EP1782897A2 - Presse avec amortissement des chocs de coupe. - Google Patents

Presse avec amortissement des chocs de coupe. Download PDF

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Publication number
EP1782897A2
EP1782897A2 EP20060015118 EP06015118A EP1782897A2 EP 1782897 A2 EP1782897 A2 EP 1782897A2 EP 20060015118 EP20060015118 EP 20060015118 EP 06015118 A EP06015118 A EP 06015118A EP 1782897 A2 EP1782897 A2 EP 1782897A2
Authority
EP
European Patent Office
Prior art keywords
press
force
plunger
hydraulic
workpiece
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.)
Granted
Application number
EP20060015118
Other languages
German (de)
English (en)
Other versions
EP1782897B1 (fr
EP1782897A3 (fr
Inventor
Jürgen Fahrenbach
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.)
L Schuler GmbH
Original Assignee
L Schuler 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 L Schuler GmbH filed Critical L Schuler GmbH
Publication of EP1782897A2 publication Critical patent/EP1782897A2/fr
Publication of EP1782897A3 publication Critical patent/EP1782897A3/fr
Application granted granted Critical
Publication of EP1782897B1 publication Critical patent/EP1782897B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/02—Punching blanks or articles with or without obtaining scrap; Notching
    • B21D28/20—Applications of drives for reducing noise or wear
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/04—Processes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/162—With control means responsive to replaceable or selectable information program
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/202—With product handling means
    • Y10T83/2092—Means to move, guide, or permit free fall or flight of product
    • Y10T83/2096—Means to move product out of contact with tool
    • Y10T83/2135—Moving stripper timed with tool stroke
    • Y10T83/215—Carried by moving tool element or its support
    • Y10T83/2153—Fluid pressure actuated stripper
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/929—Tool or tool with support
    • Y10T83/9411—Cutting couple type
    • Y10T83/9423—Punching tool
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/929—Tool or tool with support
    • Y10T83/9411—Cutting couple type
    • Y10T83/9423—Punching tool
    • Y10T83/9428—Shear-type male tool
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/929—Tool or tool with support
    • Y10T83/9454—Reciprocable type

