EP0141258A2 - Winding apparatus for forming a cotton wool package - Google Patents

Abstract

A winding apparatus (1) for forming cotton rolls comprises a first winding roll (2), a second winding roll (3), a winding tube (4) and e.g. (four) calender rolls (5) to (8). Each calender roll is movably held at both ends by means of a pair of springs (10) receiving the calender roll. Each pair of springs (10) is firmly connected at one end to the bearing body (14) of the calender rolls and at the other end by means of a carrier (13) to the side walls of the winding apparatus. A piston (26) of a pneumatic cylinder (23) pushes the calender rolls from a rest position, in which a distance D or between the calender rolls. There is a distance E between the last calender roll (8) and the first winding roll (2) in a working position in which the calender rolls are pressed against each other without a warp path in between. The position of the calender rolls in the rest position is held by the pairs of springs (10).

Description

The invention relates to a winding apparatus for forming cotton rolls with at least one rotating winding roll and a certain number of calender rolls for compressing a layer of cotton into a rollable cotton web.

Cotton wraps serve as a template for the sweeping section and for the subsequent combing process.

Calender rollers are used to press a wad of cotton in order to be able to unwind the wad of cotton without mutual felting of the wad of cotton. In order to obtain a good pressing, the cotton web should be subjected to at least two pressings before the roll is formed.

The circumferential speed of the calender rolls can be increased somewhat from roll to roll in order to accommodate the lengthening of the cotton web caused by the pressing and to obtain a small stretching of the cotton web from press passage to press passage.

The stretching of the cotton web mentioned advantageously takes place with simultaneous contact of the cotton web with the respective calender roll, in order thereby to guide the fibers, i.e. to give a so-called stroking effect and a so-called spring back (also called breathing), i.e. to avoid partial destruction of a previous pressing.

Such calender roll arrangements can be seen from German Patent No. 644 119 or English Patent No. 711 599.

In these patents, calender rolls are stacked in a vertical arrangement. It is known that the calender rolls mentioned therein, in which the shaft positions were guided in slide rails, were supported on one another with their entire weight.

This arrangement had the disadvantage that when the rollers were possibly empty, i. without an interposed cotton web, on the one hand rubbing the rollers against one another according to the different peripheral speed and on the other hand when forming a cotton roll around a calender roller, i.e. in the event of a malfunction, the calender rolls had to be lifted apart in order to free the corresponding calender roll from the winding.

In order to remedy these two disadvantages or at least to a large extent to remedy them, an arrangement of the calender rolls was chosen in which two calender rolls Pairs are arranged side by side and the aforementioned vertical arrangement was only used per pair of rollers.

Such arrangements are shown in US Patent No. 25 02 894 and in German Patent No. 629 355.

The advantages achieved by the last-mentioned calender roller arrangement were, however, at least partially bought with the disadvantage mentioned that the cotton web was no longer guided in the drawing zone between the two roller pairs, which led to the "breathing" mentioned.

According to the invention, these disadvantages are eliminated in that the calender rolls are guided as defined in the characterizing part of the first claim.

The further advantageous embodiments are described in additional claims.

The advantages achieved by the invention are, on the one hand, the simple structure and the guidance of the calender rolls which does not cause friction.

Furthermore, a roll formed around a calender roll can be removed from the calender rolls which are at rest without further movement. Likewise, when the machine is at rest, the cotton can be inserted between the first two calender rolls and then by moving the calender rolls from the rest position to the work position in the work position before the calender rolls are started.

In the following, the invention is explained on the basis of drawings which only show execution paths.

