EP0716916A1 - 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 - Google Patents

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 Download PDF

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Publication number
EP0716916A1
EP0716916A1 EP95117302A EP95117302A EP0716916A1 EP 0716916 A1 EP0716916 A1 EP 0716916A1 EP 95117302 A EP95117302 A EP 95117302A EP 95117302 A EP95117302 A EP 95117302A EP 0716916 A1 EP0716916 A1 EP 0716916A1
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EP
European Patent Office
Prior art keywords
cylinders
pressure
tappet
pressure oil
braking
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
EP95117302A
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German (de)
English (en)
Other versions
EP0716916B1 (fr
Inventor
Wieland Dr. Petter
Markus Dr. Müller
Gregor Geist
Andreas Schlag
Steffen Schmidt
Siegfried Klavehn
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.)
Umformtechnik Erfurt GmbH
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Umformtechnik Erfurt GmbH
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Publication date
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Publication of EP0716916A1 publication Critical patent/EP0716916A1/fr
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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
    • B30B1/265—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks using a fluid connecting unit between drive shaft and press ram
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0076—Noise or vibration isolation 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
    • B30B15/14—Control arrangements for mechanically-driven presses

Definitions

  • the invention relates to a method for low noise and shock-free adjustment of the upper and lower tools of mechanical seizures, in particular presses for forming sheet metal parts at high stroke rates according to the preamble of claim 1.
  • the invention further relates to a ram drive for mechanical presses with a device for Implementation of the above-mentioned method with the features of the preamble of claim 4.
  • the impact impact has a negative impact on the quality of the parts and impermissible noise pollution for the worker.
  • the costly articulated or lever presses have reduced the impact, but in many cases, especially when using pneumatic cushions, additional devices are required to pre-accelerate the moving masses. These devices cannot be used for cutting work without a cushion in the table.
  • the tappet drive is designed as an inner and outer tappet.
  • the inner plunger is driven by controllable and adjustable lifting cylinders that are attached to the outer plunger.
  • From DD 279 639 A1 and DD 295 798 A5 two solutions are known in which the alignment process was implemented by controlled lifting cylinders which are arranged between the pressure points and the tappet.
  • None of the proposed solutions fulfills the requirements of using simple means to create a powerful and robust process for the alignment process while taking into account the high efficiency of the machine.
  • the object of the invention is to propose a method and a device according to which the adjustment process when the tool is closed is safely mastered with simple means and high efficiency.
  • Claim 3 specifies a method according to which the optimum setting parameters for carrying out the method according to Claims 1 and 2 can be determined.
  • a tappet drive with a device for performing the method according to claims 1 or 2 is described in claim 4.
  • Claims 5 to 7 contain further advantageous refinements of the device according to Claim 4.
  • the optimal setting parameters are determined in the procedure described below.
  • the adjustment process is divided into two areas - the braking and the acceleration process. If the process and die cushion forces are negligibly small, the same distances are provided for braking and acceleration, i.e. half the relative stroke.
  • the following model considerations can be used as a basis for influencing the braking process in a targeted manner.
  • the dominant variable when braking is the kinetic energy of the tappet, which is characterized by the tappet mass and the current tappet speed.
  • a defined force is opposed to the tappet during the braking process (pressure of the hydraulic oil in the pressure oil reservoir) and the kinetic energy is largely converted into potential energy (spring tension work) via the braking distance. Flow-related losses occur.
  • the plunger movement can be described in a simplified manner using the equation of motion of a weakly damped, oscillatory system of the second order.
  • the solution to the differential equation is the relative path that the tappet travels in the direction of the pressure point.
  • the tappet When braking is initiated, the tappet is "uncoupled” from the drive and slows down until the desired impact speed is reached.
  • a certain braking distance is covered.
  • the braking distance and the braking speed can be represented as a function of time and the braking force as a system of equations.
  • the solution to the system of equations specifies the required braking force and the associated braking time that the plunger needs to achieve the desired impact speed after half the relative travel. This allows the crank angle to be specified at the time of impact.
  • the starting point (eg by cams) for initiating the braking process can be determined exactly.
  • the acceleration process is initiated immediately after touchdown. With the acceleration, the circuit-related constraints arise.
  • the ram assumes half of the current drive speed assuming the area of the brake and pressure point cylinders are the same.
  • the inner stop is reached. If die cushion and process forces have to be expected during the adjustment process, the spring stiffness of the enclosed hydraulic oil plays a role.