Definitions

  • the invention relates to a press, which is particularly adapted for cutting thick and / or high-strength sheets, and a method for operating such a press.
  • DE 102 52 625 A1 a system for cutting impact reduction, in which a number of hydraulic cylinders are provided in the tool. These can be arranged below, above or to the side of the workpiece. Sensors, such as ultrasonic sensors, or sensors that measure the flow velocity of the hydraulic fluid flowing out of the hydraulic cylinders, close a valve through which until now hydraulic fluid could flow out of the hydraulic cylinders.
  • the hydraulic cylinders are connected to pressure accumulators, which are under relatively high pressure. Therefore, they now generate a high drag. The force previously exerted by the punch on the workpiece is thus transferred to the moment in the hydraulic cylinder, in which the stamp begin to break through the workpiece.
  • the control device influences the force exerted by the support device on the basis of a variable that is unambiguously associated with the plunger position.
  • This size can be, for example, the plunger position itself or, as it is preferred, the press angle or some other measured size. If the press angle is used as a basis, it is assumed that a press, which is driven by a rotating shaft, as it is the case for eccentric presses, toggle presses or the like.
  • the rotational position of the drive shaft, in particular the eccentric shaft is referred to as "press angle”.
  • the press angle (or the other, the plunger position clearly characterizing size), in which preferably a sudden increase in the the support device applied counterforce should be, for example, specified and preset by the tool manufacturer.
  • the set value for the press angle can be determined workpiece and tool-specific. Such values may be retrievably stored in a table so as to have new setting values for the press angle at which the force changeover of the support device takes place when the press is converted.
  • the press can be easily adjusted to different conditions, in particular with regard to the stroke rate or the cutting force.
  • To the sheet holding device usually includes a hold-down plate, which is supported directly on the workpiece.
  • the hold-down plate extends into the immediate vicinity of the punches (punches) and thus close up to the section to be produced.
  • the sheet is to be clamped in the immediate vicinity of the cut firmly between the hold-down plate and the lower tool (punching tool) to achieve a high quality cut.
  • the press according to the invention preferably takes over the sheet holding device or else another support device after the punch has passed through the workpiece passes through the force exerted by the ram during its bottom dead center and stores the energy thus emitted by the ram. During the return stroke of the plunger, this energy is given back to the plunger and thus to the press drive.
  • the press drive is relieved overall, ie it saves energy.
  • the mechanical load on the press is reduced by avoiding too large sudden force changes.
  • a particularly firm clamping of the workpiece takes place during the breakthrough, resulting in particularly high cutting qualities.
  • the force on the sheet holding device can be introduced over a particularly large area and thus gently in the workpiece, so that the same undesirable deformations, such as bruising and the like, can be avoided.
  • the sheet holding device or the support means to a hydraulic cylinder, which with a first and connected to a second hydraulic pressure accumulator.
  • Both accumulators have, for example, a displaceably mounted piston with damped end stop.
  • membrane storage devices or storage devices may be provided in which a gas pressure pad is directly in communication with the hydraulic fluid.
  • Both accumulators preferably have different rest pressures.
  • the path leading from the hydraulic cylinder to the lower pressure accumulator is preferably regulated by an electrically controlled valve controlled by the controller.
  • the switching of the supporting force preferably from a smaller value to a larger value, at a given press angle makes it possible to start the switching operation of the hydraulic valve just before the press angle, at which the counterforce applied by the workpiece collapses, for example because the punch by the Pierces the material of the workpiece.
  • the press angle difference by which the hydraulic valve is opened prematurely may be referred to as "lead angle". With this can be time delays that arise due to the switching of the hydraulic valve and by the response delay of other components, effectively compensate. In contrast, systems that use variables to switch the hydraulic valve that characterize force collapse on the workpiece can react only retrospectively, ie with a time delay.
  • the proposal according to the invention thus makes possible an effective compensation of the otherwise occurring cutting stroke, especially at a faster operating speed of the press (large number of strokes).
  • a press 1 which has a press frame with press stands 2, 3, a press table 4 and a head piece 5, is illustrated in an extremely schematic representation.
  • a drive 6, for example, held in the form of an electric motor which drives a plunger 9 back and forth via a schematically illustrated and shown in dashed lines eccentric 7 and a connecting rod 8 also shown in dashed lines.
  • a tool 10 with an upper tool 11 and a lower tool 12 is provided.
  • the lower tool 12 is formed as a punching tool.
  • On the upper tool 11 stamp 13, 14, 15 are held, which are like the other details of the tool 10 in particular from Figure 2 can be seen.
  • the tool 10 is used to punch a workpiece 16, which is illustrated in Figure 2 as a flat workpiece.
  • a workpiece 16 which is illustrated in Figure 2 as a flat workpiece.
  • non-planar workpieces can be subjected to a punching operation in a corresponding manner.
