EP1640084B1 - Feeding device - Google Patents

Feeding device Download PDF

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Publication number
EP1640084B1
EP1640084B1 EP05021192A EP05021192A EP1640084B1 EP 1640084 B1 EP1640084 B1 EP 1640084B1 EP 05021192 A EP05021192 A EP 05021192A EP 05021192 A EP05021192 A EP 05021192A EP 1640084 B1 EP1640084 B1 EP 1640084B1
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EP
European Patent Office
Prior art keywords
clamping
feed
feed apparatus
jaw
clamping jaw
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.)
Active
Application number
EP05021192A
Other languages
German (de)
French (fr)
Other versions
EP1640084A2 (en
EP1640084A3 (en
Inventor
Johann Köpf
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.)
Otto Bihler Handels Beteiligungs GmbH
Original Assignee
Otto Bihler Handels Beteiligungs GmbH
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 Otto Bihler Handels Beteiligungs GmbH filed Critical Otto Bihler Handels Beteiligungs GmbH
Priority to EP06006565A priority Critical patent/EP1676655B1/en
Priority to PL05021192T priority patent/PL1640084T3/en
Priority to PL06006565T priority patent/PL1676655T3/en
Publication of EP1640084A2 publication Critical patent/EP1640084A2/en
Publication of EP1640084A3 publication Critical patent/EP1640084A3/en
Application granted granted Critical
Publication of EP1640084B1 publication Critical patent/EP1640084B1/en
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Anticipated expiration legal-status Critical

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Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21FWORKING OR PROCESSING OF METAL WIRE
    • B21F23/00Feeding wire in wire-working machines or apparatus
    • B21F23/002Feeding means specially adapted for handling various diameters of wire or rod
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21CMANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C1/00Manufacture of metal sheets, metal wire, metal rods, metal tubes by drawing
    • B21C1/16Metal drawing by machines or apparatus in which the drawing action is effected by other means than drums, e.g. by a longitudinally-moved carriage pulling or pushing the work or stock for making metal sheets, bars, or tubes
    • B21C1/27Carriages; Drives
    • B21C1/30Drives, e.g. carriage-traversing mechanisms; Driving elements, e.g. drawing chains; Controlling the drive
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21DWORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D43/00Feeding, 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
    • B21D43/02Advancing work in relation to the stroke of the die or tool
    • B21D43/04Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
    • B21D43/10Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work by grippers
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21DWORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D43/00Feeding, 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
    • B21D43/02Advancing work in relation to the stroke of the die or tool
    • B21D43/04Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
    • B21D43/12Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work by chains or belts
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B21MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21FWORKING OR PROCESSING OF METAL WIRE
    • B21F23/00Feeding wire in wire-working machines or apparatus
    • B21F23/005Feeding discrete lengths of wire or rod

