DE10017347A1 - Clamping caliper for holding edges of plastic films during stretching has a caliper lever with a clamping moving along a path with varying radius - Google Patents

Abstract

A caliper lever arrangement(5) includes a lever(10) which moves between positions in which the film edges(3) are held or released. When moving between the two positions a clamping head(12) of the lever performs a swiveling movement along a non-circular path.

Description

The invention relates to a clip with progressive Opening and closing characteristics according to the generic term of claim 1.

Claws are used in the technique for longitudinally moving matter Albahnen, in particular foil webs, needed. Example wise in a device for stretching art Fabric film webs are symmetrical to the direction of transport closed management on the left and right direction provided on the all around provided chain link links or clip car are on which the clips at the beginning of the device Take material or film web and until the end of Move the device. Corresponding machines are also NEN known in which the Klagenwagen not mechanically are connected to each other, but by linear motor drives independently along the endless rail guide  are movable. Such transport systems are in particular re used for stretching systems, where plastic foils can be stretched simultaneously in two axes. Appropriate Kluppenwagen are for example in DE-A-44 36 676 or in DE-A-195 10 141 discloses.

The corresponding Klup in the device pen levers, also known as knife flaps, by suitable means actuators once in their closed position, in the the material or film web between its clamp piece and the clamp table, and at the end ver the device in its open position pivots in the material or film web again release. The clips are according to the state of the art nik with an axle bolt that corresponds in one Appropriate axle bearing formed on the tiller body device. Such a clip is e.g. B. from the Offenle supply document DE 17 10 745 known.

However, the known constructions have the disadvantage on that the brackets only for a relatively limited area of film edge thicknesses are suitable. This arises in part also point out the need for the tenter lever regulations should take up as little space as possible or can, because the Kluppenwagen also in film stretching systems be moved in textile tenter frames by treatment ovens. The pinching then shifts depending on the edge thickness place between the tenter lever and the tenter table. At extreme thin material webs or foils would be the stop in Walk towards the center of the film web, while at very  thick film web edges the clamping point from the center of the web would move away. There are several reasons for this Disadvantage.

Especially in the case of film stretching systems, which after the simultaneous work principle, so the pre-film (cast film) the same ver in two essentially orthogonal axes stretch the edges depending on the process requirements gene, have very different thicknesses. This is is based on the fact that the spacing between the clips in this ver drive with the longitudinal stretch ratio increase, and thus the Tractive forces of the film essentially over the thicker edge be initiated. This is the case with simultaneous stretching systems sufficient holding forces for foils are required, the minimum Have 0.2 mm edge thickness and a maximum of up to 3 mm.

Due to the high output of modern film stretching systems More and more importance is attached to the flexibility of such Machines placed so that the machines are permanently under Full output are full. Only through a diverse Product range and with minimal effort for the Foil storage is an economical operation of such type were possible. Therefore, if possible without changeover times a change to another film product can be achieved his. But that also means that different foils thick on one and the same stretching machine should be made without changes to the clips to have to.

In addition, the edges of certain foils can  this tends to parallel to the direction of the film roll up wisely. In this case, the conventional laces because their gripping area is not double Can cover edge thickness. This means that e.g. B. at Film stretching systems did not hold the film by the clips becomes, and thus the entire production to a standstill is coming.

A clip arrangement is known from DE 17 10 745, with the improved clamping technology in one enlarger th, varying edge thickness range should be possible. According to this prior publication, it is proposed that Optimize the contour of the clamping surface. This well-known Kon However, construction has the disadvantage that the clamp area with thin foils far above the clip table in Protrudes towards the center of the train. This causes the heat transition on the surface of the web near the cleat deteriorates and there is also a risk that the large clamping surface on the clamp lever opens or Closing the clips difficult, or in extreme areas does not work reliably. Hence the edge thickness area in the mentioned prior art by Ver Extension of the clamping surface alone within narrow limits mitiert. On the other hand, of course, one Arrangement according to DE 17 10 745 also by a more extreme crumb the thickness of the clamping surface can be expanded, without the arc length of the clamp foot being too large would have to be extended. However, the gripping and self-locking behavior of the clip negatively affected become.

