EP2243204A1

EP2243204A1 - Pressurized container arrangement

Info

Publication number: EP2243204A1
Application number: EP09711571A
Authority: EP
Inventors: Andreas Kleinschmidt; Steffen Rautenberg
Original assignee: Siemens AG
Current assignee: Siemens AG
Priority date: 2008-02-22
Filing date: 2009-02-17
Publication date: 2010-10-27
Also published as: RU2010138936A; WO2009103689A1; DE102008011044A1; CN101953044A

Abstract

A pressurized container arrangement comprises a first and a second pressurized container (1, 2). The pressurized containers (1, 2) are equipped with a flange (3a, 3b) at respective ends facing one another. The pressurized containers (1, 2) are connected by way of a section (4, 4a) with a variable length. The section (4,4a) with variable length is bridged by a stabilization element (5,5a). The stabilization element (5, 5a) comprises at least one circular chassis (6, 6a, 6b) that extends around the section (4, 4a) with variable length. The chassis (6, 6a, 6b) is connected in rotationally rigid fashion to one of the flanges (3a, 3b).

Description

description

Pressure vessel assembly

The invention relates to a pressure vessel arrangement with a first pressure vessel and with a second pressure vessel, which each have a flange at mutually facing ends and which are connected via a arranged on the flanges by a stabilizing element bridged length changeable section.

Such a pressure vessel arrangement is known for example from the patent DE 198 15 151 Cl. The local pressure vessel arrangement has a first pressure vessel and a second pressure vessel, which are equipped with flanges. Between the flanges, a variable-length section is arranged, which connects the first and the second pressure vessel with each other.

In order to protect the variable-length section from excessive mechanical stress, a stabilizing element is provided. The stabilizing element has a plurality of tie rods distributed around the ^{circumference of} the flanges.

The tie rods project beyond the flanges. By an additional

Arranging the tie rods on the outer circumference of the flanges of the required space is increased. Next are a variety of projections us tips available.

It is therefore an object of the invention to provide a Druckbehälteranord ^¬ tion, which is designed as free of projections as possible. According to the invention the object is achieved in a Druckbehälteran ^¬ order of the type mentioned in that the stabilizing element has at least one annular, the County ^¬ genveränderlichen section encompassing chassis, which is rigidly connected to one of the flanges.

By using a ringförmmigen chassis, which surrounds the variable-length section, the Stabilisie ^¬ tion element on the one hand allow a change in length of the length-variable section and protect the variable-length portion from attacking from radial directions forces. Thus, the variable-length portion is shell-like protected by the annular chassis. It can be provided that the chassis is configured in its ring shape in the manner of a hollow cylinder with an annular cross-sectional area. Depending on the height of the hollow cylinder, it is possible to protect larger or smaller portions of the length ^{variable ¬} union section from external forces. Thus it is possible, preferably in the axial direction, to support a change in length due to the variable-length section. As variable-length sections preferably bellows-like designed elastically deformable ^¬ bare tubular structures can be used. Thus, for example be provided that the length-changing section by section has a smaller wall thickness than that of the pressure vessel to be joined together Wandstär ^¬ ke.

Due to the smaller wall thickness, such a variable length portion is more sensitive to allow it to react kenden forces as for example, executed as self-supporting Kon ^¬ constructions pressure vessel.

Even when using a variable-length section which can be telescoped, for example, the Use of an annular stabilizing element of Vor ^¬ part. In this case, a sealing area between mutually telescoping elements of the variable-length section can be protected from external influences. This sealing region is a place which is subject to increased mechanical stress, since there must be repeated relative movements between sealing telescoping elements. In this case, the sealing area is to be designed in such a way that it resists the pressures provided inside the pressure vessel arrangement and can withstand these for longer periods of time.

Regardless of the structural design of the variable-length section of this limits in its interior a volume which at least with an interior of one of

Pressure vessel can communicate. For this purpose, a fluid-tight connection between the variable-length section and at least one of the pressure vessels is provided.

An angularly rigid connection of the chassis to one of the flan ^¬ specific makes it possible to provide a positioning of the stabilization ^¬ element relative to at least one of the pressure vessel. Thus, it is possible to position the chassis by a simple flanging to a flange. The chassis can be connected directly or indirectly indirectly rigid angle with a flange of the pressure vessel. In an indirect connection, the chassis and the flange are connected to each other with the interposition of another module. The flanges can be designed in various ways. Depending on requirements, welding flanges, screw flanges, Los ^¬ flanges etc. may be provided. An angularly rigid composite of pressure vessel and chassis prevents relative movement between them. A further advantageous embodiment may provide that the chassis is arranged substantially within a Flanschspaltes located between the flanges.

