EP0061456A1

EP0061456A1 - Compression cylinder, of which the flexion is adjustable

Info

Publication number: EP0061456A1
Application number: EP81901918A
Authority: EP
Inventors: Christian Schiel; Robert Wolf
Original assignee: JM Voith GmbH
Current assignee: JM Voith GmbH
Priority date: 1980-06-28
Filing date: 1981-06-26
Publication date: 1982-10-06
Also published as: FI822393A0; WO1982000165A1; FI822393L; BR8108896A; USRE32586E; CS489181A2; EP0043119B1; FI70988B; US4414890A; YU158381A; JPH0229797B2; JPS57501037A; EP0043119A1; DE3165680D1; CS231986B2; FI70988C

Abstract

Un cylindre de compression, dont la flexion est reglable, comporte un manteau (21, 22), en rotation autour d'une travee (27) fixe, et qui repose sur un support d'entretoise (24) par l'intermediaire de paliers a balancier (23). La travee (27) repose egalement sur le support d'entretoise (24) au moyen d'un manchon spherique (8). Le cylindre de compression forme, en association avec un contre-cylindre (17), une zone de compression BL. Dans cette zone, est prevu, entre la travee (27) et le manteau (21), un dispositif principal de soutien (18) qui transfere les forces de soutien de la travee au manteau. La distance LE du manteau (21, 22) est egale a celle du contre-cylindre (17). En consequence on assure une bonne mise en place dans la fente entre les deux cylindres (17 et 21). Le palier a balancier (23) et le manchon spherique (8) sont disposes concentriquement a une piece en porte a faux (24a) du support d'entretoise (24). A l'exterieur de la zone de compression BL, des dispositifs de soutien supplementaires (15 et/ou 16) peuvent etre prevus. Avec ces dispositifs supplementaires, on peut, selon les besoins, imposer au manteau (21, 22) une deformation supplementaire.A compression cylinder, the flexion of which is adjustable, comprises a mantle (21, 22), rotating around a fixed span (27), and which rests on a spacer support (24) by means of bearings with balance (23). The trap (27) also rests on the spacer support (24) by means of a spherical sleeve (8). The compression cylinder forms, in association with a counter-cylinder (17), a compression zone BL. In this zone, there is provided, between the trap (27) and the mantle (21), a main support device (18) which transfers the supporting forces from the trap to the mantle. The distance LE of the mantle (21, 22) is equal to that of the counter-cylinder (17). Consequently, proper positioning is ensured in the slot between the two cylinders (17 and 21). The pendulum bearing (23) and the spherical sleeve (8) are arranged concentrically with a cantilevered part (24a) of the spacer support (24). Outside the BL compression zone, additional support devices (15 and / or 16) can be provided. With these additional devices, it is possible, as required, to impose an additional deformation on the mantle (21, 22).

Description

Press roll, the deflection of which is adjustable

Technical field

The invention relates to a press roll, the deflection of which is adjustable, in particular for the paper industry. a hollow Waizenmantei, which is rotatable about a fixed bending beam (yoke) and which can form with a counter roll a press nip through which a web passes, the axis of rotation of the two rolls and the press nip lying in a press plane, further with the following features: a) the Waizenmantei is supported at both ends by a pendulum bearing at least indirectly against the yoke; b) in the area of the press nip there is a hydraulic support device in the roll jacket which transfers support forces from the yoke to the Waizenmantei in the press plane; c) the yoke rests on its two ends, each with a support surface, directly on two support stands; d) Seen in longitudinal section, the distance between the central planes of the supporting surfaces of the yoke perpendicular to the axis of rotation of the yoke is at most slightly greater than (preferably the same as) the distance between the bearings of the counter-roller. State of the art

Press rolls of the aforementioned type and press rolls of a similar design are known from the following publications:

1. Magazine "Das Papier" 1980, No. 5, pages 165-171,

2. DE-AS 2407510,

3. US Patent 3119324,

4. DE-OS 2503051,

5. US-PS 3276102,

6. DE-AS 2418431,

7. US Patent 3766620,

8. DE-AS 2826316.

Be the press rolls, which are known from documents 1 and: 2, the roll shell of the press roll is about the same length as the roll shell of the counter roll. The roller shell is supported directly on the yoke at both ends by means of a self-aligning bearing. As a result, viewed in longitudinal section, the distance between the center planes of the self-aligning bearings (perpendicular to the roll axis of rotation) is considerably smaller than the distance between the center planes of the bearings of the counter-roll.

