EP0003745A1 - Installation d'amortissement de chocs de coupe pour presses hydrauliques - Google Patents

Installation d'amortissement de chocs de coupe pour presses hydrauliques Download PDF

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Publication number
EP0003745A1
EP0003745A1 EP79100125A EP79100125A EP0003745A1 EP 0003745 A1 EP0003745 A1 EP 0003745A1 EP 79100125 A EP79100125 A EP 79100125A EP 79100125 A EP79100125 A EP 79100125A EP 0003745 A1 EP0003745 A1 EP 0003745A1
Authority
EP
European Patent Office
Prior art keywords
tool
reciprocating piston
workpiece
cutting
movement
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.)
Withdrawn
Application number
EP79100125A
Other languages
German (de)
English (en)
Inventor
Friedrich Kollmar
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.)
Moog GmbH
Original Assignee
Moog 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 Moog GmbH filed Critical Moog GmbH
Publication of EP0003745A1 publication Critical patent/EP0003745A1/fr
Withdrawn legal-status Critical Current

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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
    • Y10T83/869—Means to drive or to guide tool
    • Y10T83/8821—With simple rectilinear reciprocating motion only
    • Y10T83/8827—Means to vary force on, or speed of, tool during stroke
    • 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
    • Y10T83/869—Means to drive or to guide tool
    • Y10T83/8821—With simple rectilinear reciprocating motion only
    • Y10T83/8858—Fluid pressure actuated

