AT399175B - Calendar for surface processing of materials - Google Patents

Calendar for surface processing of materials Download PDF

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Publication number
AT399175B
AT399175B AT162490A AT162490A AT399175B AT 399175 B AT399175 B AT 399175B AT 162490 A AT162490 A AT 162490A AT 162490 A AT162490 A AT 162490A AT 399175 B AT399175 B AT 399175B
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AT
Austria
Prior art keywords
roller
calender
pressing
fixed
fixed roller
Prior art date
Application number
AT162490A
Other languages
German (de)
Other versions
ATA162490A (en
Inventor
Peter Heitmann
Karl Volz
Original Assignee
Escher Wyss Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to DE19893936128 priority Critical patent/DE3936128C2/de
Application filed by Escher Wyss Gmbh filed Critical Escher Wyss Gmbh
Publication of ATA162490A publication Critical patent/ATA162490A/en
Application granted granted Critical
Publication of AT399175B publication Critical patent/AT399175B/en

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Classifications

    • DTEXTILES; PAPER
    • D21PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21GCALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00Calenders; Smoothing apparatus
    • D21G1/002Opening or closing mechanisms; Regulating the pressure

Description

AT 399 175 B

The invention relates to a calender for the treatment of material webs, with at least one fixed roller which is firmly supported in operation in the pressing direction and at least one loose roller which is freely movable in the pressing direction.

Such calenders are well known. In particular, the bearing journals of rollers are freely movable in longitudinal guides in the pressing direction by being subjected to limited movement as loose rollers in these guides.

The problem here is the fact that considerable frictional forces can be effective in these guides, even up to a more or less clamping effect. As a result, for example in the case of a vertical calender in the nip of the fixed roll, the expected pressing force may be one-sided, too high or too low, depending on whether an increase or decrease in the pressing force has been carried out. This leads to pressing forces deviating from the nominal value and / or to oblique pressing force profiles in the roll gap, the latter because the friction in the guides of the rolls is not always the same.

Many attempts have already been made to mitigate the effects of these friction or clamping phenomena by artificially shaking or moving the entire roll stack in order to break free of the friction. Attempts have also been made to remedy this by applying a larger or smaller additional load in some cases from the movable roller until the desired pressing forces are applied to the fixed roller.

It was partially achieved that, with approximately constant friction, the actual value of the mean line force or the line force profile in the nip on the fixed roller taken as a measure for the smoothing process is brought to the desired value. In many cases, however, it was precisely through the measures mentioned that the friction was increased until the guide jammed. In any case, the line forces in the nips, which are located between the rubbing or pinching roller and the movable roller experiencing the additional load, are falsified, which leads to a considerable disruption of the rolling process.

Therefore, the object of the invention is to provide a calender in which the abovementioned friction and clamping can be eliminated in a simple and reliable manner or at least in their adverse effect can be removed without, for example, having to significantly change an existing calender.

This object is achieved according to the invention by a device known per se for measuring the pressing forces on the fixed roll, a known device for adjusting the fixed roll in the pressing direction, a device for comparing the desired pressing force values with the measured actual pressing force values on the fixed roll and a Control device for controlling the adjustment device in accordance with the actual setpoint comparison to achieve the desired pressing forces in the nip on the fixed roller. The setpoint value for the pressing force on the fixed roller results from the parts of the weight forces acting in the pressing direction of the parts which are movable in the pressing direction and are supported on the fixed roller and the forces which are exerted on the loose rollers.

This solution makes use of the idea of making the roller, which is intended for operation as a fixed roller, at least selectively movable on the end faces in the pressing direction, depending on the supporting forces measured on the fixed roller, which are largely determined by the pressing forces. The claimed principle generally works upwards as well as downwards (vertical calender) as well as in any other position of the rolls with respect to one another, for example horizontally in a horizontal calender. An additional load can be added both from above and from below, or from the right or from the left.

By applying the invention, the disadvantageous effect of the frictional forces can be eliminated not only on the adjusted fixed roller, but also on the roller strings between the adjusted fixed roller and the roller on which the harmful frictional force occurs.

