Drive device for eccentric bearing and corresponding calender

Abstract

The invention relates to a drive device for an eccentric bearing for radially shifting a roller mounted therein, the eccentric bearing having an axially oriented bore for receiving a roller journal of the roller, and the eccentric bearing having an outer eccentric bushing and an inner eccentric bushing, the inner eccentric bushing is partially inserted into the outer eccentric bushing and has the hole, so that the eccentric bushings have an axial overlapping region, characterized in that at least one of the eccentric bushings has a free end outside the overlapping region, the free end is coupled to a drive unit, by means of which the eccentric bushings are coupled to the inner eccentric bushing. The at least one eccentric bushing is rotatable about an axial direction relative to the other eccentric bushing to set a radial off-axis offset of the bore. The invention also relates to a corresponding calender.

Description

[0001] The invention relates to a drive device for an eccentric bearing and a corresponding calender, wherein the eccentric bearing is used to radially offset a roll mounted therein, wherein the eccentric bearing has an axially oriented hole for accommodating a roll journal of the roll, and the eccentric bearing has an outer eccentric sleeve and an inner eccentric sleeve, wherein the inner eccentric sleeve is partially inserted into the outer eccentric sleeve and has the hole, so that the eccentric sleeves have an axial overlap area.

[0002] From the prior art, a printer bearing is known, which has an eccentric ring for axial displacement or angular adjustment of a cylinder mounted in the printer bearing, the eccentric rings being pivotable relative to each other and / or pivotable about the cylinder. In the solution disclosed in the prior art, the eccentric ring is adjusted by an articulated actuating assembly in the form of a pivoting lever, which is arranged on the outer end face of the bearing and can be displaced tangentially about the cylinder axis in order to set the desired eccentricity.

[0003] However, the device disclosed in the prior art has the following disadvantages: since the pivot rod extending from the drum axis is arranged on the end surface and displaced both horizontally and vertically, the device occupies a large amount of space, especially in the radial direction of the drum, and is not suitable for narrow installation space.

[0004] Therefore, an object of the present invention is to improve a drive device for an eccentric bearing so as to make it compact.

[0005] The present invention is achieved by the features of the independent claims. Advantageous embodiments are described in the dependent claims.

[0006] According to this, it is provided that at least one of the eccentric bushings has a free end outside the overlapping region, which free end is connected to a drive unit, by means of which the at least one eccentric bushing can be rotated relative to the other eccentric bushing about the axial direction in order to set the radial offset of the bore. Since at least one eccentric bushing has a free end, it is not necessary to drive the relevant eccentric bushing from the end side, but rather the force can be introduced into the eccentric bushing in a space-saving manner by means of a tangentially arranged drive unit.

[0007] It can be provided as follows: the inner eccentric sleeve is rotatably mounted in the outer eccentric sleeve. Accordingly, in the axial overlap region, a radial bearing can be provided between the outer surface of the inner eccentric sleeve and the inner surface of the outer eccentric sleeve. It can also be provided as follows: the roller journal that can be accommodated in the hole can be rotatably mounted in the inner eccentric sleeve. Accordingly, in the axial overlap region, another radial bearing can be provided on the inner surface of the inner eccentric sleeve. The eccentric bearing can be accommodated in a hole or a bushing provided in the calender frame and can be rotatably mounted therein. Accordingly, in the overlap region, a radial bearing can also be provided between the outer surface of the outer eccentric sleeve and the inner surface of the hole or bushing. In this way, the outer eccentric sleeve can rotate relative to the hole or bushing, the inner eccentric sleeve can rotate relative to the outer eccentric sleeve, and optionally the roller accommodated in the inner eccentric sleeve can rotate relative to the inner eccentric sleeve.

