CN113699822B

CN113699822B - Axle beam

Info

Publication number: CN113699822B
Application number: CN202110533307.8A
Authority: CN
Inventors: 维莱·埃罗宁; 塞波·库皮艾宁; A·米蒂宁; T·西洛玛; 约尔马·斯内尔曼; 尤哈·温帕里
Original assignee: Valmet Technologies Oy
Current assignee: Valmet Technologies Oy
Priority date: 2020-05-20
Filing date: 2021-05-17
Publication date: 2024-04-30
Anticipated expiration: 2041-05-17
Also published as: CN113699822A; EP3913135A1

Abstract

An axle beam (11) for a roll of a paper or board machine, comprising: an axle beam body (111) comprising a hollow profile with rigidity; a head (113) configured to attach the journal (13) to the axle beam (11); and a sliding surface (115) extending along the length direction of the axle beam (11) and detachably attached to the axle beam (11).

Description

Axle beam

Technical Field

The present invention relates to an axle beam. Such an axle beam is used for rolls of a fiber web forming machine, such as a paper, board, tissue or pulp machine, for example a sleeve roll, which is usually arranged in the forming section of the fiber web forming machine.

Background

The prior art bushing roller is known, for example, from DE 3142045 A1. Here, a bushing arrangement (SLEEVE ARRANGEMENT) with fixed sector support shoes/beams is arranged in the forming section of a paper or board machine. The forming section comprises two wires, each forming a closed loop. The two webs are guided such that they run in an adjacent manner along a portion of the bushing arrangement with the fixed sector support shoe/Liang Yuanzhou, forming a fabric wrap (fabric wrap) with the web sandwiched between the fabrics. Thus, the bushing arrangement with the fixed sector support shoe/beam minimizes the distance between the two wires, thereby dewatering the web between the two wires. Within the fabric wrap, the curvature of the boot element changes from a straight portion to a constant smaller radius of the lined (sleeved) boot element.

Another forming section is known from document EP 2350385B1, which is similar to the forming section of DE 3142045A1, but comprises a bushing roller with a cross section having a radius of curvature that varies. This shape makes it possible to improve the dewatering pressure caused by the change of the radius of curvature of the liner roll.

In paper and board machines, the same type of roll (e.g. bushing rolls) is used in different machine design concepts (DESIGNED MACHINE concepts), resulting in the need to take into account different boundary conditions depending on the position of the roll and its attitude. For example, the resultant force direction (resulting force direction) may vary depending on the assembled position of the rolls and as a function of different tensions of the fabric (e.g., web) being directed around at least a portion of the rolls.

In addition, in the case where the length of the roller exceeds a certain length, deflection of the roller due to gravity is another problem to be considered. This deflection is problematic because it may deteriorate the quality of the wire, especially in connection with the application of pressure on the wire for dewatering.

There is a need for an axle beam for rolls of a fiber web forming machine that provides more flexibility for different dewatering parameters and is suitable for use in various forming machine types and forming machine concepts for manufacturing different types of web.

Disclosure of Invention

According to the invention, an axle beam (11) for a roll of a fiber web forming machine, the axle beam comprising: an axle beam body (111) comprising a hollow profile with rigidity; a head (113) configured to attach a journal (axle stub, a shaft post) (13) to the axle beam (11); and a sliding surface (115) that extends along the length direction of the axle beam (11) and is curved in the transverse direction of the axle beam (11), and that is mounted to the axle beam (11) or formed together with the axle beam (11).

Such a sliding surface significantly reduces the coefficient of friction with the belt, which encircles the roller and is formed to rotate with the web travelling around a portion of the roller. Thereby, the torque acting on the axle beam due to the rotation and tensioning of the belt can be significantly reduced. The sliding surface is integrated to the axle beam and acts as a support structure part. Furthermore, even if there is a slight deflection of the axle beam, such deflection can compensate the sliding surface so that the performance of the forming fabric stretch wrap can be maintained within set parameters.

Advantageously, the axle beam (11) may have a hollow polygonal and/or round beam structure.

