EP2229537B1 - Dispositif d'entraînement hydraulique à deux chambres de pression, et procédé permettant de faire fonctionner un dispositif d'entraînement hydraulique à deux chambres de pression - Google Patents

Dispositif d'entraînement hydraulique à deux chambres de pression, et procédé permettant de faire fonctionner un dispositif d'entraînement hydraulique à deux chambres de pression Download PDF

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Publication number
EP2229537B1
EP2229537B1 EP10701488.8A EP10701488A EP2229537B1 EP 2229537 B1 EP2229537 B1 EP 2229537B1 EP 10701488 A EP10701488 A EP 10701488A EP 2229537 B1 EP2229537 B1 EP 2229537B1
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Prior art keywords
piston
pressure
working
pressure chamber
drive device
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German (de)
English (en)
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EP2229537A1 (fr
EP2229537B8 (fr
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Erfindernennung liegt noch nicht vor Die
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Voith Patent GmbH
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Voith Patent GmbH
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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
    • 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
    • F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
    • 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
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • 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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/09—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor with electrical control means

Definitions

  • the invention relates to a hydraulic working device with a displaceably guided in a cylinder chamber along a working piston, which limits a hydraulic fluid pressurizable working pressure chamber, further comprising a guided at least partially in the piston between different control states control means for controlling the flow of hydraulic fluid from a high pressure supply in the working pressure chamber for moving the piston in the working direction and from the working pressure chamber to a return chamber.
  • the invention also relates to a method for operating a hydraulic drive device, with a displaceably guided in a cylinder chamber piston which limits a working pressure chamber, wherein the working pressure chamber for moving the piston is pressurized in the working direction with hydraulic fluid.
  • Hydraulic drive devices and methods of the type mentioned are known in various designs.
  • the state of the art for example, on the EP 0 296 104 B1 directed.
  • a common feature in the prior art is that retraction and extension movements of the piston are effected by means of hydraulic fluid from a high-pressure supply.
  • Such devices are used in particular in stamping, embossing, nibbling, bending or forming machines. In this typically highly dynamic working operation, inherently high volume flows of the hydraulic fluid from the high-pressure supply occur, and sufficient energy must be provided.
  • the invention has for its object to enable an energy-saving hydraulic working operation, especially for use in stamping, embossing, nibbling, bending or forming machines.
  • a hydraulic drive device according to claim 1. It is therefore provided according to the invention that the working pressure chamber remote from the region of the piston defines a low pressure chamber which is pressurized during operation of the device by a low pressure supply for hydraulic fluid such that the piston is moved back against the working direction when the control means connects the working pressure chamber with the return chamber ,
  • the piston advantageously limits not only the working pressure chamber and the return chamber, but also a high-pressure chamber and a low-pressure chamber.
  • a pressurization of the working pressure chamber with hydraulic fluid causes a force on the piston in the working direction, while pressurization of the low-pressure chamber causes a force on the piston against the working direction.
  • the return chamber is connected in particular via a tank connection with a tank and serves to discharge the hydraulic fluid from the working pressure chamber.
  • the high-pressure chamber is connected in particular via a high-pressure connection to the high-pressure supply and serves to supply the working pressure chamber with hydraulic fluid.
  • the low-pressure space is connected in particular via a low-pressure connection to the low-pressure supply.
  • the high pressure chamber and the low pressure chamber are in particular so designed that when pressurized no resulting forces on the piston in or against the working direction
  • a further development of the invention provides that the low-pressure chamber is separated from the high-pressure supply independently of the control state of the control means.