  • the lower tool 12 then has a contour corresponding to the non-planar workpiece.
  • To the upper tool 11 includes a sheet holder plate 17 which is held on not further illustrated means on a base body 18 of the upper tool 11.
  • the main body 18 connected to the plunger 9 carries the punches 13 to 15, which are thereby rigidly connected to the plunger 9.
  • the base body 18 includes one or more hydraulic cylinders 19, 20, which together with the sheet holder plate 17 form a sheet holding device 21.
  • To the sheet holding device 21 also includes pressure pins 22 to 27, which are approximately or exactly parallel to the punches 13 to 15 are arranged and supported with its lower end face on the sheet holder plate 17. The rest, by the way essentially cylindrical pins are supported by their upper front end on floating plates 28, 29, which are thus on top of the pressure pins 22 to 27.
  • the hydraulic cylinders 19, 20 include pistons 30, 31, which delimit in the hydraulic cylinders 19, 20 corresponding with hydraulic fluid filled working spaces 32, 33 and sealed and slidably mounted in these. Piston rods 34, 35 of the pistons 30, 31 press from above onto the floating plates 28, 29 and thus the sheet metal holder plate 17 against the workpiece 16.
  • the hydraulic cylinders 19, 20 are connected via a not shown in Figure 2 and in Figure 1 only schematically shown fluid line 36 to a hydraulic system 37 for generating a blank holder force and at the same time to take over the force exerted by the plunger 9 during and after breakthrough of the workpiece 16th serves.
  • This force transition should be as infinitely variable, i. done without sudden force change.
  • the sheet holding device thus forms a support device which generates a controlled force between the plunger 9 and the press table 4.
  • To the hydraulic system 37 includes a first pressure accumulator 38 and a second pressure accumulator 39, which are both formed in the embodiment as accumulator cylinder 40, 41 with sealingly and slidably mounted therein pistons 42, 43. Both pistons 42, 43 divide in the accumulator cylinders 40, 41 each from two working chambers, the upper, each filled with a gas cushion.
  • the pressure accumulator 38 is, for example, under a pressure of about 200 bar while the pressure accumulator 39, for example, under a pressure of 400 bar, for example.
  • the pistons 42, 43 have at their lower, the respective end pieces 44, 45 side facing preferably a profiling, which is complementary to a profiling of the respective end piece 44, 45 is formed.
  • the profiling is achieved by straight or curved, e.g. formed annular concentric strips or webs, wherein the strips or webs of each piston 42, 43 in correspondingly shaped recesses of each end piece 44, 45 fit.
  • the profiles serve as cushioning, so that the pistons 42, 43, when they run against the fittings 44, 45, are gently braked.
  • Both pressure accumulators 38, 39 are connected to the fluid line 36.
  • the pressure accumulator 39 is connected via a check valve 46 and a throttle device 47 to the fluid line 36.
  • the check valve 46 is oriented so that the hydraulic fluid from the hydraulic line 36 can flow unhindered into the pressure accumulator 40, while it is forced on its way back through the throttle device 47.
  • the pressure accumulator 38 is connected via a valve device 48 to the fluid line 36 and thus the hydraulic cylinders 19, 20.
  • the valve device 48 includes, for example, a directional control valve 49 which is switchable between two states. In a first state, the flow of fluid into and out of the pressure accumulator 38 is unrestricted and unthrottled (or even throttled in an alternative embodiment), while in its other state it blocks this flow of fluid. It is thus designed as open / close valve.
  • the valve device 48 may be connected to an electric actuator 50, which is connected to a control device 53.
  • the Control device 53 designed as a microprocessor control or as another suitable electronic control. It may be formed as an independent controller for the tool 10 or may be part of the other press control.
  • control device is provided or connected to a suitable input / output means 52, such as a screen, a keyboard and the like.
  • a suitable input / output means 52 such as a screen, a keyboard and the like.
  • Operating parameters for the control of the hydraulic system 37 can be input via these input / output means 52.
  • Such an operating parameter is, for example, the press angle ⁇ , at which the valve device 48 is to switch over.
  • the controller 53 receives at least one position signal, e.g. marks the press angle.
  • the position signal can originate, for example, from an encoder 54, which detects the position of the plunger 9, in particular in the vicinity of its bottom dead center, as a displacement sensor.
  • an encoder 55 may be provided which controls the angular position of the eccentric shaft, i. detects the press angle at least in a rotation angle range in which the plunger 9 is in the vicinity of its bottom dead center.
  • a sensor 56 is also provided in the form of a force sensor which detects the force applied to the workpiece.
  • the sensor 56 is provided, for example, at the point of articulation of the connecting rod 8 on the plunger 9. If a plurality of connecting rods are provided, sensors may be provided at each of the articulation points which, like the sensor 56, are then respectively connected to the control device 53. With the sensor 56, the force exerted by the plunger 9 is detected. This force is the sum of the force exerted on the workpiece and the force exerted by the workpiece Sheet holding device 21 is received. Alternatively, it is possible to accommodate corresponding force sensors at other locations, for example as a deformation sensor in the press table 4 or as force sensors in the upper tool 11 and / or the lower tool 12.
  • the control device 53 is adapted to switch the directional control valve 49 at a certain predetermined press angle so that it locks.
