EP1842606B1 - Dispositif pour le cintrage en forme de boucles d'un fil continu - Google Patents

Dispositif pour le cintrage en forme de boucles d'un fil continu Download PDF

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Publication number
EP1842606B1
EP1842606B1 EP07006476A EP07006476A EP1842606B1 EP 1842606 B1 EP1842606 B1 EP 1842606B1 EP 07006476 A EP07006476 A EP 07006476A EP 07006476 A EP07006476 A EP 07006476A EP 1842606 B1 EP1842606 B1 EP 1842606B1
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EP
European Patent Office
Prior art keywords
wheel
pin
rotation
drive
loop
Prior art date
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Not-in-force
Application number
EP07006476A
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German (de)
English (en)
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EP1842606A1 (fr
Inventor
Hartmut Reusch
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Kugler Womako GmbH
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Kugler Womako GmbH
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Publication of EP1842606A1 publication Critical patent/EP1842606A1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21F—WORKING OR PROCESSING OF METAL WIRE
    • B21F45/00—Wire-working in the manufacture of other particular articles
    • B21F45/16—Wire-working in the manufacture of other particular articles of devices for fastening or securing purposes

Definitions

  • the invention relates to a device for looping a continuous wire to a wire comb with loop-shaped sections of substantially hairpin-shaped bent and adjacent tines and with the loop-shaped sections connecting, extending in the longitudinal direction of the wire comb and successively arranged wire sections, with two spaced apart and synchronous moving pin carriers, each carrying a number of consecutive pins in the direction of movement, wherein the rows of pins have substantially the same pitch, but the pins of the two rows of pins are offset in the direction of movement of the pin carrier against each other, with a rotatably mounted loop puller for loosely laying the wire successively alternately around a pin of a row of pins and a pin of the other row of pins and with a first drive means for rotatably driving the loop puller, According to the preamble of claim 1.
  • Such a device is known from US-A-4 047 544 known.
  • Wire combs of the aforementioned type are used in particular for binding of paper blocks by the wire combs after their preparation by a device of the aforementioned type in subsequent or downstream devices initially C-shaped pre-bent and divided into wire crest sections and then inserted and closed in the holes made in the area of one side edge of the paper blocks.
  • the first wheel is offset by a motor or other drive, which is part of the first drive means in a substantially constant rotation, while the output via the third wheel takes place, which is coupled to the axis of rotation of the rotatably mounted loop puller.
  • the coupling between the third gear of the planetary gear and the loop puller can take place either directly or via a corresponding dimensioned lower or transmission gear.
  • the first wheel forms the ring gear and the third wheel the sun gear of the planetary gear; Alternatively, it is also possible to provide the third wheel as a ring gear and the first wheel as a sun gear.
  • the drive via the ring gear or sun gear (first wheel) and the output via the sun gear or ring gear (third wheel).
  • the transmission of the drive power between the ring gear and the sun takes place via the at least one planetary gear (second wheel), which is mounted on the planet carrier.
  • This measure according to the invention now allows, in a structurally particularly clever manner, optimum adjustment of the desired movement sequence of the loop puller in relation to the movement of the pin carriers. This optimally achieves a smooth transition from the loop puller to the relevant pin of one of the two pin carriers.
  • the planetary gear according to the invention can be set for each format to the optimum operating point substantially.
  • the planetary gear according to the invention forms an automatic positive control for the movement of the loop puller.
  • This has the advantage that a simple, constant-working drive motor can be used as the drive, which is characterized by a simple construction and thus low production costs and an additional complex control is not required.
  • located in the planetary gear according to the invention large portions of the mass moment of inertia in constant relative motion and thus serve as a kind of energy storage for the impressed movement of the loop puller, which supports the control effect in terms of its movement in a clever and thus advantageous manner.
  • the invention thus provides a structurally skillful and at the same time cost-effective way to realize the desired movement with simultaneous optimal adaptation to the selected format for the impressed movement of the loop puller.
  • the drive pivots the planetary carrier reciprocally over a limited angular range, wherein the angular range and / or the angular velocity of the planet carrier are adjustable to match the rotation of the loop puller on the speed of the pins of the pin carrier and thus to find the optimum operating point.
  • the loop puller is provided with at least one bending mandrel arranged at a radial distance from its axis of rotation, which engages behind the wire for looping
  • the angular range and / or the angular velocity of the planet carrier should be adjustable such that the speed of the at least one bending mandrel of the loop puller is adjusted to the speed the pins of the pin carrier can be adjusted.