Definitions

  • the present invention relates to a feed device for feeding long material, in particular of strip, wire or profile material, along a feed direction according to the preamble of claim 1.
  • Such a device is known from US 3 684 145 A.
  • This comprises a minimal gap width changing means in the form of a merely manually operable threaded rod in order to adapt the known feed device to long material of different material thickness.
  • feed devices long material is fed to subsequent processing stations, which usually reshape the long material without cutting, in particular by bending, punching and the like.
  • a clamping device with clamping jaws is reciprocally driven by an eccentric.
  • the clamping device of the known feed device clamps the long material, then with the clamped long material, the desired feed dimension in Moves feed direction, then solves the clamping engagement and is moved back against the feed direction to the starting position.
  • feed devices in the form of so-called Rollenvorschübe known.
  • axially parallel rotatable rollers face each other, so that between their peripheral surfaces, a gap is formed, through which the long material is conveyed through.
  • the rollers lie on opposite sides of the long material and rotate in opposite directions.
  • One or both rollers are driven to impart the feed to the elongate material.
  • the feed device is designed such that the at least one clamping device has at least two clamping nip defining therebetween jaws, of which at least one of the gap width along a clamping movement path on the other jaw to and from this is movable.
  • the at least two jaws can come into abutment on respectively opposite sides of the long material and thus transmit as large a clamping force as possible to the long material.
  • the jaws are this held relative to a Klemm Rheinsève movable in this.
  • a cam track is provided, which displaces a jaw movable along the clamping movement path to and / or away from the respective other jaw.
  • Mechanical motion controls have the further advantage that they are fast and largely failsafe.
  • not only the necessary movement of the jaw can be effected by the cam track by the positive control thus taking place, but at the same time the required clamping force to be introduced by the cam track in the jaw.
  • the structure of the feed device simplified significantly.
  • the minimum gap width changing means comprises a force device in force-transmitting relationship with at least one of the two opposing jaws such that the at least one jaw is forcefully applied by the force device to the opposing jaws Jaw to and away from this is displaced.
  • a hydraulic cylinder / piston unit particularly preferably a double-acting hydraulic cylinder / piston unit, used because this is a very high power with low space requirements can be realized.
  • the variability of the minimum gap width by means of the above-described minimum gap width changing means is structurally solved in a simple manner by the cam track being displaceable with the power tool in power transmission relationship and is driven by the force of the power device for displacement, wherein a displacement of the cam track by the power device causes a displacement of the at least one cooperating with the cam track jaw.
  • the cam can be displaced relative to the clamping device as a whole simply by the power device, so that the movable along the clamping movement path jaw occupies different jaw positions with different nip widths depending on the displacement position of the cam.
  • the cam track is acted upon in a predetermined displacement direction with the biasing force of a biasing spring element.
  • the biasing spring element can shift the cam track in a defined position. This is preferably a position in which a clamping of the long material is ensured, ie a position of the smallest possible clamping gap width.
  • any material is designated which in a spatial direction has a considerable, about at least two to three times, greater extent than in the other two spatial directions.
  • the term “long material” means a band, wire or profile material, which is advantageously unwound from a supply. This leads to advantageous longer service life between a long material change on the feed device.
  • a further advantage of the clamping device according to the invention is that a dynamic load acting on the at least one clamping device can be reduced in its absolute value by selecting correspondingly large deflection radii from the change in direction of its moving speed when circulating compared with a direction-reversing clamping device at the same feed rate.
  • the centripetal acceleration resulting in a change in direction of velocity along a closed path is proportional to the square of the orbital velocity and is inversely proportional to the radius of curvature of the orbit.
  • the feed path may be formed by a straight line piece and the remainder of the closed loop path is curvedly connected to the straight feed path.
  • a greater radius of curvature of the web can be selected by accepting a larger track length.
  • the total length of the closed orbit can be kept short for a given length of the feed path in an advantageous development of the invention, if a likewise substantially rectilinear return path is provided parallel to a substantially rectilinear feed section, wherein feed path and return path are connected by curved track sections.
  • the average radius of curvature of this curved track sections corresponds to half the distance between the feed and return path.
  • the diameter of a curved web segment is of the order of magnitude of the at least one clamping device in the direction of rotation, preferably if the diameter is equal to this dimension or greater than this.
  • the maximum feed speed achievable by the feed device can be increased, since no complete circulation of a clamping device has to be awaited between two feed operations. Rather, more clamping devices according to a preferred embodiment of the invention may be provided so that when a clamped engagement with the long material clamping device is disengaged by adjustment in the release position, a not yet in clamping engagement further clamping device by adjusting in the clamping position in clamping engagement comes with the long material. It will be understood by those skilled in the art that such engagement changes need not necessarily occur at the exact same time, although this is particularly preferred because it is then ensured that a clamping device is always in clamping engagement with the elongate material. Such an intervention change can also take place in a predetermined time window containing the intervention end, for example of up to 10% of the set cycle time with which the feed device is operated.
  • the total transferable from the feed device to the long material for its transport force can be increased advantageously in that the feed device comprises a plurality of clamping devices and a plurality of clamping devices during their movement in the feed direction is simultaneously in the clamping position.
  • the transferable from each of the clamping device simultaneously located in clamping position on the long material transferable clamping forces add up to a total force, so that the long material can be greatly accelerated and slowed down again without a position inaccuracy of the strip material is to be feared after deceleration.
  • the areal pressure contact between the long material in the region of the clamping engagement as compared to the known ones, can be achieved by the planar contacting contact which is possible between the clamping jaw and the long material Roller feeders are significantly reduced. This means that, despite the transfer of high clamping forces in general, only comparatively moderate pressures act on the long material locally.
  • each clamping device can have a joint device which can be coupled or coupled to a corresponding joint counter-device of a subsequent clamping device in the direction of rotation. It is sufficient if the axes of the clamps interconnecting joints are substantially parallel, so that the mutually coupled clamping devices are rotatable relative to each other to form a closed chain.
  • the at least one clamping device is connected for common movement with a shape-variable endless motion transmission part.
  • the shape-variable endless motion transmission part can be, for example, a chain, in particular a lamella chain, which allows transmission of very high forces in the direction of rotation.
  • a flexible toothed belt is preferred as a motion transmission part. If a plastic toothed belt is used, the resilience of the plastic provides for a damping of a possibly occurring starting and / or stopping shock.
  • the advantageous use of a toothed belt with metal core, in particular steel core thereby ensures that despite the temporary damping by elastic deformation of the toothed belt in the reached end position (rest position), the desired position is achieved with high accuracy.
  • a toothed belt with double-sided tooth formation is preferred, since then both a drive force transmission device on a first side of the toothed belt can be positively engaged with this, as well as the at least one clamping device on the first opposite second side of the toothed belt in the circumferential direction positively with this can be brought into engagement, so that neither the drive force transmission device nor the at least one clamping device has slip in the direction of rotation, which allows a very high positioning accuracy even at high feed rates and short cycle times.
  • the cam track may be configured to move the jaw in one direction only or in both directions, i. H. moved towards and away from the long material.
  • the secure clamping of the long material in the clamping device is of greater importance than lifting the jaw from the long material.
  • the latter does not necessarily have to be done, for example if the surface quality of the long material is not important.
  • the jaw must not be lifted from the long material, but it is sufficient to reduce the clamping force so far that the strip material can get out of engagement with the at least one clamping device.
  • the feed device is preferably designed such that the at least one along the Klemmschisbahn movable jaw is biased by a spring means in a Abhebewolf greater gap width and cooperates with the cam track for movement in an abutment position lesser gap width.
  • a particularly high clamping force and at the same time compact construction of the at least one clamping device can be obtained according to an advantageous embodiment of the present invention, when the cam track, which adjusts the one jaw during its passage to the opposite other clamping jaw, in consideration of a passage through the Feed path orthogonal to a jaw contact surface of the other jaw is arranged at a distance.
  • the jaw abutment surface is that surface of the jaw which comes to rest on one side thereof when clamping the long material.
  • the at least one along the Klemmschisbahn movable jaw may be formed as an elongated shape at one longitudinal end of a jaw contact surface is provided for contact with the elongate material and provided at the other longitudinal end a rolling element for rolling on the cam track is.
  • it is intended to use a force acting in two opposite directions force device, so that the cam track by the force of the power device safely and selectively adjustable in both the minimum gap width increasing direction and in a selbige decreasing direction.
  • a large degree of freedom in the arrangement of the power device as well as an adjustment of a movement of a force output element of the power device to the desired displacement movement of the cam can be achieved, that the power device is connected by a gear with the cam track.
  • the transmission comprises a rotatable eccentric from the power unit, with which the cam track is connected.
  • an eccentric can be very simple to implement a linear movement of the force output element, such as the piston of a hydraulic cylinder in an angled to this, in particular orthogonal linear displacement movement of the cam track.
  • the force output element such as the piston of a hydraulic cylinder in an angled to this, in particular orthogonal linear displacement movement of the cam track.
  • eccentric dimensions such as the eccentric diameter and the eccentricity
  • a translation or reduction of movement and force can be achieved.
  • the power device can be arranged space-saving in a surrounded by the at least one circumferential clamping device area.
  • the lying within the orbit of the clamping device area which anyway belongs to the space of the feed device, can be used meaningfully to obtain a compact feed device with low space requirements.
  • the at least one clamping device rotates when a flat strip material is fed in the strip material plane or in a plane parallel to the strip material plane. With strip material level is the main extension plane referred to the strip material in the feed path. It has been found that with this circulation direction a very small space requirement can be realized.
  • At least one of two clamping nips defining therebetween clamping jaws of the at least one clamping device is resilient in a direction enlarging the nip gap.
  • both clamping jaws are designed to be yielding in a direction enlarging the clamping gap.
  • the jaw can spring at least with a small spring travel, so that the clamping force is not abruptly exerted in full on the long material, but can build up over a certain period of time.
  • the flexible design of at least one jaw is particularly advantageous in the case described above in that a plurality of clamping devices are simultaneously in the clamping position and keep a long material section clamped. Then can be compensated for by the flexibility of the jaws a possibly existing thickness variation of the long material over its length. This is particularly advantageous when using mechanical motion controls for the jaws.
  • the jaw is a substantially elongated member, which comes through a stamping movement by a translational movement to the plant to the long material, in the absence of a possible Bingenachgiebmaschine another implementation of Compliance required.
  • the at least one resilient jaw is formed at least in two parts, wherein two jaw parts are arranged relative to each other by interposition of a spring device at least in the Klemmspaltver sparungsraum.
  • the at least one flexible clamping jaw is an elongate component which is provided at least in sections with at least one recess, preferably an intersecting recess, whose course direction has a component orthogonal to the longitudinal direction of the clamping jaw.
  • clamping jaws of sufficient flexibility can be realized with very small dimensions, so that the total masses moved in the direction of rotation can be kept small.
  • a particularly advantageous effect is achieved if at least one recess, preferably a plurality of recesses, pass through the clamping jaw.
  • Such recesses can be easily prepared by drilling or by wire EDM.
  • the at least one recess passes through the clamping jaw in the region of its transverse center, so that spring travel is available in a central region of the clamping jaw.
  • successive recesses may be provided consecutively in the longitudinal direction of the clamping jaw in succession, which may be angularly offset relative to one another about a longitudinal axis of the clamping jaw in order to increase the spring action.
  • both clamping gap between them defining jaws of a clamping device with changing the gap width towards each other and away from each other movable.
  • the clamping device for receiving the two clamping gap between them defining jaws may have a one-piece housing regardless of their individual mobility, so that the alignment of the two jaws to each other also maintained over long periods of operation. Even if the housing is not integrally formed, a similar positional accuracy of the jaws to each other can be obtained over a long period of operation by attaching the clamping device to a variable-shaped endless motion transmission device, especially on the double-sided toothed timing belt, as in the one-piece housing.
  • both of a clamping gap between them defining jaws toward each other and away from each other are movable, and the second jaw in the above detailed manner for movement to the other jaw to be driven.
  • a cam track can be used, which can be developed in the same advantageous manner as the above-described cam track of the former jaw.
  • the cam tracks and the at least one clamping device preferably also the minimum gap width changing means, symmetrically arranged with respect to a symmetry plane passing through the clamping gap in the gap center between the clamping jaws.
  • a feed device according to the invention is generally designated 10. This serves to transport an elongated strip material 12 clocked along the feed direction V.
  • the feed device 10 is driven by a numerically controlled electric motor 13 via a motion-reducing intermediate gear 14. By reversing the direction of movement of the motor 13, the feed device 10 can also transport in the opposite direction.
  • the advancing device 10 has a plurality of clamping devices 16 which, driven by the electric motor 13, rotate along a closed path B (see FIG. 2).
  • Each clamp 16 has a clamp body 18 in which two opposed jaws 20 and 22 are movable toward and away from each other by varying the width of a nip formed therebetween.
  • the clamper body 18 is preferably made of HC-coated aluminum to obtain a small moving mass with sufficient robustness.
  • the clamping jaws 20 and 22, which are formed substantially identically in the embodiment of the feed device according to the invention shown in FIGS. 1-5, will be described in detail in connection with FIGS. 6a and 6b.
  • the clamping devices 16 are mirror-symmetrical with respect to a plane perpendicular to the plane of Fig. 1 center plane S of the long material 12, so that only the upper half of the clamping device 16 is explained in more detail.
  • the lower half please refer to the description of the upper half.
  • the jaw 20 is arranged in the clamping device housing 18 in the direction of the double arrow K to the strip material 12 and away from this along the straight line KB displaced.
  • the arrowhead K1 denotes a direction towards the long material 12 and the arrowhead K2 points away from the long material 12.
  • the double arrow K runs parallel to the drawing plane of FIG. 1 and orthogonal to the feed direction V.
  • the straight line KB thus describes the linear clamping movement path along which a clamping jaw is movable.
  • Two coil springs 24 and 26 clamp the jaw 20 in the direction K2 away from the long material 12 and thus bring a Wälzrolle 28 in Appendix to a cam surface 30 of a cam track 32nd
  • the roller roller 28 rolls permanently under the pressure of the coil springs 24 and 26 on the cam surface 30 of the cam track 32.
  • the cam surface 30 indicative of the strip material 12 is designed such that the clamping jaw 20 is displaced in the feed path 34 of the cam track 32 in the direction of the arrow K1 toward the strip material 12 and arrives in abutting engagement therewith.
  • the lower cam track 36 is formed with respect to the plane of symmetry S mirror image of the upper cam track 32, so that the lower jaw 22 is adjusted while passing through the feed path 34 to the long material 12 out.
  • the cam surface 30 opposite Top 38 of the cam track 32 is preferably in a plane parallel to the plane of symmetry S, so that the increase in thickness of the cam track 32 in the region of the feed path 34 leads to an approximation of the cam surface 30 to the long material 12.
  • the housing 18 of the clamping device 16 is preferably formed in one piece, so that a precise comparison of the jaws 20 and 22 is maintained even over long periods of operation.
  • the housing 18 may be excluded from the in the assembled state of the clamping devices 16 to the respective cam tracks facing sides, so that the coil springs 24 and 26 and the jaw 20 inserted in the direction of the arrow K1 in the upper half of the housing 18 of the clamping device 16 can be.
  • the jaw 22 and the biasing them against the cam track coil springs in the direction of Arrow K2 are inserted into the lower half of the housing 18 of the clamping device 16. against falling out, the respective jaws 20 and 22 are secured in the ready state of the feed device by their contact with the cam track 32.
  • the increase in thickness of the cam track 32 in the feed section 34 is not abrupt, but via an input inclination section 40. However, it is ensured that there is always more than one clamping device 16 in the feed section 34, so that the long material 12 of several clamping devices 16 clamped at the same time and can be transported in the feed direction V. Preferably, three clamping devices 16 are always in the clamping position and thus in clamping engagement with the long material 12.
  • a corresponding outlet inclination section 42 is also provided at the end of the feed path 42 to provide a smooth transition from the clamping position to the release position.
  • the rolling axis of Wälzrolle 28 of the jaw 20 of the leftmost clamping device 16 of four provided in the feed path 34 clamping means just below the end of the slope portion 40 is also located the rolling axis of the Wälzrolle 28 of the jaw of rightmost clamping device of this group of four at the beginning of the slope section 42.
  • the clamping devices 16 have at their leading end in the feed direction V a Form gleicheingriffsgeometrie 44 and at its trailing end in the feed direction V a positive connection counter-geometry 46. As can be seen in FIGS. 1 and 2, during a directional deflection of the clamping devices 16, these positive locking and positive locking counter-geometries disengage, while they are in positive engagement with the clamping devices 16 in the feed path 34.
  • This form-fitting engagement essentially serves to ensure a predetermined positional relationship of adjacent clamping devices 16 to one another and in particular prevents them Rotation of the clamping devices 16 about an orthogonal to the feed direction V and lying in the plane of FIG. 1 axis of rotation.
  • a hydraulic cylinder 48 is provided within the orbit B of the clamping devices 16 (see also Fig. 2).
  • the extendable piston rod 50 of the hydraulic cylinder 48 is connected to an upper and a lower rack 52 and 54, respectively.
  • the hydraulic cylinder 48 is double-acting, so that the piston rod 50 can be moved in and counter to the feed direction V.
  • the gear 56, to which the upper rack 52 belongs, and the gear 58, to which the lower rack 54 belongs, are mirror-symmetrical with respect to the plane of symmetry S and arranged so that only the upper gear 56 will be described.
  • the lower gear 58 reference is expressly made to the description of the transmission 56.
  • the rack 52 which is biased by a coil spring 60 against the biasing direction V, meshes with a peripheral toothing formed on cylinder rollers 62 and 64.
  • Each of these cylindrical rollers comprises at each of its axial longitudinal ends an eccentric eccentric pin arranged with respect to its central axis.
  • FIG. 1 shows the central axis 64a of the cylindrical roller 64 and the eccentric pin 66 fastened to it.
  • the eccentric pin 66, as well as the other eccentric pins of the other cylindrical rollers are coupled with the cam tracks 32 and 36 movement and force transmission, so that by rotation of the cylindrical rollers 62 and 66 due to a displacement of the rack 52 in the feed direction, the upper cam track 32 in the direction of Arrow K2 is raised orthogonal to the feed direction. Conversely, the cam track 32 by a displacement of the rack 52 against the feed direction V, for example in case of hydraulic failure caused by the biasing force of the coil spring 60, along the arrow K1 to the strip material 12th be lowered down.
  • the lower cam track 36 is moved mirror-inverted at the same displacement of the rack 54.
  • the cam tracks 32 and 36 by means of the piston rod 50, which are connected to this common motion associated racks 52 and 54 and the meshing with these cylindrical rollers on the eccentric pin disposed thereon toward each other and away from each other.
  • This makes it possible to change the minimum achievable gap width between two opposing jaws 20 and 22 in the feed path 34.
  • the feed device 10 can be adjusted by targeted application of the hydraulic cylinder 48 with hydraulic oil pressure to long materials 12 of different thickness in the spatial direction of the double arrow K.
  • Fig. 1 only indicated is a toothed belt 68, with which the clamping devices 16 are positively connected. However, the timing belt 68 is better seen in Fig. 2.
  • the feed device is essentially mirror-symmetrical not only to the plane of symmetry S parallel to the plane of the drawing, but also to a plane of symmetry T which is orthogonal to the plane of the drawing and substantially parallel to the plane of the drawing of FIG.
  • the hydraulic cylinder 48 which is also arranged substantially symmetrically to the plane of symmetry T, is circulated by the clamping devices 16, resulting in a space-saving overall arrangement of the feed device 10.
  • the hydraulic cylinder 48 is formed in an extremely advantageous manner in one piece with an inner housing 69 which supports the toothed belt guide.
  • the toothed belt 68 which is a plastic belt with steel core, is at its radially inner, as well as on its radially outer side with a toothing Mistake.
  • the radially inner toothing 68a allows exact propulsion through the drive toothed roller 70, which is driven by the coupled to the transmission output shaft 14a roller shaft 70a for rotation in the counterclockwise direction with which it is connected via a splined shaft to transmit torque.
  • the second deflection is accomplished by a idler roller 72 spaced apart from the drive roller 70 which is displaceable by and away from the drive roller by a screw 74 to maintain the timing belt 68 in a sufficiently tensioned condition.
  • the drive roller 70 and the idler roller 72 are designed substantially identical.
  • a plurality of drive and idler pulleys spaced substantially in the width direction of the toothed belt 68 can also be used.
  • the external toothing 68b of the toothed belt 68 permits a fixing of the clamping devices 16 on the toothed belt 68 that is positive in the feed direction V or in the direction of rotation, so that a high positioning accuracy of the clamping devices is possible.
  • the Klemm Rheins Republic 18 are mounted with handles 76 on the timing belt 68. Such grips 76 are provided at the upper and lower ends of each clamp body 18 and engage around and engage behind the toothed belt 68 at its edges.
  • the rear grip of the toothed belt by the gripping pieces 76 thereby only captures a tooth of the radially inner toothing 68a of the toothed belt 68 which is central in the circumferential direction with respect to the dimension of a clamping device 16 so that the clamping device 16 is fixed to the toothed belt during a deflection, the flexible toothed belt 68 itself otherwise, however, disengage from the substantially rigid housing 18 of the clamp 16 and can abut against the guide rollers 70 and 72.
  • Fig. 3 is a section along the plane III-III is shown by the feed device 10.
  • Fig. 3 is u. a. to see how the transmission output shaft 14a of the intermediate gear 14 is coupled via a shaft-hub connection 84 with the roller shaft 70a, which in turn is splined to the drive roller 70 for torque transmission.
  • the roller shaft 70a is frictionally supported for rotation by two spaced rolling bearings.
  • Fig. 3 can be seen very well that the cam surface 30 of the cam track 32 is disposed within the feed path 34 substantially parallel to a bearing plane 12a for the jaw 20 at a distance therefrom.
  • This makes it possible to use a stamp-like clamping jaw 20, which is loaded in a state of clamping substantially only by pressure. With this construction, it is possible to exert higher clamping forces on the long material 12 than in the case of bending jaws. In addition, the dimensions of the individual jaws can be kept small. It only has to be ensured that the cam surface 30 can be reliably scanned and clamping force can be exerted on the long material 12.
  • Fig. 4 which is a sectional view taken along the plane IV-IV in Fig. 1, the hydraulic cylinder 48 surrounded by the clamping means 16 and the toothed belt 68 can be seen with its piston rod 50 in cross section.
  • toothed belt 68 is gripped in its width direction at each edge of a handle 76 and engaged behind.
  • the gripping pieces 76 are screwed to the housing 18 of the clamping device 16.
  • the screws used for this purpose are shown in Fig. 1.
  • One is provided there with the reference numeral 76a.
  • Fig. 4 the gear 56 and the gear 58 for adjusting the minimum gap between the jaws 20 and 22 in the feed path 34 are shown.
  • the cylindrical roller 62 is rotatably supported about its central axis 62a.
  • a toothing formed on its lateral surface meshes with the rack 52.
  • the rack 52 is connected for common movement with the piston rod 50 of the hydraulic cylinder 48 (see Fig. 2 at KP).
  • the cylindrical roller 62 with the cam track 32 coupled eccentric pins 63a and 63b.
  • the eccentrically provided with respect to the cylinder roller axis 62a pin 63a is coupled motion and force transmitting with the cam track 32 on the return path 82, while the provided at the opposite longitudinal end eccentric pin 63b is coupled to the cam track 32 on the side of the feed path movement and force transmitting.
  • the eccentric pins 63a and 63b of the cylindrical roller 62 are aligned coaxially with each other.
  • the remaining cylindrical rollers of the gears 56 and 58 are formed substantially identical to the cylinder roller 62.
  • the eccentric pins 63a and 63b are received in holes in the cam track 32.
  • FIG. 5 shows a section along the plane VV in FIG. 1 through the axis of rotation of the idler roller 72.
  • the same components as in the preceding figures 1-4 are with the same reference numerals, reference being made to the description of FIG. 5 to the description of the preceding figures.
  • jaws 20 and 22 are shown in detail, which are used in the clamping devices 16 of the feed device 10 according to Figures 1-5. In the following, only one clamping jaw 20 will be described, this description also being applicable to the clamping jaws 22, since these clamping jaws are identical.
  • the clamping jaws 20 have at their one longitudinal end 20a a rolling roller 28 which is designed to roll on the cam surface 30.
  • a commercially available rolling bearing can be used in an advantageous manner, wherein the outer surface 28a of the bearing outer ring is used as a rolling surface.
  • the Wälzrolle 28 is rotatably mounted about a pin 88 which is mounted in the mounted on the feed device state with the cam surface 30 parallel pin axis 88a.
  • a fork-like bearing formation 90 is provided at the longitudinal end 20a of the clamping jaw 20, in which the rolling roller 28 is rotatably received.
  • To the bearing formation 90 includes in the longitudinal direction of the jaw 20 to a shaft portion 92 which extends to the second longitudinal end 20 b of the jaw 20.
  • the shaft portion 92 is formed substantially cylindrical.
  • a frusto-conical clamping surface piece 94 is provided and secured with a screw on the shaft portion 92.
  • the clamping surface piece 94 is formed of cemented carbide or ceramic and provides the low-wear jaw abutment surface 94 a, which comes in abutment of the long material 12 in this system.
  • the remaining jaw 20 is preferably made of so-called.
  • Plastic mold steel which is also used for the production of plastic injection molds.
  • the shank portion 92 of the jaw 20 is provided with a compliance. This compliance is achieved by inserting slots in the shaft portion 92.
  • the slots 92a and 92b are all parallel to each other and orthogonal to the longitudinal axis 20c of the jaw 20, which is also the longitudinal axis of the shaft portion 92.
  • the slots 92a pass through the shaft section 92 in the region of the longitudinal axis 20c, d. H. in the region of the transverse center of the shaft portion 92a.
  • the slots 92b are cut in the radial direction toward the longitudinal axis 20c by the jacket of the shaft section 92, but do not reach the longitudinal axis 20c.
  • the slots 92a and 92b alternate at substantially equal intervals, the slots 92b always being provided in pairs opposite each other with respect to the longitudinal axis 20c.
  • the slots or indentations 92b from the outer shell of the shank portion 92 can be simply sawed in, while the passing recesses 92a can be made, for example, by wire eroding.
  • the shaft 92 is first pierced, in which case the wire is inserted into the bore for the subsequent wire EDM.
  • the shank portion 92 of the jaws 20 and 22 has an elasticity which provides sufficient compliance to compensate for differences in thickness of the strip material 12. These differences in thickness are to be compensated in particular when several adjacent clamping devices 16 are located simultaneously in the feed path 34 of the feed device 10 in the clamping position.
  • the clamping jaws 20 and 22 and their shank portion 92 have up to a force of 3000 N on a linear elastic behavior. With a diameter of 12 mm of the shaft portion 92 becomes at 3000 N a spring travel reached from about 0.15 mm. Experiments have shown that until this deformation, the shaft portion 92 can be considered as Hook's spring.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Advancing Webs (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Feeding Of Articles By Means Other Than Belts Or Rollers (AREA)
  • Seal Device For Vehicle (AREA)
  • Vending Machines For Individual Products (AREA)
  • Automobile Manufacture Line, Endless Track Vehicle, Trailer (AREA)
  • Feeding Of Workpieces (AREA)
  • Surgical Instruments (AREA)
  • Transmission Devices (AREA)
  • Gripping Jigs, Holding Jigs, And Positioning Jigs (AREA)
  • Clamps And Clips (AREA)

Abstract

The mechanism to advance longitudinal material through workstations, e.g. wires or profiles to be shaped by bending or stamping, has at least one clamp with two adjustable clamping pads (20,22) to be opened and closed to hold the material or allow it to move through. At least one clamping pad is pliable, as a longitudinal component, with at least one opening (92a,92b) orthogonal to the longitudinal line (20c) of the clamping pad. The second end (20b) of the clamping pad (20) has a truncated cone clamping surface (94), of hard metal or ceramic, fastened by a screw to a shaft section (92).

Description

Die vorliegende Erfindung betrifft eine Vorschubvorrichtung zur Zuführung von Langmaterial, insbesondere von Band-, Draht- oder Profilmaterial, längs einer Vorschubrichtung nach dem Oberbegriff von Anspruch 1.The present invention relates to a feed device for feeding long material, in particular of strip, wire or profile material, along a feed direction according to the preamble of claim 1.

Eine derartige Vorrichtung ist aus der US 3 684 145 A bekannt. Diese umfasst ein Minimalspaltweiten-Veränderungsmittel in Form einer lediglich manuell betätigbaren Gewindestange, um die bekannte Vorschubvorrichtung an Langmaterial unterschiedlicher Materialdicke anzupassen.Such a device is known from US 3 684 145 A. This comprises a minimal gap width changing means in the form of a merely manually operable threaded rod in order to adapt the known feed device to long material of different material thickness.