In one arrangement of the chassis within the Flanschspaltes it is advantageous if a Chassiswandung to a provided by egg ^¬ nem flange provided flange has a corresponding wall thickness. This makes it possible to position the chassis substantially flush between the flanges. In order for projections on the circumference are avoided and thus a slim silhouette of Druckbehälteran ^¬ order can be generated. Depending on the intended Flanschspaltbreite the chassis of different heights may be ausges ^¬ tattet.

Furthermore, it can be advantageously provided that the chassis positions the variable-length portion with respect to at least one of the pressure vessels with a fixed angle.

By using the chassis to position the variable-length section relative to one of the pressure vessels, it is possible to utilize the mechanical properties of the chassis and stabilize the overall layout. For example, it may be provided that a lip is provided on the variable-length section, which lip is to be pressed directly or indirectly against a flange of the pressure vessels. The lip may be designed for example as a self ^¬ sealing member so that applied pressure force a sealing connection is produced at the lip by a via the chassis to the variable-length element. However, it can also be provided that additional sealing means such as O-rings or the like are to be arranged in the region of the lip. It can be provided that the variable-length section is indirectly pressed against a flange of a pressure vessel. ters is pressed. An indirect pressing it may be aimed ^¬ characterized, in which a further assembly is disposed between the flange and the variable-length section. For example, it may be provided that spacers, frames or other devices prevent direct contact of variable length section and flange, but that an indirect rigid connection between the variable-length section and flange is made.

A further advantageous embodiment may provide that the chassis has at least one casing side arranged Ausneh ^¬ mung.

In the case of an annular structure of the chassis, provision can be made for recesses to be arranged on the inner shell side and / or outer shell side on the chassis. Depending on the expected forces, it may be advantageous to provide the one or the other layer or alternatively alternating layers on the chassis. In addition to structurally improving properties of the recesses, a material saving is achieved on the stabilizing element, so that a low-mass but inherently stable construction is given.

Furthermore, the recesses may also be provided in order to arrange additional assemblies in them and thus to provide additional receiving space within the flange gap. For example, sensors can be integrated into the recesses, by means of which z. As temperatures, pressure or other variables are monitored at the pressure vessel assembly.

Furthermore, it can be advantageously provided that at least one recess is a continuous recess. A continuous recess makes it possible to provide a chassis which allows access to the protected areas of the variable-length section. Furthermore, material and mass is saved on the chassis. By a grid-like structure of the annular chassis wei ^¬ terhin given a protective effect of the chassis. Advantageously, it can be provided that the recesses are distributed uniformly on the circumference of the chassis, so that the areas located between the recesses form struts, wherein the struts are preferably aligned axially. Thus, it can be provided that linear struts are aligned substantially parallel to one another and thus a circumferential band of successive substantially rectangular recesses is formed on the annular chassis. In addition, the recesses may have a wide variety of shapes, so that different grating structures can be formed on the chassis as needed. Regardless of the shape of the struts or recesses a protective effect is given even in a durchbroche- nen design of the shell.

Furthermore, there is the possibility of integrating further components as described above into the continuous recesses while allowing parts of these components to protrude beyond the envelope contour formed by the outer jacket region of the chassis. For example, there is an easy way to lead supply lines, test leads, etc. out of the recesses to further processing units.

Advantageously, it can further be provided that in at least one recess a bolt protrudes, which pulls the chassis against a flange. For bracing the chassis against a flange advantageously bolts can be used. Bolts can be equipped, for example, as screws, threaded rods, rivets, etc. In this case, the bolts are mounted, for example, in guides, so that a lateral breaking of the chassis from a bolt axis, which is essentially defined by the clamping direction and coincides with this, is prevented. At the periphery of the flanges of the two Druckbehäl ^¬ ter corresponding holes may be provided, in which bolts can be fixed. For this purpose, these recesses may be provided with corresponding internal threads, or it may also be provided that the bolts protrude through the holes and secured on an outer side with a nut ^¬ who. Advantageously, a so-called bolt circle is provided on the flanges, on which a plurality of recesses are uniformly distributed in flange surfaces of the flanges. A bolt circle on the chassis corresponding to this hole circle now makes it possible to insert bolts and to clamp the chassis. It may in turn be provided that the chassis is clamped directly or with the interposition of other elements such as spacers, frame or variable-length section. This bracing stabilizes the chassis on the one hand the flange on the other hand, the flange can stabilize the chassis. Thus, a rigid structure is formed, which can absorb mechanical forces well. To protect the bolts, they can advantageously protrude into recesses of the chassis. In this case, it can be advantageously provided that the number of recesses corresponds to the number of bolts provided for bracing the chassis against a flange of a pressure vessel.