The object of the present invention is therefore that To overcome disadvantages according to the prior art and especially to create a club that is elevated Gripping area with regard to the thickness of the web edge has and in particular a small space claimed.

The task is according to the invention in accordance with pronounced 1 or 25 specified features. Advantageous te embodiments of the invention are in the dependent claims Chen specified.

The invention creates with amazingly simple means a clearly enlarged gripping range of greatly varied thicknesses of web edges to be held. About that however, the construction according to the invention also offers the advantage of better accessibility of the clamping area ches. This also makes it easier to clean compared to conventional clips. Another important advantage is that with the invention Solution by suitable choice of the swing curve on the on optimal force of the clamp lever on the edge of the web can be adjusted. So z. B. on machines which notch sensitive products such. B. polyamide or Polystyrene films are to be produced, the pressing forces caused by the self-locking effect of the clamp direction are applied, limited accordingly and be reduced.

The solution according to the invention is characterized on the one hand  all from the fact that a suitable swing curve of the Clamping surface is provided, namely such that the Swivel radius or the curvature of the swivel curve with too taking swivel bow changed.

From DE 28 30 236 a clip can be seen in the the clamp lever can be swiveled around two axes. However, the gripping area in the Not increased with regard to different edge thicknesses become. Through the second axis of rotation in this publication chung is only achieved that the clamping part of the Clip lever in a cleaning or tempering position can be brought. The tenter lever itself will also according to this previous publication only in the form of a circle bow pivoted, when opening or closing this Kluppe the tenter lever around only one axis in the circular arc is rotated and only in preparation for the end swivel into the cleaning or tempering position second axis of rotation is used.

In this case, preference is given to starting from the beginning of the pivot movement The definition is equivalent to the Hal teposition of the tenter lever the swivel radius at least increasingly enlarged during a partial pivoting movement, so that the curvature decreases on the non-linear circular path.

According to the invention is a rather steep beginning and then flattened swivel curve for the holding section of a Clutch lever provided. Such a swing curve is but not only advantageous if the web - as stated  - requires gentle clamping, even then, if a positive power transmission between the club and web is possible. Especially with textile webs So-called needle clips are often used, which Edges by means of needles pushed through the material will hold. Thanks to the new swing curve so clip arrangements can be realized on a Combination of frictional and positive holding force based hen, this is nevertheless in a space-saving construction is feasible.

The arrangement of the movement path and the swivel or tilting axis of the clamp lever in such a way that the trajectory in relation to the one to be transported Material web comes to lie concave.

An alternative solution according to the invention is based on this built that covered the holding section of the tenter lever a convex path of movement on the material web executes, so preferably the pivot or tilt axis of the Clutch lever opposite the swivel path of the Hal section of the tenter lever opposite the material web is further out. However, preference can also be given here The trajectory is not designed to be circular his.

In such a solution, it is preferably provided that a larger curvature starting from the stop position radius is realized with increasing lifting motion is reduced from the clutch table so that the curvature of the  non-linear circular path becomes larger.

The solutions according to the invention can differ by most simple construction principles can be realized. Be Solutions in the form of multi-part, z. B. four-link coupling gear, for example two Have axes of rotation so that over the gear arrangement a superimposed desired tilting movement for the club pen lever or its holding section in the corresponding Way can be realized. Through multi-part coupling In principle, transmissions are any coupling curves bar. Examples of basic design variants are not discussed in detail below, it will however in this connection to the book "Dubbel, Paperback for mechanical engineering, 17th edition, chapter 9, Gear Technology ".

Alternatively or additionally, it is also provided that the Clutch table with an adjustable support surface verse hen is. The adjustable contact surface is so ge stalt that a self-locking during the clamping process of the Edge of the material web is caused or reinforced. In this case, the tensile forces of the material web are preferred an increase in the clamping force can be achieved. This can for example by means of a wedge-shaped setting element tes or for example by means of a parallelogram or comparable solutions.

