EP3067570A1 - Accumulateur à piston - Google Patents

Accumulateur à piston Download PDF

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Publication number
EP3067570A1
EP3067570A1 EP16155949.7A EP16155949A EP3067570A1 EP 3067570 A1 EP3067570 A1 EP 3067570A1 EP 16155949 A EP16155949 A EP 16155949A EP 3067570 A1 EP3067570 A1 EP 3067570A1
Authority
EP
European Patent Office
Prior art keywords
piston
housing
bushing
piston accumulator
accumulator according
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.)
Granted
Application number
EP16155949.7A
Other languages
German (de)
English (en)
Other versions
EP3067570B1 (fr
Inventor
Olaf Nahrwold
Thomas Pippes
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.)
Carl Freudenberg KG
Original Assignee
Carl Freudenberg KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Carl Freudenberg KG filed Critical Carl Freudenberg KG
Publication of EP3067570A1 publication Critical patent/EP3067570A1/fr
Application granted granted Critical
Publication of EP3067570B1 publication Critical patent/EP3067570B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons

Definitions

  • the invention relates to a piston accumulator according to the preamble of patent claim 1.
  • piston accumulators are already known from the prior art.
  • pistons are moved, which are guided through the housing.
  • the pistons are moved against the pressure of gases.
  • 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.
  • 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.
  • thermoplastics for this purpose.
  • 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.
  • high pressure can no longer be maintained.
  • usually very expensive safety devices for the accumulator are necessary.
  • 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 piston is not guided by the housing, but by a bushing.
  • This liner is partially or completely by the pressurized fluids, namely liquids or gases, flows around and / or flows through.
  • the bush is almost not deformed by attacking pressures and is largely depressurized.
  • An expansion of the diameter of the bushing is therefore avoided.
  • the housing at least partially forms a shell for the pressure chamber, the housing may have a lower rigidity than would actually be required for producing a sealing and guiding function for the piston. It is tolerated that the diameter of the housing changes.
  • the housing can therefore be manufactured relatively inexpensively. Also, its wall thickness can be relatively low, and the choice of material is also not severely limited.
  • a piston accumulator is specified, in which a good seal and leadership of the piston is ensured, even if the diameter of the housing undergoes expansion, the strength, the weight and the cost of the piston accumulator are optimized as possible.
  • the liner could be partially or completely received within the housing.
  • the bush does not protrude beyond the outer dimensions of the housing.
  • the housing can be attached to an arrangement such that a working fluid such as a hydraulic fluid can move the piston against the pressure of a gas in the pressure chamber.
  • a working fluid such as a hydraulic fluid can move the piston against the pressure of a gas in the pressure chamber.
  • the liner could have an outer surface and an inner surface, both surfaces in contact with or pressurized by the compressible fluid. As a result, can act on both surfaces equal pressures, so that the liner is partially or completely depressurized. A bending or deformation of the liner is almost impossible. Only the material of which the liner is made must be so stable that it is almost not compressed by the pressure of the compressible fluid.
  • the compressible fluid is preferably a gas which is under pressure.
  • the liner may have an outer surface and an inner surface, wherein only the inner surface is in contact with or pressurized by the compressible fluid and wherein the outer surface is pressurisable with the working fluid.
  • the liner is formed in such a case substantially cup-shaped.
  • the bushing can be completely gas-impermeable.
  • the interior of the liner is bounded by this itself and the piston and thereby closed to the environment.
  • the liner can for example consist of a metallic material.
  • the housing does not necessarily have to be gas-impermeable.
  • the piston accumulator is characterized easy and inexpensive to produce and also has consistently good performance for a long service life.
  • the housing may be equipped on its inside for gaseous media diffusion-tight, for example by a gas-impermeable coating.
  • the size of the inner surface, which is in contact with the compressible fluid, could depend on the displacement position of the piston.
  • a working fluid can penetrate into the housing and push the piston into the housing.
  • a liquid is preferably used.
  • a gas is also conceivable to use as the working fluid.
  • the size of the inner surface, which is in contact with the working fluid, could depend on the displacement position of the piston.
  • the working fluid can relieve pressure on the bushing, namely by pressing this from the inside against the liner and counteracting the pressure of the compressible fluid or the working fluid itself, as in Fig. 2 shown.
  • the pressure of the compressible fluid in the pressure chamber approximately corresponds to the pressure under which the working fluid is.
  • the compressible fluid is preferably a gas.
  • the bushing and housing could be concentric. As a result, a simple production of the piston accumulator is possible.
  • the bushing and housing could not be concentric. This embodiment may be advantageous in certain installation spaces.
  • the liner could have a plastic or consist of a plastic. As a result, a very light piston accumulator can be realized.
  • the plastic is preferably fiber-reinforced, in particular carbon fiber reinforced and / or glass fiber reinforced.
  • the liner could have a metal or consist of a metal.
  • the bushing can withstand even more aggressive media such as machine oils.
  • the metal is preferably a steel.
  • the housing could have a plastic or consist of a plastic.
  • the plastic is preferably fiber-reinforced, in particular carbon fiber reinforced and / or glass fiber reinforced.
  • the housing could comprise a metal or consist of a metal.
  • the housing can thus also withstand more aggressive media, such as machine oils.
  • the metal is preferably aluminum.
  • the bushing and / or the housing may preferably be formed gas-diffusion-tight.
  • the bushing and / or the housing if they are not made of a metallic material, for example by a coating, be specially equipped.
  • a single piston can be selectively activated or used, while a single pressure chamber is provided for a plurality of pistons.
  • a bushing should be securely stored and / or secured in a housing. This is to be realized using very different materials, such as thermoplastics, thermosets, carbon fibers, glass fibers, aluminum and steel.
  • the liner could be resiliently and / or elastically supported against the housing.
  • 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.
  • the bush could be supported against the housing by support plates and / or at least one, in particular separate, lamella 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.
  • the support slats take over the storage of the bushing in the housing.
  • 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.
  • a separate component namely a lamellar component
  • 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.
  • the support blades may be broken or interrupted at different areas to ensure even distribution of the fluid.
  • wall thickness 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.
  • 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.
  • 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.
  • a matrix of elastomeric materials such as CR, NBR, EPDM or even thermoplastic elastomers such as TPE, TPV could be used.
  • Support slats could also be arranged only on a section between the bushing and the housing.
  • 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.
  • 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.
  • 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.
  • a gas-impermeable device such as a gas-tight, a liner or a coating is attached.
  • the piston 3 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.
  • 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 pressure chamber 2 side facing gas-impermeable.
  • 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.
  • the working fluid which is formed here by an oil.
  • Fig. 3 is a sectional view of a third embodiment of a piston accumulator with a housing 1 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.
  • 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.
  • Fig. 20 and 21 each show a separate fin component 13, through which the bushing 6 can be supported against the housing 1.
  • 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.
  • 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.
  • 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.
  • 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.