[0008] The inner hole of the outer eccentric sleeve can be eccentric relative to its outer diameter. The inner eccentric sleeve can be accommodated in the inner hole of the outer eccentric sleeve. In addition, the inner hole of the inner eccentric sleeve can be eccentric relative to the outer diameter of the inner eccentric sleeve. At the same time, in the initial position of the two eccentric sleeves, the inner hole of the inner eccentric sleeve can be concentric with the outer diameter of the outer eccentric sleeve. The inner eccentric sleeve and the outer eccentric sleeve can be rotated relative to each other or in the same direction so that the eccentricity of the inner hole of the inner eccentric sleeve can be set, wherein the direction and degree of eccentricity are variable. For this purpose, each eccentric sleeve can have a thick part and a thin part opposite to the thick part. In the above-mentioned initial position, the thick part of the outer eccentric sleeve can be close to the thin part of the inner eccentric sleeve, and the thin part of the outer eccentric sleeve can be close to the thick part of the inner eccentric sleeve. When the two eccentric sleeves are rotated relative to each other by 180°, the maximum possible eccentric offset can be achieved accordingly. In addition, by rotating the inner eccentric sleeve and the outer eccentric sleeve in opposite directions at the same time, a linear offset can be achieved. Furthermore, the deflection direction can be changed by rotating the inner eccentric sleeve and the outer eccentric sleeve in the same rotational direction at the same time.

[0009] Furthermore, it can be provided that the two eccentric sleeves have free ends on opposite sides of the overlapping area, each of which is connected to a drive unit, through which the eccentric sleeves can be rotated around the axial direction without affecting each other to set the radial off-axis offset of the hole.

[0010] Furthermore, it can be provided that the drive unit has a transmission output, for example an external toothing, which is arranged at least partially on the outer circumference of the free end and is connected to the free end. The transmission output can, for example, extend over half of the circumference of the free end of the eccentric sleeve so that the eccentric sleeve can be pivoted by 180°. As a result, the transmission output can surround the eccentric sleeve in a semicircular shape. The free end can be designed essentially as a cylindrical hollow body.

[0011] Furthermore, the drive unit may have a drive assembly coupled to the transmission output, the drive element being arranged perpendicular to the axial direction. The drive assembly may be driven to rotate or translate. For example, the drive assembly may be implemented with a rack. The drive assembly may in particular have a worm shaft engaged with the transmission output or an external toothing. In the case of a worm shaft, the drive assembly has a rotary drive motion.

[0012] It can be provided that the drive units are spaced apart from each other in the axial direction. In particular, the drive components can be spaced apart from each other in the axial direction. The spacing can correspond in particular to the distance between the transmission outputs on the free ends. It can be provided that the drive components are each accommodated in a housing that surrounds them. The housing can extend perpendicularly to the axial direction of the drive device, just like the drive components. The housing can each have an interface facing a hole or a bushing in which the drive device is accommodated. In the region of the interface, the drive component accommodated in the housing can engage with the transmission output on the free end of the eccentric sleeve that is accommodated in the hole or the bushing.

[0013] The eccentric bearing can be mounted in a bushing or a hole of the frame or in particular of the calender frame, wherein the drive assembly is driven by a motor arranged outside the bushing or hole. In case two drive devices are provided on the eccentric bearing, the drive assemblies can be arranged on the same side or on different sides of the axis of the central hole and oriented parallel to each other. It can be arranged as follows: one of the motors is coupled to one of the drive assemblies via a first side and the other motor is coupled to the other drive assembly via the opposite side. For example, in case the hole or the roller is oriented horizontally, the drive assemblies can be arranged vertically and one of the motors can be coupled to the upper side of one drive assembly and the other motor can be coupled to the lower side of the other drive assembly.

[0014] Furthermore, it can be provided that an angular offset is provided between the drive assembly and the motor. The angular offset can be designed, for example, so that the motor is arranged perpendicular to the drive assembly. The angular offset can be achieved by means of an angular gear transmission which connects the drive assembly to the motor. The angular gear transmission can be, for example, a bevel gear transmission, a bevel-planetary gear transmission or a hypoid gear transmission. The motor can in particular be a servomotor. This can control the angular position of the motor shaft as well as the rotational speed and acceleration. The servomotor can have a sensor for determining the position.