  • the angular range and / or the angular velocity of the planet gear carrier should be adjusted so that the angular velocity of the third wheel driving the loop puller is minimized in at least one defined angular position, preferably zero, is reduced.
  • the reduction of the angular velocity of the loop puller or its standstill at certain angular positions is achieved by a corresponding adjustment of the angular range and / or the angular velocity.
  • the planetary gear according to the invention can be set to the optimum operating point for each format.
  • the pin holders must also be added be replaced.
  • the distance between the two pin carriers must be adjusted accordingly.
  • an adjustment of the reciprocal pivotal movement of the planet carrier allows adaptation during operation. Due to the specific adjustability of angular velocity and / or angular range, it is possible in the transfer area, the speed of the bending cams of the loop puller in direct. Adjusting the speed of the pen pins.
  • the first wheel should be a ring gear
  • the third wheel be designed as a sun gear within the ring gear and the at least one second wheel between the first and the third wheel are.
  • the wheels of the planetary gear should consist of gears. If the first wheel is provided as a ring gear and the third wheel as a sun gear, the first wheel on its inner circumference on an internal toothing and are provided as planetary at least one second wheel and the third wheel each provided at its periphery with an external toothing.
  • gears is in principle not absolutely necessary, but it is also conceivable to provide corresponding friction wheels.
  • a further preferred embodiment is characterized in that the first drive means comprises a rotatably mounted pinion, which is in engagement with the first wheel and whose axis of rotation is substantially parallel to the axis of rotation of the first wheel, and a drive which rotates the pinion added.
  • the pinion can be in engagement with the outer circumference of the first wheel;
  • the first wheel may be provided on its outer circumference with an external toothing and the pinion a Have sprocket, which is in engagement with the external teeth of the first wheel.
  • the drive of the pinion should preferably be formed by the drive of the first drive means, so that this drive not only pivots the planet carrier, but also simultaneously sets the pinion in rotation.
  • a further preferred embodiment is characterized in that the first drive means comprises a lifting rod, which is articulated at one end to the planet carrier at a radial distance from its axis of rotation, and the servo drive the reciprocating rod in the longitudinal direction in reciprocal movements.
  • a lifting rod forms a structurally simple way to subject the planet carrier according to the invention a reciprocal pivoting.
  • the first drive device has an eccentric, which is rotatably mounted about an axis of rotation and to which the other end of the lifting rod is articulated at a radial distance from this axis of rotation, and the drive moves the eccentric in constant rotation about its axis of rotation.
  • the axis of rotation of the eccentric is substantially parallel to the axis of rotation of the first and third wheels of the planetary gear.
  • the drive not only pivots the planet carrier, but also simultaneously sets the pinion in rotation according to the above-described embodiment, should for a common drive of the pinion and the eccentric servo drive with the pinion and the eccentric, preferably via a gear and / or a revolving endless belt, be mechanically coupled.
  • the rotational speed of the eccentric For adjusting the angular range of the pivoting movement of the planet carrier and thus the stroke of the lifting rod of the radial distance of the articulation of the lifting rod of the axis of rotation of the eccentric and / or for adjusting the angular velocity of the planet carrier and thus the lifting speed of the lifting rod, the rotational speed of the eccentric should be changed accordingly be.
  • a further preferred embodiment may be provided as a pin carrier two juxtaposed, spaced apart and synchronously moving pin wheels, which have substantially the same diameter and on the circumference radially outwardly extending pins are arranged in a row, the pin rows substantially have the same pitch, but the pins of the two rows of pins are offset in the direction of rotation of the pin wheels against each other and wherein the axes of rotation of the two pin wheels are arranged at an angle to each other.
  • a first drive means is provided for driving the loop puller and a second drive means is provided for driving the two pin wheels.
  • means for rotationally fixed coupling of the axes of rotation of the two pin wheels are provided to ensure the synchronous operation of the two pin wheels safely in a structurally simple manner.
  • the second drive means should only drive the axis of rotation of one of the two pin wheels and should the axes of rotation of both pin wheels form a common kink axis, whereby the coupling means is formed by the angled connection portion of the kink axis.
  • the coupling means consists of a flexurally elastic, torsionally rigid intermediate piece.
  • the second drive means comprises two drive motors, of which one drive motor drives the axis of rotation of one pin wheel and the other drive motor drives the axis of rotation of the other pin wheel, and a control device is provided which the two drive motors so controls that they act together in the manner of a common electric wave, whereby the coupling means is formed by the control device.
