DE19940487C1 - Embossing rollers for web materials e.g. tissue paper, comprises raceways at the ends of the roller bodies to slide within ring holders in a conical structure to set the embossing gap between the rollers with precision - Google Patents

Abstract

An embossing roller assembly, comprises raceways at both ends of the roller bodies to slide within ring holders in a conical structure to set the embossing gap between the rollers with precision The raceways (3) have a conical inner ring drilling (31). The embossing roller (1), held by the raceways (3), has ring holders (11) between the roller body (10) and the journals (12) with a conical ring seat (110), to take an inserted raceway (3) with its radially expanding ring drilling (31) as it slides in. The outer diameter of the raceway (3) varies, according to the depth of insertion on the ring seat (110). The conical ring seat (110) has an increasing diameter from the side towards the journal (12) inwards, towards the roller body (10). Pressure rings (6) hold the raceways (3) in position at their ring holders (11). Each pressure ring (6) is placed at the side of a raceway (3) pushed into the ring holder (11), together with a screw locking ring and setting screws (7) for positioning in relation to the ring holder (11). Each pressure ring (6) has a sprung support against the ring holder (11). A ring groove (13) is near each ring seat (110), linked to a channel leading axially from the journal (12) for connection to a pressure supply. Both embossing rollers (1,2) have raceways (3) at both ends of their roller bodies (10,20) rolling against each other, with the embossing gap (P) between the rollers to act on the web.

Description

The invention relates to a device for embossing a material web, containing two embossing rollers with roller balls, between which an embossing gap is designed for the passage of the material web, the embossing rollers each rotatable in the device on both sides by means of axial bearing journals are stored and adjusting means are provided, by means of which the axial Distance between the embossing rollers can be changed so that the embossing gap between the roll bales of the same is adjustable in its clear width and at least one of the embossing rollers on both sides of their roll barrel with races is equipped as an adjusting device on the surface of the other Embossing roller leaving the embossing gap between the roller bales unroll, the races have a cylindrical outer surface.

In the case of embossing systems for embossing a web of material with an embossing gap have to work, such adjustment means for adjusting the Nip required. Such stamping systems usually consist of a pair of steel rollers, d. H. the embossing roller and also the other as The embossing roller serving as the counter roller is made of steel.

Various designs of the embossing rollers are known from the prior art, which can be roughly divided into four main groups:

• a) Embossing with union rollers, in which the material to be embossed between a positive and a negative engraved embossing roller that match each other are set, is deformed.  
• b) Embossing with twin rollers, the material web to be embossed between two positively engraved rollers, the engravings of both can be adjusted to each other as well as to each other.
• c) The embossing "point on point", whereby also two positively engraved Embossing rollers are used. These embossing rollers are set so that the positively engraved elements are in relation to each other. The too formative material web is between the positively related Points.
• d) The embossing "point against surface", whereby a roller is engraved positively and the corresponding second embossing roller serving as a counter roller is smooth is trained. The material web to be embossed is one-sided with the positively engraved embossing roller embossed against the smooth embossing roller.

All of the above systems require adjustability of the Embossing gap to adjust this to the material to be processed can or if necessary due to wear or material changes To be able to adjust the embossing gap.

The invention explained below is basically based on all of the aforementioned Main groups of types of embossing are applicable, however the embossing "point represent the main applications on point "and" point against surface ".

The embossing rollers are usually by means of spherical roller bearings and Bearing stones in a so-called roller frame or cassette within the Device led to each other.

For the embossing operation it is necessary that the embossing rollers are axial, some also are radially aligned with each other. This is through the jewels in Connection to the roll frame or cassette of the device as well partly via a radial setting via gear wheels on the bearing journal are mounted. In addition, the so-called embossing gap between the  Roller bales of the embossing rollers are set, d. H. the embossing rollers are set at a precisely defined distance from each other. This Distance is necessary so that the material web to be embossed does not overprint the exact embossing height is reached and the rollers are caused by unwanted Do not wear the touch prematurely.

A known adjusting device for adjusting the embossing gap is based on a riving knife adjustment with a more or less far into a gap drivable wedge, the other adjusting device has a fixed Threaded bolt and a so-called gap adjusting nut. These two The aforementioned adjustment devices are always between the bearing housings the rollers arranged.

