EP1633507A1 - Dispositif de transfert menage sur une presse - Google Patents

Dispositif de transfert menage sur une presse

Info

Publication number
EP1633507A1
EP1633507A1 EP04735864A EP04735864A EP1633507A1 EP 1633507 A1 EP1633507 A1 EP 1633507A1 EP 04735864 A EP04735864 A EP 04735864A EP 04735864 A EP04735864 A EP 04735864A EP 1633507 A1 EP1633507 A1 EP 1633507A1
Authority
EP
European Patent Office
Prior art keywords
press
movement
workpieces
transport
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.)
Withdrawn
Application number
EP04735864A
Other languages
German (de)
English (en)
Inventor
Rudolf Lüthi
Theo Egolf
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.)
Adval Tech Holding AG
Original Assignee
Adval Tech Holding 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 Adval Tech Holding AG filed Critical Adval Tech Holding AG
Publication of EP1633507A1 publication Critical patent/EP1633507A1/fr
Withdrawn legal-status Critical Current

Links

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
    • B21D43/00—Feeding, positioning or storing devices combined with, or arranged in, or specially adapted for use in connection with, apparatus for working or processing sheet metal, metal tubes or metal profiles; Associations therewith of cutting devices
    • B21D43/02—Advancing work in relation to the stroke of the die or tool
    • B21D43/04—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
    • B21D43/05—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work specially adapted for multi-stage presses
    • B21D43/055—Devices comprising a pair of longitudinally and laterally movable parallel transfer bars

