EP0935715B1 - Haltevorrichtung einer hydraulischen arbeitszylinderstange - Google Patents

Haltevorrichtung einer hydraulischen arbeitszylinderstange Download PDF

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Publication number
EP0935715B1
EP0935715B1 EP97913266A EP97913266A EP0935715B1 EP 0935715 B1 EP0935715 B1 EP 0935715B1 EP 97913266 A EP97913266 A EP 97913266A EP 97913266 A EP97913266 A EP 97913266A EP 0935715 B1 EP0935715 B1 EP 0935715B1
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EP
European Patent Office
Prior art keywords
shaft
valve
hydraulic cylinder
maintaining
chamber
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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
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EP97913266A
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English (en)
French (fr)
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EP0935715A1 (de
Inventor
Jean-Luc Andre
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Lohr Industrie SA
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Lohr Industrie SA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices

Definitions

  • the present invention relates to a device for holding in position the rod of a hydraulic cylinder. It also relates to the leak detection in the return circuit of the motor room.
  • a holding device according to the preamble of claim 1 is known from document DE-A-20 36 547.
  • Cylinders are frequently used hydraulics as drive units in assemblies lifting and lowering of a supporting structure. These sets are well known and used in the transport, but also in construction and other places where elevation movements and of lowering a load are daily and require repeated efforts greater than the human strength.
  • a cylinder is typically maintained under charging by a non-return valve inserted in the circuit cylinder supply in the direction passing towards the rod exit chamber.
  • This function of maintenance under load ensures its role as long as the sealing of the valve can be preserved. This one initially exists due to quality controls carried out in the manufacturing workshops. But the valve can present gradually or suddenly a leak after a certain period and this for various reasons related to operation or aging, or even a minor original defect gone unnoticed. we can mention, as a cause, a geometric defect for example of sphericity of the ball, a solid impurity present in the circuit oil and coming to rest on the valve seat or any other cause of poor mechanical contact or local allowance between the valve body and its seat.
  • valve To ensure a function without fail as important as maintaining security, the valve must present a total guarantee of watertightness.
  • lifting cylinders are associated with devices blocking-locking mechanisms for example locking pins or safety stops.
  • the object of the invention is to dispense with the use of these additional mechanical means of restraint, necessary to ensure the safety of the hold in the case of a hydraulic cylinder locked in load holding position.
  • the invention finds multiple applications in many areas when it comes to lifting-lowering of a load with maintenance in position of restraint and more particularly in position extension of the cylinder rod.
  • the holding device. in position of the rod of a hydraulic cylinder 1 is in the form an isolation assembly 2 mounted between a branch 3 and another branch 4 for supplying engine fluid respectively a reentry chamber 5 and a outlet chamber 6 of a rod 7 of the hydraulic cylinder 1.
  • This isolation set 2 forms a block hydraulic 8 containing an airlock chamber 9 called for simply sas convenience reasons.
  • This airlock has a lower orifice 10 provided with a valve primary check valve 11 in hydraulic connection with the outlet chamber 6 of the rod 7 of the jack and facing, an upper orifice 12 provided with a non-return valve 13 in hydraulic communication with a hydraulic input 14 extended by a channel transverse 15 for supplying engine fluid to the outlet chamber 6 from the hydraulic inlet 14.
  • the primary check valves 11 and security 13 are physically separate and mounted passers-by in the direction from top to bottom of the figures, i.e. in the direction of supply of the chamber outlet 6 of rod 7 from arrival hydraulic 14.
  • the primary valve 11 is produced in the form of a non-return valve ball 16 forced as a closing reminder against a seat of suitable shape for example conical 17 crossed in sound center through the lower hole 10.
  • the restoring force is generated by a return spring 18 trapped in a housing 19 at the lower end isolation block 2.
  • the safety check valve 13 is produced according to a first variant in the form of a frustoconical body 20 with active conical surface in contact in closed position with a flange circular 21 of an annular shoulder 22 crossed at its center through the upper opening 12.
  • the safety valve 13 opens conventionally and automatically by pressure incident.
  • the opening of the safety valve 13 can be controlled by an external command to the block isolation 2 for example by the driving force of the pressurized hydraulic fluid supplying the chamber re-entry of the rod or any other means. She additionally causes the commanded opening of the primary valve 11.
  • the safety valve 13 is extended downwards by a lower rod of control 23 which carries, threaded on its lateral surface, a return spring 24 in the closed position.
