EP1260470B1 - Method and device for active dampening of vibrations in winding machines - Google Patents

Abstract

The winding machine includes two or more rolling cylinders (a,b,c,d) which together form a vibrating system through an imbalance or out-of-roundness. At least one of the cylinders experiences an active damping in relation to the vibration forces so that a number of vibration force measurements are taken per revolution of one of the cylinders. The rotary axis of at least one cylinder is then shifted by extra energy supplied from outside depending on the actual measured value so that the vibration forces are reduced. Independent claim describes device where a cylinder is fitted at the ends with movable bearings (6,7,8) associated with measured value recorders (9,10).

Description

The invention relates to a method for damping vibrations during the winding of material webs - in particular paper and Kartonbahnen- according to the preamble of claim 1, and a winding machine according to the preamble of claim. 8

Such a method and such a device is known from DE 76 09 748 U1. Here, the out-of-roundness of the winding roll is determined with the help of an optical pickup. Depending on the out-of-roundness, the axis of rotation of a pressure roller is then displaced. This shift takes place with a phase shift of 360 ° to the occurrence of out-of-roundness, because an out-of-roundness that has once occurred will again appear in the same position during the next revolution.

US 5 961 899 A shows a calender with several rolls arranged one above the other. The lower roller is stationary. The rollers above are mounted on levers. At the bearings of the two lower rollers error sensors are arranged. Between the lower roller bearing and the bearing above Roller is arranged another error sensor. There are also speed sensors that detect the speed of the two lower rollers. When an error occurs, power generators are powered by an external power source. They are to introduce forces into the respective bearings, which are opposite to the vibration forces.

Winding machines are known in many different constructions and serve to wind a web to winding rolls. In the production of paper or board webs takes place the winding of the finished, several meters wide, web either at the end of the paper machine or at the end of a downstream coater. Such winding machines are known, for example, from the documents DE 40 07 329 A1 and EP 0 792 829 A2. The winding machine from the document DE 40 07 329 A1 corresponds to the design of the so-called Pope-Rollers. In EP 0 792 829 A2 another type of Pope roller is shown in which during winding the winding axis remains stationary, but the pressure roller is moved horizontally in response to the growing winding.

In order to produce narrower bobbins with higher winding quality, the web is divided by several longitudinal cuts in single tracks, which are wound on sleeves, which are usually made of cardboard.

This winding on sleeves is done either on so-called support roll winding machines or on so-called backup roll winding machines. From document WO 93/25461 a carrier roll winding machine is known, in which the webs is wound in an upper gusset between the two support rollers. In the outer ends of the outer sleeves guide heads engage in order to an axial

Move the bobbins in the winding bed to prevent. The document WO 93/15988 discloses a winding machine which has only one roller. This winding machine is called a backup roll winding machine. In the upper region of this support roller, the winding rollers are - with respect to the apex line of the support roller - alternately offset to each other. For holding the winding rollers on the support roller engage in the sleeves of the winding roll on both sides guide heads, which are connected to reduce the weight of the winding rollers on the support roller with piston-cylinder units.

In another prior art, the document DE 32 43 994 A1, a carrier roll winding machine is described, in which a total of three support rollers are present parallel to the axis side by side. This results in a total of two winding beds, in which the winding rollers are arranged alternately.

These mentioned winding machines have in common that always at least one roller and at least one winding roll together form a pressure line. Some of these winding machines also have an additional pressure roller, which provides the winding rollers from above with an additional contact pressure. Also, the said winding machines is common that it may, for example, by imbalance of the rollers and, above all, by the winding rollers to vibrate. The vibrations due to imbalance are synchronous with the rotational frequencies of the rollers or the winding rollers. Fluctuations - for example in the thickness - of the material to be wound up, however, lead to circumferential bumps in the surface of the wound rolls. As a result, additional vibrations are triggered, which can lead to the winding roll out of the winding bed in the case of support rollers winding machines in extreme cases.

In the document DE 196 29 205 A1 a method and an apparatus for winding a paper web to a winding roll with vibration damping is described. There, a Pope scooter with the help of tuned spring mass systems - in conjunction with absorbers (= shock absorbers) - built in parallel and / or series connection, to an oscillating in opposite phase system. This system is either still with a vibratory or with an infinitely large additional mass, for example in the form of a wall - realized. It takes place while the Detecting the horizontal vibration components by means of motion sensors to tune the system, but by this vote, the system can oscillate only in a typical fundamental frequency (which essentially corresponds to the rotational frequency of the winding roll) and in the integer multiples of the fundamental frequency. A direct reaction to instantaneous, non-periodic unevenness of the winding roll - that is, to frequency components smaller than the rotational frequency - is not possible.

