EP2367676A2 - Procédé de régulation d'une presse à forger - Google Patents

Procédé de régulation d'une presse à forger

Info

Publication number
EP2367676A2
EP2367676A2 EP09806075A EP09806075A EP2367676A2 EP 2367676 A2 EP2367676 A2 EP 2367676A2 EP 09806075 A EP09806075 A EP 09806075A EP 09806075 A EP09806075 A EP 09806075A EP 2367676 A2 EP2367676 A2 EP 2367676A2
Authority
EP
European Patent Office
Prior art keywords
plunger
ram
stroke range
forming
direct drive
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
EP09806075A
Other languages
German (de)
English (en)
Other versions
EP2367676B1 (fr
Inventor
Markus Bieg
Helmut Reuter
Alexander Schneider
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.)
L Schuler GmbH
Original Assignee
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 Mueller Weingarten AG filed Critical Mueller Weingarten AG
Publication of EP2367676A2 publication Critical patent/EP2367676A2/fr
Application granted granted Critical
Publication of EP2367676B1 publication Critical patent/EP2367676B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • B30B1/26—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
    • B30B1/266—Drive systems for the cam, eccentric or crank axis
    • 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 operating a forming machine, in particular a forging press, or a forming system according to the preamble of claim 1.
  • Mechanical forming machines or mechanical forming plants find in the industry a variety of applications.
  • An essential category in this case are the forging-crank presses, in which, for the purpose of forming a workpiece, a ram acts on the workpiece via a drive with a defined deformation energy, thereby carrying out the desired forming.
  • a pressing device in which the press ram is driven with a direct drive as the main drive, so that over a thus formed press structure any curve of the ram stroke can be adjusted over time.
  • the applicant also describes the design of the forge-type "Speed Forge” press, in which a rotary direct drive is used to manipulate the stroke time curve, in which case the forming energy is then provided shortly before the forming process energy-storing flywheel drive is engaged, which provides the plunger with the required forming energy available.
  • a disadvantage of such methods is that extremely efficient direct drives are necessary for an almost freely configurable course of the plunger movement, so that the usually extremely heavy plunger can be driven with a conventionally required stroke rate of about 30 to 60 strokes per minute.
  • extremely high power requirements are required, which in turn results in an extremely high power requirement and the resulting connected load, and additionally expensive and economically demanding direct drive motors requires.
  • the object of the present invention is therefore to provide a method in which a stroke height-dependent modification of the plunger movement is provided, and the disadvantages of the prior art, in particular the need for powerful powerful and thus energy-consuming direct drive motors is reduced.
  • the inventive method for operating a forming machine or a forming plant, in particular a forged crank press with flywheel drive moves at least one arranged on a shaft via a hinge plunger, at least temporarily via a rotary drive, which provides the required forming energy on the plunger and which is preferably designed as a flywheel drive , and continue at least temporarily via a direct drive, which allows a defined plunger movement, ie a deviation from the classical sinus rhythm of an eccentric driven crank press with concurrent eccentric speed.
  • the method according to the invention is characterized in that the fall acceleration which effectively acts on the ram is adapted via the direct drive.
  • a force counteracting the weight force is necessary, which can be achieved, for example, by a pneumatic pump
  • Pusher weight balance or the like can be generated.
  • the movement of the plunger is controlled by the balance of power considerably flexible compared to the pure eccentric linkage.
  • another direct drive acting on the ram, at least temporarily is provided, preferably a servomotor, which allows a defined periodic ram movement.
  • a second direct drive preferably a servomotor
  • the plunger experiences an acceleration force which reduces the acceleration of the fall in an upper stroke range due to the direct drive. As a result, the case of the plunger is braked, so that the increase in movement speed per time is reduced compared to the free fall.
  • the direct drive carrying out the method is designed hydraulically.
  • a hydraulic reaction force generation on the plunger for example, by a mounted in the ram guide hydraulic cylinder, the falling motion can be guided and adjusted.
  • the direct drive is designed pneumatically.
  • About a pneumatic design of the opposing force generating direct drive is achieved that learns about a pneumatic back pressure of the plunger a case acceleration reducing, preferably constant drag.
  • By providing a sufficiently large pressure reservoir it is possible to keep the plunger with a constant counterforce quasi self-weight, and to modulate the acceleration of gravity to counteract this counterforce by the back pressure of the reservoir, for example by appropriate Dossei wornen.
  • an accelerating force can in principle be exerted on the ram both by the hydraulic device, as well as by the pneumatic device.
  • the shaft on the rotary drive preferably the flywheel, engaged, so as to provide the ram required for forming the energy available.
  • the required deformation energy can thus be specified exactly by the flywheel.
  • the plunger is decoupled from the rotary drive, in particular the flywheel drive at a predetermined speed, preferably in the lower stroke range.
  • Such Abkupplungsvorgang usually takes place shortly after the conversion and releases the plunger back to the direct drive. In this way, the energy taken from the flywheel can be fed back to the flywheel by the flywheel drive independently of the plunger movement, and the plunger can be moved independently thereof.
  • the ram weight compensation of the installation is used as the direct acceleration adapting the fall acceleration.
  • a ram weight balance is often provided in such systems, in particular to compensate for the weight of the ram own weight, so that, for example, in the bearings of the joints on the eccentric shaft no complete displacement of the lubricant, and thereby damage the storage.
  • Known ram weight compensations are usually designed such that via a pneumatic force acting on the plunger from below and from above is acted upon by a pressure, and the plunger itself thereby quasi free of weight on the eccentric shaft and the crank arranged thereon can be moved.
  • Such a ram weight balance can now be used, for example, by reducing the plunger bottom pressure to put the plunger in a falling motion, wherein depending on the degree of pressure reduction, a corresponding counterforce due to the remaining residual pressure adjusts the fall acceleration.
  • an accelerated drop movement is performed by the plunger in an upper stroke.
  • the falling movement is caused by a force generated by the ram weight balance,
