CA2210935A1 - Method and device with active oscillation damping for winding a web of paper into a roll - Google Patents
Method and device with active oscillation damping for winding a web of paper into a rollInfo
- Publication number
- CA2210935A1 CA2210935A1 CA 2210935 CA2210935A CA2210935A1 CA 2210935 A1 CA2210935 A1 CA 2210935A1 CA 2210935 CA2210935 CA 2210935 CA 2210935 A CA2210935 A CA 2210935A CA 2210935 A1 CA2210935 A1 CA 2210935A1
- Authority
- CA
- Canada
- Prior art keywords
- oscillation
- pressing
- drum
- pressure
- fact
- Prior art date
- Legal status (The legal status 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 status listed.)
- Abandoned
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H18/00—Winding webs
- B65H18/08—Web-winding mechanisms
- B65H18/26—Mechanisms for controlling contact pressure on winding-web package, e.g. for regulating the quantity of air between web layers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
- F16F7/1005—Vibration-dampers; Shock-absorbers using inertia effect characterised by active control of the mass
- F16F7/1011—Vibration-dampers; Shock-absorbers using inertia effect characterised by active control of the mass by electromagnetic means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
- F16F9/0209—Telescopic
- F16F9/0218—Mono-tubular units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/06—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using both gas and liquid
- F16F9/064—Units characterised by the location or shape of the expansion chamber
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H2515/00—Physical entities not provided for in groups B65H2511/00 or B65H2513/00
- B65H2515/50—Vibrations; Oscillations
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
- B65H2601/00—Problem to be solved or advantage achieved
- B65H2601/50—Diminishing, minimizing or reducing
- B65H2601/52—Diminishing, minimizing or reducing entities relating to handling machine
- B65H2601/524—Vibration
- B65H2601/5242—Vibration by using mass damper
Abstract
An oscillation suppression resonator suppresses oscillations of a large oscillating mass in paper machine winding devices. A support device is connected with the large oscillating mass and a predetermined oscillation suppression means is movably arranged as the support device. Cylinders, which can be filled with gas or fluid, are firmly attached to the support device. The pistons of the cylinders are connected via piston rods with the mass movable on the support device. In this manner, upon deflection of the mass from an equilibrium position, a substantially harmonic oscillation takes place with a frequency which is determined by the pressure prevailing on the cylinder.
The oscillation suppression resonator is employed particularly in a device for winding traveling webs of material, particularly paper webs, so as to form a roll.
The oscillation suppression resonator is employed particularly in a device for winding traveling webs of material, particularly paper webs, so as to form a roll.
Description
CA 0221093~ 1997-07-18 METHOD AND DEVICE WITH ACTIVE OSCILLATION DAMPING
FOR WINDING A WEB OF PAPER INTO A ROLL
The present invention relates to an oscillation suppression oscillator in accordance with the preamble to Claim 1, and to a device for winding a traveling web of paper into a roll in accordance with the preamble to Claims 3 and 20.
Winding machines for the winding of paper webs can be arranged at the end of a paper machine in order to bring the web of paper~obtained there into the form of a roll (so-called Pope reel winder). However, they are also used in order to rewind a finished roll in order to produce rolls of a very specific quality of winding.
In all cases, the paper roll is to have very specific properties, in particular with respect to its hardness. The hardness of the roll should generally decrease from a certain initial value to a final value, a hard core winding at the very start being of particular importance. The decrease should be as uniform as possible from the first layer to the last layer. It should have a given gradient which is not too great and not too slight. The variation in the hardness of the roll should in no case show abrupt changes, for instance a sudden decrease. No radial or tangential stresses which impair or damage the web of paper must occur in the roll.
CA 0221093~ 1997-07-18 It has already been attempted to achieve all of this, but without success. Winding machines of known construction produce instead of this, for instance, rolls in which the core is either extremely soft or extremely hard and in which there is a strong decrease in the hardness of the roll towards the end -- for instance at four-fifths the diameter of the roll. This has the result that the first part, and therefore the extremely soft or hard core, cannot be used since the web is crushed and bursts in this region, so that this part must be thrown away as reject; in the region of the end, in which the roll has not been wound sufficiently hard, there is a lateral displacement of the layers relative to each other so that the sides of the finished roll appear frayed and the edges of the web can be easily damaged.
A poorly constructed core (too little or too great a hardness) namely does not permit a dependable forming of the rest of the roll. This problem is particularly serious in the case of pressure-sensitive papers, for instance self-duplicating (SD) papers, in the case of which narrow limits are set for the pressing of the shaft bearing the roll being produced against the outer surface of the carrier drum.
In the method known from DE 40 07 329, the roll of paper being produced is shifted in horizontal direction corresponding to the increase in the size of the roll. The roll of paper reaches a high weight, which can exceed CA 0221093~ 1997-07-18 hundreds of tons. For this reason, the roll of paper cannot, upon its growth, be pressed, in sensitive fashion, against the pressing drum.
DE 44 15 324 shows and describes a winding machine for winding a web of paper on a shaft with central drive. This machine comprises a winding station, a receiving station, and an idle pressing roller. The pressing roller rests against the circumference of the secondary roll of paper all the way up into the winding station. The web is guided in such a manner that it enters continuously, without wrapping, into the inlet slot. If such a winding device is operated with high speeds of the web, preferably more than 1000 meters a minute, then oscillations of the pressing roller occur suddenly and unexpectedly, which may lead in case of resonance to damage to the winding device. In order not to permit this to occur, the diameter of the pressing roller has been selected as small as possible, and predominantly of the same size as that of a normal web guide roller. This has the disadvantage that the pressing roller, due to the absence of sufficient flexural rigidity is not adapted to apply linear forces of any desired value and in particular not to extremely large web widths (up to about 10 meters).
From USA 5,431,261, a controlled oscillation suppressor is known. This oscillation suppressor had the disadvantage that large masses in the region of several tons, such as the CA 0221093~ 1997-07-18 previously described pressing-drum or pressure-roller device, could not be damped since as active or excited resonators there were always used ones which were tuned magnetostrictively or electrorestrictively to different frequencies.
The first object of the invention is thus to indicate resonators which can be used as oscillation suppressors for oscillations of large masses.
A second object of the invention is to provide a winding device in which the disadvantages of the prior-art devices are avoided, and in particular in the case of winding devices in accordance with the preamble to Claim 1, such as known from DE 44 15 324, oscillations of the pressing-drum or pressure-roller device which comprises a pressing-drum or pressure roller are suppressed.
In accordance with the invention, the first object is achieved by Claim 1 and the second object by the device according to Claim 3 and the method according to Claim 20.
Instead of magnetostrictive or electrorestrictive elements, the invention proposes, in order to obtain the first object, the use of hydraulic or gas-filled cylinders the stiffness KA of which is adjusted as a function of the pressure prevailing in the cylinder, against which pressure the piston must be moved. It is advantageously provided for such a device that the predetermined movable mass, i.e. a CA 0221093~ 1997-07-18 mass which carries out an oscillating movement, be arranged between two cylinders and be connected with pistons of the same rigidity. In addition to the possibility of adjusting the stiffness KA in such a system by change of pressure, it is also possible, upon the connection of the two cylinders, to introduce a damping member via a line containing a choke, whereby a given frequency spectrum or frequency band can be associated with the movement of the cylinders.
Essential reasons for the occurrence of oscillations of the pressing-drum or pressure-roller device which comprise the pressing drum or pressing rollers, referred to below as Sensomat rollers, and are part of the sensitive winding device, are, in accordance with the findings of the inventors, deviations of the wound paper roll from the ideal circular contour. As the inventors have found, a paper roll always has places which are not round, for instance compression places, which can excite the Sensomat rollers and the carrier device connected therewith to oscillation. This is due to the fact that in the case of the winding device in accordance with Claim 3, the Sensomat roller is not supported as in other device of the prior art by an infinitely large mass, for instance a foundation, but is arranged on a device which is movable relative to the paper roll, so as to move away from the center of the roll upon the increase in the diameter of the roll.
CA 0221093~ 1997-07-18 The invention therefore proposes, for the solution of the second object, in a system having a pressing-drum or pressure-roller device which is movable relative to the shaft or paper roll, an oscillation suppressor by which these oscillations which occur can be suppressed.
As example of such an oscillation suppression device, the invention proposes providing on the supporting device, which, for instance, can be developed as a rail and is fastened on the support of the pressing-drum or pressure-roller device, a mass which can move on the supporting device relative to the pressing-drum or pressure-roller device, for instance in the manner that it slides guided along the path or rolls on a rail. The movement of the mass is that of a harmonic oscillator, i.e. upon deflection of the mass from its position of rest it experiences, in the ideal case, an opposing force which increases linearly with the deflection, so that an oscillating movement, and therefore a swinging of the mass is obtained when the latter is excited to this.
This can take place by self-excitation, for instance upon occurrence of a swinging of the sensor roll or of the pressing-drum device or, in a further development of the invention, by means for exciting the oscillation, one special embodiment consisting therein that the means for exciting the oscillation comprises at least one actuator, for instance a hydraulic cylinder or a cylinder filled with gas, for CA 0221093~ 1997-07-18 instance air.
