EP0833795A1

EP0833795A1 - Pressure roller system for a winding machine

Info

Publication number: EP0833795A1
Application number: EP97916365A
Authority: EP
Inventors: Reinhard Hehner; Georg Müller; Hans-Friedrich Peters
Original assignee: Jagenberg Papiertechnik GmbH
Current assignee: Voith Paper Jagenberg GmbH
Priority date: 1996-04-19
Filing date: 1997-03-19
Publication date: 1998-04-08
Also published as: JPH11508217A; WO1997039971A1; CA2225068A1; US5853139A

Abstract

In winding machines for producing rolls (3), pressure roller systems are known which have a horizontal, vertically movable cross-head (8) to which a series of freely rotatable and individually movable roll segments (9) are secured side-by-side and with bolts parallel to the cross-head (8). In addition, there are means for adjusting the pressure exerted by the roll segments (9) on the rolls (3). According to the invention, into the bearing of each roll segment (9) on the cross-head (8) is integrated a component which either increases the bearing pressure as the distance between the roll segment (9) and the cross-head with an application force increasing depending on the distance or reduces said pressure as the distance increases with an increasing counter-force depending on the distance. Thus on the one hand the most uniform possible pressure on all rolls (3) is ensured and on the other negative effects owing to excessive differences in diameter between the rolls (3) are prevented.

Description

DESCRIPTION

Pressure roller system for a winding machine

Technical field

The invention relates to a printing roll system for a winding machine for winding material webs, in particular paper or cardboard webs divided by longitudinal cuts, according to the preamble of claim 1 and a winding machine with a pressure roller system according to the invention.

State of the art

For the winding of paper or cardboard webs into winding rolls, carrier roll winding machines are known which have two driven carrier rolls, on which the winding rolls rest next to one another with aligned sleeves during winding. Above the roller bed formed by the support rollers, a pressure roller system is arranged, which consists of a continuous pressure roller or of individual pressure roller segments, which can be moved horizontally, vertically

Traverse are attached. The pressure roller system is used to press the winding rollers from the top at the start of winding, so as to increase the line load on the contact lines between the winding rollers and the support rollers. The winding hardness of the winding rolls is decisively influenced by the line load. At the start of winding, the line load from the support weight of the winding rolls is not yet sufficient, so an additional contact pressure is applied by means of the pressure roll system, which is correspondingly reduced as the winding roll weight increases during winding. Since, when winding paper or cardboard webs divided by a longitudinal cut, transverse profile fluctuations in the web lead to different winding reel diameters, this means that with a continuous pressure roller this does not partially rest on winding rollers with a smaller diameter. To solve this problem, a generic pressure roller system is known from WO 93/15009, in which a number of freely rotatable roller segments are fastened next to one another and individually vertically movable on a crossbar. Each roll segment can thus adapt to the diameter of the winding roll below it. So that the contact pressure caused by the contact weight of the pressure roller system is the same for each roller segment, the roller segments are each mounted on a hydraulic piston-cylinder unit, which are connected to one another in a closed system.

In practice, it has been shown that this system, which is advantageous per se, reaches its limits when winding webs with a thickness that varies over the width. Since the pressure roller segments press against the winding rollers with the same contact pressure regardless of the winding roller diameter, the differences in diameter between the winding rollers become larger and larger. Due to the fact that all winding rolls are driven at the same path speed (= peripheral speed of the support roller), a different winding roll diameter also results in a different rotation speed; d. H. Smaller diameter reels are turned faster. A different speed of rotation of two adjacent winding rolls causes friction on the adjacent end faces, which can lead to undesirable effects such as markings, burn marks and, in extreme cases, to roll ejection if adjacent winding rolls with different diameters get caught.

Presentation of the invention

The invention has for its object to provide a pressure roller system that on the one hand ensures the most uniform contact pressure on all winding rolls, on the other hand avoids negative effects due to large diameter differences. This object is achieved with the features of patent claim 1.

