EP1789353B2 - Methods for carrying out a flying reel change - Google Patents

Abstract

The invention relates to methods for carrying out a flying reel change. According to said methods, a first web (02) of a reel to be replaced (06) is joined to a second web of a new reel (07), the reel to be replaced (06) running at a first web speed. The first web (02) is joined to the second web at the latest once the remainder of the reel has reached a minimum diameter. Before the first web is joined to the second web, the minimum diameter of the remainder of the reel is fixed according to the characteristics of a sleeve therefor.

Description

The invention relates to methods for carrying out a flying reel change according to the features of claim 1.

Such roll changers are used on printing machines and serve to supply the material web used as printing material. As a rule, paper webs are used. The material web is wound on a roll of material and runs from this roll of material.

So that when exhausting a roll of material not the entire printing press must be stopped, it is known to perform a so-called flying reel change. For this purpose, a new roll of material is clamped in the roll changer, where, for example, appropriate splices are prepared for connection to the running roll of material. During the flying roll change, the new roll of material is then accelerated to a peripheral speed which corresponds to the web speed of the drawn-in material web. In the actual web change of the web start of the new roll of material is connected to the expiring web and cut substantially simultaneously the running web. The web start of the new material web is drawn in this way from the old web into the press and a machine downtime is avoided.

Depending on the residual thickness of the running material roll and the geometry parameters of the running material roll, in particular its width and the tube diameter, the running material roll has a constantly changing intrinsic resonance speed.

Particularly with relatively large web widths, for example web widths> 3,600 mm, and very high web take-off speeds, for example web take-off speeds of 15 m / s, critical vibration states at the outgoing material roll can occur when a certain residual thickness is undershot due to vibration excitations in the region of the intrinsically critical resonance speed. To avoid these critical vibration states, it is therefore often necessary that the web speed must be shut down when falling below a certain residual thickness of the roll of material. In such applications, this means that either the roll of material can not be completely consumed in order to avoid critical vibration conditions or the web take-off speed must be reduced during the roll change. Both measures increase the printing costs in an undesirable manner.

The FR 2 076 474 shows a single recording for rolls of material, with two jaw rows are arranged one behind the other.

The DE 36 27 533 A1 describes a roller carrier in which a worn-out role a support device is employed.

The DE 100 56 274 A1 discloses a mandrel with two successively arranged rows of clamping troughs, wherein the diameter of a row of 150 to 160 mm and the diameter of the other row of 70 to 80 mm is variable.

By the EP 0 441 152 A , the EP 0 708 047 A and the EP 0 413 890 A are devices for unwinding rollers known, each having trunnions with movable jaws.

The US Pat. No. 3,891,158 A , the US 5,360,502 , the US 5,316,230 , the US 3,836,089 and the US 4 100 012 describe processes for roll change.

The US 3 516 617 A and the US 4 173 314 A describe methods for flying reel change, in which the reel change is performed at a determined for a reel diameter residual roll size.

From the article "Hard Paper Sleeves in Paper Rolls in Gravure" Publisher: Bundesverband Druck e.V., Biebricher Allee 79, 6200-Wiesbaden 1, article no. 86616, authors: Dr.-Ing. Manfred König and Dipl. Ing. Dirk Müller, year of publication: 1988, it is known to calculate a critical oscillation frequency as a function of a free oscillation length, outer diameter and inner diameter of a sleeve as well as density and modulus of elasticity of the sleeve material.

The invention has for its object to provide methods for performing a flying role change:

The object is achieved by the features of claim 1.

The invention is based on the idea to reduce the free vibration length of the running material roll, thereby affecting the intrinsic critical resonance speed of the running material roll in the desired manner.

When using the reel changer, the reduction of the free oscillation length between the chucking points of the outgoing material roll on the reel changer occurs in that a support device is provided which comes into contact with the peripheral surface of the outgoing material roll. This additional support of the roll of material between the clamping points, the free vibration length can be significantly reduced. If the support device is brought into abutment, for example, exactly in the middle between the clamping points on the peripheral surface of the outgoing roll of material, the free oscillation length is halved in this way and the intrinsically critical Resonanzdrehzähl moved accordingly upward.

