EP0514748B1 - Dispositif pour limiter la course d'un vérin hydraulique - Google Patents

Dispositif pour limiter la course d'un vérin hydraulique Download PDF

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Publication number
EP0514748B1
EP0514748B1 EP92108021A EP92108021A EP0514748B1 EP 0514748 B1 EP0514748 B1 EP 0514748B1 EP 92108021 A EP92108021 A EP 92108021A EP 92108021 A EP92108021 A EP 92108021A EP 0514748 B1 EP0514748 B1 EP 0514748B1
Authority
EP
European Patent Office
Prior art keywords
piston
valve
pressure
arrangement
line
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
EP92108021A
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German (de)
English (en)
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EP0514748A1 (fr
Inventor
Werner Kuttruf
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.)
BW Hydraulik GmbH
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BW Hydraulik GmbH
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Filing date
Publication date
Application filed by BW Hydraulik GmbH filed Critical BW Hydraulik GmbH
Publication of EP0514748A1 publication Critical patent/EP0514748A1/fr
Application granted granted Critical
Publication of EP0514748B1 publication Critical patent/EP0514748B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F15B15/24—Other details, e.g. assembly with regulating devices for restricting the stroke

Definitions

  • the invention relates to a device for limiting the stroke of a hydraulic cylinder according to the preamble of claim 1.
  • a stroke-dependent valve device for limiting the working movement of the piston for an auxiliary power steering device.
  • opening a valve causes a pump short circuit between the pressure and suction side of the pressure medium pump.
  • control cams are provided which are connected to the working piston and which, when the predetermined stroke end position is reached, switch off a pressure force which holds the control slide together with a spring in the rest position blocking the pump short circuit.
  • Valve and line expenditure for switching off the working pressure are relatively high in this known device.
  • the invention has for its object to provide a particularly simple and inexpensive device for limiting the stroke of the piston of a working cylinder, which can be combined with the working cylinder to form a unit in a compact design that requires structurally simple actuating elements and in which with simple means a hydromechanical Position control loop can be represented.
  • the device should be such that the stroke limitation with respect to the point in time or piston position can subsequently be easily adjusted within limits.
  • the stroke limitation is brought about by the mechanical actuation of a single valve before the predetermined end position is reached, by branching off from the pressure medium supply line such an amount of pressure medium that the working piston, which on the opposite side is exposed to the action of a constant pressure of an accumulator, in the specified end position is held hydraulically.
  • the mechanical action on the shut-off valve is not always effective, but only starts before the predetermined stroke end position of the working piston is reached.
  • For the feedback from the working piston to the shut-off valve only a relatively short distance of the entire stroke is required. It corresponds to the path from the contact closure of the towing bar with the working piston to the occurrence of the regulated state, d. H. until such a position of the slide piston is reached, in which the entire delivery of the pressure source can flow off via the branch to the tank. In this state, a hydromechanical position control loop has stabilized without the need for an external circuit.
  • shut-off valve is designed as a detachable component of the working cylinder.
  • the shut-off valve is essentially designed as follows.
  • two ring grooves lying axially one behind the other are provided, to which on the one hand the branch line and on the other hand the tank line are connected, while the slide piston has a circumferential groove adapted to the ring grooves in its axial length.
  • the first circumferential groove, to which the supply line is connected is covered by the slide piston.
  • the circumferential groove increasingly also covers the previously blocked circumferential groove, so that an increasing proportion of the delivery quantity supplied by the pressure source can flow off via the branch to the tank. Due to the fact that the diverted delivery rate does not increase suddenly, but rather over a certain period of time up to the maximum value, a sudden limitation or switching off of the working stroke of the piston is avoided.
  • the return movement of the working piston is brought about by a further reduction in the pressure on the piston bottom side of the working piston.
  • the slide piston is moved independently of the working piston by external action in the sense of a further opening of the branch line in the direction of the tank.
  • This can be done hydraulically by mechanical actuation or by actuating pistons.
  • an attachment is advantageously attached to the housing of the shut-off valve at the free end, in which two actuating pistons are mounted, by means of which the slide piston can be moved into its fully open position against the constantly acting restoring shaft.
  • the river Oder the actuating pistons are advantageously controlled with the aid of a solenoid valve.
  • the stop at the inner end of the towing bar is advantageously designed as an adjustable stop.
  • an advantageous solution of an adjustable stop provides that the stop is mounted with an internal thread on a threaded section of the tow bar, the rear end of the tow stands protruding from the device and is provided with a suitable profile for the execution of a rotating adjustment movement.
  • the stop for its part is secured against twisting in this embodiment in the hollow piston position, but is guided in an axially slidable manner.
  • the exemplary embodiment shown in the drawing includes a hydraulic cylinder (1) with a working piston (2) in the form of a differential piston, from which a hollow piston rod (3) closed at the end, which ends outside the cylinder (1).
  • the cylinder (1) is closed by a head plate (4) which delimits the working pressure chamber (5) on the piston crown side.
