EP0053370B1 - Procédé pour le contrôle d'un mécanisme hydraulique et mécanisme hydraulique pour pratiquer ce procédé - Google Patents

Procédé pour le contrôle d'un mécanisme hydraulique et mécanisme hydraulique pour pratiquer ce procédé Download PDF

Info

Publication number
EP0053370B1
EP0053370B1 EP81109942A EP81109942A EP0053370B1 EP 0053370 B1 EP0053370 B1 EP 0053370B1 EP 81109942 A EP81109942 A EP 81109942A EP 81109942 A EP81109942 A EP 81109942A EP 0053370 B1 EP0053370 B1 EP 0053370B1
Authority
EP
European Patent Office
Prior art keywords
piston
hydraulic
pressure
low
pressure accumulator
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
Application number
EP81109942A
Other languages
German (de)
English (en)
Other versions
EP0053370A3 (en
EP0053370A2 (fr
Inventor
Friedrich Bubeck
Wilhelm Polhede
Uwe Dr. Reimpell
Friedrich Stark
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.)
Balzers und Leybold Deutschland Holding AG
Original Assignee
Leybold Heraeus GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Leybold Heraeus GmbH filed Critical Leybold Heraeus GmbH
Publication of EP0053370A2 publication Critical patent/EP0053370A2/fr
Publication of EP0053370A3 publication Critical patent/EP0053370A3/de
Application granted granted Critical
Publication of EP0053370B1 publication Critical patent/EP0053370B1/fr
Expired legal-status Critical Current

Links

Images

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
    • F15B11/046—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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
    • F15B2211/31535—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having multiple pressure sources and a single 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check 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
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/46—Control of flow in the return line, i.e. meter-out 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate 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

