EP1623123B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP1623123B1
EP1623123B1 EP04738497A EP04738497A EP1623123B1 EP 1623123 B1 EP1623123 B1 EP 1623123B1 EP 04738497 A EP04738497 A EP 04738497A EP 04738497 A EP04738497 A EP 04738497A EP 1623123 B1 EP1623123 B1 EP 1623123B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
shut
valve
block
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.)
Expired - Lifetime
Application number
EP04738497A
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German (de)
English (en)
Other versions
EP1623123A1 (fr
Inventor
Heinrich Lödige
Christoph Keyl
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.)
Bosch Rexroth AG
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Bosch Rexroth AG
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Filing date
Publication date
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Publication of EP1623123A1 publication Critical patent/EP1623123A1/fr
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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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • 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
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a consumer according to the preamble of claim 1.
  • an LS control arrangement in which a hydraulic consumer, for example a double-acting cylinder for moving a load via a continuously adjustable directional control valve with pressure medium can be supplied.
  • a hydraulic consumer for example a double-acting cylinder for moving a load via a continuously adjustable directional control valve with pressure medium
  • each check valves are provided, wherein the inlet-side check valve is brought by the pressure downstream of the directional control valve in an open position.
  • the drain-side check valve can be brought by pressing a poppet in an open position, which allows the drainage of the pressure fluid from the consumer to the directional control valve.
  • suction valves can be provided, via which pressure medium can be sucked out of the tank in the event of insufficient supply. Due to the low differential pressure between the cylinder suction side and the tank pressure, however, such suction valves must have a very large cross section.
  • lowering brake valves can be used, but also a high pressure on the Need to supply side to control the flow on the drain side.
  • the invention has for its object to provide a hydraulic control arrangement for controlling a consumer, in particular a double-acting consumer, in which the risk of undersupply is minimized.
  • the control arrangement has a continuously adjustable directional control valve to which an individual pressure balance is assigned. This is acted upon in the opening direction by the force of a spring and a control pressure and in the closing direction of a pressure in the inlet upstream of the directional control valve.
  • the control pressure corresponds to the pressure in the inlet downstream of the directional control valve, d. H. the load pressure and thus corresponds to a conventional LS control.
  • the control pressure is raised so that it is higher than the pressure in the inlet downstream of the directional control valve.
  • the control pressure gradient is raised at the inlet-side control edge of the directional control valve, so that a larger pressure fluid flow is promoted to the inlet-side cylinder chamber and a shortage can be prevented.
  • this control pressure is maintained at a constant, elevated level in the event of an undersupply.
  • This raised control pressure can be tapped off, for example, in the pressure medium flow path between the outflow-side blocking block and a sequence control edge of the directional control valve.
  • control pressure can also be tapped from any other available constant pressure source.
  • the locking block has a poppet which can be acted upon by an unblocking control pressure for unlocking.
  • an unblocking control pressure for unlocking.
  • the discharge-side pressure to the poppet, so that it is acted upon in the upstroke direction by the release-control pressure and in the opposite direction by the pressure in the discharge, so that a substantially load-independent discharge control is made possible.
  • the inlet and outlet pressures are tapped downstream of the directional control valve and upstream of the respective check valve and the respective higher pressure via a shuttle valve to the spring chamber of the individual pressure compensator.
  • these two pressures can still be compared with the Entsperr horrdruck and the largest of these pressures via a shuttle valve assembly are guided to the effective in the opening direction control surface of the individual pressure compensator.
  • the pounding piston of the blocking block is acted upon in the lifting direction by a spring.
  • a compression spring can be made weaker, over which a pilot piston guided in the blocking piston is biased into its closed position.
  • the check valve can be executed with or without seat difference.
  • FIG. 1 shows a valve disk 1 of a mobile control block, via which a consumer of a mobile working device can be supplied with pressure medium.
  • the valve disc 1 receives an LS control arrangement with a continuously adjustable directional control valve 2, an individual pressure compensator 4 and two shut-off valves 6, 8, via which the consumer, for example a Hydraulic cylinder 10 pressure medium from a pump, for example a variable displacement pump 12 can be fed and via which the pressure medium from the load 10 to a tank T is traceable.
  • a cylinder chamber 14 of the hydraulic cylinder 10 is connected to a working port A and an annular space 16 to a working port B, the tank is connected to a tank port S and the variable displacement pump 12 to a pressure port P (perpendicular to the plane in Figure 1).