Definitions

  • the present invention relates to a device on a press and a method for the gradual transport of workpieces in a longitudinal direction from a receiving station through at least one processing station of the press with transport means for the workpieces, which cyclically and synchronously with the movement of the press in the longitudinal direction as well for gripping or releasing the workpieces in a substantially perpendicular transverse direction to and fro.
  • the movement of the transport means in the longitudinal direction takes place via an external drive that is only synchronized with the movement of the press.
  • Transfer devices are distinguished from so-called progressive composite tools in that the part to be formed in the press in the area of the receiving station is first separated, for example, from an endless strip, for example by cutting or punching, and then independently of the movement of the endless strip and mostly also perpendicularly to it by the at least one processing station is transported to the press.
  • the press is usually provided with several processing stations or forming stages connected in series.
  • the part to be formed is transported from the forming step to the forming step by its own endless strip from which it originates.
  • the drive can be named via a controlled third-party system (e.g. servo motor / linear motor).
  • the longitudinal movement is driven by a rotor of a servo motor that drives a system that generates the longitudinal movement (toothed belt with longitudinal guides / threaded roller spindle with longitudinal guides).
  • the longitudinal movement can alternatively be generated directly by a linear motor.
  • Feed cycle can be selected flexibly (software)
  • a mechanical transfer device similar to the type mentioned with a pair of transport bars as a means of transport for the workpieces is e.g. known from EP 0
  • the mechanical coupling also largely prevents collisions of the press tool with the means of transport.
  • transfer devices are known in which the drive of the transport means is effected via one or more external drives using servomotors, hydraulics, pneumatics, linear motors, etc. and which are synchronized in various ways with the movement of the press ram in terms of signal technology.
  • Such third-party drives are generally cheaper and also more flexible to use than the aforementioned mechanical couplings, but they cannot achieve such high stroke rates. The limit here is currently 50-150 cycles per minute. Also, if a drive fails, there is a risk of a collision between the press tool and the means of transport with mostly destructive consequences.
  • WO-A-00/20305 Another possible approach is described in WO-A-00/20305.
  • the transport means are driven in the longitudinal direction by an external drive, which is only synchronized with the eccentric shaft of the press in terms of signals.
  • the movement of the transport means for releasing the workpieces in the transverse direction is derived from the movement of the press ram by direct mechanical coupling.
  • This type of drive achieves the advantages of purely mechanical drives in terms of safety and high cycle rates with the low cost and greater flexibility of third-party drives in combination.
  • the disadvantage of this is that, in comparison to a purely mechanical longitudinal movement due to the servo motor used, only comparatively low Cycle rates significantly below 300 or even only 250 strokes / minute are possible.
  • this relates to a device on a press for the step-by-step transport of workpieces in a longitudinal direction from a receiving station through at least one processing station of the press with transport means for the workpieces, which is cyclical and synchronous with the movement of the press in the longitudinal direction and for detecting or release the workpieces back and forth in an essentially perpendicular transverse direction, the movement of the transport means in the longitudinal direction being effected by an external drive which is only synchronized with the movement of the press.
  • a first preferred embodiment is accordingly characterized in that the mechanical coupling between the external drive and the transport means is designed as a mechanical gear, particularly preferably as a mechanical cam gear.
  • a mechanical gear particularly preferably as a mechanical cam gear.
  • the use of a worm gear is possible.
  • a further preferred embodiment is characterized in that the movement of the external motor drive is synchronized with the movement of the press, in particular with the movement of an eccentric shaft of the press, via an angular step encoder.
  • Such a synchronization of the external drive and the press can actually achieve lifting speeds which are comparable to those of purely mechanical transfer devices.
  • a particularly preferred embodiment of the present invention has means which allow the external motor drive to be operated at different speeds depending on the feed cycle 1 .
  • This inherent flexibility of the third-party drive allows, among other things, the change of the feed angle and thus the reshaping of higher components in the press without requiring mechanical modifications.
  • the speed of the longitudinal movement of the transport means can be varied within certain limits without mechanical changes solely by controlling the speed of the external drive. This now without the reversal of the state of the art required Direction of rotation of the servo motor, ie at high clock rates.
  • a further preferred embodiment of the device according to the invention is characterized in that the movement of the transport means for releasing the workpieces in the transverse direction is derived from the movement of the press by direct mechanical coupling.
  • the movement of the means of transport for gripping the workpieces in the transverse direction can also be carried out by an external drive, a combination of a motorized external drive with a mechanical gearbox, i.e. is possible without reversing the direction of rotation of the external drive.
  • This is in and of itself, i.e. possibly also independent of the design of the longitudinal drive possible implementation of the transverse drive, which is new and inventive.
  • the drive of the transport means for releasing the workpieces in the transverse direction is derived from the movement of the press ram via a mechanical cam system.
  • the transport means preferably comprise transport rods which extend in the longitudinal direction on both sides of the receiving and at least one processing station and which are preferably equipped with grippers for the workpieces.
  • the present invention relates to a method for the gradual transport of workpieces on a press, particularly preferably using a device as described above.
  • Transport in a longitudinal direction from a receiving station is ensured by at least one processing station of the press with transport means for the workpieces, which is cyclical and synchronous with the movement of the press in the longitudinal direction and for gripping or releasing the workpieces in a substantially perpendicular manner Be moved back and forth.
  • the movement of the transport means in the longitudinal direction takes place via an external drive that is only synchronized with the movement of the press.
  • there and back Movement of the transport means driven by the external motor drive without reversing the rotation of the external drive.
  • a first preferred mode of operation is characterized in that the external motor drive is operated at a constant speed of rotation and direction of rotation.
  • the curve characteristic of the transmission is typically optimized for such constant operation.
  • the flexibility of an external drive in the longitudinal direction can be combined with the high number of strokes of a purely mechanical conveying in the longitudinal direction.
  • the speed of rotation of the external drive is varied in those sections of the feed cycle in which the transport means do not perform any longitudinal movement (so-called standstill sections).
  • the rotational speed of the external drive is preferably kept constant, an increased, constant rotational speed preferably being driven, for example, during the feed.
  • the speed of rotation is preferably first slowed down and the speed of rotation is subsequently accelerated to the value relevant for the subsequent section of the cycle.
