WO2012110259A1 - Système d'entraînement hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique sans accumulateur de pression - Google Patents

Système d'entraînement hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique sans accumulateur de pression Download PDF

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Publication number
WO2012110259A1
WO2012110259A1 PCT/EP2012/000735 EP2012000735W WO2012110259A1 WO 2012110259 A1 WO2012110259 A1 WO 2012110259A1 EP 2012000735 W EP2012000735 W EP 2012000735W WO 2012110259 A1 WO2012110259 A1 WO 2012110259A1
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WO
WIPO (PCT)
Prior art keywords
piston
pump
pressure
chamber
working
Prior art date
Application number
PCT/EP2012/000735
Other languages
German (de)
English (en)
Inventor
Manfred Mitze
Original Assignee
M A E Maschinen- Und Apparatebau Götzen Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by M A E Maschinen- Und Apparatebau Götzen Gmbh filed Critical M A E Maschinen- Und Apparatebau Götzen Gmbh
Priority to EP12709506.5A priority Critical patent/EP2676036B1/fr
Publication of WO2012110259A1 publication Critical patent/WO2012110259A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure
    • B30B1/34—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid pressure involving a plurality of plungers acting on the platen
    • 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • 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
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/27—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
    • F15B2211/70—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
    • F15B2211/7055—Linear output members having more than two chambers

