EP1288507B1 - Systeme d'entrainement a faible perte pour un actuateur hydraulique - Google Patents

Systeme d'entrainement a faible perte pour un actuateur hydraulique Download PDF

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Publication number
EP1288507B1
EP1288507B1 EP02023249A EP02023249A EP1288507B1 EP 1288507 B1 EP1288507 B1 EP 1288507B1 EP 02023249 A EP02023249 A EP 02023249A EP 02023249 A EP02023249 A EP 02023249A EP 1288507 B1 EP1288507 B1 EP 1288507B1
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EP
European Patent Office
Prior art keywords
drive system
drive
actuator
pump
pumps
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02023249A
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German (de)
English (en)
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EP1288507A3 (fr
EP1288507A2 (fr
Inventor
Bernhard Zervas
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Eaton Fluid Power GmbH
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Eaton Fluid Power GmbH
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Filing date
Publication date
Priority claimed from DE19642163A external-priority patent/DE19642163A1/de
Application filed by Eaton Fluid Power GmbH filed Critical Eaton Fluid Power GmbH
Priority claimed from EP96944055A external-priority patent/EP0873475B1/fr
Publication of EP1288507A2 publication Critical patent/EP1288507A2/fr
Publication of EP1288507A3 publication Critical patent/EP1288507A3/fr
Application granted granted Critical
Publication of EP1288507B1 publication Critical patent/EP1288507B1/fr
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/265—Control of multiple pressure sources
    • F15B2211/2658—Control of multiple pressure sources by control of the prime movers
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30585—Assemblies of multiple valves having a single valve for multiple output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention relates to a drive system with at least two hydraulic actuators, which can be supplied by means of at least one pump with a hydraulic fluid.
  • a drive system for a hydraulic double-acting actuator which has two working chambers. Each working chamber is associated with a pump, wherein the pumps can be driven by a common shaft or by means of independent drives.
  • a check valve is arranged, which blocks a return flow of a hydraulic medium from the working chamber to the pump.
  • a check valve is arranged, which blocks a return flow of a hydraulic medium from the working chamber to the pump.
  • a directional valve is arranged, which blocks in certain positions the output between the pump and the tank.
  • a hydraulic lifting device which is designed to be double-acting.
  • the lifting device are associated with two pumps, which can be driven together by an electric motor.
  • the working chamber arranged closer to the geodesic center of the earth can be provided with a hydraulic medium by means of both pumps.
  • the supply of hydraulic medium by a pump In the other working chamber, the supply of hydraulic medium by a pump. From the latter pump, the hydraulic medium is urged back into a tank with appropriate operation via two check valves. From the closer to the geodetic center of the earth working chamber, the hydraulic medium via a pump and a check valve is fed back into the tank.
  • the pump drives the other pump in parallel with the electric motor.
  • Machines with a plurality of actuators which are to carry out completely or partially sequentially different working movements, are usually supplied with hydraulic energy by means of a control valve circuit which is driven by one or more pumps which are driven at constant speed.
  • the technical disadvantage of these systems is a poor efficiency, because the control valves, in principle, implement hydraulic energy in heat energy.
  • a hydraulic actuator can be controlled or regulated by two bidirectionally speed-controlled pumps, without any control valve and thus extremely low-loss in four-quadrant operation.
  • the two pumps is assigned a valve circuit, in particular in sequential processes, the two pumps can each be assigned to the active actuator or single-acting operation two actuators.
  • the valve assembly advantageously allows the use of only two pumps, which can be connected via the valve assembly with the individual actuators loss. It can therefore save a larger number of pumps, which simplifies the structure and makes it more economical.
  • the valve assembly has essentially the task of producing the connection between the pumps and the actuators loss, the control functions are taken directly from the pump.
  • the valve arrangement has a plurality of switching positions, in each of which an actuator is connected in double-acting mode with the two pumps.
  • valve arrangement has switching positions which enable a connection of the two pumps with different actuators, so that therefore two actuators can be operated simultaneously.
  • the valve assembly has switching positions in which the two pumps are connected in parallel and supply an actuator together.
  • valve arrangement can be carried out with seat valves in order to fix the currently non-driven actuators leak-free.
  • valve arrangement for single-actuated actuators can be designed with counter-holding valves.
  • Such pumps are particularly simple, so that there is a cost-effective and requisitesunan devise realization.
