Device for pressing a thread onto a spool

Abstract

Device (1) for pressing a thread (2) onto a spool (3), comprising a pressure roller (4) and a roller carrier (7), wherein the pressure roller (4) has a first end (20) with a first bearing section (6) which is mounted in a first receptacle (8) of the roller carrier (7), and a second end (21) with a second bearing section (22) which is mounted in a second receptacle (8) of the roller carrier (7), and a thread guide section (5) formed between the bearing sections, wherein the pressure roller (4) has a bearing (9, 39) with an outer surface (10) in the region of the first and the second bearing sections (6, 22), wherein at least one spring-damper element (11, 23) is arranged on the outer surface (10) of the bearings (9), wherein the pressure roller (4) is rotatably connected with the bearings (9) and the spring-damper elements (11, 23). 23) are mounted in the receptacles (8, 38) of the roller carrier (7) and wherein each spring-damper element (11, 23) is formed,to fix the pressure roller (4) radially and axially relative to the roller carrier (7) with an elastic stiffness, wherein a first spring-damper element (11) is arranged in the first bearing section (6) and a second spring-damper element (23) is arranged in the second bearing section (22), and wherein the first spring-damper element (11) has a lower elastic stiffness than the second spring-damper element (23).

Description

[0001] The present invention relates to a device for pressing a thread onto a spool. Furthermore, the invention relates to a winding machine with a device according to the invention. The present invention finds particular application in the production of synthetic threads.

[0002] DE 196 32 748 A1 discloses a winding machine with a pressure roller mounted on a movable roller support. During winding of the threads, the pressure roller rests against the surfaces of the bobbins clamped on a driven bobbin mandrel and guides the threads to the surface of the bobbins. At the same time, the speed of the pressure roller is used to control the bobbin mandrel drive in order to maintain a constant peripheral speed of the continuously growing bobbins. To achieve a uniform bobbin build, the pressure roller is held against the surfaces of the bobbins with a predetermined contact force. To dampen the vibrations resulting from the driven bobbin mandrel, the bearings of the pressure roller are equipped with a damping means. O-rings are used as damping means to support an outer ring of a bearing against the roller support.However, such rubber elements have spring-damper characteristics that fluctuate significantly over their lifetime due to aging. It should also be noted that the rubber elements are typically guided in grooves, so that the damping element, consisting of several adjacent rubber elements, has a certain width, which results in a relatively high pitch stiffness. Due to the clamping between the pressure roller and the roller support, the absorption of the rubber element also depends on the relative position of the pressure roller to the roller support, so that the stiffness of the rubber element is not constant and can fluctuate greatly. It has now been observed that the vibrations occurring during winding of the coils and the loads on the pressure roller can lead to constant or time-varying misalignments of the center axes between the roller support and the bearing of the pressure roller.However, due to the high and fluctuating pitch stiffness of the rubber elements, such misalignments of the center axes cause a very uneven load on the raceways of the multi-row bearings. Furthermore, the known O-rings are not suitable for securing the pressure rollers axially relative to the roller support, i.e., parallel to a rotational axis of the pressure roller. Therefore, in the known devices for pressing a thread, the pressure rollers must be mounted on the roller support with at least one fixed bearing. This has the disadvantage that there is a rigid connection between the pressure roller and the roller support, at least in one axial direction of the pressure roller. As a result, the stiffnesses of the rubber elements on both sides of the pressure roller can vary greatly. This has a very negative impact on the stability of the spool mandrel and promotes subharmonic, self-excited wobbling of the spool mandrel.In principle, two rotating bodies rolling on each other tend to self-excite, so that in the operating range of the pressure roller the damping generated should always outweigh the excitation.

[0003] The object of the invention is therefore to at least partially solve the problems described with reference to the prior art and, in particular, to provide a device for pressing a thread against a bobbin, with which vibrations on a pressure roller can be dampened particularly effectively. Furthermore, a winding machine is to be provided that has a device for pressing a thread against a bobbin, with which vibrations on a pressure roller can be dampened particularly effectively.

[0004] These objects are achieved with a device according to the features of patent claim 1 and a winding machine according to the features of patent claim 12. Further advantageous embodiments of the invention are specified in the dependent claims. It should be noted that the features listed individually in the dependent claims can be combined with one another in any technologically expedient manner and define further embodiments of the invention. Furthermore, the features specified in the claims are further specified and explained in the description, with further preferred embodiments of the invention being presented.