[0015] Furthermore, it can be provided that the eccentric sleeves each have a setting scale that can be read from the outside of the bushing. The actual position of the eccentric sleeve can be grasped by the setting scale. It can be provided that the setting scale of one eccentric sleeve points in the axial direction and the setting scale of the other eccentric sleeve points in the radial direction, and the setting scales can be read from the corresponding places. For example, the scale of the eccentric sleeve facing the outside of the roller can be read from the end side. In addition, the setting scale of the eccentric sleeve facing the center of the roller can be read from the upper side or the lower side of the bushing that accommodates the drive device. The required off-axis offset is converted as a function of the angle of rotation of the eccentric. The increments can be read in steps of 0.2 mm in a range of 0 mm to a maximum of 4 mm.

[0016] The invention further relates to a calender having at least two rollers arranged in parallel and mounted in a calender frame, with a roll gap formed between the rollers, wherein the rollers have a roller journal mounted in the calender frame at their opposite ends, wherein at least two adjacent roller journals have a drive device according to one of the above technical solutions. Since the drive device according to the invention for driving the eccentric bearing is provided on two adjacent roller journals, only a small installation space is left, in particular for the motor for driving the drive assembly. The drive device according to the invention enables the eccentric sleeve to be adjusted by an advantageous force transmission, and thus the eccentric sleeve can be adjusted in a space-saving manner.

[0017] Furthermore, it can be provided that in the calender all roll journals of the two rolls each have a drive device as described in one of claims 1 to 13.

[0018] In particular, it can be provided that the drive assemblies of adjacent drive devices are oriented parallel to one another. For example, in the case of a horizontally oriented hole axis or roller axis, the drive assemblies can be oriented vertically. In this case, the two drive assemblies can be arranged on the same side of the hole axis or roller axis or on opposite sides. For example, the two drive assemblies can be arranged on the right or left side of the roller axis or on different sides of the roller axis, i.e. on the right and on the left side.

[0019] The motors of adjacent drive devices can be arranged to be either oriented parallel to the roller axis or away from the associated adjacent drive device. For example, a first motor of one drive device can be arranged parallel to the roller axis, and a second motor of the drive device can be arranged perpendicular to the roller axis and away from the adjacent drive device. The motors of the adjacent drive devices can then be oriented accordingly.

[0020] The arrangement may be as follows: a first support roller is adjacent to a first roller of the rollers, a second support roller is adjacent to a second roller of the rollers, and the support rollers rotate in opposite directions to the rollers. The support rollers may each have a larger diameter than the rollers. The rollers may have the same diameter, and the support rollers may also have the same diameter. The diameter of the rollers may be 200 mm. The diameter of the support rollers may be 700 mm. The axes of the rollers and the support rollers may be aligned in one plane. The first roller and the first support roller may roll on each other, and a roller gap may be formed between the second roller and the second support roller.

[0021] Further features of the present invention are described with reference to the following figures, wherein:

[0022] Figure 1 It is a conventional operating mechanism for adjusting the eccentric ring of the printer bearing in the prior art;

[0023] Figure 2 is a schematic front view of an eccentric bearing for radially offsetting a bearing journal;

[0024] Figure 3 is a perspective view of an embodiment of a drive device according to the present invention;

[0025] Figure 4 is a perspective cutaway view of a roller journal mounted in an eccentric bearing;

[0026] Figure 5 is a perspective front view of a roller calender equipped with a drive device;

[0027] Figure 6 is an overall perspective view of a roller calender equipped with a drive device; and

[0028] Figure 7 is a top view of a calender equipped with a drive device, which is used to produce an electrode film from a powdered electrode precursor material.

[0029] Figure 1 The view in shows a conventional printer bearing from the prior art, which has eccentric rings for axial displacement or oblique adjustment of a printing roller mounted in the printer bearing, the eccentric rings being pivotable relative to each other and / or being pivotable individually about the axis of the roller. The eccentric rings have the same thickness in the axial direction and are aligned with each other so that they overlap each other over their entire thickness. It can be seen that in the solution disclosed in the prior art, the eccentric rings are adjusted by an articulated pivot rod arranged on the outside of the bearing, which is displaceable tangentially around the roller to set the required eccentricity. However, the solution shown has the following disadvantages: the necessary length of the rod body and its displacement in the horizontal and vertical directions cause the solution to take up a lot of space, especially in the radial direction of the roller, and is therefore not suitable for narrow installation spaces.