  • the hydraulic forced operation is only fully effective when the oil in the pipelines is sufficiently pre-stressed. The result is a delay in the acceleration process, so that the inner stop may be reached at a higher speed than intended. In this case, the ratio between the braking and acceleration distances must be changed in such a way that the acceleration distance increases and the braking distance shortens.
  • additional hydraulically actuated pressure point cylinders 1 with single-acting short-stroke pistons 1a are arranged in the pressure points of the tappet 4 between the connecting rods and the tappet 4.
  • the piston rods 2 are articulated by brake cylinders 3 (with piston rods on both sides), while the housing is fastened to the tappet 4.
  • the upper and lower spaces of the brake cylinders 3 can be shut off from one another by the valve 5 if required. If necessary, oil is sucked out of the pressure oil reservoir 7, which is acted upon as a piston accumulator, by means of a check valve 6.
  • the pressure oil reservoir 8 serves as an energy converter for the tappet 4 to be braked and accelerated.
  • the check valve 11 When the press clutch is switched on, the check valve 11 is unlocked, so that the short-stroke pistons 1 are spread under the preload pressure of the pressure oil reservoir 8 before the tappet 4 closes with the upper tool.
  • the blocking of the valve 5 brings about rapid braking of the tappet 4 by displacing the oil from the upper spaces of the brake cylinders 3 into the pressure oil reservoir 8.
  • the short-stroke pistons 1 a push the oil into the lower spaces of the brake cylinders 3.
  • oil is drawn in from the pressure oil reservoir 7 via the check valve 6.
  • the plunger 4 with the upper tool is placed on the board 19 at a significantly reduced speed. The rest of the oil the brake cylinder 3 is pressed from the pressure point cylinders 1a into the lower spaces.
  • the tappet 4 with the upper tool, the plate 19, the sheet metal holder 20, the pressure pin 21 and the pressure pin plate (not shown) of the die cushion experience an acceleration force against the head piece 27, which acts until the short-stroke piston 1a reaches its lower mechanical stop.
  • the stroke of the short-stroke pistons 1a represents the adjustment path that the plunger 4 requires in order to be braked to the impact speed and to be accelerated again after it has been placed on the plate 19. This adjustment is made up of the braking distance and the acceleration distance.
  • the ratio of braking distance to acceleration distance is 1: 1 if no external forces act on the tappet 4 while it is being accelerated.
  • the control method provides for the process and cushion forces acting on the tappet 4 to be taken into account by changing the ratio of the braking and acceleration paths.
  • the area of the short-stroke pistons 1a depends on the maximum acceleration force which the tappet 4 can apply at a specific maximum pressure.
  • the housing of the brake cylinder 3 are firmly connected to the tappet 4. So that all elements of the hydraulic circuit are arranged in or on the plunger 4, so that no flexible hydraulic lines are required to make the hydraulic connections between fixed and moving parts of the press.
  • the piston rods 2 of the brake cylinders 3 are firmly connected to the press frame at least at one end.
  • the brake cylinder 3 must be designed as a synchronous cylinder, since both cylinder chambers are short-circuited to each other when the Adjustment process does not take place. If the piston area of the pistons of the brake cylinders 3 is equal to the area of the short-stroke pistons 1a, the speed of the tappet 4 at the end of the alignment process is half the current speed of the connecting rods. The inner stop is reached at this speed. This stop speed can be reduced by making the area of the pistons of the brake cylinders 3 smaller than that of the short-stroke pistons 1 a of the pressure points. For energetic reasons, however, equal area should be sought.
  • This seat valve interrupts the short circuit between the cylinder top and bottom of the brake cylinder 3 during the entire alignment process. With its actuation, it initiates the braking process and must be reactivated at the end of the acceleration process when the oil volume has been displaced from the pressure point cylinders 1 into the brake cylinders 3. This is done in order to avoid overfilling of the pressure oil reservoir 8 and the excess oil being sprayed off via the reservoir safety valve.
  • the oil reaches the pressure oil reservoir 8 from the upper spaces of the brake cylinders 3.
  • the check valve 6, prevents the oil quantity determined for the pressure point cylinder 1 from flowing back into the pressure oil reservoir 7 when the "spreading" of the hydraulic drive is initiated.
  • the pressure oil reservoir 7 which is designed as a piston accumulator, serves as an "oil reservoir” for the entire hydraulic circuit of the hydraulic drive and covers that during the adjustment process occurring volume requirement.
  • the pressure oil reservoir 7 is preloaded to such an extent that the large volume flows which occur briefly do not lead to negative pressure in the system.
  • the pressure oil reservoir 8 designed as a bladder accumulator, is pre-tensioned before the adjustment process so that the pressure prevailing in it causes the required braking force. During the alignment process, it takes the amount of oil that is displaced from the brake cylinders 3 and releases this amount of oil when the hydraulic drive "spreads" to the pressure point cylinder 1. If the surfaces of the pistons of the brake cylinders 3 are equal to those of the short-stroke pistons, no additional oil has to be supplied to the pressure oil reservoir 8 via the pump.
  • the pressure relief valve 9 is preferably designed as a continuous valve and also serves to set the required brake pressure within a storage tank charging control. If the pressure oil reservoir 8 is filled to the required degree, the pump is set to pressureless circulation.