[0005] The device according to the invention for pressing a thread onto a spool comprises a pressure roller and a roller support. The pressure roller has a first end with a first bearing section, which is mounted in a first receptacle of the roller support, and a second end with a second bearing section, which is mounted in a second receptacle of the roller support. A thread guide section is located between the bearing sections. In the region of the first and second bearing sections, the pressure roller has a bearing with an outer surface, with at least one spring-damper element arranged on the outer surface of the bearing. The pressure roller is rotatably mounted with the bearings and the spring-damper elements in the receptacles of the roller support, with each spring-damper element being designed to fix the pressure roller radially and axially with elastic rigidity relative to the roller support.

[0006] The threads to be pressed are in particular synthetic threads that are wound onto a spool at a speed of up to 7,000 m / min. The pressure roller is preferably made of metal and has a rotationally symmetrical cross-section. The pressure roller can be made from either a solid material or a hollow profile. The pressure roller has a thread guide section on its surface, which is a region of the pressure roller with which the thread is guided or pressed against a surface of a spool. The pressure roller has a diameter of 50 mm to 150 mm, preferably 70 mm to 100 mm, in the region of the thread guide section. The thread guide section has an axial length of 600 mm to 2400 mm. In addition, the pressure roller has at least one bearing section, which is preferably designed in the manner of a bearing journal.The at least one bearing section has a length of 20 mm to 50 mm, preferably 30 mm to 50 mm, in an axial direction of the pressure roller. The roller support is also made of metal and has at least one receptacle for the pressure roller. The roller support is preferably designed as a rocker arm that is pivotally mounted on a machine frame and has at least one receptacle for the pressure roller at at least one free end. The at least one receptacle can in particular be designed in the manner of a bearing bore. The pressure roller has a bearing in the region of the at least one bearing section. The bearing can in particular be a rolling bearing, e.g. in the manner of a ball bearing. In the case of a rolling bearing, the bearing preferably comprises an inner ring and an outer ring with rolling elements arranged between them. The bearing has an outer surface, which can in particular be an outer surface of the outer ring of the bearing.At least one spring-damper element is arranged on this outer surface of the bearing. The spring-damper element is designed to partially or even completely dampen vibrations of the pressure roller. For this purpose, the spring-damper element is at least partially elastic. Thus, the spring-damper element can be made at least partially of rubber. The pressure roller is rotatably mounted with the bearing and the at least one spring-damper element in the at least one receptacle of the roller support. Furthermore, the at least one spring-damper element is designed to secure the pressure roller relative to the roller support in a radially and axially vibration-damped manner.This means that the at least one spring-damper element is designed to transmit the forces regularly occurring on the pressure roller when pressing a thread onto a spool, both radially and axially, to the roller support, without the need for additional fixed bearings for the pressure roller. The bearing of the pressure roller is therefore preferably designed in the manner of a floating support bearing, with the at least one spring-damper element providing damping in all directions of the pressure roller. However, the play of the pressure roller in the axial direction is preferably reduced by the at least one spring-damper element due to its sufficiently high rigidity in the axial direction.In this context, axially mounted means that the forces that regularly occur when a thread is pressed against a spool can be transmitted to the roller support in an axial direction, i.e. parallel to a rotational axis of the pressure roller. Radially mounted means in particular that the forces that regularly occur when a thread is pressed against a spool can be transmitted to the roller support in a radial direction, i.e. in particular orthogonal to the rotational axis of the pressure roller. The at least one spring-damper element is thus designed and intended to fix the pressure roller radially and axially relative to the roller support, such that vibrations of the pressure roller can be dampened radially and axially by the at least one spring-damper element, wherein the elastic stiffness of the spring-damper element provides the necessary stability for the axial and radial mounting of the pressure roller.

[0007] In a further embodiment, the at least one spring-damper element has an elastic layer arranged between an inner sleeve and an outer sleeve. The elastic layer is in particular an elastomer, e.g. rubber, wherein the elastic layer between the inner sleeve and the outer sleeve can have a prestress to increase the service life of the elastic layer. The elastic layer is firmly connected to the inner sleeve and the outer sleeve to form a single component, so that the installation space is determined solely by the dimensions of the sleeves. This enables a defined positioning of the pressure roller relative to the roller carrier, even with very long pressure rollers, without any negative impact on the properties of the spring-damper element.

