EP3978159A2 - Machine à plier les chaînes permettant de fabriquer une chaîne - Google Patents

Machine à plier les chaînes permettant de fabriquer une chaîne Download PDF

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Publication number
EP3978159A2
EP3978159A2 EP21199099.9A EP21199099A EP3978159A2 EP 3978159 A2 EP3978159 A2 EP 3978159A2 EP 21199099 A EP21199099 A EP 21199099A EP 3978159 A2 EP3978159 A2 EP 3978159A2
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EP
European Patent Office
Prior art keywords
bending
chain
unit
cam
mandrel
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Granted
Application number
EP21199099.9A
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German (de)
English (en)
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EP3978159C0 (fr
EP3978159A3 (fr
EP3978159B1 (fr
Inventor
Jörg Niethammer
Wolfgang Schad
Jürgen RAUSCHER
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Wafios AG
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Wafios AG
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Publication of EP3978159A3 publication Critical patent/EP3978159A3/fr
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Publication of EP3978159C0 publication Critical patent/EP3978159C0/fr
Publication of EP3978159B1 publication Critical patent/EP3978159B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21L—MAKING METAL CHAINS
    • B21L1/00—Making chains or chain links by bending workpieces of rod, wire, or strip to form links of oval or other simple shape
    • B21L1/02—Making chains or chain links by bending workpieces of rod, wire, or strip to form links of oval or other simple shape by bending the ends of the workpieces to abut
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21L—MAKING METAL CHAINS
    • B21L3/00—Making chains or chain links by bending the chain links or link parts and subsequently welding or soldering the abutting ends

Definitions

  • the invention relates to a chain bending machine for producing chains with bent chain links.
  • Chains with chain links which are bent from wire elements in a forming process, are nowadays manufactured on a large scale with the help of special automated machine tools, which are usually referred to as chain bending machines or chain manufacturing machines, sometimes simply as chain machines.
  • Chain manufacturing typically involves two main processes, bending - commonly called chain bending - and welding - commonly called chain welding.
  • chain bending chain links are initially bent from straight wire elements of a suitable length, so-called pins or pins, and connected to other chain links, which can also be bent from wire elements or produced in some other way, e.g. by forging.
  • the finished, still open chain links of a chain strand are welded to form closed chain links, e.g. using a suitable resistance butt welding process.
  • This application relates to chain link bending with a so-called bending mandrel.
  • a so-called tiller is used as the starting workpiece for the actual bending operation to produce a chain link.
  • the tiller is a rod-shaped piece of wire cut from a supply of wire.
  • the length of the piece of wire corresponds to the processing of the desired chain link plus additional welding allowance.
  • the tiller is pressed against a bending mandrel by a holding element and thus fixed.
  • the circumference of the bending mandrel is designed according to the desired internal shape of the link.
  • a corresponding bending tool acts on the two wire ends protruding beyond the bending mandrel and partially bends the associated end of the tiller around the bending mandrel in the form of a chain link.
  • the disclosure document DE 2 028 266 A describes a chain bending machine equipped with a bending mandrel.
  • the chain bending machine comprises a bending unit for producing a bent chain link by bending a wire element around the bending mandrel in one bending plane.
  • the bending unit has two sub-units which are arranged on opposite sides of a central plane of the bending unit which is perpendicular to the bending plane.
  • the middle plane goes through the center of the bending mandrel.
  • Each of the two sub-units has a bending lever which can be pivoted about a pivot axis running perpendicularly to the bending plane. The swivel axis can be moved linearly.
  • each bending lever carries a bending tool, which is movably mounted on the bending lever and is in the form of a rotatably mounted bending roller, for engaging the wire element.
  • the bending tools are moved around the bending mandrel on predetermined trajectories.
  • the bending rollers are guided by means of guide rollers guided in grooves. These grooves are provided in a body rigidly connected to the bending mandrel to form a replaceable block. This has the advantage that the bending mandrel and the grooves can be adjusted outside the machine. Because it is not the bending rollers themselves that run in the grooves, but guide rollers, the bending rollers can roll on the tiller, which significantly reduces wear.
  • the disclosure document DE 2 531 290 A1 describes a method for bending chain links from wire pins with a predetermined length, the two free ends of the wire pin being bent around a bending mandrel.
  • a special feature is that a bending tool is placed in the area of the free ends of the pins, which is guided on a curved path during the bending process in such a way that the contact point of the bending tool on the wire pin is approximately on an involute of a circle, at least in the end area of the bending process runs, the reference point of which corresponds to the center of curvature of the side of the bending mandrel facing the respective bending tool.
