FI115554B - Plant for supporting a roll in a paper, cardboard, or finishing machine and method for controlling the boom of a roll - Google Patents

Description

9/23/2003 1 1,554 P4140

Apparatus for supporting a roll of a paper, board, or finishing machine, and a method for controlling roll deflection

The present invention relates to an apparatus for supporting a roll of a paper, board or finishing machine 5, and to a method for controlling roll deflection. The apparatus and method of the invention are well suited for use in bearing a two-shell roll of a paper or board machine. Preferably, the invention is applicable to cases involving a composite twin-shell roll. Particularly preferably, the composite roll according to the invention is used as a calender take-out roll or a roll roll for a paper or board machine.

The two-shell rolls mentioned above are known in the paper industry as so-called "roll" rollers. center-supported tracks, which will be discussed in more detail in the following. Center-supported rolls are used in the paper industry mainly as guide rollers, spreader rolls and 15 take-out rolls. Their special feature is that their bending properties differ from conventional end-supported rolls. Thus, for example, they can compensate for differences in length between the edge of the fabric and the central portion, and ensure that no wrinkles are formed in the fabric or web by bending the roll away from the web direction (spreader roll).

20

One type of spreader roll is disclosed in F1 patent 72766, in which the roll is formed by: in a resting state, two spaced apart concentric: cylindrical shells which are fixed to one another in the longitudinal direction of the roll: in the middle. Shaft pins, bearing: '25 are rotatable, are tracked along the inner sheath. When a roll of the type described above is rotated in a papermaking machine or the like, either the fabric or web of the machine causes some degree of deflection in the inner shell of the roll. However, this deflection does not transfer to the outer sheath, which is thus attached to the inner sheath only at the middle of the roll, but tends to maintain its straight cylindrical shape. Depending solely on the rigidity of the outer sheath 30, the outer sheath may either remain straight in use or may deflect in the opposite direction to the inner sheath. In both cases, the risk of wrinkling of the tissue or web is avoided.

It is also worth noting from the above-mentioned Fl Patent 72766 that it is a composite application roller 35 in which, for example, 23.9.2003 1 1 5 5 5 4 2 P4140 carbon fiber-reinforced epoxy resin.

When the roll in question is bent, at some point it is necessary to have an extreme situation in which the inner surface of the end edge of the outer shell of the roll begins to drag along the outer surface of the inner shell. Because there is a difference in circumferential velocity between these surfaces due to the same rotational speed and different large diameters, dragging between the surfaces results in both energy consumption and surface wear. Neither of these factors is desirable and the structure should be modified to minimize the impact of friction.

10

In an attempt to apply the solution of the aforementioned Fl patent to another application of centrally supported rolls, the so-called calender calipers. a take-out roller, which is treated e.g. however, US-A-4,692,971, US-A-5,438,920, WO-A1-9909329 and WO-A1-9742375 disclose some additional problems. Perhaps the most important of these is the critical characteristic frequency of the roll 15. When the outer casing of a composite roll is supported only on the inner casing and only from the center of the roll, the first critical characteristic frequency of such roll will remain relatively low if the roll diameter is maintained at the same level as the current rolls. The only way to move the roll specific frequency higher would be to increase the roll diameter, which would require increasing the diameter by about 150 to 250 mm from the dimensions currently used. This is not

• I

however, this is not possible because there is no space for rolls of this size.

»»:: Another problem which is not solved in F1 72766, as in other prior art * centrally supported rolls, is the arbitrary amount of roll curvature ': 25 or direction. The only factors that these roller features currently are *. · Determine, are track, ground traction and roll sizing. In other words, the design must know from the outset the track power to allow the roller to:.

30 Some of the above problems are solved by the roller solution discussed in US-A-3,161,125 and DE-A1-199 27 897, in which the outer casing of the roller is mounted on a fixed support and the inner casing or shaft is bearing adjustable radially. This solution prevents the roll diapers from touching each other and also stiffens the roll structure. *: Significantly. However, in all driving situations, this roller does not meet the user's expectations and expectations. For example, the outer sheath of a center-supported roll described in the above-mentioned patents P4140 23 · 9 · 2003 115554 3 cannot be flexed according to the track load, but only by forced adjustment of the inner sheath.

