EP0760031B1 - Press - Google Patents

Description

The invention relates to a press device for paper machines, especially for dewatering a paper web, with two press rollers, which form a press nip, the first press roll is fixed at least at one end in the axial direction with first bearing blocks to hold the first journal of the first press roll, with second bearing blocks for holding second journal of a stationary yoke the second Press roll, with tension elements, by means of which the second bearing blocks can each be braced against the first bearing blocks, wherein the tension elements in a relative displacement of the press rolls in Allow axial direction, and with one on the second press roll rotatable with respect to the second bearing blocks by means of rotary bearings stored roller jacket.

The invention further relates to a press device for paper machines, especially for dewatering a paper web, with two press rolls forming a press nip, the first Press roll set at least at one end in the axial direction is, with first bearing blocks for holding first bearing journals the first press roll, with second bearing blocks for mounting of second bearing journals of the second press roll, with tension elements, by means of which the second pillow blocks each compared to the first Bearing blocks are clamped, the tension elements one Allow relative displacement of the press rolls in the axial direction, and with swivel bearings for the rotatable mounting of the second bearing journal with respect to the second pedestals.

Such a pressing device is known from WO-A-92/17641.

In the known press device, two press rolls are in relation to each other arranged in parallel, between which a press nip is formed. Because the first pillow blocks and the second pillow blocks over Tension elements are braced together, results for the Transfer of the press force in the press nip a short flow of force, that does not require any parts of the chair. The chair must therefore only the dead weight of the press, but not the high ones Transfer pressing forces. The result is a simpler, lighter and space-saving design. The tension elements exist in the known pressing device from a leaf spring-like Middle part and hammer heads on the ends, which are in grooves on the Bearings are held. The pedestals are therefore immediate connected by means of the mentioned tension elements. Allow the tensile elements which are flexible in the axial direction of the press rolls a deflection of the press rolls to each other and a certain axial displacement of the press rolls to each other during the Operating due to high pressing forces or due to changes in length, e.g. can be due to thermal conditions. Im unloaded The condition of the pressing device are the tension elements either not biased at all or only very slightly.

In the known press device, the first press roll is as so-called deflection adjustment roller, i.e. the The roller has a stationary support body or a yoke which is rotatably mounted on a roll shell, which is hydraulically open the yoke is supported, even at extremely high Press forces in operation a practically deflection-free Behavior of the roll shell or, if desired, a set certain deflection of the roll shell, wherein the yoke can bend. This also makes the Structure of the warehouse considerably simplified. The second press roll is in the known arrangement as a so-called shoe press roll formed, which in turn has a stationary support body, over which a tubular press jacket rotates. In the area of the press nip, this press jacket runs over a press shoe, the shape of the counter roll, i.e. the first press roll, the is designed as a deflection adjusting roller, is adapted, so that an extremely high pressing force in the area of Press nip can be generated and at the same time gradual increase in the pressure when entering the Press nip is made possible.

With a smaller width of the paper web, the Deflection adjustment roller by a quasi-deflection-free Solid roller replaced because the load is lower.

It has been shown in the known pressing device that the tension elements, by means of which the pressing forces between the two Press rolls are transferred significantly during operation Bending loads can be exposed, which is disadvantageous affects the resilience of the tension elements. Especially, when trying to configure the known arrangement turn around, namely the shoe press roll below and the deflection adjustment roll to be placed at the top, and the deflection adjustment roller only about the tension elements on the Shoe press roller sets, can easily overload the Tension elements due to uncontrolled high bending stress to adjust.

The invention is therefore based on the object, pressing devices of the type mentioned at the outset, that the maximum bending load that the tensile elements during operation may be reduced.

This object is achieved in that the Press devices of the type mentioned means provided are to take up tilting moments that in operation on the second Bearing blocks of the second press roller are exercised.

In this way, the object of the invention is completely achieved. According to the invention it was recognized that when the Deflection adjustment roller only on the tension elements the first press roll is set up a four-bar system results, the yoke of the second press roll, which as Deflection roll is executed due to the high Bending forces deflect strongly during operation. This Deflection has an inclined position of the stationary bearing journals result. This skew would be with conventional arrangements due to the relatively large friction in the storage of the Transfer yokes in the spherical bushes to the pedestals and thus to a relatively strong tilting of the bearing blocks compared to the tension elements and thus to extreme bending stress to lead. According to the invention, this bending load avoided by providing means to access the second Bearing supports to exert tilting moments. According to the invention thus the position of the bearing blocks with respect to the tension elements defined by the fact that the pedestals no longer change strongly inclined bearing pins of the yoke can follow instead be adjusted to the position of the roll shell due to the hydraulic support of the roller jacket does not deflect the yoke or only very slightly. This will achieved according to the invention that even under heavy load Pillow blocks only a very small tilt compared to the Learn tensile elements, so that those exerted on the tensile elements Bending loads do not exceed the permissible values.

