EP2470796B1 - Verbundkolbenspeicher - Google Patents

Verbundkolbenspeicher Download PDF

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Publication number
EP2470796B1
EP2470796B1 EP10745644.4A EP10745644A EP2470796B1 EP 2470796 B1 EP2470796 B1 EP 2470796B1 EP 10745644 A EP10745644 A EP 10745644A EP 2470796 B1 EP2470796 B1 EP 2470796B1
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EP
European Patent Office
Prior art keywords
piston
accumulator
wall
concavity
wall part
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10745644.4A
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English (en)
French (fr)
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EP2470796A1 (de
Inventor
Ezzeddin Belhaj
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Parker Hannifin Manufacturing France SAS
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Parker Hannifin Manufacturing France SAS
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Publication of EP2470796A1 publication Critical patent/EP2470796A1/de
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Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F15B1/24—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with rigid separating means, e.g. pistons

Definitions

  • the present invention relates to hydropneumatic accumulators. More specifically, the invention relates to accumulators for storage and delivery of hydraulic energy, i.e. storage and delivery of pressurized fluids.
  • the accumulators of the invention are useful for a number of industries and purposes.
  • accumulators particularly piston accumulators
  • metal is a very reliable construction material having well known properties, such as limited elongation due to a high modulus of elasticity.
  • hoop stress in a pressure container may even for moderate pressures require a large wall thickness in order to maintain the integrity and avoid leakage over the piston.
  • the weight of metal accumulators becomes high, limiting the utilization in several fields and industries, like aircraft, defense, wind energy, oil and gas and sporting goods.
  • a lightweight low permeation piston-in-sleeve accumulator comprising a lightweight composite cylindrical outer pressure vessel with rounded ends, with or without a liner inside the composite cylindrical outer pressure vessel, a closeable port positioned within one end of the vessel body, a cylindrical nonpermeable sleeve, and a piston slidably disposed within said sleeve. No end caps are described or illustrated.
  • the piston has concavity on only one side.
  • the objective of the present invention is to provide composite accumulators reducing or eliminating the above-mention problems.
  • the invention provides an accumulator for storage and delivery of hydraulic energy, comprising a cylindrical accumulator chamber inside a wall part and one or two end sections, a piston arranged in the accumulator chamber and at least one seal arranged between the piston and wall part, the piston with seal has dimension to fit into the accumulator chamber dividing the accumulator chamber into two parts, the wall part is made of composite material.
  • the accumulator is distinctive in that the piston has concave end surfaces facing each respective accumulator chamber part, the shape of the concavity and the material properties of the piston are adapted such that the piston expands similarly as the wall section as the pressure varies, such that the piston with seal separate the accumulator chamber parts sealingly even though the pressure varies broadly, wherein the radial thickness of the piston Tp near the opening of said concavity and the wall thickness Tw, and the modulus of elasticity of the piston Ep and wall Ew, respectively, are such that Tp / Tw ⁇ Ew / Ep .
  • the operation pressure of the accumulator can be in a range of at least 1-690 bar, more preferably 1-1000 bar, and most preferably 1-2500 bar or even broader for the best embodiments, without leakage. No previously known composite piston accumulators can operate without leakage at comparable pressure ranges.
  • the term that the wall part is made of composite material means that the wall part do not comprise neither a metal matrix nor a metal liner.
  • the wall is preferably made of a polymer matrix with reinforcing fibres such as epoxy with carbon fibres, but the wall may include a gas tight non-metal liner.
  • the composite material matrix can be an epoxy or for example a thermoplastic polymer.
  • the reinforcing fibres are most preferable carbon fibres, but also glass fibres or other fibres can be used, even metal fibres or metal strands.
  • a gas tight seal is preferably arranged on the inner side of the wall, the gas tight seal can be a gas tight polymer such as PE (polyethylene) or a gas tight non-metal composite, such as a Teflon (PTFE) sprayed composite, which are commercially available.
