EP0125974A1 - Umformpresse und insbesondere Abkantenpresse - Google Patents

Umformpresse und insbesondere Abkantenpresse Download PDF

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Publication number
EP0125974A1
EP0125974A1 EP84400885A EP84400885A EP0125974A1 EP 0125974 A1 EP0125974 A1 EP 0125974A1 EP 84400885 A EP84400885 A EP 84400885A EP 84400885 A EP84400885 A EP 84400885A EP 0125974 A1 EP0125974 A1 EP 0125974A1
Authority
EP
European Patent Office
Prior art keywords
points
thrust
deck
forming
aprons
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
EP84400885A
Other languages
English (en)
French (fr)
Other versions
EP0125974B1 (de
Inventor
Alain Bertrand
Michel Celerier
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.)
METALURGICA BURCENA SA- MEBUSA
Original Assignee
METALURGICA BURCENA SA- MEBUSA
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 METALURGICA BURCENA SA- MEBUSA filed Critical METALURGICA BURCENA SA- MEBUSA
Priority to AT84400885T priority Critical patent/ATE26416T1/de
Publication of EP0125974A1 publication Critical patent/EP0125974A1/de
Application granted granted Critical
Publication of EP0125974B1 publication Critical patent/EP0125974B1/de
Expired legal-status Critical Current

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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
    • B30B15/007—Means for maintaining the press table, the press platen or the press ram against tilting or deflection
    • 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