The known press roller according to document 1 (in particular page 169, Fig. 1) is a so-called "floating roller". There, the hydraulic support device is designed as a semi-ring-shaped pressure chamber located between the yoke and the roll shell, which extends essentially over the entire length of the roll shell. In contrast, the press roll known from document 2 has a certain number of hydrostatic pressure shoes, which are distributed along the press nip over the length of the Waizenmanteis.

Such press rolls are used, for example, in the wet part of paper machines (as dewatering presses) or for smoothing the dried paper, for example in calenders. Especially in the last named The application requires an extremely precise fit between the press roll and the counter roll so that the thickness of the paper becomes uniform over the width of the paper web. This is intended to ensure that a roll is formed when the paper web is rolled up, the shape of which is as cylindrical as possible. If the fit between the rollers is inaccurate, then when the paper web is rolled up, non-uniform windings arise which are difficult to process further and lead to rejects.

When treating a paper web in such a roller press, it may also be desirable to exert different pressing forces on the edge regions of the paper web on the one hand and on the central region on the other hand. This is an attempt to eliminate irregularities in the paper thickness that may have been caused to other parts of the paper machine (examples: uneven basis weight across the width of the paper web, caused in the wet part of the paper machine; or uneven moisture of a felt; or uneven dryness across the width of the paper web in front of a smoothing unit). Known roll presses, which have a press roll with adjustable deflection and a solid counter roll, have the disadvantage that the desired uniformity of the thickness of the material web treated can often not yet be achieved. There are always deviations, which can vary in size depending on the level of the pressing force and which are apparently based on the fact that the distance between the bearings in the counter roll is greater than in the roll shell of the press roll.

The disadvantage described above is inherent in all known types, regardless of whether it is a "floating roller" (publication 1, page 169, Fig. 1) or a press roller according to publication 2.

It is known from document 1, with the help of a correction chamber and with the help of so-called ring elements, the interior of which is depressurized to reduce the previously observed irregularities in the web thickness. However, the design of the roller presses has remained basically unchanged. As a result, it has not been possible to completely eliminate the cause of the irregularities there.

From the publications 3 and 4 press rolls are known, the roll shell has extensions at both ends, on which the bearings for the roll shell are arranged. As a result, the distance between the Waizenmanteilager is greater than in the constructions according to documents 1 and 2. However, there the length of the yoke has been increased accordingly. In particular, the distance between the center planes of the support surfaces of the yoke is greater than in the constructions according to documents 1 and 2, in any case considerably greater than the distance between the bearings of the counter roller. This has various disadvantages: On the one hand, 8iegemomeπte occur in the machine frames that support the press roll and the counter roll. It is particularly serious that the bending moment in the middle of the yoke becomes significantly higher than before, so that the yoke diameter must be increased if the same supporting forces as before are to be transferred from the yoke to the roll shell. This makes the entire press roll larger, heavier and more expensive.

Another press roll with an extended roll jacket is known from that directly on publication 5, FIG. 9. There the yoke does not rest / support stands, but by means of additional roller bearings on the inside of the roll jacket. However, this forces you to considerably enlarge the bearings for the roll shell; because these now have to transmit both the support forces for the roll shell and the support forces for the yoke to the support stands and the machine frame.

Object of the invention

The invention is based on the object of designing a press roll whose deflection is adjustable in such a way that when pressed against the counter roll it can form a faultless fit with the latter, without the distance between the support surfaces of the yoke being appreciably greater than the distance between the bearings of the counter roll. In addition, the possibility should be created that devices for applying an arbitrary additional deflection of the ends of the roll shell can be accommodated in the press roll without increasing their main dimensions. Finally, it should be possible to equip the press roll according to the invention with a simple drive device if required.