Such known adjustment devices have the essential, however Disadvantage that the necessary internal clearance, for example for the storage of Embossing rollers used spherical roller bearings and all others Positioning games for a remaining game of storage of at least 0.05 to 0.1 mm. This remaining game then leads in the embossing operation that the Unintentionally and uncontrolledly move the embossing rollers towards each other, causing the clear width of the embossing gap is always changed. These movements are the more pronounced the greater the different load changes within one Embossing system occur, this is e.g. B. the case with so-called format embossing rollers, as they e.g. B. used for embossing handkerchiefs or napkins become. With these products, multiple layers of tissue material are used embossed with each other so that the individual layers stick together. The for embossing rollers used in these products usually have between 2 and 20 formats per roll, i.e. H. at a z. B. 16 format Embossing rollers are 5 engraving strips in the longitudinal direction, i.e. around the Embossing roller and 16 engraving strips in the transverse direction. Every time the Layers with an engraving strip running in the transverse direction are enlarged however, the printing area in the embossing operation to a multiple of the printing area of the Longitudinal engraving strips, depending on the arrangement, Number and size of formats. Due to the extreme, constantly changing  The embossing rollers within the remaining internal clearance are pressurized Vibration offset, d. H. the embossing rollers undesirably give way to everyone Crossbar. To keep this evasion within reasonable limits it is therefore necessary to set the embossing pressure higher than that for the embossing the engraving strip is necessary in the longitudinal direction, which increases wear and tear the embossing result deteriorates.

DE 297 16 031 U1 describes an adjusting device for a pair of rollers known in which the adjusting devices in one of the pivot bearings of the Embossing rollers spaced area are formed to not only one effect precise setting of the embossing gap, but beyond also the remaining internal clearance in the pivot bearings, which is responsible for the undesired Dodging the embossing rollers in the embossing operation is responsible, too eliminate.

A device for embossing a material web, in which the embossing rollers with So-called bearer rings, rolling together as races, is in the DE 198 14 009 C1 described. The races of both embossing rollers are on their respective diametrically opposite the common roll-off point Supported area on support rollers, which in turn with manual Adjustment devices are provided. Via these adjustment devices, the Distance of the races from each other and thus the resulting at the rolling point Pressure can be changed so that the embossing rollers can be preloaded against each other are and the embossing result can be influenced. Such an attitude turns out to be difficult, however, because on the one hand you have to manually work on a variety of Adjustment wheels must be made and used by the Adjustment devices a precise adjustment based on the existing Residual play in the known device is not achievable. Beyond that the known device is very expensive due to its complex mechanics and noticeable.

The object of the invention is a device for embossing a material web propose an exact setting in the simplest possible way  of the embossing gap can be made and also the internal clearance in the the rotatable bearing of the embossing roller rotating bearings is eliminated, to prevent the embossing rollers from evading in the embossing operation. About that In addition, the device to be proposed within the scope of the invention is intended to be used be manufactured with high precision.

This object is achieved by designing a device for Embossing a material web according to the characteristic features of the Claim 1 solved.

Advantageous refinements and developments of the invention are in the Subclaims specified.

To achieve the object, the invention proposes that the races have a conical inner ring bore and the races receiving embossing roller on both sides between roller bale and bearing journal with corresponding ring seats with a conical ring seat is on which the races with their conical ring bore under radial Expansion can be pushed on and the outer diameter of the races in Depending on the degree of sliding onto the ring seat is changeable.  

In this way it is possible, by adjusting the outside diameter Races the distance between the embossing rollers and thus the clear width the embossing gap remaining between the bales of the embossing rollers to be able to adjust.

The races are made so that their diameter corresponds to that the expected embossing gap is thicker or thinner than the embossing rollers. in the Embossing operation then the embossing rollers with the required Embossing pressure pressed against each other, the races of an embossing roller roll onto the surface of the other embossing roller and open the embossing zones the roller balls of the embossing rollers are contactless by the embossing gap remains between the two roll bales. By pressing the Embossing rollers also become the bearing play of the embossing roller bearings completely eliminated against the printing direction, d. H. the whole is under pressure System free of play, although the necessary clearance in the embossing rollers rotatable bearings to the relieved side is still available. Hereby are vibrations due to manufacturing-related play and / or Load changes when changing longitudinal and transverse embossings within the Embossing gap switched off, which results in a high uniformity of the preserved embossed material web and low wear of the Precipitation device.