According to the invention, it was also recognized that even in the case in which the second press roll is not used as a deflection roll trained, but (e.g. with a smaller machine width) is designed as a quasi-bending-free solid roller, strong Bending moments can be exerted on the tension elements, if the definition of the second press roll on the first press roll only done via the tension elements. Because they are attachments directly attached to the bearing blocks of the second press roller, e.g. e.g. Scraper, felt guide rollers or the like, so would this in the case of conventional arrangements for an additional bending load of the tension elements. Such attachments need on the one hand a floating bearing to accommodate changes in length Operation to compensate for the second press roller. This length compensation is more or less fraught with friction and generates tilting moments around the center during compensatory movements the pivot bearing. Can in the axial direction of the second press roll these tilting moments are not caused by the flexible tension elements are recorded and thus lead to conventional arrangements to uncontrolled inclinations of the pedestals and thus excessive bending stress on the tension elements. According to the invention the bending load is also strong in this case reduced, namely by means are provided to the on absorb the second bearing blocks exerted tilting moments. In In this case, the bearing blocks are determined immediately on the rotatable bearing pin, since the bearing pin at the relative low deflection of the solid roller only a slight one Experience passion.

Basically, a number of ways are possible to a recording of the tilting moments exerted on the second pedestals to enable.

According to a first proposal of the invention is next to each Pivot bearing of the second press roller an additional support bearing provided to keep the pedestals free of tilting.

So far, the pivot bearings are due to the high of the trunnions absorbed forces and due to the large inclination of the Bearing pins are preferably designed as self-aligning bearings that do not Can transmit tilting moments, i.e. tilting of the pedestals allow. In contrast, according to the invention, an additional Support a tilt-free support of the bearing blocks in with respect to the rotatable roller jacket, provided the second Press roll is designed as a deflection roll.

If, on the other hand, the second press roll is designed as a solid roll, so is a position fixation by means of the additional support bearings the bearing blocks on the rotating bearing journals of the solid roller reached.

According to another proposal of the invention, the pivot bearings itself be designed as a bearing, the tilting moments be able to record. For example, the pivot bearing as double-row tapered roller bearings in an O arrangement, so that the pedestals immediately without additional support bearings on the roller shell or on the bearing journal of the solid roller in its Angular position can be fixed. This version has the advantage that an additional support bearing can be dispensed with.

In addition, other options are conceivable to take a picture to achieve the tilting moments on the second pedestals. For example, the second bearing blocks can be connected to a cross member be connected to each other so that a tilt is excluded. In addition, it is conceivable to use additional devices, such as with belts, brackets, guides and the like, the bearing blocks in their position relative to the frame fix in order to avoid tilting of the pedestals.

One way to record the tilting moments on the To reach the second bearing block is that at the second bearing blocks handlebars are provided, each with a first end rigidly attached to the second bearing blocks are and each with a second end at a fixed Attack leadership, each end against displacement secures in the axial direction, but shifts in Allows vertical direction.

Also by guiding the second bearing blocks in this way Handlebars on the foundation or on the frame can be tilted of the second pedestals and thus an excessive bending load avoid the tension elements.

According to a further embodiment of the invention is only on one of the second bearing blocks, a handlebar provided with a first end rigidly attached to one of the second pedestals is and with a second end on a fixed guide which attacks the second end against displacements in the axial direction secures but shifts in the vertical direction allows, with the second bearing blocks on a horizontal Connection element are coupled together.

In this way, only one of the second is defined Bearing blocks against axial displacement using a handlebar required while on the other second bracket as a result the connection with the first of the two pedestals on one such handlebars can be dispensed with.

In an alternative version, the handlebars can also be used on the first Bearings can be guided. Such an embodiment is preferred if the first press roll immediately (without ball bushings) is mounted on the first pedestals.

According to a further embodiment of the invention, the first Pillow blocks with the second pillow blocks each over substantially vertical tabs coupled, the tabs being rigid Connecting elements are formed, each at their ends via joints with the second bearing blocks and the first bearing pins are connected, and being the distance between the tabs and the tension elements is dimensioned so that when loaded Pressing device in each case approximately that caused by the pressing force Change in length of the tension elements due to the deflection of the Shifting of the attack points of the roller ends corresponds to the respective tab.

