. The force acting on the valve body 21 closing force is independent or almost independent of the container internal pressure due to the pressure equalization and the design of the effective pressure surfaces 37, 44. For this purpose, it is provided that the first effective pressure surface 37 which acts on the valve seat surface 29 of the valve body 21 through the inner diameter of the seal 31 is determined. The second effective pressure surface 44, which faces the pre-chamber 52, is determined by an outer diameter of the seal 43. In order for a floating bearing is made possible, the inner diameter of the seal 31 corresponds to the outer diameter of the seal 43 or substantially this, so that a pressure equalization is possible. As a result, the closing force is determined by the atmospheric pressure acting from the outside and the force of the force storage element 47. Via the outlet openings 26, the atmospheric pressure acts on the outer pressure surface 48 in the closing direction, in which the force storage element 47 also acts. The resulting compressive force is determined by the size of the outer pressure surface 48 and the force of the force storage element 47. This closing force counteracts an opening force by an outer pressure surface 64 which is formed outside of the seal 31 on the annular collar 38. For a closing force to prevail, it is thus necessary that the pressure force of the force storage element 47 and the pressure force resulting from the outer pressure surface 48 is greater than the pressure acting in the opposite direction, which results from the outer pressure surface 64 on the annular collar 38.

For driving the valve body 21, the electromagnetic drive device 22 is energized, whereby a lifting movement of the valve body 21 is achieved and a detachment of the valve seat surface 29 of the valve body 21 is given by the valve seat 28 on the valve housing 18. As a result, the compressed gas can flow out through the outlet openings 26 into the pressure bag 24. During the outflow of the compressed gas, a pressure equalization between the pre-chamber 52 and the main chamber 15 or the interior of the pressure vessel 14 takes place at the same time, so that the floating bearing and the on the valve body 21 acting balance of forces due to the through hole 39 can be maintained. To close the valve body 21, the drive device 22 is stopped, so that the closing force generated by the force storage element 47 and outer pressure surfaces 48 transferred the valve body 21 in a closed position shown in FIG.

To improve the guidance of the valve body 21 in the valve housing 18, a damping ring 68 may preferably be provided on a radial peripheral surface 67 of the annular collar 38. Such a damping ring 68 can also contribute to the damping of the vibration system. This damping ring 68 has no sealing effect.

The present embodiment thus has the advantage that the valve body 21 is directly controllable, whereby short reaction times are achieved and the controllability is improved. In addition, this arrangement has the advantage due to the large flow cross-sections, that nitrogen can be used as compressed gas, whereby lower requirements for the design of the tightness of the system is given as in helium. This closure device 12 is formed as a self-contained unit and can be attached to the respective pressure vessel 14, wherein the lower portion 20 of the valve housing 18 is modified for fixing to the container opening 16. Furthermore, such a closure device 12 is temperature and pressure tolerant.

FIG. 3 shows an alternative embodiment of a closure device 12 to FIG. 1 in a closed position. FIG. 4 shows alternative embodiments according to FIG. 3 in a working position. In the following, reference is made to FIGS. 1 and 2 with regard to the correspondence of the features.

The embodiment according to FIGS. 3 and 4 differs from the embodiment in FIG. 1 in that a rotationally symmetrical guide surface 72 is provided in the container opening 18, which tube section 73 protrudes into the interior of the container and a tube section 73 in the container interior. direction pointing pipe section 74 which expands. By virtue of this preferably funnel-shaped or in particular trumpet-shaped guide surface, which is held by webs 76 to the lower section 20 of the valve housing 18, the flow field is homogenized early in the event of outflow of the compressed gas and the outflow velocity is increased. Preferably, a further rotationally symmetrical guide surface 77 is provided on an underside of the valve body, which is likewise held by webs 76 to the underside of the valve body 21. This rotationally symmetrical guide surface 77 engages in the closed position of the valve body 21 in the rotationally symmetrical guide surface 72 partially. In the open state of the closure device 12 is achieved in that the outflowing through the tubular portion 73 of the rotationally symmetric guide surface 72 volume flow is deflected via the guide surface 77 also in the direction of the outlet opening 26. At the same time, the opening speed of the valve body 21 is thereby increased due to the applied compressive force. In a working position, the expanded pipe section 74 of the rotationally symmetrical guide surface 72 and the rotationally symmetrical guide surface 77 form a fan-shaped arrangement for flow deflection.

