EP0935715B1 - Dispositif de maintien en position de la tige d'un verin hydraulique - Google Patents
Dispositif de maintien en position de la tige d'un verin hydraulique Download PDFInfo
- 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
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- valve
- hydraulic cylinder
- maintaining
- chamber
- 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
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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
- 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.
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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)
- Load-Engaging Elements For Cranes (AREA)
- Fluid-Damping Devices (AREA)
- Jigs For Machine Tools (AREA)
- Gripping Jigs, Holding Jigs, And Positioning Jigs (AREA)
- Gripping On Spindles (AREA)
Description
- le clapet anti-retour dit clapet primaire est complété par un clapet anti-retour de sécurité séparé du clapet primaire et monté en amont dans le circuit d'alimentation de cette chambre, passant dans le même sens vers cette chambre,
- un sas présentant à chacune de ses deux entrées-sorties un clapet anti-retour dont d'une part le clapet primaire placé le plus proche de cette chambre, et le clapet de sécurité,
- des moyens de fermeture différée du clapet de sécurité par rapport à celle du clapet primaire,
- un moyen de commande en ouverture des deux clapets.
- elle permet le verrouillage dans n'importe quelle position de la tige du vérin ;
- le verrouillage est automatique ;
- pour une fonction de verrouillage automatique, le dispositif hydraulique selon l'invention est peu onéreux ;
- le dispositif hydraulique apporte une grande sécurité dans le maintien de la charge.
- la figure 1 est une vue générale schématique en coupe montrant le dispositif de maintien selon l'invention monté sur les branches d'alimentation d'un vérin ;
- la figure 2 est une vue en coupe longitudinale d'une première réalisation du dispositif de maintien ;
- les figures 3 et 4 sont respectivement des vues agrandies en coupe longitudinale de la partie centrale du dispositif de maintien dans le cas des deux variantes l'une à clapet conique et l'autre à clapet à étanchéité totale, avec clapets représentés à l'état fermé ;
- la figure 5 est une vue générale schématique en coupe montrant la variante simplifiée du dispositif de maintien selon l'invention montée sur les branches d'alimentation d'un vérin avec clapets représentés à l'état fermé ;
- la figure 6 est une vue en coupe longitudinale de la variante simplifiée du dispositif de maintien.
Claims (22)
- Dispositif de maintien en position de la tige d'un vérin hydraulique (1) au moins à simple effet comprenant une chambre motrice par exemple une chambre de sortie (6) de sa tige (7) et une deuxième chambre utilisée comme chambre de rentrée (5) de sa tige et au moins un clapet anti-retour (11) à rappel élastique en fermeture sur le circuit d'alimentation d'une des chambres, monté passant vers cette chambre, dispositif constitué d'un bloc hydraulique d'isolement (2) à travers lequel est alimentée cette chambre caractérisé, en ce que :le clapet anti-retour (11) dit clapet anti-retour primaire (11) est complété par un clapet anti-retour de sécurité (13) à rappel élastique séparé du clapet primaire (11) par une chambre-sas (9) dont ils équipent chacun un des deux orifices d'extrémité pour l'alimentation d'une des chambres du vérin hydraulique, les deux clapets (11, 13) étant montés passants dans le même sens que le passage du fluide moteur vers cette chambre ;un moyen de fermeture différée du clapet de sécurité (13) par rapport à la fermeture du clapet primaire (11),un moyen de commande (30) en ouverture du clapet de sécurité (13) dont l'ouverture provoque celle du clapet primaire (11).
- Dispositif de maintien selon la revendication 1, caractérisé en ce que le moyen de commande en ouverture du clapet de sécurité (13) est commandé par une commande extérieure au bloc hydraulique d'isolement (2).
- Dispositif de maintien selon la revendication 1, caractérisé en ce que le moyen de fermeture différée du clapet de sécurité (13) par rapport au clapet primaire (11) est un moyen de retard par un ralentissement de sa course de retour.
- Dispositif de maintien selon la revendication 3, caractérisé en ce que le ralentissement de la course retour du clapet de sécurité (13) provient d'un effet d'amortissement d'un élément solidaire de son corps.
- Dispositif de maintien selon la revendication précédente, caractérisé en ce que l'effet d'amortissement est obtenu par laminage d'huile.
- Dispositif de maintien selon la revendication 4, caractérisé en ce que l'effet d'amortissement est obtenu par le frottement visqueux d'une partie de la tige du clapet de sécurité (13).
- Dispositif de maintien selon la revendication 1, caractérisé en ce que la commande en ouverture du clapet primaire (11) est une liaison de commande en ouverture qui provoque par transmission à travers le clapet de sécurité (13) l'ouverture du clapet primaire (11).
