FI118962B - Procedure for controlling the torque of a wheelchair in a fiber web machine - Google Patents

Description

118962

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

It is known in the art to use reels for fiber web machines, such as paper and board machines, in which a web made of fiber web machines, such as a paper-10 machine / board machine, is rolled into a full-width web for machine processing. The web is wound around a winding shaft, for example, a reel iron / roll, either through a surface draw in a winding nip between the winding cylinder and the forming web roll, or utilizing a center drive, wherein the winding shaft is also provided with drive. In the case of fiber web machines, such as papermaking and board machines, unwinding rollers are also used in which a roll of reel rolled on a reel is unwound at a later stage of processing for further processing of the fiber web.

t »·

The prior art known in the art of fiber web machine winders ·· «: 20 is used for carrier rollers and center rollers. • • *. * ·; the rolls being narrower than the wide web, and the sub-webs using carrier roll cutters and i center rollers form web rolls, so-called customer rolls. Stapler Cutters- • · · *. ϊ. The reel comprises carrier rolls supported by two carrier rolls to roll the web into a web roll through a nick between the other carrier roll and the resulting fibrous web roll. The carrier roll can also be used around two guide rolls. belt strapping, the so-called belt roller. For winding, ♦ · '"· * can also be used for center roll, where the forming web is supported at its center and the fibrous web is wound onto the web via the nip between the roll and the formed web. ···: ... ·. *: 30 is used to form the rolls by means of a printing roller which is used to form the web *: * ·: and which can be used for surface drawing on the web.

2 118962

As is known in the art, torque control of staple cutters and center rollers has been based on the fact that the terms derived from the slowness and roll resistance of the moving (customer rolls) are evenly distributed between the stub roll (which comes first) between. In the prior art, stiffened winding force (winding force, ideally (i.e., no loss or inertial force) excluding the sum of the circumferential forces rotating the roll, except the circumferential force of the nip to which the incoming web first touches) is set to the function of the empirically formed roll. In rollover, particularly in deceleration and acceleration phases related to shifting, there are also experientially set additional or subtractive terms for the torque control of the roller which are intended to crash the change in the structure of the resulting roll due to a change in travel speed.

15

The problem with the control strategy outlined above is that it is not based on any customs-related argument, but is in itself an arbitrarily purely empirical strategy. As a result, the roller structure has changed, especially in decelerations and accelerations, and in situations where • **: 20 other reasons have led to significant changes in travel speed. The change in the roll structure «· ·. * '· Is due in particular to the fact that in these situations, when the travel speed changes, the tangential tracts acting on the roll change. For the purposes of this specification, the term "stress" is defined as the stress distribution produced by contact due to external loads / stresses on the roller. The tangential surface fractures, in turn, are external circumferential loads acting on the roller 25 formed through the nipples. In the context of known adjustment strategies known in the art, the aim is to increase the roll force by increasing and / or decreasing the acceleration and deceleration in terms of acceleration and deceleration. «At standstill with the type of paper or board being rolled and the acceleration and deceleration at that speed and speed. As a result, torque control strategies for reels, carrier rollers, * · 3 118962 tines and center rollers have been inadequate and may have resulted in uneven rolls.

The object of the invention is to provide a method of torque control of a reel, carrier roller / center roller wherein the above disadvantages and problems of the prior art solutions are eliminated or at least minimized.

A particular object of the invention is to provide a torque control of the roller, επί 0, in particular a roll force control that keeps the magnitude of the surface fractures acting on the roller independent of velocity changes and the inertia induced by acceleration and deceleration.

In order to achieve the above and later objects, the process according to the invention is essentially characterized by what is stated in the characterizing part of claim 1.

