DE3024575C2 - Press roll with adjustable deflection - Google Patents

Description

a) da3 is the distance between the bearing centers of the self-aligning bearings (3) of the roll shell (1, 2) is at least approximately equal to the distance between the bearing centers of the counter roll and

b) that at each end of the roll the yoke bearing (8) is located on a cantilever that is from Support frame (4) in the interior of the roll shell (1, 2), namely in the radial area within the self-aligning bearing (3).

2. Preß'valze according to claim 1, wherein the self-adjusting bearing (4) of the yoke (7) spherical Have support surfaces, characterized in that the spherical Support surface of the yoke bearing (4, and the self-aligning bearing (3) of the roll shell (1,2) at least approximated have the same center.

3. Press roll according to claim 1 or 2, characterized in that the support frame (4) belonging cantilever is tubular and protrudes between the roll shell (1,2) and the yoke (/) to

4. Press roll according to one of claims 1 to 3, characterized in that the self-aligning bearings (3), as known per se, are arranged on the outside of the Waizenmaiiteis (i, 2) and in the support frames (4) designed as a bearing housing * ' ■ (Fig. 1).

5. Press roll according to claim 3, the wonn Self-aligning bearings (3) are arranged in the interior of the roll shell (1,2), characterized in that the tubular cantilever on its outside the> o Self-aligning bearing (3) and the yoke (7) on its inside (Fig. 2 or 3).

6. Press roll according to claims 1 to 5, characterized in that in the areas between the Pendeiiagern (3) and del FicuZuüc v "/ z" ü3aiZi; c> iC pressure elements (15 and / or 16) between the yoke (7) and roll shell (1) are present, with their Help an arbitrary additional bending of the rollers compared to those in the edge area of the press zone (19) the mid-range can be effected.

7. Press roll according to claim 6, characterized in that the additional pressure elements (15 and / or 16) are hydrostatic support shoes.

8. Press roll according to one of claims 1 to 7, wherein the self-aligning bearings (3) in the interior of the roll shell (I, 2, 17) are arranged, characterized in that the roll shell (1,2,17) in the Area of one of the two self-aligning bearings (3) has an outer toothed ring (17) with which a pendulum adjustable drive pinion (34) meshes

9. press roll according to claim 8, characterized in that the drive pinion (34) on one single self-aligning bearing (35) arranged in the interior of the drive pinion, which in turn is mounted on a support bolt (36) attached to the support frame rests and that the drive pinion (34) ment by means of an articulated coupling (33) with a AntriebseU (Shaft 28) is connected

The invention relates to a press roll according to the preamble of claim 1. It is based on the device known from DE-OS 24 07 510. Its essential parts are a hollow ^{roll shell, the r of which is supported} at both ends on a self-aligning bearing and can be rotated around a fixed yoke. The yoke rests on two support frames at both ends via self-adjusting bearings. The distance between the bearing centers of the yoke bearings is approximately equal to the distance between the bearing centers of a counter roll. The roll shell is supported by the yoke to such an extent by means of a hydraulic support device that it does not bend under the line force or adapts to the bend of the counter roll. Cardboard web or the like), even with variable line forces and also without bulging the co-operating rolls. In some cases it must be possible to drive the roll shell by a motor.

Such roll presses are both in the wet end of paper machines used (wet pressing}, and (for the smoothing of the dried paper machine calenders, calender). Particularly in the latter Fa * ¹ is an extremely precise fit between the rolls required for the paper thickness uniform over the web width and a cylindrical roll is formed when it is rolled up

If the fit between the Wabpn is imprecise, then When the roll is rolled up, the result is wavy lap, which is difficult to process and becomes scrap to lead. Both in wet presses and in calendering units, the edge areas may be desirable Consciously press the paper web with different intensities in relation to the central area in order to avoid irregularities to compensate for other origins (e.g. uneven basis weight distribution, unequal felt moisture, unequal dryness in front of the glazing unit )

etc.).
Bc:

the known device (r> F-O <; 74 07 510)

Bc: the known device ()

a certain number of hydrostatic pressure shoes are provided as hydraulic support equipment, which are distributed along the press nip over the length of the roll shell. With another well-known Press roll (magazine "Das Papier", issue 4, 1980, pages 125-129, Fig. 1) is the hydraulic support device 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. The two constructions agree that the roll shell of the press roll is about the same length as the roll body of the The counter roll is also the roll shell

The press roll is mounted directly on the yoke at both ends with the aid of the self-aligning bearings mentioned. As a result, in the longitudinal section, the distance between the bearing centers of the self-aligning bearings is considerably greater than the distance between the bearing centers of the Gefenwaize. In roller presses of this type, uniform calibration of the paper web gap is usually not possible. A systematic error of different magnitude, depending on the line pressure, arises, ie there are always deviations that can vary in magnitude depending on the magnitude of the pressing force. Apparently these deviations are caused by the mentioned fact that the distance between the l. '' Cut of the counter roll is greater than .up En ** ~ "-nupg between the bearing slides of the self-aligning bearings of the va! Zen jacket.