The solution according to the invention

The above object is achieved according to the invention by a press roll with the features of claim 1. It is important here that the support brackets have cantilevers which extend into the interior of the roll shell, and that the support surfaces for the yoke are provided on these cantilevers. The inventors have recognized that this arrangement is the crucial prerequisite for making the distance between the self-aligning bearings of the roll shell equal (or at least approximately the same) to the distance between the bearings of the counter roll without the distance between the support surfaces for the yoke must be increased or without having to forego the support of the yoke directly on the support frames. According to the invention, the supporting surfaces for the yoke and the spherical bearings for the roller jacket are “nested” in one another, however, in a different way than is known from document 5 and without the above-mentioned disadvantages of that known construction occurring Self-aligning bearings are used for the Waizenmantei, whose dimensions remain within the usual limits.

Compared to the press rolls known from documents 1 and 2, the Waizenmantei has a greater length, so that, if necessary, additional hydraulic support devices can be provided at the ends of the Waizenmantei. This is explained in more detail below. Furthermore the construction according to the invention provides the prerequisite for a simple, yet kinematically perfect gear drive for the roller shell. This is also described in detail below.

The most important advantage of the invention is that the distance between the self-aligning bearings of the roll shell can be made approximately the same as the distance between the bearings of the counter roll without the total length of the press roll (in particular on the yoke) having to be increased, and in this way when pressing the press roll against the counter roll, a perfect fit between the two rolls can be achieved.

The publication β mentioned at the beginning shows a design which fundamentally differs from the press roll according to the invention. There the yoke does not rest in a support frame, but over bell-shaped end parts and by means of additional roller bearings on the ends of the Waizenmanteis. Thus, the supporting forces supporting the yoke must be transmitted to a frame, support stands or the like via the aforementioned parts and via the spindle bearings of the roll shell. However, the pendulum! Ager must also transmit the supporting forces that carry the waizen mantle. This known construction, like the press roll according to document 5, has the disadvantage that not only is the number of rolling bearings larger, but also that the self-aligning bearings of the roll shell have to be dimensioned more strongly. In addition, there is a disadvantage that the supporting forces that support the yoke and act on the ends of the roll shell have an extremely disruptive effect if one wishes to generate a specific bending line of the Waizenmanteis with the aid of the hydraulic support device. In other words, it is impossible to achieve a precise fit between the waizenmantei and the counter roller.

Embodiments of the invention

Because the yoke bends during operation of the press roll, the support surfaces for the yoke are preferably spherical, as is known per se. In addition, the construction is generally like this choose that the yoke is coaxial to the roll shell when the press roll is not loaded. In this case, the spherical support surface for the yoke and the self-aligning bearing of the roll shell have the same center point at each roll end. In other words, the two centers coincide. However, one can also deviate from this as follows: The center of the spherical support surface for the yoke can be offset from the center of the roller-shell self-aligning bearing, in the radial direction towards the counter-roller. This allows a greater deflection of the yoke - with otherwise the same dimensions.

In both cases, there is a significant advantage in that - seen in a longitudinal section - the supporting forces introduced by the yoke and by the roller jacket into the support frame lie in the same line of action at each roller end. If you also arrange the center of the support surface of the support frame on the machine frame in this line of action, then there is no bending moment between the support frame and the machine frame.

Another embodiment of the invention is set out in claim 3. In other words, this means that the distance between the two support surfaces of the yoke is smaller than the distance between the roll-shell pending bearings. Certain bending moments have to be accepted. However, advantages are achieved in other respects: On the one hand, this reduces the deflection of the yoke (provided the same yoke diameter and the same load). Due to the lower deflection of the yoke, the inside width of the roll shell and thus also its outside diameter can be reduced. On the other hand, the tension in the yoke also decreases under constant load. This makes it possible to switch to less high-strength materials for the yoke, or one can reduce the yoke diameter, which in turn provides a possibility of reducing the roller diameter, In any case, the manufacturing costs of the press roll can be reduced by the measure mentioned.

Further advantageous embodiments of the press roll according to the invention are specified in claims 4 to β.

