EP0434541A1 - Hydraulische Biegepresse mit beweglichem Unterbalken - Google Patents

Hydraulische Biegepresse mit beweglichem Unterbalken Download PDF

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Publication number
EP0434541A1
EP0434541A1 EP19900403636 EP90403636A EP0434541A1 EP 0434541 A1 EP0434541 A1 EP 0434541A1 EP 19900403636 EP19900403636 EP 19900403636 EP 90403636 A EP90403636 A EP 90403636A EP 0434541 A1 EP0434541 A1 EP 0434541A1
Authority
EP
European Patent Office
Prior art keywords
deck
pressure
movable
torque
comparator
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
EP19900403636
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English (en)
French (fr)
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EP0434541B1 (de
Inventor
Jean Plazenet
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.)
Amada Europe SA
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Amada Europe SA
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Publication date
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Application filed by Amada Europe SA filed Critical Amada Europe SA
Priority to AT90403636T priority Critical patent/ATE96375T1/de
Publication of EP0434541A1 publication Critical patent/EP0434541A1/de
Application granted granted 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
    • 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
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/24—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam

Definitions

  • the present invention relates to hydraulic press brakes for the deformation of sheet metals.
  • press brakes of the type comprising a fixed upper deck and a movable lower deck actuated by at least three hydraulic cylinders, two of which are arranged at the lateral ends of the movable deck and at least one in the center, these cylinders being supplied from a unique directional distribution system controlling the up and down movements of the mobile platform.
  • the type of machine to which the invention applies according to the present application is very specific. In fact, it uses a single pressure source, a single distribution for controlling the movements and at least three working jacks, at least one of which is placed in the center.
  • the techniques used to date usually relate to presses with two upper cylinders and involve a servo-distribution member per cylinder fitted to the machine.
  • the pressure built up in the cylinder is solely as a function of the reaction of the work opposed to the movement of this cylinder, the servo-distributor controlling a volume of oil supplying the cylinder.
  • control devices of this same nature with servo-distribution, on a press with three jacks, would not allow more under eccentric load conditions to control the parallelism of deformation of the facing edges. Indeed, the pressure being established in each cylinder is only a function of the force exerted by the work in front of this cylinder and nothing under these conditions allows to act voluntarily on these pressures and therefore on the deformations .
  • US Patent 2,343,167 offers a different approach to the recovery of eccentric forces.
  • This patent enslaves the overall parallelism of the work platform, or mobile working apron, to the position of a mobile reference element.
  • This reference element not being subjected to any work effort, it completely disregards the concept of parallel deformed shapes.
  • the hydraulic balancing device uses a variable throttle member preset by the operator during preliminary tests, and therefore does not automatically adapt as needed to overcome eccentricity.
  • the preset is an all-or-nothing adjustment controlled by microswitches.
  • FR 2,545,418 basically relates to the search for the optimization of the parallelism of the faces opposite the aprons and clearly highlights the importance thereof.
  • FR 2,545,418 implements to obtain this result additional support points of one of the decks carried by auxiliary crosspieces in the same way as French patent 2,347,992, and adds one or more additional camber cylinders of the 'other deck, carried themselves by auxiliary crosspieces.
  • the present application relates to a hydraulic circuit making it possible, while retaining this basic configuration of these folding machines, to keep them whatever the working conditions centered or eccentric, the overall parallelism of the lower and upper decks as well that the optimization of the parallelism of the faces opposite these aprons.
  • the object of the invention is to control the force exerted by each of the jacks acting on the movable bulkhead to ensure on the one hand the overall parallelism and on the other hand, by acting on the force applied by each of the jacks for the same value of opposing torque, to generate a deformation curve of the movable lower deck, thus ensuring optimal parallel deformation of the two decks.
  • the invention relates to a press brake for the deformation of sheet metals, comprising a fixed upper deck and a movable lower deck actuated by at least three hydraulic cylinders, two of which are arranged at the lateral ends of the movable deck and at least one in the center.