• Fig. 1 einen Querschnitt entsprechend den Linien V, durch einen Teil eines Wickelapparates mit erfindungsgemässen Kalanderwalzen, halbschematisch dargestellt.
• Fig. 1A einen Teil von Figur 1, vergrössert dargestellt,
• Fig. 2 einen Schnitt in Pfeilrichtung I (Fig. 1) durch einen erfindungsgemässen Teil
• Fig. 3 und 4 Varianten des Wickelapparates von Figur 1,
• Fig. 5 bis 7 schematische Darstellung der Wickelapparate der Figuren 1, 3 und 4 mit einer aufgelegten Wattebahn,
• Fig. 8 eine Variante der Kalanderwalzen von Fig. 1,
• Fig. 8A einen Teil der Vorrichtung von Fig. 8, vergrössert und in Pfeilrichtung II (Fig. 8) in Draufsicht und im Schnitt dargestellt.
• Fig. 9 und 11 weitere Varianten der Kalanderwalzen von Fig. 1,
• Fig. 10 eine Variante der Kalanderwalze von Fig. 9
• Fig. 9A einen Teil der Vorrichtung von Fig. 9, vergrössert und in Pfeilrichtung III (Fig. 9) in Draufsicht und im Schnitt dargestellt,
• Fig. 11A einen Teil der Vorrichtung von Fig. 11 vergrössert und in Pfeilrichtung IV (Fig. 11) in Draufsicht und im Schnitt dargestellt,
• Fig. llB einen Teil der Vorrichtung von Fig. 11, vergrössert dargestellt,
• Fig. 12 eine Variante der Anordnung von Fig. 9 verkleinert und schematisch dargestellt,
• Fig. 13 eine Variante der Anordnung von Fig. 8, verkleinert und schematisch dargestellt,
• Fig. 14 eine Variante der Anordnung von Fig. 12, schematisch dargestellt,
• Fig. 15 eine Variante der Anordnung von Fig. 11, verkleinert und schematisch dargestellt.

Show it:

• Fig. 1 shows a cross section along lines V, through part of a winding apparatus with calender rolls according to the invention, shown semi-schematically.
• 1A shows a part of Figure 1, enlarged,
• Fig. 2 shows a section in the direction of arrow I (Fig. 1) through an inventive part
• 3 and 4 variants of the winding apparatus of Figure 1,
• 5 to 7 a schematic representation of the winding apparatus of FIGS. 1, 3 and 4 with a cotton web placed thereon,
• 8 shows a variant of the calender rolls of FIG. 1,
• 8A shows a part of the device from FIG. 8, enlarged and shown in the direction of arrow II (FIG. 8) in plan view and in section.
• 9 and 11 further variants of the calender rolls of Fig. 1,
• 10 shows a variant of the calender roll of FIG. 9
• 9A shows a part of the device of FIG. 9, enlarged and shown in the direction of arrow III (FIG. 9) in plan view and in section,
• 11A shows a part of the device of FIG. 11 enlarged and shown in the direction of arrow IV (FIG. 11) in plan view and in section,
• 11B shows part of the device of FIG. 11, enlarged,
• 12 shows a variant of the arrangement of FIG. 9 in a reduced size and shown schematically,
• 13 shows a variant of the arrangement of FIG. 8, reduced and shown schematically,
• 14 shows a variant of the arrangement of FIG. 12, shown schematically,
• Fig. 15 shows a variant of the arrangement of Fig. 11, reduced and shown schematically.

A winding apparatus 1 (FIG. 1) comprises a first winding roller 2 and a second winding roller 3 for receiving a winding tube 4, respectively the one that is accommodated on the tube 4 Winding (not shown).

Calender rolls 5 to 8 are arranged in front of the first winding roll 2, the calender roll 5 being referred to as the first, the calender roll 6 as the second, the calender roll 7 as the third and the calender roll 8 as the last calender roll.

The winder is covered by a hood 9.

The calender rolls 5 to 8 are each carried by means of two pairs of springs 10, which each consist of two spring struts 11 and 12 designed as leaf springs. Each pair of springs 10 is firmly connected on the one hand to a carrier 13 and on the other hand to a bearing body 14 receiving a shaft end of the calender rolls by means of screws 15. The carrier 13 is divided into a part 13A for receiving the screws 15 and a part 13B, which is provided with a connection surface 16 and with two threaded holes 17 for receiving screws 18 (FIG. 2).

By means of these screws 18, the carriers 13 are fastened to side walls 19 and 20 of the winding apparatus 1 in such a way that the connection surfaces 16 (FIG. 10) each abut these walls. Furthermore, the calender rolls are fastened to these walls 19 and 20 by means of these supports 13 such that the axes of rotation 21 of the calender rolls 5 to 8 each lie parallel to the rotation axis 22 of the first winding roll 2. In Figures 1 to 4 only one carrier 13 is shown per calender roll.

