EP0473739B1 - Device for straightening a wire - Google Patents

Device for straightening a wire Download PDF

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Publication number
EP0473739B1
EP0473739B1 EP91905046A EP91905046A EP0473739B1 EP 0473739 B1 EP0473739 B1 EP 0473739B1 EP 91905046 A EP91905046 A EP 91905046A EP 91905046 A EP91905046 A EP 91905046A EP 0473739 B1 EP0473739 B1 EP 0473739B1
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EP
European Patent Office
Prior art keywords
rotor
wire
jack
central guide
attached
Prior art date
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Expired - Lifetime
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EP91905046A
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German (de)
French (fr)
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EP0473739A1 (en
Inventor
Pierre-Louis Piguet
Peter Meier
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Esco SA
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Esco SA
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Priority to AT91905046T priority Critical patent/ATE90238T1/en
Publication of EP0473739A1 publication Critical patent/EP0473739A1/en
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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
    • B21F1/00—Bending wire other than coiling; Straightening wire
    • B21F1/02—Straightening

Definitions

  • the present invention relates to a device for dressing a rigid metal wire, in particular at the entrance to a machining machine, comprising a frame on which are mounted means for holding this wire, a rotor coupled to means of drive in continuous rotation, this rotor being provided with an axial conduit traversed longitudinally by the wire, a reciprocating drive means arranged to produce a relative longitudinal movement between the rotor and the wire, a movable central guide crossed by the wire and mounted in the rotor so as to be moved transversely relative to the axial duct, between a substantially centered position and an eccentric position, eccentricity control means arranged to move the central guide by means of a pressure fluid during rotation of the rotor, and stationary guides traversed by the wire and disposed in the axial duct on either side of the central guide.
  • the material is often supplied in the form of a wire delivered in a ring from which it is unwound to penetrate longitudinally into the machine.
  • a preliminary straightening of the wire is necessary to ensure the straightness of the finished part.
  • it is carried out by a dressing device installed at the entrance to the machine and operating intermittently, after each advance of the wire, for the manufacture of a new part.
  • the term "wire” used here can designate a metallic element with a circular or non-circular profile and relatively rigid, its transverse dimensions generally being of the order of several millimeters and possibly ranging up to approximately 10 to 12 mm.
  • the invention relates to a rotary type rectifier, in which the wire is arranged substantially along the axis of a rotor generally containing five guides, namely a central guide movable transversely so as to deform the wire and two pairs of stationary guides supporting the wire on either side of the central guide.
  • Dressing is obtained in a known manner by a combination of the eccentricity of the central guide, the rotation and the relative displacement of the rotor relative to the wire or vice versa. These movements cause an inflection with helical propagation in the wire, which deforms it beyond the elastic limit to an extent suitable for it to return elastically to a rectilinear form.
  • the amplitude of the eccentricity and the distance between the guides must be adapted to the dimensions and the mechanical characteristics of the different wires to be treated.
  • DE-A-2 707 970 describes an improvement of this device, where said control mechanism is actuated by a pneumatic cylinder, while the rotor rotates, in particular to return the guide to the centered position if the advance of the wire stops for some reason.
  • this pneumatic control is not intended to perform operating cycles with progressive displacement of the central guide. Besides, the device is intended to work continuously and not in cycles.
  • the object of the present invention is to provide a device making it possible to substantially avoid the drawbacks mentioned above, thanks to a simple and compact construction, making it possible to control the central guide in an easy and precise manner.
  • the invention provides a device of the type indicated in the preamble, characterized in that the reciprocating drive means comprises a first hydraulic cylinder, and in that the eccentricity control means comprise a second hydraulic cylinder which is hydraulically coupled to the first cylinder so as to operate at a speed dependent on that of the first cylinder.
  • the rotor is mounted by bearings on a carriage movable on the frame in the longitudinal direction of the wire and coupled to the first cylinder.
  • the central guide of the device comprises a support sliding radially in the rotor and provided with a support member at its end furthest from the axis of the rotor
  • the eccentricity control means comprise a sliding bush , mounted on the periphery of the rotor so as to rotate with it and provided with an axially inclined bearing surface, against which said bearing member is applied
  • said inclined bearing surface may be formed by a removable element fixed to the sliding sleeve and covering a radial bore in which the support is mounted sliding from the central guide.
  • said support member of the sliding support comprises a roller rolling on the inclined support surface, and the opposite end of said support is supported on a spring tending to keep the roller applied against said surface.
  • the eccentricity control means comprise a rotary sliding block, mounted around the sliding bushing by means of at least one bearing, this block being coupled to the second cylinder and cooperating with stops defining said positions of the central guide.
  • the rotor On each side of the central guide, the rotor may have an axial bore in which a tubular sleeve containing at least two stationary guides can be removably mounted, from a corresponding end of the rotor.
  • each guide has a guide barrel mounted inside a bearing
  • each of the tubular sleeves has a cylindrical axial bore
  • the bearings of the stationary guides are inserted into said bore of the sleeve and are held axially in positions. selected by means of interchangeable tubular spacers.
  • the hydraulic cylinders are double acting and said second cylinder, controlling the central guide, comprises two opposite chambers which are connected alternately, by means of an electrically controlled reversing valve, to an outlet of the first cylinder and a fluid return line, so that the speeds of the two cylinders are proportional to each other.
  • Said outlet of the first cylinder can be connected to a return line through a spring valve allowing said fluid flow to pass when the stroke of the second cylinder is blocked by a stop.
  • the device comprises means for measuring the speed of the rotor and for adjusting the flow of fluid actuating the first cylinder as a function of the speed of the rotor.
  • Figs. 2 and 3 show the main part of the dressing device 5, namely that which is carried by the carriage 6.
  • the carriage 6 comprises a chassis 10 fitted with sliding bearings 11 in order to be able to move back and forth on slides 12 fixed to the frame 1, by means of a double-acting hydraulic advance cylinder 13, driving a stud 14 fixed to the chassis 10.
  • This chassis carries a rotor 15 of axis 16, by means of two bearings 17, and an electric motor 18 driving in continuous rotation the rotor 15 by means of a pulley transmission 19, 20 and toothed belt 21.
  • the pulley 20 is fixed to the rotor 15 by means of a key and a screwed ring 22 provided with notches cooperating with a detector 23 to provide a signal representative of the speed of rotation of the rotor 15.
  • Each sleeve 28, 29 is provided with a cylindrical axial bore in which the guides 25 are wedged by means of tubular spacers 34 to 36 between a stop ring 37 and a nut 38 open at its center .
  • Each guide 25 comprises a guide barrel 40 provided with an orifice suitable for the section of the wire. This barrel is mounted in the inner ring of a bearing 41, the outer ring of which is adjusted in the corresponding sleeve 28, 29 and clamped between the spacers.
  • any change in the position or the type of stationary guides 25 in the dressing device can be done very quickly, since it suffices to unscrew the sleeves 28 and 29 and replace them with two other sleeves fitted beforehand with the appropriate guides. . In this way, all the positioning and centering operations of the stationary guides can be done outside the rotor.
  • stops 63 and 64 act directly at the level of the diving cylinder 62 has the advantage of avoiding any transmission of stop forces and of sparing the mechanical elements installed on the rotor.
  • the stop 64 can be adjusted while the rotor is rotating.
  • FIGS. 2 and 3 a distinction is also made between the inlet and outlet connections 66, 67 of the diving cylinder 62, for the connection of flexible hydraulic lines due to the stroke of the carriage 6, which is generally of the order 100 mm.
  • the diagram in fig. 4 shows how the advance cylinder 13 and the diving cylinder 62 are hydraulically coupled so as to operate at synchronous speeds during a wire straightening cycle.
  • the advance cylinder 13, ensuring the axial movement of the carriage 6, has inlet and outlet connections 70 and 71 which are connected to a pipe 72 for supplying pressurized fluid and to a pipe 73 for returning the fluid , through an inverting solenoid valve 74, a flow limiter 75 and, on the side of the connection 71 of the jack 13, two spring-loaded valves 76 and 77 mounted in opposition and calibrated at a pressure corresponding to approximately half of the supply pressure in line 72.
  • the hydraulic diagram shows the various organs in the rest position, before a wire straightening cycle.
  • a throttle 81 connected to the inlet 70 of the jack is adjusted as a function of the speed of the rotor in order to adjust the speed of movement of the jacks, while the other throttle 82 is open to 100%.
  • the cylinders 13 and 62 are in abutment (on the left in the diagram in FIG. 4).
  • the solenoid valve 74 is activated, so that pressurized fluid enters the jack 13 through the connector 70 and that fluid exits through the fitting 71.
  • this outgoing fluid is transmitted to the inlet 66 of the diving cylinder 62 and therefore actuates the latter in the direction of arrow C at a speed proportional to that of the cylinder 13, that is to say that the central guide is offset linearly with respect to the movement of the carriage 6.
  • the diving cylinder 62 arrives in abutment (abutment 64, fig. 3) the fluid leaving the jack 13 returns through the valve 76.
  • the central guide is returned to its centered position by deactivating the valve 78, so that the fluid leaving the connection 71 of the cylinder 13 enters the connection 67 of the cylinder 62 and actuates the latter. ci in the opposite direction to C, always at a speed proportional to that of the jack 13. Then, to return the carriage to its starting position, the valve 74 is deactivated so that it returns to the position shown in the figure and the pressurized fluid is transmitted to the connection 71 of the cylinder 13.
  • the cylinder 62 having already arrived in abutment, it no longer moves and the central guide 26 remains in the centered position.
  • the throttle 82 makes it possible to adjust the return speed of the carriage 6.
  • valve 78 is directly supplied with pressure at its inlet 84. It is therefore possible to control the diving of the central guide as if the two cylinders 13 and 62 were decoupled. However, the diving speed should not be too high, as the wire would be badly drawn. This is why there is provided the valve 80 which is activated by the pressure at the outlet of the throttle 82, so as to reduce the flow of the fluid. In normal operation, the valve is deactivated by the pressure delivered by the connection 71 of the cylinder 13.
  • the invention makes it possible to produce a dressing device having a relatively simple construction and a reduced bulk, thanks to the judicious arrangement of the elements.
  • the hydraulic control is very simple and allows without difficulty to synchronize the movements of advance and diving of the central guide in order to ensure an optimal straightening of the wire.
  • the operations of preparing and adjusting the device for straightening a given type of wire are very simplified compared to known devices, thanks to the elimination of manual centering of the material and the possibility of preparing the stationary guides outside the machine. .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Wire Processing (AREA)

