EP0521025B1 - Device for performing an operation at a given pitch on a strip - Google Patents

Device for performing an operation at a given pitch on a strip Download PDF

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Publication number
EP0521025B1
EP0521025B1 EP91905835A EP91905835A EP0521025B1 EP 0521025 B1 EP0521025 B1 EP 0521025B1 EP 91905835 A EP91905835 A EP 91905835A EP 91905835 A EP91905835 A EP 91905835A EP 0521025 B1 EP0521025 B1 EP 0521025B1
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EP
European Patent Office
Prior art keywords
block
movement
web
axis
plane
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.)
Expired - Lifetime
Application number
EP91905835A
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German (de)
French (fr)
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EP0521025A1 (en
Inventor
Michael Long
Jacques Fernand Gaudillat
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.)
Kodak Pathe SA
Eastman Kodak Co
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Kodak Pathe SA
Eastman Kodak Co
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Publication of EP0521025A1 publication Critical patent/EP0521025A1/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D5/00—Arrangements for operating and controlling machines or devices for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D5/08—Means for actuating the cutting member to effect the cut
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D5/00—Arrangements for operating and controlling machines or devices for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D5/08—Means for actuating the cutting member to effect the cut
    • B26D5/18—Toggle-link means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26F—PERFORATING; PUNCHING; CUTTING-OUT; STAMPING-OUT; SEVERING BY MEANS OTHER THAN CUTTING
    • B26F1/00—Perforating; Punching; Cutting-out; Stamping-out; Apparatus therefor
    • B26F1/0007—Perforation of photographic films
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26F—PERFORATING; PUNCHING; CUTTING-OUT; STAMPING-OUT; SEVERING BY MEANS OTHER THAN CUTTING
    • B26F1/00—Perforating; Punching; Cutting-out; Stamping-out; Apparatus therefor
    • B26F1/02—Perforating by punching, e.g. with relatively-reciprocating punch and bed
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T83/00—Cutting
    • Y10T83/465—Cutting motion of tool has component in direction of moving work
    • Y10T83/4757—Tool carrier shuttles rectilinearly parallel to direction of work feed
    • Y10T83/4763—Both members of cutting pair on same carrier