The apparatus and method of the present invention seek to eliminate at least some of the problems of the prior art presented above.

The starting point of the invention was to develop a roll whose outer casing would be at least partially self-adjusting according to the track load, i.e. the outer casing end of the roll is supported by bearings such that the bearings are movable radially and the outer casing In addition, the movement of the outer sheath can be limited by springs or the like at the ends of the outer sheath, and it is possible to support the outer sheath through dampers to the body. This is all because it solves a difficult contradiction with the requirements of the structure: the outer sheath must be flexible and curved against the load on the track but dynamically rigid on the other hand. By using damping, the dynamic movement of the outer jacket ends can be suppressed or completely eliminated, so that the specific frequencies remain high, as in the case of a rigid support, but the outer jacket ends can still bend.

20 Among the advantages of the invention, it is worth mentioning, inter alia, that: * the twin-sheath rollers v, · of the invention can adjust both deflection and direction, if necessary:: independent of track force: - critical characteristic frequency is safely high even conventional: and: * ': - the heat problems associated with prior art rollers can be eliminated.

• I

. For the apparatus according to the invention for supporting a roll 30 of a paper, board or finishing machine, which roll consists of two sheaths supported on one another in the middle of the roll, the so-called. from the inner and outer shells supported at their ends to the frame structures of said paperboard or post-processing machine, it is characterized in that the outer sheath of the roll v · 'is supported at its ends through its shaft sleeve and bearing in an adjustable position.

35 4 115554 P4140 23.9.2003

For the method of controlling the roll deflection according to the invention, the roll consists of two sheaths supported on one another in the middle of the roll, so-called. of the outer sheath and inner sheath, it is characterized in that the position of the outer sheath ends is adjusted radially and / or circumferentially with respect to the end shells 5 which are rigidly supported.

Other features of the invention will be apparent from the appended claims.

In the following, the apparatus and method of the invention will be explained in more detail with reference to the accompanying drawings, in which: Figure 1 illustrates a prior art composite structure center-supported roll described in Fl patent 72766, Figure 2 illustrates another prior art center-supported roll Figure 4 schematically shows a double-diaphragm according to a second preferred embodiment of the invention, and in particular a bearing solution thereof, Figure 4 schematically illustrates a dual-diaphragm according to a third preferred embodiment of the invention, the double-sheath roll according to Embodiment *, and in particular its bearing arrangement; 2 according to a preferred embodiment.

: 25 »: Figure 1 shows a prior art F1 composite structure with a center-supported roll 10 of the patent 72766. It consists of shaft pins 12 and 14 · '. , * of composite inner liner 16 and longitudinal inner liner. a composite outer shell 20 also attached to the central region 18.

,; The structure of the centrally supported rolls is traditionally characterized by a circumferential region of the rolls, or more broadly in an area not supported by the outer casing of the roll; · The inner casing of the roll has an annular slot 22 which allows v: or the curvature of the outer sheath 20 in the direction 35 opposite to the inner sheath 16.

P4140 23.9.2003 5 115554

The roll supported in the center of the pattern functions in practice so that when the web or fabric web force acts on the roll through the outer sheath 20, for example, downwardly and supported by bearings 12 and 14 on the paper machine frame 5, the inner roll 16 tends to However, this bending tendency does not extend to the outer jacket 20 because it is supported on the inner jacket only at the center of the inner jacket, that is, in the region where the inner jacket is substantially the same as the axis 24 through the centerline of the bearings.

10

The outer sheath, in turn, not only transmits the web force to the inner sheath, the web force curves in the opposite direction, i.e. upwardly in the figure, because the stiffness of the peripheral parts of the outer sheath is smaller than the middle part supported by the inner sheath. Thus, the outer and inner sheaths of the roll curve in opposite directions. Also known are structures in which the outer shell of the roll is intended to be kept straight, regardless of the curvature of the inner shell.

The problem with the center-supported roller solution described is e.g. the fact that, when the roll in question is bent, it is at some point subjected to an extreme situation in which the inner surface of the outer edge of the outer sheath roll begins to drag along the outer surface of the inner sheath.