[0030] Figure 2 An exemplary eccentric bearing 99 is shown for offsetting the roller journal 205 in an adjustable order of magnitude in any direction orthogonal to the center axis of the associated roller 201, 202. The eccentric bearing 99 has an outer eccentric sleeve 101, the inner hole of which is eccentric relative to the outer diameter of the outer eccentric sleeve 101. The eccentric bearing 99 also has an inner eccentric sleeve 102, the inner hole 105 of which is concentric with the outer diameter of the outer eccentric sleeve 101 in an initial position. The inner eccentric sleeve and the outer eccentric sleeves 102, 101 can rotate relative to each other or can rotate in the same direction so that the eccentricity of the inner hole 105 of the inner eccentric sleeve 102 can be set, wherein the direction and degree of offset are variable. Each eccentric sleeve 101, 102 has a thick portion and a thin portion opposite to the thick portion. In the initial position, the thick part of the outer eccentric sleeve 101 is close to the thin part of the inner eccentric sleeve 102, and the thin part of the outer eccentric sleeve 101 is close to the thick part of the inner eccentric sleeve 102. When the two eccentric sleeves 101 and 102 rotate 180 degrees relative to each other, the maximum possible eccentric offset can be achieved accordingly.

[0031] Figure 2An embodiment of a drive device 1 according to the invention is shown. An eccentric bearing 99 is accommodated in a bushing 520 that can be connected to a frame 500, and the eccentric bearing has an inner eccentric sleeve and an outer eccentric sleeve 101, 102, which can rotate relative to each other about the X axis, or can rotate relative to the bushing 520 or relative to the roller journal 205 that can be accommodated in the inner hole 105 of the inner eccentric sleeve 102. In order to drive the eccentric sleeve facing the center of the roller, a first drive unit 300 is provided, which has a drive component 302 arranged perpendicular to the X axis and accommodated in a housing 306. The housing 306 has an interface including a bushing 520, through which the drive component 302 is connected to a transmission output in the form of an external tooth 301, which is arranged on the outer periphery of the free end 104 of the eccentric sleeve, wherein the drive component 302 is tangentially hinged to the external tooth 301. The servo motor 304 driving the drive assembly 302 is connected to the drive assembly 302 via an angular gear transmission 305, wherein the motor 304 is arranged above the bushing 520 perpendicularly to the drive assembly 302 and parallel to the X axis. In order to drive the eccentric sleeve away from the center of the roller, a second drive unit 300 is provided, which is designed to correspond to the first drive unit 300, wherein the drive assembly 302 accommodated in the housing 306 is connected to the free end 104 of the eccentric sleeve away from the center of the roller. The housing 306 and the drive assembly 302 are arranged parallel to each other on the right side of the X axis. Different from the first drive unit 300, the motor 304 of the second drive unit 300 is arranged on the lower side of the bushing 520, also perpendicularly to the drive assembly 302, but not parallel to the X axis, but perpendicularly intersecting the bushing 520. In order to read the setting of the eccentric sleeve facing the center of the roller, the bushing 520 has an observation window on its upper side, through which the setting scale 400 arranged on the free end 104 can be read. In order to read the setting of the eccentric bushing remote from the roller center, the end face of the free end 104 of the eccentric bushing has a graduated ring with a further setting scale 400 , which can thus be read from the front.

