EP0543772A1 - Presse - Google Patents

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Publication number
EP0543772A1
EP0543772A1 EP92810802A EP92810802A EP0543772A1 EP 0543772 A1 EP0543772 A1 EP 0543772A1 EP 92810802 A EP92810802 A EP 92810802A EP 92810802 A EP92810802 A EP 92810802A EP 0543772 A1 EP0543772 A1 EP 0543772A1
Authority
EP
European Patent Office
Prior art keywords
press
cheek
press according
parts
gaps
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Withdrawn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
EP92810802A
Other languages
German (de)
English (en)
Inventor
Waldemar Krumholz
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.)
M&S Brugg AG
Original Assignee
M&S Brugg AG
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 M&S Brugg AG filed Critical M&S Brugg AG
Publication of EP0543772A1 publication Critical patent/EP0543772A1/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Withdrawn legal-status Critical Current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
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means
    • B21D5/0272—Deflection compensating means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/007—Means for maintaining the press table, the press platen or the press ram against tilting or deflection

Definitions

  • the invention relates to a press with at least two parallel press beams, which are located opposite one another along the work site and can be moved against one another transversely to their longitudinal extent under the influence of press forces, the press forces acting punctually in the region of the two longitudinal ends of the press beams.
  • the invention relates to a particular embodiment of such presses, namely a press brake with press beams arranged one above the other, e.g. in the form of a vertically movable upper cheek, at the two ends of which the pressing forces are introduced, and a lower cheek lying freely at both ends.
  • Press brakes of this type are known to have the disadvantage that, without special measures, the upper beam and the lower beam bend in opposite directions under load and therefore form an uneven working gap between the upper and lower tool.
  • This disadvantage has a particularly strong effect on large press brakes with a passage several meters wide between the stands and especially when machining workpieces, the width of which is significantly less than the total working width of the cheeks.
  • the lower part of the upper cheek is divided horizontally into several cheek parts, each of which is connected to a power cylinder, the counterforce of which can be controlled in accordance with the load on the respective cheek part.
  • So-called hydro cushions for changing the load distribution on the various cheek parts have also been proposed for this purpose. All these known solutions have the disadvantage that the means for generating the counterforces and for controlling these counterforces are enormously complex owing to constantly changing load distributions and make the manufacture and operation of such press brakes considerably more expensive.
  • the invention now shows another way to achieve the desired goal with simpler and less complex means, namely to exert a uniform force influence on the workpiece over the entire width of the cheek.
  • this object is achieved in that at least one of the two press beams is divided into two, the division extending transversely to the course of the press forces, and with the two beam parts abutting one another in the middle of the beam at a butt joint and on both sides of the butt joint by a gap with up to End of the beam towards the constantly increasing gap width are separated from each other, and that the force application points of the two-part press beam are on the part of the beam facing away from the work place.
  • the press beams bend in the same direction under load at the edges opposite each other at the work place, by increasing the flexibility of the beam part of the two-part press beam adjoining the work place on its sides in such a way that this beam part is inevitably one under load assumes a convex shape, in contrast to a one-piece press beam, which is always concavely bent under the same circumstances.
  • the proposed measure can be used both on a movable and on a fixed press beam and can affect both only one and both press beams. In the latter case, it is even possible to linearize the course of the working gap between the two press beams under load.
  • the effect of the measure according to the invention is essentially independent of whether the movement plane of the press bars runs vertically, horizontally or obliquely.
  • this plane of movement is normally vertical, with either the upper cheek or the lower cheek being movable and the counter cheek being fixed.
  • the weight of the cheeks or cheek parts must also be included in the calculation of the deflection lines in addition to the pressing forces.
  • the width of the columns (19) at the bar ends (20) is in the unloaded state of the divided one
  • the press beam is expediently chosen such that it corresponds in size to the maximum deflection occurring under load under the same conditions on the undivided press beam.
  • the gap width at the bar ends is preferably at least as large as the maximum deflection of an undivided press bar opposite the divided press bar, which occurs at maximum pressing force.
  • both press beams are divided into two, it is more advantageous if the width of the gaps at the beam ends is at most as large as the maximum deflection occurring on the undivided press beams under the same conditions.
  • these coupling links can be used to hold the two beam parts loosely together at the joint and to absorb the weight of the lower cheek part.
  • These coupling members are preferably arranged in the area of the bar ends, where they can additionally be designed as a means for stabilizing the bar part adjacent to the work position, for example to prevent this bar part from tipping over an axis lying in the area of the joint.
  • a preferred embodiment of the coupling members mentioned is that they are articulated with both beam parts are connected and that they have an effective freewheel during the pressing process in order to relieve the coupling members during the pressing process.