Depending on the embodiment and application, it can be provided only to form an embossing roller with races that are directly on the Roll off the roll bale of the second embossing roll serving as the counter roll or but both embossing rollers are formed with races, each roll off each other. In both cases, the embossing zones remain d. H. the area of the roll bales with the surface profiles non-contact, namely by the embossing gap between the roll bales is trained.  

If the embossing gap is to be enlarged or reduced, it is only necessary to change the outer diameter of the races, whereby a displacement of one or both embossing rollers is effected, that the center distance of the two embossing rollers changes from one another. Hereby also the embossing gap between the roll bales in its clear width set.

To change the outer diameter of the races, it is proposed that this has a cylindrical outer surface and a conical inner ring bore have and the embossing roller receiving the races on both sides between Roll balls and bearing journals with corresponding ring holders with a is conical ring seat on which the races with their conical ring bore can be pushed open with radial expansion, so that the outer diameter of the races depending on the degree of Sliding on the ring seat is changeable. Thus, the The outer diameter of the races changed in a simple manner be that the race is more or less strong with its conical inner ring bore on the conical ring seat of the ring holder is postponed. The further the race on the conical ring seat of the Ring intake is postponed, the greater its expansion is what is reflected in an increase in its outside diameter. As well can be removed by pulling the race from the conical ring seat Ring intake in the opposite direction also a reduction in Outer diameter of the races due to the correspondingly smaller degree of expansion thereof will be effected.

The conical ring seats of the ring receptacles are advantageously arranged such that it from its end facing the bearing pin towards the roll barrel have an increasing diameter.

To keep the races permanently in the desired position on the conical To fix the ring seat of the ring receptacle, what a certain desired Corresponds to the outer diameter of the races, it is proposed that  Pressure rings are provided, by means of which the races are in their position the respective ring holder can be determined. These pressure rings can for example, laterally on one pushed onto the ring holder Race are created and then by means of in the ring holder screw-in locking and adjusting screws connected to this become. These locking and adjusting screws can also be used Adjustment of the outer diameter of the races, by screwing it more or less far into the ring seat be and the race pushed onto the ring holder along the Push on the conical ring seat or let it slide until the desired one Outside diameter is reached. Each pressure ring is advantageously resilient supported against the ring receptacle, for example by corresponding, between the pressure ring and the ring seat in the area of Locking and adjusting screws arranged plate spring assemblies can be.

Since the races when pushed onto the conical ring seat of the If the ring receptacle experiences an expansion, it will sit under a press fit on the conical ring seat. Around this press fit for the purpose of adjustment and change the position of a race on the ring seat and thus a change temporarily overcome the outer diameter of the race can, it is proposed that in the area of each ring seat a circumferential An annular groove is provided with an axially from the bearing journal led out channel for the connection of a pressure source communicates. For example, an oil pressure pump serving as a pressure source can be connected to the channel connected via the oil channel under high pressure in the circumferential ring groove presses. The race on the ring seat is then temporarily expanded according to the applied oil pressure and can be pushed onto the conical ring seat in the axial direction or deducted from this, depending on the required change in the Outer diameter of the race. After the desired position the ring seat has been taken up by the race, the pressure source switched off and the resulting temporary expansion of the  Race ring lifted, which makes it in the desired position again on the conical ring seat of the ring holder under a press fit stuck.

The races are advantageously made of hardened steel, so that they can be operated with little wear even with high embossing pressure can.

The further structure and in particular the setting of the embossing gap at the The device according to the invention is described below using a Embodiment explained in more detail in the drawing. Show it:

Fig. 1 in schematic and partial cross section view of the two embossing rolls of the inventive device,

Fig. 2 shows the side view of the roller pair according to the arrow V in Fig. 1,

Fig. 3 shows the detail X of FIG. 1 in an enlarged scale;

FIGS. 4 and 5 rollers, the adjustment of the embossing gap between the embossing,

Fig. 6 in a schematic representation of the force profile in the embossing operation with the inventive device,

Fig. 7 in a schematic representation of a possible execution form of the embossed areas of usable in the inventive apparatus embossing rollers,

Fig. 8 shows the adjustment of the embossing gap in a schematic representation.

Figs. 1 and 2 show the essential part of an apparatus for embossing a web of material, namely two a pair of rollers forming embossing rollers 1, 2.

The embossing rollers 1 , 2 each have a roller barrel 10 , 20 and are rotatably supported in the device by means of bearing pins 12 , 22 provided on both sides of the roller barrel 10 , 20 in rotary bearings 4 , for example spherical roller bearings and corresponding bearing housings 5 . A surface profile can be applied to the roll bales 10 and / or 20 in accordance with the intended type of embossing, which is embossed into the material web to be embossed.

