DE3024575A1 - PRESS ROLLER WITH BENDING COMPENSATION - Google Patents

Abstract

The mantle of the pressure roller with an adjustable bend, for paper manufacture, is supported at both ends by a swivel bearing at least, through the yoke (7). The hydraulic support mechanism within the roller mantle carries supporting forces from the yoke to the roller mantle. Both ends of the yoke have supporting surfaces resting on pedestals with the space between these surfaces along the vertical centre (m) being equal to or only marginally greater than the gap (I) between the bearings of the counter roller. The gap between the swivel bearings for the roller mantle is approximately equal to the space (I) between the counter roller bearings. A collar piece ranges from the pede pedestal within the roller mantle at each roller end for the yoke support surfaces. The design allows the bend to be applied at the ends of the roller, without increasing roller dimensions, so that the required pressures can be applied along the roller length. It also allows a drive to be fitted easily.

Description

Keyword: "Concentric Support I"

The invention relates to a roll press for paper machines which at least one press roll is a "floating roll", i.

it has a rotatable roller tube, which has pressure elements from a stationary core (yoke) is supported from such that it is under the Line force does not bend or adapts to the deflection of the counter roll and causes a line force distribution that is as uniform as possible across the width, too with variable line forces and also without crowning the cooperating rollers. In some cases, the rotatable roll shell must be drivable by a motor.

Such roll presses are part of paper machines both in the wet used (wet pressing), as well as for smoothing the dried paper (smoothing units, Calender). In the latter case in particular, there is an extremely precise fit between the rollers are required so that the paper thickness is the same across the width of the web and a cylindrical roll is formed when it is rolled up.

If the fit between the rollers is imprecise, then the Rolling up wavy laps, which are difficult to process and lead to scrap. Both in wet presses and in calenders, it can happen that it is desirable that the edge areas are deliberately different from the central area to press intensively in order to compensate for irregularities of other origins (unequal Basis weight distribution, uneven felt moisture, uneven dryness in front of the calender etc.).

In two-roll smoothing units, in which a massive roll with a Floating counter roll of the conventional type cooperates, a uniform calibration of the web thickness is usually not. The result is a line pressure dependent systematic error of various sizes, which is based on the fact that the bearing distance the solid roller is greater than the distance between the spherical bearings of the roller tube the floating roller (see Das Papier, Heft 4, 1980, pp 125-129).

The construction of all known floating rollers is identical to this Faulty and an attempt is made to remedy this by means of additional internal measures To compensate for errors (see Das Papier, Heft 5, 1980, pp. 165-168 and pp. 168-171). The short distance between the spherical bearings (or the scenes in the case of the free-floating hydrostatic variant) on the one hand causes the error in the fit of the both rollers and also narrows the space inside the roller tube for attachment more effective pressure elements for an additional arbitrary edge deformation, which goes beyond compensating for errors in the fit. Stuck in this dead end the development of the floating roller today, apparently because the experts has burnt into the traditional construction of floating rollers, which are attached to the outer ends of the yoke has the support frames to the frame and further inside of these, the spherical bearing or the sliding link of the roll shell.

There is often still a drive in the space between the bearing and the support so that their distance is quite considerable, e.g. in the order of magnitude from 300 to 600 mm. It would now be conceivable to adjust the nip to fit improve that one increases the distance between the spherical bearings to the extent of the Distance to the bearing of the counter roll. However, this runs into difficulties because then In the conventional design, the support frames, which the yoke on spherical surfaces would no longer match the bearing distance of the counter roll and this creates inadmissibly high bending moments in the frame. Also is through a Increase the distance between the trestles of the yoke and the bending moment in the center of the yoke larger and the yoke diameter must be enlarged proportionally to the bearing distance are with the same line pressure. However, this makes the entire roller larger, heavier and more expensive and the problem of high bending moments in the frame remains in general unsolved.

It is the object of the present invention to provide a roller press with at least one floating roller, which is normally against a conventional roller Type of construction (suction roll or solid roll) presses, creating the ones described above Does not have disadvantages and no compensation elements to produce a good one Fit required.

It is also the object of the invention when needed in this swimmer Roll has great potential for arbitrary additional deflection of the roll ends accommodate without the main dimensions (roller diameter, length, support distance, Gearbox diameter) of the roller.

Another important job is to keep it kinematically sound To represent gear drive for the roll shell in a simple way.

It is also an object of the invention to provide a float press To create a roller that is reliable with a minimum of technical control effort can be operated.

Finally, it is an object of the invention to achieve all of these goals to achieve a cost that is equal to that of presses with floating rollers conventional design does not exceed.

