EP0615837B1 - Verfahren zur Regelung des Antriebs einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens - Google Patents

Verfahren zur Regelung des Antriebs einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens Download PDF

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Publication number
EP0615837B1
EP0615837B1 EP94103963A EP94103963A EP0615837B1 EP 0615837 B1 EP0615837 B1 EP 0615837B1 EP 94103963 A EP94103963 A EP 94103963A EP 94103963 A EP94103963 A EP 94103963A EP 0615837 B1 EP0615837 B1 EP 0615837B1
Authority
EP
European Patent Office
Prior art keywords
pressure
press ram
cylinder
pump
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.)
Expired - Lifetime
Application number
EP94103963A
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German (de)
English (en)
French (fr)
Other versions
EP0615837A1 (de
Inventor
Carsten Dipl.-Ing. Otremba
Günther Dipl.-Ing. Schaich
Joachim Dipl.-Ing. Beyer
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.)
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 EP0615837A1 publication Critical patent/EP0615837A1/de
Application granted granted Critical
Publication of EP0615837B1 publication Critical patent/EP0615837B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • B30B1/32—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 plungers under fluid pressure
    • B30B1/323—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 plungers under fluid pressure using low pressure long stroke opening and closing means, and high pressure short stroke cylinder 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
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure
    • 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 relates to a method for controlling the drive of a hydraulic press and a device for carrying out the method according to the preamble of claim 1 and the device claim.
  • a press optimization system in which different types of press controls are described.
  • the press control is referred to as a complex automation system in which a large number of function groups have to be subjected to regulation or control.
  • a hydraulic pump is provided in a pressure network, piston-cylinder units being used to drive the press ram, the pressing and working pressures of which are regulated by means of proportional valves.
  • the downward and upward movement of the press ram accomplished by pistons acting on both sides.
  • a complex valve control takes over the flow of the hydraulic medium in the pressure network.
  • the unloaded press ram is moved down and up by means of a separate rapid traverse cylinder.
  • the actual working cylinder for applying high tappet forces are therefore only during the actual machining process, for. B. used in forming or cutting a workpiece.
  • the press works with pressure regulation in the printing network, i. H. the pressure in the working cylinders is considerably increased in order to carry out the work process on the workpiece, an impressed volume flow, i. H. an approximately constant volume flow occurs.
  • Hydraulic presses are therefore rather slow due to their large hydraulic volume to be shifted and involve greater losses, since the hydraulic medium has to be transferred from low pressures to very high pressures. Pressure losses when relaxing a respective cylinder space to perform a directional movement can only be partially compensated for.
  • a piston-cylinder unit with pistons that can be loaded on both sides can be driven on both sides by a driven feed pump via a proportional valve control.
  • the "secondary control" described in this reference therefore behaves similarly to an electric DC motor, in which the mains voltage is constant and load changes are compensated for by a change in current.
  • the system pressure is kept constant and the volume flow is kept variable when the load changes.
  • the reference gives no indication of how such a secondary control can be used for a press control of a hydraulic press.
  • the invention has for its object to find a novel method for controlling the drive of a hydraulic press and an associated press, in which use is made in particular of the principle of secondary control.
  • the invention is based on the main idea that a press control or press control also allows a systematic application of the so-called "secondary control" of the drive of the press.
  • the cylinder control described in the cited literature reference is largely left by means of proportional valves in order to create a new control system.
  • a hydraulic motor used in the present invention is not intended to convert hydraulic energy into mechanical drive energy, but rather to effect a novel regulation of the volume flow in the pressure network in order to achieve a targeted control of the drive cylinder.
  • a technically novel concept for hydraulic presses is proposed, in which the various movements of the press ram and thus the piston of the piston-cylinder unit driving the press ram are coordinated with one another in such a way that the pressure network operates in a closed circuit, the maximum system pressure being generated by a pressure accumulator is determined.
  • the invention is based on the knowledge that the piston of a piston-cylinder unit is clamped on both sides at the highest possible pressure level and that a force is applied to the press ram in such a way that the lower cylinder chamber of the piston-cylinder unit facing the press ram is activated by a targeted and by means of a pump or a hydraulic motor regulated volume flow withdrawal is relieved.
  • the control of the hydraulic motor or the pump takes place via a swivel angle adjustment of the hydraulic motor.
  • the drive energy released during the downward movement of the press ram in the hydraulic motor is transmitted via a drive coupling to an in particular controllable feed pump which equally applies pressure medium to the upper cylinder space of the piston-cylinder unit.
  • the system according to the invention therefore has the advantage that valve controls by means of proportional valves for pressurizing and depressurizing the piston-cylinder units can largely be dispensed with, resulting in a faster control behavior.
  • the elimination of valves has the advantage of eliminating disruptive switching times and the associated pressure peaks in the system.
  • Another advantage of the control system according to the invention lies in the elimination of the compressibility of the pressure medium in the pressure network, since no additional volume compression takes place due to the constant high pressure level.