According to the invention, there is provided a torque control of a roller, in particular a roll force control, in which the magnitude of the surface fractures acting on the roller is dependent on the velocity changes of 20 tons and the inertia induced by acceleration and deceleration. In the torque control according to the invention, the winding force is used as a single winding parameter and the winding force is adjusted so that 9 ·, ·. · * In the most significant nipples, preferably in carrier roll cutters, are preferably the rear nipple between the carrier roll and the web the nip between the press roll 25 and the web roll, and in the center rollers the nip primarily between the winding cylinder or roll and the web roll and alternatively the nip *, # • · * ··. * nip, tangential strokes on the roll remain .

In accordance with the object of the invention, since the roll is subjected to different peripheral loads from different nip rolls, it is intended to keep these loads under control 4 118962 without affecting the structure of the roll formed during the winding. computational moments according to the applications provide guidance on the use of what different factors should be included in the adjustment strategy to achieve the desired roll structure by adjusting the winding force.

5 For the purpose of this description, the rotational resistance refers to the need for additional torque due to bearing friction and the like. Rolling resistance, or rolling resistance, refers to the resistance moments generated in nip contacts. The rolling resistors are zero when the mower is driven without paper. The rotational resistance of the roll is caused by the rotational friction of the chucks or shells. Steel surface rollers do not have rotational resistance, but belt rolls and soft surface rollers do.

In the following, the invention will be described in more detail with reference to the figures in the accompanying drawings, in which details, however, are not intended to be narrowly limited.

Fig. 1 is a schematic representation of a carrier winder.

: * * *: Figure 2 is a diagram illustrating a center roller.

··· 20 h ·: \ j Figure 3 is a schematic representation of the free roll pattern of the center roller.

Fig. 4 is a schematic representation of the free-throw pattern of a carrier roller.

Fig. 5A schematically shows the torque of the carrier winder as a function of diameter in one example case.

• M • M *

Fig. 5B schematically shows the speed and winding force of a carrier reel as a function of diameter in one example case.

30 • «• · 118962 5

As shown in Figure 1, the carrier roller comprises two carrier rolls, a back carrier roll 12 for which the web W to be rolled first comes first, and a front carrier roll 11 supported by the web roll 10. The direction of travel of the web W is denoted by the reference SW and the direction of rotation of the rear carrier roll 12 by the reference S. The roller 15 controls the nip load at the beginning of the winding and as the winding progresses. Typically, the winder winder of the winder has a plurality of web rolls 10 successively in the axial direction of the roll and these sub roll rolls are referred to as customer rolls and at the same time the web rolls in the roll are moving.

10

Figure 2 schematically shows a center roller in which the web is wound through a winding roller or roll 17 to a web roll 10. The winding core of the web 10 may be provided with a center drive 18 for rotating the web roll 10. Further, the reel shown in the figure comprises a printing roll 15. The direction of travel of the web W is denoted by reference 15 by SW.