The support device is arranged such that it can come into contact with the arrangement of the outgoing roll of material in the position provided for the flying roll change position on the peripheral surface of the running roll of material. Because the critical vibration states of the running material roll occur in particular shortly before the exhaustion of the roll of material at a relatively low residual thickness, so that in particular in the phase immediately preceding the roll change, a support of the outgoing roll is necessary.

In which type the support device is designed constructively, is basically arbitrary, as long as sufficient support of the running material roll to reduce the free length of vibration is guaranteed. According to a preferred embodiment the support device has at least one circumferentially mounted support belt which can be pressed against the circumferential surface of the running material roll. This support belt can for example be stored on rollers, and runs at a speed corresponding to the peripheral speed of the running material roll.

Depending on the application, it may be useful to greatly reduce the free oscillation length. This can be achieved in that a plurality of support means are provided, which come to rest adjacent to each other on the peripheral surface of the running roll of material to the plant. The free oscillation length only corresponds to the respective distance between two adjacent support devices or the distance between the first support device and the last support device to the clamping points of the running material roll. As a result, thus the free vibration length of the running material roll can be influenced in any way.

The support device can be implemented particularly simply if it does not have its own drive device. In this case, the support means can be driven by transmission of frictional forces from the running roll of material itself. As far as frictional forces are used to drive the support means, the support means should preferably be made of a wear-resistant material with a relatively high coefficient of friction in the region of the contact surface with the roll of material.

Alternatively, it is also conceivable that a drive device is provided on the support device, with which the support device is driven. For example, an electric motor may be provided for this purpose, with which one of the bearing rollers is driven for supporting the support belt. By appropriate control of the drive device, it is possible that this is accelerated before being brought into contact with the roll of material to a speed which is synchronized with the peripheral speed of the running material roll. In this case, it can be avoided that there is an undesirable slippage between support means and peripheral surface of the running roll of material or to web breaks in Gurtanstellung to the roll of material.

In many cases, the use of the support device is desired only in certain phases of the operation of the reel changer, in particular in the phase immediately before the flying reel change. For this reason, it is particularly advantageous if the support device is movably mounted between at least two functional positions. The first functional position corresponds to the actual insertion position in which the support device comes to rest on the circumferential surface of the running material roll and supports the roll of material accordingly. The second functional position corresponds to a rest position in which the support device is not engaged with the running material roll.

The manner in which the support device is fastened relative to the roll changer is fundamentally arbitrary. According to a first embodiment, the support means is attached to the roll stand of the roll changer. This has the advantage that the support device is moved during pivoting of the roll stand and thus no relative movement between the support means and the correspondingly associated roll of material occurs during pivoting of the roll stand. In particular, it is possible in this embodiment that the support device is brought even before the arrangement of the running roll of material in the intended position for flying role change position on the running roll of material to the plant, so that the outgoing roll of material supported even during the pivoting of the roll stand of the support means is, preferably even before the roll of material from standstill is accelerated. The employment takes place simultaneously with the support belt.

To realize this embodiment, the support means between two support arms of the roll stand can be attached, wherein the support arms also carry the corresponding associated roll of material.

As an alternative to this first embodiment, the support device may also be fastened to a foundation below the position of the outgoing material roll intended for the flying roll change, so that the support device as a result is not an integral part of the roll changer. This embodiment is particularly advantageous if the support means can be sunk in the foundation, so that the support means in its rest position, in which the support means is sunk in the foundation, no obstruction.

In order to be able to control or regulate the supporting process of the running material roll by use of the supporting device, at least one sensor for measuring a supporting parameter, for example the currently applied supporting force or the belt tension of the supporting belt, can be provided on the supporting device. The respectively provided control device or the correspondingly used control loop can process the measurement results and control or regulate the support device to a predetermined desired value.

