EP1306210A2 - Expansible mandrel, system comprising an expansible mandrel and core, a rotary printing press as well as a method for the dynamic stabilization of an expansible mandrel - Google Patents

Abstract

A tightening shaft (9) for gripping moving peripheral parts (10-14) with gripping devices (15-19) and fastening them as tight as necessary uses extra stop/buffer devices (20-24) designed to limit force exerted by the gripping devices and/or by the peripheral parts that can fasten on the tightening shaft. The stop/buffer devices limit force exerted by the peripheral parts as a method for dynamic stabilizing of the tightening shaft. <??>Independent claims are also included for a device made up of a tightening shaft, for rotary printing machine and for a method for dynamic stabilizing of a tightening shaft.

Description

The invention relates to a clamping shaft for clamping an initially movable peripheral part with a chuck for exciting if necessary attachment of the peripheral part and a method for the dynamic stabilization of a tensioning shaft, in which a first Movable part is attached to the clamping shaft if necessary. The invention also relates to a System comprising a tensioning shaft and a sleeve and a rotary printing machine.

Clamping shafts are required for a number of industrial applications. For tension shafts These are usually rotating parts. These are usually a first movable peripheral part, z. As a sleeve, via expandable elements on the clamping shaft clamped and thereby fastened excitingly on the tension shaft, so that the Clamping shaft with peripheral part are available for a rotating application. The attachment is usually about a frictional connection, in particular a frictional engagement between made the expandable clamping means of the clamping shaft and the peripheral part.

As clamping means are fixed mechanically actuated clamping means as described in EP 0 383 082 A2 known. In particular, however, are pneumatically or hydraulically expandable Clamping means for clamping a peripheral part on a tensioning shaft. You will find application in winding processes and comparable processes, in which a concentricity are sufficient from one to a few tenths of a millimeter. Such tension waves are for example described in US 3,904,144 or EP 0 629 576 A1. At the last mentioned Tensioning shaft is a longitudinally extending shaft with a circumferential Surface provided on the expandable via a fluid pressure pad for clamping a sleeve are provided. These cushions act directly on the sleeve and are depending on occurring Balance of forces, in particular in a rotational application of the tensioning shaft, Compressible, so that a symmetrical or centric position of sleeve and the pillow to the tensioning shaft indifferent and usually not given and in rotary application to an imbalance in such a tensioning shaft and a system of tensioning shaft and sleeve can lead.

Such a tensioning shaft is possibly suitable for achieving a certain concentricity, but not for achieving a concentricity in the range of one hundredths of a millimeter or a few hundredths of a millimeter. Likewise, the deteriorates Concentricity with increase of the radial forces and the torques to be transmitted, which act on the tension shaft. Due to inevitably occurring manufacturing tolerances The tension shaft and the sleeve in terms of roundness and straightness have all known Systems too much play between the tension shaft and sleeve. This causes the Friction between the clamping shaft and sleeve exclusively on the expandable cushion or elements takes place. Solutions for achieving concentricity in the area of Hundredths or a few hundredths of a millimeter are not yet known.

At this point, the invention is based on whose task it is, a tensioning shaft, a system Shaft and sleeve and a rotary printing machine and a method for dynamic Specify stabilization of a clamping shaft, in which a particularly high concentricity is guaranteed.

To solve the problem of the tension shaft, the invention is based on a Clamping shaft of the type mentioned, according to the invention additionally a stop means is provided, which is designed, forces exerted by the Aufspannmittel and / or to limit forces exerted by the peripheral part.

To solve the problem concerning the system and the rotary printing machine leads the Invention to a solution according to the features of claims 11 and 12, respectively.

Furthermore, the invention leads to a method in which the object is achieved by a method of the type mentioned above, in which according to the invention exerted by the part Forces are limited by an additional stop means.

The present invention has recognized that initially movable and then exciting on a Clamping shaft fastened parts as well as the provided clamping means itself initially movable are and for a rotating motion force - in particular frictionally engaged with each other and the tension shaft are attached. However, this does not exclude that in a rotating Application forces occur, which are based on an equilibrium of forces exciting Fixing can bring imbalance and so to a considerable imbalance and nonuniformity. The essential insight lies in the occurring Limiting forces and thereby the possibility of a plant, in particular positive Facility to use such moving parts. This is at the Clamping shaft, the system and the rotary printing form provided a stop means. at In the method, the stop means absorbs applied forces and thus limits these forces.