  • a shut-off valve (7) is detachably connected to the top plate (4).
  • a slide piston (9) is slidably mounted in a bore (8) concentric with the cylinder axis, and a return spring (10) acts on its inner end face.
  • Fig. 1 shows the slide piston (9) in its basic position, in which it is connected with its outer end face to a stop ring (11).
  • the slide piston (9) is penetrated in a central bore (12) by a towing rod (13) which extends through a bore (14) in the piston (2) into the hollow piston rod (3).
  • a ring stop (15) sits on the threaded rod (13) on a threaded section, which is guided in the longitudinal bore (16) of the piston rod (3) in a slidable manner, but secured against rotation.
  • Recesses (17) in the lateral surface of the stop (15) create a connection between the spaces on the two sides of the ring stop (15).
  • a support ring (18) is fastened to the tow bar (13) in the area of the working pressure chamber (5), which rests on the head plate (4) in the basic position and thus limits the axial mobility of the towing bar (13) in the opposite direction to the working movement of the piston (2). Furthermore, in the vicinity of the rear end of the towing bar (13), a driving ring (19) is fastened on the towing bar (19), which comes into contact with the stop ring (11) when the towing bar (13) is towing.
  • a circumferential groove (20) is incorporated on the circumference of the slide piston (9), which cooperates with two annular grooves (21, 22) in the housing (6) and is dimensioned in its axial length so that it is in the open position of the slide piston (9 ) both ring grooves (21, 22) completely covered (Fig. 3).
  • the circumferential groove (20) lies outside the inner annular groove (21), which in this position is blocked by the annular piston (9).
  • the housing for z. B. forms two piston tappets (24) which can act on the stop ring (11) when pressurized.
  • E1 a device for indicating the position of the towing bar (13) is indicated, which triggers a signal when the end piece (25) of the towing bar (13) is at the same level with the device E1.
  • a bore (26) and for the connection of the tank line T a bore (27) is provided.
  • a channel leads from the bore (26) to Pressure medium chamber (5) and on the other hand a channel to the annular groove (21).
  • the bore (27) is only connected to the annular groove (22).
  • a bore (28) is provided on the cylinder (1) for connecting a pressure medium line P2, from which a channel leads to the pressure medium space on the ring side of the piston (2).
  • the approach (23) contains a bore (30) for connecting a line (31) through which the pressure medium for acting on the tappet pistons (24) is supplied or removed.
  • the working piston (2) is in the retracted position.
  • the spool (9) of the shut-off valve (7) assumes the closed position under the action of the return spring (10).
  • the pressure medium chamber (29) can be supplied with the pressure medium from a pressure source (32) via a check valve (33).
  • On the feed line P2 is an adjustable pressure relief valve (34) on the one hand and a hydraulic pressure accumulator (35) on the other hand via a directional control valve Y2 behind the check valve. Also indicated are a pressure measuring device (36) and safety accessories (37).
  • the hydraulic pressure accumulator (35) is loaded, for. B. to a pressure of 60 bar. This pressure is in the pressure medium chamber (29) and holds the working piston (2) in the retracted position.
  • Another pressure source (38) is connected via line A1 to the bore (26) and supplies the pressure medium for the application of the working pressure chamber (5).
  • a check valve (39) prevents backflow through line A 1.
  • a switchable pressure relief valve Y3 is connected at the outgoing from the pressure source (38) line. If the valve Y3 is connected to voltage, the pressure medium flows from the pressure source (38) into the working pressure chamber (5). Since the shut-off valve (7) is closed, pressure can build up, which causes the working piston (2) to extend.
  • the extension speed depends on the delivery rate of the pressure source (38), while the pressure in the pressure medium chamber (5) (excluding external forces) depends on the area ratio of the effective piston areas and the operating pressure in the pressure medium chamber (29).
  • the extending working piston (2) comes into contact with the ring stop (17) shortly before reaching its end position with a support surface (40) provided for this purpose (start of mechanical feedback), the now moving drag rod (13) dragged along the driving ring (19) of the slide piston (9) in the opening direction.
  • the circumferential groove (20) reaches the area of the annular groove (21) and thus establishes a (branch) connection from the feed line A 1 to the tank line T.
  • part of the delivery of the pressure source (38) can flow to the tank; the extension speed of the working piston (2) is reduced because a defined counterforce is effective on the ring side of the piston (2).
  • the opening stroke of the slide piston (9) adjusts itself automatically so that the flow rate flowing in via A 1 can flow off completely via the line T.
  • the device E 1 signals this state.
  • the mechanical feedback takes up only a very small part of the total length of the working stroke of the working piston (2). It corresponds essentially to the overlap of the circumferential groove (20) with the annular groove (21).
  • the plunger pistons (24) are expediently operated with the pressure medium from the pressure source (30).
  • the line (31) is connected to the line P2 via a switchable 4/2-way valve Y1.
  • the connection T of the valve Y1 is, as usual, connected to a line leading to the tank; port A is blocked.
  • the plunger slide (9) is moved further out of its regulated position in the opening direction by extending the tappet piston (24), whereby the overlap of the circumferential groove (20) with the annular groove (21) is further increased.
  • the associated reduction in the throttle function of the shut-off valve (7) causes the pressure in the working pressure chamber (5) to drop so much that the prevailing pressure on the ring side of the working piston (2) retracts it until the starting position is reached.
  • the pressure medium that was stored in the hydraulic pressure accumulator (35) when it was extended is used for this.