  • This procedure has the advantage that the part of the bending tool that is in contact with the pin practically does not shift during the bending process, so that no grinding or rolling marks are produced on the pin surface.
  • Chain bending machines should be able to cover the widest possible range of chains, in particular a large wire diameter range, a wide variety of chain link geometries, a wide variety of bending radii, a wide variety of materials, etc.
  • the set-up times should be reduced as far as possible so that a changeover to new chain link geometries can take place with as little mechanical changeover effort as possible.
  • the object of the invention is to provide a chain bending machine of the type mentioned at the outset, in which, in comparison to conventional solutions Set-up times and adjustment times are reduced when changing between different chain link geometries. In particular, increased operator safety and increased ease of use should also be provided.
  • the invention provides, according to one formulation, a chain bending machine with the features of claim 1.
  • Advantageous developments are specified in the dependent claims. The wording of all claims is incorporated into the description by reference.
  • the chain bending machine is designed to produce chains with bent chain links. When set up, it includes a bending mandrel.
  • the bending mandrel is usually designed according to the desired internal shape of the link. It can be a split bending mandrel or an undivided bending mandrel.
  • a bending unit of the chain bending machine is designed to produce a bent chain link by bending a wire element around the bending mandrel. The bending takes place in a bending plane, which means here, among other things, that the neutral axis of the bent wire element lies in a single plane with all sections.
  • the bending unit has two sub-units.
  • the sub-units are arranged on opposite sides of a central plane of the bending unit that is perpendicular to the bending plane.
  • the bending unit can be constructed more or less mirror-symmetrically to the center plane, so that the two sub-units also have a comparable construction.
  • Each of the sub-units comprises a bending tool carrier unit which, on a component facing the bending mandrel, carries a bending tool which is intended to act on the wire element.
  • the bending tool is therefore that part of the bending unit which comes into physical contact with the wire material on the corresponding side of the bending mandrel.
  • the bending tools are movably mounted on the components of the respective bending tool carrier unit that carry them. This mobility is provided so that the bending tool can always be optimally aligned with the workpiece during the bending movement or during the gradual deformation of the wire around the bending mandrel.
  • the bending tools can be moved around the bending mandrel with the aid of the bending tool carrier unit during bending on definable trajectories. The trajectories of the bending tools only extend around part of the circumference of the bending mandrel.
  • a special feature of the chain bending machine is that it includes a freely programmable bending process control system, which is configured in such a way that different courses of trajectories of the bending tools can be specified by entering input parameters an input unit of the bending progression control system via a control unit of the chain bending machine.
  • the "free" programmability is of course only within the structurally specified limits, so that not just any trajectory can be specified, but a large variety of different trajectories can be generated within the structurally specified limits.
  • This means that different courses of trajectories of the bending tools can be set solely with the help of programming, that is to say on the software side, so that a completely software-based trajectory control is provided for the movements of the bending tools.
  • the input unit can be located on or near the chain bending machine.
  • a touch screen can be provided in conjunction with a PC and appropriate software for displays and inputs in plain text.
  • An entry at a remote location, possibly in another room or another building is also possible if required.
  • One advantage of this concept is that, with the exception of the components that come into contact with the wire (particularly the bending mandrel and, if necessary, bending tools, as well as any other geometry-dependent tools, such as retainers, turning tong jaws, tiller transport gripper jaws, etc.), no other components of the chain bending machine have to be exchanged when changing between different chain link geometries .
  • the "conversion" can therefore be carried out to a large extent by means of programming, i.e. via software. For example, compared to the solution of DE 2 028 266 A there is no need to replace the chain dimension-dependent die, which contains the guide groove for the guide rollers attached to the bending levers.
  • the bending curve control system is configured such that geometry data of the chain link to be manufactured as input parameters at the Input unit can be entered and that the bending curve control system is configured to perform specific calculations based on the geometric data for the chain link.
  • the geometric data or the input parameters describing the chain link geometry include the wire diameter, the inner pitch of the curved chain link (i.e. the clear distance between the inner chain arches in the longitudinal direction), the outer width of the chain link and, if applicable, the residual cross-section that is attached to the mutually facing ends of wedge-shaped separate pins should remain for the subsequent chain welding process.
  • the bending progression control system is preferably configured in such a way that a field of an input mask can be generated on a display device of the operating unit, in which a bent chain link is shown schematically together with input fields for the associated geometric data is.
  • the link-specific calculations may include one or more of the following calculations: tiller length calculation; calculation of tool geometries; Calculation of the trajectories of the bending tools.
  • the positions of the individual machining stations on the machine bed can be determined based on the information on the pin length. Depending on the expansion stage of the chain bending machine, these can then be adjusted manually or automatically using suitable machine axes.