In the following description of Figures 3-4 and its formulas, the symbols used are as follows: · Symbol Explanation Unit • · \ * ·; F Rolling Force N / m • · ϊ.ϊ: Fn- Static Surface Force / Width N / m * ·· '· * FPd Static Surface Force / Width N / m * ··· · ry ***** Ji Roller Inertia / Width Nm / mxs 25 0j Roller Angle Coordinate rad • · ';; *' M] Center Roll Torque / Width Nm / m · * ·; ** Μιμ Roller Rotation Torque / Width Nm / m Q3 Surface Roller (Weight Roller) · Roller · Tangential force / width N / m *: · *: 30 Ri Roll radius m R2 Radius of roller or rear roller m 6 118962 R3 Radius of surface draw roller or pressure roller m R4 1. Radius of belt roller or front roller m (^ μ Rolling resistance force in nip of roller roller or rear roller N) / m 5 ζ> 3Γμ Rolling resistance on nip of roller puller or pressure roller / width N / m ζ> 4Γμ Rolling resistance on nip of belt or front roller / width N / m W Tension before roller or rear roller N / m 10 J2 Roller roller / rear roller m / m Roller roller or rear roller na angular coordinate rad M2 Roller or rear roller torque / width Nm / m Μ2μ Roller roller or rear roller 15 Rotational resistance torque / width Nm / m Μ2τμ Roller roller or rear roller rolling resistance / width (only relevant for the roll with N m / m) . * · *. xs2 * m • * · ** · *. 20 Θ3 Angle Coordinate of Surface Draw Roller or Pressure Roller rad • · · * ·. · M3 Surface Draw Roller or Pressure Roller Torque / Width Nm / m • ·: *: Μ3μ Rotation Tightening Roller or Rear Roller «·» · Rotation Torque / Width Nm / m: ***: ™ Rolling Tension Roller or Rear Roller ·· · ”25 Rolling Torsion Torque / Width (relevant only for belt roller or» · ·; ... i soft-coated roller) Nm / m ··· J4 Mass moment of inertia of front roller or belt roller Nm / mx s2 «·· * 04 Front Angle or 1st Belt Roller Angle Coordinate rad ··· 30 M4 Front Axle or Belt Belt Torque / Width Nm / m • · Μ4μ Front Axle or Belt Roller • · 118962 7 Rotational Torsion / Width Nm / m Μ » in the case of belt rollers or soft-coated rollers) Nm / m 5 Q38tat Tangential force of surface pulling roller or printing roller at constant speed without friction / width N / m μια Rolling resistance coefficient in a roller or rear roller nip

Pr3 Rolling resistance coefficient on roller or roller nip pR4 Rolling resistance coefficient on belt roller or front roller nip 10 P2 Nipple load on roller or roller nip N / m P3 Nipple load Q / N wound roller N / m / m

Tin, Tout Internal forces of roller N / m 15

Figure 3 shows a free-face pattern of a center roller for terms relevant to rotation equations. The terms friction and winding resistance of rolls and rolls are not drawn. The roll may have a center torque Mi or a surface draw Q3 (also t * · * * · · * both can be simultaneously). The roll equilibrium equation is! * · * · '20 * # · = + (ö +) / ?, + 63 / ¾ —Λ / 1μ ~ β2, · μ ^ 1 ~ 03ίμ ^ 1 »O) * · · • ·· · •! * · 4 · · ** ·. * ··, where Μιμ is the rotational resistance of the winding station and Q3rH are the terms arising from the paper · · reel winding resistance on the winding roll and surface pull roll nipples.

• · * · 25 For example, Johnson, K.L., Contact Mechanics. Cambridge University • • 9: ***; As described in Press, Cambridge, 1985, pages 306-311, these terms can be represented if the hysteresis losses are less than 5% as follows: (? 2φ = \ ^ R2 ^ 1 Qlm ~ M-ä3 ^ 3 * (¾ • * 30 • · 8 118962 where μΚ2 and are the winding coefficients on the winding roller and surface pull roll nipples and P2 and P3 respectively the nip loads on these nipples. However, they are probably at least dependent on the running speed and possibly somewhat on the winding parameters.

Although Formula (2) is not very valid, the sum of the rolling resistance terms can be estimated quite accurately, since other terms in the rotation equations are relatively easy to determine. From the equilibrium equation of the strip under the nipple, inertial terms can be omitted. Then the equation of equation is: 10 TM-ff = Q- + T „(3)

Similarly, the equilibrium equation for a web roll wrap can be written without the centrifugal and inertia terms: 15 T „= W-Q ,. (4)

The roll equilibrium rotation equation is

• M

, *** J-βί = M2 ~ Qw & l +5 - ^ 2 - - ^ 2µ ~ ^ 2τ · μ »(^) • · · \ *! 20 • ♦ ♦ ·· • y where Μ2μ is the rolling resistance of the roller roller and the last rolling resistance term is required. .]] Only if the roller is coated. The equilibrium roller rotation equation equals • »· ··· • · = A / 3 ~ Q3R3-·3μ, (6) 25 ·, where Μ3µ is the surface draw roll rotation resistance and the last rolling resistance term • I · is only required if the surface draw roll is coated or belted.

