EP2732959B1 - Agencement d'entraînement hydraulique sans accumulateur de pression pour et avec un consommateur, notamment pour presse hydraulique, et procédé d'entraînement hydraulique sans accumulateur de pression d'un consommateur - Google Patents

Agencement d'entraînement hydraulique sans accumulateur de pression pour et avec un consommateur, notamment pour presse hydraulique, et procédé d'entraînement hydraulique sans accumulateur de pression d'un consommateur Download PDF

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Publication number
EP2732959B1
EP2732959B1 EP13005011.5A EP13005011A EP2732959B1 EP 2732959 B1 EP2732959 B1 EP 2732959B1 EP 13005011 A EP13005011 A EP 13005011A EP 2732959 B1 EP2732959 B1 EP 2732959B1
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EP
European Patent Office
Prior art keywords
pump
pressure
piston
main operating
speed
Prior art date
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Active
Application number
EP13005011.5A
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German (de)
English (en)
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EP2732959A2 (fr
EP2732959A3 (fr
Inventor
Manfred Mitze
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MAE Maschinen und Apparatebau Goetzen GmbH
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MAE Maschinen und Apparatebau Goetzen GmbH
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Publication of EP2732959A3 publication Critical patent/EP2732959A3/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
    • 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
    • F15B2211/20576—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
    • F15B2211/60—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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a pressure accumulator-free hydraulic drive assembly with the features of the preamble of claim 1.
  • the drive assembly comprises a consumer with two oppositely acting pressure chambers, one of which via a first pressure line and a pump assembly and the other via a second pressure line and the pump assembly Pressure medium can be supplied, for example, to actuate a consumer in the form of a piston / cylinder unit in a working stroke and retrieve in a return stroke to the starting position.
  • the invention further relates to a method for accumulatorless hydraulic driving a consumer according to the features of the preamble of claim 12.
  • Circuits for the motion control of hydraulic consumers are today realized in the vast majority in such a way that a working pump is constantly driven by an asynchronous motor.
  • the pumped hydraulic oil flows to a directional valve, in its rest position (closed state), the hydraulic oil, which conveys the pump, flows back to the storage tank without pressure.
  • the controlling directional valve is switched to a first working position, in which the hydraulic oil flows into the first pressure chamber (piston chamber) of the working cylinder, so that the piston rod extends.
  • the oil displaced in the pressure space opposite the piston chamber with respect to the piston flows back into the tank via the directional control valve.
  • the directional control valve is transferred to a second working position, in which the subsidized by the working pump Hydraufiköl is conveyed into the annular space of the piston / cylinder unit instead of the piston chamber, while the piston chamber is now connected via the return line to the Hydraullköltank.
  • a pressure limiting valve limits the system pressure to the permissible level. If the limit pressure is exceeded, hydraulic oil can flow off into the tank without pressure.
  • the working pump is now connected switching valveless with the piston chamber of a piston / cylinder unit.
  • the electric drive motor of the pump can be freely parameterized via a converter control in relation to speed and direction of rotation up to standstill.
  • the oil flow delivered by the working pump behaves almost proportionally to the engine speed. In this way, the hydraulic oil flow and thus also the piston movement can be influenced freely.
  • the annulus side of the piston is connected to an accumulator whose pressure is set slightly higher than the back pressure required to overcome the frictional losses and the gravity of the piston and any appended masses.
  • the actual position of the piston rod is transmitted via a displacement sensor to the control device.
  • the electric drive motor is stationary and there is no hydraulic oil conveyed and thus triggered no piston movement. If the working piston is to extend, the electric drive motor begins to rotate, the hydraulic oil flows into the piston chamber and the piston rod extends. The annular space side hydraulic oil volume flows into the accumulator and raises its pressure slightly. After reaching the desired piston position, the electric drive motor comes to a standstill via a corresponding control and the piston position is held.
  • the ability of the system for precise angular control of the electric drive motor allows a very accurate positioning of the working piston. The nominal positions are approached and held under full pressure with an accuracy of up to 1 ⁇ m without throttle losses.
