EP0216085A1 - Device for the coreless winding of web sections severed from a web along cross-perforations - Google Patents

Abstract

The device has two winding points arranged in a machine frame, which have rotatably mounted and provided with a rotary drive, freely projecting winding pins (23, 24) which can be extended into their winding position which is spread apart and retractable into their non-spread position and which have their spreading movements parallel to one another Execute levels and which are at least a distance apart from one another in the transverse direction of these levels, which is necessary for the trouble-free passage of the material web (46). During winding in one winding station, the web (46) is passed between the winding pins (23, 24) of the other winding stations. After the web has been switched over to the new winding station, the winding pins are moved out of their retracted position into their position enclosing the web between them.

Description

The invention relates to a device for coreless winding of a web of material fed continuously and spaced apart from one another with transverse perforations along a transverse perforation to supply rolls with two winding stations arranged in a machine frame, which are rotatably mounted and provided with a rotary drive, freely projecting into them relatively extendable winding position extendable and retractable in their unexpanded winding pins, wherein during the winding in one winding point the web is passed between the winding pins of the other winding point and the winding pins after Switching the web to the new winding point from its retracted position to the web between them to be extended position.

In a device of this type known from DE-AS 21 27 128, the winding pins which project freely over the width of the material web in the winding position are fastened to the free ends of levers which are pivotably mounted in a winding head and are, for example, springs in their inner, pushed-together position held and pivoted into their spread position by an axially displaceable mandrel with a conical end part which acts on corresponding guide surfaces of the levers.

This known device is structurally relatively complex because the cantilevered winding pins not only have to be extended and retracted essentially over the entire width of the web to be wound up, but because they have to be spread so far relative to each other when extending that the web runs smoothly between the Winding pins can be passed through to the other winding point.

The object of the invention is therefore to provide a device of the type specified at the outset with which the supply rolls can be wound with smaller axial displacement paths and radial spreading movements of the winding pins.

According to the invention, this object is achieved in that each winding point on each side of the web has two winding pins which are essentially aligned with one another and which perform their spreading movements relative to one another in planes parallel to one another and which have at least a distance in the transverse direction of these planes which is necessary for the trouble-free passage of the material web is.

Since winding stations or winding heads with winding pins are provided on both sides of the web, these need only execute short axial extension and retraction movements in order to securely grasp and release the web, because the winding axes guaranteeing good winding are already defined by the bilateral detection of only the edge regions of the web . Since the winding pins already have a sufficiently large transverse spacing relative to one another to ensure a trouble-free passage of the material web, they only have to make relatively small spreading movements after extending into their winding position, because there is sufficient loosening of the winding pins before pulling them out in the completely wound roll if these are returned to their unspread position. In the device according to the invention, the winding pins only need to perform a spreading movement which, after returning to their unspread position, is sufficient to loosen the winding pins in the finished roll winding and therefore only needs to be very small, while in the known device the winding pins travel over a larger radial distance, than would be required for loosening per se, must be spread in order to create such large distances between the winding pins that the web can run between them without interference.

From DE-GMS 77 12 942 winding heads with winding pins are known which, in their non-spread position relative to one another, are so far apart that the web can run between them. However, the winding pins must have such a large, freely projecting length that they extend beyond the winding web that they can be bent into their spread position by means of an expansion cone.

From US-PS 35 80 522 are in an intermittently working winding device with only one winding point, in which the web for separation from the wound web section on two Places must be clamped in order to separate them between the clamping points, extendable and retractable pairs of winding pins acting on both sides of the web, which are spread out in their extended position by a spreading wedge and spring back into their unexpanded position by pulling back the spreading wedge. In this known device, the pliers-like winding pins must be spaced so far apart that the web can be passed between them without interference, so that no corresponding measures are provided.

From CH-PS 487 791 a winding device with a frame-fixed winding point is known, which consist of two opposite pairs of winding pins provided with a rotary drive, which can be pushed towards each other to capture a material web to be wound in sections without a core, so that the two winding pins in each case move the web therebetween einfas _- sen, and are retractable to release a roll over the side edges of the web also. The known device is used for intermittent winding of web sections which are separated from an endless web, in which the winding pins, which are displaceable towards and away from one another in a common plane, perform a pincer-like opening movement for gripping the web and a corresponding closing movement when they are retracted , so that the frictional engagement of the winding pins with the winding is reduced and the winding formed can be easily stripped from it. The wrap still connected to the web then falls into a collecting trough. In order to separate the web from the winding, pairs of clamping jaws which clamp the web are provided on both sides of the winding point and a separating knife between them. Before cutting, the web clamped between the jaws is tightened by a tensioning device, so that the appropriately aligned and spread winding pins for grasping the web are stacked again can be advanced. The known winding device does not allow winding and separation of a continuously fed web. The web must not only be stopped to separate the respectively formed roll with a predetermined section length, it must also be clamped on both sides of the winding point by special clamping devices and cut through a special cutting device, which not only limits the winding performance, but also requires additional design effort.

