EP1985389B1 - Presse zum Schneiden von hochfesten Blechen - Google Patents

Presse zum Schneiden von hochfesten Blechen Download PDF

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Publication number
EP1985389B1
EP1985389B1 EP08160025A EP08160025A EP1985389B1 EP 1985389 B1 EP1985389 B1 EP 1985389B1 EP 08160025 A EP08160025 A EP 08160025A EP 08160025 A EP08160025 A EP 08160025A EP 1985389 B1 EP1985389 B1 EP 1985389B1
Authority
EP
European Patent Office
Prior art keywords
press
press according
workpiece
slide
hydraulic
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.)
Not-in-force
Application number
EP08160025A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1985389A2 (de
EP1985389A3 (de
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 EP1985389A2 publication Critical patent/EP1985389A2/de
Publication of EP1985389A3 publication Critical patent/EP1985389A3/de
Application granted granted Critical
Publication of EP1985389B1 publication Critical patent/EP1985389B1/de
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
    • 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
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/10—Devices controlling or operating blank holders independently, or in conjunction with dies

Definitions

  • the invention relates to a press for punching sheets, which is particularly adapted for cutting thick and / or high-strength sheets.
  • a deep drawing press is known with a blank holder which is pressed by a hydraulic biasing means against a sheet metal part to clamp the edge thereof.
  • the hydraulic device contains valves and other control means. With these should be achieved that the hydraulic means exert a controlled force on the blank holder.
  • the press according to claim 1, a sheet holding device which presses the tool during the forming operation against the lower tool.
  • the lower tool is for example a punching tool while the upper tool is a stamp, for example.
  • the sheet holding device is able to exert different forces.
  • a control device associated with the sheet-metal holding device can influence the force exerted by the sheet-metal holding device.
  • 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 plate holding device takes over after the breakthrough of the stamp by the workpiece, the force applied by the plunger force during this passes through its bottom dead center and stores the output of the plunger energy between. During the return stroke of the plunger, this energy is given back to the plunger and thus to the press drive.
  • a further improvement brings the alternative solution according to claim 11 with it. This allows in particular the achievement of high stroke rates. If the torque of the rupture of the plunger through the workpiece, ie the moment in which the workpiece yields, is monitored, for example by hydraulic fluid delivered by hydraulic cylinder support means being monitored for volumetric flow, a steep increase in volume flow is observed at the moment of the breakthrough. However, the occurring volume flow may well be below a value that occurs at rapid stroke rates when placing the plunger on the support, which may be formed, for example, as a sheet holding device. According to the invention, therefore, the control device releases the influence of the force applied by the support means only within a fixed path portion of the plunger movement. In this way, false identifications that would otherwise lead to gross malfunction of the press, safely excluded.
  • the fixed path portion preferably has an adjustable start ⁇ 1 or x1. In addition, it may preferably have a variably adjustable end ⁇ 2 or x2. In addition, its length can be variable and adjustable.
  • the press can be easily adjusted to different conditions, in particular with regard to the operating speed or stroke rate and the cutting force.
  • the sheet holding device or the support means to a hydraulic cylinder which is connected to a first and a second hydraulic pressure accumulator.
  • Both accumulators have e.g. a slidably 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 pressure reservoir at lower pressure is preferably regulated by a valve which controls the fluid flow, i.e., the flow rate. monitors the mass flow and closes when it exceeds a limit.
  • This flow-sensitive valve is an advantageous variant of a sensor device which serves to detect the breakdown of the workpiece.
  • a corresponding displacement measuring device or other transducer device can also be used to obtain a signal, based on which set the activation window within which the punch breakthrough is expected.
  • the puncture breakthrough is then monitored only in this activation window while the support device is passive outside the activation window or the sheet metal holding device only fulfills its sheet metal holding function.
  • the lower tool 12 is illustrated as a flat workpiece.
  • the lower tool 12 then has a contour corresponding to the non-planar workpiece.
  • 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 an in FIG. 2 not and in FIG. 1 only schematically shown fluid line 36 connected to a hydraulic system 37, which serves to generate a blank holder force and at the same time to take over the force exerted by the plunger 9 force during and after breakthrough of the workpiece 16.
  • This power transfer should be as stepless as possible, ie without a sudden force change.
  • To the hydraulic system 37 includes a first pressure accumulator 38 and a second pressure accumulator 39, both of which are formed in the embodiment as accumulator cylinder 40, 41 with sealed therein, slidably mounted 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 under a pressure of about 200 bar, for example, while the pressure accumulator 39 is e.g. under a pressure of e.g. 400 bar stands.