  • the hydraulic controls the stroke and the return stroke of a piston / cylinder unit with a first pump and a conventional multi-way valve.
  • the function of the directional valve is to switch between the lifting and the return stroke.
  • a hydraulically operated piston / cylinder unit in which the piston chamber and the annular space are each supplied by a pump and a directional control valve, the DE 40 30 950 A1 , are taken.
  • the control device described there can be changed by operating multi-way valves either between a lifting or gearhubfunktion.
  • belunge in addition to the function "return stroke” a stroke function can be selectively superimposed.
  • WO 02104 820 A1 is a drive device with two pumps provided, which are operated by one or two variable speed and Dreh politicianssvariable motors.
  • the engine (s) do not operate continuously but only when the piston / cylinder unit is to be moved, whereby directional valves in the pressure lines for reversing the pressure direction are in principle not required. Only for limiting the pressure in the pressure lines may optionally be provided an arrangement of a plurality of conventional valves or alternatively a multi-way valve.
  • the invention has the object, speed and direction variable hydraulic drive assemblies waiving accumulator for bulk consumers, especially for hydraulic presses with a need for large volumes to make usable.
  • a pressure accumulator hydraulic drive assembly with the features of claim 1 is proposed. Accordingly, a pump assembly of a variable speed driven main working pump for working strokes and further provided from a variable speed driven auxiliary pump for return strokes, the conveying direction of the auxiliary pump reversible and the auxiliary pump via a directional control valve with either the first and / or the second pressure chamber of the consumer hydraulically connected or is connectable.
  • a pump assembly of a variable speed driven main working pump for working strokes and further provided from a variable speed driven auxiliary pump for return strokes, the conveying direction of the auxiliary pump reversible and the auxiliary pump via a directional control valve with either the first and / or the second pressure chamber of the consumer hydraulically connected or is connectable.
  • the object is achieved by the features of claim 12.
  • a pressure accumulator hydraulic drive assembly with the features of claim 4 is proposed, which is also of independent inventive significance, so that the applicant reserves the right to make this solution the subject of a divisional application.
  • This solution provides that in a generic accumulatorless hydraulic drive assembly, the pump assembly consists of a variable speed driven main working pump for working strokes and a variable speed driven auxiliary pump for return strokes, and that a control device is provided, which is to be established by the auxiliary pump, against the pressure in the Working space of the consumer acting back pressure in the Hiffspumpe associated pressure chamber controls or regulates.
  • auxiliary pump at the same volume flow as the main working pump, for example, only 1/10 of the power of the main working pump needed and that the costs incurred by the additional and independently driven auxiliary pump effort is significantly lower than the cost of a suitably designed accumulator. In this case, more favorable space and weight ratios are possible than in a suitably large accumulator.
  • it can be provided to realize switching valve-free direct connections between the main working pump and the first pressure chamber or the auxiliary pump and the second pressure chamber of the consumer and thus to avoid the potentially dangerous shocks in the system when using directional control valves in the pressure lines.
  • the electric drive motor of the main working pump simultaneously drives two hydraulic oil pumps whose combined volume flow allows the working piston to extend faster.
  • the rapid traverse pump can be connected by switching a directional control valve with the return tank for hydraulic oil. Then only the second pump delivers.
  • the required torque of the electric drive motor can be limited to an economically reasonable amount.
  • Another application of the accumulator-free hydraulic drive assembly according to the invention is to combine the piston / cylinder unit of the consumer with a known rapid traverse piston and filling valves, as they are known from conventional hydraulic controls per se.
  • the necessary filling valves with the necessarily large pipes so-called rapid traverse piston are relatively expensive.
  • a mechanical gear in particular a transmission gear
  • a drive motor associated with the main work pump is provided between the main working pump and a drive motor associated with the main work pump.
  • the rotational speed of the main working pump can be changed with respect to the rotational speed of the drive motor assigned to the main working pump.
  • Due to the interposed, mechanical transmission which may have a constant ratio, it is possible to increase the usable speed range of the drive motor significantly.
