AT507835B1 - METHOD FOR SETTING THE TORQUE OF A ROLLER / WRAPPER OF A FIBERMAKING MACHINE - Google Patents

Abstract

The invention relates to a method for torque adjustment of a retractor / Aufwickler, wherein on the retractor / winder, a fiber web is wound by means of one or more winding nips in a web roll. In the method, the take-up force is adjusted such that tangential tensile forces directed from the at least one winding nip onto the web roll, i. H. the web roll of at least one winding nip concerned outer peripheral loads, regardless of the running speed and / or acceleration / deceleration remain set.

Description

Austrian Patent Office AT 507 835 B1 2010-10-15

description

METHOD FOR SETTING THE TORQUE OF A ROLLER / WRAPPER OF A FIBERMAKING MACHINE

The invention relates to a method according to the preamble of claim 1.

Reelers are known from the prior art, which are used in connection with fiber web machines, such as paper and cardboard or cardboard machines, wherein a fiber web produced by the fiber web machines, such as a paper machine / board machine, as a Web is wound in full width on machine rolls for further processing. The web is wound around a reeling shaft, e.g. a coil iron / roll, either by means of a surface tension in a winding nip between a reeling drum and a web roll produced or by using a central drive, wherein the reeling shaft is provided with a drive. In the context of fiber web machines, such as paper and board machines, dispensers or unwinders are also used, by means of which the web roll wound up by the reel is unwound in a later treatment step for further processing of the fiber web.

[0003] The prior art are known in the art as having idler winder and multi-station winder which are used in conjunction with the winder or slitter rewinder of fibrous web machines. On a slitter, a web running across the entire width is cut into narrower partial webs, and web rolls, so-called customer rolls, are formed on the carrier roll winders and multi-station winder from the partial webs. The winders of take-up roll cutters have guide rolls carried by two support rolls from which the web is wound into a web roll through a nip between a support roll and the produced fiber web roll. Also, a belt assembly, a so-called set of belt rollers, arranged around two guide rollers may be used as the guide roller. In winding, center winding may also be used in which the formed web roll or web roll being formed is supported from the center thereof and the fibrous web is wound into the web roll through a nip between a winding roll and the formed web roll. Both in conjunction with Leitwalzenaufwicklern and Mehrstationaufwicklern a pressure roller can be used to produce the roll, with the role of the web roll produced is pressed and by means of which the web roll can be subjected to a surface tension.

As is known in the art, as a basis for the torque adjustment of Leitwalzenrollenschneidern or winder and Mehrstationaufwicklern the fact has been used that the terms or by the inertia and the winding resistance of a Set (customer rolls on the rewinder) were generated evenly on the Leitwalzenrollenschneidern between a rear guide roller (on which the web comes first) and a front guide roller or on the Mehrstationenaufwickler between a winding roller and a pressure roller distributed. In arrangements known from the prior art, the take-up force (winding force in an ideal state (ie, when no losses or inertial forces occur in the state) is the sum of the circumferential forces which rotate the web roll excluding the peripheral forces of its nip, which is the incoming web first touched) empirically set as a function of the diameter of a web roll being produced. In connection with the winding, especially in deceleration and acceleration phases related to the block change, additional and decreasing terms are also set empirically at the moment setting of the winder, attempting by these terms the changes in the structure of the web roll produced to correct, which are caused by a change in running speed.

A problem with the above-mentioned adjustment strategy is that this is not based on a technical technical argument as a 1/15 Austrian Patent Office, but it is an arbitrary, purely empirically defined strategy is. For this reason, the structure has changed particularly in connection with delays and accelerations and situations in which the running speed has changed considerably for some other reason. The change in the structure of the web roll is in particular caused by the fact that in these situations in which the running speed is changed, tangential tensile forces which influence the roll change. Traction refers in this application to a stress distribution formed in a contact caused by external stresses / strains directed at the web roll. Tangential surface tensile forces, in turn, are external circumferential loads that affect the web roll produced by nips. When attempting to correct the takeup force according to acceleration and deceleration by additional and / or decreasing terms, in the context of adjustment strategies known from the prior art, such an adjustment strategy is at most of paper or paperboard strength functions wound up in the situation in question as well as the acceleration, deceleration and running speed in question. Thus, the moment adjustment strategies of reelers / rewinders, guide roll wipers and multi-station winder were incomplete, and they may have produced web rolls having an uneven structure.