'Because of the difference in circumferential velocity between the surfaces due to the same: rotational speed and different large diameters, the drag between the surfaces results in both: *; energy consumption and surface wear. Neither of these factors is desirable, so the structure should be modified so that the effect of friction is: '·: 25 minimized wherever possible. In addition, it has already been mentioned that such; the critical characteristic frequency of a centrally supported roll solution is very low, with a high risk that the roll will resonate when operating.

. Figure 2 shows the center of the prior art DE-A1-199 27 897, 30 supported rolls. In principle, a similar solution is also disclosed in US-A-> * '' 3,161,125. The partially cut two-shell roll 25 shown in the figure is already composed; · 'As is known per se in the longitudinal central region or v: at least supported by the outer and inner sheaths, 26 and 28. In this embodiment, the roll 25:',! the outer sheath being fixedly mounted on the frame structures of the paper machine or the like, or the like. The outer jacket 26 of the roll 25 is provided at both ends with a shaft sleeve 6 115554 30 having a bearing 32 on its outer periphery to rotatably support the outer jacket 26 on the end portion 26 of the roll outer sheath 26, freely in the radial direction with respect to the body 5.

The term "support structure" is used above. It is intended herein, and in the following description of the invention, to mean any structure through which a roll is supported on a frame of a paper, board or post-processing machine. Thus, it may be a beam, bracket or the like attached directly to one of the 10 frame members, or it may be a lever articulated to a suitable frame member, or it may even be directly readable on the frame of a paper, board or finishing machine. part.

Figure 2 also shows the support of the inner sheath 28 through bearings 42 and a support structure 15 to the frame structures of a paper machine, a board machine, a post-processing machine or the like. The inner shell 28 of the roll 25 is provided at both ends with an end sleeve 38 to which is attached a shaft pin 40 extending through the interior of the shaft sleeve 30 of the outer shell 26. The shaft pin 40 is pivotally supported by its bearing 42 on In other words, the adjusting means 36 make it possible to move the inner sheath radially with respect to the end of the outer sheath, thereby causing the outer sheath to be bent in the desired manner.

As previously stated, such a roll adjustable with respect to the outer casing of the roll 25 does not work as desired because the outer casing cannot be resilient to the web load but only through the adjustment of the inner casing. To make the outer casing of the roll: *, · more flexible, the starting point is a roll whose inner casing is fixedly mounted on the frame structure and the outer casing's bearing can be "stretched".

Figure 3 schematically illustrates a two-shell roll support solution according to a preferred embodiment of the invention. In this embodiment, the roll 50 consists of outer and inner shells 52 and 54, a shaft sleeve 56 and a shaft pin 66, so that the structure thereof: corresponds in part to the solution of Figure 2. Now, however, the support for the 50 outer and inner shells of the roll has been significantly modified. The inner shell 54 of the roll 50 is supported by a bearing 68 rotatably on the fixed support structure 60 so that the outer end of the shaft pin 66 of the inner shell 54 cannot move radially, unlike the solution of Fig. 2 where it was possible to adjust in the circumference. Now, the shaft sleeve 56 of the outer sheath 52 is supported by the bearing 58 in the movable bearing housing 80. In this 5 embodiment, the bearing housing 80 is supported by guides 82 to the support structure 60 such that the shaft sleeve 56

The guides can also be replaced by pivoting the outer casing bearing housing. The pivot point 10 may be rotated about the bearing of the inner sheath. For example, it would be possible to pivot the bearing housing 80 shown in Fig. 3 from its lower edge to the support structure 60 so that the bearing housing 80 can pivot in a plane perpendicular to the plane of Fig. 3, whereby the outer jacket axis

15

According to a preferred embodiment, the rails consist of two spaced rails attached to the support structure 60, between which a slider is mounted on the bearing housing 80. It is, of course, also possible to provide the bearing housing 80 with said rails and the support structure 60 with 20 slides. Naturally, the most diverse conductor structures can be used within the scope of the invention. Thus, for example, it is also possible to provide only one rail and its support in the bearing housing 80 or: the support structure 60; : as a counterpart to the support structure 60 or bearing housing 80, two or more rollers i located on either side of the rail in use. Preferably, said conductors 82: 25 are provided on either side of the shaft bushing 56 and the opening 60 provided on the support structure 60, although in one particular embodiment only one-sided control is sufficient.