Aus der Druckschrift GB-A-1 450 136 ist eine Vorrichtung mit umlaufenden Klemmbacken bekannt, bei welcher zwei Klemmbackenumläufe in ein und derselben Umlaufebene gelegen sind. Im Bereich einer Vorschubstrecke, in welcher Abschnitte der beiden Klemmbackenumläufe parallel zueinander verlaufen, werden die Klemmbacken ebenfalls durch Nockenbahnen aufeinander zu verstellt. Die Nockenbahnen sind durch eine Kolben/Zylindereinheit aufeinander zu bzw. voneinander weg bewegbar.From the document GB-A-1 450 136 a device with circumferential jaws is known in which two clamping jaw circulations are located in one and the same orbital plane. In the region of a feed path, in which sections of the two clamping jaw circulations run parallel to one another, the clamping jaws are likewise adjusted towards each other by cam tracks. The cam tracks are movable toward and away from each other by a piston / cylinder unit.

Mit derartigen Vorschubvorrichtungen wird Langmaterial nachfolgenden Bearbeitungsstationen zugeführt, welche das Langmaterial in der Regel spanlos umformen, insbesondere durch Biegen, Stanzen und dergleichen bearbeiten. Als weitere Vorschubvorrichtungen sind auch solche bekannt, bei welchen eine Klemmeinrichtung mit Klemmbacken durch einen Exzenter hin- und hergehend angetrieben ist. Die Klemmeinrichtung der bekannten Vorschubvorrichtung klemmt das Langmaterial, wird dann mit dem geklemmten Langmaterial das gewünschte Vorschubmaß in Vorschubrichtung bewegt, löst dann den Klemmeingriff und wird entgegen der Vorschubrichtung in die Ausgangsstellung zurückbewegt.With such feed devices, long material is fed to subsequent processing stations, which usually reshape the long material without cutting, in particular by bending, punching and the like. As further feed devices, those are also known in which a clamping device with clamping jaws is reciprocally driven by an eccentric. The clamping device of the known feed device clamps the long material, then with the clamped long material, the desired feed dimension in Moves feed direction, then solves the clamping engagement and is moved back against the feed direction to the starting position.

Weiterhin sind Vorschubvorrichtungen in Form sogenannter Rollenvorschübe bekannt. Bei diesen Rollenvorschüben liegen achsparallele drehbare Rollen einander gegenüber, so dass zwischen ihren Umfangsflächen ein Spalt gebildet ist, durch welchen das Langmaterial hindurchgefördert wird. Die Rollen liegen dabei an entgegengesetzten Seiten des Langmaterials an und drehen gegensinnig. Eine oder beide Rollen sind angetrieben, um dem Langmaterial die Vorschubbewegung zu erteilen.Furthermore, feed devices in the form of so-called Rollenvorschübe known. In these roller feeds axially parallel rotatable rollers face each other, so that between their peripheral surfaces, a gap is formed, through which the long material is conveyed through. The rollers lie on opposite sides of the long material and rotate in opposite directions. One or both rollers are driven to impart the feed to the elongate material.

Es ist eine Aufgabe der vorliegenden Erfindung, eine Vorschubvorrichtung der eingangs genannten Art zu verbessern, insbesondere hinsichtlich der Betriebssicherheit.It is an object of the present invention to improve a feed device of the type mentioned, in particular with regard to operational safety.

Diese Aufgabe wird erfindungsgemäß durch eine Vorrichtung mit allen Merkmalen des Anspruchs 1 gelöst.This object is achieved by a device with all features of claim 1.

Zur Klemmung des Langmaterials ist die Vorschubvorrichtung derart ausgebildet, dass die wenigstens eine Klemmeinrichtung wenigstens zwei einen Klemmspalt zwischen sich definierende Klemmbacken aufweist, von welchen wenigstens eine unter Veränderung der Spaltweite längs einer Klemmbewegungsbahn auf die jeweils andere Klemmbacke zu und von dieser weg bewegbar ist. Auf diese Art und Weise können die wenigstens zwei Klemmbacken an jeweils entgegengesetzten Seiten des Langmaterials in Anlage gelangen und so eine möglichst große Klemmkraft auf das Langmaterial übertragen. Die Klemmbacken sind hierzu relativ zu einem Klemmeinrichtungskörper beweglich in diesem gehalten.For clamping the long material, the feed device is designed such that the at least one clamping device has at least two clamping nip defining therebetween jaws, of which at least one of the gap width along a clamping movement path on the other jaw to and from this is movable. In this way, the at least two jaws can come into abutment on respectively opposite sides of the long material and thus transmit as large a clamping force as possible to the long material. The jaws are this held relative to a Klemmeinrichtungskörper movable in this.

Als Bewegungssteuerung der wenigstens einen längs der Klemmbewegungsbahn bewegbaren Klemmbacke ist eine Nockenbahn vorgesehen, welche eine längs der Klemmbewegungsbahn bewegliche Klemmbacke auf die jeweils andere Klemmbacke zu oder/und von dieser weg verlagert.As movement control of the at least one clamping jaw movable along the clamping movement path, a cam track is provided, which displaces a jaw movable along the clamping movement path to and / or away from the respective other jaw.

Mechanische Bewegungssteuerungen haben den weiteren Vorteil, dass sie schnell und weitestgehend ausfallsicher sind. Darüber hinaus kann von der Nockenbahn durch die so erfolgende Zwangssteuerung nicht nur die notwendige Bewegung der Klemmbacke bewirkt werden, sondern gleichzeitig auch die erforderliche Klemmkraft durch die Nockenbahn in die Klemmbacke eingeleitet werden. Dadurch vereinfacht sich der Aufbau der Vorschubvorrichtung ganz wesentlich.Mechanical motion controls have the further advantage that they are fast and largely failsafe. In addition, not only the necessary movement of the jaw can be effected by the cam track by the positive control thus taking place, but at the same time the required clamping force to be introduced by the cam track in the jaw. As a result, the structure of the feed device simplified significantly.

Damit die Minimalspaltweite möglichst mühelos von einer Bedienperson verändert werden kann, umfasst das Minimalspaltweiten-Veränderungsmittel ein Kraftgerät, welches mit wenigstens einer der zwei einander gegenüberliegenden Klemmbacken derart in Kraftübertragungsbeziehung steht, das die wenigstens eine Klemmbacke unter Ausübung von Kraft durch das Kraftgerät auf die jeweils gegenüberliegende Klemmbacke zu und von dieser weg verlagerbar ist. Als Kraftgerät wird eine Hydraulik-Zylinder/Kolbeneinheit, besonders bevorzugt eine doppelt wirkende Hydraulik-Zylinder/Kolbeneinheit, verwendet, da mit dieser eine sehr hohe Kraft bei geringem Bauraumaufwand realisierbar ist.In order for the minimum gap width to be changed as easily as possible by an operator, the minimum gap width changing means comprises a force device in force-transmitting relationship with at least one of the two opposing jaws such that the at least one jaw is forcefully applied by the force device to the opposing jaws Jaw to and away from this is displaced. As a power unit, a hydraulic cylinder / piston unit, particularly preferably a double-acting hydraulic cylinder / piston unit, used because this is a very high power with low space requirements can be realized.

Bei der vorliegenden Erfindung, bei welcher eine Nockenbahn als mechanische Bewegungssteuerung der Klemmbacken eingesetzt ist, ist die Veränderbarkeit der minimalen Spaltweite mit Hilfe des oben bezeichneten Minimalspalfinreiten-Veränderungsmittels konstruktiv in einfacher Weise dadurch gelöst, dass die Nockenbahn verlagerbar ist, mit dem Kraftgerät in Kraftübertragungsbeziehung steht und durch Kraft des Kraftgeräts zur Verlagerung antreibbar ist, wobei eine Verlagerung der Nockenbahn durch das Kraftgerät eine Verlagerung der wenigstens einen mit der Nockenbahn zusammenwirkenden Klemmbacke bewirkt.In the present invention, in which a cam track is used as the mechanical movement control of the jaws, the variability of the minimum gap width by means of the above-described minimum gap width changing means is structurally solved in a simple manner by the cam track being displaceable with the power tool in power transmission relationship and is driven by the force of the power device for displacement, wherein a displacement of the cam track by the power device causes a displacement of the at least one cooperating with the cam track jaw.

In diesem Falle kann durch das Kraftgerät einfach die Nockenbahn relativ zur Klemmeinrichtung als Ganzes verlagert werden, so dass die längs der Klemmbewegungsbahn bewegliche Klemmbacke je nach Verlagerungsstellung der Nockenbahn unterschiedliche Klemmbackenstellungen mit unterschiedlichen Klemmspaltweiten einnimmt.In this case, the cam can be displaced relative to the clamping device as a whole simply by the power device, so that the movable along the clamping movement path jaw occupies different jaw positions with different nip widths depending on the displacement position of the cam.

Aus Sicherheitsgründen ist die Nockenbahn in eine vorbestimmte Verlagerungsrichtung mit der Vorspannkraft eines Vorspannfederelements beaufschlagt. Bei Ausfall des Kraftgeräts kann dann das Vorspannfederelement die Nockenbahn in eine definierte Stellung verlagern. Dies ist bevorzugt eine Stellung, in der eine Klemmung des Langmaterials sichergestellt ist, also eine Stellung möglichst geringer Klemmspaltweite. Durch die von der Hydraulik-Zylinder/Kolbeneinheit aufbringbare Kraft kann diese nicht nur zur Verstellung der Nockenbahn, sondern auch zum Halten der Nockenbahn in ihrer gewählten Stellung verwendet werden.For safety reasons, the cam track is acted upon in a predetermined displacement direction with the biasing force of a biasing spring element. In case of failure of the power device then the biasing spring element can shift the cam track in a defined position. This is preferably a position in which a clamping of the long material is ensured, ie a position of the smallest possible clamping gap width. By virtue of the force that can be applied by the hydraulic cylinder / piston unit, it can be used not only for adjusting the cam track but also for holding the cam track in its selected position.

Es sei an dieser Stelle festgehalten, dass mit "Langmaterial" jedes beliebige Material bezeichnet ist, welches in einer Raumrichtung eine erheblich, etwa wenigstens zwei- bis dreifach, größere Ausdehnung besitzt als in den beiden anderen Raumrichtungen. Vorzugsweise ist mit dem Begriff "Langmaterial" jedoch ein Band-, Draht- oder Profilmaterial bezeichnet, welches vorteilhafterweise von einem Vorrat abgewickelt wird. Dies führt zu vorteilhaften längeren Betriebsdauern zwischen einem Langmaterialwechsel an der Vorschubvorrichtung.It should be noted at this point that with "long material" any material is designated which in a spatial direction has a considerable, about at least two to three times, greater extent than in the other two spatial directions. Preferably, however, the term "long material" means a band, wire or profile material, which is advantageously unwound from a supply. This leads to advantageous longer service life between a long material change on the feed device.

Ein weiterer Vorteil der erfindungsgemäßen Klemmeinrichtung liegt darin, dass eine auf die wenigstens eine Klemmeinrichtung einwirkende dynamische Belastung aus der Richtungsänderung ihrer Bewegungsgeschwindigkeit beim Umlauf verglichen mit einer richtungsumkehrenden Klemmeinrichtung bei gleicher Vorschubgeschwindigkeit in ihrem Absolutwert durch Wahl entsprechend großer Umlenkradien reduziert werden kann. Wie allgemein bekannt ist, ist die eine Richtungsänderung einer Geschwindigkeit beim Umlauf längs einer geschlossenen Bahn bewirkende Zentripetalbeschleunigung proportional zum Quadrat der Bahngeschwindigkeit und indirekt proportional zum Krümmungsradius der Bahn. So kann beispielsweise die Vorschubstrecke bei einer Ausführungsform der vorliegenden Erfindung durch ein Geradenstück gebildet sein und der Rest der geschlossenen Umlaufbahn schließt gekrümmt an die gerade Vorschubstrecke an. Je nach zur Verfügung stehendem Bauraum kann unter Inkaufnahme einer größeren Bahnlänge ein größerer Krümmungsradius der Bahn gewählt werden.A further advantage of the clamping device according to the invention is that a dynamic load acting on the at least one clamping device can be reduced in its absolute value by selecting correspondingly large deflection radii from the change in direction of its moving speed when circulating compared with a direction-reversing clamping device at the same feed rate. As is well known, the centripetal acceleration resulting in a change in direction of velocity along a closed path is proportional to the square of the orbital velocity and is inversely proportional to the radius of curvature of the orbit. For example, in one embodiment of the present invention, the feed path may be formed by a straight line piece and the remainder of the closed loop path is curvedly connected to the straight feed path. Depending on the available installation space, a greater radius of curvature of the web can be selected by accepting a larger track length.

Die Gesamtlänge der geschlossenen Umlaufbahn lässt sich bei vorgegebener Länge der Vorschubstrecke in vorteilhafter Weiterbildung der Erfindung kurz halten, wenn parallel zu einer im Wesentlichen geradlinigen Vorschubstrecke eine ebenfalls im Wesentlichen geradlinige Rücklaufstrecke vorgesehen ist, wobei Vorschubstrecke und Rücklaufstrecke durch gekrümmte Bahnabschnitte miteinander verbunden sind. Der durchschnittliche Krümmungsradius dieser gekrümmten Bahnabschnitte entspricht dabei dem halben Abstand von Vorschub- und Rücklaufstrecke. Damit die wenigstens eine Klemmeinrichtung den gekrümmten Bahnabschnitt störungsfrei und ohne übermäßige auf sie einwirkende dynamische Kräfte durchlaufen kann, ist es vorteilhaft, wenn der Durchmesser eines gekrümmten Bahnsegments in der Größenordnung der Abmessung der wenigstens einen Klemmeinrichtung in Umlaufrichtung liegt, vorzugsweise wenn der Durchmesser gleich dieser Abmessung oder größer als diese ist.The total length of the closed orbit can be kept short for a given length of the feed path in an advantageous development of the invention, if a likewise substantially rectilinear return path is provided parallel to a substantially rectilinear feed section, wherein feed path and return path are connected by curved track sections. The average radius of curvature of this curved track sections corresponds to half the distance between the feed and return path. In order for the at least one clamping device to pass through the curved track section without interference and without excessive dynamic forces acting on it, it is advantageous if the diameter of a curved web segment is of the order of magnitude of the at least one clamping device in the direction of rotation, preferably if the diameter is equal to this dimension or greater than this.

Wenn die Vorschubvorrichtung eine Mehrzahl von in Umlaufrichtung aufeinander folgenden Klemmeinrichtungen aufweist, kann die von der Vorschubeinrichtung erreichbare maximale Vorschubgeschwindigkeit erhöht werden, da zwischen zwei Vorschubvorgängen kein vollständiger Umlauf einer Klemmeinrichtung abgewartet werden muss. Vielmehr können weitere Klemmeinrichtungen gemäß einer bevorzugten Weiterbildung der Erfindung so vorgesehen sein, dass dann, wenn eine in Klemmeingriff mit dem Langmaterial befindliche Klemmeinrichtung durch Verstellung in die Lösestellung außer Eingriff gelangt, eine noch nicht in Klemmeingriff befindliche weitere Klemmeinrichtung durch Verstellung in die Klemmstellung in Klemmeingriff mit dem Langmaterial kommt. Fachleute werden dabei verstehen, dass derartige Eingriffswechsel nicht unbedingt zum exakt selben Zeitpunkt erfolgen müssen, wenngleich dies besonders bevorzugt ist, da dann sichergestellt ist, dass sich stets eine Klemmeinrichtung in Klemmeingriff mit dem Langmaterial befindet. Ein solcher Eingriffswechsel kann auch in einem vorbestimmten das Eingriffsende enthaltenden Zeitfenster erfolgen, beispielsweise von bis zu 10 % der eingestellten Taktzeit, mit welcher die Vorschubvorrichtung betrieben wird.If the feed device has a plurality of clamping devices which follow each other in the direction of rotation, the maximum feed speed achievable by the feed device can be increased, since no complete circulation of a clamping device has to be awaited between two feed operations. Rather, more clamping devices according to a preferred embodiment of the invention may be provided so that when a clamped engagement with the long material clamping device is disengaged by adjustment in the release position, a not yet in clamping engagement further clamping device by adjusting in the clamping position in clamping engagement comes with the long material. It will be understood by those skilled in the art that such engagement changes need not necessarily occur at the exact same time, although this is particularly preferred because it is then ensured that a clamping device is always in clamping engagement with the elongate material. Such an intervention change can also take place in a predetermined time window containing the intervention end, for example of up to 10% of the set cycle time with which the feed device is operated.