1 shows the calender rolls 5 to 8 in a rest position (also called a starting position), in which they have a mutual distance D of approximately 3 mm. A distance E provided between the last calender roll 8 and the first winding roll 2 in this rest position of the calender roll is also approximately 3 mm.

However, the invention is not limited to maintaining this 3 mm for the distances D and E, larger or possibly somewhat smaller distances can also be useful for the loosening of the winding on calender rolls. In this rest position, there is a balance between the sum of the spring forces per calender roll at both ends of the calender roll and the yalander roll weight.

_D is a spring legs 11 and 12 connected by means of screws 15 fixed to the supports 13 respectively with the bearing bodies 14, have a pair of springs that is known from the strength of materials'Rechteckfeder' characteristic, that is, the deflection characteristic corresponds approximately to the deflection characteristic of the 'rectangular springs' .

In order to maintain the aforementioned balance, the positions of the supports 13 on the side walls 19 and 20 are shifted until the desired distance D has the desired dimension over the entire length of the calender roll.

Smaller corrections of this position can subsequently be made possible by the holes 22 (FIG. 2) necessary for pushing through the screws 18. be chosen slightly larger than the diameter of the screws 18.

In order to move the calender rolls 5 to 8 from the rest position into a working position, which they lie against each other without an intervening wadding layer and in which the distance E is still approximately 0.2 mm, there is a pneumatic cylinder 23 on both sides of the calender rolls (in FIG. 1 and 2 only one is shown), and on the other hand a stop means 24 (FIG. 1, indicated by dash-dotted lines in FIG. 2) is provided on both sides of the calender rolls.

The cylinder 23 is supported on both sides of the calender rolls on a support 25 fastened to the corresponding wall 19 or 20 (FIG. 2, only indicated schematically in FIG. 1). On the other hand, a piston head 27 belonging to the piston 26 of the cylinder 23 bears against the leaf spring 11 relating to the calender roll 5.

The piston head 27 is designed to be U-shaped in order to be able to rest on both sides of the screw head of the screw 15 on the leaf spring 11, as shown in FIG.

The stop means 24 each consist of a support 28 fastened to the side wall 19 or 20 (FIG. 2, only shown schematically in FIG. 1) and an associated screw 29. This screw 29 serves, as can be seen from FIGS. 1 and 2, as a stop, by means of which the movement of the last calender roll 8 is stopped in such a way that said distance E does not become small in the working position of the calender rolls becomes less than approx. 0.2 mm, ie at least remains so that there is no contact between the calender roll 8 and the first winding roll 2. The head of the screw 15, the corresponding strut abuts the screw 29. The distance E can be adjusted by turning the screw 29.

FIGS. 3 and 4 show that the use of the spring-loaded calender roller guide means shown in FIG. 1 is not restricted to the arrangements shown in FIG. 1, but in a vertical arrangement (FIG. 3) or a horizontal arrangement (FIG. 4 ) can be used. The calender rolls in these figures are numbered in the same order as in FIG. 1.

The same applies to FIGS. 5 to 7, in which it is shown how a cotton web 30 is brought over the calender rolls 5 to 8 and then over the first winding roll 2 and finally to the winding tube 4.

FIGS. 8 to 11 show variants of the calender roll guide means according to the invention. The same elements therefore have the same reference numerals.

In FIG. 8, the bearing bodies 40 are guided in a guide track 41 (FIG. 8A, only indicated schematically in FIG. 8), consisting of an upper guide rail 42 and a lower guide rail 43.

The peripheral surface 44 of the bearing body 40 is accordingly adapted to the rails and is, for example, circular and has one for sliding between the This surface and the guide rails suitable fineness and width B (Fig. 8A).

In order to stabilize the calender rolls 5 to 8 guided by the guide track 41 in their longitudinal direction, the guide track 41 comprises a stop bar 45 (FIG. 8A).

In an arrangement of the calender rolls, as shown in FIG. 8, due to gravity, the calender rolls 5 to 7 tend to slide counterclockwise and the calender roll 8 clockwise in the guideway. In order to allow this only to a certain extent, in which the previously mentioned distances D and the distance E are approximately 3 mm, the bearing bodies 40 rest on pivot arms 46, the pivot arms being locked by abutments on latches 47 belonging to latches 47.

