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EP0370914A1 - Clamping head with clearance compensation - Google Patents

Clamping head with clearance compensation Download PDF

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Publication number
EP0370914A1
EP0370914A1 EP89403242A EP89403242A EP0370914A1 EP 0370914 A1 EP0370914 A1 EP 0370914A1 EP 89403242 A EP89403242 A EP 89403242A EP 89403242 A EP89403242 A EP 89403242A EP 0370914 A1 EP0370914 A1 EP 0370914A1
Authority
EP
European Patent Office
Prior art keywords
clamping
crankshaft
spring
ramp
clamping head
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP89403242A
Other languages
German (de)
French (fr)
Inventor
Maurice Biron
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Polymatic SA
Original Assignee
Polymatic SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Polymatic SA filed Critical Polymatic SA
Publication of EP0370914A1 publication Critical patent/EP0370914A1/en
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B5/00—Clamps
    • B25B5/06—Arrangements for positively actuating jaws
    • B25B5/12—Arrangements for positively actuating jaws using toggle links
    • B25B5/122—Arrangements for positively actuating jaws using toggle links with fluid drive

Definitions

  • the present invention relates to a clamping head for holding or clamping at least one part to be worked or treated, comprising a pivoting clamping member secured to a crankshaft, which is rotatably mounted in a casing and which can be moved between a position clamping and a loosening position by a drive member, which is linearly movable in the casing and which is connected to the crankshaft by a connecting rod assembly comprising at least one connecting rod, one end of which is articulated on the crankshaft and whose l hinge pin at the other end of the connecting rod carries at least one roller, which can roll on a ramp of a movable backrest provided in the casing, said backrest being biased by a spring in a direction orthogonal to the axis of rotation of the crankshaft and of the direction of movement of the drive member, to communicate a clamping force to the clamping member by means of the roller, the connecting rod and the crankshaft equin when it is in the clamping position.
  • the Applicant has already produced in 1984 a clamping head of the above-mentioned type, in which the movable backrest is constituted by a flexible metal blade, which extends roughly parallel to the direction of movement of the drive member and one end of which is rigidly fixed to the casing by a connection of the embedding type.
  • the roller rolls on the flexible blade from the embedded end to the free end of said blade.
  • the blade is deformed by bending around its point of embedding and it compresses the spring which thus stores energy.
  • the longitudinal axis of the connecting rod extends roughly orthogonally to the axis of rotation of the crankshaft and to the direction of movement of the drive member.
  • the clamping force is no longer provided by the drive member, but by the energy stored in the spring. Indeed, it repels the flexible blade, which in turn repels the connecting rod to provide the clamping force.
  • the spring is arranged so as to act on the flexible blade, near the free end of the latter, so that the force exerted by the spring is substantially collinear with the longitudinal axis of the connecting rod in the clamping position.
  • the present invention therefore aims to provide a clamping head in which one can obtain an effective clamping with a spring less powerful than in the known clamping head, and in which the clamping remains effective in a wide range of variation of the thickness of the parts to be clamped.
  • the clamping head of the invention is characterized in that the backrest can pivot around a fulcrum located near the end of the ramp where the roller is located when the crankshaft is in the position of tightening, and in that the spring acts on the backrest at a point which is further from the fulcrum than the point of contact between the roller and the ramp when the crankshaft is in the tightening position.
  • the clamping head shown in Figures 1 and 2 comprises, in known manner, a housing or body 1, composed of two parts 1a and 1b joined to each other by screws 2.
  • a crankshaft 3 is rotatably mounted in the casing 1 by means of bearings 4, ball or needle.
  • At least one of the two ends of the crankshaft 3, for example the two ends 3a and 3b protrude outside the casing 1 and have for example a square cross section to be able to be coupled to a clamping member and to move the one -this when the crankshaft 3 is rotated.
  • the clamping member may comprise, in known manner, a jaw holder 5, in the shape of a stirrup, composed of two arms 5a and 5b, which are fixed, at one of their ends, respectively to the ends 3a and 3b of the crankshaft 3 and, at their other end, at the ends of a spacer 5c.
  • a jaw (not shown) adapted to the shape of the part to be held or clamped, can be fixed in known manner to the jaw holder 5.
  • the clamping head further comprises, in a known manner, a slide 6, which is guided in the casing 1 so as to be able to move in a direction orthogonal to the axis of rotation of the crankshaft 3.
  • the latter is kinematically connected to the slide 6 by a connecting rod, which can comprise in a known manner two connecting rods 7 and 8.
  • the connecting rod 7 is articulated on the crank arm of the crankshaft 3 by an articulation axis 9
  • the connecting rod 8 is articulated on the slide 6 by an axis hinge 11 and the two connecting rods 7 and 8 are hinged together by a hinge pin 12.
  • the slide 6 can be moved in the casing 1 by means of a linear actuator 13, for example a pneumatic or hydraulic cylinder, the cylinder 14 of which is attached to the casing 1 and the piston rod 15 of which is coupled to the slide 6. More specifically, to move the slide 6 upwards (considering Figures 1 and 2), the piston rod 15 of the linear actuator 13 acts on a roller 16 carried by the axis 11 in its middle, while, to move the slide 6 downward, the piston rod 15 acts on a part 17 of the slide 6, which engages radially in a circular groove 18 of the piston rod 15, as is more particularly visible in FIGS. 6 to 8.
  • a linear actuator 13 for example a pneumatic or hydraulic cylinder
  • the clamping head further comprises, in a known manner, a backrest 19, in the form of an elongated piece having a ramp 20, which extends roughly in the direction of movement of the slide 6.
  • a backrest 19 in the form of an elongated piece having a ramp 20, which extends roughly in the direction of movement of the slide 6.
  • On the ramp 20 can roll at least one roller, for example two rollers 21, preferably with needle bearing, which are carried respectively by the ends of the axis 12, on either side of the connecting rod 8.
  • a spring or other elastic member 22 is designed to urge the backrest 19 in a direction which is orthogonal both to the direction of movement of the slide 6 and of the piston rod 15 and to the axis of rotation of the crankshaft 3.
  • the spring 22 acts in a direction such that , when the movable elements 3,6,7,8 and 15 of the clamping head occupy respective positions shown in Figures 2,6 and 8, corresponding to the closed position or clamping position of the clamping head (it will be noted that in this position the connecting rod 7 extends in a d irection parallel to the direction of action of the spring 22), the spring 22 transmits a clamping force to the jaw holder 5 via the backrest 19, the rollers 21, the connecting rod 7 and the crankshaft 3.
  • the backrest 19 can pivot around a fulcrum, for example a hinge pin 23, which is located near the end upper of the ramp 20 by considering Figures 1,2 and 8, that is to say near the end where the rollers 21 are located when the crankshaft 3 is in the clamping position ( Figures 2 and 8).
  • the spring 22 acts on the backrest 19 at a place thereof which is further from the hinge pin 23 than the point C of contact between the rollers 21 and the ramp 20, when the crankshaft 3 is in the clamping position. In this way, the force applied by the spring 22 to the backrest 19 and transmitted by the latter to the crankshaft 3, via the connecting rod 7, is multiplied by a leverage.
  • the clamping head of the invention makes it possible to obtain a greater final clamping force with a spring 22 of force equal to that of the spring of the known clamping head, or, at equal clamping forces, it allows to use a weaker spring 22 than in the known clamping head.
  • the spring 22 is constituted by a helical spring, since such a spring makes it possible to maintain an effective tightening even if the thickness of the part to be clamped varies to a relatively large extent compared to its nominal thickness (more or less 3mm in the example shown here).
  • the spring 22 may also be constituted by Belleville washers or even by a pad of elastomeric material.
  • the spring 22 will preferably be constituted by a mechanical spring (spring helical or Belleville washers) rather than by a pad made of an elastomeric material, because the pads of elastomeric material generally have elasticity characteristics which are less stable over time and which vary greatly with the frequency of the compressive stresses to which they are submitted.
  • the ramp 20 has a rectilinear profile over most of its length, and it has a hollow part 20a (FIGS. 1 and 8) near the axis of articulation 23 and a boss. 20b (better visible in FIGS. 7 and 8) at the free end of the ramp 20.
  • the hollow part 20a defines, in combination with the rollers 21 and the spring 22, a locking means capable of elastically holding the movable elements of the clamping head in the clamping position even in the event of a lack of compressed fluid in the jack 13.
  • the boss 20b defines, in combination with the rollers 21 and the spring 22, a locking means which resiliently maintains the movable elements of the clamping head in the open position or in the loosening position, even in the event of a lack of compressed fluid in the jack 13.
  • the clamping head which has been described above operates in the following manner. To begin with, it will be assumed that the movable elements of the clamping head are in the position shown in FIGS. 1 and 5, position in which the piston rod 15 of the jack 13 is completely retracted into the cylinder 14 under the action of 'a fluid under pressure admitted by an appropriate orifice of the cylinder 14. It will be noted that, even in the event of a lack of fluid under pressure, under the action of the spring 22 the boss 20b of the ramp 20 acts by its inclined part 20c (FIG. 8) on the rollers 21 to block them and, consequently, maintain the clamping head in the open position.
  • the backrest 19 Immediately after the rollers 21 have crossed the hard point formed by the boss 20b, the backrest 19 returns to its original position and as long as the jaw (not shown) carried by the jaw holder 5 does not encounter any obstacle (part to be clamped), the mobile assembly formed by elements 6, 7 and 8 moves upwards ( considering Figures 1 and 2) under the action of the piston rod 15, obliga nt thus the crankshaft 3 to rotate anti-clockwise and the jaw holder 5 to pivot correspondingly. During this time, the rollers 21 roll on the straight part of the ramp 20 without compressing the spring 22.
  • the resulting reaction force applies to the crankshaft 3 a reaction torque, directed clockwise, such as the rollers 21, while continuing to roll on the ramp 20, pushes the backrest 19 by pivoting it around its articulation axis 23 anticlockwise, thus compressing the spring 22.
  • the clamping head can be opened again by controlling the jack 13 so as to bring in its piston rod 15.
  • the slide 6 drives down the connecting rod 8 which rotates the connecting rod 7 about its articulation axis 9.
  • the backrest 19, pushing the rollers 21 under the action of the spring 22, rotates quickly the connecting rod 7 around its hinge axis 9.
  • two elastic buffers 24 (FIG. 4) are provided in said casing.
  • the spring 22 expands and the backrest 19 abuts against the shoulders 25 (FIG. 4) provided in the casing 1.
  • the boss 20b of the ramp 20 acts on the rollers 21 to maintain the clamping head in the open position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jigs For Machine Tools (AREA)
  • Chairs For Special Purposes, Such As Reclining Chairs (AREA)
  • Clamps And Clips (AREA)
  • Chain Conveyers (AREA)