According to the invention, each roller segment has an element which is integrated into its vertical bearing and which influences the contact pressure as a function of its distance from the crossmember. The contact pressure is either reduced as the distance from the crossbar increases, or it is increased as the distance decreases. As a result, a growing difference in diameter from the mean diameter of the other winding rolls is counteracted by winding either tighter or less tightly.

The subclaims contain preferred, since particularly advantageous, embodiments of the invention.

Brief description of the drawing

The drawing serves to explain the invention using two simplified exemplary embodiments. Show it:

FIG. 1 shows the side view of a carrier roller winding machine with a pressure roller system according to the invention,

FIG. 2 shows a section of a cross section through the pressure roller system,

FIG. 3 shows a section of a longitudinal section,

Figure 4 shows a detail of a longitudinal section through a further embodiment.

Ways of Carrying Out the Invention

The carrier roller winding machine shown in FIG. 1 has two driven carrier rollers 1, 2, which form a roller bed in which the winding rollers 3 rest on the carrier rollers 1, 2 during winding. The paper or cardboard web 4 is divided by a slitter 5 into individual webs, which are then through the nip between the support rollers 1, 2 into the roller bed, where they are wound onto aligned sleeves. The winding machine also has the known elements for removing full winding rolls 3 and for inserting new sleeves (ejection bar 6, winding roll lowering table 7).

Above the roller bed, a pressure roller system is arranged in the frame of the winding machine, with which the bearing weight of the winding rollers 3 on the support rollers 1, 2 can be increased at the beginning of the winding if the dead weight of the winding rollers 3 is not yet sufficient for the desired winding hardness.

The pressure roller system consists of a horizontal crossmember 8 which runs transversely to the web running direction and is mounted such that it can move vertically. On the underside of the crossmember 8, a number of roller segments 9, which are arranged closely next to one another with axes parallel to the crossmember 8, are fastened, which rest on the winding rollers 3 when the crossmember 8 is lowered. With a working width of the machine of approx. 8 m, the axial length of a segment is approx. 100 mm, its diameter approx. 260 mm. By means of a hydraulic piston-cylinder unit 10 arranged on each side of the machine, the traverse 8 with the roller segments 9 can be moved up to a rest position. At the same time, the contact pressure of the roller segments 9 on the winding rollers 3 can be adjusted with the piston-cylinder units 10 by relieving the weight by pressure from below.

The construction of two embodiments of a pressure roller system according to the invention is shown in more detail in FIGS. 2, 3 and 4:

In all embodiments, the traverse 8 is designed as a hollow profile, which has a row of openings on its underside over its length <- working width of the machine), through which a fastening rod 11 is guided outwards, at the lower end of which a bearing shell 12 for a roller segment 9 is attached. In each of the downwardly open bearing shells 1 2, a roller segment 9 is freely rotatable.

Each roller segment 9 preferably consists of a hollow cylindrical support body made of a solid material, in particular steel, on its outer lateral surface a limitedly deformable layer 28 of a cellular plastic material with a multiplicity of uniformly distributed pores is applied. The plastic material consisting of a cellular elastomer, in particular polyurethane, has a compression modulus K of less than 10 MPa, preferably between 1 MPa and 5 MPa. The size of the pores is less than 5 mm, preferably between 0.05 and 1 mm. The pores in the deformable layer are preferably partially open - that is, connected to one another - and partially closed. The proportion of open pores is 30% to 70%, preferably approximately 50%. The ratio of the open pores to the closed pores determines both the compressibility and the ability of the layer to dissipate heat generated inside in order to avoid undesired

Avoid overheating. The density of the plastic material is between 350 kg / m ³ and 700 kg / m ³ . The thickness of the layer 28 formed from it is 8 mm - 40 mm, preferably 10 mm - 20 mm, in the example about 15 mm. A compressible layer 28 with the above features has proven to be particularly suitable for applying the required contact pressure without markings on the

Winding rolls 3 under different operating conditions, e.g. B. profile fluctuations in the web 4, apply.