The swivel arms 46 are each pivotably mounted in the side walls 19 by a bolt 48 and are pivoted clockwise until the guideway is free in order to enable the introduction of the calender rolls or their bearing bodies 40 into the guideway 41. The latches 47 are therefore displaceably guided in the side walls 19 and 20 in such a way that they can be displaced from a starting position in which the stop lugs 49 rest against the side wall 19 and 20 in a working position in which the stop lug 49, as in FIG 8a, lies in front of the swivel arm 46, whereby the swiveling back of the swivel arm 46 in the clockwise direction is prevented.

The bolts 47 (only partially shown in FIG. 8) are further provided with a handle 50 (FIG. 8a) and with a stop (not shown). The latter serves for the correct positioning of the bolt and, in the working position of the bolt, rests on the outer surface 51 of the side wall 19, or on the outer surface 52 of the side wall 20.

The swivel arms 46 provided on both sides of the calender roller 8 require two stops, one of which is the bolt 47, and one spring 53 each, since the calender roller 8 moves downward in the guideway clockwise.

The spring 53 is a compression spring supported on a base 56 belonging to the side walls 19 and 20 (only indicated in FIG. 8) and urges the calender roller 8 in the guideway 41 counterclockwise into the rest position in which the swivel arm 46 on the nose 49 of the latch 47 abuts.

In this rest position of the calender roll 8, the distance E has a size of approximately 3 mm. The calender rolls 5, 6 and 7 are in the rest position due to the force of gravity (also called gravitation), which causes them to move in the counterclockwise direction in the guideway 41, by means of the swivel arms 46 on the lugs 49, the distances between the bars 47 being chosen in this way is that in this rest position, the distances D between the calender rolls are approximately 3 mm,

The working position of the calender rolls 5 to 8 is achieved in the manner described for FIGS. 1 and 2 by means of a cylinder 23 provided on both sides of the calender rolls. Accordingly no repetition of the elements and reference to the description section for FIGS. 1 and 2, ie the same elements are identified by the same reference numerals.

In the working position of the calender rolls of FIG. 8, the swivel arms 46 of the last calender roll each abut against a stop screw 54 in order to ensure that the distance E in this working position of the calender rolls is at least 0.2 mm. In this position, the swivel arms 46 assigned to the calender roll 8 are no longer in contact with the stop lugs 49, which also applies to the swivel arms which are assigned to the calender rolls 5, 6 and 7.

The stop screw 54 is each connected to the side wall 19 or 20 by means of a support 55, in which a thread is provided for receiving this screw, i. H. A swivel arm 46, a bar 47, a spring 53 and a stop screw 54 etc. are provided on each side of the calender rolls.

FIGS. 9 and 9a show a further variant, similar to the variant of FIG. 8 or 8a, in which the calender rolls move in the same way due to gravity and are locked or moved in the same way by stops or springs. Accordingly, elements with the same functions have the same reference numerals as in the descriptions of the previous figures. The essential difference from the arrangement shown in FIGS. 8 and 8a is the guidance of the calender rolls 5 to 8 by using them pendulum arms 60 are arranged pivotally. The pendulum arms 60 are pivotally attached to the side walls 19 and 20 by means of bolts 48 and accommodate the bearing bodies 61 of the calender rollers 5 to 8. The latches 47, the locking screws 54, the compression springs 53 and the cylinders 23 have the same functions with the associated accessories as in the arrangement shown in FIGS. 8 and 8a. Accordingly, the pendulum arms 60 assigned to the calender rollers 8 rest in the rest position as a result of the spring pressure of the spring 53 on the lugs 49 of the latches 47. At the same time, the pendulum arms 60 assigned to the calender rolls 5, 6 and 7 bear against the corresponding lugs 49 of the bars 47 as a result of the gravity of the calender rolls. In this rest position, the distances D and the distance E have the previously mentioned dimension of approx. 3 mm.

The displacement from this rest position into the working position in which the calender rolls, in the absence of a cotton web, lie against one another, as described for the arrangement of FIGS. 1 and 8, by means of the cylinders 23.

FIG. 10 shows a further variant of the calender roll guide in which the bearing bodies 61 are received by a resilient arm 70. This resilient arm 70 comprises a support beam 71 (not shown) fastened to the side walls 19 and 20, a support arm 72 and a leaf spring 73 connecting the support arm 72 to the support beam 71.

