EP0514748A1 - 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
EP0514748A1
EP0514748A1 EP92108021A EP92108021A EP0514748A1 EP 0514748 A1 EP0514748 A1 EP 0514748A1 EP 92108021 A EP92108021 A EP 92108021A EP 92108021 A EP92108021 A EP 92108021A EP 0514748 A1 EP0514748 A1 EP 0514748A1
Authority
EP
European Patent Office
Prior art keywords
piston
working
valve
pressure
stroke
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.)
Granted
Application number
EP92108021A
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German (de)
English (en)
Other versions
EP0514748B1 (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 designed so that the stroke limitation with respect to the time or piston position can be easily adjusted subsequently 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 rod 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 switch-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 rod 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 portion 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 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 off 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) so as to be slidable 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).
  • a driving ring (19) is fastened on the towing rod (13) in the vicinity of the rear end of the towing rod (13), which comes to rest against the stop ring (11) when the towing rod (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 is blocked in this position 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 supply line P2 is an adjustable pressure relief valve (34) behind the check valve and a hydraulic pressure accumulator (35) on the other hand via a directional control valve Y2. 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) stops and holds the working piston (2) in the retracted position.
  • Another pressure source (38) is connected via line A 1 to the bore (26) and supplies the pressure medium for the application of the working pressure space (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 towing bar (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 supply 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 piston slide (9) is moved further out of its adjusted 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 pressure in the working pressure chamber (5) drops 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
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
DE4116842A DE4116842A1 (de) 1991-05-23 1991-05-23 Einrichtung zur hubbegrenzung eines hydraulikzylinders
DE4116842 1991-05-23

Publications (2)

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

Family

ID=6432259

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92108021A Expired - Lifetime EP0514748B1 (fr) 1991-05-23 1992-05-13 Dispositif pour limiter la course d'un vérin hydraulique

Country Status (4)

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT403219B (de) * 1995-02-01 1997-12-29 Scheidl Rudolf Dipl Ing Dr Tec Vorrichtung zum ansteuern eines hydrostatischen antriebes
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
CN103697184A (zh) * 2013-12-20 2014-04-02 中国北方车辆研究所 一种滑阀阀口的通流结构
CN110985479A (zh) * 2019-12-29 2020-04-10 邵延荣 一种自动换向液压缸

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4319899A1 (de) * 1993-06-16 1995-01-05 Leinhaas Umformtechnik Gmbh Gelenkhebelpresse und Verfahren zur Steuerung der Stößelbewegung
CA2192563C (fr) * 1994-07-15 2003-03-25 Peter Jones Actionneur
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
DE102013112841A1 (de) * 2013-11-21 2015-05-21 Zf Lenksysteme Gmbh Lenksystem
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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2062890A1 (de) * 1970-12-21 1972-07-06 Frankfurter Maschinenbau Ag Vo Druckmittelbetriebener Arbeitszylinder
DE2654588A1 (de) * 1975-12-24 1977-07-07 Pierre Colly Druckzylinder
DE3506380A1 (de) * 1985-02-23 1986-08-28 Eugen 7981 Berg Rapp Arbeitszylinder fuer gasfoermige oder fluessige medien
DE3929246A1 (de) * 1989-09-02 1991-03-21 Dornier Luftfahrt Hydraulischer linearmotor

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2018977A (en) * 1933-12-23 1935-10-29 Baldwin Southwark Corp Governor
FR1175541A (fr) * 1957-05-20 1959-03-27 Ernault Batignolles H Dispositif de sécurité pour un organe mobile de machine
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
DE3922553C2 (de) * 1989-07-08 2002-03-14 Mannesmann Rexroth Ag Vorrichtung zur Entlastung eines unter hohem Druck stehenden mit Hydraulikflüssigkeit gefüllten Arbeitsraumes

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2062890A1 (de) * 1970-12-21 1972-07-06 Frankfurter Maschinenbau Ag Vo Druckmittelbetriebener Arbeitszylinder
DE2654588A1 (de) * 1975-12-24 1977-07-07 Pierre Colly Druckzylinder
DE3506380A1 (de) * 1985-02-23 1986-08-28 Eugen 7981 Berg Rapp Arbeitszylinder fuer gasfoermige oder fluessige medien
DE3929246A1 (de) * 1989-09-02 1991-03-21 Dornier Luftfahrt Hydraulischer linearmotor

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 4, no. 53 (M-8)(535) 19. April 1980 & JP-A-55 020 970 ( TSUDA TEKKOSHO ) 14. Februar 1980 *
SOVIET INVENTIONS ILLUSTRATED Section PQ, Week 8950, 31. Januar 1990 Derwent Publications Ltd., London, GB; Class Q57, AN 89-368833/50 & SU-A-1 483 121 (SHEVCHENRO) 30. Mai 1989 *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT403219B (de) * 1995-02-01 1997-12-29 Scheidl Rudolf Dipl Ing Dr Tec Vorrichtung zum ansteuern eines hydrostatischen antriebes
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
CN103697184A (zh) * 2013-12-20 2014-04-02 中国北方车辆研究所 一种滑阀阀口的通流结构
CN110985479A (zh) * 2019-12-29 2020-04-10 邵延荣 一种自动换向液压缸
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

Also Published As

Publication number Publication date
EP0514748B1 (fr) 1994-04-27
JPH05180204A (ja) 1993-07-20
US5237905A (en) 1993-08-24
JPH0751961B2 (ja) 1995-06-05
DE59200136D1 (de) 1994-06-01
DE4116842A1 (de) 1992-11-26

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