Definitions

  • the invention relates to a device for performing an operation according to a determined pitch on a strip moving in a uniform and continuous manner, and relates in particular to the perforation of photographic films, the cutting, the embossing, the stitching, the notching of products in bands.
  • Photographic films for example, carry, parallel to their edges, one or two rows of perforations allowing the film to be entrained in cameras, projection devices and in processing machines.
  • the quality of the projection in particular the stability, of the images on the screen, depends closely on the quality of the perforations, that is to say on the constancy of their pitch and the precision of execution of each perforation.
  • the required tolerances are extremely low, of the order of only a few microns on the finished perforation.
  • perforators are usually used which cut one perforation at a time, on one or both edges, each time the film is immobilized between two successive movements of the film in the perforator.
  • the film is intermittently driven into a perforation station by a reciprocating mechanism which has a claw which engages in a perforation made previously by an alternating punch which perforates the film.
  • a spindle cooperating and moving with the punch is used.
  • This pin is usually located between the punch and the claw at a distance from the punch equal to the pitch of the perforations. We make sure that the pin enters the perforation that was cut previously before the punch returns to the film contact; this is to place the film with great precision under the punch before making the perforation.
  • This pin which fits without play in the perforation, corrects small defects in the positioning of the film due to the claw.
  • the patent FR-A-2 093 796 describes a perforator for punching in a strip of perforations, in a regular pitch, comprising a punch holder block articulated in a horizontal axis on a die holder block, and also comprising a mechanism for feed to drive the strip step by step, said mechanism consisting of a claw driven by an arm mounted on an eccentric part, a perforation station for cutting the perforations and a receiving mechanism which cooperates with the strip just perforated to dispose precisely the strip to be punched in the receiving station.
  • a perforator for punching in a strip of perforations, in a regular pitch, comprising a punch holder block articulated in a horizontal axis on a die holder block, and also comprising a mechanism for feed to drive the strip step by step, said mechanism consisting of a claw driven by an arm mounted on an eccentric part, a perforation station for cutting the perforations and a receiving mechanism which cooperates with the strip just perforated to dispose precisely the strip to
  • patent FR-A-2 315 367 describes a device comprising a punch-carrying drum animated by a continuous rotational movement around its axis and bearing projecting, at its periphery, at least one punch fixed relative to said drum, and also comprising a tape transport support, of the endless type (preferably, a drum with an axis parallel to that of the punch-carrying drum), disposed near the periphery of said punch-carrying drum and driven continuous synchronous with that of the latter, said endless support, on which is the strip to be perforated, carrying at least one matrix capable of cooperating with said punch during the joint movements of said drum and said support.
  • Such devices can operate at very high rates, but require very precise and therefore very expensive mechanisms for this.
  • Patent GB-A-700 900 describes a shear cutting device for cutting lengths of bars fed continuously and comprising two cutting members, totally or partially embracing the section to be cut and arranged to allow shearing in perpendicular movements. to the longitudinal direction of the bars.
  • a device for carrying out an operation, according to a determined step, on a strip moving uniformly and continuously comprising a first block provided with a tool, mounted so as to be able, periodically, to come into engagement with a member complementary to said tool, carried by a second block, the two blocks being suspended from a fixed frame, said strip passing between the two said blocks, said device being characterized in that said periodic engagement of the tool with the complementary member is carried out by a conjugate movement of the first block describing a short portion of arc of circle around a fixed horizontal axis parallel to the running axis of the strip, the two blocks being connected at the level of said fixed horizontal axis, and that of the two blocks thus connected, which are animated parallel to the running axis of the band of a back-and-forth movement of amplitude significantly greater than that of the movement of the first block around said fixed axis and of identical period, the speed of the strip being substantially equal to the horizontal speed of the tool when said tool is in engagement with the complementary member carried
  • the reciprocating movement of amplitude A is ensured by means of a deformable structure comprising, in a plane orthogonal to the plane of the strip, two deformable parallelograms each having two sides parallel to said plane of the strip, one of these parallel sides being common to the two parallelograms and animated, in a first plane parallel to the plane of the strip, of a reciprocating movement of amplitude A / 2, the other parallel side of each of said two parallelograms being arranged in the same second plane, said other parallel side of the first parallelogram is fixed, that of the second parallelogram is movable and animated in said second plane with a back and forth movement of amplitude A, in phase with the amplitude movement of A / 2.
  • the description of the invention will relate essentially to a perforating device and, to a lesser extent, to a cutting device, but it is obvious that its operation would remain unchanged if the device were provided with a tool intended for other types. operations such as embossing, stitching, punching, or notching, the movement required by all these operations being of the same type. All these devices mainly comprise two blocks, an upper block carrying a given tool and a lower block carrying a member complementary to said tool, the arrangement of these two blocks which are the subject of the detailed description which follows.
  • FIG. 1 to which reference is now made schematically shows an embodiment of the device according to the present invention.
  • This device mainly comprises an upper block 1 provided, for example, with punches and a lower block 2 carrying, for example, a matrix between which the perforating strip 3 circulates in the direction indicated by the arrow 4.
  • the strip is arranged so as to form a short, untensioned loop 5 in order to isolate the perforating device from the pulls caused by the unwinding of the strip and to be able to compensate for differences in speed between said strip and said perforating device and which we will talk about in more detail later.
  • the strip runs at a speed of approximately 100 m / min.
  • tape drive mechanisms for example, of the toothed wheel type cooperating with the perforations previously made.
  • Such mechanisms mainly comprise a first toothed wheel 6, a roller 7 intended to maintain a correct tension of the upstream belt of a second toothed wheel 8 serving in particular to isolate the perforating device from the variations in speed generated by the devices (such as the photo reel mounting towers) placed downstream of the hole punch.
  • the punch block is fixed to the die block at the level of a horizontal axis 9 fixed in space and parallel to the axis of travel of the strip, said fixed horizontal axis also corresponding to the axis of articulation. of the punch block 1 relative to the die block 2 so that the punch block can alternately describe a short portion of an arc around said fixed axis 9 in order to be able to periodically cooperate the punches with the matrix when the tape is scrolled.
  • connection thus produced between the two blocks is, according to one embodiment, an elastic connection comprising two sets of non-coplanar leaf springs 10, 11.
  • Each leaf spring is, at one of its ends, fixed by means suitable for the punch holder block 1 and, at the other of its ends for the die holder block 2.
  • two lateral blades are arranged in a first plane parallel to the plane of the strip and a central blade is arranged in the plane perpendicular to said foreground. It is obvious that the number of blades of each of the sets may be different from what is shown in FIG. 1, as well as the angle between the two planes can be different from 90 ° provided that the punch block always rocks around a fixed axis.
  • Such a connection actually behaves as if the punch holder block was fixed on a hinge in a fixed position.
  • This type of articulation differs from the usual hinges by three important points. First, there is no play in this joint. Secondly, there is no need for lubrication and therefore maintenance is reduced, as well as the danger of oil spray on the belt, dust accumulation is minimized. Thirdly, the springs do not produce a friction torque but, on the contrary, develop a return torque practically proportional to the angle by which they flex.
  • the blades are made of steel and their thickness can vary between 2 and 3 mm and preferably is of the order of 2.5 mm, for a free length of blade (that is to say, between the two fixing points) of approximately 15 to 20 mm.
  • FIG. 2 illustrates in general the device making it possible to move, parallel to the movement of the plane of the strip, the assembly formed by the punch holder block and the die holder block.
  • the device comprises in a plane orthogonal to the plane of the strip, two deformable parallelograms 12, 13, of identical height each having two sides 14, 15; 15, 16 parallel to said plane of the strip, one of these parallel sides 15 being common to the two parallelograms and animated, in a first plane parallel to the plane of the strip, with a reciprocating movement of amplitude A / 2.
  • the other parallel side of each of the two so-called parallelograms is arranged in the same second plane.
  • Said other parallel side 14 of the first parallelogram 13 is fixed, that 16 of the second parallelogram 12 is mobile and animated in said second plane by a reciprocating movement of amplitude A in phase with the movement of amplitude A / 2.
  • the mobile side 16 describing the movement of amplitude A is connected to a first system of connecting rod-crank whose radius of the crank is R and whose length of the connecting rod is L.
  • the mobile side 15 common to the two parallelograms, and describing a movement of amplitude A / 2 is connected to a second system of connecting rod-crank whose radius of the crank is R / 2 and whose length of the connecting rod is L / 2, the two cranks rotating at the same angular speed and , preferably in phase opposition.
  • the other two sides of each of the two parallelograms are made of flexible material. With such a device, the amplitude movement A is always carried out in the same plane due to the opposite effects resulting from the movements applied to each of the two said parallel sides, as described above.
  • the suspension mechanism shown in the device of Figure 1 is based on the principle mentioned with reference to FIG. 2, and comprises a first 17 and a second flexible element, substantially identical, arranged on either side of the perforation device in the plane orthogonal to said fixed horizontal axis and defining each a central blade 20 and two side blades 19, 21 of identical height.
  • said joining element is substantially planar and arranged parallel to the plane of the strip inside the perforating device, the length of said joining element corresponding substantially to the length of the flexible elements.
  • the junction element is arranged relative to the chassis so as to be able to be at least partially free in translation in the direction of travel of the strip.
  • each of the flexible elements has their upper end secured to the chassis 23, while the upper part of the central blade of each of the elements is secured to the die-holding block 2, the two flexible elements thus arranged defining, when two parallel surfaces are not stressed in translation.
  • the height of these flexible elements is of the order of 12.7 cm and the width of the central blade 20 is equal to the sum of the widths of the side blades 19, 21.
  • the assembly consisting of the punch holder block as well as the die holder block and arranged in the manner mentioned above is capable of moving in a reciprocating movement perfectly parallel to the travel plane Of the band.
  • the upper part of the central blade of one of the flexible elements is coupled to a first connecting rod-crank device 25 whose crank describes a radius R and whose connecting rod is of length L, the lower part of said central blade being, for its part, coupled to a second connecting rod-crank device 24 whose crank describes a radius R / 2 and whose connecting rod is of length L / 2, said cranks being driven in rotation by means of a shaft 26, 27 rotating at the same angular speed, and, for reasons of balance, in phase opposition.
  • the two connecting rod-crank devices are located in the same plane, substantially in the center of the central blade.
  • Such a device allows the perforator to have a movement perfectly parallel to the plane of travel of the strip between the punches and the die. This movement is perfectly balanced, generates practically no vibration and is therefore relatively silent, the balance being achieved by counterweights 60 suitably chosen and appropriately arranged.
  • the counterweights disposed on each of the eccentrics are identical and form an angle of 180 ° with said eccentrics.
  • it is desirable unlike what is shown in FIG. 2, to have the axes carrying the counterweights substantially one below the other, the common parallel side with the two parallelograms being extended appropriately.
  • the rod-crank devices are produced by means of an eccentric mechanism.
  • a connecting rod-crank mechanism is shown schematically in FIG. 4.
  • L represents the length of the connecting rod
  • R represents the length of the crank (or of the eccentric)
  • ⁇ being the angle produced by the crank
  • ⁇ being the angle produced by the connecting rod.
  • the R / L ratio must be less than 0.25 and, according to a preferred embodiment, is of the order of 0.1. According to this same embodiment, R is of the order of 9.5 mm, L is of the order of 105.5 mm.
  • Fig. 3A to which reference is now made shows an exploded view of a perforating device according to the present invention.
  • the description which will be made of this figure will endeavor to detail more particularly the means carrying out the perforation in itself, namely the punches and the matrix.
  • a block 33 carrying the punches 34 is fixed to the upper block 31, for example by screws.
  • the punches are arranged in the form of two rows each comprising at least two punches and arranged opposite one another parallel to the axis of the strip. The two rows are spaced so as to be able to perforate the two edges of said strip at a determined pitch.
  • Each row of punches is provided, at its end opposite to the arrival edge of the strip, with at least one guide pin (not shown) of length greater than that of the punches and arranged so as to engage in one of the perforations made previously and just before the punches come into contact with the film to perforate it in order to have the punches precisely on said strip.
  • each row has twelve punches and three guide pins, but it is obvious that any other arrangement of said punches and said guide pins is possible.
  • the difference in length between the punches and guide pins is in the range of 1.2mm.
  • a die 35 is fixed provided with holes intended to cooperate with the punches
  • the lower block 32 on which the die is mounted is itself provided with holes intended for the evacuation of the pieces of tape resulting from the perforation.
  • devices are provided for guiding the strip precisely as it travels. These devices consist of a first flexible guide 36 which can be in the form of an S-shaped spring blade, and which is arranged on one of the edges of the matrix, the other edge being provided with a fixed guide. 37 and a positioning block 38 allowing adjustment of the position of the rotating guide and also allowing adjustment of its spacing relative to the flexible guide. These adjustments are carried out in a known manner, for example by means of suitable screws.
  • the die-holding block also includes a stripper block 39, arranged in a spaced relation to the die and facing said die.
  • This stripper block is intended to retain the strip when the punches leave said strip after having perforated it, the strip running between the die 35 and said stripper block 39.
  • the spacing between the die and the stripper block is of the order of 0.5 mm.
  • Figure 3B shows an exploded view of a cutting device according to the present invention.
  • the upper block 70 comprises, at its end opposite its fixed horizontal axis of rotation, a member 71 provided on one of its ends perpendicular to the axis of travel of the strip of a knife 72 , the lower block 80 comprising a member 81 arranged so as to produce a counter-knife cooperating with said knife 72.
  • the other elements of said cutting device are identical to those described in referring to the perforating device.
  • the mechanism for controlling the movement of the punch block around said fixed horizontal axis must be such as to minimize the engagement time between the punches and the strip. In fact, during this engagement time, corresponding to the actual perforation time, it is necessary to have very precise synchronization between the movement of the strip and the movement of the perforator so as to have the speed of the strip substantially equal to the horizontal speed of the punches during perforation.
  • the movement of the punch block around said fixed horizontal axis is achieved by means of a device with two rotary axes in which a uniform rotation speed of a motor axis produces a speed varying continuously during each revolution of the the axis controlling the movement of the punch block, said uniform speed of rotation of the motor axis being equal to the speed of rotation of the connecting rod-crank devices controlling the movement back and forth, parallel to the plane of the strip, of said perforation device.
  • this device with two rotary axes is, as shown schematically in FIG. 5, of the 4 bar type.
  • a first bar O1A arranged on the motor axis O1 is driven in rotation at constant speed. According to one embodiment, this speed is of the order of 1600 revolutions / min.
  • the second bar O2B is on the control axis O2 and rotates at variable speed; a third bar AB connects the free ends of the first two bars, the fourth bar being constituted by the fixed distance O1O2 separating the two axes.
  • ⁇ the angle produced by the first bar O1A
  • ⁇ the angle produced by the second bar placed on the control axis O2.
  • the dimensions of bars must be such that they verify the following relationships: 1) AB> O1O2 + O1A - O2B 2) AB ⁇ O1A - O1O2 + O2B
  • Figure 8 shows in more detail this device of the 4-bar type.
  • the axis of control WHERE is connected to the punch holder block via a connecting rod-crank mechanism 40 which may be of the eccentric type.
  • the length of the eccentric is of the order of 1.8 mm.
  • the rod 40 controlled by said eccentric is connected to the punch block at a point between the fixed horizontal axis and the rows of punches so that the punches describe a substantially vertical movement whose l amplitude is of the order of 4.5 mm. (In reality, it is an arc of a very small amplitude ( ⁇ 2 °)).
  • the punch block substantially describes an asymmetrical ellipse with respect to a horizontal axis. Such an arrangement makes it possible to be able to increase the thickness of the spring-blades forming the elastic connection and therefore to increase the rigidity of the system.
  • the motor axes controlling the horizontal movement as well as the motor axis controlling the vertical movement are driven at the same speed by means of a single motor.
  • Fig. 6 represents the variations in the angular speed of the O2B bar as a function of the angle ⁇ produced by the O1A bar arranged on the motor axis and rotating at continuous speed, said continuous speed being represented by the straight line parallel to the abscissa axis.
  • the average value of the angular speed of the O2B bar is of course equal to the angular speed of the motor axis, but said speed of the O2B bar is, in instantaneous value, sometimes higher than the speed of the motor axis, sometimes lower.
  • the eccentric controlling the movement of the punch block will of course be chosen and arranged so that the perforation actually takes place for a period during which the speed of the bar O2B is maximum, (delimited by the two vertical lines in FIG. 6), this period having to coincide with the period when the speed of the reciprocating movement of the perforator is substantially identical to that of the strip.
  • the angle ⁇ between the moment when the guide pins reach the stripper block and the moment when said guide pins leave said stripper block is also called the engagement angle and according to this embodiment is of the order of 70 °. From point B to point H, the speed of the strip must be substantially identical to the horizontal speed of the hole punch.
  • This angle of 70 ° for a drive speed of 1600 rpm represents a duration of approximately 7 ms.
  • the perforation device comprises, between the punch holder block and the die holder block, a mechanism derived from a SCOTT-RUSSELL mechanism and consisting of an X-shaped member, 50, so that it allows movement of the punch block around the fixed horizontal axis but prevents any lateral movement of one of the blocks relative to the other, thereby increasing the rigidity of the system.
  • a classic SCOTT-RUSSELL mechanism is shown in solid lines in FIG. 9. Such a device forces the point P2 to move in a movement perpendicular to the line carried by P1 and P3.
  • the broken lines represent a variant of the SCOTT RUSSELL mechanism allowing, by mirror effect, to obtain the effects of two SCOTT RUSSELL mechanisms.
  • FIG. 10 schematically shows an example of the arrangement of such a mechanism between the punch holder block and the die holder block.
  • the joints shown in Figure 9 at points P1, P2, P3 and C are replaced by flexible elements f1-f6, thus increasing the resistance to lateral movement.
  • the dimensions of the device according to the present invention are, for the embodiment shown in Figure 1, of the order of 41 cm x 37 cm x 25 cm.

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  • Life Sciences & Earth Sciences (AREA)
  • Forests & Forestry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)

Abstract

The invention concerns a device for performing an operation at a given pitch on a strip moving uniformly and continuously. The device comprises a first unit (1) fitted with a tool alternately describing a short section of an arc about a fixed horizontal axis (9) parallel to the axis of travel of the strip so that said tool can be caused to work periodically with a complementary component to said tool carried on a second unit (2), said first unit being connected to said second unit at said fixed axis, where both units thus secured and suspended from a fixed frame (20) are caused to move parallel to the axis of travel of said strip. Application to the perforation, cutting, embossing, notching and pricking of strips.

Description

L'invention concerne un dispositif pour réaliser une opération selon un pas déterminé sur une bande se déplaçant de manière uniforme et continue, et concerne notamment la perforation de films photographiques, la découpe, l'embossage, le piquage, l'encochage de produits en bandes.The invention relates to a device for performing an operation according to a determined pitch on a strip moving in a uniform and continuous manner, and relates in particular to the perforation of photographic films, the cutting, the embossing, the stitching, the notching of products in bands.