Abstract

A device for straightening a rigid wire delivered in coil form for supplying a metal-working machine is compact and easy to control. The wire is stationary in an axial conduit of a rotor supported on a carriage (B) which is moved axially by means of a first hydraulic jack (13). The rotor carries the wire by stationary guides and a central guide which is moved radially (C) between a centered position and an excentric position by means of a second hydraulic jack (62) while the rotor rotates and the carriage advances. The hydraulic fluid collected at the output (71) of the first jack is transmitted directly to an input (66 or 67) of the second jack (62) so as to actuate it at a speed proportional to that of the first.

Description

La présente invention concerne un dispositif de dressage d'un fil métallique rigide, notamment à l'entrée d'une machine d'usinage, comportant un bâti sur lequel sont montés des moyens de maintien de ce fil, un rotor couplé à des moyens d'entraînement en rotation continue, ce rotor étant pourvu d'un conduit axial traversé longitudinalement par le fil, un moyen d'entraînement en va-et-vient agencé pour produire un mouvement longitudinal relatif entre le rotor et le fil, un guide central mobile traversé par le fil et monté dans le rotor de manière à être déplacé transversalement par rapport au conduit axial, entre une position sensiblement centrée et une position excentrée, des moyens de commande d'excentration agencés pour déplacer le guide central au moyen d'une pression de fluide pendant la rotation du rotor, et des guides stationnaires traversés par le fil et disposés dans le conduit axial de part et d'autre du guide central.The present invention relates to a device for dressing a rigid metal wire, in particular at the entrance to a machining machine, comprising a frame on which are mounted means for holding this wire, a rotor coupled to means of drive in continuous rotation, this rotor being provided with an axial conduit traversed longitudinally by the wire, a reciprocating drive means arranged to produce a relative longitudinal movement between the rotor and the wire, a movable central guide crossed by the wire and mounted in the rotor so as to be moved transversely relative to the axial duct, between a substantially centered position and an eccentric position, eccentricity control means arranged to move the central guide by means of a pressure fluid during rotation of the rotor, and stationary guides traversed by the wire and disposed in the axial duct on either side of the central guide.

Dans les machines destinées à la fabrication de petites pièces par usinage, notamment par décolletage, l'alimentation en matière se fait souvent sous la forme d'un fil livré en couronne à partir de laquelle il est déroulé pour pénétrer longitudinalement dans la machine. Toutefois, un dressage préliminaire du fil est nécessaire pour assurer la rectitude de la pièce terminée. En général, il est effectué par un dispositif de dressage installé à l'entrée de la machine et opérant de manière intermittente, après chaque avance du fil, en vue de la fabrication d'une nouvelle pièce. Il faut noter que le terme de "fil" utilisé ici peut désigner un élément métallique à profil circulaire ou non et relativement rigide, ses dimensions transversales étant généralement de l'ordre de plusieurs millimètres et pouvant aller jusqu'à environ 10 à 12 mm.In machines intended for the manufacture of small parts by machining, in particular by turning, the material is often supplied in the form of a wire delivered in a ring from which it is unwound to penetrate longitudinally into the machine. However, a preliminary straightening of the wire is necessary to ensure the straightness of the finished part. In general, it is carried out by a dressing device installed at the entrance to the machine and operating intermittently, after each advance of the wire, for the manufacture of a new part. It should be noted that the term "wire" used here can designate a metallic element with a circular or non-circular profile and relatively rigid, its transverse dimensions generally being of the order of several millimeters and possibly ranging up to approximately 10 to 12 mm.

