EP1793050B1 - Hydraulikzylinder mit Endlagendämpfung - Google Patents

Hydraulikzylinder mit Endlagendämpfung Download PDF

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Publication number
EP1793050B1
EP1793050B1 EP06017903.3A EP06017903A EP1793050B1 EP 1793050 B1 EP1793050 B1 EP 1793050B1 EP 06017903 A EP06017903 A EP 06017903A EP 1793050 B1 EP1793050 B1 EP 1793050B1
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EP
European Patent Office
Prior art keywords
hydraulic cylinder
hydraulic
valve
piston
plunger
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
EP06017903.3A
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English (en)
French (fr)
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EP1793050A3 (de
EP1793050A2 (de
Inventor
Michael Stucke
Oliver Schwenkkrauss
Hans-Peter Lavergne
Thomas Zitterbart
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
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Liebherr Hydraulikbagger GmbH
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Publication of EP1793050A2 publication Critical patent/EP1793050A2/de
Publication of EP1793050A3 publication Critical patent/EP1793050A3/de
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Publication of EP1793050B1 publication Critical patent/EP1793050B1/de
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Classifications

    • 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
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E02F9/2214—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for reducing the shock generated at the stroke end
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or 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
    • F15B11/02—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
    • F15B11/046—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed depending on the position of the working member
    • F15B11/048—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed depending on the position of the working member with deceleration control
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/421—Flow control characterised by the type of actuation mechanically
    • F15B2211/424—Flow control characterised by the type of actuation mechanically actuated by an output member of the 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • 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
    • F15B2211/755—Control of acceleration or deceleration of the output member
    • 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
    • F15B2211/85—Control during special operating conditions
    • F15B2211/853—Control during special operating conditions during stopping

Definitions

  • the invention relates to a hydraulic cylinder with a piston and a piston rod according to the preamble of claim 1.
  • end position damping In order to avoid an abrupt stopping of a movement caused by a hydraulic cylinder when reaching the end position of the piston in the hydraulic cylinder, it is already known to provide end position damping. With simple cylinders and small piston speeds, stop rings are usually sufficient to catch the pistons at the stroke end. For larger piston speeds, however, a special cushioning is constructive. Here there is the possibility of damping by means of so-called damping pins on the piston rods. Frequently, hydraulic end position dampers are used. In this case, the kinetic energy of the piston mass is reduced by the fact that the rest of the volume displaced by the piston oil volume by gaps or throttles, which are provided in the end position of the cylinder, are passed.
  • Such a hydraulic cylinder is off GB 519,321 A known.
  • the object of the invention is now to equip conventional hydraulic cylinder optionally with a bottom-side damping.
  • series hydraulic cylinders without end cushioning to convert accordingly.
  • the throttle valve may consist of a displaceable in a housing via a plunger valve unit, which by actuation of the plunger in the Fluid path of the hydraulic fluid is movable to throttle in this position, the hydraulic fluid flow rate.
  • the end position damping acts only at the stroke end, a check valve is integrated in the throttle valve, over which the cushioning can be bypassed at Hubbeginn.
  • the plunger via which the displaceable valve unit can be brought into the throttle valve shortly before reaching the end position of the piston in the throttle position, acted upon by a gripper mechanism of a construction or handling machine.
  • a gripper mechanism of a construction or handling machine acted upon by a gripper mechanism of a construction or handling machine.
  • a hydraulic cylinder 10 is shown schematically.
  • a piston 12 with a piston rod 14 is slidably disposed.
  • a junction point A in the hydraulic cylinder 10 opens a hydraulic line 16.
  • a junction point B of the hydraulic cylinder 10 opens a hydraulic line 18.
  • the hydraulic lines 16 and 18 are part of a known per se in the prior art hydraulic circuit having a hydraulic sump 20 in the illustrated embodiment.
  • a control valve 22 serves for switching.
  • a switchable throttle valve 24 is integrated between the switching valve 22 and the mouth B of the hydraulic line 18.
  • the switchable throttle valve 24 has a housing 26, into which mouth points P and Z of the line 18 lead.
  • the housing 26 has a centrally mounted cylindrical chamber 28, in which the throttle valve 30 is movable in the longitudinal direction back and forth.
  • the length of the cylindrical chamber 28 and the throttle valve 30 is dimensioned so that the throttle valve between two end positions is movable back and forth.
  • the respective end positions are in the FIGS. 2 and 3 shown.
  • the throttle valve 30 In the opposite end position according to FIG. 3 is the throttle valve 30 is pushed between the orifice points P and Z, so that the hydraulic oil flowing from P to Z is throttled through this throttle valve 30.
  • the throttle valve 30 is only when the piston 12 is short of the end stop, in the end position according to FIG. 3 pressed.
  • a mechanically operated plunger 32 which transmits the movement on a displaceably mounted in the housing 26 valve piston.
  • the plunger can be actuated for example by a gripping mechanism of a construction vehicle or a handling vehicle, such as a wooden gripper. This operation is kinematically switched so that it takes place shortly before reaching the end stop and thus only leads to damping at this time.
  • valve piston 34 always in the in FIG. 2 shown end position, unless it is on the plunger 32 in the direction of the end position according to FIG. 3 is forcibly moved.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mining & Mineral Resources (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