Les films photographiques, par exemple, portent, parallèlement à leurs bords, une ou deux rangées de perforations permettant l'entraînement du film dans les appareils de prise de vues, de projection et dans les machines de traitement. Dans l'utilisation de films photographiques, on sait que la qualité de la projection, notamment la stabilité, des images sur l'écran, dépend étroitement de la qualité des perforations, c'est-à-dire de la constance de leur pas et de la précision d'éxécution de chaque perforation. A cet égard, les tolérances requises sont extrêmement faibles, de l'ordre de quelques microns seulement sur la perforation finie.Photographic films, for example, carry, parallel to their edges, one or two rows of perforations allowing the film to be entrained in cameras, projection devices and in processing machines. In the use of photographic films, it is known that the quality of the projection, in particular the stability, of the images on the screen, depends closely on the quality of the perforations, that is to say on the constancy of their pitch and the precision of execution of each perforation. In this regard, the required tolerances are extremely low, of the order of only a few microns on the finished perforation.

Pour cela, on utilise habituellement des perforatrices qui découpent une perforation à la fois, sur l'un des bords ou les deux, chaque fois que le film est immobilisé entre deux déplacements successifs du film dans la perforatrice. Le film est entraîné par intermittence dans un poste de perforation par un mécanisme de va-et-vient qui présente une griffe qui s'engage dans une perforation faite précédemment par un poinçon alternatif qui perfore le film. De manière à obtenir un pas précisément reproductible, on utilise une broche coopérant et se déplaçant avec le poinçon. Cette broche est habituellement située entre le poinçon et la griffe à une distance du poinçon égale au pas des perforations. On fait en sorte que la broche pénètre dans la perforation qui a été découpée précédemment avant que le poinçon ne revienne au contact du film ; ceci a pour but de placer avec une grande précision le film sous le poinçon avant de faire la perforation. Cette broche qui rentre sans jeu dans la perforation, corrige les petits défauts de mise en place du film dus à la griffe.For this, perforators are usually used which cut one perforation at a time, on one or both edges, each time the film is immobilized between two successive movements of the film in the perforator. The film is intermittently driven into a perforation station by a reciprocating mechanism which has a claw which engages in a perforation made previously by an alternating punch which perforates the film. In order to obtain a precisely reproducible pitch, a spindle cooperating and moving with the punch is used. This pin is usually located between the punch and the claw at a distance from the punch equal to the pitch of the perforations. We make sure that the pin enters the perforation that was cut previously before the punch returns to the film contact; this is to place the film with great precision under the punch before making the perforation. This pin which fits without play in the perforation, corrects small defects in the positioning of the film due to the claw.

Ainsi le brevet FR-A-2 093 796 décrit une perforatrice pour poinçonner dans une bande des perforations, suivant un pas régulier, comprenant un bloc porte-poinçons articulé en un axe horizontal sur un bloc porte-matrice, et comprenant également un mécanisme d'alimentation pour entraîner pas à pas la bande, ledit mécanisme étant constitué d'une griffe entraînée par un bras monté sur une partie excentrée, un poste de perforation pour découper les perforations et un mécanisme de réception qui coopère avec la bande juste perforée pour disposer avec précision la bande à perforer dans le poste de réception. Un tel dispositif, en raison notamment de la disposition des blocs porte-poinçons et porte-matrice par rapport au sens de défilement de la bande, ne peut réaliser qu'un seul trou à la fois de chaque côté de la bande. Pour cette raison, la perforatrice décrite dans le brevet ci-dessus référencé permet des cadences ne pouvant excéder 30 à 40 m/mn.Thus the patent FR-A-2 093 796 describes a perforator for punching in a strip of perforations, in a regular pitch, comprising a punch holder block articulated in a horizontal axis on a die holder block, and also comprising a mechanism for feed to drive the strip step by step, said mechanism consisting of a claw driven by an arm mounted on an eccentric part, a perforation station for cutting the perforations and a receiving mechanism which cooperates with the strip just perforated to dispose precisely the strip to be punched in the receiving station. Such a device, in particular because of the arrangement of the punch and die holder blocks with respect to the direction of travel of the strip, can only make one hole at a time on each side of the strip. For this reason, the perforator described in the patent referenced above allows speeds which cannot exceed 30 to 40 m / min.

Selon un autre dispositif connu, on réalise la perforation des bandes en continu au moyen d'un système rotatif. Ainsi le brevet FR-A-2 315 367 décrit un dispositif comprenant un tambour porte-poinçons animé d'un mouvement de rotation continu autour de son axe et portant en saillie, à sa périphérie, au moins un poinçon fixe par rapport audit tambour, et comprenant également un support de transport de bande, du type sans fin (de préférence, un tambour d'axe parallèle à celui du tambour porte-poinçon), disposé à proximité de la périphérie dudit tambour porte-poinçon et animé d'un mouvement continu synchrone avec celui de ce dernier, ledit support sans fin, sur lequel se trouve la bande à perforer, portant au moins une matrice apte à coopérer avec ledit poinçon lors des mouvements conjoints dudit tambour et dudit support. De tels dispositifs, peuvent fonctionner à des cadences très élevées, mais exigent pour cela des mécanismes de très grande précision et par conséquent, très coûteux.According to another known device, the strips are perforated continuously by means of a rotary system. Thus, patent FR-A-2 315 367 describes a device comprising a punch-carrying drum animated by a continuous rotational movement around its axis and bearing projecting, at its periphery, at least one punch fixed relative to said drum, and also comprising a tape transport support, of the endless type (preferably, a drum with an axis parallel to that of the punch-carrying drum), disposed near the periphery of said punch-carrying drum and driven continuous synchronous with that of the latter, said endless support, on which is the strip to be perforated, carrying at least one matrix capable of cooperating with said punch during the joint movements of said drum and said support. Such devices can operate at very high rates, but require very precise and therefore very expensive mechanisms for this.

Le brevet GB-A-700 900 décrit un dispositif de découpe par cisaillement pour couper des longueurs de barres alimentées en continu et comprenant deux organes de coupe, embrassant totalement ou en partie la section à couper et disposés pour permettre un cisaillement selon des mouvements perpendiculaires à la direction longitudinale des barres.Patent GB-A-700 900 describes a shear cutting device for cutting lengths of bars fed continuously and comprising two cutting members, totally or partially embracing the section to be cut and arranged to allow shearing in perpendicular movements. to the longitudinal direction of the bars.

Aussi est-ce un des objets de la présente invention que de fournir un dispositif pour réaliser une opération selon un pas déterminé sur une bande défilant de manière continue à une vitesse pouvant atteindre 100 m/mn.It is therefore one of the objects of the present invention to provide a device for carrying out an operation according to a determined pitch on a strip moving continuously at a speed of up to 100 m / min.

C'est un autre objet de la présente invention que de fournir un dispositif modulable de façon très simple afin de pouvoir modifier le pas des opérations à réaliser et de pouvoir passer d'une largeur de bande à une autre.It is another object of the present invention to provide a device that can be modulated very simply in order to be able to modify the pitch of the operations to be carried out and to be able to pass from one bandwidth to another.

C'est encore un autre objet de la présente invention que de fournir un dispositif de très grande précison et ne nécessitant qu'une très faible maintenance.It is yet another object of the present invention to provide a device of very high precision and requiring very little maintenance.

C'est encore un autre objet de la présente invention que de réaliser un dispositif d'une très grande précision tout en conservant en encombrement réduit.It is yet another object of the present invention to produce a device of very high precision while conserving in reduced bulk.

C'est encore un autre objet de la présente invention que de fournir un dispositif pouvant être équipé de différents types d'outils tels que des outils de coupe, d'embossage, de piquage, de perforation, d'encochage.It is yet another object of the present invention to provide a device which can be equipped with different types of tools such as cutting, embossing, pricking, perforating, notching tools.

D'autres objets de la présente invention apparaîtront au cours de la description détaillée qui suit.Other objects of the present invention will become apparent from the detailed description which follows.

Ces objets sont atteints au moyen d'un dispositif pour réaliser une opération, selon un pas déterminé, sur une bande se déplaçant de manière uniforme et continue, comprenant un premier bloc muni d'un outil, monté de manière à pouvoir, périodiquement, venir en engagement avec un organe complémentaire dudit outil, porté par un second bloc, les deux blocs étant suspendus à un chassis fixe, ladite bande passant entre les deux dits blocs, ledit dispositif étant caractérisé en ce que ladite mise en engagement périodique de l'outil avec l'organe complémentaire est réalisée par un mouvement conjugué du premier bloc décrivant une courte portion d'arc de cercle autour d'un axe horizontal fixe parallèle à l'axe de défilement de la bande, les deux blocs étant reliés au niveau dudit axe horizontal fixe, et de celui des deux blocs ainsi reliés, lesquels sont animés parallèlement à l'axe de défilement de la bande d'un mouvement de va-et-vient d'amplitude sensiblement supérieure à celle du mouvement du premier bloc autour dudit axe fixe et de période identique, la vitesse de la bande étant sensiblement égale à la vitesse horizontale de l'outil lorsque ledit outil est en engagement avec l'organe complémentaire porté par le second bloc.These objects are achieved by means of a device for carrying out an operation, according to a determined step, on a strip moving uniformly and continuously, comprising a first block provided with a tool, mounted so as to be able, periodically, to come into engagement with a member complementary to said tool, carried by a second block, the two blocks being suspended from a fixed frame, said strip passing between the two said blocks, said device being characterized in that said periodic engagement of the tool with the complementary member is carried out by a conjugate movement of the first block describing a short portion of arc of circle around a fixed horizontal axis parallel to the running axis of the strip, the two blocks being connected at the level of said fixed horizontal axis, and that of the two blocks thus connected, which are animated parallel to the running axis of the band of a back-and-forth movement of amplitude significantly greater than that of the movement of the first block around said fixed axis and of identical period, the speed of the strip being substantially equal to the horizontal speed of the tool when said tool is in engagement with the complementary member carried by the second block.