The object of the invention is to provide a method for torque adjustment of a Aufrol- lers / winder, Leitwalzenaufwicklers / Mehrstationenaufwicklers, in which the above-described problems and disadvantages of known from the prior art arrangements have been eliminated or at least minimized.

A particular object of the invention is to produce a torque setting of a Aufrol- lers / winder, in particular the adjustment of the winding force, which keeps the size of the web roll surface tensile forces regardless of speed changes and inertia, which generates by accelerations and decelerations become.

In order to achieve the above objects and those which will appear later, a method according to the invention is characterized mainly by what is stated in the characterizing part of claim 1. According to the invention, the moment adjustment of a retractor / rewinder is provided, in particular the setting of the take-up force, in which the magnitude of surface tension forces related to the web roll is independent of speed variations and inertia terms generated by accelerations and decelerations. In the torque adjustment according to the invention, the winding force is used as a winding parameter and the winding force is adjusted so that in the most important nips from the standpoint of the web roll structure, most suitable in Leitwalzenrollenschneidern first, the nip between the rear guide roll and the web roll and second the nip between the front guide roller or the pressure roller and the web roll and in Mehrstationaufwicklern mainly the nip between the winding drum or roller and the web roll and second, the nip between the pressure roller and the web roll, the web roll directed tangential tensile forces as the set winding force independently remain of the running speed or its derivative.

In accordance with the object of the invention, because different outer circumferential loads from different nip rollers are directed onto the web roll, it is attempted to control the loads in question without the speed variations occurring during winding having an effect on the structure of the web roll produced. Calculated moments according to advantageous embodiments of the invention form operating instructions in which different factors should be included in the adjustment strategy to achieve the desired structure of the web roll by adjusting the winding force.

In this description, rotational resistances refer to a requirement for an additional moment caused by bearing friction and so forth. Winding resistance, d. H. Rolling resistance, refers to resistance moments generated in nip contacts. Winding resistances are zero when the rotary cutter or slitter rewinder is operated without paper. The rotational resistance of the web roll is generated by Drehreibung of sockets, sockets or core closures. A rotational resistance does not occur on rolls provided with a steel surface, but occurs in sets of belt rolls and soft-surfaced rolls.

The invention will now be described in more detail with reference to the figures of the accompanying drawings, the invention being, however, not to be construed narrowly to the details thereof.

Fig. 1 shows schematically a support roll winder.

Fig. 2 shows schematically a multi-station winder.

Fig. 3 shows schematically a structural sketch of the Mehrstationenaufwicklers.

Fig. 4 shows schematically a structural sketch of the support roll winder.

Fig. 5A schematically shows the moment of the support roll winder as a function of the diameter in an example.

Fig. 5B schematically illustrates the speed and winding force of the carrier roll winder as a function of diameter in one example.

As shown in Fig. 1, a guide or Aufrollaufzenaufwickler two guide or support rollers, namely a rear support roller 12, on which a web W is wound first, and a front support roller 11, with the support of a web roll 10 is wound up. The direction of movement of the web W is indicated by the reference SW and the direction of rotation of the rear support roller 12 is denoted by S. By means of a pressure roller 15, the nip load at the start of take-up is controlled, and as take-up progresses, the main task of the pressure roller 15 is therein To hold web roll 10 in place, held by the support rollers 12, 11. On the support roll winder of a slitter winder, plural web rolls 10 are sequentially provided in the axial direction of the web roll, and these partial web rolls are referred to as customer rolls, and the web rolls simultaneously on the rewinder are one set.