  • the coupling elements can contain spring elements which are switched on in the force-locking connection thereof. These spring elements are expediently dimensioned such that they hold the two beam parts loosely together when the press beam is not loaded and, in the case of a press brake with a divided upper beam, absorb the weight of the lower beam part.
  • An additional function of these spring elements can consist in damping the force peaks acting on the coupling members at the beginning of the empty stroke of the upper cheek.
  • the coupling elements mentioned can be omitted if the two beam parts of the two-part press beam are firmly connected to one another at the joint, e.g. are screwed.
  • means are advantageously provided in the region of the beam ends of the two-part press beam which guide the two beam parts to one another.
  • the frame of the press brake is essentially composed of two vertical side walls 1 and a yoke beam 2 connecting the side walls 1 to one another on the upper side.
  • the yoke beam is box-shaped and consists of two vertical longitudinal plates 3 and 4, which are connected to one another at the ends by a vertical transverse plate 5.
  • the side walls 1 are each formed from two upstanding plates 6 and 7, which are arranged at a distance from one another leaving a space 8 and are connected to one another at the top by the yoke beam 2 and at the bottom by a web 9.
  • the active parts of the press brake form a fixed lower beam 10 and an upper beam 11, to which the bending tools can be fastened in a manner not shown.
  • the supports 12 On the inside of the two side walls 1 there are two supports 12, which form the bearing block for the lower beam 10 designed as a free-standing beam.
  • the supports 12 are each provided with a semi-cylindrical pan 13.
  • a cylindrical pin 14 is anchored at both, stepped ends of the lower beam 10, which reach between the supports 12 and whose projecting ends rest in the relevant pans 13 of the supports 12.
  • the upper cheek 10 is divided into two in the direction of the force, the upper cheek part 15 and the lower cheek part 17 adjoining the work station 16 abutting one another in the middle of the cheek and on both sides of the joint formed as the butt surface 18 by a gap 19 with a gap width increasing up to the cheek end 20 are separated.
  • the upper cheek part 15 of the upper cheek 10 hangs on its two offset ends from each of two support members 21, which are articulated on the one hand to the upper cheek part 15 and on the other hand to the piston rod 22 of a power cylinder 23, the articulated axis located on the cheek part 15 with 24 and the on the piston rod 18 located hinge axis is designated 25.
  • Each power cylinder 23 is attached to the adjacent cross plate 5 of the yoke beam 2.
  • a spherical butt joint 26 is provided for transmitting the pressing force from the piston rods 22 to the upper cheek part 15 of the upper cheek 10 and for the selective introduction of force into this cheek part 15. The details of this butt connection are not discussed in more detail here.
  • the two cheek parts 15 and 17 of the upper cheek 10 are connected to one another by coupling members 27, which are arranged near the cheek ends 20 and hold the two cheek parts 15, 17 loosely together on the abutment surface 18.
  • the mutual position of the two cheek parts 15, 17 is also secured by a fitting bolt 28 inserted on both sides in the area of the abutting surface 18.
  • the coupling members 27 are formed similarly to the support members 21 and also articulated to the cheek parts 15, 17, the articulation axes being designated 29 and 30.
  • FIG. 3 A preferred embodiment of the coupling members 27 is shown in FIG. 3.
  • the coupling member 27 is divided in the direction of force into an upper part 31 connected to the articulated axis 29 and a lower part 32 connected to the articulated axis 30.
  • the upper part 31 and the lower part 32 are connected to one another by screws 33 which secure the laterally directed legs 35 of the Push through the upper part 31 freely and are screwed into the lower part 32.
  • spring elements 36 for example plate springs, are used, which are dimensioned such that they absorb the weight of the lower cheek part 17 when the upper cheek 10 is empty and hold the two cheek parts 15, 17 loosely together. In this way it is achieved that the lower cheek part 17 assumes a stable position, that is to say it is subjected to bending in the operation of the upper cheek 10 and does not tip without resistance to the upper cheek part 15 in the case of one-sided loading.
  • Fig. 4 for the two cheeks 10 and 11 of the press brake the bending lines 45 and 46 occurring at the work station 16 are drawn in the case of a uniform load over the entire length of the cheeks, the extent of the deflection being shown in an enlarged manner.
  • the two cheeks 10 and 11 bend in the same direction under the influence of the pressing forces F p , the contact forces F a and the cheek weights G o and G u , and the deflection lines 45 and 46 run approximately parallel.
  • the press brake according to the second embodiment according to FIG. 5 differs from that according to FIGS. 1 and 2 essentially only by the means for holding the two cheek parts 15 and 17 of the upper cheek together.
  • the coupling members 27 are omitted the two cheek parts 15 and 17 are firmly connected to one another at the somewhat wider abutting surface, specifically by means of screws 37, which are arranged here in flanges 38, 39 provided on both sides of the cheek parts 15, 17.
  • the flanges 38, 39 can also be omitted and corresponding connecting screws can be arranged within the cheek parts 15, 17, with corresponding recesses, for example in the upper cheek part, for the accessibility of the screw heads 15 would have to be provided.
  • devices 40 for mutually guiding the two cheek parts 15, 17 are provided in the region of the cheek ends.
  • Each of these devices 40 is e.g. 6 from two plates 41 bridging the gap 19 between the two cheek parts 15, 17, which are fastened to the upper cheek part 15 with screws 42 and carry effective guide bodies 43 on the sides of the lower cheek part 17, these guide bodies 43 being set by adjusting screws 44 are axially adjustable.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Press Drives And Press Lines (AREA)
EP92810802A 1991-11-21 1992-10-20 Presse Withdrawn EP0543772A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4138286 1991-11-21
DE4138286A DE4138286A1 (de) 1991-11-21 1991-11-21 Presse