By bolts elongated elements, such as threaded rods, screws, profiled bars, rivets, etc., understood, which a guide, positioning or fixing of assemblies are used.

A further advantageous embodiment can provide that project into the recess, a first pin and a second pin whose pin axes are parallel to each other.

Advantageously, the recesses can also be used to accommodate several bolts protected. The bolts may be equipped with screw heads or be provided with corresponding nuts on threaded portions of the bolt, which are each located in the space of the recess. A parallel alignment of the bolts to each other allows a simplified assembly or assembly of the various components such as chassis, first pressure vessel, second pressure vessel and variable-length section. Thus, it is possible by the parallelism of the pin axes zen a zen Intein zen or make covering of the individual modules. This makes rapid mounting possible. The bolt axis is determined by the longitudinal axis of the bolt, which corresponds to the clamping direction of a ver ^¬ clamped bolt.

Advantageously, it can further be provided that the bore axes are substantially congruent.

In the provision of bolts with substantially congruent bolt axes, the bolts should preferably be arranged lying one behind the other in the axial direction. This results in an arrangement which is connected to each other in individual planes, wherein the connection of the individual planes is preferably realized in each case via directly adjacent to each other arranged assemblies. This makes it possible to disassemble the assembly in different levels and thereby only to separate the abutting in this plane modules from each other. On the abutting assemblies continue scheduled, for example, flanged, modules can remain connected.

Advantageously, it can further be provided that a bolt is elastically supported on the chassis.

An elastic support of a bolt on the chassis makes it possible to transfer forces via the stabilizing element between the two pressure vessels and to keep them away from the variable-length element. Thus, a Überbrü ^¬ ckung this variable-length element is given. In order to provide a reserve for particularly large forces, it is advantageous to provide elastic mounting on at least one ^bolt . About this elastic storage, for example, length changes can be compensated in a limited extent. So overloads are avoided.

Furthermore, it can be advantageously provided that a spring element is arranged within the recess for elastic support.

The use of a spring element makes it possible to compensate for repeated movements. Depending on the modulus of elasticity of the spring element, a more or less rigid coupling can take place via the spring element. In an arrangement of the spring element within the recess of this spring element is protected by the chassis. In the recess can accommodate a variety of spring elements. Thus, for example, be arranged as a spring element coil springs Spiralfe ^¬ countries, disc springs and combinations of different types or similar spring elements. However, it can also be provided that a highly elastic material al as an elastomer is used. Preferably, it can be provided that the spring element extends around an axis and has a corresponding recess in order to be arranged on a bolt projecting into a recess. In this case, the bolt passes through the spring element, wherein the spring tension is adjustable via a Vorkompressi ^¬ on the spring element on the bolt.

A further advantageous embodiment can provide that the chassis is held by a stud bolt spaced from a flange.

A stay bolt is understood to mean a bolt which is connected in an angularly rigid manner to an assembly. For example, stud bolts can be inserted into the holes of a bolt circle of a flange and fixed there in a fixed angle to the flange. Further arranged on the bolt elements, for example, screwed on a thread nuts or the like, a stop may be created, which realizes a spacing of an assembly, such as the Chas ^¬ sis, to the stud bolt bearing flange. The flange may be, for example, the flange of a Druckbe ^¬ container or a flange on another chassis. Through the use of studs, it is possible to limit the height of the chassis and so restrict the mass of the chassis ^¬ . The height of the chassis may vary depending on the use of the recesses provided on these. If recesses are required to accommodate particularly large sensors or the like, a chassis of greater height can be selected. It should be noted that the function ^¬ ability of the variable-length section must continue to be given. Depending on the height of the chassis, adjustments of the stabilization element can be made via the stud bolts. In particular, with an arrangement of a spring element within ^¬ half a recess, depending on the size of the spring element, a corresponding adjustment of the chassis may be necessary.

A further advantageous embodiment can provide that the chassis is pressed against one of the flanges with the interposition of a disk insulator.

