EP3067570B1 - Piston accumulator - Google Patents

Description

Technical area

The invention relates to a piston accumulator according to the preamble of patent claim 1.

State of the art

Such piston accumulators are already known from the prior art. In the pressure chambers pistons are moved, which are guided through the housing. The pistons are moved against the pressure of gases.

In the pressure chambers of these piston accumulator gases are often added under very high internal pressure. The housing of this piston accumulator must therefore have a relatively high rigidity, so that a widening derer diameter is avoided due to high internal pressures.

If there is a widening of the diameter, a piston seal can no longer develop its effect optimally. Furthermore, the guidance of the piston within the housing can no longer be guaranteed.

The rigidity of the housing is determined primarily by the wall thickness and the modulus of elasticity of the material from which the housing is made.

When designing the piston accumulators described here, one is often forced to either form higher wall thicknesses than would be required for sufficient strength, or else to use materials with a high modulus of elasticity. Both technological ways lead to increased costs and increased weight.

From the US 2,742,929 A . US 2,734,531 A and the US 2,417,873 A as well as the textbook " Introduction to Oil Hydraulics "(Vieweg + Teubner Verlag 1984 ) are also piston accumulator or pressure accumulator known.

US-2012/0273076-A1 shows another accumulator.

Individual components, namely housings and bushings, must be centered and supported relative to each other with heavy end pieces. This pressure accumulators can not be easily built.

Materials with very different expansion behavior, thermal and pressure-related, can not be used in the known pressure accumulators, as these otherwise remain tight, internal stresses are too large or certain components must be stiffer and thus designed to be heavier. In the existing pressure accumulators, the bushing must be supported at both ends due to external accelerations, especially in vehicles. As a result, the entire system is braced with different expansion of the individual components.

In the US 2,417,873 A Although a liner is attached only on one side, but has distributed around the circumference rigid support rings. These must be with appropriate Be equipped with holes so that the gas can reach the entire outer circumference of the liner. With appropriate expansion by pressure and temperature of the housing, the support effect of the support rings is lost.

Pressure accumulators made of CFRP (carbon fiber reinforced) and / or GRP (glass fiber reinforced) materials are known from the literature. These have a matrix, namely a binding system made of epoxy resins.

However, there are already known thermoplastics for this purpose. However, these have a brittle behavior, which can quickly become the cause of a danger to life and the environment in an accident, since high pressure can no longer be maintained. To reduce this risk reasonably, usually very expensive safety devices for the accumulator are necessary.

From the pamphlets US 2,742,929 A . US 2,734,531 A and US 2,417,873 A It can be seen that the connection of components usually takes place by screwing or welding. When welding, two components must be made of the same base material. When screwing two components must have corresponding screw strength.

In addition, other components, namely screws, in particular required and corresponding wall thicknesses for the thread. These structural measures make a pressure accumulator not easy, but relatively heavy.

Presentation of the invention

The invention is therefore an object of the invention to provide a piston accumulator, in which a good seal and leadership of the piston is ensured, even if the diameter of the housing a Expands expansion, the strength, the weight and the cost of the piston accumulator are optimized as possible.

The present invention achieves the aforementioned object by the features of patent claim 1.

The bushing is resiliently and / or elastically supported against the housing. Thus, expansions or deformations of the housing can be easily absorbed without disturbing the liner in their function.

The bush could be resiliently and / or elastically supported against the housing by supporting lamellae and / or at least one lamella component and / or at least one support element and / or at least one ring element. Against this background, the bush could be supported against the housing by support plates and / or at least one, in particular separate, lamellar component. Through the support slats, the liner can be stored very safely. The support lamellae compensate for the different expansion of the components bushing and housing and always support the liner well.

The support slats no longer require a second connection of the bushing. Due to the support slats, the only connection can be made very simple. Due to the support slats, the liner can be designed much thinner than before. Due to the support slats, the bushing only are still tuned to the piston and the media and no longer on the strength and rigidity of the entire pressure or piston accumulator.

In addition, the support slats take over the storage of the bushing in the housing. As a result, a relatively simple technique for connecting the two components housing and bushing can be used.

A connection, which takes into account a recording of the loads, which are due to the weight of the bushing with piston and oil and the acceleration of these components, can be designed structurally relatively simple.

A connection can then be made, for example by the EMPT method, which from the WO 2013/071985 A1 has become known for hydraulic accumulator.

Furthermore, a separate component, namely a lamellar component, with a corresponding support structure along the central axis between bushing and housing can be imagined. The support structure may also have support slats, as described here and in the figures.

