EP0417754A2 - 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 PDFInfo
- Publication number
- EP0417754A2 EP0417754A2 EP90117537A EP90117537A EP0417754A2 EP 0417754 A2 EP0417754 A2 EP 0417754A2 EP 90117537 A EP90117537 A EP 90117537A EP 90117537 A EP90117537 A EP 90117537A EP 0417754 A2 EP0417754 A2 EP 0417754A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- pressure
- cylinder
- die cushion
- press
- 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
Links
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
- 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 amount of work required is measured as a counterforce to the Sheet metal counterholder is applied via a pressure cushion or pressure cheek to which air or hydraulic medium is applied, from the product counterforce times the way. Due to the impact force exerted on the sheet metal counterholder from above, part of the energy is stored in a storage device which provides the counterforce for the sheet metal counterholder and, after the pulling process has taken place, when the pressure pad or the pressure cheek and the plunger rises again, as a restoring force on the plunger Relieve the drive. If the pressure cushion is held back in its lower position and raised again under pressure control, then the entire energy generated when the ram and the sheet metal counter-holder are lowered is converted into heat. Large presses are very large amounts of energy. For example, with a sheet metal holder force of 4,000 kN, a stroke of 200 mm occurs at a stroke rate of 15 per min. a power loss of 196 kW.
- drawing presses have been proposed that work with mechanically operated sheet metal counterholders.
- Such mechanical sheet metal supports work via lever drives, which are associated with great mechanical and therefore also financial expenditure.
- the machine body would in principle have to absorb the full pressing force of both the ram and the sheet metal counterholder.
- Hydraulic drawing presses have become known from DE-PS 883 736 or from DE 38 35 376 A1, the press rams of which are connected via connecting rods directly or indirectly via a piston-cylinder unit to a lower sheet metal holder frame for supporting the drawing cushion are.
- the die cushion is supported via the outer piston-cylinder units coupled to the connecting rods, the pressure medium of which is supplied to these units in a controllable manner.
- the pressure pad for the sheet metal counterholder is rigidly connected to these piston-cylinder units via a central connecting rod. This device therefore only serves to clamp the workpiece against the ram force.
- a disadvantage of such drawing presses is the fact that the press ram with the upper tool strikes the lower tool with sheet metal counterholder with great force and is at least associated with a high level of noise pollution. At the same time, the sheet metal counterholder has to be accelerated suddenly to the speed of the press ram, which generates a high energy requirement.
- a device 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 can be actuated by means of a special stamp.
- the ring pistons are acted upon one after the other and thus gradually displace pressure medium for the die cushion movement.
- the number of telescopic pistons determines the degree of pre-acceleration of the movable cushion masses.
- a targeted hydraulic control of a compliant sheet metal counterholder via the ram is still out DE-PS 877 590 known.
- compensating cylinders are provided, which perform a defined pressure transfer to the die cushion when the press ram moves.
- a targeted acceleration of the sheet metal counter-holder is not provided here.
- 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 which occurs when the upper tool hits the sheet metal counterholder can be considerably reduced by accelerating the die cushion masses in advance and hydraulic bracing of the sheet metal counterholder can subsequently take place .
- the process runs largely without complicated and delayed valve controls, i. H. these valve controls are kept to a minimum. This ensures a high reproducibility of the machining process due to the lack of control mechanisms.
- the device according to the invention therefore runs in the manner of a positive control.
- the invention makes use of the individual movements to perform the individual movements and, in particular, to generate the bracing of the sheet metal counter-holder.
- the kinetic energy of the press ram is not converted into heat by means of throttle valves during its downward movement, but is stored in corresponding pressure accumulators. The energy stored in this way can be reused for the ram return stroke.
- the press 1 with a pulling device in FIGS. 1 and 2 consists of a stationary press table 2 with a table support 3 for receiving a lower tool 4 for producing a workpiece, represented by a board 5 which has not yet been machined.
- the board 5 is placed on a sheet metal counterholder 6. which is guided in the lower tool 4 with stamp 4 '.
- the upper tool 7 is connected to a press ram 8.
- the sheet metal counter-holder 6 is generally supported by pressure bolts 9 on a pressure cheek 10, or also known as die cushion 10.