  • a low-cost, lower-torque motor can be used, or alternatively, a higher-flow pump.
  • the pump assembly consists of a variable speed driven main working pump for working strokes and a variable speed driven auxiliary pump for return strokes, wherein the per revolution funded volume of the main working pump and / or the auxiliary pump is variable.
  • the change in the volume delivered per revolution can preferably be regulated as a function of the pressure generated by the main working pump and / or the auxiliary pump.
  • the main working pump and / or the auxiliary pump may be formed in this solution as per se known axial piston pump or vane pump with per revolution variable volume flow.
  • the adjustment of the displacement of the pump can be done mechanically-hydraulically depending on the process pressure or a servo motor.
  • the load-dependent change in the delivery volume per revolution or the Pumpenhubraums for controlling the flow rate - ie the delivery volume per time - has the advantage that at low load, a high flow rate is achieved. This is expedient in particular for large consumers connected to the drive arrangement, since these then reach long distances or strokes in a short time.
  • the operation of the pump can be changed such that by reducing the Pumpenhubraums a lower torque of the drive motor is required, whereby the size of the drive motor can be reduced.
  • the possibility is given to achieve large volumes as needed.
  • an electrical converter in particular a frequency converter
  • a switchable brake between the electric drive motor of the pump assembly and the inverter is installed, easily higher-quality risk categories can be achieved with little effort.
  • the Applicant reserves the right to make that combination the subject of a divisional application. In the meantime, the converters have been certified as having the requirements of the second highest CE risk category 3.
  • Brakes with a correspondingly safe design are known, for example, from elevator construction.
  • the inverter can check the effectiveness of the brake at regular intervals by applying torque to the motor against the active brake, and the process controller checks to see if the rotor is moving improperly.
  • FIG. 1 shows a réelle réelletose hydraulic drive assembly in which a driven by an electric variable speed drive motor M1 hydraulic main pump P1 is connected without switching valve directly to the piston chamber K acting as a consumer 1 piston / cylinder unit via a pressure line D1.
  • an auxiliary pump P2 driven by an electric variable-speed drive motor M2 is connected to the annular space R of the load 1 via a switch valve-free direct connection D2.
  • the motor / pump unit M1 / P1 determines as a guide unit, the piston movement at least during its working stroke, as is customary even with accumulator-prone hydraulic drive assemblies.
  • a back pressure is generated, which simulates the function of an accumulator, as it is used in the accumulator hydraulic drive assemblies.
  • the torque of the motor M2 is controlled so that a certain, required for the process back pressure against the working pressure is generated and maintained.
  • This back pressure can be arbitrarily controlled or regulated regardless of the position of the piston or the piston rod.
  • it is possible to generate high stripping forces at the beginning of the return stroke for example, in a carried out by the consumer forming process of a workpiece, which are required, for example, to retrieve a forming die during the return stroke of the mold.
  • long return strokes, in particular with constant backpressure can be realized. At standstill or during the downward travel - ie in the initial range of the working stroke - the torque of the drive motor M1 can be reduced in order to save energy.
  • the motor / pump unit M2 / P2 requires only a low drive power, which is between 2% and 50% of the nominal power, compared to the main working pump which is needed by the main work pump. In many cases, about 1/10 of the rated power of the main working pump for the auxiliary pump is cheap and sufficient.
  • control lines 5A, 5B connect the controller 6 to the variable speed electric drive motors M1, M2.
  • the variable speed motors M1 and M2 are freely programmable via the control device 6, in particular in the form of a known converter, preferably in the form of a frequency converter, with respect to speed and direction of rotation - if desired, to a standstill.
  • the entire speed setting range can be traversed from standstill to the maximum permissible speed in both directions of rotation.
  • the drives can work in all four quadrants of a speed-torque diagram.
  • the drives can either drive right- or left-handed (quadrants I and II or quadrants III and IV) (quadrant I or III) or brake (quadrant II or IV). Since the hydraulic oil flow conveyed by the pumps P1 and P2 behaves approximately proportionally to the engine speed, in this way the oil flow and thus also the piston movement can be influenced freely. Pressure relief valves 4A and 4B limit the system pressure to the permissible level, so that when the set pressure is exceeded, hydraulic oil flows back into the hydraulic oil tank T via the returns 2A and 2B, respectively. The actual position of the piston rod is transmitted via the encoder 8 to the inverter control 6.