The support slats may be parallel, helical, wave-like, zigzag-shaped and squarely aligned with the major axes of the components.

Moreover, the support blades may be broken or interrupted at different areas to ensure even distribution of the fluid.

Also, a reinforced arrangement of support plates in the lower region for better absorption of the weight of the liner with oil and piston contained therein is conceivable.

Due to the good storage of the liner only the wall thickness must be matched to the leadership of the piston and separation of two fluids. As a result, wall thicknesses less than or equal to 4 mm can be realized.

The support slats and / or the lamellar component and / or the support element and / or the ring element could be formed on the bushing and / or on the housing. The support plates could be formed on the bushing and / or on the housing. The housing could have on its inner wall corresponding support plates. These support plates are designed resiliently and so can very well compensate for various conditions caused by pressure and temperature expansions of the housing relative to the liner.

An embodiment in which the support plates are attached to the outer surface of the liner is conceivable.

Moreover, a piston accumulator or pressure accumulator is conceivable, are united in the bush, housing and support plates in one component.

The housing could be fiber-reinforced and / or have a fiber reinforcement in the form of a winding. As a result, the piston accumulator or accumulator described here is constructed safer than known. This is achieved by using a matrix of elastomer during the winding of the pressure accumulator with CFRP or GFRP. Such a matrix of elastomer has a much better behavior in external hazards, such as accidents, since there is no risk of splintering of a shell here.

In addition, studies have shown that a matrix of elastomer has a better gas-tightness behavior than a purely thermoplastic or thermoset matrix.

A matrix of elastomeric materials such as CR, NBR, EPDM or even thermoplastic elastomers such as TPE, TPV could be used.

Due to the use of very different materials in pressure accumulators, pressure and temperature lead to very different changes in the length of the components. This occurs in particular in the longitudinal direction of the pressure accumulator. This is countered by the principle of fixed bearings at one end and loose bearings at the opposite end. The fixed bearing site may be manufactured by, for example, an EMPT method as mentioned above. In the floating bearing, the liner is only on multiple support points, but can still move in the longitudinal direction. The support points can attack both inside and outside of the liner.

Support slats could also be arranged only on a section between the bushing and the housing.

Against this background, it is conceivable to effect a bearing of the bushing by supporting lamellae, supporting elements, ring elements or supporting knobs. The bushing could therefore be resiliently and / or elastically supported against the housing by support lamellae and / or at least one lamella component and / or at least one support element and / or at least one ring element.

Instead of supporting slats and ring elements could be used to form a support function. The ring elements can be configured wave-shaped or zigzag-shaped. These can be arranged over the entire length of the liner or only in strategic places.

A bearing of the bushing could also be done by supporting knobs, in particular by elastic support knobs. The support nubs could be attached to the inside or inside wall of the housing. The support knobs could be arranged like a loose bearing only at one end of the housing. A ring element could also have support nubs.

The piston accumulator described here can be used in all vehicles where light piston accumulators are required (OEM, Tier 1 and Tier 2 and Aerospace). The piston accumulator could be used for commercial vehicles, for passenger cars or for airplanes.

Brief description of the drawing

Fig. 1

eine Schnittzeichnung eines Kolbenspeichers mit einem Gehäuse, welches einen Druckraum begrenzt, wobei innerhalb des Druckraums eine druckentlastete Laufbuchse aufgenommen ist, welche den Kolben führt,

Fig. 2

eine Schnittzeichnung eines Kolbenspeichers mit einem Gehäuse, bei dem das innerhalb des Druckraums befindliche, kompressible und gasförmige Fluid die Innenwand des Gehäuses nicht berührt,

Fig. 3

eine Schnittzeichnung eines Kolbenspeichers mit einem Gehäuse, welches zwei Druckräume umschließt, wobei in jedem der beiden Druckräume jeweils ein differenzdruckabhängig in axialer Richtung verfahrbarer Kolben angeordnet ist,

Fig. 4

eine schematische Schnittansicht von Stützlamellen am Gehäuse, wobei die Laufbuchse und das Gehäuse getrennte Bauteile sind und aus unterschiedlichen Werkstoffen bestehen können,

Fig. 5

eine schematische Schnittansicht von Stützlamellen an der Laufbuchse, wobei die Laufbuchse und das Gehäuse getrennte Bauteile sind und aus unterschiedlichen Werkstoffen bestehen können,