To clarify the principle of the invention, a vertical calender is now used as an example, which consists of a lower roller A, an upper roller 0 and two intermediate rollers Bi and B2. All rolls are designed as full rolls. The lower roller A is supported with its axis on both sides on an adjusting device D, D ', which in turn are supported by a measuring device C, C' on a solid surface. The adjusting device can consist, for example, of a motor with a spindle drive; the measuring device can comprise, for example, a pressure cell. Normally, the adjusting devices D, D 'are not in operation, so that there is firm, rigid support of the roller on the ground; the lower roller A therefore normally represents a fixed roller.

The support of the fixed roller A formed by the adjusting devices D, D 'and the force measuring devices C, C' thus supports the forces acting on the fixed roller A including the dead weight of the fixed roller A on the substrate. The sum of the forces K or K 'supported at the two support points for the fixed roller is composed of the proportional weight of the rollers A, Bi, B2 2

AT 399 175 B and 0, namely KA, KBi, KB2 and K0. In addition to these weight forces, additional pressing forces KP and KP 'applied to the upper roller 0 are added. This idealized force distribution must, however, be corrected for the frictional forces caused by friction in the bearings of the loose rollers 0, Bi and B2; the frictional forces Krbi, Krb-Γ, Krb2 > Krb2 \ Kro and Kro 'therefore counteract the 5 pressing forces with increasing KP or KP'.

Half of the dead weights are used as an example on each side. The following equation results for the friction-free balance of forces in the left half of a press gap S between the rollers A and Bi: 10 K - £ KA = ^ Kbi + 5 · Κβ2 + 5-Ko + Kp. (Ϊ́)

If an additional pressing force ΔΚΡ is now applied to the top roller on the left, that is to say that the pressing force is increased, the increase in pressing force in the ideal case, that is to say when there is no friction, will result in an equal increase in the supporting forces, that is to say from the force measuring sensor C. 15 measured The equation for this would be: K + ΔΚ - ^ KA = ^ Kgi + ^ Kß2 + -rKo + KP + ΔΚΡ ® 20 withAK = ΔΚΡ.

In order to obtain this increased force in the lower press nip introduced by ΔΚΡ or ΔΚΡ 'on the upper side, it is necessary that the frictional forces of the loose rollers in the lateral frames are zero. However, this is not always the case. If the coefficient of friction in the frame is high enough, an additional pressing force may not be able to overcome the static friction in the area of the bearing of a loose roller; the result is that the additional force applied via the storage of the Loswaize concerned "disappears in the chair"; that is, that the additionally applied pressing force is not supported in the area of the support of the lower fixed roller A, but already in one of the two guides of one of the overlying loose rollers, for example the roller Bi, which means that the roller 30 Bi is clamped on this side and thereby the support force at the support point of the lower fixed roller A does not change compared to the state before the pressing force was increased.

Such a " loss of pressing force " caused by clamping in the bearing of the roller Bi is expressed by the following equation: 35 K - 3rKA = jKbi + ϊ · Κβ2 + ^ Ko + KP + ΔΚΡ - Krbi © with ΔΚΡ = Krbi · 40 This equation, which - like all previous equations - the balance of forces in the left half of the Press Spaites S between the lower fixed roller A and the lower loose rollers Bi, corresponds exactly in the respective sum of forces on both sides of the equal sign to the first equation in which no additional pressing force had been applied, because the additional pressing force ΔΚΡ is equal to the sum of the frictional force KRBi · 45 This shows that the additional pressing force has no effect in the press nip; the clamping in the bearing of one of the loose rollers is the reason why the change in the applied additional pressing force ΔΚΡ does not lead to any change in the force measured by the measuring devices C and acting in the press nip S , in which case the additionally applied pressing forces on one side are not transmitted up to 50 into the press nip S and an imbalance of the rolls occurs.

