WO2008008027A1

WO2008008027A1 - Chuck arrangement, especially for a flying paster

Info

Publication number: WO2008008027A1
Application number: PCT/SE2007/050434
Authority: WO
Inventors: Hans Högberg
Original assignee: Megtec Systems Amal Aktiebolag
Priority date: 2006-07-10
Filing date: 2007-06-19
Publication date: 2008-01-17
Also published as: SE530418C2; SE0601535L

Abstract

This invention relates to a chuck arrangement, especially for paper rolls (R1, R2), comprising a chuck mechanism (301B, 302, 326) arranged on a spindle device (12, 328), said spindle device (328) being rotatably arranged by means of at least two bearings (304, 310), within a casing (306) that rotatably supports said spindle device (328), wherein a first of said bearings (304) is axially fixed in relation to said casing (306) and a piston mechanism (308, 309, 311, 340) arranged to control activation of said chuck mechanism (301B, 302, 326), wherein that said piston mechanism (308, 309, 311, 340) is arranged within said casing (306), and attached to and axially moveable with a second one of said bearings (310).

Description

CHUCK ARRANGEMENT, ESPECIALLY FOR A FLYING PASTER

TECHNICAL FIELD This invention relates to a chuck arrangement, especially for paper rolls, comprising a chuck mechanism arranged on a spindle device, said spindle device being rotatably arranged by means of at least two bearings, wherein a piston mechanism is arranged to control activation of said chuck mechanism, wherein that said piston mechanism is arranged with at least one part in between the chuck mechanism and the rearward most bearing.

PRIOR ART

Flying pasters are highly developed machines used in the printing industry to enable continuous operation, e.g. change of printing rolls. Modern flying paster design includes two arms, independent drive and core tension control. Today the most advanced model features 4-quadrant drive and breaking, e.g. to provide optimum web tension. The results is fewer web brakes, simplest splices preparation and low maintenance. As a consequence complex chuck arrangements, e.g. including automatic gripping/releasing mechanisms are requested, to safely and efficiently handle the rolls within the paster. Traditional torque operated chucks have proven to be less reliable than pneumatically operated chucks. A disadvantage with the design of known pneumatic chuck arrangements (i.e. piston operated) is that they tend to be very bulky, i.e. requiring relatively large space. Moreover known design very often lead to expensive solutions. By way of example it may be referred to flying pasters technology referred to in US 5,335,870 and US 5,445,341, but it should be understood that the invention is not limited to this preferred field, but may be used in any field having similar needs.

SUMMARY OF THE INVENTION

It is an object of the invention to eliminate or at least minimize the above disadvantage, which is achieved by means of a chuck arrangement, especially for paper rolls, comprising a chuck mechanism arranged on a spindle device, said spindle device being rotatably arranged by means of at least two bearings, wherein a piston mechanism is arranged to control activation of said chuck mechanism, wherein that said piston mechanism is arranged with at least one part in between the chuck mechanism and the rearward most bearing. Thanks to an arrangement according to the invention there is provided a basis for having a very compact and cost efficient design. BRIEF DESCRIPTIONS OF THE DRAWINGS

In the following the invention will be described in more detail with reference to the enclosed drawings, wherein:

Fig. 1 shows a first embodiment of a chuck arrangement according to the invention, in a cross sectional side view where the upper half of the drawing shows the arrangement in a gripping position and the under half shows the arrangement in a released position. Fig. 2 shows a further embodiment according to the invention, substantially along the same principles as Fig. 1, but supplemented with a breaking mechanism, Fig. 3 schematically an exemplary embodiment of a flying paster for use of a chuck arrangement according to the invention.

DETAILED DESCRIPTION

In Fig. 1 there is shown a cross sectional side view of a chuck arrangement 3OA that is mounted within a cylindrical mounting portion 300 of a reel arm 3 for a flying paster. The chuck arrangement 30A comprises a rotatable spindle 328 that is powered by a dented wheel 28, positioned at the right hand end of the spindle 328. At the other end of the spindle 328 there is chuck 33 which is arranged with a releasable gripping mechanism 302, 326 for enabling gripping (and releasing) of a hollow core, e.g. for winding and rewinding of paper rolls. In the upper half of Fig. 1 the chuck 33 is shown in its gripping position and in the under half of Fig. 1 in its released position.

