EP3593983B1 - Fluiddynamische anlage zum gesteuerten antrieb des stössels einer presse - Google Patents

Fluiddynamische anlage zum gesteuerten antrieb des stössels einer presse Download PDF

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Publication number
EP3593983B1
EP3593983B1 EP19020422.2A EP19020422A EP3593983B1 EP 3593983 B1 EP3593983 B1 EP 3593983B1 EP 19020422 A EP19020422 A EP 19020422A EP 3593983 B1 EP3593983 B1 EP 3593983B1
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Prior art keywords
pump
group
plant
fluid
servo
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EP19020422.2A
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English (en)
French (fr)
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EP3593983A1 (de
Inventor
Luciano Zanolini
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Voith Turbo Srl
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Voith Turbo Srl
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/163—Control arrangements for fluid-driven presses for accumulator-driven presses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/18—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram

Definitions

  • the invention concerns a fluid-dynamic plant for the controlled drive of the ram of a press, generally used to manage the functioning steps of the working piston and at the same time avoid waste of energy.
  • Fluid-dynamic plants which are used to move the pushing piston of a press in the active work and return travels, in particular of a press typically used in the field of production of shaped metal sheets to produce household appliances.
  • a known fluid-dynamic plant comprises, very schematically, a fluid-dynamic pump with a variable flow rate that is driven by an asynchronous motor.
  • the pump by means of a fluid-dynamic circuit in which oil flows, is connected to a control servo-valve, which functions as a multi-position distributor, and, through this, to a pressurized oil accumulator group or, alternatively according to the work positions of the servo-valve, to the chamber where the piston of the pushing cylinder slides.
  • the servo-valve in this type of fluid-dynamic group, works in practice as an element to control the movements of the cylinder which, in the work step, occur in three consecutive travel segments and precisely a first segment of rapid approach to the piece of metal sheet to be worked positioned on a work plane of the press, a second segment in which work begins and a third segment in which the work to be performed is completed.
  • the first segment has a travel of about 400 millimeters
  • the second segment has a travel of about 60 millimeters
  • the third segment has a travel of about 15 millimeters.
  • the piston In the first travel segment, the piston, starting from a resting position in which it is completely raised from the piece of metal sheet to be worked, that is, from the top dead center, rapidly descends by gravity toward it, controlled in the descent by the servo-valve, putting the stem-side seating of the piston in connection with a drain.
  • the servo-valve switches its configuration and connects the fluid-dynamic pump with an accumulator group, closing the connection between the pump and the sliding seat of the piston.
  • the pump is put into function by the asynchronous motor which assumes an active function and which, since the connection with the sliding seat of the piston is intercepted by the servo-valve, supplies pressurized oil to the accumulator group, in the specific case in the form of a pair of accumulators, until oil is accumulated inside them at a predetermined pressure value, as a function of the force necessary to complete the second travel segment.
  • the servo-valve switches its position into the configuration in which it puts the accumulator group and the sliding seat of the piston in connection with each other, typically the thrust chamber side, that is, the side opposite the stem side, in which, after the first travel segment of the piston, the pressure is substantially zero.
  • the oil pressure increases progressively, causing the piston to perform the second travel segment in which the tool starts its active action of working and pre-shaping the piece of metal sheet.
  • the servo-valve switches its position connecting the pump, typically with a variable flow rate, with the thrust side chamber of the sliding seat of the piston which, due to a further increase in the pressure inside it generated by the oil sent by the pump, of metal sheet, using the maximum pressure of the oil, known as the specification power.
  • the hydraulic drive includes a differential cylinder that has a first pressure chamber and a second pressure chamber and a differential piston, a first hydraulic pump that includes a pump intake and a pump outlet, a directional control valve having a first switching position and a second switching position, a high pressure tank and an additional hydraulic cylinder that includes an additional pressure chamber hydraulically connected with the pump intake and with the high pressure tank and an additional piston limiting the additional pressure chamber.
  • the differential piston is movably coupled with the additional piston, wherein in the first switching position of the directional control valve the first pressure chamber is hydraulically connected with the second pressure chamber and in the second switching position of the directional control valve the second pressure chamber is not hydraulically connected with the first pressure chamber.