[0008] Depending on the application, whether textile threads are wound into spools using a POY or FDY process, or technical threads using an IDY or BCF process, different winding machines are used. The design of the invention has proven particularly successful in this regard, in which the elastic layer, in the pre-tensioned state, between the inner and outer sleeves has a radial stiffness in the range of 1000 N / mm to 8000 N / mm. This allows self-excited vibrations with small or large amplitudes in the frequency range relevant for the operating speeds to be adequately dampened. The axial fixation of the pressure roller can be ensured for these applications, in particular, by an axial stiffness of the elastic layer in the range of 150 N / mm to 1200 N / mm.

[0009] The inner sleeve and the outer sleeve are preferably made of metal and have a circular cross-section. The at least one spring-damper element has an inner diameter of 20 mm to 80 mm, preferably 40 mm to 60 mm. The inner sleeve can be attached, in particular, to the outer surface of the bearing by an adhesive bond, and the outer sleeve can be attached to the at least one receptacle of the roller support by a press fit.

[0010] To prevent overloading of the at least one spring-damper element, a preferred embodiment of the invention provides for mechanically limiting the elastic mobility of the spring-damper element. For this purpose, at least one elastic spring stop is provided on the inner sleeve opposite the outer sleeve. This allows for the absorption of cardanic movements within the spring-damper element, in addition to purely radial vibrational movements.

[0011] The effect of the spring-damper element on the pressure roller is essentially also determined by its installation and arrangement within the receptacles of the roller support. To maintain the preset spring-damper characteristic on the spring-damper element, the embodiment of the invention is particularly advantageous in which the at least one receptacle of the roller support has at least one bearing half-shell detachably connected to the roller support. This allows a press fit between the outer sleeve and the roller support to be easily achieved, for example, by screwing the bearing half-shell to the roller support.

[0012] In a further expedient embodiment, the at least one spring-damper element has a support surface on the outer surface of the bearing with a length of 5 mm to 50 mm in an axial direction of the pressure roller. It has been found that such a configuration of the at least one spring-damper element is particularly suitable for establishing a secure connection between the outer surface of the bearing and the at least one spring-damper element.

[0013] In a particularly preferred embodiment, the at least one spring-damper element is arranged substantially centrally on the outer surface of the bearing in the axial direction of the pressure roller. For this purpose, the spring-damper element has a length in an axial direction of the pressure roller that is shorter than a length of the bearing in the axial direction of the pressure roller. Both the axis of the pressure roller and a bore axis of the at least one receptacle of the roller carrier can tilt towards each other as a result of vibration or due to manufacturing tolerances. In order to nevertheless ensure the most uniform loading possible on the bearing, in particular on two ball raceways of a ball bearing, the axial length, i.e. in the axial direction of the pressure roller, of the elastomer of the at least one spring-damper element must be kept small. "Small" is understood here to mean, in particular, a length of 1 to 10 mm.The at least one spring-damper element thus exhibits low pitch stiffness and high cardanic deflection, so that a mutual inclination of the rotational axis of the pressure roller and the bore axis of the at least one receptacle of the roller carrier can be compensated by pitching within the at least one spring-damper element. Furthermore, the central arrangement of the at least one spring-damper element on the outer surface of the bearing advantageously ensures that the bearing is evenly loaded. In contrast, the arrangement of O-rings across the entire bearing width led to uneven loading and thus to premature wear of the bearings.

[0014] It is also advantageous if the pressure roller has a first end with a first bearing section and a second end with a second bearing section, wherein a first spring-damper element is arranged in the first bearing section and a second spring-damper element is arranged in the second bearing section, and wherein the first spring-damper element has a lower elastic stiffness than the second spring-damper element. The first end of the pressure roller can, for example, be a drive side and the second end a sensor wheel side of the pressure roller. Due to the design of a bobbin head of a winding machine, different bearing stiffnesses can occur at the first end and the second end of the pressure roller.These different mounting stiffnesses can be compensated by a lower elastic stiffness of the first spring-damper element compared to an elastic stiffness of the second spring-damper element, so that an effective mounting stiffness of the pressure roller at the first end and the second end is substantially the same.

[0015] In a further development of the invention, it is proposed that the outer surface of the bearing has a groove that serves to accommodate an electrical conductor. The electrical conductor establishes an electrically conductive connection between the bearing and the roller support, thus preventing electrostatic charging of the pressure roller. The electrical conductor can be, in particular, an octagonal spring and / or a helical spring.