Abstract

In this clamping head for holding or gripping at least one piece to be worked or treated, comprising a gripping member (5) fixed to a crank (3) movable by a drive member connected to the crank (3) by means of a linkage (7, 8) comprising at least one link (7), a pivot axle (12) carries at least one roller (21) which can roll on a ramp (20) of a movable back plate stressed by a spring (22), in order to impart a gripping force to the gripping member (5), the back plate (19) can pivot about a bearing point (23) located near the end of the ramp (20) where the roller (21) is situated when the crank (3) is in the gripping position, and the spring (22) acts on the back plate (19) at a point which is further from the bearing point (23) than the contact point between the roller (21) and the ramp (20) when the crank (3) is in the gripping position. <IMAGE>

Description

La présente invention concerne une tête de bridage pour tenir ou serrer au moins une pièce à travailler ou à traiter, comprenant un organe pivotant de serrage solidaire d'un vilebrequin, qui est monté à rotation dans un carter et qui peut être déplacé entre une position de serrage et une position de desserrage par un organe d'entraînement, qui est linéairement mobile dans le carter et qui est relié au vilebrequin par un embiellage comportant au moins une bielle, dont l'une des extrémités est articulée sur le villebrequin et dont l'axe d'articulation, à l'autre extrémité de la bielle, porte au moins un galet, qui peut rouler sur une rampe d'un dossier mobile prévu dans le carter, ledit dossier étant sollicité par un ressort dans une direction orthogonale à l'axe de rotation du vilebrequin et à la direction de mouvement de l'organe d'entraînement, pour communiquer une force de serrage à l'organe de serrage par l'intermédiaire du galet, de la bielle et du vilebrequin quand celui-ci est dans la position de serrage.The present invention relates to a clamping head for holding or clamping at least one part to be worked or treated, comprising a pivoting clamping member secured to a crankshaft, which is rotatably mounted in a casing and which can be moved between a position clamping and a loosening position by a drive member, which is linearly movable in the casing and which is connected to the crankshaft by a connecting rod assembly comprising at least one connecting rod, one end of which is articulated on the crankshaft and whose l hinge pin at the other end of the connecting rod carries at least one roller, which can roll on a ramp of a movable backrest provided in the casing, said backrest being biased by a spring in a direction orthogonal to the axis of rotation of the crankshaft and of the direction of movement of the drive member, to communicate a clamping force to the clamping member by means of the roller, the connecting rod and the crankshaft equin when it is in the clamping position.