  • Die Erfindung betrifft einen Hydraulikzylinder mit einem Kolben und einer Kolbenstange nach dem Oberbegriff des Anspruchs 1.
  • Um ein abruptes Abstoppen einer durch einen Hydraulikzylinder bewirkten Bewegung bei Erreichen der Endlage des Kolbens im Hydraulikzylinder zu vermeiden, ist es bereits bekannt, Endlagendämpfungen vorzusehen. Bei einfachen Zylindern und kleinen Kolbengeschwindigkeiten reichen in der Regel Anschlagringe aus, um die Kolben am Hubende abzufangen. Bei größeren Kolbengeschwindigkeiten jedoch ist eine besondere Endlagendämpfung konstruktiv vorzusehen. Hier gibt es die Möglichkeit einer Dämpfung mittels sogenannter Dämpfungszapfen auf den Kolbenstangen. Häufig werden hydraulische Endlagendämpfer verwendet. Dabei wird die kinetische Energie der Kolbenmasse dadurch vermindert, dass der Rest des vom Kolben verdrängten Ölvolumens durch Spalte oder Drosseln, die im Endlagenbereich der Zylinder vorgesehen sind, geleitet werden.
  • Nachteilig bei diesen Lösungen ist es, dass die jeweiligen Hydraulikzylinder von vorneherein konstruktiv mit der Endlagendämpfung ausgestattet sein müssen. Das bedeutet, dass eine Nachrüstung von einfachen Serienhydraulikzylindern nicht möglich ist. Vielmehr müssen bereits vorhandene Serienhydraulikzylinder durch die speziell ausgestalteten Hydraulikzylinder mit Endlagendämpfung ausgetauscht werden.
  • Ein solcher Hydraulikzylinder ist aus GB 519 321 A bekannt.
  • Aufgabe der Erfindung ist es nun, konventionelle Hydraulikzylinder optional mit einer bodenseitigen Dämpfung auszustatten. Dabei sollen sich Serienhydraulikzylinder ohne Endlagendämpfung entsprechend umrüsten lassen.
  • Erfindungsgemäß wird diese Aufgabe durch einen Hydraulikzylinder mit den Merkmalen des Anspruchs 1 gelöst.
  • Diese Lösung ermöglicht es, Serienhydraulikzylinder mit einer Endlagendämpfung nachzurüsten. Dies ist dadurch bedingt, dass der eingesetzte Hydraulikzylinder nicht verändert werden muss. Dadurch entfällt auch die zusätzliche Bereitstellung eines neuen Hydraulikzylinders für den Ersatzteilbedarf. Der Anwender kann zu jedem Zeitpunkt entscheiden, ob er eine Endlagendämpfung wünscht oder nicht. Soweit das Drosselventil auf der Hydraulikfluidzulaufseite angeordnet ist, kann ein den Hydraulikzylinder schonendes und energieeffizientes Dämpfungsprinzip durch die Drosselung des Hydraulikzylinderzulauffluids erfolgen.
  • Vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den sich an den Hauptanspruch anschließenden Unteransprüchen.
  • Demnach kann das Drosselventil aus einer in einem Gehäuse über einen Stößel verschiebbaren Ventileinheit bestehen, die durch Betätigung des Stößels in den Fluidweg des Hydraulikfluids bewegbar ist, um in dieser Position den Hydraulikfluidvolumenstrom zu drosseln.
  • Damit die Endlagendämpfung nur beim Hubende wirkt, ist im Drosselventil ein Rückschlagventil integriert, über das die Endlagendämpfung bei Hubbeginn umgangen werden kann.
  • Erfindungsgemäß wird der Stößel, über den die verschiebbare Ventileinheit in dem Drosselventil kurz vor Erreichen der Endlage des Kolbens in die Drosselposition gebracht werden kann, über eine Greifermechanik einer Bau- oder Umschlagmaschine beaufschlagt. Hierdurch wird erreicht, dass die Bewegung des Kolbens im Hydraulikzylinder erst in einem gewünschten Endbereich wirksam wird. So kann beispielsweise eine Endlagendämpfung bei einem Hydraulikzylinder, der für einen Holzgreifer eingesetzt wird, vorgesehen werden.
  • Es wird eine Bau- oder Umschlagmaschine mit mindestens einem Hydraulikzylinder entsprechend dem vorher beschriebenen Aufbau gesondert unter Schutz gestellt.