  • the high-pressure supply is thus removed only during the working step (i.e., during the pre-driving) hydraulic fluid in which the piston is moved in the working direction by filling the working pressure chamber with hydraulic fluid. When the piston is moved back, no hydraulic fluid flows from the high pressure supply.
  • adjusting means are provided, by means of which the pressure of the high-pressure supply is adjustable depending on the travel of the piston and / or the working load of the piston.
  • the adjusting means are designed such that the pressure of the high pressure supply for moving the piston from its retracted end position in the working direction to or until just before recording a workload a value p1 and then, in particular during the workload, a value p2.
  • p1 is smaller than p2.
  • the adjusting means are advantageously designed such that upon further movement of the piston in the working direction after overcoming the workload, the pressure of the high-pressure supply has a value p3, where p3 is less than p2 and / or p3 is equal to p1.
  • a displacement measuring system for determining the travel path (i.e., the position) of the piston and / or a load measuring system for determining the working load of the piston.
  • these measuring systems enable optimized high-pressure connection for further energy savings.
  • control means in the region in which it is guided in the piston, along the working direction limits a pressure chamber which is pressure-connected to the low-pressure space.
  • control means is designed as a control slide guided along the working axis, which is at least partially guided in the interior of the piston, and which has control edges, which are designed to cooperate with further control edges on the piston to the Control flow of hydraulic fluid in or out of the working pressure chamber.
  • control edges which are designed to cooperate with further control edges on the piston to the Control flow of hydraulic fluid in or out of the working pressure chamber.
  • the spool can be formed in one piece or in several parts, with individual parts of the spool can be connected to each other in particular via joints. As a result, in particular alignment errors can be compensated.
  • the spool can also on the one hand in the region adjacent to the low-pressure chamber of the piston in a cylindrical guide opening and on the other hand in the cylinder housing in a further cylindrical guide opening are guided, wherein the guide openings have the same diameter.
  • a coupling rod for actuating the control slide is provided such that the control slide can be pushed by means of the coupling rod in the working direction of the piston.
  • the spool as described above defines a pressure chamber in the piston, which is pressure-connected to the low-pressure chamber, thus acting on the spool uninterrupted a force counter to the working direction.
  • the coupling rod therefore has to push this to actuate the spool this only in the working direction, but not pull the spool. It is therefore not necessary that control rod and spool are firmly connected. In particular, the coupling rod can rest only loosely on the spool.
  • the coupling rod is connected to an electromechanical transducer.
  • the electromechanical transducer is designed as a linear direct motor and its longitudinal axis movable along the working rotor is firmly connected to the coupling rod.
  • a method with the features of claim 12 is also provided.
  • the working pressure chamber for moving the piston in the working direction with hydraulic fluid with a high pressure PH is applied.
  • a low-pressure space which is delimited by a region of the piston facing away from the working pressure chamber, is acted upon by a low-pressure PN to move the piston back against the working direction.
  • PN ⁇ PH.
  • a hydraulic drive device according to the invention is used for carrying out the method. This ensures that the return movement of the piston counter to the working direction in an energy-saving manner by hydraulic fluid at low pressure is brought about. High pressure hydraulic fluid is only needed to move the piston in the direction of operation.
  • the method can be further configured in that the pressure of the hydraulic fluid pressurizing the working pressure chamber is set as a function of the travel of the piston and / or the working load of the piston.
  • the low-pressure space is continuously subjected to low pressure.
  • the high pressure of the hydraulic fluid pressurizing the working pressure chamber has a value p1 for moving the piston from its retracted end position in the working direction until or shortly before a workload is received, and then, in particular during the workload, p1 is less than p2.
  • the high pressure has a value p3, where p3 is less than p2 and / or p3 is equal to p1.
  • FIG. 1 a longitudinal section through a hydraulic drive device according to the invention in the rest position
  • FIG. 2 a part of the drive device according to FIG. 1 in the state for extending the piston as a longitudinal section
  • FIG. 3 a part of the drive device according to FIG. 1 in the state for returning the piston as a longitudinal section
