DE2832457A1 - Plastics web calendering or printing cylinder pair - has hollow sleeves supported at different locations along their length to compensate for flexure - Google Patents

Abstract

Plastics web calendering or printing cylinder pair is arranged such that the flexures caused by pressure differences at the nip are directed in opposite direction and corrected by corresp. disposition of supports, bending moments of the cylinder sleeves and elastic moduli of the sleeve materials to provide uniform nip gap independently of the nip pressure variations. Correction may be obtd. by supporting the cylinder sleeves of the pair at three points, e.g., one sleeve at two points adjacent its ends and the other sleeve at one point intermediate its length.

Description

Pair of rollers for rolling out plastic materials and for

Processing of web-shaped products The invention relates to pairs of rollers for rolling out pasty plastics and other substances into foils and for embossing, Corrugating or smoothing sheet-like products.

When processing products between two rollers act in the roller gap Forces that push the rollers apart.

When using cylindrical rollers, the deflection is in the The center of the roller is larger than the edge of the roller. When rolling out pasty materials This results in different film thicknesses between the edge of the film for films and center of the film. When embossing, corrugating or smoothing sheet-like products there are higher pressures on the rolling stock at the edge than in the middle.

For optimal processing of sheet-like products and pasty ones Substances a pair of rollers is required, its roller gap, regardless of the course the working pressure over the working width can be kept constant.

It is known that a deflection compensation is achieved by crossing the rollers can be achieved. However, this requires complex roller frames.

Furthermore, one or both rollers can be made to be crowned U.S. Patent No. 272,591 dated July 5, 1950 to compensate for deflection. An evenly However, a thick roll gap is only created with a specific one, through the corresponding one Crowning given, working pressure.

By counter-bending the elongated roller bearing journals according to the US patent No. 3 060 843 of November 9, 1961, the deflection of the rollers can also be reduced. This procedure is but only applicable to relatively thick rollers. In addition, the support bearings must absorb considerably higher forces than the forces resulting from the pressures in the roll gap.

An almost uniform roll gap thickness is also achieved by that the roll shell does not cover the entire length of the roll gap on the roll core is based, but according to the German Patent Office's disclosure no.2 299 550 from February 28, 1974, only to about 3/10 of the roll gap length in both directions from the center. A prerequisite for this, however, is an even working pressure over the entire length of the roll shell.

It is also known that a pressure medium between the roll shell and roll core on the roll side facing the roll gap according to DPa 708 of April 23, 1970 bending of the roll shell is prevented. With this procedure you can however, only webs of the width of the roll shell length can be processed. The pressure on the rolling stock is the same at all points, while the roll gap thickness according to the material thickness. For drivable roller shells, the construction very expensive.

The invention is based on the object of a uniformly thick To realize roll gap or a uniform working pressure on web-shaped rolling stock to be exercised over the entire width of the roll, regardless of the working pressure and the width of the foils to be produced or of the webs to be processed.

This object is achieved according to the invention in that the deflection the rolling is not prevented or reduced, but by the fact that the deflections the roller shells are in opposite directions at the corresponding points and do not add up, but subtract and thereby approximately cancel.

The roller pair according to the invention consists of two roller shells with one roller core each. A roll shell is supported at both ends and in the middle, while the second roll shell in two places about 3/10 in each direction from the center of the roll, on which the roll core is supported.

The position of the two support points and the ratios of the bending resistance moments of the two roll shells are chosen so that the maximum deflections of the roll shells are equal and lie in such a way that they approximately cancel each other out.

The support points of the triple supported roll shell are included radially displaceable so that the center lines when the individual components are bent of the three support points can be set so that the deflections of the two Roll shells cancel each other out.

The advantages achieved by the invention are that a more uniform Pressure can be exerted over the entire width of the rolling stock, or that one evenly thick roll gap can be set, regardless of the width of the to be machined Lanes.

Figures 1 to 12 show three different designs of roller pairs each with a triple and a double supported roll shell, their deflections are in opposite directions under the working pressure in the roll gap and thus approximate Constantly thick roll gap results.

The upper part of Figure 1 shows a roller construction in which the roll shell 6 at three points on the non-rotatably mounted in the bearings 2 and 11. watzenkern 1 is supported.

