EP1640084B1 - Dispositif d'avance - Google Patents

Dispositif d'avance Download PDF

Info

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
Authority
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)
English (en)
Other versions
EP1640084A3 (fr
EP1640084A2 (fr
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 PL06006565T priority Critical patent/PL1676655T3/pl
Priority to PL05021192T priority patent/PL1640084T3/pl
Priority to EP06006565A priority patent/EP1676655B1/fr
Publication of EP1640084A2 publication Critical patent/EP1640084A2/fr
Publication of EP1640084A3 publication Critical patent/EP1640084A3/fr
Application granted granted Critical
Publication of EP1640084B1 publication Critical patent/EP1640084B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21F—WORKING OR PROCESSING OF METAL WIRE
    • B21F23/00—Feeding wire in wire-working machines or apparatus
    • B21F23/002—Feeding means specially adapted for handling various diameters of wire or rod
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C1/00—Manufacture of metal sheets, metal wire, metal rods, metal tubes by drawing
    • B21C1/16—Metal 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
    • B21C1/27—Carriages; Drives
    • B21C1/30—Drives, e.g. carriage-traversing mechanisms; Driving elements, e.g. drawing chains; Controlling the drive
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D43/00—Feeding, positioning or storing devices combined with, or arranged in, or specially adapted for use in connection with, apparatus for working or processing sheet metal, metal tubes or metal profiles; Associations therewith of cutting devices
    • B21D43/02—Advancing work in relation to the stroke of the die or tool
    • B21D43/04—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
    • B21D43/10—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work by grippers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D43/00—Feeding, positioning or storing devices combined with, or arranged in, or specially adapted for use in connection with, apparatus for working or processing sheet metal, metal tubes or metal profiles; Associations therewith of cutting devices
    • B21D43/02—Advancing work in relation to the stroke of the die or tool
    • B21D43/04—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
    • B21D43/12—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work by chains or belts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21F—WORKING OR PROCESSING OF METAL WIRE
    • B21F23/00—Feeding wire in wire-working machines or apparatus
    • B21F23/005—Feeding 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

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

Claims (19)