It is therefore an object of the invention to provide a method and a winding machine with which can reduce or even avoid vibrations during winding.

The object is solved by the characterizing features of claims 1 and 8. Advantageous embodiments emerge from the subclaims and the description of the figures.

According to the invention occurring vibration forces (= dynamic forces) of at least one roller or a winding roll with a high sampling rate (sampling rate = number of measurements per second) are measured, and then by an immediate displacement of the axis of rotation of the vibrating body to reduce the vibrational forces.

Shifting the axis of rotation looks at a "belly" of the winding roll - in its otherwise circular shape - in such a way that the axes of rotation of the roll and the winding roll for a short time at a greater distance from each other for the duration of the "belly". In a "dent" in the winding roll is correspondingly a reduction of the distance of the axes of rotation. In the context of the invention, the axis of rotation of the winding roll or the roller or can be displaced simultaneously both axes of rotation.

The vibration damping according to the invention can also be described as follows: Depending on a roller and a winding roll roll with their lateral surfaces from each other so that the cylindrical circumference of the roller follows the quasi-cylindrical surface of the winding roll. Would a roller by means of short-term increase of force deliberately pressed against a "bump", so would by elasticities of the winding roll and possibly also the roll cover, the winding roll from the "bump" are accelerated away. This would create vibrations.

However, if a winding roll is circular and also concentric, but its center of gravity is not on its axis of rotation, then it comes to imbalance that would stimulate the winding roll and the winding machine to vibrate. Now approaches the winding of the center of gravity of the winding roll, an imaginary line connecting its axis of rotation and the nip line with the roller, the roller experiences higher bearing forces. By elasticities of the winding roll and possibly also of the roll lining, the eccentricity and thus the imbalance would increase even more. Therefore, then a counterpressing of the roller against the eccentricity is required, which is associated with an approximation of the roll rotation axis to the axis of rotation of the winding roll. This can also be called displacement of the roller rotation axis.

It may also happen that imbalance and / or irregularities of a winding roll have different effects on the roll ends of a movable roller. Therefore, a roller must not necessarily be moved axially parallel, but it can be individually reacted to the bearings with the axis displacement.

For the displacement of the axes of rotation, an additional energy is used, which is independent of a current energy state of the oscillating system (winding roll and carrier roll or pressure roller). As a result, the additional energy does not cause the vibrating system to vibrate. If the additional energy is supplied, for example, by a high-performance hydraulic pump and this hydraulic pump is additionally driven only in its lower power range, so also in the upper part of the pump characteristic declining performance, not the vibration system excite. The type of vibration damping according to the invention is an active vibration damping.

The momentary vibration forces are proportional to the momentary vibration accelerations. In the invention, therefore, not only the vibration forces for the evaluation of the vibration can be measured, but also the acceleration itself or the related physical quantities such as displacement and speed. By suitable differentiation and / or arithmetic either the forces can be determined or one uses the abovementioned physical quantities also without further processing for the control process of the active vibration damping.

The active vibration damping is already known from the automotive industry, where then the noise inside the vehicle are measured at a very high sampling rate, then then by means of a targeted control of speakers, which then - in contrast to the invention vibration damping oscillate in antiphase and thus a sound cancellation to effect. In vehicle construction, however, the required energies for active damping, in relation to the winding technique, only make up a tiny fraction of the total. This becomes all the clearer when you realize that according to the current state of the art, a finished winding roll on the Pope scooter can weigh over 100 tons.

Figur 1

eine Tragwalzen-Wickelmaschine mit aktiver Schwingungsdämpfung für eine Tragwalze mit vertikaler Ausrichtung der Schwingungsdämpfung;

Figur 2

eine Tragwalzen-Wickelmaschine mit aktiver Schwingungsdämpfung für beide Tragwalzen mit zentrischer Ausrichtung der Schwingungsdämpfung;

Figur 3

eine Tragwalzen-Wickelmaschine mit aktiver Schwingungsdämpfung für beide Tragwalzen mit waagerechter Ausrichtung der Schwingungsdämpfung;

Figur 4

eine Tragwalzen-Wickelmaschine mit drei Walzen und mit aktiver Schwingungsdämpfung für zwei Tragwalzen mit waagerechter Ausrichtung der Schwingungsdämpfung;

Figur 5

eine Stützwalzen-Wickelmaschine mit nur einer Walze und mit aktiver Schwingungsdämpfung für die Wickelrolle mit zentrischer Ausrichtung der Schwingungsdämpfung.