This has the significant advantage that the transmission of high forces in radial, circumferential and axial direction of a tensioning shaft, but received via the stop means be, so that this to a very high concentricity, in particular to a concentricity in the range of one hundredth or a few hundredths of a millimeter, leads.

Advantageous developments of the invention are described in the subclaims.

Further advantageous is the use of both conical and cylindrical sleeves as a Peripheral part possible.

In particular, one or the provided stop means allows a plurality of different Adjustments of the shaft with regard to their dynamic behavior and advantageous settings with regard to their handling.

For example, by different thickness slats as Aufspannmittel in a Use of the same clamping shaft core can be used, also different inner diameter use of clamping sleeves. For example, a thicker lamella could be used be used when a thinner clamping sleeve is used as a peripheral part. Furthermore For example, a thinner blade could be used if a collet with a larger inside diameter is aufzuspannen. Usually would have for clamping sleeves, each with different Inner diameter and the entire clamping shaft are exchanged.

A tensioning shaft of the type proposed allows a high rotational accuracy alone in that they in the expanded state in their preparation or subsequently in the Insert can be ground. It also has good wear characteristics, in particular in the case of fluid driven chucks, since there is virtually no mechanical guided and moving parts there.

In a particularly preferred embodiment of the invention is a partial or vollumfängliche Stretch layer provided on the tensioning shaft. Such a layer does not have to be full be circumferential and could be limited only to the surface of a lamella. Under Stretch layer is an elastic layer to understand. The elasticity can be due to the material be given to the expansion layer and / or through depressions or channels in or on the Layer. The stretch layer could be provided with a functional profile, for example the supply of coolant or a heating medium allowed. It would be advantageous attach such a functional profile to a fully circumferential layer.

A tensioning shaft together with the stop means circumferentially surrounding layer advantageous An elastic stretch layer offers significant additional benefits. This is how it works occurring force is not directly on the slings, but is first of absorbed the stretch layer. This will be described in detail with reference to the figures. A stretch layer allows a progressive depending on the design of their Elastitzitätseigenschaften increasing force counteracting an external force. This leads to particularly good vibration damping properties in a rotating part like the tensioning shaft of a is, in particular in a system of tensioning shaft and peripheral part, in particular a sleeve. Advantageously, such a layer is mounted on the tensioning shaft. She could, however be located on the inner circumference of a sleeve. For the course of the mentioned progressive Kraft can be set different progressive characteristics of force curves, the Counteract an external force in the event of load. Depending on the application and need Use materials with different E or K modules for the stretch layer. Stretch layer, materials of the stretch layer and optionally a functional profile of the stretch layer are advantageously designed so that when an occurring force or compression Transition from the modulus of elasticity into the K-modulus area in the stretched layer as early as possible, that is, in small already common in rotary applications Forces, takes place. This causes an increase in the counterforce in the stretch layer several orders of magnitude. The advantage here is that occurring external forces, ie in particular forces exerted by the chuck and / or the peripheral part, effectively and be limited early, so that a particularly high concentricity achieved becomes.

According to a further preferred embodiment of the invention is provided, the stop means, in particular a tie rod to make adjustable. So it is possible the partially introduce into an elastic layer einleitbare force. A peripheral part to be wound up if necessary For example, a sleeve, namely subject in general depending on the specific application different bends. The compensation of such bends can be advantageous take place over the stretch layer. Setting options for such compensation On the one hand offers the stretch layer itself and on the other hand also the slings. Especially were above the extending beyond the core of a tensioning shaft height of a Stop means to adjust the forces introduced into an elastic layer. This is above all one height adjustable tie rod, which is a stop for a circumferentially mounted Slat or segment, in particular a circle, is used. The segment becomes a circle segment Understood. The number of segments is composed of a fully circumferential Circle whose line may be interrupted but by smaller gaps. segments are to be preferred. However, it could also be slats provided. These would do not necessarily make a circle except for smaller gaps. Slats would only partially be arranged along a circular line.

A sling can, in particular in a design as a tie rod to the advantageous of Transmission of radial, circumferential and axially acting forces to serve advantageously be designed differently and varied. For example, the head profile of a Zugankers be circular, rectangular or star-shaped to a lamella or a Segment and a particularly suitable for a specific application slings to build.