Fig. 2 shows schematically a Mehrstationenaufwickler, on which the web is wound by means of a winding drum or reel in a web roll 10. The winding or coil core of the web roll 10 can be provided with a center point drive or central drive 18 for rotating the web roll 10. Furthermore, the rewinder shown in the figure has a pressure roller 15. The direction of movement of the web W is denoted by the reference SW.

In the next description of Figures 3 to 4 and the equations, the following symbols are used:

Symbol Description Unit F Winding force N / m Frr Static surface force of the pressure roller / Width N / m F pd Static surface force of the front belt roller set / width N / m Ji Moment of inertia of the web roll / Width N / mxs: 01 Load angle coordinate of the track roller wheel Mi Central moment or center moment of the web roll / width Nm / m 3/15

Austrian Patent Office AT 507 835 B1 2010-10-15 Μιμ Rolling resistance torque of the web roll / width Q3 Tangential force between the surface tension roll (pressure roller) and the web roll / width Ri Web roll radius m R2 Radius of the winding roll or back roll m R3 Radius of the surface tension roll or pressure roll R4 Radius of First Belt Roller or Front Roller 02ψ Winding Resistance Force in Nip Roller or Back Roller N / m 03ψ Winding Resistance Force in Nip Roll of Surface Tensile Roller or Pressing Roller / Width 04ψ Winding Resistance Force in Nip Roller or Front Roller / Width W Web tension before winding roller or rear roller Roller J2 Moment of inertia of the winding roller or rear roller ze / width θ2 Loading angle coordinate of the winding roller or rear roller ze M2 Moment of the winding roller or rear roller / width Μ2μ Rotation resistance torque of the winding roller or rear roller

Roll / width M2rM roll resistance torque of the winding roll or rear roll (only significant if a soft coating is on the roll) J3 mass moment of inertia of the surface tension roll or pressure roll θ3 load angle coordinate of the surface tension roll or

Pressure roll M3 Moment of surface tension roll or pressure roll / width Μ3μ Rotation resistance torque of the surface tension roll or back roll / width Μ3ψ Roll resistance torque of the surface tension roll or rear roll / width (only significant if a set of belt rolls or a soft coated roll is provided) J4 Moment of inertia of front roller or pack

Belt rollers θ4 Loading angle coordinate of the front roller or first

Belt roller M4 Moment of front roller or set of belt rollers / width Μ4μ rotational resistance torque of front roller or belt

Set of Belt Rolls / Width Μ4ψ Rolling resistance torque of the front roll or set of belt rolls / width (only significant when a set of belt rolls or a soft-coated roll is provided) Q3stat Tangential force of the surface drawing roll or pressure roll at the standard non-friction / width speed Pr2 Winding resistance coefficient in the winding nip or nip of the rear roll pR3 Wind resistance in the surface tension roll or nip nip 4/15

Nm / m N / mmmmm N / m N / m N / m N / m Nm / mx s2 wheel Nm / m Nm / m Nm / m Nm / mx S2 wheel Nm / m Nm / m Nm / m Nm / mx s2 Nm / m Nm / m Nm / mn / m AT 507 835 B1 2010-10-15 Austrian