However, if only friction and no clamping occurs, the equation changes to: K + ΔΚ - 3-KA =? KBi + £ Kß2 + jKo + KP + ΔΚΡ - Krbi - KRB2 - Krq 0 55 with ΔΚ < ΔΚΡ. 3rd

AT 399 175 B

In the calender of the present invention, therefore, the devices C, C 'for measuring the pressing forces on the fixed roll each send a measured value for the force supported on the surface on each side of the calender to the device E for comparing the pressing force setpoints with the measured pressing force - Actual values passed on to the fixed roller. The roll weights can be recorded as a system size and made available to the comparison device. The applied pressing forces are fed to the comparison device E.

If the pressing forces KP increase by Δ KPρ or KP 'by ΔΚΡ', for example, the actual pressing force values measured by the force measuring devices C, C 'do not correspond to the assigned pressing force target values determined by the comparison device, as is the case, for example, in relation to equation 3 or 4 has been explained, the control unit F for controlling the adjusting device receives corresponding commands from the comparing device E and acts on the devices D, D 'for adjusting the fixed roller in the pressing direction in such a way that the fixed roller A (one-sided or both-sided) so far upwards is adjusted until the press force values measured in the force measuring devices C, C 'again correspond to the target values.

This basic control principle is made possible by the device features specified in claim 1, namely by - the known device (C, C ') for measuring the pressing forces on the fixed roller, - the known device (D, D') for adjusting the Fixed roller in the pressing direction, - the device (E) for comparing the pressing force setpoints with the measured actual pressing force values on the fixed roller and - the control unit (F) for controlling the adjusting device in accordance with the actual setpoint comparison in order to achieve the pressing force setpoints in the nip the fixed roller.

The known systems according to the prior art do not have this inventive principle.

AT-PS 339 720 discloses a device for adjusting the contact pressure of a deflection adjusting roller with piston-like hydrostatic support elements, which are arranged on a fixed central support and on which a jacket rotatable about the support is supported, the ends of which are mounted on the support in roller bearings, whereby pressure elements are assigned to the roller, which serve to absorb the reaction forces acting on the ends of the carrier. The setting device consists of a mechanical model that simulates the force relationships in the roller, pressure conditions in the support and pressure elements being used as input variables. The aim of the invention is the automatic setting of an equilibrium state in which the rolling bearings between the jacket and the carrier are largely relieved. E.g. If the pressure in a support element group increases (by operating the manual valve or increasing the pressure on the outside of the roller), the pressure in the pressure elements is also increased. This system does not compensate for the fact that this increase in pressure from the outside may only occur on one side (by clamping), but would be desirable on both sides, since the objective is not to compensate for frictional effects in loose rollers, but rather to use a fixed roller as a counter roller.

AT-PS 366 118 describes a roller combination with a work roll, an intermediate roll (which can also act as a driven work roll) and a deflection adjustment roll, the entire rolling device being able to have two of the groups described above, which are arranged opposite one another around a roll gap, but the interaction of a deflection roll and an intermediate roll and possibly a work roll with several full rolls is possible.

The supports of the deflection roller (s) are fixed. The shafts of the intermediate rollers are supported in bearing blocks (23), wherein the bearing blocks of the lower intermediate roller are supported in the side part of the frame (1) and the bearing blocks (23) of the upper intermediate rollers (20) are supported in a carriage (24) which in the Side part of the frame (1) is vertically movable, and is adjustable by means of the motor (25) and gear (25 ') and screw (26) (pre-adjustable and adjustable depending on the measured material thickness). The bearing blocks (23) of the intermediate rollers are each supported by pressure sensors (27), so that the intermediate roller becomes the actual measuring roller. The deflection adjustment rollers, on the other hand, have no pressure sensors.

The pressure medium is distributed so that the ends (22) of the intermediate roller are relieved, i.e. that the pressure sensors (27) of a pin deliver the same signals. In this case there is a balance between the contact force of the support elements (5) and the reaction force of the rolled material M, so that the gap S is maintained.