[0016] It is also advantageous if the bearing, starting from one end of the pressure roller, has a first outer diameter region with a first diameter, a second outer diameter region with a second diameter, a third outer diameter region with a third diameter, and a fourth outer diameter region with a fourth diameter, and wherein a first step between the third outer diameter region and the fourth outer diameter region serves as a stop for a protective ring. The protective ring is a metallic ring, preferably arranged on the outer surface of the bearing, so that the bearing is protected from the ingress of thread residues.

[0017] It is particularly advantageous if the device has at least one protective ring with a stop area, wherein the at least one protective ring comes into contact with the roller support when the pressure roller is displaced in an axial direction of the pressure roller, so that further displacement of the pressure roller is prevented. The at least one spring-damper element is designed such that it can transmit the regularly occurring forces in an axial direction of the pressure roller to the roller support without the pressure roller being axially displaced out of a tolerance range. It should be clarified here that the at least one spring-damper element adjusts the pressure roller back to an axial starting position due to its elasticity when the pressure roller is relieved.However, if large axially acting special loads occur, the stop area of ​​the at least one protective ring comes into contact with the roller support and thereby prevents further displacement of the pressure roller beyond the tolerance range in order to prevent damage to the at least one spring-damper element. In particular, it is advantageous if a first protective ring is arranged on the outer surface of the first bearing and a second protective ring is arranged on the outer surface of the second bearing. The stop area of ​​the first protective ring contacts the roller support, in particular when the pressure roller is axially displaced by 1.5 mm, and the stop area of ​​the second protective ring contacts the roller support, in particular when the pressure roller is axially displaced by 2 mm.

[0018] Finally, a winding machine comprising a device of the type described above is also proposed.

[0019] The invention and the technical environment are explained in more detail below with reference to the figures. It should be noted that the figures show particularly preferred embodiments of the invention, but are not limited thereto. They schematically show: Fig. 1: an embodiment of a winding machine with a device according to the invention in a front view, Fig. 2: the embodiment of the winding machine with the device according to the invention in a side view, Fig. 3: a sectional view of the embodiment of the device according to the invention, and Fig. 4: a detailed view of the embodiment of the device according to the invention.

[0020] Fig. 1 shows a winding machine 36 with a device 1 for pressing threads 2 onto bobbins 3. The device 1 has a pressure roller 4, which is connected to the winding machine 36 via a movable roller support 7. The roller support 7 is designed as a rocker, which is held on the winding machine 36 via a pivot bearing 49. The pressure roller 4 is held at the free end of the roller support 7. The pressure roller 4 presses the threads 2 onto a surface of the bobbins 3, which are rotatably mounted on a bobbin mandrel 43.

[0021] Fig. 2 shows the winding machine 36 of the Fig. 1 in a side view. The pressure roller 4 can be seen with a thread guide section 5, in which two threads 2 are each wound onto a spool 3. The pressure roller 4 also has a first bearing section 6 at a first end 20, which is mounted in a first receptacle 8 of the roller carrier 7. In addition, the pressure roller 4 has a second bearing section 22 at a second end 21, which is mounted in a second receptacle 38 of the roller carrier 7. The first receptacle 8 of the roller carrier 7 has a (in the Fig. 2 not shown) first bearing half-shell 47 and the second receptacle 38 of the roller carrier 7 has a (in the Fig. 2 not shown) second bearing half-shell 48, as will be explained later in connection with the Fig. 3 is explained in more detail. The bearing half-shells 47 and 48 are firmly connected to the roller support 7.

[0022] Fig. 3 shows the device 1 for pressing threads 2 (not shown here) onto spools 3 (not shown here). The pressure roller 4 has a rotationally symmetrical cross-section in the first bearing section 6, the thread guide section 5, and the second bearing section 22, as can be seen from the indicated (rotational) axis 41. A first bearing 9 is arranged in the first bearing section 6, which is designed here as a bearing journal. The first bearing 9 shown here is a ball bearing with two ball races. A second bearing 39, identical to the first bearing 9, is arranged in the second bearing section 22, wherein the bearings (9, 39) are installed mirror-inverted to one another. The description of the first bearing 9 therefore also applies accordingly to the second bearing 39. A first spring-damper element 11 is arranged on the outer surface 10 of the first bearing 9.Accordingly, a second spring-damper element 23 is arranged on the outer surface 10 of the second bearing 39. Both the first spring-damper element 11 and the second spring-damper element 23 are designed to dampen vibrations of the pressure roller 4 both in a radial direction 44 and in an axial direction 19 relative to the (rotational) axis 41. The pressure roller 4 is mounted in the first receptacle 8 of the roller support 7 via the first bearing 9 and the first spring-damper element 11, and correspondingly in the second receptacle 38 of the roller support 7 via the second bearing 39 and the second spring-damper element 23. The first receptacle 8 is formed between the roller support 7 and the first bearing half-shell 47, and the second receptacle 38 is formed between the roller support 7 and the second bearing half-shell 48. The first bearing half-shell 47 and the second bearing half-shell 48 are firmly connected to the roller carrier 7.