In a further preferred embodiment of the invention is a total in particular advantageous dynamic behavior is supported by a movement, even in a rotating clamping shaft of the type mentioned, practically only in the elastic coating of the Clamping agent takes place. Possibly used to form a chuck Fluid-based pressure elements and thereby actuated lamellae or segments are fixed in their movement by the stop means. The chuck itself is In its position to the tension shaft axis by the stop means absolutely fixed., Also within the chuck means a possible relative movement of slats relative to the Pressure elements or against the stop means, in particular one or a number of tie rods, during a rotary or other operation of the tensioning shaft practically locked out. Such a movement essentially only takes place during clamping and unclamping of the peripheral part, z. B. a sleeve instead.

In the following, preferred embodiments of the invention in comparison with the state described the technique. It should be noted that many modifications and Changes regarding form and detail of an embodiment can be made, without deviating from the general idea of the invention. The in the above description, in the drawing and in the claims disclosed features of the invention can be used both individually and in any combination for the realization of the invention be essential. The general idea of the invention is not limited to the exact one Shape or detail of the preferred embodiments shown and described below or limited to an object that would be restricted compared to the claimed in the claims subject.

Fig. 1:

eine Spannwelle gemäß dem Stand der Technik mit einer darauf befindlichen Hülse ohne die Beanspruchung durch eine externe Kraft;

Fig. 2:

eine Spannwelle gemäß dem Stand der Technik mit darauf befindlicher Hülse unter Beanspruchung einer, beispielsweise durch einen Presseur hervorgerufenen, externen Kraft;

Fig. 3:

einen Querschnitt einer Spannwelle gemäß einer bevorzugten Ausführungsform mit einer darauf befindlichen Hülse ohne und unter Beanspruchung einer externen Kraft;

Fig. 4:

einen Längsschnitt einer Spannwelle gemäß einer bevorzugten Ausführungsform ohne eine Hülse;

Fig. 5:

ein Detail X eines Längsschnitts der Spannwelle gemäß einer bevorzugten Ausführungsform der Figur 4.

Embodiments and embodiments of the invention will be described with reference to the drawing. This is not necessarily to scale the embodiments; Rather, the drawing, where appropriate for explanation, executed in a schematized and / or slightly distorted form. With regard to additions to the teachings directly recognizable from the drawing reference is made to the relevant prior art. In detail, the figures of the drawing show in:

Fig. 1:

a tensioning shaft according to the prior art with a sleeve thereon without the stress of an external force;

Fig. 2:

a tensioning shaft according to the prior art with sleeve thereon under stress of an external force, for example caused by a pressure roller;

3:

a cross section of a tensioning shaft according to a preferred embodiment with a sleeve thereon without and under application of an external force;

4:

a longitudinal section of a tensioning shaft according to a preferred embodiment without a sleeve;

Fig. 5:

a detail X of a longitudinal section of the tensioning shaft according to a preferred embodiment of Figure 4.

For a detailed explanation of the operation and the advantages of the invention, this based on a preferred embodiment in comparison to the prior art for different Situations presented. For this purpose, a tensioning shaft with a located on it Sleeve and its behavior without and under stress of an external, for example by described a force of expression, described force. When looking at simplicity considered only one load level, but what the essential principle of action of Invention makes clear. The principle lets and relies on a variety of load levels transfer.

First, the case of a clamping shaft with clamped sleeve according to the prior Technology described without the action of external forces.

For this purpose, in Figure 1, a corresponding clamping shaft 1 according to the prior art with a on this sleeve 2 and occurring forces F1 and F2 shown. About pneumatic expandable chambers 3a, 3b and 4a, 4b, the frictional engagement between the clamping shaft. 1 and sleeve 2 produced. The forces F1 and F2, the case of the expandable chambers 3a and 3b are the same size and opposite in both chambers.

The same applies in the vertical plane of the brackets 4a and 4b. The force pair F1 and F2 in the horizontal plane is illustrated as follows:

The pneumatic chambers thus press on the sleeve and the forces F1 and F2 in the considered horizontal plane are the same size. The position of the sleeve with respect to the central axis M1 of the tensioning shaft 1 is therefore indifferent. It turns a middle gap X1 one. About the pneumatic chambers 3a and 3b always acts the same force, almost independently of which extent the pneumatic chambers 3a and 3b have. The same applies for the chambers 4a and 4b.