Such rotationally symmetrical guide surfaces 72, 77 can be used or attached individually or jointly as well as subsequently in a container opening 16 or on an underside of the valve body 21.

FIG. 5 shows an alternative embodiment of the closure device 12 according to FIG. 1 in a closed position. FIG. 6 shows the embodiment according to FIG. 5 in a working position. With regard to the matching features, reference is made to the description of the figures for FIGS. 1 and 2.

In this embodiment, the valve body 21 receives on its underside or to the pressure vessel 14 facing a pressure equalization-supporting element 81. This pressure compensation supporting element 81 is tubular and has, for example, a first cylindrical pipe section 83 which extends through the container opening 16 extends through into a pressure and / or flow-calm region of the pressure vessel 14. An extension section 84, which merges into a fastening section 86, adjoins this cylindrical tube section 83 in the outflow direction of the compressed gas. This attachment portion 84 is preferably cylindrical and provided for insertion into the through hole 39 of the valve body 21. Alternatively, other non-positive, positive or cohesive connections for attachment of the pressure compensation element 81 to the valve body 21 may be provided. The expansion section 84 preferably has an outer surface 87, which approximates or corresponds to a widened pipe section 74 of the rotationally symmetrical guide surface 72 or the rotationally symmetrical guide surface 77 in the geometry in order to achieve a flow deflection. By this pressure compensation element 81, which can also be called a proboscis, a quick pressure equalization in the prechamber 52 to the main chamber 15 is enabled as soon as compressed gas flows out of the pressure vessel 14 and the pressure conditions due to an opening or closing movement of the valve body 21 in the prechamber 52 change. This has the particular advantage that a closing force acting on the valve closing body 21 can be counteracted, since a negative pressure in the outflow region 32 is generated during the outflow of the compressed gas.

In the case of the abovementioned exemplary embodiment, it is fundamentally advantageous for the flow-bearing surfaces to have a rough surface, so that a boundary layer thickness of an airfoil becomes smaller, since this is easier to control in the case of turbulent flows than in the case of laminar flows.

FIGS. 7 a to e show a further alternative embodiment of a closure device 12 according to FIG. 1, wherein only that part of the part of the valve body 21 facing the container opening 16 is shown enlarged, which deviates from FIG. Incidentally, reference is made to the description of the embodiment according to FIG. In a lower portion of the valve body 21, a drive device 91 is provided. By means of this additional drive device 91 for the drive device 22, the force situation for opening on the one hand and the force situation for closing on the other hand can be optimized. This drive device 91 comprises a control element, in particular a sleeve 92, in a control chamber 93, which forms part of the through-bore 39. The control chamber 93 and the sleeve 92 are preferably formed in size such that the cross section of the through hole 39 extends completely over the length of the valve body 21. Outside the control chamber 93, a non-illustrated actuator is provided which causes an actuating movement of the sleeve 92. The sleeve 92 is movably mounted in the control chamber 93 with sufficient radial clearance. The function and effect of the drive device 91 will be described below with reference to FIGS. 7a to e. FIG. 7 a shows the closed position of the valve body 21 relative to the container opening 16. The valve seat surface 29 abuts against the valve seat 28.

By controlling the drive device 22, the valve body 21 is transferred to a working position. In this working stroke, the sleeve 92 remains in the control chamber 93. The outlet region 32 for the outflow of compressed gas is released.