For this purpose, the two embossing rollers 10 , 20 with their respective central axes M1 and M2 are rotatably mounted with respect to one another in the device such that an embossing gap, identified by reference symbol P, remains between the roller bales 10 , 20 , through which the material web to be embossed when the embossing rollers 1 , 2 pulled around their central axes M1 and M2 in a known manner and embossed on the roll bales 10 and / or 20 according to the surface profile.

For the embossing result, the inside width W of the embossing gap P, ie the remaining free space between the roll bales 10 , 20 of the embossing rolls 1 , 2, is of crucial importance and must be set individually.

For this purpose, the embossing roller 1 is formed on both sides of its roll barrel 10 with ring receptacles 11 , to which the bearing pins 12 for the rotatable mounting of the embossing roller 1 are connected in the axial direction of the central axis M1.

Races 3 with a press fit are pushed onto these ring receptacles 11 , which roll on the embossing roller 2 in the area of the roll barrel 20 identified by reference number 200 .

As can be seen in particular from the enlarged illustration according to FIG. 3, the races 3 have a cylindrical outer circumferential surface 30 which serves as a running surface and roll on the area of the roll barrel 20 of the embossing roll 2 identified by reference number 200 . The roller bale 20 of the embossing roller 2 is consequently formed in a greater width than the roller bale 10 of the embossing roller 1 , namely in accordance with the width of the races 3 additionally applied to the embossing roller 1 .

The races 3 have a larger outer diameter than the roll barrel 10 of the embossing roll 1 , so that when the race 3 rolls off the surface of the roll barrel 20 of the embossing roll 2 between the roll barrel 20 and the roll barrel 10 of embossing roll 2 and 1, the embossing gap P with desired clear width W remains.

The illustration according to FIG. 3 also shows that the ring receptacle 11 used to receive the race 3 has a conical outer surface which forms a conical ring seat 110 , the diameter of the conical ring seat 110 from the side facing the bearing pin 12 to the roll barrel 10 is formed increasing.

Correspondingly, the race 3 also has an inner ring bore 31 , which is also conical in accordance with the conical ring seat 110 of the ring receptacle 11 and with the same pitch as the ring seat 110 .

The race 3 is fixed in its position shown in FIG. 3 on the ring receptacle 11 by a pressure ring 6 which bears against the end face 32 of the race 3 facing away from the roll barrel 10 and by means of several fastening and adjusting screws which can be screwed into the ring receptacle 11 7 is attached to this. In addition, in the area of each fastening and adjusting screw 7 there is also a plate spring assembly 8 in a corresponding recess surrounding the fastening and adjusting screw 7 , by means of which the pressure ring 6 is resiliently supported with respect to the ring receptacle 11 of the embossing roller 1 .

In addition, the race 3 is dimensioned in its manufacturing dimensions so that it is shrunk onto the ring receptacle 11 in the area of its conical ring seat 110 , that is to say, when pushed onto the ring seat 110, it expands radially with a corresponding increase in its original outside diameter.

In the illustration according to Fig. 3 can also be seen further details of the bearing housing 5 for receiving the spherical roller bearing 4, namely a seal 50 for sealing against the bearing pin 12 and a bearing cover 51.

It is now essential that the embossing roller 1 is placed under pressure on the embossing roller 2 under pressure in accordance with arrow F, but only the races 3 on both sides of the roller barrel 10 roll on the areas of the race 20 of the embossing roller 2 identified by reference number 200 , but between the embossing gap P remains on the races 10 , 20 .

As can also be seen in more detail from FIG. 6, this configuration completely eliminates the internal clearance and the resulting play in the spherical roller bearings 4 for the rotatable mounting of the embossing rollers 1 and 2 . When the embossing roller 1 is pressed according to arrow F in FIG. 3 onto the surface of the embossing roller 2 , the compressive forces K1 and K2 acting on the spherical roller bearings 4 via the bearing housing 5 are completely exerted by the bearing forces K3 and K4 between the races 3 of the embossing roller 1 and the Roll bales 20 of the embossing roller 2 are lifted, as a result of which the entire system becomes free of play, but the bearing clearance required for the bearing function remains in the unloaded area of the bearing 4 .

This causes fluctuations in production and thereby caused vibrations avoided.  

