EP0321602B1 - Zangenvorschubgerät mit pneumatisch oder hydraulisch angetriebenen Kurbeltrieben - Google Patents

Zangenvorschubgerät mit pneumatisch oder hydraulisch angetriebenen Kurbeltrieben Download PDF

Info

Publication number
EP0321602B1
EP0321602B1 EP87119094A EP87119094A EP0321602B1 EP 0321602 B1 EP0321602 B1 EP 0321602B1 EP 87119094 A EP87119094 A EP 87119094A EP 87119094 A EP87119094 A EP 87119094A EP 0321602 B1 EP0321602 B1 EP 0321602B1
Authority
EP
European Patent Office
Prior art keywords
feed
crank
gripper
pinion
disposed
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
EP87119094A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0321602A1 (de
Inventor
Matthias Scheitza
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.)
Leinhaas -Industrieberatung Inh Dipl-Ing Werner Leinhaas
Original Assignee
Leinhaas -Industrieberatung Inh Dipl-Ing Werner Leinhaas
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 Leinhaas -Industrieberatung Inh Dipl-Ing Werner Leinhaas filed Critical Leinhaas -Industrieberatung Inh Dipl-Ing Werner Leinhaas
Priority to EP87119094A priority Critical patent/EP0321602B1/de
Priority to DE8787119094T priority patent/DE3775407D1/de
Priority to JP63307949A priority patent/JPH01192436A/ja
Priority to US07/281,540 priority patent/US4925078A/en
Publication of EP0321602A1 publication Critical patent/EP0321602A1/de
Application granted granted Critical
Publication of EP0321602B1 publication Critical patent/EP0321602B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • B21D43/10—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work by grippers
    • B21D43/11—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work by grippers for feeding sheet or strip material
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H20/00—Advancing webs
    • B65H20/16—Advancing webs by web-gripping means, e.g. grippers, clips
    • B65H20/18—Advancing webs by web-gripping means, e.g. grippers, clips to effect step-by-step advancement of web