The pressure vessel arrangement may for example be part of an encapsulating housing of an electric power transmission device. In this case, the pressure vessel and the variable-length section surround an electrically conductive Leiterzug. This interior of the pressure vessel assembly is equipped with a respect to the environment is under elevated pressure insulating gas, game as examples sulfur hexafluoride or nitrogen or Gemi ^¬ rule of insulating gases filled. The located in the interior of the pressure vessel assembly electrical circuit path is ent ^¬ speaking insulated from the pressure vessel assembly to lead. For this purpose, insulators are provided, which extend between the electrical conductor and the pressure vessels or the variable-length section. Advantageously, disk insulators are used which have a schei ^¬ benförmige structure. Preferably, the ticket ^¬ benisolator may be provided at its periphery with a stabilizing framework men, over which a strain is performed on a flange by means of bolts. The disk insulator may be arranged for example between a flange and a chassis so that the chassis and the flange are connected indirectly win ^¬ kelstarr each other.

The disc insulator is penetrated by one or more conductor tracks. Depending on the embodiment variant of the discs ^¬ isolator can form a gas-tight barrier over a flange of a pressure vessel so that a gas exchange between This pressure vessel and the other pressure vessel or the variable-length section is not possible. The electrical conductor runs through the glass insulator gas-tight. However, it can also be provided that corresponding channels are provided in the disc insulator, through which the insulating gas can flow between the individual interiors of the first pressure vessel, second pressure vessel and variable-length section.

The pressure vessel assembly is a capsule housing, which is possibly divided into different pressure spaces by entspre ^¬ sponding disc insulators or other barriers, be a pressure space of a pressure vessel, a plurality of pressure tanks or a pressure vessel or more pressure vessels and one or more variable length sections of limited can.

Depending on the configuration of the disk insulator, in particular when equipped with an annular peripheral frame, it can be used to compensate for the width of the flange gap formed between the flanges of the first and second pressure vessels. This can be provided for example that different Rah ^¬ mendimensionen get used so that, for example, does not require a use of separate spacers.

A further advantageous embodiment can provide that a first chassis and a second chassis are each connected to one of the flanges with a fixed angle.

Length-adjustable sections may have different compensation capacities depending on the expected relative movements between the two pressure vessels. Depending on the capa- Frequency of the variable-length section can be provided that different designed Stabilisierungsele ^¬ elements are used to correspond to Kompensati ^¬ onskapazität the variable-length section to provide a sufficiently dimensioned power bridge available. In this case, for example, be provided that two chassis are used, which are each connected with a rigid angle to one of the flanges of the pressure vessel, wherein the chassis are coupled to each other by means of elastically mounted bolts. This makes it possible that the flanges are relieved of immediacy ^¬ cash compensation attacking movements. A length compensation takes place between the mutually facing sides of the chassis. There then corresponding elastically deformable elements can be arranged, which compensate for a change in length and realize a power transmission between the pressure vessels of the pressure vessel arrangement.

Furthermore, it can be advantageously provided that the chassis is a cast body.

In order to produce cost-effective chassis, casting methods are particularly suitable. Castings can be cast approximately in their final shape to be used. Only minor rework, such as the introduction of openings for bolts, threads, surfaces to be smoothed, etc., are still to be made. Castings have a low mass, since superfluous formations can already be avoided during the casting.

Furthermore, a large number of chassis can be made, the dimensional accuracy is given even after a variety of casting operations. In the following, the invention is shown schematically with reference to a Ausführungsbei ^¬ game in a drawing and described in more detail below.

It shows the

Figure 1 is a perspective view of a pressure vessel assembly with a first variant of a stabilization ^¬ tion element, the

2 shows a section of the Stabili ^¬ sierungselementes by the first variant,

3 shows a perspective view of a Druckbehälteran- order with a second variant of a Stabili ^¬ sierungselementes that

4 shows a section through the second variant of the stabilizer ^¬ lisierungselementes.

Pressure vessel arrangements shown in the figures each have a first pressure vessel 1 and a second pressure vessel 2. The pressure vessel 1, 2 respectively act genus tung representative, that is different from those shown as a tubular container in the figures the first and second pressurized containers 1, 2 and otherwise designed pressure vessels ^¬ ter can be used.