Fig. 6

eine schematische Schnittansicht von Stützlamellen an der Laufbuchse und am Gehäuse, wobei diese einstückig als ein Bauteil ausgebildet sind,

Fig. 7

eine schematische Schnittansicht von Stützlamellen, die an einem separaten Lamellenbauteil angeordnet sind, wobei die Werkstoffe für die drei Bauteile Laufbuchse, Gehäuse und Lamellenbauteil entsprechend ihren Aufgaben ausgewählt sind, wobei die Laufbuchse eine gute Gasdichtheit, gute Ölbeständigkeit und hohe Oberflächengüte für die Führung eines Kolbens zeigt, wobei das Gehäuse eine gute Gasdichtheit, gute Druckbeständigkeit und eine gute Verbindung mit Bewicklung aufweist und wobei das Lamellenbauteil eine gute Stützwirkung, einen guten Toleranzausgleich und ein geringes Gewicht zeigt,

Fig. 8

eine schematische Schnittansicht einer Stützlamelle, die als Schräglamelle ausgestaltet ist,

Fig. 9

eine schematische Schnittansicht einer Stützlamelle, die als Schlangenlamelle ausgestaltet ist,

Fig. 10

eine schematische Schnittansicht einer Stützlamelle, die als V-Lamelle ausgestaltet ist,

Fig. 11

eine schematische Schnittansicht einer Stützlamelle, die als Sichel-Lamelle ausgestaltet ist,

Fig. 12

eine schematische Schnittansicht einer Stützlamellenanordnung an der Laufbuchse, wobei die Stützlamellen symmetrisch am Umfang verteilt sind,

Fig. 13

eine schematische Schnittansicht einer Stützlamellenanordnung an der Laufbuchse, wobei die Stützlamellen verstärkt im unteren Bereich verteilt sind,

Fig. 14

eine Stützlamellenanordnung an der Laufbuchse in einer Längsschnittdarstellung, wobei die Stützlamellen linear längs der Mittelachse angeordnet sind,

Fig. 15

eine Stützlamellenanordnung an der Laufbuchse in einer Längsschnittdarstellung, wobei die Stützlamellen wellenförmig längs der Mittelachse angeordnet sind,

Fig. 16

eine Stützlamellenanordnung an der Laufbuchse in einer Längsschnittdarstellung, wobei die Stützlamellen zick-zack-förmig längs der Mittelachse angeordnet sind,

Fig. 17

eine Stützlamellenanordnung an der Laufbuchse in einer Längsschnittdarstellung, wobei die Stützlamellen spiralförmig längs der Mittelachse angeordnet sind,

Fig. 18

eine Stützlamellenanordnung an der Laufbuchse in einer Längsschnittdarstellung, wobei die Stützlamellen rechtwinklig zur Mittelachse mit Unterbrechungen, insbesondere Bohrungen, angeordnet sind,

Fig. 19

eine Schnittansicht eines bewickelten Kolbenspeichers mit einseitiger und einfacher Anbindung einer dünnen Laufbuchse, wobei zwischen Laufbuchse und Gehäuse Raum für Stützelemente ist,

Fig. 20

eine Schnittansicht eines separaten Lamellenbauteils, bei welchem die Stützlamellen wellenförmig ausgebildet sind, wobei das Lamellenbauteil in Form eines Wellenrohrs ausgestaltet ist,

Fig. 21

eine Schnittansicht eines separaten Lamellenbauteils, bei welchem die Stützlamellen zick-zack-förmig ausgebildet sind,

Fig. 22

eine Schnittansicht eines Kolbenspeichers, bei welchem mehrere Stützelemente nur an strategischen Stellen zum Tragen kommen und eingebaut sind,

Fig. 23

eine schematische Ansicht einer Fest- / Los-Lagerung der Laufbuchse,

Fig. 24

zeigt ein Ringelement aus Elastomer, welches unterschiedliche Ausdehnungen ausgleichen soll,

Fig. 25

zeigt schematisch eine elastische Lagerung, welche hier außen dargestellt, aber auch innen möglich ist, wobei die Laufbuchse an einem Los-Lager elastisch gelagert ist,

Fig. 26

ein Ringelement mit Stütznoppen, und

Fig. 27

einen Kolbenspeicher, bei welchem die Stütznoppen am Gehäuse angeordnet sind.