La Demanderesse a déjà réalisé en 1984 une tête de bridage du type sus-indiqué, dans laquelle le dossier mobile est constitué par une lame métallique flexible, qui s'étend en gros parallèlement à la direction de mouvement de l'organe d'entraînement et dont l'une des extrémités est fixée rigidement au carter par une liaison du type encastrement. Quand l'organe d'entraînement se déplace depuis la position correspondant au desserrage à la position correspondant au serrage, le galet roule sur la lame flexible de l'extrémité encastrée vers l'extrémité libre de ladite lame. Pendant ce mouvement du galet, la lame est déformée par flexion autour de son point d'encastrement et elle comprime le ressort qui emmagasine de ce fait de l'énergie. Quand le vilebrequin arrive dans la position de serrage, l'axe longitudinal de la bielle s'étend en gros orthogonalement à l'axe de rotation du vilebrequin et à la direction de mouvement de l'organe d'entraînement. Dans ces conditions, l'effort de serrage n'est plus fourni par l'organe d'entraînement, mais par l'énergie emmagasinée dans le ressort. En effet, celui-­ci repousse la lame flexible, qui repousse à son tour la bielle pour fournir l'effort de serrage. Dans la tête de bridage connue, le ressort est disposé de manière à agir sur la lame flexible, près de l'extrémité libre de celle-ci, de telle façon que la force exercée par le ressort soit sensiblement colinéaire avec l'axe longitudinal de la bielle dans la position de serrage. Bien qu'avec un tel arrangement de la tête de bridage connue il soit en principe possible de serrer des pièces dont l'épaisseur peut varier dans les limites d'une certaine tolérance, il s'est avéré, dans la pratique, qu'il fallait utiliser un puissant ressort (un empilage de rondelles Belleville associées à un piston) pour obtenir un serrage efficace, et que la plage de tolérance sur l'épaisseur des pièces à serrer, dans laquelle le serrage reste efficace, était relativement étroite.The Applicant has already produced in 1984 a clamping head of the above-mentioned type, in which the movable backrest is constituted by a flexible metal blade, which extends roughly parallel to the direction of movement of the drive member and one end of which is rigidly fixed to the casing by a connection of the embedding type. When the drive member moves from the position corresponding to the loosening to the corresponding position when tightening, the roller rolls on the flexible blade from the embedded end to the free end of said blade. During this movement of the roller, the blade is deformed by bending around its point of embedding and it compresses the spring which thus stores energy. When the crankshaft arrives in the tightening position, the longitudinal axis of the connecting rod extends roughly orthogonally to the axis of rotation of the crankshaft and to the direction of movement of the drive member. Under these conditions, the clamping force is no longer provided by the drive member, but by the energy stored in the spring. Indeed, it repels the flexible blade, which in turn repels the connecting rod to provide the clamping force. In the known clamping head, the spring is arranged so as to act on the flexible blade, near the free end of the latter, so that the force exerted by the spring is substantially collinear with the longitudinal axis of the connecting rod in the clamping position. Although with such an arrangement of the known clamping head it is in principle possible to clamp parts whose thickness may vary within the limits of a certain tolerance, it has proved in practice that it was necessary to use a powerful spring (a stack of Belleville washers associated with a piston) to obtain an effective clamping, and that the tolerance range on the thickness of the parts to be clamped, in which the clamping remains effective, was relatively narrow.

La présente invention a donc pour but de fournir une tête de bridage dans laquelle on peut obtenir un serrage efficace avec un ressort moins puissant que dans la tête de bridage connue, et dans laquelle le serrage reste efficace dans une large plage de variation de l'épaisseur des pièces à serrer.The present invention therefore aims to provide a clamping head in which one can obtain an effective clamping with a spring less powerful than in the known clamping head, and in which the clamping remains effective in a wide range of variation of the thickness of the parts to be clamped.

A cet effet, la tête de bridage de l'invention est caractérisée en ce que le dossier peut pivoter autour d'un point d'appui situé près de l'extrémité de la rampe où se trouve le galet quand le vilebrequin est en position de serrage, et en ce que le ressort agit sur le dossier en un point qui est plus éloigné du point d'appui que le point de contact entre le galet et la rampe quand le vilebrequin est en position de serrage.To this end, the clamping head of the invention is characterized in that the backrest can pivot around a fulcrum located near the end of the ramp where the roller is located when the crankshaft is in the position of tightening, and in that the spring acts on the backrest at a point which is further from the fulcrum than the point of contact between the roller and the ramp when the crankshaft is in the tightening position.

Grâce à une telle disposition, on obtient un effet multiplicateur ou effet de levier, qui permet d'utiliser un ressort moins puissant que dans la tête de bridage connue, par exemple un ressort hélicoïdal, qui, à encombrement longitudinal égal, conserve une efficacité sur une plus grande plage de compression.Thanks to such an arrangement, a multiplier or leverage effect is obtained, which makes it possible to use a spring which is less powerful than in the known clamping head, for example a helical spring, which, with equal longitudinal dimensions, retains an efficiency on greater compression range.