• 1. Art: Die Blattfeder hat eine Biegefestigkeit, welche derjenigen des Federpaares 10 der Anordnung von Figur 1 entspricht. Daraus folgt, dass der federnde Arm 70 in der für die Figur 1 beschriebenen Weise verwendet werden kann.
• 2. Art: Die Blattfeder wird bezüglich Biegefestigkeit lediglich derart gewählt, dass sie eine biegbare Verbindung zwischen dem Tragbalken 71 und dem Tragarm 72 ergibt, ohne in der Lage zu sein, dass Gewichtsmoment der Kalanderwalzen kompensieren zu können. Daraus folgt, dass der federnde Arm 70 in der für die Figur 9 beschriebenen Weise unter folgenden Bedingungen verwendet wird:
  • Der Abstand H muss in einer solchen Relation zur Dicke der Blattfeder stehen, dass im wesentlichen kein Ausscheren der Blattfeder durch das Abstützen der Kalanderwalzen auf der Nase 49 verursacht wird. Unter Ausscheren soll eine Biegung in der Blattfeder 73 verstanden werden, welche entstehen kann, wenn sich die einander gegenüberliegenden Flächen des Tragbalkens 71 und des federnden Armes 70 relativ zueinander verschieben.

Depending on the choice of the bending strength of the leaf spring 73, this resilient arm 70 can be used in the following 2 ways:

• 1. Type: The leaf spring has a flexural strength which corresponds to that of the pair of springs 10 of the arrangement of Figure 1. It follows that the resilient arm 70 can be used in the manner described for FIG. 1.
• 2. Type: The leaf spring is only selected with respect to bending strength in such a way that it results in a bendable connection between the support beam 71 and the support arm 72, without being able to compensate for the weight moment of the calender rolls. It follows that the resilient arm 70 is used in the manner described for FIG. 9 under the following conditions:
  • The distance H must be in such a relation to the thickness of the leaf spring that essentially no swinging out of the leaf spring is caused by the support of the calender rollers on the nose 49. Shear should be understood to mean a bend in the leaf spring 73, which can arise when the opposing surfaces of the support beam 71 and the resilient arm 70 shift relative to one another.

• Das Schwenken der Pendelarme 601 aus der Arbeitsposition in die Ruheposition, in welcher die Pendelarme 601 an den Anschlagnasen 49 der Riegel 47 anliegen, geschieht mittels eines Seilzuges 82. Dieser Seilzug 82 umfasst einen auf einer je zu den Wänden 19 respektive 20 gehörenden Basis 90 befestigten Pneumatikzylinder 83 mit einem Kolben 84, an welchem ein Zugseil 85 befestigt ist.

FIGS. 11 and 11a - and 11b, respectively - ultimately show a variant in the use of pendulum arms 601 which correspond to the pendulum arms 60 of FIG. 9, but are provided with an addendum to be described. Furthermore, this variant also includes Bolt 47 and the stop screw 54 used in the same manner as that described with Figures 8 and 9. The essential method difference from the arrangement shown with Figures 1, 8 and 9 is that the movement of the calender rolls from the rest position into the working position is not carried out by the cylinder 23, but by tension springs 80, which on the one hand with the pendulum arm 601 and on the other hand, are connected to a pillar 81 fastened to the side walls 19 and 20. Each tension spring 80 is dimensioned such that it is able to pivot the calender rolls from the rest position into the working position. In this working position, the pendulum arm 601 of the calender roller 8 bears against the stop screw 54. As described for the arrangement of FIGS. 1, 8 and 9, the elements on both sides of the calender rolls are also provided for the arrangement shown in FIG. This arrangement on both sides is briefly described below:

• The pivoting of the pendulum arms 601 from the working position into the rest position, in which the pendulum arms 601 rest against the stop lugs 49 of the latches 47, is carried out by means of a cable pull 82. This cable pull 82 comprises a base 90 fastened to a wall 19 and 20, respectively Pneumatic cylinder 83 with a piston 84 to which a traction cable 85 is attached.

This traction cable is guided from the piston 84 through eyelets 86 provided on the pendulum arms 601 and through a compression spring 87 provided after each eyelet and each via a roller 88 fitted between the compression springs 87 and the eyelets 86. The end of the traction cable 85 opposite the piston 84 becomes with connected to the end of the last compression spring 87 opposite the eyelet 86.