In a further embodiment, it can be provided that the means for exciting the phase-displaced oscillation comprise a movement sensor which is arranged on the pressing-drum or pressure-roller device. By the noting of the movement of the pressing-drum or pressure-roller device the frequency of oscillation thereof can be determined. In this way it is possible in a further embodiment to determine the instantaneous oscillation frequency or oscillation frequency band of the pressing-drum or pressure-roller device.
These signals can be used, in one particularly advantageous embodiment, in order to control means for adjusting the frequency with which the mass of the oscillation suppressor oscillates. The desired tunability or variability of the frequency permits an oscillation suppression oscillator which comprises at least two cylinders which can be filled with hydraulic fluid or a gas.
In a further development of the invention it is provided that the oscillation suppressor comprises an open-loop or closed-loop control device with which, as a function of the measurement signal produced by the movement sensor, the means for adjusting the oscillation frequency are so controlled that the oscillation frequency or frequencies of the mass always correspond to the oscillation frequency or frequencies of the pressing-drum device. This can take place, for CA 0221093~ 1997-07-18 instance, in the manner that the pressures in the aforementioned cylinders are so adjusted that a given stiffness of the cylinders is obtained whereby the "spring constant" of the oscillator consisting of mass and cylinder is adjusted. This thus permits a change in the oscillation frequency of the oscillator.
The open-loop control can be expanded to a closed-loop control even if a movement sensor is provided also on the mass of the oscillator for the suppression of oscillations, so that the phase of the oscillations with respect to each other can be determined from the movement signal of the pressing-drum device and oscillation-suppression device. The oscillation excited by the actuator is excited by means of the closed-loop control in such a manner phase shifted with respect to the first that a substantially complete extinguishing of the undesired oscillation of the pressing-drum or pressure-roller device is effected, even if the undesired oscillation of the pressing-drum device changes with time.
In an entirely different concept of the oscillation suppression, it is provided that the support device not be firmly connected only with the pressing-drum or pressure-roller device but that furthermore it has a firm support on, for instance, the wall or the carrier means for the pressing drum itself, which is movable relative to the shaft. In a CA 0221093~ 1997-07-18 first embodiment of this second concept, it is provided that the oscillation suppressor comprises a hydraulic cylinder, the hydraulic lines connected to the hydraulic cylinder having a choke. If the web has an unevenness, then the piston of the cylinder of the oscillation damping device is deflected. In this way, for instance, hydraulic fluid is displaced out of the cylinder. Since the choke prevents an immediate discharge of the hydraulic oil out of the cylinder or opposes resistance to it, the stiffness is increased and thus, depending on the strength of the deflection, due to the unevenness exerts an opposing force on the Sensomat roller, with the result that an oscillating thereof is avoided.
In addition to the device, the invention also proposes a method in accordance with Claim 20 in which the oscillations, particularly resonant or sympathetic oscillations of the pressing-drum or pressure-roller device against the roller bearing the web of goods are suppressed.
In a further development, it is provided that, as additional method step, the movement of the pressing-drum or pressure-roller device be noted by a movement sensor and, on the basis of this movement signal, the oscillation frequency or the oscillation frequency band of the movement is determined.
In a further development, it can then be provided that, as a function of the frequency signal or frequency-band of CA 0221093~ 1997-07-18 the movement of the pressing-drum or pressure-roller device noted, the stiffness of the oscillation suppressor is so adjusted that the oscillation frequencies of the oscillation suppression device or the frequency band agrees with that of the pressing-drum or pressure-roller device. In this way, the undesired oscillation of the pressing-drum device is suppressed by opposite-phase oscillating of the excited oscillator.
In order to be able to adjust the phase of the compensation oscillation, a further development of the method is provided for noting the movement of the oscillation suppression oscillator mass, and for determining the phase from the movement signals of the pressing-drum or pressure-roller device and the oscillator mass, the phase and controlling the oscillator mass accordingly so as to deflect it shifted in phase.
The invention will be described below by way of example with reference to the figures.
In the drawing:
Fig. 1 is a schematic showing of an oscillation suppression device having a predetermined mass;
Fig. 2 is a schematic showing similar to Fig. 1, in which however movement sensors are arranged on the compensation mass and the oscillating mass;
Fig. 3 is an alternative embodiment of an oscillation CA 0221093~ 1997-07-18 suppression device, which is supported in fixed position;
~ig 4 shows a winding device without oscillation suppression device;
~ig. 5 is a first embodiment of a winding device having an oscillation suppression device, the Sensomat roller being rotatably mounted;
~ig. 6 is a second embodiment of a winding device having an oscillation suppression device the Sensomat roller being displaceable substantially axially;
~ig. 7 is-a winding device having an oscillation suppression device which has a movement sensor to take up the movement of the pressure roller;
~ig. 8 is a winding device such as that shown in Fig. 7, which, in addition, has a further sensor to note the movement of the oscillation suppression oscillator;
~ig. 9 is an alternative embodiment of an oscillation suppression device 5 in which the oscillation suppression device is supported fixed in position on the device bearing the Sensomat roller;
~ig. 10 is a detailed showing of the oscillation suppression device of Fig. 9;
~ig. 11 is a second embodiment of an oscillation suppression device which is supported fixed in CA 0221093~ 1997-07-18 position.
Fig. 1 shows schematically an embodiment of the arrangement in accordance with the invention of a winding device with an oscillation suppression device, the oscillation suppression device not supporting itself.
As shown in Fig. 1, the system can be described in simple fashion in the manner that a mass MW is associated with the wound roll. The pressing-drum device, comprising the Sensomat roller has a mass MSw. Should it happen for any reason whatsoever that there is oscillation of the Sensomat roller or the pressing-drum or pressure-roller device excited by the wound roll, such oscillation can be described by the model of one or more harmonic oscillators having one or more oscillation frequencies or an oscillation frequency band.
"By the model" means that the Sensomat roller has a certain stiffness KS and a certain damping Cs with respect to the wound roll. These constants determine the oscillation frequency of the harmonic oscillator. When the mass of the wound roll is much greater than the mass of the Sensomat device, then in a first approximation for the frequency with which the Sensomat roller oscillates we have ~ = ~K /M
The oscillation frequencies of the pressing-drum device lie preferably between 10 and 50 Hz. With regard to the theoretical description of oscillations, see, for instance, "Dubbel, Taschenbuch fur Maschinenbau, 18th Edition, pages CA 0221093~ 1997-07-18 B37 - B44, 1996, published by Springer Verlag, Berlin".
As oscillation damper there is provided a predetermined mass MR which oscillates freely against the mass MSw, this system, in its turn, having a given stiffness KA and a given damping CA, for the frequency of which system we again have, in first approximation, ~0 ~ ~Ko/MR.
If the mass MSw is now excited to oscillation, this undesired oscillation can be suppressed in the manner that the predetermined mass MR is excited with the same frequency, also to an oscillation which, with corresponding phase displacement, compensates for the oscillation of the mass MSw, i.e. we have ~s ~ ~o- In order to adjust the frequency of oscillation there is used essentially the variation of the stiffness KA of the oscillation suppression oscillator.
Fig. 2 is a showing of the same arrangement as Fig. 1, but the pressing-drum device with the mass MSw as well as the predetermined mass of the oscillation suppression device have movement sensors 1 and 3 respectively which obtain movement signals of the mass from which the frequency and the phase of the oscillations with respect to each other can be determined. By means of the open-loop/closed-loop controller 5 it is then possible to control the oscillator of the oscillation suppression device with the mass MR in such a manner that it oscillates both in frequency and in phase precisely in such a manner as to compensate for the CA 022l093~ l997-07-l8 oscillation of the Sensomat roller.
Fig. 3 again shows the system consisting of a mass Mw of the wound roll and MSw of the pressing-drum device which are coupled oscillationally with each other, and an oscillation suppression device, the oscillation suppression device having a fixed support 7 and the mass of the pressing-drum device or else of the Sensomat roller alone is elastically supported thereon. With a knowledge of disturbing influences which come from the wound roll having the mass Mw, such systems can be controlled in such a manner that the oscillation suppression device has a given stiffness KA and a given damping CA so that blows on the mass of the Sensomat roller or pressing-drum device are compensated for by an opposing force so that no excitation to oscillation of the Sensomat roller or pressing-drum device takes place.
Fig. 4 shows an embodiment of a winding device of the above type without the oscillation suppression device of the invention.
The winding device 10 comprises a horizontal carriage 12 which is part of the pressing-drum or pressure-roller device.
The horizontal carriage 12 is movable in horizontal direction on a guide path 14, as shown. The horizontal carriage 12 bears the pressing-drum or pressure-roller 16. The pressing drum 16 can have a drive. The supports 18 of the pressing drum 16 ("Sensomat roller") are also movable horizontally by CA 022l093~ l997-07-l8 means of a short-stroke force producer 20 ("Sensomat~) on the horizontal carriage 12. The horizontal carriage 12 furthermore bears a scraper 22 for conducting the web of paper downward (as waste).
Spaced horizontally from the horizontal carriage 12 there is a device 24 for the support of the paper roll 26 being produced (support device). The support device is merely indicated schematically here. It may have different embodiments. Thus, it can, for instance, comprise two rollers which are parallel to the roll of paper and around which a support belt is wrapped.