  • the accumulator has a non metal matrix composite wall part, with or without a gas tight non metal liner.
  • the piston is made of composite material, polymer or metal, preferably it is made of composite material or a polymer such as PEEK (polyether ether ketone) PEEK GF (polyetheretherketone glass fibre reinforced) or PEEK CF (polyetheretherketone carbon fibre reinforced).
  • Composite material pistons may preferably comprise a magnet or other means facilitating detection of piston position using sensors, such as Hall effect sensors, from outside the wall.
  • the concavity of the end faces of the piston preferably is in the form of a circle or ellipse section in cross section, or ball or ellipsoid section or similar in three dimensions, the tangent angle or angle of intersection of which exceed 30°, preferably 45°, most preferably 60° from a hypothetical flat bottom of said concave end face.
  • Said angle is preferably 90°, i.e. parallel with the cylinder axis near and at the periphery of the concavity, which is best with respect to said expansion, and facilitates manufacture.
  • the radial thickness of the piston Tp near the opening of said concavity and the wall part thickness Tw, and the modulus of elasticity of the piston material Ep and wall material Ew, respectively are such that (Tp/Tw ⁇ Ew/Ep).
  • the accumulator comprises end sections such as one or two end caps, preferably two, made of composite material, polymer or metallic material, preferably composite material. At least one of the end caps has a feedthrough or opening.
  • the accumulator comprises two threaded end caps, the wall part comprises corresponding threads, either in a composite, polymer or metallic material insert or in the inner wall surface at the ends.
  • the insert if used, preferably has larger outer grooves, threads, pins or canals distributing the shear force over a larger area than the internal threads.
  • the wall section inside either end, preferably comprises rough grooves or threads over a first distance, to which a metal or composite insert or sleeve is arranged, the insert or sleeve has adapted external rough grooves, pins or threads on the outside over said first distance and finer threads is arranged, matching end cap threads, on the inside over a second distance shorter than the first distance.
  • the wall is bonded or wound firmly to the insert or sleeve, if present, for avoiding leakage paths and improving strength, but it can be non-bonded, such as threaded and optionally including seals.
  • the windings or fibres such as carbon fibre windings, are preferably arranged in several angles to provide hoop strength, axial strength and locking of the wall section to the insert.
  • Axial reinforcing fibres are preferably locked to the external rough grooves or threads or pins of the insert by outside hoop fibres.
  • a seal is preferably arranged to seal between the gas tight liner and the end cap, thereby reducing the number of leakage paths.
  • the gas tight liner preferably extends onto the inner surface of the insert and the end cap preferably has a concave inner side extending over the seal and liner.
  • Such embodiment will in general be the most preferred embodiment, since high pressure and large range of pressure can be handled better, since the seal will be locked harder between the end cap and liner with increasing pressure.
  • the accumulator comprises end caps having a concave surface toward the accumulator chamber, the shape of the concavity and the material properties of the end caps are adapted such that the end cap expands similarly as the wall section as the pressure varies and preferably seals are arranged outside the periphery of the concavity, sealing between the end cap and either the wall part, a gas tight liner or an insert.
  • the concavity preferably is in cross section in the form of a circle or ellipse section, the tangent angle or angle of intersection of which exceed 30°, preferably 45°, most preferably 60° from a hypothetical flat bottom of said end cap face. Said angle is preferably 90°, which is best with respect to said expansion, and facilitates manufacture.
  • the concave piston end faces, and optionally the concave inner end cap faces, provide a hoop stress component resulting in radial expansion or contraction of piston and end caps with varying pressure, respectively, similarly as for the wall of the cylindrical accumulator chamber.
  • Elliptical faces also means superelliptoidic faces, which can be preferable for using less material.