  • the operator can procure and install the appropriate tools.
  • the bending paths or trajectories of the bending tools can be calculated.
  • the bending tools are preferably bending rollers rotatably mounted on the respective bending tool carrier unit, which roll on the wire without damaging the wire surface in the event of any relative movement between the circumference of the bending roller and the wire to be bent.
  • the calculation of the trajectories is preferably carried out under the boundary condition that the point of application between the bending tool and the wire remains unchanged during the bending operation, so that no relative movement between the bending tool and the wire results and in each phase of the Bending operation optimal balance of power exist.
  • other bending tools can also be used as an alternative to bending rollers.
  • bending shoes can be provided in order to get a larger contact surface instead of the line contact (given with bending rollers), in order to reduce the local surface pressure.
  • each of the bending tool carrier units has a bending lever which can be pivoted about a pivot axis running perpendicular to the bending plane.
  • Each bending lever carries a bending tool on its free end facing the bending mandrel.
  • Bending tool carrier units equipped with bending levers can have a very compact structure and can safely transmit large forces.
  • the pivotable bending lever can also be linearly displaced parallel to the bending plane, so that the bending tool can be guided parallel to the bending plane along different trajectories via a combination of linear displacement and pivoting movement.
  • a bending tool carrier unit it is possible, for example, for a bending tool carrier unit to have a cross table (also known as an XY table), i.e. a two-axis system that has two single-axis linear guide systems, thereby enabling a bending tool to be moved in two directions within the bending plane.
  • the bending tool can thus be guided parallel to the bending plane along different trajectories via a combination of two mutually orthogonal linear displacements.
  • a bending tool carrier unit has two coupled linear units that are attached to the machine frame such that they can pivot on pivot axes.
  • the pivot axes are aligned parallel to one another, but laterally offset from one another such that one linear unit executes a movement essentially parallel to a first direction and the other linear unit executes a movement essentially to a second direction orthogonal to the first direction.
  • the linear units each have extendable end pieces, the ends of which are coupled to one another and carry the bending tool in the area of the coupling.
  • each of the sub-units has a carriage which can be moved in a first direction parallel to the central plane and on which the bending lever of the sub-unit can be rotated about the pivot axis is mounted, wherein a first drive group for moving the carriage has a first servo drive and a second drive group for moving the bending lever has a second servo drive, which is preferably carried by the carriage.
  • the reciprocating linear movement of the carriage in the first direction contributes a component of movement in the first direction, the amount of which can be controlled as a function of time by means of the first servo drive.
  • the second drive group moves the bending lever and thus controls movement components of the bending tools, which run within the bending plane perpendicular to the first direction or perpendicular to the central plane.
  • the movements generated by the servo drives of the sub-units are coupled electronically via the control unit.
  • the second servo drive is preferably a traveling drive that travels along with the movement of the carriage.
  • the second servo drive can act on the associated bending lever or the bending tool attached to it over a short transmission distance. It would also be conceivable to attach the second servo drive in a stationary manner and to couple it to the bending lever via a flexible shaft or another flexible transmission device (e.g. cardan shaft with length compensation).
  • the first drive group has a first cam disk coupled to the first servo drive and/or the second drive group has a second cam disk coupled to the second servo drive.
  • the servo drives are each used to drive cam disks in rotation.
  • servo-mechanical drive groups are implemented. This means that movements of an output shaft of the servo drive can be mechanically transferred unevenly (with a variable transfer function) to the respective driven component via a cam gear, with the transfer function being specified by the course of the cam edge or the curve shape of the cam disc.
  • the combination of servo drives with cam discs allows for a favorable design both with regard to the very high forces that are sometimes required during bending and with regard to the dynamics of the bending operation, i.e. the speed profiles of the tool movements.
  • the first drive group with the first servo drive and the first cam generates the linear reciprocating movement of the carriage, which carries the bending lever of the sub-unit and preferably also the components of the associated second drive group.
  • the carriage In the variant with a cross table, the carriage carries another carriage instead of a bending lever.
  • Exemplary embodiments are particularly advantageous in which the control unit is configured in such a way that the first cam disk and/or the second cam disk is/is driven in a reversing manner between a first end position and a second end position.
  • the cam disk In contrast to conventional cam drives with a uniformly circulating drive movement, the cam disk is rotated back and forth in opposite directions of rotation with a limited angle of rotation.
  • the end positions define the limits of the transfer function implemented by the cam disc.
  • the mechanical complexity can be reduced in comparison to smooth rotating drive movements.