···· • · ·· »

According to the invention, the aim of the roll force control is to keep the magnitude of the surface traction acting on the roll independent of the velocity changes and the inertia induced by acceleration and deceleration. There is no need to go into the actual contact mechanics in this review, since the contact mechanical fit equations can be assumed to be independent of the inertia terms and the net loads on the roll.

5

Group the roll rotation equation (1) so that all the roll surface loads associated with the roll roll nip remain on the left side. This gives c-e * -a, oo Λ, J \ Λ, 10

Thus, if it is desired that the same surface loads be applied to the roller roll nip at all travel speeds and at a constant speed, the surface traction Q3 in deceleration and acceleration should be set as follows:

/ fl «M

Β3 = ^ + ^ + - ^ + ρ2, μ + ρ3, μ, (8): 'j where F is the desired (static) winding force. Correspondingly, if the winding force is applied: * * *: by the torque M j, it must be set as follows: •! 20 e ») ·« · • * • · * · ·

If both the surface draw Q3 and the center torque Mi can be used, the loads on both • · * · '• i · * roller roller and the surface draw roll can be kept independent of the change in travel speed. Re-group Equation (7) such that Q3 is also * 25 to the left of this: ···:: M »(10) * ···; Λ] Λ, Λ, 10 11B962

That is, Mj must also be selected according to equation (9). Further, by regrouping the torque roller torque equation (6) as follows 5 (H)

Rl 1¾ R, it is seen that Q3 also remains constant if the torque of the surface pulling roller is adjusted as follows: 10 ^ = 0 = -, + ^ + ^, (Π) λ3 ä3 K3 where Q3stat is the surface pulling speed when running at constant speed.

Equations (3) and (4) give 15 Q ~ -Qw = TMt-Q + -W (13) ··· • ♦]; ·· * Placing this result in the torque equation of the reel ·;. ·! · (I4)

·· ♦ S

: 20 «··: ***: According to the invention, this gives the calculated torques for the center roller equipped with a surface draw: 2 · · · · · M2 = + Μ2μ + WR1-FRl + Λ / 2Γμ (15) *: * 25 f * «·» ·· • «n K = ¥ i + FR, + fJÄ + M, li + Q, rllR, + Q,„ Ri + Mlrl, (16) • ### 1 • · u 118962

Further, in accordance with the invention, the calculated torques for the center roller with center draw are obtained: Λ / | = FRt „Η * / | θ | + Α /] μ Ί ”5 M2 = 72θ2 + Λ / 2μ + WR2 -FR2 + M2r] i (18)

In the bobbin winder, Fig. 4, the rotation equations additionally include the front roll torque and the rotation and rolling resistors. Article Mi is considered zero for this tar-10 irrigation. The roll equilibrium equation is now = (<τ-τ ")", + qa + & ", - *, - (19) where Q4 is the tangential stroke of the front or belt roller and ρ4Γμ in this nip is the roll resistance of the 15 rolls. The equilibrium equations (5) and (6) for the reel and press roll remain unchanged. As a new equation, look at the front or belt roller wheel · ···, • •:: 20 ··· ·.:. · Where M4 is the torque on the front or belt roller, Μ4μ rotational resistance and Μ4Γμ ··· winding resistance. In the case of a bobbin winder, it is more difficult to choose the appropriate winding strategy because there are several nips affecting the roll structure. Oklahoma State University Web Handling Research ··· • * * · .. * 25 Center. Semiannual Technical Review and Industry Advisory Board Meeting, Ocm> # * l · Tober 2000, Tab. the printing roller has a significant effect on the roll structure with a small roll diameter. Obviously, with a larger roll diameter, the rear roller plays a dominant role. Let's take the roller wheel as a starting point

• I

12 11β962 the equilibrium equation (19) and write it so that all the surface loads of the roll associated with the rear roll nipple ra fJ Λ, Λ, 5 are left

To achieve the same surface loads at the rear roll nip at all travel speeds and at a steady speed, the deceleration and acceleration sum of the surface ratchet at the other nipples must be set as follows:

ΓΔ M

10 Ö} + Ö »+ + + ^ + 03, -μ + £? 4, μ» (22) Ä, Λ, where F is the desired static winding force. Because there is a sum of surfaces-to-rails on the left, the implementation of the winding force is not unambiguous.