The roll shell 6 directs the working pressures over the bearing 7 and the Bearings 5 and 8, which are supported on the double eccentrics 3, 4 and 9, 10, in the Roll core. The bearings 5, 7 and 8 are designed so that angle differences between Roll shell 6 and roll core 1 are permissible.

The upper part of Figure 2 shows the roll shell 6, the bearing 8, the journal of the roller core 1 and the double eccentric 9, 10 in section, as in Figure 1 indicated. The double eccentric 9, 10 is in the position for the unloaded The condition of the roller is shown. The roller is loaded and the roller core bends by turning in opposite directions the double eccentrics 3, 4 and 9, 10 the bearings 5, 7 and 8 are adjusted by equal angular amounts so that there is a bending line as shown in exaggerated form by line 28 in FIG.

The lower part of Figure 1 shows the two-point supported counter roll. The roller core 18 with its drive pin 26 is with the bearings 13 and 25 in the Bearing blocks 14 and 24 stored.

The drive torque is provided by the roller core via the clutches 15 and 23 18 transferred to the roll shell 17. The camps 19 and 21 exceed the forces from the roll shell 17 to the roll core 18, and are designed so that angular differences between the roll shell 17 and the roll core 18 are permissible. The spacers 16, 20 and 22 define the bearings 19 and 21 with respect to the roll shell 17 axially. The roll shell 17 bends when loaded, as indicated by line 30 in FIG 3 is exaggerated.

FIG. 3 shows the bending lines of the two roll shells from FIG with uniform line load over the entire length of the roll shell. Line 28 represents the bending line of the three-point supported roll jacket from Figure 1. Arrow 27 between the lines 28 and 33 indicates the deflection of the roll shell 6 at the appropriate place. Line 30 represents the bending line of the two-point supported Roll jacket from Figure 1. Arrow 31 between lines 30 and 32 indicates the deflection of the roll shell 17 at the appropriate point.

Arrow 29 indicates the distance between the two roll shell surfaces Load at the appropriate point. As Figure 3 shows, the distance is on almost the same at all points over the entire length of the roll shell.

The upper part of Figure 4 shows a further embodiment of a roller with three-point supported roller shell. The two outer support points are located here of the roll shell 41 through the parts 39 and 43 not on the roll core 40, but via the bearings 38 and 44, which allow angular errors, in the bearing blocks 37 and 45. The roller core 40 is in the bearings 36 and 46, which also allow angular errors, and the double eccentrics 34, 35 and 47, 48 rotatably mounted in the bearing blocks 37 and 45. The roller core 40 can be driven at the journal end 49. The drive torque is via the coupling 42, the misalignment and angle error between part 43 and Roll core 40 compensates, and the part 43 is transferred to the roll shell 41. In order to roll shell 41 under load, as shown exaggerated by line 51 in Figure 6, sags, the two journals of the roller core 40 will rotate in opposite directions the double eccentric 34, 35 and 47, 48 shifted radially in the bearing blocks 37 and 45.

Figure 5 shows the bearing block 45, the double eccentric 47, 48, the bearing 46 and the journal of the roller core 40 in section, as indicated in FIG.

The description of FIG. 3 applies to FIG. 6 51 the bending line of the roll jacket 41 and line 52 the bending line of the roll jacket 50 exaggerated.

The upper part of Figure 7 shows a further embodiment of a roller with three-point supported roller shell. The pin 53 directs the drive torque via the part 57 to the roll shell 59. The working pressures are from the two ends of the roll shell 59 via the parts 57 and 61 and the bearings 55 and 62, the angular errors allow, directed into the bearing blocks 56 and 63. In the middle of the roll shell 59. the working pressures over the bearing 60, the angular error between the roll shell 59 and roller core 58 allows, passed into the roller core 58. The roller core 58 supports find out about camp 54, the angular error between the tenons of the Roll core 58 and the part 57 allows the part 57 and the bearing 55 in the bearing block 56 from. The second journal of the roller core 58 is supported by the bearing 54 and the Double eccentric 65, 66 in bearing block 63.