The spindle 328, i.e. the rotating part of the chuck arrangement 30A, comprises a number of details rotatably mounted by means of roller bearings 304, 310 and 325. At the chuck end there is a front portion of a central sleeve 301 arranged with a number of radially directed recesses 30 IB. In each one of said recesses 30 IB there is arranged a gripping device 302, 302'. Coaxially therewith and within the central sleeve 301 there is an expansion body 326. At the outward end of the expansion body there is a conical, tapered surface 326A, that interacts with correspondingly tapered surfaces of each gripping device 302A. The inwardly projecting portion 326B of the expansion body 326 is shaped with a diameter that slidably fits into the inner of a coaxial bore 30 IA within the central sleeve 301. In contact with the rear end of the expansion body 326 there is a homogeneous rod like pusher member 340, which is arranged with a radial through hole 340A. In the through hole 340A there is positioned a pin 308, that extends perpendicularly in relation to the axis of rotation L2, of the spindle 328. The end portions of said pin 308 projects into holes 309A of corresponding diameter of a pusher sleeve 309. The pusher sleeve 309 has the intermediate roller bearing 310 fixedly attached to its outer surface, at the opposite end in relation to the through holes 309A. The pusher member 340 is slidably arranged within the central bore 30 IA of the central sleeve 301. At an intermediate portion thereof the central sleeve 301 is arranged with two slot formed through passages 301F, that will allow for axial movement of the pin 308, and thereby also the pusher sleeve/member 309, 340 in relation to the central sleeve 301. Hence the outer sleeve 309 is slidably arranged outside of the central sleeve 301. The central sleeve 301 is sufficiently supported merely by the front bearing 304 (i.e. closest to the chuck) and the intermediate bearing 310 and has one front portion (including recesses 301B) extending beyond the front bearing 104 and one rear portion 30 IE extending (in the other direction) beyond the intermediate bearing 310.

Surrounding the intermediate bearing 310 there is piston body 311, to which the intermediate bearing 310 is also fixedly attached. Accordingly the piston body 311 and the outer sleeve 309 will move as a unit together with the intermediate bearing 310. The piston body 311 has a rear side wall 31 IA that delimits a piston chamber 335. The opposite side of the piston chamber 335 is formed by a piston bottom 312 that is fixedly attached to (adjacent the rear end of) a casing 306. The piston member 311 is slidably and sealingly arranged in relation to the inner surface of the casing 306. The piston bottom 312 has an inner sleeve portion 312A attached to the front side of the vertical wall 312 that is attached to the casing 306. Accordingly the sleeve portion 312 A, the vertical wall of the piston bottom 312, the rear vertical wall 31 IA of the piston member 311 and a portion of the inner wall of the casing 306 forms a sealed piston chamber 335. The latter mentioned parts do not form rotating members, which is achieved by arranging a gap 341 between the outer surface 30 IG of the central sleeve 301 and the sleeve portion 312A of the piston bottom 312.

Splines 342 are used to rotation wise interconnect the central sleeve 301 with a driving shaft portion 314, of the spindle 328. The driving shaft portion 314 is connected to a drive sleeve 346 by means of a wedge coupling 337. The drive sleeve 346 is in turn bolted to a dented wheel 347, (forming the drive wheel 28) that is driven by a chain/belt 17.

An inner most roller bearing 325 rotatably fixes the drive sleeve 346 within a support 324 that is bolted to the reel arm 3.

A spring 307 is arranged within the casing 306, between the outer most roller bearing 304 and the intermediate bearing 310. The outer most bearing 304 has its inner half fixedly attached to the central sleeve 301 and its outer half fixedly attached to an attachment sleeve 305 that is fixedly arranged within the casing 306 adjacent its outer most end. Hence the spring 307 will urge the axially moveable members 326, 340, 308, 309, 310 and 311 in a direction away from the chuck 33, thereby always apply a releasing force in relation to the gripping devices 302, 302'.

