EP1837529B1 - Commande hydraulique - Google Patents

Commande hydraulique Download PDF

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Publication number
EP1837529B1
EP1837529B1 EP20060005669 EP06005669A EP1837529B1 EP 1837529 B1 EP1837529 B1 EP 1837529B1 EP 20060005669 EP20060005669 EP 20060005669 EP 06005669 A EP06005669 A EP 06005669A EP 1837529 B1 EP1837529 B1 EP 1837529B1
Authority
EP
European Patent Office
Prior art keywords
pressure
load
valve
directional control
control 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.)
Not-in-force
Application number
EP20060005669
Other languages
German (de)
English (en)
Other versions
EP1837529A1 (fr
Inventor
Martin Dipl.-Ing. Heusser
Werner MÜNZENMAIER
Paul Von Bäumen
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.)
Putzmeister Concrete Pumps GmbH
Hawe Hydraulik GmbH and Co KG
Original Assignee
Putzmeister Concrete Pumps GmbH
Hawe Hydraulik GmbH and Co 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 Putzmeister Concrete Pumps GmbH, Hawe Hydraulik GmbH and Co KG filed Critical Putzmeister Concrete Pumps GmbH
Priority to DE200650001885 priority Critical patent/DE502006001885D1/de
Priority to ES06005669T priority patent/ES2314768T3/es
Priority to EP20060005669 priority patent/EP1837529B1/fr
Publication of EP1837529A1 publication Critical patent/EP1837529A1/fr
Application granted granted Critical
Publication of EP1837529B1 publication Critical patent/EP1837529B1/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
    • 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
    • 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
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/168—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load with an isolator valve (duplicating valve), i.e. at least one load sense [LS] pressure is derived from a work port load sense pressure but is not a work port pressure itself
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/25—Pressure control functions
    • 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
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • 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
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • 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
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/654—Methods of control of the load sensing pressure the load sensing pressure being lower than the load 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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • 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
    • F15B2211/782—Concurrent control, e.g. synchronisation of two or more actuators