Die insgesamt von der Vorschubvorrichtung auf das Langmaterial zu dessen Transport übertragbare Kraft kann in vorteilhafter Weise dadurch erhöht werden, dass die Vorschubvorrichtung eine Mehrzahl von Klemmeinrichtungen umfasst und sich eine Mehrzahl von Klemmeinrichtungen während ihrer Bewegung in Vorschubrichtung gleichzeitig in Klemmstellung befindet. Die von jeder einzelnen der sich gleichzeitig in Klemmstellung befindenden Klemmeinrichtungen auf das Langmaterial übertragbaren Klemmkräfte addieren sich zu einer Gesamtkraft, so dass das Langmaterial stark beschleunigt und auch wieder stark abgebremst werden kann, ohne dass nach dem Abbremsen eine Lageungenauigkeit des Bandmaterials zu befürchten ist. Durch den zwischen Klemmbacke und Langmaterial möglichen flächenhaften Berührkontakt kann überdies die lokale Druckbelastung des Langmaterials im Bereich des Klemmungseingriffs, verglichen mit den bekannten Rollenvorschubvorrichtungen, erheblich reduziert werden. Dies bedeutet, dass trotz der Übertragung insgesamt hoher Klemmkräfte lokal nur vergleichsweise moderate Drücke auf das Langmaterial einwirken.The total transferable from the feed device to the long material for its transport force can be increased advantageously in that the feed device comprises a plurality of clamping devices and a plurality of clamping devices during their movement in the feed direction is simultaneously in the clamping position. The transferable from each of the clamping device simultaneously located in clamping position on the long material transferable clamping forces add up to a total force, so that the long material can be greatly accelerated and slowed down again without a position inaccuracy of the strip material is to be feared after deceleration. In addition, the areal pressure contact between the long material in the region of the clamping engagement, as compared to the known ones, can be achieved by the planar contacting contact which is possible between the clamping jaw and the long material Roller feeders are significantly reduced. This means that, despite the transfer of high clamping forces in general, only comparatively moderate pressures act on the long material locally.

Grundsätzlich kann daran gedacht sein, dass mehrere Klemmeinrichtungen unmittelbar gelenkig miteinander zu einer geschlossenen Klemmeinrichtungskette verbunden sind. Hierzu kann jede Klemmeinrichtung eine Gelenkeinrichtung aufweisen, welche mit einer korrespondierenden Gelenkgegeneinrichtung einer in Umlaufrichtung nachfolgenden Klemmeinrichtung gekoppelt oder koppelbar ist. Es reicht dann aus, wenn die Achsen von die Klemmeinrichtungen miteinander verbindenden Gelenken im Wesentlichen parallel sind, so dass die miteinander gekoppelten Klemmeinrichtungen relativ zueinander zur Bildung einer geschlossenen Kette verdrehbar sind.In principle, it can be thought that several clamping devices are connected directly hinged together to form a closed clamping device chain. For this purpose, each clamping device can have a joint device which can be coupled or coupled to a corresponding joint counter-device of a subsequent clamping device in the direction of rotation. It is sufficient if the axes of the clamps interconnecting joints are substantially parallel, so that the mutually coupled clamping devices are rotatable relative to each other to form a closed chain.

Für eine gute Kraftübertragung von einem Antrieb der Vorschubvorrichtung auf die wenigstens eine Klemmeinrichtung und insbesondere für eine erleichterte Umlenkung der wenigstens einen Klemmeinrichtung in gekrümmten Abschnitten der geschlossenen Umlaufbahn ist es vorteilhaft, wenn die wenigstens eine Klemmeinrichtung zur gemeinsamen Bewegung mit einem formveränderlichen endlosen Bewegungsübertragungsteil verbunden ist.For a good power transmission from a drive of the feed device to the at least one clamping device and in particular for easier deflection of the at least one clamping device in curved sections of the closed orbit, it is advantageous if the at least one clamping device is connected for common movement with a shape-variable endless motion transmission part.

Das formveränderliche endlose Bewegungsübertragungsteil kann beispielsweise eine Kette, insbesondere Lamellenkette, sein, welche eine Übertragung von sehr hohen Kräften in Umlaufrichtung gestattet. Aus Gründen einer möglichst guten Umlenkbarkeit ist als Bewegungsübertragungsteil jedoch ein flexibler Zahnriemen bevorzugt. Verwendet man einen Kunststoff-Zahnriemen, so sorgt die Nachgiebigkeit des Kunststoffs für eine Dämpfung eines möglicherweise auftretenden Anfahr- oder/und Abbremsstoßes. Die vorteilhafte Verwendung eines Zahnriemens mit Metallseele, insbesondere Stahlseele, stellt dabei sicher, dass trotz der vorübergehenden Dämpfung durch elastische Verformung des Zahnriemens in der erreichten Endstellung (Ruhestellung) die gewünschte Position mit hoher Genauigkeit erreicht wird.The shape-variable endless motion transmission part can be, for example, a chain, in particular a lamella chain, which allows transmission of very high forces in the direction of rotation. For reasons of the best possible deflectability, however, a flexible toothed belt is preferred as a motion transmission part. If a plastic toothed belt is used, the resilience of the plastic provides for a damping of a possibly occurring starting and / or stopping shock. The advantageous use of a toothed belt with metal core, in particular steel core, thereby ensures that despite the temporary damping by elastic deformation of the toothed belt in the reached end position (rest position), the desired position is achieved with high accuracy.

Weiterhin ist ein Zahnriemen mit doppelseitiger Zahnausbildung bevorzugt, da dann sowohl eine Antriebskraft-Übertragungsvorrichtung auf einer ersten Seite des Zahnriemens formschlüssig mit diesem in Eingriff sein kann, als auch die wenigstens eine Klemmeinrichtung auf der der ersten entgegengesetzten zweiten Seite des Zahnriemens in Umfangsrichtung formschlüssig mit diesem in Eingriff gebracht sein kann, so dass weder die Antriebskraft-Übertragungsvorrichtung noch die wenigstens eine Klemmeinrichtung Schlupf in Umlaufrichtung aufweist, was eine sehr hohe Positioniergenauigkeit auch bei hohen Vorschubgeschwindigkeiten und kurzen Taktzeiten ermöglicht.Furthermore, a toothed belt with double-sided tooth formation is preferred, since then both a drive force transmission device on a first side of the toothed belt can be positively engaged with this, as well as the at least one clamping device on the first opposite second side of the toothed belt in the circumferential direction positively with this can be brought into engagement, so that neither the drive force transmission device nor the at least one clamping device has slip in the direction of rotation, which allows a very high positioning accuracy even at high feed rates and short cycle times.

Wie oben angedeutet wurde, kann die Nockenbahn derart ausgebildet sein, dass sie die Klemmbacke in nur eine Richtung bewegt oder auch in beide Richtungen, d. h. auf das Langmaterial zu und von diesem weg bewegt. Für die Erfüllung der Vorschubaufgabe ist das sichere Klemmen des Langmaterials in der Klemmeinrichtung von größerer Bedeutung als ein Abheben der Klemmbacke vom Langmaterial. Letzteres muss im Übrigen nicht zwangsweise erfolgen, etwa dann, wenn es auf die Oberflächengüte des Langmaterials nicht ankommt. In diesem Falle muss die Klemmbacke nicht vom Langmaterial abgehoben werden, sondern es reicht aus, die Klemmkraft so weit zu verringern, dass das Bandmaterial außer Eingriff mit der wenigstens einen Klemmeinrichtung gelangen kann.As indicated above, the cam track may be configured to move the jaw in one direction only or in both directions, i. H. moved towards and away from the long material. For the fulfillment of the feed task, the secure clamping of the long material in the clamping device is of greater importance than lifting the jaw from the long material. Incidentally, the latter does not necessarily have to be done, for example if the surface quality of the long material is not important. In this case, the jaw must not be lifted from the long material, but it is sufficient to reduce the clamping force so far that the strip material can get out of engagement with the at least one clamping device.

Aufgrund der vorrangigen Bedeutung eines sicheren Aufbringens der Klemmkraft ist die Vorschubvorrichtung vorzugsweise derart ausgebildet, dass die wenigstens eine längs der Klemmbewegungsbahn bewegbare Klemmbacke durch ein Federmittel in eine Abhebestellung größerer Spaltweite vorgespannt ist und mit der Nockenbahn zur Bewegung in eine Anlagestellung geringerer Spaltweite zusammenwirkt.Due to the primary importance of a safe application of the clamping force, the feed device is preferably designed such that the at least one along the Klemmbewegungsbahn movable jaw is biased by a spring means in a Abhebestellung greater gap width and cooperates with the cam track for movement in an abutment position lesser gap width.

Eine besonders hohe Klemmkraft bei gleichzeitig kompakter Bauweise der wenigstens einen Klemmeinrichtung kann gemäß einer vorteilhaften Ausführungsform der vorliegenden Erfindung dann erhalten werden, wenn die Nockenbahn, welche die eine Klemmbacke während ihres Durchlaufs auf die ihr gegenüberliegende andere Klemmbacke zu verstellt, bei Betrachtung eines Durchlaufs durch die Vorschubstrecke orthogonal zu einer Klemmbackenanlagefläche der anderen Klemmbacke mit Abstand angeordnet ist. Die Klemmbackenanlagefläche ist dabei jene Fläche der Klemmbacke, welche beim Klemmen des Langmaterials an einer Seite desselben zur Anlage kommt.A particularly high clamping force and at the same time compact construction of the at least one clamping device can be obtained according to an advantageous embodiment of the present invention, when the cam track, which adjusts the one jaw during its passage to the opposite other clamping jaw, in consideration of a passage through the Feed path orthogonal to a jaw contact surface of the other jaw is arranged at a distance. The jaw abutment surface is that surface of the jaw which comes to rest on one side thereof when clamping the long material.

Bei der genannten Anordnung der Nockenbahn ist es möglich, sehr kurze, im Wesentlichen geradlinige Klemmbacken zu verwenden, welche in Abstandsrichtung von der Nockenbahn zur jeweils gegenüberliegenden Klemmbacke und damit auch zum Langmaterial hin verlaufen. Dadurch weist die von der einen Klemmbacke auf das Langmaterial ausgeübte Kraft im Wesentlichen keine Kraftkomponente auf, welche in der Ebene der Klemmbackenanlagefläche der von der Nockenbahn bewegten Klemmbacke liegt. Die Ausbeute an nutzbarer Klemmkraft im Verhältnis zur insgesamt auf die Klemmbacke ausgeübten Kraft ist damit sehr groß.In the case of the abovementioned arrangement of the cam track, it is possible to use very short, essentially rectilinear clamping jaws which extend in the direction of spacing from the cam track to the respectively opposite clamping jaw and thus also to the long material. As a result, the force exerted by the one clamping jaw on the long material has essentially no force component which lies in the plane of the clamping jaw contact surface of the jaw moved by the cam track. The yield of usable clamping force in relation to the total force exerted on the jaw force is thus very large.

Konstruktiv kann zur Verwirklichung einer so erreichbaren sehr hohen Klemmkraft die wenigstens eine längs der Klemmbewegungsbahn bewegbare Klemmbacke als längliche Gestalt ausgebildet sein, an deren einem Längsende eine Klemmbackenanlagefläche zur Anlage an das Langmaterial vorgesehen ist und an deren anderem Längsende ein Wälzkörper zur Wälzanlage an der Nockenbahn vorgesehen ist.Constructively, to realize a so achievable very high clamping force, the at least one along the Klemmbewegungsbahn movable jaw may be formed as an elongated shape at one longitudinal end of a jaw contact surface is provided for contact with the elongate material and provided at the other longitudinal end a rolling element for rolling on the cam track is.

Vorzugsweise ist daran gedacht, ein in zwei entgegengesetzte Richtungen wirkendes Kraftgerät zu verwenden, so dass die Nockenbahn durch die Kraft des Kraftgeräts sicher und gezielt sowohl in eine die Minimalspaltweite vergrößernde Richtung als auch in eine selbige verkleinernde Richtung verstellbar ist.Preferably, it is intended to use a force acting in two opposite directions force device, so that the cam track by the force of the power device safely and selectively adjustable in both the minimum gap width increasing direction and in a selbige decreasing direction.

Ein großer Freiheitsgrad bei der Anordnung des Kraftgeräts sowie eine Anpassung einer Bewegung eines Kraftausgabeelements des Kraftgeräts an die gewünschte Verlagerungsbewegung der Nockenbahn kann dadurch erreicht werden, dass das Kraftgerät durch ein Getriebe mit der Nockenbahn verbunden ist.A large degree of freedom in the arrangement of the power device as well as an adjustment of a movement of a force output element of the power device to the desired displacement movement of the cam can be achieved, that the power device is connected by a gear with the cam track.

Hier hat sich als besonders vorteilhaft erwiesen, wenn das Getriebe einen vom Kraftgerät drehbaren Exzenter umfasst, mit welchem die Nockenbahn verbunden ist. Mit einem derartigen Exzenter lässt sich sehr einfach eine lineare Bewegung des Kraftausgabeelements, etwa des Kolbens eines Hydraulikzylinders, in eine zu dieser abgewinkelte, insbesondere orthogonale lineare Verlagerungsbewegung der Nockenbahn umsetzen. Bei geeigneter Wahl von Exzenterabmessungen, wie etwa des Exzenterdurchmessers und der Exzentrizität, können darüber hinaus auch eine Über- oder Untersetzung von Bewegung und Kraft (reziprok zur Bewegungsübertragung) erreicht werden.Here it has proved to be particularly advantageous if the transmission comprises a rotatable eccentric from the power unit, with which the cam track is connected. With such an eccentric can be very simple to implement a linear movement of the force output element, such as the piston of a hydraulic cylinder in an angled to this, in particular orthogonal linear displacement movement of the cam track. With a suitable choice of eccentric dimensions, such as the eccentric diameter and the eccentricity, in addition, a translation or reduction of movement and force (reciprocal to the motion transmission) can be achieved.

Durch das Getriebe wird weiter ermöglicht, dass das Kraftgerät bauraumsparend in einem von der wenigstens einen umlaufenden Klemmeinrichtung umgebenen Bereich angeordnet werden kann. Somit kann der innerhalb der Umlaufbahn der Klemmeinrichtung liegende Bereich, welcher ohnehin zum Bauraum der Vorschubvorrichtung gehört, sinnvoll genutzt werden, um eine kompakte Vorschubvorrichtung mit geringem Bauraumbedarf zu erhalten. Es sei darauf hingewiesen, dass vorzugsweise die wenigstens eine Klemmeinrichtung bei Vorschub eines flachen Bandmaterials in der Bandmaterialebene oder in einer zur Bandmaterialebene parallelen Umlaufebene umläuft. Mit Bandmaterialebene ist dabei die Haupterstreckungsebene des Bandmaterials in der Vorschubstrecke bezeichnet. Es hat sich erwiesen, dass mit dieser Umlaufrichtung ein sehr geringer Bauraumbedarf verwirklicht werden kann.Through the transmission is further made possible that the power device can be arranged space-saving in a surrounded by the at least one circumferential clamping device area. Thus, the lying within the orbit of the clamping device area, which anyway belongs to the space of the feed device, can be used meaningfully to obtain a compact feed device with low space requirements. It should be noted that preferably the at least one clamping device rotates when a flat strip material is fed in the strip material plane or in a plane parallel to the strip material plane. With strip material level is the main extension plane referred to the strip material in the feed path. It has been found that with this circulation direction a very small space requirement can be realized.