  • Weitere Einzelheiten und Vorteile der Erfindung werden anhand eines in der Zeichnung dargestellten Ausführungsbeispiels näher erläutert. Es zeigen:
    • Figur 1:
    ein Schaltschema des schematisch dargestellten Hydraulikzylinders gemäß einer Ausführungsform der vorliegenden Erfindung,
    Figur 2:
    das in der Hydraulikleitung des Hydraulikzylinders gemäß Figur 1 eingebaute Drosselventil in einer ersten Endlage und
    Figur 3:
    das vorgenannte Drosselventil in einer anderen Endlage.
  • In der Figur 1 ist ein Hydraulikzylinder 10 schematisch dargestellt. In diesem ist ein Kolben 12 mit einer Kolbenstange 14 verschieblich angeordnet. In einem Einmündungspunkt A im Hydraulikzylinder 10 mündet eine Hydraulikleitung 16. In dem Einmündungspunkt B des Hydraulikzylinders 10 mündet eine Hydraulikleitung 18. Die Hydraulikleitungen 16 und 18 sind Teil eines an sich im Stand der Technik bekannten Hydraulikkreislaufs, der im hier dargestellten Ausführungsbeispiel einen Hydrauliksumpf 20 aufweist. Zur Schaltung dient ein Steuerventil 22. Entsprechend der vorliegenden Erfindung ist zwischen dem Schaltventil 22 und der Mündung B der Hydraulikleitung 18 ein schaltbares Drosselventil 24 integriert. Das schaltbare Drosselventil 24 weist ein Gehäuse 26 auf, in welches Mündungspunkte P und Z der Leitung 18 hineinführen. Im Inneren weist das Gehäuse 26 eine zentrisch gelagerte zylindrische Kammer 28 auf, in der das Drosselventil 30 in Längsrichtung hin und her bewegbar ist. Dabei ist die Länge der zylindrischen Kammer 28 und des Drosselventils 30 so bemessen, dass das Drosselventil zwischen zwei Endlagen hin und her bewegbar ist. Die jeweiligen Endlagen sind in den Figuren 2 und 3 dargestellt.
  • In der Figur 2 befindet sich das Drosselventil 30 in einer Endlage, in der es nicht zwischen den Mündungen P und Z angeordnet ist. Daher kann das jeweils eintretende Hydraulikfluid durch die zylindrische Öffnung 28 hindurch ungehindert von der Mündung P zur Mündung Z und umgekehrt fließen. Hier ist also keine Drosselwirkung erzielt.
  • In der gegenüberliegenden Endstellung gemäß Figur 3 ist das Drosselventil 30 zwischen die Mündungspunkte P und Z geschoben, so dass das von P nach Z fließende Hydrauliköl über dieses Drosselventil 30 gedrosselt wird. Das Drosselventil 30 wird erst dann, wenn der Kolben 12 kurz vor dem Endanschlag ist, in die Endposition gemäß Figur 3 gedrückt. Hierzu dient ein mechanisch bedienbarer Stößel 32, der auf einem im Gehäuse 26 verschieblich gelagerten Ventilkolben die Bewegung überträgt. Dabei kann der Stößel beispielsweise durch eine Greifmechanik eines Baufahrzeuges oder eines Umschlagfahrzeuges, beispielsweise einem Holzgreifer betätigt werden. Diese Betätigung ist kinematisch so geschaltet, dass sie erst kurz vor Erreichen des Endanschlags erfolgt und damit erst zu diesem Zeitpunkt zur Dämpfung führt.
  • Wird das Steuerventil nun auf Position A geschaltet, wird das ringseitige Hydraulikvolumen aus der Mündung B gedrückt, obwohl sich der Ventilkolben 34 in seiner in Figur 3 gezeigten Endlage befindet, kann das Hydraulikfluid über ein im Drosselventil 30 integriertes Rückschlagventil 36 ungehindert abfließen, bis der Ventilkolben 34 den Zylinderraum 28 genügend geöffnet hat. Dadurch wird ein verzögerungsfreies Anfahren des Hydraulikzylinders 10 nach dem Umschalten gewährleistet.
  • Die in dem zylindrischen Raum 28 vorherrschenden Drücke bewirken, dass der Ventilkolben 34 immer in der in Figur 2 gezeigten Endlage verbleibt, es sei denn, dass er über den Stößel 32 in Richtung der Endlage gemäß Figur 3 zwangsverschoben wird.