  • the variation of the rotational speed of the external drive in the standstill sections has the particular advantage that there are virtually no moving masses (apart from the shaft of the servo motor and the worm gear and possibly a reduction gear) and accordingly Energy losses (braking) or high energy consumption (acceleration) can be avoided.
  • stroke rates of more than 200 strokes / min or more than 270 strokes / min can be achieved.
  • Strokes in the range of or more than 300 strokes / min or even more than 350 strokes / min are typically possible.
  • FIG. 1 shows a plan view of the table of a press with a transfer device
  • Figure 2 is an end view of the press with parts of the transfer device.
  • FIG. 3 shows a partial section along line III-III in FIG. 1 on a larger scale
  • FIG. 6 shows a schematic representation of the transfer system with variable feed time or with variable angles
  • Fig. 7 is a schematic representation of the feed cycle of a transfer operation with variable angles.
  • Figures 1 and 2 show more or less schematically a press table 1, guide columns 2 and a press ram 3.
  • the lower part is attached to the table 1 and the upper part of a so-called transfer tool with several processing or forming stations connected in series.
  • this tool is not shown in the drawing.
  • a transport rod 4 on both sides of the tool with grippers 5 for the workpieces, shown purely schematically.
  • the ends of the transport rods are mounted on longitudinal slides 7 by means of fastening angles 6.
  • the longitudinal slide 7 ( Figure 3) are rigidly guided along two parallel guide rods 8, which in turn are fastened in a cross slide 9 which is guided along two parallel transverse guide rods 10.
  • control rails 11 which are mounted on the press ram 3 and act with their external control cams 12 on control rollers 13 of extensions 14 of the slide 9.
  • the extensions 14 act on the piston rods 15 of pneumatic cylinders 16 in the opposite direction inwards.
  • a reliable contact pressure in the closing direction therefore always acts inwards on the extensions 14, so that the control rollers 13 always rest securely on the control cams 12 of the control rails 11.
  • transport rods 4 are spread outwards, so that a workpiece 17 clamped between two opposite holders 5 is released.
  • the holders 5 are also laterally removed from the area of the upper and lower tool parts of the press, so that the tool for machining workpieces can close in all stations.
  • FIG. 1 it is indicated that workpieces such as blanks 18 are punched out of a transverse belt 19 in a punching and receiving station and are taken over by the outermost grippers of the transport rods 4.
  • the workpieces 18 are gradually shifted to the left and are thus fed to the individual forming stations of the transfer tool one after the other. After a certain start-up time, all the forming stations are each occupied with a workpiece 18.
  • the transport rods 4 perform a closed rectangular movement per working cycle by advancing a number of detected blanks to the next forming station of the transfer tool in a first cycle, and laterally outwards in a second cycle Workpieces and removed from the overlap area with the tool, returned in a third cycle in the longitudinal direction and moved inwards to the tool in a fourth cycle to grasp the workpieces (see also Fig. 5, comment below).
  • the longitudinal drive of the transport rods 4 comprises two leaf springs 20 which are attached with their right ends to the inside of the longitudinal slide 7 and which, as indicated in FIG. 4, can follow the transverse movements of the transport rods 4.
  • the two leaf springs 20 are connected to a longitudinally movable guide carriage 21, which is driven by an electric servo motor 23 via a toothed belt 22.
  • the servo motor 23 is acted upon by a control signal 24, which is derived from the movement of the eccentric shaft of the press and with an angle rotary encoder (not shown).
  • Feed sector 25 for transporting the formed part from one tool stage to the next.
  • Standstill sector 26 for transferring the formed part from the transfer system to the forming tool.
  • angles of the 4 sectors can be assumed as follows: ⁇ feed sector 25: 120 °
  • Standstill sector 28 60 °
  • the feed angle 25 is particularly critical. The formed part has to be transported in this sector and it must not fall out of the grippers or move in it during the movement.
  • the size of the angle is crucial for determining the available usable height, at which formed parts can still be formed.
  • This height, the theoretical usable height, is shown in FIG. 5 with the reference symbol 30, and the total height, the press stroke, with the reference symbol 29.
  • the press stroke is fixed for a given arrangement.
  • both the press stroke 29 and the theoretically usable height 30 are not adjustable.
  • a servo motor 35 with a variable number of revolutions and an angular step encoder drives a mechanical cam mechanism 38, in which the sectors are optimized Aspects are designed for a maximum number of cycles of the press. This optimization is usually designed for constant engine speed.
  • a reduction gear 36 can also be arranged between the servo motor 35 and cam gear 38.
  • the servo motor 35 is an electric motor that can be switched, that is, whose output can be controlled. For example, a servo motor 35 with 3000 revolutions / min can be used, and a reduction gear 36 with a factor 1:10, so that a rotation of 300 revolutions / min is applied to the transfer gear 38.
  • the servo motor 35 is synchronized by a controller from an angle step sensor 32, which is driven by the eccentric shaft of the press 31. In order to ensure synchronization, the servo motor 35 also has an angle stepper.
  • the angle encoder is an electronic assembly that is able to divide a rotation of a shaft (e.g. eccentric shaft of the press) by 360 ° into increments of 0.044 °, for example, and calculate the respective angular position of the eccentric shaft precisely.
  • a shaft e.g. eccentric shaft of the press
  • the transfer gear 38 comprises a gear worm 37, which from the
  • Rotary movement of the servo motor 35 produces a longitudinal movement.
  • a variable feed time can thus be allowed with a fixed feed path 33. This is shown schematically in analogy to FIG. 5 in FIG. 7. • If the gear runs at the same number of revolutions as the press, the feed time corresponds to the designed feed angle (situation of Fig. 5).
  • the usable height for part reshaping is at least twice the height of the part to be reshaped, and that typically at least one third has to be calculated for the transport.
  • the motor 35 can be brought to a higher speed within the standstill section 43 of the gear worm 37 (no longitudinal movement of the transfer). In this case, the feed angle 40 is traversed in a shorter time and virtually the angle becomes smaller. In the next sector (transfer of the formed part to the tool), the motor 35 can be decelerated again in such a way that it runs synchronously with the press 31 at the latest when entering the return stroke.
  • the press is running e.g. with a nominal speed of 300 strokes / min
  • the mechanical stepping gear 38 is designed for the standard angles 120 ° / 60 ° / 120 ° / 60 °. ⁇
  • the press is started at the top dead center 39 of the press, and reaches its nominal speed after a short time.
  • the transfer feed sets still half of the feed path 33 back.
  • the transfer feed begins its return stroke 42 and runs back to its end position item E at the same speed as the press.
  • the actual work of the tool takes place in area 42. Accordingly, the grippers only close again at position E around the finished part.
  • the servo motor 35 reduces its speed (below the speed of the press).
  • NB In extreme cases the speed of the servo motor can be reduced to zero.
  • the transfer feed 40 starts at item H.
  • the area between items H and A is run through with increased speed of the transfer gear compared to the press speed. (e.g. double speed in the present example)
  • speed of the servo motor 35 By changing the speed of the servo motor 35 compared to the press speed, the cycle times of the transfer system can be adjusted individually.
  • servo motor does not have to run in stop and go mode and therefore requires less energy (typically a servo motor with half power can be used compared to a longitudinal drive with a servo motor without worm gear)
  • the servo motor changes the speed, it only has to accelerate or decelerate its own mass (rotor) and the mass of the gear worm, because the linearly moving mass of the transfer system is in the standstill sector, the performance of the transfer system can be increased by approx. 20 to 30% compared to a pure servo transfer.