Instead of a layer 28 made of a compressible material, a covering made of a rubber-elastic material can also be applied to the outer lateral surface of the support body. Then a material with a hardness of 60 - 90 Shore A is used, in the outer running layer of which are incorporated all-round, self-contained, i.e. concentrically running grooves, so that a softer running surface is created and the air can escape. The webs between the 1, 5 to 2 mm wide and approx. 2 mm deep grooves have a maximum width of 3 mm. The thickness of the layer of the rubber-like material is also 8 mm to 40 mm, preferably 10 mm to 20 mm.

Outside (FIG. 2, 3) or inside (FIG. 4) of the cross member 8, each fastening rod 11 for a roller segment 9 is guided in a vertical, non-rotatable linear guide 13, which is fastened to the cross member 8: in the embodiment according to FIGS. 2 and 3, the linear guides 13 are fastened to the underside of the crossmember 8, in the embodiment according to FIG. 4 inside the hollow profile on a longitudinal wall. The linear guide 13 preferably contains an under Preload mounted ball bearing so that their two parts are mounted so that they can move vertically relative to each other without play. The upper end of each fastening rod 11 is fastened within the cross member 8 to a double-acting piston-cylinder unit arranged vertically there. The piston-cylinder units are double-acting membrane cylinders, each of which has a chamber 16 with a liquid, for. B. hydraulic oil is filled, so it can be acted upon by a hydraulic pressure. The liquid-filled chambers 16 of all cylinders 14 are connected to one another in a closed system via lines 17, so that the same liquid pressure always prevails in each chamber 16. An expansion tank 18 is connected to the closed line system 17 via a valve 19, into which liquid can flow out of the closed system when the valve 19 is opened. The liquid pressure in the chambers 16 thus supports the roller segments 9 when resting on the winding rollers 3 against the crossmember 8. It transmits the bearing weight of the pressure roller system (reduced by the piston-cylinder units 10 to the desired extent) and thus generates the desired contact pressure of the segments 9 on the winding rollers 3, all segments 9 remaining at the same contact pressure until the correction system described below intervenes.

In the embodiment according to FIGS. 2 and 3, the pistons 15 of the piston-cylinder units are each screwed with their ends fixed to the upper wall of the crossmember 8. Each cylinder 14 of a unit is vertically movable to a limited extent, so that the distance of a roller segment 9 from the crossmember 8 can be set individually.

In the embodiment according to FIG. 4, each cylinder 14 of a unit is screwed with its upper end to the horizontal leg of an angle iron 25, the other leg of which is screwed to the inside of the longitudinal wall of the crossbar 8. In this embodiment, the movable piston represents the mounting rod 1 1, to which a roller segment 9 is attached. The linear guide 13 is located on the inside of the angle iron 25. The holder 27 for the bearing shell 12 of a roller segment 9 is fastened to its movable part 26 in order to ensure a vertical, rotationally secure linear movement. The correction system consists of elements integrated into the bearing for the vertical movement of each roller segment 9 on the crossmember 8, which act in such a way that either when the distance 9 of a segment 9 from the crossmember 8 decreases, the contact pressure on the winding rollers 3 is increased by a distance-dependent increasing additional force , or as the distance increases, the contact pressure is reduced by a distance-increasing counterforce.

In the exemplary embodiment according to FIGS. 2 and 3, the correction system consists of compression springs 20, the piston rod 15 being arranged circumferentially in this area between the cylinders 14 and the upper wall of the crossmember 8. Each compression spring 20 thus counteracts a movement of the associated segment 9 toward the crossmember 8 with a force which increases as a function of the path. This counteracts large diameter differences in the winding rolls 3 for the following reasons:

Due to the closed hydraulic system of the chambers 14, a relative increase in a winding roll diameter (for example, due to a transverse profile fluctuation of the web 4) leads to a relative movement of the roll segments 9 lying on the crossbar 8. The compression spring 20 counteracts this movement with increasing force, i. H. in addition to the hydraulic pressure, which is the same for all segments 9, the spring force of the compression springs 20 also increases the contact pressure on the winding roller 3 with these segments 9 pushed upwards. Depending on the diameter difference, the increased contact pressure means that the winding is firmer and counteracts a further increase in the diameter difference. The size of the counteracting force per deflection path can be adjusted by choosing the spring constants so that the

Correction only intervenes if there are negative diameter differences in order to achieve a uniform winding hardness in the range of acceptable differences with a uniform contact pressure.

