EP2498982B1 - Presse - Google Patents

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Publication number
EP2498982B1
EP2498982B1 EP10810753.3A EP10810753A EP2498982B1 EP 2498982 B1 EP2498982 B1 EP 2498982B1 EP 10810753 A EP10810753 A EP 10810753A EP 2498982 B1 EP2498982 B1 EP 2498982B1
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EP
European Patent Office
Prior art keywords
hydraulic
piston
hydraulic drive
unit
tool carrier
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
EP10810753.3A
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German (de)
English (en)
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EP2498982A2 (fr
Inventor
Manfred Kurz
Bernhard Russ
Martin Rauwolf
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
Original Assignee
Hoerbiger Automatisierungstechnik Holding 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.)
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Publication of EP2498982A2 publication Critical patent/EP2498982A2/fr
Application granted granted Critical
Publication of EP2498982B1 publication Critical patent/EP2498982B1/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
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high 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
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/163—Control arrangements for fluid-driven presses for accumulator-driven presses

Definitions

  • the present invention relates to a machine press having a machine structure, a lower tool carrier arranged in fixed spatial relation to the machine structure, an upper tool carrier which is linearly movable up and down by one operating stroke relative to the lower tool carrier, and an upper tool carrier acting on the upper tool carrier. the downward movement of the upper tool carrier causing hydraulic drive.
  • Machine presses of the type specified above are known in various designs.
  • a typical example of such machine presses are press brakes, as they are used for bending of sheets.
  • the relevant state of the art includes in particular the JP 05293548 A .
  • JP 05015928 A JP 2000343126 A .
  • JP 2001113317 A AT 008633 U1 .
  • EP 1228822 B1 and EP 2036711 A1 A machine press according to the preamble of claim 1 is from the AT 008633 U1 known.
  • the DE 9207905 U1 discloses a forming machine (eg hydraulic press or hydraulically driven forging machine) in which the drive comprises at least one pump cylinder which can be acted upon by a crank blowing apparatus and withdrawal cylinders which are constantly rechargeable accumulator pressure.
  • the forming force applying cylinder is connected to the pump cylinder connected via a line which is connected via a controlled non-return valve to a low-pressure vessel.
  • a second controlled check valve is arranged in a single-acting running retraction cylinder with a liquid accumulator or double action running retraction cylinder connecting line with the low pressure vessel.
  • a particularly pronounced advantage of the machine press according to the invention over the prior art is the achievable very high operating speed, ie the minimum cycle times. This is achieved by a possible in the application of the invention substantial shortening of the dead or Idle times, ie those times when the upper tool carrier of the machine press performs inefficient idle strokes.
  • the present invention uses, inter alia, the fact that in conventional Abkant- and other machine presses typically only a small proportion (eg 3mm) of the entire operating stroke (eg 40-50mm) forms the forming of the workpiece pressing, a much larger proportion of the operating stroke meanwhile represents an inefficient idle stroke.
  • the machine press according to the invention distinguishing features is of particular importance that the at least one hydraulic drive system has a designed as a pressure accumulator reservoir for the hydraulic fluid, which is biased so that in the entire relevant hydraulic drive system always, ie at any place and at any time during the entire operating cycle ', a base pressure prevails, which is above the ambient pressure (standard conditions according to DIN).
  • the upper tool carrier by means of a (permanently acting) spring means, the weight (weight) of the upper tool carrier, the attached thereto tool and the upper Tool carrier associated components of the hydraulic drive and overcompensated by the prevailing in the prevailing at least one hydraulic drive system base pressure closing force in the sense of opening the machine press, that is biased in its upper end position.
  • the opening of the machine press which in turn advantageously (see below) shortest paths and thus the lowest Let accelerating masses be realized.
  • the above-described advantageous effects of the present invention set in typical applications already at a ambient pressure only moderately exceed the base pressure, for example, even if the base pressure in the relevant hydraulic drive system always, ie at any place and at any time during the entire operating cycle 'prevails, is about 1 bar above the ambient pressure.
  • the accumulator is designed so that it still imposes a positive pressure of about 1 bar above ambient pressure with minimal filling, ie with fully lowered piston of the associated cylinder-piston unit, the hydraulic system.
  • a preferred base pressure is about 1 to 2 bar above ambient pressure.
