EP2580080B1 - Installation hydraulique - Google Patents

Installation hydraulique Download PDF

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Publication number
EP2580080B1
EP2580080B1 EP11722019.4A EP11722019A EP2580080B1 EP 2580080 B1 EP2580080 B1 EP 2580080B1 EP 11722019 A EP11722019 A EP 11722019A EP 2580080 B1 EP2580080 B1 EP 2580080B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure fluid
fluid chamber
pressurising medium
low
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
EP11722019.4A
Other languages
German (de)
English (en)
Other versions
EP2580080A1 (fr
Inventor
Frank Bauer
Daniel Feld
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.)
Hydac Technology GmbH
Original Assignee
Hydac Technology GmbH
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 Hydac Technology GmbH filed Critical Hydac Technology GmbH
Publication of EP2580080A1 publication Critical patent/EP2580080A1/fr
Application granted granted Critical
Publication of EP2580080B1 publication Critical patent/EP2580080B1/fr
Not-in-force 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
    • F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2289—Closed circuit
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/047—Preventing foaming, churning or cavitation
    • 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
    • F15B2201/20—Accumulator cushioning means
    • F15B2201/205—Accumulator cushioning means using gas
    • 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
    • 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
    • F15B2201/32—Accumulator separating means having multiple separating means, e.g. with an auxiliary piston sliding within a main piston, multiple membranes or combinations thereof
    • 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
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/415—Gas ports
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding circuits
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8609—Control during or prevention of abnormal conditions the abnormal condition being cavitation