  • This control rod 23 ends with a free end with a straight thrust front which can pass through the orifice lower 10 of the airlock 9 to push the body of the primary valve 11 in opening, that is to say away from his seat 17 against force return elastic provided by spring 18.
  • the safety valve 13 is integral with a way to slow down its stroke as a reminder of closure in order to defer its closure from that of the primary valve 11. this can guarantee the absence of significant dynamic pressure and therefore of flow in the airlock 9 during the closing phase of the safety valve 13.
  • This characteristic allows in particular consider using a seal to perfect sealing and thus increasing the efficiency of the valve of security.
  • This type of valve with seal will be called fully sealed valve 26. It constitutes the means ideal for closing the airlock 9 and for a reinforced guarantee of the holding in position under load of the cylinder rod.
  • This variant is shown in Figure 4 under the form of a fully sealed valve 26 with seal 27 by toric example resting on a throat-shaped seat 28.
  • One of the merits of the invention relates to the possibility of using a sealing valve total for example such as 26 for the second valve said security 13 due to the lack of pressure dynamic to the right of the seat when the valve.
  • the flyweight 34 of the mechanical link composite 29 has a seal 38 at the neighborhood of its lower end realizing the tightness of this segment with respect to chamber 32 in which the push-piston 30 moves.
  • the upper mobile assembly consists of a last segment 39 in the form of a rod secured to the body of the valve.
  • This rod 39 presents upwards a cylindrical upper end forming a sliding end piston 40 with play along the guide bore 35 formed in the insert 36.
  • This patch 36 delimits laterally with isolation block 2 a room ring 41 through which the engine oil arrives acts on the body of the safety valve 13.
  • the push-piston 30 actuates during opening the safety valve 13 by a motor displacement towards the bottom coming from a control means for example the force generated by the pressure of the working fluid of the reentry chamber 5 of the rod 7 of the actuator on the upper face of the plunger 30 placed in the supply duct of this chamber September.
  • the command to open the valve security 13 may come from some other means or from a other driving source.
  • the damping effect results from the presence of oil contained in the reservoir chamber 42 forming buffer and which will be gradually expelled out of this reservoir chamber 42 during the return stroke of the safety valve 13 as a closing reminder. Indeed, the oil will be removed from this chamber by rolling along the end piston 40 due to the play existing between it and its guide bore 35.
  • the damping effect also results from viscous friction of the valve stem in oil.
  • This damping effect can be used together with an appropriate distribution of the difference in stiffness of return springs valves or with geometric variations of hydraulic components. Either of these parameters can be used in isolation or in combination.
  • the airlock 9 communicates hydraulically by a channel 43 with a sensor or detector 44 sensitive to pressure, for example a pressure switch inserted in a electrical or electronic circuit whose signal is operated to report a leak by a visual, audible or other warning means.
  • a sensor or detector 44 sensitive to pressure, for example a pressure switch inserted in a electrical or electronic circuit whose signal is operated to report a leak by a visual, audible or other warning means.
  • FIG. 2 shows the block mechanical 45 of pressure switch 44 and its two pins outlet 46 and 47 for its electrical connection with the operating circuit.
  • the actuation of the safety valve is ensured by any independent means, for example electromechanical, electromagnetic or any other way.
  • the holding device according to the invention is perfectly reversible as far as concerns the power connections. So the isolation block 2 output can be connected to the reentry chamber 5 and conversely, the output 6 can be connected directly to a source of pressure.
  • the control at the output of the rod 7 of the jack is done by sending for example a pressure calibrated at the hydraulic inlet 14 of the hydraulic block 8.
  • This driving pressure will automatically open one after the other the two valves 13 and 11 against the return force of each of the springs 24 and 18 and will then supply the outlet chamber 6 of the rod.
  • the pressure will be cut off when the rod 7 of the jack will reach a desired output length.
  • the damping of the safety valve will take effect in order to guarantee the delay desired between the closings of the two valves i.e. delayed closing of the safety valve 13 by compared to that of the primary valve 11.
  • the pressure relative in the airlock will then be substantially zero.
  • Figures 5 and 6 relate to a simplified variant of the holding device in position of a charge according to the invention in which general functions are retained and implemented work by the same or equivalent means.
  • the room located under the push-piston 30 no longer communicates with the outside, but with the arrival of the rising engine fluid of the rod 7 of the hydraulic cylinder.
  • the position holding device applies mainly but not exclusively to a hydraulic cylinder 1 supporting a load carried by a support for lifting it and lowering and keeping it safe in a given position.
  • the holding device is a hydraulic isolation unit 2 in the form of a hydraulic block 8 mounted between two branches 3 and 4 engine fluid supply respectively from the reentry chamber 5 and exit chamber 6 of its rod 7 in the case of a double-acting cylinder.