Between the compression springs 87 and the rollers 88, a driver 89 is firmly connected to the rope. The length of the piston stroke must be somewhat (e.g. 5 mm) longer than the sum of all distances D (analogous to Fig. 1,8,9) and the distance E, which for the sake of clarity are not entered in Figure 11.

• 1. Die Länge LD der letzten Feder 87, d. h. der der Kalanderwalze 8 zugeordneten Feder 87, muss mindestens dem 3-fachen Abstand D, und
• 2. die Länge LD der zweitletzten Feder 87 dem 2-fachen Abstand D,
• 3. die Länge LD der drittletzten Feder dem 1-fachen Abstand D entsprechen während
• 4. für die erste Feder, (resp. viertletzte) Feder, 87 die Länge LD Null sein kann. Das Letztere würde bedeuten, dass auf die Feder 87 der ersten Kalanderwalze 5 verzichtet werden könnte und der Mitnehmer 89 so positioniert werden kann, dass dieser bei Auflage des Pendelarmes 601 an der ersten Nase 49 an der Oese 86 anliegt. Andererseits muss der erste Abstand K (Fig. 11B) zwischen der ersten Feder 87, d. h. der der Kalanderwalze 5 zugeordneten Feder 87, und dem ersten Mitnehmer 89 dem 3-fachen Abstand D, der zweite Abstand K dem 2-fachen Abstand D und der dritte Abstand K dem 1-fachen Abstand D entsprechen muss. Dass der letzte Abstand K Null ist, ist dadurch gegeben, dass das Ende des Zugseiles 85 mit dem von der Oese abgewendeten Ende der Druckfeder 87 verbunden ist.

The spring characteristic (ie the relation of the change in spring length to the change in spring force) of the springs 87 must be dimensioned such that their compressible length LD (FIG. 11b) fulfills the following conditions:

• 1. The length LD of the last spring 87, ie the spring 87 assigned to the calender roll 8, must be at least 3 times the distance D, and
• 2. the length LD of the second last spring 87 is twice the distance D,
• 3. The length LD of the third to last spring corresponds to 1 times the distance D during
• 4. for the first spring, (respectively fourth last) spring, 87 the length LD can be zero. The latter would mean that the spring 87 of the first calender roll 5 could be dispensed with and the driver 89 can be positioned such that when the pendulum arm 601 rests on the first nose 49 on the eyelet 86. On the other hand, the first distance K (FIG. 11B) between the first spring 87, ie the spring 87 assigned to the calender roll 5, and the first driver 89 must be three times the distance D, the second distance K twice the distance D and third distance K must correspond to 1 times the distance D. That the last distance K is zero is given by the fact that the End of the pull cable 85 is connected to the end of the compression spring 87 facing away from the eyelet.

Furthermore, the spring forces of the compression springs 87 must be greater than the spring forces of the tension springs 80 so that a displacement of the calender roll from the working position to the rest position is ensured.

The advantage of the arrangement shown in FIG. 11 is that the contact pressure between the calender rolls can be selected in accordance with the selection of the tension spring characteristic. FIG. 12 shows a variant of FIG. 9 and since it is only a different arrangement of the same elements, the elements have the same reference numerals as in FIG. 9. In this arrangement, the calender rolls 5 to 8 by means of the pendulum arms 60 in the rest position freely suspended. In order to move the calender rolls into the previously described working position, the cylinder 23 is activated, as described with FIG. 9, until all the calender rolls abut one another and the pendulum arms 60 assigned to the calender roll 8 bear against the stop screw 54 by the described one, which is no longer shown here Bring distance E to the desired size of 0.2 mm.

In this respect, FIG. 13 shows a variant of the arrangement shown in FIG. 8, in which the guideway 41 is shifted downwards until all the calender rollers in the guideway slide downward in the same direction by means of their gravity. This makes it possible to dispense with the compression spring 53 shown in FIG. 8. Also in this figure are there are the same elements as in Fig. 8, using the same reference numerals.