[0023] In addition, a first protective ring 33 is arranged on the outer surface 10 of the first bearing 9, and a second protective ring 40 is arranged on the outer surface 10 of the second bearing 39. The first protective ring 33 and the second protective ring 40 prevent thread remnants from the thread guide section 5 from penetrating the first bearing 9 or the second bearing 39 and damaging them. Both the first protective ring 33 and the second protective ring 40 each have a stop area 34 to ensure that the bearings 9 or 39 are securely held in the receptacles 8 or 38 of the roller carrier 7 in the event of an undesired axial displacement of the pressure roller 7, for example, in the event of a failure of the spring-damper element 11.

[0024] Fig. Figure 4 shows a detailed view of a profile cross-section of the first bearing 9 and the first spring-damper element 11, corresponding to the upper right area of ​​the Fig.3. The first spring-damper element 11 has an elastic layer 14 arranged between an inner sleeve 12 and an outer sleeve 13. The elastic layer 14, which is preferably formed as a vulcanized rubber between the sleeves 12 and 13, has an elastic stiffness preselected for the respective application to ensure the radial and axial fixation of the pressure roller to the roller support. Thus, the selected radial stiffnesses are in a range from 1000 N / mm to 8000 N / mm, and the axial stiffnesses are in a range from 150 N / mm to 1200 N / mm.

[0025] The elastic layer 14 does not extend across the entire width of the sleeves 12 and 13. Two spring stops 45 and 46 are formed laterally next to the elastic layer 14 on the inner sleeve 12, opposite the outer sleeve 13. The spring stops 45 and 46 are made of an elastic material that has a significantly higher rigidity than the elastic layer 14. The spring stops 45 and 46 on the spring-damper element 11 limit the radial mobility and the pitching mobility in the bearing points.

[0026] The contact surface between the inner sleeve 12 and the outer surface 10 of the first bearing 9 forms a support surface 15 which has a first axial length 16 in the axial direction 19. In this exemplary embodiment, the first axial length 16 of the support surface 15 of the bearing 9 is the same length as a second length 17 of the first spring-damper element 11 in the axial direction 19 of the pressure roller 4. The first bearing 9 has a third length 18 in the axial direction 19 of the pressure roller 4, wherein the second length 17 is smaller than the third length 18. The first spring-damper element 11 is arranged essentially centrally on the outer surface 10 of the first bearing 9 in the axial direction 19 of the pressure roller 4. Starting from the first end 20 of the pressure roller 4, the first bearing 9 has a first outer diameter region 24, a second outer diameter region 25, a third outer diameter region 26 and a fourth outer diameter region 27.The first outer diameter region 24 has a first diameter 28, the second outer diameter region 25 has a second diameter 29, the third outer diameter region 26 has a third diameter 30 and the fourth outer diameter region 27 has a fourth diameter 31. Between the third outer diameter region 26 and the fourth outer diameter region 27, a first step 32 serves as a stop for the first protective ring 33. Between the second outer diameter region 25 and the third outer diameter region 26, a second step 37 serves as a stop for the first spring-damper element 11. In addition, the outer surface 10 of the first bearing 9 has a groove 42 which serves to receive an electrical conductor 35.The statements regarding the first bearing 9, the first spring-damper element 11 and the first protective ring 33 can be transferred accordingly to the second bearing 39, the second spring-damper element 23 and the second protective ring 40.