D'autres caractéristiques et avantages de la présente invention ressortiront mieux au cours de la description qui va suivre d'une forme d'exécution de l'invention donnée à titre d'exemple en faisant référence aux dessins annexés sur lesquels :

  • la figure 1 est une vue en coupe verticale de la tête de bridage de l'invention, les éléments mobiles de la tête étant représentés dans une position correspondant à la position ouverte ou position de desserrage de ladite tête.
  • La figure 2 est une vue semblable à la figure 1, les éléments mobiles étant montrés dans une position correspondant à la position fermée ou position de serrage de la tête de bridage.
  • La figure 3 est une vue en coupe suivant la ligne III-III de la figure 1.
  • La figure 4 est une vue en coupe suivant la ligne IV-­IV de la figure 2.
  • La figure 5 est une vue en coupe suivant la ligne V-V de la figure 1.
  • La figure 6 est une vue en coupe suivant la ligne VI-­VI de la figure 2.
  • Les figures 7 et 8 montrent, à plus grande échelle, des détails des figures 1 et 2.
Other characteristics and advantages of the present invention will emerge more clearly during the following description of an embodiment of the invention given by way of example with reference to the appended drawings in which:
  • Figure 1 is a vertical sectional view of the clamping head of the invention, the movable elements of the head being shown in a position corresponding to the open position or loosening position of said head.
  • Figure 2 is a view similar to Figure 1, the movable elements being shown in a position corresponding to the closed position or clamping position of the clamping head.
  • Figure 3 is a sectional view along line III-III of Figure 1.
  • Figure 4 is a sectional view along line IV-IV of Figure 2.
  • Figure 5 is a sectional view along the line VV of Figure 1.
  • Figure 6 is a sectional view along line VI-VI of Figure 2.
  • Figures 7 and 8 show, on a larger scale, details of Figures 1 and 2.

La tête de bridage montrée dans les figures 1 et 2 comprend, de façon connue, un carter ou corps 1, composé de deux parties 1a et 1b assemblées l'une à l'autre par des vis 2. Un vilebrequin 3 est monté à rotation dans le carter 1 par l'intermédiaire de roulements 4, à billes ou à aiguilles. Au moins l'une des deux extrémités du vilebrequin 3, par exemple les deux extrémités 3a et 3b font saillie à l'extérieur du carter 1 et ont par exemple une section transversale carrée pour pouvoir être accouplées à un organe de serrage et pour mouvoir celui-ci quand le vilebrequin 3 est animé d'un mouvement de rotation. L'organe de serrage peut comprendre, de façon connue, un porte-mâchoire 5, en forme d'étrier, composé de deux bras 5a et 5b, qui sont fixés, à une de leurs extrémités, respectivement aux extrémités 3a et 3b du vilebrequin 3 et, à leur autre extrémité, aux extrémités d'une entretoise 5c. Une mâchoire (non montrée) adaptée à la forme de la pièce à tenir ou à serrer, peut être fixée de façon connue au porte-­mâchoire 5.The clamping head shown in Figures 1 and 2 comprises, in known manner, a housing or body 1, composed of two parts 1a and 1b joined to each other by screws 2. A crankshaft 3 is rotatably mounted in the casing 1 by means of bearings 4, ball or needle. At least one of the two ends of the crankshaft 3, for example the two ends 3a and 3b protrude outside the casing 1 and have for example a square cross section to be able to be coupled to a clamping member and to move the one -this when the crankshaft 3 is rotated. The clamping member may comprise, in known manner, a jaw holder 5, in the shape of a stirrup, composed of two arms 5a and 5b, which are fixed, at one of their ends, respectively to the ends 3a and 3b of the crankshaft 3 and, at their other end, at the ends of a spacer 5c. A jaw (not shown) adapted to the shape of the part to be held or clamped, can be fixed in known manner to the jaw holder 5.

La tête de bridage comporte en outre, de façon connue, un coulisseau 6, qui est guidé dans le carter 1 de façon à pouvoir se déplacer dans une direction orthogonale à l'axe de rotation du vilebrequin 3. Ce dernier est relié cinématiquement au coulisseau 6 par un embiellage, qui peut comprendre de façon connue deux bielles 7 et 8. La bielle 7 est articulée sur le bras de manivelle du vilebrequin 3 par un axe d'articulation 9, la bielle 8 est articulée sur le coulisseau 6 par un axe d'articulation 11 et les deux bielles 7 et 8 sont articulées entre elles par un axe d'articulation 12.The clamping head further comprises, in a known manner, a slide 6, which is guided in the casing 1 so as to be able to move in a direction orthogonal to the axis of rotation of the crankshaft 3. The latter is kinematically connected to the slide 6 by a connecting rod, which can comprise in a known manner two connecting rods 7 and 8. The connecting rod 7 is articulated on the crank arm of the crankshaft 3 by an articulation axis 9, the connecting rod 8 is articulated on the slide 6 by an axis hinge 11 and the two connecting rods 7 and 8 are hinged together by a hinge pin 12.

Le coulisseau 6 peut être déplacé dans le carter 1 au moyen d'un actionneur linéaire 13, par exemple un vérin pneumatique ou hydraulique, dont le cylindre 14 est attaché au carter 1 et dont la tige de piston 15 est accouplée au coulisseau 6. Plus précisément, pour déplacer le coulisseau 6 vers le haut (en considérant les figures 1 et 2), la tige de piston 15 de l'actionneur linéaire 13 agit sur un galet 16 porté par l'axe 11 en son milieu, tandis que, pour déplacer le coulisseau 6 vers le bas, la tige de piston 15 agit sur une partie 17 du coulisseau 6, qui s'engage radialement dans une gorge circulaire 18 de la tige de piston 15, comme cela est plus particulièrement visible dans les figures 6 à 8.The slide 6 can be moved in the casing 1 by means of a linear actuator 13, for example a pneumatic or hydraulic cylinder, the cylinder 14 of which is attached to the casing 1 and the piston rod 15 of which is coupled to the slide 6. More specifically, to move the slide 6 upwards (considering Figures 1 and 2), the piston rod 15 of the linear actuator 13 acts on a roller 16 carried by the axis 11 in its middle, while, to move the slide 6 downward, the piston rod 15 acts on a part 17 of the slide 6, which engages radially in a circular groove 18 of the piston rod 15, as is more particularly visible in FIGS. 6 to 8.