  • 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 fluid flow into and out of the pressure accumulator 38 is unrestricted or restricted, while in its other state it blocks this fluid flow.
  • the valve device 48 may be connected to a sensor device 50 which, for example, monitors and closes the mass flow ⁇ in the fluid line 36 as soon as this hydraulic flow directed into the pressure accumulator 38 exceeds a threshold value m th and then closes for such a long time remains until the pressure in the fluid line 36 drops below a threshold.
  • the sensor device 50 thus simultaneously forms a control device 51 for controlling the valve device 48 as a function of the speed of the relative movement between the pistons 28, 29 of the hydraulic cylinders 19, 20 and the plunger 9.
  • valve means 48 may also include, if necessary, a bypass valve 52 which bridges the valve means 48 and thus provides an alternative path from the hydraulic cylinders 19, 20 to the pressure accumulator 38.
  • By-pass valve 52 is, for example, an open / close valve that may be electrically pneumatically or otherwise controlled.
  • control device 53 which may be preferably designed as a microprocessor control or as another suitable electronic control.
  • the control device 53 receives at least one position signal. This may, for example, originate 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 detects the angular position of the eccentric shaft at least in a rotation angle range in which the plunger 9 is in the vicinity of its bottom dead center.
  • FIG. 3 Figure 1 illustrates an embodiment of the valve device 48 which is preferred for its fast response time. It has a main body 56, which is provided with at least one input 57 and with an output 58. Between both a channel 59 is formed, the passes longitudinally through the base body 6 and to which the channels of the input 57 and the output 58 are directed transversely. Between the input 57 and the output 58, a valve seat 60 is formed, which is associated with a valve closure member in the form of a disk 61. The latter sits on a pin and is biased by a spring in the opening direction of the valve seat 60 away. The bias can be adjusted if necessary by means of an externally accessible handle, such as an adjusting screw 62.
  • an externally accessible handle such as an adjusting screw 62.
  • the press 1 described so far operates in a first simple embodiment, which in principle manages without the control device 53, as follows:
  • the workpiece 16 is first placed on the lower tool 12, after which the plunger 9 lowers.
  • the blank holder plate 17 is in its lowest position, in which it is at least slightly below the end faces of the punches 13, 14, 15 with its underside.
  • the pistons 30, 31 in the hydraulic cylinder 19, 20 at rest.
  • the hydraulic fluid is in the hydraulic system 37 under a static pressure.
  • 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 valve 49 of 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 in FIG. 1 moved upwards against the force of the upper gas cushion.
  • the fluid flow ⁇ occurring in this process is below a threshold value, so that the sensor device 50 does not respond.
  • the directional control valve 49 closes.
  • the directional control valve 49 thus closes abruptly, wherein the closed state is maintained until a decreasing system pressure the valve closure member 61 allows to return to its open position, ie rest position.
  • FIG. 4 can be achieved by determining the activation window between the press angles ⁇ 1 and ⁇ 2 that flow peaks are detected, which are lower than the flow immediately after placing the blank holder plate 17 on the workpiece 16. This is at very fast presses (high stroke rates), at large punching strokes and especially in very rigid press racks a role in which although a very large clamping force but only a small clamping stroke occurs in the entire press frame.
  • the response threshold ⁇ th for the valve device 48 can be set very low, so that the otherwise observed punching blow to an almost imperceptible Minimum is to be limited.
  • ⁇ 1, ⁇ 2 variably. For example, they may be entered with a suitable input device. It is also possible to dynamically adjust these press angles ⁇ 1, ⁇ 2. This can for example be done by ⁇ 1 is set in a predetermined or input angular distance before punching breakthrough and ⁇ 2 at a fixed or adjustable angular distance after the punch breakthrough. As press angle of the Punch breakthrough is then used in each case the press angle from the previous punching stroke or an average value from previous punching strokes.
  • the press according to the invention allows a substantial increase of 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 continue even for difficult separation operations can be used.
  • 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 encoder-dependent or path-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 21 which clamps the workpiece 16 in question during the punching operation.
  • 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.
  • an efficient cutting impact reduction or prevention at the press results.
  • a cutting stroke is significantly weakened or does not occur.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Punching Or Piercing (AREA)
  • Control Of Presses (AREA)
  • Shearing Machines (AREA)
  • Press Drives And Press Lines (AREA)
EP08160025A 2004-06-02 2005-05-18 Presse zum Schneiden von hochfesten Blechen Not-in-force EP1985389B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004027017 2004-06-02
DE102005021028A DE102005021028B4 (de) 2004-06-02 2005-05-06 Presse zum Schneiden von hochfesten Blechen
EP20050010716 EP1602419B1 (de) 2004-06-02 2005-05-18 Presse zum Schneiden von hochfesten Blechen