The gripping force is achieved by pressurising the piston chamber 335, to urge the axially moveable members in the chuck direction to force the gripping devices 302, 302' radially outwardly. This is achieved by supplying pressurised air to a reel arm inlet 332 which is in communication with an axially extending casing passage 333 which in turn is in communication with a radial casing passage 334 leading to the pressure chamber 335. Accordingly, when pressurised air is supplied to the inlet 332 pressurisation of the chamber 335 will lead to axial displacement of the piston 311 and thereby also the wedge member 326 to force the gripping devices 302, 302' radially outwardly.

Moreover there is shown a displacement mechanism 323 used for displacement of the casing 306 from a most retracted position (as shown in Fig. 1) and a most extended position (as shown in Fig. 2). Thanks to the use of splines 342 along all the extension of the inner surface 30 IG of the central sleeve 301, the sleeve 301 will be interconnected with the splines 314A of the driving shaft 314 in every position.

The function of the chuck arrangement 30A is as follows. Rotation will be transmitted via belt 17 to the drive wheel 28, which in turn is transmitted to the driving shaft 314. The rotation is than transmitted to the central sleeve 301 via the splines 342. Central sleeve 301 will effect rotation of the pusher sleeve 309 via the pin 308 and thereby also the body 340. The gripping devices 302 follow the central sleeve 301 and also the wedge body 326 means of its frictional engagement with the gripping devices 302 and the pusher body 340. Resilient means (not shown, known per se) urge the gripping devices 302, 302' radially inwardly to always be in contact with the wedge body 326 (alternatively e.g. T-recess connection may be used between them). The spring 307, which is in contact with the outer halves of the roller bearings 304, 307 will urge the non rotating portions of the bearings to be as distant from each other as possible, as is shown in the lower most half of Fig. 1. To activate the gripping portions 302, 302' pressurized air is applied via inlet 332, through passage 333 and passage 334 into the pressure chamber 335 whereby the piston member 311 will move axially and thereby also move the intermediate bearing 310, the pusher sleeve 309, the pusher body 340 and thereby also the wedge body 326, that forces the gripping devices 302, 302' radially outwardly. Hence the piston member 311 will not participate in the rotation since it is in contact with the outer half of bearing 310, which via the balls of the bearing merely will transmit the axial movement to the rotating inner half which is fixed to the rotating pusher sleeve 309.

In Fig.2 there is shown a chuck arrangement 3OA which is exactly the same regarding the main features, as described in Fig. 1. However here the chuck is positioned in its outer most position, which is achieved by having activated the displacement mechanism 323 which by means of a dented wheel and a corresponding dented guide (on the casing 306) will cause axial displacement of the casing 306 and thereby also the chuck. The axial displacement is handled by a telescoping action of the drive shaft 314 in the central sleeve 301. As can be seen also in this outer most position of casing 306 pressurised air will be supplied to the pressure chamber 335 by means of the axial passage 333 being sufficiently long to facilitate supply in any positional of the casing 306. Hence, basic aspects of the chuck arrangement shown in Fig.2 is exactly the same as already described in Fig. 1 and will therefore not be described in more detail.