  • the second drive device for driving the two pinion wheels can be coupled to the first drive device for driving the loop puller via a common control device, wherein such a control device can preferably be an electric cycle shaft.
  • the angular arrangement of the axes of rotation of both pin wheels is adjustable to each other, which compared to the prior art advantageously leads to a simple setting and quick change of format parts.
  • the setting of different angles of the axes of rotation to each other is done with known adjusting means such as manually or motor-driven threaded spindles, linear drives or the like ..
  • the second drive means has only one drive motor which drives the axes of rotation of only one of the two pin wheels, should preferably only the axis of rotation of the removed from such a drive motor pin wheel be made adjustable, resulting in a structurally particularly simple solution.
  • At least one stripper is provided, which according to a further preferred embodiment of the invention is designed as a rotatably mounted, substantially circular disk which along its circumference with a Control cam is provided, which has at least one protruding portion which comes into abutment with the curved edge portion on the loop puller and presses this with continued rotation of the disc from the loop puller on a pin of a pin carrier.
  • This design provides a particularly simple but effective construction for forming a scraper whose angular velocity and / or angular position relative to the loop puller need only be adjusted accordingly for the scraper to operate effectively.
  • the rotary drive of the scraper with the servo drive for reciprocal pivoting of the planet carrier should be synchronized so that the projecting portion of the control cam with a bent wire section on the loop puller comes into abutment and presses it from the loop puller on a pin of a pin carrier when the angular velocity of third wheel of the planetary gear reaches its minimum.
  • the scraper is designed as a cup wheel, the axially projecting edge of the control cam forms the at least one projecting portion.
  • Another particularly simple construction is characterized in that the scraper is designed as a swash plate whose peripheral edge due to the wobbling movement has the effect of the control cam and thus forms them.
  • the scraper is designed as a swash plate whose peripheral edge due to the wobbling movement has the effect of the control cam and thus forms them.
  • the scraper if more than once per revolution of the scraper whose stripping action is required, provided as a swash plate scraper must be driven at a higher speed than the loop puller, which then, for example, with the help of a corresponding transmission gear or a separate drive can be realized.
  • the axis of rotation of the scraper should be arranged substantially parallel to the axis of rotation of the loop puller.
  • a synchronous drive to the loop puller can be realized in particular by the fact that the first drive device drives not only the loop puller but also the stripper in that the first drive device sets the stripper in a substantially continuous rotation.
  • a separate wiper may be provided.
  • FIGS. 1 and 2 are shown schematically in perspective and partially in sections, the important for the loop-shaped bending of a continuous wire components of a not shown in the figures as a whole wire bending machine for a better understanding of the wire bending process.
  • two juxtaposed and spaced pin wheels 2, 4 are provided which have the same diameter and on the circumference of radially outwardly extending pins 6 and 8 in are arranged in a row, wherein the pin rows of both pin wheels 2, 4 have the same pitch, but the pins 6, 8 of the two rows of pins in the direction of rotation of the pin wheels 2, 4 are offset from each other.
  • pins 6 of the first pin wheel 2 in the circumferential direction have a shorter width than the pins 8 of the second pin wheel 4 and thus the distance between the pins 6 of the first pin wheel 2 is greater than the distance between the pins 8 of the second pin wheel 4.
  • This different shape of the pins 6, 8 is determined in the illustrated embodiment by the desired shape of the wire 10 to be bent. However, depending on the desired shape of the wire to be bent and any other shape of the pins 8, 6 conceivable.
  • pin wheels can be used in which the width of the pins and / or the distances between the pins in the circumferential direction are equal.
  • the pins 6, 8 of the pin wheels 2, 4 have the task of forming a continuous wire 10 into a wire comb having looped sections of substantially hairpin-shaped bent and adjacent tines and wire sections connecting the looped sections and arranged one behind the other, which extend in the longitudinal direction of the wire comb thus formed in accordance with the circumferential or rotational direction of the pin wheels 2, 4.
  • a rotatably mounted loop puller 12 For mounting the wire 10 on the pins 6, 8, a rotatably mounted loop puller 12 is provided, which has an axis of rotation 14 which is coupled to a later described in detail in the drive device, whereby the loop puller 12 is set in rotation.
  • the loop puller 12 is provided in the illustrated embodiment with two diametrically arranged arms 16, 18, wherein on the first arm 16, a first bending cam 20 and on the second arm 18, a second bending cam 22 is seated.
  • the loop puller 12 is positioned adjacent to the circumference of the two pin wheels 2, 4, the bending pins 20, 22 being directed towards the circumference of the pin wheels 2, 4.
  • the axis 14 of the loop puller 12 is directed approximately radially with respect to the pin wheels 2, 4.