A pressure roller 26 is provided in the region of the support device 24. It extends over the entire width of the paper roll 26.
As shown in Fig. 4, the paper roll 28, has deviations, shown exaggerated in size, in the contour of its surface at the point 30 from the ideal circular course expected. Since this unevenness continues or increases during the entire winding process, it will come into contact at periodic intervals with the Sensomat roller 16 and in this way, via said Sensomat roller, excite the entire pressing-drum device to undesired oscillations. This is due to the fact that a closed-loop controller readjusts the short-stroke cylinder in order to maintain a given linear force in the direction of the place of indentation. The Sensomat roller 16 can, as a CA 0221093~ 1997-07-18 result of this control, start to oscillate and transmit this oscillation to the movably supported horizontal carriage 12 and thus lead to an oscillation of the entire pressing-drum device. It is to be noted that the short-stroke cylinder 20 is merely one example of pressing means by which the pressing-drum or pressure-roller device can be brought into contact with the shaft in order to apply the desired linear force to the shaft or wound roll.
The position of the winding device shown in Fig. 4 characterizes an operating phase of the winding device in which the paper roll 9 is practically completely wound. The horizontal carriage 12 is in its extreme left-hand position.
By the horizontal mobility of the pressing carriage 12, the latter travels, with simultaneous maintaining of the contact of Sensomat roller and wound roll with increasing diameter of the roll, towards the left in the embodiment shown.
As stated, the pressing drum 16 lies against the periphery of the paper roll 26 while the pressing roller 28 is still not in contact with the paper roll. Contact takes place only when a change in roll, which will not be described in this application, is to be effected.
Fig. 5 shows a second possible embodiment of a device in accordance with Fig. 4, which already comprises an oscillation suppression device. In principle, the winding device shown in Fig. 5 differs from that shown in Fig. 4 by CA 022l093~ l997-07-l8 the fact that the mobility of the pressing drum 16 ("Sensomat roller") is not produced via a horizontally movable carriage but by suspension of the Sensomat roller on a sort of a mathematical pendulum 40 which can be fastened, for instance, to a cover 42 and is rigidly connected via the connection 44 to another pendulum 46 which bears the pressing device in the form of a short-stroke cylinder 20. On the support 18 of the pressing drum 16 there is firmly attached a support device 50 which bears a guide path 52 on which a predetermined mass MR
54 is horizontally movable. The compensation mass 54 which is movable independently in horizontal direction on the guide rail 52 is connected with the piston rods 56, 58 of two cylinders 60, 62 which can be filled with gas or a liquid and are firmly anchored on the guide path. If the Sensomat roller or pressing device is completely at rest, then the compensation mass is also at rest, namely in its equilibrium position, preferably in a central position between the two cylinders. The manner of operation of the cylinders will be explained in further detail in connection with the embodiment, shown in Fig. 5, of the winding device with horizontally displaceably pressing-drum or pressure-roller device, which also has an oscillation suppression device such as shown in Fig. 5.
As already described in Fig. 5, upon oscillations of the Sensomat roller 16 which may lead to an oscillation of the CA 022l093~ l997-07-l8 entire pressing-drum device, the mass MR 54 of the oscillation suppression device 70 which rests, via the support device 50, exclusively on the support 18 of the Sensomat roller 16, excites an oscillation which compensates for the oscillation of the Sensomat roller or pressing-drum device. In this connection, it is to be noted here that the frequency of oscillation of the pressing-drum device, comprising the Sensomat roller and the horizontal carriage since the short-stroke piston 20 attempts to hold the Sensomat roller in a given position on the horizontal carriage, corresponds to the frequency with which the mass MR
oscillates. For this, it is necessary to be able to adjust the frequency of oscillation of the compensation oscillator consisting of the mass MR and the piston 60, 62. This is done in the manner that the pressure prevailing in the cylinders 60, 62 which are filled with hydraulic fluid or with gas, against which the pressure of the pistons must work upon displacement is varied. It has namely been found that, for adiabatic guidance and filling with an ideal gas, the opposing force which the pistons build up upon displacement amounts in first approximation to:
F - f(Pz) . x, in which x is the displacement of the piston rod in horizontal direction. However, this means that for the stiffness we have:
CA 0221093~ 1997-07-18 KA = f(Pz)~
and therefore the stiffness is a function of the gas pressure Pz prevailing in the cylinder.
Fig. 7 shows an embodiment of the winding device with oscillation suppression devlce 70 according to Fig. 6, in which the oscillation suppression device furthermore comprises a movement sensor 80 which notes the movement of the pressing-drum or pressure-roller device and feeds the movement signal to a control unit which determines the frequency of the movement of the pressing-drum or pressure-roller device from the movement value. The control device 82 then changes the stiffness of the oscillation suppression oscillator having the predetermined mass MR 54 in such a manner that the frequency with which this system oscillates or is excited agrees with the frequency with which the pressing-drum or pressure-roller device oscillates. Since the stiffness in the case of a cylinder filled with an ideal gas with the pre-established surrounding parameters is a function of the pressure Pz in the cylinder, it is for instance possible, based on a table drawn up in accordance with calibration measurements in which the pressure values of the cylinders 60 and 62 are associated with the stiffnesses of the oscillation suppression oscillator system to adjust KA
as desired. Therefore, in accordance with the desired frequency or stiffness, the cylinders 60 and 62 are acted on CA 0221093~ 1997-07-18 by a corresponding pressure Pz over the lines 84.
In Fig. 8, the oscillation suppression device of Fig. 7 is further developed in the manner that, in addition, there are also introduced into the system movement sensors 90, 92 which note the movement of the oscillation suppression oscillator and feed these movement signals to the control unit 82 which in the present case can operate also as closed-loop control unit. By the obtaining of this signal it is namely possible also to adapt the phase of the oscillations to each other, which makes a targeted actuation of the oscillation suppression oscillator possible so that an active oscillation suppression can be carried out. For this, special control programs are required, such as known from US
patent US-A 5,431,261, the disclosure of which is included in its entirety in the present application. US-A 5,431,261 relates to an active control process for damping oscillations of a large mass by means of a oscillation suppression oscillator. In essence, a variable force is exerted on the oscillation suppression device, which force is proportional to the displacement of the oscillation suppression mass and has a given time delay controlled by open-loop or closed-loop control. With such a control algorithm, oscillations can be actively suppressed by regulating the oscillation suppression oscillator.
CA 0221093~ 1997-07-18 In Fig. 9, an entirely different concept of a oscillation suppression on a winding device is shown.
Advantageously, in this connection no additional support device 50 as compared with the embodiments of Figs. 5 to 8 is required since the oscillation suppression system is not fastened exclusively on the bearing 18 of the Sensomat roller 16 but to it and to another support which is stationary. For example, the short-stroke cylinder can, by suitable conversion, itself be used to dampen oscillations of the Sensomat roller. This is possible by the converting of the short-stroke-cylinder, as shown in detail in Fig. 10.
The short-stroke cylinder 20 has two chambers 100 and 102 which are separated by a piston 104 which is seated on a piston rod 106, which, in its turn, is connected with the bearing 18 of the Sensomat roller 16. In the two chamber pressures P1 and P2 prevail, P1 being all cases greater than P2. In the feed line 108 to the chamber 100 and the feed line 110 to the chamber 102 there are present chokes 112 and 114 respectively. Should there now be present an ovalness or unevenness 30 in the wound roll 26, then the Sensomat roller receives a push, for instance towards the left. Due to the reduced cross section, the hydraulic liquid or the gas in the chamber 100 cannot escape rapidly enough, so that there is a rise in pressure which builds up an opposing force which is substantially linear to the displacement, so that the push of CA 0221093~ 1997-07-18 the Sensomat roller is acted on, with this arrangement, by an opposing force and thereby compensated for. An exciting of the system is no longer possible in this way. Nevertheless, at all times the same average constant linear force is introduced into the slot 116 between Sensomat 16 and roll 30.
In Fig. 9, as in all other figures, the guidance of the web of paper 120 around the Sensomat roller 16 and onto the wound roll 26 is also clearly shown.
The embodiment in accordance with Fig. 11 shows an alternative embodiment of the oscillation suppression device of the invention which is shown in Figs. 9 and 10. In contradistinction to the embodiment in accordance with Figs.
9 and 10, in this case an additional cylinder 130 is used for the compensation, which cylinder can be supported for instance in a bracket 134 on a wall 132. The web of paper 120 is passed through the opening 136 in the wall 132. The somewhat greater structural expense of Fig. 11 makes it possible, however, contrary to the embodiment of Figs. 9 and 10, to provide two separate controls for the short-stroke cylinder 20 and the oscillation suppression cylinder 130.
While the controls of the short-stroke cylinder 20 on the average see to it that the linear force in the slot 116 between the wound roll 26 and the Sensomat roller 16 is retained, any unevennesses which occur in the surface of the roll are done away with by corresponding opposing forces with CA 022l093~ l997-07-l8 the help of the oscillation suppression cylinder 130 against these unevennesses.