  • an opposing force is influenced, wherein at the time of a defined, synchronized with the speed of the rotary drive falling speed of the rotary drive is coupled to the shaft, wherein the engagement preferably in the lower stroke range, especially shortly before forming, and wherein shortly after the forming in the lower Lifting range of the rotary drive is disengaged again at synchronized ram speed, and wherein the residence time of the plunger in the lower stroke range compared to the dwell time in the upper stroke range is shortened at least in the factor 1: 2.
  • the method according to the invention can be used on the one hand in a single forming machine but on the other hand also in forming lines of a forming plant.
  • Fig. 2 is a stroke-time diagram for comparing the conventional and the inventive method
  • Fig. 3 is a schematic representation of a plant with ram weight balance 1 shows a forging crank press 1 with a movable plunger 2, which is articulated via cranks 3 to an eccentric shaft 4.
  • a servomotor 5 and, on the other hand, a flywheel 7 are arranged via a coupling 6, wherein the flywheel 7 in turn can be driven by a flywheel drive 8.
  • the ram weight balance, not shown in Fig. 1 is preferably formed pneumatically and usually has a, the plunger upwardly driving lower pressure range (negative pressure) and the plunger down driving upper pressure range (top pressure).
  • the ram weight balance can be formed in the ram guide or via a correspondingly attached to the ram piston in a pressure cylinder.
  • FIG. 2 shows a stroke time diagram 20 in which the ram stroke is plotted over time as an example.
  • the plunger at its upper reversal point at time 0 starts the movement, at time 0.5 and 1.5 seconds, a lower reversing position was reached and taken at time 1 and 2 seconds again the top dead center at maximum lift becomes.
  • a conventional stroke course 21 which has the shape of a classic sinusoid, is shown, on the other hand an inventive stroke profile 22 of a drive system according to the invention, wherein the cycle times in the present case have been set to an equal number of strokes per minute.
  • the conventional curve 21 is essentially described by a regular sinusoid, which is due to the direct articulation of the plunger on the eccentric shaft.
  • a manipulation of the workpiece to be formed may take place in the lower region.
  • manipulators can intervene in the forming machine, remove the workpiece and use a new workpiece.
  • manipulators can remove or implement the workpiece, in which case an idle stroke can take place, during which, for example, a plunger cooling is performed.
  • a cooling interval 23 is established as available in the case of a conventional stroke progression. If one considers the region in which the plunger has pressure contact with the workpiece to be formed in the lower region of the conventional stroke progression 21, the pressure contact time 24 of the forming process is indicated by way of example in FIG.
  • this Druckberntonzeit ie during the deformation of the workpiece before retracting the plunger, thermal energy between the workpiece and the plunger can be replaced, whereby the plunger heats up.
  • excessive ram heating involves disadvantages of reduced strength and thermal expansion, which in turn leads to increased tolerances.
  • the Hubverlauf a ram 22 so is held by the reduced acceleration of gravity of the plunger over a longer period in the upper stroke range, ie above, for example, 150 mm stroke.
  • the plunger can then be moved down by a corresponding influence on the acceleration on a steeper curve, wherein upon reaching a predetermined defined speed, for example at a lifting height of 50 mm, wherein always the speed sets the essential parameters, the flywheel 7 via the clutch 6 are engaged. If the ram speed present at the time of engagement corresponds exactly to the speed which is taken from a movement which is permanently synchronized with the flywheel, the coupling process takes place without wear or losses since no acceleration work has to be applied to the ram.
  • the plunger is then in the lower deformation of the flywheel from the flywheel necessary for the transformation of energy, the movement during turn coupled to the flywheel state again corresponds to a sinusoidal shape.
  • the area of the deformation 25, ie the duration of the forming contact with the workpiece is substantially reduced compared to the conventional course of the movement, whereby a less heat transfer of the workpiece takes place on the plunger.
  • Pusher weight balance can be adopted, or it can be used a different direct drive to support or to the entire movement of the plunger.
  • the time available for workpiece manipulation and tool cooling and tool lubrication is considerably extended by the extended residence time of the plunger in the upper stroke range.
  • the plunger can remain in the upper stroke range for a period of time 26 when using a method according to the invention, as a result of which an improved number of cycles and improved tact quality can be achieved effectively.
  • the ram speeds can thus be varied between 6 and 12 strokes per minute at the upper reversal point and between 30 and 60 and even 120 strokes per minute at the lower reversal point.
  • the resulting average number of strokes of the machine is between 30 and 50 strokes / min.
  • Figure 3 shows a schematic representation of a system according to the invention with ram weight balance.
  • the system is constructed in a conventional frame 30 not described in detail, which contains the necessary components, such as guides, leads, bearings, etc.
  • the plunger 31 is guided in this context in a work area 32, wherein the representation of tools, etc. has been dispensed with.
  • the plunger 31 is connected via a plunger linkage 33 with a shaft 34.
  • the plunger linkage 33 transmits the rotary shaft movement of the shaft 34 into a required stroke movement of the plunger 31.
  • a direct drive 35 such as a servo motor, arranged, which can take on the movement of the plunger influence.
  • a coupling device 36 is further provided, which connects the shaft 34 in the engaged state with a flywheel 37. Via the flywheel 37, the plunger 31 is provided with the energy required for the forming process in the working area 32. Energy taken from the flywheel 37 for forming is fed back to the flywheel 37 through a flywheel drive 38 so that it is ready for the next forming cycle. Between the forming processes, the clutch 36 is opened, so that the plunger movement independent of the movement of the flywheel 37th can be done.
  • a ram weight compensation 40 is provided on the plunger.
  • the ram weight compensation 40 is shown here only very schematically and is intended to illustrate only the principle of its function.
  • the overpressure Pi can simply be reduced, so that the plunger 31 is pulled down by its weight. If necessary, such a movement can also be accelerated by an overpressure on the upper side 44, that is to say P 2 > Pi.
  • P 1 / P2 the ratios P1 / P2 are adjusted accordingly.
  • the pressure ranges can be applied pneumatically, for example if a constant pressure is required over an enlarged pressure reservoir.
  • the pneumatic control of the pressure ranges 43 and 44 can be carried out very easily and inexpensively via a pressure reservoir and simple drain or throttle valves. But it is also a hydraulic arrangement conceivable, for example, as undamped forces should be transmitted.
  • the invention is not limited to the embodiments shown here. Rather, it includes all those embodiments which make use of the method essential to the invention. Also possible procedural plants are claimed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Forging (AREA)
  • Control Of Presses (AREA)