Landscapes

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

Abstract

L'invention concerne un dispositif ménagé sur une presse ainsi qu'un procédé permettant de transporter progressivement des pièces usinées dans la direction longitudinale, depuis un poste de réception, à travers au moins un poste de traitement de la presse. Le dispositif selon l'invention comprend des moyens de transport pour les pièces usinées qui sont déplacés selon un mouvement de va-et-vient, cycliquement et de manière synchrone avec le mouvement de la presse dans la direction longitudinale, ainsi que dans une direction transversale sensiblement perpendiculaire à ladite direction longitudinale, pour saisir et relâcher les pièces usinées. Le mouvement des moyens de transport dans la direction longitudinale se fait par l'intermédiaire d'un entraînement externe qui est uniquement synchronisé avec le mouvement de la presse. L'objectif de cette invention est de concevoir un dispositif présentant un mode de fonctionnement particulièrement souple à des cadences élevées. A cet effet, l'entraînement externe motorisé (20-24, 35-37) est accouplé mécaniquement avec les moyens de transport (4), de façon que le mouvement de va-et-vient de ces moyens de transport (4) soit possible sans inversion de rotation de l'entraînement externe (23, 35).
EP04735864A 2003-06-13 2004-06-03 Dispositif de transfert menage sur une presse Withdrawn EP1633507A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH10332003 2003-06-13
PCT/CH2004/000333 WO2004110667A1 (fr) 2003-06-13 2004-06-03 Dispositif de transfert menage sur une presse