  • the hydraulic block 8 contains an airlock chamber 9 having a lower opening 10 with non-return valve primary 11 in connection with the outlet chamber 6 and an upper orifice 12 provided with the non-return valve 13 in hydraulic communication with a hydraulic inlet 14 extended by a channel transverse 15.
  • the valves 11 and 13 are mounted passers-by from top to bottom of the figures.
  • valve primary 11 is ball 16 elastically recalled in closed position against its seat by a spring 18.
  • the safety valve 13 in the production shown for this variant is of the body type dish 48 circular with shoulder of diameter less than that of his home 49.
  • This fully sealed valve 13 allows ensure that the load remains in position.
  • the clearance 25 existing between the lower end of the rod 23 and the ball 16 determines a degree of freedom of movement between two valves and introduced in the controlled mode the delay in opening the primary valve 11 caused by opening the safety valve 13.
  • valve 13 Maintaining position security is given by valve 13.
  • the effectiveness of this safety valve depends on the holding of its seal after a significant number of maneuvers.
  • the lower end of the counterweight 34 is found next to the end of a piston 40 secured to the valve body through a reservoir chamber 42 filled with oil used as a buffer damper.
  • the slowdown function allowing closing delay of the two valves can be obtained by different means taken individually or in combination with know: the different stiffnesses of the two springs valve reminder, viscous friction of the rod of the valve 13 in the airlock chamber 9 and in general the damping of the rod in the oil and the conformation and dimensions of components Hydraulic.
  • the transverse channel 15 of the inlet hydraulic 14 has a bypass 53 to a buffer chamber 54 located under the push piston 30. From this fact, this buffer chamber 54 no longer has any communication with the outside via a vent. She is connected to inlet 14 and filled with pressurized oil. Consequently the risk of corrosion which originated from its constant communication with the outside is totally eliminated.
  • the inlet 14 coming of the supply line 55 of the chamber 6 of the jack through the device according to the invention is found connected to the cover at the same time as the buffer chamber 54.
  • the controlled movement of the push piston 30 towards the bottom by the pressure of the fluid coming from the conduit 3, causes the safety valve 13 to open then consecutively, for example by the rod 23, after mechanical thrust contact that of the primary valve 11.
  • the ascent of the plunger 30 is guaranteed by a return spring 56.
  • Another advantage of this feature relates to sealing. Sealing constraints are less important because the leaks feed the hydraulic circuit line. The consequence is possibility of removing the seal between the buffer chamber 54 and the arrival of conduit 3 to the part upper part of the piston 30 on the one hand and that which existed between the upper rod 40 of the valve security 13 and the buffer chamber 54 on the other hand.
  • This advantage further increases the reliability of the device.
  • the pressurized working fluid enters the hydraulic block 8 by the branches 15 and 53 towards the safety valve 13 and the buffer chamber 54.
  • This pressure is enough to first open the safety valve 13 then the non-return valve primary 11 to supply the cylinder through its chamber 6 of out of its rod 7.
  • Rod 7 rises with the load it supports up to the desired level programmed or not. The pressure is then cut and the rod comes to a standstill position. Immediately after immobilization, the load causes oil to return for a period of time short.
  • the safety valve 13 closes in a second time in room-airlock 9 in the absence of pressure due to insulation from the prior closing of the primary valve 11. This closing in the absence of dynamic pressure and therefore of flow protects the seal of the safety valve and avoids this one to come out of its housing.
  • the security of maintaining the charge in position is guaranteed by the two non-return valves.
  • the primary ball valve 11 allows 16 by its close immediate maintenance of the charge.
  • valve fails or leaks primary 11, however small it may be, maintaining by this only one valve is no longer guaranteed over time. This drift would lead to an involuntary lowering of the charge, slow but dangerous for the load located in below the platform held by the jack.
  • the load will remain in position practically indefinitely.
  • the control for lowering the rod 7 of the jack under load requires the opening of the two valves.
  • the force causing the opening is given by a control pressure. This can be the pressure acting on the other chamber of the double-acting cylinder or an independent control pressure or piloting.
  • the safety valve stem continues to go down.
  • the lower end of its rod 23 arrives in thrust contact with the shutter element of the primary valve and continuing its travel the constrained in opening.
  • the safety valve being in position open, its seal does not risk damage or leaving his home.
  • the retraction of the cylinder rod can also result from an otherwise ordered opening of valves i.e. independent of pressure driving causing the retraction of the rod.
  • the device according to the invention can be oriented at mounting in the opposite direction to that shown on the figures or according to any other orientation of his support.