  • a pressure compensator piston 15 of the individual pressure compensator 4 - in the following called pressure balance - in a pressure compensator bore 17 of the valve disc 1 is guided axially displaceable.
  • the pressure compensator piston 15 has a central annular groove, via which it is divided into a control collar 18 and a rear spring collar 20.
  • the pressure compensator piston 15 is biased by means of a control spring 30 supported on an end face of the pressure compensator bore 17 in a direction in which the connection between the pressure chamber 24 and the pressure channel 28 is opened.
  • a control spring 30 receiving spring chamber is connected to a control channel 34 which leads to the output of a shuttle valve 36.
  • the left in Figure 1 end face of the pressure compensator bore 16 defines with the adjacent end face of the control collar 18 a control chamber 38 which is acted upon via a further control channel with the pressure in the pressure channel 28.
  • a damping throttle 42 is further provided for damping high-frequency vibrations.
  • the Pressure channel 28 branches according to Figure 1 in two directional control valve 2 leading channels 44, 46. Details of this directional control valve 2 and the two locking blocks 6, 8 will be explained with reference to FIG.
  • the continuously adjustable directional control valve 2 has a valve slide 48 which is received in a valve bore 50 of the valve disc 1 axially displaceable.
  • the valve spool 48 is biased via a centering spring arrangement 52, 53 in its illustrated basic position. From this basic position, the valve spool 48 can be moved mechanically, electrically or hydraulically into working positions, which will be discussed in more detail later. In the illustrated embodiment, the actuation of the valve spool 48 via one or two proportional solenoids (not shown).
  • the valve bore 50 is provided with a plurality of annular spaces.
  • a central control pressure chamber 52 to a control terminal X (not shown) is connected, via which the control pressure chamber 52 can be acted upon by a constant Entsperr Strukturdruck.
  • two annular return chambers 54, 56 are provided, which are connected via the tank channels R with the return port T (see Figure 1).
  • two further annular spaces are provided, wherein the left in Figure 2 annulus are referred to below as Zulaufraum 58 and the right as drainage chamber 60.
  • Adjacent to the inflow or outflow space 58, 60 are two pressure chambers 63, 65 which are connected to the channels 44 and 46, respectively.
  • Between the central control pressure chamber 52 and the two return spaces 54, 56 of the other two annular spaces 62, 65 are provided in the valve bore 50 further.
  • the valve spool 50 has in the region of these annular spaces 62, 64 two narrow annular webs 66, 68 which shut off the connection between the central control pressure chamber 52 and the two adjacent annular spaces 62, 64 in the basic position shown in FIG.
  • control collars 70, 72 are formed, in the annular end faces each control notches are provided so that at each control collar 70, 72 a flow control edge 74 and an inlet control edge 76 is formed.
  • the geometry of the control collars 70, 72 with the control notches formed thereon is designed so that in the illustrated basic position of the inlet chamber 58 and the drain chamber 60 are open to the respective adjacent return chamber 54, 56, so that these pressure chambers are depressurized.
  • the connection between the inlet space 58 and the discharge space 60 to the outer pressure chambers 63, 65 is controlled via the inlet control edge 74.
  • Each locking block 6, 8 shown enlarged in Figure 2 each have an identical structure, so that in the following only the blocking block 6 is described.
  • Each locking block 6, 8 has a locking piston 78, which is biased against a valve seat 80.
  • the locking piston 78 is guided in a bore 79 of the disc 1. In the illustrated blocking position, the connection between an inlet chamber 82 and a working chamber 84 or the connection between a discharge chamber 86 and a working chamber 88 is shut off leak-free.
  • the locking piston 78 is designed as a hollow piston, wherein in its designed as a cone piston crown a pilot cone 90 is guided, which is biased by a pilot spring 94 against a pilot seat 92. About this pilot spring 94 and the locking piston 78 against its valve seat 80th biased.
  • the pilot poppet 90 has an axially projecting from the pilot seat 92 projection 96 which projects in the direction of the inlet chamber 82 and the discharge chamber 86 out.
  • the inlet chamber 82 of the blocking block 6 is connected via an intermediate channel 110 to the inlet chamber 58 and corresponding to the drain chamber 86 of the blocking block 8 via a further intermediate channel 112 to the drain chamber 60.
  • the space 101 on the rod side of the piston 98 is connected to the space 82 via a throttle, depending on the necessary damping.
  • the inlet chamber 58 and the outlet chamber 60 are each connected via a control line 116 or 118 to the two inputs of the shuttle valve 36. This means that the larger of the two pressures Y A , Y B picked up in the inlet space 58 and in the discharge space 60 is reported to the control channel 34 via the shuttle valve.
  • valve spool 48 of the continuously variable directional control valve 2 is shifted in the illustration of Figure 1 to the right, so that through the inlet control edge 76, the connection between the annular space 62 and the inlet space 58 and the connection between the drain chamber 60 and the return chamber 56 via the flow control edge 74 is turned on.
  • the pressure medium can then flow from the variable displacement pump 12 via the pressure chamber 24, the pressure compensator 4 opened as described below, the pressure channel 28 into the channel 44 and from there via the controlled from the inflow control edge 76 cross section of the directional control valve 4 in the intermediate channel 110 and from there into the inlet chamber 82 of the blocking block 6 flow.