It has already been forgotten; "The paper," Issue 5, 1980, pages 165-Hi), with help who correction chamber and rpit r., Fe of so-called • Ring elements, the interior of which is pressureless, previously to reduce observed non-uniformities in the web thickness. However, the design is the Press roll remained unchanged in principle. As a result, it was not possible to find the cause of the irregularities to be eliminated from scratch.

In order to achieve this, it could be thought of according to a further known construction (US-PS 3119 324) the distance between the bearing centers of the self-aligning bearings of the roll shell to increase the extent of the bearing distance of the counter roll. Realizing this thought comes across however, difficulties arise because the length of the yoke would also have to be increased; d. H. the distance between the bearing centers of the yoke bearings would no longer change with the bearing distance of the counter roller to match. This would result in an inadmissibly high level of bending in the frame. aside from that if the bending moment in the center of the yoke would be greater than before, the yoke diameter would be proportional to Distance between the yoke bearings would have to be increased, provided the line pressure remained the same. This would make the entire press roll larger, heavier and more expensive

Also with the subject Jer DE-AS 24 Io 431 is the Distance between the bearing centers of the self-aligning bearings of the Walzenlsgers approximately equal to the distance between the Bearing center of the counter roll. There, however, the yoke does not rest in a support frame, machine frame or like, but over bell-shaped end parts and by means of additional roller bearings on the ends of the Roll shell. Thus, the supporting forces bearing the yoke over the aforementioned parts and over the Self-aligning bearings of the roll shell are transferred to the machine frame. Since the self-aligning bearings too the Siüizkiäiic üöcinagen carrying the roll shell must, it is necessary to dimension the self-aligning bearings larger than the other known ones Constructions. Another major disadvantage is that the yoke supporting and to the Supporting forces acting on the ends of the roll shell are extremely disruptive when using the hydraulic support device wants to generate a certain bending line of the roll shell.

Another attempted solution is known from 'F i g. 9 the US-PS 32 76102. This construction has the Disadvantage that the yoke rests with the help of roller bearings on the inside of the roll shell. So are there additional rolling bearings required. Furthermore must in turn, the bearing carrying the roll shell are dimensioned much larger because they both the support forces for the roll shell and

- The supporting forces on the door must be transmitted by the yoke.

The invention is based on the task, a To make press roll according to the preamble of claim 1 such that they beini pressing against a Counter roll of conventional design (suction roll or

μ solid roller) together with this a faultless Can form a fit without the distance between the bearing centers of the yoke bearings to any significant degree greater than the bearing center distance of the counter roll At the same time, a soil should be added to the press roll if required

ij great potential for arbitrary additional deflection the roll ends can be accommodated without affecting the main dimensions of the press roll to enlarge. In addition, uie press roll -o can be designed to be easy to use when needed

2i) with a kinematically perfect gear drive can be equipped for the roll shell.

This object is achieved according to the invention by a Press roll with the features of claim 1 solved. It is essential here that despite an extension

3t tion of the roll shell (compared with the known Constructions according to DE-OS 24 07 510 or "Das Papier") the distance between the bearing centers of the The yoke bearing remains unchanged

ji> inside of the roll jacket extend into the Area radially inside the self-aligning bearing of the roll shell. According to the invention, the Yoke bearings and the self-aligning bearings for the roll shell are »nested«, with not only the yoke.

but also the roll shell is supported directly in the support frames. This "nesting" is possible without the support frames assuming abnormally large dimensions.

It is also essential that the distance between the bearing centers of the pendulum bearings of the roll shell at least approximately equal to the bearing center distance the counter-roll is: because through this one can When the press roll is pressed against the counter roll, there is a perfect fit between the two rolls reach.

Since the bearing center distances on the yoke, a.n. Roll shell and ^ n of the counter roll essentially are the same and there is also the attachment of the support bracket to the machine frame at the same bearing distance occurs, victory moments in the machine frame can be entirely or at least largely avoided will.

Pie claims 2 to 5 refer to advantageous embodiments of the invention.