  • cam disks In contrast to conventional solutions, in which cam disks are exchanged for cam disks with a different cam shape and other strokes when changing between different chain link geometries, cam disks do not have to be exchanged when changing the format with a reversing drive or cam disks that are designed for a reversing drive necessary.
  • the cam discs can be designed in such a way that they can be used unchanged for all operations within the working range of the chain bending machine and can be replaced if necessary.
  • the curve shape of the cam disk can thus be defined once for all chain link geometries in the work area. This means that special design measures that allow cam disks to be changed easily can be omitted, so that the transmission coupling between the servo drive and cam disk can be designed to be mechanically particularly stable and suitable for the transmission of high forces or torques.
  • the first cam disk and/or the second cam disk has a curve shape with a linear gradient. This means that in the rotational angle range between the first end position and the second end position, the radial distance between the center of rotation of the cam disk and the outer cam flank changes according to a linear function. It has been shown that the computational effort for controlling the connected servo drive can be significantly reduced compared to variants in which complicated non-linear relationships between the angle of rotation and cam position by the Shape of the cam edge is specified. Alternatively, gradients that can be described with an e-function can also be worked, for example. However, variable gradients are also possible.
  • the first cam disk is assigned a positive-action scanning arrangement with two scanning elements connected to the carriage, with the scanning elements realized, for example, by scanning rollers, being arranged at a fixed distance from one another and on opposite sides Attack curve flank sections of the cam.
  • the curve shape can be designed in such a way that in all rotary positions within this working range, the distance measured between the scanning elements between associated curve flank sections is always the same, regardless of the rotary position.
  • the second cam is assigned a positive-action scanning arrangement with two scanning elements connected to the bending lever (or another carriage), with the scanning elements, for example realized by scanning rollers, at a fixed distance are arranged to each other and act on opposite cam flank portions of the cam.
  • a cam (first cam and/or second cam) can also be designed as a bead cam.
  • the bead curve can consist of one piece. It is also possible to design the inner and outer curves of the bead cam as separate cam discs (so-called main and counter curves). Groove curves or a spring return can also be provided.
  • an arrangement between the servo drive and the driven component that is favorable in terms of space requirements and power transmission results from the fact that the first servo drive is coupled to the first cam via a first gear, with the cam being overhung on an output shaft of the gear.
  • a floating bearing means here that there is no bearing for the cam discs on the side opposite the gearbox.
  • the drive group can have a straight, stretched structure, at one end of which the overhung cam is arranged.
  • the cantilevered mounting allows the cam disc to be arranged in or near the plane in which the pivot axis of the bending lever lies and in which the force of the movement component imparted by the carriage movement is transmitted. This results in a reduction of possible transverse forces on the components that are under load during bending, which also benefits the precision of the path curve, among other things.
  • a corresponding arrangement of the components of the second drive group can be provided, so that the second servo drive is coupled to the second cam via a second gear, the second cam being overhung on the output shaft of the gear.
  • the monitoring system preferably includes a subsystem for drive monitoring, which can identify and display overload situations caused by faults.
  • the drive monitoring subsystem can be designed to record the time curves of the motor torques of the individual machine drives of the machine axes and to compare them with permissible value ranges that can be present in the form of envelope curves. If a situation defined as significant occurs, operation can be stopped automatically in order to be able to remedy the situation.
  • the schematic side view in 1 shows an exemplary embodiment of a chain bending machine 200 for producing chains which have chain links bent from wire material.
  • the chain bending machine has a large number of functional units which are mounted in a straight row on a machine frame 202.
  • a Cartesian machine coordinate system MK is shown for orientation. Its x-direction runs horizontally in the example and is also referred to here as the first direction. The y-direction perpendicular thereto, in the example also horizontal, is also referred to as the second direction. In this orientation, the z-direction points to the vertical.
  • a first pull-in device 910 together with a downstream second pull-in device 920, is used to pull in the wire DR from a wire supply, which is typically in the form of a coil, ie a wire bundle wound up in the manner of a coil.
  • the feed devices 910, 920 each have a pair of feed rollers driven in opposite directions (roller feed).
  • a straightening unit 915 with two roller straighteners connected in series is arranged between the intake devices, each of which has a number (five in the example) of axis-parallel straightening rollers, the axes of rotation of the straightening rollers of the straighteners connected in series being aligned orthogonally to one another.
  • a downstream length measuring device 925 has a measuring wheel and an opposite running wheel, which is pressed against the wire passing through and thus ensures slip-free contact between the measuring wheel and the wire.
  • An optional wire stamping device 930 is provided immediately downstream of the length measuring device, with which a logo, lettering, a number or the like can be embossed on the wire conveyed through at predetermined points. In other embodiments, this optional component is not provided.