Instead of fixing the second bearing blocks on the foundation or on the first bearing blocks with the help of handlebars that The first bearing blocks can be moved connected to the second bearing blocks via hinges become. The prerequisite for this is, however, that these tabs arranged at such a distance from the tension elements are that increases in length of the tension elements occurring under load by moving the points of attack accordingly the respective tab, which are due to the deflection of the roller ends.

In a modification of this, such a tab can only between a first and a second bearing block be provided while securing the bearing blocks to the opposite side of the pressing device in turn is achieved that the second pillow blocks over a horizontal Connection element are coupled together.

According to a further proposal of the invention, at least one of the second pillow blocks on one of the first pillow blocks secured against displacements in the axial direction.

This ensures that the second press roller no longer like in the known arrangement directly on the machine frame is fixed in the axial direction, but now on the bearing block the first press roll is guided in the axial direction. This will the bending load on the tension elements due to axial forces occur on the press roller defined by the tension elements can, significantly reduced since the bending stress is no longer can only occur on one side, but defined over the length the tension elements is distributed.

In a preferred development of the invention, one of the second Bearing blocks via a fixed in the axial direction of the press rolls, however, articulated connection movable in the longitudinal direction of the tension elements coupled to the first bracket.

In this way, the axial definition of the second Bearing block on the first bearing block in a particularly simple manner realize.

According to a further embodiment of the invention Articulated connection approximately in the middle of the longitudinal extension of the Traction element arranged.

This measure has the advantage that the maximum bending load the tension elements is further reduced, since everyone is firmly clamped End of a tension element only half the bending stress can occur. Thus, given a dimensioning the tension elements also larger deflections of the press rolls under the load in the press nip can be endured because of it resulting bending loads evenly on both ends the tension elements are divided.

A particularly simple version for the articulated connection arises if this comprises a pin which within a Guide is held displaceably in the vertical direction.

According to an alternative embodiment of the invention, one is of the second bearing blocks via a link guide with one of the first bearing blocks coupled, which are movable in the vertical direction is.

Instead of a sliding joint connection according to the above the type mentioned results in a simplified connection between the two pedestals, because the scenery guide immediately can be provided between the bearing blocks, so that this a support function at the same time when the press device is not loaded can meet between the two bearing blocks.

According to a further embodiment of the invention, it is provided that the drive-side bearing blocks by means of the articulated connection to fix each other.

This measure has the advantage that the articulation at a change of one belonging to one of the two press rolls Press jacket or when changing one passed through the press nip endless felt ribbon is not in the way.

It is understood that the above and those below Features to be explained not only in each case specified combination, but also in other combinations or can be used alone, without the scope of Leaving invention.

Fig. 1

die Führerseite einer erfindungsgemäßen Preßvorrichtung in teilweise geschnittener Vorderansicht;

Fig. 2

die Triebseite der Ausführung gemäß Fig. 1;

Fig. 3

eine gegenüber der Ausführung gemäß Fig. 1 leicht abgewandelte Ausführung der Erfindung;

Fig. 4

eine weitere Abwandlung der Erfindung in teilweise geschnittener Vorderansicht auf der Führerseite, wobei die Gegenwalze als Massivwalze ausgebildet ist;

Fig. 5

eine weitere Abwandlung der Erfindung in teilweise geschnittener Vorderansicht auf der Führerseite, wobei der obere Lagerbock mit Hilfe eines Lenkers gegen Verkippen gesichert ist, der an dem unteren Lagerbock verschieblich geführt ist;

Fig. 6

eine Seitenansicht der Ausführung gemäß Fig. 5 in vereinfachter Darstellung;

Fig. 7

eine Abwandlung der Ausführung gemäß Fig. 5, wobei der Lagerbock der oberen Preßwalze mit Hilfe eines Lenkers unmittelbar am Fundament geführt ist und

Fig. 8

eine weitere Ausführung der Erfindung, bei der die übereinanderliegenden Lagerböcke mittels einer Lasche gelenkig miteinander verbunden sind.

Preferred exemplary embodiments of the invention are explained in more detail below with reference to the drawing. Show it:

Fig. 1

the driver's side of a pressing device according to the invention in a partially sectioned front view;

Fig. 2

the drive side of the embodiment of FIG. 1;

Fig. 3

an embodiment of the invention slightly modified compared to the embodiment according to FIG. 1;

Fig. 4

a further modification of the invention in a partially sectioned front view on the driver's side, the counter roller being designed as a solid roller;

Fig. 5

a further modification of the invention in a partially sectioned front view on the driver's side, the upper bearing block being secured against tilting by means of a link which is displaceably guided on the lower bearing block;

Fig. 6

a side view of the embodiment of Figure 5 in a simplified representation.

