GB2300460A

GB2300460A - Friction coupled core support device

Info

Publication number: GB2300460A
Application number: GB9609149A
Authority: GB
Inventors: Juergen Muelling; Thomas Springer
Original assignee: Kampf GmbH and Co Maschinenfabrik
Current assignee: Kampf GmbH and Co Maschinenfabrik
Priority date: 1995-05-03
Filing date: 1996-05-01
Publication date: 1996-11-06
Anticipated expiration: 2016-05-01
Also published as: ES2132006B1; ITMI960775A0; IT1283755B1; ES2132006A1; ITMI960775A1; GB9609149D0; GB2300460B

Abstract

A frictional winding core locking device has relatively rotatable base ring (5) and pressure ring (9). The ring (5) is frictionally engaged through lubricated pads (3) and inflatable ducts (4) by drive shaft (1). The ring (9) supports a plurality of ball bearings (7) acted on by ramp surfaces (6) of ring (5). A reel core (not shown) may be axially loaded onto ring (9) with the balls (7) providing low friction to allow sliding movement of the core after which the balls lock the core to ring (9) on relative rotation of rings (5) and (9) causing ramps (6) to force the balls (7) outward against the core. The construction provides for the balls to project slightly beyond the surface of ring (9) even when fully unlocked. A modification provides for the locking to be effected by separate roller locking means, with the balls being held in a fixed position projecting above ring (9).

Description

TTTrE Friction Coupled Core Support Devlce This invention relates to a friction coupled core support device. Such devices are used in particular on roll cutting and winding machines which have a central driving shaft, on whose periphery there are distributed mutually spaced longitudinal grooves with slide strips which are mounted in a radially displaceable manner therein and are preferably controllable by varying the pressure in a respective inflatable expandable pressure medium duct. At least one annular base member is provided which bears on the driving shaft and on whose internal face the slide strips bear and on whose external face oblique ramp tracks are provided for cooperation with pressure elements which serve for the detachable fixing and the non-rotating connection of slide-on winding cores.The elements being held in a pressure ring rotatable relative to the base member.

In the friction winding device known from German Patent 42 44 218 there are provided winding hub mountings consisting of a spring-loaded rotating part as clamping member which bears on the internal face of the winding core under spring pressure with an angular edge which thus bridges a space between the external face of the pressure. ring and the internal face of the winding core which might exist owing to tolerances. For the rigid support of the winding core by bridging of the space there are provided winding hub supports which are peripherally distributed in the pressure ring and can be of various designs. In a first embodiment, therefore, a winding hub support of this type consists of a stud which is movably guided in a radial guide on the pressure ring.

At the internal end, the stud lies on a track designed as a ramp face. An alternative winding hub support consists of a pivoted supporting part rotatably mounted on the pressure ring.

When the winding cores are fitted onto the friction winding shaft, the winding cores have to be applied in a specific direction of rotation in order to pivot the angular edges of the winding hub mountings sufficiently far towards the external face of the pressure ring to allow the winding hubs to be pushed on for the first time. As the winding cores are being pushed on and also at the beginning of the rotating process, the stud and a guide member of the pivoting supporting member lie at the lowest point of the ramp face, so the stud and/or the pivoting supporting part do not project beyond the external face of the pressure ring so the application of the winding cores is not hindered.As relative pivoting of the base member and of the pressure ring continues, the stud and the pivoting supporting member are moved along the ramp face until these elements reach a position of contact against the internal face of the winding core.

The space is therefore rigidly bridged and centering and alignment of the winding hubs achieved.

As the base member bears directly on the driving shaft, rolling bearings which are otherwise required are not necessary, so relatively large rolls can be wound and comparatively narrow cutting widths achieved. However, the known friction winding shaft is quite complicated owing to the special design of the winding hub mountings and of the winding hub supports and is therefore costly as the clamping and pressure elements have to be specially produced in each case for the specific application. For the return of the winding hub supports into their retracted starting position for the removal and application of new winding cores, it is also necessary for the spring-loaded stud or the pivoting supporting part to slide back.During this recovery, however, the force can be so small, for example in the case of a small angle of inclination of the ramp guides, that obstructions can occur, making recovery difficult.