FIG. 7 also shows a simplified arrangement of a typical arrangement of longitudinal embossments 100 and transverse embossments 101 of embossing rollers 1 and 2 , which can be applied to the roller balls 10 , 20 of the embossing rollers 1 , 2 , for example in order to connect several layers of tissue to one another . For the sake of simplicity, the illustration of the race rings 3 has been omitted. Usually, it is always problematic if transverse embossments 101 , 102 meet in the area of the embossing gap P, since in this case the pressure forces in the embossing gap P briefly increase considerably compared to the pressure forces otherwise prevailing due to the longitudinal embossments 100 , 200 . Due to the elimination of the internal clearance and the residual play in the spherical roller bearings 4 for storing the embossing rollers 1 , 2 explained above with reference to FIG. 6, such emigration of the embossing rollers 1 , 2 is reliably prevented in the device shown in the figures, since the storage the embossing rollers 1 , 2 are always free of play.

Depending on the application, it is now necessary to change the clear width W of the embossing gap P between the roll bales 10 , 20 of the embossing rolls 1 , 2 , which is now explained in more detail with reference to the schematic representation in FIGS. 4, 5 and 8.

For example, in order to reduce the embossing gap P between roller bales 10 and 20 of the embossing rollers 1 , 2 , starting from the state shown in FIG. 3 and the position of the race 3 on the ring receptacle 11 according to FIG. 4, the pressure ring 6 is first loosened in the ring receptacle 11 screwed locking and adjusting screws 7 loosened. Due to the resilient support via the plate spring assemblies 8 , the pressure ring 6 is thus moved to the right according to arrow P1 in the illustration according to FIG. 4 when the adjusting screws 7 are loosened, as a result of which there is a between the pressure ring 6 and the end face 32 of the race 3 facing it Gap S1 forms. Since the race 3 has been shrunk onto the ring seat 110 of the ring receptacle 11 , it initially remains in the position shown.

As can be seen from the illustrations, however, a circumferential annular groove 13 is provided in the area of the ring seat 110 , which communicates with a channel 15 for the connection of a pressure source which is led axially out of the journal 12 and is only indicated schematically here. It is thus possible to connect a pressure source, for example an oil pressure pump, to the channel 15 by means of suitable connecting elements, which pump oil at very high pressure into the circumferential annular groove 13 of the ring seat 110 . This applied high oil pressure within the annular groove 13 widens the clamped on the ring seat 110 raceway 3 temporarily easily, so that the press fit is canceled on the ring seat 110 and the raceway 3, as shown in Fig. 5 the width of the gap S1 between the pressure ring 6 and race 3 jumps to the right according to arrow P2 until its end face 32 comes into contact with pressure ring 6 again. Then the high oil pressure applied to the ring groove 13 can be released again and the race 3 presses against the ring seat 110 of the ring receptacle 11 again , although it has been subtracted from the conical ring seat 110 by the amount of the width of the gap S1. As a result, the expansion of the race 3 caused by the conical ring seat 110 of the ring receptacle 11 becomes smaller and the race 3 contracts radially inward in the direction of arrow T, as a result of which the outer diameter of the cylindrical lateral surface 30 serving as the rolling surface is reduced. The result of this reduction in the outer diameter of the race 3 is a reduction in the inside width W of the nip P and thus an adjustment thereof, since the embossing rollers 1 , 2 now have a smaller center distance when they roll against one another.

This principle is shown again in a simplified schematic form in FIG. 8.

In the initial state, the embossing roller 1 , of which only the central axis M1 is shown in the illustration according to FIG. 8, and the embossing roller 2 with its central axis M2 are arranged in such a way that the race 3 with its cylindrical outer lateral surface 30 rolls on the roll barrel 20 . In order to reduce the embossing gap P between the roll bales 10 , 20 of the embossing rolls 1 , 2 , the race 30 with its conical ring bore 31 is pulled off the conical ring seat 110 of the ring holder 11 , ie shifted to the right in the illustrations according to arrow P1, which is caused by loosening the locking and adjusting screws 8 holding the pressure ring is effected.