In this way, not only is an oscillation of the pressing-drum or pressure-roller device, which also comprises the horizontal carriage, compensated for, but, in addition, with corresponding application of an opposing force, the wound roll is also smoothed so that, in contrast with the previous devices, the unevenness does not increase but is compensated for on the average and the desired round contour of the package is thus obtained.
The control of the oscillation suppression cylinder ls controlled as a function of the contour of the roll. For this, it is necessary to measure the contour of the package over time. This can be effected, for instance, by means of an optical or a mechanical sensor which measures deviations from the ideal round contour or else by variation of the force on the piston 130 averaged over several cycles and placed in a memory unit (not shown) so that a self-adaptive adaptation of the compensating forces to the contour of the roll is possible.
By the oscillation suppression device of the invention it is thus possible, for the first time, to suppress undesired oscillations of the pressing-drum or pressure-roller device in a winding device in which the wound roll itself is substantially fixed in space and the pressing-drum or pressure-roller device is displaced relative to the roll as it increases in size, in whlch connection a constant pressing force in the slot between Sensomat roller and roll on the average is seen to by means of a pressing device which can be designed as a short-stroke cylinder.
FOR WINDING A WEB OF PAPER INTO A ROLL
The present invention relates to an oscillation suppression oscillator in accordance with the preamble to Claim 1, and to a device for winding a traveling web of paper into a roll in accordance with the preamble to Claims 3 and 20.
Winding machines for the winding of paper webs can be arranged at the end of a paper machine in order to bring the web of paper~obtained there into the form of a roll (so-called Pope reel winder). However, they are also used in order to rewind a finished roll in order to produce rolls of a very specific quality of winding.
In all cases, the paper roll is to have very specific properties, in particular with respect to its hardness. The hardness of the roll should generally decrease from a certain initial value to a final value, a hard core winding at the very start being of particular importance. The decrease should be as uniform as possible from the first layer to the last layer. It should have a given gradient which is not too great and not too slight. The variation in the hardness of the roll should in no case show abrupt changes, for instance a sudden decrease. No radial or tangential stresses which impair or damage the web of paper must occur in the roll.
CA 0221093~ 1997-07-18 It has already been attempted to achieve all of this, but without success. Winding machines of known construction produce instead of this, for instance, rolls in which the core is either extremely soft or extremely hard and in which there is a strong decrease in the hardness of the roll towards the end -- for instance at four-fifths the diameter of the roll. This has the result that the first part, and therefore the extremely soft or hard core, cannot be used since the web is crushed and bursts in this region, so that this part must be thrown away as reject; in the region of the end, in which the roll has not been wound sufficiently hard, there is a lateral displacement of the layers relative to each other so that the sides of the finished roll appear frayed and the edges of the web can be easily damaged.
A poorly constructed core (too little or too great a hardness) namely does not permit a dependable forming of the rest of the roll. This problem is particularly serious in the case of pressure-sensitive papers, for instance self-duplicating (SD) papers, in the case of which narrow limits are set for the pressing of the shaft bearing the roll being produced against the outer surface of the carrier drum.
In the method known from DE 40 07 329, the roll of paper being produced is shifted in horizontal direction corresponding to the increase in the size of the roll. The roll of paper reaches a high weight, which can exceed CA 0221093~ 1997-07-18 hundreds of tons. For this reason, the roll of paper cannot, upon its growth, be pressed, in sensitive fashion, against the pressing drum.
DE 44 15 324 shows and describes a winding machine for winding a web of paper on a shaft with central drive. This machine comprises a winding station, a receiving station, and an idle pressing roller. The pressing roller rests against the circumference of the secondary roll of paper all the way up into the winding station. The web is guided in such a manner that it enters continuously, without wrapping, into the inlet slot. If such a winding device is operated with high speeds of the web, preferably more than 1000 meters a minute, then oscillations of the pressing roller occur suddenly and unexpectedly, which may lead in case of resonance to damage to the winding device. In order not to permit this to occur, the diameter of the pressing roller has been selected as small as possible, and predominantly of the same size as that of a normal web guide roller. This has the disadvantage that the pressing roller, due to the absence of sufficient flexural rigidity is not adapted to apply linear forces of any desired value and in particular not to extremely large web widths (up to about 10 meters).
From USA 5,431,261, a controlled oscillation suppressor is known. This oscillation suppressor had the disadvantage that large masses in the region of several tons, such as the CA 0221093~ 1997-07-18 previously described pressing-drum or pressure-roller device, could not be damped since as active or excited resonators there were always used ones which were tuned magnetostrictively or electrorestrictively to different frequencies.
The first object of the invention is thus to indicate resonators which can be used as oscillation suppressors for oscillations of large masses.
A second object of the invention is to provide a winding device in which the disadvantages of the prior-art devices are avoided, and in particular in the case of winding devices in accordance with the preamble to Claim 1, such as known from DE 44 15 324, oscillations of the pressing-drum or pressure-roller device which comprises a pressing-drum or pressure roller are suppressed.
In accordance with the invention, the first object is achieved by Claim 1 and the second object by the device according to Claim 3 and the method according to Claim 20.
Instead of magnetostrictive or electrorestrictive elements, the invention proposes, in order to obtain the first object, the use of hydraulic or gas-filled cylinders the stiffness KA of which is adjusted as a function of the pressure prevailing in the cylinder, against which pressure the piston must be moved. It is advantageously provided for such a device that the predetermined movable mass, i.e. a CA 0221093~ 1997-07-18 mass which carries out an oscillating movement, be arranged between two cylinders and be connected with pistons of the same rigidity. In addition to the possibility of adjusting the stiffness KA in such a system by change of pressure, it is also possible, upon the connection of the two cylinders, to introduce a damping member via a line containing a choke, whereby a given frequency spectrum or frequency band can be associated with the movement of the cylinders.
Essential reasons for the occurrence of oscillations of the pressing-drum or pressure-roller device which comprise the pressing drum or pressing rollers, referred to below as Sensomat rollers, and are part of the sensitive winding device, are, in accordance with the findings of the inventors, deviations of the wound paper roll from the ideal circular contour. As the inventors have found, a paper roll always has places which are not round, for instance compression places, which can excite the Sensomat rollers and the carrier device connected therewith to oscillation. This is due to the fact that in the case of the winding device in accordance with Claim 3, the Sensomat roller is not supported as in other device of the prior art by an infinitely large mass, for instance a foundation, but is arranged on a device which is movable relative to the paper roll, so as to move away from the center of the roll upon the increase in the diameter of the roll.
CA 0221093~ 1997-07-18 The invention therefore proposes, for the solution of the second object, in a system having a pressing-drum or pressure-roller device which is movable relative to the shaft or paper roll, an oscillation suppressor by which these oscillations which occur can be suppressed.
As example of such an oscillation suppression device, the invention proposes providing on the supporting device, which, for instance, can be developed as a rail and is fastened on the support of the pressing-drum or pressure-roller device, a mass which can move on the supporting device relative to the pressing-drum or pressure-roller device, for instance in the manner that it slides guided along the path or rolls on a rail. The movement of the mass is that of a harmonic oscillator, i.e. upon deflection of the mass from its position of rest it experiences, in the ideal case, an opposing force which increases linearly with the deflection, so that an oscillating movement, and therefore a swinging of the mass is obtained when the latter is excited to this.
This can take place by self-excitation, for instance upon occurrence of a swinging of the sensor roll or of the pressing-drum device or, in a further development of the invention, by means for exciting the oscillation, one special embodiment consisting therein that the means for exciting the oscillation comprises at least one actuator, for instance a hydraulic cylinder or a cylinder filled with gas, for CA 0221093~ 1997-07-18 instance air.
In a further embodiment, it can be provided that the means for exciting the phase-displaced oscillation comprise a movement sensor which is arranged on the pressing-drum or pressure-roller device. By the noting of the movement of the pressing-drum or pressure-roller device the frequency of oscillation thereof can be determined. In this way it is possible in a further embodiment to determine the instantaneous oscillation frequency or oscillation frequency band of the pressing-drum or pressure-roller device.
These signals can be used, in one particularly advantageous embodiment, in order to control means for adjusting the frequency with which the mass of the oscillation suppressor oscillates. The desired tunability or variability of the frequency permits an oscillation suppression oscillator which comprises at least two cylinders which can be filled with hydraulic fluid or a gas.
In a further development of the invention it is provided that the oscillation suppressor comprises an open-loop or closed-loop control device with which, as a function of the measurement signal produced by the movement sensor, the means for adjusting the oscillation frequency are so controlled that the oscillation frequency or frequencies of the mass always correspond to the oscillation frequency or frequencies of the pressing-drum device. This can take place, for CA 0221093~ 1997-07-18 instance, in the manner that the pressures in the aforementioned cylinders are so adjusted that a given stiffness of the cylinders is obtained whereby the "spring constant" of the oscillator consisting of mass and cylinder is adjusted. This thus permits a change in the oscillation frequency of the oscillator.
The open-loop control can be expanded to a closed-loop control even if a movement sensor is provided also on the mass of the oscillator for the suppression of oscillations, so that the phase of the oscillations with respect to each other can be determined from the movement signal of the pressing-drum device and oscillation-suppression device. The oscillation excited by the actuator is excited by means of the closed-loop control in such a manner phase shifted with respect to the first that a substantially complete extinguishing of the undesired oscillation of the pressing-drum or pressure-roller device is effected, even if the undesired oscillation of the pressing-drum device changes with time.
