FI58451B - ANORDNING FOER KONTINUERLIG TRYCKBEHANDLING AV BANOR - Google Patents

Description

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Federal Republic of Germany-Förbundsrepubliken Tyskland (DE) P 2205503-1 * Proof-Styrkt (71) Eduard Kiisters, Finkenveg 18, 1 * 15 Krefeld-Forstwald, Federal Republic of Germany-Förbundsrepubliken Tyskland (DE), (72) Eduard Kustfeld Forstwald, Valentin Appenzeller, Kempen / Ndrh.,

Federal Republic of Germany-Förbundsrepubliken Tyskland (DE) (7l *) Leitzinger Oy (5l *) Equipment for continuous pressure treatment of lines - Anordning för kontinuerlig tryckbehandling av banor

The invention relates to a device for the continuous pressure treatment of webs, in particular paper, textile and similar webs, which device has a rotating drum around which a compression strip is wound, which takes the web to be compressed between itself and the drum surface and is supported away from the web. on its side by means of friction-reducing devices arranged between the support surface and the compression strip against the support surface, the devices arranged between the support surface and the compression strip being rolling roll pieces.

When the tracks are treated with pressure by means of rollers, the area of effect of the pressure is only a narrow roller gap, which is theoretically even just a line, but which in practice is a zone of small width due to the thickness and compressibility of the material and the deformation of the roller surfaces. In order to be able to carry out the treatment up to a sufficient amount, it is therefore often necessary to repeat the treatment so that the track is passed successively through several successive slots. This takes place in a known manner, for example in a paper reader, which usually comprises a group of teas with up to 12 superimposed rolls, over which the paper web is guided by alternately turning one around the other. Between each roll, the treatment in question takes place at the desired pressure, and the total area of action is the sum of the narrow pressure zones of the individual roll slots. The manufacture of such contact surfaces requires considerable cost with numerous rollers, large roller frames, and numerous drive devices.

The object of the invention is to provide a device for the continuous pressure treatment of tracks, in which the device has a larger pressure-acting surface relative to the rollers, without having to connect a plurality of rollers in succession.

The basic idea of the invention is to widen the operating gap to which pressure is applied between two rollers, around the circumference of one roll, and thus to increase the impact surface. The expansion of the contact surface takes place in such a way that the counter-roll is partially replaced by a press strip wound around the first roll and entrained, and instead of the current practice, the material path is passed substantially directly through the roll gap between the press strip and the first roll.

Devices of this quality are known per se. The pressure which can then be applied to the web of material corresponds to the pressure at which the press strip lies against the drum and is thus determined by the pull of the press strip. This bet is again somewhat within well-defined limits. The compression belt is endless and must turn several times over the rollers or drums in its path. The bending in this case causes tensile and compressive stresses in the material of the compression strip, which must remain in the elastic range, i. to the material of the compression strip below the creep limit. Since the radii of the drums cannot be increased arbitrarily to improve the bending geometry, in a given structure there is a precisely determinable maximum possible track thickness and thus the limits of the permissible track load. The resulting radial pressures are not sufficient to produce an effect on the web that could be compared to, for example, the operation of a calender.

German patent publication 923 172 discloses an apparatus for continuous pressing comprising a rotating drum with a single-sided pressing strip wound around it about 120 °, the material to be pressed being between the pressing strip and the drum. A segment is made on the outer side of the press strip with a support surface adapted to the appearance of the press strip, which is pressed in the radial direction i 58451 against the drum. Roller pieces roll between the steel track and the support surface, which transfer pressure from the support surface to the compression strip. To achieve the pressure effect in this way, no special and difficult-to-control track tension is required. However, radial compression against the support surface results in radial forces on the drum that must be received by the drum bearing. In equipment suitable for the production of wider webs, such as paper webs, and also when it is necessary to expand the compression range in the circumferential direction when aiming for pressures comparable to rollers, there are bearing loads which cause considerable technical problems and call into question the economy of the equipment.

The object of the invention is in particular to provide a device of the general type mentioned above so that the bearing load can be reduced.