In the drawing show

Fig. 1

a sectional view of a piston accumulator with a housing which defines a pressure chamber, wherein within the pressure chamber, a pressure-relieved bushing is received, which guides the piston,

Fig. 2

a sectional view of a piston accumulator with a housing in which the located within the pressure chamber, compressible and gaseous fluid does not touch the inner wall of the housing,

Fig. 3

a sectional view of a piston accumulator with a housing which encloses two pressure chambers, wherein in each of the two pressure chambers in each case a differential pressure-dependent movable in the axial direction piston is arranged,

Fig. 4

a schematic sectional view of supporting blades on the housing, wherein the bushing and the housing are separate components and may consist of different materials,

Fig. 5

a schematic sectional view of support plates on the liner, wherein the liner and the housing are separate components and may consist of different materials,

Fig. 6

a schematic sectional view of support plates on the bushing and the housing, which are integrally formed as a component,

Fig. 7

a schematic sectional view of support plates, which are arranged on a separate plate member, wherein the materials for the three components sleeve, housing and fin component according to their tasks are selected, the liner shows good gas tightness, good oil resistance and high surface quality for the guidance of a piston wherein the housing has a good gas tightness, good pressure resistance and a good connection with winding and wherein the lamellar component shows a good support effect, a good tolerance compensation and a low weight,

Fig. 8

a schematic sectional view of a support plate, which is designed as a tilted blade,

Fig. 9

a schematic sectional view of a support plate, which is designed as a serpent lamella,

Fig. 10

a schematic sectional view of a support plate, which is designed as a V-blade,

Fig. 11

a schematic sectional view of a support plate, which is designed as a sickle blade,

Fig. 12

a schematic sectional view of a support plate assembly on the liner, wherein the support plates are distributed symmetrically on the circumference,

Fig. 13

a schematic sectional view of a support plate assembly on the liner, the support plates are increasingly distributed in the lower region,

Fig. 14

a support blade assembly on the liner in a longitudinal sectional view, wherein the support blades are arranged linearly along the central axis,

Fig. 15

a support blade assembly on the bushing in a longitudinal sectional view, wherein the support blades are arranged undulating along the central axis,

Fig. 16

a support plate assembly on the bushing in a longitudinal sectional view, wherein the support plates are arranged in a zigzag shape along the central axis,

Fig. 17

a support slat arrangement on the bushing in a longitudinal sectional view, wherein the support slats are arranged spirally along the central axis,

Fig. 18

a support plate assembly on the liner in a longitudinal sectional view, wherein the support plates are arranged at right angles to the central axis with interruptions, in particular holes,

Fig. 19

a sectional view of a wound piston accumulator with one-sided and simple connection of a thin bushing, wherein between bushing and housing space for support elements,

Fig. 20

FIG. 2 a sectional view of a separate lamellar component, in which the support lamellae are of wave-shaped design, wherein the lamellar component is designed in the form of a wave tube, FIG.

Fig. 21

3 a sectional view of a separate lamella component, in which the support lamellae are formed in a zig-zag shape,

Fig. 22

a sectional view of a piston accumulator, in which a plurality of support elements come only in strategic locations to bear and are installed,

Fig. 23

a schematic view of a fixed / lot storage of the liner,

Fig. 24

shows a ring element made of elastomer, which should compensate for different expansions,

Fig. 25

schematically shows an elastic bearing, which is shown here outside, but also inside possible, wherein the bush is mounted elastically on a loose bearing,

Fig. 26

a ring element with supporting knobs, and

Fig. 27

a piston accumulator, wherein the support knobs are arranged on the housing.

Embodiment of the invention

Fig.1 shows a sectional view of a piston accumulator, comprising a housing 1, which defines a pressure chamber 2 and a movable piston 3 receives, wherein in the pressure chamber 2, a compressible fluid is received, wherein the piston 3 has a housing side 4, which faces the pressure chamber 2 and wherein the piston 3 has a working side 5, which is zuwendbar a working fluid, which can move the piston 3. It is provided a bushing 6, within which the piston 3 is movable. The bush 6 guides the piston 3.

The compressible fluid is a gas. The housing 1 has a connection opening 11, so that working fluid can penetrate into the housing 1 and move the piston 3. The pressure chamber 2 is bounded by the bushing 6, the piston 3 and the housing 1 and includes a variable volume.

The bushing 6 is completely received within the housing 1. The bushing 6 is formed as a cylindrical tube.

The bushing 6 has an outer surface 7 and an inner surface 8, both surfaces 7, 8 being in contact with or being pressurized by the compressible fluid.