  • loop puller 12 is provided with a central head 19 which is directed to the pins 8 of the second pin wheel 4.
  • the loop puller is in the illustrated embodiment, not only rotatable about the axis 14, but also reciprocally mounted in the axial direction by a drive, not shown in the figures, so that the head 19 can be brought in each case to two adjacent pins 8 of the second pin wheel 4, to substantially close the gap between these two pins 8 to receive a portion of the wire 10.
  • a scraper 24 Adjacent to the circumference of the first pin wheel 2 and the loop puller 12, a scraper 24 is arranged, which is formed in the illustrated embodiment as rotatably mounted and driven pulley whose axis of rotation 25 is approximately parallel to the axis 14 of the loop puller 12.
  • the shape of the scraper 24 will be explained in more detail later in the description.
  • the loop puller 12 For forming the wire comb from the continuously tracking wire 10, the loop puller 12 is moved toward the second pin wheel 4 so that the head 19 of the loop puller 12 presses the wire 10 into a gap between two adjacent pins 8. At the same time, the first bending cam 20 engages behind the wire 10 at an overlying location. This operating state is in FIG. 1a shown.
  • the first bending cam 20 takes the wire 10 with it, whereby the bending process begins. This is FIG. 1b shown.
  • Figure 1c indicates that the bending process is almost completed after the first bending cam 20 almost a semicircle movement relative to the state of FIG. 1 a completed.
  • the first bending cam 20 reaches one opposite its position FIG. 1 a pivoted position by 180 °, a transfer of bent from the first bending cam 20 wire section takes place on a corresponding pin 6 of the first pin wheel 2.
  • the wiper 24 is used, which presses the bent wire section from the first bending cam 20 on the corresponding pin 6.
  • this transfer is in relation to the second bending cam in FIG. 1a recognizable.
  • the second bending cam 22 engages behind the continuously tracked wire 10 at the same location as the first bending cam 20 according to FIG FIG. 1 a.
  • the loop puller 12 For the transfer of the bent portion of the wire 10 and the thus formed wire loop of one of the bending cams 20, 22 on a pen 6 of the first pin wheel 2 ready for this purpose, the loop puller 12 must be braked and thus its rotational speed must be significantly reduced, up to at best a brief stop before then the loop puller 12 is accelerated again. Since in the illustrated embodiment, the loop puller 12 operates with two diametrically opposed bending cams 20, 22, this start-stop operation takes place twice during one revolution of the loop puller 12.
  • FIG. 2 can recognize, run the bending cams 20, 22 due to the rotation of the loop puller 12 on a circular path whose radius corresponds approximately to the distance between the two pin wheels 2, 4.
  • the axes of rotation 26, 28 of the pin wheels 2, 4 are at a small angle ⁇ to each other, although in the FIGS. 1 and 2 not recognizable, however in FIG. 3 is shown schematically, in which for reasons of clarity over the FIGS. 1 and 2 the loop puller 12 and the scraper 24 are omitted.
  • This has the consequence that with continued rotation, the distance between the pins 6, 8 initially becomes larger, whereby the laid on the pins 6, 8 wire comb is stretched and the wire comb finally obtains its predetermined shape. Subsequently, the distance between the pins 6, 8 again smaller, resulting in a low-friction decrease of the thus formed wire comb from the pins 6, 8 to feed the wire comb for further processing.
  • FIG. 3 is the angle ⁇ with respect to the pin wheel 2 slightly inclined position of the pin wheel 4 is shown schematically as a dotted line.
  • the loop puller 12 is driven by a continuously operating first servomotor 30, which is schematically illustrated in FIG FIG. 4 is shown.
  • a planetary gear 32 is connected, which not only in FIG. 4 but also in the Figures 5 and 6 is shown recognizable.
  • FIG. 4 drives the first servo motor 30 a schematically illustrated pulley 33, on which runs an also schematically illustrated endless belt 34, which transmits the rotation of a rotatably mounted pinion 36 by this with a likewise in FIG. 4 is schematically shown pulley 38 is provided, over which the endless belt 34 runs.
  • the axis of rotation 37 of the pinion 36 extends approximately parallel to the axis 14 of the loop puller 12.
  • the pinion 36 drives the planetary gear 32.
  • the pinion 36 is provided with an outer ring gear 40 which meshes with an outer ring gear 42 of a ring gear 44, which is part of the planetary gear 32.
  • the ring gear 44 also has an internal gear ring 46, which meshes with planetary gears 48 designed as gear wheels.
  • the planet gears 48 which are also part of the planetary gear, are rotatably mounted on a Planeteradong 50 and mesh with the outer ring gear of a likewise designed as a gear and rotatably mounted sun gear 52, the axis of rotation 53 coincides with the axis of rotation of the ring gear 44 and the common central axis of rotation Planetary gear 32 forms.
  • the sun gear 52 which is also part of the planetary gear 32, forms the output for transmission a rotational movement on the loop puller 12 and is therefore in the illustrated embodiment coaxial and rotationally fixed to the axis 14 of the loop puller 12 directly connected.
  • this direct coupling is alternatively also the arrangement of a lower or a transmission gear between the sun gear 52 of the planetary gear 32 and the axis 14 of the loop puller 12 conceivable.