A particularly important further idea of the invention is concerned with the design of a gear drive for the Waizenmantei. The essential features of this drive are given in claims 7 and 8. In other words, claim 7 states: seen in a longitudinal section through the press roll, an external ring gear is arranged such that its center plane perpendicular to the roll axis of rotation coincides at least approximately with the center plane of the roll shell self-aligning bearing. From the aforementioned document 7, a drive device for a press roll is known, which differs in essential details from the construction according to the invention. An external ring gear is also provided there on the roller jacket, with which a pendulum-adjustable drive pinion can be used. However, the outer ring gear is offset in the axial direction with respect to the roller jacket PendeHager. The consequence of this is that the tooth force generates a bending moment in the roll shell. Another difference is the bearing of the drive pinion. This is rigidly mounted in a gear housing separate from the support frame. The gearbox itself is mounted with hooves on an additional roller bearing inside the roll shell. As a result, the gear housing, together with the drive pinion, follows a possible inclination of the Waizenmanteis when it bends. A disadvantage of this known construction is that in addition to the support frame in which the yoke rests, an additional gear housing and an additional bearing are required. In addition, because of the drive, the yoke must be lengthened, and the support bracket supporting the yoke must be set further outwards compared to a roller that has no drive. This results in further disadvantages; in particular, the deflection of the yoke increases if its cross-sectional dimensions and the load remain unchanged. Another idea of the invention relates to measures by means of which the ends of the roll shell can be bent arbitrarily, if necessary, deviating from the normal bending line. For this purpose, additional hydraulic support devices are provided according to claims 9 to 16 in the end regions of the roll shell between the roller shell self-aligning bearings and the previously existing hydraulic support device (hereinafter referred to as "main support device"). The roller shell self-aligning bearings play a major role because they hold the shell ends so that they cannot avoid them. Corresponding pressure distribution in the additional support devices, which can be arranged to act in or against the pressure device, enables the following deformations of the bending line:

1. The additional support devices are not loaded. The waizen coat bends according to the normal sealing line. However, by changing the pressure in the main support device, pressing can be carried out either exactly or even more in the center or at the edges.

2. The additional support device is allowed to act counter to the pressing device and the pressure in the main support device is increased slightly. Result: equal pressure over a wide central area, higher pressure at the edges. If you increase the pressure in the main support device even further, you get a flat pressure profile in the edge areas and a pressure peak in the middle.

3. The additional support devices are allowed to act in the pressing device and the pressure in the main support device is reduced a little. Result: Pressing of the same size over a wide central area, pressing at the edges reduced. If you reduce the pressure in the main support device even further, you get a flat pressure profile in the edge areas and a reduced pressure in the middle. If necessary, the adjustment of the additional support devices can take place at the two roller ends to different degrees. In addition, the main support device can be divided into several, individually adjustable sections.

Compared to conventional press rolls with adjustable deflection, stronger roll deflection with lower forces is possible according to the invention. Because by increasing the distance between the self-aligning bearings of the roller shell, ^x αie effective lever arms for generating the bending moments have become considerably larger. The load on the self-aligning bearings is reduced by this enlargement of the lever arm. However, the use of additional hydraulic support devices is in principle also possible if the distance between the roller-shell self-aligning bearings is somewhat smaller than the distance between the bearings of the counter-roller (claim 17). The distance between the yoke support surfaces can be slightly larger than the LE of the counter roll. Refinements of the hydraulic support devices: The main support device in the central area can either be designed in the form of a large number of hydrostatic pressure shoes, or (in the manner of the “floating roller” mentioned at the beginning) as a continuous semi-annular pressure chamber which is filled with low-pressure oil and by means of elastic longitudinal and Circumferential sealing strips is limited. The latter embodiment has the advantage that the yoke is not weakened by bores for receiving the hydrostatic pressure shoes and can therefore be smaller in diameter, as a result of which the jacket of the roller and its weight and the manufacturing costs are reduced.

Regardless of the design of the main support device, the additional support devices can also be designed either as hydrostatic pressure shoes or as semi-annular pressure chambers.