A few examples of embodiments a-c of the invention will now be discussed.

· *** * ... * a) Set the surface roll and roll value of the press roll ···••••••• This is a practically easy-to-implement case. Groups the press roll • * · •• γ 20 weight equation (6) again • · · «· * • f · *» · o Mi »(23) R, h R> *.

• ♦ · * »· ·» · ··· ♦ · • · *** See that if M3 is selected such that ·· ·· »25 ·· '~! Ä.jr, + J & + i! IiL + "k, (24) ·: ··: Äj J? 3 λ, • · 13 118962 so the surface fractions are β.

n - f F 4 + η 4 -O +0 Äi 5 above Fn · is the static surface fraction of the printing roll.

b) Adjusting the Surface Contraction of the Front Roller or Belt Roller and the Rolling Force This case requires quite a large amount of power from the press roll motor.

10 By regrouping the terms, the torque equation (20) of the front or belt roller will be given by ^ r4 r4 r4 r,} 15 It will be seen that if M4 is selected such that ··· • · · · **! 'VM ± sF + £ &. + ^ * L + IIIa. oy, • ·. · r4 R4 R4 r4 • m «· • · * • * ·

Ml · ·. ·, · * So are the surface fractions

• M

! ...! 20

T (i M

* ...: Qi — Ffi— Φ 1 2 3 2 • M ··

• M

p. ,, ί The above Ffd is thus the pmtraction of the front / belt assembly.

• · 3 25 c) Inactive press roll 14 118962 This is a common solution, for example with card cutters. Now the surface fractions are Ci - ^^ 3n ^ ~ r3 r3 r3 '.. .. (29) n - f + I ^ Ιμ + n + nin ι 1 2 3 ^ 3®3 ι ^ 3μ μ ^ 3, -μ β »- ^ + - + - + 0 ^ + ö3r ((+ & 1 +" T - + - ^ - + - TT "

Aj Aj A3 Aj A3 5 According to the invention, the calculated torques for the carrier roller in which the surface fraction of the presser roller is set, i.e. in the embodiment a.

10 M1 = J $ 1 + M2Vi + WR2-FR2 + MlrVi (30) M3 -F ^ R ^ + y303 + Λ / 3μ + M2rti (31) M, = +3/4 „+ ^ 3 /, + (&, + &, + &, K + 3 /., (32) Λ, Λ, «· 1 15 • · ·: 1. · According to the invention, the computational moments are obtained for such a carrier roll • ·» · · *. 1: for a dilute, where the front / strap track surface fraction is set, i.e., an implementation example • · * 1 1 ··· · catb.

• 1 · • 1 · ··· ··· 9 · 20 Mt -Λθ2 + Κ2μ + WR2-FRt + Μ2, μ (33) 25 • · · · 2 • · · «·· C: 3 /, - ^ + (^ - ^) ^ + ^^ + 3 / ,, + ^ 3 / ,, + (0 ^ + 0 ,, + (2 ^) 4 + 3 / ,, (34) • · · ···· 3 • · M4 = + JÄ + M4 {I + M4ril (35) · 15 1 1 8962

According to the invention, computational moments are obtained for a carrier roller without a roller drive, i.e., in embodiment c.