L'invention concerne un redresseur du type tournant, dans lequel le fil est disposé sensiblement suivant l'axe d'un rotor contenant généralement cinq guides, à savoir un guide central mobile transversalement de manière à déformer le fil et deux paires de guides stationnaires épaulant le fil de part et d'autre du guide central. Le dressage est obtenu de manière connue par une combinaison de l'excentration du guide central, de la rotation et du déplacement relatif du rotor par rapport au fil ou inversement. Ces mouvements provoquent une inflexion à propagation hélicoïdale dans le fil, ce qui le déforme au-delà de la limite élastique dans une mesure appropriée pour qu'il revienne élastiquement à une forme rectiligne. Bien entendu, l'amplitude de l'excentration et la distance entre les guides doivent être adaptées aux dimensions et aux caractéristiques mécaniques des différents fils à traiter.The invention relates to a rotary type rectifier, in which the wire is arranged substantially along the axis of a rotor generally containing five guides, namely a central guide movable transversely so as to deform the wire and two pairs of stationary guides supporting the wire on either side of the central guide. Dressing is obtained in a known manner by a combination of the eccentricity of the central guide, the rotation and the relative displacement of the rotor relative to the wire or vice versa. These movements cause an inflection with helical propagation in the wire, which deforms it beyond the elastic limit to an extent suitable for it to return elastically to a rectilinear form. Of course, the amplitude of the eccentricity and the distance between the guides must be adapted to the dimensions and the mechanical characteristics of the different wires to be treated.

Les dispositifs connus appliquant cette technique présentent un certain nombre d'inconvénients au point de vue de la construction et de l'exploitation. La nécessité d'excentrer le guide central d'une manière progressive au cours du déplacement du rotor par rapport au fil exige des mécanismes compliqués qui sont généralement commandés par des cames actionnées par un arbre à cames à partir de la machine d'usinage. De ce fait, l'encombrement du dispositif est relativement grand et en particulier le rotor est beaucoup plus long que la distance occupée par les guides, à cause de l'espace nécessaire pour le mécanisme de commande entre les deux paliers du rotor. De plus, ce mécanisme est relativement compliqué, avec un grand nombre de renvois, de leviers etc., d'où un coût relativement élevé, des difficultés d'équilibrage et des jeux altérant la précision de fonctionnement. Par ailleurs, les constructions actuelles nécessitent un ajustement précis des guides stationnaires et cet ajustement ne peut se faire qu'à l'arrêt, d'où un temps de réglage assez long.The known devices applying this technique have a certain number of drawbacks from the point of view of construction and operation. The need to offset the central guide in a progressive manner during the movement of the rotor relative to the wire requires complicated mechanisms which are generally controlled by cams actuated by a camshaft from the machine tool. Therefore, the size of the device is relatively large and in particular the rotor is much longer than the distance occupied by the guides, because of the space required for the control mechanism between the two bearings of the rotor. In addition, this mechanism is relatively complicated, with a large number of deflections, levers, etc., resulting in a relatively high cost, difficulties in balancing and games altering the operating precision. Furthermore, current constructions require a precise adjustment of the stationary guides and this adjustment can only be made when stationary, hence a fairly long adjustment time.

La demande de brevet FR-A-2 312 314 (=DE-A-2 523 831) décrit un dispositif stationnaire de dressage que le fil à dresser traverse en continu et où l'excentricité du guide central est commandée par une douille coulissant axialement sur le rotor, cette douille ayant des surfaces inclinées axialement contre lesquelles s'appuie un support du guide central. Ce support coulisse radialement quand la douille est déplacée radialement au moyen d'un mécanisme de commande. Le DE-A-2 707 970 décrit un perfectionnement de ce dispositif, où ledit mécanisme de commande est actionné par un vérin pneumatique, pendant que le rotor tourne, notamment pour remettre le guide en position centrée si l'avance du fil s'arrête pour une raison quelconque. Toutefois, cette commande pneumatique n'est pas prévue pour effectuer des cycles de fonctionnement avec déplacement progressif du guide central. D'ailleurs le dispositif est destiné à travailler en continu et non par cycles.Patent application FR-A-2 312 314 (= DE-A-2 523 831) describes a stationary straightening device which the straightening wire crosses continuously and where the eccentricity of the central guide is controlled by an axially sliding bush. on the rotor, this bushing having axially inclined surfaces against which a support for the central guide rests. This support slides radially when the socket is moved radially by means of a control mechanism. DE-A-2 707 970 describes an improvement of this device, where said control mechanism is actuated by a pneumatic cylinder, while the rotor rotates, in particular to return the guide to the centered position if the advance of the wire stops for some reason. However, this pneumatic control is not intended to perform operating cycles with progressive displacement of the central guide. Besides, the device is intended to work continuously and not in cycles.

La présente invention a pour but de fournir un dispositif permettant d'éviter substantiellement les inconvénients mentionnés plus haut, grâce à une construction simple et compacte, permettant de commander le guide central d'une manière aisée et précise.The object of the present invention is to provide a device making it possible to substantially avoid the drawbacks mentioned above, thanks to a simple and compact construction, making it possible to control the central guide in an easy and precise manner.

Dans ce but, l'invention fournit un dispositif du type indiqué en préambule, caractérisé en ce que le moyen d'entraînement en va-et-vient comporte un premier vérin hydraulique, et en ce que les moyens de commande d'excentration comportent un second vérin hydraulique qui est couplé hydrauliquement au premier vérin de manière à fonctionner à une vitesse dépendant de celle du premier vérin.To this end, the invention provides a device of the type indicated in the preamble, characterized in that the reciprocating drive means comprises a first hydraulic cylinder, and in that the eccentricity control means comprise a second hydraulic cylinder which is hydraulically coupled to the first cylinder so as to operate at a speed dependent on that of the first cylinder.

Dans une réalisation préférée, le rotor est monté par des paliers sur un chariot mobile sur le bâti dans la direction longitudinale du fil et couplé au premier vérin.In a preferred embodiment, the rotor is mounted by bearings on a carriage movable on the frame in the longitudinal direction of the wire and coupled to the first cylinder.

Lorsque, le guide central du dispositif comporte un support coulissant radialement dans le rotor et pourvu d'un organe d'appui à son extrémité la plus éloignée de l'axe du rotor, et que les moyens de commande d'excentration comportent une douille coulissante, montée sur le pourtour du rotor de façon à tourner avec lui et pourvue d'une surface d'appui inclinée axialement, contre laquelle est appliqué ledit organe d'appui, ladite surface d'appui inclinée peut être formée par un élément démontable fixé à la douille coulissante et recouvrant un alésage radial dans lequel est monté le support coulissant du guide central. De préférence, ledit organe d'appui du support coulissant comporte un galet roulant sur la surface d'appui inclinée, et l'extrémité opposée dudit support est appuyée sur un ressort tendant à maintenir le galet appliqué contre ladite surface.When the central guide of the device comprises a support sliding radially in the rotor and provided with a support member at its end furthest from the axis of the rotor, and when the eccentricity control means comprise a sliding bush , mounted on the periphery of the rotor so as to rotate with it and provided with an axially inclined bearing surface, against which said bearing member is applied, said inclined bearing surface may be formed by a removable element fixed to the sliding sleeve and covering a radial bore in which the support is mounted sliding from the central guide. Preferably, said support member of the sliding support comprises a roller rolling on the inclined support surface, and the opposite end of said support is supported on a spring tending to keep the roller applied against said surface.

