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(11) | EP 0 846 080 B1 |
| (12) | EUROPEAN PATENT SPECIFICATION |
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| (54) |
SEPARATING DEVICE FOR WINDING DEVICES FOR MATERIAL WEBS, LONGITUDINALLY DIVIDED INTO SEVERAL PARTIAL WEBS ABTRENNVORRICHTUNG FÜR AUFWICKELVORRICHTUNGEN FÜR IN MEHRERE TEILBAHNEN LÄNGSGETEILTE WERKSTOFFBAHNEN APPAREIL DE SEPARATION POUR DES MECANISMES D'ENROULEMENT POUR MATERIAUX EN BANDES, DIVISEES LONGITUDINALEMENT EN PLUSIEURS BANDES PARTIELLES |
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| Note: Within nine months from the publication of the mention of the grant of the European patent, any person may give notice to the European Patent Office of opposition to the European patent granted. Notice of opposition shall be filed in a written reasoned statement. It shall not be deemed to have been filed until the opposition fee has been paid. (Art. 99(1) European Patent Convention). |
[0001] The invention relates to a separating device for winding devices for material webs, longitudinally divided into several partial webs, particularly those made of paper or the like, with the characteristics of the preamble of Claim 1.
[0002] In order to improve the web separation in so-called reel cutters after the cutting station, it is known to use so-called duo roll spreaders. Here, as a rule, two conventional so-called rotary stretchers are involved, i.e., rolls whose axis (and hence also their surface) ist curved. The height of the arc, i.e., the radius of the deflection line, is adjusted to the particular application. Both rotary stretchers (also several rotary stretchers are possible) are arranged essentially parallel to each other and the planes spanned by the deflection lines are arranged essentially parallel to each other for the purpose of archieving a flawless functioning. Additional conditions for a flawless functioning are that the planes, spanned by the deflection lines, are always at a right angle to the entering or exiting web and the arcs, formed by the rotary stretchers, point in the same direction.
[0003] The extent of the total separation of all partial webs that can be achieved is a constant value for the respective initial situation. Thus, with an increasing number of partial webs, the spacing gaps that are realizable between them in a certain initial situation become increasingly smaller. For the rest, the extent of the achievable separation - on the one hand - depends on the radius of the deflection line of the rotary stretchers. The greater the deflection, i.e., the smaller the deflection radius, the greater the separation. On the other hand, the extent of the separation depends on how far (in the case of a constant axial distance of the two rotary stretchers) the web entering the separating device is distanced from the web exiting the separating device perpendicular to the direction of advance of the web. The greater this distance measure, described as the effective height (=Heff), the greater the separation.
[0004] Depending on the total width of the web that has been longitudinally separated into partial webs, and depending on the number of partial webs and possibly on additional parameters, it is necessary, from case to case, to change the dimension of the separation. Since the deflection of the rotary stretchers can be changed only with great effort, it ist customary to change the effective height by pivoting the two rotary stretchers about the common pivot point. In order to meet the condition of rectangularity between the arcs of the rotary stretcher and the entering or exiting web, the alignment of these arcs with respect to the entering web, on the one hand, and the exiting web, on the other hand, must be changed during a sweep of the two rotary stretchers by means of subsequent adjustment. This is time-consuming and labor-intensive, since the rotary stretchers inside the machine are often difficult to access.
[0005] DE-B-200 75 69 discloses a separating device having at all four rolls, two of which are revolving rolls borne in a tiltable boom frame, two of which are flexed rolls borne in a swivelling cross of swivelling arms. The swivelling axis of the swivelling cross must be exactly in the middle between the axis of the revolving rolls, therefore the ends of the boom frame are stationary coupled with the revolving rolls. The amount of web separation is changed by altering the wrapping angle of a web around the flexed rolls. Maximal separation is achieved with a wrapping angle of 90°. Therefore, the axis of one revolving roll is coupled with a corresponding flexed roll by alining arms with fork-shaped guidings.
