EP1591390B1 - Reeling machine for continuous winding of a web material - Google Patents

Abstract

The air expulsion device (10) for consolidating the web layers and regulating the amount of air trapped in between them comprises a number of adjacent segment rolls (11) with their opposite ends mounted via bearing units (12) on a support profile (13) extending the width of the machine. The bearing units have a counter-bearing (14) and a resilient bearing (15) on the profile side. The counter-bearing is a hinge bearing. The resilient bearing is a preferably closed spring system, preferably a coil or leaf spring, or a preferably closed damping unit, preferably a shock absorber, or a controllable hydraulic or pneumatic piston unit.

Description

The invention relates to a winding machine for continuously winding a material web, in particular a paper or board web, on a spool to a winding roll, with a carrier drum, which forms a Ni (winding nip) with the winding roll, with a comprehensive at least one transport storage, the Tambour along a preferably horizontal guideway leads, and with an attached in the lower region of the winding machine Luftabquetschvorrichtung which can be applied upon reaching a desired layer thickness of the winding roll by means of at least one movement means.

Such winding machines are for example from the European Patent EP 0 483 092 B1 or from the PCT Publication WO 98/52858 A1 The applicant is well known and are used in particular in machines for producing or refining webs, such as paper or cardboard.

In modern winding concepts for material webs, it is necessary today, in preparation for a Tambourwechsels to bring the drum with the almost fully wound reel ("ready toboggan") in an end position (Tambourwechselposition), in which then no effective contact, no so-called nip, between the carrier drum and the winding roll is longer. In this time, in which no nip is more, must be ensured by appropriate measures that no air pockets between the individual layers of the almost fully wound reel arise. Furthermore, both the "wrapped" web tension and the line force must be maintained, so in the outer area of the winding roll to ensure the desired winding quality. The resulting problem is greater, the faster the winding machines are operated (current order of 1,500 to 2,500 m / min) and the larger the produced diameter of the finished reels are (current order of 2.5 to 4.5 m).

In a winding machine of the type described has already been attempted to solve this problem, as in the German patent application DE 44 01 804 A1 disclosed by the applicant. It is there provided a device comprising a pressure roller with an elastic coating which is pressed against a, of a carrier drum remote winding roller by means of a pneumatic drive. This device serves the purpose of preventing the formation of trapped air between the individual layers of the winding roll by maintaining the line force and to maintain the during the reel change "wrapped" web tension.

However, the illustrated pressure roller has the serious disadvantage that it is subject to deflection due to its own weight, the winding roll, for example, due to different paper thickness over the width more or less deviates from an ideal cylindrical shape and the pressure roller is therefore not uniform while maintaining a minimum Line force can apply to the surface contour of the almost fully wound winding roll across the web width. As a result, it follows that the formation of trapped air between the outer layers of the almost fully wound reel can not be completely avoided.

Furthermore, from the German Offenlegungsschrift DE 100 23 057 A1 the Applicant a winding machine for continuously winding a web, in particular a paper or board web, known on a spool to a winding roll. This winding machine comprises a carrying drum forming a nip with the winding roll, at least one bearing comprising a transporting device, which supports the tambour along a preferred manner horizontal guideway leads, and mounted in the lower part of the winding machine Luftabquetschvorrichtung which can be applied to the winding roll. The Luftabquetschvorrichtung is designed as an applyable carrier profile by means of bearings side by side eccentrically mounted segment rollers, wherein in the interior of the carrier profile is filled by at least one pressure source with a pressure medium and surrounded by a guide tube hose on which the non-rotatable bearing bushes of the bearing by means of at least a power transmission element are centrally supported.

However, the Luftabquetschvorrichtung shown has the following disadvantages: it is very expensive to manufacture and thus expensive to procure, their segment roles are neither sections nor fully driven.

It is therefore an object of the invention to improve a winding machine of the type mentioned in such a way that a desired, preferably uniform line force curve between applied Luftabquetschvorrichtung and surface contour of the almost fully wound winding roll over the web width is given away.

This object is achieved according to the invention in a winding machine of the type mentioned that the applicable Luftabquetschvorrichtung consists of several juxtaposed segment roles, which are each arranged on the front side by means of storage units on a machine-width carrier profile, wherein the bearing units profile side each have a joint bearing and a resilient mounting.