Exemplary embodiments of the invention are explained in more detail below with reference to the drawings with FIGS. 1 to 4. Each of the four figures shows a partial section through one of the two ends of a press roll and schematically the associated part of the counter roll. x) also the distances between the self-aligning bearings and the additional support devices and thus Figure 1 shows an embodiment without drive, in which the self-aligning bearing for the roll shell is arranged outside the same;

FIG. 2 shows another embodiment, likewise without a drive, in which the self-aligning bearing for the roller shell is arranged inside it;

Figure 3 shows a development of the embodiment of Figure 2 with drive;

FIG. 4 shows a further modification of the embodiment from FIG. 2.

Each roller has a floating bearing at one end, e.g. shown in Figures 1 and 2 and at the other end a fixed bearing, corresponding to Fig. 3. At the fixed bearing end, both the yoke 57 and the roller shell 51, 52, 47 are axially fixed against the frame 60, while an axial displacement at the end of the floating bearing of yoke 7; 27 and Waizenmanteis 1,2; 21, 22 can take place relative to the frame 10. Except for the means for axial fixing, the bearing on the fixed bearing side does not differ from that on the floating bearing side.

According to Figure 1, the rotatable roller jacket 1 has an extension in the form of a flanged bearing sleeve 2. This is connected via the self-aligning bearing 3 to the support bracket 4, which also serves as a bearing housing. Its interior is sealed to the outside by a cover 5 with a lip seal 6. The support bracket 4 has a tubular cantilever 4 a, which extends into the interior of the bearing sleeve 2. The yoke 7 rests in an articulated manner in the cantilever 4a of the support frame 4 with the aid of a spherical bush 8 which has a support surface 8a. A lip seal 9 seals the gap between the yoke 7 and support frame 4 to the outside. The support frame 4 is fastened on a movable bearing lever or on a frame 10. Between the casing 1 and the yoke 7, a semi-annular pressure chamber 11 is formed, which is delimited by circumferential seals 12 and by longitudinal sealing strips 13 lying opposite one another. This pressure chamber 11 can be supplied with pressure oil via a channel 14. As a result, a supporting force is applied to the jacket 1, specifically in the direction of the counter-roller 17. The length of the pressure chamber 11 (main support device) is only slightly less than the length BL of the press zone. Additional support devices in the form of hydrostatic pressure shoes 15 and 16 are provided in the two 8ereicheπ of the roll shell 1 located outside the press zone 8L. Their axes are in the press plane (which coincides with the drawing plane). They can be activated by supplying oil pressure via lines 15a and 16a. One pressure shoe 15 acts in the direction of the counter roll 17, the other opposite. As a result, an additional, targeted bending can be forced onto the ends of the Waizenmanteis 1 if necessary. Instead of the hydrostatic pressure shoes 15 and 16, semi-ring-shaped additional pressure chambers can also be provided, similar to the main pressure chamber 11.

M denotes the central plane of the bearing 20 of the counter-roller, which is perpendicular to the roll axis of rotation. The distance from this center plane to the center plane of the bearing located at the other end of the roller is the so-called bearing distance LE. The central planes of the bearing 20 and the self-aligning bearing 3 coincide at both roller ends; i.e. the storage distances are the same. The "bearing distance" of the support surfaces 8a of the yoke 7 also has the same size.

In FIG. 2, a bearing sleeve 22 is in turn flanged to a rotating roller jacket 21, which is articulated on the support bracket 24 via a pendulum roller bearing 23. Now, however, the spherical roller bearing 23 is arranged in the interior of the bearing sleeve 22; it rests with its inner ring on the cantilever 24a of the support bracket 24. A bearing cover 25 with a lip seal 26 closes off the oil space of the bearing 23 from the outside. As in FIG. 1, the yoke 27 is supported on the support bracket 24 via the spherical ring 8. In the yoke 27 there are now haydrostatic pressure shoes 18, also called “support pistons” seen that support the Waizenmantei 21 from the inside. The press roll has a plurality of such pressure shoes 18, which are lined up in the press level (main support device). Additional hydrostatic pressure shoes 15 and / or 16, which are in turn arranged outside of the pressing zone BL, can be pressurized in such a way that a corrugated bending of the roller jacket 21 is forced.