Definitions

  • the invention relates to a method for controlling a hydraulic actuator with a hydraulic cylinder, a hydraulic piston, a high-pressure source and a low-pressure accumulator for the pressure medium and with lines opening into the hydraulic cylinder for connecting the cylinder space sections separated from the piston to the high-pressure source or the low-pressure accumulator which during a first phase of movement of the piston from its one end position to its other, the enlarging space section of the hydraulic cylinder is connected to the high pressure source to accelerate the piston, while the shrinking space section is connected to the low pressure accumulator, and during a second Movement phase of the piston, the enlarging cylinder chamber is connected to the low-pressure accumulator and a braking of the piston by an increase in pressure in the decreasing cylinder chamber section by interrupting the connection m it is caused by the low pressure accumulator.
  • a control method of this type is known from DE-B-16 50 330.
  • the speed of the piston during its movement from one end position to the other is essentially uniform and is determined or limited by the amount of pressure medium delivered or by two throttles, one of which is arranged in the pressure medium supply line and one in the pressure medium discharge line.
  • the end position is braked by shutting off the unhindered pressure medium outflow from the reducing space shortly before the end of the piston movement.
  • the present invention is based on the object of proposing a control method of the type mentioned at the outset, in which the pressure of the pressure medium becomes fully effective unhindered by throttles in order to achieve the fastest possible sequence of the actuating process.
  • this object is achieved in that the deceleration phase immediately follows the acceleration phase, that the reversal takes place for the purpose of the transition from the acceleration phase to the deceleration phase at a time in which the piston has traveled about half its way and that for reversing the acceleration phase into the deceleration phase the pressure medium supply from the pressure medium source to the enlarging cylinder chamber section is blocked, and that during the deceleration phase pressure medium is displaced from the shrinking cylinder chamber section due to the inertia of the masses to be braked into a high-pressure accumulator.
  • the pressure of the pressure medium is effective unhindered during the acceleration phase, so that an optimal acceleration of the piston with its actuating mass can be achieved.
  • the deceleration phase begins, in that a connection is established between the space that is shrinking and the high-pressure source designed as a high-pressure accumulator.
  • the pressure of the high-pressure accumulator is thus also used for braking, so that the acceleration force is equal to the deceleration force.
  • the hydraulic cylinder is denoted by 1, the hydraulic piston displaceably arranged therein by 2 and the actuating mass connected by a piston rod 3 to the piston 2 by 4.
  • 4 can e.g. B. the closure member of a slide or a valve.
  • the left side of the cylinder 1 is connected to a high-pressure accumulator 6 via a valve 5 and to the low-pressure accumulator 8 via a valve 7.
  • the valve 7 is bridged by a check valve 9, which is installed in such a way that the pressure of the accumulator 6 does not occur in the low-pressure accumulator 8.
  • the right side of the cylinder 1 is connected to a further high-pressure accumulator 12 via a valve 11 and to the low-pressure accumulator 8 via the valve 13.
  • the check valve bridging the valve 13 is designated by 14.
  • the Valves 5, 7, 11 and 13 can be actuated automatically, with the aid of the control unit 15 shown as a block.
  • the check valves 18 and 19 which can be opened in the direction of the respective high-pressure accumulators 6 and 12 intended.
  • the movement of the piston 2 with the mass 4 from its left end position into its right end position takes place as follows: from the initially closed valves, the valve 5 to the high-pressure accumulator 6 and the valve 13 to the low-pressure accumulator 8 are opened at the time t o . This increases the pressure in the cylinder space 16 to the left of the piston 2, so that the piston 2 is accelerated with the mass 4 to the right.
  • the hydraulic fluid located in the cylinder chamber 17 to the right of the piston 2 flows through the valve 13 into the low-pressure accumulator.
  • the high-pressure accumulator 6 and the low-pressure accumulator 8 are separated from one another by the check valve 9.
  • the piston 2 reaches its right-hand end position (shown in broken lines and denoted by 2 '). In a corresponding manner, the piston 2 can be moved from right to left.
  • the valves 11 and 7 are first opened, whereby the acceleration phase begins.
  • the delay phase is initiated by closing these two valves and opening valve 13.
  • FIGS. 2a to 2c show a movement sequence in which the pressure reversal is carried out half way of the piston 2 or after half the time of the entire movement sequence. In such a case, the acceleration and deceleration values can be chosen to be the same. In practice, this means that the pressure in the accumulators 6 and 12 can be the same or only a high-pressure accumulator is required.
  • control valves for reversing the pressures during the piston movement can lead to disadvantages if a control valve z. B. does not switch at the right time due to stiffness. This can be avoided if the oil flows control themselves depending on the path, as is shown, for example, in FIG. 3.
  • the sections 20 and 21 of the piston rod 3 fastened on both sides to the piston 2 are designed as control pistons.
  • the oil supply and discharge channels are formed by bores 31 and 32 in the cylinder jacket; they can be expanded on the cylinder inner wall to form ring channels or control grooves 22, 23, 24, 25. These control grooves correspond to chamfered control edges 27, 28, 29, 30 on the piston and on sections 20 and 21 of the piston rod.
  • valves 11 and 13 are opened at the start by the control member; Valves 5 and 7 remain closed.
  • the pressure oil flows from the high-pressure accumulator 6 via valve 11, line 32 into the annular channel 23 and further into the cylinder space 17.
  • the oil to be displaced from the cylinder space 16 flows via the annular channel 24 into the line 31 and via the check valve 33 into the low-pressure accumulator 8
  • the control edge 28 of the control piston 21 closes the ring channel 23; the high-pressure oil inflow is shut off.
  • the control edge 30 of the piston 2 now opens the annular channel 25, which is connected to the low-pressure accumulator 8 via the already opened valve 13.
  • the previous oil flow via ring channel 24 and check valve 33 into the low-pressure accumulator 8 is interrupted by the control edge 29 of the piston 2 and the ring channel 22 is opened by the control edge 27 of the control piston 20, so that the oil to be displaced via check valve 18 in the High-pressure accumulator 6 must be promoted.
  • the desired deceleration pressure now prevails in the cylinder space 16, while only the pressure of the low-pressure accumulator 8 required for refilling acts in the annular space 17.
  • a line system 26 with adjustable throttles 35 and 36 is provided, which in the amount of Control piston 20 and 21 opens and communicates with a storage tank 37.
  • the position of the orifices 38 and 39 is selected so that they are only released by the associated control piston shortly before it reaches its one end position (the left control piston has its left end position and the right piston has its right end position).
  • a small amount of oil is then discharged into the storage tank 37 via the line system 26 and via the associated throttle, as a result of which the piston safely reaches its end position.
  • the check valves 33 and 34 bridging the valves 7 and 13 are arranged in the opposite direction to the check valves 9 and 13.
  • the check valves in the object of FIG. 1 fulfill the task of keeping the low-pressure accumulator constantly separate from the high-pressure accumulator.
  • this task is already fulfilled by the special position of the control edges and channels.
  • the valves 7 and 13 could be omitted if oil to be refilled from the storage tank 37 were replaced. This is possible if the storage tank 37 is operated at atmospheric pressure and the control grooves 24, 25 are connected to the storage tank 37 (indicated by the lines 40 and 41 shown in broken lines).
  • a certain refill pressure pressure of the low-pressure accumulator
  • a suitable pressure in the high-pressure accumulator is 200 bar.
  • the pressure in the low-pressure accumulator is expediently 20 bar.