Für einen schonenden Kraftangriff der Klemmbacke an dem Langmaterial ist es weiterhin vorteilhaft, wenn wenigstens eine von zwei einen Klemmspalt zwischen sich definierenden Klemmbacken der wenigstens einen Klemmeinrichtung in einer den Klemmspalt vergrößernden Richtung nachgiebig ausgebildet ist. Bevorzugt sind beide Klemmbacken in einer den Klemmspalt vergrößernden Richtung nachgiebig ausgebildet. Somit kann die Klemmbacke zumindest mit einem geringen Federweg federn, so dass die Klemmkraft nicht schlagartig in voller Höhe auf das Langmaterial ausgeübt wird, sondern sich über einen gewissen Zeitbereich aufbauen kann.For a gentle force application of the clamping jaw on the long material, it is furthermore advantageous if at least one of two clamping nips defining therebetween clamping jaws of the at least one clamping device is resilient in a direction enlarging the nip gap. Preferably, both clamping jaws are designed to be yielding in a direction enlarging the clamping gap. Thus, the jaw can spring at least with a small spring travel, so that the clamping force is not abruptly exerted in full on the long material, but can build up over a certain period of time.

Die nachgiebige Ausbildung von wenigstens einer Klemmbacke ist besonders in dem oben bezeichneten Fall vorteilhaft, dass mehrere Klemmeinrichtungen gleichzeitig sich in der Klemmstellung befinden und einen Langmaterialabschnitt geklemmt halten. Dann kann nämlich durch die Nachgiebigkeit der Klemmbacken eine möglicherweise vorhandene Dickenschwankung des Langmaterials über seine Länge ausgeglichen werden. Dies ist gerade bei der Verwendung von mechanischen Bewegungssteuerungen für die Klemmbacken von großem Vorteil.The flexible design of at least one jaw is particularly advantageous in the case described above in that a plurality of clamping devices are simultaneously in the clamping position and keep a long material section clamped. Then can be compensated for by the flexibility of the jaws a possibly existing thickness variation of the long material over its length. This is particularly advantageous when using mechanical motion controls for the jaws.

Grundsätzlich kann daran gedacht sein, die Klemmbacke als Kipphebel auszugestalten, so dass die Nachgiebigkeit durch entsprechende Bemessung des Hebeldurchmessers über eine bestimmte Hebellänge erreicht werden kann. Die Nachgiebigkeit wird dann einfach durch Biegung der hebelartigen Klemmbacke erreicht.In principle, it can be thought of to design the jaw as a rocker arm, so that the compliance can be achieved by appropriate dimensioning of the lever diameter over a certain lever length. The compliance is then achieved simply by bending the lever-like jaw.

Im oben bezeichneten bevorzugten Fall, bei welchem die Klemmbacke ein im Wesentlichen längliches Teil ist, welches stempelartig durch eine Translationsbewegung zur Anlage an das Langmaterial gelangt, ist in Ermangelung einer möglichen Biegenachgiebigkeit eine andere Realisierung der Nachgiebigkeit erforderlich.In the above-mentioned preferred case in which the jaw is a substantially elongated member, which comes through a stamping movement by a translational movement to the plant to the long material, in the absence of a possible Bingenachgiebigkeit another implementation of Compliance required.

Hierzu ist gemäß einer möglichen Ausführungsform denkbar, dass die wenigstens eine nachgiebige Klemmbacke wenigstens zweiteilig ausgebildet ist, wobei zwei Klemmbackenteile durch Zwischenanordnung einer Federvorrichtung zumindest in der Klemmspaltvergrößerungsrichtung relativ zueinander bewegbar angeordnet sind.For this purpose, according to a possible embodiment, it is conceivable that the at least one resilient jaw is formed at least in two parts, wherein two jaw parts are arranged relative to each other by interposition of a spring device at least in the Klemmspaltvergrößerungsrichtung.

Vorteilhafter ist es jedoch, wenn die wenigstens eine nachgiebige Klemmbacke ein längliches Bauteil ist, welches zumindest abschnittsweise mit wenigstens einer Ausnehmung, vorzugsweise einer durchsetzenden Ausnehmung, versehen ist, deren Verlaufsrichtung eine Komponente orthogonal zur Längsrichtung der Klemmbacke aufweist. Bei der letztgenannten Lösung lassen sich nämlich Klemmbacken ausreichender Nachgiebigkeit mit sehr geringen Abmessungen realisieren, so dass die insgesamt in Umlaufrichtung bewegten Massen klein gehalten werden können.It is more advantageous, however, if the at least one flexible clamping jaw is an elongate component which is provided at least in sections with at least one recess, preferably an intersecting recess, whose course direction has a component orthogonal to the longitudinal direction of the clamping jaw. In the latter solution, namely, clamping jaws of sufficient flexibility can be realized with very small dimensions, so that the total masses moved in the direction of rotation can be kept small.

Eine besonders vorteilhafte Wirkung erzielt man, wenn wenigstens eine Ausnehmung, vorzugsweise mehrere Ausnehmungen, die Klemmbacke durchsetzen. Derartige Ausnehmungen lassen sich durch Bohren oder durch Drahterodieren ohne weiteres herstellen. Besonders bevorzugt durchsetzt die wenigstens eine Ausnehmung die Klemmbacke im Bereich ihrer Quermitte, so dass in einem zentralen Bereich der Klemmbacke Federweg zur Verfügung steht. Weiterhin können in Längsrichtung der Klemmbacke aufeinander folgend mehrere durchsetzende Ausnehmungen aufeinander folgend vorgesehen sein, welche zur Erhöhung der Federwirkung winkelmä-βig um eine Längsachse der Klemmbacke zueinander versetzt sein können.A particularly advantageous effect is achieved if at least one recess, preferably a plurality of recesses, pass through the clamping jaw. Such recesses can be easily prepared by drilling or by wire EDM. Particularly preferably, the at least one recess passes through the clamping jaw in the region of its transverse center, so that spring travel is available in a central region of the clamping jaw. Furthermore, successive recesses may be provided consecutively in the longitudinal direction of the clamping jaw in succession, which may be angularly offset relative to one another about a longitudinal axis of the clamping jaw in order to increase the spring action.

Bevorzugt ist nicht nur eine der zwei einander gegenüberliegenden Klemmbacken, sondern sind beide einen Klemmspalt zwischen sich definierende Klemmbacken einer Klemmeinrichtung unter Veränderung der Spaltweite aufeinander zu und voneinander weg bewegbar. Hierdurch ist es möglich, dass beide Klemmbacken einer Klemmeinrichtung in der Lösestellung der Klemmeinrichtung vom Langmaterial abgehoben sind, so dass die Oberfläche des Langmaterials durch das Klemmen für den Vorschub desselben möglichst wenig beansprucht wird.Not only is one of the two opposing jaws preferred, but both are a clamping gap between them defining jaws of a clamping device with changing the gap width towards each other and away from each other movable. This makes it possible that both clamping jaws of a clamping device in the release position of the clamping device are lifted from the long material, so that the surface of the long material by the terminals for the feed of the same is claimed as little as possible.

In diesem Zusammenhang sei auf einen weiteren Vorteil der vorliegenden Erfindung hingewiesen: Dieser liegt darin, dass die Klemmeinrichtung zur Aufnahme der zwei einen Klemmspalt zwischen sich definierenden Klemmbacken unabhängig von ihrer individuellen Bewegbarkeit ein einstückiges Gehäuse aufweisen kann, so dass die Ausrichtung der beiden Klemmbacken zueinander auch über lange Betriebszeiten gewahrt bleibt. Selbst wenn das Gehäuse nicht einstückig ausgebildet ist, kann durch Anbringung der Klemmeinrichtung an eine oben bezeichnete formveränderliche endlose Bewegungsübertragungseinrichtung, insbesondere an den doppelseitig verzahnten Zahnriemen, eine ähnliche Lagegenauigkeit der Klemmbacken zueinander über eine lange Betriebsdauer erhalten werden wie beim einstückigen Gehäuse.In this context, reference is made to a further advantage of the present invention: This is that the clamping device for receiving the two clamping gap between them defining jaws may have a one-piece housing regardless of their individual mobility, so that the alignment of the two jaws to each other also maintained over long periods of operation. Even if the housing is not integrally formed, a similar positional accuracy of the jaws to each other can be obtained over a long period of operation by attaching the clamping device to a variable-shaped endless motion transmission device, especially on the double-sided toothed timing belt, as in the one-piece housing.

In dem Falle, dass beide von zwei einen Klemmspalt zwischen sich definierenden Klemmbacken aufeinander zu und voneinander weg bewegbar sind, kann auch die zweite Klemmbacke in der oben ausführlich geschilderten Art und Weise zur Bewegung auf die jeweils andere Klemmbacke zu angetrieben werden. Insbesondere kann hierzu eine Nockenbahn verwendet werden, welche in der gleichen vorteilhaften Art und Weise weitergebildet sein kann, wie die oben beschriebene Nockenbahn der erstgenannten Klemmbacke.In the event that both of a clamping gap between them defining jaws toward each other and away from each other are movable, and the second jaw in the above detailed manner for movement to the other jaw to be driven. In particular, for this purpose, a cam track can be used, which can be developed in the same advantageous manner as the above-described cam track of the former jaw.

Besonders günstig für die Einleitung von Kraft auf die Nockenbahn, insbesondere zur Veränderung der Minimalspaltweite, sowie zur Einleitung von Kraft durch die Klemmbacken auf das Langmaterial sind die Nockenbahnen und die wenigstens eine Klemmeinrichtung, vorzugsweise auch das Minimalspaltweiten-Veränderungsmittel, bezüglich einer zwischen den Klemmbacken den Klemmspalt in der Spaltmitte durchsetzenden Symmetrieebene symmetrisch angeordnet.Particularly favorable for the introduction of force on the cam track, in particular for changing the minimum gap width, and for the introduction of force through the jaws on the long material are the cam tracks and the at least one clamping device, preferably also the minimum gap width changing means, symmetrically arranged with respect to a symmetry plane passing through the clamping gap in the gap center between the clamping jaws.

Die vorliegende Erfindung wird im Folgenden anhand der beiliegenden Figuren näher erläutert. Es stellt dar:

Fig. 1
eine Seitenansicht einer erfindungsgemäßen Vorschubvorrichtung,
Fig. 2
eine Draufsicht der Vorschubvorrichtung von Fig. 1,
Fig. 3
eine Schnittansicht der erfindungsgemäßen Vorschubvorrichtung der Fig. 1 und 2 bei Betrachtung der Schnittebene III-III von Fig. 1,
Fig. 4
eine Schnittansicht bei Betrachtung der Schnittebene IV-IV von Fig. 1,
Fig. 5
eine Schnittansicht der Vorschubvorrichtung der Fig. 1 und 2 bei Betrachtung der Schnittebene V-V von Fig. 1,
Fig. 6a
eine Seitenansicht einer Klemmbacke der erfindungsgemäßen Vorschubvorrichtung aus den Fig. 1 - 5 und
Fig. 6b
eine Rückansicht der Klemmbacke von Fig. 6a.
The present invention will be explained in more detail below with reference to the accompanying figures. It shows:
Fig. 1
a side view of a feed device according to the invention,
Fig. 2
a top view of the feed device of Fig. 1,
Fig. 3
1 is a sectional view of the feed device according to the invention of FIGS. 1 and 2 when viewing the sectional plane III-III of FIG. 1,
Fig. 4
a sectional view when looking at the section plane IV-IV of Fig. 1,
Fig. 5
1 is a sectional view of the feed device of FIGS. 1 and 2 when viewing the sectional plane VV of FIG. 1,
Fig. 6a
a side view of a jaw of the feed device according to the invention from FIGS. 1-5 and
Fig. 6b
a rear view of the jaw of Fig. 6a.

In Fig. 1 ist eine erfindungsgemäße Vorschubvorrichtung allgemein mit 10 bezeichnet. Diese dient dazu, ein längliches Bandmaterial 12 getaktet längs der Vorschubrichtung V zu transportieren. Hierzu wird die Vorschubvorrichtung 10 von einem numerisch gesteuerten Elektromotor 13 über ein bewegungsuntersetzendes Zwischengetriebe 14 angetrieben. Durch Bewegungsrichtungsumkehr des Motors 13 kann die Vorschubvorrichtung 10 auch in die entgegengesetzte Richtung transportieren.In Fig. 1, a feed device according to the invention is generally designated 10. This serves to transport an elongated strip material 12 clocked along the feed direction V. For this purpose, the feed device 10 is driven by a numerically controlled electric motor 13 via a motion-reducing intermediate gear 14. By reversing the direction of movement of the motor 13, the feed device 10 can also transport in the opposite direction.

Die Vorschubvorrichtung 10 weist eine Mehrzahl von Klemmeinrichtungen 16 auf, welche vom Elektromotor 13 angetrieben längs einer geschlossenen Bahn B umlaufen (siehe Fig. 2).The advancing device 10 has a plurality of clamping devices 16 which, driven by the electric motor 13, rotate along a closed path B (see FIG. 2).

Jede Klemmeinrichung 16 hat einen Klemmeinrichtungskörper 18, in welchem zwei einander gegenüberliegende Klemmbacken 20 und 22 unter Veränderung der Weite eines zwischen ihnen gebildeten Klemmspalts aufeinander zu und voneinander weg bewegbar sind. Der Klemmeinrichtungskörper 18 ist vorzugsweise aus HC-beschichtetem Aluminium hergestellt, um eine geringe bewegte Masse bei ausreichender Robustheit zu erhalten. Die Klemmbacken 20 und 22, welche in dem in den Figuren 1 - 5 gezeigten Ausführungsbeispiel der erfindungsgemäßen Vorschubvorrichtung im Wesentlichen identisch ausgebildet sind, werden im Zusammenhang mit Fig. 6a und 6b ausführlich beschrieben werden.Each clamp 16 has a clamp body 18 in which two opposed jaws 20 and 22 are movable toward and away from each other by varying the width of a nip formed therebetween. The clamper body 18 is preferably made of HC-coated aluminum to obtain a small moving mass with sufficient robustness. The clamping jaws 20 and 22, which are formed substantially identically in the embodiment of the feed device according to the invention shown in FIGS. 1-5, will be described in detail in connection with FIGS. 6a and 6b.

Die Klemmeinrichtungen 16 sind bezüglich einer zur Zeichenebene von Fig. 1 orthogonalen Mittelebene S des Langmaterials 12 spiegelsymmetrisch ausgebildet, so dass nur die obere Hälfte der Klemmeinrichtung 16 näher erläutert wird. Für die Beschreibung der unteren Hälfte wird auf die Beschreibung der oberen Hälfte verwiesen.The clamping devices 16 are mirror-symmetrical with respect to a plane perpendicular to the plane of Fig. 1 center plane S of the long material 12, so that only the upper half of the clamping device 16 is explained in more detail. For the description of the lower half, please refer to the description of the upper half.

Die Klemmbacke 20 ist in dem Klemmeinrichtungsgehäuse 18 in Richtung des Doppelpfeils K zum Bandmaterial 12 hin und von diesem weg längs der Geraden KB verlagerbar angeordnet. Dabei bezeichnet die Pfeilspitze K1 eine Richtung auf das Langmaterial 12 zu und die Pfeilspitze K2 eine Richtung vom Langmaterial 12 weg. Der Doppelpfeil K verläuft parallel zur Zeichenebene der Fig. 1 und orthogonal zur Vorschubrichtung V. Die Gerade KB beschreibt somit die lineare Klemmbewegungsbahn, längs welcher eine Klemmbacke bewegbar ist.The jaw 20 is arranged in the clamping device housing 18 in the direction of the double arrow K to the strip material 12 and away from this along the straight line KB displaced. In this case, the arrowhead K1 denotes a direction towards the long material 12 and the arrowhead K2 points away from the long material 12. The double arrow K runs parallel to the drawing plane of FIG. 1 and orthogonal to the feed direction V. The straight line KB thus describes the linear clamping movement path along which a clamping jaw is movable.