  • FIG. 4 the time course of the travel of the piston and the set pressure of the high pressure supply.
  • the in the Figures 1-3 shown hydraulic working device has a cylinder 3 and a piston 5.
  • the piston 5 is displaceable and sealing in a cylinder chamber 8 along a working axis 10 guided.
  • the piston 5 is integrally connected to a piston rod 6, which projects beyond the cylinder 3 in a working direction 11.
  • the piston rod 6 may be connected to a punching tool (not shown) for forming a workpiece (not shown).
  • the piston 5 defines a working pressure chamber 13, a return chamber 15, a high pressure chamber 17 and a low pressure chamber 19, which are filled with hydraulic fluid for operating the device in the manner described below.
  • Pressurization of the working pressure chamber 13 with hydraulic fluid causes a force on the piston 5 in the working direction 11, while pressurization of the low-pressure chamber 19 causes a force on the piston 5 against the working direction 11.
  • the return chamber 15 is connected via a tank connection 16 with a tank 22 and serves to discharge the hydraulic fluid.
  • the high pressure chamber 17 is connected via a high pressure port 18 to a high pressure supply 24 for hydraulic fluid and serves to supply the working pressure chamber 13 with hydraulic fluid.
  • the low-pressure space 19 is connected via a low-pressure connection 20 to a low-pressure supply 26 for hydraulic fluid.
  • the piston 5 has a coaxial cylindrical bore 28 in which a control means 29 in the form of a spool 30 along the working axis 10 is guided longitudinally displaceable and sealing.
  • the axial end portions 32 and 34 of the spool 30 are formed like a piston.
  • the piston-side end portion 32 is sealingly guided in a cylindrical guide bore 36 in the piston 5 and limited in the piston 5 a pressure chamber 38 which is pressure-connected to the low-pressure chamber 19.
  • the piston 5 facing away from the end portion 34 of the spool 30 is sealingly guided in a cylindrical guide bore 40 in the cylinder 3.
  • the diameters of the guide bores 36 and 40 are the same size.
  • the spool 30 has through windows 48 with control edges 42 and 43. These are designed to cooperate with control edges 45 and 46 on the piston to a hydraulic follow-up control for piston. 5 and spool 30 to provide.
  • the return chamber 15 and the high pressure chamber 17 have flow openings 41 and 44, which connect the return chamber 15 and the high-pressure chamber with the axial bore 28 for the spool 30.
  • the piston-side control edges 45 are in communication with the flow opening 41 and thus with the return chamber 15, the piston-side control edges 46 with the flow opening 44 and thus with the high pressure chamber 17.
  • the control edges 42 and 43 on the spool 30 have the same or a slightly smaller distance from each other By shifting the spool 30 along the working axis 10, consequently, the working pressure space 13 can be pressure-connected either to the return space 15 or to the high-pressure space 17.
  • the low-pressure chamber 19, regardless of the position of the spool 30 has no pressure connection to the high-pressure chamber 17 or to the return chamber 15.
  • a coupling rod 50 is provided, by means of which the spool 30 can be pushed in the direction of work 11.
  • the coupling rod 50 is only loosely on the piston-like end portion 34 of the spool 30 at.
  • the coupling rod 50 is on the other hand firmly connected to the rotor 52 of an electromechanical transducer 54, which is designed in particular as a linear direct motor.
  • adjustment means 60 are provided. These set the pressure of the high pressure supply 24 dependent on the travel, i. the position of the piston 5 along the working direction 11 a. The position of the piston 5 along the working axis 10 is determined via a displacement measuring system 62. Furthermore, it can be provided that the adjusting means 60 adjust the pressure of the high pressure supply 24 as a function of the working load of the piston 5, which are determined by means of a load measuring system (not shown).
  • the hydraulic drive device 1 operates in the manner described below in the in FIG. 1 shown Rest position, the spool 30 is held by the coupling rod 50 in the rest position.
  • the force acting on the spool 30 by the low pressure in the pressure chamber 38 is counteracted counter to the working direction 11 by the control rod 50.
  • a flow of hydraulic fluid from the high pressure chamber 17 in the working pressure chamber 13 or the working pressure chamber 13 in the return chamber 15 is prevented, since the flow openings 41 and 44 are sealingly covered by the spool 30.