(1) According to the main idea of the invention, these objects can be achieved in that the jacket pipe is lengthened compared to the conventional design, so that the spherical support surfaces between the yoke and the frame are concentric within the spherical bearing of the mantle come to rest. It is amazing that one such "nesting" is possible without thereby reducing the diameter of the outer housing or the support frames assume abnormally large dimensions. About that in addition, the overall construction is not more complicated or complicated by this measure more expensive. On the contrary, there are decisive simplifications on the drive side and discounts.

(2) After a further thought, the bearing distances of the spherical bearings of the jacket adapted to the distance of the trestles, so that the Center of the spherical bearings with the center of the spherical support surfaces the yoke support collapses. This allows the support surface of the support frame take place on the frame at the same bearing distance, so that no bending moments arise between the support frame and the frame, regardless of whether the supporting force introduced into the support frame by the spherical bearing or the spherical surface will. In addition, this is the most space-saving design.

(3) Another thought provides that at both ends of the roller the frame or the support frame mounted on the frame with a tubular Cantilever from the side between the inner ring of the spherical bearing of the shell and the yoke protrudes and carries these parts.

(4) There is also provision for the removal of the two spherical ones To make bearings of the shell about the same size as the bearing distance of the counter roll.

Differences of about 1 m in the storage distances as they are today in are usually present, create a badly incorrect fit in the nip. To With the present idea it is easily possible to find out the difference between the bearing distances to be reduced to less than 30 cm or preferably to zero.

(5) Another idea provides for the end areas of the roll shell between the spherical bearings and the contact area, which depends on the circumstances corresponds to the width of the paper, the width of the felt or the length of the barrel of the roller, to attach additional pressure elements, which are suitable, the coat if necessary to bend arbitrarily in the end area deviating from the normal bending line. Included the spherical jacket bearings play a major role because they keep the jacket ends in such a way make sure that they cannot evade. Through appropriate pressure distribution in the additional pressure elements, which are arranged to act in or against the pressing direction the following deformations of the bending line are possible: 1. Without additional elements: Normal bending line, due to a change in the force of the pressure elements in the area of the press zone can be pressed evenly, more strongly in the middle or more strongly at the edges.

2. Additional elements act against the direction of pressure, force of the pressure elements slightly increased in the contact area: the same amount of pressure over a wide central area, higher pressure on the edges.

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

4. Additional elements act in the direction of pressure, force i.d. Slightly reduced in the middle area: equal pressure over a wide middle area, Pressure at the edges reduced.

5. As 4., but with less force in the middle area: even pressure profile in the edge areas, reduced pressure in the middle.

The setting of the additional elements on the driver and drive side can Of course, the pressure elements can also be made differently strong in the pressing area be divided into several, individually adjustable sections.

Compared to conventional floating rolls, there is a stronger roll shell deflection Possible with less force because of the increase in the bearing distance the spherical bearings of the roll shell are the effective lever arms for generating the Bending moments have increased considerably. Also the load on the radial bearing is reduced by this enlargement of the lever arm.

(6) Provision is also made for the additional pressure elements to be oscillating to train adjustable hydrostatic pressure shoes. The pressure elements in the middle area can either also be provided as hydrostatic pressure shoes, or but as a continuous plenum, which is filled with low-pressure oil and elastic Sealing strips is sealed. The latter version has the advantage that the yoke is not weakened by bores for the hydrostatic cylinder and therefore in diameter can be smaller, whereby the jacket of the roller and its weight and the Manufacturing costs can be reduced.

(7) Includes a final preferred embodiment of the invention a particularly simple method of propulsion, which as a consequence of the main idea the invention becomes possible and especially when the second additional idea is implemented (3) leads to a compact and cheap solution.

According to this configuration, the is concentrically above the outer ring spherical shell bearing on the drive side attached a ring gear with which a pendulum adjustable drive pinion meshes.

This in turn is driven by a drive motor via articulated links emotional.

The invention is explained in more detail with reference to FIGS. 1-3.

All three figures show a partial section through the end of a swimmer Roller.

Figure 1 shows an embodiment with a floating bearing without a drive.

Figure 2 shows another embodiment with a floating bearing, too without drive.

Figure 3 shows an embodiment with a fastener, with a drive.

Each roller has a lot at one end and a lot at the other end Fixed bearing. At the end of the fixed bearing, both the yoke and the roll shell are axial fixed immovably against the frame, while an axial one at the floating bearing end Shifting of the yoke and the roll shell relative to the frame can take place. Apart from the means for -axially fixing, the bearing on the fixed bearing side differs not from the one on the non-locating side.

In Figure 1, 1 is the rotatable roll shell on which the bearing sleeve 2 is flanged. This is via the spherical bearing 3 with the support frame 4 tied together. The oil space of the bearing 3 is to the outside through a cover 5 with a lip seal 6 sealed. The yoke 7 is supported by a spherical sleeve 8 in an articulated manner in the support frame 4 from.