The invention will now be explained in more detail with reference to the simplified drawings. Show it:

FIG. 1

an active vibration damping type winding roll winding machine for a vertical vibration damping type supporting roll;

FIG. 2

a carrier roll winding machine with active vibration damping for both carrier rolls with centric alignment of the vibration damping;

FIG. 3

a carrier roll winding machine with active vibration damping for both support rollers with horizontal alignment of the vibration damping;

FIG. 4

a carrier roll winding machine with three rollers and with active vibration damping for two carrier rolls with horizontal alignment of the vibration damping;

FIG. 5

a backup roll winding machine with only one roller and with active vibration damping for the winding roll with centric alignment of the vibration damping.

FIG. 1 shows a carrier roll winding machine with two rolls a, b. On the rollers a, b (= body) rests the winding roll c (= body). Since according to the invention winding roll and / or roller can experience an active vibration damping and because of the avoidance of or-formulations in the characterizing part of the main claims and in the dependent claims, reference is made here to the correspondence to the term "body". A material web 16 partially wraps around the roller a and is wound on a sleeve 15 by the direction of rotation of the rollers a, b. A pressure roller d may optionally be present. The roller b has two bearings 7 (due to the side view in FIG. 1, only one bearing can be represented). On at least one of the bearings 7, a transducer 9 is arranged. This transducer 9 is not affected by forces, since it is not in the power flow between the winding roll c and an abutment 18. However, if the transducer 9 is an accelerometer, it is capable of registering oscillations of the bearing 7. The bearing 7 is held by means of a strut 17 and an abutment 19 substantially in its horizontal position. Between the bearing 7 and the abutment 18, an actuator 11, preferably in the form of a hydraulic cylinder, is arranged. Connecting lines of the hydraulic cylinder have been omitted here for clarity. Alternatively, as actuators 11 and linear motors can be used. Now provides the transducer 9 a signal on a "bump" in the winding roll c, so an evaluation, not shown, in response to the signal of the transducer 9, cause a vertical travel for the bearing 7. Through the travel, there is an axis-parallel displacement of the axis of rotation 2 of the roller b.

In a carrier roll winding machine in which a winding roll has two rolls in contact simultaneously, the vibration damping is particularly difficult because not only the vibrations on a nip (roller and winding roll) occur, but at the same time provides a second nip for vibrations. Therefore, there are interactions between the three bodies (rolls a, b, and roll c). By means of a suitable calculation model, the necessary axis-parallel movements of the roller b are calculated from the bearing forces. In this way, especially the problems of interactions are to be solved as far as possible.

In the carrier roll winding machine of Figure 1, only the roller b is actively damped vibration. As a result, vibrational forces, which are produced by the unwinding of the winding roller c on the support roller a or by the unwinding of the pressure roller d, still remain. Therefore, in a further development of the invention, which can be seen in Figure 2, and the support roller a is actively damped vibration. In addition, the actuators 11, 12 directed substantially to the center of the winding roll c and the transducers 9, 10 are arranged between the bearings 6, 7 and the actuators 11, 12. Furthermore, the bearings 6, 7 slide in guides 13, 14. As a result, struts 17 and abutment 19 as in Figure 1 are not required. Due to the substantially centric alignment of the actuators 11, 12 there are only minor forces on the guide surfaces of the guides 13, 14. This means that a design effort for the capture of vertical and horizontal force components is only minor nature.

Because a total of two rollers are now displaceable in FIG. 2 (that is, they can be displaced axially parallel with their axes of rotation) and each axle finally has two bearings, a complex vibration system is created since there are many interactions between the bodies a, b, c, d involved , To take account of these circumstances, it is recommended that the measurement signals are processed in a computer program. Today's computer performance enables real-time data processing of more than 100 Hz sampling rate.

With the figure 3 is to illustrate a further arrangement of the actuators 11, 12 in a carrier roll winding machine. Here, the actuators 11, 12 are aligned horizontally. The guides 13, 14 must be formed on one side only supporting because of the weight of the winding roll c. Now, if the actuators 11, 12 are aligned horizontally, it can be sensitively responded because the horizontal component allows for a large travel small vertical components.

Because in a carrier roll winding machine only the outer ends of the sleeves 15 of the outer winding roll c are accessible to guide heads, there are only here leadership heads. Therefore, in this winding machine type no force acting on the winding roller c, but the actuator can always attack only one of the support rollers.

With the figure 4, a three-roll winding machine is now shown. Here, the winding rollers c are arranged alternately to the apex line of the roller d and perpendicular to the plane of the drawing offset from one another. As a result, can engage on both sides of each winding roller c in the sleeves 15 guide heads. Again, the principle of horizontal alignment of the actuators 11, 12 has been realized. The roller d learns in this embodiment, no active vibration damping.

Because the individual winding rollers c can be provided with guide heads in FIG. 4, alternatively or additionally an active vibration damping could act on each individual winding roller.