Dans une forme de réalisation préférée, les moyens de commande d'excentration comportent un bloc coulissant rotatif, monté autour de la douille coulissante au moyen d'au moins un roulement, ce bloc étant couplé au second vérin et coopérant avec des butées définissant lesdites positions du guide central.In a preferred embodiment, the eccentricity control means comprise a rotary sliding block, mounted around the sliding bushing by means of at least one bearing, this block being coupled to the second cylinder and cooperating with stops defining said positions of the central guide.

De chaque côté du guide central, le rotor peut comporter un alésage axial dans lequel un manchon tubulaire contenant au moins deux guides stationnaires peut être monté de manière amovible, à partir d'une extrémité correspondante du rotor. De préférence, chaque guide comporte un canon de guidage monté à l'intérieur d'un roulement, chacun des manchons tubulaires comporte un alésage axial cylindrique, et les roulements des guides stationnaires sont insérés dans ledit alésage du manchon et sont maintenus axialement dans des positions respectives sélectionnées au moyen d'entretoises tubulaires interchangeables.On each side of the central guide, the rotor may have an axial bore in which a tubular sleeve containing at least two stationary guides can be removably mounted, from a corresponding end of the rotor. Preferably, each guide has a guide barrel mounted inside a bearing, each of the tubular sleeves has a cylindrical axial bore, and the bearings of the stationary guides are inserted into said bore of the sleeve and are held axially in positions. selected by means of interchangeable tubular spacers.

Dans une forme avantageuse de l'invention, les vérins hydrauliques sont à double effet et ledit second vérin, commandant le guide central, comporte deux chambres opposées qui sont raccordées alternativement, grâce à une vanne d'inversion à commande électrique, à une sortie du premier vérin et à une conduite du retour de fluide, de sorte que les vitesses des deux vérins sont proportionnelles l'une à l'autre. Ladite sortie du premier vérin peut être raccordée à une conduite de retour à travers un clapet à ressort laissant passer ledit débit de fluide quand la course du second vérin est bloquée par une butée. De préférence, le dispositif comporte des moyens pour mesurer la vitesse du rotor et pour régler le débit de fluide actionnant le premier vérin en fonction de la vitesse du rotor.In an advantageous form of the invention, the hydraulic cylinders are double acting and said second cylinder, controlling the central guide, comprises two opposite chambers which are connected alternately, by means of an electrically controlled reversing valve, to an outlet of the first cylinder and a fluid return line, so that the speeds of the two cylinders are proportional to each other. Said outlet of the first cylinder can be connected to a return line through a spring valve allowing said fluid flow to pass when the stroke of the second cylinder is blocked by a stop. Preferably, the device comprises means for measuring the speed of the rotor and for adjusting the flow of fluid actuating the first cylinder as a function of the speed of the rotor.

La présente invention sera mieux comprise à l'aide de la description suivante d'une forme de réalisation préférée, en référence aux dessins annexés, dans lesquels :

  • la fig. 1 est une vue latérale schématique d'une installation comprenant un dispositif de dressage selon l'invention, associé à une machine d'usinage du fil dressé par ce dispositif,
  • la fig. 2 est une vue de l'arrière du chariot du dispositif de dressage, dans le sens d'avancement du fil,
  • la fig. 3 est une vue en coupe axiale suivant la ligne III-III de la fig. 2, et
  • la fig. 4 représente schématiquement le circuit hydraulique du dispositif.
The present invention will be better understood with the aid of the following description of a preferred embodiment, with reference to the appended drawings, in which:
  • fig. 1 is a schematic side view of an installation comprising a dressing device according to the invention, associated with a machine for machining the wire drawn by this device,
  • fig. 2 is a view of the rear of the carriage of the dressing device, in the direction of advance of the wire,
  • fig. 3 is an axial sectional view along line III-III of FIG. 2, and
  • fig. 4 schematically represents the hydraulic circuit of the device.

En référence à la fig. 1, un bâti commun 1 porte un dérouleur 2 pour un fil métallique rigide 3 enroulé sur un touret 4, un dispositif 5 de dressage du fil selon l'invention, équipé d'un chariot 6 mobile en va-et-vient le long du fil, et une machine d'usinage 7 telle qu'une décolleteuse, usinant des tronçons successifs du fil 3 et équipée d'un dispositif 8 de maintien et d'avance intermittente du fil 3 dans le sens de la flèche A. Le dispositif de dressage 5 redresse une longueur déterminée du fil 3 pendant que celui-ci est maintenu arrêté par le dispositif 8, par exemple immédiatement après une opération d'avance. Le dressage s'effectue au cours d'un déplacement du chariot 6 dans le sens de la flèche B.With reference to fig. 1, a common frame 1 carries an unwinder 2 for a rigid metal wire 3 wound on a reel 4, a device 5 for straightening the wire according to the invention, equipped with a carriage 6 movable back and forth along the wire, and a machining machine 7 such as a bar turning machine, machining successive sections of wire 3 and equipped with a device 8 for intermittently holding and advancing wire 3 in the direction of arrow A. The device dressing 5 straightens a determined length of the wire 3 while the latter is kept stopped by the device 8, for example immediately after an advance operation. The dressing takes place during a movement of the carriage 6 in the direction of the arrow B.

Les fig. 2 et 3 montrent la partie principale du dispositif de dressage 5, à savoir celle qui est portée par le chariot 6. Toutefois, afin de clarifier le dessin, certains éléments tels que les liaisons électriques ou hydrauliques ne sont pas représentés en détail. Le chariot 6 comporte un châssis 10 équipé de paliers coulissants 11 pour pouvoir se déplacer en va-et-vient sur des glissières 12 fixées au bâti 1, au moyen d'un vérin hydraulique d'avance 13 à double effet, attaquant un plot 14 fixé au châssis 10. Ce châssis porte un rotor 15 d'axe 16, grâce à deux roulements 17, et un moteur électrique 18 entraînant en rotation continue le rotor 15 au moyen d'une transmission à poulies 19, 20 et à courroie crantée 21. La poulie 20 est fixée sur le rotor 15 au moyen d'une clavette et d'une bague vissée 22 pourvue d'encoches coopérant avec un détecteur 23 pour fournir un signal représentatif de la vitesse de rotation du rotor 15.Figs. 2 and 3 show the main part of the dressing device 5, namely that which is carried by the carriage 6. However, in order to clarify the drawing, certain elements such as the electrical or hydraulic connections are not shown in detail. The carriage 6 comprises a chassis 10 fitted with sliding bearings 11 in order to be able to move back and forth on slides 12 fixed to the frame 1, by means of a double-acting hydraulic advance cylinder 13, driving a stud 14 fixed to the chassis 10. This chassis carries a rotor 15 of axis 16, by means of two bearings 17, and an electric motor 18 driving in continuous rotation the rotor 15 by means of a pulley transmission 19, 20 and toothed belt 21. The pulley 20 is fixed to the rotor 15 by means of a key and a screwed ring 22 provided with notches cooperating with a detector 23 to provide a signal representative of the speed of rotation of the rotor 15.