The use of the support device in reelstands, in which material rolls with a width of greater than or equal to 3,600 mm are processed, offers particularly great advantages. In particular, in the case of gravure printing with rotogravure printing presses, such broad printing material webs are used, the high printing speeds in gravure printing leading to the problems mentioned with intrinsically critical resonance speeds.

After the method for operating the new reel changer, the support device is already before the arrangement of the running material roll in the position suitable for flying reel change on the running material roll brought to the plant. During pivoting of the roll stand for the arrangement of the running roll of material in the position suitable for flying roll change position, the support device remains in engagement with the running roll of material and ensures that the running roll of material is also supported during the pivoting operation. As soon as the roll stand has reached the end position in which the running material roll assumes the position suitable for flying roll change, the support device remains in engagement with the running roll of material until the flying roll change has ended and the old roll of material can be braked accordingly.

As an alternative to reducing the free oscillation length or preferably in combination, a support device may be provided. The avoidance of intrinsically critical resonance speeds can also be improved by reducing the free oscillation length of the outgoing material web by using longer mandrels.

So that the longer mandrels in the contact surface to the inner circumference of the sleeve of the running roll of material apply a sufficient clamping force, it is proposed that at least two clamping jaws are arranged one behind the other on the mandrel parallel to the longitudinal axis of the support pin. By increasing the number of clamping jaws a higher clamping force can be applied, so that in addition to the reduction of the clamping length and the quality of the clamping by increasing the Einspannsteifigkeit (increasing the chuck factor) is achieved.

Paper widths of more than 4,000 mm, in particular of 4,300 mm and sleeves / quills with a diameter of 150 mm without a central support no reliable role change at material web speeds greater than 15 m / s with currently customary in the industry sleeves. Here, without support with long sleeves, material web speeds of max. 12 m / s can be achieved.

Preferably, several clamping jaws adjacent to each other in a clamping jaw row, in particular evenly spaced from each other, distributed over the circumference of the trunnion. According to a preferred embodiment, two clamping jaw rows arranged in the axial direction, each with eight clamping jaws, are arranged in the circumferential direction on the clamping mandrel, which leads to a high-strength clamping of the material roll on the clamping mandrel.

Embodiments of the invention are illustrated in the drawings and will be described in more detail below.

Fig. 1

ein erstes Ausführungsbeispiel eines Rollenwechslers mit Stützeinrichtung in seitlicher Ansicht;

Fig. 2

ein zweites Ausführungsbeispiel eines Rollenwechslers mit Stützeinrichtung in seitlicher Ansicht;

Fig. 3

einen Spanndorn in perspektivischer Ansicht;

Fig. 4

ein Tragzapfen im Querschnitt;

Fig. 5

einen Querschnitt durch eine Materialrolle mit Aufnahmen;

Fig. 6

eine schematische Ansicht eines Scherenhubtisches mit einer neuen Materialrolle;

Fig. 7

eine schematische Ansicht eines Scherenhubtisches mit einer Stützeinrichtung an einer ablaufenden Materialrolle;

Fig. 8

eine schematische Ansicht des Rollenwechslers.

Show it:

Fig. 1

a first embodiment of a roll changer with support means in a side view;

Fig. 2

a second embodiment of a roll changer with support means in a side view;

Fig. 3

a mandrel in perspective view;

Fig. 4

a trunnion in cross section;

Fig. 5

a cross section through a roll of material with recordings;

Fig. 6

a schematic view of a scissor lift with a new roll of material;

Fig. 7

a schematic view of a scissor lift with a support means on a running roll of material;

Fig. 8

a schematic view of the roll changer.

In Fig. 1 is a first embodiment of a roll exchanger 01 for feeding a web of material 02, in particular a paper web, shown schematically in a printing press, not shown. On reel changer 01 a pivotable about a pivot axis 03 roll stand 04 is provided, which is formed by two in the image plane behind one another supporting arms. At the free ends of the roll stand 04, in each case opposite receptacles 05, for example clamping mandrels 05 are fastened, between which material rolls 06; 07 can be clamped on the roll changer 01.