Patent office ÜR4 Coil drag coefficient in the nip roll or nip of the front roll - p2 Nip load in the nip or nip roll N / m p3 Nip load in the surface nip roll N / m p4 Nip load in the nip roll nip or nip n / m Q +; Q ', Qw Rewinder internal force variable N / m Tin, T0ut Rewinder internal force variable N / m Fig. 3 shows a structural sketch of the multi-station winder for the part of the important terms from the viewpoint of the rotation equations. The friction and Wickelwiderstandsterme the rollers and the web roll are not drawn. There may be a center moment Mi or surface tension Q3 in the web roll (both may be present at the same time). The rotational equilibrium equation of the web roll is: where Μίμ is the rotational resistance moment of a wind-up station and Q2rM and Q3rM terms which are generated in the winding roll and surface tension rolls and caused by the winding resistance of the paper roll. For example, as described in the publication Johnson, K.L., Contact Mechanics, Cambridge University Press, in a case where hysteresis losses are less than 5%, these terms may be expressed as follows: ö2r / i = Οίτμ = > (2) where pR2 and Pr3 are winding resistance coefficients in winding roll and surface nip rolls, and P2 and P3 are nip loads in these nips, respectively. In the equation (2), it would be desirable that these winding resistance coefficients be constants. However, they are probably at least dependent on the running speed and possibly a little on winding parameters. Although equation (2) would not be exactly valid, the sum of the winding resistance terms can be calculated relatively accurately because the other terms of the rotation equation can be set relatively easily. From the equilibrium equation of a tail below the nip, inertial terms may be omitted as invalid variables. Then the equilibrium equation is as follows: r "-β * = β '+ ^ (3) Similarly, the equilibrium equation of a tail of a winding roll wrapper can be written without centrifugal and inertial terms: T, = W-Qw. (4) The rotation equilibrium equation of the winding roller is: J292 = M2-QwR2 + Q-R, -Μ1μ-Μ1τμ, (5) where Μ2μ is the rotation resistance of the winding roller and the last rolling resistance is 5/15 > Austrian Patent Office AT 507 835 B1 2010-10-15 term is only necessary if the winding roller is a coated or covered roller. The rotational equilibrium equation of the surface tension roller is J303 = Mi - Ö3Ä3 -Μίμ ~ Μ1τμ, (6) where Μ2μ is the rotational resistance of the surface tension roller and the last rolling resistance term is only required when the surface tension roller is coated or strapped.

According to the invention, the task of Wickelwalzeneinstellung is to keep the size of the web tension influencing Oberflächenzugkräfte regardless of speed and inertia generated by acceleration and deceleration terms. In this description, there is no need to go into the actual contact mechanics because equations related to the contact mechanics can be considered independent of inertial terms and payloads directed to the web roll.

The rotation equation (1) of the web roll is changed so that all surface loads of the web roll, which relate to the winding nip, remain on the left side. This results in:

If it is then desired that the same surface loads prevail in the reeling nip at all running speeds and with uniform speed, deceleration and acceleration, the surface tension Q3 must be set as follows:

Wherein F is the desired (static) winding force. If the winding force is obtained with the moment Mt, it must be set as follows:

If it is desired to use both surface tension Q3 and center moment Mi, the loads of both the winding roller and surface tension nip can be kept independent of the change in running speed. The equation (7) is changed so that also Q3 is on the left side of the equation:

ΓοιΛ-0 + -03- This means that then Mi must also be selected according to the equation (9). Furthermore, by changing the moment equation (6) of the surface tension roller as follows

Clearly indicates that Q3 remains constant when the moment of the surface tension roller is set as follows: ______________________________________

MiÄ, a

Zstat Jβ% M (12) where Q3stat is a surface tension when traveling at standard running speed and without friction.

Equations (3) and (4) give: Q - Qw = TMt-Q + -W (13) Substituting this result into the moment equations of the winding roller gives (14) This results in accordance with the invention calculated moments for the surface multitask winder: M2 = Jβ2 + M2 / I + WR2-FR2 + M2rfl (15) M3 = Jβ3 + FR3 + ^ - Jλ + Μ1μ + QlrMR3 + βsr / A rP (16) * 1 [0039 ] This further gives, in accordance with the invention, calculated moments for the multi-station winder provided with a central drive: M ^ FR + Jβ + M + Q + Q ^ R, (17) M2 = Jβ1 + M2fl + WR2-FR2 + M2rft ( 18). On the idler, Fig. 4, the torque and rotation and rolling resistances of the front roller are also included in the rotational equations. The moment Mi is considered zero in this view. The rotational equilibrium equation of the web roll will now become Jβi = (Q + ~ Tout) R \ + QA + QiRi ~ Miss

