WO2011012290A1 - Presse dotée d'une commande à manivelle à entraînement direct - Google Patents

Presse dotée d'une commande à manivelle à entraînement direct Download PDF

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Publication number
WO2011012290A1
WO2011012290A1 PCT/EP2010/004596 EP2010004596W WO2011012290A1 WO 2011012290 A1 WO2011012290 A1 WO 2011012290A1 EP 2010004596 W EP2010004596 W EP 2010004596W WO 2011012290 A1 WO2011012290 A1 WO 2011012290A1
Authority
WO
WIPO (PCT)
Prior art keywords
press
crankshaft
press according
rotor
drive
Prior art date
Application number
PCT/EP2010/004596
Other languages
German (de)
English (en)
Inventor
Matthias Graf
Original Assignee
Dieffenbacher Gmbh + Co. Kg
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 Dieffenbacher Gmbh + Co. Kg filed Critical Dieffenbacher Gmbh + Co. Kg
Publication of WO2011012290A1 publication Critical patent/WO2011012290A1/fr

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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
    • B30B1/26—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

Definitions

  • the invention relates to a press with a directly driven crank mechanism according to the preamble of claim 1.
  • Manufacturing machines with a reversing ram usually have a motor drive and a crank mechanism, the
  • Movement transforms transforms.
  • manufacturing equipment is used as presses for forming or cutting workpieces.
  • automotive industry required press lines, consisting of several successively arranged presses and associated
  • Transport system for example, from simple supplied coils (flat roll metal tape) complicated geometries, such as fenders,
  • high-speed presses are designed as mechanical presses as shown above.
  • crank mechanism is a drive which can transform a rotational movement (from a motor) into a linear movement and finds in the literature as an eccentric drive or
  • Thrust crank drive or the like precipitated.
  • the main task of the crank mechanism is to convert a rotational movement into a translational movement, using an eccentric or, as will be the case, a crankshaft.
  • On the crankshaft there is an eccentric bearing, which is mounted outside the axis of rotation of the crankshaft, or in the further crankpin, on which a thrust linkage, referred to as the connecting rod, is usually arranged.
  • the power flow of the drive can from the smallest possible denominator of the crank mechanism, a crankshaft and a crank pin, to a plunger over several stations such as cranks, joint drives, u. a. or just a connecting rod.
  • press frame for the supporting frame of the press.
  • all press frames are included in their possible embodiments thereof, such as built press frame of several items (top crosshead and bottom, side stand) as well as press frame in window frame construction.
  • Direct drives and servo presses are characterized by the fact that through the use of, preferably DC motors, via a
  • a drive system for a forming machine has become known that shows a direct drive for a drive system of a press.
  • the shaft output of the direct drive is still translated via a gear before the driving force on the shaft on a
  • crankshaft and finally can be transferred to a crank pin.
  • Main drive shaft (flange, clamping set or splined shaft) with the
  • Main drive shaft must be connected. Especially with large forces in large presses limit these shaft-hub connections the ability to design a press even at high forces smaller and especially with a low moment of inertia. Also, these compounds are extremely vulnerable to alternating load operation, for example, a pendulum stroke, and for incidents.
  • An overload protection for a malfunction (classic case is a workpiece coming from two boards in the press) must be designed so that the shaft-hub connections are not damaged in the event of a fault. But that in turn reduces the
  • the object of the invention is to provide a press that optimizes the previously known drive trains in a press in the field of stiffness, power flow and continuous load capacity.
  • a press especially a large press with high tonnage, to be created, which can do without a high mass in the drive train in the crankshaft and thus is also suitable for a pendulum stroke.
  • the solution of the problem for a press according to the invention can be found in the characterizing part of claim 1.
  • the press can be designed with a short overall length, in particular in an arrangement of the direct drive within the support structure (press frame), which is particularly advantageous for servo presses in press lines for the production of large body parts.
  • connection rod or joint gear connections carried out on the plunger.
  • the distances transversely and longitudinally between the pressure points or the connecting rods can not be chosen arbitrarily, but must be selected according to aspects with regard to the reduction of the ram deflection.
  • the length of the press head in the direction of passage is thus determined by the connecting rod distance and the necessary structure of the main bearing and support structures.
  • the advantages of the invention also show an improved control and regulation quality of the system in this context. Due to the high rigidity of the drive system and the precisely adjustable torque and angular position control of the engine, there is no measurable deviation between two crankpins and thus at the connecting rods on a crankshaft. The process data can additionally be recorded immediately. The press points through the
  • Direct drive no additional mechanical transmission links (e.g., gear stages).
  • the parameters measured on the motor such as speed, torque and angular position, can be converted without errors into ram speed, pressing force and ram position. Falsifications due to frictional losses or torsion, backlash etc. are excellently eliminated.
  • Permanent magnet motors especially at a high drive power, have a fairly high noise level.
  • Noise emissions are easily reduced, e.g. by closing the press head at the top and bottom.
  • the overall efficiency of the press improves significantly, as much less unused forces by the twist or the
  • Torque absorption in the bearings occur in a flying bearing of the engine.
  • the stator of the direct drive can be supported in the press head and / or with a
  • the engine thus has no own storage and the bearing of the rotor within the stator is characterized by the
  • the direct drive is placed on the supporting part of the crankshaft, ie it is located between the pressing force receiving main bearings of the mechanical drive.
  • the motor is then also between the main carrying
  • Support structures (at least two press frames of the press) and
  • the connecting rods or, in the case of joint drives, the pivoting levers leading to the connecting rod can either be located on the left and right of the engine and thus between the engine and the main bearing (support structure of the press head) or on one side between the engine and one of the main bearings