Zwei Schraubenfedern 24 und 26 spannen die Klemmbacke 20 in der Richtung K2 vom Langmaterial 12 weg und bringen so eine Wälzrolle 28 in Anlage an eine Nockenfläche 30 einer Nockenbahn 32.Two coil springs 24 and 26 clamp the jaw 20 in the direction K2 away from the long material 12 and thus bring a Wälzrolle 28 in Appendix to a cam surface 30 of a cam track 32nd

Während ihrer Bewegung längs der geschlossenen Bahn B wälzt so die Wälzrolle 28 unter der Andruckkraft der Schraubenfedern 24 und 26 dauerhaft auf der Nockenfläche 30 der Nockenbahn 32 ab. Die zum Bandmaterial 12 hinweisende Nockenfläche 30 ist dabei derart gestaltet, dass die Klemmbacke 20 in der Vorschubstrecke 34 der Nockenbahn 32 in Richtung des Pfeils K1 zum Bandmaterial 12 hin verlagert wird und mit diesem in Anlageeingriff gelangt.During its movement along the closed path B, the roller roller 28 rolls permanently under the pressure of the coil springs 24 and 26 on the cam surface 30 of the cam track 32. The cam surface 30 indicative of the strip material 12 is designed such that the clamping jaw 20 is displaced in the feed path 34 of the cam track 32 in the direction of the arrow K1 toward the strip material 12 and arrives in abutting engagement therewith.

Die untere Nockenbahn 36 ist bezogen auf die Symmetrieebene S spiegelbildlich zur oberen Nockenbahn 32 ausgebildet, so dass auch die untere Klemmbacke 22 bei Durchlauf durch die Vorschubstrecke 34 zum Langmaterial 12 hin verstellt wird.The lower cam track 36 is formed with respect to the plane of symmetry S mirror image of the upper cam track 32, so that the lower jaw 22 is adjusted while passing through the feed path 34 to the long material 12 out.

Die Verstellung der Klemmbacke 20 in Richtung des Pfeils K1 auf das Langmaterial 12 zu erfolgt einfach dadurch, dass die Dicke a der Nockenbahn 32 in der Vorschubstrecke 34 größer bemessen ist als die Dicke b der Nockenbahn 32 außerhalb der Vorschubstrecke 34. Die der Nockenfläche 30 entgegengesetzte Oberseite 38 der Nockenbahn 32 liegt vorzugsweise in einer zur Symmetrieebene S parallelen Ebene, so dass die Dickenzunahme der Nockenbahn 32 im Bereich der Vorschubstrecke 34 zu einer Annäherung der Nockenfläche 30 an das Langmaterial 12 führt.The adjustment of the jaw 20 in the direction of the arrow K1 on the long material 12 to simply by the fact that the thickness a of the cam track 32 in the feed section 34 is sized larger than the thickness b of the cam track 32 outside the feed path 34. The cam surface 30 opposite Top 38 of the cam track 32 is preferably in a plane parallel to the plane of symmetry S, so that the increase in thickness of the cam track 32 in the region of the feed path 34 leads to an approximation of the cam surface 30 to the long material 12.

Das Gehäuse 18 der Klemmeinrichtung 16 ist vorzugsweise einstückig ausgebildet, so dass eine präzise Gegenüberstellung der Klemmbacken 20 und 22 auch über lange Betriebszeiten gewahrt bleibt. Die Gehäuse 18 können dabei von den im montierten Zustand der Klemmeinrichtungen 16 zu den jeweiligen Nockenbahnen hinweisenden Seiten aus ausgenommen sein, so dass die Schraubenfedern 24 und 26 sowie die Klemmbacke 20 in Richtung des Pfeils K1 in die obere Hälfte des Gehäuses 18 der Klemmeinrichtung 16 eingesetzt werden können. Ebenso können die Klemmbacke 22 und die sie gegen die Nockenbahn vorspannenden Schraubenfedern in Richtung des Pfeils K2 in die untere Hälfte des Gehäuses 18 der Klemmeinrichtung 16 eingesetzt werden. Gegen ein Herausfallen sind die jeweiligen Klemmbacken 20 und 22 in einsatzbereitem Zustand der Vorschubvorrichtung durch ihre Anlage an der Nockenbahn 32 gesichert.The housing 18 of the clamping device 16 is preferably formed in one piece, so that a precise comparison of the jaws 20 and 22 is maintained even over long periods of operation. The housing 18 may be excluded from the in the assembled state of the clamping devices 16 to the respective cam tracks facing sides, so that the coil springs 24 and 26 and the jaw 20 inserted in the direction of the arrow K1 in the upper half of the housing 18 of the clamping device 16 can be. Similarly, the jaw 22 and the biasing them against the cam track coil springs in the direction of Arrow K2 are inserted into the lower half of the housing 18 of the clamping device 16. Against falling out, the respective jaws 20 and 22 are secured in the ready state of the feed device by their contact with the cam track 32.

Die Dickenzunahme der Nockenbahn 32 in der Vorschubstrecke 34 erfolgt nicht schlagartig, sondern über einen Eingangs-Neigungsabschnitt 40. Es ist jedoch dafür gesorgt, dass sich stets mehr als eine Klemmeinrichtung 16 in der Vorschubstrecke 34 befindet, so dass das Langmaterial 12 von mehreren Klemmeinrichtungen 16 gleichzeitig geklemmt ist und in Vorschubrichtung V transportiert werden kann. Vorzugsweise sind stets drei Klemmeinrichtungen 16 in der Klemmstellung und somit in Klemmeingriff mit dem Langmaterial 12. Ein entsprechender Austritts-Neigungsabschnitt 42 ist auch am Ende der Vorschubstrecke 42 vorgesehen, um für einen stetigen Übergang von der Klemmstellung in die Lösestellung zu sorgen.The increase in thickness of the cam track 32 in the feed section 34 is not abrupt, but via an input inclination section 40. However, it is ensured that there is always more than one clamping device 16 in the feed section 34, so that the long material 12 of several clamping devices 16 clamped at the same time and can be transported in the feed direction V. Preferably, three clamping devices 16 are always in the clamping position and thus in clamping engagement with the long material 12. A corresponding outlet inclination section 42 is also provided at the end of the feed path 42 to provide a smooth transition from the clamping position to the release position.

In dem in Fig. 1 gezeigten Beispiel befindet sich die Wälzachse der Wälzrolle 28 der Klemmbacke 20 der ganz linken Klemmeinrichtung 16 von vier in der Vorschubstrecke 34 vorgesehenen Klemmeinrichtungen genau unter dem Ende des Neigungsabschnitts 40. Ebenso befindet sich die Wälzachse der Wälzrolle 28 der Klemmbacke der ganz rechten Klemmeinrichtung dieser Vierergruppe unter dem Beginn des Neigungsabschnitts 42.In the example shown in FIG. 1, the rolling axis of Wälzrolle 28 of the jaw 20 of the leftmost clamping device 16 of four provided in the feed path 34 clamping means just below the end of the slope portion 40 is also located the rolling axis of the Wälzrolle 28 of the jaw of rightmost clamping device of this group of four at the beginning of the slope section 42.

Die Klemmeinrichtungen 16 weisen an ihrem in Vorschubrichtung V vorlaufenden Ende eine Formschlusseingriffsgeometrie 44 und an ihrem in Vorschubrichtung V nachlaufenden Ende eine Formschlussgegengeometrie 46 auf. Wie in den Fig. 1 und 2 zu erkennen ist, gelangen während einer Richtungsumlenkung der Klemmeinrichtungen 16 diese Formschlusseingriffs-und Formschlussgegengeometrien außer Eingriff, während sie dann, wenn sich die Klemmeinrichtungen 16 in der Vorschubstrecke 34 befinden, in Formschlusseingriff sind. Dieser Formschlusseingriff dient im Wesentlichen der Sicherstellung einer vorbestimmten Lagebeziehung benachbarter Klemmeinrichtungen 16 zueinander und verhindert insbesondere ein Verdrehen der Klemmeinrichtungen 16 um eine zur Vorschubrichtung V orthogonale und in der Zeichenebene der Fig. 1 liegende Drehachse.The clamping devices 16 have at their leading end in the feed direction V a Formschlusseingriffsgeometrie 44 and at its trailing end in the feed direction V a positive connection counter-geometry 46. As can be seen in FIGS. 1 and 2, during a directional deflection of the clamping devices 16, these positive locking and positive locking counter-geometries disengage, while they are in positive engagement with the clamping devices 16 in the feed path 34. This form-fitting engagement essentially serves to ensure a predetermined positional relationship of adjacent clamping devices 16 to one another and in particular prevents them Rotation of the clamping devices 16 about an orthogonal to the feed direction V and lying in the plane of FIG. 1 axis of rotation.

Wie in Fig. 1 durch strichlinierte Darstellung ebenfalls zu erkennen ist, ist innerhalb der Umlaufbahn B der Klemmeinrichtungen 16 ein Hydraulikzylinder 48 vorgesehen (siehe auch Fig. 2). Die ausfahrbare Kolbenstange 50 des Hydraulikzylinders 48 ist mit einer oberen und einer unteren Zahnstange 52 bzw. 54 verbunden. In dem in den Fig. 1 - 6 gezeigten Beispiel ist der Hydraulikzylinder 48 doppelt wirkend, so dass die Kolbenstange 50 in und entgegen der Vorschubrichtung V verfahrbar ist. Das Getriebe 56, zu welchem die obere Zahnstange 52 gehört, und das Getriebe 58, zu welchem die untere Zahnstange 54 gehört, sind bezüglich der Symmetrieebene S spiegelsymmetrisch ausgebildet und angeordnet, so dass lediglich das obere Getriebe 56 beschrieben wird. Für die Beschreibung des unteren Getriebes 58 wird ausdrücklich auf die Beschreibung des Getriebes 56 verwiesen.As can also be seen in Fig. 1 by a dashed line, a hydraulic cylinder 48 is provided within the orbit B of the clamping devices 16 (see also Fig. 2). The extendable piston rod 50 of the hydraulic cylinder 48 is connected to an upper and a lower rack 52 and 54, respectively. In the example shown in FIGS. 1-6, the hydraulic cylinder 48 is double-acting, so that the piston rod 50 can be moved in and counter to the feed direction V. The gear 56, to which the upper rack 52 belongs, and the gear 58, to which the lower rack 54 belongs, are mirror-symmetrical with respect to the plane of symmetry S and arranged so that only the upper gear 56 will be described. For the description of the lower gear 58, reference is expressly made to the description of the transmission 56.

Die Zahnstange 52, welche durch eine Schraubenfeder 60 entgegen der Vorspannrichtung V vorgespannt ist, kämmt mit einer Umfangsverzahnung, welche an Zylinderwalzen 62 und 64 ausgebildet ist. Jede dieser Zylinderwalzen umfasst an jedem ihrer axialen Längsenden einen bezüglich ihrer Mittelachse exzentrisch angeordneten Exzenterzapfen. Beispielhaft ist in Fig. 1 die Mittelachse 64a der Zylinderwalze 64 und der an ihr befestigte Exzenterzapfen 66 gezeigt.The rack 52, which is biased by a coil spring 60 against the biasing direction V, meshes with a peripheral toothing formed on cylinder rollers 62 and 64. Each of these cylindrical rollers comprises at each of its axial longitudinal ends an eccentric eccentric pin arranged with respect to its central axis. By way of example, FIG. 1 shows the central axis 64a of the cylindrical roller 64 and the eccentric pin 66 fastened to it.

Der Exzenterzapfen 66, wie auch die übrigen Exzenterzapfen der weiteren Zylinderwalzen sind mit den Nockenbahnen 32 und 36 bewegungs- und kraftübertragungsmäßig gekoppelt, so dass durch eine Drehung der Zylinderwalzen 62 und 66 aufgrund einer Verschiebung der Zahnstange 52 in Vorschubrichtung die obere Nockenbahn 32 in Richtung des Pfeils K2 orthogonal zur Vorschubrichtung angehoben wird. Umgekehrt kann die Nockenbahn 32 durch eine Verschiebung der Zahnstange 52 entgegen der Vorschubrichtung V, beispielsweise bei Hydraulikausfall bewirkt durch die Vorspannkraft der Schraubenfeder 60, längs des Pfeils K1 zum Bandmaterial 12 hin abgesenkt werden.The eccentric pin 66, as well as the other eccentric pins of the other cylindrical rollers are coupled with the cam tracks 32 and 36 movement and force transmission, so that by rotation of the cylindrical rollers 62 and 66 due to a displacement of the rack 52 in the feed direction, the upper cam track 32 in the direction of Arrow K2 is raised orthogonal to the feed direction. Conversely, the cam track 32 by a displacement of the rack 52 against the feed direction V, for example in case of hydraulic failure caused by the biasing force of the coil spring 60, along the arrow K1 to the strip material 12th be lowered down.

Aufgrund der spiegelsymmetrischen Ausbildung des unteren Getriebes 58 wird die untere Nockenbahn 36 bei gleicher Verlagerung der Zahnstange 54 spiegelverkehrt bewegt. Dadurch können die Nockenbahnen 32 und 36 mittels der Kolbenstange 50, der mit dieser zur gemeinsamen Bewegung verbundenen Zahnstangen 52 und 54 sowie der mit diesen kämmenden Zylinderwalzen über die daran angeordneten Exzenterzapfen aufeinander zu und voneinander weg bewegt werden. Dadurch ist es möglich, die minimal erreichbare Spaltweite zwischen zwei sich einander gegenüberstehenden Klemmbacken 20 und 22 in der Vorschubstrecke 34 zu verändern. Auf diese Art und Weise kann die Vorschubvorrichtung 10 durch gezielte Beaufschlagung des Hydraulikzylinders 48 mit Hydrauliköldruck an Langmaterialien 12 unterschiedlicher Dicke in der Raumrichtung des Doppelpfeils K angepasst werden.Due to the mirror-symmetrical design of the lower gear 58, the lower cam track 36 is moved mirror-inverted at the same displacement of the rack 54. Thereby, the cam tracks 32 and 36 by means of the piston rod 50, which are connected to this common motion associated racks 52 and 54 and the meshing with these cylindrical rollers on the eccentric pin disposed thereon toward each other and away from each other. This makes it possible to change the minimum achievable gap width between two opposing jaws 20 and 22 in the feed path 34. In this way, the feed device 10 can be adjusted by targeted application of the hydraulic cylinder 48 with hydraulic oil pressure to long materials 12 of different thickness in the spatial direction of the double arrow K.

In Fig. 1 lediglich angedeutet ist ein Zahnriemen 68, mit dem die Klemmeinrichtungen 16 formschlüssig verbunden sind. Der Zahnriemen 68 ist jedoch besser in Fig. 2 zu erkennen.In Fig. 1 only indicated is a toothed belt 68, with which the clamping devices 16 are positively connected. However, the timing belt 68 is better seen in Fig. 2.

Wie in Fig. 2 zu erkennen ist, ist die Vorschubvorrichtung nicht nur zu der zur Zeichenebene parallelen Symmetrieebene S, sondern auch zu einer zur Zeichenebene der Fig. 2 orthogonalen und zur Zeichenebene der Fig. 1 im Wesentlichen parallelen Symmetrieebene T im Wesentlichen spiegelsymmetrisch. Der Hydraulikzylinder 48, welcher auch im Wesentlichen symmetrisch zur Symmetrieebene T angeordnet ist, wird von den Klemmeinrichtungen 16 umlaufen, was zu einer raumsparenden Gesamtanordnung der Vorschubvorrichtung 10 führt. Der Hydraulikzylinder 48 ist äußerst vorteilhaft einstückig mit einem die Zahnriemenführung lagernden Innengehäuse 69 ausgebildet.As can be seen in FIG. 2, the feed device is essentially mirror-symmetrical not only to the plane of symmetry S parallel to the plane of the drawing, but also to a plane of symmetry T which is orthogonal to the plane of the drawing and substantially parallel to the plane of the drawing of FIG. The hydraulic cylinder 48, which is also arranged substantially symmetrically to the plane of symmetry T, is circulated by the clamping devices 16, resulting in a space-saving overall arrangement of the feed device 10. The hydraulic cylinder 48 is formed in an extremely advantageous manner in one piece with an inner housing 69 which supports the toothed belt guide.