Under the influence of external forces, as is usually the case with systems from the tensioning shaft and sleeve is the case, leads the indifferent position of the sleeve with respect to the central axis M1 to an unfavorable situation.

In Figure 2 is a schematic of the load of the system with an externally acting force F5, the on the system of clamping shaft 5 and sleeve 6 acts shown. This force can, for example be imprinted by a-Presseur P. As the forces F3 and F4 of the pneumatic Chambers 7a and 7b are equal and opposite, causes the external force F5 a movement of the sleeve 6 in the direction of the force F5. An analog effect would to adjust in the vertical plane of the chambers 8a and 8b. In this example will be the chambers 8a and 8b deformed. The named movement only comes to a standstill when the sleeve 6 touches the tensioning shaft in the area of the chamber 7b. The sleeve 6 moves So during a rotational movement and under the influence of an external force F5 constantly in the direction of the force F5 to the clamping shaft 5, so that the sleeve 6 almost never centric to Center axis M1 and the clamping shaft 5 is positioned. The extent of the movement is here depending on the existing without load average gap X1, as shown in Figure 1. In Figure 2 it can be seen that under load of the external force F5, the gap X2 on the Side of the force F5 is less than X1 and the gap X3 on the opposite side of Force F5 is greater than X1.

Bei einer noch so geringen externen Kraft F5 geht die Hülse 6 also in einen dynamischen Zustand über. Die Beschleunigung der Hülse mittels m a endet erst, wenn Sie mit dem Kern der Spannwelle 5 in Berührung kommt. Die Kräfte F4 und F3 sind gleich groß und entgegengerichtet und vermögen nicht, die Hülse 6 auf der Spannwelle 5 gemäß dem Stand der Technik zu zentrieren.The clamped sleeve 6 is thus accelerated by means of ma under the action of an external force F5, where m is the mass of the sleeve and a is the acceleration. This leads in particular to an imbalance in the system of tensioning shaft and sleeve.

With even the slightest external force F5, the sleeve 6 thus changes into a dynamic state. The acceleration of the sleeve by means of ma ends only when it comes into contact with the core of the tensioning shaft 5. The forces F4 and F3 are equal and opposite and are not able to center the sleeve 6 on the tensioning shaft 5 according to the prior art.

FIG. 3 schematically shows a preferred embodiment of the invention. there a tensioning shaft 9 has a plurality of shell-shaped segments 10, 11, 12, 13 and 14. These Segments can be fluid-driven, in particular pneumatic or hydraulic Chambers 15, 16, 17, 18 and 19 are moved radially away from the core of the clamping shaft 9. The radial movement of the segments is limited by tie rods 20, 21, 22, 23 and 24. It could be used instead of the segments and lamellae. A lamella would have in the circumferential direction a smaller extension than a segment. The number of chambers, slats or segments can be varied individually or together as needed. In the preferred embodiment, each five chambers and segments are advantageous.

On the segments, or optionally lamellae, the tension shaft is an expansion layer, So an elastic coating 25. In the assembled state of the clamping shaft 9 with Sleeve 26 and expanded chambers 15, 16, 17, 18, and 19 become the elastic coating 25 compressed on the segments 10, 11, 12, 13 and 14. The thus elastic surface 25th the segments 10, 11, 12, 13 and 14 also advantageously ensures that manufacturing tolerances as roundness and straightness, especially in the parts tensioning shaft 9 and sleeve 26 balanced can be.

Above all, due to the limitation of the radial movement of the segments 10, 11, 12, 13 and 14 defines the position thereof with respect to the center axis M2. This leads to a defined position of the sleeve 26 with respect to the center axis M2 and with respect to the clamping shaft 9. A gap occurs advantageous practically not on

In the preferred embodiment of the tensioning shaft 9, a situation without external forces is different than in the prior art and can be illustrated as follows.

The pneumatic chambers 15, 16, 17, 18 and 19 press on the segments 10, 11, 12, 13 and 14, so that in a clearly defined on the tie rods 20, 21, 22, 23 and 24 position method. The friction is not direct, but under the action of the chambers on the Segments and the elastic coating 25 to the sleeve 26 made. Part of the forces F7 and F8, provided under the action and by the pneumatic chambers is going into the compression F9 and F12 of the elastic coating of the segments, and another part F10 and F 11 goes into the tie rods. The tie rods form a stop the height h for the segments. F9 and F12 are thus frozen in the coating.