In a further embodiment of the invention it is provided that the winding stations have support plates with bushings rotatably mounted in them and provided with the rotary drives, that the winding pins consist of angle levers which are pivotably mounted on a common transverse axis of a support piece which is rotatable at the front end of a scissors is aligned with the central axis of the bushing aligned piston rod of a pressure-medium piston cylinder unit that is fixed to the frame, that the longer, the winding pins forming scissor-like legs of the bushing are guided in a longitudinally displaceable manner and acted upon by springs in the direction of their unexpanded position and that the shorter legs of the angle levers, which are angled approximately at right angles, open Support opposite sides of the outward-facing end faces of the bushings towards the end of the feed movement in such a way that their longer legs that pass through the bushings are spread apart.

In order to ensure that the winding pins are in a position when they are pushed forward from their retracted position, in which they are able to enclose the web running to the other winding point in a fork-like manner between them, in a further embodiment of the invention it is provided that the support piece has a radial arm is provided, which cooperates with a frame-mounted control cam when retracting the piston rod and thereby rotates the longer legs in such a way that their central planes lying between their pivoting planes lie in the plane of the path to be grasped by them when they extend.

The support piece is expediently provided with two radial arms offset from one another by 180 °, which cooperate with a control cam which is fixed to the frame and concentrically surrounds the piston rod and which, starting from an apex, has two symmetrical, approximately elliptically curved, outwardly extending branches.

According to an inventive development, the winding stations are arranged in a turret-like manner in the machine frame in that the two support plates are designed in the form of circular disks and at least one is provided with external teeth which mesh with a drive pinion, and in that the support plates are provided with the winding stations offset by 180 °. The winding stations can be changed by rotating the backing plates or turning them back and forth.

In a further embodiment of the invention, it is provided that a central shaft, which is provided with a rotary drive, is mounted in the support plates and is alternately in drive connection via clutch-brake combinations with two parallel intermediate shafts mounted in the support plates, one of which via gear wheels , Belts or chains the rotary drive of the bushings of the winding stations is derived.

In order to be able to adjust the winding device to different formats, the guide rings are guided on the trusses of the frame so as to be displaceable and, for opposite adjustment, are provided with spindle nuts into which a spindle fixed to the frame is screwed, the central shaft and the drive elements being rotatably mounted on the support plates Intermediate shafts, which are designed as multi-spline shafts, are guided so as to be axially displaceable.

• Fig. 1 eine Seitenansicht der Wickelvorrichtung,
• Fig. 2 eine Draufsicht auf die Wickelvorrichtung nach Fig. 1,
• Fig. 3 einen Schnitt durch einen Wickelkopf einer Wickelstelle in vergrößerter Darstellung und
• Fig. 4 einen Schnitt durch die Kolbenstange und das Tragstück längs der Linie IV - IV in Fig. 3.

An embodiment of the invention is explained below with reference to the drawing. In this shows

• 1 is a side view of the winding device,
• 2 is a plan view of the winding device of FIG. 1,
• Fig. 3 shows a section through a winding head of a winding station in an enlarged view and
• 4 shows a section through the piston rod and the support piece along the line IV-IV in FIG. 3.

The side walls 1, 2 of the machine frame are connected to one another by a cross-beam 3, which forms a guide for support rings 4, 5 which are mounted on the cross-slide. The support rings 4, 5 are additionally provided with spindle nuts 6, 7, into which the spindle 8 is screwed for opposing adjustment of the support rings 4, 5 with opposite threads. The spindle 8 is rotatably but axially immovably mounted in the frame walls 1, 2 and provided with a handwheel 9.

The support rings 4, 5 are provided with mutually aligned annular inner edges 10, 11, on which rollers 12 provided with circumferential grooves run, which are mounted on the outer sides of circular disks 13, 14, the outer edges of which are provided with teeth 15. The disc-shaped Plates 13 are offset by 180 ° with opposing end windings 16, 17 and 18, 19. The winding heads are of identical design, so that only the configuration of the winding head 16 is explained below with reference to FIG. 3.

The bearing ring 20 provided with a flange is held in a bore in the disk-shaped plate 13. In this bearing ring, the bushing 21 is rotatably supported by two roller bearings. The toothed belt pulley 22 is wedged onto the bushing 21 on the outside of the disk-shaped plate 13. The bushing 21 serves to guide the scissor-like winding pins 23, 24 arranged axially displaceably therein.