This results in the advantage that the respective joint bearing ensures exact positioning of the corresponding segmented roller, whereas the respective resilient mounting enables automatic and individual adjustability of the corresponding segmented roller in the necessary adjustment range to the surface contour of the almost fully wound winding roller. This creates the possibility of a desired, preferably uniform line force curve between applied segment rollers, that is, applied Luftabquetschvorrichtung and surface contour of the almost fully wound winding roll over the web width away to ensure. Any unevenness in the surface contour of the almost fully wound winding roll, in particular in the edge regions, are compensated by an automatic setting of the individual segment rolls. Thus, locally different contact forces are avoided. The technical structure of the Luftabquetschvorrichtung invention also results in a highly self-damping system which largely eliminates vibrations induced by the web or by the winding roll.

In an embodiment which is suitable in particular for retrofitting to existing winding machines, the bearing units each have two bearing plates on the profile side, which are connected to one another by means of the respective pivot bearing and the respective resilient mounting. The one bearing plate is mounted on the carrier profile, in particular releasably by means of screwing or unsolvable by means of welds, whereas the other bearing plate carries a arranged between two segment rollers bearing wall including bearing eye, in particular by means of welds. This embodiment is characterized in particular by a high degree of flexibility and rigidity.

A simpler embodiment, which is particularly suitable for new winding machines, has a respective pivot bearing, which is arranged directly on a bearing wall arranged between two segment rollers and on the machine-width carrier profile. This embodiment provides particular cost and weight advantages.

So that an optimal application of the segmented roll to the surface contour of the almost fully wound winding roll becomes possible, the joint support is preferably arranged on the winding roll side facing the storage unit and the resilient storage preferably on the side facing away from the winding roll of the storage unit. Moreover, this results in the smallest possible spread the optionally offset laying lines of the segment rolls to said surface contour.

The joint bearing is preferably designed as a hinge bearing, since this type of storage brings certain advantages in terms of reliability and maintenance requirements.

The resilient mounting comprises in a preferred embodiment a preferably closed spring system, in particular a screw or leaf spring, a preferably closed damping unit, in particular a shock absorber, or a controllable piston unit with hydraulic or pneumatic actuation. These types of compliant bearing meet the requirements placed on them at low cost, low cost of ownership and high reliability.

When using controllable resilient bearings, the same are preferably sectioned across the machine width, wherein different forces can be generated in the individual sections. The generation of the different effective forces is in particular caused and monitored by a control unit known per se. The individual sections can in turn be controlled in groups, for example symmetrically to the material web. Moreover, the generation of different effective forces in the individual sections makes it possible to set a desired pressure profile, which is advantageous in particular for NCR papers and / or for not exactly cylindrical winding rolls. The pressure profile can in particular also serve to displace possibly trapped air outwards towards the edges of the winding roll, for example with greater effective forces in the region of the web center and smaller effective forces in the two edge regions.

So that no speed differences arise between two adjacent segment rollers, they are preferably coupled to one another with an axle coupling. This creates at least partially same circumferential speeds at the segment rollers. Furthermore, circumferential forces can also be transmitted to the winding roll via coupled segment rolls, which can be used, for example, to decelerate the winding roll.

In the context of an optimal configuration of the air squeezing device, the segmented rollers can preferably be driven by means of at least one drive unit preferably arranged on the front side of the air squeezing device. Thus, the segment rolls can also be pre-accelerated to the circumferential speed of the same before they are applied to the surface contour, so that in turn a smooth, that is, smooth application of the segmented rolls is made possible.

With regard to the technological requirements of the Luftabquetschvorrichtung it is advantageous if the segment roll has a diameter in the range of 200 to 500 mm, preferably from 250 to 350 mm. The width of the individual segment rolls can vary in a range of 200 to 2,500 mm, depending on whether over the entire width of the web equalization of the contact force (small width ranges) or only at the two edges of the web is to take place a balance (large width range in the middle of the track, small width areas at the edges of the course). These dimensions ensure that the web due to the action of Luftabquetschvorrichtung undergoes any damage, such as grooves or other markings, and property changes, such as highlights.

Furthermore, in order to maximize the avoidance of air accumulation in front of the air squeezing device, it is advantageous if the segmented roller has a rubberized and / or grooved surface. The rubberized surface of the segmented roll preferably has a hardness in the range of 50-200 P & J (Pussy & Jones), preferably 80-120 P & J (Pussy & Jones).