  • the drive via the ring gear 42 and the output via the sun gear 52 In principle, however, it is also conceivable to provide the drive via the sun gear and the output via the ring gear. In any case, while the transmission of the drive power between the ring gear 44 and the sun gear 52 takes place via the planetary gears 48, which are rotatably mounted on the planet carrier 50.
  • the planet carrier 50 is fixed in the conventional manner of such operation of a planetary gear, in the present case deviates from this known principle by the planetary gear 50 is not fixed, but is pivotally mounted about a rotation axis 53, which yes the central axis of rotation of the planetary gear 32 forms about which the ring gear 44 and the sun gear 52 are rotatably mounted.
  • the planet carrier 50 is reciprocally pivotable about the axis of rotation 53 over a limited angular range.
  • a lifting rod 56 is articulated at its one end on the planet carrier 50 via a pivot pin 54 arranged at a radial distance from the axis of rotation 53.
  • the lifting rod 56 is articulated via a pivot pin 58 eccentrically to a rotary shaft 60, so that the pivot pin 58 is arranged at a radial distance from the axis of rotation 61 of the rotary shaft 60. Because of the eccentric bearing of the pivot pin 58, the rotary shaft 60 together with the pivot pin 58, the effect of an eccentric and thus can be referred to together as the eccentric component formed by the pivot pin 58 and the rotary shaft 60 component.
  • Coaxially and rotatably coupled to the rotary shaft 60 is an in FIG. 4 only schematically illustrated pulley 62, via which of the first servomotor 30th driven endless belt 34 is also guided.
  • the first servo motor 30 serves not only to drive the pinion 36 and thus the planetary gear 32, but at the same time to drive the rotary shaft 60.
  • the lifting rod 56 Due to the eccentric arrangement of the pivot 58, the lifting rod 56 performs reciprocal lifting movements according to the in the Figures 5 and 6 shown double arrow. As a result, the lifting rod 56 is moved in the manner of a connecting rod.
  • the reciprocal lifting movement in turn leads by the articulation of the lifting rod 56 via the pivot pin 54 on the planet carrier 50 to a reciprocal pivoting of the planet carrier 50 over a limited angular range.
  • the eccentric bearing of the pivot pin 58 and the rotational speed of the pivot shaft 58 supporting rotary shaft 60 should be dimensioned in the present embodiment so that in each case after a 180 ° rotation of the loop puller 12 briefly reaches its minimum rotational or angular velocity in certain application cases can also be zero, and as described above, in an angular position, which allows the transfer of a bent wire portion of one of its bending cams 20, 22 on a corresponding pin 6. Previously, the loop puller 12 must be braked accordingly and then accelerated again.
  • the eccentric stroke ie the length of the stroke of the lifting rod 56 can be adjusted.
  • Such adjustability of the eccentric stroke makes it possible, in the stationary region of the loop puller 12, to set the speed of the bending cams 20, 22 exactly in accordance with the speed of the pins 6, 8 to the circumference of the constantly rotating pinwheels 2, 4.
  • the planetary gear 32 can be set to the optimum operating point substantially for each format.
  • the pin wheels 2, 4 must be replaced, especially if a different pitch of the pins 6, 8 is required.
  • the distance between the two pinwheels 2, 4 should be variable in order to adjust different widths for the wire comb can.
  • different spacers can be used, which is not shown in the drawings.
  • the axes of rotation 26, 28 of the pin wheels 2, 4 at a small angle ⁇ inclined to each other.
  • This angle arrangement should be adjustable, which advantageously supports easy setting and rapid change of format parts.
  • the adjustment of the desired angle of the axes of rotation 26, 28 of the two pin wheels 2, 4 to each other with known adjusting means such as manually or motor-driven threaded spindles, linear drives or the like.
  • the axes of rotation 26, 28 of the two pin wheels 2, 4 may form a common bending axis.
  • a universal joint or a flexurally elastic, torsionally rigid intermediate piece which in FIG. 3 is shown schematically as a dot-dashed element.
  • FIG. 3 furthermore schematically can be seen, in the illustrated embodiment, only the rotation axis 28 of the remote from the second servomotor 64 pin wheel 4 made adjustable.
  • angle encoders should have at least one absolute value transmitter for the sun gear 52. Absolute encoders have the advantage, in particular for the device described here, that after a power failure, the positions of the drives are further stored and thus known.
  • the scraper 24 is formed as a rotatably mounted about a rotation axis 25 disc.
  • the scraper 24 has a control cam 66 which is provided with a protruding portion 66 a.
  • This projecting portion 66a of the cam 66 comes with continued rotation of the disc-shaped scraper 24 in abutment with that of a bending cam (as shown in FIG. 7 it is the bending cam 20) of the loop puller 12 held, a wire loop forming bent portion of the wire 10 and presses this bent portion of the wire 10 via a standing pin 6 of the first pin wheel 2.
  • the transfer takes place twice during a 360 ° rotation, namely at an angular distance of 180 °, the control cam 66 of the wiper 24 must have two projecting portions 66a at an angular distance of 180 °.
  • the scraper 24 is designed as a cup wheel, which has in the axial direction projecting edge on the pin wheel 2 and the cam 66 forms.
  • the loop puller 12 and the scraper 24 rotate synchronously with each other.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Retarders (AREA)
  • Wire Processing (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)

