EP1316524B1 - Winding shaft with friction coupling - Google Patents

Abstract

Friction winding shaft comprises a number of rings (12) arranged next to each other and placed on a central drive shaft (8). The rings each have an outer surface (23) with clamping bodies (25) distributed on the periphery of the ring. The clamping bodies are received in recesses (29) of the rings and pivot about axes parallel to the friction winding shaft axis. The recesses interact with stopping surface (30, 31) which limit the pivoting movement. The stopping surfaces are dimensioned and arranged so that the clamping bodies determine a circular line (42) with their tips (27). <??>Preferred Features: During winding, each clamping body is supported by a cylindrical base body on the base of the recess. Each recess for receiving a clamping body is formed in an axis symmetrical manner to a symmetrical axis formed by a radial projection of the ring.

Description

The invention relates to a friction winding shaft, in particular for slitter-winder and winding machines, for the frictional reception of tubular winding cores for aufwickelnde strip-shaped belts with the other features according to the preamble of claim 1.

A preferred but not exclusive field of application of these winding shafts is thus the winding of strip-like bands or films, such as adhesive strips, which are divided by the production width into narrow strips and assembled on sleeve-shaped hubs. Here, several hubs are pushed side by side on a shaft and rotated in the winding. The torque transmission to the individual winding core takes place by frictional engagement, so that in the case of a blockage only the individual winding core is held. At the same time a specific same winding tension is achieved for each sleeve. The reproducible winding tension increases the quality and accuracy of the winding.

So so roll cutting and winding machines are known (DE 28 56 066 A1), in which for the winding of the strip-shaped bands two spaced Friktionswickelwellen are provided, each second strip-shaped band on the one Friktionswickelwelle and the each intermediate strip-shaped bands are wound on the other Friktionswickelwelle.

For rotational drive of the winding cores a plurality of rings is provided, which are tightly but tightly against each other rotatably mounted on a drive shaft. The rings have in the outer circumferential surface longitudinal slots in which leaf springs are used .The leaf springs are slightly inclined to the radial in the drive direction and lie with their free ends with bias against the inner surface of the hubs on.

Another, from the conceptual design comparable comparable, in the structural design, however, modified Friktionswickelwelle has become known from DE 42 44 218 C1. There winding core holders are used in the form of spring-loaded rotary parts as a clamping body with respect to a retaining ring outer surface projecting abutment edges. The roof-shaped abutment edges are slightly inclined to the radial aligned in the drive direction and apply according to the spring tension on the inner core hub. Another friction winding shaft is disclosed in WO005694.

The procedure at the beginning of a winding process as well as its termination is the same in both arrangements described above. First, the hubs are attached to the rings, wherein the hubs are pushed in the direction of the present inclination of the leaf springs or with simultaneous pivoting of the clamping body relative to the radial. Thereafter, the wound tapes are attached to the hubs and started the friction winding shaft. If the hubs are to be removed with the wound tapes, the bands are separated, so that the tape tension is eliminated. To remove the hubs from the Friktionswickelwelle they are rotated relative to the now stationary rings in the prevailing drive direction. This is possible because this rotation is in the direction of the inclination of the hub supports (spring-loaded clamp body or leaf springs) takes place. By rotating in this direction and moving sideways, the hubs with the wound-up belts can be removed from the friction winding shaft and new hubs can be placed accordingly.

The structural design of the Friktionswickelwelle, in particular as regards the arrangement of the attached hub supports, so by the intended operation of the slitter and winder, in particular by the respective given shaft rotation, predetermined. The same applies, and this should be mentioned for the sake of completeness, in structurally constructed otherwise Friktionswickelwellen, as shown for example in US Patent 4,693,431, where serve as a clamping body in inclined to the lateral surface extending channels moving ball elements.

Therefore, even when ordering and upgrading the friction winding shaft, that is, when equipping with the rings provided with clamping bodies, the later direction of rotation in production operation must be taken into account. It is important to ensure a uniform and correct insertion of the rings, so that a rotationally fixed coupling of the deferred hubs can be guaranteed. A prepared in so far Friktionswickelwelle would not be applicable to a slitter and winder with opposite direction of rotation, because then the hubs would slip through. For use with such an opposite direction of rotation, the rings would have to be removed from the drive shaft, turned over and replaced, which means a considerable effort.

The object of the invention is therefore to further develop a generic friction winding shaft in such a way that it is extremely flexible in terms of its application possibilities and nevertheless allows continued easy handling, in particular with regard to the attachment of the winding cores.

