EP0333052B1 - Appareil d'étirage pour la déformation de côles - Google Patents

Appareil d'étirage pour la déformation de côles Download PDF

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Publication number
EP0333052B1
EP0333052B1 EP89104248A EP89104248A EP0333052B1 EP 0333052 B1 EP0333052 B1 EP 0333052B1 EP 89104248 A EP89104248 A EP 89104248A EP 89104248 A EP89104248 A EP 89104248A EP 0333052 B1 EP0333052 B1 EP 0333052B1
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EP
European Patent Office
Prior art keywords
pressure
piston
cylinder
pressure medium
line
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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
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EP89104248A
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German (de)
English (en)
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EP0333052A3 (en
EP0333052A2 (fr
Inventor
Erhardt Reitter
Karl Hehl
Herbert Dipl.-Ing. Kraibühler
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Individual
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Individual
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Priority to AT89104248T priority Critical patent/ATE91653T1/de
Publication of EP0333052A2 publication Critical patent/EP0333052A2/fr
Publication of EP0333052A3 publication Critical patent/EP0333052A3/de
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Publication of EP0333052B1 publication Critical patent/EP0333052B1/fr
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    • 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
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/10—Devices controlling or operating blank holders independently, or in conjunction with dies
    • B21D24/14—Devices controlling or operating blank holders independently, or in conjunction with dies pneumatically or hydraulically

