EP0417753A2 - Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes - Google Patents

Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes Download PDF

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Publication number
EP0417753A2
EP0417753A2 EP90117536A EP90117536A EP0417753A2 EP 0417753 A2 EP0417753 A2 EP 0417753A2 EP 90117536 A EP90117536 A EP 90117536A EP 90117536 A EP90117536 A EP 90117536A EP 0417753 A2 EP0417753 A2 EP 0417753A2
Authority
EP
European Patent Office
Prior art keywords
piston
cylinder
press
pressure
cylinder unit
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
EP90117536A
Other languages
German (de)
English (en)
Other versions
EP0417753B1 (fr
EP0417753A3 (en
Inventor
Erich Harsch
Gebhard Engler
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.)
Maschinenfabrik Mueller Weingarten AG
Mueller Weingarten AG
Original Assignee
Maschinenfabrik Mueller Weingarten AG
Mueller Weingarten AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Maschinenfabrik Mueller Weingarten AG, Mueller Weingarten AG filed Critical Maschinenfabrik Mueller Weingarten AG
Publication of EP0417753A2 publication Critical patent/EP0417753A2/fr
Publication of EP0417753A3 publication Critical patent/EP0417753A3/de
Application granted granted Critical
Publication of EP0417753B1 publication Critical patent/EP0417753B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • 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
    • 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