  • the regulation of the press takes place as a kind of "engine control” instead of a “valve control” in conventional systems, with a hydraulic motor taking over the volume flow control.
  • the energy recovery in the hydraulic motor assigned to the rapid traverse cylinder is advantageous, in which the potential energy generated is converted during at least part of the downward movement of the press ram. This energy is used to convey hydraulic medium into the pressure network. Pressure losses in the system are compensated by a single motor drive of the feed pump.
  • the figure shows a schematic representation of a hydraulic press with control elements for regulating the press according to the invention.
  • the press 1 shown in the figure consists of a, for. B. in portal construction manufactured press frame 2, in which a lower press table 3 for receiving a lower tool, not shown, and a press ram 4 for receiving an upper tool, also not shown, are mounted.
  • the up and down movement of the press ram 4 takes place hydraulically via two press cylinders 5, 6 which act laterally on the press ram serve as a working cylinder for performing the forming process on the workpiece or the like.
  • two press cylinders 5, 6 which act laterally on the press ram serve as a working cylinder for performing the forming process on the workpiece or the like.
  • four press cylinders arranged in the corner regions of the press ram can also be provided, it being possible for two further press cylinders to be arranged behind the press cylinders 5, 6.
  • an additional rapid traverse cylinder 7 is used as a separate piston-cylinder unit in order to carry out the pure downward movement or the upward stroke of the press ram.
  • Both the press cylinders 5, 6 and the rapid traverse cylinder 7 each have a piston rod 8 passing through the cylinder chamber and an inner piston 9 which can be acted upon with hydraulic medium on both sides in the cylinder chamber 10.
  • the cylinder space below the piston 9 is designated 10, the cylinder space above it is designated 10 '.
  • the piston 9 is in the almost uppermost position, i.e. H. the press ram 4 approximately at top dead center.
  • the pressures in the cylinder space 10 of the press cylinders 5, 6 can be determined by means of pressure measuring units 11, 11 '.
  • the ram path of the press ram 4 can be determined via a displacement measuring device or speed measuring direction 12, 12 ', whereby inclined positions of the press ram can be detected.
  • a drive unit 13, to be described in more detail, is provided as the drive for the rapid traverse cylinder, with a first hydraulic line 14 to the upper cylinder space 10 'and a second hydraulic line 15 to the lower cylinder space 10 of the rapid traction cylinder 7.
  • Corresponding cylinder space supply openings are identified by reference numeral 16.
  • the drive of the press cylinder 5, 6 is generally shown in the figure using the example of the press cylinder 5, 6. This drive can be transferred to all other press cylinders in the system.
  • the drive of the press cylinder 6, which applies to all press cylinders, is described below.
  • a pressure accumulator 18 is provided in a system pressure network 17 and is charged to the maximum system pressure p max .
  • a first pressure line 19 leads via an associated cylinder space supply opening 16 into the upper cylinder space 10 'of the press cylinder 6.
  • a second pressure line 21 leads via a controllable multi-way valve 22 and the continued pressure line 21' to a lower cylinder space supply opening 16 and thence to the lower cylinder chamber 10 of the press cylinder 6.
  • a further crossing point 23 is located in line 21 ', from where the pressure line 24 leads to a controllable pump 25 which is designed as a controllable hydraulic motor.
  • Another controllable feed pump 26 sits on the same drive shaft 27 as the pump 25, so that the drive of the pump 25 is transferred to the pump 26.
  • An additional electric motor 28 serves to drive the feed pump 26.
  • the pump 25 is associated with a hydraulic medium reservoir 29, the pump 26 with a further hydraulic medium reservoir 30.
  • Another pressure line 31 leads from the pump 26 to a crossing point 32 in the system pressure network.
  • a higher-level control directs and monitors the machine functions, with the individual axes being driven in a closed control loop.
  • the press table 3 can have one or more die cushions or pressure cheeks 33 with a corresponding die cushion controller 34.
  • the hydraulic press works as follows:
  • Phase 1 concerns a stop-start rapid traverse and a braking process down to the working speed when the ram is being lowered.
  • This phase is carried out solely by the rapid traverse cylinder 7 in connection with the drive unit 13.
  • the position and the speed of the movement of the piston 9 in the rapid traverse cylinder 7 is determined directly by the speed and the direction of rotation of a first pump 35 in the drive unit 13.
  • the setpoints for this are specified by the control electronics with the aid of the position measuring systems 12, 12 'and a speed measuring system 36.
  • a controllable hydraulic motor 37 which drives the pump 35 via a common drive shaft 38, serves as an actuator.
  • the pump 35 conveys the pressure medium in a closed circuit via the pressure line 14 to the upper cylinder space 10 'and via the pressure line 15 to the lower cylinder space 10 of the rapid-traction cylinder 7.
  • the hydraulic motor 37 is driven via a pressure line 39 of the system pressure network, which branches off at the crossing point 20 .
  • a hydraulic medium tank 40 serves as a pressure medium reservoir for the hydraulic motor 37 with the corresponding direction of rotation.
  • the pump system with the pumps 35 and the hydraulic motor 37 represent the secondary unit already known in the art with a control principle based on the secondary control.
  • the hydraulic motor 37 serves to operate a pump system of a rapid-motion cylinder 7.
  • the press cylinders 5, 6 are without force. This is explained using the example of the press cylinder 6 as follows:
  • the pump 25 is in a stop position with a flow rate equal to 0 during the first phase. This can be achieved by regulating the pump 25.
  • the downstream pump 26 can charge or maintain the storage pressure as system pressure via the power of the associated drive motor 28 and supply it to the storage 18 via line 31. Line 24 is therefore irrelevant in the first phase.