  • a preferred mode of operation is the following: When the load is at a standstill, the motors M1 and M2 are generally almost at rest, unless a leakage or the like is to be compensated. When the engine is stopped, no oil is pumped and thus no piston movement is initiated.
  • the motor M1 starts to rotate and the hydraulic oil flows into the piston chamber K (filling mode of the pump P1), so that the piston rod S extends.
  • the torque of the motor M2 running in the discharge mode of the pump P2 can be limited to a relatively low value.
  • the running in the emptying mode of the pump P2 motor M2 prevents, for example, that a hanging on the load load is lowered uncontrollably.
  • the direction of rotation of the motor M2 thus corresponds to the emptying mode of the pump P2, ie hydraulic oil is withdrawn from the annulus controlled while maintaining a certain back pressure against the piston of the consumer or drained.
  • the pump P2 is therefore from the annular space side flowing hydraulic oil volume be put into reverse rotation at low pressure, ie, that the motor M1 in turn drives the motor M2 and the motor M2 decelerates this driving force, since it runs slower than the drive torque of the motor M1 corresponded.
  • the oil flows back to the tank T without pressure after flowing through the pump P2.
  • the control device 6 of the motor M2 the engine braking torque of the motor M2 can be varied and thus a predefinable back pressure can be maintained. Since both electric motors M1 and M2 are accurately controlled, this allows a very exact positioning of the piston rod, whose target positions can be approached and held under full pressure and without throttle losses with an accuracy of up to 1 micron. If necessary, a position of the piston can be approached exactly at a speed close to 0 with high or even full pressure.
  • the generated by the limited drive torque of the motor M2 flow rate of the pump P2 is just so large that the reversed pump P1 from the piston chamber K promoted amount of oil on the annulus side R is replaced.
  • the piston comes to a precise stop position.
  • the embodiment according to FIG. 2 differs from the one after FIG. 1 by the use of a known so-called rapid traverse piston 3 'and a filling valve 9 and a third pressure line D3, which via an on / off valve 11 can be connected in bypass to the switching valve-less pressure line D1.
  • the rapid traverse piston 3 ' is inserted into the piston of the piston-cylinder unit 1.
  • the pump current of the main working pump P1 is not directed to the main piston, but to the much smaller diameter rapid traverse piston.
  • the piston rod S extends so much faster. Hydraulic oil for filling the piston chamber K is sucked out of the tank T via a non-returnable, serving as a filling valve 9 check valve.
  • the main piston surface is switched with the valve 11, so that the full piston force can be achieved.
  • the filling valve 9 is also opened in order to drive at high speed here too.
  • FIGS. 3A to 3C differs from the one after FIG. 1 by the use of the shadow valve 13 and the additional pressure line D4, with which the annular space R of the piston rod S with the valve 13 and depending on the switching position of the valve 13 with the piston chamber K of the piston / cylinder unit 1 can be connected.
  • the valve 13 is in the in FIG. 3B shown position "parallel arrows" switched. Both motors M1 and M2 are controlled via the control unit 6 with the same direction of rotation and speed.
  • the pump P1 delivers via the pressure line D1 directly into the piston chamber K, the pump P2 via the pressure line D4 also. Above the line D2 while the annular space R is connected to the piston chamber K.
  • the piston rod S extends because of the larger in relation to the surface of the annular space R surface of the piston K from.
  • the quantity of oil displaced from the annular space R via the pressure line D2 also flows into the piston space K via line D4. In this way, high exit speeds can be achieved by combining the delivery rates of the pumps P1 and P2 and additionally by using the quantity of oil flowing out of the annular space become.
  • FIG. 4 shows a hydraulic control for a machine that meets the highest CE risk category 4.
