EP2838719B1 - Presse - Google Patents

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Publication number
EP2838719B1
EP2838719B1 EP13702914.6A EP13702914A EP2838719B1 EP 2838719 B1 EP2838719 B1 EP 2838719B1 EP 13702914 A EP13702914 A EP 13702914A EP 2838719 B1 EP2838719 B1 EP 2838719B1
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EP
European Patent Office
Prior art keywords
pressure
automatic press
press according
hydraulic
motor
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.)
Active
Application number
EP13702914.6A
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German (de)
English (en)
Other versions
EP2838719A1 (fr
Inventor
Martin Rauwolf
Bernhard Russ
Roland Thurner
Ilker Oezcanoglu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hoerbiger Automatisierungstechnik Holding GmbH
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Hoerbiger Automatisierungstechnik Holding GmbH
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Publication of EP2838719A1 publication Critical patent/EP2838719A1/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
    • B30B15/166—Electrical control arrangements
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0052—Details of, or accessories for, presses; Auxiliary measures in connection with pressing for fluid driven presses
    • 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
    • B30B15/24—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam

Definitions

  • the present invention relates to a machine press comprising a machine frame, a lower tool carrier (preferably fixed to the machine frame), an upper tool carrier which is linearly movable up and down by one operating stroke by means of a hydraulic drive system relative to the lower tool carrier, and a numerical machine control ,
  • Machine presses of the type mentioned above can be found in various designs in the prior art. So are (cf. EP 231735 A1 ) Machine presses already known in which the hydraulic drive system comprises two piston-cylinder units, by means of which the upper tool carrier is moved, and a single, both piston-cylinder units together with hydraulic fluid supplying motor-pump unit (hydraulic unit). The loading of the two piston-cylinder units is controlled via actuatable by the machine control valves.
  • machine presses are known with two piston-cylinder units which together serve to move the upper tool carrier, in which case the hydraulic drive system also has two separate motor-pump units, each of which supplies only one associated piston-cylinder unit with hydraulic fluid.
  • the speed of lifting and lowering the upper tool carrier typically depends on the engine speed, by reversing the direction of rotation of the pump (Reversible pump) is switched between lifting and lowering.
  • a machine press having the features of the preamble of claim 1 is known from EP0692327 A1 known.
  • the present invention has for its object to provide a machine press of the type mentioned, which is characterized by a very high energy efficiency at relatively low production costs and compact design of the hydraulic drive system.
  • a machine press of the type described above further characterized by the combination specified in claim 1 functionally synergetic interacting features distinguished.
  • the upper tool carrier of a machine press which may be in particular a press brake, with the aid of at least two front hydraulic drive system comprehensive hydraulic cylinder moves linearly up and down.
  • at least one hydraulic cylinder which is preferably designed in each case as a double-acting differential cylinder, part of a separate hydraulic drive unit, so that the hydraulic drive system comprises at least two separate, each having its own motor-pump unit having hydraulic drive units.
  • Each of the motor-pump units draws hydraulic fluid from a tank and supplies it to a main pressure line.
  • valves which are preferably designed as proportional valves, controlled the at least one hydraulic cylinder of the respective hydraulic drive unit to - depending on the pressurization of the lifting-working space or the sink working space - to raise or lower the upper tool carrier, whereby by an appropriate hydraulic circuit (see below) can be carried out an express lowering of the upper tool carrier alone under its own weight, ie without pressurizing the sink working space.
  • the numerical machine control of the machine press contains a speed profile and a pressure profile. Both are defined by a work cycle of the machine press.
  • the numerical machine control acts on the at least two mutually (hydraulically) independent hydraulic drive units, i. the engine of the respective motor-pump unit and each different valves controlling a.
  • the numerical machine control uses the speed profile to control the speed of the engine of the respective hydraulic drive unit.
  • the motor drives the pumps with the speed specified by the numerical machine control phase-dependent speed, which is so dimensioned that the required for the desired movement of the upper tool carrier volumetric flow of hydraulic fluid - possibly plus a security surcharge (see below) - is provided.
  • the respective pump draws in an amount of hydraulic fluid corresponding to the rotational speed from the tank and feeds it to the main pressure line.
  • the numerical machine control uses the pressure profile to supply the at least two hydraulic drive units each with a supply pressure which is the maximum prevailing in the respective main pressure line in a phase-dependent manner.