  • Another disadvantage is that the pump sends oil to an accumulator group until it reaches an excessive predetermined pressure therein, in particular at the beginning of the performance of the second segment, that is, when the mold is simply resting on the metal sheet and the beginning of the deformation occurs with a limited thrust.
  • a further disadvantage is that the servo-valve produces, during the steps of controlling the flows of pressurized oil, a high overheating which requires the adoption of suitable and expensive cooling devices, both air/oil and also water/oil.
  • Another disadvantage is that the asynchronous motor used for the functioning of the fluid-dynamic pump has to have a sufficiently high power to perform the third travel segment in the required time.
  • One object of the invention is to improve the state of the art.
  • Another object of the invention is to provide a fluid-dynamic plant for the controlled drive of the ram of a press that allows to generate energy when it is not required to drive the piston of the press, in particular during the rapid descent step, when the oil present in the stem-side chamber of the cylinder makes the step, when the oil present in the stem-side chamber of the cylinder makes the servo-pump rotate, transforming the latter into a motor and the brushless motor into a generator.
  • a further object of the invention is to provide a fluid-dynamic plant for the controlled drive of the ram of a press that does not produce overheating.
  • Another object of the invention is to provide a fluid-dynamic plant for the controlled drive of the ram in the third travel segment, that is, when the maximum force is required to complete the third segment within the minimum time required.
  • a fluid-dynamic plant is provided for the controlled drive of the ram of a press, in accordance with the characteristics of claim 1.
  • references from T1 to T8 generally indicate fluid-dynamic drains provided in the plant for the controlled drive of the ram of a press, according to the invention, and BC generally indicates a battery of capacitors.
  • Reference 40 indicates a conventional cylinder of a press, which comprises a piston 20 which is received sliding in a sliding seating 30.
  • the piston 20 has a stem 12 and divides the sliding seating 30 into two parts, namely a stem-side chamber 30A and a thrust-side chamber 30B.
  • the latter is connected to a suction valve 13 which allows to supply oil to the thrust chamber 30B under certain conditions described below, oil that is contained in a tank 13A.
  • the stem-side chamber 30A is connected by means of a line 31 to a first pump 1 able to rotate alternately in two directions of rotation, indicated respectively with SX and DX, and which is mechanically connected to a first servo-motor 11 of the brushless type, hereafter first servo-motor 11 for short.
  • a distributor 3 is positioned along the line 31, which has two functioning positions, indicated with 3A and 3B respectively.
  • a safety unit 4 is interposed between the distributor 3 and the stem-side chamber 30A, which has the task of preventing the accidental fall of the piston 20 and which comprises a safety valve (not shown) which can be activated or deactivated on command.
  • a maximum pressure valve 2 is provided which can be pre-calibrated and which serves to maintain the first pump 1 in safe conditions, that is, to drain oil to an outlet T1 in case of excessive increase of the pressure.
  • the distributor 3 is connected to an accumulator group 6, comprising in practice one or more accumulators associated with one another in a battery, by means of a second line 32 and a pressure transducer 5 is disposed upstream thereof, which is pre-calibrated to interrupt the functioning of the first pump 1 when a predetermined pressure value is reached inside the accumulator group 6.
  • An interception cartridge 7 is disposed immediately downstream of the accumulator group 6, which has the function of intercepting the oil that comes from the accumulator group 6 under certain functioning conditions of the fluid-dynamic group according to the invention.
  • the interception cartridge 7 is controlled by a second distributor, or pilot 8, which has two work positions, namely a position 8A, in which the interception cartridge 7 is maintained in a closed position, and a position 8B in which the interception cartridge 7 is free to open the connection of the second line 32 toward an power generating group.
  • a second distributor or pilot 8 which has two work positions, namely a position 8A, in which the interception cartridge 7 is maintained in a closed position, and a position 8B in which the interception cartridge 7 is free to open the connection of the second line 32 toward an power generating group.
  • a unidirectional valve 36 is located on the second line that allows the passage of a flow of oil only from the distributor 3 toward the accumulator group 6.
  • the power generating group comprises a second pumping group consisting of two pumps, namely a second 9A and a third 9B pump, both of the type with two quadrants, which have respective directions of rotation R1 and R2 and which are mechanically connected to each other.