  • Figure 1 is a schematic view of a mechanical press with a
  • Press frame and a press table wherein in the upper part of the press, in the head area, the drive system consisting of two crank gears, each with a crankshaft, a crank pin and a ram operatively connected
  • FIG. 2 shows a further embodiment in side view according to FIG. 1, wherein two connecting rods are also arranged on a tappet, these being driven separately from one another via a crank drive, wherein the crankshaft is replaced by a thru axle and carries an eccentric wheel with a motor arranged directly thereon,
  • FIG. 3 shows another embodiment of the press drive in
  • Figure 4 is a schematic view of a preferred embodiment
  • Figure 5 is a side view of Figure 4 showing the storage of
  • Figure 6 shows a further preferred embodiment of the crank mechanism with a joint drive
  • Figure 7 shows a possible arrangement of the press according to the invention in one
  • the press 21 is at least a press frame 9, a table 8 mounted therein and one by means of at least one
  • this press 21 for incorporation of tools 15 or for the production of workpieces (not shown) by means of at least one manufacturing method used in a tool 15, wherein the tool at least one
  • crankshaft 1 with at least one crank pin 2 and at least one connecting rod 3 is arranged as the crank drive 12, with at least one direct drive driving directly the crankshaft 1 being provided as the motor 14 for driving the crankshaft 1.
  • crank mechanism 12 also called eccentric, may be arranged instead of the connecting rod 3 or between the connecting rod and the crank pin, a hinge drive or a crank or similar intermediate devices, usually for lifting height adjustment, from
  • crank mechanism 12 is operatively connected thereto, wherein these are in turn arranged operatively connected to the ram 5 on the output side.
  • the engine is substantially adjacent to one
  • crankpin 2 is arranged on the crankshaft 1.
  • a so-called crank disk may be integrated in or on the engine.
  • the stator of the motor is designed so that this assumes the function of the crank disc and the crank pin outside the central axis of the crankshaft 1 leads.
  • a rotor (10) or essential parts of the rotor (10) of an engine (10) with at least one crank pin (2) and / or part of the crankshaft (1) is designed as a one-piece machine element.
  • At least one motor (14) can be arranged between the crankpins (2).
  • the rotor 10 of the motor 14 can be arranged on the crankshaft, wherein according to FIGS. 2 and 3,
  • crank mechanism 12 leads, by means of bearings 29 on the
  • Thrust axle 27 is mounted. In this embodiment, preferably rotates only the eccentric 26, which as a one-piece machine element
  • the two bearings 29 between the thru-axle 27 and the eccentric 26 rotatably mounted on the axle 27 can also be designed as a continuous main bearing 29.
  • a holder 30 is provided, which is connected at the top to the press frame 9.
  • the motor 14 has as a direct drive usually a stator 4 with a drive winding 23 and a rotor 10 disposed therein with permanent magnets 23 and would then be designed as a permanent magnet motor.
  • at least one engine 14 is arranged between the crankpins 2 on at least two crankpins 2 on a crankshaft 1.
  • a symmetrical arrangement is preferable in a plurality of motors or crankpins. It can thus be provided that, in the case of several motors 14 and a plurality of crankpins 2, at least two motors 14 are symmetrical to one of the central axes of the
  • Press frame and / or one of the central axes of the plunger 5 and / or to the longitudinal center of the crankshaft 1 and / or arrangement of the crank pin 2 on the crankshaft 1 are arranged. It would also be advantageous if the rotor 10 of the motor 14 and the crankshaft 1 and / or the crank pin 2 consist of a one-piece machine element. Also, in the crank mechanism 12, a height adjustment for the stroke of the plunger 5 may be arranged. An overload protection 11 preserves the press
  • the stator 4 of the motor 14 is arranged with a holder 30 for receiving the reaction torques substantially within the press frame 9 and / or the head region above the up and down plunger 5.
  • the stator 4 of the engine 14 may be arranged to the crankshaft 1 and / or the rotor 10 without a bearing.
  • the stator 4 is guided coaxially to the crankshaft 1 and / or the rotor via the bearings of the crankshaft.
  • the stator 4 of a motor 14 may be arranged on a bearing 31 on the rotor 10 and to compensate for the torques occurring on the stator 4 a
  • Torque support 32 with connection to the press frame 9 make sense.
  • Figure 4 shows that at two
  • each stator 4 of a motor 14 is disposed on a bearing 31 on the rotor 10 and to compensate for the torques occurring at the stators 4 a torque arm 32 with connection to the engine 14 on the adjacent crankshaft first
  • the motor 14 and the crank mechanism 12 may be disposed within a support structure formed by the press frame 9, wherein in particular press force of over 200 tons, preferably over 500 tons, more preferably over 800 tons can be effected in such press frame.
  • the stroke of the plunger 5 of over 300 m, preferably over 600 mm, more preferably of over 900 mm possible.
  • the press 21 for a manufacturing process, at least the primary forming, the separation, the joining, the coating and / or the forming, in particular the
  • FIG. 6 shows, instead of a crank mechanism 12, which has a joint drive 33 instead of the connecting rods 3.
  • FIG. 7 shows the use of the press 21 as the head press 18 of a press line 17, as an incorporation press for tools 15
  • At least one rotor 10 of the motor 14 may be arranged with a flying bearing on at least one end of the crankshaft 1, provided that the execution as a one-piece
  • Machine element is ensured by the rotor to the crank pin.
  • the engine or the rotor of the engine is then located outside the main bearing of the crankshaft or the supporting structure or the press frame of the press.
  • the bearings 24 of the crankshaft 1 in from the
  • Press frame 9 removable bearing plates arranged so that a
  • Opening can be opened with a mounting diameter in the press frame, the diameter of preferably equal to or greater than the diameter of the rotor on the shaft respectively of the largest Diameter on the shaft corresponds. It can be helpful during assembly that a crankshaft 1 divided at least once in the longitudinal axis is arranged in the press, which has, for example, a flange connection, removable bearing journals or a shaft / hub connection.
  • the rotor 10 is arranged undetachably on the crankshaft 1.
  • a shrink fit for the connection of the rotor 12 with the crankshaft 1 a shrink fit, a welded joint, a solder joint, a Reibsch donethetic, a bond and / or another inseparable joint connection can be used.
  • a preferred embodiment of the rotor 10 would be grooves and / or recesses for receiving the
  • Permanent magnets 22 which are used only after the completion of the one-piece machine element.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)