  • This phase-dependent maximum pressure is typically based on the maximum pressure required in the respective working phase for a specific pressing operation to which the relevant pressure profile is tailored, possibly increased by a safety margin (see below), wherein the specification of the maximum pressure can additionally also fulfill a safety function, which protects the hydraulic drive unit from overpressure.
  • the respective pressure limiting unit individually controls the supply pressure prevailing in the relevant main pressure line, at least during part of the work cycle (in particular in the phase of the so-called “force pressing”, see below) Lowered predetermined phase-dependent maximum pressure, depending on demand.
  • the supply pressure by means of the respective pressure limiting unit for each of the hydraulic drive units is at least temporarily individually limited to the smaller pressure from the maximum pressure given by the pressure profile and the actually existing on the at least one hydraulic cylinder load pressure plus an additional charge, where the relevant load pressure, if the relevant period of load-dependent pressure limiting extends from the lowering phase into the lifting phase, depending on the working phase at the sink working space or else at the lifting working space of the at least a hydraulic cylinder is applied.
  • This further limitation allows an adjustment of the supply pressure limited to the actual demand- and operation-dependent load pressure limited by the numerical machine control based on predicted required pressure values.
  • the actual supply pressure in each of the at least two hydraulic drive units can thus advantageously be set individually to the respective load pressure of the relevant hydraulic drive unit.
  • this is an important aspect in terms of energy efficiency; because in asymmetric pressing tasks, where the different hydraulic cylinders of the hydraulic drive system have different forces to provide (eg off-centering of the workpiece in a mono press or centering of the workpiece in a tandem press), hydraulic power in each of the motor-pump units only becomes provided in the amount actually required (taking into account a security surcharge).
  • the pressure-limiting unit has a pressure limiter which can be controlled by the numerical machine control and a separate, hydraulically-mechanical pressure balance connected in parallel thereto for flow-related purposes.
  • a pressure is set on the pressure limiter in phase-dependent manner / which prescribes the maximum pressure which is set phase-dependent in the main pressure line.
  • the pressure compensator adopts the respective load-dependent regulation of the supply pressure to a pressure level which is more or less below the phase-dependent maximum pressure, depending on the respective actual load on the hydraulic cylinder. The latter results preferably from the respective actual momentary load pressure taking a surcharge.
  • a pilot valve operable by the machine control is fluidically connected upstream / that - depending on the position of the pilot valve - either the supply pressure or the tank pressure is applied to the second control input of the pressure compensator.
  • This can be targeted causes / that the pressure compensator is only temporarily effective / so that the pressure compensator can be put inoperative especially in those operating phases of the machine press in which they (eg by hydraulic vibration and / or resonance effects) adversely affect the performance would. Is in this way, i. ensured by influencing the machine control that the pressure compensator is effective only during lowering, especially the power lowering, loses the above-mentioned shuttle valve in importance.
  • the said pilot valve may preferably also have a further function within the relevant hydraulic drive unit, for example the control of a lowering the working chamber of the respective hydraulic cylinder associated controllable Nachsaugventils in such a machine press, which is designed solely on the weight of the upper tool carrier rapid lowering is.
  • the respective pressure-limiting unit comprises in one Unit integrates a controllable by the numerical machine control electronic pressure compensator with also adjustable by the machine control pressure limiter, with a control technical superposition of both functionalities takes place.
  • the advantage here is the combination of the pressure balance and the pressure limiter in a compact component.
  • machine press 1 shown as a press brake has a machine frame 3 comprising two C-frames 2.
  • a lower tool carrier 4 with a lower tool 5 is arranged on this.
  • a stocked with an upper tool 6, in Fig. 1 in its uppermost position shown upper tool carrier 7 is linearly movable up and down relative to the lower tool carrier 4 by an operating stroke H. Since the in Fig. 1 shown press brake to this extent corresponds to the well-known state of the art, further explanations are unnecessary in this respect.
  • a hydraulic drive system is provided.
  • This comprises two hydraulic drive units, namely a left hydraulic drive unit 8 and a right hydraulic drive unit 9, which together form the hydraulic drive system 10 acting on the upper tool carrier 7.
  • the two hydraulic drive units 8 and 9 are closed and self-sufficient, i. they have no hydraulic connection to each other. They are designed in the form of complete drives 11.
  • Fig. 2 illustrated press brake corresponds in terms of essential design features of those of FIG. I, so that reference is made to the above explanations.