This object is achieved by the features of claim 1.

Accordingly, in the clamping body receiving recesses of the rings on both sides abutment surfaces are so dimensioned and aligned that define their pivot end positions located clamping body of each ring with their tips define a circle whose diameter is smaller or at most equal to the inner diameter d _w , while for a circle defined by the clamping body points located in their dead center positions, the resulting diameter d _{t is} greater than the inner diameter d _{w of} the winding core.

With this embodiment of a friction winding shaft according to the invention, the particular advantage is associated that it allows trouble-free assembly with winding cores in both directions of rotation and under load, d. H. ensures a rotationally fixed coupling of the winding core on the friction winding shaft during the winding process in the corresponding direction of rotation. Thus, only one for both directions of rotation either immediately usable Friktionswickelwellen-execution is required, which advantageously reduces the production costs and in particular the logistics costs for orders, shipping, storage and use.

Since now, unlike the generic state of the art, each clamping body is not supported on a lateral contact surface of an annular recess, but with its cylindrical base body at the bottom of the recess, it is advantageous according to a development of the invention according to claim 2, when the terminal body tip with a the rotational direction D ₁ or D _{2 of} the drive shaft opposite circumferential _core force F _u1 or F _{u2 includes} an acute angle δ, so that the clamping body is close to its pivot end position and its tip can interlock correspondingly intense with the winding _{core inner surface} .

In an advantageous development according to claim 3, each recess in a ring for receiving a clamping body is axially symmetrical to an axis of symmetry formed by a radial beam, the dead center position of each clamping body is aligned with the radial beam. This is advantageous insofar as with respect to the two possible directions of rotation of the Friktionswickelwelle same conditions with respect to ease of placement with winding cores or with respect to reliable driving connection under load are found.

In order to ensure this radial-symmetrical arrangement or dead center position of each clamp body is proposed according to claim 4, that a notch in the clamp body for receiving a spring load ensuring spring wire is aligned orthogonal to the symmetry axis formed by the radial beam.

Clamping body with stepped tip and a tip angle α of 50 ° to 60 °, preferably 54 °, as well as with two-sided chamfers of about 45 ° (inclination angle γ) ensure both an optimal rotationally fixed coupling or driving connection as well as a simple placement of the hubs. This is claimed in claim 5.

To induce an optimal positive connection between the inner winding surface and stepped terminal tip is in conjunction with the tip angle α, as indicated in claim 5 correspondingly proposed according to claim 6, an opening angle β of the annular recesses of about 30 °.

Reference to a drawing, the invention is explained in detail below.

Fig. 1

eine perspektivische Ansicht einer Rollenschneid- und Wickelmaschine,

Fig. 2

eine Friktionswickelwelle in einer Seitenansicht, teilweise abgebrochen,

Fig. 3

einen im Maßstab vergrößerten Schnitt durch die Friktionswickelwelle entlang der Linie III - III aus Fig.2 mit in Ausnehmungen eingesetzten Klemmkörpern,

Fig. 4

eine im Maßstab nochmals vergrößerte, abschnittsweise Darstellung einer Friktionswickelwelle mit Klemmkörper, und

Fig. 5

eine Einzelteildarstellung eines Klemmkörpers in einer Seitenansicht.

Show it:

Fig. 1

a perspective view of a slitter and winding machine,

Fig. 2

a Friktionswickelwelle in a side view, partially canceled,

Fig. 3

a scale enlarged section through the Friktionswickelwelle along the line III - III of Figure 2 with inserted in recesses clamping bodies,

Fig. 4

a scale enlarged again in sections, a representation of a Friktionswickelwelle with clamping body, and

Fig. 5

an itemized view of a clamp body in a side view.

In Fig. 1, a roll cutting and winding machine 1 is shown in which withdrawn from a supply roll 2, a material web 3 and divided by adjacent cutting blade 4 in a number of strip-shaped bands 5. These are wound on Friction winding shafts 6, 7 wherein one band is wound on the one Friktionswickelwelle 6 and the adjacent belt on the other Friction winding shaft 7.

From a side view of one of the construction of identical friction Friktionswickelwellen 6, 7 of FIG. 2 and additionally from Fig. 3 it can be seen that these each consist of a central drive shaft 8 with three offset circumferentially arranged longitudinal grooves 9, in each of which a Outside facing pressure bar 10 and a Blähschlauch 11 used are. Of course, alternatively, more than three longitudinal grooves may be provided, each with contained pressure bar 10 and inflation tube 11.