At mutually facing ends, the pressure vessels 1,2 each have a flange 3a, 3b. Furthermore, in the pressure vessels 1, 2 shown in the figures, the arrangement of flanges is also provided at opposite ends of the pressure vessel 1, 2. The flanges 3 a, 3 b are each aligned coaxially to a longitudinal axis A. 1 shows a pressure vessel assembly in which the first and second pressure vessels 1, 2 are connected by a length ^¬ variable section. 4 The length-variable section 4 is designed in the form of a tubular thin-walled element, wherein a fold-like structure is provided in the central section, so that a bellows is formed. Via the bellows, a sufficient distance is made available on the variable-length section 4 in order to be able to undertake a reversible deformation of the variable-length section 4 in the axial direction A. A more detailed representation of the variable-length section 4 is the figure 2 removable. The variable-length section 4 connects the two pressure vessels 1, 2 with each other.

In order to stabilize the two pressure vessels 12 against each other and to keep the variable-length section 4 in particular free of radial forces, a stabilizing element 5 is provided. The stabilizing element 5 has an annular chassis 6. The annular chassis 6 ^¬ engages the variable-length section 4 and offers the possibility of the two flanges 3a, 3b of the first and two ^¬ th pressure vessel 1, 2 bridging the variable-length section 4 to connect with each other. In the present example, the chassis 6 is rigidly connected to the flange 3 a of the first pressure vessel 1. It is an indirect connection between the chassis 6 and flange 3a is provided, wherein between flange 3a and chassis 6, a disc insulator 7 is arranged.

In the pressure vessels 1, 2 and the variable-length section 4, the arrangement of an electrical conductor strip is provided in the interior, which is guided isolated from the pressure vessel arrangement. For electrically isolated arrangements tion, the disc insulator 7 is provided. The disk insulator 7 can form a gas-tight barrier within the pressure vessel arrangement or provide a gas exchange between the interior spaces of the first and / or second pressure vessel and the variable-length section 4. The walls of the first and second pressure vessel and the variable-length section 4 limit the pressure chambers of the pressure vessel arrangement in the radial direction.

2 shows a section through the first variant of the stabilizing element 5, wherein the adjacent flanges 3a, 3b and the disc insulator 7 are visible in the cutout. The disk insulator 7 has an annular frame 8 on its outer periphery. The annular frame 8 abuts against the flange 3 a of the first pressure vessel 1. In the flanges 3a, 3b are each provided similar hole circles. The hole circles have a plurality of holes in wel ^¬ che bolts, for example in the form of screws can be inserted. In the annular frame 8, a corresponding bolt circle is provided, which is provided with internal threads. Screws 9 can now be screwed into these internal threads in order to press the annular frame 8 of the disk insulator 7 against the flange 3a of the first pressure vessel. The Iso ^¬ liermaterial has in the edge region, at which the annular frame 8 collides with the insulating material, each ^¬ recesses 10, in which sealing means, such as O-rings, can be inserted. Via the sealing means a ^trailing seal provided for in the interior of the pressure vessel 1 or the variable-length portion 4 pressure chambers occurs. In the present case, the variable-length portion 4 is planar if ^¬ tubular and provided at its front ends each with an outwardly bulging lip 11. A lip 11 is of a correspondingly out form ^¬ th first front side of the chassis 6 against the Ausneh- mung 10 located sealant pressed so that a pressure-resistant system of the variable-length section 4 takes place on the disc insulator 7. The chassis 6 is also provided on its the disk insulator 7 and the flange 3 a of the first pressure vessel 1 facing end side with a kor ^¬ respondierenden bolt circle so that screws 9 press the chassis 6 against the disk insulator 7 and the variable-length section 4 with his Lip 11 is kept sealed. Thus, the chassis 6 and the variable-length section 4 are connected in an angularly rigid manner to the flange 3a of the first pressure vessel 1 via the disk insulator 7.

The chassis 6 has an annular structure, wherein a ring is structured in the manner of a hollow cylinder. On the shell side, the chassis 6 is penetrated by through recesses 12. The continuous recesses 12 are designed such that webs are arranged between them, which are aligned substantially parallel to the longitudinal axis A of the hollow cylindrical structure of the chassis 6. To this longitudinal axis A, all screw connections acting on the chassis 6 are aligned in parallel, which are provided for connecting the chassis 6 to further containers or assemblies of the pressure vessel arrangement. The axes of bolts 9 are defined by the direction of their tensioning effects.