  • the third pump 9B is mechanically connected to a second servo-motor 10 of the brushless type, hereafter second servo-motor 10 for short, while the second pump 9A is connected to the thrust-side chamber 30B by means of the third line 35 and to a drain T7 by means of a fourth line 36.
  • a quick decompression group is interposed between the thrust-side chamber 30B and the second pump 9A, which serves to quickly decompress the thrust-side chamber 30B after the step in which the piston 20 works a piece to be worked has been completed, and to allow the piston 20 to return to the top dead center of the sliding seating 30.
  • FIG. 3 a second possible embodiment of the fluid-dynamic plant for the controlled drive of the ram of a press, according to the invention, is shown.
  • the difference with respect to the first version of fig. 1 is that the second pump 9A and the third pump 9B of the second pumping group have been replaced with a single pump 9C of the type with four quadrants and double direction of rotation, as indicated with the arrows SX and DX.
  • the suction of the pump 9C is connected to the draint T7 which also uses the quick decompression group 14.
  • the latter comprises a pair of interception cartridges 14C which are located in parallel and which are commanded by a third distributor, or pilot 15, which has two work positions 15A and 15B.
  • Both the interception cartridges 14C are maintained in the normally closed position in order to intercept the flow of oil, in which the pilot 15 is in the work position 15A and only in a certain condition described below do they switch their position from normally closed to open.
  • the operation of the invention is as follows: in order to perform work on a piece positioned in a known manner between a mold 12A and a counter-mold 12B of a press, the piston 20 has to perform a first travel segment of rapid approach, indicatively of about 400 millimeters, a second segment to deform the piece, of about a further 60 millimeters, and finally a third segment of about 15 millimeters to complete the work of the piece.
  • the piston 20 rises upward, until it reaches a top dead center (TDC) of the sliding seating 30, ready for a subsequent work cycle of another piece.
  • TDC top dead center
  • the piston 20 In the starting configuration of each work cycle, the piston 20 is therefore in a position raised to the TDC and this position is maintained by the anti-fall safety unit 4 in which the safety valve is in a closed configuration, while the distributor 3 is in the work position 3B and the first pump 1, driven by the first servo-motor 11, recharges the accumulator group 6, in which pressurized oil is already present, a residue of a previous work cycle.
  • the interception cartridge 7 is in a closed configuration since the pilot 8 is in the work position 8A connecting it to the outlet T6.
  • the configuration of the fluid-dynamic group for presses according to the invention is as follows: the safety unit 4 is deactivated by switching the safety valve to the open position.
  • the first pump 1 is driven in rotation in the direction SX by the pressurized oil which comes from the stem-side chamber 30A through the fluid dynamic line 31, thrust by the displacement caused by the weight of the piston 20, integral with the ram: the first pump 1 therefore is in a passive functioning step in which it drives the first servo-motor 11 which controls its speed of rotation.
  • the first servo-motor 11, therefore, in this step has the dual function both of generator of power, which can be sent to the battery of capacitors BC, or released directly to a utility electric network, and also of device to control the speed of rotation of the first pump 1 and, consequently, the speed of descent of the piston 20.
  • the distributor 3 switches its work position from 3A to 3B ( fig. 2 ), connecting the first pump 1 with the accumulator group 6.
  • the interception cartridge 7, advantageously calibrated to a predetermined threshold value, is maintained in the closed position by the work position 8A of the pilot 8, the one-way valve 36 prevents oil return refluxes toward the first pump 1 and the accumulator group 6 is charged up to a maximum pressure, determined by the maximum value to which the pressure transducer 5 is calibrated.
  • the pilot 8 is switched to the work position 8B in which the interception cartridge 7 moves from the closed position to the open position, so that the oil coming from the accumulator group 6 reaches the third pump 9B making it rotate.
  • the third pump 9B drives both the second servo-motor 10 and also the second pump 9A to which it is mechanically connected and the latter sends oil toward the thrust-side chamber 30B of the sliding seating 30, removing it from the tank T7.
  • the pressure inside the thrust-side chamber 30B increases progressively, causing the piston 20 to perform the second travel segment, typically intended to deform the piece between the mold 12A and the counter-mold 12B.
  • the oil that occupies the stem-side chamber 30A is progressively drained toward the outlet T2, allowing the piston 20 to descend and to perform the second travel segment of deformation.
  • the second servo-motor 10, in this step, acts as a generator of power which is sent to the first servo-motor 11 which is simultaneously rotating the first pump 1 in order to send oil to the accumulator group 6.
