CN113697573A

CN113697573A - Lining roller

Info

Publication number: CN113697573A
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: 2021-11-26
Anticipated expiration: 2041-05-17
Also published as: CN113697573B; EP3913136A1

Abstract

A bushing roller (1) comprises a shaft beam (11), which shaft beam (11) has a shaft journal (13). The shaft journal (13) is supported in a bearing structure (21). Furthermore, the lining 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 around and relative to the axle beam (11). The moving device (22) is configured to rotate the axle beam (11) within the support structure (21).

Description

Lining roller

Technical Field

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

Background

A prior art lining roller is known, for example, from DE 3142045a 1. Here, a lining arrangement (sleeve arrangement) with fixed (stationary) 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 wires are guided such that they run along a portion of the circumference of the bushing roller in an adjacent manner, forming a fabric wrap (fabric wrap) in which the web is sandwiched between the fabrics of the wires. The bushing roller thus minimizes the distance between the two wires, thereby dewatering the web located between the two wires. Within the fabric wrap, the curvature of the shoe element changes from a straight portion to a constant smaller radius of the sleeved (sleeved) shoe element.

Another forming section is known from document EP 2350385B1, which is similar to the forming section of DE 3142045a1, but comprises a lining roller with a cross section of varying radius of curvature. This shape makes it possible to improve the dewatering pressure caused by the change in the radius of curvature of the lining 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 a shaft beam (11) with a shaft journal (13). The journal (13) is supported in a bearing structure (21). Furthermore, the roller head (31) is 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 the axle beam (11) and relative to the axle beam (11). Furthermore, a movement device (22) configured to rotate the axle beam (11) within the support structure (21) is provided.

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 liner roll has a right circular (perfect circular) cross-sectional shape, the fabric tension wrap (fabric wrap) formed between the two webs that is directed around the circumferential portion of the liner roll may be varied. Examples of parameters of the fabric stretch wrap to be changed are its length, pressure, or travel time/dwell time of the web through the fabric stretch 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 moderate the activation of the liner roll by turning a longer portion of the slip region to the peak pressure fabric wrap region. In this case, the retraction of the forming element may be omitted.

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

The above arrangement enables a linear motion to be transferred to a 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 (post) of the liner roller needs to be roughly set. Fine tuning of the de-watering sector can then be performed as required, 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 actuating means comprise a screw, a gear, a worm wheel, a rigging screw (23) or a hydraulic cylinder.

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

Advantageously, the axle beam (11) may be made of a hollow polygonal and/or circular beam structure.

Polygonal in the sense of the present invention means that the angled line segments form a closed structure in a rounded 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, the rigidity with respect to the axial length of the liner roll is significantly improved.

Advantageously, at least a part of the axle beam body may have a polygonal cross-section with 6 to 12 corners (corner), preferably rounded corners, or a corresponding angle, or at least a part of the axle beam body may have a circular cross-section. Unexpectedly, the very stiff and tall I-beam and square beams developed for belt roll nips (belt rolls) are not suitable for use in bushing rolls with fabric tension wrap, as these beams are not well suited for uniform (even) moderate multi-directional loading or rotation of the beams to different drive positions.

The hollow structure enables accommodation of suitable equipment, such as collecting and/or outlet parts for fluids, such as oil and air, and supply means, which equipment can be arranged in a space-saving manner inside the axle beam. Here, it should be noted that the axle beam itself rotates only when actuated by the moving device, while 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 tensioning of the belt.

Advantageously, the internal moving 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 the axial direction.

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

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. Also, excessive sliding movement of the roller head can be prevented when the belt is tensioned.

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

Thus, it is possible to arrange inlet and outlet pipes for fluid such as lubricating oil, while the pressure inside the belt can be maintained.

Advantageously, the roller head (31) may comprise tensioning means 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 device may be arranged inside or outside the roller.