  • the two hydraulic drive units 8 and 9 are not executed here as a structural unit forming a complete drive solution, but rather in a dissolved design.
  • the hydraulic cylinder-piston unit 12 is spatially separated from the associated, the tank and the flanged-on motor-pump unit 15 comprehensive assembly 46 with the flanged to the respective cylinder 13 valve block 45.
  • Each of the two complete drives 11 (mirror-inverted) 11 ( Fig. 1 ) or each of the two - also mirror-inverted - hydraulic drive units 8 and 9 ( Fig. 2 ) includes in particular (see also the hydraulic circuit diagram Fig. 3 ) designed as a differential cylinder hydraulic cylinder-piston unit (“hydraulic cylinder") 12 with a cylinder 13 and a guided therein piston 14, the piston rod is fixedly connected to the upper tool carrier 7, a hydraulic cylinder 12 acting on hydraulic unit 15 with a constant pump with a direction of rotation running hydraulic pump 16, which is driven by a frequency-controlled asynchronous motor (without feedback) running electric motor 17, and a hydraulic fluid-storing tank 18.
  • the speed of the motor 17 and thus the flow rate of the 12 pump 16 is phase-dependent on the machine control 21 adjustable, for which purpose in the numerical machine control 21 a speed profile is stored.
  • the main pressure line 20 is connected to the piston working space 24, which represents the sink working space, while in the position "lifting” with the lifting working space forming piston rod working space 25, in this position "lifting” the Piston working chamber 24 (also, see below) is connected via the valve 22 to the tank 18.
  • the valve 22 is reversed to "lifting". Initially, a so-called “decompression” takes place in order to control the high pressure in the piston working chambers 24, whereby in the decompression phase with the said pressure reduction, the reduction of possible deformations of the machine structure which has occurred during force pressing is accompanied.
  • the decompression phase involves a controlled upward movement of the upper tool carrier 7 over a predetermined path at (slow) operating speed by correspondingly loading the lifting work spaces 25 of the two hydraulic drive units 8 and 9.
  • the existing pressure in the main pressure line 20 is controlled both phase-dependent and load-dependent during the work cycle 'by a complex pressure limiting unit, the load-dependent control takes into account a different stress on the at least two hydraulic drive units of the hydraulic drive system.
  • a pressure limiter 34 connected between the main pressure line 20 and the tank 18 is provided.
  • the pressure threshold in which the connection between the main pressure line 20 and the tank 18 is opened, is adjustable over the pressure prevailing in a control line 36 pressure.
  • the prevailing in the control line 36 pressure is limited by a switched between the control line 36 and the tank 18 pressure relief valve 37, the set value thus dictates the maximum in the main pressure line 20 prevailing pressure.
  • a (via a stored in the machine control phase-dependent pressure profile) via the machine control 21 controlled lowering of the in Control line 36 existing pressure levels is about the - to the pressure relief valve 37 fluidly connected in parallel - controllable by the machine control 21 adjustable pressure relief valve 38 possible.
  • Such a lowering of the pressure level in the control line 36 causes a corresponding reduction of the pressure threshold, in which a connection between the main pressure line 20 and the tank 18 is made via the cartridge 35, and accordingly a (profile-controlled) setting of the maximum in the main pressure line 20 pressure.
  • a hydraulic-mechanical pressure compensator 39 is connected between the main pressure line 20 and the tank 18, which in turn - in the active phase of the pressure compensator 39 - limits the maximum setting in the main pressure line 20 pressure, namely to a value , which is a predetermined amount ("supplement") above the currently prevailing at the hydraulic cylinder 13 load pressure.
  • the control input 40 of the pressure compensator 39 is connected via the control line 41 with a shuttle valve 42, which in turn switches the higher of the applied pressure at its two inputs to the control line 41.
  • the one input of the shuttle valve 42 is in communication with the piston working space 24 and the line 32 connected thereto; the other is connected to the piston rod working space 25 associated line 33, in which the valves 26 and 27 are connected.
  • the pressure compensator 39 can be controlled via the machine control 21 switched on and off by the control line 31, via which the suction valve 28 is switched, is also connected to a second control input 43 of the pressure compensator 39. In this way, with the suction valve 28 open, the pressure compensator 39 is inoperative, i. a connection of the main pressure line 20 to the tank 18 via the pressure compensator 39 is excluded.
  • the motor 17 can stand, for example, in the phase of rapid downward movement of the upper tool carrier, so that the pump 16 promotes no hydraulic fluid.
  • the pump speed can be set for example to a value between 10% and 100% of the design speed, the speed is set so that the calculated for the movement of the upper tool carrier 7 flow rate always a Safety margin (eg 5%) is exceeded.
  • the relevant reserve will be over the above-described pressure limiting unit is regulated and returned to the tank 18.
  • the pump speed may even be raised beyond the design speed, eg to a value of 130% of the design speed.