  • the same accumulator group 6 feeds the second pump 9A and the third pump 9B and of these, the third pump 9B rotates the second servo-motor 10, which therefore acts as a generator.
  • the first servo-motor 11 is stopped while the second servo-motor 10 is active which, by driving the second pump 9A and the third pump 9B, sends oil coming from the accumulator group 6 to the thrust-side chamber 30B.
  • piston 20 After completing the work cycle of the piece, piston 20 has be returned to the TDC of the sliding seating 30 to then begin a subsequent work cycle.
  • the quick decompression group 14 is activated which puts, through the fluid-dynamic line 35, the thrust-side chamber 30B in communication with the drain T7, quickly and progressively reducing the pressure inside the thrust-side chamber 30B.
  • the distributor 3 switches its work position from 3B to 3A restoring the connection between the first pump 1 and the stem-side chamber 30A.
  • the first servo-motor 11 is activated and drives the first pump 1 into rotation in the direction DX, which sends oil toward the stem-side chamber 30A, passing through the safety unit 4, still in an inactive configuration.
  • This configuration of the fluid-dynamic plant allows to progressively fill the stem-side chamber 30A with pressurized oil by raising the piston 20 until it reaches the TDC position.
  • the safety unit 4 When this position is reached, the safety unit 4 is reactivated, the safety valve thereof closes and the plant is ready to perform a subsequent work cycle as described.
  • the first pump 1 driven by the first servo-motor 11, once again sends oil to the accumulator group 6 in order to top up the oil used in the previous work cycle.
  • the "transfer" of the press i.e. the device typically provided to grip and translate the pieces to be worked onto the work surface, repositions the piece to be worked between the mold 12A and the counter-mold 12B.
  • the transmission of oil to the accumulator group 6 is interrupted when the pressure transducer 5 signals that the predetermined pressure at which it is calibrated has been reached.
  • the second servo-motor 10 which commands the second pump 9A and the third pump 9B, or, in the alternative version, the four-quadrant pump 9C, no longer operates as a generator, but as a servo-motor which sends oil to the thrust-side chamber 30B of the piston 20 which commands the advance of the ram having a high pressure present in the accumulator group 6.
  • the second pump 9A and the third pump 9B, or the four-quadrant pump 9C could also have a cubic capacity three times greater than that of the first pump 1, since they have a second servo-motor 10 which has the same or similar sizes to those of the first servo-motor 11, because the difference in pressure between the one present in the accumulator group 6 and the pressure necessary to make the ram advance is substantially equal to one third of the pressure available on the first pump 1.
  • the pump 1 remains deactivated while only the second servo-motor 10 functions, which commands the second pump 9A and the third pump 9B, or the four-quadrant pump 9C.
  • the sizes of the first servo-motor 11 are contained, because the first pump 1, which, in the example in question, typically has a flow rate of 150 Lt/min, is in turn sized in order to make the ram, and therefore the piston 20, rise toward the TDC at a desired speed, as well as to load the accumulator group 6 when the press is stopped.
  • the step of rapid descent of the ram is controlled by the first servo-motor 11 which functions as a generator and the energy produced can be fed into a supply network or it can load the battery of capacitors BC.
  • the opening of the interception cartridge 7 connects the accumulator group 6 with the two pumps 9A and 9B: the difference in pressure that exists between the accumulator group 6 and the pressure necessary to make the piston 20 perform the second travel segment produces energy by means of the second servo-motor 10 which in this condition functions as a generator.
  • the first pump 1 stops so as to not generate a simultaneous functioning of the two servo-motors 10 and 11.
  • the two pumps 9A and 9B are driven by the second servo-motor 10 which has the characteristic of having sizes similar to those of the first servo-motor 11, because, despite having a high cubic capacity so as to quickly complete the third travel segment, it has the advantage of removing oil from the accumulator group 6 in which a residual pressure of about 190 bar remains, after having completed the third travel segment.
  • the two pumps 9A and 9B supply pressurized oil to the thrust-side chamber 30B of the sliding seating 30 at the desired pressure of 280 bar, removing oil from the accumulator group 6 loaded at a pressure of about 210 bar.
  • the two pumps 9A and 9B Compared to the first pump 1, which in this specific case has a flow rate of 150 Lt/min operating at 240 bar (load value of the battery of accumulators) absorbing 64 kW, the two pumps 9A and 9B have a total flow rate of 400 Lt/min to feed the thrust-side chamber 30B of the cylinder at 280 bar and work with a pressure of 90 bar, absorbing equally 64 kW.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Presses (AREA)
  • Silver Salt Photography Or Processing Solution Therefor (AREA)