Definitions

  • the invention relates to a mechanical or hydraulic press with a pulling device or drawing step of a step press according to the preamble of claim 1.
  • the sheet to be drawn is therefore pressed against the by the upper part of the tool Pressed sheet metal counterholder and moved it against the force of the die cushion. Here, it is deformed by the drawing die fixed on the press table.
  • a device of the generic type for pre-accelerating the movable cushion masses in drawing presses has become known.
  • a gradual acceleration of the die cushion from zero to almost ram speed is achieved. This is done by means of a complicated telescopic cylinder in a control line system, with a telescopic ring piston which is moved by means of a plunger which can be actuated via the press ram.
  • the ring pistons are acted upon one after the other and thus displace pressure medium for the pre-acceleration of the die cushion movement in a step-like manner and thus path-dependent.
  • the number of telescopic pistons determines the degree of pre-acceleration of the movable cushion masses.
  • Different stroke rates of the drawing press and working pressures can be achieved in this known device by adjusting the starting position of the punch connected to the press ram.
  • the path-dependent control measures are then implemented hydraulically via the step-shaped annular pistons.
  • a disadvantage of this known device is the complicated structure of the piston-cylinder unit with the step-shaped annular piston integrated therein.
  • the gradation of the ring pistons results in a fixed gradation of the hydraulic pressures that build up for the pre-acceleration of the sheet metal counter age, which is a very inflexible solution.
  • the press according to the invention with the characterizing features of claim 1 has the advantage that it contains a pulling device, by means of which the impact noise that occurs when the upper tool hits the sheet metal counterholder can be considerably reduced by accelerating the die cushion mass beforehand, with very simple circuitry and structural measures be used.
  • the pre-acceleration process largely takes place without complicated and delayed valve control, i. H. valve controls are kept to a minimum. Nevertheless, it is possible to influence the process to a large extent if the initial requirements change, whereby the reproducibility of the processing process is guaranteed due to the absence of extensive control mechanisms.
  • the pre-acceleration process of the sheet metal counterholder is to be carried out with separate hydraulic cylinders in the present invention, which are coupled to the movement of the press ram.
  • An optimal effect of this process is achieved by a path and time recording of the individual movement processes as well as by a targeted hydraulic control of the pressure medium causing the pre-acceleration.
  • the device can run in the manner of an individually set positive control.
  • the press 1 with the pulling device 2 in FIGS. 1 and 4 consists of a stationary lower press table 3 with a designed as a sliding table 4 table support for receiving a lower tool 5 for producing a workpiece, represented by a not yet machined board 6.
  • the board 6 is placed on a sheet metal counter-holder 7, which is guided in the lower tool 5 with stamp 5 '.
  • the upper tool 8 is connected to a press ram 9.
  • the sheet metal counterholder 7 is supported on a pressure cheek 11 by means of pressure bolts 10.
  • the pressure cheek 11 is supported by an underlying, central piston-cylinder unit 12, which is pneumatically operated and acts like a spring that presses upwards.
  • a further piston-cylinder unit 13 is provided below the piston-cylinder unit 12 in operative connection with the same piston rod 19 and serves as a hydraulic damping cylinder for damping the upward-directed piston movement of the piston-cylinder unit 12 above.
  • the piston-cylinder units 12 and 13 are shown again in more detail in their circuit arrangement in FIGS. 2 and 6.
  • the piston-cylinder unit 12, known per se - hereinafter referred to as pneumatic cylinder 12 - consists of a cylinder housing 14 with an upper 15 and a lower 16 pressure chamber, each of which is passed through by a piston 17, 18 which can be acted upon on one side.
  • a piston rod 19 passing through the entire cylinder housing 14 connects the upper and lower pistons 17, 18 and protrudes from the cylinder housing 14 in the upper and lower regions.
  • the upwardly projecting area 19 'of the piston rod 19 supports the pressure cheek 11, which is only indicated in FIGS called another damping cylinder 13 -.
  • the piston rod 19 ⁇ with provided with a piston 20 which runs within the damping cylinder 13.
  • an oil tank 21 preloaded with air is arranged around the damping cylinder 13.
  • a throttle bore 22 with a downstream hydraulic circuit 23 is used to actuate the damping cylinder 13.
  • a 2/2-way valve 24 with a downstream 3/2-way valve 25 is provided, which on the one hand with the throttle bore 22 and on the other hand with a feed bore 26 to the damping cylinder 13 with the upper pressure chamber 46.
  • the control circuit provides a further access 27 to the oil container 21.
  • the pressure chambers 15, 16 of the pneumatic cylinder 12 arranged above the damping cylinder 13 are provided with pressure medium from a pneumatic accumulator 29 via a pressure line 28, the pressure of which can be infinitely adjusted.
  • hydraulic cylinders 33 are provided on the stand 32 of the press 2, the respective piston rod 34 of which is firmly connected to the press ram 9 via a calotte 35.
  • a piston 36 which can be acted upon from both sides, runs in the hydraulic cylinder 33, the upper piston rod 34 being extended downwards with the same diameter, so that an upper pressure chamber 37 and lower pressure chamber 38 which have a constant cross section are established.
  • the two upper pressure chambers 37 of the two hydraulic cylinders 33 arranged laterally in the stator area are connected to one another via a pressure line 39 and connected to a hydraulic pump 40.
  • a memory 41 is connected to the upper pressure spaces 37.
  • the lower pressure chambers 38 of the two hydraulic cylinders 33 are also connected to one another via a further pressure line 42 connected, wherein an adjustable proportional valve 43 connects the upper 39 and lower pressure line 42 and thus the upper 37 and lower 38 pressure chambers.
  • the pressure line 42 connecting the lower pressure spaces 38 is connected via a 2/2-way valve 45 to the pressure space 46 provided above the piston 20 of the damping cylinder 13.
  • a first distance meter 47 for determining the press ram travel 9 is provided on the press ram 9.
  • the movement of the puller, i.e. H. the movement of the pressure cheek 11 is detected via the movement of the piston rod 19.
  • a further odometer 48 is attached to the piston 20 of the damping cylinder 13.
  • the operating cycle of the press with the pulling device begins in accordance with the starting position shown in FIG. H. with the press ram 9 raised. While the press ram 9 with the upper tool 8 attached to it moves downward, the proportional valve 43 shown in FIG. 2 is opened, so that when the piston 36 moves downward, the pressure medium located in the lower pressure chamber 38 of the hydraulic cylinder 33 is above the pressure line 42, the proportional valve 43, the upper pressure lines 39 is displaced into the upper pressure chamber 37. The path of the press ram 9 is detected via the path measuring device 47.
  • the proportional valve 43 Shortly before the upper tool 8 hits the sheet-metal counterholder 7, the proportional valve 43 closed, whereby the oil displaced in the lower pressure chamber 38 is no longer conveyed into the upper pressure chamber 37 but via the line 44 and the valve 45 into the upper pressure chamber 46 of the damping cylinder 13.