Dans le dispositif selon la présente invention, le mouvement de va-et-vient d'amplitude A est assuré au moyen d'une structure déformable comprenant, dans un plan orthogonal au plan de la bande, deux parallélogrammes déformables présentant chacun deux côtés parallèles audit plan de la bande, l'un de ces côtés parallèles étant commun aux deux parallélogrammmes et animé, selon un premier plan parallèle au plan de la bande d'un mouvement de va-et-vient d'amplitude A/2, l'autre côté parallèle de chacun des deux dits parallélogrammes étant disposé dans un même deuxième plan, ledit autre côté parallèle du premier parallélogramme est fixe, celui du second parallélogramme est mobile et animé dans ledit deuxième plan d'un mouvement de va-et-vient d'amplitude A, en phase avec le mouvement d'amplitude de A/2.In the device according to the present invention, the reciprocating movement of amplitude A is ensured by means of a deformable structure comprising, in a plane orthogonal to the plane of the strip, two deformable parallelograms each having two sides parallel to said plane of the strip, one of these parallel sides being common to the two parallelograms and animated, in a first plane parallel to the plane of the strip, of a reciprocating movement of amplitude A / 2, the other parallel side of each of said two parallelograms being arranged in the same second plane, said other parallel side of the first parallelogram is fixed, that of the second parallelogram is movable and animated in said second plane with a back and forth movement of amplitude A, in phase with the amplitude movement of A / 2.

L'invention sera décrite plus en détail en faisant référence aux planches de dessins annexés dans lesquels :

  • la figure 1 représente de façon schématique un mode de réalisation du dispositif selon la présente invention,
  • la figure 2 illustre de manière générale un dispositif permettant de réaliser un mouvement de va-et-vient parfaitement parallèle à un plan,
  • la figure 3A représente une vue éclatée du dispositif selon la présente invention muni d'un outil de perforation,
  • la figure 3B représente une vue éclatée du dispositif selon la présente invention muni d'un outil de coupe,
  • la figure 4 représente de façon schématique un mécanisme bielle-manivelle tel que ceux utilisés dans le dispositif selon la présente invention,
  • la figure 5 représente de façon schématique un exemple de dispositif destiné à commander le mouvement du bloc supérieur par rapport au bloc inférieur,
  • la figure 6 est un graphique représentant les variations de vitesse du dispositif de commande du mouvement du bloc supérieur en fonction de l'angle réalisé par une barre motrice tournant à vitesse constante,
  • la figure 7 est un graphique représentant les variations de vitesse du mouvement de va-et-vient du dispositif selon la présente invention dans un plan parallèle au plan de la bande,
  • la figure 8 représente de façon plus détaillée un dispositif du type à 4 barres permettant de commander le mouvement du bloc supérieur par rapport au bloc inférieur,
  • la figure 9 représente de façon schématique un mécanisme du type mécanisme de SCOTT-RUSSEL utilisé dans la présente invention,
  • la figure 10 représente un mécanisme de SCOTT-RUSSEL tel que disposé dans le dispositif selon la présente invention.
The invention will be described in more detail with reference to the accompanying drawing plates in which:
  • FIG. 1 schematically represents an embodiment of the device according to the present invention,
  • FIG. 2 generally illustrates a device making it possible to perform a reciprocating movement perfectly parallel to a plane,
  • FIG. 3A represents an exploded view of the device according to the present invention provided with a perforation tool,
  • FIG. 3B represents an exploded view of the device according to the present invention provided with a cutting tool,
  • Figure 4 shows schematically a connecting rod-crank mechanism such as those used in the device according to the present invention,
  • FIG. 5 schematically represents an example of a device intended to control the movement of the upper block relative to the lower block,
  • FIG. 6 is a graph representing the variations in speed of the device for controlling the movement of the upper block as a function of the angle produced by a power bar rotating at constant speed,
  • FIG. 7 is a graph showing the variations in speed of the reciprocating movement of the device according to the present invention in a plane parallel to the plane of the strip,
  • FIG. 8 shows in more detail a device of the 4-bar type making it possible to control the movement of the upper block relative to the lower block,
  • FIG. 9 schematically represents a mechanism of the SCOTT-RUSSEL mechanism type used in the present invention,
  • Figure 10 shows a SCOTT-RUSSEL mechanism as arranged in the device according to the present invention.

La description de l'invention portera essentiellement sur un dispositif de perforation et, dans une moindre mesure, sur un dispositif de coupe, mais il est évident que son fonctionnement resterait inchangé si le dispositif était pourvu d'un outil destiné à d'autres types d'opérations telles que l'embossage, le piquage, le poinçonnage, ou l'encochage, le mouvement requis par toutes ces opérations étant du même type. Tous ces dispositifs comprennent principalement deux blocs, un bloc supérieur portant un outil donné et un bloc inférieur portant un organe complémentaire dudit outil, l'agencement de ces deux blocs faisant l'objet de la description détaillée qui suit.The description of the invention will relate essentially to a perforating device and, to a lesser extent, to a cutting device, but it is obvious that its operation would remain unchanged if the device were provided with a tool intended for other types. operations such as embossing, stitching, punching, or notching, the movement required by all these operations being of the same type. All these devices mainly comprise two blocks, an upper block carrying a given tool and a lower block carrying a member complementary to said tool, the arrangement of these two blocks which are the subject of the detailed description which follows.

La figure 1 à laquelle on fait maintenant référence représente de façon schématique un mode de réalisation du dispositif selon la présente invention.Figure 1 to which reference is now made schematically shows an embodiment of the device according to the present invention.

Ce dispositif comprend principalement un bloc supérieur 1 pourvu, par exemple, de poinçons et un bloc inférieur 2 portant, par exemple, une matrice entre lesquels circule la bande à perforer 3 dans le sens indiqué par la flèche 4. A l'entrée du dispositif de perforation, la bande est disposée de façon à réaliser une courte boucle 5 non tendue afin d'isoler le dispositif de perforation des tractions provoquées par le déroulement de la bande et de pouvoir compenser des différences de vitesse entre ladite bande et ledit dispositif de perforation et dont on reparlera plus en détail par la suite. Selon un mode de réalisation, la bande défile à une vitesse d'environ 100 m/mn. A la sortie de la perforatrice sont prévus des mécanismes d'entraînement de la bande, par exemple, du type à roues dentées coopérant avec les perforations précédemment réalisées. De tels mécanismes comprennent principalement une première roue dentée 6, un rouleau 7 destiné à maintenir une tension correcte de la bande amont d'une seconde roue dentée 8 servant notamment à isoler le dispositif de perforation des variations de vitesse générées par les dispositifs (tels que les tours de montage de bobines photographiques) placés en aval de la perforatrice. Le bloc porte-poinçons est fixé au bloc porte-matrice au niveau d'un axe horizontal 9 fixe dans l'espace et parallèle à l'axe de défilement de la bande, ledit axe horizontal fixe correspondant également à l'axe d'articulation du bloc porte-poinçons 1 par rapport au bloc porte-matrice 2 de manière à ce que le bloc porte-poinçons puisse décrire alternativement une courte portion d'arc de cercle autour dudit axe fixe 9 afin de pouvoir faire coopérer périodiquement les poinçons avec la matrice lors du défilement de la bande. La liaison ainsi réalisée entre les deux blocs est, selon un mode de réalisation, une liaison élastique comprenant deux jeux de lames-ressort non coplanaires 10, 11. Chaque lame-ressort est, en l'une de ses extrémités, fixée par un moyen approprié au bloc porte-poinçons 1 et, en l'autre de ses extrémités au bloc porte-matrice 2. Dans le montage représenté à la Fig. 1 deux lames latérales sont disposées dans un premier plan parallèle au plan de la bande et une lame centrale est disposée dans le plan perpendiculaire audit premier plan. Il est évident que le nombre de lames de chacun des jeux peut être différent de ce qui est représenté en Fig. 1, de même que l'angle entre les deux plans peut être différent de 90° à condition que le bloc porte-poinçons bascule toujours autour d'un axe fixe. Une telle liaison se comporte en réalité comme si le bloc porte-poinçons était fixé sur une charnière de position fixe.This device mainly comprises an upper block 1 provided, for example, with punches and a lower block 2 carrying, for example, a matrix between which the perforating strip 3 circulates in the direction indicated by the arrow 4. At the entry of the device of perforation, the strip is arranged so as to form a short, untensioned loop 5 in order to isolate the perforating device from the pulls caused by the unwinding of the strip and to be able to compensate for differences in speed between said strip and said perforating device and which we will talk about in more detail later. According to one embodiment, the strip runs at a speed of approximately 100 m / min. At the outlet of the perforator are provided tape drive mechanisms, for example, of the toothed wheel type cooperating with the perforations previously made. Such mechanisms mainly comprise a first toothed wheel 6, a roller 7 intended to maintain a correct tension of the upstream belt of a second toothed wheel 8 serving in particular to isolate the perforating device from the variations in speed generated by the devices (such as the photo reel mounting towers) placed downstream of the hole punch. The punch block is fixed to the die block at the level of a horizontal axis 9 fixed in space and parallel to the axis of travel of the strip, said fixed horizontal axis also corresponding to the axis of articulation. of the punch block 1 relative to the die block 2 so that the punch block can alternately describe a short portion of an arc around said fixed axis 9 in order to be able to periodically cooperate the punches with the matrix when the tape is scrolled. The connection thus produced between the two blocks is, according to one embodiment, an elastic connection comprising two sets of non-coplanar leaf springs 10, 11. Each leaf spring is, at one of its ends, fixed by means suitable for the punch holder block 1 and, at the other of its ends for the die holder block 2. In the assembly shown in FIG. 1 two lateral blades are arranged in a first plane parallel to the plane of the strip and a central blade is arranged in the plane perpendicular to said foreground. It is obvious that the number of blades of each of the sets may be different from what is shown in FIG. 1, as well as the angle between the two planes can be different from 90 ° provided that the punch block always rocks around a fixed axis. Such a connection actually behaves as if the punch holder block was fixed on a hinge in a fixed position.

Ce type d'articulation diffère des charnières habituelles par trois points importants. Premièrement, il n'y a aucun jeu dans cette articulation. Deuxièmement, il n'y a pas besoin de lubrification et de ce fait l'entretien est réduit, ainsi que le danger de projection d'huile sur la bande, les accumulations de poussières sont minimisées. Troisièmement, les ressorts ne produisent pas de couple de frottement mais, au contraire, développent un couple de rappel pratiquement proportionnel à l'angle dont ils fléchissent.This type of articulation differs from the usual hinges by three important points. First, there is no play in this joint. Secondly, there is no need for lubrication and therefore maintenance is reduced, as well as the danger of oil spray on the belt, dust accumulation is minimized. Thirdly, the springs do not produce a friction torque but, on the contrary, develop a return torque practically proportional to the angle by which they flex.

Selon un mode de réalisation, les lames sont en acier et leur épaisseur peut varier entre 2 et 3 mm et de préférence est de l'ordre de 2,5 mm, pour une longueur libre de lame (c'est-à-dire, entre les deux points de fixation) d'environ 15 à 20 mm.According to one embodiment, the blades are made of steel and their thickness can vary between 2 and 3 mm and preferably is of the order of 2.5 mm, for a free length of blade (that is to say, between the two fixing points) of approximately 15 to 20 mm.