  • the cylinders being supplied from a hydraulic circuit comprising a pump driven by a motor, a directional distributor controlling the movements of raising and lowering of the movable platform, a device for detecting the possible presence of a tilting torque on the movable deck, and a comparator and computer system connected to the detection device and comprising control outputs of a regulation system according to the detected tilting, characterized in that all the jacks are connected to a common directional distributor by means of pressure control means controlled by the sy stema comparator and calculator, the latter being capable of controlling a continuous reduction of the pressure exerted on the jack situated on the side opposite to the direction of the tilting torque, and possibly also on the jack situated in the center, so as to create a torque antagonistic as a function of the data received from the detection device, this antagonistic couple being capable on the one hand of counterbalancing in a continuous and proportional manner the tilting torque thus guaranteeing the overall parallelism and on the other hand ensuring the maintenance in parallel work areas on
  • the means provided for ensuring pressure control on one or more of the jacks, actuating the movable lower bulkhead, can give rise to different embodiments.
  • the device for detecting any tilting of the movable apron as well as the comparator and calculator device can be the subject of various embodiments.
  • the press brake shown in Figures 1 and 2 is of the type comprising a fixed upper deck 1 and a movable lower deck 2.
  • the upper deck is carried by a frame comprising two transverse flanges 3.
  • this apron 2 is actuated by three single-acting hydraulic cylinders arranged symmetrically with respect to the median vertical axis XY of the machine. Two of these jacks 5a and 5b are arranged near one and the other end sides of the deck 2. As for the third jack 5c, it is placed in the center along the axis XY. These cylinders are supported on the vertical panels 4 of the machine frame and they are intended to ensure the vertical displacements of the deck 2 and to apply the desired working force therefrom from bottom to top, when bending a sheet 7 between two tools adapted to this press, in this case a punch 8 carried by the fixed upper deck 1 and a die 9 carried by the movable lower deck 2.
  • This last deck is guided by four pairs of rollers 10 mounted freely rotatable on it and which are placed in contact with vertical guide tracks provided respectively on a fixed spacer 11 secured to the crosspieces 4 of the frame, and on the fixed body of the central jack 5c .
  • the three jacks 5a, 5b, 5c are supplied from a directional distributor 12 as can be seen by referring to the diagram of the hydraulic control circuit, which is shown in FIG. 3.
  • This circuit also includes a pump 13 driven by a motor 14.
  • the movement of the distributor slide 12 in one direction or the other makes it possible to move the lower apron 2 up or down, this latter movement being effected by the action of the weight of the apron.
  • the present hydraulic circuit further comprises pressure control means in the form of proportional pressure reducers 15a, 15b and 15c in number equal to the working cylinders of the movable deck.
  • pressure control means in the form of proportional pressure reducers 15a, 15b and 15c in number equal to the working cylinders of the movable deck.
  • Each of these pressure reducers is associated with one of these cylinders, as shown in the diagram in FIG. 3. Consequently by acting on one and / or the other of these reducers, it is possible to reduce continuously the control pressure of the corresponding jack (s).
  • a detection device is also provided for detecting any tilting of the movable lower deck 2 when using this press.
  • this device is designed to be able to detect both the appearance of such a tilting and the direction thereof.
  • the detection device thus provided is constituted by two linear displacement sensors, provided at one and the other end of the lower deck 2.
  • These sensors designated by the general references 16a and 16b, can be digital sensors with optical reading, or analog sensors with inductive, potentiometric or other effect.
  • each of these sensors has a movable index 22 carried by the deck 2 and which moves opposite a fixed vertical strip 23 secured to one of the crosspieces 4 of the frame, or vice vice versa.
  • Each of these sensors is therefore capable of measuring the displacement stroke of the corresponding end of the movable platform 2.
  • Each of these two sensors is capable of emitting an electrical signal which is a function of the extent of the displacement measured.
  • these two sensors are connected to an electronic circuit comprising a comparator and computer system 24 to which they are connected (see FIG. 5) and which comprises power outputs A, B and C connected to the control members of the reducers 15a, 15b, 15c .
  • the comparator / calculator is able to determine if there is displacement identity or if on the contrary there is a difference corresponding to a tilting of the lower deck 2. This comparator is then able to determine both the importance of the torque of tilting, and the meaning of it.