QprPR \ ~ QirPR1 ~ Q * rPR1 > Where Q4 is the tangential tensile force of the set of front or belt rolls and Q4rM is the winding resistance of the paper roll produced in this nip. The equilibrium equations (5) and (6) of the winding and pressure roller remain unchanged. As a new equation, the rotational equilibrium equation of the set of front or belt rolls is considered. Jβ4 ~ M4-Q4R4-M4M ~ M4rp, (20) where M4 is the moment of the set of front or belt rollers, Μ4μ is the rotation resistance torque and Μ4φ is the winding resistance torque. In the case of the support roll winder, selecting a suitable winding force strategy is more difficult because multiple nips affect the web roll structure. According to studies published in the Oklahoma State University Web Handling Research Center. Among other things, the nip roll has an important effect on the web roll structure with a small web roll diameter, among other things, as indicated in the Semiannual Technical Review and Industry Advisory Board Meeting, October 2000, Table 2. Obviously, with a larger web roll diameter, the part of the back roll is dominant. Take the rotation equation (19) of the web roll as a starting point and convert it so that all surface loads of the web roll related to the nip of the back roll remain on the left side

Ff) M ζ, -β * = a + a - ^ - ητ - öu - (21> Λ, Λ, [0043] If desired, the same surface stresses in the nip of the rear roll at all running speeds and at uniform speed , Deceleration and acceleration, the sum of the surface tensile forces in the other nips must be set as follows: Q3 + Q4 = F + ^ + -Y- + Q2 ^ + Q3rM + Q4rM '(22) where F is the desired static Since there is a sum of surface tensile forces on the left side, the realization of the winding force is not clear.

Next, some application examples a-c of the invention will be discussed.

A) Adjusting the surface tensile force and winding force of a pressure roller In practice, this is a case carried out in a simple manner. The rotation equilibrium equation (6) of the pressure roller is switched (23) M3 Jβ, M3m M3r / l ^ λ, R3 r3 r3 It is clear that if M3 is chosen such that (24) YES Μ1μ, Myr * 3 [ 0049] the surface tensile forces are as follows 03 = ^ r > (25)

T ä M

Thus, Frr is the static surface tensile force of the pressure roller.

B) adjusting the surface tension and winding force of a front roller or a

Belt Roller Carrying out this case requires relatively high performance of the pinch roller motor. By rearranging the terms, the moment equation (20) of the set of front or belt rolls (26) yields Jβi Μ4μ M, rfl ^ K R * R4 ^ 4 It is clear that when M4 is selected such that M ± R < = F, I YES j R < K R < (27) The surface tensile forces are then (28) a = -f-r> + ^ - + ^ + a "+ ö ^ + a". Et Q * = Ffd Thus, Ffd is the surface tensile force of the set of front / belt rollers.

C) Driveless Pressure Roller This is a common arrangement e.g. on cardboard roll cutters. Now, the surface tensile forces q _Jssj Μ3μ Μ, τμ ^ 3 ~ R, R, R, JA Μ * (29) Q <= F + ^ + ^ - + Q2rfl + Q3rfI + Q <ril + - ¥ - + '3 τμ

Rr Ri '4τμ

This results in calculated moments according to the invention for such a nip winder in which the surface tensile force of the nip roll is adjusted, i. H. in the embodiment a M2 - J-bi + Μ2μ + WR2 ~ FR2 + ^ 2τμ (30) M3 = FnR3 + JA + Μ3μ + M3fm (31)

Mt = Jß, + (FF ") Ä, + §- / 4 + M," + §A "+ (ß! R" + & "+ & ,,) *, + M" f (32) Λ This provides, according to the invention, calculated moments for such a nip roller winder in which the surface tension of the set of front / belt rollers is adjusted, i. H. in the embodiment b 9/15

Claims (8)