Claims (22)

  1. Vorrichtung zum Halten eines Schaftes eines zumindest einfach wirkenden Hydraulikzylinders (1) in Stellung, mit einer Antriebskammer, wie einer Austriebskammer (6) für den Schaft (7) und mit einer zweiten Kammer, die als Rückkehrkammer (5) des Schaftes verwendet wird, und mit mindestens einem in Schließrichtung elastisch beaufschlagten Rückschlagventil (11) im Versorgungskreis einer der Kammern, das zum Durchlass zu der Kammer angeordnet ist, wobei die Vorrichtung einen hydraulischen Trennblock (2) bildet, durch welchen die entsprechende Kammer versorgt wird, dadurch gekennzeichnet,
    dass das Rückschlagventil (11) durch ein elastisch beaufschlagtes Sicherheitsrückschlagventil (13) vervollständigt wird, welches von dem primären Ventil (11) durch eine Schleusenkammer (9) getrennt ist, deren beide Endöffnungen mit jeweils einem der Ventile versehen sind, um eine Kammer des Hydraulikzylinders zu versorgen, wobei die beiden Ventile (11, 13) gleichsinnig in Flußrichtung des Antriebsfluids zu der Kammer hin angeordnet sind,
    weiterhin gekennzeichnet durch
    ein Mittel zum verzögerten Schließen des Sicherheitsventils (13) relativ zum Schließen des Primärventils (11),
    ein Steuermittel (30) zum Öffnen des Sicherheitsventils (13), dessen Öffnen das offene Primärventils (11) bewirkt.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Steuermittel (30) zum Öffnen des Sicherheitsventils (13) durch eine externe Steuerung am hydraulischen Trennblock (2) steuerbar ist.
  3. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Schließmittel zum verzögerten Schließen des Sicherheitsventils (13) relativ zum Primärventil (11) ein Verzögerungsmittel durch Verlangsamung seiner Rückkehrbewegung ist.
  4. Vorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass die Verlangsamung der Rückkehrbewegung des Sicherheitsventils (13) von einem Dämpfungseffekt eines mit seinem Körper festen Elements herrührt.
  5. Vorrichtung nach dem vorangehenden Anspruch, dadurch gekennzeichnet, dass der Dämpfungseffekt durch eine Öldrosselung bewirkt ist.
  6. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass der Dämpfungseffekt durch viskose Reibung eines Teils des Schafts des Sicherheitsventils (13) bewirkt ist.
  7. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Öffnungssteuerung des Primärventils (11) eine Öffnungssteuerungsverbindung ist, die durch Übertragung über das Sicherheitsventil (13) die Öffnung des Primärventils (11) bewirkt.
  8. Vorrichtung nach dem vorangehenden Anspruch, dadurch gekennzeichnet, dass die Übertragung der Öffnungssteuerung des Primärventils (11) ein Übertragungsspiel aufweist, das physisch die beiden Ventile trennt.
  9. Vorrichtung nach dem vorangehenden Anspruch, dadurch gekennzeichnet, dass die Öffnungssteuerungsverbindung des Primärventils (11) in einem Schaft (23) endet, der mit dem Körper des Sicherheitsventils (13) fest verbunden ist, wobei die Länge des Schafts (23) ein Spiel (25) zwischen seinem Ende und dem Körper des Primärventils (11) lässt, wenn beide Ventile geschlossen sind.
  10. Vorrichtung nach Anspruch 7 oder 8, dadurch gekennzeichnet, dass die Öffnungssteuerungsverbindung des Primärventils (11) über das Sicherheitsventil (13) ein Mittel zum Verzögern des Schließens des Sicherheitsventils (13) relativ zu dem Schließen des Primärventils (11) aufweist.
  11. Vorrichtung nach einem der Ansprüche 1 und 6 bis 9, dadurch gekennzeichnet, dass das Sicherheitsventil (13) durch Druck zum Öffnen ansteuerbar ist.
  12. Vorrichtung nach dem vorangehenden Anspruch, dadurch gekennzeichnet, dass der Steuerdruck der Betätigungsdruck der anderen Kammer des Zylinders (1) ist.