Claims (14)

  1. Presse automatique (1), en particulier presse-plieuse, comprenant un bâti de machine (3), un porte-outil inférieur (4), un porte-outil supérieur (7), qui peut être déplacé, par rapport au porte-outil inférieur, de haut en bas de façon linéaire, d'une course opérationnelle (H) au moyen d'un système d'entraînement hydraulique et une commande numérique de machine (21), pour laquelle la presse automatique comporte de plus les caractéristiques suivantes :
    Le système d'entraînement hydraulique comprend au moins deux unités d'entraînement hydrauliques (8,9) indépendantes l'une de l'autre, pour lequel chacune des unités d'entraînement hydrauliques comporte de son côté les caractéristiques suivantes :
    - au moins un vérin hydraulique (12) actionne la course linéaire de haut en bas du porte-outil supérieur (7) et est relié par des soupapes (22,26,27) et une conduite de pression principale (20) se trouvant sous une pression d'alimentation à une pompe (16) entraînée par un moteur (17), laquelle aspire du liquide hydraulique depuis un réservoir (18),
    - le régime du moteur (17) peut être réglé par la commande numérique de machine (21), caractérisée en ce que dans la commande numérique de machine un profil de régime défini par le cycle de travail est mémorisé et
    - en ce qu'une unité de limitation de pression limite l'intensité de la pression d'alimentation au moins pendant une partie du cycle de travail à la pression plus faible à partir d'un profil de pression mémorisé dans la commande numérique de machine (21), défini par le cycle de travail et d'une pression de charge effective augmentée d'un supplément sur au moins un vérin hydraulique (12).
  2. Presse automatique selon la revendication 1 caractérisée en ce que l'unité de limitation de pression comporte un limiteur de pression (34) pouvant être piloté par la commande numérique de machine et une balance de pression (39) spéciale, mécanique de type hydraulique, raccordée à cet effet en parallèle sur le plan de l'écoulement.
  3. Presse automatique selon la revendication 2 caractérisée en ce que la pression de charge s'appliquant au moins à un vérin hydraulique (12) sur l'espace de travail de montée (25) et l'espace de travail de descente (24) est diminuée par une soupape à deux voies (42) et la plus haute des deux valeurs de pression est attribuée à une entrée de commande (40) de la balance de pression (39).
  4. Presse automatique selon la revendication 2 ou 3 caractérisée en ce qu'une soupape pilote (29) pouvant être commandée par la commande de machine (21) est connectée avant une deuxième entrée de commande (43) de la balance de pression (39) par le biais de laquelle, soit la pression d'alimentation, soit la pression de réservoir, est appliquée à la deuxième entrée de commande de la balance de pression.
  5. Presse automatique selon la revendication 1 caractérisée en ce que l'unité de limitation de pression comprend, intégrée dans une unité modulaire, une balance de pression électronique pouvant être pilotée par la commande numérique de machine (21) avec limiteur de pression réglable par la commande numérique de machine.
  6. Presse automatique selon l'une quelconque des revendications précédentes caractérisée en ce que le réservoir (18) est ouvert et se trouve sous pression atmosphérique.
  7. Presse automatique selon l'une quelconque des revendications précédentes caractérisée en ce que la pompe (16) est une pompe avec un volume de refoulement constant, un sens de débit et un sens de rotation.
  8. Presse automatique selon l'une quelconque des revendications précédentes caractérisée en ce que le moteur (17) est un moteur asynchrone à régulation de fréquence sans rétroaction.
  9. Presse automatique selon l'une quelconque des revendications précédentes caractérisée en ce que le cycle de travail, pour lequel le profil de régime et le profil de pression spécifient préalablement en fonction de la phase le régime du moteur (17) ou la pression d'alimentation maximale, comprend au moins les phases Descente Rapide, Descente Forcée et Montée du porte-outil supérieur (7).
  10. Presse automatique selon la revendication 9 caractérisée en ce que le moteur (17) ne se tourne pas selon le profil de régime dans la phase Descente Rapide du porte-outil supérieur (7).
  11. Presse automatique selon la revendication 9 ou 10 caractérisée en ce que selon le profil de régime, le régime du moteur dans la phase Montée du porte-outil supérieur (7) dépasse le régime du moteur dans la phase Descente Forcée.
  12. Presse automatique selon l'une quelconque des revendications 9 à 11 caractérisée en ce que la commande numérique (21) comprend une unité d'entrée sur laquelle il est possible d'entrer au moins les nombres de tours du profil de régime et les pressions du profil de pression.
  13. Presse automatique selon l'une quelconque des revendications précédentes caractérisée en ce que chaque unité d'entraînement hydraulique (8,9) comporte exactement un vérin hydraulique (12) exécuté comme un vérin différentiel.
  14. Presse automatique selon la revendication 13 caractérisée en ce que le vérin différentiel présente une rapport de surface entre l'espace de travail Montée (25) et l'espace de travail Descente (24) inférieur à 0,1.
EP13702914.6A 2012-04-17 2013-01-31 Presse Active EP2838719B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102012007511 2012-04-17
DE102012015118A DE102012015118B3 (de) 2012-04-17 2012-07-30 Maschinenpresse
PCT/EP2013/000293 WO2013156095A1 (fr) 2012-04-17 2013-01-31 Presse