  • the comparator and computer 24 has an input E through which the data are entered. defining the general working conditions. This instruction can be carried out during programming if the entry of information is entirely manual as is generally the case on a numerical control, and / or at the start of the work operation if the entry of information is obtained by a system. probe, microswitches or any other form of sheet metal presence detectors or force zones such as strain gauges.
  • the working conditions are differentiated by the nominal position of the sheet, that is to say that which does not take into account positioning errors, by its length, its thickness and the type of tool used. It should be considered that this information is part of that usually communicated to the digital control of the press brake when fitted; in this case, only one transfer of information takes place via input E from the digital control.
  • the folding can be normal, centered with the simple possibility of accidental off-centering, it can be partially off-center or include operations of different natures: folding, punching or striking which can be carried out on tool units, some of which are strongly off-center.
  • the deformations of the aprons are essentially a function of the nature of these working conditions. This is why the comparator and computer must take account of the information supplied at the input E, in addition to that received from the sensors 16a and 16b to calculate the magnitude of the signals supplied to the outputs A, B, C and transmitted to the reducers 15a, 15b, 15c, respectively to the reduction gear 15 and to the connection valves 21a, 21b, 21c according to an embodiment described with reference to FIG. 4.
  • These orders can be in particular either the metered supply of output A alone or the differentiated supply of outputs A and C for the tilting in one direction, either the metered supply of output B alone, or the differentiated supply of outputs B and C for tilting in the other direction.
  • FIG. 4 shows another embodiment of the hydraulic control circuit of this press brake. This embodiment differs from the previous one in that only one pressure reducer is designated, designated by the general reference 15.
  • the hydraulic circuit for controlling the three cylinders 5a, 5b and 5c is arranged so that it is possible to apply to each cylinder, either the normal pressure coming from the pump 13, or a reduced pressure, the value of which is determined by the single reducer 15.
  • three connection valves 21a, 21b and 21c are provided, each of which is associated with one of the jacks and makes it possible to apply to it either the normal pressure or the reduced pressure determined by the reducer 15.
  • connection valves 21a, 21b and 21c are connected, like the pressure reducer (15), to the comparator-computer.
  • this comparator-computer simultaneously supplies the pressure reducer (15) and two of the valves 21a, 21b, 21c, to cause a reduction in pressure on the central jack and the jack work located on the side opposite to that where off-center work is carried out. This creates an antagonistic couple counterbalancing the tilting torque and restoring overall parallelism.
  • the device for detecting the appearance of a tilting torque on the movable lower bulkhead could be produced differently from what is provided in the case of the two examples described above where monitoring of a difference in displacement of one end of the movable deck relative to the other.
  • a detection system comprising several strain gauges suitably arranged to detect differences in forces exerted on one and the other parts of the movable deck. The strain gauges thus provided would then be connected to a comparator / calculator circuit making it possible to determine both the appearance of a difference between the forces exerted and the direction of this difference.
  • the pressure reducing means could also be produced in a different way provided that these make it possible to achieve a pressure reduction, not globally for all of the working cylinders of the movable lower bulkhead, but for each of these jacks taken alone or more of them.
  • the present invention thus makes it possible to preserve the structure of the machines comprising a single pressure source, a single distribution for controlling the movements, and at least three working jacks, one of which at least disposed in the center, this under the general conditions of mechanical production. of these machines while allowing centered or eccentric work under conditions that maintain overall parallelism and the optimization of parallelism of the faces opposite the upper and lower decks.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Control Of Presses (AREA)
  • Press Drives And Press Lines (AREA)
  • Veneer Processing And Manufacture Of Plywood (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Glass Compositions (AREA)
  • Laminated Bodies (AREA)
  • Fluid-Pressure Circuits (AREA)
EP90403636A 1989-12-19 1990-12-18 Hydraulische Biegepresse mit beweglichem Unterbalken Expired - Lifetime EP0434541B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90403636T ATE96375T1 (de) 1989-12-19 1990-12-18 Hydraulische biegepresse mit beweglichem unterbalken.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8916778A FR2655907B1 (fr) 1989-12-19 1989-12-19 Presse plieuse hydraulique a tablier inferieur mobile.
FR8916778 1989-12-19