Der Zahnriemen 68, welcher ein Kunststoffriemen mit Stahlseele ist, ist an seiner radial inneren, wie auch an seiner radial äußeren Seite mit einer Verzahnung versehen. Die radial innere Verzahnung 68a gestattet dabei einen exakten Vortrieb durch die Antriebszahnwalze 70, welche durch die mit der Getriebeausgangswelle 14a gekoppelte Walzenwelle 70a zur Drehung im Gegenuhrzeigersinn angetrieben ist, mit welcher sie über eine Keilwellenverzahnung drehmomentübertragend verbunden ist.The toothed belt 68, which is a plastic belt with steel core, is at its radially inner, as well as on its radially outer side with a toothing Mistake. The radially inner toothing 68a allows exact propulsion through the drive toothed roller 70, which is driven by the coupled to the transmission output shaft 14a roller shaft 70a for rotation in the counterclockwise direction with which it is connected via a splined shaft to transmit torque.

Die zweite Umlenkung wird durch eine mit Abstand von der Antriebswalze 70 vorgesehene Mitläuferwalze 72 erreicht, welche durch eine Schraube 74 von der Antriebswalze weg und auf diese zu verlagerbar ist, um den Zahnriemen 68 in einem ausreichend gespannten Zustand zu halten. Die Antriebswalze 70 und die Mitläuferwalze 72 sind im Wesentlichen identisch ausgestaltet.The second deflection is accomplished by a idler roller 72 spaced apart from the drive roller 70 which is displaceable by and away from the drive roller by a screw 74 to maintain the timing belt 68 in a sufficiently tensioned condition. The drive roller 70 and the idler roller 72 are designed substantially identical.

Alternativ zur Antriebswalze 70 und zur Mitläuferwalze 72 kann, wenn der zur Verfügung stehende Bauraum dies erfordert, auch eine Mehrzahl von im Wesentlichen in Breitenrichtung des Zahnriemens 68 beabstandeten Antriebs- und Mitläuferscheiben eingesetzt werden.As an alternative to the drive roller 70 and the idler roller 72, if the available installation space so requires, a plurality of drive and idler pulleys spaced substantially in the width direction of the toothed belt 68 can also be used.

Die Außenverzahnung 68b des Zahnriemens 68 gestattet eine in Vorschubrichtung V bzw. in Umlaufrichtung formschlüssige Festlegung der Klemmeinrichtungen 16 am Zahnriemen 68, so dass eine hohe Positioniergenauigkeit der Klemmeinrichtungen möglich ist. Die Klemmeinrichtungskörper 18 sind dabei mit Griffstücken 76 am Zahnriemen 68 eingehängt. Derartige Griffstücke 76 sind am oberen und am unteren Ende eines jeden Klemmeinrichtungskörpers 18 vorgesehen und umgreifen sowie hintergreifen den Zahnriemen 68 an dessen Rändern.The external toothing 68b of the toothed belt 68 permits a fixing of the clamping devices 16 on the toothed belt 68 that is positive in the feed direction V or in the direction of rotation, so that a high positioning accuracy of the clamping devices is possible. The Klemmeinrichtungskörper 18 are mounted with handles 76 on the timing belt 68. Such grips 76 are provided at the upper and lower ends of each clamp body 18 and engage around and engage behind the toothed belt 68 at its edges.

Der Hintergriff des Zahnriemens durch die Griffstücke 76 erfasst dabei lediglich einen bezüglich der Abmessung einer Klemmeinrichtung 16 in Umlaufrichtung zentralen Zahn der radial inneren Verzahnung 68a des Zahnriemens 68, so dass bei einer Umlenkung die Klemmeinrichtung 16 zwar am Zahnriemen fixiert ist, der flexible Zahnriemen 68 sich ansonsten jedoch von dem im Wesentlichen starren Gehäuse 18 der Klemmeinrichtung 16 lösen und an den Umlenkwalzen 70 und 72 anliegen kann.The rear grip of the toothed belt by the gripping pieces 76 thereby only captures a tooth of the radially inner toothing 68a of the toothed belt 68 which is central in the circumferential direction with respect to the dimension of a clamping device 16 so that the clamping device 16 is fixed to the toothed belt during a deflection, the flexible toothed belt 68 itself otherwise, however, disengage from the substantially rigid housing 18 of the clamp 16 and can abut against the guide rollers 70 and 72.

In Fig. 2 ist weiter zu sehen, dass zwischen den Umlenkabschnitten 78 und 80 spiegelbildlich bezüglich der Symmetrieebene T zu der im Wesentlichen geraden Vorschubstrecke 34 eine ebenfalls im Wesentlichen gerade Rücklaufstrecke 82 vorgesehen ist.In Fig. 2 it can be seen further that between the deflection sections 78 and 80 in mirror image with respect to the plane of symmetry T to the substantially straight feed path 34, a likewise substantially straight return path 82 is provided.

In Fig. 3 ist ein Schnitt längs der Ebene III-III durch die Vorschubvorrichtung 10 dargestellt.In Fig. 3 is a section along the plane III-III is shown by the feed device 10.

In Fig. 3 ist u. a. zu erkennen, wie die Getriebeausgangswelle 14a des Zwischengetriebes 14 über eine Welle-Nabe-Verbindung 84 mit der Walzenwelle 70a gekoppelt ist, die wiederum durch Keilverzahnung mit der Antriebswalze 70 zur Drehmomentübertragung gekoppelt ist. Die Walzenwelle 70a ist durch zwei mit Abstand voneinander angeordnete Wälzlager reibungsarm zur Drehung gelagert.In Fig. 3 is u. a. to see how the transmission output shaft 14a of the intermediate gear 14 is coupled via a shaft-hub connection 84 with the roller shaft 70a, which in turn is splined to the drive roller 70 for torque transmission. The roller shaft 70a is frictionally supported for rotation by two spaced rolling bearings.

In Fig. 3 ist sehr gut zu erkennen, dass die Nockenfläche 30 der Nockenbahn 32 innerhalb der Vorschubstrecke 34 im Wesentlichen parallel zu einer Anlageebene 12a für die Klemmbacke 20 mit Abstand von dieser angeordnet ist. Dadurch ist es möglich, eine stempelartige Klemmbacke 20 einzusetzen, welche im Zustand einer Klemmung im Wesentlichen nur durch Druck belastet ist. Bei dieser Konstruktion ist es möglich, höhere Klemmkräfte auf das Langmaterial 12 auszuüben als bei auf Biegung beanspruchten Klemmbacken. Darüber hinaus können die Abmessungen der einzelnen Klemmbacken klein gehalten werden. Es muss lediglich sichergestellt sein, dass die Nockenfläche 30 sicher abgetastet und Klemmkraft auf das Langmaterial 12 ausgeübt werden kann.In Fig. 3 can be seen very well that the cam surface 30 of the cam track 32 is disposed within the feed path 34 substantially parallel to a bearing plane 12a for the jaw 20 at a distance therefrom. This makes it possible to use a stamp-like clamping jaw 20, which is loaded in a state of clamping substantially only by pressure. With this construction, it is possible to exert higher clamping forces on the long material 12 than in the case of bending jaws. In addition, the dimensions of the individual jaws can be kept small. It only has to be ensured that the cam surface 30 can be reliably scanned and clamping force can be exerted on the long material 12.

In Fig. 4, welche eine Schnittansicht längs der Ebene IV-IV in Fig. 1 ist, ist im Querschnitt der von den Klemmeinrichtungen 16 und dem Zahnriemen 68 umgebene Hydraulikzylinder 48 mit seiner Kolbenstange 50 zu erkennen.In Fig. 4, which is a sectional view taken along the plane IV-IV in Fig. 1, the hydraulic cylinder 48 surrounded by the clamping means 16 and the toothed belt 68 can be seen with its piston rod 50 in cross section.

Darüber hinaus ist zu erkennen, wie der Zahnriemen 68 in seiner Breitenrichtung an jedem Rand von je einem Griffstück 76 umgriffen und hintergriffen wird. Die Griffstücke 76 sind mit dem Gehäuse 18 der Klemmeinrichtung 16 verschraubt. Die hierfür verwendeten Schrauben sind in Fig. 1 gezeigt. Eine ist dort mit dem Bezugszeichen 76a versehen.In addition, it can be seen how the toothed belt 68 is gripped in its width direction at each edge of a handle 76 and engaged behind. The gripping pieces 76 are screwed to the housing 18 of the clamping device 16. The screws used for this purpose are shown in Fig. 1. One is provided there with the reference numeral 76a.

Weiterhin sind in Fig. 4 das Getriebe 56 und das Getriebe 58 zur Einstellung des Minimalspalts zwischen den Klemmbacken 20 und 22 in der Vorschubstrecke 34 dargestellt. Die Zylinderwalze 62 ist um ihre Mittelachse 62a drehbar gelagert. Eine an ihrer Mantelfläche ausgebildete Verzahnung kämmt mit der Zahnstange 52. Die Zahnstange 52 ist zur gemeinsamen Bewegung mit der Kolbenstange 50 des Hydraulikzylinders 48 verbunden (s. Fig. 2 bei KP).Furthermore, in Fig. 4, the gear 56 and the gear 58 for adjusting the minimum gap between the jaws 20 and 22 in the feed path 34 are shown. The cylindrical roller 62 is rotatably supported about its central axis 62a. A toothing formed on its lateral surface meshes with the rack 52. The rack 52 is connected for common movement with the piston rod 50 of the hydraulic cylinder 48 (see Fig. 2 at KP).

An ihren beiden Längsenden weist die Zylinderwalze 62 mit der Nockenbahn 32 gekoppelte Exzenterzapfen 63a und 63b auf. Der bezüglich der Zylinderwalzenachse 62a exzentrisch vorgesehene Zapfen 63a ist bewegungs- und kraftübertragend mit der Nockenbahn 32 auf der Rücklaufstrecke 82 gekoppelt, während der am entgegengesetzten Längsende vorgesehene Exzenterzapfen 63b mit der Nockenbahn 32 auf der Seite der Vorschubstrecke bewegungs- und kraftübertragend gekoppelt ist. Durch eine Verdrehung der Zylinderwalze 62 um ihre Zylinderachse 62a verlagern sich die Exzenterzapfen 63a und 63b in Richtung des Doppelpfeils K und verlagern so die Nockenbahn 32 von der Ebene S des Langmaterials 12 in der Vorschubstrecke 34 weg bzw. auf diese zu. Die Exzenterzapfen 63a und 63b der Zylinderwalze 62 sind koaxial zueinander ausgerichtet. Die übrigen Zylinderwalzen der Getriebe 56 und 58 sind im Wesentlichen identisch zur Zylinderwalze 62 ausgebildet. Die Exzenterzapfen 63a und 63b sind in Löchern in der Nockenbahn 32 aufgenommen.At its two longitudinal ends, the cylindrical roller 62 with the cam track 32 coupled eccentric pins 63a and 63b. The eccentrically provided with respect to the cylinder roller axis 62a pin 63a is coupled motion and force transmitting with the cam track 32 on the return path 82, while the provided at the opposite longitudinal end eccentric pin 63b is coupled to the cam track 32 on the side of the feed path movement and force transmitting. By a rotation of the cylindrical roller 62 about its cylinder axis 62a, the eccentric pins 63a and 63b shift in the direction of the double arrow K, thus displacing the cam track 32 away from the plane S of the long material 12 in the feed path 34 or towards it. The eccentric pins 63a and 63b of the cylindrical roller 62 are aligned coaxially with each other. The remaining cylindrical rollers of the gears 56 and 58 are formed substantially identical to the cylinder roller 62. The eccentric pins 63a and 63b are received in holes in the cam track 32.

Der Vollständigkeit halber wird auf Fig. 5 verwiesen, welche einen Schnitt längs der Ebene V-V in Fig. 1 durch die Drehachse der Mitläuferwalze 72 zeigt. Gleiche Bauteile wie in den vorhergehenden Figuren 1 - 4 sind mit gleichen Bezugszeichen versehen, wobei zur Beschreibung der Fig. 5 auf die Beschreibung der vorhergehenden Figuren verwiesen wird.For the sake of completeness, reference is made to FIG. 5, which shows a section along the plane VV in FIG. 1 through the axis of rotation of the idler roller 72. The same components as in the preceding figures 1-4 are with the same reference numerals, reference being made to the description of FIG. 5 to the description of the preceding figures.

In den Figuren 6a und 6b sind Klemmbacken 20 und 22 ausführlich dargestellt, welche in den Klemmeinrichtungen 16 der Vorschubvorrichtung 10 gemäß Figuren 1 - 5 eingesetzt sind. Im Folgenden wird lediglich eine Klemmbacke 20 beschrieben, wobei diese Beschreibung auch auf die Klemmbacken 22 anzuwenden ist, da diese Klemmbacken identisch ausgebildet sind.In Figures 6a and 6b jaws 20 and 22 are shown in detail, which are used in the clamping devices 16 of the feed device 10 according to Figures 1-5. In the following, only one clamping jaw 20 will be described, this description also being applicable to the clamping jaws 22, since these clamping jaws are identical.

Wie bereits zuvor beschrieben wurde, weisen die Klemmbacken 20 an ihrem einen Längsende 20a eine Wälzrolle 28 auf, welche zum Abwälzen auf der Nockenfläche 30 ausgebildet ist. Hierfür kann in vorteilhafter Weise ein im Handel erhältliches Wälzlager verwendet werden, wobei die Außenfläche 28a des Lageraußenrings als Wälzfläche verwendet wird. Die Wälzrolle 28 ist um einen Bolzen 88 drehbar gelagert, welcher im an der Vorschubvorrichtung montierten Zustand mit zur Nockenfläche 30 paralleler Bolzenachse 88a angeordnet ist. Zur günstigeren Krafteinleitung ist am Längsende 20a der Klemmbacke 20 eine gabelartige Lagerausbildung 90 vorgesehen, in welcher die Wälzrolle 28 drehbar aufgenommen ist.As has already been described above, the clamping jaws 20 have at their one longitudinal end 20a a rolling roller 28 which is designed to roll on the cam surface 30. For this purpose, a commercially available rolling bearing can be used in an advantageous manner, wherein the outer surface 28a of the bearing outer ring is used as a rolling surface. The Wälzrolle 28 is rotatably mounted about a pin 88 which is mounted in the mounted on the feed device state with the cam surface 30 parallel pin axis 88a. For more favorable introduction of force, a fork-like bearing formation 90 is provided at the longitudinal end 20a of the clamping jaw 20, in which the rolling roller 28 is rotatably received.

An die Lagerausbildung 90 schließt in Längsrichtung der Klemmbacke 20 ein Schaftabschnitt 92 an, welcher bis zum zweiten Längsende 20b der Klemmbacke 20 reicht. Der Schaftabschnitt 92 ist im Wesentlichen zylindrisch ausgebildet.To the bearing formation 90 includes in the longitudinal direction of the jaw 20 to a shaft portion 92 which extends to the second longitudinal end 20 b of the jaw 20. The shaft portion 92 is formed substantially cylindrical.

Am zweiten Längsende 20b der Klemmbacke 20 ist ein kegelstumpfförmiges Klemmflächenstück 94 vorgesehen und mit einer Schraube am Schaftabschnitt 92 gesichert.At the second longitudinal end 20b of the jaw 20, a frusto-conical clamping surface piece 94 is provided and secured with a screw on the shaft portion 92.