Definitions

  • the invention relates to a forming press and more particularly to a press brake.
  • the forming presses generally comprise two aprons, one of which, called a slide, is mobile.
  • the aprons are equipped with means for carrying forming tools, the sheet being arranged between the tools of the aprons to be shaped under the combined action of the slide and the opposite fixed apron.
  • the slide is generally moved hydraulically by jacks but other pneumatic or mechanical means can obviously be used.
  • a conventional arrangement of a press brake consists in subjecting the slider to the action of two end jacks while the fixed deck rests on two supports located substantially in alignment with said jacks relative to the direction of movement of the slider.
  • the longitudinal deformation curves of the decks are substantially symmetrical with respect to the plane of separation of the decks so that the maximum difference between the decks is at near the middle of the thrust points (cylinders and fixed supports) and represents twice the maximum deformation of each deck.
  • the maximum difference between the two aprons is an important parameter of the precision of the fold produced and in the above-mentioned case the two aprons in action being more apart in the middle than at the ends, the fold will be more open in the center than in said ends,
  • central thrust To decrease the maximum distance between the two deformed aprons sets and thus improve the fold of the sheet, it was imagined to submit one of the aprons to two end cylinders or respectively two supports and the other apron to a support or respectively one or more cylinders arranged in its center ( provision hereinafter referred to as central thrust).
  • the deformations of the aprons also each in the form of an arc, are curved in the same direction and the maximum difference between the two aprons is significantly reduced since in this case the maximum difference is obtained by subtracting the arrows of each deformation curve, whereas in the case of lateral thrust, the maximum deviation was obtained by adding said arrows.
  • the maximum differences of the aprons are also a function of other factors and in particular of the inertia of the aprons. For example, for substantially equal maximum deviations between the two lateral thrust and central thrust arrangements, the inertias of the decks of the central thrust arrangement would be considerably reduced.
  • the object of the invention is to propose an arrangement which makes it possible to minimize the maximum difference between the two aprons and to reduce the maximum deformations of each deck in order to minimize the "saber" effect mentioned above.
  • reducing the maximum gap reduces the tolerance gap on the fold.
  • the invention is more particularly intended for press brakes, it also relates to all kinds of presses, for example planing, stamping etc.
  • each deck of which is subjected to thrust points, resulting from the reaction of fixed supports and / or from the direct or transmitted action of jacks is remarkable in that the distribution and the number of thrust points of each deck are such that the longitudinal deformation curve of each deck in action for forming over the entire length of the press, is wavy and symmetrical with respect to its midpoint while the two curves have maximums and minimums having substantially the same longitudinal coordinates.
  • the deformation curves are therefore wavy and no longer reduced to a single arc as before, which is a priori original compared to the goal to be achieved.
  • one of the decks is subjected to an integer number n of thrust points, at least equal to two, while the other opposite deck is subjected to (n + 1) thrust points which are offset and alternated two by two with the n thrust points of the first deck relative to parallels to the direction of movement of the movable deck, said thrust points of the two decks being arranged symmetrically relative to the median plane perpendicular to said decks.
  • the offset of the thrust points of one deck relative to the other which is a function of the length of total forming possible, and the distribution of forces on the decks are determined so as to obtain (n + 1) common points and substantially aligned on the deformation curves including the two end points, and this assuming d '' forming over the entire length of the aprons.
  • the invention further recommends that the inertia ratio between the two decks is preferably determined so as to obtain a maximum difference between the deformation curves, as small as possible.
  • the invention also provides a particular and original arrangement of the intermediate thrust points in the case of composite decks, as well as servo means, in particular for distributing the forces on the decks.
  • Figure 1 shows the principle of the invention for a so-called five-point thrust, each thrust point represented here by a double arrow which can be, as has already been said, a fixed support or the direct or indirect transmission of the action d 'a cylinder.
  • the thrust points of the upper deck are three in number symmetrically arranged and those of the opposite lower deck (i) are two.
  • the thrust points of the lower deck are offset by an A value from the end points of the upper deck and alternate with them (the value of being a proportional function of 2L).
  • the curves 2a to 2d correspond of course to mathematical functions which make it possible to study the maximum difference (Emax) between the two curves.
  • the value L will be imposed by requirements (folding capacity equal to 2L) and if it is not possible then to choose exactly the values of k, J and ⁇ , determined above, according to the other manufacturing constraints (total weight, cost, etc.) it will always be possible to determine the best value (s) for one or two parameters as a function of the value (s) set for the others, all the more so as the results obtained exceed the expectation of agreement between the calculation and the material tolerances.
  • FIGS. 2c and 2d clearly show, moreover, that the fact of imposing an alignment at the three points 0, M and 0 ′ requires that the axis of the sheet which would happen to be disposed between the decks, to be brought back to the vicinity of the straight line (it is clear that the curves of FIGS. 2a to 2d are shown without regard to the sheet).
  • the inertia (Ii, Is) of each deck was assumed to be constant throughout said deck but it is conceivable to further improve the device by imagining a variation of inertia along the length of at least one of the decks to bring its deformation curve as close as possible to the straight line and / or further reduce the maximum difference between the deformation curves.
  • the movable apron or slide can be both the lower apron and the upper apron, these can also be monobloc or composite.
  • the pushing points can be push cylinders, cambering or correction cylinders or fixed supports.
  • Figure 3 shows a possible embodiment.
  • the slide 1 and the fixed deck 2 are mounted in a frame formed by two flanges 3 and 4 joined together notably by a bracing beam 5 also serving as distribution box.
  • the slider 1 slides with the aid of transverse and longitudinal guide means which are not more particularly shown.
  • the slide 1 is in this example, a composite deck and comprises a central core 6 to which two lateral cheeks 7, 8 are placed, arranged on either side of the core 6.
  • the fixed deck 2 is composed in substantially the same way by a central core 11 secured to two cheeks 12 and 13 by means of pins or pins 14, 15.
  • the slide 1 is moved by jacks 16 and 17 arranged at its ends and in such a way that they act on the cheeks 7 and 8 of the slide and therefore, by reaction of the pins 9 and 10, on the central core 6, which as the drawing shows, goes beyond said cheeks so that it will act on the sheet to be folded by means of a tool with which it will be equipped.
  • the cylinders 16 and 17 are double and the central thrust axes pass through the pins 9 and 10.
  • the cheeks 12 and 13 of the deck 2 have on the top a beam 18 intended to receive the tool combined with that carried by the slide so that here the force is transmitted by the pins 14 and 15 to the central core 11 assumed to be fixed.
  • the central part of the slide (in the direction of its largest dimension) has a hole in which a cambering cylinder 19 is arranged.
  • This cylinder 19 is arranged so as to urge the core cen trale 6 of the slide by resting on the cheeks 7 and 8 (it could be the reverse with working cheeks 7 and 8).
  • the jack 19 could for example be placed in a notch of said apron and bear on the beam 5.
  • FIG. 4 schematically shows, by way of example at least in part, such an assembly.
  • the slide 1 the fixed deck 2, the frame flanges 3 and 4 , the thrust cylinders 16, 17 and the camber cylinder 19.
  • the jacks 16, 17 and 19 are controlled by servo valves S1, S2, and S3 respectively supplied by pumps P1, P2 and auxiliary pumps Pa.
  • Electronic and / or mechanical and / or hydraulic logic takes information from control means such as the pedal shown diagrammatically in Pc, from data entry means (instructions) and from measurement means in the form of sensors.
  • control means such as the pedal shown diagrammatically in Pc
  • data entry means instructions
  • measurement means in the form of sensors.
  • force F1, F2 which permanently measure the bending force actually applied and its preparation with respect to the plane of symmetry of the press
  • position sensors Cl, C2 which permanently measure the relative positions of the ends of the deck 2 and of the slide 1
  • a moment sensor M which permanently measures the bending moment in the center of the slide and which will be discussed in more detail below (the oblique arrows shown in the drawing represent the connection with the logic).
  • the pedal Pc controls via the above-mentioned logic and the valves SI and S2: the advance, stop and return of the slide 1.
  • the data or instructions are entered by the logic input unit and relate to the nature, thickness and possibly the length of the sheet as well as the characteristics of the fold to be obtained (angle of the fold, dimensions of the tooling. ..) so as to determine a folding depth and therefore an end position of the slide.
  • the logic processing unit uses the instructions given and the information received from the measurement means to modulate the controls of the servo valves.
  • the force F to be applied depends on the characteristics of the sheet (nature of the metal, thickness, length). This force F is generally determined by means of charts, or by calculation in the case of certain numerical controls, and then preset on the machine.
  • the force sensors F1 and F2 which measure the distribution of the thrusts and which are arranged in the flanges of the frame or the pins or elsewhere (jacks, etc.) thus deliver two pieces of information to the logic which are the total force d, folding-F and, by difference, the eccentricity of the thrust.
  • the logic By acting on Sl, 52 the logic thus controls the conformity of the real bending force with respect to the calculated theoretical value and the parallelism of execution of the fold. It can however be noted here that it is always the position sensors C1, C2 which serve as a servo reference for the parallelism, the offset data being used elsewhere.
  • the length of the sheet to be bent can be displayed and entered by the logic as already said, but it is particularly interesting and original to determine it by means of the sensor M, the measurements of which are a function of said bending length, of the force F and eccentricity.
  • the logic can easily, from the information from the sensor M, deduce the value of k therefrom.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)
  • Shaping Of Tube Ends By Bending Or Straightening (AREA)
EP84400885A 1983-05-05 1984-05-02 Umformpresse und insbesondere Abkantenpresse Expired EP0125974B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84400885T ATE26416T1 (de) 1983-05-05 1984-05-02 Umformpresse und insbesondere abkantenpresse.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8307535 1983-05-05
FR8307535A FR2545418B1 (fr) 1983-05-05 1983-05-05 Presse a former, et plus particulierement presse plieuse