Publications (2)

Publication Number Publication Date
EP0434541A1 true EP0434541A1 (de) 1991-06-26
EP0434541B1 EP0434541B1 (de) 1993-10-27

Family

ID=9388669

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90403636A Expired - Lifetime EP0434541B1 (de) 1989-12-19 1990-12-18 Hydraulische Biegepresse mit beweglichem Unterbalken

Country Status (14)

Country Link
US (1) US5243902A (de)
EP (1) EP0434541B1 (de)
JP (1) JP2505337B2 (de)
KR (1) KR100211550B1 (de)
AT (1) ATE96375T1 (de)
BR (1) BR9007127A (de)
CA (1) CA2046914A1 (de)
DE (1) DE69004234T2 (de)
DK (1) DK0434541T3 (de)
ES (1) ES2046748T3 (de)
FI (1) FI95111C (de)
FR (1) FR2655907B1 (de)
PT (1) PT96282B (de)
WO (1) WO1991008894A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2705052A1 (fr) * 1993-05-10 1994-11-18 Treillet Jean Système d'équilibrage pour presse-plieuse à 3 vérins et plus.

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2727954B2 (ja) * 1994-03-03 1998-03-18 トヨタ自動車株式会社 プレス装置
JP2812201B2 (ja) * 1994-07-15 1998-10-22 トヨタ自動車株式会社 プレス装置
JP3060908B2 (ja) * 1994-12-21 2000-07-10 トヨタ自動車株式会社 プレス機械の均圧装置
US6246922B1 (en) 1998-04-17 2001-06-12 Hydro-Cam Engineering Company Automatic computer controlled programmable multi-purpose apparatus to produce variable design stampings
US6250216B1 (en) 1999-03-19 2001-06-26 The Minster Machine Company Press deflection controller and method of controlling press deflection
DE60022074T2 (de) * 1999-10-20 2006-02-02 Amada Co., Ltd., Isehara Abkantpresse und bewegungsverfahren des kolbens einer abkantpresse
JP3689010B2 (ja) 2001-03-15 2005-08-31 株式会社放電精密加工研究所 プレス機
JP4343574B2 (ja) * 2003-04-15 2009-10-14 株式会社放電精密加工研究所 プレス成形機
DE10340794B4 (de) * 2003-09-02 2012-08-16 Ise Automotive Gmbh Folgewerkzeug zum Herstellen eines komplex geformten und mit Öffnungen in verschiedenen Ebenen versehenen Bauteils
WO2006017638A2 (en) * 2004-08-04 2006-02-16 The Coe Manufacturing Company Platen press
DE102012100325C5 (de) * 2012-01-16 2019-06-19 Schuler Pressen Gmbh Verwendung von Daten des Kraftflusses in einer Presse für den Betrieb eines Stößels
DE102012108933B4 (de) * 2012-09-21 2019-08-08 Schuler Pressen Gmbh Verfahren zum Betreiben einer Werkzeugmaschine oder Arbeitsmaschine und danach ausgeführte Werkzeugmaschine oder Arbeitsmaschine mit einer Verbindungsanordnung für ein Hubelement
IT201800020791A1 (it) * 2018-12-21 2020-06-21 Bystronic Laser Ag Panel bending machine with a system for maintaining the parallelism of the movable members and a respective method

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2343167A (en) * 1941-06-21 1944-02-29 Hydraulic Dev Corp Inc Press leveling means
FR1108366A (fr) * 1954-07-02 1956-01-12 Servomecanismes Electroniques Perfectionnements aux systèmes de commande de vérins
FR1497961A (fr) * 1966-10-27 1967-10-13 Schweizerische Lokomotiv Procédé pour imposer la marche en synchronisme à des pistons de travail mus hydrauliquement
US3469435A (en) * 1966-08-08 1969-09-30 Niagara Machine & Tool Works Level control for hydraulic press brakes and the like
DE2849578A1 (de) * 1978-11-15 1980-05-29 Handels Und Service Gmbh Masch Regelung fuer einen hydraulischen pressenantrieb
EP0231735A1 (de) * 1985-12-30 1987-08-12 HOERBIGER HYDRAULIK GmbH Gleichlaufregeleinrichtung für einen hydraulischen Mehrzylinderantrieb