Definitions

  • the invention relates to a drawing tool according to the preamble of claim 1.
  • Every change is triggered by a negative criterion, such as the risk of tearing on the drawing part, that the drawing speed is too low and brings the corresponding hydraulic elements into or out of action.
  • Changes in the sheet holding force, the pulling force and the pulling speed can also be alternated in order to achieve a rapid and at the same time energy-saving pulling process during this pulling process.
  • the basic requirements for a controlled discharge of pressure medium from the cylinder spaces of the hydraulic unit into a pressure accumulator or into the pressure medium reservoir as well as for re-feeding into the cylinder spaces from a pressure accumulator are present, whereby further possibilities of influencing the drawing process can be developed.
  • a drawing process or a time segment thereof can take place with the drawing ring stationary or with the drawing punch stationary.
  • a further embodiment according to claim 3 ensures that, with the construction of the hydraulic unit being favorable in terms of production engineering, the drawing tool can be returned to its starting position from the cylinder space delimited by the central piston after the drawing process has been completed.
  • the oil which is necessarily displaced from this cylinder chamber can be fed into the rear cylinder chamber of the working piston to accelerate the drawing process.
  • the sheet holding force can be adjusted in accordance with the respective drawing technical requirements before the start and during the drawing process by appropriately presetting the pressure of the pressure limiting valve 36, the optimum initial sheet holding force having been empirically determined beforehand.
  • the pressure in the hydraulic system is reduced thanks to the pressure booster if there is a risk of the pulling part tearing off.
  • a flow path change corresponding to the respective drawing-technical requirements leads to an optimization of the drawing process with regard to energy saving and drawing speed, while avoiding any risk of tearing off, the limiting pressures or cross-sections to be preset on the pressure-limiting valve and on the throttle valve generally being empirically determined beforehand.
  • the drawing speed can be increased with a corresponding adjustment of the sheet holding force.
  • the drawn part can be produced by opening the third flow path to the pressure accumulator while the drawing piston is stationary. If the flow path is only opened temporarily, there is a corresponding temporary pressure drop via the hydraulic system.
  • the drawing process can take place with the ring piston at a standstill.
  • the drawing tool is used for forming preferably flat sheets, for example in containers, pots, sinks and the like.
  • An external driving force A acts on the drawing tool from outside for forming. It usually comes from a hydraulic press, the press head of which drives the drawing ring 18 of the drawing tool. Together with the drawing ring 18, a sheet metal holder 15 is moved during the forming process.
  • a circuit board 47 is clamped between the drawing ring and the sheet metal holder at the beginning of the drawing process.
  • a drawing die arranged coaxially in the sheet metal holder can be moved into the drawing ring 18.
  • the movement of the movement unit 18, 15 carrying the respective circuit board 47 can be converted into a simultaneous but opposite movement of the drawing punch 17 with the aid of a hydraulic unit H of the drawing tool.
  • the hydraulic unit H comprises a central working piston 12, an annular piston 13 enclosing it and a cylinder 10d enclosing the annular piston, which is part of a cylinder housing 10 of the hydraulic unit H.
  • the annular piston 13, which can be driven indirectly by the driving force A, can be supported on the pressure medium of a cylinder space 48.
  • the working piston 12, which is designed as a differential piston, can be acted upon with pressure medium on both sides.
  • the pressure medium displaced from the cylinder space 48 during the drawing process by the annular piston 13 drives the working piston at least temporarily during the drawing process.
  • Cylinder spaces 51, 52 and 48 delimited from the base of the cylinder housing 10 are hydraulically separated from one another by a separation sleeve 10a projecting from this base.
  • the annular piston 13 guided on the cylinder 10d of the cylinder housing 10 is guided on the working piston 12 by means of a radial flange 13a which overlaps the separating sleeve 10a.
  • the inner circumferential surface 13b of the annular piston 13 is located at a distance from the outer circumferential surface of the separating sleeve 10a.
  • the working piston 12 which can be acted upon from the rear from the cylinder space 51 can be acted upon in the opposite manner from a cylinder space 49 which lies in a central recess of the cup-shaped working piston 12.
  • the cylinder chamber 49 is delimited by a central piston 10c anchored in the base of the cylinder housing 10 and an annular part 12b screwed to the working piston 12.