  • an embodiment of the drive which has a co-operating with the drive means control, which is designed as a control circuit and at least one sensor, the position, speed and / or acceleration of the actuator and / or the pressure acting on the actuator or of detected forces applied to the actuator. In this way it is possible to adapt the drive very variable to the actual conditions.
  • the drive cooperates with a double-acting piston arrangement.
  • it is generally combined with any hydraulic actuators, for example, with single-acting actuators, hydraulic motors or gear assemblies.
  • FIG. 1 shows an actuator 1 designed as a hydraulically double-acting piston arrangement, which has a piston 5, which is movable in a cylinder 3 and on which a piston rod 7 is mounted.
  • the piston 5 and the piston rod 7 are inserted into the cylinder 3 so that two pressure chambers 9 and 11 are formed.
  • the first pressure chamber 9 is connected via a feed line 13 to a pump 15, which is assigned a drive device 17.
  • this comprises an electric motor 19, which is connected to the first pump 15 via a shaft 21, which is only indicated here.
  • the first pump 15 is connected via a supply line 23 to a tank 25.
  • Parallel to the pump 15, a valve 27 is provided, which is connected on the one hand to the supply line 13 and on the other hand to the supply line 23.
  • the valve 27 is designed here as a check valve, which is arranged so that at a negative pressure in the supply line 13, the existing hydraulic fluid in the tank 25 can be sucked, even if the first pump 15 should not be driven.
  • a second pump 15 ' delivers a hydraulic medium from the tank 25 via a supply line 13'.
  • the second pump 15 ' is connected to the tank 25 via a supply line 23'.
  • the second pump 15 ' is associated with a drive device 17'. It is possible to drive the two pumps 15 and 15 'via a single motor, for example electric motor 19.
  • the drive device 17 ' comprises a second electric motor 19' which drives the second pump 15 'via a shaft 21' indicated here.
  • a valve is again provided here, formed as a check valve 27 'and is arranged so that at a negative pressure in the supply line 13' hydraulic medium via the supply line 23 'from the tank 25 can be sucked.
  • the supply line 13 ' is connected via a pressure relief valve 29' to the return line 31 leading to the tank 25.
  • the hydraulic system associated with the actuator 1 may be formed with a cooler 33 which is integrated here into the supply line 23 to the first pump 15. It is also possible to install this cooler 33 at any point of the hydraulic system. Finally, it is conceivable to provide one or more of the supply lines with cooling fins to dissipate excess heat.
  • the drive shown in Figure 1 for the actuator 1 also has a control 35, which is connected via control lines 37 and 37 'to the electric motors 19 and 19'.
  • At least one sensor 39 is associated with the actuator 1, the output signals of which are fed via a signal line 41 to an evaluation circuit 43 which forms a control circuit 45 together with the drive 35.
  • the evaluation circuit 43 can be supplied via a line 47 at least one external signal, via which the drive for the actuator 1 can be influenced.
  • the sensor 39 which may comprise an analog-to-digital converter, is capable of detecting a wide variety of physical quantities of the actuator 1, for example its position, the speed and / or acceleration of the piston 5 and the piston rod 7, respectively, in the supply lines 13 and / or 13 'given pressure and / or the forces exerted by the actuator 1 forces. It is also possible that physical variables of the actuator 1 are detected indirectly by sensors in the feed lines 13 and 13 'or in the drive 35 and / or the evaluation circuit 43 or the electric motors 19 and 19'. One or more sensors, for example current or speed sensors, may also be integrated in the control 35 or the electric motors 19 and 19 '. As a result, if necessary, the external sensor 39 can be omitted and a modular design of the drive can be realized.
  • Figure 1 shows that a total of a drive for an actuator 1 can be realized, which allows a two- or four-quadrant operation. This is possible both when the control 35 is realized as a control circuit or when this, as shown in the figure, is designed as a control circuit, for example as a single-loop control loop.
  • the control circuit may comprise continuous controllers, for example PID and / or state controllers with / without observer or discontinuous controllers. It may also be constructed such that one or more of the physical quantities are controlled in parallel or sequentially.
  • regulators with integrating components are preferably used, that is, regulators with I, PI or PID behavior.
  • the control circuit can be realized by means of analog or digital technology or a combination of analog and digital technology.
  • the pumps 15 and 15 'designed as constant pumps that is, they have a constant displacement volume. It is also conceivable to design one or both of the pumps as variable displacement pumps, wherein one or two displacement chambers can be realized. It is essential that a four-quadrant drive can be realized without installing any throttle valves in the supply lines 13 and 13 '. The drive for the actuator 1 therefore operates particularly low loss. From the above, it is also clear that the drive is very simple and thus cost-effective, because even for a four-quadrant drive only pumps with a constant displacement volume are required, so relatively inexpensive realizable pumps. It only requires a drive for the pumps, which allows variable flow rates.