FIG. 3 shows an exemplary embodiment with a drive device and with a semi-ring-shaped pressure chamber 11 (corresponding to FIG. 1) but without an additional support device. However, one could also provide such an additional support device if necessary. A bearing sleeve 52 and a toothed ring 47 are screwed to the roller shell 51. The roller jacket extended in this way is again mounted with a pendulum roller bearing 53 on the cantilever 54a of the support bracket 54. The yoke 57 is again connected in an articulated manner to the cantilever 54a via the ball sleeve 8. A lip seal 59 seals the gap between the support bracket 54 and a sleeve 60 pushed onto the yoke 57. A spring ring 61 holds the ball sleeve 8 axially via the sleeve 60 (fixed bearing). The support bracket 54 is attached to a pressure lever, pressure piston or frame 10. The bearing 53 is secured via a support ring 62 and a spring ring 63 against axial displacement relative to the support bracket 54. On the other hand, the ring gear 47 is secured against displacement 53 via the support ring 64 and spring ring 65 relative to the bearing 53 (fixed bearing).

A nose 26, which is attached to the support bracket 54, projects into a groove 67 of the yoke 57 and secures it against rotation. Such an anti-rotation device is omitted in FIGS. 1 and 2.

A drive shaft 68 with key 69 is driven via a drive shaft, not shown. The drive shaft 68 is mounted in a spherical bearing 30 and sealed with a lip seal 31 in a cover 32. The bearing 30 and the cover 32 rest in a bearing plate 30 a which is screwed onto the section block 54. The shaft 68 exaggerates an angularly adjustable tooth coupling 33 to a drive pinion 34 which meshes with the ring gear 47. A spherical bearing 35 is provided in the center of the drive pinion 34. With this it can be swiveled. mounted on a retaining bolt 36 which is rigidly attached to the support bracket 54 by means of a molded collar 37 and a screw 38. If, during operation of the press roll, the roll shell 51 bends and the ring gear 47 tilts accordingly, the pinion 34 can adapt to this inclination without difficulty.

The bearing 35 is held axially on the one hand by a spring ring 39 in the pinion 34, and on the other hand by a retaining ring 40 and a spring ring 41 on the retaining bolt 36. The support bracket 54 is also a gear housing for the gears 34 and 47. In the area of the bearing sleeve 52 is the interior of the gear housing 54 is sealed to the outside by means of cover 55 and lip seal 56.

A counter roll and its mounting are arranged in the same way as in FIG. 2, but are not visible in FIG. 3.

In FIG. 4, all of the components that have not changed from the embodiment of FIG. 2 are provided with the same reference numerals as there. The only difference is that the cantilever 24b is extended by the dimension e into the inside of the roll shell 21,22, and accordingly the yoke 27 can be made shorter.

Claims

1. Press roll, the deflection of which is adjustable, in particular for the paper industry, with a hollow roll shell (1) which can be rotated about a fixed bending beam (yoke 7) and which can form a press nip with a counter roll (17) , wherein the axes of rotation of the two rolls and the press nip lie in a press plane, further with the following features:

a) the Waizenmantei (1) is supported at both ends by a self-aligning bearing (3) at least indirectly against the yoke (7); b) inside the roll shell (1) there is a hydraulic support device (11) which transfers support forces from the yoke (7) to the roll shell (1) in the pressing plane; c) the yoke (7) rests on its two ends, each with a support surface (8a) on two support stands (4); d) Seen in longitudinal section, the distance between the center planes (m) of the support flats (8a) of the yoke (7), which are perpendicular to the roll axis of rotation, is at most slightly greater than (preferably the same as) the distance (LE) between the bearings (20) Counter roll (17);

characterized, e) that the distance between the pendulum bearings (3) of the roller shell (1) is at least approximately equal to the distance (LE) between the bearings (20) of the counter-roller (17) and f) that the support surface (8a) is at each roller end for the yoke (7) is located on a cantilever piece (4a) which extends from the support frame (4) into the interior of the roll shell (1).