Definitions

  • the invention relates to a device for damping the cutting impact in hydraulic presses according to the preamble of claim 1.
  • Hydraulic presses are used, among other things, to punch workpieces, for example sheet metal. Step through the material as the tool moves relatively high forces between the punch and the die of the tool, which lead to very considerable deformation energies in the workpiece and the press, in particular in the hydraulic oil of the press cylinder of the press.
  • the present invention has for its object to provide a device of the type mentioned, which is easy to use and leads to an improved shock absorption.
  • the present invention is based on the knowledge that most materials, in particular metal, change with increasing load and the beginning of deformation into a state in which the further material deformation takes place at a significantly lower load.
  • this material characteristic is taken into account in that when the material gets into the easily deformable state, the force exerted on the tool is automatically reduced becomes.
  • the energy stored in the press, the tool, the workpiece and the oil in the hydraulic system is already reduced while the tool is still in the workpiece. In known presses, the initially required force is maintained until the tool exits the workpiece.
  • the control used here guides the tool through the workpiece according to a predetermined travel-time function and leaves it at a relatively low speed. It is essential that the force exerted on the tool at the end of the punching movement is automatically significantly reduced compared to the force initially to be applied.
  • the control starts and reduces the hydraulic pressure and thus the force on the tool until actual and target value match again.
  • the pressure in the hydraulics is already reduced during the cutting movement by the control system, so that the elastic energies initially built up in the press and the hydraulics are almost completely degraded when the tool exits the workpiece.
  • an embodiment is specified which leads to a very simple control loop and in which the predetermined function for the setpoint is generated by superimposing a constant basic level and a signal which changes over time.
  • Fig. 1 shows a typical press as it is used for punching materials, for example sheet metal. It has a press frame 1, on the C-shaped arm of which a reciprocating piston 2 is movably mounted in a cylinder acting on both sides in the vertical direction. On the lower piston rod 3 of the piston, a punch 4a of a tool is attached, the associated die 4b of which rests on the lower part of the frame 1.
  • a quantity servo valve 5, which is controlled by control electronics 6, is connected to the two chambers of the reciprocating piston 2.
  • a displacement sensor 7 is arranged on the lower part of the frame 1 of the press, the output signal of which is fed to the control electronics 6.
  • Reference number 8 is a setpoint generator referred to, the output signal is also supplied to the control electronics 6.
  • Fig. 2 the entire control loop, which also includes the press itself, is shown in more detail in a block diagram.
  • the controlled system of this control circuit contains a position control amplifier 6a, the quantity servo valve 5 and the press cylinder 2.
  • the displacement sensor 7 In the feedback branch there is the displacement sensor 7, the output signal of which is fed to a summation point 9 with a negative sign.
  • the output signal of the setpoint generator 8 and the output signal of the setpoint generator 8 and the output signal of a function generator 10 are also fed to this summation point.
  • the input of this function generator 10 is connected to the displacement sensor 7.
  • the reference numeral 11 designates all those parts of the control circuit which supply disturbance variables, for example the workpiece which bends during the stamping process and the parts of the press which deform. These variables are effective in the control circuit in front of the reciprocating piston 2.
  • the disturbance variable block 11 is therefore coupled to the input of the reciprocating piston 2. This disturbance variable block is irrelevant for understanding the control loop.
  • the function of the control loop shown in FIG. 2 is explained in more detail below. It is assumed that there is a die for punching the workpiece 12 on the die 4b of the press 1.
  • the punch 4a of the tool is in an initial position, as shown in FIG. 1. From this starting position, the plunger 4a is moved down relatively quickly in that hydraulic oil is pumped into the upper chamber of the reciprocating piston 2 via the pump connected to the hydraulics 5. This is done in the usual way. If the punch 4a just touches the workpiece 12, or a short distance in front of it, the displacement sensor 7 is replaced by a suitable one actuated part connected to the piston. The further movement of the piston now takes place via the control loop, as shown in FIG. 2.
  • the now following movement of the plunger 4a caused by the control loop lies in the time diagram according to FIG. 4 between the times t a and t b .
  • the setpoint generator 8 emits a constant basic output signal.
  • the function generator 10 is triggered, which now emits a signal which rises in time and which is superimposed on the signal from the setpoint transmitter 8 at the summation point 9.
  • This control loop can be viewed in such a way that it is controlled by a setpoint, which is composed of the sum signal from the signals from the setpoint generator 8 and the function generator 10.
  • the actual actual size is determined on the displacement sensor 7 and fed to the summation point 9 with a negative sign.
  • the servo valve 5 receives an electrical output signal via the position control amplifier 6a, which causes the pump connected to the servo valve 5 to pump hydraulic oil into the upper chamber of the reciprocating piston 2.
  • Electrically controlled servo valves which are suitable for this purpose are known and need not be explained in more detail here. If the plunger 4a touches the workpiece 12, the control circuit has the effect that the hydraulic pressure in the upper chamber of the reciprocating piston 2 is increased considerably, so that the actual displacement path of the piston is tracked to the predetermined desired value.
  • the end of the control can be triggered again by the solenoid 7, which overrides the control in a predetermined end position and reconnects the servo valve to the usual servo circuit via a circuit, not shown here ensures a rapid return movement of the plunger 4a by pressurizing the lower chamber of the reciprocating piston 2. This ead movement is shown in FIG. 4 after the time t b .
  • the function generator 10 only has to deliver a steadily increasing output signal which is superimposed on the constant signal of the setpoint generator 8.
  • a linearly increasing output signal can lead to very useful results.
  • the exit area Speed of the stamp 4a from the workpiece 12 can be further reduced by generating a logarithmic signal instead of a linearly increasing signal in the function generator 10, which increases significantly more at the time t a at the beginning of the control than at the time t b at the end of the control .
  • the time period between the times t a and t b is advantageously chosen to be 1 to 2 seconds.
  • the cheapest setting of the setpoint generator 8 can easily be found in practice. First, a value is set at which the punch 4a breaks through the workpiece 12, which naturally results in a cut blow. In the subsequent punching operations, the setpoint is gradually reduced until the press works without a cut.
  • FIG. 3 shows a practical exemplary embodiment of the control loop, as is shown schematically in FIG. 2.
  • a potentiometer is used as setpoint generator 8, which is connected to a fixed voltage with its end connections.
  • the constant basic setpoint which is supplied to the summation point 9 in FIG. 2, is taken off via the center tap of this potentiometer.
  • the summation point 9 shown in FIG. 2 is formed by the negative connection of an operational amplifier 13, which is contained in the position control amplifier 6a.
  • the actual signal from the actual value transmitter 7 is also fed to this negative connection.
  • the output of this operational amplifier 13 is connected to the electrically controllable servo valve 5, of which only the control coil is shown in FIG. 3.
  • the function generator 10 contains a capacitor 14, which acts as a charging capacitor and supplies a linearly increasing voltage at the output of the function generator 10.
  • a constant voltage of a correction potentiometer 15 is superimposed on the signal from the actual value transmitter 7, as a result of which the starting point t a the regulation can be set. It is within the scope of the skilled person to modify the function generator so that, for example, it delivers a logarithmic function such as that shown in broken lines as a second alternative between the times t a and t b in FIG. 4.
  • a displacement potentiometer the end connections of which are at a constant voltage, can be used, for example, as the displacement sensor 7.
  • Other conventional sensing elements can also be used which are suitable for reproducing the position of a mechanical element, here the die 4b or the piston rod 3, in an analog form.
  • photoelectric sensing elements also appear to be very suitable here.
  • the specified regulation has the advantage that it can also be used to easily retrofit presses that have not yet had a cut impact damping.
  • the control only needs to be connected to the already existing hydraulic system in such presses with double-acting pulling winches, without any structural modifications being necessary.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Presses (AREA)
  • Punching Or Piercing (AREA)
EP79100125A 1978-02-24 1979-01-16 Installation d'amortissement de chocs de coupe pour presses hydrauliques Withdrawn EP0003745A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2808091 1978-02-24
DE19782808091 DE2808091A1 (de) 1978-02-24 1978-02-24 Einrichtung zum daempfen des schnittschlags bei hydraulischen pressen