Thus, the embodiment shown in Fig. 3 is characterized in that the outer shell 52 of the double-shell roll 50 30 is supported by the bearing 58 in the bearing housing 80 which is allowed to move freely within the radius of the deflection of the shell 50 of the roll 50. ; · 'Direction. Here, as in the other embodiments shown in Figures 3-6, it is easy to determine the direction in which the shaft sleeve 56 and the end portion of the outer sheath 52 are allowed to move. By making a portion 35 of the guide structure 60 associated with the support structure 60, it is possible to adjust the amount and direction of deflection 115554 of the outer sheath 52.

If, for example, the roll bending force has a track force, the movement of the ends of the outer shell 52 in the direction of the track force can be practically prevented by arranging the conductors 5 82 in a plane perpendicular to the track force direction. In this case, the roll as a whole curves "inward", which in itself is not necessarily the desired direction of curvature. However, the curvature is likely to be relatively limited, since the stiffness of both rollers of the roll resists bending. If the guides, on the other hand, are completely parallel to the track force, the roll acts like conventional center-supported rolls 10, depending on its rigidity, the roll outer shell 52 curves more or less 'outward' in the direction of the track. The third option naturally lies between these two extreme options described above. Then the direction of the guides is somewhere between the direction of the track force and the direction perpendicular to it. It provides a controlled deflection of the roll outer shell 15. As a specific example, the position of the guides is such that the outer shell of the roll is not curved at all, but remains a straight cylinder.

Figure 4 shows a slightly further developed alternative to the outer shell 52 of the roll 50 from the embodiment of Figure 3. Otherwise, the construction used is the same and includes the same alternatives as the solution shown in Figure 3 except that the solution j * in Figure 4 employs a resilient element 86, preferably a spring pack, to support the outer housing 52 · * bearing housing 80. Preferably : the ends are selected to correspond to the inner sheath · supporting the outer sheath 52 in the middle; I stiffness. In this case, the resilient elements 86 are as elastic as the inner shell 54 Γ: 25, so that the outer shell 52 is practically non-bending.

• · •.

Naturally, it is also possible to dimension the resilient element 86 so that the outer sheath 52 is slightly bent but not as much as without the resilient element 86. added stiffness. When this resilient element 86 is further coupled to the guides 82 which are rotatable in the circumferential direction 30, adjustability of the roll deflection is obtained. very versatile.

With respect to the positioning of the resilient element 86, it is worth mentioning that it may: be located as shown in Figures 4 and 5, i.e. between the bearing housing 35 80 of the bearing 58 of the shaft sleeve 56 and the support structure 60, substantially in the same circumferential position; However, the resilient element does not necessarily need to position itself as an extension of the rails in the same axial plane, but may, for example, remain stationary when changing the direction of the rails. In this case, of course, the actual stiffness effect of the element in question changes as the direction of the conductors changes. A third alternative construction or positioning of the flexible element 5 is to place the element in connection with the conductors 82 either on the bearing housing 80 or on the support structure 60. In this case, the rotation of the rails does not affect the stiffness effect of the resilient element, since the element is always aligned with the direction of movement allowed by the rails.

Figure 5 further shows an additional alternative of the same type of new-shell roller 50 shown in Figure 3. In this embodiment, a damping element 90 is provided on the opposite side of the bearing housing 80 relative to the resilient element 86. The purpose of this element 90 is to dampen the vibration of the bearing 58 of the outer shell 52. This has been found to be necessary in some structures where the bearing 58, the resilient element 86 and the rails 82 are as smooth as possible, thereby allowing the bearing 58 to oscillate in the plane allowed by the rails and naturally extremely harmful. Preferably, the damping element 90 is a damping cylinder or a pair of cylinders.