Definitions

  • the invention relates to a gripper feed device with pneumatically or hydraulically driven crank drives, as known from EP-A-0033252.
  • the aim of this invention is to present such a new construction and to justify its necessity. It is a device of the type mentioned at the beginning for the automatic advancement of strip, strip or profile material in presses, punches or similar machines.
  • This publication describes a feed in which two pliers are attached to the opposite strands of a horizontally running roller chain.
  • This chain is cyclically driven by a reversible hydraulic motor, which in turn is powered by an electric motor-driven hydraulic pump.
  • This system is primarily intended for feed lengths greater than 1000 mm, where the use of hydraulic cylinders would be too expensive and designs with system-related idle stroke would require extremely long positioning times.
  • This patent application describes a simple feed with only one movable pliers, which is not driven by a cylinder, but by an electropneumatic swivel module, which in turn rotates a crank arm adjustable in radius by 180 ° in or against the feed direction.
  • a sinuidal gear is used here to drive the feed tongs in order to achieve smooth start and stop. Since the stroke adjustment on this device is carried out by presetting the crank radius, readjustment or readjustment of the feed length is only possible when the vehicle is stationary.
  • a further disadvantage is the fact that the drivable swivel device must perform a full rotation even with the smallest strokes, which, as already mentioned above, leads to an uneconomically high air consumption.
  • This application describes a feed that broadly summarizes the advantages of the three applications previously mentioned.
  • This is also a double gripper feed, the opposite movement of the gripper is generated by two eccentric discs.
  • This is also intended to achieve particularly gentle starting and braking of the pliers.
  • the stroke length adjustment of the feed tongs is done here, as under c), by a common presetting of the crank radii and is also only possible when the vehicle is stationary.
  • the cyclical swiveling movement of the eccentric discs by 180 ° is achieved in this system by a traction mechanism drive that wraps around both eccentric discs, one strand of which is correspondingly moved by the feed stroke by means of a pneumatic or hydraulic cylinder.
  • a disadvantage of this system is the impossibility of adjusting the stroke during the run and the fact that the driving cylinder must travel its full stroke even with small pliers strokes.
  • Another shortcoming of this system is the property that the maximum stroke length of each feed tongs is limited by the diameter of the driving eccentric disk.
  • an automatic punching system for processing tapes and strips is almost always the same. It essentially consists of an unwinding device for the strip and the so-called reel, a straightening machine for straightening the strip that is curved due to the winding process, and a feeder, which is responsible for pushing the strip into the machine tool cyclically according to the press cycle.
  • clamping force of the belt It depends on the required acceleration and the mass or cross-section of the belt to be transported in order to ensure rapid advancement without slipping through the belt.
  • the tensile force of the feed is also important here, in order to pull a strip through the straightening machine depending on the cross section or curvature, provided that it does not have its own drive.
  • the tensile force also influences the maximum transferable acceleration on the belt.
  • the respective feed is selected according to the task of the system.
  • the path is therefore followed by punching holes in the band in a first station or notching on the side of the band and then the band at the next press stroke, i.e. at the next forming station, using search pins or other types of stops positioned in the tool for the subsequent manufacturing processes.
  • the positioning speed can be influenced by the use of very fast controls, low-mass components and by a suitable damping system for the cyclically moving parts of the feed. Since the often insufficient positioning speed of conventional feeds, when used with modern press systems, often drastically reduce the theoretically possible number of cycles, special attention was paid to this point in the development of this invention.
  • the band feed is carried out by the cyclic linear movement of the feed clamp which clamps the band.
  • a fixed holding tongs now fixes the belt.
  • clamp feeders In order to bring the feed tongs back to the starting position, clamp feeders have to carry out an idle stroke per cycle.
  • the feed tongs are driven by pneumatic or hydraulic cylinders, the pneumatics covering the range of smaller band widths, i.e. smaller tongs sizes up to approx. 250 mm and smaller feed strokes up to approx. 350 mm. Hydraulic drives are used for tasks that exceed these values, since they can transmit larger forces and the pneumatics are uneconomical with regard to air consumption and actuating speed.
  • the clamping forces in the holding or feed tongs are also carried out pneumatically or hydraulically by means of short stroke or bellows cylinders, corresponding to the drive of the feed.
  • the stroke of the feed tongs is limited by one or two adjustable stops.
  • the adjustment is usually divided into a coarse and fine adjustment and is only possible with most devices at a standstill.
  • the stroke is displayed by simply measuring the stop position using a slide gauge, by means of attached scales with vernier and, in the case of particularly complex devices, by mechanical or electronic counting devices.
  • the belt to be fed is clamped between two rolls, either one or both of which are driven, and advanced by the opposite movement of the rolls.
  • the drive is mainly carried out by hydraulic motors, in the case of smaller ones by the use of stepper motors, the rotation of which is usually transmitted to the rollers by low-mass toothed belt drives.
  • the clamping between the rollers which theoretically corresponds to a line, is often problematic. This can lead to slippage of the belt at high rotational accelerations of the rollers or also to squeezing or imprints on the belt when transporting soft materials such as aluminum.
  • the above-mentioned ventilation which is necessary when using follow-on tools, proves to be difficult to implement technically, i.e. exposing the belt for a short time between two feed strokes.
  • Mechanisms such as control cams or pneumatic systems are used to briefly lift one of the two rollers.
  • a constructive pre-selection can already be made for this on the basis of the aforementioned criteria.
  • the pliers must therefore be connected to each other via a mechanical system and set in motion by a drive.
  • a mechanical system and set in motion by a drive To meet the demands for jerk-free acceleration and reduction of the drive power in the range of the set end position of the feed tongs, the use of an articulated drive of whatever type in the drive system of the feed offers itself.
  • the search for control technology solutions is abandoned from the outset, since on the one hand they would probably not prove to be responsive enough, on the other hand they would be too expensive when using a hydraulic drive, and even when using a pneumatic drive because of the compressibility of the air would be impossible to point out.