Publications (1)

Publication Number Publication Date
EP0003745A1 true EP0003745A1 (fr) 1979-09-05

Family

ID=6032896

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79100125A Withdrawn EP0003745A1 (fr) 1978-02-24 1979-01-16 Installation d'amortissement de chocs de coupe pour presses hydrauliques

Country Status (4)

Country Link
US (1) US4208935A (fr)
EP (1) EP0003745A1 (fr)
JP (1) JPS54123789A (fr)
DE (1) DE2808091A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2186394A (en) * 1986-02-07 1987-08-12 Amada Co Ltd Controlling the stroke of a press or shearing machine
GB2213086A (en) * 1987-12-04 1989-08-09 Amada Co Ltd Method and device for controlling the stroke of a press machine
GB2219669A (en) * 1988-06-07 1989-12-13 Hiroshi Sato Press brake with a displacement sensor
CN105965934A (zh) * 2016-06-30 2016-09-28 嘉善中建钢结构安装有限公司 一种压型装置

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3334093A1 (de) * 1983-09-21 1985-04-11 Robert Bosch Gmbh, 7000 Stuttgart Verfahren und schaltung zur ermittlung des verbauchsoptimalen getriebeganges eines kraftfahrzeugantriebes
JPS63501202A (ja) * 1985-10-18 1988-05-12 ユニバ−サル・エンジニアリング・デベロ−プメント・カンパニ−・プロプライアタリイ・リミテツド 押抜きプレスの改良
US5042336A (en) * 1989-03-03 1991-08-27 Capps David F Control apparatus and method for progressive fracture of workpieces
US5176054A (en) * 1989-03-03 1993-01-05 Capps David F Control apparatus and method for progressive fracture of workpieces
DE4110761C1 (fr) * 1991-04-03 1992-04-02 Harald Perchtoldsdorf At Engel
DE4224277A1 (de) * 1992-07-23 1994-01-27 Lenhauser Hammerwerk Gmbh Gelenkhebelpresse
US5913956A (en) * 1995-06-07 1999-06-22 Capps; David F. Apparatus and method for progressive fracture of work pieces in mechanical presses
DE19529134A1 (de) * 1995-08-08 1997-02-13 Lindemann Maschfab Gmbh Einrichtung zur Dämpfung des Schnittschlages von Schrottscheren
WO2001034317A1 (fr) * 1999-11-05 2001-05-17 Amada Company, Limited Presse-plieuse et procede de commande de pompe a ecoulement bidirectionnel du cylindre hydraulique de la presse-plieuse
DK1507980T3 (da) * 2002-05-24 2006-09-25 Metso Lindemann Gmbh Hydraulisk styring i et hydrauligsk system, navnlig til driften af en skrotsaks
DE102005021028B4 (de) * 2004-06-02 2009-06-25 Schuler Pressen Gmbh & Co. Kg Presse zum Schneiden von hochfesten Blechen
CA2568685A1 (fr) 2004-06-02 2005-12-22 Stefan Fellenberg Procede et dispositif de decoupe de toles haute resistance, et presse correspondante
US20080022821A1 (en) * 2006-07-26 2008-01-31 Heidelberger Druckmaschinen Ag Sheet punching and embossing machine
CN105537374A (zh) * 2015-12-16 2016-05-04 无锡福镁轻合金科技有限公司 一种小型高速电机轴的内六方自动化精密加工装置
CN105396934B (zh) * 2015-12-23 2017-03-29 安徽鲲鹏装备模具制造有限公司 一种带自动力的冲裁模具