With no or small external forces, the compressed elastic coating is always endeavor to have the same tension in each finite part of the circumference of the tensioning shaft 9. The result is that the stresses and forces are balanced. Thus, the rest position the sleeve 26 with respect to the center position M2 of the clamping shaft 9 clearly defined and not indifferent, but in any case much more precise than in the prior art.

In the preferred embodiment, an externally acting force F6, as indicated in Figure 3, a particularly favorable situation. The forces acting on them can be represented as follows:

In the case that the external force F6 is greater than the frozen at rest Force F9 and F12 in the elastic coating, this leads to the external force F6 opposite side of the sleeve 26 to the following facts:

The total resulting force F13 of the pneumatic chambers is inserted into the tie rods of the corresponding, here left, page, as introduced in the above diagram. The drag F14 is provided by the named tie rods of the corresponding side. On the sleeve No force acts on the elastic coating in the direction of the external force F6, since cancel the forces F13 and F14.

On the side facing the external force, here on the right, as in the diagram above, the unloaded state force F12 increases to F17. This is about the elastic coating, caused by the resulting force F15 of the pneumatic Chambers against the external force F6, transferred to the sleeve. Take the tie rods on this side correspondingly less force F16 on F16 is thus smaller than the force F14, which pick up the tie rods on the opposite side.

Even in case of stress, the difference to the prior art becomes clear. The first existing force F12 of the elastic coating, in the same direction of the external Force F6 acts on the sleeve, it decreases with increasing external force F6, until it finally reaches the value zero.

The pneumatic chambers acting in the same direction of the external force would be in the State of the art, however, always press with the same force, which in its sum always the Value zero forms. In the prior art, these thus do not act in the direction of movement the external force. In the prior art, the pneumatic provided there serve Clamping elements not for centering a sleeve on a shaft, but they provide only for the transmission of circumferential forces, radial and axial forces acting on the Sleeve act.

In the proposed tensioning shaft 9 and the system of tensioning shaft 9 and sleeve 26th takes the force exerted by the sleeve 26 on the external force and the force which pushes the sleeve 26 in the direction of the external force decreases. At the preferred Embodiment is thus counteracted a movement of the sleeve 26 in the direction of the external force.

In the preferred embodiment, movement of the sleeve relative to the central axis the tension wave only within a drastically reduced range of motion allowed.

In the prior art, therefore, only the force of the external force counteracts in the load case, which results from the mass of the sleeve and its acceleration towards the tensioning shaft. In the invention counteracts the external force and a progressively increasing force, the based on the mass and the acceleration of the sleeve.

The preferred embodiment also advantageously allows a plurality of different Adjustments of the shaft with regard to its dynamic behavior. So can For example, the frozen tension stored at rest in the elastic layer is to be set. The adjustment can advantageously be made via a compressibility or E-modulus or depressions of the elastic coating 25 happen. There is one Transition from modulus of elasticity into the K-modulus range even with small usual forces especially advantageous. The adjustment can also be made via compression, i. H. the dimension the inner diameter of the sleeve to the outer dimension of the expanded core without sleeve done. Similarly, the force at rest between the tie rods and the elastic Layer is divided, so for example, the ratio of F12 to F11, set become.

Further adjustment possibilities arise over the height h of the tie rods, the training the tie rods, the segments and the chambers.

In the figure 4 is an axial section through a clamping shaft 9 of a preferred embodiment shown as a cross section in Figure 3 is shown. Each tie rod shown in Figure 3 20, 21, 22, 23 or 24 can be repeatedly arranged longitudinally along the tensioning shaft to to form a series of tie rods 30 shown in FIG. The tie rods 30 are height adjustable embedded in the tensioning shaft 9. For example, they were easiest to settle realize with angled head bolts. Further details about the tie rod 30 of an additional elastic layer or stretch layer 25 and lamellae or segments 10, 11, 12, 13 and FIG. 14 can be found in detail X, which is shown in greater detail in FIG.

FIG. 5 shows the tensioning shaft 9, which has a core 9a. The core 9a is conically tapered towards its end 9b for clamping in a rotary printing machine. The swivel head 30, which is rotatably inserted in the tensioning shaft 9, forms a stop for one of the lamellae 10, 11, 12, 13 and 14, which in FIG is provided. Instead of the oblique head screw could also any other screw be used. The head of the screw could also be designed differently. In the present Embodiment, a dovetail fit on the head to the blade is preferred. However, any other fold or fit could be used. Especially The head of the screw does not need to be covered by the lamella as in this one Embodiment. The head could also stay free. This would have the advantage that the Slat should not be postponed on the anchor head, but the anchor simply could be screwed.