  • the drive shown here also meets high safety requirements, because on the one hand pressure relief valves 29, 29 'and on the other hand designed as a Nachsaugventile valves 27, 27' are provided.
  • the valves 27, 27 ', 29 and 29' have only a safety function and are not needed for the normal operation of the drive, that is, they are inactive.
  • a particularly simple structure can be achieved in that the electric motors 19 and 19 'with the associated pumps 15 and 15' can be formed as a unit.
  • the delivery rate of the pumps is achieved by adjusting the motor speed or the speed, which is possible with the aid of the control 35. This can also be integrated into the motor and pump unit, resulting in a particularly compact design. Since the actuator between the two pumps 15 and 15 'is clamped, results in a high rigidity.
  • the simple drive for the actuator for a position and pressure control and / or for a speed and pressure control can be designed.
  • the drive for the actuator can additionally be controlled, in addition to the speed-dependent delivery rate regulation by the electric motors 19, 19', by changing the displacement volume of the pumps. It thus turns out that the drive for the actuator 1 can be varied in many ways and adapted to different fields of use.
  • FIG. 2 shows a drive system 51, which consists of several, in the present case, four actuators 1.1 to 1.4.
  • a drive system 51 is part of a machine, which performs various working movements in whole or in part sequential operation.
  • the actuators 1.1 to 1.3 are each a hydraulic double-acting piston cylinder, as has already been described in connection with Figure 1. For a second description is therefore omitted. Only the actuator 1.4 differs insofar as this is a hydraulic motor.
  • the pump unit 53 has two pumps 15, 15 ', which are driven by the electric motor 19 or 19' with the shaft 21 or 21 '.
  • the two supply lines 23, 23 'of the two pumps 15, 15' are connected to the tank 25.
  • the check valves 27, 27 'shown in FIG. 1, as well as the overpressure valves 29, 29' are shown as a switching block 55 for the sake of clarity. However, the operation corresponds to that of the valves 27 and 29th
  • control and control unit 57 is shown only as a functional block.
  • the control unit 57 comprises for each actuator a control circuit 45, which comprises a control 35 and an evaluation circuit 43.
  • the evaluation circuit 43 assigned to an actuator is supplied with the signal supplied by the sensor 39 via the line 41.
  • the wiring of the aforementioned components corresponds to that described with reference to the figure 1, so that the exact functioning at this point does not need to be discussed in more detail.
  • FIG. 2 furthermore shows a valve arrangement 59, which is connected in the supply lines 13 coming from the two pumps 15, 15 'and leading to the actuators.
  • the valve assembly has two hydraulic inputs 61.1 and 61.2, wherein the first input 61.1 is connected to the pump 15 and the second input 61.2 is connected to the pump 15 '.
  • two outputs 63.1, 63.1 'to 63.4, 63.4' are provided for each actuator 1.1 to 1.4.
  • the outputs 63.1 to 63.4 are each connected to the supply line 13 of an actuator 1.1 to 1.4, the outputs 63.1 'to 63.4' each with the supply line 13 'of an actuator.
  • the valve assembly 59 has a plurality of, preferably four switching positions in the present embodiment, in which the inputs 61.1 and 61.2 are connected to predetermined outputs 63 loss.
  • the input 61.1 is connected to the output 63.1 and the input 61.2 is connected to the output 63.1 '.
  • the pump 15 is connected to the supply line 13 and the pump 15 'to the supply line 13'.
  • the operation of the actuator 1.1 in conjunction with the control device 57 and the pump unit 53 corresponds to the operation of the arrangement in Figure 1, which is why a further description is omitted here.
  • the switching position of the valve arrangement 59 can be changed, for example, via a control line 63 of the control unit 57.
  • other associations of pump unit 53 and the actuators per switching position are conceivable.
  • FIG 3 a schematic diagram of a drive is shown to explain the technical environment, which is not the subject of the invention, but essentially corresponds to the aforementioned embodiment of Figure 2. On a repeated description of the parts identified by the same reference numerals is therefore omitted. The only difference is that the valve assembly 59 allows a different assignment of the inputs 61.1 and 61.2 to the outputs 63.1 to 63.4.
  • the input 61.1 is connected to the output 63.2 and the input 61.2 is connected to the output 63.4.
  • the valve arrangement 59 has an output 65, which leads via a line 67 to the tank 25.
  • This output 65 is connected on the one hand to the output 63.2 'and on the other hand to the output 63.4'.
  • valve assembly 59 can be formed so that a switch position is provided for each desired operating combination of two actuators.
  • FIG. 4 shows a further drive which likewise is not the subject of the invention and whose fundamental structure corresponds to the exemplary embodiment shown in FIG. On a repeated description of the parts identified by the same reference numerals is therefore omitted.
  • FIG. 4 shows that the inputs 61.1 and 61.2 in the switching position of the valve arrangement 59 shown are connected to the output 63.3, while the output 63.3 'is connected to the output 65.
  • actuators 1.1, 1.2 and 1.4 can then be connected to the two pumps 15, 15 '.