Claims (28)

  1. Dispositif pour le cintrage en forme de boucles d'un fil métallique (10) continu pour former un peigne de fil comportant des portions en forme de boucles formées de dents recourbées sensiblement en forme d'épingles à cheveux et placées côte à côte, et des portions de fil reliant les portions en forme de boucles, s'étendant dans la direction longitudinale du peigne de fil et disposées successivement,
    comprenant
    deux porte-ergots (2, 4) mutuellement distants et déplacés l'un par rapport à l'autre de manière synchrone, portant chacun une rangée d'ergots (6, 8) disposés successivement dans la direction de déplacement, les rangées d'ergots ayant sensiblement le même pas, les ergots (6, 8) des deux rangées d'ergots étant, cependant, décalés entre eux dans la direction de déplacement des porte-ergots (2, 4),
    un boucleur (12) monté à rotation pour la pose, en forme de boucles, du fil (10) de manière successivement alternée autour d'un ergot (6) de l'une des rangées d'ergots et d'un ergot (8) de l'autre rangée d'ergots, et
    un premier dispositif d'entraînement pour l'entraînement en rotation du boucleur (12),
    caractérisé en ce que le premier dispositif d'entraînement présente
    un engrenage planétaire (32) comprenant une première roue (44) entraînée de manière sensiblement constante, au moins une deuxième roue (48) engrenant avec la première roue (44) et montée à rotation en tant que satellite sur un porte-satellites (50) et une troisième roue (52) montée à rotation coaxialement à la première roue (44), engrenant avec ladite au moins deuxième roue (48) et entraînant en rotation le boucleur (12),
    le porte-satellites (50) étant monté à rotation autour d'un axe de rotation (53) disposé coaxialement à la première et à la troisième roue (44, 52), et
    un mécanisme d'entraînement (30) pour le pivotement réciproque du porte-satellites (50).
  2. Dispositif selon la revendication 1,
    caractérisé en ce que le mécanisme d'entraînement (30) fait pivoter réciproquement le porte-satellites (50) sur une plage angulaire limitée, la plage angulaire et/ou la vitesse angulaire du porte-satellites (50) étant réglables pour aligner la rotation du boucleur (12) sur la vitesse des ergots (6, 8) des porte-ergots (2, 4).
  3. Dispositif selon la revendication 2, dans lequel le boucleur (12) est doté d'au moins un mandrin de cintrage (20, 22) radialement écarté de son axe de rotation (14) et venant en prise derrière le fil (10) pour la pose en forme de boucles,
    caractérisé en ce que la plage angulaire et/ou la vitesse angulaire du porte-satellites (50) sont réglables de façon que la vitesse dudit au moins un mandrin de cintrage (20, 22) du boucleur (12) puisse être alignée sur la vitesse des ergots (6, 8) des porte-ergots (2, 4).
  4. Dispositif selon la revendication 2 ou 3,
    caractérisé en ce que la plage angulaire et/ou la vitesse angulaire du porte-satellites (50) sont réglables de façon que la vitesse angulaire de la troisième roue (52) dans au moins une position angulaire définie soit réduite à un minimum, de préférence zéro.
  5. Dispositif selon au moins l'une des revendications précédentes,
    caractérisé en ce que la première roue (44) est une roue creuse, la troisième roue (52) est agencée en tant que pignon solaire à l'intérieur de la roue creuse et ladite au moins deuxième roue (48) est située entre la première et la troisième roue (44, 52).
  6. Dispositif selon au moins l'une des revendications précédentes,
    caractérisé en ce que les roues (44, 48, 52) de l'engrenage planétaire (32) sont des roues dentées.
  7. Dispositif selon les revendications 5 et 6,
    caractérisé en ce que la première roue (44) présente, sur sa périphérie intérieure, une denture intérieure (46), et ladite au moins deuxième roue (48) et la troisième roue (52) portent respectivement sur leur périphérie une denture extérieure.
  8. Dispositif selon au moins l'une des revendications précédentes,
    caractérisé en ce que le premier dispositif d'entraînement présente un pignon (36) monté à rotation qui engrène avec la première roue (44) et dont l'axe de rotation (37) est sensiblement parallèle à l'axe de rotation (53) de la première roue (44), et un mécanisme d'entraînement (30) qui met le pignon (36) en rotation.
  9. Dispositif selon la revendication 8,
    caractérisé en ce que le pignon (36) engrène avec le pourtour extérieur de la première roue (44),
  10. Dispositif selon la revendication 9,
    caractérisé en ce que la première roue (44) porte, sur sa périphérie extérieure, une denture extérieure (42) et que le pignon (36) présente une couronne dentée (40) engrenant avec la denture extérieure (42) de la première roue (44).
  11. Dispositif selon au moins l'une des revendications 8 à 10,
    caractérisé en ce que l'entraînement du pignon (36) est formé par le mécanisme d'entraînement (30).
  12. Dispositif selon au moins l'une des revendications précédentes,
    caractérisé en ce que le premier dispositif d'entraînement présente une tige de levage (56) qui est articulée, en l'une de ses extrémités, au porte-satellites (50) à une distance radiale par rapport à son axe de rotation (53), et en ce que le mécanisme d'entraînement (30) entraîne la tige de levage (56) dans des mouvements réciproques dans la direction longitudinale de celle-ci.
  13. Dispositif selon la revendication 12,
    caractérisé en ce que le premier dispositif d'entraînement présente un excentrique (58, 60) qui est monté à rotation autour d'un axe de rotation (61) et sur lequel est articulée l'autre extrémité de la tige de levage (56) à une distance radiale de cet axe de rotation (61), et en ce que le mécanisme d'entraînement (30) met l'excentrique (58, 60) en rotation constante autour de son axe de rotation.
  14. Dispositif selon la revendication 13,
    caractérisé en ce que l'axe de rotation (61) de l'excentrique (58, 60) s'étend de manière sensiblement parallèle à l'axe de rotation (53) de la première et de la troisième roue (44, 52).
  15. Dispositif selon les revendications 11 et 14,
    caractérisé en ce que, pour un entraînement commun du pignon (36) et de l'excentrique (58, 60), le mécanisme d'entraînement (30) est couplé mécaniquement au pignon (36) et à l'excentrique (58, 60), de préférence par l'intermédiaire d'un réducteur et/ou d'une courroie sans fin (34) en mouvement.