In an entirely different concept of the oscillation suppression, it is provided that the support device not be firmly connected only with the pressing-drum or pressure-roller device but that furthermore it has a firm support on, for instance, the wall or the carrier means for the pressing drum itself, which is movable relative to the shaft. In a CA 0221093~ 1997-07-18 first embodiment of this second concept, it is provided that the oscillation suppressor comprises a hydraulic cylinder, the hydraulic lines connected to the hydraulic cylinder having a choke. If the web has an unevenness, then the piston of the cylinder of the oscillation damping device is deflected. In this way, for instance, hydraulic fluid is displaced out of the cylinder. Since the choke prevents an immediate discharge of the hydraulic oil out of the cylinder or opposes resistance to it, the stiffness is increased and thus, depending on the strength of the deflection, due to the unevenness exerts an opposing force on the Sensomat roller, with the result that an oscillating thereof is avoided.
In addition to the device, the invention also proposes a method in accordance with Claim 20 in which the oscillations, particularly resonant or sympathetic oscillations of the pressing-drum or pressure-roller device against the roller bearing the web of goods are suppressed.
In a further development, it is provided that, as additional method step, the movement of the pressing-drum or pressure-roller device be noted by a movement sensor and, on the basis of this movement signal, the oscillation frequency or the oscillation frequency band of the movement is determined.
In a further development, it can then be provided that, as a function of the frequency signal or frequency-band of CA 0221093~ 1997-07-18 the movement of the pressing-drum or pressure-roller device noted, the stiffness of the oscillation suppressor is so adjusted that the oscillation frequencies of the oscillation suppression device or the frequency band agrees with that of the pressing-drum or pressure-roller device. In this way, the undesired oscillation of the pressing-drum device is suppressed by opposite-phase oscillating of the excited oscillator.
In order to be able to adjust the phase of the compensation oscillation, a further development of the method is provided for noting the movement of the oscillation suppression oscillator mass, and for determining the phase from the movement signals of the pressing-drum or pressure-roller device and the oscillator mass, the phase and controlling the oscillator mass accordingly so as to deflect it shifted in phase.
The invention will be described below by way of example with reference to the figures.
In the drawing:
Fig. 1 is a schematic showing of an oscillation suppression device having a predetermined mass;
Fig. 2 is a schematic showing similar to Fig. 1, in which however movement sensors are arranged on the compensation mass and the oscillating mass;
Fig. 3 is an alternative embodiment of an oscillation CA 0221093~ 1997-07-18 suppression device, which is supported in fixed position;
~ig 4 shows a winding device without oscillation suppression device;
~ig. 5 is a first embodiment of a winding device having an oscillation suppression device, the Sensomat roller being rotatably mounted;
~ig. 6 is a second embodiment of a winding device having an oscillation suppression device the Sensomat roller being displaceable substantially axially;
~ig. 7 is-a winding device having an oscillation suppression device which has a movement sensor to take up the movement of the pressure roller;
~ig. 8 is a winding device such as that shown in Fig. 7, which, in addition, has a further sensor to note the movement of the oscillation suppression oscillator;
~ig. 9 is an alternative embodiment of an oscillation suppression device 5 in which the oscillation suppression device is supported fixed in position on the device bearing the Sensomat roller;
~ig. 10 is a detailed showing of the oscillation suppression device of Fig. 9;
~ig. 11 is a second embodiment of an oscillation suppression device which is supported fixed in CA 0221093~ 1997-07-18 position.
Fig. 1 shows schematically an embodiment of the arrangement in accordance with the invention of a winding device with an oscillation suppression device, the oscillation suppression device not supporting itself.
As shown in Fig. 1, the system can be described in simple fashion in the manner that a mass MW is associated with the wound roll. The pressing-drum device, comprising the Sensomat roller has a mass MSw. Should it happen for any reason whatsoever that there is oscillation of the Sensomat roller or the pressing-drum or pressure-roller device excited by the wound roll, such oscillation can be described by the model of one or more harmonic oscillators having one or more oscillation frequencies or an oscillation frequency band.
"By the model" means that the Sensomat roller has a certain stiffness KS and a certain damping Cs with respect to the wound roll. These constants determine the oscillation frequency of the harmonic oscillator. When the mass of the wound roll is much greater than the mass of the Sensomat device, then in a first approximation for the frequency with which the Sensomat roller oscillates we have ~ = ~K /M
The oscillation frequencies of the pressing-drum device lie preferably between 10 and 50 Hz. With regard to the theoretical description of oscillations, see, for instance, "Dubbel, Taschenbuch fur Maschinenbau, 18th Edition, pages CA 0221093~ 1997-07-18 B37 - B44, 1996, published by Springer Verlag, Berlin".
As oscillation damper there is provided a predetermined mass MR which oscillates freely against the mass MSw, this system, in its turn, having a given stiffness KA and a given damping CA, for the frequency of which system we again have, in first approximation, ~0 ~ ~Ko/MR.
If the mass MSw is now excited to oscillation, this undesired oscillation can be suppressed in the manner that the predetermined mass MR is excited with the same frequency, also to an oscillation which, with corresponding phase displacement, compensates for the oscillation of the mass MSw, i.e. we have ~s ~ ~o- In order to adjust the frequency of oscillation there is used essentially the variation of the stiffness KA of the oscillation suppression oscillator.
Fig. 2 is a showing of the same arrangement as Fig. 1, but the pressing-drum device with the mass MSw as well as the predetermined mass of the oscillation suppression device have movement sensors 1 and 3 respectively which obtain movement signals of the mass from which the frequency and the phase of the oscillations with respect to each other can be determined. By means of the open-loop/closed-loop controller 5 it is then possible to control the oscillator of the oscillation suppression device with the mass MR in such a manner that it oscillates both in frequency and in phase precisely in such a manner as to compensate for the CA 022l093~ l997-07-l8 oscillation of the Sensomat roller.
Fig. 3 again shows the system consisting of a mass Mw of the wound roll and MSw of the pressing-drum device which are coupled oscillationally with each other, and an oscillation suppression device, the oscillation suppression device having a fixed support 7 and the mass of the pressing-drum device or else of the Sensomat roller alone is elastically supported thereon. With a knowledge of disturbing influences which come from the wound roll having the mass Mw, such systems can be controlled in such a manner that the oscillation suppression device has a given stiffness KA and a given damping CA so that blows on the mass of the Sensomat roller or pressing-drum device are compensated for by an opposing force so that no excitation to oscillation of the Sensomat roller or pressing-drum device takes place.
Fig. 4 shows an embodiment of a winding device of the above type without the oscillation suppression device of the invention.
The winding device 10 comprises a horizontal carriage 12 which is part of the pressing-drum or pressure-roller device.
The horizontal carriage 12 is movable in horizontal direction on a guide path 14, as shown. The horizontal carriage 12 bears the pressing-drum or pressure-roller 16. The pressing drum 16 can have a drive. The supports 18 of the pressing drum 16 ("Sensomat roller") are also movable horizontally by CA 022l093~ l997-07-l8 means of a short-stroke force producer 20 ("Sensomat~) on the horizontal carriage 12. The horizontal carriage 12 furthermore bears a scraper 22 for conducting the web of paper downward (as waste).
Spaced horizontally from the horizontal carriage 12 there is a device 24 for the support of the paper roll 26 being produced (support device). The support device is merely indicated schematically here. It may have different embodiments. Thus, it can, for instance, comprise two rollers which are parallel to the roll of paper and around which a support belt is wrapped.
A pressure roller 26 is provided in the region of the support device 24. It extends over the entire width of the paper roll 26.
As shown in Fig. 4, the paper roll 28, has deviations, shown exaggerated in size, in the contour of its surface at the point 30 from the ideal circular course expected. Since this unevenness continues or increases during the entire winding process, it will come into contact at periodic intervals with the Sensomat roller 16 and in this way, via said Sensomat roller, excite the entire pressing-drum device to undesired oscillations. This is due to the fact that a closed-loop controller readjusts the short-stroke cylinder in order to maintain a given linear force in the direction of the place of indentation. The Sensomat roller 16 can, as a CA 0221093~ 1997-07-18 result of this control, start to oscillate and transmit this oscillation to the movably supported horizontal carriage 12 and thus lead to an oscillation of the entire pressing-drum device. It is to be noted that the short-stroke cylinder 20 is merely one example of pressing means by which the pressing-drum or pressure-roller device can be brought into contact with the shaft in order to apply the desired linear force to the shaft or wound roll.
The position of the winding device shown in Fig. 4 characterizes an operating phase of the winding device in which the paper roll 9 is practically completely wound. The horizontal carriage 12 is in its extreme left-hand position.
By the horizontal mobility of the pressing carriage 12, the latter travels, with simultaneous maintaining of the contact of Sensomat roller and wound roll with increasing diameter of the roll, towards the left in the embodiment shown.
As stated, the pressing drum 16 lies against the periphery of the paper roll 26 while the pressing roller 28 is still not in contact with the paper roll. Contact takes place only when a change in roll, which will not be described in this application, is to be effected.
