EP2600012B1 - Système hydraulique - Google Patents

Système hydraulique Download PDF

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Publication number
EP2600012B1
EP2600012B1 EP12008005.6A EP12008005A EP2600012B1 EP 2600012 B1 EP2600012 B1 EP 2600012B1 EP 12008005 A EP12008005 A EP 12008005A EP 2600012 B1 EP2600012 B1 EP 2600012B1
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EP
European Patent Office
Prior art keywords
main control
pressure
control valves
hydraulic
valve
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.)
Active
Application number
EP12008005.6A
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German (de)
English (en)
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EP2600012A3 (fr
EP2600012A2 (fr
Inventor
Simon Meier
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.)
Liebherr Hydraulikbagger GmbH
Original Assignee
Liebherr Hydraulikbagger 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.)
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Publication of EP2600012A2 publication Critical patent/EP2600012A2/fr
Publication of EP2600012A3 publication Critical patent/EP2600012A3/fr
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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
    • F15B18/00—Parallel arrangements of independent servomotor systems
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/20—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors controlling several interacting or sequentially-operating members
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/07—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors in distinct sequence
    • 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
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/783—Sequential control
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7762—Fluid pressure type

Definitions

  • the present invention relates to a hydraulic system with at least two main control valves and with a hydraulic pilot control system for controlling the main control valves.
  • the object of the present invention is to provide a simpler and more reliable system.
  • a hydraulic system according to the upper handle of claims 1 and 2 is from CN 201513115 U known.
  • the hydraulic system according to the invention comprises at least two main control valves and a hydraulic pilot control system for controlling the main control systems.
  • the hydraulic pilot control system and / or the main control valves are constructed in such a way that the at least two main control valves open one after the other.
  • the hydraulic or mechanical design of the hydraulic system can be used to open the main control valves in a certain sequence and thus to implement a cascade connection.
  • the system can be constructed in such a way that the at least two main control valves open at different control pressures of a common control transmitter. This also makes it possible to implement a cascade connection in a hydraulically pilot-controlled multi-circuit system in which the main control valves open in a certain sequence.
  • the main control valves can be used to control one or more consumers.
  • the cascade connection can be implemented using mechanically and / or hydraulically different main control valves.
  • the at least two main control valves can be equipped with springs of different spring force, so that the main control valves open at different control pressures due to the different spring force.
  • the spring of a first main control valve can open in a first control pressure range, while the spring of a second main control valve opens in a second control pressure range.
  • the main control valves can be constructed identically.
  • the at least two main control valves can have different valve rods and / or valve housings, which lead to an opening of the at least two main control valves with different strokes.
  • the opening starts of the main control valves are mechanically defined differently on the valve rods or the valve housings. This can be done, for example, in the form of grooves or holes on the valve rods.
  • valves open at different strokes and thus at different control pressures.
  • At least one of the main control valves is acted on by a counter pressure which counteracts the control pressure.
  • the same effect can be achieved as with an increased spring strength, since the counter pressure is added to the spring pressure and must first be overcome by the control pressure in order to open the main control valve.
  • the back pressure can be constant.
  • a corresponding pressure source is advantageously provided for this.
  • cascade connection can also be implemented by a corresponding configuration of the pilot control unit. This means that identical main control valves can also be used.
  • At least one of the main control valves is controlled via a pressure reducing valve, the output pressure of which is controlled via the control pressure for another main control valve.
  • another control pressure for the one main control valve can be generated via the pressure reducing valve.
  • the pressure reducing valve can have a pressure ratio unequal to 1 between the control pressure and the outlet pressure, so that the outlet pressure for controlling the one main control valve is in a fixed ratio to the control pressure for the other main control valve.
  • At least one of the main control valves is acted on by a pressure cut-off valve with a counter-control pressure which counteracts the control pressure.
  • the pressure cut-off valve is advantageously acted upon by the control pressure, so that the counter-control pressure up to a cut-off pressure increases with the control pressure. This also enables the main control valve, which is acted upon by the counter-control pressure, to be opened later.