L'assemblage des deux blocs réalisant le dispositif de perforation est suspendu au chassis fixe d'une façon que l'on va maintenant décrire en détail.The assembly of the two blocks making the perforation device is suspended from the fixed frame so that we will now describe in detail.

La figure 2 illustre de manière générale le dispositif permettant de déplacer, parallèlement au mouvement du plan de la bande, l'assemblage formé du bloc porte-poinçons et du bloc porte-matrice. Le dispositif comprend dans un plan orthogonal au plan de la bande, deux parallélogrammes déformables 12, 13, de hauteur identique présentant chacun deux côtés 14, 15 ; 15, 16 parallèles audit plan de la bande, l'un de ces côtés parallèles 15 étant commun aux deux parallélogrammes et animé, selon un premier plan parallèle au plan de la bande, d'un mouvement de va-et-vient d'amplitude A/2. L'autre côté parallèle de chacun des deux dits parallélogrammes est disposé dans un même deuxième plan. Ledit autre côté parallèle 14 du premier parallélogramme 13 est fixe, celui 16 du second parallélogramme 12 est mobile et animé dans ledit deuxième plan d'un mouvement de va-et-vient d'amplitude A en phase avec le mouvement d'amplitude A/2. Le côté mobile 16 décrivant le mouvement d'amplitude A est relié à un premier système de bielle-manivelle dont le rayon de la manivelle est R et dont la longueur de la bielle est L. Le côté mobile 15 commun aux deux parallélogrammes, et décrivant un mouvement d'amplitude A/2 est relié à un second système de bielle-manivelle dont le rayon de la manivelle est R/2 et dont la longueur de la bielle est L/2, les deux manivelles tournant à la même vitesse angulaire et, de préférence, en opposition de phase. Les deux autres côtés de chacun des deux parallélogrammes sont constitués d'un matériau flexible. Avec un tel dispositif, le mouvement d'amplitude A s'effectue toujours dans un même plan en raison des effets opposés résultant des mouvements appliqués à chacun des deux dits côtés parallèles, tels que décrits ci-avant.FIG. 2 illustrates in general the device making it possible to move, parallel to the movement of the plane of the strip, the assembly formed by the punch holder block and the die holder block. The device comprises in a plane orthogonal to the plane of the strip, two deformable parallelograms 12, 13, of identical height each having two sides 14, 15; 15, 16 parallel to said plane of the strip, one of these parallel sides 15 being common to the two parallelograms and animated, in a first plane parallel to the plane of the strip, with a reciprocating movement of amplitude A / 2. The other parallel side of each of the two so-called parallelograms is arranged in the same second plane. Said other parallel side 14 of the first parallelogram 13 is fixed, that 16 of the second parallelogram 12 is mobile and animated in said second plane by a reciprocating movement of amplitude A in phase with the movement of amplitude A / 2. The mobile side 16 describing the movement of amplitude A is connected to a first system of connecting rod-crank whose radius of the crank is R and whose length of the connecting rod is L. The mobile side 15 common to the two parallelograms, and describing a movement of amplitude A / 2 is connected to a second system of connecting rod-crank whose radius of the crank is R / 2 and whose length of the connecting rod is L / 2, the two cranks rotating at the same angular speed and , preferably in phase opposition. The other two sides of each of the two parallelograms are made of flexible material. With such a device, the amplitude movement A is always carried out in the same plane due to the opposite effects resulting from the movements applied to each of the two said parallel sides, as described above.

Selon un mode de réalisation particulier, le mécanisme de suspension représenté dans le dispositif de la figure 1 est basé sur le principe évoqué en référence à la figure 2, et comprend un premier 17 et un second 18 élément flexible, sensiblement identiques, disposés de part et d'autre du dispositif de perforation dans le plan orthogonal audit axe horizontal fixe et définissant chacun une lame centrale 20 et deux lames latérales 19, 21 de hauteur identiques.According to a particular embodiment, the suspension mechanism shown in the device of Figure 1 is based on the principle mentioned with reference to FIG. 2, and comprises a first 17 and a second flexible element, substantially identical, arranged on either side of the perforation device in the plane orthogonal to said fixed horizontal axis and defining each a central blade 20 and two side blades 19, 21 of identical height.

Les extrémités inférieures desdites lames latérales et de ladite lame centrale du premier élément sont rendues solidaires de l'extrémité inférieure des lames latérales, et de la lame centrale du second élément, respectivement, au moyen d'un élément de jonction 22. Selon le mode de réalisation représenté à la figure 1, ledit élément de jonction est sensiblement plan et disposé parallèlement au plan de la bande à l'intérieur du dispositif de perforation, la longueur dudit élément de jonction correspondant sensiblement à la longueur des éléments flexibles. L'élément de jonction est disposé par rapport au chassis de façon à pouvoir être au moins partiellement libre en translation dans le sens de défilement de la bande. Les lames latérales de chacun des éléments flexibles ont leur extrémité supérieure solidaire du chassis 23, tandis que la partie supérieure de la lame centrale de chacun des éléments est solidaire du bloc porte-matrice 2, les deux éléments flexibles ainsi disposés définissant, lorsqu'ils ne sont pas sollicités en translation, deux surfaces parallèles. Selon un mode de réalisation particulier, la hauteur de ces éléments flexibles est de l'ordre de 12,7 cm et la largeur de la lame centrale 20 est égale à la somme des largeurs des lames latérales 19, 21.The lower ends of said lateral blades and of said central blade of the first element are made integral with the lower end of the lateral blades, and of the central blade of the second element, respectively, by means of a joining element 22. According to the mode of embodiment shown in FIG. 1, said joining element is substantially planar and arranged parallel to the plane of the strip inside the perforating device, the length of said joining element corresponding substantially to the length of the flexible elements. The junction element is arranged relative to the chassis so as to be able to be at least partially free in translation in the direction of travel of the strip. The lateral blades of each of the flexible elements have their upper end secured to the chassis 23, while the upper part of the central blade of each of the elements is secured to the die-holding block 2, the two flexible elements thus arranged defining, when two parallel surfaces are not stressed in translation. According to a particular embodiment, the height of these flexible elements is of the order of 12.7 cm and the width of the central blade 20 is equal to the sum of the widths of the side blades 19, 21.

L'assemblage constitué du bloc porte-poinçons ainsi que du bloc porte-matrice et disposé de la manière évoquée précédemment est apte à se déplacer selon un mouvement de va-et-vient parfaitement parallèle au plan de défilement de la bande. A cet effet, la partie supérieure de la lame centrale d'un des éléments flexibles est couplée à un premier dispositif bielle-manivelle 25 dont la manivelle décrit un rayon R et dont la bielle est de longueur L, la partie inférieure de ladite lame centrale étant, quant à elle, couplée à un second dispositif bielle-manivelle 24 dont la manivelle décrit un rayon R/2 et dont la bielle est de longueur L/2, les dites manivelles étant entraînées en rotation au moyen d'un arbre 26, 27 tournant à la même vitesse angulaire, et, pour des raisons d'équilibre, en opposition de phase.The assembly consisting of the punch holder block as well as the die holder block and arranged in the manner mentioned above is capable of moving in a reciprocating movement perfectly parallel to the travel plane Of the band. For this purpose, the upper part of the central blade of one of the flexible elements is coupled to a first connecting rod-crank device 25 whose crank describes a radius R and whose connecting rod is of length L, the lower part of said central blade being, for its part, coupled to a second connecting rod-crank device 24 whose crank describes a radius R / 2 and whose connecting rod is of length L / 2, said cranks being driven in rotation by means of a shaft 26, 27 rotating at the same angular speed, and, for reasons of balance, in phase opposition.

Les deux dispositifs bielle-manivelle sont situés dans le même plan, sensiblement au centre de la lame centrale. Un tel dispositif permet à la perforatrice d'avoir un mouvement parfaitement parallèle au plan de défilement de la bande entre les poinçons et la matrice. Ce mouvement est parfaitement équilibré, ne génère pratiquement aucune vibration et est donc relativement silencieux, l'équilibre étant réalisé par des contrepoids 60 choisis convenablement et disposés de manière appropriée. Dans le mode de réalisation de la figure 1, les contrepoids disposés sur chacun des excentriques sont identiques et forment un angle de 180° avec lesdits excentriques. De même, pour des raisons d'équilibre du mouvement, il est souhaitable, à la différence de ce qui est représenté en figure 2, de disposer les axes portant les contrepoids sensiblement l'un en dessous de l'autre, le côté paralléle commun aux deux parallélogrammes étant prolongé de manière appropriée. Selon un mode de réalisation particulier, les dispositifs bielle-manivelle sont réalisés au moyen d'un mécanisme à excentrique. A des fins d'explications plus détaillées par la suite, un mécanisme bielle-manivelle est représenté de façon schématique en Fig. 4.The two connecting rod-crank devices are located in the same plane, substantially in the center of the central blade. Such a device allows the perforator to have a movement perfectly parallel to the plane of travel of the strip between the punches and the die. This movement is perfectly balanced, generates practically no vibration and is therefore relatively silent, the balance being achieved by counterweights 60 suitably chosen and appropriately arranged. In the embodiment of Figure 1, the counterweights disposed on each of the eccentrics are identical and form an angle of 180 ° with said eccentrics. Similarly, for reasons of equilibrium of the movement, it is desirable, unlike what is shown in FIG. 2, to have the axes carrying the counterweights substantially one below the other, the common parallel side with the two parallelograms being extended appropriately. According to a particular embodiment, the rod-crank devices are produced by means of an eccentric mechanism. For the purpose of more detailed explanations below, a connecting rod-crank mechanism is shown schematically in FIG. 4.

Ainsi que représenté à la Fig. 4, le mouvement horizontal de va-et-vient est symbolisé par la flèche bidirectionnelle 30, L représente la longueur de la bielle, R représente la longueur de la manivelle (ou de l'excentrique), ϑ étant l'angle réalisé par la manivelle, Φ étant l'angle réalisé par la bielle. Le rapport R/L doit être inférieur à 0,25 et, selon un mode de réalisation préféré, est de l'ordre de 0,1. Selon ce même mode de réalisation, R est de l'ordre de 9,5 mm, L est de l'ordre de 105,5 mm.As shown in FIG. 4, the horizontal back-and-forth movement is symbolized by the arrow bidirectional 30, L represents the length of the connecting rod, R represents the length of the crank (or of the eccentric), ϑ being the angle produced by the crank, Φ being the angle produced by the connecting rod. The R / L ratio must be less than 0.25 and, according to a preferred embodiment, is of the order of 0.1. According to this same embodiment, R is of the order of 9.5 mm, L is of the order of 105.5 mm.