Definitions

  • the invention relates to a hydraulic control device according to the preamble of patent claim 1.
  • the switching valve is a 2/2-solenoid switching valve, which is arranged between the outlet of the control pump and the load pressure line branch in the input block. Between the magnetic switching valve and the load pressure line branch, a change-over valve connects either the load pressure line branch or the output of the magnetic switching valve to the control connection (short circuit) in a pressure-dependent manner.
  • the solenoid switching valve serves to achieve a switching time gain which may be useful when there is a very long line to the directional control valves or the consumers delaying the response, a directional control valve is deflected.
  • control pump started up and the solenoid switching valve switched to passage, so that builds from the pump supply pressure control pressure at the control connection.
  • the control pump initially goes to maximum pressure and then regulates automatically back. Since no load pressure prevails in the load pressure reporting system at this point in time, the drain valve blocks and, if necessary, delivers the control pump against a safety valve, so that e ⁇ at least substantially constant admission pressure, for example, of about 250 bar.
  • this consumer is initially supplied with the form, which also creates a load pressure in the load pressure detection system, which when reaching a certain height either actuates the shuttle valve and the load pressure line branch again connects to the control port, and decouples the solenoid valve, or it Then the solenoid valve is moved back to the shut-off, so that the load pressure reaches the control port. Then, the operation is carried out with variable pressure of the control pump, possibly even under the influence of the regulating drain valve.
  • the supports of the vehicle are extended, in which case no other working tools driving consumers until the supports have properly stabilized the vehicle.
  • the solenoid valve and its interconnection represent an undesirable overhead and latent sources of interference.
  • the invention has for its object to provide a hydraulic control device of the type mentioned, which is structurally easier and cheaper than the known despite a Heidelbergzeit threads.
  • a separate operating mode direction control valve is expediently integrated into the control device in order to be able to make a preselection between different consumer groups, each of which comprises at least one consumer and is controlled independently of the other group. Initially, the operation is carried out with a substantially constant supply form, in order to avoid switching time delays with the associated disadvantages as soon as a consumer is to be moved.
  • the mode selector control valve also has the advantage of only upshifting the control pump prior to actual control of a consumer to adjust the supply pre-pressure. This is particularly useful in an application in which, for example, supports of a vehicle must be operated.
  • an operator with eye contact has to extend each support for himself, which he does for example with a directional control valve in or on the support cylinder with a view of the support. None of the other consumers driving tools is controlled. Only when the supports are properly extended and anchored is the operating mode directional control valve changed over to the other control position in order to be able to move the working tools when the vehicle is supported, but initially again with the substantially constant supply pre-pressure and a variable amount. which is controlled via the respective directional control valve until sufficient load pressure is reported.
  • the 3/2-way switching valve is operatively associated with the operating mode directional control valve which selectively decides which of the exclusively operable consumers are controlled.
  • pilot pressure is automatically applied via the 3/2-way switching valve to the control connection via the pilot pressure line branch in order to raise or regulate the control pump, so that substantially constant supply form is pending. Only when the load pressure of a Lastyakabgriff one of the directional control valves has risen so far that it overcomes the force of the spring of the 3/2-way switching valve, this switches to transfer this load pressure to the control connection of the control pump, so that then variable supply pressure supplies.
  • the consumers which are operated anyway at constant supply form, may optionally even be connected directly to the operating mode directional control valve. Appropriately, however, directional control valves are also provided for these consumers.
  • Another important idea is to place between the load pressure tap of the operating mode directional control valve and the 3/2-way switching valve, a load pressure limiting valve which limits the load pressure for up-regulating the control pump in view of the desired, constant supply form. Even if the operation of the operating mode direction control valve at its load tap should result in a higher load pressure for any reason, thanks to the load pressure limiting valve, care is taken that the control connection of the control pump receives the load pressure limited to the desired admission pressure.
  • the force of the spring of the 3/2-way switching valve is set to a selected load pressure limit, so that only then the load pressure is reported to the control connection of the control pump when it reaches a predetermined value.
  • the spring side should be relieved to the tank.
  • control device is integrated into a special vehicle which has supports for which the constant supply pressure is sufficient for extension.
  • the operating mode directional control valve is designed with a blocking neutral position, i. shuts off the main connections in the pressure line and the tank line in the zero position.
  • the 3/2-way switching valve is housed together with the load pressure limiting valve in an intermediate block which is attached to the operating mode directional control valve and the input block or inserted therebetween.
  • FIG. 1 a block diagram of the hydraulic control device with symbolically indicated consumers.
  • the hydraulic control device S is supplied by a control pump R via a pressure line 10 with pressure medium.
  • the control pump has a control connection 1, which is acted upon by a load pressure line branch 17 with control pressure to regulate the control pump as needed.
  • an input block 2 is provided, which is combined with an intermediate block 3 and a direction selection control valve 4 in a convenient manner (block design), with further parallel-connected directional control valves 5, 5 '), for example, in series, to the operating mode directional control valve 4 and the intermediate block 3 are grown.