Polygonal in the sense of the present invention means that the angled line segments form a closed structure within the circular or curved portion. The length of the line segments and the angle between two adjacent ones of the line segments may vary. Alternatively, a polygonal shape may also be understood as a box-like shape or a tubular shape forming a closed tube with a plurality of walls. By employing such a polygonal structure, the stiffness with respect to the axial length of the bushing roller is significantly improved over conventional inadequate square beam solutions.

Advantageously, at least a portion of the axle beam body (111) may have a polygonal cross-section with 6 to 12 angles (horns) or corresponding angles, which are preferably rounded, or at least a portion of the axle beam body (111) has a circular cross-section. Unexpectedly, the very stiff and high I beams (I beams) and square beams developed for the belt roll nip (belt roll press nip) are not suitable for bushing rolls with fabric tension wrap because these beams are poor (horn) for moderate multi-directional loading or turning of Liang Junyun (even) to different drive positions.

Thus, the stiffness of the individual (differential) portions of the axle beam may be increased when desired, while other portions of the axle beam may be manufactured in a less laborious manner.

Advantageously, the axle beam body (111) may be made of at least two bent metal sheets bonded together.

For example, the metal sheets may be bonded by welding. Thereby, the stiffness of the axle beam structure can be increased, in particular at the joint.

Advantageously, the thickness of the wall of the axle beam body (111) may be 30mm to 60mm.

Wall thicknesses in the above-mentioned ranges can still be produced, for example, by bending of these (metal) sheets, while the stiffness properties of the produced axle beam body are excellent. Furthermore, if the thickness of the wall (the plurality of sheets forming the axle beam) is too great, the roundness (roundness) of the corner will be affected.

Advantageously, one or more openings (117) may be provided in the axle beam body (111).

Such openings allow access to the interior of the axle beam, where conduits for lubricating oil and other fluids and/or various actuators, for example for lifting mechanisms, may be provided. Furthermore, the stiffness of the axle beam is not affected due to the polygonal or circular cross section, despite the presence of the openings. The opening may be closed by, for example, a hatch or other suitable means.

Advantageously, the head (113) may comprise an annular element fitted adjacent to the axle beam body (111) and having a plurality of mounting holes (1131).

This arrangement provides the possibility of combining the axle beam with different journals, thereby increasing the number of variants of the roller that can be manufactured.

Advantageously, the cross-section of the axle beam body (111) may be symmetrical in different planes and/or in the cross-section of the axle beam body (111) the extension in at least one direction exceeds the extension in a direction orthogonal to this one direction. That is, in the cross-section of the axle beam, the height dimension may be different from the width dimension.

Furthermore, advantageously, the axle beam body (111) may comprise a movable forming element (119), which movable forming element (119) is arranged adjacent to the sliding surface.

Such forming elements can be used to vary the cross section of the rolls, i.e. the cross section of the belt travelling around the axle beam, in order to vary the properties of the fabric tensioning wrap formed by the rolls. Since the forming element is movable, various cross-sectional shapes can be set.

Advantageously, the axle beam body (111) may include a tubing configured to supply a lubrication fluid to the sliding surface (115).

Drawings

Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings, in which:

fig. 1 is a schematic view of a forming section of a paper or board machine employing a bushing roller according to the invention;

FIG. 2 is a perspective view of a bearing structure supporting the journals of the bushing rollers in accordance with the present invention;

FIG. 3 is a perspective view of an axle beam of a bushing roller according to the present invention;

FIG. 4 is a cross-sectional view along the length axis of a bushing roller according to the invention; and

Fig. 5 is a cross-sectional view perpendicular to the length axis of the bushing roller according to the invention.