- the die cushion 10 lies on a die cushion tray 10 '. Both parts together form the die cushion unit 10, 10 '.
- the press ram 8 is connected via at least two laterally arranged connecting rods 11 or four connecting rods 11 arranged in its corner regions connected to the lower part of the pulling device.
- the connecting rods 11 serve as piston rods 11 for a first piston-cylinder unit 12 with pistons 13 and, in FIG. 1, cylinder space 14 underneath for the pressure medium.
- This first piston-cylinder unit 11, 12, 13, 14 is referred to below as the pump cylinder 12.
- the die cushion unit 10, 10 'and in particular the die cushion holder 10' is supported downwards via at least two lateral and in particular four arranged in the corner regions of the die cushion second piston-cylinder units 15, which are referred to below as pressure cylinder 15.
- the pressure cylinder 15 consist of a piston rod 16 connected to the die cushion tray 10, a piston 17 arranged at the end thereof and a cylinder chamber 18 for pressure medium which completely surrounds the piston.
- the cylinder chamber located above the piston 17 is denoted by 18 ', the cylinder chamber arranged below the piston 17 is denoted by 18 ⁇ .
- the pressure chamber 14 of each pump cylinder 12 is connected via a pressure line 19 to the upper pressure chamber 18 'of the pressure cylinder 15.
- the lower pressure chamber 18 ' is connected to a pressure accumulator 21 via a pressure line 20.
- the pressure line 19 is connected via a further pressure line 22 to a further pressure accumulator 23 via a check valve 24.
- the pressure line 22 is also assigned a further pressure accumulator 25 via a pressure line 26, which is controlled in a controllable manner by means of a hydraulic valve 27.
- Another line 28 connects the pressure line 22 to a pressure relief valve 29 which is connected to a pressure oil outlet device 31 via a further pressure valve 30.
- the first piston cylinder unit or the pump cylinder 12 is connected with its pressure chamber 14, however, a line 32 to a metering reservoir 33, a further piston-cylinder unit 34 with piston 35 and cylinder chamber 36 being connected in between.
- the piston 35 is guided in the cylinder chamber 36 over a defined distance s 1 to an upper stop 37, an adjusting device 38 accomplishing the path specification.
- the embodiment of the pulling device according to FIG. 2 differs from that according to FIG. 1 only in that the first piston-cylinder unit 12, i. H. the pump cylinder 12, not in the lower part of the pulling device via the connecting rods 11, as in FIG. 1, but in the upper part of the pulling device, i. H. is arranged above the press ram 8.
- the connecting line 19 between this upper pump cylinder 12 and the lower pressure cylinder 15 is drawn from top to bottom in the pulling device. 2
- the piston rod 11 of the pump cylinder 12 is in turn connected to a piston 13, the pressure chamber 14 being now integrated in the upper housing of the pulling device 1.
- the effective cross-sectional area of the pressure chamber 14 is reduced by the piston rod 11, which must be taken into account when adjusting the pressure.
- the pressure accumulator 23 with check valve 24 via line 22 and the pressure relief valve 29 with pressure valve 30 via line 28 are further connected to line 19 in the upper region of the pulling device in the head part of the pulling device. Furthermore, the piston-cylinder unit 34 with the metering reservoir 33 as well as the piston 35, the cylinder chamber 36 and the adjusting device 38 in the upper head part of the Pulling device integrated.
- the pressure accumulator 25 with a controllable hydraulic valve 27 and a connecting line 26 to the pressure line 19 also remains in the embodiment of FIG. 2 in the lower region of the drawing device.
- auxiliary cylinder 39 consists of a piston 41 which is arranged in a cylinder space 40 and can be acted upon by pressure from the pressure line 20 on its upper side via a pressure line 42; H. the upper pressure chamber 40 'is connected via the pressure line 42 to the lower pressure chamber 18' of the pressure cylinder 15 and to the pressure accumulator 21 equally.
- the cylinder space 40 has a defined height h, the piston 41 being able to move down a defined distance s 2 before it moves against a stop 43 formed by the wall of the cylinder space.
- the directional control valve 30, which is designed as a solenoid valve, is actuated and the flow through the check valve 29 is thus blocked.