The main difference between the embodiment of Fig. 1 and Fig.2 is that the Fig. 2 embodiment presents a less sophisticated arrangement than that in Fig.l. Fig. 1 presents a four quadrant application, i.e. facilitating drive of the chuck in both directions and also retardation/braking by means of the motor in both directions. In contrast the arrangement shown in Fig. 2 presents a one quadrant application (of course also a 2Q drive may be used, i.e. having the dented wheel 347 fixed to the shaft 314), i.e. implying need of both a breaking mechanism 315, 320, 321 and a freewheel hub 28A. It should be noted that exactly the same driving shaft 314 is used in both Fig. 1 and Fig. 2 embodiment. The support housing 324, however, is differently arranged, to allow for positioning of the break arrangement 315, 320, 321 between the driven wheel 28 and the reel arm 3, i.e. the support housing 324 has a decreased axial length which will lead to an inner most bearing 325 being positioned closer to the reel arm 3 than in Fig. 1. Moreover the drive sleeve 346 will be made longer than in Fig 1, and at an intermediate position thereof there is arranged a flange 339 to which the brake disk 315 is attached, to always follow the rotation of the driven shaft 314. Brake pads 321 are arranged at three brake callipers 320 which are fixed to the reel arm 3. The drive sleeve 346 is rotation wise connected to the drive shaft 314 by means of a wedge coupling 337, which wedge coupling also interconnects an inner drive sleeve 338. A bearing 336 is arranged between the dented driven wheel 347 and the outer drive sleeve 338. Further there is arranged a freewheel hub 28A between the dented wheel 347 and the drive sleeve 338, which facilitates that torque may only be transmitted from the dented wheel 347 to the driven shaft 314 in one direction. Except for the further features described above the embodiment shown in Fig. 2 has a function that is exactly the same as already described in relation to Fig. 1.

In Fig. 3 there is shown a schematic cross sectional side view of a flying paster wherein a chuck arrangement according to the invention may be used. The flying paster shown in Fig. 3 is of the kind having straight reel arms 3, 5. The reel arms 3, 5 are axially moveably arranged on a turret 46, which is rotatably arranged within support around a central horizontal axis Ll frame 1. The turret 46 comprises endplates 45, 47 connected to hub portions 44, 48. The hub portions 44, 48 are immovable axially but rotatably arranged to one side each 10, 12 of the frame, by means of bearings (not shown), to allow the turret 46 to rotate without any axial movement. The right hand side of the turret 46 is connected to a motor 40 and a transmission 41, 42 to control the rotation of the turret 46. The motor 40 is fixedly attached to the frame 1. The motor 40 drives a dented driven wheel 41, which is in contact with a correspondingly dented driven wheel

43 fixedly attached to the driven turret hub 44. Hence the part of the transmission 42 that is fixed to the turret 46 includes a dented wheel 43 arranged on the outer side of the right hand wall 12 and at the other side of the hub 44, i.e. the inside of the wall 12 an endplate 45. Accordingly the rotation transmitting portion 42 for the turret comprises and endplate 45 attached to the turret, positioned within said frame 1 and a hub portion

44 that extends through the side wall 12 to the driven wheel 43. Further it is shown that the hub portion 44 protrudes beyond the annular portion with the driven wheel 43. Adjacent the outer end of the protruding hub 44, and also adjacent the inner end, there are arranged bearings 26. The inner annular portion of these bearings 26 support a first portion 23 of a shaft 23, 24, 25.

The shaft 23, 24, 25 is telescopically arranged by means of splines. The splines will allow the intermediate shaft portion 24 to be axially moveable within a hollow centre portion of an outer shaft 23 and also within a hollow centre portion of an inner shaft 25. Adjacent the outer end of the outer shaft 23, there is fixedly attached a dented wheel 22. The dented wheel 22 is powered via a dented belt 21 by means of a motor 20 that is fixedly attached to a attachment base 12A at the outer side of the side wall 12 of the frame 1, in a position to not interfere with the other motor 40 (e.g. diametrically), preferably at a distant that allows for sufficient space to allow for varying kind and size of motors to be attached at the same location 12A . The intermediate shaft 24 is arranged with splines along its outer surface and the inner shaft 23 and outer shaft 25 respectively are arranged with corresponding splines at their inner surfaces, to allow transmission of torque from the motor 20, via belt 21, via dented wheel 22, via outer shaft 23, via intermediate shaft 24, to outer shaft 25. Adjacent the outer end of the inner shaft 25 there is fixedly attached a dented chain wheel 26. The dented chain wheel drives an endless chain 27, which in turn drives a first driven chain wheel 28 and a second driven chain wheel 29. Each one of said driven chain wheels 28, 29 are arranged in connection with a first 3OA and a second 3OB chuck arrangement, according to fig 2 of the invention, i.e. comprising a free wheel hub 28A. An opposite, non-driven, chuck arrangement 5OA, 5OB is arranged on the second arm 5 on the other side of the turret 46. The chuck arrangements 30A, 30B, 5OB, 5OA are provided for holding a first roll Rl and a second roll R2 respectively. A first 33 and a third chuck 53 hold the first roll Rl and a corresponding second and fourth chuck hold the second roll R2. The chuck arrangements 30A, 5OA allow the chucks 33, 53 to safely grip into the hollow core of the roll Rl and also to release the core (as is known per se).