  • the operating mode direction control valve 4 is formed with blocking zero position (as shown) and connected to the pressure line 10 and a tank line 11.
  • a plurality of consumers 6 are connected via a line 31, either directly or via dashed lines indicated direction control valves 32, and via a further line 35 in parallel the directional control valves 5, 5 ', which define at least one directional control valve group, namely for consumers 7, 8, for example, power tools of a machine or a device.
  • the consumers 6 are for example cylinders for supports.
  • a drain valve 12 which operates in the manner of a pressure compensator and the pressure line 10 connects either to the tank line 11 or blocks this connection.
  • the drain valve 12 is e.g. a control valve, which is acted upon in the up direction by a pilot pressure from the pump line 10 and in the feed direction of a control spring and a pilot pressure from a pilot line 38, which branches off from the pressure line 10 and leads to a pilot pressure-reducing valve 16, for example, a reduced pressure for hydraulic pilot controls the operating mode direction control valve 4 and also the other directional control valves 5, 5 'sets.
  • a hydraulic damping device 14 for the load pressure line branch 17 and a pressure relief valve to the tank line 11 are included in the input block 2, as well as a main pressure relief valve 13 between the pressure line 10 and the tank line 11. Further, in the input block 2, a part 18 of the load pressure line branch 17 to the control connection 1 included.
  • the part 18 of the load pressure line branch 17 is connected to a load pressure line 19, which comes from a switching valve V, which serves to set in the switching position shown an operation with a substantially constant supply form.
  • the switching valve V is designed according to the invention as a hydraulically and pressure-dependent operable 3/2-way switching valve.
  • the 3/2-way switching valve 29 is held by a spring 30 in the switching position shown, in which there is a Lastyakabgriff 20 of the operating mode direction control valve 4 via a control pressure line 21 connects to the load pressure line 19.
  • the pilot control pressure reported to the 3/2-way switching valve 29 in the load pressure discharge 19 is limited by a pilot pressure limiting valve D.
  • a control pressure line 28 of a load pressure signaling or LS system is also connected, which comes from Lastabgriffen 25 of the other directional control valves 5, 5 'and changeover valves 27 contains, to transmit the highest load pressure.
  • the load pressure tap 25, for example, the directional control valve 5 is connected via a control pressure line 26 to the shuttle valve 27.
  • the force of the spring 30, which holds the 3/2-way switching valve 29 in the switching position shown (constant supply form) is set to a certain load pressure limit below which is not switched.
  • the line 31 is connected to the consumers 6, while the other output via a line 35 to the pressure sides of the further directional control valves 5, 5 'leads.
  • control pump R is driven and the directional control valves 4, 5, 5 'are in their zero positions, optionally supplied by the control pump base pressure discharged via the drain valve 12 from the pressure line 10 into the tank line 11. There is no significant system pressure.
  • the operating mode direction control valve 4 is switched to its switching position b (by proportional solenoid with hydraulic pilot control, as indicated), so that the pressure line 10 is connected to the line 31, while the pressure line 35 is relieved.
  • the load pressure is tapped and reported via the passage 24 to the load pressure tap 20, and further brought over the control pressure line 21 to the 3/2-way switching valve 29, which is held by the spring 30 in the switching position shown.
  • This pilot pressure can only reach the limit set at the load pressure limiting valve D. For example, corresponding to a supply pressure between 250 to 300 bar.
  • This pilot pressure is transmitted via the pilot control line 19 through the input block 2 and the load pressure line branch 18, 17 to the control connection 1 of the control pump R.
  • the control pump R pivots up, for example, to the maximum pressure, and then back to adjust the supply pressure. Since the passage 22 is shut off, pressure builds on the closing control side of the drain valve 12 via the load pressure line 38, which keeps the drain valve 12 closed.
  • the substantially constant supply pre-pressure for example 250 to 300 bar, is used in the line 31 for actuating the consumer 6, optionally with variable amount, possibly by means of the directional control valves 32.
  • the further directional control valves 5, 5 ' still receive no pressure.
  • the hydraulic damping device 14 damps any pressure fluctuations of the pilot or load pressure.
  • the pilot pressure reducing valve 16 adjusts the desired pilot pressure for the operational direction control valve 4, as well as the other directional control valves 5, 5 '.
  • the load pressure limiting valve D limits, so to speak, the supply pre-pressure to the desired value, so that in this operation, the main pressure relief valve 13 does not need to address, because the control pump delivers only one supply form, which is lower than the set at the main pressure relief valve 13 pressure limit.
  • the directional control valve 5 (or 5 ') adjusted in one of its switching positions a or b, then the build-up load pressure at the Last Kunststoffabgriff 25 is tapped and brought over the control pressure line 26 and the shuttle valve 27 and the control pressure line 28 to the 2/3-way switching valve 29 , Only when the tapped load pressure exceeds the limit determined by the spring 30, the 3/2-way switching valve 29 is switched to its other switching position, so that the load pressure from the load pressure line 28 via the load pressure line 19 and on to the control port 1 is reported.
  • the control pump R now works with a variable supply pressure, which depends on the load pressure reported at the control connection 1. As long as the operating mode direction control valve 4 is in the switching position a, therefore, the consumers 7, 8 can be properly controlled (LS control).
  • the drain valve 12 When operating with a variable supply pressure, the drain valve 12 may also be regulated as a function of the load pressure in the control pressure line 38 and the opening pilot pressure reported from the pressure line 10.
  • the 3/2-way switching valve 29 is provided with the load pressure limiting valve D expediently in the intermediate block 3, which fits to the other components of the hydraulic control device. Alternatively, it would also be possible to integrate the 3/2-way switching valve 29 and the load pressure limiting valve D directly into the operating mode-way control valve 4, or to place it at the control connection 1.