  • a spine bending device 935 is arranged behind it in the wire conveying direction, with which a spine bend can be produced on the wire.
  • a notching device 940 for creating notches on opposite sides of the wire without cutting it.
  • a camera system with a 945 camera is provided to monitor the notch depth.
  • a downstream shearing station or separating station 950 is used to sever a piece of wire DS or a pin of a predetermined length from the supplied wire at the point provided with notches.
  • a downstream transport device 955 (also called pin transport) is used to feed the pins to the downstream bending station 210, whose structure and function, inter alia, in connection with the 2 and 3 be described in more detail.
  • 2 shows a schematic isometric representation of some components of the bending station 210.
  • 3 shows a schematic plan view of a first part of a bending unit of the bending station.
  • All controllable components of the chain bending machine 200 are connected to the control unit 190 of the chain bending machine, which contains, among other things, the power supplies and position detection of the drives, a central processing unit and memory units. With the help of the control software active in the control unit, the movements of all machine axes can be variably controlled on the basis of setting parameters.
  • a display and operating unit 195 connected to the control unit 190 serves as an interface to the machine operator.
  • Chain bending is automated in the bending station 210 using a so-called bending mandrel 105, which is mounted on a vertically movable bending mandrel holder 106 and is designed as a divided bending mandrel.
  • a rod-shaped piece of wire (pin) that has not yet been bent or has a slight back bend is transported from an upstream station in the direction of arrow F (conveying direction) to the bending mandrel.
  • the pin which may be provided with a back bend, is pressed by a holding element (not shown) from the side of the bending unit onto the bending mandrel and fixed there.
  • the circumference of the bending mandrel that comes into contact with the pin is designed according to the desired internal shape of the link.
  • the bending mandrel serves as a counter-holder during bending and essentially defines the shape of the inside of the bent chain link.
  • the bending unit 100 working together with the bending mandrel 105 is designed to wrap a wire element fixed on the bending mandrel around the bending mandrel in a bending plane in order to produce a bent chain link and thereby deform it plastically.
  • the bending plane corresponds to the plane in which the neutral axis of the wire element bent to form a chain link lies.
  • the origin of the machine coordinate system can be chosen such that the bending plane coincides with the x-y plane spanned by the first and second directions.
  • the bending unit 100 is constructed essentially mirror-symmetrically to a central plane 122, which runs parallel to the x-z plane and thus perpendicular to the bending plane, centrally through the bending unit 100 and the bending mandrel 105.
  • the bending unit 100 comprises two sub-units that are essentially mirror-symmetrical to the central plane 122, namely a 1 first partial unit 110-1 shown at the back and an in 1 second partial unit 110-2 shown at the front, in which the associated drives are not shown for reasons of clarity.
  • the structure of a sub-unit is easily recognizable when these two sub-units are viewed together and is explained in more detail below with reference to the first sub-unit 110-1. This is in 2 shown schematically in plan view.
  • Each of the sub-units comprises a bending tool carrier unit which, on a component facing the bending mandrel 105, carries a bending tool 148 which is intended for engaging on the wire element.
  • the two bending tool carrier units are each equipped with a bending lever 130 .
  • the first sub-unit 110-1 has a carriage 120 that can be moved parallel to the x-direction and is guided on two mutually parallel guide rails 123 that are mounted on the upper side of the machine frame.
  • the carriage 120 carries a bending lever 130, which is a component of the bending tool carrier unit and is pivotable to a limited extent on a pivot bearing of the carriage about a pivot axis 132 running perpendicular to the bending plane.
  • the bending lever has a torsion-resistant S-shape and is designed as a two-armed lever in such a way that the pivot axis 132 lies approximately in the middle between the ends of the lever, with the two lever arms being at an angle of approximately 90° to 120° to one another.
  • the bending lever 130 has a bending tool 148 in the form of a bending roller 148 at its free end bent inwardly in the direction of the bending mandrel 105, which is freely rotatably mounted on the bending lever.
  • the axis of rotation runs parallel to the pivot axis 132.
  • the bending roller has a concave circumferential groove which serves as a contact surface for contact with the wire element to be bent Chain link is provided.
  • the bending lever is mounted both at the top and at the bottom in a plate-shaped component of the carriage 120, which is flat in the shape of a box in this area.
  • the bending tools 148 (bending rollers) carried by the bending levers 130 grip the two wire ends that protrude laterally beyond the bending mandrel 105 and partially bend the associated pin end around the bending mandrel 105 in the form of a chain link.
  • the bending tools move around a part of the bending mandrel precisely along predetermined trajectories. In 1 a finished bent chain link KG on the bending mandrel 105 is shown.