2. Press roll according to claim 1, wherein the yoke (7) has spherical support surfaces (8a), characterized in that the spherical support surface (8a) and the self-aligning bearing (3) of the Waizenmanteis (1) have at least approximately the same center at each Walzeneπde.

3. Press roll according to claim 1, characterized in that the distance between the center planes (m) of the two support surfaces (8a) of the yoke (27 ') is smaller than the distance (LE) between the bearings of the counter roll (Fig.4).

4. Press roll according to one of claims 1 to 3, characterized in that the cantilever (4a; 24a) belonging to the support bracket (4; 24) is tubular and between the waizenmantei (1, 2; 21,22) and the yoke (7th ); 27) protrudes.

5. Press roll according to one of claims 1 to 3, characterized in that the self-aligning bearings (3), as known per se, are arranged between the outside of the Waizenmanteis (1, 2) and the support blocks (4) designed as a bearing housing (Figure 1 ).

6. Press roll according to claim 4, wherein the self-aligning bearings (23; 53) are arranged in the interior of the roll shell (21, 22; 51, 52, 47), characterized in that the collar (24a; 54a) on its outside the self-aligning bearing ( 23; 53) and on its inside carries the yoke (27; 57) (Figure 2 or 3).

7. Press roll according to claim 6, characterized in that the roller jacket (51, 52, 47) in the region of one of the two self-aligning bearings (53) has an external ring gear (47) with which a pendulum-mounted drive pinion (34) meshes.

8. Press roll according to claim 7, characterized in that the drive pinion (34) is mounted on a single inside its arranged self-aligning bearing (35) which in turn rests on a support bolt (36) rigidly fastened to the support bracket (54), and that Drive pinion (34) is connected to a drive element (shaft 68) by means of an articulated coupling (33).

9. Press roll according to one of claims 1 to 8, characterized in that at each end of the roll shell (1; 21) between the hydraulic support device (11; 18) and the pendeu bearing (3; 23) and between the yoke (7; 27 ) and the Waizenmantei (1; 21) at least one additional hydraulic support device (15 and / or 16) is present, which can be acted upon by pressure medium independently of the first-mentioned support device (11; 18) (Fig. 1 or 2).

10. Press roll according to claim 9, characterized in that the additional hydraulic support devices are hydrostatic pressure shoes (15, 16).

11. Press roller according to claim 9, characterized in that the additional hydraulic support devices are semi-annular pressure chambers which are located between the yoke and the Waizenmantel and which are limited by symmetrical to the press plane longitudinal seals and by order to start seals.

12. Press roll according to one of claims 9 to 11, characterized in that an additional support device (15, 16) arranged on one roll end can be pressurized independently of an additional support device arranged on the other roll end.

13. Press roll according to one of claims 9 to 12, characterized in that the support forces generated by the additional support devices (15) are directed towards the counter roll (17).

14. Press roll according to one of claims 9 to 12, characterized in that the supporting forces generated by the additional support devices (16) are directed away from the counter roll (17).

15. Press roll according to one of claims 9 to 12, characterized in that at each roll end two additional support devices (15 and 16) are provided, the effective directions lying in the press plane are opposite to each other.

16. Press roll according to one of claims 9 to 15, characterized in that the additional hydraulic support devices (15, 16) - seen in longitudinal section - are essentially outside the press zone (BL).

17. Press roll, the deflection of which is adjustable, in particular for the paper industry, with a hollow roll shell which is rotatable about a fixed bending support (yoke) and which can form a press nip with a counter roll, the axes of rotation of the two rolls and the press nip lie in a press plane, further with the following features:

a) the roll shell is supported at both ends at least indirectly against the yoke by a self-aligning bearing; b) inside the roll shell there is a hydraulic support device which transfers support forces from the yoke to the roll shell in the press plane;

c) the yoke rests on its two ends, each with a support surface on two support stands;

characterized in that at each end of the roll shell between the hydraulic support device and the self-aligning bearing and between the Jpch and the roll shell there is at least one additional hydraulic support device which can be pressurized with pressure medium independently of the first-mentioned support device.