  • the proportional valve 43 is triggered by the travel meter 47 and closed in a ramp-controlled manner, ie according to a predetermined, preferably linear shut-off characteristic.
  • Fig. 3 the sequence of movements of the pulling device in dependence on the set ramp is shown in principle.
  • the X-axis shows the angle of rotation of the mechanically driven rotating plunger drive, the Y-axis the plunger stroke.
  • Curve 49 shows the path of the press ram 9, the bottom dead center being identified by UT.
  • the path of the pressure cheek 11 and thus the sheet metal counterholder 7 is shown with reference number 50.
  • the pre-acceleration process of the sheet metal counter-holder 7 begins, ie the proportional valve 43 begins to close the passage of the pressure medium.
  • the pre-acceleration of the sheet-metal counter-holder 7 from point 51 to point 52 takes place over the distance "a" before the upper tool 8 touches the sheet-metal counter-holder 7 at point 52 at the angle of rotation X2.
  • the sheet metal counterholder with die cushion between points 52 (X2) and 53 (X3) corresponds to curve 54 in the same way as the upper tool.
  • press ram 9 After passing through the bottom dead center UT, the press ram 9 together with the sheet metal counterholder 7 again moves up to the point 53, the pneumatic cushion 12 bringing about the upward movement of the die cushion and thus the sheet metal counterholder. From the point 53 (angle of rotation X3) press ram 9 and sheet metal counterpart 7 separate by the action of the damping.
  • the area ratio of the effective area of the hydraulic cylinder 33 and the damping cylinder 13, i. H. the relative speed of the pistons 36 to the piston 20 relative to one another is determined by the ratio of the effective piston areas of the two pistons 36 of the hydraulic cylinders 33 to the effective upper surface of the piston 20 of the damping cylinder 13.
  • the area ratio is chosen so that during the acceleration phase of the sheet-metal counterholder 7, this runs more slowly than the press ram 9, whereby the upper tool 8 overtakes the sheet-metal counterholder 7 in a certain way and places it on the pulling device. This is recognized by a pressure drop at the pressure sensor 55.
  • the distance traveled by the pulling device until the upper tool 8 is placed on the sheet-metal counterholder 7 can be checked on the basis of the travel meter 48. After the pre-acceleration has been completed, the proportional valve 43 is opened again, the damping cylinder 13 absorbing the required oil volume via a check valve 56 after the valve 45 has been closed.
  • the 2/2-way valve 24 and the valve 25 are opened so that the pulling device, following the press ram 9, can move up again.
  • the upward movement is braked by the throttle bore 22 and, in particular, an impact impact in the upper end position of the sheet metal counter-holder is avoided.
  • the damping cylinder 13 is therefore used both to dampen the upward movement of the pneumatic cylinder 12 acting as a spring and to generate the previously described pre-acceleration of the die cushion with sheet metal counterholder 7. After the pulling process, the 2/2-way valve 24 is closed again.
  • the press according to the invention shown in FIGS. 4 to 6 is basically constructed in the same way as the press described above with the following differences in construction and mode of operation:
  • the hydraulic cylinders 33 provided in this embodiment are attached directly to the press ram 9, the piston rod 34 of the piston 36, which can be acted on from both sides, being connected via a calotte 35 to an adjusting device 57, which in turn is fixedly attached to the stand 32.
  • the adjusting device 57 provides a variable height adjustment of the piston rod 34 via an adjusting screw 58, i. H. the starting position of the piston 36 can be varied in height.
  • the wall of the hydraulic cylinder 33 contains an upper through bore 59, a lower through bore 60 analogously to the illustration in FIG. 2.
  • a through bore 62 is provided in the middle height range of the hydraulic cylinder, which serves as a control well. 5 shows the view of this control bore from the direction Y in FIG. 4 in more detail.
  • the press according to Figures 4 to 6 works as follows:
  • the starting position of the piston 36 is determined by the Height adjustment device 57, 58 predetermined depending on the application and mode of operation of the device.
  • the hydraulic cylinder 33 moves downward, as a result of which the piston 36 moves upward in the cylinder space of the hydraulic cylinder 33 and the pressure medium located in the upper pressure space 37 via the central through bore 62 and a bypass line 63 in the housing wall of the hydraulic cylinder 33 and the lower bore 60 is conveyed into the lower pressure chamber 38.
  • the upper through bore 59 remains closed during this overflow from the upper 37 to the lower 38 pressure chamber via the valve 63.
  • the position of the piston 36 can be positioned with the adjusting device 58 to determine the start of acceleration. In addition, this also adjusts to different tool heights.
  • the distance traveled can again be checked on the travel meter 48.
  • the valve 63 is opened after the pre-acceleration and the valve 45 is closed. This allows the rest of the drawing process the pressure medium from the upper pressure chamber 37 via the valve 63 into the lower pressure chamber 38 through the through holes 59, 60 in the hydraulic cylinder 33.
  • the required amount of the hydraulic medium for the damping cylinder 13 is removed from the oil container 21. This applies both to the exemplary embodiment according to FIGS. 1 and 4.
  • one or more and in particular two hydraulic cylinders 33 are accordingly arranged laterally in the region of the press ram 9 on the stand 32 of the press, the press ram 9 moving the respective piston rods or the cylinder housing.
  • the hydraulic medium displaced in the cylinder space or pressure space is preferably displaced into a damping cylinder 13 with the aid of a proportional valve 43 in conjunction with position measuring devices 47, 48, as a result of which the pulling device is set in motion before the upper tool 8 hits the sheet metal counterholder 7.
  • the speed of the die cushion G is chosen to be lower than that of the press ram; however, it runs in the same way and in the same direction as the ram movement. As a result, the upper tool can be placed gently on the sheet metal counterholder according to a predetermined path.
  • one or more hydraulic cylinders 33 are arranged directly on the press ram 9, their piston rods 34 being connected to the stand 32 via adjusting mechanisms 57, 58.
  • the Hydraulic cylinders 33 have special openings 62 in the walls, which are arranged in a triangular shape (see FIG. 5), which are gradually closed by the piston 36 when the press ram 9 drops shortly before the press ram hits the pulling device, as a result of which in the damping cylinders 13 displaced oil volume flow increases more and more and results in an acceleration of the drawing device or the sheet metal counter-holder.
  • the effective area of the sum of the pistons 36 of the hydraulic cylinders 33 is smaller than that of the piston 20 of the damping cylinder 13, so that the press ram 9 catches up with the sheet metal counter-holder 7, the speed of which is analogous to the ram speed, in a certain way.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Presses And Accessory Devices Thereof (AREA)
EP90117536A 1989-09-12 1990-09-12 Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes Expired - Lifetime EP0417753B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3930347 1989-09-12
DE3930347 1989-09-12