/ For this purpose, the device according to the invention is characterized in that the support surface is formed by an open ring which covers the circumference of the drum substantially more than 180 °, extending up to the axial gap, and the ends of which are connected to each other under tensile stress. The open support ring rotates around the drum more than 180 ° and terminates in an area where the ends of the support ring again approach each other as they rotate around the drum. Due to this and the traction between the ends of the support ring, the support ring can act as a tensioning path which, due to its circumferential traction, generates a radial force on the compression strip and the drum. This force creates pressure on the track. Instead of in the known device the force of the support surface was directed unilaterally against the drum, at least part of the force now remains inside the support ring and remains separate from the bearing of the drum. The forces exerted on the drum in the imaginary 180 ° part of the support ring according to the invention form a resultant result, which means a rather considerable force on the bearing of the drum. What is important, then, is that the support ring rotates more than 180 ° around the drum. Outside the 180 ° portion, the area of the support ring acting on the drum indicates forces which result in a decrease in said resultant result because they partially cancel out the former forces. However, the distribution of forces is not completely even, as it is necessary to leave a gap in the support ring somewhere free for the insertion and discharge of the track and the compression strip rotating with it.

4 58451

Despite the fact that lower resultant bearing forces have been obtained by forming the support surface as an open support ring, the operating surface has expanded almost over the entire circumference of the drum.

The support ring may be formed as a steel plate bent around the drum. For example, sheets about 6-12 mm thick can be used, which are preformed to match the shape of the drum. The shape of the support ring changes only slightly in use, in contrast to the compression strip, which changes direction as it travels and is bent back and forth. The dimensioning of the support ring thus leaves the desired freedom, while the compression strip may have the small wall strength required to reduce the bending stresses, since the support ring has eliminated its pressure-raising function.

In order to take full advantage of the effect of the support ring on the tensioning of the track, it is recommended that the compression pin be guided around the drum in a manner known per se in the form of an open narrow-necked loop ring and that the ends of the support ring extend close to the neck. In this way, the support ring surrounds the drum almost completely, and the gap required to lead in and out of the track and the press strip is as narrow as possible.

It is expedient to use controllable force elements which apply tensile stress to the ends of the support ring.

This allows the desired working pressure to be adjusted in the same way as when changing the position of a pair of rollers.

In a preferred embodiment of the invention, traction elements arranged outside the track width can be used, through which the tensile stress acting on the ends of the support ring is transmitted.

The material web and the compression strip can pass in the space between the traction elements between the support ring and the drum.

One possibility is that the traction elements immediately engage the ends of the support ring.

This presupposes, of course, a corresponding reinforcement of the ends of the support ring, so that they do not deform under the influence of forces acting only on both sides.

5 58451

However, it is also possible that the traction elements engage in the vicinity of the neck of the loop ring formed by the compression strip, outside it and inside the compression strip, which run transversely over the track width and are provided with spaced transverse gripping ends at the ends of the support ring.

In this way, the traction can be applied to several points distributed over the width of the track at the edge of the slit of the support ring, and the uniformity of the application of the forces is no longer tied to the bending strength of these edges. The transverse beams can be made very rigid without difficulty so that they can collect large bending moments.

In a suitable embodiment of the invention, a support is used in the region of the neck of the loop ring, which is supported against the thrust bearing of the drum, and pulling elements which are immediately adhering thereto are arranged at both ends of the support ring.

The ends of the support ring are then not connected to each other immediately, but through a support which dissipates the forces on the drum bearing caused by the incomplete rotation of the support ring around the drum.

The traction elements arranged at both ends of the support ring can independently apply a traction force between the end of the support ring in question and the support.

The independent effect of the forces is advantageous because by adjusting it accordingly, the equalization of the forces transmitted from the rotating drum to the support ring in the circumferential direction is achieved. In this case, the second traction element is adjusted to a stronger traction against the circumferential force than the other.

In a simplified embodiment, a force element is used which can move the point of connection of the force-transmitting traction anchors away from the drum bearing.

In this case, the transmission members can be formed as rigid anchors and only one force-applying device is required on each side.

The compression strip can in principle be formed of any suitable material, for example also plastic or the like.

Embodiments of the invention are shown schematically in the drawing.

Figures 1-4 are simplified side views of devices in which tensile stress between the ends of a support ring is provided in various ways;

Figures 5-7 show different embodiments of roller chains that can be used between the compression strip and the support ring.