The variant shown in FIG. 14 is a similar arrangement to that in FIG. 12, with the only difference that the calender rolls are not arranged in a horizontal but in a rising straight line. The advantage of this arrangement over that of FIG. 12 is that it is more space-saving. The elements are the same as in Fig. 12 respect. 9, so that the same reference numerals have also been used here. 15 shows a variant of the with

11 shows the arrangement shown, in which, on the one hand, the cable pull 82 pulls the calender rolls from the rest position into the working position and, on the other hand, that the last calender roll 8 is arranged freely suspended. This rearrangement has the advantage over that of FIG. 11 that the tension springs 80 can be dispensed with.

The cable pull 82, in exactly the same way as described for FIG. 11, has a pull cable 85, the tension springs 87, the rollers 88 and the drivers 89.

In addition, the distances between the drivers 89 and the compression springs 87 described for FIG. 15 are provided in the same sense.

Ultimately, the calender rolls are also in this

Figure in the working position when all the calender rollers lie against each other and the pendulum arms 60 associated with the last calender roller rest against the locking screw 54.

Since this figure is the same element As in the elements used in the arrangement designated by FIG. 11, the same reference numerals have been used and, for the sake of clarity, certain reference numerals have not been used.

Claims (20)

1. winding apparatus for forming cotton rolls with at least one rotating winding roll and a certain number of calender rolls for compressing a layer of cotton into a rollable cotton web,
characterized,
that the calender rolls can be moved within a given range by means of guide means. 2. winding apparatus according to claim 1,
characterized,
that said area is delimited by a rest position and by a working position of the calender rolls. 3. winding apparatus according to claim 1 and 2,
characterized,
that the guide means automatically move the calender rolls into the rest position. 4. winding apparatus according to claim 1 to 3,
characterized,
that the leadership means are means of strength. 5. winding apparatus according to claim 1 to 4,
characterized,
that the guide means are a pair of springs, with two individual springs held at a distance from one another, one end of the pair of springs stationary and the other end is connected to components of the calender roll. 6. winding apparatus according to claim 1 to 5,
characterized,
that the pair of springs comprises two leaf springs, which are firmly connected on the one hand to a fixed support and on the other hand to the bearing bodies of the calender rolls. 7. winding apparatus according to claim 1 to 3,
characterized,
that at least one force means acting on the guide means moves the calender rolls into the working position. 8. winding apparatus according to claim 1 to 3,
characterized,
that the guide means are a combination of guide elements and power means. 9. winding apparatus according to claim 8,
characterized,
that the guide elements are a guide track for the indirect reception of the calender rolls and two swivel arms per calender roll, which can be positioned by locking means, for the indirect positioning of the calender rolls in the rest position. 10. winding apparatus according to claim 8,
characterized,
that the guide elements to swing arms on Include the calender rolls, which can be positioned by means of detents for positioning the calender rolls in the rest position. 11. winding apparatus according to claim 8,
characterized,
that the force means for moving the calender rolls into the rest position are the gravity of the individual calender rolls. 12. winding apparatus according to claim 8,
characterized,
that the force means for moving the calender rolls into the rest position are the gravity of the calender rolls and / or springs. 13. winding apparatus according to claim 8,
characterized,
that the power means for moving the calender rolls into the rest position is a cable pull pulled by a drive means. 14. winding apparatus according to claim 7,
characterized,
that the power means is a driving means. 15. winding apparatus according to claim 13,
characterized,
that the drive means is a pneumatic cylinder. 16. winding apparatus according to claim 14,
characterized,
that the drive means is a pneumatic cylinder. 17. winding apparatus according to claim 7 and 10,
characterized,
that the power means are two springs provided per calender roll and acting on the pendulum arms. 18. winding apparatus according to claim 2,
characterized,
that the calender roller delivering the cotton layer to the winding roller is held in its working position by a lock. 19. winding roller for forming cotton wafers with at least one rotating winding roller and a certain number of calender rollers for compacting a cotton layer to form a windable cotton web,
characterized,
that the calender rolls are arranged in a crescent shape around the winding rolls and can be moved from a rest position into a working position within a given area by means of guide means. 20. winding apparatus according to claim 19,
characterized,
that the winding rollers in the rest position are at a mutual distance and the next calender roller is at a distance from the winding roller of 2-5 mm, preferably 3 mm
and that in the working position the calender rolls are pressed against each other and the distance between the last calender roller and the winding roller is reduced to a minimum such that there is no contact between this last calender roller and the winding roller even without a cotton layer.

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