Detailed Description

Fig. 1 shows an example of a schematic structure of a forming section 1000 of a paper or board machine employing a bushing roller 1 according to the invention. Headbox 1001 is used to supply pulp suspension between wires 1009, 1015. Wires 1009, 1015 are guided as closed loops. A wire loop 1015 is guided by a plurality of guide rollers, a forming roller 1005, and a liner roller 1. The second wire 1009 is guided in another closed loop by a number of dedicated (indexed) guide rolls 1007, the forming roll 1005 and the liner roll 1. Between forming roll 1005 and a guide roll 1007a of a plurality of guide rolls 1007 dedicated to a second web 1009, both web 1015 and web 1009 travel in a parallel manner sandwiching the web thus formed (sandwich).

A forming gap (forming gap) is formed between the two webs (web 1015 and web 1009) at the respective circumferential portions of forming roll 1005 and liner roll 1, with a constant radius fabric tension wrap on the forming roll and a varying radius fabric tension wrap on the liner roll, with both web 1015 and web 1009 travelling along the circumferential portions of both rolls. Because the web 1015 and the web 1009 are slightly elongated in the portions not affected by the rolls, the pressure acting on the web in these forming nips is higher than in the unsupported portions of the web.

The forming gap and fabric tension wrap formed at forming roll 1005 is used to receive pulp suspension from headbox 1001. To provide such fabric forming gap and tight wrapping at the forming roll 1005, the second web is directed to the forming roll by means of breast roll 1007b, the breast roll 1007b being arranged close to the forming roll 1005 such that the diffuser portion of the headbox 1001 is arranged between the forming roll 1005 and the breast roll 1007 b. Thus, a first dewatering of the web is performed at the forming roll 1005.

Another fabric tension wrap is formed at the bushing roller 1. Since the present description is mainly directed to the liner roller 1, the fabric tension wrap formed at the liner roller 1 will be described as "fabric tension wrap" hereinafter, while the fabric tension wrap formed at the forming roller 1005 will be described as "constant radius fabric tension wrap" or simply "fabric tension wrap" (at the forming roller 1005), if desired.

In addition, other devices for dewatering the web are arranged in the forming section, such as dewatering elements 1003 or suction boxes 1011. It should be understood that the above description of the forming section based on fig. 1 is by way of example only and does not limit the forming section to the mesh arrangement and elements shown in fig. 1 and described above. That is, additional dewatering elements and suction boxes may be provided alongside the elements described. Alternatively, one or more of the dewatering elements and/or suction boxes shown may be omitted. Furthermore, different types of web forming concepts may be selected that are applicable to all types of forming machines, headboxes, layouts and webs. Also, the function of the bushing roller and its position in the forming machine may vary depending on the specific needs of the particular web to be formed.

To form the web, the pulp suspension is fed from the headbox 1001 into a fabric tensioning wrap and forming gap at the forming roll 1005 where a first dewatering takes place. From there, the web is wrapped in tension between wire 1015 and wire 1009 by guide bushing roller 1 and fabric. The web thus passes through dewatering device 1003, which increases the dryness (dryness content, dryness) of the web. In the fabric tensioning wrap, a second dewatering is performed. As will be described below, with the aid of the bushing roller 1 according to the invention, it is possible to set fabric-tensioning wrap parameters such as its length, the pressure it is applied to, the travel time of the web through the fabric-tensioning wrap, etc. Thus, an effective dewatering takes place before the web is further led via the suction box 1011 to be taken over (to take over) and transferred to the next section, e.g. the press section of a fiber web forming machine.

The bushing roller 1 according to the invention comprises an axle beam 11 and a journal 13. As can be seen from fig. 2, the journal 13 is supported in a base (e.g., bearing structure) 21. Further, as can be seen from fig. 4, the liner roller 1 includes a roller head 31 supporting a belt 41. The belt 41 is tensioned around the axle beam 11 and is rotatable relative to the axle beam 11. In particular, the rotation of the belt 41 is caused by the direct contact of the wire 1015 with the belt 41 due to the wire tension during the common path when passing the bushing roller 1.

Referring back to fig. 2, the base 21 includes an annular flange 25, the annular flange 25 being mounted on the journal 13 in such a way that torque can be transferred from the flange 25 to the journal 13.