Publications (2)

Publication Number Publication Date
EP0125974A1 true EP0125974A1 (de) 1984-11-21
EP0125974B1 EP0125974B1 (de) 1987-04-08

Family

ID=9288633

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84400885A Expired EP0125974B1 (de) 1983-05-05 1984-05-02 Umformpresse und insbesondere Abkantenpresse

Country Status (6)

Country Link
EP (1) EP0125974B1 (de)
JP (1) JPS6046821A (de)
AT (1) ATE26416T1 (de)
CA (1) CA1252377A (de)
DE (1) DE3463006D1 (de)
FR (1) FR2545418B1 (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0543772A1 (de) * 1991-11-21 1993-05-26 M + S Brugg Ag Presse
GB2226515B (en) * 1988-12-29 1993-06-02 Amada Co Ltd Sheet workpiece bending machine
EP0544137A2 (de) * 1991-11-25 1993-06-02 Umformtechnik ERFURT GmbH Tisch- und/oder Stösselbaugruppe einer Umformmaschine
FR2708219A1 (fr) * 1993-07-27 1995-02-03 Amada Europ Sa Procédé de compensation des déformations des tabliers de presses hydrauliques, tabliers et presses hydrauliques ainsi équipés.
AT507946B1 (de) * 2009-03-13 2011-10-15 Amada Europ Sa Abkantpresse zum biegen von folien
DE102011116085A1 (de) * 2011-10-12 2013-04-18 Weinbrenner Maschinenbau Gmbh Biegemaschine