  16. Dispositif selon au moins l'une des revendications 2 à 4, ainsi que selon au moins l'une des revendications 13 à 15,
    caractérisé en ce que, pour le réglage de la plage angulaire du mouvement de pivotement du porte-satellites (50), la distance radiale de l'articulation de la tige de levage (56) par rapport à l'axe de rotation (61) de l'excentrique (58, 60), et/ou pour le réglage de la vitesse angulaire du porte-satellites (50), la vitesse de rotation de l'excentrique (58, 60) est variable de manière correspondante.
  17. Dispositif pour le cintrage en forme de boucles d'un fil métallique (10) continu pour former un peigne de fil comportant des portions en forme de boucles formées de dents recourbées sensiblement en forme d'épingles à cheveux et placées côte à côte, et des portions de fil reliant les portions en forme de boucles, s'étendant dans la direction longitudinale du peigne de fil et disposées successivement, en particulier selon au moins l'une des revendications précédentes,
    comprenant
    deux roues à ergots (2, 4) situées côte à côte, mutuellement distantes et déplacées l'une par rapport à l'autre de manière synchrone, qui présentent sensiblement le même diamètre et sur le pourtour desquelles sont disposés, sur une rangée, des ergots (6, 8) s'étendant radialement vers l'extérieur, les rangées d'ergots ayant sensiblement le même pas, les ergots (6, 8) des deux rangées d'ergots étant, cependant, décalés les uns par rapport aux autres dans le sens de rotation des roues à ergots (2, 4), et les axes de rotation (26, 28) des deux roues à ergots (2, 4) étant disposés en formant entre eux un angle,
    un boucleur (12) pour la pose, en forme de boucles, du fil (10) de manière successivement alternée autour d'un ergot (6) de l'une des rangées d'ergots et d'un ergot (8) de l'autre rangée d'ergots, et
    un premier dispositif d'entraînement pour l'entraînement du boucleur (12), et
    un deuxième dispositif d'entraînement (64) pour l'entraînement des deux roues à ergots (2, 4),
    caractérisé par un moyen (65) pour le couplage solidaire en rotation des axes de rotation (26, 28) des deux roues à ergots.
  18. Dispositif selon la revendication 17,
    caractérisé en ce que le deuxième dispositif d'entraînement (64) n'entraîne que l'axe de rotation de l'une des deux roues à ergots (2) et les axes de rotation (26, 28) des deux roues à ergots (2, 4) forment un axe d'articulation commun, le moyen d'accouplement étant alors formé par la partie de liaison coudée de l'axe d'articulation.
  19. Dispositif selon la revendication 17,
    caractérisé en ce que le deuxième dispositif d'entraînement (64) n'entraîne que l'axe de rotation (26) de l'une des roues à ergots (2, 4) et le moyen d'accouplement (65) consiste en un joint de Cardan.
  20. Dispositif selon la revendication 17,
    caractérisé en ce que le deuxième dispositif d'entraînement (64) n'entraîne que l'axe de rotation (26) de l'une des roues à ergots (2) et le moyen d'accouplement (65) consiste en une pièce intermédiaire élastique en flexion et rigide à la torsion.
  21. Dispositif selon la revendication 17,
    caractérisé en ce que le deuxième dispositif d'entraînement présente deux moteurs d'entraînement, dont l'un des moteurs d'entraînement entraîne l'axe de rotation de l'une des roues à ergots et l'autre moteur d'entraînement entraîne l'axe de rotation de l'autre roue à ergots, et en ce qu'est prévu un dispositif de commande qui commande les deux moteurs d'entraînement de telle façon qu'ils coopèrent à la manière d'un arbre électrique commun, le moyen d'accouplement étant alors formé par le dispositif de commande.
  22. Dispositif selon au moins l'une des revendications 17 à 21, caractérisé en ce que l'agencement angulaire des axes de rotation (26, 28) des deux roues à ergots (2, 4) est réglable.
  23. Dispositif selon au moins l'une des revendications précédentes,
    comprenant au moins un dévêtisseur (24) pour transférer une portion de fil cintré du boucleur (12) sur un ergot (6) de l'un des deux porte-ergots (2),
    caractérisé en ce que le dévêtisseur (24) est conçu sous forme de disque sensiblement circulaire monté à rotation qui, le long de sa périphérie, est pourvu d'une came (66) qui présente au moins une partie en saillie (66a), laquelle vient en appui sur la portion de fil cintré sur le boucleur (12) et presse celle-ci, lors de la rotation continue du disque, du boucleur (12) sur un ergot (6) d'un porte-ergots (2).
  24. Dispositif selon au moins l'une des revendications 2 à 4, ainsi que selon la revendication 23,
    caractérisé en ce que l'entraînement en rotation du dévêtisseur (24) est synchronisé avec le mécanisme d'entraînement (30) pour le pivotement réciproque du porte-satellites (50) de façon telle que ladite au moins une partie en saillie (66a) de la came (66) vient en appui sur une portion de fil cintré sur le boucleur (12) et presse celle-ci du boucleur (12) sur un ergot (6) d'un porte-ergots (2), lorsque la vitesse angulaire de la troisième roue (52) de l'engrenage planétaire (32) atteint son minimum.
  25. Dispositif selon la revendication 23 ou 24,
    caractérisé en ce que le dévêtisseur (24) est conçu en tant que meule forme coupelle dont le bord convexe en direction axiale forme la came (66).
  26. Dispositif selon au moins l'une des revendications 23 à 25, caractérisé en ce que le dévêtisseur est conçu sous forme de plateau oscillant.
  27. Dispositif selon au moins l'une des revendications 23 à 26, caractérisé en ce que l'axe de rotation (25) du dévêtisseur (24) est disposé de façon sensiblement parallèle à l'axe de rotation (14) du boucleur (12).
  28. Dispositif selon au moins l'une des revendications 23 à 27, caractérisé en ce que le premier dispositif d'entraînement entraîne le dévêtisseur (24) et met celui-ci en rotation sensiblement continue.
EP07006476A 2006-04-03 2007-03-29 Dispositif pour le cintrage en forme de boucles d'un fil continu Not-in-force EP1842606B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006015809A DE102006015809A1 (de) 2006-04-03 2006-04-03 Vorrichtung zum schleifenförmigen Biegen eines fortlaufenden Drahtes