Whether the tensioning device is provided separately or in the form of an internal displacement device, it is preferred to arrange the tensioning device inside the roller head.

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

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

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

Advantageously, the lining roller (1) can have an irregular shape in cross-section.

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

Drawings

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

figure 1 is a schematic view of a forming section of a paper or board machine using a liner roll according to the invention;

FIG. 2 is a perspective view of a support structure supporting journals of a liner roll according to 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 liner roll according to the present invention; and

fig. 5 is a cross-sectional view perpendicular to the length axis of the bushing roller in accordance with the present invention.

Detailed Description

Figure 1 shows an example of a schematic structure of a forming section 1000 of a paper or board machine using a bushing roll 1 according to the invention. The headbox 1001 is used to feed a pulp suspension (pulp suspension) between

wires

1009, 1015, both

wires

1009, 1015 being guided as closed loops. The wire loop 1015 is guided by a plurality of guide rolls 1013, a forming roll 1005 and a bushing roll 1. The second wire 1009 is guided in a further closed loop by a number of dedicated guide rolls 1007, said forming roll 1005 and said lining roll 1. Between forming roll 1005 and a guide roll 1007a of a plurality of guide rolls 1007 dedicated to a second wire 1009, both

wires

1015 and 1009 run in parallel, sandwiching the web thus formed (sandwich).

A forming gap (forming gap) is formed between the two webs (web 1015 and web 1009) at respective circumferential portions of forming roll 1005 and bushing roll 1, with constant radius fabric tension wrap over the forming roll and varying radius fabric tension wrap over the bushing roll, with web 1015 and web 1009 both traveling along the circumferential portions of the two rolls. Since the wire 1015 and the wire 1009 are slightly elongated in the portions not affected by the rolls, the pressure exerted on the web by the wire tension is higher in these fabric tension wraps than in the portions where the wire is unsupported.

The forming gap and fabric tension wrap formed at forming roll 1005 is used to receive the stock suspension from headbox 1001. In order to provide such a forming gap and fabric tension wrap at the forming roll 1005, the second wire is guided to the forming roll by means of a breast roll 1007b, which breast roll 1007b is arranged close to the forming roll 1005, so that the diffuser part 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 primarily directed to the bushing roll 1, the fabric forming wrap formed at bushing roll 1 will be described hereinafter as a "fabric forming wrap", while the fabric forming wrap formed at forming roll 1005 will be described as a "constant radius fabric tension wrap", or simply "fabric tension wrap", if desired (at forming roll 1005).

Furthermore, 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 arrangements of wires and elements shown in fig. 1 and described above. That is, additional dewatering elements and suction boxes may be provided alongside the described elements. Alternatively, one or more of the dewatering elements and/or suction boxes shown may be omitted. Furthermore, different types of web forming concepts can be selected that are applicable to all types of forming machines, headbox, layout and web. Also, the function of the liner roll and its position in the forming machine may vary depending on the specific needs of the particular web being formed.

To form the web, the pulp suspension is fed from the headbox 1001 into a constant radius fabric tight wrap and forming gap at the forming roll 1005, where a first dewatering takes place. From there, the web is wrapped taut between wire 1015 and wire 1009 by guide bushing roller 1 and the fabric. Thereby, the web passes through the dewatering device 1003, which increases the dryness content of the web. In the tight wrapping of the fabric, a second dewatering takes place. With the aid of the bushing roller 1 according to the invention, it is possible to set fabric stretch wrap parameters, such as its length, the pressure to which it is applied, the travel time of the web through the fabric stretch wrap, etc., as described below. Thus, effective dewatering takes place before the web is further guided via the suction box 1011 of the pipe to be taken over and transferred to the next section, e.g. the press section of the fiber web forming machine.