The construction of the ei finuungsgciiiducii ric? Wai / -c iidt ucii wciic: cii Vui zug specified in claim 1. that in the areas between the self-aligning bearings of the roll shell and the press zone (i.e. outside the press zone) nunmt.ir the necessary space for Vci Tügung stands for additional pressure elements. With their help, an arbitrary additional bending of the roller ends in the edge area of the press zone relative to the central area can be brought about, if necessary.

The self-aligning bearings of the roll shell play a major role here, because they hold the shell ends tight that this does not evade! can. Through appropriate pressure distribution in the additional pressure elements, which act in or against the pressing direction

can be arranged, the following deformations of the bending line are possible:

1. Without additional elements: Normaie bending line, by changing the force of the pressure elements in the area of the pressing zone, pressing can be done evenly or more strongly in the middle or more strongly at the edges.

2. Additional elements work against the pressing direction. The force of the pressure retardant in the press zone is slightly increased: the same amount of pressure over one wide central area, higher pressure on the edges.

3. As 2, but higher forces in the middle area: Flat pressure profile in the edge areas. Pressure f; point in the middle.

4. Additional elements act in the pressure direction, force in the pressure elements in the central area slightly reduced: equal pressure over a wide mistletoe area. Pressing on the edges reduced

5. As 4, but lower force in the middle area: flat pressure profile in the edge areas, reduced Print in the middle.

25th

The setting of the additional elements on the driver and drive side can of course also be made to different degrees. The pressure elements that lie within the Prelizone can be divided into several, individually adjustable sections ^r -ein, corresponding to the i (r from DE-OS 23 25 721 known press roll.

Compared to conventional press rolls with adjustable deflection, there is a stronger roll shell deflection possible with lower forces, because by increasing the bearing distance of the Self-aligning bearings of the roll shell are the more effective lever arms for generating the Bkgemomente considerably got bigger. The load on the roller shell bearings is also reduced by this increase in the Leverage reduced

According to claim 7 it is provided that the additional pressure elements are designed as pendulum adjustable hydrostatic support shoes. The pressure elements, which are located within the press zone, can either also be designed as hydrostatic support shoes , or as a continuous plenum, which is filled with low-pressure oil and sealed by elastic sealing strips . "is weakened and can therefore be smaller in diameter, whereby the jacket of the roller and its weight and the manufacturing costs are reduced.

· Claims 8 and 9 relate to one particular simple design of the drive for the roll shell. which as a consequence of the main idea of the Invention becomes possible and leads to a compact and cheap solution and which the according to the Main idea of the invention achievable good fit in the nip with simultaneous freedom from moments in & o Frame not affected

Although from US-PS 37 66 620 a drive device known for a press roll, in which an external gear rim is also provided on the roll shell, with which a pendulum adjustable drive pinion ° 5 meshes, however, there the external gear rim is offset in the axial direction with respect to the roller shell self-aligning bearing As a result, the tooth force generates a bending moment in the roll shell. Another The difference lies in the bearing of the drive pinion. This is in a separate from the support frame Rigidly mounted gear housing «the gear housing itself is in the Stored inside the roll shell. As a result, the gear housing follows together with the drive pinion a possible inclination of the roll shell when it bends. A disadvantage of this known one Construction is. that next to detrt retainer. by doing the hole rests the said separate gear housing and the additional roller bearings are required. In addition, the yoke and the yoke bearing the yoke must be lengthened because of the drive The support frame must be set further outwards compared to a roller that does not have a drive This results in further disadvantages; in particular, the yoke increases when the yoke is poured through Cross-sectional dimensions and the load remain unchanged.

A ere drive device is known from US-PS 38 89 334. A disadvantage of this roller drive is that the drive sprocket! only indirectly via the tooth coupling located inside it and is mounted on the shaft in the transmission housing Therefore the drive pinion is not out of alignment in the axial direction, a complicated double helical toothing necessary.

Embodiments of the invention are given below explained in more detail with reference to the drawing. All three figures show a partial longitudinal section through one of the Ends of a press roll with adjustable deflection.

F i g. 1 shows an embodiment with! ^ Slager without Drive.

F i g. 2 shows another embodiment with a floating bearing, also without a drive.

F i g. 3 shows an embodiment with a fixed bearing, with a drive.

Each roller has a floating bearing at one end and a fixed bearing at the other end. At the end of the fixed camp are both the yoke and the roll shell axially fixed immovably against the frame while on Floating bearing end an axial displacement of the yoke and the roll shell relative to the frame take place can. Except for means for axial fixing, the bearing on the fixed bearing side does not differ from that one on the floating bearing side.