On the drive shaft 8 rings 12 are plugged, the structure of which is shown in detail in Figs. 3 and 4 in more detail. Thin washers 13, preferably corresponding to the outer diameter of the rings 12, are inserted between them. The rings 12 are on the shims 13 against each other tight and rotatable and are held together by laterally screwed on threaded portions 15 clamping discs 14 in the axial direction.

On the rings 12 tubular winding cores 16 are attached, which are held with the aid of resiliently Vorspannung Wickelkernhalterungen17. The rings 12 are so narrow that a winding core 16 usually covers several of them. By means of front-side pin 18, each friction winding shaft 6, 7 is received in lateral cheeks 19 of the roll cutting and winding machine 1. Here, also via not shown drive elements of the drive (arrow 20) of the friction winding shafts 6, 7th

When winding the strip-shaped bands 5 are formed by deviations in the thickness of the material web 3 different Aufwickeldurchmesser, so that the wound on the friction winding shaft 6.7 winding cores 16 can not be driven at the same speed. Therefore, the drive shaft 8 is driven at a slightly higher speed than is necessary for winding the strip-shaped bands 5 per se. The attached to the drive shaft 8 rings 12 are driven by frictional engagement between the ring inner surfaces and the friction surfaces on the pressure bars 10, but they slip something to compensate for the difference between the input speed and Aufwickeldrehzahl on the drive shaft 8 something. The size of the frictional engagement is adjustable by pressure change in the inflatable tubes 11, which act on the pressure bars 10.

As is further apparent from FIGS. 3 and 4, each ring 12 is divided into two concentrically arranged ring elements, namely an inner friction ring 21, preferably made of metal, and an outer retaining ring 22, preferably made of a plastic material, divided. Between both, no relative movement is possible. While at the Friktionsring- inner surface of the pressure bars 10 abuts the retaining ring 22 distributed over its circumference, the hub supports 17. In the exemplary embodiment, five winding core holders 17 (distributed at a distance of 72 ° over the circumference) are provided.

On the retaining ring 22 of the sleeve-shaped core 16 is attached, which usually consists of paper (cardboard) or plastic and in its inner diameter d _{w is} slightly larger than the outer diameter d _{a of} the retaining ring 22. This results between the retaining ring outer surface 23 and winding core Inner surface 24 a slight distance.

Each winding core holder 17 consists of a spring-loaded rotary member in the form of a clamping body 25, which in turn has a cylindrical base body 26 and an adjoining sprag tip 27. A point angle α of 50 ° to 60 °, in the exemplary embodiment preferably 54 °, has proven to be particularly favorable. The cylindrical base body 26 is supported in each case on a likewise cylindrical base 28 of a recess 29 incorporated in the retaining ring outer surface 23, which opens in a funnel shape and thereby left and right abutment surfaces 30, 31 has, to which the edges of the terminal body tip 27 during pivoting ( Pivot axis 32) come to rest. With regard to the tip angle α of 54 °, it has proven to be particularly advantageous for the mode of operation of the invention if an opening angle β of the recess 29 of approximately 30 ° (see Fig. 3) is provided.

Each clamping body 25 is, and this is apparent in particular from FIG. 5, provided in the region of the terminal body tip 27 with two-sided run-on slopes 33, which preferably have a slope (inclination angle γ) of 45 °. The clamping body 25 is also equipped with a notch 34, which serves to receive a spring wire 35 to hold the clamping body 25 in a desired starting position, its dead center position.

The notch 34 is oriented orthogonal to an axis of symmetry formed by a radial beam 36, starting from the friction winding shaft axis 37. This results in a radial beam symmetrical arrangement or dead center position of each clamp body 25. This ensures the spring wire 35 is placed on the one hand in the notch 34 and on the other in a recess 38 of the retaining ring 22, where it can support each end.

All located in their dead center clamping body 25 define with their respective sprag tip 27 a circle 41, which has a diameter d _t . A circle line 42 resulting from the terminal body tips 27 of the clamping bodies 25 pivoted in their end positions upon contacting the stop surfaces 30, 31 has a diameter d _e which is slightly smaller than or equal to the inner diameter d _{w of} the winding core.