[0027] The present invention is characterized by a particularly effective damping of the vibrations of the pressure roller. List of reference symbols 1 device 2 threads 3 coil 4 pressure roller 5 Thread guide section 6 first camp section 7 roller supports 8 first recording 9 first camp 10 Exterior area 11 first spring-damper element 12 inner sleeve 13 outer sleeve 14 elastic layer 15 support surface 16 first axial length 17 second axial length 18 third axial length 19 axial direction 20 first end 21 second end 22 second camp section 23 second spring-damper element 24 first outer diameter range 25 second outer diameter range 26 third outer diameter range 27 fourth outer diameter range 28 first diameter 29 second diameter 30 third diameter 31 fourth diameter 32 first stage 33 first protective ring 34 Stop area 35 electrical conductor 36 winding machine 37 second stage 38 second shot 39 second camp 40 second protective ring 41 (rotation) axis 42 grooves 43 Coil mandrel 44 radial direction 45 first spring stop 46 second spring stop 47 first bearing half shell 48 second bearing half shell 49 swivel bearings

Claims

[1] Device (1) for pressing a thread (2) onto a spool (3), comprising a pressure roller (4) and a roller support (7), wherein the pressure roller (4) has a first end (20) with a first bearing section (6) which is mounted in a first receptacle (8) of the roller support (7), and a second end (21) with a second bearing section (22) which is mounted in a second receptacle (8) of the roller support (7), and a thread guide section (5) formed between the bearing sections, wherein the pressure roller (4) has a bearing (9, 39) with an outer surface (10) in the region of the first and the second bearing section (6, 22), wherein at least one spring-damper element (11, 23) is arranged on the outer surface (10) of the bearing (9), wherein the pressure roller (4) is rotatably connected to the bearings (9) and the Spring-damper elements (11, 23) are mounted in the receptacles (8, 38) of the roller support (7) and wherein each spring-damper element (11, 23) is formed,to fix the pressure roller (4) relative to the roller support (7) radially and axially with an elastic stiffness, wherein a first spring-damper element (11) is arranged in the first bearing section (6) and a second spring-damper element (23) is arranged in the second bearing section (22), and wherein the first spring-damper element (11) has a lower elastic stiffness than the second spring-damper element (23). [2] Device according to claim 1, wherein the at least one spring-damper element (11, 23) has an elastic layer (14) arranged between an inner sleeve (12) and an outer sleeve (13). [3] Device according to claim 2, wherein the elastic layer (14) has a predetermined radial stiffness in the range of 1000 N / mm to 8000 N / mm. [4] Device according to claim 2 or 3, wherein the elastic layer (14) has a predetermined axial stiffness in the range of 150 N / mm to 1200 N / mm. [5] Device according to one of the preceding claims, wherein the at least one spring-damper element has at least one elastic spring stop (45, 46) arranged on the inner sleeve (12) opposite the outer sleeve (13). [6] Device according to one of the preceding claims, wherein at least one receptacle (8, 38) of the roller support (7) has at least one bearing half-shell (47, 48) detachably connected to the roller support (7). [7] Device (1) according to one of the preceding claims, wherein the at least one spring-damper element (11, 23) has a support surface (15) on the outer surface (10) of the bearing (9) with a length (16) in an axial direction (19) of the pressure roller (4) of 5 mm to 50 mm. [8] Device (1) according to one of the preceding claims, wherein at least one spring-damper element (11, 23) is arranged in the axial direction (19) of the pressure roller (4) substantially centrally on the outer surface (10) of the bearing (9, 39). [9] Device (1) according to one of the preceding claims, wherein the outer surface (10) of the bearing (9) has a groove (42) which serves to receive an electrical conductor (35), wherein the electrical conductor (35) establishes an electrically conductive connection between the bearing (9) and the roller support (7), so that an electrostatic charging of the pressure roller (4) can be prevented. [10] Device (1) according to one of the preceding claims, wherein the bearing (9), starting from one end (20, 21) of the pressure roller (4), has a first outer diameter region (24) with a first diameter (28), a second outer diameter region (25) with a second diameter (29), a third outer diameter region (26) with a third diameter (30) and a fourth outer diameter region (27) with a fourth diameter (31), and wherein between the third outer diameter region (26) and the fourth outer diameter region (27) a first step (32) serves as a stop for a protective ring (33, 40). [11] Device (1) according to claim 8, comprising at least one protective ring (33, 40) with a stop region (34), wherein the at least one protective ring (33, 40) comes into contact with the roller support (7) upon displacement of the pressure roller (4) in an axial direction (19) of the pressure roller (4), so that further displacement of the pressure roller (4) is prevented. [12] Winding machine (36) comprising a device according to one of the preceding claims.

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