  • the concavity can also be a cylindrical bore in the end faces, preferably with rounded inner corner or edge, leaving a sufficiently thick sleeve-like section on either side of the piston or inner side of the end cap, which represents a preferred embodiment.
  • the material properties and dimensions are chosen so as to balance the deformations in order to avoid gaps for leakage.
  • the surface roughness, on the inner surface of the cylindrical accumulator chamber and the sealing surfaces on the piston and end caps, are preferably 0,4 ⁇ m or finer, as measured according to DIN EN ISO 4287.
  • FIG. 1 illustrating an accumulator 8 of the invention.
  • the accumulator 8 comprises a cylindrical accumulator chamber inside a composite wall part 3 and one or two end sections 1, a piston 4 arranged in the accumulator chamber and at least one seal 6,7 arranged between the piston 4 and wall part 3, the piston 4 with seal 6,7 has dimension to fit into the accumulator chamber dividing the accumulator chamber into two parts C1 and C2, respectively.
  • the piston 4 has concave end surfaces 4a, 4b facing each respective accumulator chamber part.
  • Item 5 is a guide ring
  • seal 6 is a primary seal whilst seal 7 is a secondary seal.
  • Item 2 is an insert or sleeve or end ring with two relatively large grooves toward the wall section in order to distribute the shear stress to a larger area.
  • the piston 4 is made of composite.
  • end caps 1 and insert 2 are made of stainless steel, however in other preferable embodiments one or both of said items can be made of composite material or polymer, which reduce the weight further. End caps and inserts can alternatively be made in titanium or aluminium.
  • the wall part 3 as illustrated is made of composite material with epoxy matrix and reinforcing carbon fibres wound in order to increase hoop stress strength.
  • FIG. 2 illustrating an embodiment of a carbon fibre composite piston 4, according to the invention, for use in an accumulator of the invention.
  • a similar design can preferably also be used for end caps.
  • Pistons and end caps having concave surfaces facing the accumulator chamber, and shape of the concavity and material properties adapted such that the piston or end cap expands similarly as the wall section as the pressure varies in a range of 1 - 690 bar or wider, are embodiments of the invention.
  • the piston illustrated in Fig. 2 includes a magnet 9 for easier detection of piston position from outside the wall part. The magnet could alternatively be arranged around the periphery if the piston.
  • FIG 3 is a sketch and in part longitudinal section of another accumulator 8 according to the present invention.
  • the piston 4 is similar as for the embodiment illustrated in Fig.1 , but the end caps 1 have concave inner faces, a gas tight liner 10 is arranged inside a cylindrical composite wall part 3 and the liner 10 extends into the space between an insert 2 and the end cap on either side. In each of said spaces, a seal 11 is arranged. Pressure in the accumulator chambers C1 and C2 will due to the concavity provide a radial pressure component on the end caps 1 and piston 4, which radial pressure component increases with pressure and improves the sealing properties at increasing pressure. If the composite wall section is sufficiently gas tight, the gas tight liner can be omitted and the seals can be arranged between the end cap and either the composite wall or an insert.
  • the composite material, how it is arranged and how the parts of the accumulator are manufactured can be varied broadly, using good engineering practice. Further information can be found in reference textbooks such as: Graphite/Epoxy: Daniel, I.M., and Ori, I., Engineering Mechanics of Composite Materials, Oxford University Press, 1994 , and Carbon/Epoxy: Barbero, E.J., Introduction to Composite Materials Design, Taylor and Francis, 1999 .
  • the weight is 0,15 that of a corresponding carbon steel wall part and also 0,15 that of a corresponding stainless steel wall part.
  • the accumulator weight can be reduced to about 0,15 that of a corresponding steel accumulator.
  • the accumulator of the invention is also very favourable over aluminium accumulators, as the specific strength (S u / ⁇ , that is ultimate tensile strength / density) of carbon fibre composites is about ten times higher and the specific stiffness (E/ ⁇ , that is modulus of elasticity / density) is about three times higher than for aluminium, respectively. Corresponding values for specific strength and specific stiffness for graphite composites compared to aluminium are about 3,2 and 7, respectively.
  • the accumulators of the invention may comprise any features as illustrated or described in any operative combination, which combinations are embodiments of the invention.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Claims (8)