[0006] A generic separating device is known from EP-A-0 431 275 comprising a regulation mechanism which is fitted to correct the directional angles between the rolls and the web to desired values, preferably 90°, by means of rods being swiftable around their endportions and a swing mechanism, which is fitted to act upon the rolls to alter the deflection angles of the webs.
[0007] Based on this, it is the objective of the invention to render the subsequent adjustment of the arcs a generic separating device avoidable. The objective is accomplished by a separating device with the characteristics of Claim 1. The invention is based on the basic concept that through a sweep of the support frame of the two rotary stretchers, the arc alignment of the rotary stretchers is necessarily adjusted with respect to the entering or exiting web. Thereby, any type of subsequent alignment of the arcs of the rotary stretchers in the separating device is completely eliminated.
[0008] Advantageous embodiments of the subject matter of the invention, assuring in particular a simple layout of the arc adjustment transmissions, are contained in additional claims.
[0009] The structural components which are mentioned above, as well as those claimed in the examples, which are to be used in accordance whith the invention, are not subject to special exceptional conditions with respect to their size, form, material selection and technical conception, so that the selection criteria known in the respective area of application can find unlimited application.
[0010] Further details, characteristics and advantages of the subject matter of the invention are apparent from the subsequent description of the accompanying drawing in which - for example - three preferred embodiments of a separating device of the invention are shown.
[0011] In the drawing,
- Figure 1
- shows a perspective basic representation of a generic separating device;
- Figure 2A/B
- shows a first embodiment in different operating positions of the separating device in frontal view (schematic);
- Figure 3A/B
- shows a second embodiment in the same type of representation and
- Figure 4A/B
- shows a third embodiment in the same type of representation.
[0012] As can best be seen by means of Figure 1, in all three embodiments according to the Figures 2A to 4B, respectively, two rolls 1, 2, forming a roll pair, are arranged with axial alignment parallel to one other in a support frame 9. The rolls 1, 2 are rotatably mounted in the support frame 9 in a manner wherein they can be freely turned or driven about their respective axes of rotation 21 or 22. Both roll axes are bowed with essentially the same deflection radius. The deflection lines of the axes of rotation 21 and 22 are indicated in Figure 1 with B1 and B2, respectively. Both deflection lines - described in the subsequent text also as arcs - span a plane, wherein the plane, spanned by the arc B1, is aligned at a right angle with respect to the entering web and the plane, spanned by the arc B2 is at a right angle to the exiting web. The material web 30, guided between both rolls 1 and 2, is longitudinally divided into partial webs 30', 30'' ... . While the entering partial webs (respectively on the left of the illustration) extend side-by-side partically in a gapless manner parallel to each other, the exiting partial webs are distanced from each other by means of mutual spacing gaps G', G'', ... and in turn extend parallel to each other. Due to the fact that the entering partial webs are guided across the inner arc of the roll 1, the partial webs between the rolls 1 and 2 do not extend in a parallel arrangement, but in a fanned out configuration. Due to the fact that they are guided along the roll 2 around its outer arc, the obtained spread dimension (or separating dimension) is frozen, so to speak, since the exiting partial webs are again aligned parallel to each other and subsequently can be rolled into rolls 31, i.e., partial rolls 31', 31'', ... on any desired winding device. Merely as an example, in Figure 1, a so-called double king roll winding device is shown, wherein the partial webs 30', 30'', ... are guided between the two driven king rolls 32 and 33. At that time, they wrap around the first entering king roll 32 and are rolled up in the winding bed present between the parallel king rolls 32 and 33 into the rolls 31', 31'', ... .