Comme on le voit dans la fig. 3, le rotor 15 entoure un conduit axial 24 dans lequel le fil 3 (non représenté dans cette figure) est guidé le long de l'axe 16 au moyen de quatre guides stationnaires 25 et d'un guide central 26 mobile transversalement. En pratique, ces différents guides doivent être espacés les uns des autres dans une mesure correspondant approximativement à dix fois le diamètre du fil. Les guides stationnaires 25 sont montés deux à deux dans un manchon arrière 28 et un manchon avant 29 qui sont facilement amovibles, car ils sont insérés dans un alésage axial du rotor et vissés dans celui-ci grâce à des filetages 30, 31 et des épaulements de butée 32, 33. Chaque manchon 28, 29 est pourvu d'un alésage axial cylindrique dans lequel les guides 25 sont calés au moyen d'entretoises tubulaires 34 à 36 entre une bague d'arrêt 37 et un écrou 38 ouvert en son centre. Chaque guide 25 comporte un canon de guidage 40 pourvu d'un orifice approprié à la section du fil. Ce canon est monté dans la bague intérieure d'un roulement 41 dont la bague extérieure est ajustée dans le manchon correspondant 28, 29 et serrée entre les entretoises.As seen in fig. 3, the rotor 15 surrounds an axial duct 24 in which the wire 3 (not shown in this figure) is guided along the axis 16 by means of four stationary guides 25 and a central guide 26 movable transversely. In practice, these different guides must be spaced from each other to an extent corresponding approximately to ten times the diameter of the wire. The stationary guides 25 are mounted in pairs in a rear sleeve 28 and a front sleeve 29 which are easily removable, because they are inserted into an axial bore of the rotor and screwed into it by means of threads 30, 31 and the shoulders stop 32, 33. Each sleeve 28, 29 is provided with a cylindrical axial bore in which the guides 25 are wedged by means of tubular spacers 34 to 36 between a stop ring 37 and a nut 38 open at its center . Each guide 25 comprises a guide barrel 40 provided with an orifice suitable for the section of the wire. This barrel is mounted in the inner ring of a bearing 41, the outer ring of which is adjusted in the corresponding sleeve 28, 29 and clamped between the spacers.

Ainsi, tout changement de la position ou du type des guides stationnaires 25 dans le dispositif de dressage peut se faire très rapidement, puisqu'il suffit de dévisser les manchons 28 et 29 et de les remplacer par deux autres manchons équipés au préalable des guides appropriés. De cette manière, toutes les opérations de positionnement et de centrage des guides stationnaires peuvent se faire en dehors du rotor.Thus, any change in the position or the type of stationary guides 25 in the dressing device can be done very quickly, since it suffices to unscrew the sleeves 28 and 29 and replace them with two other sleeves fitted beforehand with the appropriate guides. . In this way, all the positioning and centering operations of the stationary guides can be done outside the rotor.

Le guide mobile 26 comporte aussi un canon de dressage 42 traversé par le fil et un roulement 43 fixé dans un support 44 qui est monté de manière coulissante dans un alésage radial 45 du rotor, où il est guidé au moyen d'une cheville 46 et d'une rainure 47. Le support 44 est poussé, en direction d'une position centrée du guide 26, par un ressort 48 appuyé contre un couvercle 49. Ce ressort joue un rôle essentiellement à l'arrêt, car pendant la rotation du rotor le support 44 est sollicité dans le même sens par la force centrifuge. Du côté opposé au ressort, le support 44 est équipé d'un galet 50 s'appuyant contre une surface 51 inclinée axialement, formant une rampe mobile dont les déplacements axiaux commandent les déplacements radiaux du guide central 26, entre une position centrée et une position excentrée ajustable.The movable guide 26 also includes a straightening barrel 42 traversed by the wire and a bearing 43 fixed in a support 44 which is slidably mounted in a radial bore 45 of the rotor, where it is guided by means of a pin 46 and a groove 47. The support 44 is pushed, in the direction of a centered position of the guide 26, by a spring 48 pressed against a cover 49. This spring plays a role essentially when stationary, because during the rotation of the rotor the support 44 is biased in the same direction by the centrifugal force. On the side opposite to the spring, the support 44 is equipped with a roller 50 pressing against an axially inclined surface 51, forming a movable ramp whose axial movements control the radial movements of the central guide 26, between a centered position and a position adjustable offset.

Une douille cylindrique rotative 52 pourvue d'un collet 53 est montée de manière coulissante axialement sur la surface extérieure cylindrique du rotor 15, où elle est guidée par une clavette non représentée. Le collet 53 est interrompu en regard de l'alésage radial 45 du rotor, pour permettre l'entrée et la sortie du guide central 26 et de son support 44, ainsi que pour le montage d'une pièce en forme de coin 54 pourvue de la surface inclinée 51. Cette pièce est fixée au collet 53 par deux vis latérales 55 permettant de l'enlever facilement pour changer le guide 26. Un bloc coulissant 56 entoure la douille rotative 52, sur laquelle il est monté au moyen d'un roulement 57 lui permettant d'exercer une poussée axiale sur la douille sans tourner avec elle. Ce bloc 56 est pourvu d'une protubérance inférieure 58 dans laquelle est fixé un axe de guidage 59 monté dans une coulisse longitudinale 60 à l'intérieur du chariot. Une extrémité de l'axe 59 est solidaire du piston 61 d'un vérin hydraulique à double effet 62 appelé vérin de plongée, car il commande le mouvement d'excentration du guide central 26. Une extrémité 63 du corps du vérin 62 forme une butée pour l'axe 59, cette butée définissant la position centrée du guide 26. L'autre extrémité de l'axe 59 coopère avec une butée réglable formée par une vis 64 à côté de laquelle le chariot porte une règle graduée 65. Ceci permet d'ajuster facilement l'excentricité maximale du guide central 26, sans qu'une butée soit nécessaire sur le rotor. Le fait que les butées 63 et 64 agissent directement au niveau du vérin de plongée 62 a l'avantage d'éviter toute transmission d'efforts de butée et de ménager les éléments mécaniques installés sur le rotor. De plus, on peut régler la butée 64 pendant que le rotor tourne. Dans les figures 2 et 3, on distingue également les raccords d'entrée et de sortie 66, 67 du vérin de plongée 62, pour le branchement de conduites hydrauliques flexibles en raison de la course du chariot 6, laquelle est généralement de l'ordre de 100 mm.A rotary cylindrical sleeve 52 provided with a collar 53 is slidably mounted axially on the cylindrical external surface of the rotor 15, where it is guided by a key not shown. The collar 53 is interrupted opposite the radial bore 45 of the rotor, to allow the entry and exit of the central guide 26 and its support 44, as well as for the mounting of a wedge-shaped part 54 provided with the inclined surface 51. This part is fixed to the collar 53 by two lateral screws 55 allowing it to be easily removed to change the guide 26. A sliding block 56 surrounds the rotary sleeve 52, on which it is mounted by means of a bearing 57 allowing it to exert an axial thrust on the sleeve without turning with it. This block 56 is provided with a lower protrusion 58 in which is fixed a guide pin 59 mounted in a longitudinal slide 60 inside the carriage. One end of the axis 59 is integral with the piston 61 of a double-acting hydraulic cylinder 62 called a diving cylinder, because it controls the eccentric movement of the central guide 26. One end 63 of the body of the cylinder 62 forms a stop for the axis 59, this stop defining the centered position of the guide 26. The other end of the axis 59 cooperates with an adjustable stop formed by a screw 64 next to which the carriage carries a graduated rule 65. This allows d '' easily adjust the maximum eccentricity of the central guide 26, without a stop being necessary on the rotor. The fact that the stops 63 and 64 act directly at the level of the diving cylinder 62 has the advantage of avoiding any transmission of stop forces and of sparing the mechanical elements installed on the rotor. In addition, the stop 64 can be adjusted while the rotor is rotating. In FIGS. 2 and 3, a distinction is also made between the inlet and outlet connections 66, 67 of the diving cylinder 62, for the connection of flexible hydraulic lines due to the stroke of the carriage 6, which is generally of the order 100 mm.