With the first face of the chassis 6 of the stabilization ^¬ approximately element 5 against the disc insulator 7 respectively ge ^¬ gen the first pressure container 1 is pressed. In a second end face of the chassis 6, which is remote from the first end face, wherein the end faces are substantially parallel to each other, a lower bolt circle is arranged. This bolt circle also corresponds to the hole circles of the flanges 3 a, 3 b or to the bolt circle of the disk insulator 7. In this case, the bolt holes in the first end face and the second end face of the chassis 6 are ^aligned so that bolts or screws which pass through the holes of the hole circles have axes lying parallel to one another, in particular congruently arranged axes. The bolt circle of the second end face of the chassis 6 is connected via stud bolts 13 to the flange 3b of the second pressure vessel 2. These stud bolts 13 are angularly fixed in the holes of a bolt circle of the flange 3b of the second pressure container 2. The studs 13 each have ei ^¬ NEN bolt, which is attached via oppositely countered nuts 14a, 14b on the flange 3b of the second pressure vessel 2 angle ^¬ rigid. In order to connect a lip 11 of the length- ^variable section 4 in a gastight manner to the second pressure vessel 2, the flange 3a has a recess 10. The recess 10 is provided to receive a sealing means, which produces a sealing point between the second pressure vessel 2 facing lip 11 of the variable-length section 4 and the flange 3b of the second pressure vessel 2. In order to produce a contact force between the lip 11 and the flange 3b, a loose flange 15 is inserted between the oppositely countered nuts 14a, 14b, which is connected to the stud bolt 13 angularly fixed to the flange 3b. About the lips 11 of the variable-length portion 4 and the loose flange 15 and the first Stirnsei ^¬ te of the chassis 6 is a bracing of the variable-length section 4 against sealant in the recesses 10 made ^¬ light. This gives the possibility to hermetically seal the interior of the pressure vessel assembly.

Due to the elasticity of the variable-length section 4, a radial absorption of forces by the variable-length section 4 is only possible to a limited extent. Therefore penetrate the studs 13 the bolt circle of the chassis 6 on the second end face. On the stud bolts 13 each ^¬ proposals in the form of stop nuts 16 are arranged. The stop nuts 16 determine the axial distance between the chassis 6 and the loose flange 15 and the flange 3b of the second pressure vessel 2. An adjustment of the stop ^¬ nuts 16 is given a possibility, the width of a located between the flanges 3a, 3b flange gap on a Set minimum. The stud bolts 13 protrude further into the continuous recesses 12 of the chassis 6. The stud bolts 13 are each provided with one or more spring elements 17 in the interior of the continuous recesses 12. The spring elements 17 are, for example Schraubenfe ^¬ countries, disc springs or similar elastic elements, which allows a tension of the studs 13 against the stop nuts 16 and consequently against the flange 36 of the second pressure vessel 2. About serving as a clamping element Vorspann ^¬ nuts 18, the spring elements 17 can be biased. This gives the possibility, the two pressure vessels

12 to remove each other, ie the flange gap formed between the flanges 3a, 3b can be enlarged ver ^¬ in the axial direction. In such a movement, the variable-length section 4 and the spring elements 17 who ^¬ additionally compresses. A maximum extension of the flange gap between the flanges 3a, 3b is achieved with a complete compression of the spring elements 17. With such a widening of the flange gap, the stop nuts are released from a contact force of the chassis 6, the chassis 6 is about the stud bolts 13 and spring elements

13 against the flange 3b of the second pressure vessel 2 is pressed.

By a suitable choice of the positions of the stop nuts 16 and the length of the spring elements 17 and the position of the biasing nuts 18 on the stud bolt 13 is a one Position of a minimum and maximum permissible Flanschspaltbreite allows.

FIG. 3 shows a further pressure vessel arrangement which has a first pressure vessel 1 and a second pressure vessel 2. At the mutually facing ends, these each have a flange 3a, 3b. The pressure vessel ^arrangement shown in FIG. 3 has a variable-length section 4a, which is provided for the realization of larger strokes. In order to support larger strokes, 5a is provided ^¬ view a second variant of a stabilizing element, the second variant of the stabilizing element 5a has a first chassis and a second chassis 6a 6b. The first chassis 6a is in turn connected in a rigid angle with the interposition of a disk insulator 7 with the flange 3a of the first pressure vessel 1. The second chassis 6 b is rigidly connected to the flange 3 b of the second pressure vessel 2. The two chassis 6a, 6b each encompass the variable-length section 4a.