Figure 8 is a side view of an apparatus with a web of material passing between a drum and a plastic web;

Figure 9 is a side view of an apparatus in which a web of material passes between a plastic web and a press strip.

In Figure 1 the web material passes through one of open loop section shape of the drum 2 around the rotating shaft 3 in the direction of the arrow 4. Outside the track 1, the compression strip 5 rotates with it so that the track 1 is closed between the compression strip 5 and the surface of the drum for most of the circumference of the drum 2.

Outside the compression strip 5 there is an open support ring 6 which also surrounds the drum 2 for most of its circumference and leaves only a gap 8 in the neck 7 of the loop-shaped track through which the track 1 and the compression strip 5 enter between the support ring 6 and the drum surface. state.

The support ring 6 does not move compared to the rotating drum 4 and the accompanying press belt 5. To reduce the friction between the press belt 5 and the support ring 6, roller chains 9 are used which roll in the wheels of the press belt 5 between this outer side and the inner side of the support ring 6. The roller chains 9 are arranged quite tightly next to each other over the width of the track and allow pressure to be transferred on the support surface of the entire support ring 6 as it passes.

The ends 6 'and 6 "of the support ring 6 are connected to each other by traction elements 10 made on both sides of the track 1 outside it. The traction elements 10 pull the ends 6', 6" of the support ring 6 against each other so that the support ring 6 acts as a tensioning track and applies a radial pressure of 58451. to the roller chains 9 which transfer this to the compression belt 5 or the track 1. However, since the support ring 6, although stable, is not completely rigid, the radial pressure caused by its circumferential traction is distributed substantially evenly over the circumference of the drum 2. The support ring 6 can consist of, for example, a 6-12 mm strong steel plate.

Fig. 2 shows a modified embodiment in which the ends 6 'and 6 "of the support ring 6 are not connected to each other immediately, but through traction elements 11, 12 arranged at each end 6', 6", which are arranged on each side of the track width and engage a support 13 which relies on drum bearing. The support 13 receives a force arising from the angularity of the direction of the forces of the traction elements 11, 12. The directions of the forces of the traction elements 11, 12 correspond to the tangents of the drum 2 at the height of the ends 6 'and 6 "of the support ring 6. The higher the ends 6, 6" are pulled on the drum, i.e. the closer they are to each other, the flatter the tangents and the smaller the resultant force received by the support 13 and in particular by its bearing on the drum shaft 13.

Fig. 3 shows an embodiment in which a traction element is not provided on each side of both ends 6 ', 6 "of the support ring 6, but the support 13 has a force member 14 which raises the gripping point of the anchor rods 16, 17 connected to the ends 6' and 6", i.e. can be moved further away from the shaft 3 of the drum 2. This also creates a traction between the ends 6 ', 6 "which results in the desired tightening effect. In the embodiment shown, the force element 14 is a thrust generating force element; a support tension generating device could be placed above the support 13. to achieve.

Fig. 4 shows a further embodiment in which the tensile force acts between two transverse beams 18 formed as I-beams, which are connected by traction elements 10 and extend over the width of the track. The transverse beams 18 transfer the force across the track width through the split transmission members 19 to the ends 6 ', 6 ”of the support ring. The transverse beams 18 receive the bending stress generated by the action of traction only on the sides in the traction elements 10. In order to compensate for the different forces generated by the bending, the transmission members 19 can be hydraulic force elements which are hydraulically connected to each other.

The quality of the force elements 10, 11, 12, 14 is in itself freely selectable.

S8451

Spindles, hydraulic cylinders, or the like can be used. Due to the short operating distances of the power members, large-area hydraulic units with membrane-like pressure pads are especially recommended.

Figure 5 shows a suitable embodiment of the roller chains 9. The roller chains comprise rollers 20, 21 of different lengths arranged side by side towards the joint 2, which are arranged alternately in successive members and connected to each other by rectangularly bent tie rails 22. The rollers 20, 21 are detachably mounted and form adjacent end faces so that immediately side by side without a gap. Due to the fact that the spaces between the rollers 21, 20 of each member are arranged in a zig-zag shape, each point in the width of the chain becomes overridden by the rollers.