  • the design of the pressure accumulator and its adaptation to the other components of the hydraulic drive system takes place in such a way that the maximum pressure in the pressure accumulator, which adjusts itself when the piston of the cylinder-piston unit is completely raised and thus the maximum filling of the pressure accumulator, is not more than about 5 bar, particularly preferably about 4 to 5 bar.
  • a first preferred embodiment of the invention is characterized in that the hydraulic drive comprises two hydraulic drive systems each having at least one cylinder-piston unit, wherein each of the two hydraulic drive systems comprises a separate hydraulic unit.
  • the hydraulic drive comprises two hydraulic drive systems each having at least one cylinder-piston unit, wherein each of the two hydraulic drive systems comprises a separate hydraulic unit.
  • the spring unit is integrated in at least one hydraulic cylinder-piston unit of the at least one hydraulic drive system. It is particularly preferably designed as a gas spring.
  • the (filled with hydraulic fluid) piston rod working space of the relevant hydraulic cylinder-piston unit hydraulically with an external, correspondingly biased pressure accumulator -
  • This has nothing to do with the pressure accumulator described above in the hydraulic drive system - be connected.
  • the (gas-filled) piston rod working space can communicate with internal gas-filled compensation chambers provided inside the cylinder-piston unit, which can be arranged in particular in the piston and / or in the housing, in order to optimally adapt the spring characteristic of the gas spring to the respective application.
  • Such internal compensation spaces in turn allow the Design of particularly compact and lightweight drive units with minimal moving masses, because the axial length of the piston rod working space does not need to exceed the stroke of the drive unit appreciably, only to provide the maximum compressed gas filling receiving residual space.
  • the arrangement of the said compensation chamber in the piston at a suitable location can, moreover, contribute to a further reduction in weight.
  • the area ratio between the second effective working surface and the first effective working surface is at least 3.
  • a machine control is provided which is acted upon by a pressure sensor determining the working pressure in the at least one hydraulic drive system.
  • the consideration of the existing in the respective individual pressing task in the hydraulic drive specific pressure conditions in the machine control allows a targeted individual influence on the hydraulic drive, not only to minimize the duration of each cycle ', but also with regard to the quality of the result of workpiece forming.
  • the off-center feed of the machine press with a workpiece control technology compensate.
  • Yet another preferred embodiment of the machine press according to the invention is characterized in that in the at least one hydraulic drive system, the at least one hydraulic cylinder-piston unit and the associated hydraulic unit constitute a complete drive with a common control, valve and line block to the the assigned accumulator is directly connected, so that no free pipe or hose lines exist.
  • optimal structural and functional conditions can be achieved in many respects, namely with regard to the required installation space, the achievable efficiency, the installation effort, the reliability, the maintenance and service friendliness. This meets the needs of the user and interests as far as possible, especially in the case of such a hydraulic complete drive with a - completely closed by the execution of the reservoir for the hydraulic fluid pressure accumulator - hydraulic system only electrical interfaces for machine control must exist.
  • the hydraulic unit is according to another preferred embodiment of the invention as Reversieraggregat, i. designed as an aggregate with reversible conveyor. More details are given below.
  • the at least one hydraulic drive system comprises two (optionally differently configured) optionally switchable hydraulic pumps.
  • the admission of the at least one hydraulic cylinder-piston unit in rapid traverse and in the press gear in a larger spectrum can be individually adapted to the specific pressing task, in particular by applying the first effective piston surface in rapid traverse with two parallel operated hydraulic pumps and loading the second effective piston area in the press gear with only one hydraulic pump.
  • the at least one hydraulic drive system comprises two selectively switchable hydraulic cylinder-piston units, one of which can be connected in rapid traverse by hydraulic connection of the two working spaces with each other - as a differential cylinder.
  • the at least one hydraulic drive system comprises two selectively switchable hydraulic cylinder-piston units, one of which can be connected in rapid traverse by hydraulic connection of the two working spaces with each other - as a differential cylinder.
  • machine press 1 shown as a press brake has a machine structure 3 comprising two C-frames 2.
  • a lower tool carrier 4 with a lower bending tool 5 is arranged on this.
  • Upper tool carrier 7, which is shown in its uppermost position, can be moved linearly up and down relative to lower tool carrier 4 by one operating stroke H (double arrow A). 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. This also applies to constructive details known as such, not shown here, eg with regard to the connection of the bending tools with the respective associated tool carrier.