FIG. 4 shows a section through the second variant of the stabilizing element 5a. An annular frame 8 of the disc insulator 7 has a corresponding bolt circle to the bolt circle of the flange 3a of the first pressure vessel 1. By means of introduced into the bolt circle of the disk ^¬ insulator 7 threads screws 9 are used for attaching the disc insulator 7 to the flange 3a and the first chassis 6a on the disc insulator 7. To that extent a fixing of the insulator disc 7 and ERS system chassis 6a on the flange 3a of the first pressure vessel 1 is carried out as in the prior art of Figures 1 and 2 Druckbe ^¬ hälteranordnung. The disc insulator 7 in turn has recesses 10, in which sealing means can be inserted to a gas-tight bond between disc insulator 7 and Make flange 3a and a lip 11 of the variable-length stabilization element 4a. The lip 11 of the ^variable- length section 4 a is pressed against the disc insulator 7 by means of a first end face of the first chassis 6 a.

Notwithstanding the construction shown in Figures 1 and 2, the lip 11 at the other end of the variable-length portion 4a waiving a loose flange by means of the second chassis 6b using the first

Front side against the flange 3b of the second pressure vessel 2 are pressed. Also in the flange 3b of the second pressure vessel 2, a recess 10 is arranged, in which sealing ^¬ medium can be inserted to form a gas-tight bond between the variable-length section 4 and the flange 3b of the second pressure vessel 2. The second chassis 6b is pressed against the flange 3b at its first end side via a screw connection 9, which projects into a hole of the bolt circle of the flange 3b of the second pressure vessel. In the present case the holes of the hole circle of the flange 3b of the second pressure vessel 2 is such dimensio ^¬ defined that a thread of the bolt 9 is free hindurchbe ^¬ wegbar. The screw 9 is secured on the side facing away from the second Chas ^¬ sis 6b side of the flange 3b by means of a mother and clamped. Thus, the second chassis 6b is rigidly connected to the flange 3b of the second pressure vessel 2. The first and second chassis 6a, 6b have ei ^¬ NEN structurally the same construction as the chassis 6, wel ^¬ ches is shown in Figures 1 and 2. FIG.

In order to connect the mutually facing second end faces of the first and the second chassis 6a, 6b with each other, a bolt circle is provided on the second end faces in each case, wherein these bolt holes each to the hole circles to the first th end faces of the first and second chassis 6a, 6b correspond and continue with the hole circles of the disc insulator 7 and the hole circles of the flanges 3a, 3b of the first and second pressure vessel 1, 2 correspond. All hole circles are axially aligned one behind the other aligned ^¬ so that all bolts axes extend in mutually paral lel ^¬ and are congruent. The corresponding hole circles on the second end face, ie on the side of the chassis 6a, 6b, which face each other, elastically mounted bolts 18a are inserted. The Bol ^¬ zen 18a protrude respectively through an end wall of the first chassis 6a and through an end wall of the second chassis 6b in recess 12 of the first and second chassis 6a, 6b. A central portion of the elastically mounted pin 18 a is limited by stop nuts 16. The stop nuts 16 abut against the second end faces of the first and second chassis 6a, 6b. About the position of the stop nuts 16 is a minimum width of the Flanschspal ^¬ tes between the flanges 3a, 3b of the first and second pressure vessel 1, 2 is determined. At the projecting into the recesses of the chassis 6a, 6b ends of the bolt 18a spring elements 17a are arranged. In this case the Fe ^¬ the elements 17a are designed in the form of stacks of Belleville washers, which are pushed onto the ends of the bolts 18a. As with the embodiment variant according to FIGS. 1 and 2, protective sleeves can be pushed onto the bolts 18a between the spring elements 17. End side, the spring ^¬ elements 17 are set on the bolt 18 a patch biasing ^¬ tern 18 in their bias.

With a change in length, ie with a distance of the flanges 3a, 3b from each other in the direction of the longitudinal axis A, there is an additional compression of the spring elements 17a. The compression can be up to a complete compression ming the spring elements 17a progress. By adjusting the preload nuts 18, a bias of the spring elements 17 a can be adjusted, so that the maximum possible ^¬ possible way, which is zurücklegbar of the flanges 3 a, 3 b, is limited by the position of the biasing nuts 18.