By this removal of the race 3 from the conical ring seat 110 of the ring receptacle 11 , the expansion of the race 3 is reduced, whereby its outer diameter A is reduced to a reduced outer diameter A 'when moving in the direction of arrow P1, which is caused by the displacement in the direction of arrow P1 and the slope or Inclination of the conical ring receptacle 110 and the corresponding wall 31 of the conical ring bore of the race 3 is dependent. Due to this reduced diameter A 'of the race 3 , which can also be seen in FIG. 8 with the aid of the race 3 shown in broken lines, the race 3 continues to roll on the roll barrel 20 of the embossing roll 2 , but the embossing roll 2 is displaced less far, so that a displacement P3 of the embossing roller 2 accordingly occurs, as a result of which the central axis M2 is shifted to the position shown by M2 'and closer to the central axis M1. Correspondingly, the roll barrel 20 of the embossing roll 2 is also shifted into the position shown in dashed lines according to arrow P3, which ultimately brings about a reduction in the clear width W of the stamping gap P between the roll barrel 10 and the roll barrel 20 .

Likewise, it is also possible in the reverse manner to enlarge the roller gap P, namely by pushing the race 3 further against the direction of the arrow P1 onto the conical ring seat 110 of the ring receptacle 11 , as a result of which its widening is enlarged and this is ultimately reflected in an enlarged outer diameter, whereby the embossing roller 2 is displaced in the opposite direction of the arrow P3 and the embossing gap P is enlarged.

It is essential in the embodiment shown in FIGS . 3 to 5 that the setting of the embossing gap can be carried out in a simple manner with high precision. In accordance with the angle of inclination α of the conical ring seat 110 of the ring seat 11 , the displacement path of the race 3 on the conical ring seat 110 of the ring seat 11 required for the adjustment of the embossing gap P can be calculated exactly. If the conical ring seat 110 of the ring receptacle 11 has a slope of 1:10, for example, for the adjustment of the clear width W of the embossing gap P by 1/10 mm, the race 3 is displaced in the axial direction according to arrow P1 or contrary to arrow P1 exactly 1 mm necessary. On the basis of the slope of the conical ring seat 110 of the ring receptacle 11, the exact displacement path of the race 3 required for the desired change in the embossing gap can thus be calculated.

With a desired reduction in the clear width of the embossing gap P, the pressure ring 6 is thus first moved away from the race 3 in the direction of arrow P1 by loosening the locking and adjusting screws 7 and under pressure of the plate spring assemblies 89 until a gap width D1 is established which corresponds to the Desired displacement of the race 3 corresponds to the slope of the conical ring receptacle 110 . After expansion of the race 3 by means of high oil pressure in the ring groove 13 , the latter jumps according to arrow P2 in FIG. 5 by the set gap width D1 until it rests on the race 6 , so that an exact displacement of the race 3 by the set displacement path corresponding to the gap width D1 is effected.

It is also possible to set a precise increase in the clear width of the embossing gap P. In this case, starting from the illustration according to FIG. 5, the gap S2 is first measured between the end face 33 of the race 3 facing the roll barrel 10 and the end face 14 of the roll barrel 10, and the race 3 is widened by applying a high oil pressure in the circumferential annular groove 13 . Subsequently, by tightening the locking and adjusting screws 7 via the pressure ring 6, the race 3 thus detached can be pushed more strongly against the direction of the arrow P2 onto the conical ring seat of the ring receptacle 11 until the gap S2 is a desired amount corresponding to the exact displacement path has been reduced. Subsequently, the oil pressure is removed from the circumferential annular groove 13 and the displaced race 3 is seated in the direction of arrow T and clamps radially inward on the conical ring seat 110 of the ring receptacle 11 , whereby it expands more sharply in accordance with the further pushed position on the conical ring seat 110 and thus has an outer diameter corresponding to the slope of the conical ring seat 110 , as a result of which the embossing gap P has been enlarged to the desired extent in its clear width W.

The embossing gap can therefore be readjusted as follows sum up:

At the end of the journal 12 , an oil pressure pump is installed at a corresponding connection.

Now for a reduction of the embossing gap, the locking and adjusting screws 7 of the pressure ring 6 are loosened, whereby the disc springs located between the pressure ring 6 and the ring receptacle 11 press the pressure ring 6 away from the race 3 and the gap S1 thus created between the race 3 and Pressure ring 6 precisely by means of a measuring instrument, for. B. Spy can be determined. The pressure ring 6 is now moved at a distance D1 from the race 3 which corresponds exactly to the desired displacement path of the race 3 .

Now the race 3 is pressurized by the oil pressure pump via the ring groove 13 and is expanded by the pressure present, loosens and jumps from the conical ring seat 110 of the ring receptacle 11 by the set amount until it rests on the pressure ring 6 .