  • two hydraulic drive systems namely a left hydraulic drive system 8 and a right hydraulic drive system 9 are provided, which together form a force acting on the upper tool carrier 7 hydraulic drive 10.
  • the two hydraulic drive systems 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.
  • Each of the two complete drives 11 embodied in mirror image form comprises in particular (compare also the hydraulic circuit diagram according to FIG Fig. 3 ) a hydraulic cylinder-piston unit 12 with a cylinder 13 and a guided therein piston 14 whose piston rod is fixedly connected to the upper tool carrier 7, and a hydraulic cylinder-piston unit 12 acting hydraulic unit 15 with a driven by an electric motor 16 reversible hydraulic pump 17.
  • the hydraulic pump 17 is a built-in pump in a common control -, Valve and line block 18 housed, which at the same time also forms a pump block and at the directly and the cylinder 13 and the electric motor 16 are flanged.
  • a pressure accumulator 19 is flanged directly to the control, valve and line block 18, which forms a reservoir and expansion tank for the hydraulic fluid of the hydraulic drive system 8 and in particular the hydraulic unit 15 supplies.
  • the hydraulic system is hermetically sealed. In him, the hydraulic fluid is clamped and prevails constantly and everywhere at least one lying above the ambient pressure base pressure, which is impressed him through the pressure accumulator 19.
  • valves 20 and a filter 33 are flanged for the hydraulic oil directly to the control, valve and line block 18 and the hydraulic pump is housed in this, none of said hydraulic components interconnecting free, ie outside the control, valve - And line block 18 laid pipe or hose lines.
  • the upper tool carrier 7 is by means of a spring device 21, the weight of the upper tool carrier 7, the attached thereto tool 6 and connected to the upper tool carrier components of the hydraulic drive 10, that is, the piston 14 of the two hydraulic drive systems 8 and 9, and by The overriding of the base pressure in the two hydraulic drive systems implied closing force, in its upper end position ( Fig. 1 ).
  • the spring device is integrated into the hydraulic cylinder-piston units 12 of the two hydraulic drive systems 8 and 9 such that in each case the piston rod working chamber 22 of the hydraulic cylinder-piston units 12 is hydraulically connected to an associated external pressure accumulator 23.
  • the external pressure accumulator 23 is flanged directly to the associated cylinder 13, so that in turn no pressure accumulator 23 with the associated hydraulic cylinder-piston unit 12 connecting free pipe or hose exists.
  • the spring unit 21 is designed as a gas spring. Since the upward movement of the upper tool carrier 7 takes place solely by the spring means 21, ie by acting on the Kolbenstangenarbeitsschreib 22 by the respectively associated pressure accumulator 23, the hydraulic system of the spring means 21 forms a closed system, in particular by none of the two cylinder-piston units '12 a hydraulic connection between the piston rod side working space 22 and the piston-side working space 24 is made.
  • the hydraulic drive 10 of the press brake is switchable between a rapid traverse and a press gear.
  • the upward force of the spring device 21 constantly acts on the upper tool carrier 7 at such a height that the weight of all the movable components of the press brake and the closing force implied by the base pressure prevailing in the two hydraulic drive systems are overcompensated and the upper tool carrier in FIG its uppermost position is biased, even at rapid traction active movement of the upper tool carrier 7 by the hydraulic drive 10, but not a free movement due to gravity.
  • This is achieved by a respective auxiliary piston 26 dips into the piston 14 of the two hydraulic cylinder-piston units 12, namely in each case a bore 25 introduced therein. More about this is the AT 8633 U1 ( Fig.
  • the hydraulic unit 15 and the hydraulic cylinder-piston unit 12, in particular its auxiliary piston 26 and first effective piston surface 27, are coordinated so that at rapid traction - taking into account the weight of the movable components of the press brake and the closing force, the is adjusted by the provided via the pressure accumulator 19, prevailing in the piston working chamber 24 base pressure - the opposing force of the spring means 21 can be overcome.
  • the valve 30 is switched so that the hydraulic unit 15 acts in parallel on the piston working space 24 and the auxiliary working space 28.
  • the delivery of the hydraulic unit 15 is shut down and stopped so that the upper tool carrier stops.
  • the tool then stops for a short time before the so-called "decompression stroke” begins, ie the slow, controlled lifting of the upper tool and opening of the press over a small stroke (eg 2-3 mm) by reversal of the reversible hydraulic unit.
  • the valve 30 and the Nachsaugventil 32 are reversed, so that adjusted in the piston working space 24 of the pressure accumulator 19 to the system impressed base pressure and the piston 14th retracts under the action of the spring means 21.
  • the retraction of the piston 14 takes place in the Rapid traverse controlled (braked) by the auxiliary work space 28 is controlled and controlled in the pressure accumulator 19 via the still operated with respect to the closing of the press reverse flow direction hydraulic unit 15.
  • Fig. 3 is shown in this hydraulic drive system, the flow rate of the hydraulic unit 15 and adjustable.