The winding pins 23, 24 are formed by the longer legs of angle levers, which are pivoted about the common axis 25 in a forked end piece 26 by small swivel angles. In the area of the bearing bores, shorter legs 27, 28 are connected to the legs forming the winding pins 23, 24, which carry rollers 29, 30 at the ends, by means of which they are supported on the outer side surface 31 of the toothed pulley 22.

The support piece 26 is rotatably supported by the roller bearing 33 in an axial bore 34 of the piston rod 35.

The associated pneumatic cylinders 36 are each firmly connected to the disk-shaped plates 13, 14 in a manner not shown. For this purpose, the pneumatic cylinders 36 have flange plates at their outer ends, which are connected to the disk-shaped plates 13, 14 by means of stud bolts parallel to the pneumatic cylinders.

By retracting and extending the piston rod 35, the winding pins 23, 24 are pushed out over the front of the bushing ₂₁ and withdrawn in their area. Since the traist piece 26 is rotatably supported in the piston rod 35, it can rotate with the bushing 21.

A pressure piece 38, 39 is supported on each of the scissor-type winding pins 23, 24. The pressure pieces 38, 39 are acted upon by the compression springs 40, 41, which are clamped between them and the abutments 42, 43 connected to the bushing 21. The spring-loaded pressure pieces 38, 39 seek to pivot the winding pins 23, 24 into their position pivoted in relation to one another. If the support member 26 is displaced in the direction of the bushing 21 by the piston rod 35, at the end of this feed movement the shorter legs 27, 28 connected to the winding pins 23, 24 meet the outer side surface 31 of the toothed pulley 22 via the rollers 29, 30 that the spreading pins 23, 24 are pivoted into their spread position shown in FIG. 3 by further advancement of the support piece 26.

In the holding and guide plate for the pressure pieces 38, 39, guide slots for the winding pins 23, 24 are provided, which hold them transversely to their pivoting planes at such a distance from one another that in their extended position the web 46 to be wound up in sections runs smoothly between them can.

The support piece 26 which is forked at the front end for mounting the winding pins 23, 24 has radially projecting arms 50, 51 which are offset by 180 ° and whose end regions interact with guide curves 52, 53 which are concentric on the end face of the piston rod 35 facing the winding head 6 enclosing sleeve S4 are provided. As can be seen from FIG. 4, the guide curve consists of two branches 52, 53, starting from an upper vertex 55, which are symmetrical to the vertex 55 are arranged and have an approximately elliptical course. If one of the radial arms 50, 51 strikes one of the branches 52, 53 of the guide curve when the piston rod 35 is pulled back, the latter slides on this branch while rotating the support member 26 until the opposite arm 50 or 51 also hits the opposite branch 52 , 53 of the guide curve comes to bear. In this position, a further retraction movement is blocked and the winding pins 23, 24 are aligned with the material web to be grasped by them in such a way that they grip them between them when they are pushed forward again.

The motor 60 is flanged to the frame wall 2 to drive the winding heads 16 to 19. The output shaft of the motor 60 is connected to a central splined shaft 62 via a toothed belt drive 61. The splined shaft 62 passes through hubs 63, 64 of clutch-brake combinations 65, 66, which alternately couple the toothed pulleys 67, 68 to the splined shaft 62. Parallel to the central spline shaft 62, spline intermediate shafts 70, 71 are provided, which pass through rotatably mounted hubs 72 to 75 in the disk-shaped plates 13, 14, on which toothed pulleys are fastened, which in the form shown in FIG. 2, the winding heads via endless toothed belts Drive 16 to 19.

The required switching current is supplied to the clutch-brake combinations 65, 66 via slip rings 77.

In order to be able to supply the required compressed air to the pneumatic cylinders 36, the central splined shaft 62 is provided, in a manner not shown, with an axial bore and a rotary feedthrough, from which the compressed air is fed to the pneumatic cylinders 36 through lines, also not shown. The turret formed by the rotatable and axially adjustable disc-shaped plates 13, 14 with the winding heads 16 to 19 can be rotated via the geared motor 80, the drive pinion 81 of which meshes with the toothing of the disc 13.

To form the winding rolls, the web 46 is, for example, in the manner shown in FIG. 1 via guide rolls 85, 86. passed from the winding heads 16, 17 existing winding station. The fed web 46 runs between the winding pins 23, 24 of the winding heads 18, 19 which are arranged at a distance from one another. If a sufficiently long section with a predetermined number, for example, of garbage bags separated by transverse perforation lines, has been wound up, the clutch-brake combinations are switched over so that the winding heads 16, 17 are stopped and the winding heads 18, 19 of the other winding point between which the Material web runs through, start up. Through this start, the web is torn along a transverse perforation line, which is currently between the two winding stations, so that the finished wound roll can be stripped off by retracting the winding pins, while the following roll is wound in the other winding station.