[0032] Figure 4A cross-sectional view of a roller 201 and an eccentric bearing 99 mounted on a roller journal 205 of the roller 201 is shown. The roller 201 is mounted in a frame 500, which has a bushing 520 in which the roller journal 205 is accommodated together with the eccentric bearing 99. The eccentric bearing 99 essentially comprises an inner eccentric sleeve 102 and an outer eccentric sleeve 101, wherein the roller journal 205 is accommodated in an inner bore 105 of the inner eccentric sleeve 102. The inner eccentric sleeve 102 is partially inserted into the outer eccentric sleeve 101, so that the eccentric sleeves have an axial overlap area 103. The outer eccentric sleeve 101 is mounted in the drum sleeve in an axially rotatable manner via a first radial bearing 110. The inner eccentric sleeve 102 is mounted in the outer eccentric sleeve 101 in an axially rotatable manner via a second axially rotatable radial bearing 120. The roller journal 205 is in turn mounted in the inner eccentric sleeve 130 in an axially rotatable manner via a third radial bearing 130. In the illustrated orientation, the eccentric bearing 99 is in an initial position in which the thick part of the outer eccentric sleeve 101 is close to the thin part of the inner eccentric sleeve 102, and the thin part of the outer eccentric sleeve 101 is close to the thick part of the inner eccentric sleeve 102, so that the roller journal 205 is centered without displacement. The eccentric sleeves 101 and 102 can be adjusted separately by a separate drive unit 300. For this purpose, the eccentric sleeves 101, 102 each have a free end 104 extending away from the axial overlap area 103 opposite to each other, and each free end has a transmission output in the form of an external tooth 301, by which the eccentric sleeves 101, 102 can be adjusted separately. On the front side, the inner eccentric sleeve 102 facing away from the center of the roller has a setting scale 400 that can be read from the end side. On the rear side, the outer eccentric sleeve 101 facing the center of the roller has a setting scale 400 that can be read from the circumference.

[0033] Figure 5 A perspective front view of a calender 2 is shown, which has two rollers 201 mounted horizontally and parallel in a frame 500, which rollers form a roll gap 220 and are therefore arranged very close together. A drive device 1 with two drive units 300 is mounted on each roller journal 205 extending from the frame. As shown in the figure, the drive components 302 each have a worm shaft 303, which engages with the associated external toothing 301. The drive components 302 are all arranged vertically on the side of the roller 201 facing away from the roll gap 220, wherein the motor 304 of each drive device 1 is arranged above the associated roller 201 and the motor 304 of each drive device 1 is arranged below the associated roller 201. At the same time, all motors are oriented perpendicularly to the drive components 302 and parallel to the roller axis X.

[0034] Figure 6 Show Figure 5The general view of the calender 2 is shown. As shown in the general view, the roller journals 205 arranged at the opposite ends of the roller 201 are installed in the frame 500 in a substantially mirrored manner, wherein a drive device 1 having an eccentric bearing 99 and two drive units 300 is mounted on each roller journal 205. The roller gap 220 of several millimeters formed between the rollers 201 can be clearly seen, which requires the connecting components (such as drive units 300) on the end sides of the rollers 201 to adopt an extremely compact design. All motors 304 are installed on the side of the roller 201 away from the roller gap 220, wherein a motor 304 installed parallel to the roller axis X is respectively installed on the upper side and the lower side of the roller 201.

[0035] Figure 7 3 is a top view of a multi-roll calender 3, which shows the arrangement relationship between the rollers 201 and the support rollers 210 in an integrated rolling system according to one embodiment. The multi-roll calender 2 is used to manufacture a diaphragm (not shown) coated with electrode films 601 and 602 on both sides. The array has two calender devices 2 positioned against each other at the end sides, and the calender devices have opposite main conveying directions Y1 and Y2. The calender devices 2 each have eight rollers 201, 210, 310 installed in a frame 500. On the input side, the device has two rollers 201 supported laterally by support rollers 210, which act as grinders for manufacturing electrode films 601 and 602 with powdered electrode precursor materials. Four conveying rollers 310 are also connected behind the support rollers, which process the electrode films into the required width and thickness and make them uniform. The end rollers 210 on the input side are designed as support rollers 210 that roll directly on the first roller 201. The conveying rollers 310 on the outlet side form a shared end roll gap 13 in which the electrode films 601 , 602 are applied to the separator.

[0036] The features of the present invention disclosed in the above description, drawings and claims can be used to implement the present invention both individually and in any combination.