Definitions

  • the invention relates to a hydraulic system, in particular for a commercial vehicle, such as a construction machine, with a reversible in the conveying direction and variably adjustable in the delivery pressure medium pump, wherein the pressure medium pump takes the pressure fluid via a first fluid-conducting connection of a low-pressure fluid chamber of a double piston accumulator and in a High-pressure fluid space of the double-piston accumulator promotes, which is arranged between the pressure medium pump and the consumer and that the volume of the low-pressure fluid space is greater than the volume of the high-pressure fluid chamber.
  • Hydraulic equipment for commercial vehicles are generally composed of multiple hydrostatic drive systems.
  • these include the cooling, control and feeding hydraulics as well as the driving hydraulics.
  • these systems can work partially independently of each other and fulfill their respective function.
  • the steering system In moving construction machines, the steering system is regularly operated with a steering valve with so-called "open center", wherein a constant pump often formed as external gear pump promotes non-actuated steering system against the pressure fluid tank of the construction machine.
  • a vane pump with adjustable displacement For passenger cars takes over the promotion of pressure medium within an open system thus formed usually a vane pump with adjustable displacement.
  • a so-called open hydraulic circuit for example, the functions cooling, control and supply circuit can be covered with only one pressure medium pump. It may be an external gear pump with a constant displacement volume, which is attached to a power take-off of the internal combustion engine as a motor unit.
  • a cooling motor formed, for example, as districtenzahnradkonstantmotor a parallel connection of control and feed hydraulic circuit can be provided.
  • the control pressure system is used for signal transmission of certain machine characteristics, such as the control of a disk parking brake or a Schwenkwinkelverstell Road the drive pump by means of trigger valve.
  • certain machine characteristics such as the control of a disk parking brake or a Schwenkwinkelverstell
  • trigger valve By the use of the feed system, both the supply of fresh, purified hydraulic oil and an internal leakage compensation takes place.
  • a hydraulic energy storage system in which a motor-pump unit is arranged between a high-pressure accumulator and a low-pressure accumulator.
  • valves are provided in the piston of the low-pressure accumulator, which allow depending on the actuation of the piston feeding the hydraulic fluid into the low-pressure fluid chamber and thus the hydraulic circuit.
  • it is also known to compensate for the power peaks of the motor unit, in particular in the form of an internal combustion engine, by the use of a pressure medium accumulator, wherein the accumulator is charged or discharged in response to a current power output of the motor unit.
  • the total power of the motor unit in the sense of downsizing can be limited to a predefinable value, for example to the legally prescribed motor power class up to 56kW.
  • the pressure medium supply to the consumers and to a pressure fluid reservoir of the hydraulic system is often controlled by a so-called priority valve.
  • a connection and disconnection of the pressure medium supply to one or more consumers is controlled by a further valve.
  • the invention is therefore based on the object to provide a hydraulic system for a commercial vehicle, which on the one hand allows a reduction in performance for the internal combustion engine and on the other hand, the problem of cavitation is solved.
  • the pressure medium pressure in the low-pressure fluid chamber is chosen such that it is sufficient to actuate a pilot control device for the pressure medium pump.
  • the pilot control device may be a hydraulic device provided with one or more adjusting cylinders, for example to determine the pivoting angle of a cam ring of a vane pump or the like, and thus to specify the flow rate and conveying direction of the pressure medium pump.
  • the suction side of the pressure medium pump a pressure medium is removed from a low-pressure fluid chamber of the hydraulic system and conveyed into a high-pressure fluid chamber of the hydraulic system, a constructive measure is taken, always biased by the pressure fluid pump pressure medium slightly or such that the Cavitation in the hydraulic system is avoided.
  • the volume the low-pressure fluid space is greater or substantially greater than the volume of the high-pressure fluid chamber, so that it is ensured in each operating phase of the hydraulic system that sufficiently biased pressure medium of the pressure medium pump can be fed.
  • the volume of the low-pressure fluid space is dimensioned such that leakage oil losses of the hydraulic system have no influence on their operation.
  • the low-pressure fluid space can be removed from the pressure medium or the fluid-conducting connection between the low-pressure fluid space and the pressure medium pump can be connected to a fluid-conducting connection to the pressure medium container.
  • this is a check valve that allows an influx into said fluid-carrying connection or in the low-pressure fluid chamber only when the pressure medium pump in a reverse rotation phase, such as when accelerating, by a guided by them pressure medium return flow from the consumer, pressure medium in the high pressure Fluid space pumps.
  • the check valve opens and allows a withdrawal of pressure medium from the pressure medium container by negative pressure in said fluid-carrying connection.