Under structural or manufacturing aspects, the carrier profile is preferably a carrier tube with a rectangular and / or square tube cross-section.

In order to achieve the greatest possible avoidance of air inclusions between the individual layers of the winding roll, the Luftabquetschvorrichtung can be applied in a peripheral region of the lateral surface of the winding roll, which extends at least from the feed point of the web on the outer surface of the winding roll to the vertical low point of the winding roll. Upstream and downstream jobs provide a loss of effectiveness in terms of the aforementioned avoidance.

With regard to runability and efficiency of the winding machine, it is advantageous, indeed necessary, to apply the air-squeezing device to the winding roll before opening the nip between the carrying drum and the winding roll in order to avoid air pockets and / or a lateral course of the material web.

The Luftabquetschvorrichtung is substantially linear, preferably horizontally and / or vertically, and / or substantially along a contour of a circular segment can be applied. These application movements result in practice in terms of their regulations and moving mass or mass changes advantages.

It is also advantageous that when forming an effective region between the winding roll and the air squeezing device, the superordinate active force in the effective region can be regulated by a displacement of the air squeezing device. This results in a good, up to the last winding layers present winding result, that is, a winding roll with a defined uniform winding hardness over the entire winding time, achieved as a fine adjustment of the active force in the effective range between the winding roll and Luftabquetschvorrichtung during the final winding phase, in the nip between the carrier drum and the winding roll is no longer possible is possible.

Further features and advantages of the invention will become apparent from the dependent claims and the following description of preferred embodiments with reference to the drawings.

Figur 1:

eine schematische Seitenansicht einer Wickelmaschine mit erfindungsgemäßer Luftabquetschvorrichtung während der Hauptwickelphase;

Figur 2:

eine schematisierte Seitenansicht einer Wickelmaschine mit erfindungsgemäßer Luftabquetschvorrichtung während der Endwickelphase;

Figur 3:

eine schematische Darstellung (Querschnitt) der erfindungsgemäßen Luftabquetschvorrichtung; und

Figur 4:

eine schematische und teilweise Darstellung (Längsschnitt) der erfindungsgemäßen Luftabquetschvorrichtung.

Show it

FIG. 1:

a schematic side view of a winding machine with inventive Luftabquetschvorrichtung during the main winding phase;

FIG. 2:

a schematic side view of a winding machine with inventive Luftabquetschvorrichtung during Endwickelphase;

FIG. 3:

a schematic representation (cross section) of the Luftabquetschvorrichtung invention; and

FIG. 4:

a schematic and partial representation (longitudinal section) of the Luftabquetschvorrichtung invention.

In the FIG. 1 Shaped winding machine 1 shown in schematic form for continuously winding a material web 2, in particular a paper or board web, on a spool 3 to a winding roll 4 comprises a carrier drum 5 also referred to as Anpresstrommel or support roller, either rigidly mounted or along an imaginary dashed lines shown horizontal line G is displaceable by means of a pressing device, not shown (double arrow P1) and by a drive, in the case shown by a center drive, is driven. The various storage and movement types for the carrier drum 5 are particularly in the German Offenlegungsschrift DE 198 07 897 A1 the applicant s discloses; its content is hereby made the subject of this description.

The material web 2 is led out either from a calender not shown here or a likewise not shown here dryer section of a paper or board machine, then wraps around a spreader roller, not shown, and then runs in the direction of arrow on the outer surface 6 of the carrier drum 5, wraps around the lateral surface 6 of the carrier drum 5 by a certain angle (circumferential area) to detachment by the resulting winding roll 4. The detachment of the web 2 from the carrier drum 5 and the transfer to the resulting winding roll 4 is done in the so-called nip (Winding nip) 7, which forms during the main winding phase between the carrier drum 5 and the winding roller 4.

The winding roller 4 is guided by means of a lifting device, not shown, a movable transport device in the direction indicated by the arrow P2 movement direction. The transport device can be formed, for example, by a spindle drive which comprises a threaded spindle driven by an electric motor. The transport device serves to hold and guide the main roll 3 resting on the preferably horizontal rails (guideway) 9. A device for regulating the line force L arising in the nip 7 during the main winding phase is, for example, in the already mentioned German Offenlegungsschrift DE 198 07 897 A1 disclosed by the applicant. In the in FIG. 1 shown main winding phase is an empty drum ("empty drum") 8 held by a holding device, not shown at a distance from the carrier drum 5 ("standby position").