Fig. 5 shows a second possible embodiment of a device in accordance with Fig. 4, which already comprises an oscillation suppression device. In principle, the winding device shown in Fig. 5 differs from that shown in Fig. 4 by CA 022l093~ l997-07-l8 the fact that the mobility of the pressing drum 16 ("Sensomat roller") is not produced via a horizontally movable carriage but by suspension of the Sensomat roller on a sort of a mathematical pendulum 40 which can be fastened, for instance, to a cover 42 and is rigidly connected via the connection 44 to another pendulum 46 which bears the pressing device in the form of a short-stroke cylinder 20. On the support 18 of the pressing drum 16 there is firmly attached a support device 50 which bears a guide path 52 on which a predetermined mass MR
54 is horizontally movable. The compensation mass 54 which is movable independently in horizontal direction on the guide rail 52 is connected with the piston rods 56, 58 of two cylinders 60, 62 which can be filled with gas or a liquid and are firmly anchored on the guide path. If the Sensomat roller or pressing device is completely at rest, then the compensation mass is also at rest, namely in its equilibrium position, preferably in a central position between the two cylinders. The manner of operation of the cylinders will be explained in further detail in connection with the embodiment, shown in Fig. 5, of the winding device with horizontally displaceably pressing-drum or pressure-roller device, which also has an oscillation suppression device such as shown in Fig. 5.
As already described in Fig. 5, upon oscillations of the Sensomat roller 16 which may lead to an oscillation of the CA 022l093~ l997-07-l8 entire pressing-drum device, the mass MR 54 of the oscillation suppression device 70 which rests, via the support device 50, exclusively on the support 18 of the Sensomat roller 16, excites an oscillation which compensates for the oscillation of the Sensomat roller or pressing-drum device. In this connection, it is to be noted here that the frequency of oscillation of the pressing-drum device, comprising the Sensomat roller and the horizontal carriage since the short-stroke piston 20 attempts to hold the Sensomat roller in a given position on the horizontal carriage, corresponds to the frequency with which the mass MR
oscillates. For this, it is necessary to be able to adjust the frequency of oscillation of the compensation oscillator consisting of the mass MR and the piston 60, 62. This is done in the manner that the pressure prevailing in the cylinders 60, 62 which are filled with hydraulic fluid or with gas, against which the pressure of the pistons must work upon displacement is varied. It has namely been found that, for adiabatic guidance and filling with an ideal gas, the opposing force which the pistons build up upon displacement amounts in first approximation to:
F - f(Pz) . x, in which x is the displacement of the piston rod in horizontal direction. However, this means that for the stiffness we have:
CA 0221093~ 1997-07-18 KA = f(Pz)~
and therefore the stiffness is a function of the gas pressure Pz prevailing in the cylinder.
Fig. 7 shows an embodiment of the winding device with oscillation suppression devlce 70 according to Fig. 6, in which the oscillation suppression device furthermore comprises a movement sensor 80 which notes the movement of the pressing-drum or pressure-roller device and feeds the movement signal to a control unit which determines the frequency of the movement of the pressing-drum or pressure-roller device from the movement value. The control device 82 then changes the stiffness of the oscillation suppression oscillator having the predetermined mass MR 54 in such a manner that the frequency with which this system oscillates or is excited agrees with the frequency with which the pressing-drum or pressure-roller device oscillates. Since the stiffness in the case of a cylinder filled with an ideal gas with the pre-established surrounding parameters is a function of the pressure Pz in the cylinder, it is for instance possible, based on a table drawn up in accordance with calibration measurements in which the pressure values of the cylinders 60 and 62 are associated with the stiffnesses of the oscillation suppression oscillator system to adjust KA
as desired. Therefore, in accordance with the desired frequency or stiffness, the cylinders 60 and 62 are acted on CA 0221093~ 1997-07-18 by a corresponding pressure Pz over the lines 84.
In Fig. 8, the oscillation suppression device of Fig. 7 is further developed in the manner that, in addition, there are also introduced into the system movement sensors 90, 92 which note the movement of the oscillation suppression oscillator and feed these movement signals to the control unit 82 which in the present case can operate also as closed-loop control unit. By the obtaining of this signal it is namely possible also to adapt the phase of the oscillations to each other, which makes a targeted actuation of the oscillation suppression oscillator possible so that an active oscillation suppression can be carried out. For this, special control programs are required, such as known from US
patent US-A 5,431,261, the disclosure of which is included in its entirety in the present application. US-A 5,431,261 relates to an active control process for damping oscillations of a large mass by means of a oscillation suppression oscillator. In essence, a variable force is exerted on the oscillation suppression device, which force is proportional to the displacement of the oscillation suppression mass and has a given time delay controlled by open-loop or closed-loop control. With such a control algorithm, oscillations can be actively suppressed by regulating the oscillation suppression oscillator.
CA 0221093~ 1997-07-18 In Fig. 9, an entirely different concept of a oscillation suppression on a winding device is shown.
Advantageously, in this connection no additional support device 50 as compared with the embodiments of Figs. 5 to 8 is required since the oscillation suppression system is not fastened exclusively on the bearing 18 of the Sensomat roller 16 but to it and to another support which is stationary. For example, the short-stroke cylinder can, by suitable conversion, itself be used to dampen oscillations of the Sensomat roller. This is possible by the converting of the short-stroke-cylinder, as shown in detail in Fig. 10.
The short-stroke cylinder 20 has two chambers 100 and 102 which are separated by a piston 104 which is seated on a piston rod 106, which, in its turn, is connected with the bearing 18 of the Sensomat roller 16. In the two chamber pressures P1 and P2 prevail, P1 being all cases greater than P2. In the feed line 108 to the chamber 100 and the feed line 110 to the chamber 102 there are present chokes 112 and 114 respectively. Should there now be present an ovalness or unevenness 30 in the wound roll 26, then the Sensomat roller receives a push, for instance towards the left. Due to the reduced cross section, the hydraulic liquid or the gas in the chamber 100 cannot escape rapidly enough, so that there is a rise in pressure which builds up an opposing force which is substantially linear to the displacement, so that the push of CA 0221093~ 1997-07-18 the Sensomat roller is acted on, with this arrangement, by an opposing force and thereby compensated for. An exciting of the system is no longer possible in this way. Nevertheless, at all times the same average constant linear force is introduced into the slot 116 between Sensomat 16 and roll 30.
In Fig. 9, as in all other figures, the guidance of the web of paper 120 around the Sensomat roller 16 and onto the wound roll 26 is also clearly shown.
The embodiment in accordance with Fig. 11 shows an alternative embodiment of the oscillation suppression device of the invention which is shown in Figs. 9 and 10. In contradistinction to the embodiment in accordance with Figs.
9 and 10, in this case an additional cylinder 130 is used for the compensation, which cylinder can be supported for instance in a bracket 134 on a wall 132. The web of paper 120 is passed through the opening 136 in the wall 132. The somewhat greater structural expense of Fig. 11 makes it possible, however, contrary to the embodiment of Figs. 9 and 10, to provide two separate controls for the short-stroke cylinder 20 and the oscillation suppression cylinder 130.
While the controls of the short-stroke cylinder 20 on the average see to it that the linear force in the slot 116 between the wound roll 26 and the Sensomat roller 16 is retained, any unevennesses which occur in the surface of the roll are done away with by corresponding opposing forces with CA 022l093~ l997-07-l8 the help of the oscillation suppression cylinder 130 against these unevennesses.
In this way, not only is an oscillation of the pressing-drum or pressure-roller device, which also comprises the horizontal carriage, compensated for, but, in addition, with corresponding application of an opposing force, the wound roll is also smoothed so that, in contrast with the previous devices, the unevenness does not increase but is compensated for on the average and the desired round contour of the package is thus obtained.
The control of the oscillation suppression cylinder ls controlled as a function of the contour of the roll. For this, it is necessary to measure the contour of the package over time. This can be effected, for instance, by means of an optical or a mechanical sensor which measures deviations from the ideal round contour or else by variation of the force on the piston 130 averaged over several cycles and placed in a memory unit (not shown) so that a self-adaptive adaptation of the compensating forces to the contour of the roll is possible.
By the oscillation suppression device of the invention it is thus possible, for the first time, to suppress undesired oscillations of the pressing-drum or pressure-roller device in a winding device in which the wound roll itself is substantially fixed in space and the pressing-drum or pressure-roller device is displaced relative to the roll as it increases in size, in whlch connection a constant pressing force in the slot between Sensomat roller and roll on the average is seen to by means of a pressing device which can be designed as a short-stroke cylinder.
Claims (27)
1. An oscillation suppression resonator for suppressing oscillations of a large oscillating mass, having 1.1 a support device (50) which is connected with said large oscillating mass;
1.2 a predetermined oscillation suppression mass (MR 54), which is arranged movably on the support device (50);
characterized by the fact that the resonator furthermore comprises 1.3 cylinders (60, 62) which can be filled with gas or fluid and which are firmly attached to the support device (50);
1.4 the pistons of the cylinders being connected via piston rods (56, 58) with the mass movable on the support device, so that upon deflection of the mass (MR 54) from an equilibrium position, a substantially harmonic oscillation takes place with a frequency which is determined by the pressure (Pz) prevailing in the cylinder.