  • the pressure compensator 4 is acted upon in the closing direction of the pressure in the control channel 40 and thus the pressure in the channel 44 and in the opening direction of the force of the control spring 30 and the pressure in the control channel 34.
  • the pressure in the inlet chamber 58 is greater than the pressure in the drain chamber 60, so that correspondingly in the spring chamber 32 of the individual pressure compensator 4, the pressure is applied downstream of the controlled from the inlet control edge 76 cross section. That is, by this inlet control edge 76 of the effective Determined cross-section of an inlet orifice, wherein the pressure compensator piston 15 is adjusted in its control position such that the pressure drop across this orifice is held constant load pressure independent.
  • control pressure PX is guided through the annular space 64 and the connecting channel 108 in the Entsperr mortraum 106, so that the poppet 98 of the locking block 8 is brought in the illustration of Figure 2 to the right in abutment against the projection 96 of the pilot poppet 90.
  • the Entsperr thoroughlyteil is chosen so that it is sufficient to lift the pilot cone 90 via the poppet 98 from its pilot seat 92 against the force of the pilot spring 94 and against the force acting on the seat load pressure.
  • the spring chamber 120 When pilot control is open, the spring chamber 120, which is connected via a diaphragm 122 with the working chamber 88 and thus acted upon by the pressure at the working port B, via the feedforward control with the discharge chamber 86 and via the intermediate channel 112, the discharge chamber 60, via the Sequence control edge 74 controlled flow cross section of the directional control valve 2, the return chamber 56 and the return R connected to the tank T and thus relieved of pressure in the closing direction.
  • the pressure compensated locking piston 78 can then be lifted by the poppet 98 from its valve seat, so that the pressure medium along the aforementioned pressure medium flow path to the tank T can flow out.
  • the running pressure medium volume flow is throttled at the flow control edge 74 of the valve spool 48, so that 56 sets a pressure gradient between the drain chamber 60 and the return chamber.
  • the flow control takes place practically by the feedback of the pressure in the discharge chamber 86, which acts on the end face of the piston rod 100 and the annular surface of the poppet 98, so that this one hand from Entsperr torturedruck in Entsperr tortureraum 106 and on the other hand by the pressure equivalent of the pilot spring 94 and the pressure acting on the piston rod 100 pressure is applied. That is, on the outlet side, a flow regulator is formed by the blocking block 8 and the outlet-side measuring orifice, in which the control pressure difference results from the pressures or pressure equivalents acting on the topping piston.
  • the pressure in the flow is thus regulated by pulling force through a structurally fixed constant, independent of the load pressure at port B and thus in the annulus 16 pressure. This means that there is a load pressure-independent control both on the inlet side and on the outlet side.
  • control channel 34 pressure could also be tapped from any constant pressure source.
  • FIG. 3 such an embodiment is realized.
  • the basic structure of this embodiment corresponds to that of Figure 2, so that only the essential differences will be discussed here.
  • the control arrangement according to Figure 3 also has a directional control valve 2, an individual pressure compensator 4 and two locking blocks 6, 8.
  • the two on both sides of the control pressure chamber 52 arranged annular ribs 66, 68 are formed so that the two annular spaces 62, 64 in the basic position of the continuously adjustable directional control valve 2 are connected to the two return spaces 54, 56, so that the back sides of the two topping pistons 98 are depressurized.
  • control arrangement according to FIG. 3 has a second shuttle valve 128, by means of which the pressure in the inlet space 58 is compared with the pressure in the annular space 64, while the pressure in the discharge space 60 is compared with the pressure in the annular space 62 via a third shuttle valve 130.
  • the outputs of the two shuttle valves 128, 130 are connected to the inputs of the shuttle valve 36, whose output is connected via the control channel 34 to the spring chamber 32 of the individual pressure compensator 4.
  • the inventive construction eliminates the need to provide Nachsaugventile or the like. Since a shortage of the consumer is almost impossible, and cavitation phenomena at the control edges of the directional control valve 2 can be avoided. Furthermore, air discharges on the suction side of the cylinder are avoided. Another advantage is the fact that the increase in the inlet pressure is much lower than is the case with the solutions described above with bias valves in the process or in a lowering-brake valve.
  • the locking piston 78 is the rear side with the same diameter as the valve seat 80 executed. But it could also be a blocking block with a seat difference can be used.
  • a hydraulic control arrangement for controlling a consumer, with a continuously adjustable directional control valve, an individual pressure compensator associated therewith and blocking blocks arranged downstream of the directional control valve.
  • the pressure compensator is subjected to a higher pressure instead of the pressure in the inlet (load pressure) in the event of an undersupply of the consumer, so that the control pressure difference at the inlet control edge is raised.