Definitions

  • Accumulator-free hydraulic drive arrangement for and with a consumer, in particular for presses, and method for operating such an accumulatorless hydraulic drive assembly
  • the invention relates to an accumulatorless hydraulic drive arrangement for and with a consumer, in particular for presses with the features of the preamble of claim 1 and a method for operating such accumulatorless hydraulic drive assembly with the features of the preamble of claim 17.
  • the invention of a pressure accumulatorless hydraulic drive arrangement with working piston, additional rapid traction piston and ring-like return piston in particular if the pressure-saving hydraulic drive arrangement for and with a consumer, in particular for pressing, has a double-acting piston / cylinder unit comprising a working piston, a piston rod and a cylinder space, in which the reversibly movable working piston, the cylinder chamber on the one hand into a first piston chamber and the second piston chamber complementing the first piston chamber and on the other hand into a ring groove surrounding the piston rod m
  • a first pressure line supplies the first piston space
  • a second pressure line supplies the second piston space
  • a third pressure line supplies the annular space with pressure medium which is conveyed by at least one pump that can be driven in a variable speed and / or rotation direction.
  • Speed-variable hydraulic drives for large cylinders are carried out approximately according to WO 2010/020427.
  • the hydraulic cylinder may be equipped with an additional rapid traverse piston chamber.
  • the first pump first conveys exclusively in the relatively small-area rapid traverse cylinder.
  • the working piston is filled with pressureless hydraulic oil through an open filling valve. To build up a significant pressing force, the filling valve is closed. By actuating a switching valve, the large piston chamber is now also connected to the first pump. Thus, a high power can be generated at low speed. Plants according to this circuit concept have been implemented many times and prove themselves in practice.
  • the disadvantage is the high construction costs for the two motor pump stations. Especially with large consumers, the inverter controls and power supplies used for the motor drive are quite expensive. The large directional control valves for switching the pump delivery flow from rapid traverse piston to the large piston surface are also expensive.
  • the object of the invention is to further develop the mentioned variable-speed drive in such a way that only one single electric motor and accordingly also only a single inverter is required. Another goal is to reduce the number of switchable valves to reduce construction and maintenance costs.
  • a pressure accumulator hydraulic drive arrangement for and with a consumer, in particular for presses with the features of claim 1 and a method with the features of claim 17 is proposed.
  • the invention is based on the concept of providing a directionally variable pump arrangement comprising a variable-speed motor with at least two pumps in a pressure-hydraulic drive assembly with working piston, supplementary rapid-action piston and ring-like return piston and the three cylinder (or piston ) To connect rooms via three pressure lines individually and directly with the pumps such that a rapid traverse takes place in both directions.
  • said drive assemblies generally a pressure accumulator, as according to DE 103 29 067 A1, require or act on the same piston surface, as according to DE 103 29 067 A1, DE197 15 157 A1 or JP 08014108 A WO 02/04820 A1.
  • the two pumps are designed for different delivery rates or pressures to drive a differential piston, so a double-acting piston with different sized piston surfaces, as in DE 103 29 067 A1, DE 197 71515 A1 or WO 02/04820 A1.
  • the pumps drive on the same press completely different systems, as in the CH PS 481 750. All of these drive assemblies require at least one fluid switching valve and / or very large presses, ie with very large-volume piston exceptionally large-sized pumps and / a lot of time for long strokes.
  • at least one pump arrangement a first pump which can be driven in variable speed and / or direction of rotation, and a second pump which can be driven in variable speed and / or direction of rotation, as well as a speed-driven jointly pump. and / or rotationally variable drive.
  • the pressure medium can be stored substantially without pressure.
  • the first pump is connected via a first pressure line to the first piston chamber or connectable.
  • the second pump is connected on the one hand via a second pressure line to the second piston chamber and on the other hand via the third pressure line to the annular space or connectable.
  • the common drive can be an electric motor. This could u.
  • A. be a (permanent-field) servomotor as well as a standard asynchronous motor with a corresponding 4-quadrant inverter.
  • a valve disposed in front of the working piston switching valve for redirecting the pressurized fluid can be omitted.
  • control algorithms for the inverter of an electric drive motor are easier because no more two motor-pump combinations work against each other.
  • the new units can be combined cost-effectively.
  • the first pump and / or the second pump preferably has an adjustable delivery volume in favor of a variable operation, in particular if an external adjusting device is provided, which can respond to hydraulic or electrical control variables of an external control, such as in an inverter.
  • the first piston chamber can be connected to the tank via a supply line having a filling valve or can be connected in order to accelerate the filling of the working cylinder with working fluid in a rapid traverse phase.
  • At least one further pump arrangement corresponding to the first pump arrangement which acts in parallel with the piston / cylinder unit in the same direction as the first pump arrangement, it is possible to operate particularly bulky piston / cylinder units.