Publications (2)

Publication Number Publication Date
EP1842606A1 EP1842606A1 (fr) 2007-10-10
EP1842606B1 true EP1842606B1 (fr) 2010-06-30

Family

ID=38057307

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Application Number Title Priority Date Filing Date
EP07006476A Not-in-force EP1842606B1 (fr) 2006-04-03 2007-03-29 Dispositif pour le cintrage en forme de boucles d'un fil continu

Country Status (4)

Country Link
EP (1) EP1842606B1 (fr)
CN (1) CN100548529C (fr)
AT (1) ATE472382T1 (fr)
DE (2) DE102006015809A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008025663B3 (de) * 2008-05-28 2009-12-03 Kugler-Womako Gmbh Vorrichtung zum schleifenförmigen Biegen eines fortlaufenden Drahtes
DE102015122493B4 (de) 2015-12-22 2023-01-19 Karl Storz Se & Co. Kg Hilfsvorrichtung für das Bilden eines chirurgischen Knotens
CN111203496A (zh) * 2020-01-07 2020-05-29 储幸高 一种钢筋压弯时的省力压弯装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2003600A1 (fr) * 1969-05-05 1969-11-07 Liouville Roger
US3805579A (en) * 1970-05-15 1974-04-23 Mead Corp Wire forming method
US3691808A (en) * 1970-05-15 1972-09-19 Mead Corp Wire forming machine
US4047544A (en) * 1976-12-27 1977-09-13 The Mead Corporation Wire forming apparatus
DE2908223C2 (de) * 1979-03-02 1982-12-02 Bielomatik Leuze Gmbh + Co, 7442 Neuffen Verfahren und Vorrichtung zur Herstellung eines zick-zackförmigen Bandes aus Draht
US4373558A (en) * 1980-09-24 1983-02-15 Spiral Binding Company, Inc. Bookbinding wire stock production method and apparatus
DE3240341A1 (de) * 1981-11-14 1983-05-26 Womako Maschinenkonstruktionen GmbH, 7440 Nürtingen Vorrichtung zum schleifenfoermigen biegen eines fortlaufenden drahtes

Also Published As

Publication number Publication date
CN101077514A (zh) 2007-11-28
ATE472382T1 (de) 2010-07-15
CN100548529C (zh) 2009-10-14
EP1842606A1 (fr) 2007-10-10
DE102006015809A1 (de) 2007-10-04
DE502007004228D1 (de) 2010-08-12

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