On reel changer 01, in the process state shown, an outgoing material roll 06 and a new material roll 07 prepared for the flying reel change are clamped. The roll stand 04 was previously in the in Fig. 1 shown pivoted position, so that the running material roll 06 occupies the required position for the flying role change. To support the new roll of material 07 and to transfer the driving forces (acceleration + brake stop) in the loading position, a support belt 08 is pressed from below against the circumference of the new roll of material 07.

Once the roll stand 04 in preparation for a flying roll change the in Fig. 1 has moved to the position shown mounted on the foundation 09 below the outgoing roll of material 06 support device 11 is extended upward until a supported on rollers 13 support belt 12 comes to rest on the circumference of the running roll of material 06 to the plant. For extending the support means 11 pneumatic actuating cylinder 14 are provided. The support belt 12 is synchronized by a frequency-controlled three-phase motor, not shown, to paper web speed. This web breaks are avoided when hiring.

Due to the pressure of the support belt 12 on the circumference of the running material roll 06, the free oscillation length of the roll of material 06 is shortened between the receptacles 05, so that the intrinsic critical resonance speed of the roll of material 06 is shifted to a non-critical speed range.

In Fig. 2 a second embodiment of a roll changer 16 is shown. On the reel changer 16, in turn, the material web 02, the pivot axis 03, the roll stand 04, the receptacles 05, the expiring roll of material 06, the new roll of material 07 and a support belt 08 are provided for supporting and transmitting the driving forces of the new roll of material 07.

In contrast to the reel changer 01, two support devices 17 and 18 are provided on the reel changer 16, which are each assigned to the left or right clamping point on the reel stand 04. As indicated by the support means 17 by dashed lines, the support means 17 and 18 can be adjusted in linear guides 19 and in this way at the changing diameters of the material rolls 06; 07 adapted and tracked.

On the support means 17 and 18 each support straps 22 are provided, which at the periphery of the supported material roll 06; 07 can be brought to the plant. For turning on and off the support belts 22 pneumatic actuating cylinder 21 are provided by the retraction and extension of the bearing structure of the support straps 22 can be pivoted.

Before a flying reel change with the roll changer 16, the procedure is as follows. First, the running material roll 06 is still in the so-called flow position on the right side of the pivot axis 03 (not shown). In this position, the expiring roll of material 06 is unwound as the printing process progresses until a certain roll diameter, i. H. a certain residual thickness of the roll of material 06 has fallen below. After falling below this predetermined residual thickness of the actuating cylinder 21 is extended and thereby brought the support belt 22 on the circumference of the roll of material 06 to the plant. In this way, the intrinsic resonance speed of the roll of material 06 is shifted in a non-critical speed range, so that the material web 02 can be withdrawn at an unchanged speed.

Once the roll of material 06 is unwound to a residual thickness that makes a roll change inevitable, the roll of material 06 is pivoted by pivoting the roll stand 04 in the position to the left of the pivot axis 03, as in Fig. 2 is shown. Also during the pivoting movement of the support belt 22 abuts the periphery of the roll of material 06 and supports them in this way.

After the roll of material 06 in Fig. 2 shown adhesive position or loading position left of the pivot axis 03 has reached and prepared for roll change new roll of material 07 is stretched in the reel changer 16, the flying reel change between the roll of material 06 and the roll of material 07 can be performed in a known manner. A reduction of the take-off speed of the web of material 02 is not necessary since the critical resonance speed of the roll of material 06 is shifted by use of the support device 17 into an uncritical range.

Since the support means 17; 18 can already be employed in the new, still at a standstill roll of material 07 and so rests during acceleration, it can be designed without a drive motor.