[0013] In order to be able to change the spacing gabs G', G'', ... in accordance with the total width of the material web 30 and depending on the number of partial webs 30', 30'' ... created therefrom, or dependent on other factors, the effective height, i.e., the lateral displacement between the partial webs, which enter a separating device, indicated in total with 100, is changed with respect to the webs extending parallel thereto. This is explained in detail by means of the subsequent description of the Figures 2A to 4B:
[0014] In the embodiments of the invention, the separating device 100 for winding devices for material webs 30, that are longitudinally divided into several partial webs, as represented in the examples, has two rolls 1 and 2 of a roll pair 1, 2, which are flexed essentially in the same direction. The rolls 1 and 2 are rotatably arranged with spherical bearings in a support frame 9 such that the roll surface can be rotated about the respective axis of rotation 21 or 22 either freely or possibly in a driven manner. The crown of the arcs of the two rolls 1 and 2, which is indicated in the drawing by means of the associated radius vector A or B, does not change its direction in space during the rotation of the roll surface about the respective axis 21 or 22. Thus, the directions of the vectors A and B are stationary, as long as no special adjustment is undertaken. The support frame 9, carrying the two rolls 1 and 2 in a rotatable manner, can be pivoted on a stand 10 or a pair of stands about a central swivelling axis 7 which extends parallel to the rolls 1 and 2. The rotatably arranged support frame, located at the other front face which is opposite the observer, is shown while the support frame, which is near the observer, has been omitted in order to provide an unobstructed view of the transmission near the observer.
[0015] With the operarting positions shown in Figures 2A, 3A and 4A, the material webs 30 extend in a straight line between a roll 34, arranged in the inlet area and a roll 32 assigned to the outlet area. The entering web touches the roll 1 merely at the two outer edges of the material web, i.e, near the two front ends of the roll 1. The exiting web touches the rotary stretcher 2 which is second in the direction of advance of the web only at its peak. Thus, in this operating position, the webs of material remain completely uninfluenced by the pair of rotary stretchers - a separation does not take place. The same thing applies if, starting from this operating position, the support frame 9 were to be turned clockwise. However, if the support frame 9 is turned counterclockwise, this results in the operating positions in which a separation of the partial webs takes place. Such an operating position is shown as an example in the Figures 2B, 3B and 4B. In these Figures, for the sake of clarity, merely the outermost edge of the material web pointing towards the observer is drawn in.
[0016] As is clarified by comparing the respectively accompanying Figures 2A with 2B, 3A with 3B and 4A with 4B, the crown vector A of the first rotary stretcher 1 encloses a 90° angle with respect to the entering web. In the same manner, the exiting web also encloses an angle of 90° with respect to the crown vector B of the second rotary stretcher 2. This is automatically brought about in all three embodiments in that during a horizontal sweep of the support frame 9 into a new operating position, the crown vectors 4A and 4B of the two rotary stretchers 1 and 2 are turned in the direction opposite the pivot direction of the support frame 9 sufficiently far that at each angle position of the support frame 9, a well-defined angle position of the crown vector A and B with respect to the stand 10, is set, i.e., such that the 90° condition is assured in each position of the stand 9 at both rotary stretchers 1 and 2. In order to achieve this, in each embodiment, at least one pair of transmissions is provided, which effects a simultaneous, automatic twisting of the deflection lindes B1 and B2 with respect to the crown vector A or B of the flexed rolls 1 and 2 during a horizontal sweep of the support frame 9 with respect to the stand 10 such that the transmissions are necessarily operated by means of the sweep movement of the support frame 9. Therefore, with the examples shown and preferred so far in the drawing, the stand 9 is respectively a part of at least the one pair of transmissions.
[0017] With all examples, respectively one transmission, each consisting of the structural components 3, 5 and 8, is arranged between the swivelling axis 7 of the support frame 9 and the axis of rotation 21 of the first rotary stretcher 1. The other transmission consists of the structural components 8, 6 and 4 and is effective between the swivelling axis 7 of the support frame 9 and the axis of rotation 22 of the second rotary stretcher 2. It is also possible to provide a pair of transmissions at each of the two front ends of the roll. However, as a rule, it is sufficient and is shown in the three examples, that the one transmission (transmission 3, 5, 8) be provided at the one front end of the roll and the other transmission (transmission 8, 6, 4) be provided at the opposite front end. For the sake of clarity, in the example according to Figures 2A/B, merely the transmission 8, 6, 4, provided at the opposite front end of the roll, is shown. In the case of the remaining two examples, according to Figures 3A to 4B, merely the transmission 3, 5, 8, visible when the support frame which is near the observer is omitted, is shown in order to maintain the clarity of the Figures as far as possible. The transmission of the transmission pair which, arranged at the other front end of the roll is executed in the same manner as the pair of transmissions visible in the drawing.