  • the reciprocating linear movement of the carriage 120 in the first direction is achieved using a first drive assembly 140 .
  • This includes a first servo drive 142, which is mounted with its motor shaft in a horizontal orientation on a motor bearing 143 fixed to the machine.
  • the rotation of the motor shaft is transmitted to a first cam disk 145 via a connected gear 144 in the form of a planetary gear.
  • the first cam disk 145 is overhung on the output shaft of the gear 144, which means here that all pivot bearings for mounting the first cam disk are arranged on the side of the drive or the gear.
  • the first cam disk 145 can be brought very close to the center plane 112 .
  • the lateral distance A1 between the center of the cam and a vertical plane passing through the pivot axis 132 is approximately the same as the radius of the axle or shaft that supports the flexure.
  • the rotation of the first cam disk 145 generated with the aid of the first drive 142 is transferred into a linear movement of the carriage 120 via its external cam flank.
  • two scanning elements in the form of rollers 146-1, 146-2 are mounted on a carrier 124 which is fixedly connected to the carriage 120 and which follow the flank of the cam when the cam disk rotates.
  • the rotation of the first cam disk 145 generated with the aid of the first drive 142 is not continuous over more than 360°, but reversing in such a way that the cam disk only reverses between a first end position and a second end position moved back and forth over a limited range of rotation angles (less than 180°), but not rotated indefinitely.
  • the two pickup rollers 146-1, 146-2 are parts of a positive-action pickup arrangement 146, with which the rotational movement of the cam disc in both directions of travel of the carriage is positively transmitted from the cam disc to the pickup arrangement connected to the carriage.
  • the shape of the cam disk is such that, within the end positions, the diameter DK of the cam disk, measured at the level of the axes of rotation of the follower rollers 146-1, 146-2, is constant regardless of the rotational position. In this way, a coupling between the cam disk and the slide is realized without play in both directions of movement of the slide.
  • the curve shape has a linear or constant gradient in the working range used, which makes it particularly easy to calculate the relationship between the rotation of the cam disk by means of the servo drive and the slide movement, i.e. the transfer function between the servo drive and slide movement.
  • the back and forth oscillating stroke movements of the carriage 120 in the first direction only contribute to the movement of the bending rollers 148 a movement component (x-component) running in the first direction.
  • An analogous drive configuration with reciprocating drive is provided for moving the flexure 130 .
  • the components of the second drive group 150 are used for this purpose.
  • the reversing rotary movement of the motor shaft is transmitted via a gear 154 in the form of a planetary gear to a second cam disk 155 which is overhung on the output shaft of the gear 154 . Since no bearing for the cam disk is required on the side facing away from the drive, it can be mounted with its center plane in the bending plane for optimized power transmission.
  • the second cam disk 155 is designed as a bead cam with an outer cam flank and an inner cam flank. It is assigned a positive-action scanning arrangement 156 with two scanning elements 156-1, 156-2 connected to the bending lever 130, which are arranged at a fixed distance from one another and act on opposite sides of the circumferential bead on the cam disk. At its end opposite the bending roller, the bending lever 130 has a first scanning element 156-1 in the form of a scanning roller, which is rotatably mounted in the bending lever and, when the second cam disk 155 rotates, rolls on its outer cam flank.
  • the bending lever carries a second sensing member 156-2 in the form of a sensing roller, which simultaneously rolls on the inner curve flank, so that in every rotational position of the cam disk, a backlash-free entrainment of the bending lever is ensured, regardless of the direction of rotation.
  • the bending lever 130 is constructed in several parts.
  • the lever arm leading to the follower roller 156 and the part of that lever arm which is closer to the pivot axis 132 and carries the bending roller 148 remain unchanged for all chain link geometries within the working range.
  • the outer part 133 of the lever arm, which carries the bending roller 148, is exchangeably attached to the remaining part in the area of an interface 134 by means of fastening screws and can be easily exchanged to adapt to a different bending geometry and/or different wire diameters.
  • the working movements of the bending lever 130 generated by the second servo drive 152 primarily act as movement components of the bending rollers 148 in the second direction (y-direction) and to a lesser extent also with components in the first direction perpendicular thereto.
  • the first servo drive 142 and the second servo drive 152 are each connected to the control unit 190 of the chain bending machine, so that the movement characteristics of the cam disks connected to it can be precisely controlled by the position control, speed control and/or torque control of the respective servo drive.
  • This concept enables the creation of freely programmable movements of the bending tools of the chain bending machine.
  • All four servo drives for the machine axes (linear axis with slide, rotary axis for bending lever) are electrically connected to a control unit 190, which contains, among other things, the power supplies and position detection of the drives, a central computer unit and memory units.