  • the picture shows a control similar to the one in the FIG. 1 shown; Controls of pictures 2 to 3 can be changed in the same way. The actual hydraulic control remains completely unchanged.
  • an electrically switchable brake B is installed between the motor M1 and the pump P1, an electrically switchable brake B is installed.
  • the braking torque is applied via springs, the ventilation is carried out by an electrically operated coil.
  • the brake is released by switching on the coil, for safe standstill it remains closed.

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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)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Claims (17)

  1. Agencement d'entraînement hydraulique dépourvu d'accumulateur de pression, pour et avec un grand consommateur (1), à savoir pour une presse hydraulique, avec deux chambres de pression (K, R) à effet opposé, dont l'une peut être alimentée par l'intermédiaire d'une première conduite sous pression (D1) et par un agencement de pompes (20) et l'autre peut être alimentée par l'intermédiaire d'une deuxième conduite sous pression (D2) et par l'agencement de pompes (20) avec des agents sous pression,
    caractérisé en ce que
    l'agencement de pompes (20) est composé d'une pompe de service principale (P1) entraînée à régime variable pour des courses de travail et d'une pompe auxiliaire (P2) entraînée à régime variable pour des courses de retour, la pompe de service principale (P1) et/ou la pompe auxiliaire (P2) étant conçue sous la forme d'une pompe à pistons axiaux ou d'une pompe à palettes,
    la direction de transport de la pompe auxiliaire (P2) est inversable et la pompe auxiliaire (P2) est ou peut être reliée hydrauliquement par l'intermédiaire d'un distributeur (13) au choix, avec la première (K) et/ou avec la deuxième (R) chambre de pression du consommateur (1), et
    hormis la pompe de service principale (P1), il est prévu une pompe à vitesse rapide avec un piston à vitesse rapide (3') mis en oeuvre dans le piston d'une unité piston/cylindre, une troisième conduite sous pression (D3) étant prévue, qui par l'intermédiaire d'une soupape d'ouverture/de fermeture (11) peut être commutée sur une dérivation vers la première conduite sous pression (D1), sachant qu'une fermeture de la soupape d'ouverture/de fermeture (11) a pour effet de diriger le flux de pompage de la pompe de service principale (P1) non pas sur le piston principal de la pompe de service principale (P1), mais sur le piston à vitesse rapide (3') de diamètre inférieur, suite à quoi, la tige de piston (S) peut sortir plus rapidement, et après l'atteinte d'une pression réglable, la surface du piston principal pouvant être commutée, à l'aide de la soupape d'ouverture/de fermeture (11).
  2. Agencement selon la revendication 1, caractérisé par une conduite de remplissage (7), reliant la chambre du piston (K) avec le réservoir (T), dans laquelle est placée une soupape de remplissage (9), lors de la course de retour, la soupape de remplissage (9) s'ouvrant également, pour pouvoir actionner l'agencement à vitesse plus élevée lors de la course de retour.
  3. Agencement selon l'une quelconque des revendications 1 ou 2, caractérisé en ce que l'espace annulaire (R) et la chambre du piston (K) peuvent être au choix, reliés hydrauliquement l'un à l'autre et de nouveau séparés l'un de l'autre par l'intermédiaire d'une conduite sous pression (D2, D4) commutable.
  4. Agencement selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la chambre du piston (K) peut être reliée par l'intermédiaire du distributeur (13) au choix avec une conduite de vidange (12).
  5. Agencement selon l'une quelconque des revendications 1 à 4, caractérisé en ce que
    l'agencement de pompes (20) est composé d'une pompe de service principale (P1) entraînée en régime variable pour des courses de travail et d'une pompe auxiliaire (P2) entraînée en régime variable pour des courses de retour et
    en ce qu'il est prévu un système de commande (6) permettant de commander ou de régler dans la chambre de pression associée à la pompe auxiliaire une contre-pression qui doit être établie par la pompe auxiliaire (P2), agissant à l'encontre de la pression dans la chambre de travail du consommateur (1).