Fig. 3 shows a receptacle 05, which comes for example as a mandrel 05 to the roll changers 01 and 16 are used. On the mandrel 05, a support pin 24 is provided, whose outer circumference on the inner circumference of a roll of material 06; 07, in particular on the inner circumference of a sleeve 10, z. B. a cardboard tube 10, comes to rest. For non-rotatable connection of the roll of material 06; 07 with the mandrels 05 by force and form fit a plurality of clamping jaws 26, in particular however at least four clamping jaws 26 are provided in the axial direction of the support pin 24 to the support pin 24. Since the support pins 24 have a large insertion depth with which the free oscillation length between the clamping points can be reduced, at least two clamping jaws 26 in the direction of the longitudinal axis of the support pin 24, ie in the axial direction of the support pin 24, arranged one behind the other, which are aligned. A plurality of mutually adjacent clamping jaws 26 are distributed over the circumference of the support pin 24, in particular evenly spaced. The juxtaposed clamping jaws 26 form annular clamping jaw rows 27 and 28, each with eight clamping jaws 26. The supporting pin 24 of the clamping mandrel 05 has an outer diameter D24 of about 150 mm.

In the Fig. 4 a trunnion 24 is shown in cross section. A length 124 of the trunnion 24 in the axial direction of the trunnion 24 is at least 250 mm. Also advantageous are lengths 124 of the trunnions 24 of at least 300 mm, in particular of at least 330 mm. A length 126 of the clamping jaws 26 is in the axial direction of the support pin 24 at least 80 mm, in particular at least 95 mm. A sum of the lengths 126 of the clamping jaws 26 in the axial direction of the supporting pin 24 is at least 300 mm, in particular 340 mm. In a further embodiment, the sum of the lengths 126 of the clamping jaws 26 is 380 mm. A diameter D24 of the trunnion 24 is greater than 140 mm, in particular it is between 145 mm and 155 mm. Particularly advantageous is a diameter D24 between 148 mm and 152 mm.

Fig. 5 shows a lying in the two receptacles 05 roll of material 06; 07 with a sleeve 10, as it is preferably used in the reel changer described.

In this case, a length 110 of the sleeve 10 of the roll of material 06; 07, which rests on the clamping jaws 26 of the support pin 24, more than 4000 mm, in particular more than 4200 mm. A wall thickness b10 of the sleeve 10 is more than 10 mm, in particular it is greater than 15 mm. In particular, a sleeve wall thickness b10 greater than 17 mm, in particular greater than 20 mm, is advantageous. An inner diameter d10 of the sleeve 10 is 150.2 + 0.2 mm.

Alternatively or in support of the measures for reducing the free clamping length of the roll of material, a determination of the web speed and / or the residual roll diameter during the flying reel change can also be carried out for carrying out the flying reel change.

As already described, when flying reel change a first material web of a changing material roll 06; 02, which runs at a first web speed, connected to a second material web 29 of a new roll of material 07, which runs at a second web speed. Before the first material web 02 is joined to the second material web 29, the first web speed can be reduced to a second web speed, so that during joining the first web 02 has the second web speed.

It is possible, before joining the webs 02; 29 a minimum diameter of the rest roller 06 as a function of a width b02 of the material web 02; Determine 29, which determines when the two webs 02; 29 at the latest be connected.

In another embodiment, the second, predetermined during bonding web speed or the minimum diameter of the residual role 06 depending on material properties of the sleeve 10 of a roll of material 06; 07 fixed.

Geometric dimensions, the sleeve 10 of the roll of material 06; 07 concern, z. B. Size of the inner diameter d10 of the sleeve 10 or the wall thickness b10 of the sleeve 10 or the modulus of elasticity determine in other embodiments, the reduced web speed or the minimum diameter of the remaining roll 06 of the first roll of material 02 during bonding.

The second, predetermined during bonding web speed or the minimum diameter of the residual role 06 is set in a further embodiment by the geometric dimension of the receptacle 10, in particular of the trunnion 24. Also, the reduced web speed depending on the length 126 of the clamping jaws 26 of the trunnion 26 can be set.

The reduction of the web speed and / or the determination of the minimum diameter of the residual roll 06 is controlled by a program together with the joining process.