  • the solution to the overall problem according to the invention provides that that the two collets, which are each guided in guides on both sides, and these are positively connected on the drive side by the two racks fixed to them and the intermeshing, rotatably mounted pinion, that when the pinion is rotated in direction a, the two pliers execute a movement towards one another, that when the pinion is rotated in direction b, the collets move away from each other in direction b1, the cyclical pivoting movement of the pinion being converted into a cyclically opposed collet movement by the toothed racks arranged opposite one another, that the pressure rollers are assigned to the sides of the racks facing away from the tooth in an adjustable alignment with the pinion, that the pinion is driven via a shaft a gear stage by the cyclical following a sinuidal function, in connection with the crank disc, and this by a pressure cylinder, the piston rod of which is pivotally connected to the crank pin mounted on the crank disc, the rectified cylinder tube of which is a common pivoting movement
  • the summary definition of the essential characteristics of the request for protection allows the creation of a clamp feeder that meets the main requirements of the task.
  • the main shaft and the shaft driving the pinion can be driven in a step-down manner by a connecting or intermediate gear stage, it being provided that the gear stage is formed by a chain or belt drive.
  • the two cylinders are arranged on the crank disk and on a collet in such a way that when the piston rod returns in the direction of the collet, the torque to the cam disk axis towards the end position decreases more strongly. and the respective retracting cylinder has the function of a damping cylinder.
  • the adjusting disk which is rotatably arranged on a bush on the shaft, is assigned a second disk, the periphery of which is equipped with worm teeth, into which a worm engages and, when the worm rotates, the bearing journal arranged on the periphery of the adjusting disk its position changes, and thus the distance between the main shaft and the collet can be changed via the bearing pin provided on the pliers side, and that this change also changes the distance between the crank pin and the pin via the piston rod and the cylinder.
  • Cyclic counter-rotating pliers movement with one of the pliers in the start position. An idle stroke is not necessary.
  • Both pliers are moved by one drive, which ensures synchronous pliers movement with a short overall length of the overall system. Optimal positioning accuracy due to the movement between two stops.
  • the feed play adjustment or readjustment option is made possible by changing the toothing distance between the pinion and the rack.
  • the braking power is greatly reduced due to the fact that the accelerating forces or moments continuously decrease towards the end of the stroke.
  • the braking distance is automatically changed by positively driven cams. This means that little or no adjustment of the damping strength to the new stroke conditions is necessary.
  • the collets 1 are shown in their outer end position with solid lines and in their inner end position with broken lines ( Figure 1).
  • the collets 1 are guided on both sides in the guides 2. Both collets 1 are positively connected on the drive side by the two racks 3 fixed to them and the rotatably mounted pinion 4.
  • the pinion 4 rotates in the direction a
  • the two pliers now perform a movement a 'towards one another.
  • the pinion 4 rotates in the direction b
  • the collets 1 move away from one another in the direction b '.
  • the cyclical pivoting movement of the pinion 4 is thus converted into a cyclical counter-rotating pliers movement by the racks 3 arranged opposite.
  • the pressure rollers 5 are adjustably assigned in alignment with the pinion 4 on the side of the rack 3 facing away from the tooth.
  • the pinion 4 already described is now driven by the main shaft 8 via the shaft 6 and the step-down gear stage 7 - shown here as a belt drive.
  • the cyclic a sinuidal function — rotary movement of the shaft 8 is generated by the crank disk 9 firmly connected to it.
  • Position 10 shows one of the driving pneumatic or hydraulic cylinders, whose piston rod 11 is pivotally connected to the crank pin 12 mounted on the crank disk 9 and the cylinder tube of which can also perform a pivoting movement around the bearing pin 13.
  • the throttle function of the respective retracting cylinder is to be switched on via a cam 20 mounted centrally between the bearing journals 12 and 12.1. which triggers a switch 21 each time it passes through the center line of the crank disk 9 shown here horizontally. Since the cylinder movement takes place alternately symmetrically, the cam 20 always runs past the switch 21 regardless of the stroke setting after the respectively set half rotation of the crank disk 18. The length of the braking distance is therefore not always constant, as is the case with conventional feed devices, but corresponds to half a feed length.
  • the adjustment of the feed length or the adjustment of the swivel angle of the adjusting disk 18 should take place in that the collet 1, on which the two cylinders 10 and 10.1 are articulated by means of the bearing journal 13 and 13.1, are displaced in the direction of the adjusting disk 18 when the feed length is reduced or, when the feed length is increased, are moved away from it. Since a movement of the adjustment slide 14 is not required for the functioning of the system, an adjustment of the stroke length in the barrel is possible without any problems.
  • the kinematic equation of motion of the drive system can be derived from the equation of the offset crank drive known in technical mechanics.
  • the adjusting disk 18 is connected to the adjusting slide 14 by means of the bearing bolts 15 and 17 and the connecting rod 16 connecting them. With a corresponding rotation of the adjusting disk 18, the adjusting slide 14 now moves, depending on the direction of rotation, towards or away from the crank disc. If the pull rod 16 is now arranged in any plane parallel to one of the driving cylinders, adjusting the adjusting disk 18 by a few degrees results in the same change in the swing angle of the crank disk 9.
  • the movement function imposed by the adjusting disk 18 and the adjusting slide 14 exactly represents the movement characteristic according to which the distance s has to be changed in order to achieve a linear adjustment.
  • FIG. 1 shows a possible solution in such a way that the adjusting disk 18 is not mounted next to, but above the crank disk 9, as shown in FIG. 3 or FIG. This enables a more compact solution.
  • the compact design of this solution principle is also illustrated in FIG. 1.
  • the overall length is determined exclusively by the collet stroke and is no longer than in conventional collet feeders, where the space for the second collet shown here would be required by the driving cylinder.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Feeding Of Workpieces (AREA)
  • Manipulator (AREA)
  • Advancing Webs (AREA)
  • Press Drives And Press Lines (AREA)
EP87119094A 1987-12-23 1987-12-23 Zangenvorschubgerät mit pneumatisch oder hydraulisch angetriebenen Kurbeltrieben Expired - Lifetime EP0321602B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP87119094A EP0321602B1 (de) 1987-12-23 1987-12-23 Zangenvorschubgerät mit pneumatisch oder hydraulisch angetriebenen Kurbeltrieben
DE8787119094T DE3775407D1 (de) 1987-12-23 1987-12-23 Zangenvorschubgeraet mit pneumatisch oder hydraulisch angetriebenen kurbeltrieben.
JP63307949A JPH01192436A (ja) 1987-12-23 1988-12-07 空気圧又は油圧駆動されるクランク装置を備えた挟持送り装置
US07/281,540 US4925078A (en) 1987-12-23 1988-12-08 Gripper feed device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP87119094A EP0321602B1 (de) 1987-12-23 1987-12-23 Zangenvorschubgerät mit pneumatisch oder hydraulisch angetriebenen Kurbeltrieben