La tête de bridage comporte en outre, de façon connue, un dossier 19, sous la forme d'une pièce allongée présentant une rampe 20, qui s'étend en gros dans la direction de mouvement du coulisseau 6. Sur la rampe 20 peut rouler au moins un galet, par exemple deux galets 21, de préférence avec roulement à aiguilles, qui sont portés respectivement par les extrémités de l'axe 12, de part et d'autre de la bielle 8. Un ressort ou autre organe élastique 22 est prévu pour solliciter le dossier 19 dans une direction qui est orthogonale à la fois à la direction de mouvement du coulisseau 6 et de la tige de piston 15 et à l'axe de rotation du vilebrequin 3. Le ressort 22 agit dans un sens tel que, lorsque les éléments mobiles 3,6,7,8 et 15 de la tête de bridage occupent des positions respectives montrées sur les figures 2,6 et 8, correspondant à la position fermée ou position de serrage de la tête de bridage (on notera que dans cette position la bielle 7 s'étend dans une direction parallèle à la direction d'action du ressort 22), le ressort 22 transmette une force de serrage au porte-mâchoire 5 par l'intermédiaire du dossier 19, des galets 21, de la bielle 7 et du vilebrequin 3.The clamping head further comprises, in a known manner, a backrest 19, in the form of an elongated piece having a ramp 20, which extends roughly in the direction of movement of the slide 6. On the ramp 20 can roll at least one roller, for example two rollers 21, preferably with needle bearing, which are carried respectively by the ends of the axis 12, on either side of the connecting rod 8. A spring or other elastic member 22 is designed to urge the backrest 19 in a direction which is orthogonal both to the direction of movement of the slide 6 and of the piston rod 15 and to the axis of rotation of the crankshaft 3. The spring 22 acts in a direction such that , when the movable elements 3,6,7,8 and 15 of the clamping head occupy respective positions shown in Figures 2,6 and 8, corresponding to the closed position or clamping position of the clamping head (it will be noted that in this position the connecting rod 7 extends in a d irection parallel to the direction of action of the spring 22), the spring 22 transmits a clamping force to the jaw holder 5 via the backrest 19, the rollers 21, the connecting rod 7 and the crankshaft 3.

Conformément à la présente invention, le dossier 19 peut pivoter autour d'un point d'appui, par exemple un axe d'articulation 23, qui est situé près de l'extrémité supérieure de la rampe 20 en considérant les figures 1,2 et 8, c'est-à-dire près de l'extrémité où se trouvent les galets 21 quand le vilebrequin 3 est en position de serrage (figures 2 et 8). En outre, suivant une autre caractéristique de l'invention, le ressort 22 agit sur le dossier 19 à un endroit de celui-ci qui est plus éloigné de l'axe d'articulation 23 que le point C de contact entre les galets 21 et la rampe 20, quand le vilebrequin 3 est en position de serrage. De cette manière, la force appliquée par le ressort 22 au dossier 19 et transmise par celui-ci au vilebrequin 3, par l'intermédiaire de la bielle 7, est multipliée par un effet de levier. Il en résulte que, en comparaison des têtes de bridage antérieurement connues, dans lesquelles le dossier était encastré à son extrémité inférieure dans le carter et dans lesquelles la direction d'action du ressort était confondue avec l'axe longitudinal de la bielle 7 en position de serrage, la tête de bridage de l'invention permet d'obtenir une force finale de serrage plus grande avec un ressort 22 de force égale à celle du ressort de la tête de bridage connue, ou, à forces égales de serrage, elle permet d'utiliser un ressort 22 plus faible que dans la tête de bridage connue. De préférence, le ressort 22 est constitué par un ressort hélicoïdal, car un tel ressort permet de conserver un serrage efficace même si l'épaisseur de la pièce à serrer varie dans une mesure relativement large par rapport à son épaisseur nominale (plus ou moins 3mm dans l'exemple représenté ici). Toutefois, si cette condition n'est pas critique, le ressort 22 pourra également être constitué par des rondelles Belleville ou encore par un tampon en matière élastomère. Toutefois, dans tous les cas où l'organe de serrage de la tête de bridage devra pouvoir être fermé et ouvert de manière répétitive à brefs intervalles de temps, le ressort 22 sera de préférence constitué par un ressort mécanique (ressort hélicoïdal ou rondelles Belleville) plutôt que par un tampon en une matière élastomère, car les tampons en matière élastomère ont en général des caractéristiques d'élasticité qui sont moins stables dans le temps et qui varient grandement avec la fréquence des contraintes de compression auxquelles ils sont soumis.According to the present invention, the backrest 19 can pivot around a fulcrum, for example a hinge pin 23, which is located near the end upper of the ramp 20 by considering Figures 1,2 and 8, that is to say near the end where the rollers 21 are located when the crankshaft 3 is in the clamping position (Figures 2 and 8). In addition, according to another characteristic of the invention, the spring 22 acts on the backrest 19 at a place thereof which is further from the hinge pin 23 than the point C of contact between the rollers 21 and the ramp 20, when the crankshaft 3 is in the clamping position. In this way, the force applied by the spring 22 to the backrest 19 and transmitted by the latter to the crankshaft 3, via the connecting rod 7, is multiplied by a leverage. It follows that, in comparison with the previously known clamping heads, in which the backrest was embedded at its lower end in the casing and in which the direction of action of the spring coincided with the longitudinal axis of the connecting rod 7 in position clamping, the clamping head of the invention makes it possible to obtain a greater final clamping force with a spring 22 of force equal to that of the spring of the known clamping head, or, at equal clamping forces, it allows to use a weaker spring 22 than in the known clamping head. Preferably, the spring 22 is constituted by a helical spring, since such a spring makes it possible to maintain an effective tightening even if the thickness of the part to be clamped varies to a relatively large extent compared to its nominal thickness (more or less 3mm in the example shown here). However, if this condition is not critical, the spring 22 may also be constituted by Belleville washers or even by a pad of elastomeric material. However, in all cases where the clamping head of the clamping head must be able to be closed and repeatedly opened at short intervals, the spring 22 will preferably be constituted by a mechanical spring (spring helical or Belleville washers) rather than by a pad made of an elastomeric material, because the pads of elastomeric material generally have elasticity characteristics which are less stable over time and which vary greatly with the frequency of the compressive stresses to which they are submitted.