- the pressure medium cannot flow from the pressure chamber 14 of the pump cylinder 12 via the lines 19, 22, 28 into an outlet 44. Rather, the pressure medium displaced by the piston 13 during the downward movement of the press ram 8 is pressed out of the pressure chamber 14 via the line 32 into the lower cylinder chamber 36 ', so that the piston 35 of the piston-cylinder unit 34 is pressed upward.
- the starting position of this piston 35 is adjusted by the adjusting device or adjusting screw 38, so that the distance s 1 of the piston 35 that can be covered is adjustable.
- the pressure medium located above the piston 35 is hereby pressed into the metering reservoir 33, which is prestressed with a prestressing pressure of approximately 8 bar.
- the upper stop surface 37 limits the upward stroke of the piston 35 to the adjustable distance s 1. A pressure increase thus takes place in the metering reservoir 33.
- the pressure medium is introduced from the pressure chamber 14 into the upper cylinder chamber 18 'of the second piston-cylinder unit 15 or the pressure cylinder 15 upon further downward movement of the piston 13 of the pump cylinder 12.
- the downward movement of the piston 17 and thus the die cushion unit 10, 10 'including sheet metal counterhold 6 is initiated.
- the pressure in the upper cylinder chamber 18 ' opposes the pressure in the lower cylinder chamber 18raum. This is first determined from the pressure of the pressure accumulator 21, which with a maximum pressure, for. B. about 200 bar, is biased according to the maximum die cushion force.
- the pressure accumulator 21 is connected via the line 42 to the upper pressure surface 41 'of the piston 41.
- the effective lower pressure surface 17 ⁇ of the piston 17 is approximately 10% larger than the upper effective pressure surface 41 'of the piston 41.
- the stroke of the piston 41 of the auxiliary cylinder 39 is, for example, s2 ⁇ 20 mm before the piston 41st moves against the lower housing stop during the downward movement of the die cushion unit. Thereafter, the pressure line 42 is meaningless with regard to the movement sequence of the die cushion unit. During this stroke by the amount s2 during the downward movement of the die cushion, the die cushion force is only about 10% of the maximum pretensioning force.
- the upper effective piston area 17 'of the piston 17 is approximately 20% larger than the lower effective piston area 13' of the piston 13.
- the die cushion speed is therefore 0.8 times the ram speed. This state applies to the pre-acceleration of the plate counter-holder 6, i. H. before the upper tool hits the sheet metal counterholder. Then the upper tool 7 or the press ram 8 and the sheet metal counter-holder 6 and thus the die cushion unit 10 move downward at the same speed.
- the start of the pre-acceleration of the sheet metal counterholder is set by the adjusting device 38, ie the piston 35 first runs through the set path s 1 until it stops; then the deflection of the pressure medium of the pump cylinder 12 takes place from the pressure chamber 14 in the upper pressure chamber 18 '.
- the pre-acceleration movement of the die cushion starts at a distance from the upper tool 7 to the board 5 of approximately 4 mm when the upper tool touches the board after a 16 mm counter-stroke. This route is taken into account, as is the route for oil compression by the adjusting device 38, ie the route s 1.
- the pre-acceleration of the die cushion unit 10, 10 'and thus the sheet metal counter-holder 6 takes place without substantial counterpressure of the pressure accumulator 21. This takes place due to the downward movement of the piston 41 by the amount of s2. During this path, the pressure force of the pressure accumulator 21 acts both on the somewhat larger lower pressure surface 17 'and on the upper pressure surface 41'. As a result, the die cushion unit 10, 10 'quasi in equilibrium. The pre-acceleration of the sheet metal counterholder 6 continues until the upper tool 7 has caught up with the sheet metal counterholder 6 and is seated thereon.
- the pressure of the pressure medium from the pump cylinder 12 is therefore used in the cylinder space 18 of the pressure cylinder 15 to pre-accelerate the die cushion unit and thus the sheet metal counter-holder.
- This pressure is composed of a static working pressure and a required acceleration pressure.
- the static working pressure results from the area difference between the pressure cylinder surface 17 ⁇ of the piston 17 minus the auxiliary cylinder surface 41 'of the piston 41 divided by the upper ring surface 17' of the piston 17.