- Dispositif de maintien selon la revendication précédente, caractérisé en ce que la transmission de commande en ouverture du clapet primaire (11) présente un jeu de transmission qui dissocie physiquement les deux clapets.
- Dispositif de maintien selon la revendication précédente, caractérisé en ce que la liaison de commande en ouverture du clapet primaire (11) se termine par une tige (23) solidaire du corps du clapet de sécurité (13), tige dont la longueur laisse un jeu (25) entre son extrémité et le corps du clapet primaire (11) lorsque les deux clapets sont fermés.
- Dispositif de maintien selon les revendications précédentes 7 et 8, caractérisé en ce que la liaison de la commande en ouverture du clapet primaire (11) à travers le clapet de sécurité (13) comprend le moyen de retard à la fermeture du clapet de sécurité (13) par rapport à celle du clapet primaire (11).
- Dispositif de maintien selon l'une quelconque des revendications 1 et de 6 à 9, caractérisé en ce que le clapet de sécurité (13) est commandé en ouverture par une pression.
- Dispositif de maintien selon la revendication précédente caractérisé en ce que la pression de commande est la pression d'actionnement de l'autre chambre du vérin.
- Dispositif de maintien selon la revendication précédente, caractérisé en ce que le clapet de sécurité (13) est commandé en ouverture par la pression actionnant la tige (7) du vérin en rentrée.
- Dispositif de maintien selon la revendication 10 caractérisé en ce que la liaison de commande en ouverture et le moyen de retard sont constitués d'une liaison mécanique composite (29) formée d'une suite d'éléments comprenant un piston-poussoir (30) sur lequel s'exerce une pression de commande, un élément de liaison sous la forme d'une masselotte (34) à déplacement guidé dans un alésage-guide (35), masselotte (34) en contact de poussée avec le piston-poussoir (30), de l'extrémité conformée en piston d'extrémité (40) d'une tige constituant. la prolongation du corps (20) du clapet de sécurité (13), ce piston d'extrémité (40) coulissant avec jeu dans le même alésage-guide (35) que la masselotte(34), et en ce que la masselotte (34) et le piston d'extrémité (40) sont distants sur l'alésage-guide (35) d'un espace formant avec la paroi latérale de l'alésage-guide (35) une chambre-réservoir (42) d'huile et en ce que le piston-poussoir (30) appuyant sur la masselotte (34) est mobile dans une chambre (32) ouverte à l'atmosphère et reçoit la pression du fluide alimentant la chambre opposée du vérin à celle alimentée à travers le sas (9).
- Dispositif de maintien selon l'une quelconque des revendications précédentes, caractérisé en ce que le clapet de sécurité (13) est un clapet (26) à joint d'étanchéité.
- Dispositif de maintien selon l'une quelconque des revendications précédentes, caractérisé en ce que la chambre située sous le piston-poussoir (30) est une chambre-tampon (54) remplie d'huile isolée de l'atmosphère et reliée à l'entrée (14) du fluide moteur par une dérivation (53).
- Dispositif de maintien selon la revendication 4, caractérisé en ce que l'effet d'amortissement est obtenu par les différences de raideur des clapets (11, 13).
- Dispositif de maintien selon la revendication 4, caractérisé en ce que l'effet d'amortissement est obtenu par des différences de conformation et de dimensions des composants hydrauliques.
- Dispositif de maintien selon la revendication 4 ou 17 ou 18, caractérisé en ce que l'effet d'amortissement est obtenu par la combinaison de l'amortissement hydraulique avec les différences de raideur des ressorts de rappel des ressorts des clapets et avec la différence de conformation et de dimensions des composants hydrauliques.
- Dispositif de maintien selon l'une quelconque des revendications précédentes, caractérisé en ce que le vérin est à simple effet.
- Dispositif de maintien selon l'une quelconque des revendications précédentes, caractérisé en ce que l'actionnement du clapet de sécurité (13) est assuré par un moyen quelconque indépendant par exemple électromécanique, électromagnétique ou tout autre moyen.
- Dispositif de maintien selon l'une quelconque des revendications précédentes, caractérisé en ce que sur le sas (9) est monté un capteur ou détecteur (44) sensible à la pression, le dépassement d'une pression de référence étant exploité par un circuit de détection et d'alerte.