Suivant une autre caractéristique de l'invention, la rampe 20 a un profil rectiligne sur la majeure partie de sa longueur, et elle comporte une partie en creux 20a (figures 1 et 8) près de l'axe d'articulation 23 et un bossage 20b (mieux visible dans les figures 7 et 8) à l'extrémité libre de la rampe 20. La partie en creux 20a définit, en combinaison avec les galets 21 et le ressort 22, un moyen de blocage propre à maintenir élastiquement les éléments mobiles de la tête de bridage en position de serrage même en cas de manque de fluide comprimé dans le vérin 13. De même, le bossage 20b définit, en combinaison avec les galets 21 et le ressort 22, un moyen de blocage, qui maintient élastiquement les éléments mobiles de la tête de bridage en position ouverte ou position de desserrage, même en cas de manque de fluide comprimé dans le vérin 13.According to another characteristic of the invention, the ramp 20 has a rectilinear profile over most of its length, and it has a hollow part 20a (FIGS. 1 and 8) near the axis of articulation 23 and a boss. 20b (better visible in FIGS. 7 and 8) at the free end of the ramp 20. The hollow part 20a defines, in combination with the rollers 21 and the spring 22, a locking means capable of elastically holding the movable elements of the clamping head in the clamping position even in the event of a lack of compressed fluid in the jack 13. Similarly, the boss 20b defines, in combination with the rollers 21 and the spring 22, a locking means which resiliently maintains the movable elements of the clamping head in the open position or in the loosening position, even in the event of a lack of compressed fluid in the jack 13.

La tête de bridage qui a été décrite ci-dessus fonctionne de la manière suivante. Pour commencer, on supposera que les éléments mobiles de la tête de bridage se trouvent dans la position montrée sur les figures 1 et 5, position dans laquelle la tige de piston 15 du vérin 13 est complètement rentrée dans le cylindre 14 sous l'action d'un fluide sous pression admis par un orifice approprié du cylindre 14. On notera que, même en cas de manque de fluide sous pression, sous l'action du ressort 22 le bossage 20b de la rampe 20 agit par sa partie inclinée 20c (figure 8) sur les galets 21 pour bloquer ceux-ci et, par suite, maintenir la tête de bridage dans la position ouverte.The clamping head which has been described above operates in the following manner. To begin with, it will be assumed that the movable elements of the clamping head are in the position shown in FIGS. 1 and 5, position in which the piston rod 15 of the jack 13 is completely retracted into the cylinder 14 under the action of 'a fluid under pressure admitted by an appropriate orifice of the cylinder 14. It will be noted that, even in the event of a lack of fluid under pressure, under the action of the spring 22 the boss 20b of the ramp 20 acts by its inclined part 20c (FIG. 8) on the rollers 21 to block them and, consequently, maintain the clamping head in the open position.

Quand la source de fluide sous pression est commutée pour admettre le fluide sous pression dans le cylindre 14 à travers un autre orifice de celui-ci, pour faire sortir la tige de piston 15, celle-ci applique, par l'intermédiaire du galet 16 et de l'axe 11, une poussée à la bielle 8. Cette poussée est transmise, par l'intermédiaire de l'axe 12 et des galets 21, au dossier 19, ce qui a pour effet de le faire pivoter autour de son axe d'articulation 23 en comprimant le ressort 22. Il en résulte que le bossage 20b de la rampe 20 s'efface pour laisser passer les galets 21. Aussitôt après que les galets 21 ont franchi le point dur constitué par le bossage 20b, le dossier 19 reprend sa place initiale et tant que la mâchoire (non montrée) portée par le porte-­mâchoire 5 ne rencontre aucun obstacle (pièce à serrer), l'équipage mobile formé par les éléments 6,7 et 8 se déplace vers le haut (en considérant les figures 1 et 2) sous l'action de la tige de piston 15, obligeant ainsi le vilebrequin 3 à tourner dans le sens inverse des aiguilles d'une montre et le porte-mâchoire 5 à pivoter de manière correspondante. Pendant ce temps, les galets 21 roulent sur la partie rectiligne de la rampe 20 sans comprimer le ressort 22.When the source of pressurized fluid is switched to admit the pressurized fluid into the cylinder 14 through another orifice therein, to cause the piston rod 15 to come out, the latter applies, by means of the roller 16 and from the axis 11, a thrust at the connecting rod 8. This thrust is transmitted, via the axis 12 and the rollers 21, to the backrest 19, which has the effect of making it pivot about its axis 23 by compressing the spring 22. As a result, the boss 20b of the ramp 20 disappears to allow the rollers to pass 21. Immediately after the rollers 21 have crossed the hard point formed by the boss 20b, the backrest 19 returns to its original position and as long as the jaw (not shown) carried by the jaw holder 5 does not encounter any obstacle (part to be clamped), the mobile assembly formed by elements 6, 7 and 8 moves upwards ( considering Figures 1 and 2) under the action of the piston rod 15, obliga nt thus the crankshaft 3 to rotate anti-clockwise and the jaw holder 5 to pivot correspondingly. During this time, the rollers 21 roll on the straight part of the ramp 20 without compressing the spring 22.

Quand la mâchoire fixée au porte-mâchoire 5 rencontre la pièce à serrer, la force de réaction qui en résulte applique au vilebrequin 3 un couple de réaction, dirigé dans le sens des aiguilles d'une montre, tel que les galets 21, tout en continuant à rouler sur la rampe 20, pousse le dossier 19 en le faisant pivoter autour de son axe d'articulation 23 dans le sens inverse des aiguilles d'une montre, comprimant ainsi le ressort 22.When the jaw attached to the jaw holder 5 meets the part to be clamped, the resulting reaction force applies to the crankshaft 3 a reaction torque, directed clockwise, such as the rollers 21, while continuing to roll on the ramp 20, pushes the backrest 19 by pivoting it around its articulation axis 23 anticlockwise, thus compressing the spring 22.

Quand la tige de piston 15 arrive dans la position montrée dans les figures 2,6 et 8, les bielles 7 et 8 étant pratiquement en butée contre la paroi supérieure de la cavité interne du carter 1, les galets 21 s'engagent dans la partie en creux 20a de la rampe 20. A ce moment, l'axe longitudinal de la bielle 7 s'étend perpendiculairement à la fois à l'axe longitudinal de la tige de piston 15 et à l'axe de rotation du vilebrequin 3. Il en résulte que la tige de piston 15 ne fournit plus aucun effort utile pour le serrage, l'effort de serrage étant alors uniquement fourni par le ressort 22, dont la force est transmise au porte-mâchoire 5 par l'intermédiaire du dossier 19, des galets 21, de la bielle 7 et du vilebrequin 3. On notera que même en cas de manque de fluide sous pression dans le vérin 14, la tête de bridage reste alors dans la position fermée du fait de l'engagement des galets 21 dans la partie en creux 20a de la rampe 20.When the piston rod 15 arrives in the position shown in FIGS. 2,6 and 8, the connecting rods 7 and 8 being practically in abutment against the upper wall of the internal cavity of the casing 1, the rollers 21 engage in the part recessed 20a of the ramp 20. A this moment, the longitudinal axis of the connecting rod 7 extends perpendicular both to the longitudinal axis of the piston rod 15 and to the axis of rotation of the crankshaft 3. As a result, the piston rod 15 does not no longer provides any useful force for tightening, the tightening force then being only supplied by the spring 22, the force of which is transmitted to the jaw holder 5 via the backrest 19, the rollers 21, the connecting rod 7 and of the crankshaft 3. It will be noted that even in the event of a lack of pressurized fluid in the jack 14, the clamping head then remains in the closed position due to the engagement of the rollers 21 in the hollow part 20a of the ramp 20 .