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

Claims (8)

  1. Dispositif pour limiter la course d'un vérin hydraulique, notamment de presses ou analogues, comprenant un piston de travail sur les deux côtés duquel peut être appliquée la pression et se présentant sous la forme d'un piston différentiel à partir duquel s'étend sur un côté une tige de piston creuse (3), caractérisé par les particularités suivantes:
    a) la chambre de pression de travail (5) sur le côté arrière du piston est remplie au moyen d'un agent de pression provenant d'une source de pression (38) par l'intermédiaire d'une conduite d'amenée (A₁) et se vide en direction du réservoir par l'intermédiaire d'une soupape d'arrêt (7) qui est reliée coaxialement au côté du fond du piston du vérin de travail (1),
    b) la chambre (29) située sur le côté annulaire du piston de travail (2) est alimentée constamment en agent de pression par l'action d'un accumulateur de pression (35), et
    c) la soupape d'arrêt (7) contient un piston coulissant (9) qui est maintenu dans la position de fermeture par une force de rappel élastique, par exemple d'un ressort (10), piston au moyen duquel une dérivation partant de la conduite d'amenée (A₁) et allant vers le vérin de travail (1) peut être raccordée de façon réglable à une conduite (T) allant au réservoir,
    d) une tige d'entraînement (13) s'étend dans le piston coulissant et parvient par une extrémité passant par le piston de travail (2) jusqu'à l'intérieur (16) de la tige creuse (3) de ce piston de travail (2), et vient en contact avec ce dernier par une butée (15) prévue à son extrémité, avantque soit atteinte la position d'extrémité du mouvement de travail du piston de travail (2),
    e) un élément annulaire rapporté (19) est monté sur l'extrémité opposée de la tige d'entraînement (13), au moyen duquel le piston coulissant (9) est déplacé par contact dans la direction de sa position d'ouverture jusqu'à ce que soit établi un état de pleine puissance dans lequel le piston de travail (2) est maintenu hydrauliquement dans sa position d'extrémité,
    f) la soupape d'arrêt (7) est associée au moins à un coulisseau de commande (24) entraîné par l'agent de pression, qui peut agir sur le piston coulissant dans le sens de la poursuite de son mouvement d'ouverture quand le mouvement de travail du piston de travail (2) est terminé, par lequel ce dernier quitte sa position de pleine puissance qu'il occupait jusqu'alors et qui réduit la pression de l'agent de pression qui agit sur le côté arrière du piston par la poursuite de l'ouverture de la dérivation de la conduite d'amenée (A₁) vers la conduite de réservoir (T), de manière que le piston de travail (2) soit ramené en arrière vers sa position de départ en raison de la prépondérance de la contre-pression agissant sur le côté annulaire.
  2. Dispositif selon la revendication 1, caractérisé en ce que la source de pression (38) destinée à la course de travail est reliée d'une part par un clapet de non-retour (39) à la conduite d'amenée (A₁) et d'autre part par une soupape limitatrice de pression et commandable (Y₃) à une conduite de sortie.
  3. Dispositif selon la revendication 1 ou 2, caractérisé en ce que la soupape d'arrêt (7) forme un élément composant détachable du vérin de travail (1).
  4. Dispositif selon l'une des revendications 1 à 3, caractérisé en ce que sont prévues dans l'alésage (8) du boîtier destiné au piston coulissant (9) deux rainures annulaires (21, 22) disposées axialement l'une à l'arrière de l'autre, auxquelles sont raccordées d'une part la conduite de dérivation et d'autre part la conduite de réservoir (T), et en ce que la piston coulissant (9) comprend une rainure périphérique (20) qui recouvre également de façon croissante la seconde rainure annulaire arrière axiale (21) lorsque le piston coulissant a quitté la position de départ.
  5. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce qu'un élément rapporté (23) est monté sur l'extrémité frontale libre du boîtier (6) de la soupape d'arrêt (7), élément dans lequel sont montés deux coulisseaux d'actionnement (24) par lesquels le piston coulissant (9) peut être déplacé vers sa position d'ouverture totale à l'encontre de la force de rappel.
  6. Dispositif selon l'une des revendications 1 à 5, caractérisé en ce que le ou les coulisseaux d'actionnement (24) peuvent être commandés par une électrovanne (Y₁).
  7. Dispositif selon l'une des revendications 1 à 6, caractérisé en ce que la butée (15) de la tige d'entraînement (13) peut être déplacée axialement depuis l'extérieur.
  8. Dispositif selon la revendication 7, caractérisé en ce que la butée (15) est montée par un filetage interne sur une section filetée (131) de la tige d'entraînement (13) et en ce que l'extrémité arrière de la tige d'entraînement (13) fait saillie à l'extérieur de l'élément rapporté (23) et est munie d'un profil approprié ou analogue pour permettre l'exécution d'un mouvement de rotation en vue du réglage de la limitation de la course.
EP92108021A 1991-05-23 1992-05-13 Dispositif pour limiter la course d'un vérin hydraulique Expired - Lifetime EP0514748B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4116842 1991-05-23
DE4116842A DE4116842A1 (de) 1991-05-23 1991-05-23 Einrichtung zur hubbegrenzung eines hydraulikzylinders