  • first, the second and / or the third pressure line switching valve-free, in particular free of safety-related switching valves is operable or, thereby u.
  • A. Prevents or reduces impacts in the hydraulic system.
  • the pump arrangement comprises a third pump which can be driven in a variable speed and / or rotational direction and which is drivable together with the two other pumps by the common drive, the three pressure lines being assigned to each of the three pumps, the control of the piston / cylinder Unit, simplified.
  • a first piston in particular the working piston, is effective on one side and at least one, preferably double effective piston / cylinder unit, if desired, by a double-acting piston / cylinder auxiliary unit in rapid traverse forward and réellebewegbar and at least one of the piston chambers, in particular the second piston chamber and the annular space in the at least one pelt effective piston / cylinder unit or auxiliary unit are provided, characterized z.
  • the at least one converter is connected or connectable to a pressure sensor associated with the working piston and / or to a displacement encoder associated with the working piston, and the at least one converter has a comparatively high safety level, in particular category 3 according to the guideline DIN EN 954-1 or Performance Level d to ISO 13849.
  • Highest safety requirements eg category 4 according to guideline DIN EN 954-1 or performance level e according to ISO 13849 are also required by combining with other elements, such as a brake included in the pump arrangement. reachable.
  • the accumulatorless hydraulic drive assembly for a consumer, in particular for presses is operated in one embodiment such that in a double-acting, a piston, a piston rod and a cylinder chamber comprehensive piston / cylinder unit of the working piston, the cylinder chamber on the one hand in a the first piston chamber and a second piston chamber which complements the first piston chamber and is divided into an annular space surrounding the piston rod, reversing the first piston chamber via a first pressure line, the second piston chamber via a second pressure line and the annular space via a third pressure line supplied to a pressure medium, that a first and a second speed and / or Drehidess variably driven pump are driven together by a variable speed and / or Drehrich- variable speed drive das.druck the pressure medium in one with the at least one piston / cylinder unit U.N d the pump assembly is hydraulically connected or connectable tank is stored, that the second pump in a first direction of rotation of the common drive a working fluid under extension of the piston rod at rapid traverse via the second pressure line in
  • the ratio of the Eilgangkolbenization F2 to the working piston surface F1 and / or to the annular space F3 is preferably less than or equal to 1 and / or
  • the drive of the pump assembly is associated with a drive shaft, via which the first pump and the second pump are jointly driven and / or
  • the first pump assembly corresponding pump assembly is provided which act in parallel with the piston / cylinder unit in the same direction with the first pump assembly and / or
  • the first D1, the second D2 and / or the third D3 pressure line via check valves to the tank are connectable.
  • the above-mentioned and the claimed components to be used according to the invention described in the exemplary embodiments are not subject to special conditions of size, shape, material selection and technical design, so that the selection criteria known in the field of application can be used without restriction.
  • 1A is a pressure accumulatorless hydraulic drive assembly as a block diagram
  • Fig. 1 B is an alternative to Fig.lA pressure accumulator hydraulic drive assembly with brake as a block diagram
  • FIG. 2A is a block diagram of a modular accumulatorless hydraulic drive arrangement for large systems
  • Fig. 2B is a single module of the modular drive assembly of Fig. 2A;
  • FIG. 3 shows a third embodiment of a druck explicatiosen hydraulic drive arrangement for large plants as a block diagram
  • FIG. 4 shows a fourth embodiment of a tik Stammiosen hydraulic drive assembly for large plants as a block diagram
  • Figure 5 shows a fifth embodiment of tik explicatiosen hydraulic drive assembly for large plants as a block diagram.
  • FIGS. 1A, 1B show a double-acting piston / cylinder unit 20 comprising a working piston 21, a piston rod 22 and a cylinder space.
  • the reversibly movable piston 21 the cylinder chamber on the one hand into a first piston chamber 23A (or working cylinder) and a first piston chamber a so-called rapid traction piston 21 A receiving second piston chamber 23B (or rapid traverse cylinder) and on the other hand in a piston rod 22 surrounding annular space 23C (or remindholzylinder) divided.
  • the rapid traction piston 21A may be oriented in a direction opposite to the piston rod, as shown, or (not shown) in a direction similar to the piston rod.
  • the piston / cylinder unit 20 is connected to a first pressure line D1 supplying the first piston chamber 23A with a pressure medium, a second pressure line D2 supplying pressure fluid to the second piston chamber 23B, and a third pressure line D3 supplying the annular space 23C with pressure medium.
  • a single drive 33 designed as a servomotor drives a double pump in the form of two, in particular variable speed, pumps 31, 32 on a single drive shaft 33A.
  • Both pumps are preferably equipped with a device for adjusting their delivery volume.
  • the adjustment can be done purely inside the pump by a control device that changes the flow rate, for example, the current pressure following. Pumps with adjusting devices of this type are available on the market.
  • an adjusting device 39A, 39B, 39C can be used, which can respond to hydraulic or electrical manipulated variables of an external control, such as in an inverter 35.