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0824963B2 (ja) * 1985-09-06 1996-03-13 株式会社アマダ 折曲機械のラム駆動制御装置
JP4601841B2 (ja) * 2001-02-26 2010-12-22 株式会社アマダエンジニアリングセンター プレスブレーキ

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1200920A (fr) * 1958-07-01 1959-12-24 Dispositif pour la compensation et le contrôle des déformations subies par les parties actives de presses ou machines analogues
FR1240703A (fr) * 1959-07-31 1960-09-09 Achard Perfectionnements aux presses à plier
CH378832A (de) * 1960-03-24 1964-06-30 Lanfranconi Domenico Einrichtung zum Steuern hydraulischer Arbeitsmaschinen mit mehreren Presszylindern
DE1527979A1 (de) * 1966-07-14 1971-11-04 Karl Guerr Abkantpresse
US3677009A (en) * 1970-11-12 1972-07-18 Kelso Marine Inc Control arrangement for the male die of a hydraulic press brake
FR2294776A1 (fr) * 1974-12-18 1976-07-16 Siempelkamp Gmbh & Co Presse hydraulique a plier les toles
WO1982002360A1 (fr) * 1981-01-13 1982-07-22 Huber Arthur Presse hydraulique comportant un tablier fixe et un tablier mobile

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2347992A1 (fr) * 1976-04-13 1977-11-10 Promecan Sisson Lehmann Presse plieuse ou machine analogue

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1200920A (fr) * 1958-07-01 1959-12-24 Dispositif pour la compensation et le contrôle des déformations subies par les parties actives de presses ou machines analogues
FR1240703A (fr) * 1959-07-31 1960-09-09 Achard Perfectionnements aux presses à plier
CH378832A (de) * 1960-03-24 1964-06-30 Lanfranconi Domenico Einrichtung zum Steuern hydraulischer Arbeitsmaschinen mit mehreren Presszylindern
DE1527979A1 (de) * 1966-07-14 1971-11-04 Karl Guerr Abkantpresse
US3677009A (en) * 1970-11-12 1972-07-18 Kelso Marine Inc Control arrangement for the male die of a hydraulic press brake
FR2294776A1 (fr) * 1974-12-18 1976-07-16 Siempelkamp Gmbh & Co Presse hydraulique a plier les toles
WO1982002360A1 (fr) * 1981-01-13 1982-07-22 Huber Arthur Presse hydraulique comportant un tablier fixe et un tablier mobile

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2226515B (en) * 1988-12-29 1993-06-02 Amada Co Ltd Sheet workpiece bending machine
EP0543772A1 (de) * 1991-11-21 1993-05-26 M + S Brugg Ag Presse
EP0544137A2 (de) * 1991-11-25 1993-06-02 Umformtechnik ERFURT GmbH Tisch- und/oder Stösselbaugruppe einer Umformmaschine
EP0544137A3 (en) * 1991-11-25 1993-06-30 Umformtechnik Erfurt Gmbh Table or ram assembly for a forming machine
FR2708219A1 (fr) * 1993-07-27 1995-02-03 Amada Europ Sa Procédé de compensation des déformations des tabliers de presses hydrauliques, tabliers et presses hydrauliques ainsi équipés.
AT507946B1 (de) * 2009-03-13 2011-10-15 Amada Europ Sa Abkantpresse zum biegen von folien
DE102011116085A1 (de) * 2011-10-12 2013-04-18 Weinbrenner Maschinenbau Gmbh Biegemaschine

Also Published As

Publication number Publication date
DE3463006D1 (en) 1987-05-14
CA1252377A (fr) 1989-04-11
FR2545418B1 (fr) 1986-11-07
JPS6046821A (ja) 1985-03-13
ATE26416T1 (de) 1987-04-15
FR2545418A1 (fr) 1984-11-09
EP0125974B1 (de) 1987-04-08

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