  • the latter is associated with the fact that the capacity of the accumulator 19 is comparatively low, at least significantly smaller than the conventionally used ventilated tanks, so that only a reduced surface is available for heat dissipation.
  • the machine control S communicates via corresponding control lines with the motor 16 of the hydraulic unit 15 and the valve 30 and the Nachsaugventil 32, namely the corresponding components of both hydraulic drive systems 8 and 9.
  • FIG. 4 illustrated modified hydraulic system differs from the one after Fig. 3 essentially by another embodiment of the hydraulic unit 15 '.
  • a pressure relief valve 36 is provided on the pressure side, which abgrest beyond the existing in the respective operating point requirement flow.
  • a 3/3-Wegevantil 37 is disposed between the hydraulic unit 15 'and the hydraulic cylinder-piston unit 12.
  • the directional control valve 37 is reversed to its open position, wherein the pressure reduction takes place both in the piston working space 24 and in the auxiliary working space 28 and the slow, controlled lifting of the upper tool and opening the press controlled via a discharge edge.
  • the valve 30 and the Nachsaugventil 32 are reversed, so that in the piston working space 24 of the pressure accumulator 19 impressed on the system base pressure adjusts and the piston 14 retracts under the action of the spring means 21.
  • the retraction of the piston 14 takes place in rapid traverse controlled (braked) by the auxiliary working space 28 via the directional control valve 37, namely controlled by the discharge edge and controlled in the pressure accumulator 19 is emptied.
  • a pressure in the hydraulic cylinder-piston unit 12 prevailing working pressure constantly receiving pressure sensor 39 is processed in the machine control S. It can be used in particular as auxiliary control variable in the sense that the signal of the independently operating displacement encoder is checked for its plausibility and possibly modified for further processing in the controller. The latter comes especially into consideration when the displacement measurement signal (eg in the case of a stuck component and / or excessive static friction) indicates no movement, but the pressure signal indicates such a working pressure within the hydraulic system that movement of the upper tool carrier would actually be expected.
  • the displacement measurement signal eg in the case of a stuck component and / or excessive static friction
  • the control can be optimized in terms of the most accurate compliance with a given speed profile for the upper tool carrier, which can contribute to the cycle time - in particular by minimizing the transitional periods - to further shorten.
  • the hydraulic system according to the in Fig. 5 illustrated hydraulic circuit diagram differs from the after Fig. 4 in particular in that it has two structurally separate hydraulic cylinder-piston units 12'A and 12'B, whose pistons 14 ', however, are both connected to the upper tool carrier 7 and coupled to each other in this way.
  • the two hydraulic cylinder-piston units 12'A and 12'B is optional, via the valve 30 'switchable, only one acted upon by the hydraulic unit 15', namely the hydraulic cylinder-piston unit 12 'shown on the right in the drawing.
  • A, or both cylinder-piston units 12'A and 12'B simultaneously and in parallel.
  • the hydraulic cylinder-piston unit 12'A In rapid traverse alone, the hydraulic cylinder-piston unit 12'A is acted upon, so that the first effective piston surface 45 is identical to the end face of the piston 14'A.
  • the piston working space 24'B of the other hydraulic cylinder-piston unit 12'B which has no connection to the associated, in turn acted solely by the spring device 21 piston rod working chamber 22'B, fills via the Nachsaugventil 32.
  • the piston working space 24'A and the piston rod working space 22'A of the hydraulic cylinder-piston unit 12'A are short-circuited via the valve 40; In this switching position of the valve 40, the hydraulic cylinder-piston unit 12'A acts as a differential cylinder.
  • FIG. 6 illustrated modified hydraulic system differs from the one after Fig. 5 While the pressure side of one pump 17 “A is constantly connected to the pressure port 42 of the directional control valve 37, the pressure side of the other pump 17” B can be connected to the pressure reservoir 19 via the valve 43 and Pump 17 “B thus be switched to circulation promotion.
  • both pumps 17 “A and 17” B convey to the hydraulic cylinder-piston unit 12'A.
  • the check valve 44 secures the pressure side of the pump 17 "A against the valve 43.
  • the piston rod working chamber 22 is filled with a spring gas, wherein the gas filling is under a bias voltage via a corresponding filling pressure.
  • the seals 51 which are illustrated schematically on the piston 14 and which bear sealingly on the inner surface 50 of the cylinder 13, are designed in a manner known to be suitable in view of the fact that they delimit a gas space from the piston-side hydraulic working space 24.
  • With the piston rod working space 22 are via respective channels 52 and 53 two - each annular running - compensation spaces fluidly in communication, namely a cylinder-side first compensation chamber 54 and a piston-side second compensation chamber 55.
  • Fig. 7 is a schematic representation after it is particularly readily apparent that the cylinder 13 may not be constructed in one piece, but - in such a known manner - is assembled from several parts.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Control Of Presses (AREA)