Publications (3)

Publication Number Publication Date
EP0417753A2 true EP0417753A2 (fr) 1991-03-20
EP0417753A3 EP0417753A3 (en) 1991-06-05
EP0417753B1 EP0417753B1 (fr) 1993-09-22

Family

ID=6389200

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90117536A Expired - Lifetime EP0417753B1 (fr) 1989-09-12 1990-09-12 Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes

Country Status (3)

Country Link
EP (1) EP0417753B1 (fr)
DE (1) DE59002828D1 (fr)
ES (1) ES2045701T3 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0556390A1 (fr) * 1990-11-02 1993-08-25 Kabushiki Kaisha Komatsu Seisakusho Dispositif de coussin de serre-flan d'une presse
ES2084558A2 (es) * 1993-11-25 1996-05-01 Fagor S Coop Ltda Sistema de preceleracion para un cojin hidraulico de prensa.
EP0716916A1 (fr) * 1994-11-23 1996-06-19 Umformtechnik ERFURT GmbH Procédé d'ajustement de l'impact des outils supérieurs et inférieurs d'une presse, diminuant le bruit, et entraînement du coulisseau avec un dispositif d'application du procédé
EP0744230A1 (fr) * 1995-05-22 1996-11-27 Toyota Jidosha Kabushiki Kaisha Procédé et dispositif de formage d'une pièce dans lesquels la plaque du coussin est poussée vers le bas des amortisseurs montés entre l'outil et ladite plaque avant le serrage de la pièce entre l'outil et la bague d'emboutissage
CN106003784A (zh) * 2016-07-31 2016-10-12 江阴市瑞丰液压机械有限公司 筒形结构的液压机