  1. Dispositif d'avance pour une alimentation en matériau oblong (12), en particulier en matériau de type bande, fil ou profilé, le long d'une direction d'avance (V), la direction d'avance présentant au moins un dispositif de blocage (16) avec au moins deux mâchoires de blocage (20, 22) définissant entre elles une fente de blocage, mâchoires dont au moins l'une (20, 22) est mobile en direction de l'autre mâchoire de blocage (20, 22) et depuis celle-ci en modifiant la largeur de fente le long d'une voie de mouvement de blocage (KB), lequel dispositif de blocage (16) est mobile entre une position de blocage dans laquelle il tient bloqué le matériau oblong (12) entre les mâchoires de blocage (20, 22) et une position de libération dans laquelle il libère le matériau oblong (12) en vue d'un mouvement par rapport aux mâchoires de blocage (20, 22), et lequel est mobile dans la direction d'avance (V) au moins dans la position de blocage, dans lequel le dispositif de blocage (16) au nombre d'au moins un est prévu circulant le long d'une voie (B) fermée, dans lequel une trajectoire d'avance (34) de la voie de circulation (B) s'étend dans la direction d'avance (V) et le dispositif de blocage (16) se trouve, pendant un parcours de la trajectoire d'avance (34) au moins par sections dans la position de blocage, dans lequel, comme commande de déplacement de la mâchoire de blocage (20, 22) au nombre d'au moins une mobile le long de la direction de mouvement de blocage (KB), il est prévu une voie de came (32, 36) qui déplace la mâchoire de blocage (20, 22) en direction de l'autre mâchoire de blocage (20, 22) ou l'en écarte, dans lequel le dispositif d'avance comprend de plus un dispositif (48, 50, 56, 58) de variation de la largeur minimale de fente avec un appareil de puissance, qui est conformé pour modifier la largeur de fente la plus faible apparaissant en régime normal d'avance pendant un parcours de la trajectoire d'avance (34) entre deux mâchoires de blocage (20, 22) en vis-à-vis, et dans lequel la voie de came (32, 36) est déplaçable, est en relation de transmission de force avec l'appareil de puissance et peut être mise en mouvement par la force de l'appareil de puissance, un déplacement de la voie de came (32, 36) par l'appareil de puissance provoquant un déplacement de la mâchoire de blocage (20, 22) au nombre d'au moins une coopérant avec la voie de came (32, 36),
    caractérisé en ce que les moyens (48, 50, 56, 58) de variation de la largeur minimale de fente comprennent une unité à piston/cylindre hydraulique (48, 50) comme appareil de puissance, qui se trouve en relation de transmission de force avec au moins l'une des deux mâchoires de blocage (20, 22) en vis-à-vis, de telle manière que la mâchoire de blocage au nombre d'au moins une peut être rapprochée ou écartée de la mâchoire de blocage (20, 22) opposée par application d'une force par l'appareil de puissance, la voie de came (32, 36) étant exposée dans une direction de déplacement (K1) prédéterminée à la force de précontrainte d'un élément (60) à ressort de précontrainte.
  2. Dispositif d'avance selon la revendication 1, caractérisé en ce qu'il présente une pluralité de dispositifs de blocage (16) se suivant dans la direction de circulation.
  3. Dispositif d'avance selon la revendication 2, caractérisé en ce qu'une pluralité de dispositifs de blocage (16) se trouve simultanément en position de blocage pendant leur mouvement dans la direction d'avance (V).
  4. Dispositif d'avance selon l'une des revendications précédentes, caractérisé en ce que le dispositif de blocage (16) au nombre d'au moins un est relié à une partie (68) de transmission de mouvement sans fin ayant une forme variable, en vue d'un mouvement commun avec elle,
  5. Dispositif d'avance selon la revendication 4, caractérisé en ce que la partie (68) de transmission de mouvement est une courroie dentée (68), de préférence avec des dents (68a, 68b) formées des deux côtés, en particulier une courroie dentée en matière plastique (68) à âme métallique.
  6. Dispositif d'avance selon l'une des revendications précédentes, caractérisé en ce que la mâchoire de blocage (20, 22) au nombre d'au moins une mobile le long de la voie de mouvement de blocage (KB) est précontrainte par un moyen à ressort (24, 26) en direction d'une position de soulèvement ayant une plus grande largeur de fente et coopère avec la voie à came (32, 36) pour un mouvement vers une position d'appui présentant une largeur de fente plus faible.
  7. Dispositif d'avance selon la revendication 6, caractérisé en ce que la mâchoire de blocage (20, 22) au nombre d'au moins une mobile le long de la voie de mouvement de blocage (KB) présente une forme oblongue, à une extrémité longitudinale (20b) de laquelle est prévue une surface (94a) d'appui de mâchoire de blocage destinée à s'appuyer contre le matériau oblong (12), et à l'autre extrémité longitudinale (20a) de laquelle est prévu un corps roulant (28) pour un appui roulant contre la voie de came (32, 36).
  8. Dispositif d'avance selon l'une des revendications précédentes, caractérisé en ce que la voie de came (32, 36) est précontrainte dans une direction de déplacement (K1) provoquant une réduction de la largeur de la fente de blocage.
  9. Dispositif d'avance selon l'une des revendications précédentes, caractérisé en ce que l'appareil de puissance est relié à la voie de came (32, 36) par un engrenage (56, 58).
  10. Dispositif d'avance selon la revendication 9, caractérisé en ce que l'engrenage (56, 58) comprend un excentrique (63a, 63b, 64a) pouvant être tourné par l'appareil de puissance (48, 50) et auquel est reliée la voie de came (32, 36).
  11. Dispositif d'avance selon la revendication 9 ou 10, caractérisé en ce que l'appareil de puissance (48, 50) est placé dans une zone entourée par le dispositif de blocage (16) au nombre d'au moins un.
  12. Dispositif d'avance selon l'une des revendications précédentes, caractérisé en ce que le dispositif de blocage (16) au nombre d'au moins un comprend au moins deux mâchoires de blocage (20, 22) définissant entre elles une fente de blocage, dont au moins l'une, de préférence les deux, est ou sont réalisé(s) souple(s) dans une direction augmentant la fente de blocage.
  13. Dispositif d'avance selon la revendication 12, caractérisé en ce que la mâchoire de blocage souple (20, 22) au nombre d'au moins une est réalisée en deux parties, deux parties de mâchoire de blocage étant placées mobiles l'une par rapport à l'autre au moins dans la direction d'agrandissement de la fente de blocage, par interposition d'un dispositif à ressort.
  14. Dispositif d'avance selon la revendication 13, caractérisé en ce que la mâchoire de blocage souple (20, 22) au nombre d'au moins une est un composant oblong qui est muni au moins par endroits d'au moins un évidement (92a, 92b), de préférence un évidement traversant (92a), dont la direction d'extension présente une composante perpendiculaire à la direction longitudinale (20c) de la mâchoire de blocage (20, 22).
  15. Dispositif d'avance selon la revendication 14, caractérisé en ce qu'au moins un évidement (92a) traverse la mâchoire de blocage (20, 22), de préférence au niveau de son centre transversal (en 20c).
  16. Dispositif d'avance selon l'une des revendications précédentes, caractérisé en ce que chacune de deux mâchoires de blocage (20, 22) d'un dispositif de blocage (16) définissant entre elles une fente de blocage peut être rapprochée et écartée de l'autre en modifiant la largeur de la fente.
  17. Dispositif d'avance selon la revendication 16, caractérisé en ce que comme commande de déplacement de chaque mâchoire de blocage (20, 22) mobile le long de la direction de mouvement de blocage (KB), il est prévu à chaque fois une voie de came (32, 36) qui déplace la mâchoire de blocage (20, 22) en direction de l'autre mâchoire de blocage (20, 22) ou l'en écarte, de préférence les deux mâchoires de blocage (20, 22) opposées et/ou les deux voies de came (32, 36) étant réalisées avec des caractéristiques d'au moins l'une des revendications 6 à 19.
  18. Dispositif d'avance selon l'une des revendications précédentes, caractérisé en ce que les voies de came (32, 36) et le dispositif de blocage (16) au nombre d'au moins un, de préférence également le moyen (48, 50, 56, 58) de variation de la largeur minimale de fente sont disposés symétriquement par rapport à un plan de symétrie (S) passant entre les mâchoires de blocage (20, 22) par la fente de blocage, au milieu de la fente.
  19. Dispositif d'avance selon l'une des revendications précédentes, caractérisé en ce que le dispositif de blocage (16) au nombre d'au moins un présente un corps de dispositif de blocage (18) et des mâchoires de blocage (20, 22) tenues mobiles par rapport à lui sur le corps de dispositif de blocage (18), un déplacement du dispositif de blocage (16) au nombre d'au moins un entre la position de blocage et la position de libération s'effectuant par déplacement des mâchoires de blocage (20, 22) par rapport au corps de dispositif de blocage (18).
EP05021192A 2004-09-28 2005-09-28 Dispositif d'avance Active EP1640084B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PL06006565T PL1676655T3 (pl) 2004-09-28 2005-09-28 Urządzenie posuwowe z podatną szczęką zaciskową
PL05021192T PL1640084T3 (pl) 2004-09-28 2005-09-28 Urządzenie posuwowe
EP06006565A EP1676655B1 (fr) 2004-09-28 2005-09-28 Dispositif d'avance avec mâchoire de serrage souple