  • the coupling rod 50 If the coupling rod 50 is moved by the linear direct motor 54 in the working direction, the coupling rod 50 also pushes the control slide 30 in the working direction. As in FIG. 2 As a result, the high-pressure chamber 17 is pressure-connected to the working pressure chamber 13 and hydraulic fluid flows from the high-pressure supply 24 via the high-pressure chamber 17 through the through-windows 48 into the working pressure chamber 13. As a result, a force acts in the working direction 11 on the piston 5 and the piston 5 is moved in the working direction 11. The piston 5 follows the movement of the spool 30 until the control edges 43 and 46 again as in FIG. 1 illustrated close, so that a flow of hydraulic fluid from the high-pressure chamber 17 is prevented in the working pressure chamber 13 or the working pressure chamber 13 in the return chamber 15. It then turns back to a rest position similar to the one in FIG. 1 illustrated situation.
  • the high-pressure space 17 which is designed essentially as an annular space, extends so far in the axial direction that the high-pressure port 18 communicates with the flow opening 44 over the entire stroke. In operation, we also closed off by the spool 30 Flow opening 44 of the high-pressure chamber 17 is subjected to high pressure; however, a resultant force that moves the piston 5 in one direction does not result.
  • a hose connection between the high-pressure connection 18 and the flow-through opening 44 could also be provided.
  • the coupling rod 50 is moved by the linear direct motor 54 against the working direction of the end portion 34 of the spool 30 away. Due to the pressure prevailing in the pressure chamber 38 low pressure of the spool 30 is moved counter to the working direction 11. As in FIG. 3 illustrated, thereby opens a gap between the control edges 42 on the spool 30 and the control edges 45 on the piston 5, so that the working pressure chamber 13 is pressure-connected to the return chamber 15. Due to the low pressure prevailing in the low pressure chamber 19, a force counteracts the working direction 11 on the piston 5. The piston 5 can now move counter to the working direction 11, wherein the hydraulic fluid located in the working pressure chamber 13 through the passage window 48 in the return chamber 15 and there is displaced into the tank 22.
  • the piston 5 and the spool 30 move so long against the working direction 11 until further movement of the spool 30 is prevented by abutment of the end portion 34 of the spool 30 to the coupling rod 50. Then, the spool shifts back into a position in which the gap between the control edges 42 and 45 is closed. It turns then again a rest position similar to the FIG. 1 illustrated rest position.
  • the full working force of the piston 5 in the working direction 11 is not during the entire working cycle from forward and backward movement of the piston 5 is required. Rather, the full working force is only required when striking a piston rod 6 connected to the punching tool (not shown) on a workpiece (not shown) and during the penetration of the workpiece.
  • the adjusting means 60 adjust the pressure of the high pressure supply 24 depending on the travel path, ie from the position of the piston 5.
  • FIG. 4 the time course of the position of the piston 5 is shown together with the time course of the set by the adjusting means 60 pressure of the high-pressure supply 24.
  • the piston 5 is moved in the working direction 11 up to the position POS1, in which the punching tool connected to the piston rod strikes the workpiece to be deformed.
  • the pressure of the high pressure supply 24 is set to a low value p1, which may be selected to be equal to that of the low pressure supply 26 in particular.
  • the travel is detected by the displacement measuring system 62 and compared with a preset value, which corresponds for example to the distance of the punching tool in retracted end position of the piston 5 to the workpiece.
  • the adjusting means 60 increase the pressure of the high-pressure supply 24 to a value p2, which is significantly higher than p1 and typically corresponds to the maximum pressure of the high-pressure supply 24. This high pressure is maintained for the further movement of the piston 5 in the working direction 11 until the punching tool attached to the piston rod 6 has penetrated the workpiece (position POS2 of the piston 5 in FIG. 4 ). Thus, the workload on the piston 5 decreases.
  • the adjusting means 60 reduce the pressure of the high-pressure supply 24 to a value p3 which is less than the pressure p2 and in particular equal to the pressure of the low-pressure supply 26.
  • the spool 30 blocks a further flow of hydraulic fluid from the high-pressure supply 24 into the working pressure chamber 13. An energy-consuming volumetric flow of hydraulic fluid from the high-pressure supply 24 is therefore prevented.
  • the return movement is effected only by a volume flow of hydraulic fluid from the low pressure supply 26.
  • the described embodiment of the invention reduces the energy consumption in typical use with repeated extension and retraction of the piston 5 considerably. This is done on the one hand in that the return movement of the piston 5 against the working direction 11 is basically caused by hydraulic fluid from an energy-saving low-pressure supply 26. On the other hand, the energy requirement is further reduced by the described, depending on the travel and / or the workload of the piston 5 high-pressure connection of the high-pressure supply 24.