[0018] In the example according to the Figures 2A/B, at the structural components of the rotary stretcher 1 which are fixed, i.e., not rotatable about the axis of rotation 21 or 22, an adjustment lever 3A or 4A is arranged without rotational play. The one pivot point of each of the adjustment levers 3A or 4A coincides with the axis of rotation 21 or 22. At the other pivot point, respectively, a lug for the pivotable attachment of a steering device or of a pressure/slide rod 5A or 6A is provided. The respectively other end of these pressure/slide rods 5A and 6A is rotatably connected to the lug of another lever 8A. This lever 8A is fixed with respect to the stand 10 and is rotatable with respect to the support frame 9.
[0019] This transmission functions in the following manner: If the support frame 9 is turned, for example, starting from the operating postion shown in Figure 2A into the operating position shown in Figure 2B counterclockwise about the swivelling axis 7, effective between the support frame 9 and the stand 10, then the axes of rotation 21 and 22 of the rotary stretchers 1 and 2 are also displaced counterclockwise with respect to the swivelling axis 7. The paths covered at that time by the axes of rotation 21 or 22 are equal in length, because in the example shown and, in that sense, preferred according to the invention, the swivelling axis 7 is arranged in the middle of the connection line between the axes of rotation 21 and 22. Since the lug of the lever 8A is not displaced during this sweep movement of the stand 9, as mentioned above but, remains stationary with respect to the stand 10, the counterclockwise displacement of the axes of rotation 21 and 22 causes the pressure/slide rods 5A and 6A to turn the adjustment levers 3A and 4A clockwise about the axes of rotation 21 or 22 of the rotary stretchers 1 and 2, i.e., the crown vectors A and B to turn clockwise by the same angle. An appropriate layout of this steering transmission manages to maintain the 90°-condition in each operating position of the separation device. For adjustment purposes, the length of the pressure/slide rods 5A and 6A can be changed. A relatively simple to achieve sweep of the support frame 9 thus effects a necessary synchronous turning of the crown vectors A and B while permanently maintaining the 90°-condition.
[0020] With the embodiment according to Figures 3A/B, the transmissions of each transmission pair are realized by respectively two wheels 8B and 3B, as well as a belt or a chain 5B, which continuously runs around both transmission wheels. At all angular positions of the support frame 9, the gearwheel 8B ist held unturnable with respect to the stand 10. Its axis is coaxially aligned with the swivelling axis 7 of the support frame 9. The gearwheel 3B and gearwheel 4B, not visible in the drawing, at the other front end of the roll is arranged with respect to the crown vector A or B of the first or second rotary stretcher in a position which is fixed with regard to the respecitve axis of rotation 21 and 22. During a sweep of the support frame 9, this transmission arrangement causes the crown vectors A or B of the two rotary stretchers 1 and 2 to be turned in the opposite direction with respect to the stand 10, with the transmission layout again being selected such that the 90°-condition is maintained in all swivel positions of the support frame 9.
[0021] In the embodiment according to Figures 4A/B, pure toothed gearings are used as gearings of the transmission pair. A transmission wheel 8C, in accordance with the manner in the example according to Figure 3A/B, is fixed with respect to the stand 10 and is attached coaxially to the swivelling axis 7 of the support frame 9. Also the gearwheel 3C, arranged coaxially to the axis of rotation 21 of the first rotary stretcher, and the gearwheel 4C, not visible in the drawing, at the other front end of the roll, as in the embodiment according to the Figures 3A/B, is arranged in a fixed manner with the arc, i.e., the crown vector A or B of the first or second rotary stretcher.