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

Claims (15)

  1. Système d'entraînement pour un ou plusieurs actionneurs (1) hydrauliques à effet double qui comprennent respectivement deux chambres de travail (9, 11), dont le volume est variable et qui sont séparées l'une de l'autre au moyen d'un élément actionneur (5) entraîné par une variation de volume, le système d'entraînement comprenant deux pompes (15, 15') alimentant les chambres de travail (9, 11) avec un fluide hydraulique, caractérisé en ce que respectivement un dispositif d'entraînement (17, 17') conçu comme moteur électrique (19, 19') pour la livraison de débits réglables différemment les uns des autres est attribué à chaque pompe (15, 15'), en ce que les moteurs électriques (19, 19') sont reliés à une commande d'amorçage (35, 57) au moyen de respectivement une ligne de commande (37, 37'), et en ce que respectivement une pompe (15, 15') peut être attribuée à chaque chambre de travail (9, 11), la pompe (15, 15') respective transportant le fluide hydraulique d'un réservoir (25) dans la chambre de travail (9,11) ou le refoulant de la chambre de travail (9,11) vers la pompe (15, 15') respective au moyen d'une conduite d'arrivée (13, 13'), la pompe (15, 15') respective entraînant le moteur électrique (19, 19') qui lui est attribué en générant de l'énergie électrique.
  2. Système d'entraînement selon la revendication 1, caractérisé en ce qu'un dispositif de soupape (59) avec des entrées et des sorties est prévu, les pompes (15, 15') pouvant être reliées dans une première position de commutation au moyen d'une première entrée (61.1) et d'une première sortie (63.1) à une première chambre de travail (9) et au moyen d'une seconde entrée (61.2) et d'une seconde sortie (63.1') à une seconde chambre de travail (11) d'un actionneur (1.1).
  3. Système d'entraînement selon la revendication 2, caractérisé en ce que le dispositif de soupape (59) est réalisé avec des soupapes à siège, afin de définir les actionneurs éventuellement sans fuite.
  4. Système d'entraînement selon la revendication 2, caractérisé en ce qu'au moins une pompe (15, 15') présente un volume de refoulement constant et/ou au moins une pompe (15, 15') est conçue comme pompe à cylindrée variable.
  5. Système d'entraînement selon l'une quelconque des revendications précédentes, caractérisé en ce que la commande d'amorçage (57, 35) est conçue comme circuit de commande.
  6. Système d'entraînement selon l'une quelconque des revendications précédentes, caractérisé en ce que la commande d'amorçage (57, 35) est conçue comme un circuit de réglage (45) et comprend au moins un capteur (39).
  7. Système d'entraînement selon la revendication 6, caractérisé en ce qu'au moins un capteur (39) est attribué à l'actionneur (1).
  8. Système d'entraînement selon la revendication 6 ou 7, caractérisé en ce que le capteur (39) enregistre la position, la vitesse et/ou l'accélération de l'actionneur (1) et/ou la pression agissant sur l'actionneur (1) et/ou les forces exercées par l'actionneur (1).
  9. Système d'entraînement selon l'une quelconque des revendications 6 à 8, caractérisé en ce que le circuit de réglage (45) comprend des régulateurs et/ou des régulateurs d'état continu avec/sans observateur ou des régulateurs discontinus.
