CN113697573B

CN113697573B - Bush roller

Info

Publication number: CN113697573B
Application number: CN202110532998.XA
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: 2023-09-01
Anticipated expiration: 2041-05-17
Also published as: CN113697573A; EP3913136A1

Abstract

A bushing roller (1) comprises an axle beam (11), the axle beam (11) having a journal (13). The journal (13) is supported in a bearing structure (21). Furthermore, the bushing roller (1) comprises a roller head (31), the roller head (31) being configured to support the belt (41), the belt (41) being tensioned around the axle beam (11) and being rotatable around the axle beam (11). The belt (41) is rotatable about and relative to the axle beam (11). The moving means (22) are configured to rotate the axle beam (11) within the support structure (21).

Description

Bush roller

Technical Field

The present invention relates to a sleeve roller (sleeve roller). Typically such a bushing roll is arranged in the forming section of a fibre web forming machine, such as a paper, board, tissue or pulp machine.

Background

The bushing roller of the prior art is known, for example, from document DE 3142045 A1. Here, a bushing arrangement (sleeve arrangement) with stationary sector supporting 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 wires are guided such that they run in an adjacent manner along a part of the circumference of the bushing roller, thereby forming a fabric wrap (fabric wrap) in which the web is sandwiched between the fabrics of the wires. The bushing roll thus 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 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 having a cross section with a varying radius of curvature. This shape makes it possible to improve the dewatering pressure caused by the change of the radius of curvature of the liner roll.

There is a need for a bushing roller that provides greater flexibility for different dewatering parameters.

Disclosure of Invention

According to the invention, a bushing roller (1) comprises an axle beam (11) with a journal (axle stub) (13). The journal (13) is supported in a bearing structure (bearing structure ) (21). Furthermore, the roller head (31) is configured to support a belt (41), the belt (41) being tensioned around the axle beam (11) and being rotatable around the axle beam (11). The belt (41) is rotatable about the axle beam (11) and is rotatable relative to the axle beam (11). Furthermore, a displacement device (22) is provided, which is configured to rotate the axle beam (11) within the support structure (21).

The above-described construction of the bushing roller enables the axle beam to rotate about its axis between different fixed positions of the axle beam. Thus, unless the bushing roller has a perfect circular (perfect circle) cross-sectional shape, the fabric tension wrap (fabric tension wrap) formed between two webs that are directed around the circumferential portion of the bushing roller can be changed. Examples of parameters of the fabric tension wrap to be changed are its length, pressure, or travel time/residence time of the web through the fabric tension wrap. That is, the water removal sector (water removal sector) can be arbitrarily adjusted as needed. Rotation (also referred to as turning) of the axle beam may be used to mitigate activation of the bushing roller by turning a longer portion of the sliding region into the peak pressure fabric wrap region. In this case, the retraction of the shaping element can be omitted.

Advantageously, the movement means (22) may comprise an annular flange (25) surrounding said journal (13), and actuation means configured to cause a rotary movement of the annular flange (25).

The arrangement described above enables linear motion to be transferred to rotational motion of the journal. Thereby, the rotation angle of the axle beam can be accurately set. Therefore, when the liner roller is mounted, only the posture (posture) of the liner roller needs to be roughly set. Fine-tuning of the dewatering sectors may then be performed as desired, even during operation of the paper or board machine. However, rotation is only possible to a certain extent and not a full 360 ° rotation.

Advantageously, the actuation means comprise screws, gears, worm gears, lashing screws (23) or hydraulic cylinders.

These particular moving means enable the above-mentioned advantages of precisely setting the rotation angle of the axle beam.

Advantageously, the axle beam (11) may be made of hollow polygonal and/or round beam construction.

Polygonal in the sense of the present invention means that the angled line segments form a closed structure within a 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 polygon may also be understood as a box-like shape or a tubular shape forming a closed tube with a plurality of walls. By adopting such a polygonal structure, rigidity with respect to the axial length of the liner roller is significantly improved.

Advantageously, at least a portion of the axle beam body may have a polygonal cross-section with 6 to 12 corners (horns) or corresponding angles, preferably rounded corners, or at least a portion of the axle beam body 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 tensioning wraps, as these beams are not well suited for moderate multi-directional loading or turning of Liang Junyun (even) to different drive positions.

The hollow structure enables to house suitable equipment, such as collecting and/or outlet portions for fluids such as oil and air and supply means, which can be arranged inside the axle beam in a space-saving manner. Here, it should be noted that the axle beam itself rotates only when actuated by the moving means, whereas the belt rotates continuously around the axle beam when the paper or board machine is running.

Advantageously, the roller head (31) can be supported by a sliding device (32) arranged on the journal (13).

This configuration enables the belt to be tensioned.

Advantageously, the internal displacement means (35) may be arranged inside the axle beam (11) and engage with the roller head (31). The internal moving device (35) may be configured to move the roller head (31) in an axial direction.

Thus, the axial position of one or both roller heads can be adjusted arbitrarily as desired.

Advantageously, indexing means may be arranged between the roller head (31) and the support structure (21). The indexing means may be configured to indicate the distance from the roller head (31) to the support structure (21).

Thus, the distance of the roller head to the support structure can be accurately set. Further, excessive sliding movement of the roller head can be prevented when the belt is tensioned.

Advantageously, the roller head (31) can comprise an opening through the journal (13), which can be closed in an airtight manner.

Thus, inlet and outlet pipes for fluids such as lubricating oil and the like can be arranged while the pressure inside the belt can be maintained.