Publications (2)

Publication Number Publication Date
EP0514748A1 EP0514748A1 (fr) 1992-11-25
EP0514748B1 true EP0514748B1 (fr) 1994-04-27

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EP92108021A Expired - Lifetime EP0514748B1 (fr) 1991-05-23 1992-05-13 Dispositif pour limiter la course d'un vérin hydraulique

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US (1) US5237905A (fr)
EP (1) EP0514748B1 (fr)
JP (1) JPH0751961B2 (fr)
DE (2) DE4116842A1 (fr)

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DE4319899A1 (de) * 1993-06-16 1995-01-05 Leinhaas Umformtechnik Gmbh Gelenkhebelpresse und Verfahren zur Steuerung der Stößelbewegung
DE69529339T2 (de) * 1994-07-15 2003-09-04 Tyco Flow Control Pacific Pty Aktuator
AT403219B (de) * 1995-02-01 1997-12-29 Scheidl Rudolf Dipl Ing Dr Tec Vorrichtung zum ansteuern eines hydrostatischen antriebes
US6649035B2 (en) 2001-05-04 2003-11-18 Ross Operating Valve Company Low energy and non-heat transferring crust breaking system
US6732761B2 (en) * 2001-08-03 2004-05-11 Ross Operating Valve Company Solenoid valve for reduced energy consumption
US20080048457A1 (en) * 2006-08-28 2008-02-28 Patel Bhanuprasad S Hydraulic energy conversion system
JP5535502B2 (ja) * 2009-03-16 2014-07-02 川崎重工業株式会社 摩擦撹拌接合装置及び方法
JP5534358B2 (ja) * 2011-06-15 2014-06-25 日立建機株式会社 圧油エネルギ回収装置及びこれを用いた建設機械
CN102996569A (zh) * 2012-12-28 2013-03-27 无锡市拓发自控设备有限公司 防止超程的压力机平衡缸
DE102013112841A1 (de) * 2013-11-21 2015-05-21 Zf Lenksysteme Gmbh Lenksystem
CN103697184B (zh) * 2013-12-20 2016-03-16 中国北方车辆研究所 一种滑阀阀口的通流结构
CN107859663A (zh) * 2017-10-25 2018-03-30 成都弗格森液压机电有限公司 一种伺服液压系统中多余力的抑制装置
CN110985479B (zh) * 2019-12-29 2021-08-27 山东金利液压科技有限公司 一种自动换向液压缸

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FR1175541A (fr) * 1957-05-20 1959-03-27 Ernault Batignolles H Dispositif de sécurité pour un organe mobile de machine
DE2062890C3 (de) * 1970-12-21 1974-05-16 Frankfurter Maschinenbau Ag, Vorm. Pokorny & Wittekind, 6000 Frankfurt Druckmittelbetriebener Arbeitszylinder
CH549163A (de) * 1972-03-06 1974-05-15 Sig Schweiz Industrieges Hydraulischer verstaerker.
DE2323522A1 (de) * 1973-05-10 1974-11-28 Zahnradfabrik Friedrichshafen Hydraulische lenkbegrenzung fuer eine hilfskraftlenkeinrichtung, insbesondere fuer kraftfahrzeuge
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DE3929246A1 (de) * 1989-09-02 1991-03-21 Dornier Luftfahrt Hydraulischer linearmotor

Also Published As

Publication number Publication date
JPH05180204A (ja) 1993-07-20
US5237905A (en) 1993-08-24
DE4116842A1 (de) 1992-11-26
EP0514748A1 (fr) 1992-11-25
JPH0751961B2 (ja) 1995-06-05
DE59200136D1 (de) 1994-06-01

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