  • a first main control valve can be activated via a pressure reducing valve, while a second main control valve is acted upon by a counter-control pressure via a pressure cut-off valve.
  • valve rods or valve housings can be used.
  • more than one pressure reducing valve or more than one pressure cut-off valve can be used, which then operate accordingly with different pressure ratios or with different cut-off pressures.
  • the hydraulic system according to the invention advantageously has a common control transmitter, via which the at least two main control valves can be actuated.
  • this control transmitter can generate a control pressure for actuating the at least two main control valves.
  • the design of the main control valves or the pilot control unit according to the invention then ensures different opening starts of the main control valves despite the common control transmitter.
  • the hydraulic system according to the invention also has a common high-pressure supply for supplying the at least one two main control valves with hydraulic pressure.
  • the high-pressure supply advantageously includes a variable displacement pump, which is controlled depending on the needs of the connected consumer or consumers.
  • the cascading of the opening starts according to the invention allows the use of such a pressure supply despite hydraulic pilot control.
  • variable displacement pump is advantageously controlled via a load-sensing arrangement.
  • variable displacement pump is controlled in such a way that a certain pressure drop is maintained across all main control valves and, at the same time, a maximum pressure is not exceeded.
  • a subsequent summation for controlling the load-sensing arrangement takes place.
  • the at least two main control valves can be supplied with hydraulic pressure via at least two separate high-pressure supplies, in particular via separate variable pumps.
  • the cascade control according to the invention ensures that at low required flow rates only one of the two main control valves opens and thus only one of the two hydraulic pumps is used to supply the consumer or consumers. If more power is required, the other main control valve also opens, so that the second hydraulic pump is also used for the supply.
  • variable displacement pumps are each controlled via a load-sensing arrangement.
  • system according to the invention can also be used with more than two main control valves and / or more than two separate high-pressure supplies.
  • the at least two main control valves control separate consumers.
  • two hydraulic cylinders can be controlled via the two control valves.
  • the two hydraulic cylinders can be used to successively extend or retract different elements, e.g. for telescoping telescopic drawers out or in.
  • one or more hydraulic pumps can be used to supply pressure.
  • the at least two main control valves control the same consumer. This is particularly advantageous if the maximum control amount required is not made available via a single main control valve.
  • the two main control valves are particularly advantageously supplied with hydraulic fluid via separate hydraulic pumps.
  • the pressure supply can also take place here via only one hydraulic pump.
  • the present invention further includes a hydraulically powered implement having a hydraulic system as described above.
  • a hydraulically powered implement having a hydraulic system as described above.
  • it is a mobile work device.
  • the present invention is particularly preferably used in construction, earthmoving and / or handling equipment.
  • the present invention comprises a hydraulic excavator with a hydraulic system according to the invention.
  • the working device can comprise at least two separate hydraulic pumps for supplying consumers of the working device with hydraulic fluid, the at least two main control valves being supplied with hydraulic pressure separately from the at least two separate hydraulic pumps.
  • the two main control valves advantageously supply the same consumer with hydraulic fluid.
  • the consumer who is supplied with hydraulic pressure by both main control valves can be a slewing gear, a running gear and / or a hydraulic cylinder, in particular for lifting and / or moving a boom or tool.
  • the two main control valves can also be used to supply two separate consumers with hydraulic fluid.
  • the at least two consumers can be, for example, a slewing gear, a running gear and / or hydraulic cylinders for lifting and / or moving a boom or tool.
  • the exemplary embodiments of the present invention relate to a hydraulic system with two main control valves, in particular as part of an LS multi-circuit system with downstream summation, which are operated hydraulically in a pilot-controlled manner.
  • a cascade connection is provided, by means of which the hydraulic control slides used as main control valves are opened in a certain sequence.
  • the system is controlled via a common pilot transmitter 2, in particular a control handle, via which a desired control pressure for pilot control is generated.
  • the pilot control transmitter can be, for example, a joystick.
  • the pilot control transmitter 1 can be controlled via a pilot control pressure source 15, as shown, for example, in Figure 3 is shown, are subjected to a constant pilot pressure and reduces this to the desired control pressure.
  • the constant pilot pressure can be 35 bar, for example.
  • the hydraulic system according to the invention now allows the opening times to be cascaded despite this common control.