To provide torque, flange 25 is connected with lasso screw 23 by means of joint 22. That is, one end of the cinch screw 23 is attached to the flange 25 by means of the joint 22. The other end of the cinch screw 23, opposite the end attached to the joint, is secured to the base 21. Thus, by turning the binding screw 23, its length can be lengthened or shortened, thereby causing the flange 25 to rotate. The rotation of the flange 25 is transferred to the journal 13, thereby rotating the axle beam 11 and the journal of the bushing roller 1. The flange 25 and the joint 22 form a displacement device according to the invention, and the binding screw 23 is an example of an actuation device according to the invention.

That is, instead of a lashing screw, the actuation means may comprise a screw, a gear, a worm gear, a hydraulic cylinder or other means adapted to provide a longitudinal movement which is subsequently transferred to the rotational movement of the flange 25.

As can be seen from fig. 3, the axle beam 11 is made of a hollow polygonal structure with rounded corners (8 in the embodiment). Furthermore, the cross section of the axle beam body 111 is symmetrical in different planes, the width of the axle beam 11 (in the y-direction in the figure) being larger than its height (in the z-direction in the figure). The thickness of the plate forming the axle beam body 111 is between 30mm and 60 mm. This geometry of the axle beam gives excellent stiffness in its axial direction (the direction of the rotation axis a) while still being able to form the desired cross-sectional shape.

Rounded corners in the sense of the present invention are understood to mean corners having an arcuate, convex, curved portion with a certain radius of curvature.

The head 113 of the axle beam 11 has a flange-like shape and is provided with a plurality of mounting holes 1131. The head 113 is surrounded by an axle beam body 111, the axle beam body 111 being formed of two bent metal sheets 111a, 111 b. The two metal sheets 111a, 111b are welded together at their edges to form a hollow body. These edges are arranged in parallel with the axis of rotation a of the bushing roller 1.

Further, in the axle beam 11, a service opening 117 and other openings are provided to enable access to the interior space of the axle beam 11. Some or all of these openings may be closed with a hatch.

As can be seen from fig. 4, the journal 13 is mounted to the head 113. The roller head 31 is arranged in a sliding manner on the journal 13. Thus, the roller head 31 can move in the axial direction of the liner roller 1. To achieve this movement of the roller head 31, hydraulic cylinders (only one of which is shown in fig. 4) 35 are fixed inside the axle beam. The piston rod of each hydraulic cylinder 35 extends through the head 113 of the axle beam 11 and is fixed to the roller head. Thus, the roller head 31 can be moved in a sliding manner in the direction of the rotation axis a, i.e., to the left and right in fig. 4. Thereby, the axial position of the roller head 31 can be determined on one side, while the tension of the belt 41 fixed to the roller head 31 and encircling the axle beam 11 can be adjusted on the other side. The plurality of hydraulic cylinders 35 are arranged in such a manner that the belt 41 is tensioned by symmetrical tensioning forces.

To accurately determine the position of the roller head 31 and/or to prevent excessive stretching of the belt 41, a plurality of indexing means (indexing means ) (not shown) are provided to inform the user of the amount of roller head movement. In this embodiment, the indexing means shows the distance from the inside (right side in fig. 4) of the base 21 to the roller head 31.

Further, an opening passing through the journal 13 is provided in the roller head 31. The opening may be closed in a gastight manner and used for arranging inlet and outlet pipes, for example for a fluid, such as lubricating oil. Since the opening can be closed in an airtight manner, the pressure inside the belt 41 can be maintained.

As shown in fig. 5, the axle beam has a sliding surface 115. The sliding surface extends along the length of the axle beam 11 and is curved in the transverse direction. In this embodiment, the sliding surface is a single component mounted to the axle beam 11, but it may instead be integrally formed with the axle beam 11.