  • the ring part 12b encloses the shaft 10b of the central, stationary piston 10c sealing.
  • the rear cylinder space 51 communicates with a further cylinder space 52. This is delimited by the bottom 12a of the working piston 12 and by the central piston 10c.
  • the drawing punch 17 is received by the working piston 12 via a cylindrical intermediate piece 17a.
  • An adapter ring 14 between the sheet metal holder 15 and the upper edge of the annular piston 13 serves to transmit the driving force from the sheet metal holder 15 to the annular piston 13.
  • a knife ring 16 is arranged to be displaceable to a limited extent. When the remaining blank is bent from the edge of the finished drawn part, this knife ring 16 interacts with stationary stops 16a. These are supported on the end edge of the cylinder 10d of the cylinder housing 10 and, when the sheet metal holder moves downward, plunge into corresponding bores in this sheet metal holder.
  • Working pistons 12 and annular pistons 13 can be acted upon from the hydraulically separated cylinder spaces 51, 52 on the one hand and 48 on the other.
  • the cylinder spaces mentioned can be connected to one another via three alternative flow paths, which are each designed differently hydraulically.
  • the first flow path is via line 20.
  • the second flow path is via line 20a.
  • the third flow path is formed by line 20b.
  • the alternative flow paths in the * communicating cylinder spaces 51, 52 and 48 require a pressure curve at a different pressure level during the drawing process.
  • the flow path change can be triggered by a pressure sensor 21 which detects the pressure of the pressure medium in the communicating cylinder spaces 51, 52; 48 and which delivers switching impulses when preset limit pressures are exceeded.
  • a 2-way valve 34 and the pressure sensor 21 are arranged in the line 20 of the first flow path.
  • line 20a of the second flow path there is a controllable pressure relief valve that can be set to different limit pressures 36 with an upstream check valve 35.
  • a 2-way valve 40, a throttle valve 22 and a piston accumulator 24 acting as a hydraulic pressure intensifier are inserted in line 20b of the third flow path.
  • the pressure medium introduced into the cylinder spaces 51, 52 under pressure during the drawing process via the three alternative flow paths acts on the working piston 12 via an action surface which is larger than the cross-sectional area of the piston head 12a.
  • the working piston acts as a pressure intensifier, which is possible in that the stationary piston 10c projects radially beyond its shaft 10b, which results in the enlargement of the pressure area.
  • the driving force A can be converted into a larger force of the drawing piston (with a smaller drawing path). *) via connection channel 50
  • the pressure medium filling of the cylinder space 49 delimited by the ring part 12b and by the central piston 10c can be introduced into the rear cylinder space 51 of the working piston 12.
  • the pressure medium displaced from the cylinder space 49 during the drawing process reaches the line 45 into the cylinder spaces 51, 52 via channel 11.
  • the empty cylinder space 49 is refilled from a pressure accumulator 26. With this reset, a volume of pressure medium corresponding to the volume of the cylinder space 49 can be displaced from the cylinder spaces 50, 51, 48 into the pressure medium reservoir 27.
  • the right cylinder space 24b of the piston accumulator 24 can be connected to the pressure accumulator 26 via a line 41 provided with a 2-way valve 25, which in turn can be connected to all cylinder spaces of the hydraulic unit for recharging or for pressure relief.
  • the pressure accumulator 26 itself can be reloaded from the pressure medium reservoir 27 by means of a feed pump 39.
  • the working piston 12 can be driven by means of a pressure source P when the annular piston 13 is stationary, that is to say when the driving force A is switched off. That from the cylinder chamber 49 displaced pressure medium is discharged into the pressure medium reservoir 27 via a 2-way valve 28. The discharge can also take place via a valve 30 which opens when an upper pressure limit is exceeded.
  • the 2-way valve 40 and the throttle valve 22 in the line 20b of the third flow path can be bridged by means of a bypass line 20b.
  • a check valve 23 which releases a predetermined pressure in the flow direction in the flow direction is arranged in this.
  • the mass moved when folding the rest of the blank from the edge of the finished drawn part, which is represented in the illustrated embodiment by the drawing ring 18, the sheet metal holder 15, the adapter ring 14 and the annular piston 13, can be eliminated by throttling the outflow of the pressure medium from the bending resistance Cylinder chamber 48 are stopped. This is done with the help of the throttle valve 22 arranged in the line 20b of the third flow path in dependence on and the pressure drop triggered by the elimination of the folding resistor.