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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)

Claims (11)

  1. Dispositif de commande hydraulique (S) pour un groupe de consommateurs, en particulier pour un outillage avec des groupes de consommateurs (6, 7, 8) exploitables de façon exclusivement sélective, comprenant une pompe à débit variable (R) qui est raccordée à des distributeurs (4, 5) des consommateurs par l'intermédiaire d'un bloc d'entrée (2) avec une soupape d'échappement (12), une soupape de sûreté (13) et un embranchement de conduite sous pression de charge (17, 18) d'un système de signalisation de pression de charge menant à un raccord de réglage (1) de la pompe à débit variable (R), et comprenant une soupape de commande (V), qui peut être commutée entre une position de commutation pour un fonctionnement sous pression d'alimentation essentiellement constante de la pompe à débit variable et une position de commutation avec pression d'alimentation variable de la pompe à débit variable, caractérisé en ce que la soupape de commande (V) est un distributeur 3/2 (29), qui peut être commuté dans la position de commutation pour le fonctionnement sous pression d'alimentation variable, par voie hydraulique et en fonction de la pression, contre un ressort (30) définissant la position de commutation pour le fonctionnement sous pression d'alimentation essentiellement constante.
  2. Dispositif de commande hydraulique suivant la revendication 1, caractérisé en ce qu'il est prévu un distributeur (4) sélecteur de fonctionnement en série entre le bloc d'entrée (2) et des groupes de distributeurs (5, 5', 32) montés parallèlement en aval, distributeur par lequel est réglable le fonctionnement sous pression d'alimentation constante lors de l'actionnement à partir d'une position zéro par l'intermédiaire du distributeur 3/2 (29).
  3. Dispositif de commande hydraulique suivant la revendication 2, caractérisé en ce que le distributeur (4) sélecteur de fonctionnement présente une prise de pression de charge (20), que le distributeur 3/2 (29) est disposé entre l'embranchement de conduite sous pression de charge (17, 18), menant au raccord de réglage (1) et, parallèlement à la prise de pression de charge (20) du distributeur (4) sélecteur de fonctionnement, des prises de pression de charge (25) d'au moins un groupe de distributeurs (5, 5') et relie l'embranchement de conduite sous pression de charge (17, 18) en cours de fonctionnement sous pression d'alimentation constante, soit à la prise de pression de charge du distributeur (4) sélecteur de fonctionnement, soit aux prises de pression de charge du ou des groupes de distributeurs (5, 5'), et que le distributeur 3/2 (29) peut être commuté dans la position de commutation pour le fonctionnement sous pression d'alimentation variable par la pression de charge de l'une des prises de pression de charge (25) du ou des groupes de distributeurs (5, 5').
  4. Dispositif de commande hydraulique suivant la revendication 3, caractérisé en ce qu'au moins un consommateur (6) est raccordé au distributeur (4) sélecteur de fonctionnement, soit directement, soit par l'intermédiaire d'au moins un autre distributeur (32), et peut être exploité à débit variable en cours de fonctionnement sous pression d'alimentation constante.
  5. Dispositif de commande hydraulique suivant la revendication 3, caractérisé en ce que le distributeur (4) sélecteur de fonctionnement et les distributeurs du ou des groupes de distributeurs (5, 5') soulagent dans la position zéro la prise de pression de charge respective (20, 25) en direction du réservoir (9).