The size of the inner surface 8, which is in contact with the compressible fluid, depends on the displacement position of the piston 3. The size of the inner surface 8, which is in contact with the working fluid, also depends on the displacement position of the piston 3. The further the piston 3 is forced back from the working fluid into the housing 1, the more inner surface 8 is in contact with the working fluid. The piston 3 slides on the inner surface 8 and is guided by the bushing 6.

The bushing 6 and the housing 1 are arranged concentrically. The bush 6 is made of a metal, namely steel. The housing 1 consists of a fiber-reinforced plastic. The plastic may for example be carbon fiber reinforced or glass fiber reinforced. In addition, on the inside of the housing, a gas-impermeable device, such as a gas-tight, a liner or a coating is attached.

On the piston 3, two guide rings 9 are arranged axially between which a sealing ring 10 is located. The piston 3 is convex on its working side 5 and concave on its housing side 4. The piston 3 is U-shaped in cross section.

The housing 1 and the bush 6 are arranged concentrically with each other. The outer surface 7 of the bushing 6 is completely surrounded by gas. The inner surface 8 is dependent on the position of the Piston 3 with gas or liquid acted upon. The inner surface 8 is acted upon in dependence on the position of the piston 3 more with gas or more with liquid.

In Fig. 2 is a sectional view of a second embodiment of a piston accumulator shown with a housing 1, in which the compressible and gaseous fluid located in the pressure chamber 2, the inner wall of the housing 1 is not directly touched.

The bushing 6 is cup-shaped and closed on the housing side 4 of the piston 3 facing end side by a bottom, which forms part of the housing 1 and is formed on the side facing the pressure chamber 2 gas-impermeable.

This can be done by a gas impermeable device, such as a gas sealer, a liner or a coating.

The bushing 6 consists in the embodiment shown of a metallic material and is therefore completely gas-impermeable. By such an embodiment of the bushing 6, the housing 1 does not need to be formed also gas-impermeable. Because the compressible fluid can not practically escape from the pressure chamber 2, the piston accumulator has consistently good service properties during a long service life.

The bush 6 has an outer surface 7 and an inner surface 8, with only the inner surface 8 is in contact with the compressible and gaseous fluid from the pressure chamber 2 and is pressurized by this.

The outer surface 7 is pressurizable with the working fluid, which is formed here by an oil. In the embodiment shown, no point on the inside or inside wall of the housing 1 with compressible and gaseous fluid from the pressure chamber 2 in contact.

In Fig. 3 is a sectional view of a third embodiment of a piston accumulator with a housing 1 is shown, which encloses two pressure chambers 2, wherein in each of the two pressure chambers 2 each a differential pressure-dependent movable in the axial direction of the piston 3 is arranged.

As a result, if necessary, each individual piston 3 can be selectively activated and used.

The 4 to 18 show that the bushing 6 is resiliently and elastically supported against the housing 1 by support plates 12. The support plates 12 may be formed on the bushing 6 and / or on the housing 1.

The support blades 12 make an angle with the central axis 14 of the bushing 6 or are inclined to this in another way. This results in a resilient and / or elastic support of the bushing 6 against the housing 1, when this expands or contracts.

Fig. 4 shows a schematic sectional view of support plates 12 on the housing 1, wherein the bushing 6 and the housing 1 are separate components and made of different materials.

Fig. 5 shows a schematic sectional view of support plates 12 on the bushing 6, wherein the bushing 6 and the housing 1 are separate components and made of different materials.

Fig. 6 shows a schematic sectional view of support plates 12 on the bushing 6 and the housing 1, wherein these are integrally formed as a component.

Fig. 7 shows a schematic sectional view of support plates 12 which are arranged on a separate plate member 13, wherein the materials for the three components sleeve 6, housing 1 and fin component 13 are selected according to their tasks, wherein the liner 6 has a good gas tightness, good oil resistance and high Surface quality for the guidance of a piston 3 shows, wherein the housing 1 has a good gas tightness, good pressure resistance and a good connection with winding and wherein the lamellar component 13 shows a good support effect, a good tolerance compensation and a low weight.

Fig. 8 shows a schematic sectional view of a support plate 12, which is designed as a tilted blade.

Fig. 9 shows a schematic sectional view of a support plate 12, which is designed as a serpentine lamella.

Fig. 10 shows a schematic sectional view of a support plate 12, which is designed as a V-blade.

Fig. 11 shows a schematic sectional view of a support plate 12, which is designed as a sickle blade.

Fig. 12 shows a schematic sectional view of a support plate assembly on the bushing 6, wherein the support plates 12 are distributed symmetrically around the circumference.