The problem of jamming of the rolls is not dealt with in this known roll combination, since all rolls are designed as deep rolls. If one were to apply such a regulation to calenders with loose rollers, this regulation would no longer work properly even the first time a loose roller was clamped, since it would not be recognized that the force shift occurring due to clamping forces is undesirable. 4th

AT 399 175 B

DE-OS 35 33 210 discloses a method and a control device for controlling the line pressure distribution in roller arrangements with at least one roller (10) with a fixed crosshead (1) and a hollow roller (3) surrounding this crosshead, which is provided by several along the hollow roller successive support elements (8) on the crosshead (1) is supported from the inside. 5 The line pressure distribution is controlled with a computer depending on the web width and a specified line pressure profile. The web width is measured by a sensor (33), the line pressure profile is set manually or determined by a web thickness sensor (30,32). The known calculation model is completely different from that according to the present invention, since in the known case the parameters web width, web thickness or predetermined line pressure profile serve to control the support elements. In contrast, according to the present invention, the pressure forces are calculated by comparing the pressure force applied and the pressure force actually measured at the nip, so that friction forces occurring in the calender can be taken into account.

DE-PS 36 22 398 describes a method and the control device for separating the rolls of a calender, in which the bottom roll (16) of the roll stack as a deflection compensating roll with 15 a non-rotatably mounted support (17) and a roll jacket (20) rotatable about it is formed, the roller jacket being supported on the carrier by means of hydraulic roller jacket supporting elements (21) and the carrier relative to the stand (1) of the calender by means of hydraulic carrier supporting devices (18). This known method and control device serves different purposes than the device according to the invention. 20 DE-OS 36 40 161 describes a special device for positioning roller surfaces of rollers, in particular intermediate rollers in a calender, which lift the roller surface, to relieve them, to lower them from one working position into another desired position and to hold them can

EP-A1 0 229 210 relates to a control circuit 10 to 16 for a hydrostatically mounted support roller 25 1, which has a plurality of hydrostatic bearings 7a to 7d, each of which by means of a

Control valve 10a to 10d can be supplied with a hydraulic medium. The control circuit includes two displacement transducers 12a, 12b arranged on the edges of the support roller 1, the output signal representing the position of the edge being combined with a set position signal to form a position deviation signal. The control takes place in that the control circuit for each control valve (10a-10d) has a proportional control element (14a-14d) which supplies the control valve (10a-10d) with a valve control signal which is proportional to the sum of the respective position deviation signal (14a , 14b) and a correction signal (k2-k *) for setting a pressure profile. This known regulation differs from the device according to the invention, because the manipulated values are calculated by the signals measured by displacement sensors and serve the purpose of holding the roller in a defined position, but not to compensate for frictional forces.

EP-A1 0 290 637 describes a method for adjusting the contact forces at each point of action of a bending compensation roller that can be pressurized. This method is similar to the mode of operation of the device according to AT-PS 339 720 already cited at the beginning, but a mathematical model (pressure reaction matrix) is used instead of the mechanical model described in AT-PS 339 720 40 to simulate the contact forces.

Further aspects of the present invention will now be discussed.

According to the invention, it is not necessary to know which of the rollers rubs or jams in their guides.

A fixed roller can be combined with a loose roller as the smallest unit. 45 Loose rollers, which bring additional forces, are also conceivable.

In connection with a standing calender, the fixed roller can be provided as either the top or bottom roller.

In connection with a horizontal calender, the fixed roller can be provided as either the rightmost or leftmost roller. so It is also possible to provide the fixed roller in the intermediate area of the calender.

The fixed roller itself can expediently be designed as a deflection compensation roller with a fixed lateral rotary bearing of the roller shell. A roller of this type is disclosed, for example, in U.S. Patent 3,119,314. The pressing forces are applied by hydraulic elements which press along the pressing line against the inside of the roll shell, whereby a very uniform line force profile can be set.

The fixed roller can also be designed as a deflection compensating roller with a roll jacket which is movable over the entire length in the pressing direction and which can be fixed in a selectable position for operation in the pressing direction by a distance measuring device. In addition to the uniform 5

AT 399 175 B gen line force profile, this roller type is also particularly suitable for electronic-hydraulic control systems with high integration density.

The loose roller, which can bring in additional forces, is advantageously conceivable as a deflection compensating roller with a roller jacket movable in the pressing direction.

Load cells can be used to measure the loads on the rollers or hydraulic or pneumatic pressures of load systems of the rollers can be used.