Further, in the axle beam body 111, a movable forming element 119 is arranged adjacent to the sliding surface 115. That is, the forming elements are arranged such that the belt 41 passing over the sliding surface 115 then passes over (go over) the forming elements 119. In cross section, the surface 1195 of the forming element 119 that abuts the belt 41 has a curved, convex shape. The radius of curvature of the curved, convex shape of surface 1195 becomes smaller in the direction of rotation of belt 41. The radius of curvature of the forming element becomes smaller than the radius of the bushing roller. The forming element is movable so that its height protruding from the axle body 111 can be varied. In the axle beam body 111, a pipe system is provided to supply lubricating fluid to the sliding surface 115.

Since the movable forming element 119 is configured to protrude from the axle beam 11, it abuts the belt 41 rotating around the axle beam 11. By varying the protruding height of the forming element 119, the cross-sectional shape of the loop formed by the strip 41 is varied.

For the purpose of the protrusion or retraction, the movable shaping element 119 is formed to move forward and backward along its protruding direction z. This is achieved by means of a piston 1192 accommodated in a cylinder 1193. The piston 1192 can function in two directions. Thus, the movable forming element 119 is formed to protrude by a desired height. When in the operating position beyond the radius of the bushing roller, the protrusion of the forming element can affect the belt. Therefore, good lubrication must be placed before the forming element to ensure smooth sliding of the belt over the element, tensioning the belt outwards. During start-up of the fiber web forming machine, the forming elements may be retracted inside the roll head circle to reduce friction.

The protrusion/projection (outstroke, outward stroke) of the forming element from the roll head/belt circle may be 10mm to 120mm, advantageously 20mm to 70mm. When the sliding surface is arranged a few millimeters (tens of millimeters) below the head/belt but with the same radius, belt recessing/inward bulging (inwards bulging) may also occur before the elements are formed. This helps to reduce the amount of protrusion required, thereby extending the useful life of the belt.

The movable forming element 119 is supported at the axle beam 11 by means of a hinge 1191. Thus, the position of the movable shaping element 119 can not only be varied in a linear manner, but also be tilted. Advantageously (favorable), the moving means of the articulated forming element can also be tilted/articulated.

In the travelling direction of the belt 41, the sliding surface 115 is arranged before the movable forming element 119. The cross section of the sliding surface 115 has the same radius of curvature as the bushing roller/roller head 31. Furthermore, the sliding surface is surface treated and may preferably be provided with recesses (depressions), such as pits (dimples). In addition, the lubrication device 1151 is arranged before the sliding surface 115 in the rotation direction of the belt 41. Thus, the coefficient of friction of the sliding surface 115 may be significantly reduced, allowing the belt 41 to run smoothly on the sliding surface 115 before reaching the movable forming element 119.

It will be appreciated that the cross-sectional shape of the liner roll 1 may vary depending on the requirements of the web being formed, due to the movable forming element 119. Moreover, these changes may be made while the paper or board machine is running. Furthermore, not only the cross section of the bush roller 1 can be changed, but also the rotational position of the movable forming element can be changed by rotating the shaft neck 13 via the lasso screw 23 and the flange 25. Thereby, the change of the fabric tension wrapping parameters can be influenced in a number of ways, which improves dewatering and forming of the web. Reference numeral 116 indicates a plurality of additional sliding elements, one of which is disposed behind and adjacent to the movable forming element 119.

Further, fig. 4 and 5 show the pipes 110, 112, 114 for supplying and discharging the lubricant (see arrows in the pipes in fig. 4). The supply and discharge takes place via holes in the journal 13. In addition, these pipes are supported inside the axle beam 11. The main drain 120 is used to return lubricant that needs to be cooled and filtered before being re-fed (newly) to the liner rollers. In addition to the lubricant feed conduits, smaller hydraulic conduits are shown, such as those labeled 118, 118a, 118 b. These latter hydraulic lines 118, 118a, 118b are used to actuate the piston 1192. The connection of the hydraulic actuator, lubricant collector device and lubricant feed/injection conduit is made by means of a steel reinforced hose (steel enforced hose) to allow thermal movement and bending.

While the present invention has been described based on its presently preferred embodiments, the scope of the invention is not limited to the foregoing description and drawings, but is defined by the claims.