FIG. 4 further shows a tubular electrically conductive conductor run 19, which is mounted centrally above the windshield insulator 7 in the pressure vessel arrangement. The electrical conductor 19 is surrounded by a pressurized gas, wel ^¬ ches in the interior of the variable-length portion 4a and the first and second pressure vessel 1,2 is arranged. Due to the gas-tight design of the connection of pressure vessels 1, 2, variable-length section 4a or disk insulator 7 escape of a gas from the interior of the pressure vessel assembly is avoided. The disk insulator 7 can be designed such that it represents a gas-tight barrier between the pressure chambers defined by the variable-length section 4a and the first pressure vessel 1. However, it can also be provided that on the

Disc insulator 7 channels are provided, which allows a circulation of insulating gas between the interiors of the first pressure vessel 1 and the second pressure vessel 2 and the variable-length portion 4a.

The arrangements shown in the figures are variable with respect to their embodiments. Thus, it may be provided, for example, that the shape of the recesses 12, the position of bolts, screws and nuts, the spring elements used to make the shape of the variable-length section 4, 4a different. Further, for example, be provided that instead of the use of screw-nuts continuous bolts are used, which are secured with nuts or that instead of using a variable-length section 4a, 4b with a bellows-like section a telescopic arrangement is used.

To protect the spring elements 17, 17a can be provided that the recesses 12 are covered on the outer shell side of the chassis 6, 6a, 6b with a shield. The shield can completely span the recesses 12 or only partially cover. It is advantageous if at least the spring elements 17, 17a are protected against direct attack by external forces. Thus, it can be provided that a plate, for example made of a plastic shell-like on a chassis 6, 6a, 6b is placed, the shield can cover one or more recesses.

Various methods can be used to produce a chassis 6, 6a, 6b. It is advantageous to carry out the chassis by means of a casting process as a cast body. Thus, it is possible to provide a lightweight construction which can absorb mechanical forces well.

Claims

claims

1. Pressure vessel arrangement with a first pressure vessel (1) and with a second pressure vessel (2), which at each of facing ends each have a flange (3a, 3b) and which via one of the flanges (3a, 3b) arranged by a stabilizing element ( 5,5a) bridged length changed ^¬ sary portion (4,4a) are connected, characterized in that the stabilizing element (5,5a) at least one ring-shaped, the variable-length portion encompassing chassis (6, 6a, 6b) comprises that a rigid angle with a Flan ^¬ cal (3a, 3b) is connected.

2. Pressure vessel arrangement according to claim 1, characterized in that the chassis (6, 6a, 6b) is disposed substantially within a zwi ^¬ 's the flanges (3a, 3b) located Flanschspaltes.

3. Pressure vessel arrangement according to claim 1, wherein the chassis (6, 6a, 6b) positions the variable-length section (4, 4a) angularly fixed with respect to at least one of the pressure vessels (1, 2).

4. Pressure vessel arrangement according to one of claims 1 to 3, d a d u r c h e c e n e c e in that the chassis (6, 6 a, 6 b) at least one shell side arranged recess (12).

5. Pressure vessel arrangement according to claim 4, characterized in that at least one recess (12) is a continuous Ausneh ^¬ tion (12).

6. Pressure vessel arrangement according to one of claims 4 or 5, characterized in that in at least one recess (12) a bolt (9,13,18a) projects, which the chassis (6, 6a, 6b) against a flange (3a, 3b) pulls.

7. Pressure vessel arrangement according to claim 6, characterized in that in the recess a first pin (9) and a second pin (13, 18a) protrude whose pin axes are parallel to one another.

8. The pressure vessel assembly according to claim 7, wherein a pin axis is substantially congruent.

Pressure vessel arrangement according to one of claims 6 to 8, characterized in that a bolt (13, 18a) is elastically supported on the chassis.

10. Pressure vessel arrangement according to claim 9, characterized in that a spring element (17, 17a) is arranged within the recess (12) for elastic support.

11. The pressure vessel arrangement according to claim 1, wherein the chassis (6, 6a, 6b) is held at a distance from a flange (3a, 3b) via a stud bolt (13).

12. Pressure vessel arrangement according to one of claims 1 to 11, characterized in that the chassis (6, 6a, 6b) with the interposition of a Scheibenisola ^¬ sector (7) against one of the flanges (3a, 3b) is pressed.

13. Pressure vessel arrangement according to one of claims 1 to 12, characterized in that a first chassis (6a) and a second chassis (6b) depending ^¬ Weil with one of the flanges (3a, 3b) is connected rigid angle.

14. A pressure vessel assembly according to any one of claims 1 to 13, wherein a chassis (6, 6a, 6b) is a cast body.