  • the control software active in the control unit the movements of all machine axes can be variably controlled on the basis of setting parameters.
  • the trajectories on which the bending rollers are to run can be freely specified by means of programming within design-related limits.
  • a display and operating unit 195 connected to the control unit 190 serves as an interface to the machine operator.
  • the user can enter certain parameters relevant to the bending process, eg the desired chain link geometry (geometry data), possibly various workpiece properties (workpiece data) and tool data, on an input unit 196 of the operating unit before the bending process begins.
  • input unit 196 comprises a touch-sensitive screen (touchscreen).
  • the control unit 190 is the central component of the freely programmable bending progression control system of the chain bending machine 200. With this system, different courses of trajectories of the bending tools can be specified by entering input parameters on an input unit via the control unit 190.
  • the bending curve control system is programmed by a machine operator via the display and operating unit 195. Programming can, for example, proceed as follows.
  • the starting point for programming are the dimensions of the chain link to be bent.
  • 4 shows an example of a field F of an input mask, in which a curved chain link KG is shown schematically together with associated input windows for entering the geometric data.
  • the input parameters include the wire diameter d, the inner pitch tb of the curved chain link (i.e. the clear distance between the inner chain arches in the longitudinal direction), the outer width bb2 of the chain link and, if applicable, the residual cross-section k of the ends of the wedge-shaped separated pins that face each other should remain for the subsequent chain welding process as well as the angle (aperture angle) of the notch, whose input field is in 4 recognizable by the " sign.
  • the control system calculates the pin length from the geometry data and uses this to determine the positions of various processing stations on the machine bed, such as the position of the notching device, and the axis movements, such as the infeed movement required for the calculated pin length.
  • the calculated axis movements take place according to a pre-configured sequence stored in the controller, which describes the functional sequence of the machine for setting up and producing the chain.
  • the positions of the processing stations are displayed to the operator and must be set manually by him. In other embodiments it is provided that the work stations are positioned by their own positioning drives.
  • the tool geometries of the tools to be used by the operator are then calculated from the input data and the design rules for the tools stored in the control. This applies, for example, to the infeed rollers of the infeed devices 910, 920, sometimes to the straightening rollers of the straightening unit 915, possibly to a stamping tool, to embossing plates in the function group for spine bending, to notching knives of the notching device 940, for cutting bushes and counter holders in the cutting station 950, for transport jaws for transporting the tiller, for the bending mandrel and a holding mandrel as well as for the bending rollers. Differing dimensions of these tools can be adjusted by the operator and are taken into account in the calculations.
  • the bending paths are calculated. These can be influenced by the operator, for example to correct the elastic deflection.
  • the electronic cam discs for the individual axes are generated based on the bending paths.
  • the term "cam plate" is understood here to mean a clear assignment between a master drive and a slave drive.
  • An electronic cam disk can exist, for example, in the form of a support point table with reference position values for the slave drive in relation to the course over time, ie in the form of a path-time diagram for the slave drive.
  • a virtual cam is generated for each side of the bending station (left and right sub-unit) of the bending unit.
  • the X and Y axis movements required to generate the bending path are calculated and coupled to the virtual cam disk.
  • the calculation is preferably carried out under the boundary condition that the point of application between the tool (bending roller) and the workpiece (wire or wire pin) remains unchanged during the bending operation, so that there is no relative movement between the bending tool and the wire and optimal force ratios are present in every phase of the bending operation . This allows an optimized protection of the wire material even with high forces.
  • This path-controlled bending process can be used within the working range of the chain bending machine with the same mechanical equipment of the chain bending machine for numerous different chain link geometries.
  • a format change ie a change to a different chain link geometry
  • the other components of the bending unit, in particular the cam discs do not have to be changed.
  • This makes the number possible Interchangeable components are reduced to a minimum, so that assembly times, set-up times and adjustment times can be significantly reduced compared to conventional solutions.
  • there is a great deal of freedom with regard to the shape of the chain link since the bending rollers can be guided around the bending mandrel on almost any path.
  • the straight tiller is first pre-bent in a U-shape, then a first leg is bent and then the second leg is bent.
  • the exemplary embodiments show the processing of round wire, i.e. wire with a circular cross-section.
  • wires with a different cross-section profile can also be processed, e.g. with a D profile.
  • some or all of the tools that come into contact with the workpiece must be designed accordingly.
  • the chain bender 200 is equipped with a monitoring system for monitoring the operation of the chain bender and for detecting malfunctions.
  • the monitoring system preferably includes a drive monitoring subsystem, which can identify and display fault-related overload situations.