  • This press angle is just before the bottom dead center at the point at which it is expected that a punching operation to be performed on the workpiece leads to a material separation.
  • the position of the eccentric at which this occurs is called the breakthrough angle.
  • the breakthrough angle is just before the bottom dead center of the plunger 9. After passing through the bottom dead center, the controller 53, the valve device 48 open again.
  • the blank holder plate 17 touches the workpiece 16, it presses the workpiece 16 against the lower tool 12.
  • the blank holder plate 17 thus stops while the plunger 9 moves toward the workpiece 16. Also remain standing the pressure pins 22 to 27, the floating plates 28, 29 and the pistons 30, 31.
  • the volume of the working chambers 32, 33 is reduced and hydraulic fluid via the fluid line 36 and the open directional control valve 49th the valve device 48 is driven into the pressure accumulator 38, which has a lower static pressure than the pressure accumulator 39.
  • the piston 43 is moved upward in FIG. 1 against the force of the upper gas cushion. Because of the pressure prevailing in the accumulator 39 higher pressure piston 42 remains in the lowest position.
  • the leading to the pressure accumulator 38 hydraulic line is shut off.
  • Switching the Valve device 48 may alternatively be made shortly before reaching the breakthrough angle, dH with an angular or temporal overfeed.
  • the necessary Vorhaltewinkel is eg via the input / output device 52 can be entered.
  • the return switching of the valve device 48 can take place at a predetermined, after bottom dead center press angle and done by the controller 53 based on the monitored press angle.
  • a sensor device for example a proximity switch, which recognizes when the piston 42 approaches the end piece 44.
  • the valve 48 can be opened again in order to reactivate the pressure accumulator 38.
  • the control device 53 is connected to the control device 53.
  • the fluid line 36 may be connected to a pressure sensor connected to the controller 53. This then switches the valve device 48 back to the open state when the fluid pressure prevailing in the fluid line 36 drops below a given limit, which is approximately on the order of magnitude of the pressure of the pressure accumulator 38.
  • the time profile of the force measured by the sensor 56 can be determined. If the drop in force, i. the negative slope of the gradient I too steep, this can be detected by the control device 53 as a breakthrough of the workpiece 16. Based on this, the control device 53 can close the valve device 48 immediately. Alternatively or additionally, the stored breakdown angle can be corrected to the now detected value. In this way, an adaptive, i. Self-learning control device 53 is created, which adapts itself during operation in terms of the breakdown angle itself. The optimization goal is to minimize the force drop occurring in the course I according to FIG. 3 between the angles ⁇ 1 and ⁇ 2.
  • the controller 53 may be configured by doing so automatically by adjusting the advance angle. However, it is also possible to specify the angle, as mentioned above, manually.
  • the system according to the invention allows a significant increase in the hold-down force, in particular during the performance of the punching operation, ie while the punches 13, 14, 15 penetrate through the material of the workpiece.
  • the actual cutting force can be reduced to one sixth of the theoretical thrust.
  • the sheet holding device 21 causes a particularly firm clamping of the workpiece 16 and thus causes an improvement of the cut as well as a cutting impact damping.
  • the press 1 is biased to equalize or compensate the games. This leads to a reduction in the total compressive force of the system compared to classical cutting impact damping systems. However, this also means that older presses can continue to be used even for difficult separation operations.
  • the force exerted on the blank holder plate force is preferably designed approximately to 40% of the pressing force.
  • the separation process can be monitored, evaluated and controlled by the use of a fast evaluation and control device, such as the control device 53.
  • the system can be largely self-sufficient, ie independently formed and used by the press 1. For example, it can be part of the tool, and thus be used in principle in different presses.
  • press-specific parameters can be changed via program or system-specific flash cards.
  • the pressures in the hydraulic cylinders 19, 20 can be permanently monitored angularly or distance-dependent.
  • the resulting envelopes allow for permanent process monitoring.
  • the control of the bypass valve 52 takes place crank angle or path-dependent on the same system.
  • the process data and faults can be stored via data storage systems and traced back in case of damage.
  • systems for detecting overload cases can be provided.
  • a sheet holding device which firmly clamps the workpiece in question during the punching process.
  • the clamping force is increased up to 40% or more percent of the ram force.
  • the force exerted by the sheet holding device during the workpiece breakthrough can be increased again.
  • the increase of the clamping force is preferably controlled in dependence on the press angle. On the one hand improves the cut quality while on the other hand results in an efficient cutting impact reduction or prevention on the press. A cutting stroke is significantly weakened or does not occur.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Presses (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
EP20060015118 2005-11-07 2006-07-20 Presse avec amortissement des chocs de coupe. Not-in-force EP1782897B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200510053350 DE102005053350A1 (de) 2005-11-07 2005-11-07 Presse mit Schnittschlagdämpfung