  • the cascade connection can be implemented via different valve springs of the main control valves or via different slide opening starts of the main control valves.
  • a hydraulic cascade pilot control unit can also be provided, so that the cascade connection takes place via the pilot control.
  • valve springs 6 and 7 of the two main spools 2 and 3 are selected so that, for. B. the spring of the slide 2 in a first pressure range and the spring of the slide 3 in a second pressure range.
  • the spring 6 of the slide 2 can be selected so that it responds in a pressure range between 0 and 20 bar, while the spring 7 of the slide 3 responds from 20 to 35 bar. Different opening starts are achieved through the different valve springs.
  • a pressure source or corresponding circuit 9 can be provided, which this with a back pressure.
  • the same effect is achieved as by the mechanical strengthening of the spring strength of the slide 3.
  • the valve 3 is acted upon by a counter-control pressure from the circuit 9 via the counter-control pressure connection 8, the counter-pressure advantageously being constant.
  • the same spring strength can be used as for the slide 2, which is now amplified via the pressure source 9, since the counter pressure is added to the spring pressure.
  • the spring strength for the valve 3 can also be between 0 and 20 bar and be increased by 10 bar from the pressure source 9.
  • the opening starts of the main slide 2 'and 3' are mechanically defined differently on the valve rods 10 and 11. Depending on the manufacturer of the basic slide, this can take the form of grooves or holes. As a result, a cascade connection can be created using the slide hardware without corresponding circuit logic.
  • both pistons 10 and 11 thus have the same stroke 12, but the piston of the main control valve 2 'opens after a short distance, while the piston of the main control valve 3' only opens by the stroke 13 later.
  • this is achieved in that the groove 14 on the valve rod 11 of the main control valve 3 'is shorter than the groove 14' on the valve rod 10 of the main control valve 2 ', and thus the pressure supply P with the one leading to the consumer only with a larger stroke Opening A or A 'connects.
  • valve springs 6 'and 7' can also be designed identically, so that the different opening starts occur solely through the mechanical configuration of the valve rods. Alternatively, this could also be done by a different mechanical configuration of the valve housing.
  • the cascade connection is implemented via a corresponding configuration of the pilot valve unit.
  • the main control slide 2 'and 3' can be used unchanged.
  • a pressure reducing valve 16 can be provided which is acted upon by the constant pilot pressure from the pilot pressure source 15.
  • the pressure reducing valve 16 is acted upon by the control pressure 17 of the pilot control transmitter 1 and has a specific pressure ratio x, so that x times the control pressure 17 is present at the pressure outlet 18 of the pressure reducing valve 16.
  • the first main control valve 2 ' is acted upon by the actual control pressure 17, the second main control valve 3' by the changed control pressure 18 of the pressure reducing valve.
  • the piston control 5 of the main control valve 3 'thus acts x times the control pressure specified by the control transmitter, while the piston control 4 of the main control valve 2' is affected by the simple control pressure specified on the control transmitter 1.
  • a pressure cut-off valve 19 can be provided which is acted upon by the control pressure from the pilot pressure transmitter 1 and has a defined cut-off pressure.
  • a counter pressure is exerted on the piston 4 of the main control valve 2 'via the pressure from the pressure cut-off valve 19.
  • the same pressure acts on both sides a and b of the main control valve 2 ', so that it remains in the neutral position.
  • both main control valves could also be achieved only with two main control valves, in each case via pressure reducing valves with different pressure ratios, or via pressure cut-off valves with different cut-off pressures.
  • Figures 4a to 4d Four exemplary embodiments for the use of the cascade circuit according to the invention with one or more hydraulic pumps and / or one or more consumers are shown.
  • Fig. 4a the two main control valves 2 and 3 are completely connected in parallel. They are supplied by a common hydraulic pump 30 and control the same consumer 40.
  • Fig. 4b the two main control valves 2 and 3 are only connected in parallel with regard to the pump side. They are therefore supplied by a common hydraulic pump 30, but control separate consumers 41 and 42.
  • Fig. 4c the two main control valves 2 and 3 are connected in parallel only with regard to the consumer side. They are therefore supplied by two separate hydraulic pumps 31 and 32, but control the same consumer 40.
  • FIG. 5 An exemplary embodiment is shown in which more than two main control valves 50 to 53 are supplied separately from hydraulic pumps 31 to 34 on the pump side, but control the same consumer 40.
  • the hydraulic system is advantageously designed such that the more than two main control valves 50 to 53 open or close in a defined sequence.
  • the present invention makes it possible, in particular in the case of a high-pressure supply to a multi-circuit system, to operate the main control valves hydraulically in a pilot-controlled manner by means of a load-sensing control with a subsequent summation, and yet to achieve a cascade connection.
  • Hydraulic systems according to the invention can be used in particular in the case of mobile work machines, such as, for example, a hydraulic excavator.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Claims (13)