Thus, the embodiment may be changed. For example, the described cross-sectional shape need not be provided for the entire axle beam body, but only a portion of the axle beam body may have a polygonal cross-section. The other one or more portions may have different cross-sections.

The polygonal cross section may have 6 to 12 angles or corresponding angles. Although it is preferred that the corners are rounded, such rounded corners are not explicitly necessary, for example in case the metal sheet is not bent but a plurality of metal strips are welded together to form an axle beam body.

Furthermore, at least a portion of the axle beam body may have a circular cross-section.

Instead of a continuous change, the radius of curvature of the curved shape of the surface of the forming element that adjoins the belt may be changed in a stepwise manner (stepwise). The number of steps may be 3 to 12.

Although no specific range of wrapping is mentioned above, the sliding surface may cover a 30 ° to 120 ° sector of the bushing roller, so that a web with a common wrap on the bushing roller may drive the belt by means of the supported sliding surface.

Although in this embodiment the lubrication means is arranged before the sliding surface in the direction of rotation of the belt, the lubrication means may alternatively or additionally be provided by the sliding surface. The arrangement of the lubrication means depends on the assembly before the formation of the sliding surface.

Although polygonal structures in cross-section of the axle beam have been described, in some cases more complex dimensional shapes (e.g., T-beam, Y-beam, or X-beam cross-sections) may be used to form the axle beam.

Claims

1. An axle beam (11) for a fibre web forming machine, characterized in that a bushing roll (1) of the fibre web forming machine forms a forming gap between two wire loops at respective circumferential portions of the forming roll (1005) and the bushing roll (1), the forming gap having a constant radius of fabric tensioning wrap on the forming roll (1005) and a varying radius of fabric tensioning wrap on the bushing roll (1), both wire loops travelling along the circumferential portions of the forming roll (1005) and the bushing roll (1), the axle beam (11) comprising:

an axle beam body (111) comprising a hollow profile with rigidity;

-a head (113) configured to attach a journal (13) to the axle beam (11); and

A sliding surface (115) extending along the length of the axle beam (11) and being curved in the transverse direction of the axle beam (11), the sliding surface (115) being integrated to the axle beam (11) and being configured to reduce the coefficient of friction between a belt (41) and the axle beam (11), the belt (41) being tensioned around the axle beam (11) and being rotatable around and relative to the axle beam (11),

Wherein the axle beam body (111) comprises a movable forming element (119), the movable forming element (119) being arranged adjacent to the sliding surface.

2. Axle beam (11) according to claim 1, wherein the axle beam (11) has a hollow polygonal and/or round beam structure.

3. Axle beam (11) according to claim 2, wherein

At least a portion of the axle beam body (111) has a polygonal cross-section with 6 to 12 corners, or

At least a portion of the axle beam body (111) has a circular cross-section.

4. An axle beam (11) according to claim 3, wherein the angle is a rounded angle.

5. Axle beam (11) according to any one of claims 1 to 4, wherein the axle beam body (111) is made of at least two bent metal sheets bonded together.

6. The axle beam (11) according to any one of claims 1 to 4, wherein the thickness of the wall of the axle beam body (111) is 30mm to 60mm.

7. Axle beam (11) according to any one of claims 1 to 4, wherein one or more openings (117) are provided in the axle beam body (111).

8. The axle beam (11) according to any one of claims 1 to 4, wherein the head (113) comprises an annular element fitted adjacent to the axle beam body (111) and having a plurality of mounting holes (1131).

9. Axle beam (11) according to any of claims 1-4, wherein the cross-section of the axle beam body (111) is symmetrical in different planes.

10. The axle beam (11) according to any one of claims 1-4, wherein in a cross-section of the axle beam body (111) the extension in at least one direction exceeds the extension in a direction orthogonal to the at least one direction.

11. The axle beam (11) according to any one of claims 1 to 4, wherein the axle beam body (111) comprises a conduit system configured to supply a lubricating fluid to the sliding surface (115).