  • the pressure medium passes through the piston accumulator 24 into the pressure accumulator 26, the 2-way valve 33 being controlled in the closed position and the 2-way valve 25 in the open position.
  • Fig. 1 shows the out of operation drawing tool with the entire associated hydraulic system with the board inserted.
  • the figures 2-8 are used to explain specific different procedures in the operation of the drawing tool, which correspond to the different drawing requirements.
  • the lines and rooms through which the respective process flows are emphasized by a stronger line. All organs not included in the process sequence, in which there is consequently no pressure, are omitted.
  • the drawing tool is switched to the first flow path.
  • the pressure medium flows from the cylinder space 48 via the line 20 with a two-way valve 34 into the cylinder space 51 and additionally via the connecting channel 50 into the cylinder space 52.
  • Fig. 3 In this figure, the drawing tool is switched to the second flow path.
  • the pressure medium is displaced from the cylinder space 48 with the partial inclusion of the line 20 of the first flow path via a check valve 35 and an adjustable pressure relief valve 36 in a line 20a into the cylinder spaces 51, 52 in order to drive the drive piston 12.
  • the switching of this flow path makes sense if an adjusted setting of the sheet holding force is important before the drawing process begins or if a control of the sheet holding force is indicated during the drawing process.
  • the drawing process only begins when the sheet metal holding force, that is to say the pressure in the cylinder space 48, exceeds the limit pressure set in the pressure relief valve 36.
  • This limit pressure is adjustable or changeable depending on the pressure sensor 21, so that the sheet metal holder force can be adapted to the respective drawing requirements during the drawing process.
  • Fig. 4 When switching the third flow path according to Fig. 4, the pressure medium coming from the cylinder space 48, including the line 20 of the first flow path, via line 20b, via a two-way valve 40, a throttle valve 22 and via a piston accumulator 24 and via Another directional control valve 33 is pressed into the cylinder spaces 51, 52 in order to drive the working piston 12.
  • the piston accumulator 24 is designed as a pressure intensifier.
  • Fig. 8 It shows how the drawing tool is returned from its end position to the starting position after the drawing process.
  • pressure medium passes from a pressure accumulator 26 via the initial section of a line 42 and via line 43 and the directional control valve 32 as well as the channel 11 in the shaft 10b into the initially empty cylinder space 49, in order to drive the working piston 12 in one direction from there. which is opposite to the direction of pull.
  • the pressure medium displaced from the cylinder spaces 51, 52 when the working piston is returned to its starting position can, for example return to the cylinder space 48 via the first flow path.
  • the pressure medium is fed from the cylinder space 49 into the cylinder spaces 51, 52 during the drawing process to accelerate the drawing process, then when the drawing tool is reset, a to displace volume corresponding to the injected volume from the cylinder spaces 51, 52 into the pressure medium reservoir 27.
  • Such a partial exchange is advantageous because it prevents the temperature of the pressure medium in the cylinder spaces from rising above a critical limit and enables the pressure medium to be kept clean by filtering the portion that is exchanged.
  • FIGS. 5, 6 illustrate process sequences in which the drawing process takes place with the drawing punch 17 (FIG. 5) or with the sheet holder 15 stationary, so that there is no opposite movement of the sheet holder and drawing punch.
  • Such a procedure may be required for certain difficult drawn parts. It may also be necessary to allow such a procedure to take place only in a particularly critical section of the entire drawing process, with switching between the first, second or third flow path before and after this section of the drawing process in order to save energy and to accelerate the drawing process Flow paths are changed.
  • the drawing process driven by the external force A, is effected exclusively by the movement of the drawing ring 18, sheet metal holder 15, adapter ring 14 and annular piston 13, while the working piston is not being acted upon.
  • This is achieved in that the pressure medium displaced from the cylinder space 48 reaches the left storage space 24a of the pressure accumulator 24 via the line 20b, the directional control valve 40 and the throttle valve 22.
  • the piston 24c becomes shifted to the right and displaces pressure medium from the right storage space 24b of the piston accumulator.
  • the displaced pressure medium passes through the directional control valve 25, the line 41 into the pressure accumulator 26. If required, this can be reloaded from the pressure medium reservoir by means of the feed pump 39 via the check valve 38.