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004047048A DE102004047048A1 (de) 2004-09-28 2004-09-28 Vorschubvorrichtung

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP06006565A Division EP1676655B1 (fr) 2004-09-28 2005-09-28 Dispositif d'avance avec mâchoire de serrage souple

Publications (3)

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

Family

ID=35347045

Family Applications (2)

Application Number Title Priority Date Filing Date
EP06006565A Active EP1676655B1 (fr) 2004-09-28 2005-09-28 Dispositif d'avance avec mâchoire de serrage souple
EP05021192A Active EP1640084B1 (fr) 2004-09-28 2005-09-28 Dispositif d'avance

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP06006565A Active EP1676655B1 (fr) 2004-09-28 2005-09-28 Dispositif d'avance avec mâchoire de serrage souple

Country Status (5)

Country Link
EP (2) EP1676655B1 (fr)
AT (2) ATE359136T1 (fr)
DE (3) DE102004047048A1 (fr)
ES (2) ES2285622T3 (fr)
PL (2) PL1640084T3 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE502007001488D1 (de) 2007-01-08 2009-10-22 Bruderer Ag Vorrichtung zum intermittierenden Zuführen eines band- oder drahtförmigen Halbzeugmaterials zu einer Presse
DE102007034708B3 (de) * 2007-07-25 2009-04-09 Data M Software Gmbh Flexibler Niederhalter für eine Profilieranlage zum flexiblen Walzprofilieren von Kalt- oder Warmprofilen mit veränderlichem Querschnitt
FR2924367B1 (fr) * 2007-11-30 2010-05-07 Modernes Atel Dispositif d'avance d'un materiau en bande destine a alimenter une machine outil et machine equipee d'un tel dispositif
DE102009017003A1 (de) 2009-04-14 2010-10-21 Groche, Peter, Prof. Dipl.-Wirtsch.-Ing. Dr.-Ing. Selbstausrichtender Niederhalter
DE102009022829B3 (de) * 2009-05-27 2011-02-24 Data M Sheet Metal Solutions Gmbh Walzprofiliervorrichtung und -verfahren
DE202009007527U1 (de) * 2009-05-27 2009-08-27 Data M Sheet Metal Solutions Gmbh Flexibler Niederhalter für Walzprofilieranlagen
ES2552584B1 (es) * 2014-05-27 2016-09-14 Mariano Camps I Fills, S.L. Máquina formadora de fibras de alambre metálico y conjunto correspondiente
CN105328065A (zh) * 2015-12-04 2016-02-17 四川燚成钢结构有限公司 一种具有清点功能的型材输送装置
DE102016104182B4 (de) * 2016-03-08 2017-10-26 Muhr Und Bender Kg Vorrichtung und Verfahren zum Transportieren von metallischem Langmaterial
CN106425645A (zh) * 2016-11-17 2017-02-22 黄河交通学院 一种自动化机床用送料装置
CN113333643A (zh) * 2020-02-18 2021-09-03 广东博智林机器人有限公司 箍筋上料装置以及钢筋加工设备