  13. Vorrichtung nach dem vorangehenden Anspruch, dadurch gekennzeichnet, dass das Sicherheitsventil (13) zum Öffnen durch den den Schaft (7) des Zylinders zurückführenden Druck steuerbar ist.
  14. Vorrichtung nach Anspruch 10, dadurch gekennzeichnet, dass die Öffnungssteuerungsverbindung und das Verzögerungsmittel durch eine mechanische Kombinationsverbindung (29) gebildet sind, die durch eine Folge von Elementen gebildet ist, die einen Druckkolben (13), auf den ein Steuerdruck wirkt und ein Verbindungselement in Form eines Ausgleichskörpers (34) zur geführten Verschiebung in einer Führungsbohrung (35) aufweist, wobei die Ausgleichskörper (34) in Druckkontakt mit dem Druckkolben (30) steht, über ein angepasstes Ende eines Endkolbens (40) eines Schafts, der eine Verlängerung des Körpers (20) des Sicherheitsventils (13) bildet, wobei der Endkolben (40) mit Spiel in der gleichen Führungsbohrung (35) wie der Ausgleichskörper (34) geführt ist,
    dass der Ausgleichskörper (34) und der Endkolben (40) in der Führungsbohrung (35) einen Relativabstand aufweisen, der mit der Umfangswandung der Führungsbohrung (35) eine Öl-Reservoir-Kammer (42) bildet und
    dass der auf den Ausgleichskörper (34) wirkende Druckkolben (30) in einer Kammer (32), die zur Atmosphäre offen ist, beweglich ist und dem Druck des Fluids ausgesetzt ist, welches die Kammer versorgt, die der durch die Schleuse (9) versorgten Kammer des Zylinders gegenüberliegt.
  15. Vorrichtung nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass das Sicherheitsventil (13) ein mit einer Dichtung versehenes Ventil (26) ist.
  16. Vorrichtung nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die unter dem Druckkolben (30) angeordnete Kammer eine gegen die Atmosphäre isolierte ölgefüllte Pufferkammer (54) ist; die mit dem Einlass (14) des Fluidantriebs durch einen Bypass (53) verbunden ist.
  17. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass der Dämpfungseffekt durch Steifigkeitsunterschiede der Ventile (11, 13) bewirkbar ist.
  18. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass der Dämpfungseffekt durch Gestalt- und Dimensionsunterschiede der hydraulischen Komponenten bewirkt ist.
  19. Vorrichtung nach Anspruch 4, 17 oder 18, dadurch gekennzeichnet, dass der Dämpfungseffekt durch Kombination hydraulischer Dämpfung mit Steifigkeitsunterschieden der Rückstellfedern der Ventile und durch Gestalt- und Dimensionsunterschiede der hydraulischen Komponenten bewirkt ist.
  20. Vorrichtung nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass der Zylinder ein einfach wirkender Zylinder ist.
  21. Vorrichtung nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die Wirkung des Sicherheitsventils (13) durch ein beliebiges unabhängiges Mittel sichergestellt ist, beispielsweise ein elektromechanisches, elektromagnetisches oder jegliches andere Mittel.
  22. Vorrichtung nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass an der Schleuse (9) ein drucksensibler Aufnehmer oder Detektor (44) derart angeordnet ist, dass das Überschreiten eines Referenzdruckes durch einen Detektions- und Alarmschaltkreis nutzbar ist.
EP97913266A 1996-11-07 1997-11-06 Haltevorrichtung einer hydraulischen arbeitszylinderstange Expired - Lifetime EP0935715B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9613778 1996-11-07
FR9613778A FR2755481B1 (fr) 1996-11-07 1996-11-07 Dispositif de maintien en position et sous charge d'un verin hydraulique
PCT/FR1997/001994 WO1998020260A2 (fr) 1996-11-07 1997-11-06 Dispositif de maintien en position de la tige d'un verin hydraulique