Now the pressure in the annular groove 13 is released again and the locking and adjusting screws 7 are checked for tight fit. The race now has a reduced diameter which corresponds exactly to the desired reduction in the inside width W of the embossing gap P.

This process is repeated accordingly on the opposite race 3 of the embossing roller 1 .

If the embossing gap P is to be enlarged, the races 3 are also pressurized and expanded as described, but the pressure rings 6 are not loosened, but are further tightened using the securing and adjusting screws 7 . The race 3 thus moves in the direction of the roll barrel 10 , and the calculated measure for the gap enlargement is measured in this case at the gap S2 between the race 3 and the roll barrel 10 .

In this way, a play-free mounting of the embossing rollers 1 , 2 with the elimination of the remaining play due to internal clearance as well as a particularly simple adjustment of the embossing gap are made possible. The construction explained above in the drawings also makes it possible to prefabricate the race rings and shrink them onto the likewise prefabricated embossing rollers with a conical ring seat 110 . The bearing seats of the embossing roller on the bearing journal 12 as well as the races 3 and the roller barrel 10 can then be ground in a single setting, as a result of which extremely high concentricity can be achieved.

Depending on the desired type of embossing, it is possible to form only one embossing roller 1 with a surface profile and to form the second embossing roller 2 serving as a counter roller, for example with a smooth roller bale. Of course, it is also possible to also equip the second embossing roller 2 with a surface profile, only the areas marked with reference number 200 on which the races 3 roll have to be made smooth.

It is also possible, instead of the embodiment shown in the figures, in which only one embossing roller 1 is formed with races 3 , to also form both embossing rollers 1 , 2 with corresponding races 3 , which roll against one another, the embossing gap between the roller balls 10 , 20 P remains for the passage of the material web to be embossed.

Claims (8)

1.Device for embossing a material web, comprising two embossing rollers with roller balls, between which an embossing gap is formed for the passage of the material web, the embossing rollers being rotatably supported on both sides in the apparatus by means of axial bearing journals and adjusting means being provided by means of which the axial distance is changeable between the embossing rollers, so that the clear width of the embossing gap between the roller bales thereof can be adjusted and at least one of the embossing rollers is equipped on both sides of its roller bale with races as adjusting means which roll on the surface of the other embossing roller while leaving the embossing gap between the roller bales wherein the running rings have a cylindrical outer surface, characterized in that the running rings (3) have a conical inner ring bore (31) and the races (3) receiving the embossing roller (1) on both sides between the roll barrel (10) and Bearing journal ( 12 ) with corresponding ring receptacles ( 11 ) is designed with a conical ring seat ( 110 ), onto which the race rings ( 3 ) with their conical ring bore ( 31 ) can be pushed with radial expansion and the outer diameter (A) of the race rings ( 3 ) is changeable depending on the degree of being pushed onto the ring seat ( 110 ). 2. Device according to claim 1, characterized in that the conical ring seats ( 110 ) of the ring receptacles ( 11 ) from their end facing the bearing journal ( 12 ) to the roll barrel ( 10 ) have an increasing diameter. 3. Device according to one of claims 1 or 2, characterized in that pressure rings ( 6 ) are provided, by means of which the races ( 3 ) in their position on the respective ring receptacle ( 11 ) can be fixed. 4. The device according to claim 3, characterized in that each pressure ring ( 6 ) laterally on a ring holder ( 11 ) pushed on the race ( 3 ) and by means of the ring holder ( 11 ) screwable locking and adjusting screws ( 7 ) can be connected to this and is displaceable with respect to the ring seat ( 11 ). 5. Apparatus according to claim 3 or 4, characterized in that each pressure ring ( 6 ) is resiliently supported with respect to the ring receptacle ( 11 ). 6. Device according to one of claims 1 to 5, characterized in that in the region of each ring seat ( 110 ) a circumferential annular groove ( 13 ) is provided which with an axially from the bearing pin ( 12 ) led out channel ( 15 ) for the connection of a Pressure source communicates. 7. Device according to one of claims 1 to 6, characterized in that the races ( 3 ) are made of hardened steel. 8. Device according to one of claims 1 to 7, characterized in that both embossing rollers ( 1 , 2 ) on both sides of their respective roll barrel ( 10 , 20 ) are formed with races ( 3 ) which roll against each other, wherein between the roll barrel ( 10 , 20 ) the embossing gap (P) remains.