La Fig. 3A à laquelle on fait maintenant référence représente une vue éclatée d'un dispositif de perforation selon la présente invention. La description qui va être faite de cette figure va s'attacher à détailler plus particulièrement les moyens réalisant la perforation en elle-même, à savoir les poinçons et la matrice. En son extrémité opposée à son axe de rotation horizontal fixe, on fixe au bloc supérieur 31, par exemple au moyen de vis, un bloc 33 portant les poinçons 34. Dans le mode de réalisation représenté, les poinçons sont disposés sous la forme de deux rangées comprenant chacune au moins deux poinçons et disposées en regard l'une de l'autre parallèlement à l'axe de la bande. Les deux rangées sont espacées de manière à pouvoir perforer les deux bords de ladite bande selon un pas déterminé. Chaque rangée de poinçons est pourvue, en son extrémité opposée au bord d'arrivée de la bande, d'au moins une broche de guidage (non représentée) de longueur supérieure à celle des poinçons et disposée de façon à s'engager dans une des perforations faites précédemment et juste avant que les poinçons ne viennent au contact du film pour le perforer afin de disposer avec précision les poinçons sur ladite bande. Selon un mode de réalisation, chaque rangée comporte douze poinçons et trois broches de guidage, mais il est évident que tout autre arrangement desdits poinçons et desdites broches de guidage est possible. De même, à titre d'exemple, la différence de longueur entre les poinçons et les broches de guidage est de l'ordre de 1,2 mm. Sur l'extrémité du bloc inférieur 32, dit bloc porte-matrice, on fixe une matrice 35 pourvue de trous destinés à coopérer avec les poinçons, le bloc inférieur 32 sur lequel est montée la matrice étant lui-même pourvu de trous destinés à l'évacuation des morceaux de bande résultant de la perforation. De chaque côté de la matrice, on prévoit des dispositifs destinés à guider la bande précisément lors de son défilement. Ces dispositifs se composent d'un premier guide flexible 36 qui peut être sous la forme d'une lame ressort en forme de S, et qui est disposé sur un des bords de la matrice, l'autre bord étant pourvu d'un guide fixe 37 et d'un bloc de positionnement 38 permettant un réglage de la position du guide en rotation et permettant également le réglage de son espacement par rapport au guide flexible. Ces réglages s'effectuent de manière connue, par exemple au moyen de vis appropriées. Le bloc porte-matrice comporte également un bloc dévétisseur 39, disposé de manière espacée par rapport à la matrice et en regard de ladite matrice. Ce bloc dévétisseur est destiné à retenir la bande lorsque les poinçons quittent ladite bande après l'avoir perforée, la bande défilant entre la matrice 35 et ledit bloc dévétisseur 39. A titre d'exemple, l'espacement entre la matrice et le bloc dévétisseur est de l'ordre de 0,5 mm.Fig. 3A to which reference is now made shows an exploded view of a perforating device according to the present invention. The description which will be made of this figure will endeavor to detail more particularly the means carrying out the perforation in itself, namely the punches and the matrix. At its end opposite to its fixed horizontal axis of rotation, a block 33 carrying the punches 34 is fixed to the upper block 31, for example by screws. In the embodiment shown, the punches are arranged in the form of two rows each comprising at least two punches and arranged opposite one another parallel to the axis of the strip. The two rows are spaced so as to be able to perforate the two edges of said strip at a determined pitch. Each row of punches is provided, at its end opposite to the arrival edge of the strip, with at least one guide pin (not shown) of length greater than that of the punches and arranged so as to engage in one of the perforations made previously and just before the punches come into contact with the film to perforate it in order to have the punches precisely on said strip. According to one embodiment, each row has twelve punches and three guide pins, but it is obvious that any other arrangement of said punches and said guide pins is possible. Similarly, by way of example, the difference in length between the punches and guide pins is in the range of 1.2mm. On the end of the lower block 32, called the die holder block, a die 35 is fixed provided with holes intended to cooperate with the punches, the lower block 32 on which the die is mounted is itself provided with holes intended for the evacuation of the pieces of tape resulting from the perforation. On each side of the matrix, devices are provided for guiding the strip precisely as it travels. These devices consist of a first flexible guide 36 which can be in the form of an S-shaped spring blade, and which is arranged on one of the edges of the matrix, the other edge being provided with a fixed guide. 37 and a positioning block 38 allowing adjustment of the position of the rotating guide and also allowing adjustment of its spacing relative to the flexible guide. These adjustments are carried out in a known manner, for example by means of suitable screws. The die-holding block also includes a stripper block 39, arranged in a spaced relation to the die and facing said die. This stripper block is intended to retain the strip when the punches leave said strip after having perforated it, the strip running between the die 35 and said stripper block 39. For example, the spacing between the die and the stripper block is of the order of 0.5 mm.

La figure 3B représente une vue éclatée d'un dispositif de découpe selon la présente invention. Ainsi que représenté à la figure 3B le bloc supérieur 70 comporte en son extrémité opposée à son axe de rotation horizontal fixe, un organe 71 muni sur l'une de ses extrémités perpendiculaires à l'axe de défilement de la bande d'un couteau 72, le bloc inférieur 80 comportant un organe 81 disposé de façon à réaliser un contre-couteau coopérant avec ledit couteau 72. Les autres éléments dudit dispositif de découpe sont identiques à ceux décrits en faisant référence au dispositif de perforation.Figure 3B shows an exploded view of a cutting device according to the present invention. As shown in FIG. 3B, the upper block 70 comprises, at its end opposite its fixed horizontal axis of rotation, a member 71 provided on one of its ends perpendicular to the axis of travel of the strip of a knife 72 , the lower block 80 comprising a member 81 arranged so as to produce a counter-knife cooperating with said knife 72. The other elements of said cutting device are identical to those described in referring to the perforating device.

Le mécanisme permettant de commander le mouvement du bloc porte-poinçons autour dudit axe horizontal fixe doit être tel qu'il permette de minimiser le temps d'engagement entre les poinçons et la bande. En effet, pendant ce temps d'engagement, correspondant au temps de perforation proprement dit, il est nécessaire d'avoir une synchronisation très précise entre le mouvement de la bande et le mouvement de la perforatrice de façon à avoir la vitesse de la bande sensiblement égale à la vitesse horizontale des poinçons en cours de perforation.The mechanism for controlling the movement of the punch block around said fixed horizontal axis must be such as to minimize the engagement time between the punches and the strip. In fact, during this engagement time, corresponding to the actual perforation time, it is necessary to have very precise synchronization between the movement of the strip and the movement of the perforator so as to have the speed of the strip substantially equal to the horizontal speed of the punches during perforation.

A cet effet, le mouvement du bloc porte-poinçons autour dudit axe horizontal fixe est réalisé au moyen d'un dispositif à deux axes rotatifs dans lequel une vitesse de rotation uniforme d'un axe moteur produit une vitesse variant continuellement pendant chaque tour de l'axe commandant le mouvement du bloc porte-poinçons, ladite vitesse de rotation uniforme de l'axe moteur étant égale à la vitesse de rotation des dispositifs bielle-manivelle commandant le mouvement de va-et-vient, parallèlement au plan de la bande, dudit dispositif de perforation. Selon un mode de réalisation, ce dispositif à deux axes rotatifs est, ainsi que représenté de façon schématique à la Fig. 5, du type à 4 barres. Une première barre O₁A disposée sur l'axe moteur O₁ est entraînée en rotation à vitesse constante. Selon un mode de réalisation, cette vitesse est de l'ordre de 1600 tours/mn. La deuxième barre O₂B est sur l'axe de commande O₂ et tourne à vitesse variable ; une troisième barre AB relie les extrémités libres des deux premières barres, la quatrième barre étant constituée par la distance fixe O₁O₂ séparant les deux axes. Dans la suite de la description, on appelera α, l'angle réalisé par la première barre O₁A, et β l'angle réalisé par la seconde barre disposée sur l'axe de commande O₂. Les dimensions des barres doivent être telles qu'elles vérifient les relations suivantes :

1)   AB > O₁O₂ + O₁A - O₂B

Figure imgb0001


2)   AB < O₁A - O₁O₂ + O₂B
Figure imgb0002

   La figure 8 représente de façon plus détaillée ce dispositif du type à 4 barres. Selon un mode de réalisation particulier O₁A = 2,54 cm ; AB = 2,48 cm ; O₂B = 1,84 cm ; O₁O₂ = 1,46 cm. L'axe de
commande O₂ est relié au bloc porte-poinçons par l'intermédiaire d'un mécanisme bielle-manivelle 40 qui peut être du type à excentrique. Selon un mode de réalisation, la longueur de l'excentrique est de l'ordre de 1,8 mm. Ainsi que représenté à la figure 3, la bielle 40 commandée par ledit excentrique est reliée au bloc porte-poinçons en un point situé entre l'axe horizontal fixe et les rangées de poinçons de telle sorte que les poinçons décrivent un mouvement sensiblement vertical dont l'amplitude est de l'ordre de 4,5 mm. (En réalité, il s'agit d'un arc de cercle de très faible amplitude (≃ 2°)). Cette amplitude est inférieure d'environ 75 % à l'amplitude du mouvement vertical des dispositifs connus jusqu'à présent et ce, pour une même amplitude de déplacement dans le sens de la bande. Selon la présente invention le bloc porte-poinçons décrit sensiblement une ellipse dissymétrique par rapport à un axe horizontal. Une telle disposition permet de pouvoir augmenter l'épaisseur des lames-ressort formant la liaison élastique et donc d'augmenter la rigidité du système.For this purpose, the movement of the punch block around said fixed horizontal axis is achieved by means of a device with two rotary axes in which a uniform rotation speed of a motor axis produces a speed varying continuously during each revolution of the the axis controlling the movement of the punch block, said uniform speed of rotation of the motor axis being equal to the speed of rotation of the connecting rod-crank devices controlling the movement back and forth, parallel to the plane of the strip, of said perforation device. According to one embodiment, this device with two rotary axes is, as shown schematically in FIG. 5, of the 4 bar type. A first bar O₁A arranged on the motor axis O₁ is driven in rotation at constant speed. According to one embodiment, this speed is of the order of 1600 revolutions / min. The second bar O₂B is on the control axis O₂ and rotates at variable speed; a third bar AB connects the free ends of the first two bars, the fourth bar being constituted by the fixed distance O₁O₂ separating the two axes. In the following description, we will call α, the angle produced by the first bar O₁A, and β the angle produced by the second bar placed on the control axis O₂. The dimensions of bars must be such that they verify the following relationships:

1) AB> O₁O₂ + O₁A - O₂B
Figure imgb0001

2) AB <O₁A - O₁O₂ + O₂B
Figure imgb0002

Figure 8 shows in more detail this device of the 4-bar type. According to a particular embodiment O₁A = 2.54 cm; AB = 2.48 cm; O₂B = 1.84 cm; WHERE = 1.46 cm. The axis of
control WHERE is connected to the punch holder block via a connecting rod-crank mechanism 40 which may be of the eccentric type. According to one embodiment, the length of the eccentric is of the order of 1.8 mm. As shown in Figure 3, the rod 40 controlled by said eccentric is connected to the punch block at a point between the fixed horizontal axis and the rows of punches so that the punches describe a substantially vertical movement whose l amplitude is of the order of 4.5 mm. (In reality, it is an arc of a very small amplitude (≃ 2 °)). This amplitude is approximately 75% less than the amplitude of the vertical movement of the devices known up to now, for the same amplitude of movement in the direction of the strip. According to the present invention, the punch block substantially describes an asymmetrical ellipse with respect to a horizontal axis. Such an arrangement makes it possible to be able to increase the thickness of the spring-blades forming the elastic connection and therefore to increase the rigidity of the system.