Figure 8 shows the bearing block 63, the double eccentric 65, 66, the bearing 64 and the journal of the roller core 58 in section, as indicated in FIG.

The deflection of the roller core 58 when loaded is caused by opposite directions rotate the double eccentric 65,66 balanced by equal angular amounts, so that can set a bending line of the roll shell 59, as indicated by line 68 in Figure 9 is exaggerated.

Line 69 in Figure 9 shows the bending line of the two-point exaggerated supported roll jacket 67, which is shown in the lower part of FIG.

The upper part of FIG. 10 shows a further embodiment of a roller with three-point supported roller shell. The pin 70 directs the drive torque via the part 74 to the roll shell 76. The working pressures are from the two ends of the roll shell 76 over the parts 74 and 78 and the bearings 72 and 79, the angular errors allow, directed into the bearing blocks 73 and 80. In the middle of the roll shell 76 the working pressures via the bearing 77, the angular error between the roll shell 76 and roll core 75 allows, passed into the roll core 75.

The roller core 75 is supported by the bearing 71, the part 74 and the Bearing 72 in bearing block 73. The second journal of the fixed roller core 75 is supported in the laberbock 80 by means of the adjusting screw 81. Figure 11 shows the Bearing block 80 the pin of the roller core 75 and the adjusting screw 81 with pinned Nut 82 in section, as indicated in FIG.

The deflection of the fixed roller core 75 is by corresponding adjust balanced on the adjusting screw 81, so that a bending line of the Roll shell 76 can be set, as exaggerated by line 84 in FIG is shown.

Line 85 in Figure 12 shows the bending line of the two-point exaggerated supported roll jacket 83, which is shown in the lower part of Figure 10.

Claims (5)

Claims 0 pair of rollers for rolling out plastic materials for foils or for print processing of materials in web form in calenders, Rolling mills or printing machines, characterized in that the deflections the roll shells, caused by the pressures in the roll gap, are in opposite directions and through corresponding positions of the support points, corresponding bending resistance moments equalize the roll shells and the corresponding modulus of elasticity of the shell materials, so that an approximately evenly thick roll gap over the entire length of the roll shell arises, regardless of the respective pressure in the roll gap and the width of the material web, achieved in that the support points of the roll shells are not opposite each other, but are arranged as for example by Figure 1 for a combination a pair of rollers with two-point and three-point supported roller shells is and how it is by combining three-point and four-point or four-point and roll shell pairs supported at five points, and so on, is also possible. 2. A three-point supported roller, as in the upper part of figure 1 shown, consisting of a rotatable roll shell 6 and a stationary one roller core mounted in the bearing blocks 2 and 11, characterized in that die.beiden Bearings 5 and 8 at the ends of the roll shell can be shifted radially in such a way that that the difference in deflection of the roller core 1 between the bearing point .7 in the Center of the roll shell and the bearings 5 and 8 balanced at the ends of the roll shell, and a bending line of the roll mantle is reached, as indicated by line 28 in FIG 3 is exaggerated. 3. A three-point supported roller as in the upper part of figure 4 shown, characterized in that the two ends of the roll shell directly are supported in the bearing blocks 37 and 45 and the deflection of the roller core 40 when loaded by radial displacement of its pins in the bearing blocks 37 and 45 can be compensated so that a bending line of the roll shell is established, as shown exaggerated by line 51 in Figure 6, the drive torque of the roller via the pin 49, the coupling 42 and the part 43 in the roller shell can be initiated. 4. A three-point supported roller, as in the upper part of figure 7 shown, characterized in that the ends of the roll shell directly in the bearing blocks are supported and the drive torque via the pin 53 and the Part 57 is introduced into the roll shell, the deflection of the roll core 58 is compensated by radial displacement of the pin in the bearing block 63 so that that a bending line appears, as exaggerated by line 68 in FIG is shown. 5. A three-point supported roller, as shown in the upper part of Figure 10 is shown, characterized in that the ends of the roll shell are supported directly in the bearing blocks and the drive torque via the journal 70 and the part 74 is introduced into the roll shell, the deflection of the fixed roller core 75 by radial displacement of the pin in the bearing block 80 is balanced in such a way that a bending line is set, as shown by line 84 is shown exaggerated in FIG.