In the event that hydraulic or pneumatic pressures of the load systems are used as measured variables, a combined regulation of the roller height correction and the pressing force correction in the case of deflection compensating rollers is appropriate. The control unit for roller height correction can be omitted and a system with high integration density results.

Lifting gear, piston systems or other mechanical devices can be used to change the position of the front ends of the respective fixed roller.

In connection with a fixed roller as a deflection compensation roller with a roll jacket which can be moved over the entire length in the pressing direction and which can be fixed in a selectable position for operation in the pressing direction by a distance measuring device, the adjustment mentioned can be changed by changing the selectable position e.g. by making appropriate entries in a controller fixing the position of the roll shell or by changing the position of the entire deflection compensation roll. Another conceivable measure is that the distance in the distance measuring device is artificially reduced and a readjustment is thus initiated.

The readjustment of the position of the fixed roller towards or away from the rubbing or clamping roller can be automated separately at both roller ends depending on the actual-target pressure force differences between the fixed and loose rollers.

Further advantageous embodiments result from the subclaims.

The invention is explained in more detail below with reference to exemplary embodiments shown purely schematically in the drawings. It shows:

1 a is a schematic view of a calender,

1 b is a schematic side view of the calender according to FIG. 1 a,

2 a to 2 e different standing calenders, or a horizontal calender and

3 a and 3 b a 2-roll construction in the longitudinal or cross section.

A calender consists of several rollers arranged one behind the other, which form between them a nip through which the paper web to be smoothed runs. In the case of a standing calender according to FIGS. 1 a and 1 b, a lower roller 12 and an upper roller 14 with intermediate rollers 16, 17 and 18 arranged between them are provided. In Fig. 1 a part of the intermediate rolls is not shown. Although either the upper or the lower roller or even an additional intermediate roller can be provided as a so-called fixed roller, in the example shown in FIG. 1 a the lower roller 12 is designed as a so-called deflection compensating roller with a roller jacket 13 and a yoke 15. This roller serves as a fixed roller. It can be of different types. Either the roller jacket 13 is laterally supported by itself, and the bending compensation of the jacket 13 takes place via intermediate supports which can be acted upon by oil hydraulics, or the roller jacket is no longer supported laterally, but the support is provided only over the length of the roller jacket 13 on the yoke 15 Deflection balancing wafers are well known.

A position sensor 20, which is connected to a position controller 22, is located on the roller jacket 13 or on the yoke 15. The deflection compensation supports symbolized by the arrows 24 are supplied with hydraulic oil in order to apply different pressure over the length of the roller with regard to a line force profile in the roller gap 26 between the intermediate roller 18 and the lower fixed roller 12. The hydraulic oil pressure is regulated via an oil pressure regulator 28 connected to the position regulator. The oil pressure at the various points in the nip can be displayed graphically on a monitor via lines 30.

The position sensors 20 report the actual position of the roller jacket 13 to the position controller 22, which permanently corrects the oil pressures of all zones in such a way that the roller jacket 13 and thus the entire roller package assumes and maintains a defined, horizontal height. The entire roller package hovers within very narrow limits, so to speak.

The rollers are guided in vertical versions by lateral pins 32. The rollers normally lie on top of each other in the vertical calender due to the weight of the rollers. However, an additional pressure on the part of the upper roller 14 can also be applied in accordance with miles 34. The upper roller 14 can also be a deflection compensation roller.

If, for example, a jam occurs in the vertical version of the intermediate roller 17 on the right side, this manifests itself in a yielding of the roller shell 13 upwards, so that the position guide 6

AT 399 175 B ler 20 on the right side in Fig. 1 a forms a spacing in the vertical direction of the associated sensor parts. Thus, the position sensor on the side of the clamp registers the reduced load there as a slight upward movement of the jacket and therefore also controls correspondingly lower oil pressures on this side. The line forces now applied by the self-loading deflection compensating roller are uniformly increasing from the side of the clamp to the full load on the opposite side, which is indicated as an obliquely depressing line force profile via the lines 30 on the monitor. The different line profile is documented by the arrows of different lengths in the area of the roller in FIG. 1 a. According to the invention, the lower roller 12, designed as a fixed roller, is now on the right side, i.e. on the side of the clamp, traced upwards in such a way that a linear force profile that is uniform over the length of the roller is established in accordance with the setpoints. This means that the actual hard roll for readjustment can be adjusted at least on the end faces in the direction of the other rolls.