  • the sheet metal holder is stopped during the drawing process by shedding off the external force A, while the working piston 12 and thus the drawing punch 17 are driven and effect the drawing process.
  • pressure medium is pressed into the initially empty cylinder spaces 51, 52 from a separate pressure medium source P via a check valve 53 and via a line section of line 20 of the first flow path, in order to drive the working piston 12 in the direction of pull.
  • the pressure medium displaced from the cylinder chamber 49 reaches the pressure accumulator 26 via the directional valve 32.
  • the drawing tool is reset to the starting position, as described above, by introducing pressure medium from the pressure accumulator 26 into the initially empty cylinder space 49.
  • Fig. 7 illustrates the process for folding the remaining board 47 from the edge of the finished drawn part.
  • the drawing punch 17 with the working piston on the one hand and the moving unit consisting of drawing ring, sheet metal holder 15 adapter ring 14 and annular piston 13 are used moved down synchronously.
  • the knife ring 16 which is arranged to be displaceable to a limited extent in the sheet metal holder 15, runs onto bolt-shaped stationary stops 16a in order to be moved over a slight distance for the work process relative to the aforementioned movement unit and thus relative to the drawn part or to the plate 47.
  • the bending resistance in the hydraulic system suddenly disappears, which equates to a sudden drop in pressure.
  • the outflow of the pressure medium from the cylinder 48 is throttled with the aid of the throttle valve 22 at the moment of the pressure drop as a function of the pressure sensor 21, as described above.
  • the pressure medium filling of the cylinder space 48 (FIG. 5) or the pressure medium filling of the cylinder space 49 (FIG. 6) is displaced into the pressure accumulator 26, specifically against the pressure prevailing there.
  • the pressure accumulator 26 is raised to a correspondingly higher pressure level. This means that the energy additionally required for pressing the pressure medium into the pressure accumulator is stored in the pressure accumulator 26 and is available again for a subsequent operation (e.g. for an operation according to FIGS. 7 and 8).
  • a safety valve 30 in the * line 44 allows the pressure medium filling of the cylinder space 49 to flow into the pressure medium reservoir 27, so that no damage can occur in the hydraulic system.
  • the construction shown in the illustrative embodiment can be substantially shortened by omitting the cylindrical intermediate piece 17a and / or by omitting the adapter ring 14 in the direction of the axis of symmetry. In this sense, it may also be expedient under certain circumstances to design the drive piston 12 as such at the same time as a drawing punch, so that a separate drawing punch 17 is omitted. * provided with check valves 31,29
  • a major advantage of the drawing tool according to the invention is that the external force A acting on the drawing ring can be converted into a substantially larger, opposing drawing force.
  • the entire pressure surface of the working piston 12 is composed of a pressure surface on the rear and the end face of the central piston 10c. This also provides the prerequisite for the fact that, if necessary, the external force A can be converted into an opposing pulling force of the same size, but which pulling force acts on a smaller drawing piston or a smaller drawing tool.
  • the specific computer program initially determined empirically for each drawn part according to shape, material and depth of drawing gives the drawing device the endeavor to work at the highest possible drawing speeds without the risk of tearing.
  • the pulling part can be torn off by means of the pressure sensor 21 by transitioning to one of the numerous flow alternatives of lower pressure or lower pulling speed (e.g. from the second flow path to the first or third flow path or from the first flow path to the third flow path) or by partially releasing pressure medium from the Avoid cylinder space 48 or 51.52 or by stopping external force A or the plunger. If, after the pressure drop occurs, the pressure in the system rises again up to the critical pressure limit due to increasing drawing resistance (forming resistance), the hydraulic system can switch from the current flow alternative to a flow alternative of even lower pressure.
  • the interconnection of stationary pistons 10c, annular piston 13 and cylinder housing 10 or cylinder block leads to such a space-saving construction of the drawing tool that it can also be operated in extremely small presses, in particular in injection molding machines.
  • the hydraulic unit H is clamped in the one mold clamping plate of the injection molding machine and another unit of the drawing tool comprising the drawing ring and the sheet metal holder on the second mold clamping plate of the injection molding machine.
  • the drawing tool therefore works with a horizontal drawing axis. * at least temporarily