The invention is described below with reference to drawings Referring to various possible embodiments  explained. Show in detail

Fig. 1: a schematic representation of a desired pivot path for a Klup pen lever with non-circular Ver pivot path for its holding portion;

Fig. 2: an alternative embodiment compared to the embodiment of Figure 1, in which the holding portion of the Kloppelhe lever from its holding position with a more vertical component of movement ge compared to the clutch table;

Fig. 3: another embodiment with egg ner S-shaped path of a Klup penhebels;

Fig. 4: a schematic perspective presen- tation of a tenter lever arrangement;

Fig. 5a-5d: four examples of an eccentric rotary axis body for the Kloppelhebelanord voltage according to Fig. 4;

Fig. 6a-6c: three modified embodiments with tenter levers that include a knee joint;

Fig. 7a and 7b: two examples of a four-link gear arrangement of an adjustable clip lever, which is adjustable via two ver pivotable levers;

Fig. 8a: another modified Ausführungsbei game with a height-adjustable support of a clip table; and

FIG. 8b shows a modified embodiment to Fig. 6.

In Fig. 1 a partial view is shown on a material web 1 in cross section transversely to the advance movement, the advance movement takes place perpendicular to the drawing plane.

In the schematic cross-sectional view according to FIG. 1, the right edge 3 of the material web can also be seen, which is held clamped on a clip arrangement 5 , who is supposed to.

For this purpose, the clip arrangement 5 comprises a so-called clip table 7 , above which a clip lever 10 is pivotally arranged, which is pivotable with its holding section 12 on a movement path 14 between a clamping position and a release position.

In the clamping position, the edge 3 of the material web 1 is held and secured between the holding section 12 and the clip table 7 .

. From the view in Figure 1 it can be seen that - as usual in itself - the pivotal path of movement 14 of the Klup is designed concave penhebels 10 relative to the material web 1, so that therefore the pan or tilt axis of the clips lever 10 to the material web 1 is nearer than the ge compared to distant pivoting motion path 14th

In the exemplary embodiment shown, no fixed pivot or tilt axis 16 is now provided for the clip lever compared to the entire clip arrangement, but a positionally variable pivot or tilt axis 16 and / or an arrangement in which the effective length 10 'of the clip lever 10 is on its way Swivel movement, ie at least over a portion of its swivel movement is changeable ver.

For this purpose, it is indicated in FIG. 1 that in the holding and fixing position, the pivot or tilt axis 16 is located at the point identified by reference number 16 ', whereas the position of the pivot or tilt axis 16 identified by reference number 16 "is located elsewhere when the clip lever is pivoted into the corresponding release position. In the clamped position, the effective clip lever length 100 'is shorter than the effective clip lever length 100 "with the clip lever pivoted into the release position.

It also follows that the swivel movement path 14 does not follow a circular path, but the swivel movement path does not run in a circular manner.

The swivel movement path 14 can thus be described as pro gressive, since the curve starting from the clamping point on the tenter table 7 has a path course starting from a radius of curvature r ₀ with an increasingly larger swivel arc length r.

The exemplary embodiment according to FIG. 2 initially differs from that according to FIG. 1 in that the clip lever 10 in the immediate vicinity of its fixing or stop position on the clip table 7 does not run tangentially, but rather vertically to it. This may be because by realizing that the pivotal movement of web 14 ge genüber of the material web 1 is not concave, but is made convex running, in other words the swivel or tilting axis 16 of the lever arrangement with respect to the material web 1 is arranged further outward than in the embodiment according to Fig. 1.

But also in this embodiment, a non-circular swivel movement path 14 is preferably seen before. The curve curve course according to FIG. 2 results in principle in comparison to that according to FIG. 1 by a reflection about a virtual axis. The radius of curvature and thus the effective length 100 'of the clip lever 10 is large in its fixing and holding position of the material web 1 and becomes smaller with increasing pivoting movement away from its fixing position.

This curve shape has the advantage that when fixing the edge of the material web there is a tendency that the edge 3 of the material web is pushed into the clamping area. This means that even with uneven film edges, this geometry makes plant operation even safer.

A further modification is shown with reference to FIG. 3, in which an S-shaped movement path results for the clamping section 12 of a clip lever. This embodiment has the advantage that even in a solution with a three-point position according to FIG. 2, self-locking can be achieved, as is basically realized in an embodiment according to FIG. 1. Also in this embodiment, the respective effective pivoting and tilting axes 16 and the respective effective Klup penhebellängen 100 'and 100 "are shown in different movements.

A basic embodiment of a clip lever arrangement according to the Invention is shown with reference to the perspective view of FIG. 4.