Fig. 7

a modification of the embodiment of FIG. 5, wherein the bearing block of the upper press roll is guided directly to the foundation with the aid of a handlebar and

Fig. 8

a further embodiment of the invention, in which the superimposed bearing blocks are articulated to one another by means of a bracket.

In Figures 1 and 2 is a pressing device according to the invention designated overall by the number 10.

The press device 10 comprises a first press roll 14, which as So-called shoe press roll with a hydraulically pressed Press shoe 11 is formed, and one above the first Press roll 14 arranged second, parallel to this press roll 16, which is designed as a so-called deflection adjustment roller. The structure of a deflection adjustment roller and a shoe press roller is generally known, for which purpose, for example US-A-5,338,279 and to which DE 92 03 395 U1 is referred to the disclosure of which is hereby incorporated by reference.

The first press roll 14 comprises a in a manner known per se Press jacket 17, which is mounted on a fixed by means of support disks 13 Support body 22 is rotatably mounted and by means of the press shoe 11 can be pressed hydraulically onto the second press roller 16. Between the first press roll 14 and the second press roll 16 is so a press nip 12 is formed through which one to be dewatered Paper web together with usually at least one felt web is performed (not shown).

The first press roll 14 is with the first two journals 52, 53 of the stationary support body 22 rigidly on first bearing blocks 18, 19 stored.

The first bearing block 18 is on the drive side 38 Fixed bearing fixed in the axial direction. Of the For this purpose, the first bearing block 18 is connected to the frame via a joint 43 44 connected, which is fixed on a foundation 42. Consequently is only a pivoting or on the drive side 38 "Inclination" of the first bracket 18 possible, but not Movement in the axial direction 28. On the driver's side 40 is against the first bearing block 19 via a "floating bearing" in the axial direction slidably set. For this purpose, the bearing block 19 is a Double joint 47 connected to the frame 45 (cf. DE 42 10 685 C1), which is attached to the foundation. With deflection of the support body 22, the bearing blocks 18, 19 according to the Tilt the journals 52, 53.

The second press roll designed as a deflection roll 16 has a fixed yoke 15, the two ends of which as Bearing journals are formed, which in second bearing blocks 20, 21 are stored. For this, as can be seen from FIG. 1, each journal 55 a collar 56 with a curved outer surface on which can be pivoted in a correspondingly shaped sleeve 57 is mounted to pivot movements of the bearing pin 55 To allow deflection of the yoke 15 in the event of a load. The second bearing blocks 20, 21 of the second press roller 16 are each in pairs with tension elements 26 on the ones below first bearing blocks 18, 19 set.

While the tension elements 26 in the idle state under none or are only under very low pre-tension, take this under Load when the press shoe 11 is pressed against the second press roll 16 the load on and transfer it directly to the first bearing blocks 18, 19. Thus there is an immediate flow of force from the second bearing blocks 20, 21 via the tension elements 26 the first bearing blocks 18, 19 guaranteed under load.

There is also an axial displacement under load between the first press roll 14 and the second press roll 16 possible.

The second press roll 16 has a roll shell 58 which with its two ends on the second bearing blocks 20, 21 is rotatably mounted by means of rotary bearings, and hydraulically on Yoke 15 is supported.

According to the invention, the rotary bearings are designed as bearings that Can absorb tilting moments. The one shown in Fig. 1 Rotary bearing 25 is a two-row tapered roller bearing in an O arrangement trained so that this ensures that the second Driver-side bearing block 21 with the end of the roller tube 58 is aligned. The same applies to the drive side Bearing block 20.

Since the second press roller 16 is formed as a deflection adjusting roller the bearing pins 55 bend under load, while the roller jacket 58 is hydraulically supported on the yoke 15, is largely free of deflection or a desired one (low) deflection. So the ends come up of the roller tube 58 under load significantly less oblique than the second bearing pin 55. Since each of the collar 56 on the Bushing 57 when the yoke 15 bends considerable frictional forces are transferred to the second bearing blocks 20, 21, would without the tilting training of the pivot bearings tilt the second bearing blocks 20, 21 with the bearing journal 55 since the tensile elements which are flexible in the axial direction of the press roll 16 26 can not absorb these frictional forces, which leads to a strong bending stress of the tension elements 26 would result.

Due to the ability of the pivot bearings to absorb tilting moments such a tilt is avoided, and the second Bearing blocks 20, 21 are at the ends of the roller tube 58 fixed in position. This will cause excessive and undefined bending stress of the tension elements 26 avoided.