Back pivoting springs are required between the holding ring and the base member to prevent this.

An object of this invention is to provide a friction coupled core winding shaft which is suitable for winding relatively large wound rolls with a minimum cutting width, and which nevertheless has a smooth uniform winding action and allows easy application and removal of the winding cores on the winding shaft using particularly simple means.

According to this invention there is provided a friction coupled core supporting and winding device for roll cutting and winding machines having a central drive shaft around the periphery of which there are provided mutually spaced longitudinal grooves with slide strips which are radially displaceable preferably by varying the pressure in a respective expandable pressure medium duct, at least one annular base member located on the drive shaft and of which an internal face bears on the slide strips, an external face having ramp tracks cooperating with pressure locking elements which serve for the releasable locking of and non-rotatable coupling with slide on winding cores, the pressure elements being held in recesses in a pressure ring rotatable relative to the base member, wherein the pressure locking elements comprise rolling elements, such as balls, projecting slightly beyond the external face of the pressure ring even when the pressure elements are inoperative, said elements serving to guide the positioning of the winding cores onto the pressure ring.

With this arrangement the pressure elements have a dual role in that on the one hand they act as clamping elements for the winding core support for coupling to the friction winding shaft and on the other hand they act as ball bearing bushes when the friction winding shaft is applied to and removed from the core. The design of these elements as balls capable of universal movement in all directions enables the cores to be locked and winding cores to be moved easily when released. Furthermore, the balls are stock items and are thus an inexpensive means of locking and guiding the winding cores.

According to this invention there is also provided a friction coupled core supporting and winding device for roll cutting and winding machines having a central drive shaft around the periphery of which there are provided mutually spaced longitudinal grooves with slide strips which are radially displaceable preferably by varying the pressure in a respective expandable pressure medium duct, at least one annular base member located on the drive shaft and of which an internal face bears on the slide strips, an external face having ramp tracks cooperating with pressure locking elements which serve for the releasable locking of and non-rotatable coupling with slide on winding cotes, the pressure elements being held in recesses in a pressure ring rotatable relative to the base member, wherein rolling elements such as balls are provided projecting slightly beyond the external face of the pressure ring even when the pressure elements are inoperative, serving to guide the positioning of the cores onto the pressure ring.

In a further preferred embodiment comprising a modification, balls forming the elements which serve to guide the winding cores in longitudinal displacement and which project slightly beyond the external face of the pressure ring in the unlocked state of the means are provided in addition to the pressure elements serving for the locking and coupling of the winding cores. In this case, the balls serve only to provide low friction sliding of the winding tube cores into position. They therefore serve only as ball bearing guides and not essentially for locking the friction means to the core.

Locking in this event may be carried out by use of cylindrical rollers which, like the balls, are mounted in the pressure ring and are moved radially by the ramps.

The cylindrical rollers are thus forced outwardly by the ramps on the external face of the base member while the balls remain in a fixed position without change.

It has been found that it is quite sufficient if the balls project some 0.1 to 0.2 mm beyond the external face of the pressure ring in the unlocked state. During application of the winding cores, only the balls are contacted so application and removal is not accompanied by difficulties due to the unloaded state.

In a preferred embodiment in which balls are used as pressure elements, it has proved advantageous if recesses receiving the ends of an arcuate spring plate acting on the pressure elements are arranged at the ends viewed in the peripheral direction, of the ramp tracks in the base member acting on the pressure elements. This preferably curved or angular plate fulfils two functions; firstly the balls are always pressed outwardly by the plate, ensuring that the balls of any friction means bear against a winding core regardless of the tolerances, so all friction means in the region of a winding core are therefore invariably under pressure and therefore contribute to the driving of the winding core; and secondly, hardening of the ramp tracks can be omitted owing to the spring plate which is preferably of steel and hardened.Furthermore, the recesses at the ramp track ends prevent the spring plate from jamming between the base member and the pressure ring. The spring action of the plate is achieved because it is installed with a slight bias.