  1. Système hydraulique avec au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") et avec un système hydraulique pilote pour actionner les soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3"), le système hydraulique pilote et/ou les soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") étant conçus de telle sorte que les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") s'ouvrent l'une après l'autre,
    caractérisé en ce que
    le système hydraulique pilote est relié hydrauliquement à toutes les soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") par une ligne pilote commune se ramifiant vers les soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3").
  2. Système hydraulique avec au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") et avec un système hydraulique pilote pour actionner les soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3"), le système hydraulique pilote et/out les soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") étant conçus de telle sorte que les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") s'ouvrent l'une après l'autre, caractérisé en ce qu'au moins une des soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") est actionnée par une soupape de réduction de pression (16) dont la pression de sortie (18) est actionnée par la pression de commande (17) d'une autre soupape de commande principale (2, 3 ; 2', 3' ; 2", 3"), la soupape de réduction de pression (16) présentant avantageusement un rapport de pression (x) différent de 1 entre la pression de commande (17) et la pression de sortie (18) et/ou caractérisé en ce qu'au moins une des soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") est sollicitée par une contre-pression de commande, qui s'oppose à la pression de commande (17) et augmente avec la pression de commande (17) jusqu'à une pression d'arrêt, au moyen d'une soupape d'arrêt de pression (19).
  3. Système hydraulique selon la revendication 1 ou 2, dans lequel les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") comportent des ressorts (6, 7) avec une force élastique différente, qui conduisent à une ouverture des au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") à des pressions de commande (17) différentes.
  4. Système hydraulique selon l'une quelconque des revendications précédentes, dans lequel les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") comportent des tiges de soupapes (10, 11) et/ou des boîtiers de soupapes différents, qui conduisent à une ouverture des au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") à des courses différentes.
  5. Système hydraulique selon l'une quelconque des revendications précédentes, dans lequel au moins une des soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") est sollicitée par une contre-pression qui s'oppose à la pression de commande (17), la contre-pression étant avantageusement constante.
  6. Système hydraulique selon l'une quelconque des revendications précédentes, dans lequel les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") peuvent être actionnées par l'intermédiaire d'un transmetteur de commande commun (1), le transmetteur de commande (1) générant avantageusement une pression pilote pour actionner les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3").
  7. Système hydraulique selon l'une quelconque des revendications précédentes, dans lequel les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") sont alimentées en pression hydraulique par une alimentation haute pression commune, en particulier par une pompe à cylindrée variable commune (30, 31, 32, 33), la pompe à cylindrée variable (30, 31, 32, 33) étant avantageusement actionnée par un système de détection de charge, une sommation en aval étant en outre effectuée avantageusement.
  8. Système hydraulique selon l'une quelconque des revendications 1 à 6, dans lequel les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") sont alimentées en pression hydraulique par au moins deux sources de haute pression séparées, en particulier par des pompes à cylindrée variable séparées (30, 31, 32, 33), les pompes à cylindrée variable (30, 31, 32, 33) étant avantageusement actionnées chacune par un système de détection de charge.
  9. Système hydraulique selon l'une quelconque des revendications précédentes, dans lequel les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") actionnent des consommateurs différents (40, 41).
  10. Système hydraulique selon l'une quelconque des revendications 1 à 8, dans lequel les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") actionnent le même consommateur (40, 41).
  11. Machine de travail à entraînement hydraulique avec un système hydraulique selon l'une quelconque des revendications 1 à 10, en particulier machine de travail mobile, en particulier machine de construction, de terrassement et/ou de manutention, en particulier pelle hydraulique.
  12. Machine de travail à entraînement hydraulique selon la revendication 11, comportant au moins deux pompes hydrauliques séparées pour alimenter des consommateurs (40, 41) de la machine de travail en fluide hydraulique, les au moins deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3") étant alimentées en pression hydraulique séparément des au moins deux pompes hydrauliques séparées et alimentant avantageusement le même consommateur (40, 41) en fluide hydraulique.
  13. Machine de travail à entraînement hydraulique selon la revendication 12, dans lequel le consommateur (40, 41), qui est sollicité par pression hydraulique au moyen des deux soupapes de commande principales (2, 3 ; 2', 3' ; 2", 3"), est un mécanisme de rotation, un mécanisme de translation et/ou un vérin hydraulique, en particulier pour lever et/ou déplacer une flèche ou un outil.
EP12008005.6A 2011-12-01 2012-11-28 Système hydraulique Active EP2600012B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201110119945 DE102011119945A1 (de) 2011-12-01 2011-12-01 Hydrauliksystem

Publications (3)

Publication Number Publication Date
EP2600012A2 EP2600012A2 (fr) 2013-06-05
EP2600012A3 EP2600012A3 (fr) 2016-12-21
EP2600012B1 true EP2600012B1 (fr) 2020-04-01

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EP12008005.6A Active EP2600012B1 (fr) 2011-12-01 2012-11-28 Système hydraulique

Country Status (5)

Country Link
US (1) US9897115B2 (fr)
EP (1) EP2600012B1 (fr)
CN (1) CN103133450B (fr)
DE (1) DE102011119945A1 (fr)
RU (1) RU2599698C2 (fr)

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EP2600012A3 (fr) 2016-12-21
US20130139909A1 (en) 2013-06-06
US9897115B2 (en) 2018-02-20
CN103133450A (zh) 2013-06-05
RU2012151537A (ru) 2014-06-10
EP2600012A2 (fr) 2013-06-05
CN103133450B (zh) 2017-04-12
RU2599698C2 (ru) 2016-10-10
DE102011119945A1 (de) 2013-06-06

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