Fig. 13 shows a schematic sectional view of a support plate assembly on the bushing 6, wherein the support plates 12 are more distributed in the lower region.

Fig. 14 shows a support blade assembly on the bushing 6 in a longitudinal sectional view, wherein the support plates 12 are arranged linearly along the central axis 14.

Fig. 15 shows a support plate assembly on the bushing 6 in a longitudinal sectional view, wherein the support plates 12 are arranged wave-shaped along the central axis 14.

Fig. 16 shows a support blade assembly on the bushing 6 in a longitudinal sectional view, wherein the support plates 12 are arranged in a zigzag shape along the central axis 14,

Fig. 17 shows a support blade assembly on the bushing 6 in a longitudinal sectional view, wherein the support plates 12 are arranged spirally along the central axis 14.

Fig. 18 shows a support plate assembly on the bushing 6 in a longitudinal sectional view, wherein the support plates 12 at right angles to the central axis 14 with interruptions, in particular holes, are arranged.

Fig. 19 shows a sectional view of a wound piston accumulator with one-sided and simple connection of a thin bushing 6. The housing 1 is formed fiber-reinforced and has a fiber reinforcement in the form of a winding.

The Fig. 20 and 21 each show a separate fin component 13, through which the bushing 6 can be supported against the housing 1. Thus, a piston accumulator can be created in which the bushing 6 is resiliently and / or elastically supported against the housing 1 by at least one lamella component 13.

Fig. 20 shows a sectional view of a separate fin component 13, wherein the support plates 12 are formed wave-shaped.

Fig. 21 shows a sectional view of a separate fin component 13, wherein the support plates 12 are formed zigzag-shaped.

Fig. 22 shows a piston accumulator, in which several, here two concrete, supporting elements 13a come only at strategic points to bear and are installed. In this piston accumulator, the bushing 6 is resiliently and / or elastically supported against the housing 1 by at least one support element 13a.

Fig. 23 shows a schematic view of a fixed / loose bearing of the bushing. 6

Fig. 24 shows a ring member 13b made of elastomer, which should compensate for different expansions. Thus, a piston accumulator can be created in which the bushing 6 is resiliently and / or elastically supported against the housing 1 by at least one ring element 13b.

Fig. 25 schematically shows an elastic bearing, which is shown here outside, but also inside possible, wherein the bushing 6 is elastically mounted on a loose bearing.

Fig. 26 shows a ring member 13b with support studs 15. Thus, a piston accumulator can be created in which the bush 6 is resiliently and / or elastically supported against the housing 1 by at least one ring member 13b, wherein the ring member 13b has support knobs 15 made of elastomer.

Fig. 27 shows a piston accumulator, in which support nubs 15 are arranged on the housing 1.

Claims (10)

1. Piston accumulator, comprising a housing (1) which delimits a pressure chamber (2) and receives a displaceable piston (3), wherein compressible fluid is received in the pressure chamber (2), wherein the piston (3) has a housing side (4) which faces the pressure chamber (2), and wherein the piston (3) has an operating side (5) which is capable of facing an operating fluid which can move the piston (3), wherein a cylinder liner (6) within which the piston (3) is displaceable is provided, characterized in that the cylinder liner (6) is supported in a resilient and/or elastic manner in relation to the housing (1).
2. Piston accumulator according to Claim 1, characterized in that the cylinder liner (6) is supported in a resilient and/or elastic manner in relation to the housing (1) by way of support fins (12) .
3. Piston accumulator according to Claim 2, characterized in that the support fins (12) are configured on the cylinder liner (6).
4. Piston accumulator according to Claim 2, characterized in that the support fins (12) are configured on the housing (1).
5. Piston accumulator according to Claim 1, characterized in that the cylinder liner (6) is supported in a resilient and/or elastic manner in relation to a housing (1) by at least one fin component (13).
6. Piston accumulator according to Claim 5, characterized in that the fin component (13) is configured on the cylinder liner (6).
7. Piston accumulator according to Claim 5, characterized in that the fin component (13) is configured on the housing (1).
8. Piston accumulator according to Claim 1, characterized in that the cylinder liner (6) is supported in a resilient and/or elastic manner in relation to the housing (1) by at least one ring element (13b).
9. Piston accumulator according to Claim 8, characterized in that the ring element (13b) is configured on the cylinder liner (6).
10. Piston accumulator according to Claim 8, characterized in that the ring element (13b) is configured on the housing (1).

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