Alternatively, it is also possible to fasten the spring 20 at both ends to the upper wall of the crossmember 8 and to the cylinder 14, so that it acts as a tension spring against movement of the associated segment 9 with a force that increases as a function of the path. The result is that winding rolls 3 with a relatively smaller diameter are wound softer, that is, their diameter increases relatively. This also works undesirable large difference between the diameters of two adjacent winding rolls 3.

In the embodiment according to FIG. 4, the compression spring 20 is arranged between the horizontal leg of the angle iron 25 and the movable part 26 of the linear guide 13 and thus counteracts a relative movement of the roller segments 9 towards the cross member 8 with increasing force.

If a roller segment 9 is located - as shown in FIG. 2 for the right segment - above a longitudinal section, that is to say in the region of two winding rollers 3, it must be deactivated by lifting it in order to wind these formats. The same applies to segments 9 which are outside the web width when processing narrower webs 4. In the double-acting piston-cylinder units according to the exemplary embodiments, the second chamber 21, which is not loaded with liquid, can advantageously be used to carry out the inactivating lifting movement of a segment 9.

Every second chamber 21 of a cylinder 14 is connected to its own pressure line 22 with a valve 23, via which a pressure medium, preferably compressed air, is supplied from a common source 24 and at the same time the pressure can be released from the chamber 21. An increase in pressure in the chamber 21 leads to a lifting of the segment 9 if the hydraulic pressure in the other chamber 16 is lower.

The use of double-acting piston-cylinder units makes it possible to carry out the correction function instead of using springs 20 by correspondingly controlling the pneumatic pressure in the chambers 21. In this alternative embodiment, not shown in the figures, the pressure roller system contains a control device which controls the pneumatic counterpressure in the chambers 21 as a function of the path. For each roller segment 9, the back pressure in the associated chamber 21 is controlled depending on the path so that when the distance of the roller segment 9 from the crossmember 8 decreases, the back pressure is reduced in order to increase the contact pressure of the roller segments 9, or with increasing distance by increasing the back pressure the contact pressure of the roller segments 9 is reduced depending on the route. In the embodiment according to FIG. 4 with a lower pneumatic chamber 21, with a relative movement of the roller segments 9 downwards - that is to say with an increasing distance of the segments 9 from the cross member 8 - the pneumatic pressure acting upwards in the chamber 21 would be increased by the contact pressure of segments 9 to decrease.

The setting of the system, including the activation of the desired segments 9, is carried out as follows at the start of the rewind:

First, when the valve 19 is open, that is to say when the hydraulic system is open to the expansion tank 18, each cylinder 14 is moved completely upward by supplying compressed air into the chamber 21 against the pressure of the spring 20, so that all the segments 9 are in the upper, inactive position .

The valves 19 of the segments 9 to be activated are then opened. Their chambers 16 are filled with hydraulic fluid to such an extent that the segments 9 lower into a middle working position of the adjustment path. The valves 19 are then closed. The crossbeam 8 with the segments 9 is then lowered onto the new sleeves for the winding rolls 3, which have meanwhile been inserted into the winding machine. The segments 9 initially support the winding of the web starts on the new sleeves and then produce the desired line pressure on the contact lines between the support rollers 1, 2 and the winding rollers 3.

The required contact pressure, which decreases as the winding roll diameter increases, is controlled depending on the winding roll diameter via the lateral piston-cylinder units 10 which counteract the weight of the pressure roll system.

Claims

PATENT TO PRÜCHE

1.