Since each clamping body 25 is supported with its cylindrical base body 26 on the likewise cylindrical base 28 of the recess 29, it is advantageous for a secure hooking of the sprag tip 27 with the winding core inner surface 24, when the clamping body 25 under load, ie during the winding, relative strongly inclined to the radial beam 36, that is near its pivoting end position. Advantageously, the terminal body tip closes with one of the rotational direction D ₁ or D _{2 of} the drive shaft opposite circumferential _core force F _u1 or F _u2 an acute angle δ a.

The arrangement shown has the following function.

At the beginning of a winding process, the hubs 16 are attached to the rings 12, wherein they are pushed in accordance with the winding direction or drive shaft rotational direction D ₁ or D ₂ with a clockwise or counterclockwise rotation. As a result, the clamping body 25 relative to the radial beam 36 (symmetry axis) is pivoted accordingly, whereby the sliding of the hubs 16 is only possible. Thereafter, the coils to be wound 5 are attached to the winding cores 16 and started the drive shaft. Due to the frictional connection via inflatable tubes 11 and pressure strips 10, this drive is transmitted via the friction ring 21 to the retaining ring 22. The correspondingly loaded by the attached band 5 winding core 16 exerts a counteracting force F _u1 or Fu ₂ , so that the winding _{core inner surface 24 securely hooked with the sprag tip} 27 of the corresponding close to its end position pivoted clamp body 25 and thus a reliable driving connection is made , In a counter-directional drive of the drive shaft 8 results in a correspondingly opposite situation with respect to pivot end position of the clamping body 25 or relative to the winding core 16 exerted counter-directed force F _u1 and F _u2 .

Claims (6)

1. Winding shaft with friction coupling (6, 7), in particular for a reel-cutting and wind-up machine (1), for the frictional receiving of sleeve-shaped winding cores (16) for strip-form bands (5) or the like which are to be wound up, with a multiplicity of rings (12) which are placed onto a central drive shaft (8), are situated next to one another and have winding-core mounts, which protrude resiliently in each case over the ring outer surface (23), are distributed on the circumference of the ring, are designed as clamping bodies (25) and are intended for the releasable securing and rotationally fixed coupling of the winding cores (16) via clamping-body tips (27) making contact with the winding-core inner surface (24), the clamping bodies (25) being received in recesses (29) of the rings (12) in a manner such that they can be pivoted about axes (32) parallel to the axis (37) of the winding shaft with friction coupling, and the recesses (29) having stop surfaces (30, 31) on both sides, limiting the pivoting movement, characterized in that the two stop surfaces (30, 31) are dimensioned and arranged in such a manner that the clamping bodies (25) in their pivoting end positions define, by means of their clamping-body tips (27), a circular line (42), for the diameter d_e of which the following applies: $${\mathrm{d}}_{\mathrm{e}}\le {\mathrm{d}}_{\mathrm{w}},$$

   

   
   where d_w is the winding-core inside diameter, while the clamping-body tips (27) in their dead centre positions situated between the end positions on radial lines (36) of the ring (12) define a circular line (41), for the diameter d_t of which the following relationship applies: $${\mathrm{d}}_{\mathrm{t}}>{\mathrm{d}}_{\mathrm{w}}.$$

   
2. Winding shaft with friction coupling according to Claim 1, characterized in that, during the winding-up operation, each clamping body (25) is supported by a cylindrical base body (26) on the base (28) of the recess (29) and the clamping-body tip (27) encloses an acute angle δ with a winding-core circumferential force F_u1, F_u2 opposed to the direction of rotation D₁, D₂ of the drive shaft (8).
3. Winding shaft with friction coupling according to Claim 1, characterized in that each recess (29) for receiving a clamping body (25) is axially symmetrical to an axis of symmetry formed by a radial line (36) of the ring (12), the dead centre position of the clamping body (25) being aligned with the radial line (36).
4. Winding shaft with friction coupling according to Claim 3, characterized in that a notch (34) in the clamping body (25) for receiving a spring wire (35), which ensures the spring loading, is aligned orthogonally to the axis of symmetry formed by the radial line (36).
5. Winding shaft with friction coupling according to Claim 1, characterized in that the clamping-body tip (27) has a tip angle α of 50° to 60°, preferably 54°, and, in addition, is equipped with run-on slopes (33) on both sides which each have an angle of inclination γ of 45°.
6. Winding shaft with friction coupling according to Claim 5, characterized in that, corresponding to the geometry of the clamping-body tip (27), the recess (29) has a funnel-shaped opening with an opening angle β = 30°.

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