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0074421A1 (fr) * 1981-09-12 1983-03-23 L. SCHULER GmbH Agencement d'emboutissage pour presses à poinçon d'emboutissage actionné mécaniquement
DE3619109A1 (de) * 1985-10-30 1987-05-07 Warnke Umformtech Veb K Einrichtung zur auftreffstossdaempfung fuer ziehkissen an pressen
DE3640788A1 (de) * 1986-11-28 1988-06-01 Schuler Gmbh L Zieheinrichtung fuer eine presse
DE3835470A1 (de) * 1987-12-14 1989-06-22 Warnke Umformtech Veb K Rueckzugssteuerung fuer ziehkissen an pressen
DE8905994U1 (de) * 1989-05-13 1989-07-20 Maschinenfabrik Müller-Weingarten AG, 7987 Weingarten Pneumatische Zieheinrichtung für Pressen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0074421A1 (fr) * 1981-09-12 1983-03-23 L. SCHULER GmbH Agencement d'emboutissage pour presses à poinçon d'emboutissage actionné mécaniquement
DE3619109A1 (de) * 1985-10-30 1987-05-07 Warnke Umformtech Veb K Einrichtung zur auftreffstossdaempfung fuer ziehkissen an pressen
DE3640788A1 (de) * 1986-11-28 1988-06-01 Schuler Gmbh L Zieheinrichtung fuer eine presse
DE3835470A1 (de) * 1987-12-14 1989-06-22 Warnke Umformtech Veb K Rueckzugssteuerung fuer ziehkissen an pressen
DE8905994U1 (de) * 1989-05-13 1989-07-20 Maschinenfabrik Müller-Weingarten AG, 7987 Weingarten Pneumatische Zieheinrichtung für Pressen

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0556390A1 (fr) * 1990-11-02 1993-08-25 Kabushiki Kaisha Komatsu Seisakusho Dispositif de coussin de serre-flan d'une presse
EP0556390A4 (en) * 1990-11-02 1993-12-15 Kabushiki Kaisha Komatsu Seisakusho Die cushion device of press machine
US5339665A (en) * 1990-11-02 1994-08-23 Kabushiki Kaisha Komatsu Seisakusho Die-cushion apparatus of press machine
ES2084558A2 (es) * 1993-11-25 1996-05-01 Fagor S Coop Ltda Sistema de preceleracion para un cojin hidraulico de prensa.
EP0716916A1 (fr) * 1994-11-23 1996-06-19 Umformtechnik ERFURT GmbH Procédé d'ajustement de l'impact des outils supérieurs et inférieurs d'une presse, diminuant le bruit, et entraînement du coulisseau avec un dispositif d'application du procédé
EP0744230A1 (fr) * 1995-05-22 1996-11-27 Toyota Jidosha Kabushiki Kaisha Procédé et dispositif de formage d'une pièce dans lesquels la plaque du coussin est poussée vers le bas des amortisseurs montés entre l'outil et ladite plaque avant le serrage de la pièce entre l'outil et la bague d'emboutissage
US5623848A (en) * 1995-05-22 1997-04-29 Toyota Jidosha Kabushiki Kaisha Pressing method and system wherein cushion platen is lowered by cooperation of shock absorbers and cylinders before holding of blank between die and pressure ring
CN1064867C (zh) * 1995-05-22 2001-04-25 丰田自动车株式会社 冲压方法和冲压***
CN106003784A (zh) * 2016-07-31 2016-10-12 江阴市瑞丰液压机械有限公司 筒形结构的液压机

Also Published As

Publication number Publication date
EP0417753B1 (fr) 1993-09-22
EP0417753A3 (en) 1991-06-05
ES2045701T3 (es) 1994-01-16
DE59002828D1 (de) 1993-10-28

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