Pour des raisons de synchronisation, les axes moteur commandant le mouvement horizontal ainsi que l'axe moteur commandant le mouvement vertical sont entraînés à la même vitesse au moyen d'un unique moteur.For synchronization reasons, the motor axes controlling the horizontal movement as well as the motor axis controlling the vertical movement are driven at the same speed by means of a single motor.

La Fig. 6 représente les variations de la vitesse angulaire de la barre O₂B en fonction de l'angle α réalisé par la barre O₁A disposée sur l'axe moteur et tournant à vitesse continue, ladite vitesse continue étant représentée par la droite parallèle à l'axe des abscisses. La valeur moyenne de la vitesse angulaire de la barre O₂B est bien sûr égale à la vitesse angulaire de l'axe moteur, mais ladite vitesse de la barre O₂B est, en valeur instantanée, tantôt supérieure à la vitesse de l'axe moteur, tantôt inférieure. Dans le but de minimiser le temps de contact des poinçons avec la bande, l'excentrique commandant le mouvement du bloc porte-poinçons sera bien sûr choisi et disposé de telle sorte que la perforation ait effectivement lieu pendant une durée au cours de laquelle la vitesse de la barre O₂B est maximale, (délimitée par les deux lignes verticales sur la figure 6), cette période devant coincider avec la période où la vitesse du mouvement de va-et-vient de la perforatrice est sensiblement identique à celle de la bande.Fig. 6 represents the variations in the angular speed of the O₂B bar as a function of the angle α produced by the O₁A bar arranged on the motor axis and rotating at continuous speed, said continuous speed being represented by the straight line parallel to the abscissa axis. The average value of the angular speed of the O₂B bar is of course equal to the angular speed of the motor axis, but said speed of the O₂B bar is, in instantaneous value, sometimes higher than the speed of the motor axis, sometimes lower. In order to minimize the contact time of the punches with the band, the eccentric controlling the movement of the punch block will of course be chosen and arranged so that the perforation actually takes place for a period during which the speed of the bar O₂B is maximum, (delimited by the two vertical lines in FIG. 6), this period having to coincide with the period when the speed of the reciprocating movement of the perforator is substantially identical to that of the strip.

La Fig. 7 à laquelle on fait maintenant référence est un graphique représentant la vitesse du mouvement de va-et-vient de la perforatrice sur une portion de période du mouvement de la manivelle commandant ledit mouvement. On porte en abscisse l'angle ϑ réalisé par la manivelle et en ordonnée la vitesse de déplacement horizontale de la perforatrice (en % par rapport à la vitesse maximale dudit déplacement). La vitesse uniforme de déplacement du film est également représentée par une droite parallèle à l'axe des abscisses correspondant dans ce mode de réalisation particulier à une vitesse de 100 m/min. Plusieurs points représentant des positions particulières des poinçons et des broches de guidage ont été portés sur la courbe : (dans cet exemple, on a les valeurs suivantes : R = 9,5 mm L = 105,4 mm ; pénétration des poinçons = 0,25 mm ; différence de longueur entre les poinçons et les broches de guidage = 1,1 mm ; vitesse d'entraînement de la manivelle = 1600 tours/mn). Ces positions particulières sont les suivantes :

  • point A : les broches de guidage atteignent le bloc dévétisseur ; 52°<ϑ<58°
  • point B : les broches de guidage atteignent le plan de la bande
  • point C : les broches de guidage sont disposées dans les perforations précédentes correspondantes
  • point D : les poinçons arrivent au contact de la bande
  • point E : les poinçons perforent la bande ; ils sont au maximum de leur course
  • point F : les poinçons quittent le plan de la bande
  • point G : les broches de guidage quittent le plan de la bande
  • point H : les broches de guidage quittent le bloc dévétisseur 122°<ϑ<128°.
Fig. 7 to which reference is now made is a graph representing the speed of the reciprocating movement of the perforator over a period portion of the movement of the crank controlling said movement. The angle ϑ made by the crank is plotted on the abscissa and the speed of horizontal movement of the perforator on the ordinate (in% relative to the maximum speed of said movement). The uniform speed of movement of the film is also represented by a straight line parallel to the axis of the corresponding abscissa in this particular embodiment at a speed of 100 m / min. Several points representing particular positions of the punches and guide pins were plotted on the curve: (in this example, we have the following values: R = 9.5 mm L = 105.4 mm; penetration of the punches = 0, 25 mm; length difference between punches and guide pins = 1.1 mm; crank drive speed = 1600 rpm). These particular positions are as follows:
  • point A: the guide pins reach the stripper block; 52 ° <ϑ <58 °
  • point B: the guide pins reach the plane of the strip
  • point C: the guide pins are arranged in the corresponding previous perforations
  • point D: the punches come into contact with the strip
  • point E: the punches perforate the strip; they are at their maximum
  • point F: the punches leave the plane of the strip
  • point G: the guide pins leave the strip plane
  • point H: the guide pins leave the stripper block 122 ° <ϑ <128 °.

L'angle ϑ compris entre l'instant où les broches de guidage atteignent le bloc dévétisseur et l'instant où lesdites broches de guidage quittent ledit bloc dévétisseur est aussi appelé angle d'engagement et selon ce mode de réalisation est de l'ordre de 70°. A partir du point B jusqu'au point H, il est nécessaire que la vitesse de la bande soit sensiblement identique à la vitesse horizontale de la perforatrice. Entre ces deux points, la courte période pendant laquelle la vitesse horizontale est supérieure à la vitesse de la bande est compensée en faisant réaliser à la bande, juste en amont de la perforatrice, une boucle non tendue, Cet angle d'engagement, d'environ 70°, correspond également à un angle d'environ 70° de la barre reliée à l'axe moteur O₁ du mécanisme à quatre barres évoqué précédemment, Lorsque ladite barre, reliée à l'axe moteur, parcourt cet angle α ≃ 70° à une vitesse constante de 1600 tours/mn, la barre reliée à l'axe de commande O₂ parcourt un angle β≃ 153°, à la vitesse variable telle que délimitée par les deux lignes verticales représentées à la figure 6. Selon un mode de réalisation particulier, cet angle d'engagement de 70° correspond, dans l'exemple utilisé, à l'intervalle Δα = [121° - 191°]

Figure imgb0003
pour la manivelle disposée sur l'axe moteur et à l'intervalle Δβ = [161° - 314°]
Figure imgb0004
 pour la manivelle disposée sur l'axe de commande O₂. Ces intervalles sont portés sur le schéma de la figure 8. Cet angle de 70° pour une vitesse d'entraînement de 1600 tours/mn représente une durée d'environ 7 ms.The angle ϑ between the moment when the guide pins reach the stripper block and the moment when said guide pins leave said stripper block is also called the engagement angle and according to this embodiment is of the order of 70 °. From point B to point H, the speed of the strip must be substantially identical to the horizontal speed of the hole punch. Between these two points, the short period during which the horizontal speed is greater than the speed of the strip is compensated for by making the strip, just upstream of the perforator, an unstretched loop, This angle of engagement, approximately 70 °, also corresponds to an angle of approximately 70 ° of the bar connected to the motor axis O₁ of the four-bar mechanism mentioned above, When said bar, connected to the motor axis, traverses this angle α ≃ 70 ° at a constant speed of 1600 rpm, the bar connected to the control axis O₂ travels an angle β≃ 153 °, at variable speed as delimited by the two vertical lines represented in FIG. 6. According to a particular embodiment, this angle of engagement of 70 ° corresponds, in the example used, to the interval Δα = [121 ° - 191 °]
Figure imgb0003
 for the crank arranged on the motor axis and at the interval Δβ = [161 ° - 314 °]
Figure imgb0004
 for the crank arranged on the O l'axe control axis. These intervals are shown in the diagram in FIG. 8. This angle of 70 ° for a drive speed of 1600 rpm represents a duration of approximately 7 ms.

Ainsi que représenté en figure 1, le dispositif de perforation selon la présente invention comprend entre le bloc porte-poinçons et le bloc porte-matrice un mécanisme dérivé d'un mécanisme de SCOTT-RUSSELL et constitué d'un organe en X, 50, de telle sorte qu'il permette un mouvement du bloc porte-poinçons autour de l'axe horizontal fixe mais empêche tout mouvement latéral de l'un des blocs par rapport à l'autre, permettant ainsi d'accroître la rigidité du système. Un mécanisme de SCOTT-RUSSELL classique est représenté en traits continus à la figure 9. Un tel dispositif contraint le point P₂ à se déplacer selon un mouvement perpendiculaire à la droite portée par P₁ et P₃. Les traits interrompus représentent une variante du mécanisme de SCOTT RUSSELL permettant, par effet miroir, d'obtenir les effets de deux mécanismes de SCOTT RUSSELL. Une telle disposition accroît la résistance au mouvement latéral entre les blocs. La figure 10 représente de façon schématique un exemple de disposition d'un tel mécanisme entre le bloc porte-poinçons et le bloc porte-matrice. Les articulations représentées à la figure 9 aux points P₁, P₂, P₃ et C sont remplacées par des éléments flexibles f₁-f₆, augmentant ainsi la résistance au mouvement latéral. Les déformations des éléments flexibles f₁-f₆ sont telles qu'elles conservent les relations géométriques nécessaires à un tel mécanisme, à savoir P₁C = P₂C = P₃C

Figure imgb0005
.As shown in FIG. 1, the perforation device according to the present invention comprises, between the punch holder block and the die holder block, a mechanism derived from a SCOTT-RUSSELL mechanism and consisting of an X-shaped member, 50, so that it allows movement of the punch block around the fixed horizontal axis but prevents any lateral movement of one of the blocks relative to the other, thereby increasing the rigidity of the system. A classic SCOTT-RUSSELL mechanism is shown in solid lines in FIG. 9. Such a device forces the point P₂ to move in a movement perpendicular to the line carried by P₁ and P₃. The broken lines represent a variant of the SCOTT RUSSELL mechanism allowing, by mirror effect, to obtain the effects of two SCOTT RUSSELL mechanisms. Such an arrangement increases the resistance to lateral movement between the blocks. FIG. 10 schematically shows an example of the arrangement of such a mechanism between the punch holder block and the die holder block. The joints shown in Figure 9 at points P₁, P₂, P₃ and C are replaced by flexible elements f₁-f₆, thus increasing the resistance to lateral movement. The deformations of the flexible elements f₁-f₆ are such that they preserve the geometrical relations necessary for such a mechanism, namely P₁C = P₂C = P₃C
Figure imgb0005
 .