Smooth and uniform winding is also assisted if, according to a preferred feature, the slide strips are formed by an impregnated sliding bearing material which seeps a lubricant, for example oil, at least on the contact side facing the internal surface of the base member or, in an alternative design, by lubricated felt strips or if the slide strips are formed directly by flexible strips consisting of a grease impregnated material.

The oil emitted from the felt strips ensures that the mating sliding surfaces, steel shaft (driving shaft) and friction member (base member) are separated by a very thin oil film and seizure of the friction members is therefore avoided. A reliable, comparatively high loadable friction winding shaft is thus obtained. The lubricated felt strips also have the effect that the sliding movement is free from binding and erratic frictional effects and is therefore very smooth and uniform. This also has a positive influence on the winding process.

This invention is further described with reference to preferred embodiments shown in the drawings as examples only and described in more detail hereinafter.

In the drawings: Figure 1 shows a view of a ball friction means according to this invention, Figure 2 shows a section along line II-II of Figure 1, Figure 3 shows a view of a modified embodiment of the friction means, Figure 4 shows a section along line IV-IV of Figure 3, Figure 5 shows a further modified embodiment of the friction means, Figure 6 shows a section along line VI-VI of Figure 5, Figure 7 shows a section along line VII-VII of Figure 5, Figure 8 shows a friction means corresponding to that shown in Figure 1 with an additional pressure device.

Figure 9 shows a section along line IX-IX of Figure 8.

Figures 1 and 2 show a friction means for use on a roll cutting and winding machine not shown in detail.

The friction coupled winding shaft shown consists of a central driving shaft 1 with three peripherally distributed longitudinal grooves 2 each containing a respective slide strip 3 directed towards the exterior and a radially expandable inflatable pressure duct 4.

Around driving shaft 1 is an annular base ring member 5 with an internal face against which the slide strips 3 bear. The slide strips, which extend over the entire length or substantially over the entire length of the driving shaft, consist either of oil-impregnated felt strips or a grease impregnated bearing material. A number of peripherally distributed, obliquely extending ramp track surfaces 6 which cooperate with pressure elements 7 comprising balls are arranged around the exterior of the base member 5. The balls 7 are positioned in apertures 8 in a pressure ring 9 in such a way that they project about 0.1 to 0.2 mm beyond the external face of the ring 9 even in the unlocked state of the friction means. In Figure 1, a spacer ring 11 is shown as well as a securing ring 12. The spacer ring 11 consisting of a bearing material lies loosely between two adjacent friction means.

The arrangement illustrated operates as follows: Winding cores (not shown) are placed over the friction winding shaft at the beginning of a winding operation. As the balls 7 project somewhat beyond the exterior of the pressure ring 9, the winding cores can easily be pushed axially onto the friction winding shaft over the balls into the respective desired or required position. The inflatable ducts 4 have previously been expanded so frictional contact with the base member 5 is made via the slide strips 3 whereby the base member 5 accordingly rotates in a clockwise direction together with the rotational movement of the driving shaft 1.

The balls 7 are thus pressed further outwardly owing to the oblique progression of the tracks 6 so the winding cores are finally held firmly in the required position.

In the unlocked state of the friction means, the balls resume their original position in which they project only slightly beyond the external face of the pressure ring 9.

The removal of the final wound rolls can therefore also take place particularly easily.

In the embodiment according to Figures 3 and 4, the balls are arranged in two adjacent rows. Such means are particularly suitable for carrying heavy loads. An arrangement of at least two rows of balls is particularly advantageous with increasing tube diameters and thinner or narrower winding cores. Thus, with larger core diameters, for example, one row of balls can be peripherally offset from the other row of balls so that balls in one row are arranged, for example, at 150, 450 etc. and the balls of the other row at 300, 600, etc. A ball offset of this type produces more uniform pressure points, preventing undesirable distortion of the winding cores. It is quite conceivable with even greater tube diameters to provide four or even six rows of balls which are each offset from the respective adjacent row of balls in the above described manner.Regardless of whether there are two or six rows of balls and independently of the diameter of the driving shaft, the space between successive balls can advantageously be kept between at least 55 mm and at most 85 mm within one respective row of balls in the circumferential direction. If balls in a row of balls are inserted with smaller spacing than the above-mentioned minimum amount, the tracks or ramps operating them are too steep with the result that the clamping effect cannot be adjusted sufficiently sensitively. Conversely, if comparatively few balls are provided within one row of balls, i.e. the spaces exceed the maximum range, the tracks or ramps become too long and an acceptable clamping effect is no longer achieved.