Publications (2)

Publication Number Publication Date
EP0321602A1 EP0321602A1 (de) 1989-06-28
EP0321602B1 true EP0321602B1 (de) 1991-12-18

Family

ID=8197537

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87119094A Expired - Lifetime EP0321602B1 (de) 1987-12-23 1987-12-23 Zangenvorschubgerät mit pneumatisch oder hydraulisch angetriebenen Kurbeltrieben

Country Status (4)

Country Link
US (1) US4925078A (ja)
EP (1) EP0321602B1 (ja)
JP (1) JPH01192436A (ja)
DE (1) DE3775407D1 (ja)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK0487456T3 (da) * 1990-11-23 1995-01-30 Styner & Bienz Ag Fremgangsmåde og indretning til fremføring af et bånd eller en strimmel, især til udskæring af råemner
IT1266010B1 (it) * 1993-12-30 1996-12-16 Dalcos Srl Alimentatore a pinze per nastri di lamiera
CN109108951B (zh) * 2018-10-23 2023-10-03 嘉兴新维液压缸有限公司 一种自动送料机械手装置
CN112173782A (zh) * 2020-09-29 2021-01-05 熊婷婷 一种印刷纸张切割前对齐整理装置
CN112570765A (zh) * 2020-12-11 2021-03-30 江西昌浩实业有限公司 一种门窗定位钻套时的待加工门窗输送装置