  • the unlockable check valve 11 is activated when the drawing process is complete and the plunger 4 must be brought back to its starting position. That is, the pressure point cylinders (1) are refilled by connecting them to the pressure oil reservoir 8 via the unlockable check valve 11.
  • the "acceleration”, ie the second phase of the alignment process, is initiated. It is ensured by switching to a higher pressure level that that emerging from the pressure point cylinders 1 "Excess" oil no longer reaches the pressure oil reservoir 7 via a pressure limiting valve, but is forced into the lower spaces of the brake cylinder 3. Thus, a “hydraulic ratio” is activated, which moves the plunger 4 against the tool at half the speed of the connecting rods.
  • the tappet 4 is braked with the upper tool analogously to the circuit arrangement according to FIG. 2 with the check valve 11 open.
  • This unlockable check valve 11 is also initially opened during the acceleration process. It closes before the short-stroke pistons 1a have reached the end position.
  • the continuous valve 10 acts as a damping valve until the short-stroke piston 1a stops.
  • the balancing device is designed to be controllable and brakes the plunger 4 to the required waypoint and with sufficient intensity after decoupling the flow of force in the pressure points.
  • at least one valve 15 is arranged between the balancing cylinder 13 and the expansion tank 14.
  • Pressure relief valves 16 are installed in the pressure chamber of the balancing cylinders 13 on the one hand to avoid impermissible pressures and on the other hand at least one check valve 17 to prevent a negative pressure.
  • the short-stroke pistons 1 a can travel their stroke when the oil enclosed in the pressure point cylinders 1 is pressed into the pressure oil reservoir 7 via the switching or continuous valve 18. Due to the stroke initiation via the drive, not shown, the tappet 4 with the upper tool goes into the closed position.
  • the valve 15 is switched into the blocking position, so that an increased pressure rise in the pressure chamber of the balancing cylinder 13 occurs. This also increases the hydraulic pressure in the pressure point cylinders 1, since the valve 18 also increases is in the locked position. Before the upper tool hits the circuit board 19, the valve 18 is opened depending on the crank angle. The increased balancing force is able to effectively brake the tappet 4, the drive pushing the pressure oil from the pressure point cylinders 1 via the valve 18 into the pressure oil reservoir 7 via the short-stroke piston 1a. The signal is given in such a way that the stroke of the short-stroke piston 1a has not yet been covered before the upper tool reaches the plate 19. As a result of the tappet braking as the tappet movement progresses, the impact speed is significantly reduced.
  • the sheet metal holder 20 with the pressure bolts 21 and the mass-affecting elements of the die cushion are accelerated at a reduced speed and at the same time the cushion force is overcome.
  • the valve 15 is opened so that the pressures in the balancing cylinder 13 and the expansion tank 14 can equalize. In the lowest position, valve 15 is closed again. Due to the pressure collapse in the balancing cylinders 13, the tappet 4 can no longer follow the movement of the drive of the short-stroke pistons 1a. This creates a suction in the pressure point cylinders 1 and the check valve 22 or valve 18 returns the oil from the pressure oil reservoir 7 back to the pressure point cylinder 1. It is also conceivable to alternatively replace the pneumatic balancing cylinders 13 and the expansion tank 14 with hydraulic working cylinders and hydraulic pressure accumulators with hydraulic valves connected in between.
  • hydraulic working cylinders 23 act shortly before the upper tool hits the lower tool on the tappet 4.
  • the piston rods 24 can be coupled to the tappet 4 or acted on by adjusting spindles (not shown here).
  • the working cylinders 23 can be arranged on the lower tool carrier, the machine table, in the side stand or on the head piece 27.
  • the continuous valve 25 is activated via control cams so that the upper tool on the circuit board 19 hits before the short-stroke pistons 1a have completed their stroke.
  • the pressure chamber of the working cylinders 23 can be depressurized. Via the check valve 26, the pressure chamber is filled again during the run-up of the tappet 4, so that the piston rods 24 reach their starting position.
  • the housing of the brake cylinder 3 is mounted on the tappet 4, the piston rod of which is articulated on the head piece 27.
  • the oil is exchanged in volume from the piston chamber on the rod side into the other piston chamber of the brake cylinder 3.
  • the valve 5 is opened and the volume deficit is eliminated by means of expansion tank 28.
  • the expansion tank 28 is preloaded.
  • a pressure relief valve 29 secures the pressure chamber on the rod side of the brake cylinder 3 against impermissible operating pressures.
  • the valve 5 is closed. A braking effect is exerted on the tappet 4 via the enclosed oil column. The relative movement between the short-stroke piston 1a and its stop is achieved by opening the valve 18.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Punching Or Piercing (AREA)
EP95117302A 1994-11-23 1995-11-03 Procédé d'ajustement de l'impact des outils supérieurs et inférieurs d'une presse, diminuant le bruit, et entraínement du coulisseau avec un dispositif d'application du procédé Expired - Lifetime EP0716916B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4441569 1994-11-23
DE4441569A DE4441569A1 (de) 1994-11-23 1994-11-23 Verfahren zum lärm- und stoßarmen Angleichen des Ober- und Unterwerkzeuges von mechanischen Pressen und Stößelantrieb mit einer Einrichtung zur Durchführung des Verfahrens