  1. Speicher (8) zum Speichern und Liefern von hydraulischer Energie, umfassend eine zylindrische Speicherkammer innerhalb eines Wandteils (3) und ein oder zwei Endabschnitte (1), einen Kolben (4), welcher in der Speicherkammer angeordnet ist, und zumindest eine Dichtung (6, 7), welche zwischen dem Kolben (4) und dem Wandteil (3) angeordnet ist, wobei der Kolben (4) mit der Dichtung (6, 7) eine Dimension aufweist, um in die Speicherkammer zu passen, wobei er die Speicherkammer in zwei Teile (C1, C2) teilt, wobei das Wandteil (3) aus einem Kompositmaterial hergestellt ist, dadurch gekennzeichnet, dass der Kolben (4) konkave Endoberflächen (4a, 4b) aufweist, welche jeweils dem entsprechenden Speicherkammerteil (C1, C2) zugewandt sind, wobei die Form der Konkavität und die Materialeigenschaften des Kolbens (4) so angepasst sind, dass der Kolben (4) sich ähnlich wie der Wandabschnitt (3) ausdehnt, wenn der Druck sich ändert, so dass der Kolben (4) mit der Dichtung (6, 7) die Speicherkammerteile (C1, C2) dichtend trennt, auch wenn der Druck deutlich variiert, wobei die radiale Dicke des Kolbens Tp nahe der Öffnung der Konkavität und die Wandteildicke Tw, und der Elastizitätsmodul des Kolbenmaterials Ep und des Wandmaterials Ew jeweils so sind, dass (Tp/Tw ≤ Ew/Ep).
  2. Speicher nach Anspruch 1, dadurch gekennzeichnet, dass der Kolben aus einem Komposit- oder Polymermaterial hergestellt ist.
  3. Speicher nach Anspruch 1, dadurch gekennzeichnet, dass die Konkavität der Endflächen des Kolbens in der Form eines Kreises oder eines Ellipsenabschnitts, oder eines Ball- oder Ellipsoidabschnitts ist, wobei dessen Tangentenwinkel oder Schnittwinkel von einem hypothetisch flachen Boden der konkaven Endfläche 30° übersteigt.
  4. Speicher nach Anspruch 1, dadurch gekennzeichnet, dass der Speicher zwei Endabschnitte in Form von Endkappen aufweist, welche aus einem Kompositmaterial oder metallischen Material, wie Edelstahl, hergestellt sind, wobei vorzugsweise jede der Endkappen eine Durchgangsöffnung für ein Fluid aufweist, wobei vorzugsweise jede der Endkappen mit einem Gewinde versehen ist und das Wandteil korrespondierende Gewinde entweder in einem Einsatz oder in der inneren Wandoberflächen an den Enden umfasst.
  5. Speicher nach Anspruch 1, dadurch gekennzeichnet, dass der Wandabschnitt, innerhalb jeden Endes, raue Rillen oder Gewinde auf der Außenseite über eine erste Strecke aufweist, zu welcher ein Metall- oder Kompositeinsatz oder -Hülse angeordnet ist, wobei der Einsatz oder die Hülse angepasste raue Rillen oder Gewinde auf der Außenseite über die erste Strecke hat, und zu den Endkappengewinden passend feine Gewinde auf einer Innenseite über eine zweite Strecke angeordnet sind, welcher kürzer als die erste Strecke ist.
  6. Speicher nach Anspruch 1, dadurch gekennzeichnet, dass der Speicher Endkappen mit einer konkaven Oberfläche gegen die Speicherkammer umfasst, wobei die Form der Konkavität und die Materialeigenschaften der Endkappen so angepasst sind, dass die Endkappen sich ähnlich wie der Wandabschnitt ausdehnen, wenn sich der Druck verändert, und vorzugsweise Dichtungen außerhalb eines Umfangs der Konkavität angeordnet sind, welche zwischen der Endkappe und entweder dem Wandteil, einem gasdichten Liner oder einem Einsatz dichten.
  7. Speicher nach Anspruch 6, dadurch gekennzeichnet, dass die Konkavität im Querschnitt in der Form eines Kreis oder Ellipsenabschnitts ist, wobei dessen Tangentenwinkel oder ein Schnittwinkel von einer hypothetisch flachen Bodenfläche der konkaven Endkappenfläche 30° übersteigt.
  8. Speicher nach Anspruch 1, dadurch gekennzeichnet, dass der Kolben einen Magneten oder andere Mittel umfasst, welche ein Erkennen der Kolbenposition durch Verwenden von Sensoren, wie einem Halleffektsensor, von einer Außenseite des Wandteils erleichtert.
EP10745644.4A 2009-08-26 2010-08-26 Verbundkolbenspeicher Not-in-force EP2470796B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NO20092896 2009-08-26
PCT/EP2010/062450 WO2011023747A1 (en) 2009-08-26 2010-08-26 Composite piston accumulator