Pressure roller system for a winding machine for the production of winding rollers (3) with a horizontally running and vertically movable crossbar (8), to which a number of freely rotatable and individually vertically movable roller segments (9) are fastened next to one another and with axes parallel to the crossbar (8) , And with means for adjusting the contact pressure of the roller segments (9) on the winding rollers (3), characterized in that an element is integrated in the storage of each roller segment (9) on the crossmember (8), which either with decreasing distance of the roller segment (9) of the crossbeam (8) increases the contact pressure with the distance-increasing additional force or decreases the contact pressure with increasing distance with the distance-dependent increasing counterforce.

Second

Pressure roller system according to claim 1, characterized in that each roller segment (9) is mounted on the crossmember (8) via a vertical linear guide (13).

Third

Pressure roller system according to claim 1 or 2, characterized in that for each roller segment (9) a compression spring (20) counteracts the movement towards the crossmember (20).

4th

Pressure roller system according to claim 1 or 2, characterized in that in each roller segment (9) a tension spring counteracts the movement away from the crossmember (8). Pressure roller system according to one of claims 1 to 4, characterized gekenn¬ characterized in that the contact pressure is generated by the weight of the pressure roller system and each roller segment (9) is supported by a hydraulic piston-cylinder unit (14) on the crossmember (8).

6th

Pressure roller system according to claim 5, characterized in that the liquid-filled chambers (16) of all piston-cylinder units (14) of the roller segments (9) are connected to one another in a closed system.

7.

Pressure roller system according to claim 5 or 6, characterized in that the roller segments (9) are fastened to double-acting piston-cylinder units (14), the second chamber (21) of which can be acted upon separately with pressure, preferably with air pressure.

8th.

Pressure roller system according to claim 7, characterized by a control device which controls the pneumatic pressure in every second chamber (21) in a way that either reduces the pneumatic counterpressure by the contact pressure when the distance of the roller segment (9) from the crossmember (8) decreases to increase the roller segments (9), or as the distance increases, a back pressure increases depending on the distance in order to reduce the contact pressure of the roller segments (9).

9th

Pressure roller system according to one of claims 1 to 8, characterized gekenn¬ characterized in that each roller segment (9) on its outer lateral surface a deformable layer (28) made of a cellular plastic material with a plurality of evenly distributed pores and a compression module K of less than 10 MPa having. Pressure roller system according to claim 9, characterized in that the layer (28) consists of a cellular elastomer, in particular polyurethane, with a compression modulus K between 1 MPa and 5 MPa.

11th

Pressure roller system according to Claim 9 or 10, characterized in that the size of the pores is less than 5 mm, preferably between 0.05 mm and 1 mm.

12th

Pressure roller system according to one of claims 9 to 11, characterized gekenn¬ characterized in that the pores in the layer (28) are partially open and partially closed, the proportion of open pores 30% to 70%, preferably about 50%, is.

13th

Pressure roller system according to one of claims 1 to 8, characterized gekenn¬ characterized in that each roller segment (9) on its outer surface has a deformable layer of a rubber-like material with a hardness between 60 Shore A and 90 Shore A, in the tread circumferential grooves are incorporated .

14. Pressure roller system according to claim 13, characterized in that the width of the webs between the grooves is a maximum of 3 mm.

15th

Pressure roller system according to one of Claims 9 to 14, characterized * in that the thickness of the layer (28) is 8 mm to 40 mm, preferably 10 mm to 20 mm.

16th

Pressure roller system according to one of Claims 1 to 15, characterized in that a piston-cylinder unit (10) pulling from above or pressing from below acts laterally on the crossmember (8).

17th

Carrier roller winding machine for winding a material web (4), in particular paper or cardboard web, divided by longitudinal cuts, with two driven, parallel carrier rollers (1, 2), between which a roller bed is formed, on which the winding rollers (3) are coiled during winding aligned axes, characterized in that a pressure roller system according to one of claims 1 to 16 is arranged in the frame of the winding machine above the roller bed.