In the modified embodiment shown in Figures 5 to 7, the balls 7 act not as pressure elements but merely as guide elements for the sliding movement of the winding cores. The winding cores are locked by further pressure elements 13 which are designed as cylindrical rollers in the embodiment illustrated. The cylindrical rollers 13 therefore cooperate with the obliquely arranged tracks 6, while the balls in their recessed 8 in the pressure ring 5 are held fixed in position.

Finally, Figures 8 and 9 show an additional pressure device for the balls 7 in a variation corresponding to Figures 1 and 2. As shown in particular in Figure 9, recesses 14 are arranged at the ends of the oblique tracks 6, as viewed in the circumferential direction, into which recesses 14 are inserted the ends of steel spring plates 15 which are kept under initial tension and which additionally loads the balls in an outward direction. By this means better contact between the balls and the winding cores is provided regardless of tolerances. Jamming of the spring plate between the base member and the pressure ring is prevented by the shape of the plate 15. In this case, the tracks 6 do not need to be hardened as the ball runs over the hardened plate in each case.

Claims

CLANS

1. Friction coupled core supporting and winding device for roll cutting and winding machines having a central drive shaft around the periphery of which there are provided mutually spaced longitudinal grooves with slide strips which are radially displaceable preferably by varying the pressure in a respective expandable pressure medium duct, at least one annular base member located on the drive shaft and of which an internal face bears on the slide strips, an external face having ramp tracks cooperating with pressure locking elements which serve for the releasable locking of and non-rotatablC coupling with slide on winding cores, the pressure elements being held in recesses in a pressure ring rotatable relative to the base member, wherein the pressure locking elements comprise rolling elements, such as balls, projecting slightly beyond the external face of the pressure ring even when the pressure elements are inoperative, said elements serving to guide the positioning of the winding cores onto the pressure ring.

2. A device according to Claim 1, wherein the rolling elements are balls arranged in a plurality of adjacent rows within the pressure ring.

3. Friction coupled core supporting and winding device for roll cutting and winding machines having a central drive shaft around the periphery of which there are provided mutually spaced longitudinal grooves with slide strips which are radially displaceable preferably by varying the pressure in a respective expandable pressure medium duct, at least one annular base member located on the drive shaft and of which an internal face bears on the slide strips, an external face having ramp tracks cooperating with pressure locking elements which serve for the releasable locking of and non-rotatable coupling with slide on winding cores, the pressure elements being held in recesses in a pressure ring rotatable relative to the base member, wherein rolling elements such as balls are provided projecting slightly beyond the external face of the pressure ring even when the pressure elements are inoperative, serving to guide the positioning of the cores onto the pressure ring.

4. A device according to Claim 3, wherein the pressure elements comprise cylindrical rollers.

5. A device according to any one of Claims 1 to 4, wherein the rolling elements or balls project some 0. 1 to 0.2 mm beyond the external face of the pressure ring in the unlocked state of the friction device.

6. A device according to any one of Claims 1 to 5, wherein recesses receive the ends of a curved spring plate acting on a pressure locking element, the recesses being arranged at each end of the ramp track.

7. A device according to Claim 6, wherein the tracks are unhardened.

8. A device according to any one of Claims 1 to 7, wherein the slide strips are formed by a bearing material which exudes a lubricant at least on the face contacting the internal face of the base member.

9. A device according to Claim 8, wherein the slide strips are formed by lubricated felt strips.

10. A device according to Claim 9, wherein the slide strips are formed by flexible strips consisting of a grease impregnated material.

11. A device according to any preceding claim limited by Claim 2, wherein the balls of one row are mutually peripherally offset from the balls of an adjacent other row or rows.

12. A device according to any one of Claims 1 to 11, wherein the spacing between successive balls in the circumferential direction within one respective row of balls is at least 55 mm and at most 85 mm.

13. A friction coupled core locking device as described herein and exemplified with reference to the drawings.