The bushing roller 1 according to the invention comprises a shaft beam 11 and a shaft journal 13. As can be seen in fig. 2, the journal 13 is supported in a base (e.g., a support structure) 21. Furthermore, as can be seen from fig. 4, the lining roller 1 comprises a roller head 31 supporting a belt 41. The belt 41 is tensioned around the axle beam 11 and can rotate 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 tension wrap 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 a manner that can transfer torque from the flange 25 to the journal 13.

To provide torque, the flange 25 is connected to the tightening screw 23 by means of a joint 22. That is, one end of the tightening screw 23 is attached to the flange 25 by means of the joint 22. The other end of the tightening screw 23 opposite to the end attached to the joint is fixed to the base 21. Thus, by turning the tightening screw 23, its length can be lengthened or shortened, thereby causing rotation of the flange 25. The rotation of the flange 25 is transmitted to the shaft journal 13, thereby rotating the shaft beam 11 and the shaft journal of the lining roll 1. The flange 25 and the joint 22 form a moving means according to the invention, the tightening screw 23 being one example of an actuating means according to the invention.

That is, instead of a cable screw, the actuating means may comprise a screw, gear, worm gear, hydraulic cylinder or other suitable means for providing a longitudinal movement which is then transferred to a 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). Further, the cross section of the axle beam body 111 is symmetrical in different planes, and the width (in the y direction in the drawing) of the axle beam 11 is larger than the height (in the z direction in the drawing). The thickness of the plate forming the axle beam body 111 is between 30mm and 60 mm. This geometry of the axle beam results in excellent stiffness in its axial direction (direction of the axis of rotation a) while still allowing the desired cross-sectional shape to be formed.

Rounded corners in the sense of the present invention are to be understood as meaning corners having an arc-shaped, convex, curved portion with a certain radius of curvature.

The head portion 113 of the axle beam 11 has a flange-like shape and is provided with a plurality of mounting holes 1131. The head portion 113 is surrounded by the axle beam body 111, and the axle beam body 111 is constituted by two

bent metal pieces

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 maintenance opening 117 and other openings are provided to enable access to the inner space of the axle beam 11. Some or all of these openings may be closed with windows (hatches).

As can be seen in fig. 4, the journal 13 is mounted to the head 113. The roller head 31 is slidably disposed 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. Accordingly, the roller head 31 can be moved in a sliding manner in the direction of the rotation axis a, i.e., leftward and rightward in fig. 4. Thereby, the axial position of the roller head 31 can be determined on one side, while the tension of the band 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 way that the belt 41 is tensioned by symmetrical tensioning forces.

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

Furthermore, an opening is provided in the roller head 31 through the journal 13. The opening can be closed in a gastight manner and is used for arranging, for example, inlet and outlet pipes for a fluid, for example 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 in the length direction 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 formed integrally with the axle beam 11.

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

Since the movable shaping 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 projection height of the shaping elements 119, the cross-sectional shape of the loop formed by the strip 41 is varied.

For the purpose of projection or retraction, the movable shaping element 119 is formed to move forward and backward along its projection direction z. This is achieved by means of a piston 1192 housed in a cylinder 1193. The piston 1192 is able to act in both directions. Thus, the movable shaping element 119 is formed to protrude by a desired height. The protrusion of the forming elements can affect the belt when the radius of the bushing roller is exceeded in the operating position. Therefore, good lubrication must be arranged before the forming element to ensure a smooth belt sliding over said element, thereby tensioning the belt outwards. Upon activation, the forming element may be retracted inside the roller head circle to reduce friction.

The amount of protrusion/projection of the forming element from the roll head/band circle (outstreke, outward stroke) may be 10mm-120mm, advantageously 20mm-70 mm. Belt indenting/inward bulging (belt indenting/inward bulging) may also occur before the forming element when the sliding surface is arranged a few millimeters (tens of millimeters) below the head/belt, but within the same radius. This helps to reduce the amount of protrusion required, thereby contributing to an extended useful life of the belt.

The movable shaping 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 changed in a linear manner, but also be inclined. Advantageously (revolute), the movement means of the articulated forming element can also be inclined/articulated.