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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)
EP16155949.7A 2015-03-12 2016-02-16 Accumulateur à piston Active EP3067570B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015003140.6A DE102015003140A1 (de) 2015-03-12 2015-03-12 Kolbenspeicher

Publications (2)

Publication Number Publication Date
EP3067570A1 true EP3067570A1 (fr) 2016-09-14
EP3067570B1 EP3067570B1 (fr) 2019-10-09

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ID=55532099

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16155949.7A Active EP3067570B1 (fr) 2015-03-12 2016-02-16 Accumulateur à piston

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EP (1) EP3067570B1 (fr)
DE (1) DE102015003140A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021052682A1 (fr) * 2019-09-17 2021-03-25 Audi Ag Accumulateur à piston permettant de stocker un fluide, en particulier pour un véhicule à moteur et véhicule à moteur ayant au moins un tel accumulateur à piston

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022000976A1 (de) 2022-03-22 2023-09-28 Hydac Technology Gmbh Kolbenspeicher

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2417873A (en) 1944-05-12 1947-03-25 New York Air Brake Co Accumulator
US2734531A (en) 1956-02-14 Hydraulic accumulators
US2742929A (en) 1953-03-27 1956-04-24 Gen Motors Corp Pressure storage device
FR1135747A (fr) * 1954-10-30 1957-05-03 Perfectionnements aux accumulateurs oléo-pneumatiques
DE3617957A1 (de) * 1985-05-30 1986-12-04 Magnaghi Oleodinamica S.p.A., Mailand/Milano Druckakkumulator
US20120273076A1 (en) * 2011-04-28 2012-11-01 Robert Bosch Gmbh Compact hydraulic accumulator
DE102011106817A1 (de) * 2011-07-07 2013-01-10 Daimler Ag Hydropneumatische Energiespeichervorrichtung mit radial ineinander angeordneten Gasvolumen
WO2013071985A1 (fr) 2011-11-17 2013-05-23 Carl Freudenberg Kg Accumulateur hydraulique
EP2881593A1 (fr) * 2013-11-25 2015-06-10 Carl Freudenberg KG Accumulateur à piston

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB581268A (en) * 1944-08-17 1946-10-07 New York Air Brake Co Improvements in hydraulic accumulators
US2703108A (en) * 1950-12-04 1955-03-01 Tommy J Mccuistion Accumulator
DE3728555A1 (de) * 1987-08-27 1989-03-09 Kloeckner Humboldt Deutz Ag Kolbendruckspeicher fuer hydraulikoel

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2734531A (en) 1956-02-14 Hydraulic accumulators
US2417873A (en) 1944-05-12 1947-03-25 New York Air Brake Co Accumulator
US2742929A (en) 1953-03-27 1956-04-24 Gen Motors Corp Pressure storage device
FR1135747A (fr) * 1954-10-30 1957-05-03 Perfectionnements aux accumulateurs oléo-pneumatiques
DE3617957A1 (de) * 1985-05-30 1986-12-04 Magnaghi Oleodinamica S.p.A., Mailand/Milano Druckakkumulator
US20120273076A1 (en) * 2011-04-28 2012-11-01 Robert Bosch Gmbh Compact hydraulic accumulator
DE102011106817A1 (de) * 2011-07-07 2013-01-10 Daimler Ag Hydropneumatische Energiespeichervorrichtung mit radial ineinander angeordneten Gasvolumen
WO2013071985A1 (fr) 2011-11-17 2013-05-23 Carl Freudenberg Kg Accumulateur hydraulique
EP2881593A1 (fr) * 2013-11-25 2015-06-10 Carl Freudenberg KG Accumulateur à piston

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"Einführung in die Ölhydraulik", 1984, VIEWEG + TEUBNER VERLAG

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021052682A1 (fr) * 2019-09-17 2021-03-25 Audi Ag Accumulateur à piston permettant de stocker un fluide, en particulier pour un véhicule à moteur et véhicule à moteur ayant au moins un tel accumulateur à piston

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DE102015003140A1 (de) 2016-09-15
EP3067570B1 (fr) 2019-10-09

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