Les dimensions du dispositif selon la présente invention sont, pour le mode de réalisation représenté à la figure 1, de l'ordre de 41 cm x 37 cm x 25 cm.The dimensions of the device according to the present invention are, for the embodiment shown in Figure 1, of the order of 41 cm x 37 cm x 25 cm.

Claims (22)

  1. Device for carrying out an operation, according to a given pitch, on a uniformly and continuously movable web (3), comprising a first block (1, 31, 70) provided with a tool (34, 72), arranged so as to, periodically, be able to engage a member (35, 81) complementary to said tool (34, 72) which is provided on a second block (2, 32, 80), the said two blocks being hung to a stationary frame (23), said web moving between said two blocks, said device being characterized in that said periodical engagement of the tool (34, 72) with the complementary member (35, 81) is realized by a combined movement of the first block (1, 31, 70) describing a short portion of an arc of a circle around a stationary horizontal axis (9) parallel to the movement axis of the web (3), said two blocks being connected at the level of said stationary horizontal axis (9), and the movement of the two connected blocks which are driven, parallel to the movement axis of the web (3) by a reciprocating movement of magnitude substantially greater than that of the movement of the first block (1, 31, 70) around said stationary axis (9) and of identical period, the velocity of said web (3) being substantially equal to the horizontal velocity of the tool (34, 72) when said tool (34, 72) engage said complementary member (35, 81) provided on said second block.
  2. Device according to claim 1, characterised in that said reciprocating movement of magnitude A is ensured by means of a structure which can be distorted comprising, in a plane orthogonal to the plane of the web (3), two parallelograms (12, 13) which can be distorted each having two sides (14, 15 ; 15, 16) parallel to said plane of the web (3), one of these parallel sides being common to the two parallelograms (12, 13) and driven, according to a first plane parallel to the plane of the web in a reciprocating movement of magnitude A/2, said other parallel side (14) of the first parallelogram (13) is stationary, that (16) of the second parallelogram (12) is movable and driven in said second plane in a reciprocating movement, of magnitude A and in phase with the movement of magnitude A/2.
  3. Device according to claim 2, characterised in that the two other sides (14, 16) of said parallelograms (12, 13) are constructed of a flexible material.
  4. Device according to claim 1, characterised in that the reciprocating movement is provided by means of a mechanism comprising a first and a second flexible member, (17) and (18), arranged on both sides of said device in the plane perpendicular to said stationary horizontal axis and each defining a central blade (20) and two side blades, (19) and (21), the lower end of said side blades (19, 21) and of said central blade (20) of said first member (17) being respectively connected to the lower end of the side blades (19, 21) and with the central blade (20) of said second member (18) by means of a joining member (22) arranged parallel to the plane of the web, said joining member being partially free translationally in the direction of movement of the web (3), said side blades(19, 21) of each of the flexible members having their upper end connected to the frame (23), said central blades(20) of said flexible members (17, 18) having their upper end being connected to said second block (2, 32, 80), the central blade (20) of one(18) of the flexible members (17, 18) having its upper end connected to a first crank-connecting rod device (25), of which the crank describes a radius R and the connecting rod is of length L, and having its lower end connected to a second crank-connecting rod device (24) of which the crank describes a radius R/2 and the connecting rod is of length L/2, said cranks turning at the same angular speed and in opposite phase.
  5. Device according to claim 4, characterised in that the magnitude of the reciprocating movement is in the order of 20 mm.
  6. Device according to either of claims 4 or 5, characterised in that the crank-connecting rod device are achieved by means of mechanisms with eccentric.
  7. Device according to any one of claims 4 to 6, characterised in that the ratio R:L is less than 0.25.
  8. Device according to any one of claims 1 to 7, characterised in that the link from the first block (1, 31, 70) to the second block (2, 32, 80) is an elastic one comprising two sets of non-coplanar spring blades, (10) and (11), the intersecting straight line of the two planes corresponding to the stationary horizontal axis (9) around which said first block (1, 31, 70) swings, one end of each spring blade being fastened to said first block (1, 31, 70) and the other to said second block (2).
  9. Device according to claim 8, characterised in that one of said planes is parallel to the plane of the web, the other plane being substantially perpendicular to the first.
  10. Device according to either of claims 8 or 9, characterised in that the thickness of said blades (10, 11) lies between 2 and 3 mm.
  11. Device according to any one of claims 1 to 10, characterised in that the movement of said first block (1, 31, 70) around said stationary horizontal axis (9) is achieved by means of a device with two rotating axes (O₁, O₂) in which a speed of uniform rotation of a motor axis (O₁) produces a speed varying continuously during each revolution of the axis controlling the movement of said first block (1, 31, 70) around said stationary horizontal axis (9), said speed of uniform rotation of the motor axis (O₁) being equal to the speed of rotation of the crank-connecting rod devices (24, 25) controlling the reciprocating movement of said device parallel to the plane of the web.
  12. Device according to claim 11, characterised in that the device with two rotating axes (O₁, O₂) is of a four-bar linkage type, a first bar O₁A on the motor axis, and a second bar O₂B on the control axis, the two said bars having their free end connected to a third bar AB, and the fourth bar consisting of the fixed distance O₁O₂ separating the two said axes.
  13. Device according to claim 12, characterised in that the control movement of the first block (1, 31, 70) is transmitted to said first block (1, 31, 70) by a mechanism with eccentric.
  14. Device according to any one of claims 1 to 13, characterised in that a flexible device (50) is provided between the first block (1, 31, 70) and said second block (2, 32, 80), parallel to said stationary horizontal axis (9), derived from a mechanism of the type such as a SCOTT-RUSSEL mechanism, so as to prevent any translational movement, in the direction of the movement axis of the web (3), by said first block (1, 31, 70) in relation to said second block (2, 32, 80).
  15. Device according to any one of claims 1 to 14, characterised in that it is fitted with a perforating tool, said first block (31) having a series of punches (34), said second block (32) having a die block (35) suitable to cooperate with said punches (34).
  16. Device according to claim 15, characterised in that the punch block support arm comprises two arrays of punches (34), each comprising at least two punches, arranged opposite each other, parallel to the axis of the web (3) and spaced so as to be able to perforate the two edges of said web, according to a given pitch, each array being provided at its end opposite the inlet edge of the web (3) with at least one guide pin of length greater than that of the punches, arranged so as to engage with one of the perforations made previously and just before the punches (34) come into contact with the web (3), to perforate it, in order to accurately position the punches (34) on said web (3).
  17. Device according to claim 16, characterised in that each of said arrays comprises twelve punches and three guide pins.
  18. Device according to either of claims 16 or 17, characterised in that the length difference between the punches (34) and the guide pins is in the order of 1.2 mm.
  19. Device according to any one of claims 1 to 14, characterised in that it is fitted with a cutting tool, said first block (70) being provided with a knife (72), said second block (80) being provided with a bedknife (81) suitable for cooperating with said knife (72).
  20. Device according to any one of claims 1 to 14, characterised in that it is fitted with a stitching tool.
  21. Device according to any one of claims 1 to 14, characterised in that it is fitted with an embossing tool.
  22. Device according to any one of claims 1 to 14, characterised in that it is fitted with a notching tool.
EP91905835A 1990-03-19 1991-03-11 Device for performing an operation at a given pitch on a strip Expired - Lifetime EP0521025B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9003697A FR2659589B1 (en) 1990-03-19 1990-03-19 DEVICE FOR PERFORMING AN OPERATION ACCORDING TO A DETERMINED STEP.
FR9003697 1990-03-19
PCT/FR1991/000191 WO1991014550A1 (en) 1990-03-19 1991-03-11 Device for performing an operation at a given pitch on a strip

Publications (2)

Publication Number Publication Date
EP0521025A1 EP0521025A1 (en) 1993-01-07
EP0521025B1 true EP0521025B1 (en) 1994-12-28

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EP91905835A Expired - Lifetime EP0521025B1 (en) 1990-03-19 1991-03-11 Device for performing an operation at a given pitch on a strip

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US (1) US5263393A (en)
EP (1) EP0521025B1 (en)
JP (1) JPH05505768A (en)
DE (1) DE69106350T2 (en)
FR (1) FR2659589B1 (en)
WO (1) WO1991014550A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0733950A1 (en) * 1995-03-24 1996-09-25 Eastman Kodak Company Splice cutting and film re-shaping apparatus
CN113878629B (en) * 2021-09-24 2023-03-10 温州市众邦拉链有限公司 Zipper strip cutting equipment

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FR2315367A1 (en) * 1975-06-26 1977-01-21 Kodak Pathe IMPROVEMENTS TO TAPE PERFORATION DEVICES, ESPECIALLY PHOTOGRAPHIC AND CINEMATOGRAPHIC FILMS

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FR2315367A1 (en) * 1975-06-26 1977-01-21 Kodak Pathe IMPROVEMENTS TO TAPE PERFORATION DEVICES, ESPECIALLY PHOTOGRAPHIC AND CINEMATOGRAPHIC FILMS

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DE69106350D1 (en) 1995-02-09
WO1991014550A1 (en) 1991-10-03
FR2659589A1 (en) 1991-09-20
EP0521025A1 (en) 1993-01-07
US5263393A (en) 1993-11-23
JPH05505768A (en) 1993-08-26
DE69106350T2 (en) 1995-07-13
FR2659589B1 (en) 1992-06-12

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