Landscapes

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

Claims (8)

1. Procédé de commande d'un actionneur hydraulique comprenant un cylindre hydraulique (1), un piston hydraulique (2), une source haute pression (6, 12), un réservoir basse pression (8, 37) pour le fluide de pression et des canalisations débouchant dans le cylindre hydraulique (1) pour relier ses chambres (16, 17) séparées par le piston à la source haute pression ou au réservoir basse pression; et dans lequel pendant une première phase du mouvement du piston (2) entre ses deux positions limites, la chambre croissante du cylindre hydraulique (1) est reliée à la source haute pression (6, 12) pour accélérer le piston, tandis que la chambre décroissante est reliée au réservoir basse pression (8, 37), et pendant une seconde phase du mouvement du piston (2), la chambre croissante du cylindre est reliée au réservoir basse pression et le piston est freiné par une élévation de pression dans la chambre décroissante, due à l'interruption de la liaison avec le réservoir basse pression (8, 37), ledit procédé étant caractérisé en ce que la phase de décélération suit immédiatement la phase d'accélération; l'inversion pour passer de la phase d'accélération à la phase de décélération se fait à un instant où le piston a effectué sensiblement la moitié de sa course; l'alimentation de la chambre décroissante du cylindre en fluide par la source haute pression (6, 12) est fermée pour l'inversion de la phase d'accélération à la phase de décélération; et pendant la phase de décélération, du fluide est refoulé de la chambre décroissante du cylindre dans un réservoir haute pression (6, 12) par suite de l'inertie des masses à freiner (2, 3, 4).
2. Procédé selon revendication 1, caractérisé en ce que l'inversion est automatique.
3. Actionneur hydraulique pour la mise en oeuvre du procédé selon une des revendications 1 ou 2, comprenant un cylindre hydraulique (1), un piston hydraulique (2), une source haute pression (6, 12), un réservoir basse pression (8, 37) pour le fluide de pression, des canalisations débouchant dans le cylindre hydraulique (1) pour relier sa chambre à la source haute pression ou au réservoir basse pression, et des moyens d'inversion de ces liaisons pendant le mouvement du piston hydraulique (2) entre ses positions limites, ledit actionneur étant caractérisé en ce que les chambres du cylindre (16, 17) formées par le piston (2) sont reliées chacune par une valve (5, 11) avec un clapet de nonretour (18, 19) en parallèle à la source haute pression (6, 12) et par une valve (7, 13) en parallèle avec un clapet de nonretour (9, 14) au réservoir basse pression (8, 37).
4. Actionneur hydraulique selon revendication 3, caractérisé en ce que le piston (2) présente deux arêtes de commande (29, 30) qui interagissent chacune avec un orifice de commande (24, 25) du cylindre, relié au réservoir basse pression (8, 37); et un piston de commande (20, 21) est prévu de chaque côté du piston (2) et présente une arête de commande (27, 28) interagissant avec un orifice de commande (22, 23) du cylindre, que la valve de commande (5, 11) en parallèle avec le clapet de nonretour (18, 19) relie à la source haute pression (6, 12), les orifices de commande (22, 24; 23, 25) et les arêtes de commande (27, 29; 28, 30) affectés à une chambre du cylindre (16, 17) sont disposés de façon que l'orifice de commande (24, 25) relié au réservoir basse pression s'ouvre quand l'orifice de commande (22, 23) relié à la source haute pression se ferme et inversement.
5. Actionneur hydraulique selon revendication 4, caractérisé en ce que le piston (2) est équipé d'une tige (3) fixée sur ses deux faces; et des secteurs de la tige (3) sont réalisés en pistons de commande (20, 21
6. Actionneur hydraulique selon une des revendications 4 ou 5, caractérisé en ce qu'une partie au moins des orifices de commande (22 à 25) situés sur la paroi intérieure du cylindre hydraulique est réalisée sous forme de gorge annulaire.
7. Actionneur hydraulique selon une quelconque des revendications 3 à 6, caractérisé en ce que le réservoir basse pression (37) est un réservoir fonctionnant sous la pression atmosphérique.
8. Actionneur hydraulique selon une quelconque des revendications 4 à 7, caractérisé en ce qu'un réservoir (37) est relié à la chambre du cylindre hydraulique (1) par des canalisations équipées d'étrangleurs réglables (35, 36); et la position des embouchures (38, 39) des lignes équipées d'étrangleurs (35, 36) est choisie de façon que le piston de commande correspondant (20 ou 21) les dégage juste avant d'atteindre ses positions limites.
EP81109942A 1980-11-27 1981-11-27 Procédé pour le contrôle d'un mécanisme hydraulique et mécanisme hydraulique pour pratiquer ce procédé Expired EP0053370B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3044675 1980-11-27
DE19803044675 DE3044675A1 (de) 1980-11-27 1980-11-27 Verfahren zur steuerung eines hydraulischen antriebs und fuer die durchfuehrung dieses steuerungsverfahrens geeigneter hydraulischer antrieb