As can be seen from Fig. 2, the second drive side is also Bearing block 20 via a sliding joint 32 with the first drive-side bearing block 18 connected. This articulation 32 consists in the simplest case of an arm 35, which is approximately in the middle of the longitudinal extent of the tension element 26 on the bearing block 18 is attached. At the end of the arm 35 there is a pin 34, which is rotatable within a vertical direction 30 extending guide 33 held and in the vertical direction 30 is movable. The guide 36 is rigid with the second drive-side bearing block 20 connected. So that's the second drive-side bearing block 20 in the axial direction 28 on the underlying first bearing block 18 set, but can be in Move vertical direction 30, for example, provided that the tension elements 26 stretch under load. Also tilting the pedestal 18 is possible.

By defining the second press roller 16 via the articulation 32 on the drive side 38 on the first bearing block 18 the bending stress exerted on the tension elements 26 during operation minimized and with the arrangement of the articulation 32 in the middle the longitudinal extension of the tension elements 26 evenly on the Split ends of the tension elements 26.

Since the tension elements 26 themselves are flexible in the axial direction 28 are trained and thus absorb only very low transverse forces can, the hinge connection 32 makes a determination the second press roll 16 with respect to the first press roll 14 reached in the axial direction, and at the same time there are bending stresses of the tension elements 26 evenly on the ends of the Train elements 26 divided. Thus, in the tension elements 26 also avoided those bending stresses caused by axial forces acting on the second press roll 16 are caused.

As can be seen from FIG. 2, the tension elements 26 in FIG known hammer heads 48 at both ends, with which they are held in T-shaped grooves of the second bearing blocks while they are in simple with their lower hammer heads Engage grooves of the first bearing blocks 18, 19.

3 is a modification of that in FIGS. 1 and 2 shown execution designated overall with the number 60. The same reference numbers are used for corresponding parts used. The press device 60 differs from that previously described embodiment essentially in that instead of a pivot bearing, which absorbs tilting moments enables, as usual with conventional arrangements Rotary bearing 25a, which is designed as a self-aligning bearing, is provided is. To fix the position of the second bearing blocks 21a reach, additional support bearings 27a are provided by means of the second bearing blocks 21a coaxial to the ends of the Roll shell 58 are aligned. Otherwise corresponds 3 completely the previously based on the Figures 1 and 2 described embodiment.

A further modification of the invention is shown in FIG. 4 and designated overall by the number 70. Here too again the same reference numbers are used for corresponding parts.

The second press roller 16 is in this embodiment as a solid roller executed, which may be the case when the paper machine has a smaller web width, so that a total of less deflection with the same line force is, so that a simpler version than a solid roller is sufficient.

So here is the second press roller 16 at each end with their end bearing journal 55b directly on the second bearing block 21b rotatably supported by a pivot bearing 25b.

Since the bearing pin 55b due to the quasi-deflection-free bend second press roller 16 only a little and also in the rotating pivot bearings 25b, which are designed as self-aligning bearings, only very small frictional forces are generated exerted small tilting moments on the second bearing blocks 21b, so that no additional position fixing of the second Pillow blocks would be necessary. However, attachments become immediate attached to the second pedestals 21b, such as scrapers, Felt guide rollers and the like, this would be due to the friction Axial compensation of the attachments in turn to one Tilt the second bearing blocks, which in turn lead to a would result in excessive bending stress of the tension elements 26.

For this reason, additional support bearings according to the invention 27b provided on the bearing journal 55b of the second press roller 16, around the second pedestals 21b coaxially with the journals 55b align. Again, instead of this configuration, it would be possible where the pivot bearing 25b as a spherical roller bearing are designed to use pivot bearings, the tilting moments can transmit.

Another embodiment of the invention is shown in FIGS 6 and generally designated by the number 80. Also here again the same reference numbers for corresponding Parts used.

The press device 80 comprises an upper press roll 16, which as Solid roller is formed, and a lower press roller 14, the executed as a shoe press roll in the manner described above is.

The second, upper press roll 16 is with its two bearing journals 55c in the manner previously described with reference to FIG. 4 in each case by means of a spherical roller bearing 25c in the second bearing blocks 21c stored.

Contrary to the embodiment according to FIG. 4, however, there is no support bearing provided to absorb tilting moments.

In order to tilt the upper bearing blocks 21c with respect to the first, Avoid lower pedestals 19c instead on the second bracket 21c a handlebar 82 attached to the first Bearing block 19c is guided.

In this case, the plate is essentially designed as a plate Handlebar 82 at its upper end 83 via screws 89 with the related second bracket 21c connected.