  • the pump delivery flow can be adjusted proportionally to an input signal from "zero" up to the maximum delivery flow
  • Such an adjustment device is manufactured, for example, by BoschRexroth under the name "HS4" for the axial piston pumps of the A4 series.
  • the servo motor closest to the pump 32 is connected on its one side with the serving as remindholzylinder annular space 23 C and on the other side with the piston space 23 B serving as a rapid traverse cylinder. Both piston surfaces F3 and F2 are approximately equal.
  • the (first) pump 31 is on its one side with a tank 40, on the other side with the cylinder serving as a working piston chamber 23 A fluidly connected.
  • the piston chamber 23A is equipped with a filling valve 34 to fill the piston chamber automatically very quickly when it increases.
  • the displacement sensor 36 installed on the piston rod 22 reports the current piston position to a converter 35 supplying the drive 33 with electrical voltage.
  • the drive at least one mechanical transmission for torque transmission to at least one of the pumps and / or at least one additional pump of the same drive train can be advantageously assigned, in particular to use motors with compared to the pump relatively higher speeds to be able to. It is also helpful if the pump arrangement comprises a brake, in particular in order to promote a control valve-less operation.
  • the at least one converter 35 may be connected or connectable to a pressure sensor associated with the working piston 21 and / or a displacement transmitter 36 associated with the working piston 21 and / or have a comparatively high safety level, in particular category 3 according to the guideline DIN EN 954-1 or Performance Level d according to ISO 13849.
  • the highest safety requirements are also met (eg Category 4 according to the guideline DIN EN 954-1 or Performance Level e according to ISO 13849 ) reachable.
  • the (second) pump 32 conveys oil into the piston space 23B of the comparatively small-area rapid traverse piston 21A. At the same time, the pump sucks oil out of the annulus 23C.
  • the filling valve 34 is open so that the oil flow required to fill the piston chamber 23A serving as the working cylinder can be sucked from the tank 40.
  • the first Pump 31 is z. B. by the common shaft 33 A to the pump 32 by the servo motor M at the same speed as the pump 32 driven.
  • the delivery flow is preferably set to the maximum via the adjusting device of each pump, so that the pump delivery flow supplements that through the filling valve. This happens at comparatively low pump pressure.
  • fill valve 34 e.g. closed at a certain pressure
  • the pump 31 now fills the large (first) piston chamber 23A alone.
  • the delivery volume of the pump 32 is thereby reduced, either as a function of pressure or by means of an active adjustment device, which is preferably controlled via the converter 35, to a predefinable value, for example corresponding to the area ratio of the two piston surfaces F1 and F2. For example, if F1 is ten times greater than F2, the flow rate is reduced to about 1/10 of the volume flow delivered during rapid traverse.
  • the positioning is done in the usual way by stopping the servomotor M.
  • the pressurized oil drives the servomotor, which now acts as a generator.
  • the resulting electrical energy is supplied to the DC link of the inverter and can optionally be fed back into the electrical network.
  • the method corresponds in principle to that described in WO 2010/020427. Method.
  • the reversed pump 32 now promotes in the (lower) annular space 23 C of the piston / cylinder unit 20, so that the piston rod 22 retracts at rapid traverse speed.
  • the pump sucks the oil 32 from the Eilgangkolbenraum 23B.
  • the pump 31 is preferably operated at full flow to assist the possibly switchable Greetil when emptying the cylinder.
  • Both pumps and motors and converters are limited in their actual available nominal size. For large cylinders, this may not be sufficient.
  • two or more of the drives can be combined into one unit and preferably the two motors can be operated in synchronism according to the master-slave system.
  • FIG. 2A shows by way of example a double module. Thus, regardless of the size of the system always the same components can be used, which simplifies commissioning and spare parts inventory.
  • FIG. 3 An alternative embodiment of Figure 3 shows the use of a triple pump.
  • the three pumps 31, 32, 43 are jointly driven by the drive 33 via the common drive shaft 33A and are connected on the one hand to the tank 40 and on the other hand to one of the pressure lines D1, D2 and D3 respectively and thus supply the first and second separately Piston chambers 23A, 23B and the annular space 23C in the same direction of actuation as described above to Figures 1 to 3.
  • This allows more flexibility in the press design. Also increases the number of usable pumps, because versions can be used that can not build pressure on both ports.
  • the piston surfaces F2 and F3 can then be quite different from each other.
  • the working piston 21 is effective on one side and at least one (in the drawing two) double-acting piston / cylinder auxiliary units 24A, 24B via a bridge member 25 in rapid traverse forward and réellebewegbar.
  • the second piston space 23B and the annular space 23C are provided in the double-acting piston / cylinder auxiliary units 24A, 24B.
  • the working piston 21 is effective on one side and at least one (in the drawing two) double-acting piston / cylinder auxiliary units 24A, 24B via a bridge member 25th in rapid traverse forward and réellebewegbar.
  • the displacer 21 B of Figure 4 is provided according to Fig. 5 in the second piston chamber, only an opening for substantially unpressurized subsequent flow of fluid when the appended for the rapid traverse load is correspondingly large. The same goal can be achieved in the embodiments of FIGS. 1A to 3, when the displacer 21 B are replaced by such openings.