  6. Agencement selon la revendication 5, caractérisé en ce que la première conduite sous pression (D1) est une liaison directe, dépourvue de soupape de commutation entre la pompe de service principale (P1) et la première chambre de pression (K) et la deuxième conduite sous pression (D2) est une liaison directe, dépourvue de soupape de commutation entre la pompe auxiliaire (P2) et la deuxième chambre de pression (R).
  7. Agencement selon l'une quelconque des revendications 1 à 6, caractérisé en ce que la puissance nominale de la pompe auxiliaire (P2) correspond à de 2 % à 50 % de la puissance nominale, de préférence à environ 10 % de la puissance nominale de la pompe de service principale (P1).
  8. Agencement selon l'une quelconque des revendications 1 à 7, caractérisé en ce qu'entre la pompe de service principale (P1) et le moteur d'entraînement (M1) associé à la pompe de service principale (P1), il est prévu une transmission mécanique via laquelle le régime de la pompe de service principale (P1) est variable par rapport au régime du moteur d'entraînement (M1) associé à la pompe de service principale (P1).
  9. Agencement selon l'une quelconque des revendications 1 à 8, caractérisé en ce que le volume transporté à chaque tour de la pompe de service principale (P1) et/ou de la pompe auxiliaire (P2) est variable, la variation du volume transporté à chaque tour étant réglable de préférence en fonction de la pression générée par la pompe de service principale (P1) et/ou la pompe auxiliaire (P2).
  10. Agencement selon l'une quelconque des revendications 1 à 9, caractérisé en ce que l'agencement de pompes (20) comporte au moins une pompe entraînée par un moteur d'entraînement électrique pouvant être entraîné à régime variable pour des courses de travail de l'agencement d'entraînement hydraulique conçu en tant que transmission hydraulique, sur laquelle les conduites sous pression (D1, D2) sont exemptes de soupapes de commutation déterminantes en matière de sécurité, et en ce qu'un système de commande (6) conçu sous la forme d'un convertisseur présente une catégorie de risque CE élevée, connue en soi pour le moteur d'entraînement électrique, en remplacement d'une commande hydraulique.
  11. Agencement selon la revendication 10, caractérisé par un frein (8), qui est actif entre le moteur d'entraînement (M1) électrique et la pompe de service (P1).
  12. Procédé d'entraînement hydraulique sans accumulateur de pression d'un grand consommateur (1), à savoir d'une presse hydraulique, avec deux chambres de pression (K, R) à effet opposé, dont l'une est alimentée par l'intermédiaire d'une première conduite sous pression (D1) et par un agencement de pompes (20) et l'autre est alimentée par l'intermédiaire d'une deuxième conduite sous pression (D2) et par l'agencement de pompes (20) avec des agents sous pression,
    caractérisé en ce
    qu'en remplacement d'un accumulateur de pression, on utilise une pompe de service principale (P1) entraînée à régime variable pour des courses de travail et une pompe auxiliaire (P2) entraînée à régime variable pour des courses de retour et au moyen d'un système de commande (6), la pompe auxiliaire (P2) établit ou maintient une contre-pression à l'encontre de la pression dans la chambre de travail du consommateur (1), la pompe de service principale (P1) et/ou la pompe auxiliaire (P2) étant conçue sous la forme d'une pompe à pistons axiaux ou d'une pompe à palettes, et
    en ce qu'hormis la pompe de service principale (P1), on fait fonctionner une pompe à vitesse rapide avec un piston à vitesse rapide (3') mis en oeuvre dans le piston d'une unité piston/cylindre, une troisième conduite sous pression (D3) étant prévue, qu'on commute par l'intermédiaire d'une soupape d'ouverture/de fermeture (11) dans une dérivation vers la première conduite sous pression (D1), sachant qu'une fermeture de la soupape d'ouverture/de fermeture (11) a pour effet de diriger le flux de pompage de la pompe de service principale (P1) non pas sur le piston principal de la pompe de service principale (P1), mais sur le piston à vitesse rapide (3') de diamètre inférieur, suite à quoi, la tige de piston (S) sort plus rapidement, et après l'atteinte d'une pression réglable, à l'aide de la soupape d'ouverture/de fermeture (11), on commute la surface du piston principal, et une conduite de remplissage (7) reliant la chambre du piston (K) avec le réservoir (T), dans laquelle est placée une soupape de remplissage (9) étant prévue, lors de la course de retour, la soupape de remplissage (9) s'ouvrant également pour actionner l'agencement à une vitesse plus élevée.