Publications (1)

Publication Number Publication Date
EP0543772A1 true EP0543772A1 (fr) 1993-05-26

Family

ID=6445283

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92810802A Withdrawn EP0543772A1 (fr) 1991-11-21 1992-10-20 Presse

Country Status (5)

Country Link
US (1) US5293972A (fr)
EP (1) EP0543772A1 (fr)
JP (1) JPH07100178B2 (fr)
CN (1) CN1073380A (fr)
DE (1) DE4138286A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2782942A1 (fr) * 1998-09-09 2000-03-10 Amada Europ Sa Presse plieuse a tablier inferieur actif
EP1714760A3 (fr) * 2005-04-21 2007-08-01 Trebax S.R.L. Moule pour le pressage de carrreaux en céramique
WO2010042962A2 (fr) * 2008-10-15 2010-04-22 Trumpf Maschinen Austria Gmbh & Co. Kg. Presse à cintrer dotée d'un dispositif support pour un moyen d'entraînement
EP2210681A2 (fr) 2009-01-27 2010-07-28 Trumpf Maschinen Austria GmbH & CO. KG. Presse à plier dotée d'une barre de pressage en plusieurs parties
CN105934290A (zh) * 2013-12-04 2016-09-07 特鲁普机械奥地利有限公司及两合公司 压弯机

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4235971C1 (de) * 1992-10-26 1994-04-07 M & S Brugg Ag Brugg Abkantpresse
KR100229130B1 (ko) * 1996-08-16 1999-12-01 윤종용 냉장고의 외상 벤딩장치
DE19923217A1 (de) * 1999-05-20 2000-11-30 Walter Hommel Verfahren zum Verhindern der Durchbiegung bei Elementen, die unter Belastung stehen
FR2797407B1 (fr) * 1999-08-09 2001-11-02 Amada Europ Sa Presse plieuse a tablier inferieur muni de fentes
US6868351B1 (en) * 1999-10-19 2005-03-15 The Minster Machine Company Displacement based dynamic load monitor
ITTO20020904A1 (it) * 2002-10-17 2004-04-18 Alberto Arduino Pressa piegatrce con trave portautensile sostanzialmente
NL1029177C2 (nl) * 2005-06-02 2006-12-05 Safan Bv Pers.
AT507808B1 (de) 2009-01-27 2011-02-15 Trumpf Maschinen Austria Gmbh Biegepresse mit einem antriebsbalken und elastisch gekuppelten biegebalken
FR2942981B1 (fr) * 2009-03-13 2011-04-08 Amada Europe Presse plieuse pour le pliage de feuilles
EP2722164B1 (fr) * 2012-10-18 2017-01-18 Nivora IP B.V. Moyens formant un ressort et dispositif pour travailler un matériau en feuille
AT515153B1 (de) * 2013-12-04 2015-08-15 Trumpf Maschinen Austria Gmbh Biegemaschine
AT516493B1 (de) * 2015-02-25 2016-06-15 Trumpf Maschinen Austria Gmbh & Co Kg Abkantpresse
CN105415743B (zh) * 2015-12-25 2017-05-24 常熟市华德粉末冶金有限公司 一种垫片类粉末冶金产品的整形机构
CN110421026B (zh) * 2019-08-06 2020-10-16 青岛伟利达钢材加工配送有限责任公司 一种钢板自动化挤压弯曲成型工业机械