  • the piston of the high pressure fluid space may be biased by a gas pressure of a biasing space as mentioned.
  • the biasing space may be acted upon by a gas pressure in a gas supply device.
  • the biasing space is limited by a fixed end wall of the housing of the high pressure fluid chamber or the dual piston accumulator.
  • the end wall preferably has a connection point for the gas supply device, for example in the manner of a nitrogen storage.
  • FIGURE shows a schematic diagram of a hydraulic system with an arrangement of a high-pressure fluid chamber and a low-pressure fluid chamber in a housing of a double-piston accumulator in principle and not to scale.
  • a hydraulic system 1 for a work machine for example in the form of a construction machine.
  • the hydraulic system 1 in particular its pressure medium pump 2 is driven by a motor unit, not shown internal combustion engine, for example in the form of a diesel engine, with a predeterminable effective drive power.
  • the pressure medium pump 2 is reversible in its conveying direction and variably adjustable in its delivery volume.
  • the pressure medium pump 2 selectively delivers from a low-pressure fluid chamber 5 (ND) of a double-piston accumulator 6 into a high-pressure fluid chamber 7 (HD) a pressure medium 3 via a fluid-conducting connection 4.
  • the pertinent double piston accumulator 6 has a designated as a whole with 16 housing.
  • the housing 16 is in the form of a cylinder tube, but may also have other cross-sectional shapes.
  • two longitudinally movable pistons 13, 17 are arranged, which are fixedly connected to each other via a coupling element 18 in the form of a coupling rod 19.
  • the coupling rod 19 in turn is moved longitudinally with the piston 13, 17 in a partition wall 20 of the housing 16.
  • the partition is in the manner of a cylindrical intermediate portion of the housing 16 trained.
  • the partition wall 20 with the adjacent opposing pistons 13, 17 defines two fluid spaces in the form of low-pressure fluid chamber 5 and in the form of the high-pressure fluid chamber 7.
  • the partition wall 20 corresponding sealing systems, not shown on.
  • the housing 16 is delimited by two end walls 21, 22, which form the closure cover of the double-piston accumulator 6. Between the viewed in the direction of the figure left end wall 21 and the adjacent opposite piston 13 is bounded by these parts, a biasing chamber 14 with variable volume, which is a predetermined internal gas pressure via a connection point 23 of a pressure vessel 15 impressed.
  • the pressure vessel 15 is preferably designed as a nitrogen storage of conventional design.
  • the gas (N 2 ) with prescribable gas pressure located in the preload space 14 forms a type of gas or pressure cushion.
  • the opposite piston 17 defines together with the end wall 22 an ambient space 24, which preferably has the respective ambient pressure. In the surrounding space 24, however, another working gas could also be used in a non-illustrated embodiment of the solution according to the invention, such as the nitrogen (N 2 ) mentioned in the prestressing space 14.
  • the ambient space 24 is connected via a leak oil line 26 with a pressure medium container 10 (tank) for the purpose of removing leakage oil of the double piston accumulator 6. Furthermore, an accumulator 11 acts on the first fluid-conducting connection 4, which leads from the low-pressure fluid chamber 5 to the pressure medium pump 2. The fluid pressure in the first fluid-conducting connection 4 also serves to act on a pilot control device 12 for influencing the flow rate and the conveying direction of the pressure medium pump 2.
  • the volume of the low-pressure fluid chamber 5 is chosen to be much larger than the volume of the high-pressure fluid chamber 7, wherein in the embodiment shown, the inner diameter of the housing part with the low-pressure fluid chamber 5 is chosen to be much larger than that in the housing part of the high-pressure fluid chamber. 7 the case is. In this way, sufficient stored pressure medium, provided for the operation of the hydraulic system 1, so that the pressure medium pump 2 can be supplied safely and permanently with pressure medium even with external or internal leakage volume flows.
  • a check valve 8 is provided in the second fluid-carrying connection 9, at a point between the pressure medium tank 10 (tank) and a node 25 between the pressure accumulator 11 and the pressure medium pump second If the low-pressure fluid chamber 5 is undersupplied with the pressure medium, it is possible that pressure medium is sucked in from the pressure medium container 10 via the non-return valve 8 which opens toward the pressure medium pump 2 and supplied to the pressure medium pump 2 under the pretension pressure of the pressure accumulator 11. In this way, a prestressed pressure medium supply to the pressure medium pump 2 is twice possible. In particular, pressure medium 3 is then sucked in from the pressure medium container 10 via the check valve 8 when the pressure medium pump 2 is accelerated and pressure medium is conveyed from the low-pressure fluid space 5 into the high-pressure fluid space 7.
  • the double-piston accumulator 6 makes it possible to bias pressure medium 3 flowing as a connecting link from and to the pressure medium pump 2.
  • the volume on the low pressure side, that is, in the low pressure fluid space 5, is increased as the volume on the high pressure side, that is, in the high pressure fluid space 7, decreases.
  • the double piston accumulator 6 is constructed substantially symmetrically with respect to its longitudinal axis and center axis and thus structurally simple and inexpensive to produce.