  13. Procédé selon la revendication 12, caractérisé en ce que pendant la course de travail du consommateur, on inverse la direction de transport de la pompe auxiliaire (P2) et on détourne le flux de transport de la pompe auxiliaire (P2) d'une liaison initiale sur la chambre du piston (K) du consommateur (1) vers une liaison sur l'espace annulaire (R) du consommateur (1).
  14. Procédé selon la revendication 12 ou 13, caractérisé en ce qu'on fait varier le régime de la pompe de service principale (P1) par rapport au régime d'un moteur d'entraînement (M1) associé à la pompe de service principale (P1), la variation du régime de la pompe de service principale (P1) par rapport au régime du moteur d'entraînement (M1) associé à la pompe de service principale (P1) s'effectuant de préférence via une transmission mécanique prévue entre la pompe de service principale (P1) et le moteur d'entraînement (M1) associé à la pompe de service principale (P1).
  15. Procédé selon l'une quelconque des revendications 12 à 14, caractérisé en ce que qu'on fait varier le volume transporté à chaque tour de la pompe de service principale (P1) et/ou de la pompe auxiliaire (P2), la variation du volume transporté à chaque tour étant réglé de préférence en fonction de la pression générée par la pompe de service principale (P1) et/ou la pompe auxiliaire (P2).
  16. Procédé selon l'une quelconque des revendications 12 à 15, pour lequel l'agencement de pompes (20) est composé d'au moins une pompe entraînée à régime variable, caractérisé en ce que les conduites sous pression (D1, D2) sont traversées par l'huile hydraulique sans soupapes de commutation déterminantes en matière de sécurité et en ce que l'au moins un moteur d'entraînement de pompe à régime variable est amorcé par un convertisseur électrique appartenant à une catégorie de risque CE élevée.
  17. Procédé selon la revendication 16, caractérisé en ce qu'on utilise de manière redondante un frein (8) actif entre le moteur d'entraînement (M1) électrique et la pompe de service (P1).
EP13005011.5A 2008-08-21 2009-08-21 Agencement d'entraînement hydraulique sans accumulateur de pression pour et avec un consommateur, notamment pour presse hydraulique, et procédé d'entraînement hydraulique sans accumulateur de pression d'un consommateur Active EP2732959B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008039011.9A DE102008039011B4 (de) 2008-08-21 2008-08-21 Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers
EP09778039.9A EP2328747B1 (fr) 2008-08-21 2009-08-21 Système de commande hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses hydrauliques, et procédé de commande hydraulique d'un consommateur sans utilisation d'un accumulateur de pression

Related Parent Applications (3)

Application Number Title Priority Date Filing Date
PCT/EP2009/006088 Previously-Filed-Application WO2010020427A1 (fr) 2008-08-21 2009-08-21 Système de commande hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses hydrauliques, et procédé de commande hydraulique d'un consommateur sans utilisation d'un accumulateur de pression
EP09778039.9A Division-Into EP2328747B1 (fr) 2008-08-21 2009-08-21 Système de commande hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses hydrauliques, et procédé de commande hydraulique d'un consommateur sans utilisation d'un accumulateur de pression