Abstract

L'invention concerne une presse (21) comprenant au moins un cadre de presse (9), une table montée dans ce cadre et un coulisseau (5) entraîné par au moins une transmission à bielle (12) et servant à préparer des outils (15) ou à fabriquer des pièces au moyen d'au moins un procédé de fabrication dans un outil (15), une partie supérieure d'outil (6) est disposée sur le coulisseau (5) et une partie inférieure de l'outil (7) étant montée sur la table de presse (8), au moins un arbre à manivelle (1) doté d'au moins un maneton de manivelle (2) et d'au moins une bielle (3) est monté en tant que transmission à bielle (12) et au moins un entraînement direct entraînant directement l'arbre à manivelle (1) étant disposé en tant que moteur (14) servant à entraîner l'arbre à manivelle (1), au moins un rotor (10) ou des parties essentielles du rotor (10) d'un moteur (10) comprenant au moins un maneton de manivelle (2) et/ou une partie de l'arbre de manivelle (1) étant disposé en tant qu'élément de moteur.
PCT/EP2010/004596 2009-07-29 2010-07-27 Presse dotée d'une commande à manivelle à entraînement direct WO2011012290A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910035214 DE102009035214A1 (de) 2009-07-29 2009-07-29 Presse mit einem direkt angetriebenen Kurbeltrieb
DE102009035214.7 2009-07-29