[0022] Instead of the belt or the chain 5B in the example according to the Figures 3A/B, in the example according to Figures 4A/B, there is a toothed wheel 5C or 6C, which is rotatably mounted at the free end of a one-armed lever 5D or 6D. The levers 5D or 6D are attached in a fixed manner at their other end coaxially to the swivelling axis 7 at the support frame 9. In the same way, basically, the transmission wheel 5C or 6C may be provided directly at the support frame 9 in a rotatable manner. In each case, the gearwheel 5C or 6C engages the gearwheel 8C as well as the gearwheel 3C or 4C of the accompanying transmission. Also, in the case of this transmission pair, a pivoting of the support frame 9 about its swivelling axis 7 leads to the point where the arcs, i.e., the crown vectors A and B of the first and second rotary stretcher, turn in opposite direction with respect to the stand 10, where, again, the transmission layout assures that the 90°-condition is maintained in all swivelling positions of the support frame 9.
List of reference numerals
[0023]
- 1
- roll
- 2
- roll
- 3A
- adjusting lever
- 3B
- gearwheel
- 3C
- gearwheel
- 4A
- adjusting lever
- 4B
- gearwheel
- 4C
- gearwheel
- 5A
- pressure/slide rod
- 5B
- belt or chain
- 5C
- gearwheel
- 6A
- pressure/slide rod
- 6B
- belt or chain
- 6C
- gearwheel
- 7
- swivelling axis
- 8A
- lever
- 8B
- gearwheel
- 8C
- gearwheel
- 9
- supporting frame
- 10
- stand
- 21
- axis of rotation
- 22
- axis of rotation
- 30
- material webs
- 30'
- partial webs
- 30''
- material webs (lap) rolled as a partial web
- 31'
- partial roll
- 31''
- partial roll
- 32
- first king roll
- 33
- second king roll
- 34
- roll
- 100
- separating device
- B1
- deflection line
- B2
- deflection line
- A
- crown vector
- B
- crown vector
- G'
- spacing gap
- G''
- spacing gap
with at least two rolls (1 and 2) which are essentially parallel to each other and are flexed essentially in the same direction,
with a stand (10) for the pivotable arrangement of at least two rolls (1, 2) about a common swivelling axis (7),
with a support frame (9) for the rotatable arrangement of at least the two rolls (1,
2) about their respective axis of rotation (21, 22) and for the horizontal sweep of
at least the two rolls (1, 2) with respect to the stand (10), about the common swivelling
axis (7),
characterized in that
at least one transmission pair (3, 5, 8; 8, 6, 4) for the simultaneous, automatic twisting of the deflection line (B1, B2) of at least the two flexed rolls (1, 2) during the horizontal sweep of the support frame (9) with respect to the stand (10) is provided in such a way, that the transmissions are necessarily operated by the sweep movement and that from at least the one transmission pair (3, 5, 8; 8, 6, 4) the one transmission (3, 5, 8) acts between the swivelling axis (7) of the support frame (9) and the axis of rotation (21) of the one roll (1) and the other transmission (8, 6, 4) acts between the swivelling axis (7) of the support frame (9) and the axis of rotation (22) of the other roll (2).
at least one adjustment lever (3A or 4A) each, pivotable about the axis of rotation (21 or 22), for twisting the deflection lines (B1 or B2) of the rolls (1 or 2),
at least one lever (8A), arranged in a fixed manner with respect to the stand, or a bearing element, arranged in a stationary or fixed manner at the stand for the purpose of interacting with the pivotable adjustement lever (3A or 4A) and
consists of pressure/slide rods (5A or 6A), connecting the free ends of the adjustement levers (3A or 4A), of each transmission (3, 5, 8; 8, 6, 4) to the free end of the lever (8A) or to the bearing element at the stand (10).