EP09778039.9A Division EP2328747B1 (fr) 2008-08-21 2009-08-21 Système de commande hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses hydrauliques, et procédé de commande hydraulique d'un consommateur sans utilisation d'un accumulateur de pression

Publications (3)

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EP2732959A2 EP2732959A2 (fr) 2014-05-21
EP2732959A3 EP2732959A3 (fr) 2014-06-11
EP2732959B1 true EP2732959B1 (fr) 2018-05-02

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EP13005011.5A Active EP2732959B1 (fr) 2008-08-21 2009-08-21 Agencement d'entraînement hydraulique sans accumulateur de pression pour et avec un consommateur, notamment pour presse hydraulique, et procédé d'entraînement hydraulique sans accumulateur de pression d'un consommateur
EP09778039.9A Active EP2328747B1 (fr) 2008-08-21 2009-08-21 Système de commande hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses hydrauliques, et procédé de commande hydraulique d'un consommateur sans utilisation d'un accumulateur de pression

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EP (2) EP2732959B1 (fr)
DE (1) DE102008039011B4 (fr)
ES (2) ES2541670T3 (fr)
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DE102010017912B4 (de) * 2010-04-21 2022-08-25 Voith Patent Gmbh Hydraulischer Antrieb und Verfahren zum Betreiben eines hydraulischen Antriebs
DE102010034610A1 (de) 2010-08-18 2012-02-23 Robert Bosch Gmbh Hydraulischer Linearantrieb
DE102011000473B4 (de) * 2011-02-02 2017-07-13 Langenstein & Schemann Gmbh Pressmaschine und Verfahren zum Pressen von Werkstücken
DE102011011750A1 (de) 2011-02-18 2012-08-23 MAE Maschinen- u. Apparatebau Götzen GmbH Druckspeicherlose hydraulische Antriebsanordnung für und mit einem Verbraucher, insbesondere für Pressen sowie Verfahren zum Betreiben einer solchen druckspeicherlosen hydraulischen Antriebsanordnung
KR102198076B1 (ko) 2011-02-23 2021-01-05 섀플러 테크놀로지스 아게 운트 코. 카게 클러치의 작동을 위한 유압 장치
DE102011053615A1 (de) * 2011-09-14 2013-03-14 Ring Maschinenbau Gmbh & Co.Kg Verfahren zum Betreiben einer Stanze
EP2824334A1 (fr) 2013-07-08 2015-01-14 Siemens Aktiengesellschaft Entraînement linéaire hydraulique
DE102014218884B4 (de) 2014-09-19 2020-12-10 Voith Patent Gmbh Hydraulischer Antrieb mit Eilhub und Lasthub
CN105172196B (zh) * 2015-09-30 2017-04-12 天津市天锻压力机有限公司 高速连杆多工位压力机的自动化上料控制系统及控制方法
WO2017186712A1 (fr) 2016-04-25 2017-11-02 Robert Bosch Gmbh Arbre hydraulique pour une presse
DE102016011778A1 (de) 2016-08-11 2018-02-15 M A E Maschinen- Und Apparatebau Götzen Gmbh Hydraulische, insbesondere druckspeicherlose, Antriebsanordnung für und mit einem Verbraucher, insbesondere für Pressen, sowie Verfahren zum Betreiben einer solchen hydraulischen Antriebsanordnung
CN106762871B (zh) * 2017-03-09 2018-11-13 桂林星辰科技股份有限公司 一种单电机双泵的伺服泵控液压直线驱动系统及控制方法
JP6551490B2 (ja) * 2017-11-02 2019-07-31 ダイキン工業株式会社 油圧装置
CN112739914B (zh) 2018-08-21 2024-02-20 西门子能源美国公司 具有用于每个致动方向的不同的泵的双作用液压致动器
EP3620296B1 (fr) * 2018-09-10 2023-03-15 Maschinenfabrik Bermatingen GmbH & Co. KG Presse à balles ainsi que procédé de commande pour une telle presse à balles
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JP6662445B1 (ja) * 2018-12-26 2020-03-11 ダイキン工業株式会社 ダイクッション装置およびプレス機械

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ES2693422T3 (es) 2018-12-11
EP2328747A1 (fr) 2011-06-08
WO2010020427A1 (fr) 2010-02-25
EP2328747B1 (fr) 2015-04-08
DE102008039011B4 (de) 2020-01-16
ES2541670T3 (es) 2015-07-23
EP2732959A2 (fr) 2014-05-21
DE102008039011A1 (de) 2010-02-25
EP2732959A3 (fr) 2014-06-11

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