- the die cushion When the upper tool 7 strikes the sheet metal counterholder 6, the die cushion is suddenly accelerated from 80% to 100% ram speed against approximately 10% die cushion force. After a 20 mm die cushion stroke, the piston 41 of the auxiliary cylinder 39 runs against its stop 43. The die cushion force then suddenly increases to approximately 99% of that determined by the pressure accumulator 21 Strength increased. The remaining portion of the force of 10% is still effective by the compressed medium required for the pre-acceleration on the annular surface 17 'of the piston 17. During the further downward movement of the die cushion unit, the force acting on the die cushion can be changed by pressure change in the line 19 or 22 by means of the hydraulic valve 27 by pressure medium from the pressure accumulator 25.
- the pressure accumulator 25 is preloaded so high that the cushion force can be canceled by counter pressure in the pressure cylinder 15.
- the hydraulic valve 27 connects the hydraulic line 22 either to the pressure accumulator 25 or to an unpressurized hydraulic tank 46. In the basic position (starting position), both stops are blocked.
- the pressure relief valve 29 pretensions the hydraulic line 22 with approximately 5 bar.
- the die cushion 10 moves upward at approximately 80% of the speed of the press ram 8. This is done in the pressure accumulator 21 energy stored during the downward movement of the press ram 8 is now used in addition to the ram upward movement. Approx. 20 mm before the upper end of the stroke, the die cushion rest 10 'hits the lower plunger 45 of the auxiliary cylinder 39. As a result, the die cushion upward force is suddenly reduced to approximately 10% of the maximum force, since in turn the balance between the upper piston surface 41' and the lower one Set piston surface 17 ⁇ via the connecting line 20, 42.
- the press ram 8 is accordingly connected to a plurality of pump cylinders 12, which are arranged in particular in the four corner regions. These pump cylinders 12 interact with pressure cylinders 15 in the sense of a pre-acceleration of the pressure cheek 10 and a subsequent bracing.
- the dosing memory 33 with the adjusting device 38 Hydraulic tensioning of the die cushion during the downward stroke of the press ram, so to speak, unlocked and tensioned again only shortly before the upper tool 7 strikes the sheet metal counterholder 6, thus initiating a preliminary movement.
- the differential speed between the press ram 8 and the pressure cheek 10 and thus the speed of impact of the upper tool 7 on the sheet metal holder 6 can be determined.
- the pressure in the hydraulic line 22 and thus in the connecting line 19 and thus in the effective pressure space between the pump cylinder 12 and pressure cylinder 15 can be controlled by means of the hydraulic valve 27 and / or program-controlled.
- the majority of the pressure energy required for the die cushion force during the downward movement is not converted into heat, but can be stored in the pressure accumulator 21 and 33 and reused for the upward movement of the press ram 8.
- the auxiliary cylinder 39 reduces the force on the pressure cheek 10 during its preliminary differential movement downwards until the time when the piston 41 is seated.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Presses And Accessory Devices Thereof (AREA)
- Shaping Metal By Deep-Drawing, Or The Like (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3930349 | 1989-09-12 | ||
DE3930349 | 1989-09-12 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0417754A2 true EP0417754A2 (fr) | 1991-03-20 |
EP0417754A3 EP0417754A3 (en) | 1991-06-12 |
EP0417754B1 EP0417754B1 (fr) | 1993-09-08 |
Family
ID=6389202
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP90117537A Expired - Lifetime EP0417754B1 (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) | EP0417754B1 (fr) |
DE (1) | DE59002628D1 (fr) |