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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)
  • Valve Device For Special Equipments (AREA)
  • Safety Valves (AREA)

Claims (8)

  1. Dispositif de commande hydraulique pour amorcer un consommateur (10), avec un distributeur (2) réglable en permanence par le biais duquel deux raccords de travail (A, B) reliés au consommateur (10) peuvent être reliés à un raccord de pression ou d'alimentation (P) ou bien à un raccord d'écoulement (T), un bloc de retenue déblocable (6, 8) étant prévu dans au moins une conduite de travail qui sert de conduite d'écoulement et avec une balance de pression individuelle (4) affectée au distributeur (2) réglable en permanence, laquelle peut être soumise, dans le sens d'ouverture, à la force d'un ressort (30) et à une pression de commande et, dans le sens de fermeture, à la pression en amont du distributeur (2), caractérisé en ce que la pression de commande est transmise par un dispositif de comparaison (36, 128, 130) destiné à comparer la pression de charge effective dans l'alimentation à une pression constante, la balance de pression individuelle (4) étant soumise à la pression constante, lorsque cette dernière est plus élevée que la pression de charge effective dans l'alimentation.
  2. Dispositif de commande hydraulique selon la revendication 1, la pression de commande étant mesurée dans le chemin d'écoulement du fluide sous pression entre le bloc de retenue (6, 8) côté écoulement et une arête de commande d'écoulement (74) du distributeur (2).
  3. Dispositif de commande hydraulique selon l'une quelconque des revendications précédentes, le bloc de retenue (6, 8) étant doté d'un piston de poussée (98) qui peut être soumis à une pression de commande de déblocage (Px) pour être débloqué, la pression de commande correspondant à la pression de commande de déblocage.
  4. Dispositif de commande hydraulique avec un bloc de retenue (6, 8) selon la revendication 3, le piston de poussée (98) étant soumis à la pression de charge côté écoulement dans le sens de fermeture du bloc de retenue (6, 8).
  5. Dispositif de commande hydraulique selon l'une quelconque des revendications précédentes, un bloc de retenue (6, 8) étant respectivement affecté à l'alimentation en fluide sous pression et à l'écoulement de fluide sous pression, et la plus élevée des pressions étant prélevée en tant que pression de commande entre les blocs de retenue (6, 8) et le distributeur (2) via un sélecteur de circuit (36).
  6. Dispositif de commande hydraulique selon la revendication 4, la plus élevée des pressions suivantes - pression de commande de déblocage, pression en aval d'un diaphragme de mesure d'alimentation du distributeur (2) et pression en aval d'un diaphragme de mesure d'écoulement - étant prélevée par un dispositif de sélection de circuit (128, 130, 36) comme pression de commande.
  7. Dispositif de commande hydraulique selon l'une quelconque des revendications précédentes, le bloc de retenue (6, 8) étant doté d'un piston de blocage (78) précontraint contre un siège de soupape (80), le piston de blocage étant lui-même doté d'un siège pilote (92), contre lequel un cône pilote (90) est précontraint au moyen d'un ressort pilote (94), le cône pilote (90) pouvant être soulevé du siège pilote (92) au moyen d'un piston de poussée (98) et le piston de poussée (98) étant précontraint par un ressort de pression dans une direction opposée par rapport au piston d'arrêt (6, 8).
  8. Dispositif de commande hydraulique selon l'une quelconque des revendications précédentes, le bloc de retenue (6, 8) étant réalisé sans différence de siège.
EP04738497A 2003-05-15 2004-05-10 Dispositif de commande hydraulique Expired - Lifetime EP1623123B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10321914A DE10321914A1 (de) 2003-05-15 2003-05-15 Hydraulische Steueranordnung
PCT/DE2004/000969 WO2004104426A1 (fr) 2003-05-15 2004-05-10 Dispositif de commande hydraulique