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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 (it) * 1973-07-23 1975-07-30 Danieli Off Mecc Dispositivo di tiro continuo a cingoli per eseguire l operazione di trafilatura rettilinea pelatura rettifica di filo o tubo metallico
DE3505372C2 (de) * 1985-02-16 1986-12-04 Peddinghaus, Carl Ullrich, Dr., 5600 Wuppertal Vorrichtung für eine längenmaßgesteuerte Zuführung von Profilstahlstäben zu einer Werkzeugmaschine
DE4004312A1 (de) * 1990-02-13 1991-08-14 Kabelmetal Electro Gmbh Vorrichtung zum abziehen und/oder fuehren von langgestrecktem gut

Also Published As

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

Similar Documents

Publication Publication Date Title
EP1640084B1 (fr) Dispositif d'avance
EP3033187B1 (fr) Dispositif de transfert d'une pièce
EP2734462B1 (fr) Dispositif et procédé permettant d'arrêter et/ou d'orienter des produits transportés sur un convoyeur, et convoyeur
DE69203085T3 (de) Antriebsvorrichtung für eine Ziehmaschine.
DE60222101T2 (de) Vorrichtung zum antreiben und damit hergestelltes spannwerkeug
EP0462324A1 (fr) Dispositif de serrage pour le serrage de pièces à usiner
DE2613269C3 (fr)
EP1336440A1 (fr) Dispositif pour le mouvement des pièces avec des barres d'amenage
DE69406018T2 (de) Zangen-vorschubgerät für metallstreifen
DE3001271A1 (de) Zufuehrungseinrichtung vom walzentyp zum zufuehren von flaechigem material
DE102011006173B3 (de) Spanneinrichtung zum Spannen eines Werkstücks sowie Biegemaschine mit einer solchen Spanneinrichtung
DE2525616C3 (de) Verstellvorrichtung einer Werkstücktransporteinrichtung von Stufenpressen
DE2555150A1 (de) Vorrichtung zum erzeugen des foerderhubes in transfereinrichtungen
DE10059312C2 (de) Zentriervorrichtung für Fördergut
WO2010006572A1 (fr) Granulateur de joncs à espace de coupe réglable
EP0321602B1 (fr) Dispositif d'avancement à pinces avec mécanismes à manivelle entraînés pneumatiquement ou hydrauliquement
DE19722287B4 (de) Drahtvorschub- und Ziehvorrichtung
DE69703978T2 (de) Vorrichtung zum regeln der grösse eines werkzeugmaschinen-blechhalters
EP1870179A2 (fr) Dispositif pour l' avancement cadencé d'une bande de matière
DE3132646A1 (de) Walzvorrichtung und verfahren zum walzen stangenfoermigen materials
DE10244483B4 (de) Profilwalzmaschine mit Kraftrahmen zum Walzen mit außenverzahnten Rundwalzwerkzeugen
DE3112810C2 (fr)
DE29613831U1 (de) Vorrichtung zum beidseitigen Beschleifen mit einer Ausrichtvorrichtung
EP2145727B1 (fr) Unité coulissante
DE2158777A1 (de) Vorschubeinrichtung zum zufuehren von draht- oder bandfoermigem material

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20060323

17Q First examination report despatched

Effective date: 20060809

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

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

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 502005000577

Country of ref document: DE

Date of ref document: 20070524

Kind code of ref document: P

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

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20070621

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

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070811

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

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070911

ET Fr: translation filed
REG Reference to a national code

Ref country code: PL

Ref legal event code: T3

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2285622

Country of ref document: ES

Kind code of ref document: T3

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

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

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

26N No opposition filed

Effective date: 20080114

BERE Be: lapsed

Owner name: OTTO BIHLER HANDELS-BETEILIGUNGS-GMBH

Effective date: 20070930

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

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070930

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070712

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

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

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

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070930

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

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070928

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

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

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

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

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

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20070928

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

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070411

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071012

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090930

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090930

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

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

Ref country code: GB

Payment date: 20220920

Year of fee payment: 18

Ref country code: DE

Payment date: 20220630

Year of fee payment: 18

Ref country code: CZ

Payment date: 20220923

Year of fee payment: 18

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

Ref country code: PL

Payment date: 20220915

Year of fee payment: 18

Ref country code: FR

Payment date: 20220922

Year of fee payment: 18

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

Ref country code: IT

Payment date: 20220926

Year of fee payment: 18

Ref country code: ES

Payment date: 20221121

Year of fee payment: 18

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230512

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005000577

Country of ref document: DE

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

Ref country code: CZ

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230928

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20230928

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

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230928