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1350209A (fr) * 1962-09-20 1964-01-24 Matra Werke Gmbh Presse, notamment presse hydraulique
US3205749A (en) * 1963-03-21 1965-09-14 Schenk Horst Dieter Hydraulic cutting and punching press
FR1514011A (fr) * 1966-05-12 1968-02-16 Minster Machine Co Appareil servant à supprimer les vibrations dues aux chocs dans les presses
DE1577187A1 (de) * 1964-12-11 1970-02-26 Horst Schenk Gegendrucksystem in Presse,insbesondere in hydraulischer Presse
GB1210877A (en) * 1967-03-22 1970-11-04 Asea Ab Improvements in hydraulic presses
FR2183055A1 (fr) * 1972-04-29 1973-12-14 Schuler Gmbh L
FR2201183A1 (fr) * 1972-09-29 1974-04-26 Schuler Gmbh L
FR2366930A1 (fr) * 1976-10-11 1978-05-05 Osterwalder Ag Presse a commande hydraulique
FR2372023A1 (fr) * 1976-11-26 1978-06-23 Frieseke & Hoepfner Gmbh Installation d'amortissement de chocs de coupe pour machines d'estampage de tous genres

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3827328A (en) * 1972-12-26 1974-08-06 Greenerd Press & Machine Co In Control system for hydraulic presses
SU565752A1 (ru) * 1974-02-14 1977-07-25 Предприятие П/Я А-7734 Способ формообразовани поверхности деталей
FR2323478A1 (fr) * 1975-09-10 1977-04-08 Jambon Anciens Ateliers H Presse hydraulique pour operation de cisaillage ou de tronconnage

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1350209A (fr) * 1962-09-20 1964-01-24 Matra Werke Gmbh Presse, notamment presse hydraulique
US3205749A (en) * 1963-03-21 1965-09-14 Schenk Horst Dieter Hydraulic cutting and punching press
DE1577187A1 (de) * 1964-12-11 1970-02-26 Horst Schenk Gegendrucksystem in Presse,insbesondere in hydraulischer Presse
FR1514011A (fr) * 1966-05-12 1968-02-16 Minster Machine Co Appareil servant à supprimer les vibrations dues aux chocs dans les presses
GB1210877A (en) * 1967-03-22 1970-11-04 Asea Ab Improvements in hydraulic presses
FR2183055A1 (fr) * 1972-04-29 1973-12-14 Schuler Gmbh L
FR2201183A1 (fr) * 1972-09-29 1974-04-26 Schuler Gmbh L
FR2366930A1 (fr) * 1976-10-11 1978-05-05 Osterwalder Ag Presse a commande hydraulique
FR2372023A1 (fr) * 1976-11-26 1978-06-23 Frieseke & Hoepfner Gmbh Installation d'amortissement de chocs de coupe pour machines d'estampage de tous genres

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2186394A (en) * 1986-02-07 1987-08-12 Amada Co Ltd Controlling the stroke of a press or shearing machine
FR2594062A1 (fr) * 1986-02-07 1987-08-14 Amada Co Ltd Procede pour controler la course d'une machine de traitement de plaques
GB2186394B (en) * 1986-02-07 1990-05-16 Amada Co Ltd Method and apparatus for controlling the stroke of plate processing machine
GB2213086A (en) * 1987-12-04 1989-08-09 Amada Co Ltd Method and device for controlling the stroke of a press machine
US5027631A (en) * 1987-12-04 1991-07-02 Amada Company, Limited Method and device for controlling the stroke of a press machine
US5031431A (en) * 1987-12-04 1991-07-16 Amada Company, Limited Method and device for controlling the stroke of a press machine
GB2213086B (en) * 1987-12-04 1992-08-05 Amada Co Ltd Method and device for controlling the stroke of a press machine
GB2219669A (en) * 1988-06-07 1989-12-13 Hiroshi Sato Press brake with a displacement sensor
CN105965934A (zh) * 2016-06-30 2016-09-28 嘉善中建钢结构安装有限公司 一种压型装置
CN105965934B (zh) * 2016-06-30 2018-02-09 嘉善中建钢结构安装有限公司 一种压型装置

Also Published As

Publication number Publication date
JPS54123789A (en) 1979-09-26
US4208935A (en) 1980-06-24
DE2808091A1 (de) 1979-08-30

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Inventor name: KOLLMAR, FRIEDRICH