In the lower part of the winding machine 1, an air squeezing device 10 is shown in dot-dashed form, which stands in no active relationship with the winding roller 4 during the illustrated main winding phase. It is rather in a waiting position. The Luftabquetschvorrichtung 10 can be moved by generally known mechanisms both substantially linear (arrows), preferably horizontally and / or vertically, as well as substantially along a Kontor a circle segment (arrow) and it is on reaching a desired layer thickness S to the winding roll 4th can be applied by means of at least one known movement device.

The FIG. 2 shows a schematic side view of a winding machine 1 with inventive Luftabquetschvorrichtung 10 during Endwickelphase. During this Endwickelphase the winding roller 4 is moved with the transport device already described by the carrier drum 5 with the dissolution of the nip and forming a free Bahnzugs away. Time is then offset the previously held at a distance from the carrier drum 5 empty spool 8 from the holding device, not shown, mounted on the carrier drum 5 with the formation of a new nip 7. With the web separation, not shown, then begins the Anwickelphase for the empty drum 8, wherein the winding roller 4 is then no longer wound and horizontally (arrow P2) in an end position E (Tambourwechselposition) is moved.

The FIG. 3 shows a schematic representation (cross section) of the Luftabquetschvorrichtung 10 according to the invention.

The can be applied to the winding roll 4 Luftabquetschvorrichtung 10 consists of a plurality of juxtaposed segment rollers 11, which are respectively arranged on the front side by means of storage units 12 on a machine-width support section 13, the storage units 12 profile side each having a hinge bearing 14, preferably in the form of a hinge bearing, and a resilient mounting 15 with a preferred adjustment V (arrow) in the range of 1 to 30 mm, preferably from 2 to 15 mm.

The bearing units 12 have profile-side two bearing plates 16.1, 16.2, wherein the lower bearing plate 16.1 is mounted on the support section 13 and wherein the upper bearing plate 16.2 carries a arranged between two segment rollers 11 bearing wall 17 together bearing eye 18 carries. The two bearing plates 16.1, 16.2 are connected to each other by means of the respective joint bearing 14 and the respective resilient mounting 15, wherein the joint bearing 14 is disposed on the winding roller 4 side facing the bearing unit 12 and wherein the resilient mounting 15 on the side facing away from the winding roll 4 the storage unit 12 is arranged. The bearing plates 16.1, 16.2 may of course also extend over at least two adjacent segment rollers 11.

In another, but not shown form, the respective joint bearing can also be arranged directly on a bearing wall arranged between two segment rollers and on the machine-width carrier profile.

The resilient mounting 15 includes a preferably closed spring system 19, in particular a screw or leaf spring. However, it may also comprise a preferably closed damping unit, in particular a shock absorber, or a controllable piston unit with hydraulic or pneumatic actuation.

The carrier profile 13 is shown in the representation of FIG. 3 a support tube with a rectangular and / or square tube cross-section. However, it may also have a polygonal tube cross-section, if the application allows.

In the FIG. 3 it can be seen that the Luftabquetschvorrichtung 10 in a peripheral region U to the lateral surface 20 of the winding roll 4 is substantially linear, preferably horizontally and / or vertically, and / or substantially along a contour of a circular segment can be applied. The peripheral region U extends at least from the contact point A of the material web 2 on the lateral surface 20 of the winding roll 4 to the vertical low point T of the winding roll 4th

The Luftabquetschvorrichtung 10 is before opening of the nip 7 (FIG. FIG. 1 ) between the carrier drum 5 and the winding roller 4 to the winding roller 4 can be applied.

Immediately upon formation of an effective region W between the winding roll 4 and the air squeezing device 10 (FIG. FIG. 2 ), the superordinate effective force K in the effective range W is regulated by a displacement of the air squeezing device 10. Such a control loop belongs to the field of knowledge of the average person skilled in the art and is, for example, in the already mentioned German Offenlegungsschrift DE 198 07 897 A1 Applicant for a carrier drum disclosed. The Luftabquetschvorrichtung 10 is displaced while maintaining the parent effective force K in the effective range W to the winding roll 4. The displacement is preferred only then terminated when the winding roller 4 horizontal (arrow P2) has reached its end position E (Tambourwechselposition).