Fig. 6 is a more detailed end view of a two-roll roll head support solution v according to a preferred embodiment of the invention, which generally corresponds to the solution schematically shown in Fig. 5. In the alternative embodiment shown in Fig. 6:, the bearing housing 80 of the outer shell of the roller 50 is supported by • flexible members 86 on both sides of the support structure. The movement of the outer sheath 25 and guide the direction of movement defined by the guide rails 82, in connection with which attenuate elements 90 are also provided, are formed on two sides of the bearing housing 80

t »I

cylindrical piston devices located within the bearing housing 80 and jv. support structure in many different ways. For example, it is possible to attach the cylinders • to the piston rod of the piston device and the hydraulic damping cylinder I | <30 in bearing housing. Then, when bores or other flow paths of the desired size are provided on the piston in the damping cylinder and attached to the piston rod, the structure acts as the desired effective damping of the hydraulic fluid flow::: 35. Of course, these hydraulic flow-inhibiting flow paths ίο 1 1 5554 P4140 23.9.2003 can, if desired, also be arranged to pass through the cylinder jacket or even from the outside via a separate throttle valve.

In other words, the moving bearing still has the hydraulic damping 5 described above which, despite the movement of the end, raises the specific frequency of the roll in the desired manner. Hydraulic damping can replace the linear bearing described earlier in this application by also positioning the dampers at 90 degrees to the linear conductor path. Thus, in order to implement the hydraulic training system described above, each cylinder end requires a pressure accumulator, a hydraulic piping and hydraulic cylinders 10 (2-4 units / end). The damping system is pressurized to 1 ... 50 bananas, for example.

Figure 7 is a side elevational view of the dual-shell roll support solution of Figure 6 on the one hand and a new type of double-shell roll shell solution on the other. With respect to the roll end support solution, it is only worth noting that Figure 15 illustrates a situation in which the roll 150 is secured to its support structure 60 and the roll is thought to be loaded with a web force perpendicular to the plane of the paper. In this case, both the guides 82 and the damping elements 90 acting in the form of a cylinder-piston device act in the direction of the track force.

In a known manner, a new type of dual-sheath roller 150 consists of an outer sheath 152 and an inner sheath 154. The roll sheaths mentioned in the solution of the invention:. v is not necessarily actually attached to one another, but to the inner sheath 154, which is substantially * »• 'centerline CL, is provided with a bulge 156 having an outer diameter substantially equal to the inner diameter of the outer sheath 152. Preferably, said outer diameter of the bulge 156 is: slightly larger than the inner diameter of the outer sheath 152, but only to the extent that the inner sheath 154 can be inserted into the outer sheath 152 without causing any bulge on the outer surface of the outer sheath 152. Other ways to connect the inner and outer sheath; with each other are e.g. bonding or shrinkage, or they can be integrated. already in the structure when the diapers are made,. 30 composite materials.

The solution described above can greatly simplify the manufacture of centrally supported rolls * I t v ·. In addition, in the solution described, the roll diapers can operate i. E. More independently in their own task, that is to say, without significantly affecting each other's tasks.

n 11 5554 P4140 23.9.2003

The roller construction of the type illustrated in Fig. 7 can be used in any object where center-supported rollers are generally used, and the roller structure illustrated particularly preferably is suitable for use with the inventive support solutions shown in Figures 3-6.

The double-sheath roll of the present invention is preferably of a composite structure such that at least the outer sheath comprises a fiber-reinforced polymeric material. The outer sheath may then be carbon fiber fibrous epoxy. The inner sheath 10 may be of the same material or of a homogeneous material, for example steel.

As seen above, a completely new type of support for dual-shelf rolls has been developed that can reduce or even eliminate many of the problems and disadvantages inherent in prior art rolls. The alternative support solutions described above by way of example provide the ability to control and control the deflection and deflection of dual-shelf rolls as required. Further, it should be noted that where in a conventional center-supported roll, the outer sheath is either supported only in its central area by the inner sheath or solidly supported by support structures, the solution of the invention 20 is supported not only in its central area;

:: This kind of support also considerably stiffens the roll structure, thus raising the critical characteristic frequencies for relatively small rolls, and. · Also gives the outer jacket some flexibility. In addition, a simple · ': 25 double-sheath roll and its manufacturing method are described above. From the foregoing invention. However, it should be noted from the description that the invention has been described in the light of only a few exemplary and schematic embodiments. Thus, it is clear that the invention may depart significantly from the foregoing, while remaining within the scope of the appended claims.