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

Abstract

L'invention concerne un système d'entraînement hydraulique (10) sans accumulateur de pression pour un consommateur et présentant un consommateur, en particulier pour des presses, ledit système comportant tout d'abord un ensemble piston/cylindre (20) à double action comprenant un piston de travail (21), une tige de piston (22) et une chambre de cylindre (23). Le piston de travail (21) mobile de manière réversible divise la chambre de cylindre d'une part en une première chambre de piston (23A) et en une deuxième chambre de piston (23B) complémentaire de la première chambre de piston et d'autre part en une chambre annulaire (23C) entourant la tige de piston (22). Le système d'entraînement comprend en outre une première conduite de pression (D1) alimentant la première chambre de piston (23A) en fluide sous pression, une deuxième conduite de pression (D2) alimentant la deuxième chambre de piston (23B) en fluide sous pression, ainsi qu'une troisième conduite de pression (D3) alimentant la chambre annulaire (23C) en fluide sous pression. Au moins un ensemble pompe (30) comprend une première et une deuxième pompe (31, 32) pouvant être entraînées selon une vitesse de rotation et/ou une direction de rotation variable, ainsi qu'un entraînement (33) à vitesse de rotation et/ou direction de rotation variable entraînant les deux pompes. Un réservoir (40) dans lequel peut être stocké le fluide sous pression est relié ou peut être relié hydrauliquement à l'ensemble piston/cylindre (20) et à l'ensemble pompe (30). La deuxième pompe (32) est reliée ou peut être reliée d'une part à la deuxième chambre de piston (23B) par l'intermédiaire de la deuxième conduite de pression (D2) et d'autre part à la chambre annulaire (23C) par l'intermédiaire de la troisième conduite de pression (D3), tandis que la première pompe (31) est reliée ou peut être reliée à la première chambre de piston (23A) par l'intermédiaire de la première conduite de pression (D1).
PCT/EP2012/000735 2011-02-18 2012-02-20 Système d'entraînement hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique sans accumulateur de pression WO2012110259A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12709506.5A EP2676036B1 (fr) 2011-02-18 2012-02-20 Système d'entraînement hydraulique sans accumulateur de pression pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique sans accumulateur de pression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011011750.4 2011-02-18
DE201110011750 DE102011011750A1 (de) 2011-02-18 2011-02-18 Druckspeicherlose hydraulische Antriebsanordnung für und mit einem Verbraucher, insbesondere für Pressen sowie Verfahren zum Betreiben einer solchen druckspeicherlosen hydraulischen Antriebsanordnung

Publications (1)

Publication Number Publication Date
WO2012110259A1 true WO2012110259A1 (fr) 2012-08-23

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Country Status (3)

Country Link
EP (1) EP2676036B1 (fr)
DE (1) DE102011011750A1 (fr)
WO (1) WO2012110259A1 (fr)

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WO2016072354A1 (fr) * 2014-11-03 2016-05-12 日本エアロフォージ株式会社 Dispositif de presse à forger hydraulique et procédé pour le réglage de ce dernier
WO2017186712A1 (fr) 2016-04-25 2017-11-02 Robert Bosch Gmbh Arbre hydraulique pour une presse
WO2018028832A1 (fr) 2016-08-11 2018-02-15 M A E Maschinen- Und Apparatebau Götzen Gmbh Système d'entraînement hydraulique, en particulier sans accumulateur de pression, pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique
CN113994090A (zh) * 2019-06-05 2022-01-28 罗伯特·博世有限公司 泵、尤其是燃料高压泵
US11384777B2 (en) 2018-08-21 2022-07-12 Siemens Energy, Inc. Double-acting hydraulic actuator with different pumps for each actuation direction

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DE102012006981B4 (de) * 2012-04-05 2019-02-21 Schuler Pressen Gmbh Hydraulische Presse
EP2983906A4 (fr) * 2013-04-08 2016-12-28 Thermochem Recovery Int Inc Système alimentateur hydraulique comportant un étage de compression avec circuit hydraulique multi-cylindre
DE102015105400B4 (de) * 2015-04-09 2022-06-02 Langenstein & Schemann Gmbh Umformmaschine, insbesondere Schmiedehammer, und Verfahren zum Steuern einer Umformmaschine
DE102017106449A1 (de) 2017-03-24 2018-09-27 Böllhoff Verbindungstechnik GmbH Mehrstufige Fügevorrichtung und Fügeverfahren dafür
DE102017219246A1 (de) 2017-10-26 2019-05-02 Robert Bosch Gmbh Anordnung aus einer Hydromaschine und einem Elektromotor zum Antreiben der Hydromaschine
DE202018003042U1 (de) * 2018-06-29 2019-10-01 M A E Maschinen- Und Apparatebau Götzen Gmbh Hydraulischer Zylinderantrieb und hydraulischer Pressenantrieb
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
DE102021121461A1 (de) 2021-08-18 2023-02-23 Dorst Technologies Gmbh & Co. Kg Pulverpresse mit hydraulischem Pressenantrieb

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