Publications (1)

Publication Number Publication Date
WO2011012290A1 true WO2011012290A1 (fr) 2011-02-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/004596 WO2011012290A1 (fr) 2009-07-29 2010-07-27 Presse dotée d'une commande à manivelle à entraînement direct

Country Status (2)

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DE (1) DE102009035214A1 (fr)
WO (1) WO2011012290A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014115238A1 (de) * 2014-10-20 2016-04-21 Schuler Pressen Gmbh Pressenantriebsvorrichtung für eine Presse und Presse mit Pressenantriebsvorrichtung
EP3045302A1 (fr) * 2015-01-14 2016-07-20 Yamada Dobby Co., Ltd. Machine de pressage
US10723095B2 (en) 2014-10-20 2020-07-28 Schuler Pressen Gmbh Press drive device for a press, and press comprising a press drive device

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2840710A1 (de) 1978-06-05 1979-12-06 Klaussner Hans Jurgen Mechanische exzenterpresse
GB2042387A (en) * 1979-02-23 1980-09-24 Klaussner H Drive and control arrangement for an eccentric press
DE19916369A1 (de) * 1999-04-13 2000-10-19 Harald Garth Maschine zum Stanzen, Biegen und/oder Montieren von Blechteilen
JP2001062596A (ja) * 1999-08-24 2001-03-13 Ns Engineering:Kk プレス機械の組立方法並びにプレス機械
DE10260127A1 (de) 2002-12-19 2004-07-15 Siemens Ag Pressvorrichtung
EP1541330A1 (fr) * 2002-06-18 2005-06-15 Amada Company, Ltd. Systeme d'entrainement asservi et systeme de finissage en continu pour presse
EP1892081A2 (fr) * 2001-12-21 2008-02-27 Aida Engineering, Ltd. Presse
WO2009156199A1 (fr) * 2008-06-18 2009-12-30 Schuler Pressen Gmbh & Co. Kg Entraînement direct de presse
WO2010009694A2 (fr) * 2008-07-25 2010-01-28 Müller Weingarten AG Système d'entraînement d'une presse de formage
JP2010188392A (ja) * 2009-02-19 2010-09-02 Komatsu Ltd 電動サーボプレス

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2840710A1 (de) 1978-06-05 1979-12-06 Klaussner Hans Jurgen Mechanische exzenterpresse
GB2042387A (en) * 1979-02-23 1980-09-24 Klaussner H Drive and control arrangement for an eccentric press
DE19916369A1 (de) * 1999-04-13 2000-10-19 Harald Garth Maschine zum Stanzen, Biegen und/oder Montieren von Blechteilen
JP2001062596A (ja) * 1999-08-24 2001-03-13 Ns Engineering:Kk プレス機械の組立方法並びにプレス機械
EP1892081A2 (fr) * 2001-12-21 2008-02-27 Aida Engineering, Ltd. Presse
EP1541330A1 (fr) * 2002-06-18 2005-06-15 Amada Company, Ltd. Systeme d'entrainement asservi et systeme de finissage en continu pour presse
DE10260127A1 (de) 2002-12-19 2004-07-15 Siemens Ag Pressvorrichtung
WO2009156199A1 (fr) * 2008-06-18 2009-12-30 Schuler Pressen Gmbh & Co. Kg Entraînement direct de presse
WO2010009694A2 (fr) * 2008-07-25 2010-01-28 Müller Weingarten AG Système d'entraînement d'une presse de formage
JP2010188392A (ja) * 2009-02-19 2010-09-02 Komatsu Ltd 電動サーボプレス

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014115238A1 (de) * 2014-10-20 2016-04-21 Schuler Pressen Gmbh Pressenantriebsvorrichtung für eine Presse und Presse mit Pressenantriebsvorrichtung
DE102014115238B4 (de) * 2014-10-20 2017-02-02 Schuler Pressen Gmbh Pressenantriebsvorrichtung für eine Presse und Presse mit Pressenantriebsvorrichtung
US10723095B2 (en) 2014-10-20 2020-07-28 Schuler Pressen Gmbh Press drive device for a press, and press comprising a press drive device
EP3045302A1 (fr) * 2015-01-14 2016-07-20 Yamada Dobby Co., Ltd. Machine de pressage

Also Published As

Publication number Publication date
DE102009035214A1 (de) 2011-02-24

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