mit mindestens zwei im wesentlichen parallel zueinander angeordneten, im wesentlichen in die gleiche Richtung durchgebogenen Walzen (1 und 2),
mit einem Ständer (10) zur schwenkbaren Lagerung der mindestens zwei Walzen (1, 2) um eine gemeinsame Schwenkachse (7),
mit einem Traggestell (9) zur drehbaren Lagerung der mindestens zwei Walzen (1, 2)
um ihre jeweilige Drehachse (21, 22) und zum Verschwenken der mindestens zwei Walzen
(1, 2) bezüglich des Ständers (10) um die gemeinsame Schwenkachse (7),
dadurch gekennzeichnet,
daß zumindest ein Getriebepaar (3, 5, 8; 8, 6, 4) zum gleichzeitigen, selbsttätigen Verdrehen der Durchbiegungslinie (B1, B2) der mindestens zwei durchgebogenen Walzen (1, 2) beim horizontalen Verschwenken des Traggestells (9) bezüglich des Ständers (10) derart vorgesehen ist, daß die Getriebe durch die Verschwenkbewegung zwangsbetätigt werden und daß von dem mindestens einen Getriebepaar (3, 5, 8; 8, 6, 4) das eine Getriebe (3, 5, 8) zwischen der Schwenkachse (7) des Traggestells (9) und der Drehachse (21) der einen Walze (1) und das andere Getriebe (8, 6, 4) zwischen der Schwenkachse (7) des Traggestells (9) und der Drehachse (22) der anderen Walze (2) wirksam ist.
aus mindestens je einem um die Drehachse (21 bzw. 22) der Walze (1 bzw. 2) schwenkbaren Verstellhebel (3A bzw. 4A) zum Verdrehen der Durchbiegungslinien (B1 bzw. B2) der Walzen (1 bzw. 2),
aus zumindest einem bezüglich des Ständers fixierten Hebel (8A) oder aus einem ortsfest an dem Ständer angeordneten oder fixierten Lagerungselement zum Zusammenwirken mit dem schwenkbaren Verstellhebel (3A bzw. 4A) sowie
aus die freien Enden der Verstellhebel (3A bzw. 4A) jedes Getriebes (3, 5, 8; 8, 6, 4) mit dem freien Ende des Hebels (8A) oder mit dem Lagerungselement am Ständer (10) verbindenden Lenkern oder Druck-/Schubstangen (5A bzw. 6A)
bestehen.avec au moins deux rouleaux (1 et 2) qui sont essentiellement parallèles l'un à l'autre et qui sont fléchis essentiellement dans la même direction,
avec un montant (10) pour l'agencement pivotant d'au moins deux rouleaux (1, 2) autour d'un axe de pivotement commun (7),
avec un châssis de support (9) pour l'agencement tournant d'au moins deux rouleaux (1, 2) autour de leur axe de rotation respectif (21, 22) et pour le balayage horizontal des deux rouleaux précités (1, 2) par rapport au montant (10), autour de l'axe de pivotement commun (7),
caractérisé en ce qu'au moins une paire de transmissions (3, 5, 8 ; 8, 6, 4) pour la torsion automatique simultanée de la ligne de déflection (B1, B2) des deux rouleaux fléchis (1, 2) pendant le balayage horizontal du châssis de support (9) par rapport au montant (10) est réalisé de telle manière que les transmissions sont nécessairement amenées à fonctionner par le mouvement de balayage et que, parmi ladite, au moins une, paire de transmissions (3, 5, 8 ; 8, 6, 4), une transmission (3, 5, 8) agit entre l'axe de pivotement (7) du châssis de support (9) et l'axe de rotation (21) d'un rouleau (1) et l'autre transmission (8, 6, 4) agit entre l'axe de pivotement (7) du châssis de support (9) et l'axe de rotation (22) de l'autre rouleau (2).
d'au moins un levier (8A) agencé d'une manière fixe par rapport au montant, où un élément de palier agencé d'une manière stationnaire ou fixe au montant en vue d'une interaction avec le levier d'ajustement pivotant (3A ou 4A) et
constituées de tiges de pression/de coulissement (5A ou 6A), reliant les extrémités libres des leviers d'ajustement (3A ou 4A) de chaque transmission (3, 5, 8 ; 8, 6, 4) à l'extrémité libre du levier (8A) ou à l'élément de palier au montant (10).