Figure 6 shows a chain 9 with always 3 adjacent rollers 23, 24, 25 of different lengths in successive members. Consecutive members are connected by straight tie rails, however, in several successive members the tie rails are arranged to move to the same side in a zigzag manner so that the tie rails run as a whole inside the chain in a zigzag fashion, again having the effect that the width of each chain the roller rolls over the point again.

Fig. 7 shows yet another embodiment of a suitable chain substantially corresponding to Fig. 6, in which the tie rails do not run zigzagly but move continuously to the same side, whereby the tie rail chain is cut as it approaches a certain distance from the chain edge and starts on the opposite side of the chain. new communication rail chain.

The chains of Figures 5, 6 and 7 run mostly immediately next to each other, but independently of each other, so that no difficulty arises in positioning the edges of the roller shafts.

Fig. 8 shows a somewhat more detailed embodiment corresponding to the general structure of Fig. 2. The passage of the track 1 and the pressing strip 5 in the form of an open loop ring around the drum 2 is provided by drums 30 forming the neck of the loop ring. In the exemplary embodiment, the roller chains 9 rolling between the compression strip 5 and the support ring 6 58451 are guided over the rollers 31 arranged in a substantially square manner from the outside around the drum 2. The compression strip 5 is guided over the rollers 32 in the same way outside the roller chains 9 around the drum 2. A further track 34 is arranged between the pressing strip 5 and the goods track 1, which is passed outside the pressing tape 5 over the rollers 33 around the drum 2. The roller chains 9, the pressing belt 5 and the additional track 34 can be tightened independently of each other by tightening devices indicated by arrows 35, 36 and 37, respectively. The axes of all drums 30, 31, 32, 33 run parallel to the axis 3 of the drum 2.

In the embodiment of Figure 8, the additional web 34 is made of polyamide, which web has a special surface pattern for the surface treatment of paper, for example. The web 1 is a paper data which is thus surface treated between the polyamide web 34 and the surface of the drum 2, which can be further promoted by heating the drum 2. It is also possible to control the use of the polyamide web 34 or the press strip 5 so that the speed of the polyamide web 34 is different. a friction effect is obtained.

Fig. 9 shows another embodiment, which for the most part corresponds to Fig. 8. The only difference is the different arrangement of the additional track 38, namely that the track 1 runs between the additional track 38 and the compression strip 5. The additional track 38 passes over a single support roller 9 arranged above the neck of the loop ring. In order to achieve friction, in this case a corresponding speed difference is caused between the auxiliary track 38 and the compression strip 5, between the tracks of which the goods track 1 passes.

Claims (9)

Apparatus for continuous printing of webs, in particular paper, textile and such webs, which has a rotating drum, which is encircled by an accompanying printing strip, which occupies the material web for printing between itself and the surface of the drum and which is supported by its side, away from the web by means of friction-reducing devices arranged between the support surface and the printing belt, the devices placed between the support surface and the printing belt are rolling roller parts, characterized in that the support surface is an open ring (6) which covers substantially over 180 ° of the drum circuit (2) and extends upwardly to an axial slot (8), and whose ends (6 ', 6 ") are joined to each other under tension. 2. Device according to claim 1, characterized in that the open ring (6) consists of an adjusting plate, which is bent around the drum (2). Device according to Claim 1 or 2, characterized in that the pressure band (5) is arranged in a known manner around the drum (2) in the form of an open winding ring which has a neck (7) and that the support ring (6) ends (6 ', 6 ") extend to the vicinity of the shaft (7). Device according to any of claims 1-3, characterized by the use of controllable force elements (10, 11, 12, 14) which direct the tension to the ends of the open support ring (61, 6 "). 5. Device according to claim 4, characterized in that said force element is made up of tension elements (10) arranged directly outside the bandwidth, which are arranged directly between the ends (6 ', 6 ") of the support ring (6) for effecting the tension. Device according to claim 5, characterized in that the tensioning elements (10) immediately engage with the ends (6 ', 6') of the support ring (6). Device according to claim 5, characterized in that the tensioning elements engage with the neck ring (7) in the vicinity of the crossbars (18) arranged transverse to it which extend across the