Publications (2)

Publication Number Publication Date
EP2838719A1 EP2838719A1 (fr) 2015-02-25
EP2838719B1 true EP2838719B1 (fr) 2016-05-04

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP13702914.6A Active EP2838719B1 (fr) 2012-04-17 2013-01-31 Presse

Country Status (6)

Country Link
US (1) US9168713B2 (fr)
EP (1) EP2838719B1 (fr)
JP (1) JP6208746B2 (fr)
CN (1) CN104540666B (fr)
DE (1) DE102012015118B3 (fr)
WO (1) WO2013156095A1 (fr)

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DE102021006222B3 (de) 2021-12-16 2023-04-20 Hydac International Gmbh Pressenvorrichtung und 2/2-Wege-Proportional-Sitzventil

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CN103894455A (zh) * 2014-02-28 2014-07-02 南通太和机械集团有限公司 一种多墙板结构折弯机
DE202015106161U1 (de) * 2015-11-13 2015-11-27 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulische Antriebseinheit
CN105235267A (zh) * 2015-11-18 2016-01-13 合肥合锻机床股份有限公司 一种液压机滑块的液压支撑系统
CN105365248B (zh) * 2015-11-25 2017-08-01 浙江大学舟山海洋研究中心 机液联合式大行程高速冲床驱动系统
DE102016114635B4 (de) 2016-08-08 2018-09-20 Hoerbiger Automatisierungstechnik Holding Gmbh Bearbeitungsmaschine
JP2019058935A (ja) * 2017-09-27 2019-04-18 新東工業株式会社 鋳造装置及び鋳造方法
US20190152180A1 (en) * 2017-11-17 2019-05-23 Donovan Mills Hydraulic Pelletizer
WO2019102410A1 (fr) * 2017-11-24 2019-05-31 Danieli & C. Officine Meccaniche S.P.A. Presse d'extrusion d'un matériau métallique
RU2687122C1 (ru) * 2018-07-24 2019-05-07 Валерий Владимирович Бодров Гидропривод подвижной траверсы вертикального пресса
AT526048A1 (de) * 2022-04-05 2023-10-15 Trumpf Maschinen Austria Gmbh & Co Kg Umformmaschine zum Umformen von Werkstücken sowie ein Verfahren hierfür

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Publication number Priority date Publication date Assignee Title
DE102021006222B3 (de) 2021-12-16 2023-04-20 Hydac International Gmbh Pressenvorrichtung und 2/2-Wege-Proportional-Sitzventil

Also Published As

Publication number Publication date
CN104540666B (zh) 2017-05-17
JP2015514586A (ja) 2015-05-21
WO2013156095A1 (fr) 2013-10-24
JP6208746B2 (ja) 2017-10-04
EP2838719A1 (fr) 2015-02-25
DE102012015118B3 (de) 2013-10-10
US9168713B2 (en) 2015-10-27
US20150033963A1 (en) 2015-02-05
CN104540666A (zh) 2015-04-22

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