  10. Système d'entraînement selon l'une quelconque des revendications 6 à 9, caractérisé en ce que le circuit de réglage (45) peut être réalisé au moyen de la technique analogique et/ou la technique numérique.
  11. Système d'entraînement selon l'une quelconque des revendications 6 à 10, caractérisé par un circuit de réglage (45), avec lequel un réglage parallèle ou séquentiel d'au moins une grandeur physique enregistrée peut être réalisée.
  12. Système d'entraînement selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif d'entraînement (17, 17') et la commande d'amorçage (57, 35) sont conçus comme une unité.
  13. Système d'entraînement selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif d'entraînement (17, 17') comprend au moins un moteur électrique (19, 19') avec régime variable pour les deux sens de rotation.
  14. Système d'entraînement selon la revendication 2 et l'une quelconque des revendications 6 à 13, caractérisé en ce que les commandes d'amorçage (35), la commande du dispositif de soupape (59) et les circuits de réglage (45) sont regroupés pour former une unité de commande (57).
  15. Système d'entraînement selon l'une quelconque des revendications précédentes, caractérisé en ce que les commandes d'amorçage (35), les circuits de réglage (45) ou l'unité de commande (57) disposent d'un système de bus pour l'échange des données.
EP02023249A 1996-01-10 1996-12-21 Systeme d'entrainement a faible perte pour un actuateur hydraulique Expired - Lifetime EP1288507B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19600650A DE19600650C2 (de) 1996-01-10 1996-01-10 Antrieb für einen hydraulischen doppelwirkenden Aktuator
DE19600650 1996-01-10
DE19642163 1996-10-12
DE19642163A DE19642163A1 (de) 1996-01-10 1996-10-12 Verlustarmer Antrieb für mehrere hydraulische Aktuatoren
EP96944055A EP0873475B1 (fr) 1996-01-10 1996-12-21 Systeme d'entrainement a faible perte pour plusieurs actuateurs hydrauliques

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP96944055A Division EP0873475B1 (fr) 1996-01-10 1996-12-21 Systeme d'entrainement a faible perte pour plusieurs actuateurs hydrauliques

Publications (3)

Publication Number Publication Date
EP1288507A2 EP1288507A2 (fr) 2003-03-05
EP1288507A3 EP1288507A3 (fr) 2003-05-07
EP1288507B1 true EP1288507B1 (fr) 2006-01-18

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EP02023249A Expired - Lifetime EP1288507B1 (fr) 1996-01-10 1996-12-21 Systeme d'entrainement a faible perte pour un actuateur hydraulique

Country Status (4)

Country Link
EP (1) EP1288507B1 (fr)
DE (2) DE19600650C2 (fr)
IN (1) IN188385B (fr)
ZA (1) ZA9777B (fr)

Cited By (3)

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DE102010017912A1 (de) 2010-04-21 2011-10-27 Voith Patent Gmbh Hydraulischer Antrieb und Verfahren zum Betreiben eines hydraulischen Antriebs
DE102014218885A1 (de) * 2014-09-19 2016-03-24 Voith Patent Gmbh Hydraulischer Antrieb mit Eilhub und Lasthub
DE102014218884A1 (de) * 2014-09-19 2016-03-24 Voith Patent Gmbh Hydraulischer Antrieb mit Eilhub und Lasthub