Quand la ou les pièces serrées par la tête de bridage a ou ont subi le traitement désiré, la tête de bridage peut être à nouveau ouverte en commandant le vérin 13 de manière a faire rentrer sa tige de piston 15. Au début du mouvement de rentrée de la tige de piston 15, le coulisseau 6 entraîne vers le bas la bielle 8 qui fait tourner la bielle 7 autour de son axe d'articulation 9. Le dossier 19, poussant les galets 21 sous l'action du ressort 22, fait tourner rapidement la bielle 7 autour de son axe d'articulation 9. Afin d'amortir le choc des galets 21 sur des guides intérieurs du carter 1, deux tampons élastiques 24 (figure 4) sont prévus dans ledit carter. Pendant le mouvement de rentrée de la tige de piston 15, le ressort 22 se détend et le dossier 19 vient en butée contre des épaulements 25 (figure 4) prévus dans le carter 1. A la fin du mouvement de rentrée de la tige de piston 15, le bossage 20b de la rampe 20 vient agir sur les galets 21 pour maintenir la tête de bridage dans la position ouverte.When the piece (s) clamped by the clamping head has or have undergone the desired treatment, the clamping head can be opened again by controlling the jack 13 so as to bring in its piston rod 15. At the start of the retraction movement of the piston rod 15, the slide 6 drives down the connecting rod 8 which rotates the connecting rod 7 about its articulation axis 9. The backrest 19, pushing the rollers 21 under the action of the spring 22, rotates quickly the connecting rod 7 around its hinge axis 9. In order to absorb the impact of the rollers 21 on the inner guides of the casing 1, two elastic buffers 24 (FIG. 4) are provided in said casing. During the retraction movement of the piston rod 15, the spring 22 expands and the backrest 19 abuts against the shoulders 25 (FIG. 4) provided in the casing 1. At the end of the retraction movement of the piston rod 15, the boss 20b of the ramp 20 acts on the rollers 21 to maintain the clamping head in the open position.

Il va de soi que la forme d'exécution de l'invention qui a été décrite ci-dessus a été donnée à titre d'exemple purement indicatif et nullement limitatif, et que de nombreuses modifications peuvent être facilement apportées par l'homme de l'art sans pour autant sortir du cadre de la présente invention tel qu'il est défini dans les revendications suivantes. Par exemple, au lieu de relier le vilebrequin 3 au coulisseau 6 par un embiellage composé de deux bielles 7 et 8, l'embiellage peut ne comporter qu'une seule bielle comme cela est connu.It goes without saying that the embodiment of the invention which has been described above has been given by way of purely indicative and in no way limiting example, and that numerous modifications can be easily provided by those skilled in the art without departing from the scope of the present invention as defined in the following claims. For example, instead of connecting the crankshaft 3 to the slide 6 by a connecting rod assembly made up of two connecting rods 7 and 8, the connecting rod assembly can comprise only one connecting rod as is known.

Claims (4)

1.- Tête de bridage pour tenir ou serrer au moins une pièce à travailler au à traiter, comprenant un organe pivotant de serrage (5) solidaire d'un vilebrequin (3), qui est monté à rotation dans un carter (1) et qui peut être déplacé entre une position de serrage et une position de desserrage par un organe d'entraînement (6,15), qui est linéairement mobile dans le carter (1) et qui est relié au vilebrequin (3) par un embiellage (7,8) comportant au moins une bielle (7), dont l'une des extrémités est articulée sur le vilebrequin et dont l'axe d'articulation (12), à l'autre extrémité de la bielle, porte au moins un galet (21), qui peut rouler sur une rampe (20) d'un dossier mobile (19) prévu dans le carter (1), ledit dossier étant sollicité par un ressort (22) dans une direction orthogonale à l'axe de rotation du vilebrequin (3) et à la direction de mouvement de l'organe d'entraînement (6, 15), pour communiquer une force de serrage à l'organe de serrage (5) par l'intermédiaire du galet (21), de la bielle (7) et du vilebrequin (3) quand celui-ci est dans la position de serrage, caractérisée en ce que le dossier (19) peut pivoter autour d'un point d'appui (23) situé près de l'extrémité de la rampe (20) où se trouve le galet (21) quand le vilebrequin (3) est en position de serrage, et en ce que le ressort (22) agit sur le dossier (19) en un point qui est plus éloigné du point d'appui (23) que le point de contact (C) entre le galet (21) et la rampe (20) quand le vilebrequin (3) est en position de serrage.1.- Clamping head for holding or clamping at least one workpiece to be treated, comprising a pivoting clamping member (5) integral with a crankshaft (3), which is rotatably mounted in a casing (1) and which can be moved between a clamping position and a loosening position by a drive member (6,15), which is linearly movable in the housing (1) and which is connected to the crankshaft (3) by a connecting rod (7 , 8) comprising at least one connecting rod (7), one of whose ends is articulated on the crankshaft and whose articulation axis (12), at the other end of the connecting rod, carries at least one roller ( 21), which can roll on a ramp (20) of a movable backrest (19) provided in the casing (1), said backrest being biased by a spring (22) in a direction orthogonal to the axis of rotation of the crankshaft (3) and to the direction of movement of the drive member (6, 15), to communicate a clamping force to the clamping member (5) through the i n intermediate of the roller (21), the connecting rod (7) and the crankshaft (3) when the latter is in the clamping position, characterized in that the backrest (19) can pivot around a fulcrum ( 23) located near the end of the ramp (20) where the roller (21) is located when the crankshaft (3) is in the clamping position, and in that the spring (22) acts on the backrest (19) at a point which is further from the fulcrum (23) than the point of contact (C) between the roller (21) and the ramp (20) when the crankshaft (3) is in the clamping position. 2.- Tête de bridage selon la revendication 1, caractérisée en ce que le point d'appui (23) est constitué par un axe d'articulation.2.- clamping head according to claim 1, characterized in that the fulcrum (23) is constituted by a hinge pin. 3.- Tête de bridage selon la revendication 1 ou 2, caractérisée en ce que le ressort (22) est un ressort hélicoïdal.3.- clamping head according to claim 1 or 2, characterized in that the spring (22) is a helical spring. 4.- Tête de bridage selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la rampe (20) a un profil rectiligne sur la majeure partie de sa longueur et comporte une partie (20a) en creux à son extrémité adjacente au point d'appui (23) et un bossage (20b) à son extrémité opposée libre, ladite partie en creux et ledit bossage définissant, en combinaison avec le galet (21) et le ressort (22), des moyens de blocage propres à maintenir élastiquement les éléments mobiles (3,6,7,8) de la tête de bridage respectivement dans la position de serrage et dans la position de desserrage.4.- clamping head according to any one of claims 1 to 3, characterized in that the ramp (20) has a rectilinear profile over most of its length and has a hollow portion (20a) at its adjacent end at the fulcrum (23) and a boss (20b) at its free opposite end, said hollow part and said boss defining, in combination with the roller (21) and the spring (22), specific locking means for resiliently holding the movable elements (3,6,7,8) of the clamping head respectively in the clamping position and in the loosening position.
EP89403242A 1988-11-25 1989-11-23 Clamping head with clearance compensation Withdrawn EP0370914A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8815396A FR2639569B1 (en) 1988-11-25 1988-11-25 CLAMPING HEAD WITH RETRACTION OF GAMES
FR8815396 1988-11-25

