EP0434541B1 - Hydraulische Biegepresse mit beweglichem Unterbalken - Google Patents
Hydraulische Biegepresse mit beweglichem Unterbalken Download PDFInfo
- Publication number
- EP0434541B1 EP0434541B1 EP90403636A EP90403636A EP0434541B1 EP 0434541 B1 EP0434541 B1 EP 0434541B1 EP 90403636 A EP90403636 A EP 90403636A EP 90403636 A EP90403636 A EP 90403636A EP 0434541 B1 EP0434541 B1 EP 0434541B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- torque
- cylinders
- pressure
- movable
- 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.)
- Expired - Lifetime
Links
- 238000005452 bending Methods 0.000 title claims abstract description 7
- 238000001514 detection method Methods 0.000 claims abstract description 9
- 239000003638 chemical reducing agent Substances 0.000 claims description 18
- 230000003042 antagnostic effect Effects 0.000 claims description 4
- 239000002184 metal Substances 0.000 claims description 4
- 229910052751 metal Inorganic materials 0.000 claims description 4
- 150000002739 metals Chemical class 0.000 claims description 3
- 230000015572 biosynthetic process Effects 0.000 claims 1
- 238000003786 synthesis reaction Methods 0.000 claims 1
- 238000006073 displacement reaction Methods 0.000 description 7
- 238000009826 distribution Methods 0.000 description 7
- 238000005457 optimization Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 239000010959 steel Substances 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 238000012937 correction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000011084 recovery Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000001939 inductive effect Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 230000001151 other effect Effects 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 239000000523 sample Substances 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Images
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.
- Document FR-A-1 108 366 describes a press with two hydraulic cylinders associated with a control device intended to establish a synchronous operation of these.
- This device comprises for each cylinder a device for measuring the displacement thereof associated with a directional servo-distribution by cylinder.
- the servo distributors are connected to a single pump so as to obtain the same pressure drops in the two distributors.
- control devices of this same nature with servo-distribution, on a press with three cylinders, would not allow more under conditions of eccentric load to control the parallelism of deformation of the facing edges. Indeed, the pressure 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 subject of the invention is a press brake for the deformation of sheet metals, as described in the first claim.
- 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.
- Figure 1 is a schematic front elevational view of a press brake according to the invention.
- Figure 2 is an end elevational view.
- FIGS 3 and 4 show two different embodiments of the hydraulic circuit for controlling the press brake according to the invention.
- FIG. 5 is a diagram of the control circuit for the pressure reducers provided in the hydraulic circuit, in the case where the tilting detection is carried out by measuring the strokes of the two ends of the lower deck, then by calculating the difference which represents tilting.
- 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 deck 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 latter 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 bulkhead 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 kinds: 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 circuit for controlling this press brake. This embodiment differs from the previous one by the fact that there is only one pressure reducer 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 working located on the side opposite to that on which 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 which maintain the overall parallelism and the optimization of the 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)
- Fluid-Pressure Circuits (AREA)
- Veneer Processing And Manufacture Of Plywood (AREA)
- Laminated Bodies (AREA)
- Presses And Accessory Devices Thereof (AREA)
- Glass Compositions (AREA)
Claims (3)
- Hydraulische Biegepresse für die Verformung von Metallblechen mit einem festen Oberbalken (1) und einem beweglichen Unterbalken (2), der vermittels mindestens dreier Hydraulikzylinder (5a, 5b, 5c) betätigbar ist, von denen zwei an den seitlichen Enden des beweglichen Unterbalkens (2) und mindestens einer im Zentrum entsprechend ihrer Achse angeordnet sind, mit den Hydraulikzylindern (5a, 5b, 5c), die von einem Hydraulikkreis mit einer von einem Motor (14) angestriebenen Pumpe (13) gespeist werden, einem Richtungsverteiler (12), der die Auf- und Abbewegungen des beweglichen Unterbalkens (2) steuert, einem Verschiebungsaufnehmer (16a, 16b) für das eventuelle Auftreten eines Kippmomentes des beweglichen Unterbalkens (2) und einer Auswerteeinheit (24), die mit dem Verschiebungsaufnehmer (16a, 16b) verbunden ist und Steuerausgänge (A, B, C) eines Regelsystems in Abhängigkeit von der festgestellten Kippung aufweist, wobei alle Hydraulikzylinder (5a, 5b, 5c) unter Einschaltung von Drucksteuermitteln (15a, 15b, 15c; 15) mit einem gemeinsamen Richtungsverteiler (12) verbunden sind, der von der Auswerteeinheit (24) gesteuert ist, die dazu dient, kontinuierlich den einwirkenden Druck in dem Hydraulikzylinder (5a oder 5b), der auf der entgegengesetzen Seite zur Richtung des Kippmomentes angeordnet ist, und eventuell auch in dem mittig angeordneten Hydraulikzylinder (5c) zu reduzieren, um ein Gegenmoment als Funktion der empfangenen Daten des Verschiebungsaufnehmers (16a, 16b) zu schaffen, dadurch gekennzeichnet, daß die Auswerteeinheit (24) zusätzlich einen Eingang (E) aufweist, der die Eingabe von Hilfsdaten, die die Veränderung der generellen Arbeitsbedingungen beschreiben, gestattet, und daß das Gegenmoment eine Funktion einer Synthese der Daten des Verschiebungsaufnehmers (16a, 16b) und der des Eingangs (E) ist, wobei das so erzeugte Gegenmoment geeignet ist, einerseits kontinuierlich und proportional das Kippmomemt auszugleichen, sodaß insgesamt die Parallelität erreicht wird, und andererseits die Beibehaltung der Arbeitszonen der gegenseitigen Ränder der Balken (1, 2), die sich während der Arbeit deformieren, in Parallelität zu sichern.