Austrian Patent Office AT 507 835 B1 2010-10-15 M ^ Ja + M ^ + WRz-FRz + M ^ (33) This gives, according to the invention, calculated moments for such a carrier roll winder in which there is no nip roller drive, i.e., a nip roller. H. in the embodiment c (36) (37) The examples shown in Figs. 5A and 5B are of a support roll winder in which the surface tensile force and the winding force of the pressure roll are adjusted based on the equations (30) - (32), wherein the winding force F = 500 N / m, the web tension W = 300 N / m, the surface force of the pressure roller Frr = 100 N / m, the running speed v = 40m / s, the acceleration a = 1 m / s2, the density 1000 kg / m3 and the Web thickness is 0. 1 mm. The thin lines shown in Figs. 5A and 5B describe a common type of control in which the surface force Frr = 0. In the common type of moment control, d. H. executed without the method according to the invention, the winding force is too small for accelerations and too large for delays. The most significant defectiveness without the method according to the invention occurs with a large web roll diameter at which the inertia of the set is high. In particular, in the completion delays, a controller without the method according to the invention can easily produce too hard a surface of the web roll. The invention has been described above only with reference to some of its advantageous embodiments, but the details of which the invention should by no means be narrowly limited. A method of adjusting a winding torque in one or more winding nips of a reel-up / rewinder for winding a fibrous web into a web roll, characterized by the following steps: adjusting the winding force, i. the sum of the peripheral loads that rotate the web roll excluding the peripheral loads of the winding nip that the incoming web first touches so that the tangential tensile forces, i. H. external circumferential loads which affect the web roll formed by the winding nip and which are dependent on at least one wiper. Austrian Patent Office AT 507 835 B1 2010-10-15 ckelspalt are directed to the web roll, d. H. outer circumferential loads affecting the web roll from at least one winding nip, irrespective of the running speed and / or acceleration / deceleration, forming a calculated winding torque to achieve a desired web roll structure by adjusting the winding force. 2. The method according to claim 1, characterized in that in the method, the winding force is set on a Mehrstationenaufwickler. A method according to claim 1 or 2, characterized in that the method generates a calculated moment to achieve a desired web roll structure by adjusting the winding force for a surface drawn multiturn winder based on the following equations: Mi ~ Ji ^ 2 + M2fl + WR2-FR2 + Mlrfl (15) A method according to any one of claims 1 to 3, characterized in that the method generates a calculated moment to achieve a desired web roll structure by adjusting the winding force for a multi-station rewinder provided with a central drive based on the following equations: Mi = FA + YES + Mlfl + Q2rMR {+ Q3rpA (17) M2 = J262 + M2fi + WR1-FR2 + M2ril (18) 5. The method according to claim 1, characterized in that in the method, the winding force is set on a support roll winder. A method according to claim 1 or 5, characterized in that in the method a calculated moment is generated for a support roll winder in which the surface tensile force of a pressure roll is set based on the following equations: M2 = J2e2 + M2tt + WR2-FR2 + M2rjJ (30) M3 = FrrR3 + Jβ2 + Μ3μ + M3rfl (31) 11/15 (32) Austrian Patent Office AT 507 835 B1 2010-10-15 A method according to any one of claims 1, 5 or 6, characterized in that in the method a calculated moment is generated for a carrier roll winder wherein the surface tensile force of a set of front / belt rolls is set based on the following equations: M2 = J2ei + M2fl + WR2-FR1 + M2rii (33) M, = JÄ + (FF) 1) R, Aä + M "+ (& + B" + 0 ,,,) 11, + M, rll AA (34 ) MA-FfdR4 + JAG4 + M4β + M4 ^ (35) A method according to any one of claims 1, 5 to 7, characterized in that in the method a calculated moment is generated for a carrier roll winder in which no pinch roller drive is present, based on the following equations: M2-J202 + M2 + WR2- FR2 + M2 rn (36) ft M, = JÄ + FR, Λ YES 3 YES + M4, + ^ M, "+ (ß" + ß, "+ ßj Ä, + AA Ai ...... DD Μ + -M + -iM 1ν14τμΎ q 1ν1ΙτμΎ "- l l / i Aj A (37) See 3 sheet drawings 12/15