For quick transfer of the valve body 21 in a closed position, the drive device 91 is actuated. By driving the sleeve 92, this is led out of the control chamber 93 by a lifting movement, so that it is guided into the outlet region 32 and allows a primary blocking of the radial outlet openings 26, as shown in Figure 7c. Due to the changed pressure situation occurs a sudden transfer of the valve body 21 in a Schließpositioπ, as shown in Figure 7d. Subsequently, the sleeve 92 is completely retracted into the control chamber 93, as shown in Figure 7e, so that a reopening movement of the valve body 21 is not hindered. The retraction of the sleeve 92 in the control chamber 93 can be achieved for example by a spring force. Such an alternative embodiment can also be superimposed on the embodiments according to FIGS. 3 to 6.

Claims

claims

1. A closure device for a pressurized gas-filled pressure vessel (14) of a cold gas generator (11), the pressure vessel (14) comprising a vessel opening (16) to which the closure device (12) can be arranged to form a cold gas generator (11), with a valve body (21) which closes at least one outlet opening (26) communicating with the surroundings in a closed position and which can be moved to a working position by a drive device (22) for opening the at least one outlet opening (26), characterized

- That the valve body (21) is slidably disposed in a valve housing (18) and with an antechamber (52) in the valve housing (18) and a main chamber (15) which is formed by a pressure chamber of the pressure vessel (14) communicates, - That the valve body (21) facing the main chamber (15), effective pressure surface (37) and an antechamber (52) facing, effective pressure surface (44) which are equal or approximately equal in size, which with the filling pressure of Main chamber (15) can be acted upon,

- That the valve body (21) has an outer effective pressure surface (64) acts on the atmospheric pressure in the opening direction and a further outer effective pressure surface (48) comprises, acts on the atmospheric pressure in the closing direction and at which a force storage element (47 ) attacks and

- That the compressive force which acts in the opening direction and resulting from the outer effective, acted upon by atmospheric pressure pressure surface (64) is smaller than the closing force acting in the closing direction and from the effective outer pressure surface (48) acted upon by atmospheric pressure and the force the energy storage element (47) results.

2. Apparatus according to claim 1, characterized in that the first effective pressure surface (37) on the valve body (21) facing the main chamber (15) by a seal (3I) ₇ in particular Sitzdichtuπg, and the second effective pressure surface (44) on Valve body (21) facing the Vorkammer (52), by a seal (43), in particular Sitzdϊchtung is limited, wherein an inner diameter of the seal (31) at the first to the main chamber (15) facing the pressure surface (37) equal to a outer diameter of the seal (43) on the further pre-chamber (52) facing effective pressure surface (44) is provided.

3. Closure device according to claim 1 or 2, characterized in that for forming the first and further effective pressure surface (37, 44) an at least two-part valve body (21) is formed.

4. Closure device according to claim 3, characterized in that between the at least two-part valve body (21) a seal (36) is provided, which has a permanent tightness.

5. Closure device according to one of the preceding claims, characterized in that the valve housing (18) is formed at least in two parts and preferably comprises a lower portion (19) and upper portion (20).

6. Closure device according to claim 5, characterized in that between the at least two-part valve housing (18) a seal (63) is provided, which has a permanent tightness.

7. Closure device according to one of the preceding claims, characterized in that the valve body (21) has one or more in the direction of displacement of the valve body (21) extending through holes, which connects the main chamber (15) and the prechamber (52), preferably a large central through hole (39) is provided.

8. Closure device according to one of the preceding claims, characterized in that the input and / or output of the central through-bore (39) has a funnel-shaped or trumpet-shaped profile.

9. Closure device according to one of the preceding claims, characterized in that the valve body (21) has a diameter-tapered region (46), in which a radially inwardly directed annular collar (50) of the valve housing (18) engages.

10. Closure device according to claim 9, characterized in that in the tapered region (46) the force storage element (47) is arranged, which on an annular surface (51) of the inwardly directed annular collar (50) of the valve housing (18) engages and opposite to an outer pressure surface (48) which is provided on a radially outwardly directed annular collar (38) of the valve body (21).

11. Closure device according to one of the preceding claims, characterized in that on the pre-chamber (52) adjacent the drive device (22) is provided and a receiving space (58) for an actuator (59) which drives an armature (60).