Publications (3)

Publication Number Publication Date
EP0053370A2 EP0053370A2 (fr) 1982-06-09
EP0053370A3 EP0053370A3 (en) 1983-05-04
EP0053370B1 true EP0053370B1 (fr) 1986-10-15

Family

ID=6117710

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81109942A Expired EP0053370B1 (fr) 1980-11-27 1981-11-27 Procédé pour le contrôle d'un mécanisme hydraulique et mécanisme hydraulique pour pratiquer ce procédé

Country Status (2)

Country Link
EP (1) EP0053370B1 (fr)
DE (1) DE3044675A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3206162A1 (de) * 1982-02-20 1983-09-01 Hartmann & Lämmle GmbH & Co KG, 7255 Rutesheim Antrieb fuer eine mittels eines hydromotors bewegbaren masse
SE437861B (sv) * 1983-02-03 1985-03-18 Goran Palmers Anordning vid medelst hydraul-cylinder drivna maskiner med en av en drivkella via en energiackumulatordriven pump
DE3583147D1 (de) * 1985-12-13 1991-07-11 Schenck Ag Carl Verfahren und vorrichtung zur erzeugung von stossartigen belastungen an einem pruefling.
DE4439667C2 (de) * 1994-11-07 1998-07-02 Festo Ag & Co Arbeitszylinder
DE102014212129A1 (de) * 2014-06-25 2015-12-31 Robert Bosch Gmbh Hydraulische Anordnung
KR102092481B1 (ko) * 2018-12-19 2020-04-20 주식회사 두산 건설장비용 선회모터의 반전방지 밸브

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1650330B2 (de) * 1966-11-30 1978-07-06 The Cessna Aircraft Co., Wichita, Kan. (V.St.A.) Einrichtung zum Abbremsen eines doppeltwirkenden hydraulischen Stellantriebs am Hubende