Claims (13)

  1. Presse de machine (1), en particulier presse plieuse, comprenant une structure de machine (3), un support d'outil inférieur (4) disposé en relation spatiale fixe par rapport à la structure de la machine, un support d'outil supérieur (7) qui peut se déplacer de haut en bas (A) de façon linéaire sur une course de service (H) par rapport au support d'outil inférieur (4), et un entraînement hydraulique (10) agissant sur le support d'outil supérieur, effectuant le mouvement dirigé vers le bas du support d'outil supérieur, lequel présente au moins un système d'entraînement hydraulique (8 ; 9) fermé autosuffisant, lequel comprend de son côté au moins une unité piston-cylindre hydraulique (12 ; 12'A, 12'B) et au moins un groupe hydraulique (15, 15' ; 15") alimentant celle-ci, alimenté par un récipient de réserve, avec les attributs suivants :
    - l'au moins un système d'entraînement hydraulique (8 ; 9) peut passer d'une avance rapide dans laquelle une première surface de piston active (27 ; 45) est alimentée par l'au moins un groupe hydraulique, et une marche de pression, dans laquelle l'au moins un groupe hydraulique alimente une surface de piston (48 ; 47) essentiellement supérieure par rapport à la première surface de piston active,
    - il n'y a aucune liaison hydraulique entre l'espace de travail côté tige de piston (22 ; 22'b) et l'espace de travail côté piston (24 ; 24 'B), d'au moins une unité piston-cylindre (12 ; 12'B) de l'au moins un système d'entraînement hydraulique ;
    - le support d'outil supérieur (7) est précontraint dans sa position finale supérieure au moyen d'un dispositif de ressort (21) qui surcompense le poids du support d'outil supérieur, de l'outil monté dessus et des composantes de l'entraînement hydraulique reliées au support d'outil supérieur ainsi que la force de fermeture implicite par la pression de base régnant dans l'au moins système d'entraînement hydraulique ;
    caractérisée en ce que
    - le fluide hydraulique de l'au moins un système d'entraînement hydraulique est stocké dans un accumulateur hydraulique (19) formant le récipient de réserve, qui imprime constamment à la totalité du système d'entraînement hydraulique concerné une pression de base supérieure à la pression environnante.
  2. Presse de machine selon la revendication 1, caractérisée en ce que l'entraînement hydraulique (10) comprend deux systèmes d'entraînement hydrauliques (8, 9) avec chacun au moins une unité piston-cylindre (12 ; 12'A, 12'B), sachant que chacun des deux systèmes d'entraînement hydrauliques comprend son propre groupe hydraulique (15 ; 15', 15").
  3. Presse de machine selon la revendication 1 ou 2, caractérisée en ce que le dispositif de ressort (21) est intégré dans au moins une unité piston-cylindre hydraulique (12 ; 12'B) de l'au moins un système d'entraînement hydraulique (8, 9).
  4. Presse de machine selon la revendication 3, caractérisée en ce que le dispositif de ressort (21) est conçu en tant que ressort à gaz, sachant que l'espace de travail de la tige de piston (22) présente un remplissage au gaz.
  5. Presse de machine selon la revendication 4, caractérisée en ce qu'un espace de compensation côté piston rempli de gaz (55) et/ou un espace de compensation côté cylindre rempli de gaz (54) est/sont raccordé(s) en technique d'écoulement sur l'espace de travail de la tige de piston (22).
  6. Presse de machine selon la revendication 3, caractérisée en ce que le dispositif de ressort (21) est conçu en tant que ressort à gaz, sachant que de préférence, l'espace de travail de la tige de piston (22 ; 22'B) de l'unité piston-cylindre hydraulique (12 ; 12'B) est relié hydrauliquement à un accumulateur hydraulique externe (23).
  7. Presse de machine selon l'une des revendications 1 à 6, caractérisée en ce que le rapport surfacique entre la seconde surface de piston active (48) et la première surface de piston active (27) est au moins de 3.
  8. Presse de machine selon l'une des revendications 1 à 7, caractérisée en ce qu'une commande de machine (S) est prévue, qui est alimentée par un capteur de pression (39, 41) calculant la pression de travail dans l'au moins un système d'entraînement hydraulique (8, 9).
  9. Presse de machine selon l'une des revendications 1 à 8, caractérisée en ce que dans l'au moins un système d'entraînement hydraulique (8, 9), l'au moins une unité piston-cylindre hydraulique (12) et le groupe hydraulique (15) correspondant représentent un entraînement complet (11) avec un bloc commande, soupapes et conduites (18) commun sur lequel également l'accumulateur hydraulique (19) est directement raccordé, de sorte qu'il n'existe aucune ligne de tuyaux ou de flexibles libre.
  10. Presse de machine selon l'une des revendications 1 à 9, caractérisée en ce que l'au moins un système d'entraînement hydraulique (8, 9) comprend deux pompes hydrauliques (17"A, 17"B) pouvant être raccordées au choix, de conception différente de préférence.
  11. Presse de machine selon l'une des revendications 1 à 10, caractérisée en ce que l'au moins un système d'entraînement hydraulique (8, 9) comprend deux unités piston-cylindre hydrauliques (12'A, 12'B) pouvant être raccordées au choix, desquelles une (12'a) peut être branchée en avance rapide en tant que cylindre différentiel.
  12. Presse de machine selon l'une des revendications 1 à 11, caractérisée en ce que de l'au moins unité piston-cylindre hydraulique (12 ; 12'A, 12'B), le cylindre (13) est disposé dans une relation spatiale fixe par rapport à la structure de machine (3) et la tige de piston est reliée au support d'outil (7) supérieur.
  13. Presse de machine selon l'une des revendications 1 à 12, caractérisée en ce que le groupe hydraulique est conçu réversible.
EP10810753.3A 2009-11-11 2010-11-10 Presse Active EP2498982B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009052531A DE102009052531A1 (de) 2009-11-11 2009-11-11 Maschinenpresse
PCT/EP2010/006842 WO2011057773A2 (fr) 2009-11-11 2010-11-10 Presse