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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)
  • Control Of Presses (AREA)
  • Press Drives And Press Lines (AREA)

Claims (15)

  1. Dispositif d'entraînement hydraulique (1) comprenant un piston (5) délimitant une chambre de pression de travail (13), sollicitée en pression par un liquide hydraulique, guidé mobile le long d'un axe de travail (10), dans une chambre du cylindre (8), et comprenant un moyen de commande (29), guidé au moins par endroits dans le piston (5), entre différents états de commande, et servant à la commande du débit du liquide hydraulique provenant d'une alimentation haute pression (24) dans la chambre de pression de travail (13), pour le déplacement du piston dans le sens (11) du travail et de la chambre de pression de travail (13) vers une chambre de retour (15), caractérisé en ce que la zone du piston (5) opposée à la chambre de pression de travail (13) délimite une chambre basse pression (19) qui, en régime de fonctionnement du dispositif, est sollicitée en pression par une alimentation basse pression (26) pour le liquide hydraulique, de telle façon que le piston (5) soit déplacé en retour, à l'encontre du sens (11) du travail, si le moyen de commande (29) relie la chambre de pression de travail (13) à la chambre de retour (15).
  2. Dispositif d'entraînement selon la revendication 1, caractérisé en ce que la chambre basse pression (19) est séparée de l'alimentation haute pression (24) indépendamment de l'état de commande du moyen de commande (29).
  3. Dispositif d'entraînement selon la revendication 1 ou 2, caractérisé en ce que des moyens de réglage (60) permettent de régler la pression de l'alimentation haute pression (24) indépendamment de la course de déplacement le long du sens (11) du travail du piston (5) et/ou de la charge de travail du piston (5).
  4. Dispositif d'entraînement selon la revendication 3, caractérisé en ce que les moyens de réglage (60) sont conçus de telle sorte que la pression de l'alimentation haute pression (24), destinée à déplacer le piston (5) de sa position finale revenue au point de départ dans le sens (11) du travail jusqu'à ou un peu avant la réception d'une charge de travail, présente une valeur p1 puis, en particulier pendant la charge de travail, une valeur p2, p1 < p2.
  5. Dispositif d'entraînement selon la revendication 4, caractérisé en ce que les moyens de réglage (60) sont conçus de telle sorte que lorsque le piston (5) effectue un autre déplacement dans le sens (11) du travail, après avoir surmonté la charge de travail, la pression de l'alimentation haute pression (24) présente une valeur p3, p3 < p2 et/ou p3 = p1.
  6. Dispositif d'entraînement selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un système de mesure de course (62) est destiné à déterminer la course de déplacement du piston (5) et/ou un système de mesure de charge est destiné à déterminer la charge de travail du piston (5).
  7. Dispositif d'entraînement selon l'une quelconque des revendications précédentes, caractérisé en ce que le moyen de commande (29), dans la zone dans laquelle il est guidé dans le piston (5), délimite le long du sens (11) du travail une chambre de pression (38) reliée en pression à la chambre basse pression (19).
  8. Dispositif d'entraînement selon l'une quelconque des revendications précédentes, caractérisé en ce que le moyen de commande (29) est conçu comme un tiroir de commande (30) guidé au moins par endroits à l'intérieur du piston (5) le long de l'axe de travail (10), ledit tiroir comprenant des arêtes de commande (42, 43) conçues pour coopérer avec d'autres arêtes de commande (45, 46) sur le piston (5), afin de commander le débit de liquide hydraulique entrant dans la chambre de pression de travail (13) ou en sortant.
  9. Dispositif d'entraînement selon la revendication 8, caractérisé en ce que le tiroir de commande (30) est guidé d'une part dans la zone du piston (5) adjacente à la chambre basse pression (19) dans une ouverture de guidage cylindrique (36) et d'autre part dans le boîtier de cylindre (3) dans une autre ouverture de guidage cylindrique (40), les ouvertures de guidage (36, 40) présentant le même diamètre.
  10. Dispositif d'entraînement selon la revendication 8 ou 9, caractérisé en ce qu'une barre d'accouplement (50) destinée à actionner le tiroir de commande (30) est prévue de telle sorte que le tiroir de commande (30) puisse être déplacé au moyen de la barre d'accouplement (50) dans le sens (11) du travail du piston.
  11. Dispositif d'entraînement hydraulique selon la revendication 10, caractérisé en ce que la barre d'accouplement (50) est reliée à un convertisseur électromécanique (54).
  12. Procédé permettant de faire fonctionner un dispositif d'entraînement hydraulique selon l'une quelconque des revendications précédentes, comprenant un piston (5) guidé mobile dans une chambre de cylindre (8) et délimitant une chambre de pression de travail (13), la chambre de pression de travail (13) étant soumise à l'effet d'une haute pression PH par un liquide hydraulique pour déplacer le piston (5) dans le sens (11) du travail, caractérisé en ce que pour ramener le piston (5) à l'encontre du sens (11) du travail, une chambre basse pression (19), délimitée par une zone du piston (5) opposée à la chambre de pression de travail (13), est soumise à l'effet d'une basse pression PN, PN <= PH.
  13. Procédé selon la revendication 12, caractérisé en ce que la haute pression du liquide hydraulique sollicitant en pression la chambre de travail de pression (13) est réglée en fonction de la cours de déplacement du piston (5) et/ou de la charge de travail du piston (5).
  14. Procédé selon la revendication 12 ou 13, caractérisé en ce que la chambre basse pression (19) est soumise à l'effet d'une basse pression de manière ininterrompue.
  15. Procédé selon la revendication 12, 13 ou 14, caractérisé en ce que la haute pression du liquide hydraulique, sollicitant en pression la chambre de pression de travail (13) et destinée à déplacer le piston (5) de sa position finale ramenée au point de départ dans le sens (11) du travail jusqu'à ou un peu avant la réception d'une charge de travail, présente une valeur p1 puis, en particulier pendant la charge de travail, une valeur p2, p1 < p2, et au cas où un autre déplacement du piston (5) dans le sens (11) du travail, une fois la charge surmontée, serait prévu, la haute pression présente une valeur p3, p3 < p2 et/ou p3 = p1.
EP10701488.8A 2009-01-23 2010-01-11 Dispositif d'entraînement hydraulique à deux chambres de pression, et procédé permettant de faire fonctionner un dispositif d'entraînement hydraulique à deux chambres de pression Active EP2229537B8 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910005998 DE102009005998B4 (de) 2009-01-23 2009-01-23 Hydraulische Antriebsvorrichtung mit zwei Druckräumen und Verfahren zum Betreiben einer hydraulischen Antriebsvorrichtung mit zwei Druckräumen
PCT/EP2010/050199 WO2010084043A1 (fr) 2009-01-23 2010-01-11 Dispositif d'entraînement hydraulique à deux chambres de pression, et procédé permettant de faire fonctionner un dispositif d'entraînement hydraulique à deux chambres de pression