The loading of the roller carrier 04 with the roll of material 06 by means of a sliding carriage 31, z. B. a scissor lift 31, as in the FIGS. 6 and 7 is shown. On the sliding carriage 31 wheels 33 are mounted, by which a horizontal movement of the sliding carriage 31 is possible. A movement in height is also possible. On the sliding carriage 31 is a support means 11 with a support belt 12 which is pivotally mounted on the scissor lift 31, arranged. This support device 11 is essentially the same, previously described support means 11. The support means 11 is motor-driven, z. B. by an AC motor, the support belt 12; 22 of the support device 11 accelerated to web speed and then applies by hydraulic to the expired roll of material 07. The braking of the roll of material 07 is also supported by this engine, since the motor of the support device 11 along with the axle motor of the roller stand 04 slows down the same torque curve until the residual role 07 comes to a standstill.

The roll of material 06 is transported by a chain-driven trolley 32 to the paster 01. There, the trolley 32 moves with the material roll 06 mounted thereon at the ground level into the sliding carriage 31. On the trolley 32 wheels 34 are mounted, with which a movement of the trolley is made possible within the Scherenhubtisches 31. The scissor lift table 31 moves into a centering position and raises the roll of material 06 to about 1600 mm above the floor. Subsequently, the centered roll of material 06 is brought into the Einachsposition of the roll stand 04. Upon reaching the Einachsposition the signal "quill before" to the roll stand 04. The receptacles 05 with the support pin 24 are moved into the roll of material 06. Are the receptacles 05 retracted with the trunnions 24 in the roll of material 06 and the jaws 26 spread, the scissor lift 31 is lowered and moved to the normal position with the signal "role einzeachst".

During the roll change, the support device 11 moves after the Rollenarmdrehung to the expiring roll of material 07 (support position) and stabilizes them in the middle. With the command "knife before" the running material web 29 is separated from the roll of material 07 and stopped via the axle motor of the roll stand 04. As already described above, the stopping operation of the material roll 07 is supported by the support device 11 of the scissor lift table 31. The support belt 12 pivots off, the scissor lift table 31 moves into its loading position to load a new roll of material 07.

Meanwhile, the sleeve 10 of the rest roller 07 with a residual sleeve crane, in particular a clamp crane with trolley, removed and transported for disposal in a car.

A schematic view of the roll changer with different stages of roll supply is in the Fig. 8 shown.

LIST OF REFERENCE NUMBERS

01

reelstands

02

Material web, first

03

Swivel axis (04)

04

roller stand

05

Recording, mandrel

06

Roll of material, draining; residual role

07

Material roll, new

08

Support Belt

09

foundation

10

Sleeve, cardboard sleeve

11

support means

12

Support Belt

13

role

14

actuating cylinder

15

-

16

reelstands

17

support means

18

support means

19

linear guide

20

-

21

actuating cylinder

22

Support Belt

23

-

24

supporting journal

25

-

26

jaw

27

Jaw series

28

Jaw series

29

Material web, second

30

-

31

Pushcart, scissor lift table

32

tram

33

Wheel (31)

34

Wheel (32)

b02

Width of the material web

b10

Wall thickness of the sleeve

110

Length of the sleeve

124

Length of the trunnion

126

Length of the clamping jaw

d10

Inner diameter of the sleeve

D24

Diameter of the trunnion

Claims (1)

1. Method for carrying out a flying reel change, a first material web (02) of a material reel (06) to be changed being connected to a second material web (29) of a new material reel (07), the material reel (06) to be changed running at a first web speed, the first material web (02) being connected to the second material web (29) at the latest on reaching a minimum diameter of the residual reel (06), this minimum diameter of the residual reel (06) being determined as a function of the properties of a core (10) of the residual reel (06) before the connection of the first material web (02) to the second material web (29), the minimum diameter of the residual reel (06) being determined as a function of material properties of the core (10) of the material reel (06; 07), the first web speed being reduced to a second web speed before the connection of the first material web (02) to the second material web (29) and the first material web (02) being connected to the second material web (29) at this reduced web speed, the reduction of the web speed being controlled together with the connection process by means of a programme, and the determination of the minimum diameter of the residual reel (06) together with the connection process being controlled by means of the programme.

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