Publications (2)

Publication Number Publication Date
EP0935715A1 EP0935715A1 (de) 1999-08-18
EP0935715B1 true EP0935715B1 (de) 2004-01-21

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EP97913266A Expired - Lifetime EP0935715B1 (de) 1996-11-07 1997-11-06 Haltevorrichtung einer hydraulischen arbeitszylinderstange

Country Status (11)

Country Link
US (1) US5913810A (de)
EP (1) EP0935715B1 (de)
CN (1) CN1103411C (de)
AT (1) ATE258274T1 (de)
CA (1) CA2270579A1 (de)
DE (1) DE69727307T2 (de)
ES (1) ES2216132T3 (de)
FR (1) FR2755481B1 (de)
RU (1) RU2191298C2 (de)
UA (1) UA46875C2 (de)
WO (1) WO1998020260A2 (de)

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DE102020109615A1 (de) 2020-04-07 2021-10-07 Neumeister Hydraulik Gmbh Vorrichtung zum halten eines schafts eines hydraulikzylinders in stellung und verfahren zum entsperren und absperren eines sekundär-rückschlagventils der vorrichtung

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EP2816238B1 (de) * 2012-02-16 2016-02-10 Kosmek Ltd. Zylindervorrichtung mit einem kraftverstärker
US9611871B2 (en) 2013-09-13 2017-04-04 Norbert J. Kot Pneumatic valve assembly and method
CN104019080A (zh) * 2014-06-23 2014-09-03 柳州柳工液压件有限公司 补油油缸
US11618232B2 (en) 2017-08-01 2023-04-04 Moog Gmbh Apparatus for controlling the switch-over of hydraulic cylinders
WO2019030354A1 (en) * 2017-08-11 2019-02-14 Eaton Intelligent Power Limited COLLECTOR HAVING A LOADED PILOT STOP VALVE AND A PURGE VALVE
EP3660365B1 (de) * 2018-11-27 2021-07-21 Hamilton Sundstrand Corporation Servoventil
DE102019218400A1 (de) * 2019-11-27 2021-05-27 Hawe Hydraulik Se Ventilkegel, Lasthalteventil mit Ventilkegel und Verfahren zur Montage eines Rückschlagventils
FR3104653B1 (fr) 2019-12-17 2021-11-19 Lohr Ind Bloc de securite a electrovanne pour verin et circuit hydraulique contenant plusieurs verins equipes de tels blocs

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US4913190A (en) * 1989-04-24 1990-04-03 Deere & Company Detent mechanism for a control valve
SU1753068A1 (ru) * 1990-06-07 1992-08-07 Московское станкостроительное производственное объединение "Красный пролетарий" Односторонний гидрозамок
US5261456A (en) * 1992-11-02 1993-11-16 Deere & Company Transmission engagement override valve
NL1000038C2 (nl) * 1995-04-04 1996-10-07 Applied Power Inc Hydraulische kantelinrichting voor een kabine.

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3049663A1 (fr) * 2016-03-31 2017-10-06 Lohr Ind Bloc de securite a double clapet pour verin hydraulique
WO2017191380A1 (fr) * 2016-03-31 2017-11-09 Lohr Industrie Bloc de sécurité à double clapet pour vérin hydraulique
US10760595B2 (en) 2016-03-31 2020-09-01 Lohr Industrie Dual-valve security unit for hydraulic cylinders
DE102020109615A1 (de) 2020-04-07 2021-10-07 Neumeister Hydraulik Gmbh Vorrichtung zum halten eines schafts eines hydraulikzylinders in stellung und verfahren zum entsperren und absperren eines sekundär-rückschlagventils der vorrichtung
WO2021204319A1 (de) 2020-04-07 2021-10-14 Neumeister Hydraulik Gmbh Vorrichtung zum halten eines schafts eines hydraulikzylinders in stellung und verfahren zum entsperren und absperren eines sekundär-rückschlagventils der vorrichtung

Also Published As

Publication number Publication date
US5913810A (en) 1999-06-22
CN1244236A (zh) 2000-02-09
ES2216132T3 (es) 2004-10-16
WO1998020260A3 (fr) 2002-10-03
DE69727307T2 (de) 2004-11-18
EP0935715A1 (de) 1999-08-18
CN1103411C (zh) 2003-03-19
FR2755481B1 (fr) 1998-12-24
UA46875C2 (uk) 2002-06-17
DE69727307D1 (de) 2004-02-26
FR2755481A1 (fr) 1998-05-07
RU2191298C2 (ru) 2002-10-20
ATE258274T1 (de) 2004-02-15
WO1998020260A2 (fr) 1998-05-14
CA2270579A1 (fr) 1998-05-14

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