It should also be mentioned that in the case of a jam on the right side of the intermediate roller 17, the conditions above this roller are still in order, as is shown by the arrows there in FIG. 1 a. The conditions below the clamp are brought back into the desired state over the entire length of the rollers by the readjustment.

Fig. 2 shows in Fig. 2 a to 2 d standing calender and in Fig. 2 e a horizontal calender in a schematic representation. 2 a, the rollers 14 and 16 are loose rollers which are guided with guide parts 27 in vertical guides 19. The lower roller 12 is a fixed roller here.

In FIG. 2 b, the upper roller 14 is also a fixed roller like the lower roller 12, which, however, can still be moved here by a lifting unit 21 for an active application of compressive force. This movement can also be affected by Klemmer. in FIG. 2 c the lower roller 12 is a fixed roller, the upper roller 14 being vertically movable by a lifting unit 21 for the application of pressure force.

FIG. 2 d, like the calender in FIG. 2 b, has a lower roller 12, which can be moved by a lifting unit 21, and an intermediate fixed roller 14 " on.

In the horizontal calender of FIG. 2 e, the right outer roller 14 'is a fixed roller and the left outer roller 12' is a roller which can be moved by a lifting unit 21 '. The intermediate rolls 16 'can also be moved with guide parts 27' in a guide 19 'as loose rolls.

With a view to simplifying the system, a measurement can be carried out separately at both ends of the fixed roller. It does not matter whether the load is due to the dead weight and an additional load when the calender is standing at the top or by applying force at the bottom. In any case, it must be ensured that, taking into account the target load, the actual load, which may also occur unilaterally when clamping, is eliminated again by a slight movement of the fixed roller at the corresponding end and brought to the target value. As measurements of the loads e.g. the hydraulic or pneumatic pressures of the pressure systems are used.

There is also the possibility of detecting the respective actual value in the area of the support of the fixed roller via pressure transducers and then carrying out a regulation to the setpoint. Lifting gear, piston systems or other mechanical devices are suitable for changing the position of the respective fixed roller.

Measuring and positioning systems can also occur in combination, e.g. the so-called " floating stack principle " with the position sensors in combination with self-loading deflection compensation rollers.

The readjustment of the position of the fixed roller towards or away from the rubbing roller can be automated as a function of the difference between the setpoint pressure difference of the two extreme, spaced-apart roller gaps, separately at both roller ends. The system does not need to know which of the rollers are rubbing or jamming in their guides.

3a and 3b, a two-roll system can be seen. The roller jacket 13 is supported on the yoke 15 by means of pressure tappets 42, these pressure tappets 42 being selectively pressurizable via a chamber 43 and an oil line 44, as can be seen from the arrows in FIG. 3a in the area of the pressure tappets 42. The outer edge of the roll shell 13 is supported on a link 38 via a bearing 40. This backdrop is vertically movable on a backdrop guide of the yoke 15, as indicated by the arrow in Fig. 3b. Thus, depending on the pressurization of the pressure tappets 42 and the applied pressing force, it can move vertically relative to the yoke 15, specifically along the corresponding vertical guide surfaces 50. The mentioned clampings can occur there due to increased friction. The movement of the roller shell 13 relative to the yoke 15 can be detected by a displacement sensor 46. Here it is possible to compensate for a disharmony of the pressing forces in the event of jamming by a simple software control alone. 7

Claims (13)