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP20050010716 Division EP1602419B1 (de) 2004-06-02 2005-05-18 Presse zum Schneiden von hochfesten Blechen
EP05010716.8 Division 2005-05-18

Publications (3)

Publication Number Publication Date
EP1985389A2 EP1985389A2 (de) 2008-10-29
EP1985389A3 EP1985389A3 (de) 2008-11-05
EP1985389B1 true EP1985389B1 (de) 2012-02-01

Family

ID=34936621

Family Applications (2)

Application Number Title Priority Date Filing Date
EP20050010716 Not-in-force EP1602419B1 (de) 2004-06-02 2005-05-18 Presse zum Schneiden von hochfesten Blechen
EP08160025A Not-in-force EP1985389B1 (de) 2004-06-02 2005-05-18 Presse zum Schneiden von hochfesten Blechen

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP20050010716 Not-in-force EP1602419B1 (de) 2004-06-02 2005-05-18 Presse zum Schneiden von hochfesten Blechen

Country Status (3)

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EP (2) EP1602419B1 (es)
DE (2) DE102005021028B4 (es)
ES (2) ES2381607T3 (es)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005053350A1 (de) 2005-11-07 2007-05-10 Schuler Pressen Gmbh & Co. Kg Presse mit Schnittschlagdämpfung
DE102006039463A1 (de) * 2006-08-23 2008-02-28 Müller Weingarten AG Verfahren und Vorrichtung zur Schnittschlagdämpfung
DE102009048483B4 (de) * 2009-09-29 2012-08-16 Voith Patent Gmbh Schnittschlagdämpfung
DE102014111241A1 (de) 2014-08-07 2016-02-11 Schuler Pressen Gmbh Blech- oder Sinterteil für einen Stator oder einen Läufer einer elektrischen Maschine sowie Verfahren zu dessen Herstellung
CN104384291B (zh) * 2014-10-08 2016-08-24 四川百世昌重型机械有限公司 液压机缓冲调节与机械定程复合装置
DE102015106859B4 (de) 2015-05-04 2018-06-14 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Verfahren zum Scherschneiden hochfester Werkstoffe und Schneidwerkzeuganordnung
CN113415779B (zh) * 2021-07-03 2022-11-25 江西乔扬数控设备有限公司 一种闭式压力机自动注油装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2290743A (en) * 1939-12-11 1942-07-21 Hydraulic Dev Corp Inc Blank-holder press
DE2808091A1 (de) * 1978-02-24 1979-08-30 Moog Gmbh Einrichtung zum daempfen des schnittschlags bei hydraulischen pressen
DE2928777A1 (de) * 1979-07-17 1981-02-05 Profil Verbindungstechnik Gmbh Schlagdaempfer zur laermreduzierung bei maschinen mit hin- und hergehenden maschinenteilen
BE1004564A3 (fr) * 1990-08-30 1992-12-15 Cockerill Rech & Dev Dispositif de regulation de la force de serre-flan dans une presse.
JP3319786B2 (ja) * 1992-09-02 2002-09-03 株式会社小松製作所 プレスのブレークスルー緩衝装置およびその制御方法
BE1010313A3 (fr) * 1996-05-30 1998-06-02 S C Rech Et Dev Groupe Cockeri Amelioration au systeme de regulation de la force de serre-flan dans une presse.
DE10252625B4 (de) * 2001-11-14 2008-09-04 Schuler Pressen Gmbh & Co. Kg Presse mit Schnittschlagreduzierung

Also Published As

Publication number Publication date
EP1985389A2 (de) 2008-10-29
EP1985389A3 (de) 2008-11-05
ES2346980T3 (es) 2010-10-22
ES2381607T3 (es) 2012-05-29
EP1602419A1 (de) 2005-12-07
DE102005021028B4 (de) 2009-06-25
EP1602419B1 (de) 2010-06-23
DE102005021028A1 (de) 2005-12-29
DE502005009780D1 (de) 2010-08-05

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