Publications (3)

Publication Number Publication Date
EP2229537A1 EP2229537A1 (fr) 2010-09-22
EP2229537B1 true EP2229537B1 (fr) 2013-07-24
EP2229537B8 EP2229537B8 (fr) 2013-10-30

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EP10701488.8A Active EP2229537B8 (fr) 2009-01-23 2010-01-11 Dispositif d'entraînement hydraulique à deux chambres de pression, et procédé permettant de faire fonctionner un dispositif d'entraînement hydraulique à deux chambres de pression

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US (1) US9121419B2 (fr)
EP (1) EP2229537B8 (fr)
CN (1) CN102292554B (fr)
DE (1) DE102009005998B4 (fr)
WO (1) WO2010084043A1 (fr)

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JP5538096B2 (ja) * 2010-06-30 2014-07-02 三菱アルミニウム株式会社 油圧装置の制御方法と油圧装置
DE102013104717B4 (de) 2013-05-07 2022-02-17 Ewo Fluid Power Gmbh Hydraulikzylinder mit integriertem Wegaufnehmer
CN105020190A (zh) * 2014-04-30 2015-11-04 张凯 阀芯内直动导控机构及流体控制阀
CN108331801A (zh) * 2018-04-13 2018-07-27 王志海 一种液压缸及含有该液压缸的液压设备
CN110285109B (zh) * 2019-05-24 2020-09-04 南京蒙福液压机械有限公司 一种气动控制阀及气液压力转换控制装置

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FR1574501A (fr) * 1967-07-20 1969-07-11
US3664234A (en) * 1970-04-27 1972-05-23 Sperry Rand Corp Digital electrohydraulic servo actuator
US3961561A (en) * 1971-11-08 1976-06-08 Applied Power Inc. Proportional force amplifier
DE3246738A1 (de) 1982-09-28 1984-03-29 Dr. H. Tiefenbach Gmbh & Co, 4300 Essen Mit eigenmedium gesteuertes hydraulikventil mit einstellbarem durchlassquerschnitt
US4907492A (en) * 1987-06-16 1990-03-13 Sig Schweizerische Industrie-Gesellschaft Apertured valve disposed in hollow piston rod of follower-type motor
DE3720266A1 (de) 1987-06-19 1988-12-29 Bw Hydraulik Gmbh Elektrohydraulisches regelsystem
DE19632368A1 (de) 1996-08-10 1998-02-12 Bosch Gmbh Robert Elektrohydraulisches Regelwegeventil
DE10255454A1 (de) 2002-11-28 2004-06-09 Tries Gmbh + Co. Kg Steuerventil
ATE389530T1 (de) 2003-05-16 2008-04-15 Bosch Rexroth Ag Hydraulischer antrieb

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Publication number Publication date
CN102292554A (zh) 2011-12-21
EP2229537A1 (fr) 2010-09-22
US20110271667A1 (en) 2011-11-10
DE102009005998A1 (de) 2010-08-05
US9121419B2 (en) 2015-09-01
EP2229537B8 (fr) 2013-10-30
CN102292554B (zh) 2014-07-09
DE102009005998B4 (de) 2012-12-27
WO2010084043A1 (fr) 2010-07-29

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