Publications (3)

Publication Number Publication Date
EP1782897A2 true EP1782897A2 (fr) 2007-05-09
EP1782897A3 EP1782897A3 (fr) 2008-05-21
EP1782897B1 EP1782897B1 (fr) 2014-08-20

Family

ID=37714540

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060015118 Not-in-force EP1782897B1 (fr) 2005-11-07 2006-07-20 Presse avec amortissement des chocs de coupe.

Country Status (4)

Country Link
US (1) US8302517B2 (fr)
EP (1) EP1782897B1 (fr)
DE (1) DE102005053350A1 (fr)
ES (1) ES2507068T3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102612415A (zh) * 2009-09-29 2012-07-25 沃依特专利有限责任公司 用于做功机器的切割冲击衰减的装置和方法
WO2017100810A1 (fr) * 2015-12-14 2017-06-22 Materials Center Leoben Forschung Gmbh Procédé et dispositif de séparation d'une pièce
CN114571523A (zh) * 2022-04-08 2022-06-03 河北钛通滤清器有限公司 一种纸带张紧度可自适应调整的滤纸分切机

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US20090126545A1 (en) * 2007-11-15 2009-05-21 Advanced Foundry Specialist, Llc Automated trim press and shuttle system
DE102009057409B4 (de) * 2009-12-08 2013-02-28 Schuler Pressen Gmbh & Co. Kg Stößelantrieb mit Belastungsprofilanpasssung
ES2396083B1 (es) * 2011-08-01 2014-09-02 MONDRAGON GOI ESKOLA POLITEKNIKOA J. Mª. ARIZMENDIARRIETA, S.COOP. Sistema de amortiguamiento para una prensa y método de amortiguamiento
CN103009580A (zh) * 2011-09-27 2013-04-03 鸿富锦精密工业（深圳）有限公司 浇口切除系统
US20140137624A1 (en) * 2012-08-15 2014-05-22 Kenneth L. Smedberg Die cushion system and method
ES2839075T3 (es) 2015-07-06 2021-07-05 Feintool Int Holding Ag Procedimiento y dispositivo para reducir el impacto de corte en una prensa de corte de precisión
DE102017214660B4 (de) * 2017-08-22 2022-12-15 Bayerische Motoren Werke Aktiengesellschaft Druckbolzen einer Presse sowie Presse mit Druckbolzen
DE102021108310A1 (de) * 2021-04-01 2022-10-06 Lisa Dräxlmaier GmbH Stanzvorrichtung
DE102021125418A1 (de) 2021-09-30 2023-03-30 Trumpf Werkzeugmaschinen Gmbh + Co. Kg Verfahren zur Überwachung von Bearbeitungsprozessen in einer Bearbeitungsmaschine sowie Bearbeitungsmaschinen
DE102022100935A1 (de) 2022-01-17 2023-07-20 TRUMPF Werkzeugmaschinen SE + Co. KG Verfahren und Stanzmaschine zum Ermitteln einer Stempelaufsetzposition eines Stempels der Stanzmaschine

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DE2804185A1 (de) 1977-02-07 1978-08-10 Gulf & Western Mfg Co Stossdaempfvorrichtung
US5673601A (en) 1992-09-02 1997-10-07 Komatsu Ltd. Breakthrough buffer for presses and control method therefor
DE10252625A1 (de) 2001-11-14 2003-05-28 Schuler Pressen Gmbh & Co Presse mit Schnittschlagreduzierung
EP1602419A1 (fr) 2004-06-02 2005-12-07 Schuler Pressen GmbH & Co. KG Presse pour découper des tôles de haute résistance
WO2005120741A2 (fr) 2004-06-02 2005-12-22 Stefan Fellenberg Procede et dispositif de decoupe de toles haute resistance, et presse correspondante

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102612415A (zh) * 2009-09-29 2012-07-25 沃依特专利有限责任公司 用于做功机器的切割冲击衰减的装置和方法
CN102612415B (zh) * 2009-09-29 2015-03-18 沃依特专利有限责任公司 用于做功机器的切割冲击衰减的装置和方法
WO2017100810A1 (fr) * 2015-12-14 2017-06-22 Materials Center Leoben Forschung Gmbh Procédé et dispositif de séparation d'une pièce
CN114571523A (zh) * 2022-04-08 2022-06-03 河北钛通滤清器有限公司 一种纸带张紧度可自适应调整的滤纸分切机
CN114571523B (zh) * 2022-04-08 2023-12-19 河北钛通滤清器有限公司 一种纸带张紧度可自适应调整的滤纸分切机

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US8302517B2 (en) 2012-11-06
ES2507068T3 (es) 2014-10-14
US20070101841A1 (en) 2007-05-10
EP1782897A3 (fr) 2008-05-21
DE102005053350A1 (de) 2007-05-10

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