Claims (9)

  1. Fluiddynamische Anlage zum gesteuerten Antrieb eines Stößels einer Presse, umfassend:
    - einen Schubkolben (20), der in einem Schiebesitz (30) einer Presse schiebbar aufgenommen ist, der vom Stößel in eine schaftseitige Kammer (30A) und in eine schubseitige Kammer (30B) geteilt ist;
    - eine erste Pumpe (1) eines Druckmediums, die von einem ersten Servomotor (11) angetrieben und/oder gesteuert wird, der funktionsmäßig damit verbunden ist;
    - eine Speichergruppe (6) des genannten Druckmediums, die alternativ mit der genannten ersten Pumpe (1) oder mit dem genannten Schiebesitz (30) fluiddynamisch verbunden ist;
    - eine Verteilergruppe (3) zur abwechselnden fluiddynamischen Verbindung der genannten ersten Pumpe (1) mit dem genannten Schiebesitz (30) oder der genannten ersten Pumpe (1) mit der genannten Speichergruppe (6);
    - eine Stromerzeugergruppe (34), die zwischen der genannten Speichergruppe (6) und der genannten schubseitigen Kammer (30B) zwischengeschaltet ist,
    DADURCH GEKENNZEICHNET, DASS ein zweiter Verteiler oder Steuergerät (8) zum Steuern einer Patrone (7) für das Abfangen des genannten Druckmediums zwischen der genannten Speichergruppe (6) und der genannten Stromerzeugergruppe (34) zwischengeschaltet ist.
  2. Anlage nach Anspruch 1, worin die genannte Stromerzeugergruppe (34) eine zweite Antriebspumpengruppe (9A,9B;9C) umfasst, die mit der genannten schubseitigen Kammer (30B) und mit der genannten Speichergruppe (6) fluiddynamisch verbunden ist.
  3. Anlage nach Anspruch 2, worin die genannte zweite Pumpengruppe (9A,9B;9C) mit einem zweiten Servomotor (10) verbunden ist, der von der genannten zweiten Pumpengruppe angetrieben ist und vom genannten ersten Servomotor (11) unabhängig ist.
  4. Anlage nach Anspruch 2, worin die genannte zweite Pumpengruppe umfasst:
    - eine zweite Zwei-Quadranten-Pumpe (9A); und
    - eine dritte Zwei-Quadranten-Pumpe (9B), die mit der genannten zweiten Zwei-Quadranten-Pumpe (9A) verbunden ist.
  5. Anlage nach Anspruch 2, worin die genannte zweite Pumpengruppe (9A,9B;9C) eine Vier-Quadranten-Pumpe (9C) umfasst.
  6. Anlage nach Anspruch 1, worin eine Schnell-Dekompressions-Gruppe (14) zwischen der genannten schubseitigen Kammer (30B) und der genannten Stromerzeugergruppe (34) zwischengeschaltet ist.
  7. Anlage nach Anspruch 1, worin ein Einweg-Ventil (36) zwischen der genannten ersten Pumpe (1) und der genannten Speichergruppe (6) zwischengeschaltet ist.
  8. Anlage nach Anspruch 7, worin zumindest ein Druckwandler (5) zwischen dem genannten Einweg-Ventil (36) und der genannten Speichergruppe (6) zwischengeschaltet ist.
  9. Anlage nach Anspruch 1, worin die genannte schubseitige Kammer (30B) mit einem Tank (13A) verbunden ist, um das genannte Druckmedium mit der Zwischenschaltung eines Einweg-Ventils (13) aufzunehmen.
EP19020422.2A 2018-07-09 2019-07-09 Fluiddynamische anlage zum gesteuerten antrieb des stössels einer presse Active EP3593983B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT102018000007019A IT201800007019A1 (it) 2018-07-09 2018-07-09 Impianto fluidodinamico per l'azionamento controllato della slitta di una pressa

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Publication Number Publication Date
EP3593983A1 EP3593983A1 (de) 2020-01-15
EP3593983B1 true EP3593983B1 (de) 2023-06-07

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Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4320213A1 (de) * 1993-06-18 1994-12-22 Schloemann Siemag Ag Stauchpressenhauptantrieb
EP0641644A1 (de) * 1993-09-02 1995-03-08 Maschinenfabrik Müller-Weingarten AG Verfahren zur Regelung des Antriebs einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens
EP1092097B1 (de) * 1998-06-27 2004-09-22 Bruun EcoMate AB Mobile arbeitsmaschine
DE19831624A1 (de) * 1998-07-15 2000-01-20 Mueller Weingarten Maschf Hydraulischer Antrieb für eine Presse
ATE444157T1 (de) * 2000-09-20 2009-10-15 Laeis Gmbh Steuervorrichtung für eine hydraulische presse sowie verfahren zu deren betrieb
WO2011105973A1 (en) * 2010-02-25 2011-09-01 Demirer Teknolojik Sistemler Sanayi̇ Ticaret Limited Sirketi Hydraulic system providing power saving in ceramic press machines and method for providing it
DE102012006981B4 (de) * 2012-04-05 2019-02-21 Schuler Pressen Gmbh Hydraulische Presse
DE102014218886B3 (de) * 2014-09-19 2015-11-12 Voith Patent Gmbh Hydraulischer Antrieb mit Eilhub und Lasthub

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IT201800007019A1 (it) 2020-01-09

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