Publications (2)

Publication Number Publication Date
EP1623123A1 EP1623123A1 (fr) 2006-02-08
EP1623123B1 true EP1623123B1 (fr) 2007-08-15

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EP04738497A Expired - Lifetime EP1623123B1 (fr) 2003-05-15 2004-05-10 Dispositif de commande hydraulique

Country Status (6)

Country Link
US (1) US7249554B2 (fr)
EP (1) EP1623123B1 (fr)
AT (1) ATE370335T1 (fr)
DE (2) DE10321914A1 (fr)
DK (1) DK1623123T3 (fr)
WO (1) WO2004104426A1 (fr)

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DE102005029821A1 (de) 2005-04-04 2006-10-05 Bosch Rexroth Ag Wegeventil und damit ausgeführte LS-Steueranordnung
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KR101471288B1 (ko) * 2013-05-06 2014-12-09 현대중공업 주식회사 선회밀림방지장치를 구비한 굴삭기 선회장치
US10590962B2 (en) 2016-05-16 2020-03-17 Parker-Hannifin Corporation Directional control valve
SE544628C2 (en) * 2018-07-23 2022-09-27 Joab Foersaeljnings Ab Hydraulic system and method for controlling the speed and pressure of a hydraulic cylinder

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Also Published As

Publication number Publication date
EP1623123A1 (fr) 2006-02-08
ATE370335T1 (de) 2007-09-15
US20060162544A1 (en) 2006-07-27
DE502004004652D1 (de) 2007-09-27
WO2004104426A1 (fr) 2004-12-02
US7249554B2 (en) 2007-07-31
DK1623123T3 (da) 2007-12-17
DE10321914A1 (de) 2004-12-02

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