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EP0370914A1 true EP0370914A1 (en) 1990-05-30

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DE (1) DE370914T1 (en)
ES (1) ES2015837A4 (en)
FR (1) FR2639569B1 (en)

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EP0596808A1 (en) * 1992-11-05 1994-05-11 Martin Breiter Clamping head
DE9412722U1 (en) * 1994-08-06 1994-09-29 DE-STA-CO Metallerzeugnisse GmbH, 61449 Steinbach Toggle clamp device
EP0849046A1 (en) * 1996-12-17 1998-06-24 DE-STA-CO Metallerzeugnisse GmbH Actuating mechanism
EP0894573A2 (en) * 1997-07-29 1999-02-03 Benteler Ag Workpiece clamp
DE19751950C1 (en) * 1997-11-24 1999-03-04 Isi International Sa Toggle actuated vehicle bodywork clamp
ITTO20120106A1 (en) * 2012-02-08 2013-08-09 Vep Automation Srl PIECE LOCKING EQUIPMENT, PARTICULARLY OF SHEET SHEETS
WO2020071301A1 (en) * 2018-10-05 2020-04-09 Smc Corporation Clamping device

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EP0145631A1 (en) * 1983-12-02 1985-06-19 ETUDES TECHNIQUES-FRANCHE COMTE-ALSACE ETFA Sàrl Pneumatic clamping device with a toggle link
EP0216710A1 (en) * 1985-09-24 1987-04-01 Fabrice Goussu Multiple-head clamping device with a single remote control

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Publication number Priority date Publication date Assignee Title
FR2296494A1 (en) * 1974-12-31 1976-07-30 Carel Fouche Languepin Pneumatic clamping arrangement for industrial purposes - has double acting cylinder for actuating a rotating clamping lever
FR2540021A1 (en) * 1983-01-27 1984-08-03 Franche Comte Alsace Etudes Te Pneumatic clamping device for the knee joint
FR2542656A3 (en) * 1983-03-16 1984-09-21 Destaco Metallerzeug Gmbh KNEE CLAMP DEVICE COMPRISING A DOUBLE-EFFECTED JACK
EP0145631A1 (en) * 1983-12-02 1985-06-19 ETUDES TECHNIQUES-FRANCHE COMTE-ALSACE ETFA Sàrl Pneumatic clamping device with a toggle link
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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0596808A1 (en) * 1992-11-05 1994-05-11 Martin Breiter Clamping head
DE9412722U1 (en) * 1994-08-06 1994-09-29 DE-STA-CO Metallerzeugnisse GmbH, 61449 Steinbach Toggle clamp device
EP0849046A1 (en) * 1996-12-17 1998-06-24 DE-STA-CO Metallerzeugnisse GmbH Actuating mechanism
EP0894573A3 (en) * 1997-07-29 1999-04-28 Benteler Ag Workpiece clamp
DE19732600A1 (en) * 1997-07-29 1999-02-25 Benteler Werke Ag Component clamp
EP0894573A2 (en) * 1997-07-29 1999-02-03 Benteler Ag Workpiece clamp
DE19732600C2 (en) * 1997-07-29 2000-03-30 Benteler Werke Ag Component clamp
US6206353B1 (en) 1997-07-29 2001-03-27 Benteler Werke Ag Clamping device for structural components
DE19751950C1 (en) * 1997-11-24 1999-03-04 Isi International Sa Toggle actuated vehicle bodywork clamp
EP0917932A1 (en) * 1997-11-24 1999-05-26 I.S.I. International S.A. Toggle-lever clamp, in particular for use in car bodywork construction
ITTO20120106A1 (en) * 2012-02-08 2013-08-09 Vep Automation Srl PIECE LOCKING EQUIPMENT, PARTICULARLY OF SHEET SHEETS
EP2626174A1 (en) * 2012-02-08 2013-08-14 VEP Automation S.r.l. Clamping apparatus for clamping workworkpieces, particularly sheets
WO2020071301A1 (en) * 2018-10-05 2020-04-09 Smc Corporation Clamping device
US11413724B2 (en) * 2018-10-05 2022-08-16 Smc Corporation Clamping device

Also Published As

Publication number Publication date
DE370914T1 (en) 1990-11-08
FR2639569A1 (en) 1990-06-01
FR2639569B1 (en) 1991-01-18
ES2015837A4 (en) 1990-09-16

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