In principle, the exemplary embodiment according to FIG. 4 is an exemplary embodiment in which the clip lever 10 is integrated in a four-part coupling system.

According to FIG. 3, the tenter lever includes an upper actuating or triggering section 21 and a holding section 12 which is rather lower than the swiveling or tilting axis 16 and which is at least in view parallel to the swiveling or tilting axis 16 slightly curved or ball-shaped.

On the side facing the material web, a gear axis 23 parallel to the pivoting / tilting axis 16 is also formed on the tenter lever, on which a gear rod 25 is pivotally held. At the opposite end, the gear rod 25 is also pivotally movable on a fixed bearing 27 about a fixed bearing axis 29 .

Finally, the swivel and tilt axis 16 , which is shown in the exemplary embodiment shown only to clarify the bearing situation with an oversized axial length, is realized as an eccentric axis. For this purpose, the axle body 16 a of the swivel and tilt axis 16 at the end 31 ends in an eccentrically seated axle body 16 b, which is anchored and held in the claws in a corresponding fixed bearing 20 so that it can rotate.

In contrast to the long eccentric axis in practice the bearing point is as close as possible to the Clamp lever cheeks are placed to make a compact construction to realize wisely.

This embodiment is a four-link coupling gear. As a result, a forced movement for the clutch lever 10 is realized such that during the pivoting movement of the gear rod 25 describes a circular path around the fixed bearing axis 29 and the clip lever performs a superimposed circular Ver pivoting movement relative to its gear axis 23 . Here, the tenter lever rotates on the axle body 16 a of its pivot and tilt axis 16 , the eccentric axis executing a rotational movement about the eccentric axle body bolts 16 b in their bearings by the forced guidance. Building on such a principle, the non-circular swivel movement path indicated in FIG. 1 can be realized for the holding section 12 of the clip lever arrangement 5 .

The sake of completeness, it is noted that in place of the transmission rod 25 also a different type of Ge gear element 25 may be provided, for example in the form of a spring, in particular a compression spring which is supported between a fixed bearing 29 and a corresponding Ge gear bearings 23rd This could create a dead center characteristic, such that the spring clip device 10 is held in its setting in its fixing and holding position by means of this spring device, whereas it is biased in the open position after the dead center has been exceeded.

The component 25 can also be designed as a length-adjustable sliding piece with or without a spring. Furthermore, it can be advantageous if a spring provided has a certain damping characteristic. It is also possible that a combination of a spring and a damper can be used (with or without a length-adjustable sliding piece, which is preferably articulated at its opposite ends as shown in FIG. 4).

FIGS. 5a and 5b show two different variants of the eccentric pin, such as may be used for the execution of a Kop pelgetriebes. The variant has 4 b with respect to the variant according to Fig. 4a the advantage that the annular surfaces are larger for the storage of the bolt ends and thus the bearing load is reduced at this point. In principle, the eccentric geometry should be designed in such a way that the maximum load on the bearing points is as low as possible in order to prevent a bearing from knocking out or to increase the service life of the bearings. It goes without saying that all known slide or roller bearing systems can be used for the storage. In particular, the use of special bearing bushes or lubrication-free bearing materials, e.g. B. based on polyimide, which are suitable for the required operating temperatures and loads.

In Fig. 5c, a further variant is shown, in which the eccentric pin is designed as a component, but consists of two telescopic cylinders. In comparison to FIGS. 4a and 4b, this design has an additional rotary joint or an additional rotary surface 160 between the outer surface of the smaller and the inner surface of the larger cylinder.

Referring to Fig. 5D is a possibility of realizing a four-membered dome transmission for a clip lever is shown in FIG. 4 are reproduced. In Fig. 5d, the axle body 16 a and the eccentric axle body bolt 16 b is shown. Opposite to the axle body 16 a, a concentric axle disk 16 c is provided. This opens up the possibility of inserting the pivot axis 16 thus formed into a corresponding bore in the tenter lever 10 , the bearing of the tenter lever being carried out once on the axle body 16 a and the concentric axle disk 16 c.