During the winding of a roll, the position of the winding points is changed by rotating the disk-shaped plates 13, 14, so that the winding heads 16, 17 in FIG. 1 are then in the lower position. The winding pins drawn in during the change of the winding positions are then extended again so that they grip the material web 46 passing between them and are in their standby position for the subsequent winding process.

Claims (11)

1.Device for coreless winding of a web of material which is fed continuously and is spaced apart with transverse perforations along a transverse perforation line to form supply rolls with two winding stations arranged in a machine frame, the freely cantilevered, rotatably mounted and provided with a rotary drive, in their relative to each other have spread winding position extendable and retractable in their unexpanded winding pins, wherein during the winding in one winding point the web is passed between the winding pins of the other winding point and the winding pins after switching the web to the new winding point from their retracted position to their position enclosing the web between them,
characterized,
that each winding point (16, 17; 18, 19) on both sides of the web (46) has two winding pins (23, 24) which are essentially aligned with one another and which perform their spreading movements relative to one another in mutually parallel planes and which have at least one in the transverse direction of these planes Have a distance from each other that is required for the trouble-free passage of the material web (46). 2. Device according to claim 1, characterized in that the winding points (16, 17; 18, 19) support plates (13, 14) with rotatably mounted therein and with the rotary drives (22) provided bushings (21) that the winding pins (23, 24) consist of angle levers, which are pivotally mounted on a common transverse axis (25) of a supporting piece (26) in a scissor-like manner, which rotatably at the front end of a piston rod (35), aligned with the central axis of the bushing (21), of a pressure medium held fixed to the frame - Piston-cylinder unit is mounted so that the longer, the winding pins (23, 24) forming scissors-like legs in the bushing (21) are longitudinally displaceable and acted upon by springs (40, 41) in the direction of their unspread position and that the approximately support the angled lever at right angles, angled shorter legs (27, 28) on opposite sides of the outwardly facing end faces of the bushings towards the end of the feed movement in such a way that their longer n, the bushing (21) penetrating and the winding pins (23, 24) forming legs are spread. 3. Apparatus according to claim 2, characterized in that on the inner end faces of the bushings (21) on the longer legs (23, 24) supported pressure pieces (38, 39) are guided in a transversely movable manner, between which and attached to the bushing (21) Abutments (42, 43) compression springs (40, 41) are clamped. 4. Apparatus according to claim 2 or 3, characterized in that the shorter legs (27, 28) are supported on the outer end face (31) of a drive disc (32) wedged onto the bushing (21). 5. Device according to one of claims 2 to 4, characterized in that the shorter legs carry support rollers (29, 30) at their free ends. 6. Device according to one of claims 2 to 5, characterized in that the support piece (26) is provided with a radial arm which cooperates with a frame-fixed control curve when retracting the piston rod (35) and thereby the longer legs forming the winding pins in such a way rotates that their center planes lying between their swivel planes lie in the plane of the path to be grasped by them when they are extended. 7. Device according to one of claims 2 to 6, characterized in that the support piece (26) with two 180 ° offset radial arms (50, 51) which cooperate with a control cam which is fixed to the frame and concentrically surrounds the piston rod (35) and which, starting from an apex (55), has two symmetrical, approximately elliptically curved branches (52, 53) extending outwards. 8. Device according to one of claims 2 to 7, characterized in that the two support plates (13, 14) are circular disc-shaped and at least one is provided with an external toothing (15) which meshes with a drive pinion (81), and that Support plates (13, 14) offset by 180 ° are provided with the winding points (16, 17; 18, 19). 9. The device according to claim 8, characterized in that in the support plates (13, 14) a central, with a rotary drive (60, 61) provided shaft (62) is mounted, the clutch-brake combinations (65, 66) alternately with two parallel to this, in the support plates (13, 14) mounted intermediate shafts (70, 71) is in drive connection, from which the rotary drive of the bushings (21) of the winding stations is derived via gears, belts or chains. 10. The device according to claim 8 or 9, characterized in that the disc-shaped support plates (13, 14) are provided with at least three lateral, provided with circumferential grooves wheels (12) which run in annular guides of frame-fixed guide rings (4, 5). 11. The device according to any one of claims 8 to 10, characterized in that the guide rings (4, 5) on cross members (3) of the frame (1, 2) guided and displaceable relative to each other with spindle nuts (6, 7) are, in which a frame-mounted spindle (8) is screwed, and that in the drive plates (13, 14) rotatably mounted drive elements, the central shaft (62) and the intermediate shafts (70, 71), which are designed as multi-spline shafts, axially are guided.

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