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US6374606B1 (en) 1999-03-19 2002-04-23 Caterpillar S.A.R.L. Dual pump ejector system for articulated trucks and the like having horizontal discharge
WO2000057066A2 (fr) * 1999-03-19 2000-09-28 Caterpillar, Inc. Systeme et procede de commande d'ejection de materiaux d'un vehicule
DE102005010638A1 (de) * 2005-03-08 2006-09-28 Bosch Rexroth Aktiengesellschaft Hydraulische Betätigungsvorrichtung, insbesondere für ein Cabriolet
DE102008039011B4 (de) * 2008-08-21 2020-01-16 MAE Maschinen- u. Apparatebau Götzen GmbH Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers
DE102008053766A1 (de) * 2008-10-21 2010-04-22 Voith Patent Gmbh Hydraulischer Pressenantrieb und Verfahren zum Betreiben eines hydraulischen Pressenantriebs
EP2712688B1 (fr) 2012-09-28 2020-12-02 Siemens Aktiengesellschaft Entraînement de coussin hydraulique et procédé de fonctionnement d'un entraînement de coussin hydraulique
DE102013212937A1 (de) * 2013-07-03 2014-07-10 Voith Patent Gmbh Vorrichtung zum Öffnen und Schließen der Leitschaufeln einer hydraulischen Maschine
EP2824334A1 (fr) 2013-07-08 2015-01-14 Siemens Aktiengesellschaft Entraînement linéaire hydraulique
CN104179736B (zh) * 2014-08-15 2016-08-24 徐工集团工程机械股份有限公司科技分公司 一种工程机械定量泵调速液压系统
JPWO2017056702A1 (ja) * 2015-09-28 2018-06-14 ボッシュ・レックスロス株式会社 油圧シリンダ駆動装置
EP3173163A1 (fr) 2015-11-30 2017-05-31 Siemens Aktiengesellschaft Procédé de commande ou de régulation du mouvement d'un outil, système hydraulique, presse dotée de coussin de serre-flan et dispositif de commande
EP3824191A1 (fr) 2018-08-21 2021-05-26 Siemens Energy, Inc. Actionneur hydraulique à double effet avec différentes pompes pour chaque direction d'actionnement
CN109915442A (zh) * 2019-03-19 2019-06-21 江门市蒙德电气股份有限公司 一种基于双向进压调节的液压缸位置控制系统及控制方法
DE102019121974A1 (de) 2019-08-15 2021-02-18 Voith Patent Gmbh Überhitzungsschutz für hydraulische Systeme

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DE3148174A1 (de) * 1981-12-05 1983-06-09 Robert Bosch Gmbh, 7000 Stuttgart Elektrohydraulischer stellantrieb
SE461391B (sv) * 1987-10-28 1990-02-12 Bt Ind Ab Hydraulisk lyftanordning
DE4008792A1 (de) * 1990-03-19 1991-09-26 Rexroth Mannesmann Gmbh Antrieb fuer einen hydraulischen zylinder, insbesondere differentialzylinder
DE4030950A1 (de) * 1990-09-29 1992-04-02 Bosch Gmbh Robert Hydraulische steuereinrichtung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010017912A1 (de) 2010-04-21 2011-10-27 Voith Patent Gmbh Hydraulischer Antrieb und Verfahren zum Betreiben eines hydraulischen Antriebs
DE102010017912B4 (de) 2010-04-21 2022-08-25 Voith Patent Gmbh Hydraulischer Antrieb und Verfahren zum Betreiben eines hydraulischen Antriebs
DE102014218885A1 (de) * 2014-09-19 2016-03-24 Voith Patent Gmbh Hydraulischer Antrieb mit Eilhub und Lasthub
DE102014218884A1 (de) * 2014-09-19 2016-03-24 Voith Patent Gmbh Hydraulischer Antrieb mit Eilhub und Lasthub
DE102014218884B4 (de) * 2014-09-19 2020-12-10 Voith Patent Gmbh Hydraulischer Antrieb mit Eilhub und Lasthub

Also Published As

Publication number Publication date
EP1288507A3 (fr) 2003-05-07
ZA9777B (en) 1997-07-11
IN188385B (fr) 2002-09-14
DE19600650A1 (de) 1997-07-24
DE59610776D1 (de) 2003-11-20
DE19600650C2 (de) 2003-05-28
EP1288507A2 (fr) 2003-03-05

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