A lip seal 9 seals the gap between the yoke 7 and Ab based block 4 to the outside. The support frame 4 is on a bearing lever or frame 10 attached.

In a semi-cylindrical space 11 between jacket 1 and yoke 7, which on the front side by seal 12 and in the circumferential direction by 2 opposing sealing strips 13 is limited, an oil pressure serving to support the jacket 1 is thereby created produces 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 Arbitrarily activated under adjustable pressure via the supply lines 17 and 18, to force an additional bend on the ends of the jacket.

In FIG. 2, a bearing sleeve is again attached to a rotating jacket 1 2, which is hinged to the support frame 4 via a spherical bearing 3. A bearing cover 5 with a lip seal 6 closes the oil space of the bearing to the outside away. The yoke 7 held non-rotatably on the fixed bearing side is supported by the spherical yoke Ring 8 on the support frame 4.

This is attached to a frame or pressure lever 10. In the yoke 7 hydrostatic support pistons 18 are mounted in the area of the pressing zone 19, which Press against the roller shell 1 from the inside.

Additional hydrostatic support piston 15 and / or 16 outside the Pressing area 19 can be so pressurized that a desired bending the surface line is enforced.

In Figure 3- a roll shell 1 is over a bearing sleeve 2, a ring gear 17 and a spherical bearing 3 rotatably mounted on a support frame A. The oil room of the bearing housing in the support frame 4 is by means of cover 5 and lip seal 6 according to sealed on the outside.

A yoke 7 is articulated to the support frame via a ball sleeve 8 4 connected. A lip seal 9 seals the gap between the support frame 4 and a sleeve 20 pushed onto the yoke 7.

A spring ring 21 holds the ball sleeve 8 axially via the sleeve 20 (fixed bearing). The support frame 4 is attached to a pressure lever, pressure piston or frame 10. A semi-cylindrical oil pressure chamber 11 is formed by oil supply channels (not shown) supplied with pressure oil. This space is opposed by sealing rings 12 and on the yoke 7 Sealing strips 13 delimited to the outside. The spherical bearing 3 is on a support ring 22 and a spring ring 23 against axial displacement with respect to the support frame 4 secured. On the other hand, the ring gear 17 is supported by a support ring 24 and a 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 in and secures this against rotation.

A drive shaft 28 with feather key 29 is via a not shown PTO shaft driven. The drive shaft 28 is in a spherical bearing 30 stored and sealed with lip seal 31 in cover 32.

It drives the drive pinion via an angularly adjustable tooth coupling 33 34, which meshes with the ring gear 17. The drive pinion 34 is pivotable mounted on the spherical bearing 35, which in turn on a retaining bolt 36 is seated, which is fastened to the support frame 4 by means of a washer 37 and a screw 38.

The bearing 35 is held axially by a spring ring 39. At the end of the retaining bolt 36, a retaining ring 40 and a spring ring 41 are attached to the axial Definition of warehouse 35.

Claims (7)

Keyword: "Concentric support 11! Patent claims rs (1 press roll with Deflection compensation, especially for the paper industry with a crocodile jacket, which can be rotated around a fixed yoke and with spherical ones at both ends Storage is positioned opposite the machine frame and also pressure elements contains1 which transfer compressive forces from the yoke to the jacket in the contact area of the roller, as well as with spherically adjustable support surfaces between the yoke and the machine frame, characterized in that the support surfaces between (8 and 4) for the yoke (7) are arranged radially inside the spherical bearing (3) of the shell (1). 2. Press roll according to claim 1, characterized in that the spherical adjustable support surfaces for the yoke (7) and the corresponding spherical Bearings (3) of the shell (1) have at least approximately the same center. 3. Press roll according to one of claims 1 and 2, characterized in that that at both ends of the roller the frame (4) via a tubular cantilever of the side between the inner ring of the spherical bearing (3) and the yoke (7) protrudes and on its outside the spherical bearing (3) and on its inside the Yoke (7) carries (Figures 2 and 3). 4. Press roll according to one of claims 1 to 3, characterized in that that in the areas between the spherical Bearings (3) and the Press zone (19) additional pressure elements (15) between yoke (7) and roll shell (1) are available, with the help of which an arbitrary additional bending of the roller ends can be effected in the edge area of the pressing zone (19) relative to the central area. 5. Press roll according to one of claims 1 to 4; characterized, that the additional pressure elements (15) are hydrostatic support shoes. 6. Press roll according to claim 3, characterized in that the outer ring of one of the two spherical bearings (3) of the shell (1) a toothed ring (17) carries with which a pendulum adjustable drive pinion (34) meshes .. 7. Press roll according to one of claims 1 to 6, which has a counter roll is assigned without deflection compensation, characterized in that the distance of the spherical bearings (3) of the shell (1) at least approximately equal to the distance are the bearings of the counter roll.