; 30 * i · *>

• f ♦ I

I | »·

Claims (20)

1. Devices for supporting the roll of the paper, cardboard or finishing machine, which roll consists of two sheaths, a so-called inner sheath (54; 154) and outer sheath (52; 5,152), which are supported on each other in the middle region of the roller (50; 150), the ends of which sheaths are supported against the frame structures of said paper, cardboard or finishing machine, characterized in that the outer casing (52, 152) of the roller (50) is supported at its ends by a shaft sleeve (56) and a bearing (58) against a support structure (60) in such a way that its position is adjustable. 10 Devices according to claim 1, characterized in that the outer casing (52; 152) of the roller (50) is supported at its ends in connection with the support structure (60) by means of guides (82) which allow the ends of the ends in the radial direction. Devices according to claim 2, characterized in that said guides (82) comprise one or more sliding rails or rods and in connection with the sliding pieces (s) operating, one of which is arranged in connection with the bearing housings (80) in the outer casing (52). ; 152) end bearings (58) and the others in connection with the support structure (60). 20 Devices according to claim 1, characterized in that the outer casing (52; 152) of the roller (50; 150) is supported at its ends in connection with the supporting structure (60) by means of: · resilient means (86). • · · j ·. ·; 25 Devices according to claim 4, characterized in that said resilient means (86) is a spring package, by means of which the bearing housing (80) in the bearing (58) of the roller: *. * (50; 150) outer jacket (52; 152) is supported against the support structure (60). • * t I ' Devices according to claim 1, characterized in that the outer casing (52; 152) of the roller (50; 150) is supported at its ends in connection with the supporting structure (60) by means of motion damping means (90). Devices according to claim 6, characterized in that said movement damping means (90) is a piston-cylinder combination. 35 i6 1 1 5554 Devices according to claim 1, characterized in that said piston-cylinder combination (90) also functions simultaneously as guides (82) which control the movement of the ends. Devices according to Claim 1, characterized in that said support structure 5 (60) comprises levers arranged on the respective ends of the roll, by means of which the levers (50; 150) are connected to the fixed support structures of the paper, cardboard or finishing machine. Devices according to Claim 1, characterized in that said roller (50; 150) is a withdrawal roller on the gloss and that its sheaths (52, 54; 152, 154) are supported at their ends by means of levers against paper or carton machine support structure. Devices according to any one of the preceding claims 1-10, characterized in that the ends of the inner sheath (54; 154) of the roller (50; 150) are movably supported by means of shaft pins (66) and bearings (68) against the paper or paperboard machine. support structure (60). Devices according to claim 1, characterized in that said roller (150) provided with two sheaths comprises a free-standing outer sheath (152) and inner sheath (154), which are arranged at a distance from one another by means of a bulge (156). arranged between their abutment surfaces on the center line of the roll (CL). Devices according to claim 12, characterized in that said protrusion (156) is arranged on the outside of the inner sheath (154). I t * • · Devices according to claim 12, characterized in that said bulge (156), ...: is arranged on the inside of the outer jacket (152). Devices according to any one of the preceding claims 1-14, characterized in that the roller (50; 150) is constructed of composite material. 30 Devices according to Claim 1, characterized in that the outer casing (52; 152) of the roller (50) is supported at its ends in connection with the support structure (60) by means of joints which allow the movement of the ends in the radial direction. Devices according to Claim 16, characterized in that the bearing housing (80) on the outer sheath (52; 152) of the roll it (1) 5554 (50) is secured to the supporting structure in such a way that the bearing housing (80) of the outer sheath can move in a plane. perpendicular to the axis of the roller inner body. 5 A method for controlling the bending of a roller, said roller (50; 150) comprising two sheaths, a so-called outer sheath (52; 152) and inner sheath (54; 154), which are supported on each other in the middle region of the roller, characterized in that the position of the ends of the outer sheath (52,152) is radially and / or circumferentially installed relative to the fixed shaft ends of the inner sheath. 10 19. Method according to claim 18, characterized in that the movement of the ends of the outer sheath (52; 152) is limited by a resilient means (86). 20. A method according to claim 18, characterized in that the movement of the ends of the outer jacket (52; 152) is damped by resilient means (90). 20 i I · »i l t» * ·; »· >> · · I · 4« «'* f t •> *» · * »*