  • the drive monitoring subsystem is designed to record the motor torque curves over time for the individual machine drives of the machine axes. With the help of adjustable envelope curves, overloading of the machine and tools, caused, for example, by material breakage and/or tool breakage or by collisions during setup, can be detected and prevented.
  • the monitoring system may be designed to automatically stop operation of the plant when a significant overload problem is detected by the drive monitoring subsystem. It is specified at which drive the excessive machine torque that caused the shutdown occurred, so that an operator can quickly determine the more precise cause of the malfunction and eliminate it, for example, by replacing a worn tool.
  • the monitoring system of the chain bender 200 also includes a sub-system for monitoring the notch depth of the notches created by the notching device 940 .
  • Broken or worn scoring blades can result in insufficiently deep scores, which subsequently cause chain welding problems. By the time this is noticed in the process, several meters of chain can have been produced, which are then considered scrap. With a notch depth monitoring subsystem, developing problems in the area of the cause can be identified in time.
  • an optical measurement of the notch point using the 945 camera is provided for this purpose.
  • a system for determining the force that is required when shearing off the wire pin can also be provided.
  • a notch depth that is too small increases the required shearing force.
  • monitoring the motor torque for the machine axis that drives the shear assembly 950 may indicate under-scoring problems with the scoring assembly 940.
  • the shearing force can be determined on the shearing device 950, for example via the required drive torque or via a separate force sensor.
  • a monitoring system for a chain bending machine can also be advantageous, independently of the other features of the chain bending machine explained by way of example, in other chain bending machines, for example in those whose bending station is designed differently than in the exemplary embodiment in FIG 1 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Wire Processing (AREA)
EP21199099.9A 2020-10-02 2021-09-27 Machine à plier les chaînes permettant de fabriquer une chaîne Active EP3978159B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102020212482.5A DE102020212482A1 (de) 2020-10-02 2020-10-02 Kettenbiegemaschine zum Herstellen einer Kette

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EP3978159A2 true EP3978159A2 (fr) 2022-04-06
EP3978159A3 EP3978159A3 (fr) 2022-07-06
EP3978159C0 EP3978159C0 (fr) 2025-02-12
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Cited By (1)

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CN119055975A (zh) * 2024-11-07 2024-12-03 中玖闪光医疗科技有限公司 一种电子凸轮控制的准直器系统及控制方法、电子设备

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DE2028266A1 (de) 1970-06-09 1971-12-16 Wafios Maschinen Wagner Vorrichtung zum Biegen von em teiligen Kettengliedern
DE2531290A1 (de) 1975-07-12 1977-01-27 Meyer Roth Pastor Maschf Verfahren zum biegen von kettengliedern und kettengliedbiegemaschine zur durchfuehrung des verfahrens

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DE1123891B (de) * 1957-06-24 1962-02-15 Meyer Roth Pastor Maschf Vorrichtung zum Biegen von einteiligen Kettengliedern
FR2184450B1 (fr) * 1972-05-17 1974-09-27 Ts Pro Ktno Kon
DE4214205A1 (de) 1992-04-30 1993-11-04 Happich Gmbh Gebr Vorrichtung zum biegen von profilleistenabschnitten o. dgl.
CN100496803C (zh) 2007-10-31 2009-06-10 王洪军 金属锻造圆环链自动串接编结方法及装置
CN101658896B (zh) * 2009-08-31 2011-01-05 王洪军 高强度金属圆环链无损伤自动弯链机构
DE102012220273B4 (de) 2012-11-07 2014-08-28 Wafios Ag Kettenbiegemaschine
CN103418738A (zh) * 2013-08-13 2013-12-04 江苏金茂制链有限公司 紧凑链一次定位弯曲成型接链方法
CN211276417U (zh) 2019-12-31 2020-08-18 河南启欧通用机械有限公司 一种全自动智能编链机成型机构

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DE2028266A1 (de) 1970-06-09 1971-12-16 Wafios Maschinen Wagner Vorrichtung zum Biegen von em teiligen Kettengliedern
DE2531290A1 (de) 1975-07-12 1977-01-27 Meyer Roth Pastor Maschf Verfahren zum biegen von kettengliedern und kettengliedbiegemaschine zur durchfuehrung des verfahrens

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Publication number Priority date Publication date Assignee Title
CN119055975A (zh) * 2024-11-07 2024-12-03 中玖闪光医疗科技有限公司 一种电子凸轮控制的准直器系统及控制方法、电子设备

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EP3978159C0 (fr) 2025-02-12
EP3978159A3 (fr) 2022-07-06
EP3978159B1 (fr) 2025-02-12
DE102020212482A1 (de) 2022-04-07

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