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2406508A (en) * 1945-03-02 1946-08-27 Robert A Papsdorf Self-acting stock feed
US2468236A (en) * 1946-02-15 1949-04-26 Harold E Rue Device for feeding strip material
DE1265106B (de) * 1965-04-07 1968-04-04 Frei Hans Joachim Zangenvorschubgeraet fuer Blechbaender oder Blechstreifen
AU3051067A (en) * 1967-11-29 1970-06-04 Vilcan Electrics Proprietary Limited Hitch feeder
US3583268A (en) * 1970-05-15 1971-06-08 Albert W Scribner High speed stock feeder
NL7107756A (ja) * 1970-06-09 1971-12-13
DE2441681A1 (de) * 1974-08-05 1976-03-11 Paul Vinson Presse zur werkstoffbearbeitung
FR2474357A1 (fr) * 1980-01-24 1981-07-31 Normatic Sa Dispositif pour deplacer des produits en bobines ou en barres vers une machine
US4580710A (en) * 1982-08-10 1986-04-08 Plessey Incorporated Stock feeder with hydraulic shock absorber
DE3373635D1 (en) * 1983-05-04 1987-10-22 Bruderer Maschinenfabrik Ag E Gripper feeding device for presses or the like
US4610380A (en) * 1984-10-26 1986-09-09 Pressmate, Inc. Stagger feeder

Also Published As

Publication number Publication date
JPH01192436A (ja) 1989-08-02
US4925078A (en) 1990-05-15
DE3775407D1 (de) 1992-01-30
EP0321602A1 (de) 1989-06-28

Similar Documents

Publication Publication Date Title
EP1591174B1 (de) Biegevorrichtung für stab- und rohrförmige Werkstücke
DE102007051894B4 (de) Freigabemechanismus und mit diesem versehenen Richtvorrichtung
EP1640084B1 (de) Vorschubvorrichtung
DE2461466B2 (de) Drahtsägemaschine
EP0121826A2 (de) Stanz- und Biegewerkzeug-Aggregat
EP2289643B1 (de) Vorrichtung zum Biegen länglicher Werkstücke
DE3143177C2 (de) Walzenzuführungseinrichtung
AT401896B (de) Verfahren zum biegen eines werkstückes aus blech sowie blechbiegemaschine
DE2613269C3 (ja)
EP0321602B1 (de) Zangenvorschubgerät mit pneumatisch oder hydraulisch angetriebenen Kurbeltrieben
DE4127779C2 (de) Vorrichtung zum Vorschub eines Abschnitts einer dünnen Materialbahn mit vorbestimmter Schrittlänge
DE2312158C3 (de) Biegemaschine zur Herstellung von KraftfahrzeugstoOstangen aus geraden Metallprofilen
DE2131013A1 (de) Presse,insbesondere Ziehpresse
DE4419827A1 (de) Vorrichtung und Verfahren für das Reduzieren des Durchmessers eines zylindrischen Werkstückes
DE2801107C3 (de) Verfahren und Vorrichtung zur Herstellung von zylindrischen Schraubenfedern aus Draht
DE19526064C2 (de) Materialvorschubeinrichtung
EP0561025A1 (de) Einrichtung zum Herstellen von gebogenen Abschnitten an einem Rohr, insbesondere zur Herstellung einer Rohrschlange
EP1304181A1 (de) Vorrichtung zum schrittweisen Vorschieben eines bandförmigen Werkstückes
EP1345715B1 (de) Schmiedepresse mit stellvorrichtung auf matrizenseite
EP0188648B1 (de) Transferpresse
EP2529922B1 (de) Antriebseinrichtung für einen Press-, Stanz- oder Umformautomaten
DE10244483B4 (de) Profilwalzmaschine mit Kraftrahmen zum Walzen mit außenverzahnten Rundwalzwerkzeugen
DE202006016203U1 (de) Umformaggregat, insbesondere Biegeaggregat
WO2001062408A1 (de) Biegevorrichtung zum biegen von plastisch verformbarem bandmaterial
EP1181749B1 (de) Zuführvorrichtung für elektrische kontaktelemente in crimpwerkzeuge einer crimppresse

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE ES FR GB GR IT LI LU NL SE

RBV Designated contracting states (corrected)

Designated state(s): DE FR IT

17P Request for examination filed

Effective date: 19900224

17Q First examination report despatched

Effective date: 19910531

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR IT

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

REF Corresponds to:

Ref document number: 3775407

Country of ref document: DE

Date of ref document: 19920130

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19920214

Year of fee payment: 5

ET Fr: translation filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19920225

Year of fee payment: 5

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19930831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19930901

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051223