Claims (3)

  1. Hydraulikzylinder (10) mit einem Kolben (12) mit Kolbenstange (14), wobei am Hydraulikzylinder (10) zwei Hydraulikleitungen (16, 18) mit einem Steuerventil (22) anschließen, wobei in mindestens einer Hydraulikleitung (18) ein schaltbares Drosselventil (30) eingesetzt ist, das von einer Stellung, in der das Hydraulikfluid ungehindert strömen kann in eine Stellung, in der das Drosselventil (24) wirksam ist, umstellbar ist wobei das Drosselventil (24) aus einer in einem Gehäuse (26) über einen Stößel (32) verschiebbaren Ventileinheit besteht, die durch Betätigung des Stößels (32) in den Fluidweg des Hydraulikfluids bewegbar ist, um in dieser Position den Hydraulikfluidvolumenstrom zu drosseln,
    dadurch gekennzeichnet,
    dass der Stößel (32) von einer Greifermechanik einer Bau- oder Umschlagmaschine beaufschlagbar ist.
  2. Hydraulikzylinder nach Anspruch 1, dadurch gekennzeichnet, dass in dem Drosselventil ein Rückschlagventil integriert ist.
  3. Bau- oder Umschlagmaschine mit mindestens einem Hydraulikzylinder (10) nach einem der vorgenannten Ansprüche.
EP06017903.3A 2005-12-05 2006-08-28 Hydraulikzylinder mit Endlagendämpfung Active EP1793050B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200520018999 DE202005018999U1 (de) 2005-12-05 2005-12-05 Hydraulikzylinder mit Endlagendämpfung

Publications (3)

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EP1793050A2 EP1793050A2 (de) 2007-06-06
EP1793050A3 EP1793050A3 (de) 2011-08-03
EP1793050B1 true EP1793050B1 (de) 2015-10-14

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DE (1) DE202005018999U1 (de)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB519321A (en) * 1937-09-29 1940-03-21 Vickers Inc Improvements in hydraulic feed control system
JPS57161307A (en) * 1981-09-28 1982-10-04 Amada Co Ltd Adjusting device of stroke in cylinder mechanism
US4915014A (en) * 1985-05-08 1990-04-10 Deere & Company Disk harrow hydraulic wing balancing system
DE20114538U1 (de) * 2001-09-03 2001-10-31 Küpper-Weisser GmbH, 78199 Bräunlingen Hydrauliksystem für die Eigengewichtsentlastung von Anbaugeräten
WO2002014698A1 (en) * 2000-08-15 2002-02-21 Parker Hannifin Ab Pneumatic actuator system
WO2004099626A1 (en) * 2003-05-07 2004-11-18 G.Fluid S.R.L. Pilote check valve with variable throttle
WO2005005843A1 (de) * 2003-07-10 2005-01-20 Hydac System Gmbh Fluidkühlvorrichtung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3465519A (en) * 1967-08-18 1969-09-09 Webster Electric Co Inc Hydraulic flow controlling apparatus
KR920701697A (ko) * 1989-06-26 1992-08-12 가따다 데쯔야 유압 회로 장치
FR2699609B1 (fr) * 1992-12-22 1995-02-10 Hydromo Procédé et dispositif pour la mise en mouvement ou l'arrêt d'un moteur hydraulique entraînant un ensemble présentant une grande inertie.
US6868672B2 (en) * 2003-05-13 2005-03-22 Sauer-Danfoss, Inc. Method of controlling a swinging boom and apparatus for controlling the same

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB519321A (en) * 1937-09-29 1940-03-21 Vickers Inc Improvements in hydraulic feed control system
JPS57161307A (en) * 1981-09-28 1982-10-04 Amada Co Ltd Adjusting device of stroke in cylinder mechanism
US4915014A (en) * 1985-05-08 1990-04-10 Deere & Company Disk harrow hydraulic wing balancing system
WO2002014698A1 (en) * 2000-08-15 2002-02-21 Parker Hannifin Ab Pneumatic actuator system
DE20114538U1 (de) * 2001-09-03 2001-10-31 Küpper-Weisser GmbH, 78199 Bräunlingen Hydrauliksystem für die Eigengewichtsentlastung von Anbaugeräten
WO2004099626A1 (en) * 2003-05-07 2004-11-18 G.Fluid S.R.L. Pilote check valve with variable throttle
WO2005005843A1 (de) * 2003-07-10 2005-01-20 Hydac System Gmbh Fluidkühlvorrichtung

Also Published As

Publication number Publication date
DE202005018999U1 (de) 2007-04-12
EP1793050A3 (de) 2011-08-03
EP1793050A2 (de) 2007-06-06

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