- Biegepresse nach Anspruch 1, dadurch gekennzeichnet, daß die Drucksteuermittel ebenso Druckminderer (15a, 15b, 15c) wie auch Hydraulikzylinder (5a, 5b, 5c), die den beweglichen Unterbalken (2) betätigen, aufweisen, und daß jeder Druckminderer je mit einem Hydraulikzylinder verbunden ist.
- Biegepresse nach Anspruch 1, dadurch gekennzeichnet, daß die Drucksteuermittel einen einzigen proportional arbeitenden Druckminderer (15) aufweisen, der in den hydraulischen Steuerkreis eingeschaltet und an jeden Hydraulikzylinder (5a, 5b, 5c) unter Zwischenschaltung eines entsprechenden Verbindungsventils (21a, 21b, 21c), welches die Betätigung des betreffenden Hydraulikzylinders gestattet, angeschlossen ist, und zwar entweder mit normalem oder mit reduziertem Steuerdruck.
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 |
---|---|---|---|
FR8916778 | 1989-12-19 | ||
FR8916778A FR2655907B1 (fr) | 1989-12-19 | 1989-12-19 | Presse plieuse hydraulique a tablier inferieur mobile. |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0434541A1 EP0434541A1 (de) | 1991-06-26 |
EP0434541B1 true 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) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2705052B1 (fr) * | 1993-05-10 | 1995-06-30 | Treillet Jean | Systeme d'equilibrage pour presse-plieuse a 3 verins et plus. |
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 |
US6959581B2 (en) * | 1999-10-20 | 2005-11-01 | Amada Company, Limited | Press brake and ram movement method for press brake |
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 |
CA2576174A1 (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 |
Family Cites Families (18)
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 |
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 |
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 |
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 |
DE2849578A1 (de) * | 1978-11-15 | 1980-05-29 | Handels Und Service Gmbh Masch | Regelung fuer einen hydraulischen pressenantrieb |
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 |
AT385466B (de) * | 1985-12-30 | 1988-04-11 | Hoerbiger Hydraulik | Gleichlaufregeleinrichtung fuer einen hydraulischen mehrzylinderantrieb |
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 |
-
1989
- 1989-12-19 FR FR8916778A patent/FR2655907B1/fr not_active Expired - Fee Related
-
1990
- 1990-12-18 CA CA002046914A patent/CA2046914A1/en not_active Abandoned
- 1990-12-18 EP EP90403636A patent/EP0434541B1/de not_active Expired - Lifetime
- 1990-12-18 BR BR909007127A patent/BR9007127A/pt not_active IP Right Cessation
- 1990-12-18 ES ES199090403636T patent/ES2046748T3/es not_active Expired - Lifetime
- 1990-12-18 WO PCT/FR1990/000918 patent/WO1991008894A1/fr active IP Right Grant
- 1990-12-18 DK DK90403636.5T patent/DK0434541T3/da active
- 1990-12-18 US US07/752,506 patent/US5243902A/en not_active Expired - Fee Related
- 1990-12-18 KR KR1019910700924A patent/KR100211550B1/ko not_active IP Right Cessation
- 1990-12-18 DE DE90403636T patent/DE69004234T2/de not_active Expired - Fee Related
- 1990-12-18 AT AT90403636T patent/ATE96375T1/de not_active IP Right Cessation
- 1990-12-18 JP JP3501847A patent/JP2505337B2/ja not_active Expired - Fee Related
- 1990-12-19 PT PT96282A patent/PT96282B/pt not_active IP Right Cessation
-
1991
- 1991-08-16 FI FI913879A patent/FI95111C/fi not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
FI95111C (fi) | 1995-12-27 |
KR100211550B1 (ko) | 1999-08-02 |
FR2655907A1 (fr) | 1991-06-21 |
EP0434541A1 (de) | 1991-06-26 |
FI913879A0 (fi) | 1991-08-16 |
FR2655907B1 (fr) | 1993-07-30 |
BR9007127A (pt) | 1991-11-26 |
DE69004234T2 (de) | 1994-05-05 |
ATE96375T1 (de) | 1993-11-15 |
FI95111B (fi) | 1995-09-15 |
KR920700897A (ko) | 1992-08-10 |
PT96282A (pt) | 1992-09-30 |
JP2505337B2 (ja) | 1996-06-05 |
WO1991008894A1 (fr) | 1991-06-27 |
PT96282B (pt) | 1998-07-31 |
CA2046914A1 (en) | 1991-06-20 |
US5243902A (en) | 1993-09-14 |
DK0434541T3 (da) | 1994-02-21 |
ES2046748T3 (es) | 1994-02-01 |
JPH04505890A (ja) | 1992-10-15 |
DE69004234D1 (de) | 1993-12-02 |
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