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Control Of Presses (AREA)
  • Press Drives And Press Lines (AREA)
  • Pens And Brushes (AREA)
  • Mounting, Exchange, And Manufacturing Of Dies (AREA)

Claims (10)

  1. Outillage d'emboutissage pour le formage de tôles, de préférence planes (flans 47), possédant une matrice d'emboutissage (18) pouvant être mue par une force motrice externe (A), un serre-flan (15) déplaçable ensemble avec la matrice (18) comme une unité mobile (18, 15) et un poinçon d'emboutissage (17) pouvant être engagé dans la matrice (18) en vue de la déformation des flans (47), ainsi qu'une unité hydraulique par laquelle le mouvement de l'unité mobile (18, 25), entraînant avec elle le flan (47) à déformer, peut être transformé en un mouvement simultané, mais de sens contraire, du poinçon (17), unité hydraulique qui comprend un piston de travail central (12), un piston annulaire (13) qui l'entoure, ainsi qu'un corps de cylindre entourant le piston annulaire, dans lequel le piston annulaire (13), pouvant être mû indirectement par la force motrice (A) et pouvant s'appuyer sur le fluide de pression contenu dans une chambre de cylindre (48), est susceptible d'être sollicité d'un côté par du fluide de pression et le piston de travail (12), réalisé comme un piston différentiel (pièce annulaire 12b), est susceptible d'être sollicité des deux côtés par du fluide de pression, et dans lequel le fluide de pression refoulé par le piston annulaire (13) hors de la chambre de cylindre (48) pendant l'opération d'emboutissage, sert à mouvoir au moins temporairement le piston de travail (12), caractérisé en ce que le piston de travail (12) et le piston annulaire (13) peuvent être sollicités par du fluide de pression à partir de chambres de cylindre (51, 52 d'une part et 48 d'autre part) hydrauliquement séparées entre elles, chambres qui communiquent au moins temporairement entre elles par au moins deux trajets de circulation alternatifs (premier trajet de circulation par la conduite 20; deuxième trajet de circulation par la conduite 20a; troisième trajet de circulation par la conduite 20b) qui impliquent, en raison de conceptions hydrauliques différentes, des variations de pression s'effectuant à des niveaux de pression différents dans les chambres de cylindre (51, 52; 48) communiquant entre elles lors de l'opération d'emboutissage, qu'un capteur de pression (21) est prévu pour détecter la pression du fluide dans au moins l'une des deux chambres de cylindre (51, 52; 48) et délivrer, en cas de dépassement de pressions limites préréglées, des impulsions de commande, et que les trajets de circulation alternatifs peuvent être mis en service par les impulsions de commande fournies par le capteur de pression (21).
  2. Outillage d'emboutissage selon la revendication 1, caractérisé en ce que les chambres de cylindre (51, 52; 48), délimitées par le fond d'un corps de cylindre (10), sont séparées hydrauliquement l'une de l'autre par un manchon de séparation (10a) faisant saillie de ce fond, et que le piston annulaire (13), guidé sur le cylindre (10d) du corps de cylindre (10) est guidé sur le piston de travail (12) au moyen d'un épaississement radial (13a) recouvrant le manchon de séparation (10a), la surface latérale intérieure (13b) du piston annulaire (13) étant espacée de la surface latérale extérieure du manchon de séparation (10a).
  3. Outillage d'emboutissage selon la revendication 1 ou 2, caractérisé en ce que le piston de travail (12), dont le côté arrière peut être sollicité par du fluide de pression à partir de la chambre de cylindre (51), peut être sollicité en sens contraire par du fluide de pression à partir d'une chambre de cylindre (49) située dans un évidement central du piston de travail (12), en forme de godet, et délimitée par un piston central (10c) ancré dans le fond du corps de cylindre (10) et par une pièce annulaire (12b) reliée au piston de travail (12), la chambre de cylindre arrière (51) communiquant avec une autre chambre de cylindre (52) délimitée par le fond (12a) du piston de travail (12) et par le piston central (10c).
  4. Outillage d'emboutissage selon une des revendications précédentes, caractérisée en ce que la conduite (20) du premier trajet de circulation comporte une vanne (34) à plusieurs voies et un capteur de pression (21), la conduite (20a) du deuxième trajet de circulation comporte une soupape limitatrice de pression (36) commandée, réglable à différentes pressions limites et précédée d'un clapet antiretour (35), et la conduite (20b), du troisième trajet de circulation comporte une vanne (40) à plusieurs voies, une soupape d'étranglement (22) et un accumulateur à piston (24) agissant comme un convertisseur de pression hydraulique.