Publications (2)

Publication Number Publication Date
EP0716916A1 true EP0716916A1 (fr) 1996-06-19
EP0716916B1 EP0716916B1 (fr) 1999-08-25

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EP95117302A Expired - Lifetime EP0716916B1 (fr) 1994-11-23 1995-11-03 Procédé d'ajustement de l'impact des outils supérieurs et inférieurs d'une presse, diminuant le bruit, et entraínement du coulisseau avec un dispositif d'application du procédé

Country Status (3)

Country Link
EP (1) EP0716916B1 (fr)
DE (2) DE4441569A1 (fr)
ES (1) ES2134984T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015016773A1 (de) 2015-12-23 2017-06-29 Wieland Petter Verfahren zum Bearbeiten und zur Formgebung metallischer und anderer Werkstoffe

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1062187A (fr) * 1952-08-25 1954-04-20 Dorstener Eisengiesserei U Mas Procédé de commande de presses à poinçon entraînées mécaniquement
DD279639A1 (de) 1989-01-27 1990-06-13 Warnke Umformtech Veb K Antrieb fuer mechanische pressen
EP0417753A2 (fr) * 1989-09-12 1991-03-20 Maschinenfabrik Müller-Weingarten AG Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes
DD295798A5 (de) 1990-06-26 1991-11-14 Umformtechnik Erfurt Gmbh I G Antrieb mit steuerung fuer mechanische pressen
DE4112942A1 (de) 1991-04-20 1992-10-22 Schuler Gmbh L Mechanisch-hydraulische presse
DE4130004A1 (de) 1991-09-10 1993-03-11 Erfurt Umformtechnik Gmbh Antrieb fuer den stoessel von mechanischen pressen
EP0596697A1 (fr) * 1992-11-05 1994-05-11 Toyota Jidosha Kabushiki Kaisha Procédé et dispositif pour mesurer et régler les forces de pressage dans une presse
DE4302263A1 (de) * 1993-01-28 1994-08-04 Horst Baltschun Mechanische Stufenpresse mit hydraulischen Arbeitshubeinheiten

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1062187A (fr) * 1952-08-25 1954-04-20 Dorstener Eisengiesserei U Mas Procédé de commande de presses à poinçon entraînées mécaniquement
DD279639A1 (de) 1989-01-27 1990-06-13 Warnke Umformtech Veb K Antrieb fuer mechanische pressen
DE3935011A1 (de) * 1989-01-27 1990-08-02 Warnke Umformtech Veb K Antrieb fuer mechanische pressen
EP0417753A2 (fr) * 1989-09-12 1991-03-20 Maschinenfabrik Müller-Weingarten AG Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes
DD295798A5 (de) 1990-06-26 1991-11-14 Umformtechnik Erfurt Gmbh I G Antrieb mit steuerung fuer mechanische pressen
FR2663587A1 (fr) * 1990-06-26 1991-12-27 Erfurt Umformtechnik Gmbh Mecanisme d'entrainement avec commande pour presses mecaniques.
DE4112942A1 (de) 1991-04-20 1992-10-22 Schuler Gmbh L Mechanisch-hydraulische presse
DE4130004A1 (de) 1991-09-10 1993-03-11 Erfurt Umformtechnik Gmbh Antrieb fuer den stoessel von mechanischen pressen
EP0596697A1 (fr) * 1992-11-05 1994-05-11 Toyota Jidosha Kabushiki Kaisha Procédé et dispositif pour mesurer et régler les forces de pressage dans une presse
DE4302263A1 (de) * 1993-01-28 1994-08-04 Horst Baltschun Mechanische Stufenpresse mit hydraulischen Arbeitshubeinheiten

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015016773A1 (de) 2015-12-23 2017-06-29 Wieland Petter Verfahren zum Bearbeiten und zur Formgebung metallischer und anderer Werkstoffe

Also Published As

Publication number Publication date
ES2134984T3 (es) 1999-10-16
DE4441569A1 (de) 1996-05-30
DE59506687D1 (de) 1999-09-30
EP0716916B1 (fr) 1999-08-25

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