The FIG. 4 shows a schematic and partial illustration (longitudinal section) of the Luftabquetschvorrichtung 10 according to the invention.

The applicable Luftabquetschvorrichtung 10 consists, as already mentioned, of a plurality of juxtaposed segment rollers 11, which are each arranged on the front side by means of storage units 12 (double storage unit between two segment rollers 11, single storage unit on end-side segment roller 11) on a machine-width carrier profile, not shown. The bearing units 12 each have two bearing plates on the profile side, wherein only the upper bearing plate 16. 2 is shown, which carries a bearing wall 17 arranged between two segment rollers 11 together with bearing eye 18. The two segment rollers 11 end of the Luftabquetschvorrichtung 10 are merely simply stored in a bearing wall 17 together with bearing eye 18.

Two adjacent segment rollers 11 are mounted in a common bearing sleeve 21 by means of rolling bearings 22 and coupled to each other with an axle coupling 23 of known type.

Furthermore, the segment rollers 11 are drivable by means of at least one drive unit 24, preferably arranged on the front side of the air squeezing device 10, wherein in the FIG. 4 only the drive pulley 25 of the not explicitly shown drive unit 24 is shown; However, the drive pulley 25 may also be formed as a drive pinion. Thus, the segment rollers 11 can be vorbeschleunigt before applying to the surface contour of the almost fully wound reel 4 to the peripheral speed derselbigen, so that in turn a smooth, that is jerkless application of the segment rollers 11 is made possible.

The segment rollers 11 have a diameter D in the range of 200 to 500 mm, preferably 250 to 350 mm, and a width B in a range of 200 to 2,500 mm.

Furthermore, the segment rollers 11 rubberized ( FIG. 3 ) and / or grooved surfaces 26; Of course, they may also have flat surfaces 26. The rubberized surfaces 26 of the segmented rollers 11 preferably have a hardness H in the range of 50 to 200 P & J, preferably 80 to 120 P & J.

The flexible and non-detailed bearings of the bearing units 12 can be sectioned across the machine width, wherein in the individual sections by different forces K (dashed lines) on the bearing units 12 different contact pressures in the individual sections can be generated. The generation of the different effective forces K is preferably caused and monitored by a known control unit 27.

In summary, it should be noted that a winding machine of the type mentioned above is improved by the invention, that a desired, preferably uniform line force curve between applied Luftabquetschvorrichtung and surface contour of the almost fully wound winding roll over the web width is given away.

LIST OF REFERENCE NUMBERS

1

winder

2

web

3

drummer

4

reel

5

carrying drum

6

Lateral surface (carrier drum)

7

Nip (winding gap)

8th

Empty Tambour ("empty tambour")

9

Rail (guideway)

10

Luftabquetschvorrichtung

11

segment role

12

storage unit

13

carrier profile

14

joint bearing

15

Compliant storage

16.1, 16.2

bearing plate

17

bearing wall

18

bearing eye

19

spring system

20

Lateral surface (winding roll)

21

bearing sleeve

22

roller bearing

23

axis coupling

24

drive unit

25

sheave

26

surface

27

control unit

A

accumulating point

B

width

D

diameter

e

end position

G

Horizontal straight line

H

hardness

K

Effectiveness (dashed line)

L

line force

P1

double arrow

P2

arrow

S

layer thickness

T

Low point (winding roll)

U

Peripheral area (winding roll)

V

Adjustment path (arrow)

W

effective range

Claims (21)