Referring to Fig. 6a and 6b modifications are shown in which the clip lever 10 is divided into two parts for example, and the two Kluppenhebelabschnitte 100 a, 100 includes b, wherein the Kluppenhebelabschnitt 100a in sections with the holding 12 is provided, via a pivot axis 39 with the further tenter lever section 100 b is connected, which carries it. The swivel axis 39 is in turn preferably running parallel to the not shown pivot and tilt axis 16 of the clip lever 10 angeord net.

In the embodiment of Fig. 6a, a spring device 41 in the form of a spiral spring 41 a (a Zugfe the) is provided, which after performing a pivotal movement of the clip lever 10 , ie its Kluppenhebelab section 10 b about its pivot axis 16 corresponding to the arrow representation 43 to an inward-facing (in relation to a left in Fig. 5a material web 1 ) opposite pivoting movement accordingly the arrow 45 is pivoted in the direction of the material web. For this purpose, the helical spring 41 a, which is subject to tension, is supported at one section point on the tenter lever section 100 a and with the other section point on the tenter lever section 100 b.

In the exemplary embodiment according to FIG. 6 b, a spring device 41 with a compression or leaf spring 41 b is used, which implements a corresponding pivoting movement for the toggle joint when the holding section 12 is lifted off the clutch table 7 .

Finally, in FIGS . 6a, 6b are incorporated into the clip table 7 or a clamping element 45 is shown hatched thereon. This clamping element 46 can be provided with a suitable tenter table surface (clamping surface) or be made of suitable materials, so that the gripping behavior of the system as a whole can be optimized by such an insert. This applies in particular with regard to hardness and roughness or with regard to the coefficient of friction of the selected materials, all of which contribute decisively to the holding capacity. The same also applies to the clamping surface of the Klup pen levers. Here too, positive clamping properties can be achieved by means of appropriate coatings or coatings using inserts. Particularly in the case of notch-sensitive products, softer surfaces of the clamping elements are preferably used.

In the exemplary embodiment according to FIG. 6c, a further right variant to the exemplary embodiments according to FIGS. 6a, 5b is shown. Here, too, the clip lever 10 includes a rotary or knee joint 39, whereby the clip lever 10 penhebelabschnitt in a bottom provided with the holding portion 12 Klup 100 a and a lever located above the knee joint and the actual pivot axis 16 is divided Kluppenhebelabschnitt b 100th Here, a spring arrangement 41 , 41 c now preferably engages on or in the vicinity of the knee joint 39 and, on the other hand, is supported on a fixed bearing 42 on the claw arrangement. The spring device 41 , 41 c is subjected to pressure. With this arrangement, additional clamping forces are exerted on the edge 3 of the mate rialbahn 1 in the clamping and fixing position, since the distance between the axis of rotation 16 at least in the position shown and the clip table 7 despite the pressure forces introduced via the spring device 41 c cannot be enlarged.

7a and 7b, reference is subsequent to Fig. Withdrawn, the further embodiment is a four membered Gear Unit for a clip lever 10, which is approximately, for example in the exporting via two levers 48 and 49 to form a non-circular Verschwenkungsbahn pivotable. For this purpose, the levers 48 , 49 are each once in a fixed position on a bearing 48.1 or a bearing 49.1 and can be pivoted with the actual clamp lever via pivot joints or bearings 48.2 or 49.2 which can also be pivoted therewith .

In the embodiment according to FIG. 7b, the actual clutch lever 10 is of the same design, but in particular the upper pivot lever 49 has a different length from the exemplary embodiment according to FIG. 7a and is held pivotably about this bearing in relation to the fixed bearing 49.1 provided elsewhere.

In the embodiment according to FIG. 8a, it is further shown that the holding forces, which are caused by the self-locking effect of the clip construction, can be increased by means of a suitable construction of the clip table. Especially with a relatively steep swivel curve of the clip lever 10 , the normal force on the film edge, which is induced by the film pull, can be so low that the frictional forces are no longer sufficient to hold the film during the treatment processes. A displaceable, wedge-shaped support 49 can be used as a technical solution for the design of a corresponding clip table. This wedge 49 is mounted on an inclined surface of the clip body, so that as the film pull increases, the movable body moves in the direction of the center of the web and, at the same time, the upper surface 7 'of the wedge is raised. In this way, an increase in the normal force on the edge of the film is brought about by an increasing film pull, and thus the holding forces are also increased.