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 (fr) | 1999-08-18 |
EP0935715B1 true EP0935715B1 (fr) | 2004-01-21 |
Family
ID=9497542
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97913266A Expired - Lifetime EP0935715B1 (fr) | 1996-11-07 | 1997-11-06 | Dispositif de maintien en position de la tige d'un verin hydraulique |
Country Status (11)
Country | Link |
---|---|
US (1) | US5913810A (fr) |
EP (1) | EP0935715B1 (fr) |
CN (1) | CN1103411C (fr) |
AT (1) | ATE258274T1 (fr) |
CA (1) | CA2270579A1 (fr) |
DE (1) | DE69727307T2 (fr) |
ES (1) | ES2216132T3 (fr) |
FR (1) | FR2755481B1 (fr) |
RU (1) | RU2191298C2 (fr) |
UA (1) | UA46875C2 (fr) |
WO (1) | WO1998020260A2 (fr) |
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CN104105890B (zh) * | 2012-02-16 | 2016-02-24 | 克斯美库股份有限公司 | 带助力机构的缸装置 |
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 |
EP3609692B1 (fr) * | 2017-08-01 | 2021-07-21 | Moog GmbH | Appareil pour commander la permutation des vérins hydrauliques |
WO2019030354A1 (fr) * | 2017-08-11 | 2019-02-14 | Eaton Intelligent Power Limited | Collecteur doté d'une soupape d'arrêt pilotée de charge et d'une soupape de purge |
EP3660365B1 (fr) * | 2018-11-27 | 2021-07-21 | Hamilton Sundstrand Corporation | Servovanne |
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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US2702044A (en) * | 1953-11-23 | 1955-02-15 | Albert D Johnston | Automatic supply and exhaust valve |
US2797550A (en) * | 1954-05-05 | 1957-07-02 | Stelzer William | Hydraulic elevators |
US3381587A (en) * | 1965-09-10 | 1968-05-07 | Deere & Co | Hydraulic control system |
DE2036547C3 (de) * | 1970-07-23 | 1973-10-31 | Fried. Krupp Gmbh, 4300 Essen | Brems und Sperreinrichtung fur em hydrostatisches Triebwerk |
DE2305835A1 (de) * | 1973-02-07 | 1974-08-15 | Danfoss As | Hydraulische steuereinrichtung, insbesondere lenkeinrichtung |
WO1981000600A1 (fr) * | 1979-08-30 | 1981-03-05 | Caterpillar Tractor Co | Soupape de verrouillage avec piston a longueur variable et systeme hydraulique pour un outil utilisant celui-ci |
US4355565A (en) * | 1980-03-24 | 1982-10-26 | Caterpillar Tractor Co. | Fluid circuit with zero leak load check and by-pass valve |
IT213216Z2 (it) * | 1987-05-15 | 1989-11-09 | Oil Control Spa | Perfezionamenti a valvola idraulica di controllo,in particolareper circuiti idraulici con distributore anche a centro chiuso |
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. |
-
1996
- 1996-11-07 FR FR9613778A patent/FR2755481B1/fr not_active Expired - Fee Related
-
1997
- 1997-11-06 RU RU99112128/06A patent/RU2191298C2/ru active
- 1997-11-06 EP EP97913266A patent/EP0935715B1/fr not_active Expired - Lifetime
- 1997-11-06 AT AT97913266T patent/ATE258274T1/de not_active IP Right Cessation
- 1997-11-06 WO PCT/FR1997/001994 patent/WO1998020260A2/fr active IP Right Grant
- 1997-11-06 UA UA99063105A patent/UA46875C2/uk unknown
- 1997-11-06 CN CN97199511A patent/CN1103411C/zh not_active Expired - Lifetime
- 1997-11-06 DE DE1997627307 patent/DE69727307T2/de not_active Expired - Lifetime
- 1997-11-06 CA CA002270579A patent/CA2270579A1/fr not_active Abandoned
- 1997-11-06 ES ES97913266T patent/ES2216132T3/es not_active Expired - Lifetime
- 1997-11-07 US US08/966,186 patent/US5913810A/en not_active Expired - Lifetime
Cited By (5)
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 (fr) | 2020-04-07 | 2021-10-14 | Neumeister Hydraulik Gmbh | Dispositif de maintien d'une tige d'un vérin hydraulique en position, et procédé de déblocage et de blocage d'un clapet de non-retour secondaire du dispositif |
Also Published As
Publication number | Publication date |
---|---|
DE69727307D1 (de) | 2004-02-26 |
ATE258274T1 (de) | 2004-02-15 |
ES2216132T3 (es) | 2004-10-16 |
CN1103411C (zh) | 2003-03-19 |
UA46875C2 (uk) | 2002-06-17 |
EP0935715A1 (fr) | 1999-08-18 |
FR2755481A1 (fr) | 1998-05-07 |
FR2755481B1 (fr) | 1998-12-24 |
DE69727307T2 (de) | 2004-11-18 |
RU2191298C2 (ru) | 2002-10-20 |
CN1244236A (zh) | 2000-02-09 |
US5913810A (en) | 1999-06-22 |
CA2270579A1 (fr) | 1998-05-14 |
WO1998020260A2 (fr) | 1998-05-14 |
WO1998020260A3 (fr) | 2002-10-03 |
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