Publications (2)

Publication Number Publication Date
EP2498982A2 EP2498982A2 (fr) 2012-09-19
EP2498982B1 true EP2498982B1 (fr) 2015-02-25

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EP10810753.3A Active EP2498982B1 (fr) 2009-11-11 2010-11-10 Presse

Country Status (9)

Country Link
US (1) US9044913B2 (fr)
EP (1) EP2498982B1 (fr)
JP (1) JP5576939B2 (fr)
CN (1) CN102725135B (fr)
DE (1) DE102009052531A1 (fr)
DK (1) DK2498982T3 (fr)
ES (1) ES2537627T3 (fr)
PT (1) PT2498982E (fr)
WO (1) WO2011057773A2 (fr)

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DE102012013098B4 (de) 2012-06-30 2014-08-07 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
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EP3311961B9 (fr) * 2016-10-20 2021-11-24 Bucher Hydraulics Erding GmbH Robot et dispositif d'équilibrage pour un robot
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WO2011057773A2 (fr) 2011-05-19
ES2537627T3 (es) 2015-06-10
US20120272840A1 (en) 2012-11-01
DE102009052531A1 (de) 2011-05-12
JP5576939B2 (ja) 2014-08-20
EP2498982A2 (fr) 2012-09-19
PT2498982E (pt) 2015-06-01
CN102725135A (zh) 2012-10-10
CN102725135B (zh) 2015-05-13
WO2011057773A3 (fr) 2011-07-14
US9044913B2 (en) 2015-06-02
JP2013510719A (ja) 2013-03-28
DK2498982T3 (en) 2015-05-11

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