The handlebar 82 has at its second, lower end two outer, downward extensions 81, within each of which a groove 85 is formed, in each of which a pin 86 is displaceable is guided, which is fixed to the journal 53c.

Each link 82 is thus rigid with a second bracket 21c connected and with its second, lower end 84 am Bearing journal 53c fixed in the horizontal direction 28, but in Vertical direction 30 slidably guided.

While only the driver's side 40 is shown in FIG. 5, is on the drive side, not shown in the drawing Press device 80 also a corresponding handlebar on Upper, second bracket provided in a guide on first lower bracket is set in the axial direction, however is guided displaceably in the vertical direction.

In addition, there is an articulated connection on the drive side between the second bearing block and the first bearing block accordingly 2 provided in the middle of the Attacks longitudinal extension of the tension elements. This additional Sliding joint is required to avoid the second Press roll 16 in the axial direction 28 to the drive side or to Avoid driver side, since the tension elements 26 alone none Bending forces can absorb (otherwise would kinematically result in a four-bar transmission).

A bending overload of the tension elements is thus caused Tilting of the second bearing blocks or by axial movements the second press roller 16 avoided.

An alternative version could only be on one side the pressing device 80, preferably on the drive side, the Connection of the second bearing block to the first bearing block by means of of the handlebar may be provided while the second bracket 21c on the driver side 40 of the pressing device 80 by a horizontal 7 with the other second Bearing block is connected and thus secured against tipping is.

In Fig. 6 there is also one on the side of the second bracket 21c provided felt guide roller 87, via which in the felt web 88 together with the one to be dewatered Paper web is guided. Such a felt guide roller 87 is required on the one hand a floating bearing to accommodate changes in length Operation to compensate for the second press roller. This length compensation is more or less fraught with friction and generates tilting moments around the center during compensatory movements the spherical roller bearing 25c by the previously described Construction to be included.

Another modification of the pressing device according to the invention is shown in FIG. 7 and overall with the number 90 designated. Here too, the same reference numbers are used used for corresponding parts.

Again, the second, upper press roll 16 is a solid roll executed by means of a spherical roller bearing 25d on both Bearing pin 55d is mounted on the second bearing blocks 21d.

The first, lower press roll 14 is again a shoe press roll trained, but in a modification of the previously described Execution with its journal 53d each by means of a collar 97 in a ball bushing 96 of the respective first bearing block 19d is stored.

In this embodiment, one of the first bearing blocks is preferred on the drive side 38, designed as a fixed bearing and according Fig. 2 attached to the foundation 42 via a joint. So is only a swivel or "inclination" on the drive side 38 of the first bearing block 19d possible, but none Movement in the axial direction 28. The opposite side, the Driver's side, is attached to the foundation via a floating bearing. (In Fig. 7 is a modification of the previously described embodiments the drive side 38 on the left side of the pressing device 90 shown.)

Securing the upper, second bracket 21d against Axial displacements take place through a link guide 98, the immediately between the upper bracket 21d and the lower Bearing block 19d is arranged. This link guide 98 points at the top and at the bottom one across Web 100 extending in the axial direction, which in a groove 99th engages on the upper bracket 21d or on the lower bracket 19d.

This is an alternative version to the articulated connection 32, which was explained with reference to FIG. 2.

Such a link guide 98 is only on the drive side 38 provided. A certain disadvantage of this scenery tour 98 is that, contrary to the embodiment according to FIG. 2, the axial connection between the two bearing blocks 19d and 21d not exactly in the middle of the longitudinal extension of the tension elements 26 but attacks at the top.

As long as the second press roll 16, that is, the counter roll Shoe press roll 14, which is designed as a solid roll, are the occurring tilting moments on the second bearing blocks 21d, however relatively low, so that a not completely uniform Distribution of the bending load over the tension elements 26 is not is absolutely necessary.

In the embodiment according to FIG. 7, in order to absorb the tilting moments a handlebar 92 with its upper end 93 on the upper bracket 21d, e.g. by means of screws, not shown.

In contrast to that previously described with reference to FIGS. 5 and 6 Execution is the handlebar 92 with its lower end 94 not on the first bearing block below, but instead led directly to a guide 95, the stationary on Foundation 42 is set. The sliding guide 95 allows Shifts in the vertical direction 30, however, sets the bottom End 94 of the handlebar 92 in the axial direction.

Overall, the combination of the handlebar 92 with the Link guide 98 of the upper bearing block 21d on the drive side 38 secured against tilting and against axial displacement.