1.2 a predetermined oscillation suppression mass (MR 54), which is arranged movably on the support device (50);
characterized by the fact that the resonator furthermore comprises 1.3 cylinders (60, 62) which can be filled with gas or fluid and which are firmly attached to the support device (50);
1.4 the pistons of the cylinders being connected via piston rods (56, 58) with the mass movable on the support device, so that upon deflection of the mass (MR 54) from an equilibrium position, a substantially harmonic oscillation takes place with a frequency which is determined by the pressure (Pz) prevailing in the cylinder.
2. An oscillation suppression resonator according to Claim 1, characterized by the fact that the cylinders (60, 62) are filled with a gas, and that the pressures in the cylinder at room temperature are so selected that the gas behaves as an ideal gas.
3. A device for winding traveling webs of material, particularly paper webs (120), so as to form a roll (26), 3.1 having a shaft on which the web (12) is wound;
3.2 having a pressing-drum or a pressure-roller device (12, 16, 18), which is movable relative to the shaft; and 3.3 having a pressing device (20) by which the pressing drum (16) or pressure roller of the pressing-drum or pressure-roller device can be brought into contact with the shaft in order to apply a linear force to the shaft;
characterized by the fact that 3.4 the winding device comprises an oscillation suppression device (70) for the pressing-drum or pressure-roller device by which oscillations, and particularly resonance oscillations, of the pressing-drum or pressure-roller device (12, 16, 18) are suppressed during the winding.
3.2 having a pressing-drum or a pressure-roller device (12, 16, 18), which is movable relative to the shaft; and 3.3 having a pressing device (20) by which the pressing drum (16) or pressure roller of the pressing-drum or pressure-roller device can be brought into contact with the shaft in order to apply a linear force to the shaft;
characterized by the fact that 3.4 the winding device comprises an oscillation suppression device (70) for the pressing-drum or pressure-roller device by which oscillations, and particularly resonance oscillations, of the pressing-drum or pressure-roller device (12, 16, 18) are suppressed during the winding.
4. A winding device according to Claim 3, characterized by the fact that the oscillation suppression device (70) comprises a support means (50) which is rigidly connected to the pressing-drum or pressure-roller device.
5. A winding device according to Claim 4, characterized by the fact that the oscillation suppression device (70) comprises a predetermined mass (54) which is arranged movable with respect to the pressing-drum or pressure-roller device on or at the support device (50).
6. A winding device according to Claim 5, characterized by the fact that the oscillation suppression device (70) comprises means for exciting an oscillation which is shifted in phase from the oscillation of the pressing-drum or pressure-roller device.
7. A winding device according to Claim 6, characterized by the fact that said means for exciting the phase-shifted oscillation of the predetermined mass comprises at least one actuator (60, 62) for exciting the oscillation.
8. A winding device according to either of Claims 6 and 7, characterized by the fact that the means for exciting the phase-shifted oscillation comprises at least one movement sensor (80) which is arranged on the pressing-drum or pressure-roller device.
9. A winding device according to Claim 8, characterized by the fact that the movement sensor(s) (80) arranged on the pressing-drum or pressure-roller device receive a signal from which the instantaneous frequency of the oscillation of the pressing-drum or pressure-roller device can be determined.
10. A winding device according to any of Claims 6 to 9, characterized by the fact that the means for exciting the phase-shifted oscillation of the mass comprise means for adjusting the frequency of oscillation of the mass.
11. A winding device according to any of Claims 6 to 10, characterized by the fact that the means for exciting the phase-shifted oscillation comprise cylinders filled with gas or fluid the stiffness KA of which cylinders can be adjusted as a function of the pressure (Pz) prevailing in the cylinder (60, 62).
12. A winding device according to any of Claims 6 to 11, characterized by the fact that the means for exciting the phase-shifted oscillation of the predetermined mass comprises an open-loop/closed-loop controller (82) by which, as a function of the measurement signal received by the movement sensor (80), the means for adjusting the oscillation frequency are so controlled that the oscillation frequencies with which the mass of the oscillation suppression device oscillates corresponds to the frequencies of the oscillation of the pressing-drum or pressure-roller device.
13. A winding device according to any of Claims 6 to 11, characterized by the fact that the means for exciting the phase-shifted oscillation of the predetermined mass comprises an open-loop/closed-loop control device with which, as a function of the measurement signal noted by the movement sensor, the means for adjusting the frequency of oscillation are controlled in such a manner that the oscillation frequency band which forms the basis for the oscillation of the mass of the oscillation suppression device corresponds essentially to the oscillation frequency band of the oscillations of the pressing-drum or pressure-roller device.
14. A winding device according to Claim 12 or 13, characterized by the fact that the means for exciting the phase-shifted oscillation comprises at least one movement sensor (90) for obtaining a movement signal of the predetermined mass (MR 54) so that, from the signal of the movement sensor of the pressing-drum or pressure-roller device and the signal of the movement sensor of the predetermined mass, the phase of the oscillations with respect to each other is determined and can be fed to the control device so that the oscillation of the oscillation suppression device which is excited by the actuator is so shifted in phase from the oscillation of the pressing-drum or pressure-roller device that a substantially complete extinguishing of the oscillation of the pressing-drum or pressure-roller device is obtained.
15. A winding device according to Claim 3, characterized by the fact that the oscillation suppression device comprises a support device which is rigidly attached to the pressing-drum or pressure-roller device, and that the oscillation suppression device furthermore has a stationary support.
16. A winding device according to Claim 15, characterized by the fact that the oscillation suppression device comprises a cylinder which can be filled with gas or liquid, the lines connected to the cylinder having at least one choke (112, 114).
17. A winding device according to Claim 15, characterized by the fact that the oscillation suppression device comprises at least one actuator (130).
18. A winding device according to Claim 17, characterized by the fact that the oscillation suppression device comprises a contour sensor by which the outer contour of the roll is noted.
19. A winding device according to Claim 18, characterized by the fact that the oscillation suppression device comprises an open-loop/closed-loop control device which controls at least one actuator (130) in such a manner that excitations to oscillation which result due to the uneven contour of the roll are suppressed.
20. A method of winding traveling webs of material, particularly paper webs, so as to form a roll, in which 20.1 during the entire process of winding, the pressing roller is pressed against the outer surface of the roll being produced of web of material;
20.2 the center of the roll of web of material remains substantially fixed in position during the entire process of winding; and 20.3 the pressing-drum or pressure-roller device is shifted or deflected to the extent to which the roll of material increases without it coming out of contact with the roll of material;
characterized by the fact that 20.4 oscillations, particularly resonance oscillations of the pressing-drum or pressure-roller device against the roll of material, are suppressed.
20.2 the center of the roll of web of material remains substantially fixed in position during the entire process of winding; and 20.3 the pressing-drum or pressure-roller device is shifted or deflected to the extent to which the roll of material increases without it coming out of contact with the roll of material;
characterized by the fact that 20.4 oscillations, particularly resonance oscillations of the pressing-drum or pressure-roller device against the roll of material, are suppressed.
21. A method according to Claim 20, characterized by the fact that the movement of the pressing-drum or pressure-roller device is noted by a movement sensor and the oscillation frequencies or the oscillation frequency band of the movement determined therefrom.
22. A method according to Claim 21, characterized by the fact that, as a function of the frequency signal of the movement of the pressing-drum or pressure-roller device, the stiffness of the oscillation suppression device is so adjusted that the oscillation frequencies of the oscillation suppression device, which comprises a predetermined mass, corresponds to the oscillation frequencies of the pressing-drum or pressure-roller device.
23. A method according to Claim 22, characterized by the fact that, as a function of the frequency signal of the movement of the pressing-drum or pressure-roller device, the stiffness and damping of the oscillation suppression device is so adjusted that the oscillation frequency band with which the mass of the oscillation suppression device oscillates corresponds to the oscillation frequency band with which the pressing-drum or pressure-roller device oscillates.
24. A method according to Claims 21 to 23, characterized by the fact that the movement of the oscillation suppression device is recorded by a further movement sensor and the phase of the movement of the oscillation suppression device with respect to the movement of the pressing-drum or pressure-roller device is determined therefrom.
25. A method according to any of Claims 21 to 24, characterized by the fact that the actuator is so shifted in phase in order to excite the oscillation of the oscillation suppression device that the oscillation of the pressing-drum or pressure-roller device is substantially suppressed.
26. A method according to Claim 20, characterized by the fact that the contour of the wound roll is recorded by means of a contour sensor.