In Fig. 1 you can see the rotatable roll shell 1. to which the bearing sleeve 2 is flanged. This is via the self-aligning bearing 3 with the support 4 tied together. The self-aligning bearing sits with its inner ring on the outside of the bearing sleeve 2. The oil chamber of the Bearing 3 is sealed to the outside by a cover 5 with a lip seal 6. The yoke 7 is supported via a spherical sleeve 8 articulated in the support frame 4, namely in a tubular cantilever piece that is extends from the support frame into the interior of the roll shell 1,2 A lip seal 9 seals the gap between yoke 7 and support frame 4 to the outside. The support frame 4 is on a bearing lever or frame 10 attached

In a semi-cylindrical space 11 between the jacket 1 and yoke 7, which is end face by seal 12 and in the circumferential direction by two opposite Sealing strips 13 is limited, a to support the Shell 1 serving oil pressure is generated in that oil under the desired pressure through the bore 14 in the semi-cylindrical pressure chamber 11 is promoted.

Hydrostatic pistons 15 and 16 with an axis in the press plane can be arbitrarily adjusted Pressure via the supply lines 17 and ig are activated to give the jacket ends an additional bending to impose.

In Figure 2, a bearing sleeve 2 is again kneed on a rotating roll shell 1, which is mounted on the support frame 4 via a Per jellager 3. Notwithstanding FIG. 1 sits the self-aligning bearing with its outer ring inside the bearing sleeve 2 and with its inner ring on the cantilever of the Abstückbokkes 4. A bearing cover 5 with a lip seal 6 closes off the oil space of the bearing from the outside. That on The yoke 7 held in a rotationally fixed manner on the fixed bearing side is supported on the support frame 4 via the spherical ring 8. This is on attached to a frame or pressure lever 10. 5m yoke 7 are hydrostatic support pistons 18 in the area of Bearing pressure zone 19, which press against the roll shell 1 from the inside. Additional hydrostatic Support piston 15 and / or 16 outside the pressing zone 19 can be pressurized so that a intentional bending of the surface line is forced.

In Fig. 3, a roll shell 1 can be rotated via a bearing sleeve 2, a toothed ring 17 and a self-aligning bearing 3 mounted on the cantilever of the support frame 4 The oil space of the bearing housing in the support frame 4 is by means of Lid 5 and lip seal 6 sealed to the outside.

A yoke 7 is articulated to the support frame 4 via a ball sleeve 8. A lip seal 9 seals the gap between the support frame 4 and one the yoke 7 pushed onto the sleeve 20. A spring ring 21 holds the ball sleeve 8 axially via the sleeve 20 (fixed bearing). The support frame 4 is on a pressure lever, Pressure piston or frame 10 attached. A half-cylinder Oil pressure chamber 11 is not through

Oil supply channels shown are supplied with pressure oil. This space is created by sealing rings 12 and on the yoke 7 opposing dright strips 13 delimited to the outside. The self-aligning bearing 3 is supported by a support ring 22 and a spring ring 23 secured against axial displacement with respect to the support frame 4. on the other hand is the ring gear 17 via support ring 24 and spring ring 25 secured against displacement in relation to bearing 3 (fixed bearing).

A nose 26, which is attached to the support frame 4, protrudes into a groove 27 of the yoke 7 and secures this against twisting. A drive shaft 28 with feather key 29 is via a cardan shaft, not shown driven. The drive shaft 28 is mounted in a spherical bearing 30 and has a lip seal

31 sealed in the cover 32. It drives the drive belt via an angularly adjustable tooth coupling 33 34 at. which meshes with the ring gear 17. The drive pinion 34 can be swiveled on the self-aligning bearing 35 stored, which in turn sits on a retaining bolt 36, which by means of washer 37 and screw 38 on Support frame 4 is attached.

The pinion 34 is held axially on the bearing 35 by a spring ring 39. At the end of the retaining bolt 36 are a locking ring 40 and a spring ring 41 are attached to axially fix the bearing 35.

For this purpose 2 sheets of drawings

Claims (1)

30 24 57ü claims: 1. Press roll, the deflection of which is adjustable, especially for the paper industry, with a hollow roll shell (1, 2), which is supported at both ends on a self-aligning bearing (3) and rotatable about a fixed yoke (7) that is connected to its two ends rests on two support frames (4) via self-adjusting bearings (8), the distance between the bearing centers of the yoke bearings (8) being approximately equal to the distance between the bearing centers of the counter roll, and in the area of the press zone (19) a preferably hydraulic support device (11 to 14 or 18) is located, which transfers supporting forces from the yoke (7) to the roll shell (1);
characterized.