Family Cites Families (12)

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Publication number Priority date Publication date Assignee Title
US3129625A (en) * 1963-01-07 1964-04-21 Niagara Machine & Tool Works Level and slope control for reciprocating machines
FR1362471A (fr) * 1963-02-28 1964-06-05 Promecam Ets Perfectionnements aux presses plieuses
FR1539817A (fr) * 1967-07-26 1968-09-20 Promecam Sisson Lehmann Soc Machine hydraulique pour la déformation de métaux en feuilles
JPS518232B1 (de) * 1969-09-12 1976-03-15
US4148203A (en) * 1977-10-07 1979-04-10 Dreis & Krump Mfg. Co. Computer-controlled press brake
GB2076324B (en) * 1980-05-26 1985-06-19 Amada Co Ltd Hydraulic presses
JPS5922109A (ja) * 1982-07-29 1984-02-04 Uchida Yuatsu Kiki Kogyo Kk ３本のシリンダの同調制御方法
US4608852A (en) * 1983-08-24 1986-09-02 Amada Company, Limited Press machine
US4784058A (en) * 1986-08-13 1988-11-15 Kabushiki Kaisha Kobe Seiko Sho Press control for maintaining a level position and a uniform pressure on a workpiece
US4819467A (en) * 1986-09-17 1989-04-11 Cincinnati Incorporated Adaptive control system for hydraulic press brake
CA1275892C (en) * 1986-10-10 1990-11-06 Ronald Ballantyne Hydraulic cylinder device for platen spacing indication and control
US4923383A (en) * 1987-12-26 1990-05-08 Kabushiki Kaisha Kobe Seiko Sho Apparatus for mold aligning in a compression molding machine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2343167A (en) * 1941-06-21 1944-02-29 Hydraulic Dev Corp Inc Press leveling means
FR1108366A (fr) * 1954-07-02 1956-01-12 Servomecanismes Electroniques Perfectionnements aux systèmes de commande de vérins
US3469435A (en) * 1966-08-08 1969-09-30 Niagara Machine & Tool Works Level control for hydraulic press brakes and the like
FR1497961A (fr) * 1966-10-27 1967-10-13 Schweizerische Lokomotiv Procédé pour imposer la marche en synchronisme à des pistons de travail mus hydrauliquement
DE2849578A1 (de) * 1978-11-15 1980-05-29 Handels Und Service Gmbh Masch Regelung fuer einen hydraulischen pressenantrieb
EP0231735A1 (de) * 1985-12-30 1987-08-12 HOERBIGER HYDRAULIK GmbH Gleichlaufregeleinrichtung für einen hydraulischen Mehrzylinderantrieb

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2705052A1 (fr) * 1993-05-10 1994-11-18 Treillet Jean Système d'équilibrage pour presse-plieuse à 3 vérins et plus.
WO1994026510A1 (fr) * 1993-05-10 1994-11-24 Jean Treillet Systeme d'equilibrage pour presse-plieuse

Also Published As

Publication number Publication date
JPH04505890A (ja) 1992-10-15
DK0434541T3 (da) 1994-02-21
ES2046748T3 (es) 1994-02-01
DE69004234D1 (de) 1993-12-02
FR2655907A1 (fr) 1991-06-21
FI95111B (fi) 1995-09-15
US5243902A (en) 1993-09-14
PT96282A (pt) 1992-09-30
ATE96375T1 (de) 1993-11-15
EP0434541B1 (de) 1993-10-27
DE69004234T2 (de) 1994-05-05
KR100211550B1 (ko) 1999-08-02
KR920700897A (ko) 1992-08-10
PT96282B (pt) 1998-07-31
JP2505337B2 (ja) 1996-06-05
WO1991008894A1 (fr) 1991-06-27
BR9007127A (pt) 1991-11-26
FR2655907B1 (fr) 1993-07-30
FI913879A0 (fi) 1991-08-16
CA2046914A1 (en) 1991-06-20
FI95111C (fi) 1995-12-27

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