1. Winding machine (1) for continuously winding a material web (2), in particular a paper or board web, on to a spool (3) to form a wound reel (4), having a carrier drum (5) which forms a nip (7) with the wound reel (4), having a mounting which comprises at least one transport device which guides the spool (3) along a preferably horizontal guide track (9), having a device (10) for squeezing out air, which is fitted in the lower region of the winding machine (1) and which can be set on the wound reel (4) by means of at least one movement device when a desired layer thickness (S) has been reached, the device (10) for squeezing out air, which can be set on, comprising a plurality of segment rollers (11) which are mounted beside one another and in each case at the ends are arranged by means of bearing units (12) on a machine-width carrier profile (13),
   characterized in that
   the bearing units (12) each have on the profile side an articulated mounting (14) and a compliant mounting (15).
2. Winding machine (1) according to Claim 1,
   characterized in that
   the bearing units (12) on the profile side each have two bearing plates (16.1, 16.2), one bearing plate (16.1) being fitted to the carrier profile (13) and the other bearing plate (16.2) being arranged on a bearing wall (17) arranged between two segment rollers (11), and
   in that the two bearing plates (16.1, 16.2) are connected to each other by means of the respective articulated mounting (14) and the respective compliant mounting (15).
3. Winding machine (1) according to Claim 1,
   characterized in that
   the respective articulated mounting (14) is arranged directly on a bearing wall (17) arranged between two segment rollers (11) and on the machine-width carrier profile (13).
4. Winding machine (1) according to Claim 1, 2 or 3,
   characterized in that
   the articulated mounting (14) is arranged on the side of the bearing unit (12) that faces the wound reel (4), and
   in that the compliant mounting (15) is arranged on the side of the bearing unit (12) that faces away from the wound reel (4).
5. Winding machine (1) according to one of the preceding claims,
   characterized in that
   the articulated mounting (14) is constructed as a hinged mounting.
6. Winding machine (1) according to one of the preceding claims,
   characterized in that
   the compliant mounting (15) comprises a preferably self-contained spring system (19), in particular a helical or leaf spring.
7. Winding machine (1) according to one of Claims 1 to 5,
   characterized in that
   the compliant mounting (15) comprises a preferably self-contained damping unit, in particular a shock absorber.
8. Winding machine (1) according to one of Claims 1 to 5,
   characterized in that
   the compliant mounting (15) comprises a controllable piston unit with hydraulic or pneumatic loading.
9. Winding machine (1) according to Claim 8,
   characterized in that
   the compliant mountings (15) are sectioned over the machine width, and
   in that different effective forces (K) can be produced in the individual sections.
10. Winding machine (1) according to one of the preceding claims,
    characterized in that
    two adjacent segment rollers (11) can be coupled to each other, preferably by means of a shaft coupling (23).
11. Winding machine (1) according to one of the preceding claims,
    characterized in that
    the segment rollers (11) can be driven by means of at least one drive unit (24), preferably arranged at the end of the device (10) for squeezing out air.
12. Winding machine (1) according to one of the preceding claims,
    characterized in that
    the segment roller (11) has a diameter (D) in the range from 200 to 500 mm, preferably from 250 to 350 mm.
13. Winding machine (1) according to one of the preceding claims,
    characterized in that
    the segment roller (11) has a width (B) in the range from 200 to 2500 mm.
14. Winding machine (1) according to one of the preceding claims,
    characterized in that
    the segment roller (11) has a rubber-covered and/or grooved surface (26).
15. Winding machine (1) according to Claim 14,
    characterized in that
    the rubber-covered surface (26) has a hardness (H) in the range from 50 to 200 P&J, preferably from 80 to 120 P&J.
16. Winding machine (1) according to one of the preceding claims,
    characterized in that
    the carrier profile (13) is a carrier tube with a rectangular and/or square tube cross section.
17. Winding machine (1) according to one of the preceding claims,
    characterized in that
    the device (10) for squeezing out air can be set on the circumferential surface (20) of the wound reel (4) in a circumferential region (U) which reaches at least from the point (A) at which the material web (2) runs onto the circumferential surface (20) of the wound reel (4) as far as the vertical low point (T) of the wound reel (4).
18. Winding machine (1) according to one of the preceding claims,
    characterized in that
    the device (10) for squeezing out air can be set on the wound reel (4) before the opening of the nip (7) between the carrier drum (5) and the wound reel (4).
19. Winding machine (1) according to one of the preceding claims,
    characterized in that
    the device (10) for squeezing out air can be set on substantially linearly, preferably vertically.
20. Winding machine (1) according to one of Claims 1 to 18,
    characterized in that
    the device (10) for squeezing out air can be set on substantially along the contour of a circular segment.
21. Winding machine (1) according to one of the preceding claims,
    characterized in that
    during the formation of an active region (W) between the wound reel (4) and the device (10) for squeezing out air, the higher-order effective force (K) in the active region (W) can be controlled by means of a displacement of the device (10) for squeezing out air.

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