The engagement of guide heads in the winding rollers c - in conjunction with the active vibration damping according to the invention is shown in FIG. The dashed double circles on the roller d show the sleeves 15 in position during the winding start. On a roller d, the winding rollers c are arranged alternately to their apex line and perpendicular to the plane of the drawing. Therefore, the ends of the sleeves 15 of each winding roller c are accessible to guide heads. Depending on the desired winding hardness, the winding rollers c are lifted by actuators so that not the full weight of the winding roll c comes to fruition. As a result, the contact pressure of the winding roll c on the roll d can be made smaller than the normal force of the winding roll own weight. In the winding machine type shown here, the mechanism for lifting the winding roll c is now combined with the active vibration damping. It is understood that here by means of the guide heads but also an additional contact pressure could be realized.

If, in the described solutions, either only the axis of rotation of a roll or only that of a winding roll is displaced, reaction forces are produced on the machine frame and on the foundations. However, if the axes of the roller and the winding roller are displaced simultaneously in the context of the active vibration damping and the respective displacement paths of the axes of rotation are chosen inversely proportional to the masses of the corresponding body, then no forces are applied to the foundations after the momentum set. If the impacts of the winding roll on a roll are inelastic or partially elastic, then the corresponding modifications of the pulse set apply.

Finally, it should be emphasized that the active vibration damping can be used not only in support or backup roll winding machines, ie for longitudinally divided webs 16, but also for the Pope scooter and its advancements. Here then can act both on the bearings of the pressure roller, as well as on the bearings of the winding axis active vibration damping. Furthermore, the present invention can also be applied to wrapping machines and also to uncoiling stations for coating machines.

Claims (12)

1. Method for damping vibrations in winders for material webs, in particular of paper and paperboard, having the following features:

   - at least two cylindrical bodies (a, b, c, d) which roll on one another form a nip with one another,

   - one of the bodies (a, b, c, d) is a wound reel and the other body (a, b, c, d) is a roll which bears against it,

   - the two bodies (a, b, c, d) form an oscillating system as a result of unbalance or non-roundness,

   characterized in that

   - at least one of the bodies (a, b, c, d) of the vibration system is subjected to active damping with regard to the oscillating forces,

   - that is to say, a multiplicity of vibration force measurements are carried out per revolution of one of the bodies (a, b, c, d),

   - the rotational axis (1, 2, 3, 4, 5) of at least one body (a, b, c, d) is displaced as a function of the actual measured value in such a way that the vibration forces are reduced,

   - the rotational axis (1, 2, 3, 4, 5) is displaced by means of additional energy which is supplied to the system from outside.
2. Method according to Claim 1, characterized in that at least four measured values are obtained per revolution of one of the bodies (a, b, c, d).
3. Method according to either of Claims 1 and 2, characterized in that the displacement of the rotational axis (1, 2, 3, 4, 5) which results from the last measured value is concluded before a new measured value is obtained, by way of which there is therefore real-time data processing.
4. Method according to one of Claims 1 to 3, characterized in that the measured values are processed in a computational program.
5. Method according to Claim 4, characterized in that the computational program contains an algorithm which registers the temporal profile of the measured values as a function of the unwinding of the body, the algorithm detecting the next revolution of the rotating body as a result of the sequence of the measured values and, as a result, arriving more quickly in its data processing to the values for the displacement for the rotational axis.
6. Method according to Claim 5, characterized in that the algorithm is capable of learning with regard to the parameters of the oscillating system and is therefore self-adapting.
7. Method according to one of Claims 1 to 6, characterized in that the number of measured values is smaller at the beginning of winding and is raised as the diameter of the wound reel increases.
8. Apparatus for carrying out the method according to one of Claims 1 to 7, by means of a winder having at least two bodies (a, b, c, d), one of the bodies (a, b, c, d) being a roll and the other body (a, b, c, d) being a wound reel, and at least one body (a, b, c, d) being equipped at the ends of its rotational axis (1, 2, 3, 4, 5) with displaceable bearings (6, 7, 8), on which additional energy acts in the form of actuating elements (11, 12), characterized in that these bearings (6, 7, 8) are assigned vibration-force measured-value sensors (9, 10) and the actuating elements (11, 12) displace the bearings as a function of the signal of the vibration-force measured-value sensors (9, 10) in such a way that vibration forces are reduced.
9. Apparatus according to Claim 8, characterized in that the actuating element (11, 12) comprises a hydraulic cylinder.
10. Apparatus according to either of Claims 8 and 9, characterized in that the additional energy is oriented vertically.
11. Apparatus according to either of Claims 8 and 9, characterized in that the additional energy is oriented horizontally.
12. Apparatus according to either of Claims 8 and 9, characterized in that the additional energy is oriented in the direction of the rotational axis (1, 2, 3, 4, 5) of the associated body (a, b, c, d).

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