Publications (1)

Publication Number Publication Date
EP1633507A1 true EP1633507A1 (fr) 2006-03-15

Family

ID=33546148

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04735864A Withdrawn EP1633507A1 (fr) 2003-06-13 2004-06-03 Dispositif de transfert menage sur une presse

Country Status (5)

Country Link
US (1) US20060230809A1 (fr)
EP (1) EP1633507A1 (fr)
JP (1) JP2006527088A (fr)
CN (1) CN1805806A (fr)
WO (1) WO2004110667A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005062860A1 (de) * 2005-12-29 2007-07-12 Robert Bosch Gmbh Verfahren und Vorrichtung zum Herstellen gebogener Federelemente
JP2010284716A (ja) * 2009-06-15 2010-12-24 Denso Corp 金型
DE202012006529U1 (de) * 2012-07-09 2012-11-07 Steinhoff & Braun's Gmbh Halte- und Transportvorrichtung
ES2934802T3 (es) * 2018-09-18 2023-02-27 Siemens Ag Planificación de movimiento para un sistema de transporte de una instalación de servoprensas
EP3702062A1 (fr) 2019-03-01 2020-09-02 Adval Tech Holding AG Dispositif d'avancement pour une presse de transfert
CN112935180B (zh) * 2021-01-20 2022-10-04 浙江洪扬汽车零部件有限公司 一种高速螺母成型机
CN114682669A (zh) * 2022-03-31 2022-07-01 江苏亚威机床股份有限公司 一种数控转塔冲床双伺服智能行程补偿冲压系统

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US2934194A (en) * 1959-01-13 1960-04-26 Bliss E W Co Work feed console
US4032018A (en) * 1975-11-21 1977-06-28 Wallis Bernard J Workpiece transfer mechanism
JPH063580B2 (ja) * 1984-09-14 1994-01-12 ソニー株式会社 対数変換方式
US4785657A (en) * 1985-05-17 1988-11-22 Connell Limited Partnership Transfer feed mechanism for power presses
JPH0649380Y2 (ja) * 1988-08-03 1994-12-14 アイダエンジニアリング株式会社 トランスファプレス機械のフィードバー駆動装置
DE4309643C2 (de) * 1993-03-25 2002-06-13 Schuler Pressen Gmbh & Co Umsetzeinrichtung für den Werkstücktransport
DE4428772A1 (de) * 1994-08-13 1996-02-15 Schuler Pressen Gmbh & Co Einrichtung zum dreidimensionalen Antrieb von Greiferschienen
US5640875A (en) * 1995-10-20 1997-06-24 Livernois Die And Automation Die transfer system with modular transfer drive
JPH10146629A (ja) * 1996-11-18 1998-06-02 Aida Eng Ltd トランスファプレスの手動クランプ・アンクランプ装置
US6050124A (en) * 1998-02-04 2000-04-18 Komatsu Ltd. Transfer feeder having two different drive modes and method of its operation
ATE223639T1 (de) * 1998-05-04 2002-09-15 Vantico Ag Vorrichtung zum transportieren dünner platten, insbesondere leiterplatten
ATE261890T1 (de) * 1998-10-05 2004-04-15 Adval Tech Holding Ag Transfervorrichtung an einer presse
JP3773405B2 (ja) * 2000-09-29 2006-05-10 アイダエンジニアリング株式会社 トランスファ装置
US7128195B2 (en) * 2004-03-22 2006-10-31 Linear Transfer Systems Ltd. Workpiece transfer system for stamping press

Non-Patent Citations (1)

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Title
See references of WO2004110667A1 *

Also Published As

Publication number Publication date
JP2006527088A (ja) 2006-11-30
CN1805806A (zh) 2006-07-19
WO2004110667A1 (fr) 2004-12-23
US20060230809A1 (en) 2006-10-19

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