  1. AT 399 175 B 1. Calender for the treatment of material webs, with at least one fixed roller which is firmly supported in operation in the pressing direction and with at least one loose roller which is freely movable in the pressing direction, characterized in that a known device for measuring the pressing forces on the fixed roller (12), it is further provided that a device (24, 42) known per se for adjusting the fixed roller (12) in the pressing direction is provided, and that there is also a device for comparing the desired pressing force values with the measured values Actual pressing force values are provided on the fixed roller and finally a control unit (28) for controlling the adjusting device is provided on the fixed roller in accordance with the actual / actual value comparison in order to achieve the desired pressing forces in the nip (Fig. 1a, Rg. 3a).
  2. 2. Calender according to claim 1, characterized in that in connection with a standing calender the fixed roller (12) is provided as the top roller. 15
  3. 3. Calender according to claim 1, characterized in that in connection with a standing calender, the fixed roller (12) is provided as the bottom roller.
  4. 4. Calender according to claim 1, characterized in that in connection with a horizontal 20 calender the fixed roller (12) is provided as the rightmost roller.
  5. 5. Calender according to claim 1, characterized in that the fixed roller (12) is provided as the outermost left roller in connection with a horizontal calender.
  6. 6. Calender according to one of claims 3 to 5, characterized in that a further fixed roller (14 ") is provided in the intermediate area of the calender.
  7. 7. Calender according to one of claims 1 to 6, characterized in that the fixed roller (12) is designed as a deflection compensating roller with a fixed lateral rotary bearing of the roll shell. 30th
  8. 8. Calender according to one of claims 1 to 6, characterized in that the fixed roller (12) is designed as a deflection compensating roller with over its entire length in the pressing direction movable roller jacket (13) with the help of a distance measuring device (20) in a selectable position for the operation in the pressing direction can be fixed (Fig. 1a). 35
  9. 9. Calender according to claim 1, characterized in that at least one of the loose rollers (14, 16) comprises a device for applying an additional force and a measuring device is provided for measuring this force.
  10. 10. Calender according to one or more of claims 7, 8 or 9, characterized in that the measuring device detects the hydraulic or pneumatic pressures from the load system of the roller or rollers.
  11. 11. Calender according to claim 1 or 9, characterized in that load cells 45 are used as measuring devices.
  12. 12. Calender according to claim 1, characterized in that a lifting gear is provided as the adjusting device. so
  13. 13. Calender according to claim 1, characterized in that a hydraulic or pneumatic piston stroke system (21) is provided as the adjusting device. Including 3 sheets of drawings 8 55
AT162490A 1989-10-30 1990-08-01 Calendar for surface processing of materials AT399175B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19893936128 DE3936128C2 (en) 1989-10-30 1989-10-30

Publications (2)

Publication Number Publication Date
ATA162490A ATA162490A (en) 1994-08-15
AT399175B true AT399175B (en) 1995-03-27

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AT (1) AT399175B (en)
CA (1) CA2027460C (en)
DE (1) DE3936128C2 (en)
FI (1) FI95938C (en)
GB (1) GB2237584B (en)

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DE9314568U1 (en) * 1993-09-27 1995-02-02 Kuesters Eduard Maschf Roller
FI96334C (en) * 1993-11-24 1996-06-10 Valmet Paper Machinery Inc Method for calendering paper or similar web material and calender applying the method
DE19520479C2 (en) * 1994-06-23 1996-07-11 Kuesters Eduard Maschf Calibration calender for plastic films
DE19511145C2 (en) * 1995-03-27 2000-07-13 Voith Sulzer Finishing Gmbh Calender for double-sided paper treatment
DE29720192U1 (en) 1997-11-14 1999-03-25 Kuesters Eduard Maschf Calender for treating a web
DE102009050201A1 (en) 2009-10-21 2011-04-28 Fleissner Gmbh Calendar device for treatment of e.g. plastic film, has supporting bodies provided below roller for changing linear pressure of roll gap between rollers, where bodies are impinged on outer circumference of rollers

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GB2237584A (en) 1991-05-08
FI904759D0 (en)
DE3936128C2 (en) 1991-11-21
FI95938C (en) 1996-04-10
FI904759A0 (en) 1990-09-27
CA2027460A1 (en) 1991-05-01
FI95938B (en) 1995-12-29
ATA162490A (en) 1994-08-15
GB2237584B (en) 1994-03-09
CA2027460C (en) 2000-03-28
DE3936128A1 (en) 1991-05-02
GB9022049D0 (en) 1990-11-21

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