Abstract

L'invention concerne un procédé pour faire fonctionner une machine de formage ou un dispositif de formage. Dans une zone supérieure de la course, le coulisseau décrit un mouvement de chute accéléré; le mouvement de chute est influencé, de préférence freiné, par une force produite par l'équilibrage du poids du coulisseau; lorsque la vitesse de chute atteint une vitesse définie, synchronisée avec la vitesse de l'entraînement rotatif, l'entraînement rotatif est accouplé à l'arbre; le processus d'accouplement est de préférence réalisé dans la zone inférieure de la course, notamment peu avant le formage; peu après formage, l'entraînement rotatif est désaccouplé dans la zone inférieure de la course lorsque la vitesse du coulisseau est synchronisée; et la durée d'arrêt du coulisseau dans la zone inférieure de la course est au moins réduite d'un facteur 1:2 par rapport à la durée d'arrêt dans la zone supérieure de la course.
EP09806075.9A 2008-12-22 2009-12-21 Procédé de régulation d'une presse à forger Active EP2367676B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810064229 DE102008064229A1 (de) 2008-12-22 2008-12-22 Verfahren zur Regelung einer Schmiedepresse
PCT/DE2009/001792 WO2010072208A2 (fr) 2008-12-22 2009-12-21 Procédé de régulation d'une presse à forger