On the opposite side of the leader could now also a corresponding fuse is provided by means of a link 92 be.

In an alternative embodiment, however, instead of one in FIG such handlebar to secure the driver's upper Bearing bracket only a horizontal connecting element 101 between the two upper bearing blocks 21d in the form of a Crossbar provided so that due to the tilt-free held drive-side bracket 21d also the driver side second bracket is secured against tipping.

Another modification of the previously described embodiment of the Press device according to the invention is shown in Fig. 8 and designated overall by the number 110.

Here, the upper, second press roll 16 is again a solid roll trained and on both journals 55e by means of spherical roller bearings 25e rotatably mounted on the second bearing blocks 21e.

The first press roll 14 is in turn designed as a shoe press roll and with their two journals 53e in the first Bearing blocks 19e directly (without using ball bushings) stored, as previously described with reference to FIG. 5 has been.

8 again shows the driver's side 40.

In contrast to the embodiment according to FIG. 5 are to be avoided no handlebars are provided for tilting the second bearing blocks 21e, which are slidably guided on the first bearing blocks 19e but the upper, second pillow blocks 21e are each with the first pedestals 19e underneath on both sides the pressing device 110 articulated via tabs 112. Each tab is designed as a rigid connecting rod that at its first, upper end 113 via a joint 115 with a Recording 120 is connected to the second bracket 21e is attached. The journal 53e of the lower press roller 14 has a projection 117 on which the lower end 114 of the Tab 112 is in turn fastened by means of a joint 116.

Such a tab connection is at both ends of the Press device 110 provided. In addition, is on the driver's side a hinge connection 32 as shown in FIG. 2 is provided to a to achieve axial definition.

In order now when the pressing device 110 is loaded with the nominal pressing force to achieve in the press nip 12 that the second bearing blocks 21e can not be tilted and thus a bending Overloading the tension elements 26 is excluded, the Tabs 112 at such a distance a from the center of the Tension elements 26 may be arranged such that the elongation ΔL of the tension elements 26 due to the pressing force just the shift X corresponds to each tab 112 due to the deflections of the two press rolls 14, 16 on the journals 53e and 55e. It is therefore a system-specific dimensioning of the Distance a of the tabs 112 from the tension elements 26 is required, in order to avoid tilting of the second bearing blocks 21e.

In Fig. 8, the distance .DELTA.L due to the Elongation of the tension elements 26 under load, resulting in a corresponding displacement of the axis of rotation 118 of the second Press roll 16 leads upwards. The first press roll 14 which in the example shown is designed as a shoe press roll, suffers a deflection of its stationary beam 22 what leads to a corresponding inclination of the journal 53e, which is indicated by the dash-dotted line 119. The displacement of the tab 112 at the joints 115 caused in this way, 116 upward must be the displacement ΔL of the axis of rotation 118 the second press roller 16 (in the extension of the tension elements 26 measured) correspond.

With such a design it is ensured that both Bearing blocks of the upper press roll 16 tilt-free at nominal load are kept so that a bending overload of the Tension elements 26 is avoided.

In an alternative embodiment, the device according to FIG. 8 can also be used only be provided on the drive side, while a horizontal 7, the two upper bearing blocks connects and thus also against the driver-side bearing block Tilting secures.

Unless the second press roll 16 is modified from that shown Execution as a deflection adjustment roller (cf. Fig. 3) is carried out as a result of the storage means Ball bushings have higher frictional moments and thus stronger tilting moments on. The tabs 112 must then be suitably stronger be dimensioned.

It is understood that in addition to the configurations shown the pressing devices with "floating" counter roll also numerous other configurations are possible without the frame to leave the invention.

Claims (15)