  • the lower cylinder space 10 and the upper cylinder space 10 'of the press cylinder 6 are connected via the controllable short-circuit valve 22, which is open in the first phase.
  • the pressure level in the press cylinder 6 is therefore in both cylinder spaces 10, 10 ', d. H. on the same associated piston surfaces to the system pressure, so that a resulting force on the piston 9 is not given.
  • This control enables the falling energy of the rapid traverse-down movement or the braking movement of the press ram 4 in the lower region to be recovered, since the pump 35 is driven by the weight of the press ram and the hydraulic motor 37 via the drive shaft 38 in the sense of charging the pressure accumulator 18 drives. For this, hydraulic medium is removed from the hydraulic medium container 40.
  • the working cylinder or press cylinder 6 can already be biased in this phase 1 to the required high and maximum press pressure in the system pressure network, for which purpose the falling energy of the press ram via the drive unit 13 does work. This avoids the additional pressure build-up times that are unavoidable with conventional press controls.
  • the speed control of the press ram 4 is taken over by the working cylinders or press cylinders 5, 6.
  • This phase can already take place during the braking movement at the end of the rapid traverse of the rapid traverse cylinder 7 or immediately after the latter have been completed.
  • the speed is further determined by the rapid traverse cylinder 7 in the manner described above.
  • the plunger can have speed measuring systems in connection with the displacement measuring systems 12, 12 'for determining the plunger speed.
  • Phase 2 is again described below using the press cylinder 6.
  • the short-circuit valve 22 is closed and the pump 25 swung out, i.e. H. brought from the locked position into a through position with a regulated passage.
  • the design of the short-circuit valves with check valve function of the check valve 41 makes this transition between the closing of the short-circuit valve 22 and the opening of the pump 25 completely problem-free in terms of control technology.
  • the time behavior of the closing of the short-circuit valve 22 and the pivoting out of the pump 25 does not have to be exactly synchronized, which represents a considerable simplification compared to previous solutions.
  • the pump 25 should have a slight advance in the opening behavior before the short-circuit valve 22 closes.
  • Phase 3 describes the actual process of the press.
  • the speed of the press ram 4 is determined by the volume flow V of the pump 25 (arrow 42), which is taken from the lower cylinder space 10 of the working cylinder 6.
  • the speed of the pump 25 is determined by the drive motor 28 and kept almost constant.
  • the volume flow from the lower cylinder space 10 of the working cylinder 6 through the pump 25 is determined solely by the adjustable swivel angle ⁇ of this pump.
  • the corresponding oil volume is replenished via the pressure network 17, the pressure network 17 being supplied with pressure medium by the reservoir 18 and the pump 26.
  • the press ram continues again at the specified speed.
  • the process is supported by the influence of the pump swivel angle ⁇ by the higher-level control system to the extent that the swivel angle ⁇ is increased when the speed is reduced in order to reduce the pressure reduction time and the following error.
  • the plunger 4 can perform a non-parallel downward movement due to the uneven application of force, which is recognized by the side-mounted measuring systems 12, 12 '.
  • the leading cylinder can be braked by swiveling in the pump swivel angle or the trailing cylinder can be accelerated by swiveling out the pump swivel angle.
  • the implementation of a system pressure network with a high or maximum pressure level is achieved, which enables the economical use of storage for energy storage. In this way, power peaks can be covered and the installed power can be significantly reduced compared to conventional technology, since no high pressure differences have to be installed.
  • the pump control instead of a valve control enables energy recovery of the energy stored in the lower cylinder spaces 10, which is not possible in the case of conventionally preloaded systems with valve control.
  • the plunger can be kept in parallel independently, since the pressures in the lower cylinder spaces 10 only decrease at the location of the action of the external force.
  • a parallel holding of the plunger can also take place in particular without separate counter-holding cylinders or parallel holding cylinders, i. H. without other mechanical components and without loss of ram force.
  • a cut impact damping is also implicitly contained in the concept described, which, for example, prevents the plunger from breaking through on the workpiece, because the maximum speed of the plunger is limited by the pump delivery volume V from the lower cylinder space 10 and is not like conventional valve controls results from the existing pressure conditions and the valve characteristics.
  • This cut impact damping works without separate counter cylinders and without other mechanical components, ie without loss of ram force.
  • phase 4 the direction is reversed at the bottom dead center of the press ram. In this position, the press ram has a speed of 0.
  • the maximum pressing force is limited in that the pressure reduction in the lower cylinder spaces 10 of the respective working cylinder only takes place up to a predetermined value. This is achieved by the higher-level control and in particular by corresponding adjustment of the swivel angle ⁇ of the pump 25. After an adjustable pressure holding time has elapsed, the respective short-circuit valve 22 is opened and the pump 25 is pivoted to 0.
  • phase 5 causes an upward rapid traverse.
  • this phase is controlled analogously to phase 1. Any power peaks during acceleration can be taken from the memory 18 of the system pressure network 17.
EP94103963A 1993-03-16 1994-03-15 Verfahren zur Regelung des Antriebs einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens Expired - Lifetime EP0615837B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4308344 1993-03-16
DE4308344A DE4308344A1 (de) 1993-03-16 1993-03-16 Verfahren zur Regelung des Antriebs einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens

Publications (2)

Publication Number Publication Date
EP0615837A1 EP0615837A1 (de) 1994-09-21
EP0615837B1 true EP0615837B1 (de) 1997-05-02

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Application Number Title Priority Date Filing Date
EP94103963A Expired - Lifetime EP0615837B1 (de) 1993-03-16 1994-03-15 Verfahren zur Regelung des Antriebs einer hydraulischen Presse und Vorrichtung zur Durchführung des Verfahrens

Country Status (6)

Country Link
US (1) US5460084A (ja)
EP (1) EP0615837B1 (ja)
JP (1) JPH06297200A (ja)
CA (1) CA2119101A1 (ja)
DE (2) DE4308344A1 (ja)
ES (1) ES2102086T3 (ja)

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Publication number Priority date Publication date Assignee Title
EP3115190A1 (de) 2015-07-06 2017-01-11 Feintool International Holding AG Vorrichtung und verfahren zum steuern des hauptantriebs einer feinschneidpresse
US10479040B2 (en) 2015-07-06 2019-11-19 Feintool International Holding Ag Device and method for controlling the primary drive of a fine blanking press

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ES2102086T3 (es) 1997-07-16
DE59402579D1 (de) 1997-06-05
US5460084A (en) 1995-10-24
CA2119101A1 (en) 1994-09-17
JPH06297200A (ja) 1994-10-25
EP0615837A1 (de) 1994-09-21
DE4308344A1 (de) 1994-09-22

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