In the direction of travel of the belt 41, the sliding surface 115 is arranged in front of 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. Further, the sliding surface is subjected to surface treatment, and may preferably be provided with depressions (depressions), such as dimples (dimples). In addition, a lubricating device 1151 is arranged in front of the sliding surface 115 in the rotational direction of the belt 41. Thus, the coefficient of friction of the sliding surface 115 may be significantly reduced, so that the belt 41 runs smoothly on the sliding surface 115 before reaching the movable shaping element 119.

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

Further, fig. 4 and 5

show conduits

110, 112, 114 for supplying and discharging lubricant (see arrows in the conduits in fig. 4). The supply and discharge takes place via holes in the shaft journal 13. Furthermore, these pipes are supported inside the axle beam 11. The main drain line 120 is used to return lubricant that needs to be cooled and filtered before being re-fed (newly) to the bushing rollers. In addition to the lubricant feed conduits, smaller hydraulic conduits are shown, such as those labeled 118, 118a, 118 b. These latter

hydraulic conduits

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 pipe is made by means of steel reinforced hoses (reinforced hose) to allow thermal movements and bending.

While this invention has been described in connection with what is presently considered to be the preferred embodiment, the scope of the invention is not limited to the foregoing description and drawings, but is defined by the claims.

Accordingly, variations may be made to the embodiments. 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 portion or 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 corners, 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 the axle beam body.

Further, 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 adjoining the belt may change stepwise (stepwise). The number of steps may be 3 to 12.

Although no particular range of wrapping is mentioned above, the sliding surface may cover a sector of 30 ° to 120 ° of the bushing roller, so that a net with a mutual wrapping on the bushing roller can drive the belt by means of the supporting sliding surface.

Although in this embodiment the lubricating means is arranged before the sliding surface in the direction of rotation of the belt, the lubricating means may alternatively or additionally be provided by the sliding surface. The arrangement of the lubricating device depends on the assembly (assembly) before the sliding element is formed.

Although a polygonal configuration in the cross-section of the axle beam has 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), the 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);

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

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

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

3. A bushing roller (1) according to claim 2, wherein said actuating means comprises a screw, a gear or worm wheel or a tightening screw (23) or a hydraulic cylinder.

4. The bushing roller (1) of any of the preceding claims, wherein the axle beam (11) is made of a hollow polygonal and/or circular beam structure.

5. The bushing roller (1) of any one of the preceding claims, wherein the roller head (31) is supported by a sliding arrangement (32) arranged on the journal (13).

6. The bushing roller (1) of any one of the preceding claims, further comprising:

an internal moving device (35) arranged inside the axle beam (11) and engaged with the roller head (31), the internal moving device (35) being configured to move the roller head (31) in an axial direction.

7. The bushing roller (1) of claim 6, wherein an indexing device is arranged between the roller head (31) and the support structure (21), the indexing device being configured to indicate a distance from the roller head (31) to the support structure (21).

8. The bushing roller (1) of any one of the preceding claims, wherein the roller head (31) comprises an opening through the journal (13), the opening being configured to be closed in a gas-tight manner.

9. The bushing roller (1) of any one of the preceding claims, wherein the moving device of the roller head (31) serves as a tensioning device configured to tension the belt (41).

10. The bushing roller (1) of claim 9, wherein the tensioning device is arranged inside or outside the roller head (31).

11. A bushing roller (1) according to claim 9 or 10, wherein the tensioning means are arranged in a manner providing a symmetrical tensioning force to the roller head (31).

12. Bushing roller (1) according to one of the preceding claims, wherein the support structure (21) is a rocker bearing or a pedestal.

13. The bushing roller (1) of any preceding claim, wherein the diameter of the bushing roller is between 700mm and 1600 mm.

14. A bushing roller (1) according to any of the preceding claims, wherein in cross-section the bushing roller (1) has an irregular shape.