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1263514B (de) * 1961-07-27 1968-03-14 Siemens Ag Hydraulischer Antrieb
FR1563208A (fr) * 1968-03-01 1969-04-11
CH473319A (de) * 1968-06-19 1969-05-31 Hydrel Ag Maschf Vollhydraulische Vorrichtung an Maschine oder Apparat mit geradlinig hin- und hergehendem Teil, für weitgehend last- und geschwindigkeitsunabhängige Genauigkeitsumsteuerung der Bewegung des Teils zwischen zwei einstellbaren Umsteuerpunkten
US3563273A (en) * 1968-10-28 1971-02-16 Carl R Mills Actuator valve
FR2129156A5 (fr) * 1971-03-17 1972-10-27 Citroen Sa
DE2245129A1 (de) * 1972-09-14 1974-03-21 Bosch Gmbh Robert Arbeitszylinder
NL7214004A (fr) * 1972-10-17 1974-04-19
CH568495A5 (fr) * 1974-03-11 1975-10-31 Haeny & Cie Ag
NL182162C (nl) * 1977-01-10 1988-01-18 Hydraudyne Bv Inrichting voor het hydraulisch of pneumatisch aandrijven en afremmen van een werktuig.
DE2821489C3 (de) * 1978-05-17 1981-03-19 Danfoss A/S, 6430 Nordborg Ventilanordnung mit zwei aufeinander gleitenden Ventilteilen
GB2035464B (en) * 1978-11-28 1982-12-15 Dartec Ltd Actuator protection assemblies
DE2851478A1 (de) * 1978-11-28 1980-06-04 Mts Systems Gmbh Schnell schaltende antriebsvorrichtung

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1650330B2 (de) * 1966-11-30 1978-07-06 The Cessna Aircraft Co., Wichita, Kan. (V.St.A.) Einrichtung zum Abbremsen eines doppeltwirkenden hydraulischen Stellantriebs am Hubende

Also Published As

Publication number Publication date
EP0053370A3 (en) 1983-05-04
DE3044675A1 (de) 1982-07-08
EP0053370A2 (fr) 1982-06-09

Similar Documents

Publication Publication Date Title
DE3323363C2 (fr)
EP2644903B1 (fr) Procédé et dispositif de commande hydraulique pour la commande d'un consommateur
DE19734966B4 (de) Hydraulikhammer
DE112005002529B4 (de) Hydraulisch betätigte Giesseinheit
DE2512480B2 (de) Ventilvorrichtung für einen hydraulisch betätigbaren elektrischen Leistungsschalter
DE2102591A1 (de) Hydraulik Pumpe
EP0053370B1 (fr) Procédé pour le contrôle d'un mécanisme hydraulique et mécanisme hydraulique pour pratiquer ce procédé
DE3818068A1 (de) Geschwindigkeitsreduzierer fuer pneumatische antriebe
DE2649775A1 (de) Ventil mit einem laengsschieber
DE3341641C2 (fr)
DE2003584A1 (de) Einrichtung zur Druckmittelverteilung
DE2647372A1 (de) Einrichtung bei einem lastbewegenden hydraulikmotor zum verhindern einer unkontrollierbaren lastbewegung bei einem leitungsbruch
DE1007627B (de) Steuerventil mit Kolbenschieber fuer hydraulische Pressen
DE2647140A1 (de) Ventil mit einem laengsschieber
DE69420713T2 (de) Durch druckmittel angetriebene vorrichtung die eine lineare bewegung ausführt
DE19652298A1 (de) Hochdruckpumpenanordnung
DE873209C (de) Einrichtung fuer druckmittelbetriebene Anlagen
DE3016929C2 (fr)
DE112005002551B4 (de) Hydraulisch betätigte Giesseinheit
DE1627617B1 (de) Ölhydraulische Steuerung für die Schritt- bzw. Drehschrittbewegung eines Schmiedemanipulators
EP3447313A1 (fr) Vérin à position intermédiaire et procédé d'actionnement d'un tel vérin
DE549480C (de) Hydraulischer Antrieb fuer Arbeits-, insbesondere Werkzeugmaschinen mit langen Huebenund grossen Geschwindigkeiten des hin und her gehenden Teiles
DE856393C (de) Kolbenschiebersteuerung fuer Zentralschmierapparate
EP0152937B1 (fr) Elément de commande hydraulique pour navettes de tissage
DE2234986C3 (de) Pneumatische Folgesteuereinrichtung für die Steuerung mehrerer Servomotoren

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19811208

AK Designated contracting states

Designated state(s): CH FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): CH FR GB IT LI

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH FR GB IT LI

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19881127

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19881130

Ref country code: CH

Effective date: 19881130

GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19890731

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

ITTA It: last paid annual fee