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1982002360A1 (fr) * 1981-01-13 1982-07-22 Huber Arthur Presse hydraulique comportant un tablier fixe et un tablier mobile
EP0125974A1 (fr) * 1983-05-05 1984-11-21 Metalurgica Burcena, Sa- Mebusa Presse à former et plus particulièrement presse plieuse
US4580434A (en) * 1983-11-14 1986-04-08 Cincinnati Incorporated Deflection compensating assembly for a press brake
US4620435A (en) * 1984-10-24 1986-11-04 Cincinnati Incorporated Deflection compensating assembly for fabricating machine tools
EP0440818A1 (fr) * 1989-08-31 1991-08-14 Kabushiki Kaisha Komatsu Seisakusho Dispositif de commande pour une presse plieuse

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA612808A (en) * 1961-01-17 The Commonwealth Engineering Company Of Ohio Brake beam compensation
US4045995A (en) * 1975-10-29 1977-09-06 Steel Structures, Inc. Fluid-mechanical drive for press brake
JPS5546329U (fr) * 1978-09-19 1980-03-26
FR2507507B1 (fr) * 1981-06-16 1986-07-04 Promecan Sisson Lehmann Dispositif de bombage d'un porte-outil d'une presse plieuse ou analogue
US4426873A (en) * 1982-04-16 1984-01-24 Canron Corporation Deflection compensating means for press brakes and the like
JPS60261623A (ja) * 1984-06-08 1985-12-24 Amada Co Ltd プレスブレ−キのたわみ補正装置
US5067340A (en) * 1988-05-05 1991-11-26 Macgregor Donald C Precision press brake
CH680773A5 (fr) * 1989-09-11 1992-11-13 Beyeler Machines Sa

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1982002360A1 (fr) * 1981-01-13 1982-07-22 Huber Arthur Presse hydraulique comportant un tablier fixe et un tablier mobile
EP0125974A1 (fr) * 1983-05-05 1984-11-21 Metalurgica Burcena, Sa- Mebusa Presse à former et plus particulièrement presse plieuse
US4580434A (en) * 1983-11-14 1986-04-08 Cincinnati Incorporated Deflection compensating assembly for a press brake
US4620435A (en) * 1984-10-24 1986-11-04 Cincinnati Incorporated Deflection compensating assembly for fabricating machine tools
EP0440818A1 (fr) * 1989-08-31 1991-08-14 Kabushiki Kaisha Komatsu Seisakusho Dispositif de commande pour une presse plieuse

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2782942A1 (fr) * 1998-09-09 2000-03-10 Amada Europ Sa Presse plieuse a tablier inferieur actif
WO2000013813A1 (fr) * 1998-09-09 2000-03-16 Amada Europe Presse plieuse a tablier inferieur actif
US6401512B1 (en) 1998-09-09 2002-06-11 Amada Europe Press brake with active lower table
EP1714760A3 (fr) * 2005-04-21 2007-08-01 Trebax S.R.L. Moule pour le pressage de carrreaux en céramique
WO2010042962A2 (fr) * 2008-10-15 2010-04-22 Trumpf Maschinen Austria Gmbh & Co. Kg. Presse à cintrer dotée d'un dispositif support pour un moyen d'entraînement
WO2010042962A3 (fr) * 2008-10-15 2010-06-10 Trumpf Maschinen Austria Gmbh & Co. Kg. Presse à cintrer dotée d'un dispositif support pour un moyen d'entraînement
US8511132B2 (en) 2008-10-15 2013-08-20 Trumpf Maschinen Austria Gmbh & Co. Kg. Bending press having support bearing device for drive means
EP2210681A2 (fr) 2009-01-27 2010-07-28 Trumpf Maschinen Austria GmbH & CO. KG. Presse à plier dotée d'une barre de pressage en plusieurs parties
CN105934290A (zh) * 2013-12-04 2016-09-07 特鲁普机械奥地利有限公司及两合公司 压弯机
CN105934290B (zh) * 2013-12-04 2018-01-12 特鲁普机械奥地利有限公司及两合公司 压弯机

Also Published As

Publication number Publication date
DE4138286A1 (de) 1993-05-27
JPH05208219A (ja) 1993-08-20
JPH07100178B2 (ja) 1995-11-01
CN1073380A (zh) 1993-06-23
US5293972A (en) 1994-03-15

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