5 M2- J2Ö2 + M2il + WR, -FR2 + M2ril (36) M, = + 4-Jfi, + Μ, μ + (& „+ β,„ + a,) R, + Λ, Λ} Ä3 (37 )

The examples shown in Figures 5Λ and 5B are of a carrier roller, in which the surface roll and roll force are determined by formulas (30) to (32), where the roll force F = 500 N / M, web tension W = 300 N / m, surface roll force Fn = 100 N / m, running speed v = 40m / s, acceleration a = 1m / s2, density 1000kg / m3, web thickness 15 0.1mm. The thin lines shown in Figures 5A and 5B depict a current control of .1 ···. of a segment with a surface force Frr = 0. With current control, i.e., the torque control, carried out without the method of the invention, the acceleration force is too small. j in cannons and too big in decelerations. The most significant error effect without the method of the invention is the large roll diameter, whereby the migration slowness is ··· ·: 20 large. Particularly in the final deceleration, the control without the method of the invention * ··: 1 1 1: can easily make the surface of the roll too hard.

···: The invention has been described above with reference only to some advantageous embodiments thereof, but the details are not intended to be narrowly limited.

··· 1 ··· · · · · · · · · · · · · · · · · · · · · · · · · · ·

Claims (8)

16 1 1 8962 1, A method of torque control of a reel, wherein the fiber web is wound into a web by means of one or more reeling nipples, characterized in that the method adjusts the reeling force such that tangential actions on at least one reeling nip regardless of acceleration / deceleration. Method according to Claim 1, characterized in that the method adjusts the winding force in the center roller. Method according to Claim 1 or 2, characterized in that the method generates a calculated torque to achieve the desired roller structure by adjusting the winding force for a center roller with surface draw with the formulas M2 = jg2 + Μ2µ + WR2-FR2 + Mlni (15). • · ·· ♦ ·· · 20 M, = + FR, + ij-Jfi, + Μ1µ + + α, Λ + Λί ,, (16) * «Ai • · 1 • · • * · •» I • M · basis. • · · «· • • *« A method according to any one of claims 1 to 3, characterized in that in the method 25, a calculated torque is generated to achieve the field of the desired roller roll by adjusting the winding force with the center stroke. * · 'For the center roller of the formulas ·· · • · • * • 1 · · Ml = FRy · * ·· ·®Α 4 "Qlr ^ Ry + Qiry.Ry (17) 17 11896 2 M2 = J2 & 2 + M1Vi + WR1-FR2 + M2ni (18) 5 Method according to Claim 1, characterized in that the winding force is adjusted in the paddle roller. Method according to claim 1 or 5, characterized in that in the method * 10, a calculated torque is generated for the carrier roller, in which the surface fraction of the printing roller is set, according to the formulas M2-Λ2 + 22μ + WR2-FR2 + M2 ) 15 Ai4 = 7/4 + (Fi-ir) Ä4 + §-7je; + Af4, + - ^ ww + (e ^ + ani + a ^) Ä, + ^ „,: ***: (32) a · ·: * · *: Based on. • · • a * • ·· a · ·. · *: 20 A method according to any one of claims 1, 5 or 6, characterized in that the method generates a computational moment for the carrier roller in which the front / belt track surface fraction is set, according to the formulas! ··· - 'M, = J1% 2 + Mlr + WIt1-FR1 + M2, "(33) 9 25 • aa ms = j,% + (ff / 4) äjj, e, + mv + ^ - m" + {Q ^ + Qirf + & „) *, + M, v (34) a ·· Ä | / Cj • a • · is 118962 based on M4 = FfdR4 + J4Q4 + Μ4μ + M4ril (35). A method according to any one of claims 1, 5 to 7, characterized in that method 5 generates a calculated torque for a non-press roller carrier using the formulas M2 = J2®2 + Μ2μ + WRz - FR} + M2iv (36) M, = Jfi, + FR, + £ Jfr + £ Jfis + + (öw + öJr # + & Γμ) S, + Λ, K3 K3 "ä 'M 10 (37) Based on, · 1φ • 1 • t • · · · · · · • • «» »» »1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 · · · · · · · · · · · · · · · · · · ···