Finally, any other fastener may be used instead of or in addition to a screw serve as anchors. For example, dowels could be beneficial.

A circumferential, in this case, fully circumferential, on the tensioning shaft 9 attached stretch 32 is in this embodiment of a support of the stretch 32b and the Stretching layer 32a itself formed. This allows advantageous setting options of Stretching itself, especially in terms of their stability and in terms of dynamic Behavior of the tensioning shaft 9. The assembly of stretch layer 32, lamella or segment 31 and clamping shaft 9 is advantageously carried out via a shaped piece 33, which on a Edge of the clamping shaft 9 is seated and holds the said parts in a form-fitting manner. An attachment of the molding 33 on the clamping shaft 9 via a screw 34th

Those disclosed in the foregoing description, in the drawings and in the claims Features of the invention may be used individually as well as in any combination be essential for the realization of the invention.

Claims (14)

Clamping shaft (9) for clamping an initially movable peripheral part (26), with a clamping means (15, 16, 17, 18, 19) for fastening the peripheral part (26), which is exciting if necessary, characterized in that in addition a stop means (20, 21 , 22, 23, 24) adapted to exert forces (F1, F2, F3, F4, F7) exerted by the chucking means (15, 16, 17, 18, 19, 10, 11, 12, 13, 14) , F8, F13, F15) and / or forces exerted by the peripheral part (26) (F5, F6). Clamping shaft (9) according to claim 1, characterized in that the peripheral part (26) is a sleeve (26). Clamping shaft (9) according to one of claims 1 or 2, characterized in that the clamping means comprises a fluid-driven clamping means (15, 16, 17, 18, 19). Clamping shaft (9) according to claim 3, characterized in that the clamping means by pneumatic and / or hydraulic elements (15, 16, 17, 18, 19) actuated lamellae (10, 11, 12, 13, 14). Clamping shaft (9) according to claim 4, characterized in that the lamella (10, 11, 12, 13, 14) is formed a circumferentially to the body of the clamping shaft (9) arranged segment. Clamping shaft (9) according to one of claims 1 to 5, characterized in that the stop means (20, 21, 22, 23, 24) for force limitation is fixedly connected to the body of the tensioning shaft (9). Clamping shaft (9) according to one of claims 1 to 6, characterized in that the stop means (20, 21, 22, 23, 24) has a stop for the clamping means (10, 11, 12, 13, A tensioning shaft (9) according to any one of claims 1 to 7, characterized in that the abutment means (10, 11, 12, 13, 14) extend completely or partially around the body of the tensioning shaft (9) and at at least one circumferential location by the abutment means (20, 21, 22, 23, 24) is durable. Clamping shaft (9) according to one of claims 1 to 8, characterized in that the stop means comprises a tie rod (20, 21, 22, 23, 24), which a stop for one of a pneumatic or hydraulic element (15, 16, 17 , 18, 19) forms an actuated segment or lamella (10, 11, 12, 13, 14) of a chuck. Clamping shaft (9) according to one of claims 1 to 9, characterized by an outer circumferential expansion layer (25). System comprising a tensioning shaft (9) according to Claim 1 and a sleeve (26) arranged on the outside, characterized by an expansion layer (25) located therebetween. Rotary printing machine with a system according to claim 11. Method for the dynamic stabilization of a tensioning shaft (9), in which an initially movable part (26, 15, 16, 17, 18, 19, 10, 11, 12, 13, 14) is fastened to the tensioning shaft when required, characterized that the forces exerted by the part (26, 15, 16, 17, 18, 19, 10, 11, 12, 13, 14) are limited by an additional stop means (20, 21, 22, 23, 24). A method according to claim 13, characterized in that an initially movable peripheral part (26) is fastened as required by an initially movable Aufspannmittel (15, 16, 17, 18, 19, 10, 11, 12, 13, 14) exciting and the of the forces exerted on the clamping means (15, 16, 17, 18, 19, 10, 11, 12, 13, 14) and / or the forces exerted by the peripheral part (26) via the additional stop means (20, 21, 22, 23, 24).

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