Si la surface inclinée 51 est plane ou conique d'axe 16, le déplacement radial du guide central 26 est linéaire par rapport à la course du vérin de plongée 62. Le rapport entre ces deux déplacements est défini par l'inclinaison de la surface 51, ce qui permet une grande précision de la commande et de l'ajustement des positions extrêmes du guide.If the inclined surface 51 is planar or conical with an axis 16, the radial displacement of the central guide 26 is linear with respect to the stroke of the diving cylinder 62. The ratio between these two displacements is defined by the inclination of the surface 51 , which allows great precision in the control and adjustment of the extreme positions of the guide.

En général, le rotor 15 tourne continuellement et à une vitesse constante pendant les opérations d'usinage, d'avance et de dressage du fil. Le dressage s'effectue pendant le mouvement d'aller du chariot 6 dans le sens de la flèche B. Pendant ce temps, le vérin de plongée 62 est actionné de façon à déplacer progressivement vers la gauche, à partir de la position de repos de la fig. 3, le bloc coulissant 56 et la douille rotative 52, pour abaisser le guide central 26 jusqu'à sa position excentrée définie par la butée 64. L'ensemble reste quelques instants dans cette positon puis le vérin 62 est actionné dans l'autre sens de façon à ramener progressivement le guide central 26 en position centrée avant la fin de la course du chariot. Pour éviter de casser le fil et pour obtenir un dressage convenable, il est important que le mouvement de plongée du guide central 26 soit progressif et synchronisé avec son mouvement axial par rapport au fil, c'est-à-dire avec le mouvement du chariot sous l'effet du vérin d'avance 13. Ce problème est résolu d'une manière simple grâce à la commande hydraulique.In general, the rotor 15 rotates continuously and at a constant speed during the operations of machining, advancing and straightening the wire. The dressing takes place during the forward movement of the carriage 6 in the direction of the arrow B. During this time, the diving cylinder 62 is actuated so as to move gradually to the left, from the rest position of fig. 3, the sliding block 56 and the rotary sleeve 52, to lower the central guide 26 to its eccentric position defined by the stop 64. The assembly remains for a few moments in this position and then the jack 62 is actuated in the other direction so as to gradually return the central guide 26 to the centered position before the end of the carriage stroke. To avoid breaking the wire and to obtain a suitable dressing, it is important that the plunging movement of the central guide 26 is progressive and synchronized with its axial movement relative to the wire, that is to say with the movement of the carriage. under the effect of the advance cylinder 13. This problem is solved in a simple manner by means of the hydraulic control.

Le schéma de la fig. 4 montre comment le vérin d'avance 13 et le vérin de plongée 62 sont couplés hydrauliquement de manière à fonctionner à des vitesses synchrones au cours d'un cycle de dressage du fil. Le vérin d'avance 13, assurant le déplacement axial du chariot 6, possède des raccords d'entrée et de sortie 70 et 71 qui sont reliés à une conduite 72 d'alimentation en fluide sous pression et à une conduite 73 de retour du fluide, à travers une électrovanne inverseuse 74, un limiteur de débit 75 et, du côté du raccord 71 du vérin 13, deux clapets à ressorts 76 et 77 montés en opposition et tarés à une pression correspondant à environ la moitié de la pression d'alimentation dans la conduite 72.The diagram in fig. 4 shows how the advance cylinder 13 and the diving cylinder 62 are hydraulically coupled so as to operate at synchronous speeds during a wire straightening cycle. The advance cylinder 13, ensuring the axial movement of the carriage 6, has inlet and outlet connections 70 and 71 which are connected to a pipe 72 for supplying pressurized fluid and to a pipe 73 for returning the fluid , through an inverting solenoid valve 74, a flow limiter 75 and, on the side of the connection 71 of the jack 13, two spring-loaded valves 76 and 77 mounted in opposition and calibrated at a pressure corresponding to approximately half of the supply pressure in line 72.

Les raccords d'entrée et de sortie 66 et 67 du vérin de plongée 62 sont reliés, à travers une électrovanne inverseuse 78, d'une part à une conduite de retour 79 et d'autre part au raccord 71 du vérin 13 à travers une vanne 80 pilotée par les pressions respectives régnant de part et d'autre des clapets 76 et 77. Pendant la marche normale du dispositif, cette vanne ne joue pas de rôle et reste dans la position représentée.The inlet and outlet connections 66 and 67 of the diving cylinder 62 are connected, through an inverting solenoid valve 78, on the one hand to a return pipe 79 and on the other hand to the connector 71 of the cylinder 13 through a valve 80 controlled by the respective pressures prevailing on either side of the valves 76 and 77. During normal operation of the device, this valve does not play a role and remains in the position shown.