1. Pressing apparatus for a paper machine, in particular for the dewatering of a paper web, comprising two press rolls (14, 16) which form a press gap (12), with the first press roll 14 being fixed in the axial direction at at least one end, first bearing blocks (18, 19) for mounting first bearing spigots (52, 53) of the first press roll (14), second bearing blocks (20, 21, 21a) for the mounting of second bearing spigots (54, 55) of a stationary yoke (15) of the second press roll (16), tie elements (26), by means of which the second bearing blocks (20, 21, 21a) can each be clamped relative to the first bearing blocks (18, 19), with the tie elements (26) permitting a relative displacement of the press rolls (14, 16) in the axial direction (28), and a roll jacket (58) rotatably mounted on the second press roll (16) by means of rotary bearings (25, 25a) with respect to the second bearing blocks (21, 21a), characterised in that means (25, 27a) are provided in order to pick up tilting moments exerted onto the second bearing blocks (20, 21, 21a).
2. Pressing apparatus for the dewatering of watery, web-like material, in particular for the dewatering of a paper web, comprising two press rolls (14, 16) which form a press gap (12), with the first press roll 14 being fixed in the axial direction at at least one end, first bearing blocks (19, 19c, 19d, 19e) for mounting first bearing spigots (53, 53c, 53d, 53e) of the first press roll (14), second bearing blocks (21b, 21c, 21d, 21e) for the mounting of second bearing spigots (55, 55b, 55c, 55d, 55e) of the stationary yoke (15) of the second press roll (16), and tie elements (26), by means of which the second bearing blocks (21b, 21c, 21d, 21e) can each be clamped relative to the first bearing blocks (19, 19c, 19d, 19e), with the tie elements (26) permitting a relative displacement of the press rolls (14, 16) in the axial direction (28), and rotary bearings (25b, 25c, 25d, 25e) for the rotatable mounting of the second bearing spigots (55b, 55c, 55d, 55e) with respect to the second bearing blocks (19, 19c, 19d, 19e), characterised in that means (27b, 82, 92, 112) are provided in order to pick up tilting moments exerted onto the second bearing blocks (21b, 21c, 21d, 21e).
3. Pressing apparatus in accordance with claim 1 or claim 2, characterised in that support bearings (27a, 27b) are provided in order to hold the rotary bearings (25a, 25b) free from tilting.
4. Pressing apparatus in accordance with claim 1 or claim 2, characterised in that the rotary bearings (25) are formed as bearings which can take up tilting moments.
5. Pressing apparatus in accordance with claim 4, characterised in that the rotary bearings (25) are formed as a two-row conical roller bearing in O-shaped arrangement.
6. Pressing apparatus in accordance with claim 1 or claim 2, characterised in that a link (82, 92) is provided at at least one second bearing block (21c, 21d) and is rigidly secured at a first end (83, 93) to the second bearing block (21c, 21d) and acts at its second end (84, 94) on a guide (85, 86, 95) which is of fixed location or provided on one of the first bearing blocks (19c) and which secures the second end (84, 94) against displacements in the axial direction (28) but permits displacements in the vertical direction (30).
7. Pressing apparatus in accordance with claim 1 or claim 2, characterised in that at least one second bearing block (21e) is coupled to a first bearing block (19e) via a lug (112), with the lug (112) being formed as a rigid connection element which is connected at its ends (113, 114) via respective joints (115, 116) to the second bearing block (21e) and to the bearing spigot (53e) of the first press roll (14) respectively, with the spacing (a) between the lug (112) and the tie elements (26) being so dimensioned that with the press apparatus loaded, the change in length (ΔL) of the tie elements (26) brought about by the pressing force corresponds to the displacement (X) of the joints (115, 116) of the lug (112) brought about by the bending deflection of the press rolls (14, 16).
8. Pressing apparatus in accordance with one or more of the preceding claims, characterised in that the second bearing blocks (25d) are coupled together via a horizontal connection element (101).
9. Pressing apparatus in accordance with one or more of the preceding claims, characterised in that one of the second bearing blocks (20, 21d) is secured at one of the first bearing blocks (18, 19d) against displacements in the axial direction (28).
10. Pressing apparatus in accordance with one or more of the preceding claims, characterised in that the tie elements (26) are elastically deformable in bending in the axial direction (28) of the press rolls (14, 16) and are respectively rigidly clamped at their ends to the first (18, 19, 19c, 19d, 19e) and second (20, 21, 21a, 21b, 21c, 21d, 21e) bearing blocks respectively.
11. Pressing apparatus in accordance with one or more of the preceding claims, characterised in that one of the second bearing blocks (20) is coupled to one of the first bearing blocks (18) via a movable joint (32) fixed in the axial direction (28) of the press rolls (14,16) but movable in the longitudinal direction (30) of the tie elements (26).
12. Pressing apparatus in accordance with claim 11, characterised in that the movable joint (32) is arranged approximately at the centre of the longitudinal extent of the draw member (26).
13. Pressing apparatus in accordance with claim 12, characterised in that the movable joint (32) includes a spigot (42) which is displaceably mounted in the vertical direction (30) within a guide (36).
14. Pressing apparatus in accordance with one or more of the claims 1 to 10, characterised in that one of the second bearing blocks (21d) is coupled via a sliding guide (98) to one of the first bearing blocks (19d) which is movable in the vertical direction, but is fixed in the axial direction (28) of the press rolls.
15. Pressing apparatus in accordance with one or more of the claims 9 to 14, characterised in that the drive-side bearing blocks are fixed to one another.

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