Although a rolling bearing is shown schematically in this example, the invention also includes a sliding bearing. Here too, all known and suitable materials come into consideration as material pairings for the bearings, in particular also from the above-mentioned group of polyimides. In order that the wedge-shaped component safely returns to the starting position after the film web has been released, it is advantageous that a spring 53 presses the wedge-shaped element 49 back into the starting position. Deviating from FIG. 8a, a tension spring can of course also be used on the opposite side of the wedge-shaped supports 49 instead of a compression spring. The return device does not necessarily have to be limited to spring elements, but can also be realized, for example, by magnetic arrangements, in particular based on the attraction or repulsion forces of permanent magnets.

Fig. 8b relates to a modified embodiment compared to Fig. 8a. The support 49 is not designed wedge-shaped in this embodiment, but plate-shaped. An adjustment movement with respect to the actual clip body 7 is realized in that the support plate 49 can be pivoted in a constant parallel orientation by a parallel link 61 , whereby the same effect as in the embodiment according to FIG. 8a can be realized.

Claims (28)

1. clamping clip for holding edges ( 3 ) of moving material webs ( 1 ), in particular plastic films, with a clip lever arrangement ( 5 ) which comprises a clip lever ( 10 ) which is pivotable between a fixing position and a release position for the edge ( 3 ) of the material web ( 1 ) can be moved, characterized in that the holding section ( 12 ) of the clip lever ( 10 ) carries out a non-circular swivel movement at least in a partial swivel area. 2. Clamp according to claim 1, characterized in that the swivel and movement path ( 14 ) of the holding section ( 12 ) starting from the fixing position on the Klup pentisch ( 7 ) at least in a partial swivel range per gressive with an increase in the effective radius of curvature (r) runs. 3. Clamp according to claim 1 or 2, characterized in that the swivel or movement path ( 14 ) bezo gene on the material web ( 1 ) is concave. 4. tension clip according to claim 1 or 2, characterized in that the holding section ( 12 ) of the clip lever ( 10 ) has a movement and swivel path ( 14 ), from its fixing position on the clip table ( 7 ) with respect to the clip table ( 7 ) greater vertical motion component than horizontal motion component. 5. Clamp according to one of claims 1, 2 or 4, characterized in that the movement or swivel path ( 14 ) of the holding section ( 12 ) of the clamp lever ( 10 ) describes a convex movement path relative to the material web ( 1 ). 6. Tenter clip according to one of claims 1, 2, 4 or 5, characterized in that the pivot or tilt axis ( 16 ) of the tenter lever ( 10 ) relative to the material web ( 1 ) is more distant than the movement and pivot path ( 14 ) of it Holding section ( 12 ). 7. Tension clip according to one of claims 1, 2 or 4 to 6, characterized in that the movement and swivel path ( 14 ) of the holding section ( 12 ) of the tenter lever ( 10 ) starting from its fixing and holding position on the tenter table ( 7 ) ver progressively at least in a partial swivel range while reducing the effective radius of curvature (r), preferably with a constant change in the radius of curvature. 8. Clamp according to one of claims 1 to 7, characterized in that the holding section ( 12 ) of the Kloppelhe lever ( 10 ) in the side view executes an S-shaped movement and swivel path ( 14 ) at least in a partial swivel range. 9. Clamp according to claim 8, characterized in that the S-shaped movement and swivel path ( 14 ) is oriented such that the end of the movement and swivel path ( 14 ) before reaching the fixing and holding position of the holding section ( 12 ) in the fixing position on the clip table ( 7 ) with respect to the material web ( 1 ) has a concave orientation. 10. A tenter clip according to one of claims 1 to 9, characterized in that the tenter lever (10) is divided at least two and a rotary or knee joint (39) about which the retaining portion (12) carrying the clip lever portion (100 a) with respect to the further tenter lever section ( 100 b) carrying it is relatively pivotable. 11. Clamp according to claim 10, characterized in that the effective lever length of the pivotable ( 39 ) relatively pivotable tenter lever section ( 100 a) compared to the other tether lever section ( 100 b) carrying it is comparatively short, in particular less than 50%, in particular less than 25% or 10% of the total length of the clip lever ( 10 ). 