  6. Dispositif de commande hydraulique suivant la revendication 3, caractérisé en ce qu'il est prévu, entre la prise de pression de charge (20) du distributeur (4) sélecteur de fonctionnement et le distributeur 3/2 (29), une soupape de limitation de pression de charge (D) qui peut être commandée par la pression de charge sur la prise de pression de charge (20, 23, 24).
  7. Dispositif de commande hydraulique suivant la revendication 3, caractérisé en ce que la force du ressort (30) du distributeur 3/2 (29) est réglée sur une limite sélectionnée de la pression de charge des prises de pression de charge (2b) du ou des groupes de distributeurs (5, 5').
  8. Dispositif de commande hydraulique suivant la revendication 1, caractérisé en ce que le côté ressort du distributeur 3/2 (29) est soulagé en direction du réservoir (9).
  9. Dispositif de commande hydraulique suivant l'une au moins des revendications précédentes, caractérisé en ce que le dispositif de commande (S) est incorporé dans une grue ou dans une échelle mécanique ou dans une pompe à béton ou dans un véhicule à plate-forme de levage ou dans un véhicule de foresterie avec des montants pouvant être sortis par voie hydraulique et d'autres consommateurs (7, 8), que les montants ou au moins un consommateur (7, 8) raccordé au(x) groupe(s) de distributeurs (5, 5') peuvent être commandés par le distributeur (4) sélecteur de fonctionnement sélectivement en cours de fonctionnement sous pression d'alimentation constante, et que seuls les consommateurs (7, 8) peuvent être commandés en cours de fonctionnement sous pression d'alimentation variable.
  10. Dispositif de commande hydraulique suivant la revendication 2, caractérisé en ce que le distributeur (4) sélecteur de fonctionnement est réalisé avec une position zéro de blocage.
  11. Dispositif de commande hydraulique suivant l'une au moins des revendications précédentes, caractérisé en ce que le distributeur 3/2 (29) et la soupape de limitation de pression de charge (D) sont disposés dans un bloc intermédiaire (3), rapporté sur le distributeur (4) sélecteur de fonctionnement et sur le bloc d'entrée (2).
EP20060005669 2006-03-20 2006-03-20 Commande hydraulique Not-in-force EP1837529B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE200650001885 DE502006001885D1 (de) 2006-03-20 2006-03-20 Hydraulische Steuervorrichtung
ES06005669T ES2314768T3 (es) 2006-03-20 2006-03-20 Dispositivo de control hidraulico.
EP20060005669 EP1837529B1 (fr) 2006-03-20 2006-03-20 Commande hydraulique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20060005669 EP1837529B1 (fr) 2006-03-20 2006-03-20 Commande hydraulique

Publications (2)

Publication Number Publication Date
EP1837529A1 EP1837529A1 (fr) 2007-09-26
EP1837529B1 true EP1837529B1 (fr) 2008-10-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060005669 Not-in-force EP1837529B1 (fr) 2006-03-20 2006-03-20 Commande hydraulique

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EP (1) EP1837529B1 (fr)
DE (1) DE502006001885D1 (fr)
ES (1) ES2314768T3 (fr)

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EP3093505B1 (fr) 2015-05-11 2017-08-23 HAWE Hydraulik SE Dispositif de commande hydraulique et sélecteur
DE102020209387B3 (de) * 2020-07-24 2021-07-15 Hawe Hydraulik Se Vorwahlventil, Hydraulikventilverband und Hydrauliksteuervorrichtung

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KR100379863B1 (ko) * 1999-04-26 2003-04-11 히다치 겡키 가부시키 가이샤 유압회로장치
WO2001055603A1 (fr) * 2000-01-25 2001-08-02 Hitachi Construction Machinery Co., Ltd. Dispositif de commande hydraulique

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EP1837529A1 (fr) 2007-09-26
DE502006001885D1 (de) 2008-12-04
ES2314768T3 (es) 2009-03-16

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