Advantageously, the roller head (31) may comprise tensioning devices configured to tension the belt (41).

The tensioning device may be provided separately or an internal moving device may be used to tension the belt.

Advantageously, the tensioning means may be arranged inside or outside the roller.

Whether the tensioning means are provided separately or in the form of an internal displacement means, it is preferred that the tensioning means are arranged inside the roller head.

Advantageously, the tensioning means may be arranged in such a way as to provide symmetrical tensioning forces to the roller head (31). However, asymmetric tension forces may be used so that there is less tension in the sector protruding the forming element.

Advantageously, the supporting structure (21) may be a rocker bearing (rocker bearing) or a pedestal (pepestal).

Advantageously, the diameter of the bushing roller may be between 700mm and 1600 mm.

Advantageously, in a sectional view, the bushing roller (1) may have an irregular shape.

The irregular shape may be realized, for example, by a shaped element arranged at or in the axle beam, or the axle beam itself may have an irregular shape. The irregular shape of the cross section of the bushing roller enables to obtain the desired parameter settings of the fabric tensioning wrap in a shortened (shortened) time, depending on the irregular shape.

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, both wires 1009, 1015 being guided as closed loops. A wire loop 1015 is guided by a plurality of guide rollers 1013, 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 mesh 1015 and mesh 1009 are slightly elongated in the portions that are not affected by the rolls, in these fabric tensioning wraps the pressure exerted by the mesh tension on the web is higher than in the unsupported portions of the mesh.

The forming gap and fabric tension wrap formed at forming roll 1005 is used to receive pulp suspension from headbox 1001. To provide such a forming gap and fabric tensioning wrap 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 adjacent 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 forming wrap is formed at the liner roll 1. Since the present description is directed mainly to the liner roll 1, the fabric forming wrap formed at the liner roll 1 will be described hereinafter as "fabric forming wrap", while the fabric forming wrap formed at the forming roll 1005 will be described as "constant radius fabric tensioning wrap", or simply "fabric tensioning wrap" (at the forming roll 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 constant radius 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. Thus, the web passes through dewatering device 1003, which increases the 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 web 1015 coming into direct contact with the belt 41 as it passes through the bushing roller 1, due to the web being wound in tension during the common path.

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.

In order to accurately determine the position of the roller head 31 and/or prevent excessive stretching of the belt 41, a plurality of indexing means (not shown) are provided to inform the user of the amount of movement of the roller head. 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 a smooth belt running on the element, thus tensioning the belt outwards. Upon activation, the forming element may be retracted inside the roller head circle to reduce friction.

The protrusion/projection of the forming element out of the roll head/belt circle (outtroke) may be 10mm-120mm, advantageously 20mm-70mm. When the sliding surface is arranged at a few millimeters (tens of millimeters) below the head/belt, but within the same radius, belt recessing/inward bulging may also occur before the forming element. This helps reduce the amount of protrusion required, thereby helping to extend 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 (favorabaly), 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 preferably may be provided with depressions (depressions), such as pits (dumples). 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 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, the lubricant collector device and the 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 shaping element adjoining the belt can be changed 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 forming the sliding element.

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. A bushing roller (1) comprising:

-an axle beam (11) having a journal (13), said journal (13) being supported in a bearing structure (21);

-a roller head (31) configured to support a belt (41), the belt (41) being tensioned around the axle beam (11) and rotatable around the axle beam (11);

-said belt (41) being rotatable around and relative to said axle beam (11); and

-a moving device (22) configured to rotate the axle beam (11) within the supporting structure (21).

2. Bushing roller (1) according to claim 1, wherein the moving means (22) comprise an annular flange (25) surrounding the journal (13), and actuating means configured to cause a rotational movement of the annular flange (25).

3. Bushing roller (1) according to claim 2, wherein the actuation means comprise screws, gears or worm gears or hydraulic cylinders.

4. Bushing roller (1) according to claim 2, wherein the actuation means comprise a binding screw (23).

5. Bushing roller (1) according to any of claims 1-4, wherein the axle beam (11) is made of a hollow polygonal and/or round beam structure.

6. Bushing roller (1) according to any of claims 1-4, wherein the roller head (31) is supported by a sliding device (32) arranged on the journal (13).

7. The bushing roller (1) according to any one of claims 1 to 4, further comprising:

-an inner movement device (35) arranged inside the axle beam (11) and engaging with the roller head (31), the inner movement device (35) being configured to move the roller head (31) in an axial direction.

8. Bushing roller (1) according to claim 7, wherein an indexing device is arranged between the roller head (31) and the support structure (21), the indexing device being configured to indicate the distance from the roller head (31) to the support structure (21).

9. Bushing roller (1) according to any of claims 1-4, wherein the roller head (31) comprises an opening through the journal (13), which opening is configured to be closed in an airtight manner.

10. Bushing roller (1) according to any of claims 1-4, wherein the movement means of the roller head (31) are used as tensioning means configured to tension the belt (41).

11. Bushing roller (1) according to claim 10, wherein the tensioning device is arranged inside or outside the roller head (31).

12. Bushing roller (1) according to claim 10, wherein the tensioning device is arranged in such a way that a symmetrical tensioning force is provided to the roller head (31).

13. Bushing roller (1) according to any of claims 1-4, wherein the support structure (21) is a rocker bearing or a pedestal.

14. Bushing roller (1) according to any of claims 1-4, wherein the bushing roller has a diameter between 700mm and 1600 mm.

15. Bushing roller (1) according to any of claims 1-4, wherein the bushing roller (1) has an irregular shape in cross-section.