12. Closure device according to claim 11, characterized in that the armature (60) is designed as an annular disc.

13. Closure device according to claim 11 or 12, characterized in that the armature (60) is permanently attached to the valve body.

14. Closure device according to one of claims 11 to 13, characterized in that the receiving space (59) in the housing (56) of the drive device (22) by a sealing plate (61) is pressure-tight manner.

15. Closure device according to claim 14, characterized in that the sealing plate (61) is designed as a stop for the damped opening movement of the valve body (21).

16. Closure device according to one of claims 11 to 15, characterized in that a housing (56) of the drive device (22) on the valve housing (18) is releasably attached and preferably in a separation point has a seal (63).

17. Closure device according to one of the preceding claims, characterized in that a container opening (16) closing radial annular collar (38) of the valve body (21) on a radial outer peripheral surface (67) has a non-sealing Damping ring (68) which engages an inner periphery of the valve housing (18).

18. A closure device according to one of the preceding claims, characterized in that in the container opening (16) of the pressure vessel (14) a rotationally symmetrical guide surface (72) is arranged, which in the main chamber (15) directed pipe section (73), in Outflow direction of the compressed gas in a flared pipe section (74) passes.

19. Closure device according to claim 18, characterized in that the rotationally symmetrical guide surface (72) is positioned by webs (76) coaxial to the longitudinal axis of the container opening (16).

20. Closure device according to one of the preceding claims, characterized in that on a main chamber (15) facing the region of the valve body (21) a rotationally symmetrical guide surface (77) is provided, which for deflecting the outflowing compressed gas in the direction of the outlet openings (26). is trained.

21. A closure device according to claim 20, characterized in that the rotationally symmetrical guide surface (77) has a funnel-shaped or trumpet-shaped geometry, wherein the small opening cross section of the rotationally symmetrical guide surface (77) to the container opening (16) and the large opening cross-section to the valve body (21).

22. Closure device according to claim 20 or 21, characterized in that the rotationally symmetrical guide surface (77) on the valve body (21) is held by webs coaxial with the longitudinal axis of the valve body (21).

23. Closure device according to one of the preceding claims, characterized in that on an underside of the valve body (21) having a central through hole (39), a is provided at least in a closed position of the valve body (21) in a pressure and / or flow-calmed region of the pressure vessel (14).

24. Closure device according to claim 23, characterized in that the pressure compensation supporting element (81) has a preferably cylindrical pipe section (83) which extends into the main chamber (15) and has a fastening section (84) which is in or on a through-bore (8). 39) of the valve body (21) acts.

25. Closure device according to claim 23 or 24, characterized in that an expansion section (84) is provided between the tube section (83) and the attachment section (86) of the pressure compensation-supporting element (81).

26. Closure device according to one of claims 23 to 25, characterized in that an outer surface of the widening portion (84) has a trumpet or funnel-shaped guide surface for Strömungsumleπkung.

27. Closure device according to one of claims 23 to 26, characterized in that the fastening portion (86) of the pressure compensation supporting element (81) in the through hole (39) of the valve body (21) inserted, in particular pressed.

28. Closure device according to one of the preceding claims, characterized in that in the pressure vessel (14), the valve housing (18) and the valve body (21) provided flow-forming surfaces have a rough surface.

29. Closure device according to one of the preceding claims, characterized in that in a container opening (16) of the pressure vessel (14) facing the region of the valve body (21) a Antriebsein direction (91) is provided, which is controllable to control the closing movement of the valve body (21).

30. Closure device according to claim 13, characterized in that the drive device (91) on the underside of the valve body (21) comprises a control chamber in which a control element, in particular a sleeve (92), in the opening and closing direction of the valve body (21). is movably arranged.

31. A closure device according to claim 29 or 30, characterized in that the control element, in particular the sleeve (92), in the working position of the valve body (21) is controllable such that this an outlet region (32) between the container opening (16) and the Partially closes outlet openings (26).

32. Closure device according to one of claims 30 to 31, characterized in that the control element, in particular the sleeve (92) of the drive device (91), with a radial clearance in the control chamber (93) of the valve body (21) is arranged.