ES (1) | ES2045702T3 (fr) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0692323A3 (fr) * | 1994-07-15 | 1996-04-10 | Toyota Motor Co Ltd | Presse à cylindres d'amortissement comportant deux chambres dont la différence de pression est ajustable par un réglage de la force de retenue des pièces découpées |
ES2084558A2 (es) * | 1993-11-25 | 1996-05-01 | Fagor S Coop Ltda | Sistema de preceleracion para un cojin hidraulico de prensa. |
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 |
EP1138406A2 (fr) * | 2000-03-30 | 2001-10-04 | FAGOR, S.Coop | Presse avec un coussin hydraulique et un système pour regler la force de pression et la position du serre-flan dudit coussin hydraulique |
WO2002087801A1 (fr) * | 2001-04-27 | 2002-11-07 | Schuler Pressen Gmbh & Co.Kg | Dispositif d'emboutissage hydraulique |
WO2006040105A2 (fr) * | 2004-10-07 | 2006-04-20 | Feintool International Management Ag | Procede et dispositif pour la fabrication et/ou l'usinage de pieces |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10125078B4 (de) * | 2001-04-27 | 2007-04-05 | Schuler Pressen Gmbh & Co. Kg | Hydraulische Zieheinrichtung |
DE102006057051A1 (de) | 2006-11-30 | 2008-07-03 | Müller Weingarten AG | Umformpresse mit im Schiebetisch integrierter Ziehkissenfunktionalität |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3619109A1 (de) * | 1985-10-30 | 1987-05-07 | Warnke Umformtech Veb K | Einrichtung zur auftreffstossdaempfung fuer ziehkissen an pressen |
DE3835470A1 (de) * | 1987-12-14 | 1989-06-22 | Warnke Umformtech Veb K | Rueckzugssteuerung fuer ziehkissen an pressen |
-
1990
- 1990-09-12 EP EP90117537A patent/EP0417754B1/fr not_active Expired - Lifetime
- 1990-09-12 DE DE90117537T patent/DE59002628D1/de not_active Expired - Fee Related
- 1990-09-12 ES ES90117537T patent/ES2045702T3/es not_active Expired - Lifetime
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3619109A1 (de) * | 1985-10-30 | 1987-05-07 | Warnke Umformtech Veb K | Einrichtung zur auftreffstossdaempfung fuer ziehkissen an pressen |
DE3835470A1 (de) * | 1987-12-14 | 1989-06-22 | Warnke Umformtech Veb K | Rueckzugssteuerung fuer ziehkissen an pressen |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ES2084558A2 (es) * | 1993-11-25 | 1996-05-01 | Fagor S Coop Ltda | Sistema de preceleracion para un cojin hidraulico de prensa. |
EP0692323A3 (fr) * | 1994-07-15 | 1996-04-10 | Toyota Motor Co Ltd | Presse à cylindres d'amortissement comportant deux chambres dont la différence de pression est ajustable par un réglage de la force de retenue des pièces découpées |
US5687598A (en) * | 1994-07-15 | 1997-11-18 | Toyota Jidosha Kabushiki Kaisha | Press having cushioning cylinders each having two chambers whose pressure difference is adjustable to control blank-holding force |
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 | 冲压方法和冲压系统 |
EP1138406A2 (fr) * | 2000-03-30 | 2001-10-04 | FAGOR, S.Coop | Presse avec un coussin hydraulique et un système pour regler la force de pression et la position du serre-flan dudit coussin hydraulique |
EP1138406A3 (fr) * | 2000-03-30 | 2003-05-21 | FAGOR, S.Coop | Presse avec un coussin hydraulique et un système pour regler la force de pression et la position du serre-flan dudit coussin hydraulique |
WO2002087801A1 (fr) * | 2001-04-27 | 2002-11-07 | Schuler Pressen Gmbh & Co.Kg | Dispositif d'emboutissage hydraulique |
WO2006040105A2 (fr) * | 2004-10-07 | 2006-04-20 | Feintool International Management Ag | Procede et dispositif pour la fabrication et/ou l'usinage de pieces |
WO2006040105A3 (fr) * | 2004-10-07 | 2006-10-26 | Feintool Internat Man Ag | Procede et dispositif pour la fabrication et/ou l'usinage de pieces |
JP2008515641A (ja) * | 2004-10-07 | 2008-05-15 | ファインツール インターナショナル マネージメント アーゲー | 部品を製造及び/又は加工する方法及びその装置 |
US7681427B2 (en) | 2004-10-07 | 2010-03-23 | Feintool International Management Ag | Method and device for the production and/or machining of pieces |
Also Published As
Publication number | Publication date |
---|---|
DE59002628D1 (de) | 1993-10-14 |
ES2045702T3 (es) | 1994-01-16 |
EP0417754A3 (en) | 1991-06-12 |
EP0417754B1 (fr) | 1993-09-08 |
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