12. Tension clip according to claim 10 or 11, characterized in that the two tenter lever sections ( 100 a, 100 b) which can be pivoted relative to one another via a swivel joint can be pivoted relative to one another via a tension or compression spring ( 41 a, 41 b), preferably with Ver using a spiral or leaf spring. 13. Clamp according to one of claims 10 to 12, characterized in that the tension or compression springs ( 41 , 41 a, 41 b) at two section points on the two via the swivel joint ( 39 ) cooperating clip lever sections ( 100 a, 100 b ) are supported. 14. Clamp according to one of claims 10 to 12, characterized in that the spring device ( 41 , 41 c) on the tenter lever ( 10 ), preferably on or in the vicinity of the rotary or knee joint ( 39 ) on the one hand and on a fixed bearing ( 42 ) of the clip carriage arrangement is supported and a fixing position pressurizes the toggle lever ( 10 ) in the sense of increasing the pressure forces in the direction of the clip table ( 7 ). 15. Clamp according to one of claims 1 to 14, characterized in that the clip lever ( 10 ) is part of a coupling gear, preferably part of a four-bar coupling gear. 16. Clamp according to one of claims 1 to 15, characterized in that the pivoting and tilting axis ( 16 ) of the clip lever ( 10 ) is designed as an eccentric axis ( 16 a, 16 b). 17. Clamp according to one of claims 1 to 16, characterized in that the clip lever ( 10 ) with a white direct articulated gear rod ( 25 ), which is pivotable about a fixed bearing ( 27 ) of the clip carriage arrangement, is coupled to be tiltable. 18. Clamp according to one of claims 1 to 16, characterized in that the clip lever ( 10 ) is coupled via a wide res gear element ( 25 ) relative to a fixed bearing ( 27 ), preferably via a length-adjustable sliding piece and / or a spring device , in particular a compression spring device. 19. Clamp according to claim 18, characterized in that the spring device has a damping characteristic has and / or from a combination of a spring with a damper device. 20. Clamp according to one of claims 1 or 19, characterized in that the eccentric axis ( 16 ) is designed so that the outer axle bearing bolts or disks ( 16 b) have a larger diameter than the remaining axle body section ( 16 a). 21. Clamp according to one of claims 1 or 19, characterized in that the eccentric axis ( 16 ) is designed such that the outer axle bearing bolts or disks ( 16 b) have a smaller diameter than the remaining axle body section ( 16 a). 22. Clamp according to one of claims 1 to 21, characterized in that the eccentric axis ( 16 ) outer axle bearing pin ( 16 b) and an inner axle bearing section ( 16 a), which are differently dimensioned, the dimensioned with a smaller diameter Axle bearing section ( 16 a) is inserted into a corresponding bore in the larger dimensioned axle bearing section ( 16 b) and is preferably held rotatably. 23. Clamp according to one of claims 1 to 22, characterized in that the clamp lever ( 10 ) is pivotably guided via at least two pivotable levers ( 48 , 49 ), each lever ( 48 , 49 ) about a fixed bearing ( 48.1 , 49.1 ) is pivotable and for this purpose each of the two levers is connected to the tenter lever ( 10 ) via a pivotable rotary connection ( 48.2 , 49.2 ). 24. Tension clip according to one of claims 1 to 23, characterized in that the clip lever ( 10 ) is at least slightly angled. 25. Clamp according to the preamble of claim 1, in particular according to one of claims 1 to 24, characterized in that the clip table ( 7 ) comprises an adjustable support ( 49 ) which is adjustable while increasing the self-locking forces during the clamping process, ie in Is adjustable in the direction of the clip lever ( 10 ). 26. Clamp according to claim 25, characterized in that the height-adjustable support ( 49 ) consists of a wedge-shaped support ( 49 ) which is guided against an inclined surface ( 51 ) movable and thus adjustable in height. 27. Clamp according to claim 25, characterized in that the support ( 49 ) is adjustable in height by means of a lever guide, in particular a parallelogram guide. 28. Clamp according to one of claims 25 to 27, characterized in that a spring device ( 53 ) is provided which is designed as a compression and / or tension spring device, via which the support ( 49 ) after release of the material web ( 1 ) can be returned to its starting position.