Le schéma hydraulique montre les différents organes en position de repos, avant un cycle de dressage du fil. Dans le régulateur 75, un étranglement 81 raccordé à l'entrée 70 du vérin est réglé en fonction de la vitesse du rotor afin d'ajuster la vitesse de déplacement des vérins, tandis que l'autre étranglement 82 est ouvert à 100%. Les vérins 13 et 62 sont en butée (à gauche dans le schéma de la fig. 4). Pour commencer le cycle de dressage du fil et produire le déplacement du chariot 6 dans le sens B, on active l'électrovanne 74, si bien que du fluide sous pression entre dans le vérin 13 par le raccord 70 et que du fluide en sort par le raccord 71. Après activation de l'électrovanne 78, ce fluide sortant est transmis à l'entrée 66 du vérin de plongée 62 et actionne donc celui-ci dans le sens de la flèche C à une vitesse proportionnelle à celle du vérin 13, c'est-à-dire que le guide central est excentré linéairement par rapport au déplacement du chariot 6. Quand le vérin de plongée 62 arrive en butée (butée 64, fig. 3) le fluide sortant du vérin 13 revient par le clapet 76.The hydraulic diagram shows the various organs in the rest position, before a wire straightening cycle. In the regulator 75, a throttle 81 connected to the inlet 70 of the jack is adjusted as a function of the speed of the rotor in order to adjust the speed of movement of the jacks, while the other throttle 82 is open to 100%. The cylinders 13 and 62 are in abutment (on the left in the diagram in FIG. 4). To start the wire straightening cycle and produce the movement of the carriage 6 in direction B, the solenoid valve 74 is activated, so that pressurized fluid enters the jack 13 through the connector 70 and that fluid exits through the fitting 71. After activation of the solenoid valve 78, this outgoing fluid is transmitted to the inlet 66 of the diving cylinder 62 and therefore actuates the latter in the direction of arrow C at a speed proportional to that of the cylinder 13, that is to say that the central guide is offset linearly with respect to the movement of the carriage 6. When the diving cylinder 62 arrives in abutment (abutment 64, fig. 3) the fluid leaving the jack 13 returns through the valve 76.

Avant que le chariot ait terminé sa course, on commande le retour du guide central vers sa positon centrée en désactivant la vanne 78, de sorte que le fluide sortant du raccord 71 du vérin 13 entre dans le raccord 67 du vérin 62 et actionne celui-ci dans le sens opposé à C, toujours à une vitesse proportionnelle à celle du vérin 13. Ensuite, pour ramener le chariot à sa position de départ, on désactive la vanne 74 pour qu'elle retrouve la position représentée dans la figure et que le fluide sous pression soit transmis au raccord 71 du vérin 13. Le vérin 62 étant déjà arrivé en butée, il ne se déplace plus et le guide central 26 reste en position centrée. L'étranglement 82 permet d'ajuster la vitesse de retour du chariot 6.Before the carriage has completed its travel, the central guide is returned to its centered position by deactivating the valve 78, so that the fluid leaving the connection 71 of the cylinder 13 enters the connection 67 of the cylinder 62 and actuates the latter. ci in the opposite direction to C, always at a speed proportional to that of the jack 13. Then, to return the carriage to its starting position, the valve 74 is deactivated so that it returns to the position shown in the figure and the pressurized fluid is transmitted to the connection 71 of the cylinder 13. The cylinder 62 having already arrived in abutment, it no longer moves and the central guide 26 remains in the centered position. The throttle 82 makes it possible to adjust the return speed of the carriage 6.

Lors des réglages manuels des paramètres de dressage, le chariot et le vérin d'avance 13 sont au repos, de sorte que la vanne 78 est directement alimentée en pression à son entrée 84. On peut donc commander la plongée du guide central comme si les deux vérins 13 et 62 étaient découplés. Cependant, la vitesse de plongée ne doit pas être trop importante, car le fil serait mal dressé. C'est pourquoi on a prévu la vanne 80 qui est activée par la pression à la sortie de l'étranglement 82, de manière à réduire le débit du fluide. En fonctionnement normal, la vanne est désactivée par la pression refoulée par le raccord 71 du vérin 13.During manual adjustments of the dressing parameters, the carriage and the advance cylinder 13 are at rest, so that the valve 78 is directly supplied with pressure at its inlet 84. It is therefore possible to control the diving of the central guide as if the two cylinders 13 and 62 were decoupled. However, the diving speed should not be too high, as the wire would be badly drawn. This is why there is provided the valve 80 which is activated by the pressure at the outlet of the throttle 82, so as to reduce the flow of the fluid. In normal operation, the valve is deactivated by the pressure delivered by the connection 71 of the cylinder 13.

L'effort nécessaire à l'excentration du guide central varie fortement en fonction de la nature et des dimensions du matériau à dresser. D'autre part, le choix de la pression d'ouverture ΔP1 du clapet anti-retour 76 doit permettre de dresser la matière la plus résistante.The effort required to offset the central guide varies greatly depending on the nature and dimensions of the material to be dressed. On the other hand, the choice of the opening pressure ΔP1 of the non-return valve 76 must make it possible to draw up the most resistant material.

Il en résulte que, lors du dressage de matière de petite dimension, la différence de pression nécessaire entre les points 84 et 73 pour actionner le vérin de plongée 62 serait nettement inférieure à la valeur réglée sur le clapet 76. De ce fait, lorsque le vérin 62 arrivera en butée, la pression au raccord 71 augmentera brusquement jusqu'à un niveau permettant l'ouverture du clapet 76, ce qui occasionnera un à-coup. Celui-ci est évité par l'utilisation d'un régulateur de différence de pression 85 qui permet d'ajuster la différence de pression ΔP2 entre les points 73 et 84 à une valeur proche mais toujours inférieure à la valeur ΔP1 réglée sur le clapet 76. La pression en 71 est donc maintenue presque constante quelle que soit la résistance offerte par la matière lors du dressage. Ceci permet donc au dispositif de travailler sur une large gamme de matières et de dimensions.It follows that, when dressing small material, the pressure difference required between points 84 and 73 to actuate the diving cylinder 62 would be much lower than the value set on the valve 76. Therefore, when the cylinder 62 will come to a stop, the pressure at fitting 71 will suddenly increase up to a level allowing the opening of the valve 76, which will cause a jerk. This is avoided by the use of a pressure difference regulator 85 which makes it possible to adjust the pressure difference ΔP2 between points 73 and 84 to a value close but always less than the value ΔP1 set on valve 76 The pressure at 71 is therefore kept almost constant whatever the resistance offered by the material during dressing. This therefore allows the device to work on a wide range of materials and dimensions.

La description qui précède montre que l'invention permet de réaliser un dispositif de dressage ayant une construction relativement simple et un encombrement réduit, grâce à la disposition judicieuse des éléments. Par ailleurs, la commande hydraulique est très simple et permet sans difficulté de synchroniser les mouvements d'avance et de plongée du guide central afin d'assurer un dressage optimal du fil. Enfin, les opérations de préparation et de réglage du dispositif pour dresser un type de fil donné sont très simplifiées par rapport aux dispositifs connus, grâce à la suppression du centrage manuel de la matière et à la possibilité de préparer les guides stationnaires hors de la machine.The foregoing description shows that the invention makes it possible to produce a dressing device having a relatively simple construction and a reduced bulk, thanks to the judicious arrangement of the elements. In addition, the hydraulic control is very simple and allows without difficulty to synchronize the movements of advance and diving of the central guide in order to ensure an optimal straightening of the wire. Finally, the operations of preparing and adjusting the device for straightening a given type of wire are very simplified compared to known devices, thanks to the elimination of manual centering of the material and the possibility of preparing the stationary guides outside the machine. .