Claims (5)

  1. Installation hydraulique, notamment pour un véhicule utilitaire, comme un engin de chantier, comprenant une pompe (2) à fluide sous pression, dont le sens de refoulement peut être inversé et dont le volume de refoulement peut être réglé de façon variable, dans laquelle la pompe (2) à fluide sous pression prélève le fluide (3) sous pression, par une première liaison (4) fluidique, d'une chambre (5) de fluide basse pression d'un accumulateur (6) à double piston, et le refoule dans une chambre (7) de fluide haute pression de l'accumulateur (6) à double piston, qui est disposé entre la pompe (2) à fluide sous pression et l'utilisateur, et dans laquelle le volume de la chambre (5) de fluide basse pression est plus grand que le volume de la chambre (7) de fluide haute pression, caractérisée en ce que le fluide (3) sous pression sert dans la chambre (5) de fluide basse pression à l'alimentation d'un dispositif (12) de pilotage du volume de refoulement et du sens de refoulement de la pompe (2) à fluide sous pression.
  2. Installation hydraulique suivant la revendication 1, caractérisée en ce que la chambre (5) de fluide basse pression communique avec le réservoir (10) de fluide sous pression par une deuxième liaison (9) fluidique, par l'intermédiaire d'un clapet (8) antiretour s'ouvrant dans le sens allant vers la pompe (2) à fluide sous pression.
  3. Installation hydraulique suivant la revendication 1 ou 2, caractérisée en ce que la première ou la deuxième liaison (4, 9) fluidique communique avec un accumulateur (11) de fluide sous pression entre le clapet (8) antiretour et la pompe (2) à fluide sous pression.
  4. Installation hydraulique suivant l'une des revendications 1 à 3, caractérisée en ce qu'au moins un piston (13) de l'accumulateur (6) à double piston délimite une chambre (14) de prédétente, ayant une pression interne de gaz pouvant être donnée à l'avance et en ce que l'espace (14) de prédétente communique avec un réservoir (15) sous pression.
  5. Installation hydraulique suivant l'une des revendications précédentes, caractérisée en ce que la pompe (2) à fluide sous pression prélève le fluide (3) sous pression, par l'intermédiaire d'une première liaison (4) fluidique, d'une chambre (5) de fluide basse pression d'un accumulateur (6) à double piston, et le refoule dans une chambre (7) de fluide haute pression de l'accumulateur (6) à double piston, dont les volumes pour du fluide sont couplés mécaniquement.
EP11722019.4A 2010-06-08 2011-05-27 Installation hydraulique Not-in-force EP2580080B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010023016A DE102010023016A1 (de) 2010-06-08 2010-06-08 Hydraulische Anlage
PCT/EP2011/002642 WO2011154101A1 (fr) 2010-06-08 2011-05-27 Installation hydraulique

Publications (2)

Publication Number Publication Date
EP2580080A1 EP2580080A1 (fr) 2013-04-17
EP2580080B1 true EP2580080B1 (fr) 2014-08-27

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11722019.4A Not-in-force EP2580080B1 (fr) 2010-06-08 2011-05-27 Installation hydraulique

Country Status (3)

Country Link
EP (1) EP2580080B1 (fr)
DE (1) DE102010023016A1 (fr)
WO (1) WO2011154101A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6208139B2 (ja) * 2011-10-10 2017-10-04 ロブソン, アンガス ピーターROBSON, Angus Peter アキュムレータ
CN104564577A (zh) * 2013-10-29 2015-04-29 北京精密机电控制设备研究所 一种伺服电动泵
US11661960B2 (en) 2020-03-27 2023-05-30 Smc Corporation Pressure-booster output stabilizer

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2286798A (en) * 1940-05-16 1942-06-16 Hydraulic Dev Corp Inc Hydraulic circuit for press brakes
DE3829646A1 (de) * 1988-09-01 1990-03-15 Teves Gmbh Alfred Reservoir fuer einen druckmittelkreis, insbesondere flugzeughydraulikkreis
FR2786442B1 (fr) * 1998-12-01 2001-03-02 Peugeot Dispositif formant toit coulissant de vehicule automobile
AU3001502A (en) * 2000-11-28 2002-06-11 Ifield Technology Ltd Hydraulic energy storage systems
AUPR170400A0 (en) * 2000-11-28 2000-12-21 Ifield Technology Ltd Emergency energy release for hydraulic energy storage systems
DE102006048399B4 (de) * 2006-10-12 2018-05-09 Liebherr-Aerospace Lindenberg Gmbh Vorrichtung zur Entriegelung eines Bauteils eines Flugzeuges
US7926501B2 (en) * 2007-02-07 2011-04-19 National Oilwell Varco L.P. Subsea pressure systems for fluid recovery

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Publication number Publication date
WO2011154101A1 (fr) 2011-12-15
DE102010023016A1 (de) 2011-12-08
EP2580080A1 (fr) 2013-04-17

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