Publications (2)

Publication Number Publication Date
EP2470796A1 EP2470796A1 (de) 2012-07-04
EP2470796B1 true EP2470796B1 (de) 2017-03-22

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EP10745644.4A Not-in-force EP2470796B1 (de) 2009-08-26 2010-08-26 Verbundkolbenspeicher

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WO (1) WO2011023747A1 (de)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD736260S1 (en) 2012-07-03 2015-08-11 Eaton Corporation Composite differential piston
USD735758S1 (en) 2014-10-13 2015-08-04 Eaton Corporation Composite differential plenum
DE102013220093A1 (de) * 2013-10-02 2015-04-02 Robert Bosch Gmbh Kolbenspeicher
DE102013220094A1 (de) * 2013-10-02 2015-04-02 Robert Bosch Gmbh Kolbenspeicher
US9435356B1 (en) 2015-07-13 2016-09-06 Steelhead Composites, Llc. Lightweight piston accumulator
DE102017000362A1 (de) * 2017-01-17 2018-07-19 Liebherr-Components Kirchdorf GmbH Zylinder-Kolben-Vorrichtung mit einem aus einem Faserverbundwerkstoff gefertigtem Zylinder
DE102019124968B3 (de) 2019-09-17 2021-01-21 Audi Ag Gaskolbenspeicher

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2240394A1 (de) * 1972-08-17 1974-02-28 Licentia Gmbh Hydro-pneumatischer kraftspeicher
US20050194054A1 (en) * 2004-03-08 2005-09-08 Moskalik Andrew J. Lightweight low permeation piston-in-sleeve accumulator

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8409493U1 (de) * 1984-11-08 Bolenz & Schäfer Maschinenfabrik Zweigniederlassung der Rexnord GmbH, 3560 Biedenkopf Druckspeicher
BE788031A (fr) * 1971-08-27 1973-02-26 Babcock & Wilcox Co Perfectionnements aux echangeurs de chaleur et a leur fabrication
IT1185613B (it) * 1985-05-30 1987-11-12 Magnaghi Cleodinamica Spa Accumulatore di pressione gas-olio con struttura in materiali compositi per circuiti idraulici di velivoli
DE102004002266A1 (de) * 2004-01-16 2005-08-11 Hydac Technology Gmbh Kolbenspeicher
US8695643B2 (en) * 2007-11-08 2014-04-15 Parker-Hannifin Corporation Lightweight high pressure repairable piston composite accumulator with slip flange
DE102009016570A1 (de) * 2009-04-06 2010-10-07 Robert Bosch Gmbh Kolbenspeicher

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2240394A1 (de) * 1972-08-17 1974-02-28 Licentia Gmbh Hydro-pneumatischer kraftspeicher
US20050194054A1 (en) * 2004-03-08 2005-09-08 Moskalik Andrew J. Lightweight low permeation piston-in-sleeve accumulator

Also Published As

Publication number Publication date
WO2011023747A1 (en) 2011-03-03
EP2470796A1 (de) 2012-07-04

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