Publications (2)

Publication Number Publication Date
EP2367676A2 true EP2367676A2 (fr) 2011-09-28
EP2367676B1 EP2367676B1 (fr) 2016-06-01

Family

ID=42201011

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09806075.9A Active EP2367676B1 (fr) 2008-12-22 2009-12-21 Procédé de régulation d'une presse à forger

Country Status (4)

Country Link
EP (1) EP2367676B1 (fr)
DE (1) DE102008064229A1 (fr)
ES (1) ES2588992T3 (fr)
WO (1) WO2010072208A2 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009050390A1 (de) 2009-10-22 2011-04-28 Müller Weingarten AG Arbeitsverfahren und Einrichtung zum Betreiben von Pressen
DE102010049492B4 (de) 2010-10-27 2013-04-18 Schuler Pressen Gmbh Mechanische Umformmaschine, insbesondere Kurbelpresse sowie Verfahren zur Bereitstellung einer mechanischen Umformmaschine
JP5770584B2 (ja) 2011-09-27 2015-08-26 住友重機械工業株式会社 鍛造プレス装置およびその制御方法
DE102012108933B4 (de) * 2012-09-21 2019-08-08 Schuler Pressen Gmbh Verfahren zum Betreiben einer Werkzeugmaschine oder Arbeitsmaschine und danach ausgeführte Werkzeugmaschine oder Arbeitsmaschine mit einer Verbindungsanordnung für ein Hubelement
DE102015222995A1 (de) * 2015-11-20 2017-05-24 Sms Group Gmbh Weggebundene Presse mit Kulissenstein
WO2021019017A2 (fr) * 2019-07-30 2021-02-04 Kama Gmbh Entraînement oscillant de machine

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3869927A (en) * 1973-09-06 1975-03-11 Gulf & Western Ind Prod Co Geared drag link-slider-crank press
FR2296518A1 (fr) * 1975-01-06 1976-07-30 Gulf & Western Mfg Co Presse mecanique de travail du metal
JP2570812B2 (ja) * 1988-05-31 1997-01-16 石川島播磨重工業株式会社 鍛造プレス装置
DD291294A5 (de) * 1989-12-29 1991-06-27 Komb. Umformtechnik "Herbert Warnke",De Einrichtung zur steuerung des energetischen und dynamischen verhaltens von antrieben in umformmaschinen
JPH0751900A (ja) * 1993-08-21 1995-02-28 Sumitomo Heavy Ind Ltd クランクプレスのバランサ吊上げ力制御方法及びそのための装置
JPH08197298A (ja) * 1995-01-26 1996-08-06 Amada Co Ltd スライドモーション可変プレス
US6453806B1 (en) * 1998-03-26 2002-09-24 The Minster Machine Company Infinite variable slide motion for a mechanical power press
JP3437758B2 (ja) * 1998-03-31 2003-08-18 住友重機械工業株式会社 クランクプレス
WO2003106154A1 (fr) * 2002-06-18 2003-12-24 株式会社アマダ Systeme d'entrainement asservi et systeme de finissage en continu pour presse
DE10260127A1 (de) 2002-12-19 2004-07-15 Siemens Ag Pressvorrichtung
DE102005038583B4 (de) * 2005-08-16 2007-12-27 Schuler Pressen Gmbh & Co. Kg Pressen-Antriebsmodul und Verfahren zur Bereitstellung einer Pressenbaureihe

Non-Patent Citations (1)

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Title
See references of WO2010072208A2 *

Also Published As

Publication number Publication date
ES2588992T3 (es) 2016-11-08
WO2010072208A2 (fr) 2010-07-01
EP2367676B1 (fr) 2016-06-01
DE102008064229A1 (de) 2010-07-01
WO2010072208A3 (fr) 2010-12-29

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