  5. Outillage d'emboutissage selon une des revendications précédentes, caractérisé en ce que (à des fins d'augmentation de la vitesse de l'opération d'emboutissage) le remplissage en fluide de pression de la chambre de cylindre (49) délimitée par la pièce annulaire (12b) et le piston central (10c), peut être introduit à travers une conduite (45) pourvue d'une vanne (19) à plusieurs vannes dans la chambre de cylindre arrière (51) du piston de travail (12) et, à des fins de rappel de l'outillage d'emboutissage à la position de départ, la chambre de cylindre vide (49) peut être remplie de nouveau à partir d'un accumulateur hydraulique (26), rappel au cours duquel un volume de fluide de pression correspondant au volume de la chambre de cylindre (49) peut être refoulé hors des chambres de cylindre (50, 51; 48) dans un réservoir de fluide de pression (27).
  6. Outillage d'emboutissage selon la revendication 5, caractérisé en ce que la chambre de cylindre droite (24b) de l'accumulateur à piston (24) peut être mise en communication, par une conduite (41) munie d'une vanne (25) à plusieurs voies, avec l'accumulateur hydraulique (26), lequel est susceptible d'être relié à toutes les chambres de cylindre de l'unité hydraulique, accumulateur (26) qui est rechargeable à partir du réservoir de fluide de pression (27) par une pompe alimentaire (39).
  7. Outillage d'emboutissage selon une des revendications précédentes, caractérisé en ce que le piston de travail (12) peut être mû à l'aide d'une source de pression (P) pendant que le piston annulaire (13) est arrêté et le fluide de pression refoulé hors de la chambre de cylindre (49) peut être évacué à travers une vanne (32) à plusieurs voies dans l'accumulateur hydraulique (26) (figure 6).
  8. Outillage d'emboutissage selon une des revendications 4 à 7, caractérisé en ce qu'une dérivation peut être établie sur la vanne (40) à plusieurs voies et la soupape d'étranglement (22) dans la conduite (20b) du troisième trajet de circulation au moyen d'une conduite de dérivation (20b') dans laquelle est disposé un clapet antiretour (23) autorisant le passage dans le sens de l'écoulement sous une pression prédéterminée.
  9. Outillage d'emboutissage selon une des revendications précédentes et comportant un couteau de découpage (16) disposé mobile en translation de façon limitée dans le serre-flan (15) et servant à découper ce qui reste du flan du bord de la pièce emboutie finie, caractérisé en ce que les organes déplacés lors de l'opération de découpage (matrice 18, serre-flan 15, piston annulaire 13), peuvent être freinés, à la disparition de la résistance opposée au découpage, par étranglement du fluide de pression s'écoulant hors de la chambre de cylindre (48) du piston annulaire (13) dans l'accumulateur hydraulique (26) (figure 7).
  10. Outillage d'emboutissage selon la revendication 9, caractérisé en ce que l'écoulement du fluide de pression hors de la chambre de cylindre (48) peut être étranglé, à l'aide de la soupape d'étranglement (22) disposée dans la conduite (20b) du troisième trajet de circulation, en fonction de la chute de pression déclenchée par la disparition de la résistance opposée au découpage, alors que la vanne (33) à plusieurs voies est fermée et que la vanne (25) à plusieurs voies est ouverte.
EP89104248A 1988-03-12 1989-03-10 Appareil d'étirage pour la déformation de côles Expired - Lifetime EP0333052B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89104248T ATE91653T1 (de) 1988-03-12 1989-03-10 Ziehwerkzeug zum umformen von blechen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3808262 1988-03-12
DE3808262 1988-03-12

Publications (3)

Publication Number Publication Date
EP0333052A2 EP0333052A2 (fr) 1989-09-20
EP0333052A3 EP0333052A3 (en) 1990-09-26
EP0333052B1 true EP0333052B1 (fr) 1993-07-21

Family

ID=6349548

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89104248A Expired - Lifetime EP0333052B1 (fr) 1988-03-12 1989-03-10 Appareil d'étirage pour la déformation de côles

Country Status (6)

Country Link
US (1) US4909061A (fr)
EP (1) EP0333052B1 (fr)
JP (1) JPH01309798A (fr)
AT (1) ATE91653T1 (fr)
DE (1) DE58904930D1 (fr)
ES (1) ES2043917T3 (fr)

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EP0333052A3 (en) 1990-09-26
EP0333052A2 (fr) 1989-09-20
DE58904930D1 (de) 1993-08-26
JPH01309798A (ja) 1989-12-14
US4909061A (en) 1990-03-20
ES2043917T3 (es) 1994-01-01
ATE91653T1 (de) 1993-08-15

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