Das Klemmflächenstück 94 ist aus Hartmetall oder Keramik gebildet und stellt die verschleißarme Klemmbackenanlagefläche 94a bereit, welche beim Klemmen des Langmaterials 12 in Anlage an dieses gelangt. Die übrige Klemmbacke 20 ist vorzugsweise aus sog. Kunststoffformenstahl hergestellt, welcher auch zur Anfertigung von Kunststoffspritzgussformen verwendet wird.The clamping surface piece 94 is formed of cemented carbide or ceramic and provides the low-wear jaw abutment surface 94 a, which comes in abutment of the long material 12 in this system. The remaining jaw 20 is preferably made of so-called. Plastic mold steel, which is also used for the production of plastic injection molds.

Der Schaftabschnitt 92 der Klemmbacke 20 ist mit einer Nachgiebigkeit versehen. Diese Nachgiebigkeit wird erreicht durch Einbringen von Schlitzen in den Schaftabschnitt 92. Die Schlitze 92a und 92b verlaufen dabei alle zueinander parallel und orthogonal zur Längsachse 20c der Klemmbacke 20, welche auch die Längsachse des Schaftabschnitts 92 ist. Dabei durchsetzen die Schlitze 92a den Schaftabschnitt 92 im Bereich der Längsachse 20c, d. h. im Bereich der Quermitte des Schaftabschnitts 92a. Die Schlitze 92b sind dagegen vom Mantel des Schaftabschnitts 92 in radialer Richtung zur Längsachse 20c hin eingeschnitten, erreichen die Längsachse 20c jedoch nicht.The shank portion 92 of the jaw 20 is provided with a compliance. This compliance is achieved by inserting slots in the shaft portion 92. The slots 92a and 92b are all parallel to each other and orthogonal to the longitudinal axis 20c of the jaw 20, which is also the longitudinal axis of the shaft portion 92. The slots 92a pass through the shaft section 92 in the region of the longitudinal axis 20c, d. H. in the region of the transverse center of the shaft portion 92a. On the other hand, the slots 92b are cut in the radial direction toward the longitudinal axis 20c by the jacket of the shaft section 92, but do not reach the longitudinal axis 20c.

In Längsachsenrichtung wechseln die Schlitze 92a und 92b einander in im Wesentlichen gleichen Abständen ab, wobei die Schlitze 92b stets paarweise einander bezüglich der Längsachse 20c gegenüberliegend vorgesehen sind. Die Schlitze oder Einkerbungen 92b vom Außenmantel des Schaftabschnitts 92 her können einfach eingesägt werden, während die durchsetzenden Ausnehmungen 92a beispielsweise durch Drahterodieren hergestellt sein können. Hierfür wird zunächst der Schaft 92 durchbohrt, wobei dann in die Bohrung der Draht für das nachfolgende Drahterodieren eingelegt wird. Durch diese Ausnehmungen 92a und 92b weist der Schaftabschnitt 92 der Klemmbacken 20 und 22 eine Elastizität auf, welche eine ausreichende Nachgiebigkeit zum Ausgleich von Dickenunterschieden des Bandmaterials 12 bereitstellt. Diese Dickenunterschiede sind insbesondere dann auszugleichen, wenn mehrere benachbarte Klemmeinrichtungen 16 sich gleichzeitig in der Vorschubstrecke 34 der Vorschubvorrichtung 10 in der Klemmstellung befinden.In the longitudinal axis direction, the slots 92a and 92b alternate at substantially equal intervals, the slots 92b always being provided in pairs opposite each other with respect to the longitudinal axis 20c. The slots or indentations 92b from the outer shell of the shank portion 92 can be simply sawed in, while the passing recesses 92a can be made, for example, by wire eroding. For this purpose, the shaft 92 is first pierced, in which case the wire is inserted into the bore for the subsequent wire EDM. Through these recesses 92a and 92b, the shank portion 92 of the jaws 20 and 22 has an elasticity which provides sufficient compliance to compensate for differences in thickness of the strip material 12. These differences in thickness are to be compensated in particular when several adjacent clamping devices 16 are located simultaneously in the feed path 34 of the feed device 10 in the clamping position.

Die Klemmbacken 20 und 22 bzw. ihr Schaftabschnitt 92 weisen bis zu einer Kraft von 3000 N ein lineares Elastizitätsverhalten auf. Bei einem Durchmesser von 12 mm des Schaftabschnitts 92 wird bei 3000 N ein Federweg von ca. 0,15 mm erreicht. Versuche haben gezeigt, dass bis zu dieser Verformung der Schaftabschnitt 92 als Hook'sche Feder angesehen werden kann.The clamping jaws 20 and 22 and their shank portion 92 have up to a force of 3000 N on a linear elastic behavior. With a diameter of 12 mm of the shaft portion 92 becomes at 3000 N a spring travel reached from about 0.15 mm. Experiments have shown that until this deformation, the shaft portion 92 can be considered as Hook's spring.

Claims (19)

  1. A feed apparatus for feeding long material (2), in particular strip, wire or profile material, along a feed apparatus (V), wherein the feed apparatus has at least one clamping device (16) with at least two clamping jaws (20,22) which define a clamping gap between them and at least one (20,22) of which can move, while varying the gap width, along a clamping movement path (KB) on the respective other clamping jaw (20,22) towards and away from the latter, which clamping device (16) is adjustable between a clamping position, in which it keeps the long material (12) clamped between the clamping jaws (20,22), and a release position, in which it releases the long material (12) for movement relative to the clamping jaws (20,22), and which can move in feed direction (V) at least in the clamping position, wherein the at least one clamping device (16) is provided revolving along a closed path (B), wherein a feed course (34) of the revolving path (B) extends in the feed direction (V) and wherein while passing through the feed course (34) the clamping device (16) is situated at least in sections in the clamping position, wherein a cam path (32,36) is provided as motion control of the at least one clamping jaw (20,22) movable along the clamping movement path (KB), which cam path displaces the clamping jaw (20,22) on the respective other clamping jaw (20,22) towards and/or away from the latter, wherein the feed apparatus also comprises a minimum gap width varying means (48,50,56,58) with a power device which is designed to vary the smallest gap width occurring in normal feed operation during one passage through the feed course (34) between two mutually opposed clamping jaws (20,22), and wherein the cam path (32,36) can be displaced, is in force-transmitting relationship with the power device and can be driven by the force of the power device for displacement, wherein displacement of the cam path (32,36) by the power device induces displacement of the at least one clamping jaw (20,22) co-operating with the cam path (32,36),
    characterised in that the minimum gap width varying means (48,50,56,58) comprises a hydraulic piston/cylinder unit (48,50) as power device, which is in force-transmitting relationship with at least one of the two mutually opposed clamping jaws (20,22) so that the at least one clamping jaw can be can be displaced while force is being exerted by the power device on the respective opposed clamping jaw (20,22) towards and/or away from the latter, wherein the cam path (32,36) is acted upon by the preloading force of a preloading spring element (60) in a predetermined displacement direction (K1) .
  2. A feed apparatus according to Claim 1,
    characterised in that the it has a plurality of clamping devices (16) succeeding one another in revolving direction.
  3. A feed apparatus according to Claim 2,
    characterised in that a plurality of clamping devices (16) are situated simultaneously in the clamping position during their movement in feed direction (V).
  4. A feed apparatus according to any one of the preceding Claims, characterised in that the at least one clamping device (16) is connected to an endless motion-transmitting member (68) of variable form for common movement therewith.
  5. A feed apparatus according to Claim 4,
    characterised in that the motion-transmitting member (68) is a toothed belt (68), preferably of double-sided toothed design (68a,68b), in particular a plastics toothed belt (68) with a metal core.
  6. A feed apparatus according to any one of the preceding Claims, characterised in that the at least one clamping jaw (20,22) movable along the clamping movement path (KB) is biased by a spring means (24,26) into a lifting position of larger gap width and it co-operates with the cam path (32,36) for movement into an abutment position of smaller gap width.
  7. A feed apparatus according to Claim 6,
    characterised in that the at least one clamping jaw (20,22) movable along the clamping movement path (KB) is of elongate form, at one longitudinal end (20b) of which there is provided a clamping jaw abutment surface (94a) for abutment against the long material (12), and at the other longitudinal end (20a) of which there is provided a rolling body (28) for rolling abutment against the cam path (32,36).
  8. A feed apparatus according to any one of the preceding Claims, characterised in that the cam path (32,36) is biased in a displacement direction (K1) inducing a reduction in clamping gap width.
  9. A feed apparatus according to any one of the preceding Claims, characterised in that the power device is connected by a transmission (56,68) to the cam path (32,36).
  10. A feed apparatus according to Claim 9,
    characterised in that the transmission (56,58) comprises an eccentric (63a,63b,64a) which can be rotated by the power device (48,50) and with which the cam path (32,36) is connected.
  11. A feed apparatus according to Claim 9 or 10, characterised in that the power device (48,50) is disposed in a zone surrounded by the at least one revolving clamping device (16).
  12. A feed apparatus according to any one of the preceding Claims, characterised in that the at least one clamping device (16) comprises at least two clamping jaws (20,22) which between them define a clamping gap and at least one of which, preferably two, is/are designed to be resilient in a direction enlarging the clamping gap.
  13. A feed apparatus according to Claim 12,
    characterised in that the at least one resilient clamping jaw (20,22) is in at least two parts, wherein by the interposition of a spring means two clamping jaw parts are arranged to be movable relative to one another at least in the clamping gap enlarging direction.
  14. A feed apparatus according to Claim 13,
    characterised in that the at least one resilient clamping jaw (20,22) is an elongate component which is provided at least in sections with at least one recess (92a,92b), preferably a through-recess (92a), the direction of extension of which has a component orthogonal to the longitudinal direction (20c) of the clamping jaw (20,22).
  15. A feed apparatus according to Claim 14,
    characterised in that at least one recess (92a) passes through the clamping jaw (20,22), preferably in the vicinity of its transverse centre (at 20c).
  16. A feed apparatus according to any one of the preceding Claims, characterised in that each individual clamping jaw of two clamping jaws (20,22) of a clamping device (16), which between them define a clamping gap, can move on the respective other one towards and away therefrom while varying the gap width.
  17. A feed apparatus according to Claim 16,
    characterised in that as motion control of each clamping jaw (20,22) movable along the clamping movement path (KB) there is provided a cam path (32,36) which displaces a clamping jaw (20,22) on the respective other clamping jaw (20,22) towards and/or away from the latter, wherein preferably the two opposed clamping jaws (20,22) and/or the two cam paths (32,36) are designed with features from at least one of Claims 6 to 19.
  18. A feed apparatus according to any one of the preceding Claims, characterised in that the cam paths (32,36) and the at least one clamping device (16), preferably also the minimum gap width varying means (48,50,56,58), are arranged symmetrically relative to a plane of symmetry (S) between the clamping jaws (20,22) and passing through the clamping gap in the gap centre.
  19. A feed apparatus according to any one of the preceding Claims, characterised in that the at least one clamping device (16) has a clamping device body (18) and clamping jaws (20,22) which are retained movably relative thereto on the clamping device body (18), wherein adjustment of the at least one clamping device (16) takes place between the clamping position and the release position by moving the clamping jaws (20,22) relative to the clamping device body (18).
EP05021192A 2004-09-28 2005-09-28 Feeding device Active EP1640084B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP06006565A EP1676655B1 (en) 2004-09-28 2005-09-28 Feeding device with resilient clamping jaw
PL05021192T PL1640084T3 (en) 2004-09-28 2005-09-28 Feeding device
PL06006565T PL1676655T3 (en) 2004-09-28 2005-09-28 Feeding device with resilient clamping jaw

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004047048A DE102004047048A1 (en) 2004-09-28 2004-09-28 feed device

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP06006565A Division EP1676655B1 (en) 2004-09-28 2005-09-28 Feeding device with resilient clamping jaw

Publications (3)

Publication Number Publication Date
EP1640084A2 EP1640084A2 (en) 2006-03-29
EP1640084A3 EP1640084A3 (en) 2006-04-05
EP1640084B1 true EP1640084B1 (en) 2007-04-11

Family

ID=35347045

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EP05021192A Active EP1640084B1 (en) 2004-09-28 2005-09-28 Feeding device
EP06006565A Active EP1676655B1 (en) 2004-09-28 2005-09-28 Feeding device with resilient clamping jaw

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP06006565A Active EP1676655B1 (en) 2004-09-28 2005-09-28 Feeding device with resilient clamping jaw

Country Status (5)

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EP (2) EP1640084B1 (en)
AT (2) ATE386599T1 (en)
DE (3) DE102004047048A1 (en)
ES (2) ES2285622T3 (en)
PL (2) PL1676655T3 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1941957B1 (en) 2007-01-08 2009-09-09 Bruderer Ag Device for intermittent feed of a semifinished product in strip or wire form to a press
DE102007034708B3 (en) * 2007-07-25 2009-04-09 Data M Software Gmbh Flexible hold-down device for a profiling line for flexible roll forming of cold or hot profiles with variable cross section
FR2924367B1 (en) * 2007-11-30 2010-05-07 Modernes Atel DEVICE FOR ADVANCING A STRIP MATERIAL FOR FEEDING A MACHINE TOOL AND MACHINE EQUIPPED WITH SUCH A DEVICE
DE102009017003A1 (en) 2009-04-14 2010-10-21 Groche, Peter, Prof. Dipl.-Wirtsch.-Ing. Dr.-Ing. Device for suppressing semi-finished profiled component, has suppressing elements pressurized by passive spring with force in latitude direction and limited in latitude direction by geometry element of component
DE102009022829B3 (en) * 2009-05-27 2011-02-24 Data M Sheet Metal Solutions Gmbh Roll profiling apparatus and method
DE202009007527U1 (en) * 2009-05-27 2009-08-27 Data M Sheet Metal Solutions Gmbh Flexible hold-down for roll forming systems
ES2552584B1 (en) * 2014-05-27 2016-09-14 Mariano Camps I Fills, S.L. Metal wire fiber forming machine and corresponding set
CN105328065A (en) * 2015-12-04 2016-02-17 四川燚成钢结构有限公司 Section bar conveying device with checking function
DE102016104182B4 (en) 2016-03-08 2017-10-26 Muhr Und Bender Kg Apparatus and method for transporting metallic long material
CN106425645A (en) * 2016-11-17 2017-02-22 黄河交通学院 Feeding device for automatic machine tool
CN113333643A (en) * 2020-02-18 2021-09-03 广东博智林机器人有限公司 Stirrup loading attachment and reinforcing bar processing equipment

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US1911157A (en) * 1927-12-28 1933-05-23 Union Drawn Steel Company Mechanism for drawing metal
US2961138A (en) * 1958-12-30 1960-11-22 Gen Electric Feed mechanism
US3684145A (en) * 1970-11-16 1972-08-15 Sylvania Electric Prod Rectilinear feed apparatus
IT991338B (en) * 1973-07-23 1975-07-30 Danieli Off Mecc CONTINUOUS TRACKING DEVICE WITH TRACKS TO PERFORM THE OPERATION OF STRAIGHT DRAWING PEELING GRINDING OF WIRE OR METAL PIPE
DE3505372C2 (en) * 1985-02-16 1986-12-04 Peddinghaus, Carl Ullrich, Dr., 5600 Wuppertal Device for a length-controlled feeding of profile steel bars to a machine tool
DE4004312A1 (en) * 1990-02-13 1991-08-14 Kabelmetal Electro Gmbh DEVICE FOR DRAWING AND / OR LEADING LONG STRETCHED GOODS

Also Published As

Publication number Publication date
PL1676655T3 (en) 2008-07-31
PL1640084T3 (en) 2007-09-28
ES2285622T3 (en) 2007-11-16
ATE359136T1 (en) 2007-05-15
DE502005002906D1 (en) 2008-04-03
EP1676655A1 (en) 2006-07-05
EP1676655B1 (en) 2008-02-20
ATE386599T1 (en) 2008-03-15
EP1640084A2 (en) 2006-03-29
ES2301107T3 (en) 2008-06-16
DE102004047048A1 (en) 2006-04-06
EP1640084A3 (en) 2006-04-05
DE502005000577D1 (en) 2007-05-24

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