Les mêmes principes de construction et de fonctionnement sont applicables à un dispositif où c'est le fil qui se déplace longitudinalement pendant l'opération de dressage, grâce à un vérin hydraulique remplaçant le vérin 13, tandis que le rotor reste en place.The same principles of construction and operation are applicable to a device where it is the wire which moves longitudinally during the dressing operation, thanks to a hydraulic cylinder replacing the cylinder 13, while the rotor remains in place.

Claims (10)

  1. Device for straightening a rigid wire, especially wire at the inlet of a machine finishing apparatus, comprising :
    - a frame (1) to which means (8) for maintaining the wire are attached;
    - a rotor (15) attached to means for driving it in continuous rotation, said rotor being provided with an axial conduit (24) longitudinally traversed by the wire,
    - a means for producing backward and forward motion designed to cause relative longitudinal movement between the rotor (15) and the wire (3),
    - a movable central guide (26) traversed by the wire and attached to the rotor so as to be transversely displaced in relation to the axial conduit between a substantially centered and an eccentric position,
    - means for controlling eccentric positioning designed to displace the central guide (26) by means of fluid pressure during rotor rotation, and
    - stationary guides (25) traversed by the wire and disposed in the axial conduit on either side of the central guide,
    characterized in that the means for producing backward and forward motion comprises a first hydraulic jack (13), and in that the means for controlling eccentric positioning comprises a second hydraulic jack (62) hydraulically connected to the first jack (13) so that its functioning speed depends upon that of the first jack.
  2. Device according to claim 1, characterized in that the rotor (15) is attached by bearings (17) to a carriage (6) movable on the frame in the longitudinal direction of the wire (3) and attached to the first jack (13).
  3. Device according to claim 1, in which the central guide (26) comprises a support (44) radially slidable within the rotor and with a contact means (50) at the end farthest from the axle (16) of the rotor, and in which the means for controlling eccentric positioning comprises a slidable bushing (52) attached to the periphery of the rotor so that it turns with it, and having an axially inclined contact surface (51) in contact with said contact means, characterized in that said axially inclined contact surface (51) is formed of a removable element (54) affixed to the slidable bushing (12) and which covers a radial groove (45) to which slidable support (44) of the central guide is attached.
  4. Device according to claim 3, characterized in that said contact means on the slidable support (44) comprises a pulley (50) rotating upon the inclined contact surface, and in that the end opposite said support (44) is in contact with a spring (48) tending to maintain the pulley against said contact surface (51).
  5. Device according to claim 3, characterized in that the means for controlling eccentric positioning comprise a rotatable slidable block (56) attached around the slidable bushing by means of a bearing (57), said block being connected to the second jack (62) and cooperating with stops (63, 64) defining said positions of the central guide.
  6. Device according to claim 1, characterized in that on each side of the central guide (26), the rotor (15) has an axial groove within which a tubular sleeve (28, 29) containing at least two stationary guides (25) is removably attached, beginning at a corresponding rotor extremity.
  7. Device according to claim 6, characterized in that each guide (25, 26) comprises a guide cylinder (40, 42) attached inside a bearing (41, 43), in that each tubular sleeve (28, 29) comprises a cylindrical axial groove, and in that the bearings (41) on the stationary guides are inserted into said sleeve groove and are axially maintained in respective positions chosen by means of interchangeable tubular cross pieces (34, 35, 36).
  8. Device according to claim 1, characterized in that the hydraulic jacks (13, 62) are two-way jacks and in that said second jack (62) controlling the central guide has two opposite chambers which are alternatively connected by means of an electrically controlled solenoid reversal valve (78) to the output (71) of the first jack (13) and to a fluid return conduit (79), so that the speed of each jack is proportionate to the other.
  9. Device according to claim 8, characterized in that said output (71) of the first jack is connected to a return conduit (73) through a spring valve (76) allowing passage of the fluid when the course of the second jack (62) is blocked by a stop (64).
  10. Device according to claim 8, characterized in that it comprises means (23, 81) for measuring the speed of the rotor (15) and to regulate the flow of fluid actuating the first jack (13) as a function of rotor speed.
EP91905046A 1990-03-26 1991-03-21 Device for straightening a wire Expired - Lifetime EP0473739B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT91905046T ATE90238T1 (en) 1990-03-26 1991-03-21 WIRE STRAIGHTENING DEVICE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9003994A FR2659879B1 (en) 1990-03-26 1990-03-26 DEVICE FOR DRESSING A METAL WIRE.
FR9003994 1990-03-26

Publications (2)

Publication Number Publication Date
EP0473739A1 EP0473739A1 (en) 1992-03-11
EP0473739B1 true EP0473739B1 (en) 1993-06-09

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP91905046A Expired - Lifetime EP0473739B1 (en) 1990-03-26 1991-03-21 Device for straightening a wire

Country Status (5)

Country Link
US (1) US5161399A (en)
EP (1) EP0473739B1 (en)
JP (1) JPH04506771A (en)
FR (1) FR2659879B1 (en)
WO (1) WO1991014522A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2463040A1 (en) 2010-12-10 2012-06-13 Wafios Ag Rotary wire straightener
DE102013201551B3 (en) * 2013-01-30 2014-02-27 Wafios Ag Straightening machine for wire

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2708882A1 (en) * 1993-08-10 1995-02-17 Latour Fils Sa Method and device for straightening metal wires for a bending machine
US6527056B2 (en) 2001-04-02 2003-03-04 Ctes, L.C. Variable OD coiled tubing strings
ES2346608B1 (en) * 2007-10-04 2011-08-03 Estrimec, S.L. WIRE ENDERZAADORA MACHINE.

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US1847454A (en) * 1928-06-28 1932-03-01 Ac Spark Plug Co Wire straightener
US2172134A (en) * 1936-07-06 1939-09-05 Wright Albert Frederick James Apparatus for straightening wires and rods
DE1034576B (en) * 1954-11-16 1958-07-24 Evg Entwicklung Verwert Ges Device for straightening wires
US3277682A (en) * 1963-08-30 1966-10-11 A H Nilson Machine Company Wire straighteners
NL7604956A (en) * 1975-05-30 1976-12-02 Louis Hans MACHINE FOR ALIGNING WIRE.
DE2523831C3 (en) * 1975-05-30 1978-07-27 Louis, Hans, 5650 Solingen Device for straightening wire

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2463040A1 (en) 2010-12-10 2012-06-13 Wafios Ag Rotary wire straightener
DE102010054111A1 (en) 2010-12-10 2012-06-14 Wafios Ag Straightening device for the rotating straightening of wire
DE102010054111B4 (en) * 2010-12-10 2013-06-13 Wafios Ag Straightening device for the rotating straightening of wire
DE102013201551B3 (en) * 2013-01-30 2014-02-27 Wafios Ag Straightening machine for wire

Also Published As

Publication number Publication date
US5161399A (en) 1992-11-10
WO1991014522A1 (en) 1991-10-03
FR2659879B1 (en) 1992-07-31
JPH04506771A (en) 1992-11-26
FR2659879A1 (en) 1991-09-27
EP0473739A1 (en) 1992-03-11

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