27. A method according to Claim 26, characterized by the fact that the actuator of the oscillation suppression device is so actuated on basis of the contour signal of the contour sensor that oscillations of the pressing-drum or pressure-roller device which are caused by unevennesses in the wound roll are substantially suppressed.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE1996129205 DE19629205A1 (en) | 1996-07-19 | 1996-07-19 | Method and device for winding a paper web into a roll with active vibration damping |
| DE19629205.0 | 1996-07-19 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2210935A1 true CA2210935A1 (en) | 1998-01-19 |
Family
ID=7800304
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2210935 Abandoned CA2210935A1 (en) | 1996-07-19 | 1997-07-18 | Method and device with active oscillation damping for winding a web of paper into a roll |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP0819638A3 (en) |
| JP (1) | JPH1077143A (en) |
| KR (1) | KR980010014A (en) |
| CA (1) | CA2210935A1 (en) |
| DE (1) | DE19629205A1 (en) |
| ID (1) | ID18654A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6186437B1 (en) | 1998-05-07 | 2001-02-13 | Valmet Corporation | Method and device for applying a load to a reel in a reel-up of a paper web |
| CN102191714A (en) * | 2010-03-09 | 2011-09-21 | 美卓造纸机械公司 | Device and method for regulating force in gap between two rolls |
| US8372245B2 (en) | 2009-03-18 | 2013-02-12 | Metso Paper, Inc. | Roll assembly for a fiber-web machine and method of attenuating vibration of a fiber-web machine roll |
| CN112938577A (en) * | 2021-03-12 | 2021-06-11 | 郑州财经学院 | Drawing paper winding device for art design |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19614300B4 (en) * | 1995-04-21 | 2004-08-26 | Abb Patent Gmbh | Process for self-regulating compensation for the effects of uneven concentricity of a roll |
| DE19652769A1 (en) | 1996-12-18 | 1998-06-25 | Voith Sulzer Papiermasch Gmbh | Method and device for damping contact vibrations |
| FI101320B1 (en) * | 1997-04-30 | 1998-05-29 | Valmet Corp | Method and plant for damping oscillation in a paper machine or in a paper finishing device |
| US5961899A (en) * | 1997-07-15 | 1999-10-05 | Lord Corporation | Vibration control apparatus and method for calender rolls and the like |
| FI110424B (en) * | 1998-06-18 | 2003-01-31 | Metso Paper Inc | The winder and the method for winding the web |
| CA2279609C (en) | 1998-08-06 | 2007-05-01 | Voith Sulzer Papiertechnik Patent Gmbh | Device to actively weaken undesirable vibrations in a rotating roll; device for treatment of a material web; specifically a paper or cardboard web |
| DE10115862A1 (en) * | 2001-03-30 | 2002-10-17 | Jagenberg Papiertech Gmbh | Winding machine for winding a material web, in particular a paper or cardboard web, into winding rolls |
| DE10125192A1 (en) * | 2001-05-23 | 2002-11-28 | Voith Paper Patent Gmbh | Method and device for active vibration damping in winding machines |
| DE10137063A1 (en) * | 2001-07-28 | 2003-02-13 | Voith Paper Patent Gmbh | Paper or carton web winding pressure regulated by a electro-mechanical jack acting on the gap between two rollers |
| DE20114750U1 (en) * | 2001-09-06 | 2002-11-28 | Brueckner Maschbau | Arrangement for operating a contact roller |
| EP1444155B1 (en) * | 2001-10-24 | 2007-02-14 | Windmöller & Hölscher KG | Device for pressing one moving machine piece against another |
| FI118234B (en) | 2005-05-20 | 2007-08-31 | Metso Paper Inc | Actuator for linear movement |
| FI123116B (en) | 2006-03-28 | 2012-11-15 | Metso Paper Inc | The control valve |
| FI118961B (en) * | 2006-04-06 | 2008-05-30 | Metso Paper Inc | A method of damping vibrations by scrollers |
| FI122166B (en) * | 2008-06-17 | 2011-09-30 | Metso Paper Inc | Method and arrangement for controlling vibrations |
| FI122033B (en) * | 2008-06-18 | 2011-07-29 | Metso Paper Inc | Rolling arrangement and roller cutting machine in a fiber web machine |
| KR100864306B1 (en) | 2008-07-15 | 2008-10-20 | (주)로이포스 | Tape rewinding machine |
| JP4658184B2 (en) * | 2008-12-10 | 2011-03-23 | 株式会社日本製鋼所 | Vibration suppression device |
| DE102010023921A1 (en) * | 2010-06-16 | 2011-12-22 | Kampf Schneid- Und Wickeltechnik Gmbh & Co. Kg | Winding machine for the production of winding rolls of material webs |
| EP2730709B1 (en) * | 2012-11-13 | 2019-02-27 | Wölfel Beratende Ingenieure GmbH & Co. KG | Vibration absorber assembly |
| EP2813451B1 (en) * | 2013-06-11 | 2017-03-29 | Valmet Technologies, Inc. | A two-drum winder |
| DE102013222896A1 (en) * | 2013-11-11 | 2015-05-13 | Koenig & Bauer Aktiengesellschaft | Device for winding a material web into a multi-layered roll |
| WO2020239589A1 (en) * | 2019-05-24 | 2020-12-03 | Primetals Technologies Austria GmbH | Industrial installation having a damping system for damping vibrations |
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| US2819775A (en) * | 1953-07-31 | 1958-01-14 | Wilhelm S Everett | Vibration absorber |
| DE1921773U (en) * | 1959-09-28 | 1965-08-19 | Hoesch Ag | HYDRO-DYNAMIC SHOCK ABSORBER. |
| DE1302513C2 (en) * | 1965-02-01 | 1977-09-22 | Pagendarm, Erich, 2000 Hamburg | WINDING DEVICE FOR RAIL-SHAPED MATERIAL WITH AT LEAST ONE DRIVE ROLLER ATTACKING THE CIRCUMFERENCE OF THE WINDING |
| US3334834A (en) * | 1965-05-14 | 1967-08-08 | Curtis Marble Machine Co | Rolling head |
| DE1560065A1 (en) * | 1966-08-05 | 1971-09-23 | Hobbs Manufacturing Co | Device for controlling the winding density of the goods to be pulled off by means of a winding device |
| US3602448A (en) * | 1970-02-03 | 1971-08-31 | Alcan Res & Dev | Web-winding apparatus |
| US3917246A (en) * | 1974-04-15 | 1975-11-04 | Joseph R Gartner | Tunable vibration absorber |
| DE2613453A1 (en) * | 1976-03-30 | 1977-10-13 | Bernhard Bruene | Coiling machine for metal foil - is designed to eliminate vibrational stresses causing deformation of the foil |
| DE3011385A1 (en) * | 1980-03-25 | 1981-10-01 | Hauni-Werke Körber & Co KG, 2050 Hamburg | SUPPORT ROLLER ROLLING DEVICE FOR ENDLESS MATERIAL SHEETS |
| DE3347733A1 (en) * | 1983-12-31 | 1985-11-07 | Lenze GmbH & Co KG Aerzen, 3258 Aerzen | Contact roller control system for a winding device |
| DE3836367C1 (en) * | 1988-10-26 | 1989-12-14 | J.M. Voith Gmbh, 7920 Heidenheim, De | |
| DE4103799A1 (en) * | 1991-02-08 | 1992-08-13 | Kuesters Eduard Maschf | DEVICE FOR REWINDING A PLASTIC FILM SHEET |
| DE4201327A1 (en) * | 1992-01-20 | 1993-07-22 | Feldmuehle Ag Stora | Winding device for film foil or paper webs with rough surface - has pressure cylinder connected to buffer filled with pressurised gas, gas chamber being separated from hydraulic chamber by membrane |
| DE4201326A1 (en) * | 1992-01-20 | 1993-07-22 | Feldmuehle Ag Stora | Winding machine for winding up paper webs - has brake element connected to bearing blocks and engaging fixed brake comprised of plates which press against brake element |
| JP3442811B2 (en) * | 1993-03-17 | 2003-09-02 | 三菱重工業株式会社 | Press roll control method and device for winding machine |
-
1996
- 1996-07-19 DE DE1996129205 patent/DE19629205A1/en not_active Withdrawn
-
1997
- 1997-06-21 EP EP97110173A patent/EP0819638A3/en not_active Withdrawn
- 1997-07-18 ID IDP972500A patent/ID18654A/en unknown
- 1997-07-18 JP JP9193896A patent/JPH1077143A/en active Pending
- 1997-07-18 CA CA 2210935 patent/CA2210935A1/en not_active Abandoned
- 1997-07-19 KR KR1019970033885A patent/KR980010014A/en not_active Application Discontinuation
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6186437B1 (en) | 1998-05-07 | 2001-02-13 | Valmet Corporation | Method and device for applying a load to a reel in a reel-up of a paper web |
| US8372245B2 (en) | 2009-03-18 | 2013-02-12 | Metso Paper, Inc. | Roll assembly for a fiber-web machine and method of attenuating vibration of a fiber-web machine roll |
| CN102191714A (en) * | 2010-03-09 | 2011-09-21 | 美卓造纸机械公司 | Device and method for regulating force in gap between two rolls |
| CN112938577A (en) * | 2021-03-12 | 2021-06-11 | 郑州财经学院 | Drawing paper winding device for art design |
| CN112938577B (en) * | 2021-03-12 | 2022-08-16 | 郑州财经学院 | Drawing paper winding device for art design |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0819638A2 (en) | 1998-01-21 |
| JPH1077143A (en) | 1998-03-24 |
| KR980010014A (en) | 1998-04-30 |
| ID18654A (en) | 1998-04-30 |
| EP0819638A3 (en) | 1998-09-09 |
| DE19629205A1 (en) | 1998-01-22 |
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