Assuming that the upper roll Rl is being unwound, that process will continue until that roll Rl is close to being empty. In conjunction therewith the turret 46 will be rotated by means of the motor 40 and the corresponding transmission 41, 42, to move the full roll R2 into the splicing position. Simultaneously that full roll R2 will be accelerated by means of motor 20 and the corresponding transmission 21 - 29 to obtain a synchronous speed in relation to the web that is being unwound. Thanks to the free wheel hub 28A the spindle 328 of the chuck arrangement 30A that is connected to the first roll Rl will be free wheeling, since the smaller diameter of the first roll Rl will require a much higher rotational speed than that of the larger roll R2. Once the second roll R2 has been spliced in (known per se), the turret may be rotated and the remaining core of the first roll Rl may be removed by deactivating the piston 311 to release the chucks 33, 53 and activating the displacement mechanism 323, to remove the spindles 52, 328 out of position (i.e. displaceable chucks) from the centre core of the emptied roll Rl. Thereafter a new roll may be put into position and the process may be continued without any interruption being necessary.

The main advantage of a design according to the invention is that an efficient mechanism is obtained that is also very compact and thereby allows for cost efficient design of the paster seen as a whole. Thanks to the design optimised support/bearings may be achieved that leads to small friction losses. The invention is not limited by the above described embodiments but may be varied within the scope of the appended claims. For instance, as is evident for the skilled person, also a hydraulically operated piston may be used.

Claims

1. Chuck arrangement, especially for paper rolls (Rl , R2), comprising a chuck mechanism (301B, 302, 326) arranged on a spindle device (12, 328), said spindle device (328) being rotatably arranged by means of at least two bearings (304, 310), within a casing (306) that rotatably supports said spindle device (328), wherein a first of said bearings (304) is axially fixed in relation to said casing (306) and a piston mechanism (308, 309, 311, 340) arranged to control activation of said chuck mechanism (301B, 302, 326), charac teriz e d in that said piston mechanism (308, 309, 311, 340) is arranged within said casing (306), and attached to and axially moveable with a second one of said bearings (310).

2. Chuck arrangement according to claim 1, ch aract eri z e d in that said second bearing (310) is positioned rearward most in relation to the chuck mechanism (301B, 302, 326).

3. Chuck arrangement according to claim I or 2, charac teriz e d in that said piston mechanism includes at least one part (309, 340) that is rotatably arranged and coaxial with the centre axis (L2) of said spindle device (328).

4. Chuck arrangement according to claim 1, ch aract eri z e d in that said casing (306) is slidably arranged within a recess (300).

5. Chuck arrangement according to claim 4, characteriz e d in that a drive mechanism (323) is arranged to control the axial position of said casing (306).

6. Chuck arrangement according to any preceding claim, c harac teriz e d in that said piston mechanism is arranged radially partly outside and partly inside of a central sleeve (301) that is coaxially arranged in relation to said spindle device (328).

7. Chuck arrangement according to claim 6, c harac teri z e d in that said central sleeve (301) has an extension that over bridges the distance between said two bearings (304, 301).

8. Chuck arrangement according to claim 7, characterized in that said central sleeve (301) is arranged with recesses (301B) arranged to accurately control radial movement of gripping devices (302, 302') of said chuck mechanism (301B, 302, 326).

9. Chuck arrangement according to claim 7, characterized in that said central sleeve (301) at its innermost end is arranged with inwardly protruding splines (301G), for interaction with a driveshaft (314).