[0037] Explanation of symbols

[0038] 1 Drive unit

[0039] 2 Calender

[0040] 13 End roll gap

[0041] 99 Eccentric bearing

[0042] 100 Preload device

[0043] 101 External eccentric sleeve

[0044] 102 inner eccentric sleeve

[0045] 103 Axial overlap area

[0046] 104 Free end

[0047] 105 Inner hole of inner eccentric sleeve

[0048] 110 First radial bearing

[0049] 120 Second radial bearing

[0050] 130 Third radial bearing

[0051] 201 Roller

[0052] 205 Roller journal

[0053] 210 Support roller

[0054] 220 Roller Gap

[0055] 300 Drivers

[0056] 301 External teeth

[0057] 302 drive components

[0058] 303 Worm shaft

[0059] 304 Motor

[0060] 305 Angle gear transmission

[0061] 310 conveyor roller

[0062] 400 Set scale

[0063] 500 rack

[0064] 501 Bearing

[0065] 520 Bushing

[0066] 601 First electrode film

[0067] 602 Second electrode film

[0068] X-axis

[0069] Y1 Conveying direction of the first electrode film

[0070] Y2: Transport direction of the second electrode film.

Claims

1. A drive device (1) for an eccentric bearing (99) for radially deflecting a roller mounted therein, wherein the eccentric bearing (99) has a hole (105) oriented in the axial direction (X) for accommodating a roller journal (205) of a roller (201), and the eccentric bearing (99) has an outer eccentric sleeve (101) and an inner eccentric sleeve (102), the inner eccentric sleeve being partially inserted into the outer eccentric sleeve (101) and having the hole (105), so that the eccentric sleeves (101, 102) have an axial overlapping area (103), characterized in that At least one of the eccentric sleeves (101, 102) has a free end (104) outside the axial overlapping area (103), and the free end is connected to a drive unit (300), through which at least one eccentric sleeve (101, 102) can be rotated around an axial direction (X) relative to the other eccentric sleeve (101, 102) to set the radial off-axis offset of the hole (105).

2. The drive device (1) as claimed in claim 1, wherein the two eccentric sleeves (101, 102) have free ends (104) on opposite sides of the axial overlapping area (103), and each of the free ends is connected to a drive unit (300), through which the eccentric sleeves (101, 102) can rotate around the axial direction (X) without affecting each other to set the radial off-axis offset of the hole (105).

3. A drive device (1) according to claim 1 or 2, wherein the drive unit (300) has a transmission output portion, such as an external tooth (301), which is at least partially arranged on the outer periphery of the free end (104) and connected to the free end.

4. The drive device (1) according to claim 3, wherein the drive unit (1) has a drive component (302) connected to the transmission output part, and the drive component is arranged perpendicular to the axial direction (X).

5. The drive device (1) according to claim 4, wherein the drive assembly (302) has a worm shaft (303) which engages with the transmission output part or the external toothing (301).

6. The drive device (1) according to any one of the preceding claims 2 to 5, wherein the drive units (300) are spaced apart from one another in the axial direction (X).

7. A drive device (1) as described in any one of claims 4 to 6, wherein the eccentric bearing (99) is installed in a bushing (520) of a frame (500), and wherein the drive assembly (302) is driven by a motor (304) arranged outside the bushing (520).

8. The drive device (1) according to any one of claims 4 to 7, wherein an angular offset is provided between the drive assembly (302) and the motor (304).

9. The drive device (1) according to claim 8, wherein the angular offset is designed so that the motor (304) is arranged perpendicular to the drive assembly (302).

10. The drive device (1) according to any one of claims 8 or 9, wherein the angular offset is achieved by means of an angular gear transmission (305) coupling the drive assembly (302) with the motor (304).

11. The drive device (1) according to any one of claims 7 to 10, wherein the motor (304) is a servomotor.

12. The drive device (1) according to any one of claims 1 to 11, wherein the eccentric sleeves (101, 102) each have a setting scale (400) which can be read from the outside of the bushing (520).

13. The drive device (1) according to claim 11, wherein: The setting scale (400) of one of the eccentric sleeves (101, 102) points in the axial direction, and the setting scale (400) of the other eccentric sleeve (101, 102) points in the radial direction (Y), and the setting scales (400) can be read from corresponding locations respectively.

14. A calender (2) comprising at least two rollers (201) arranged in parallel and mounted in a frame (500) of the calender, a roller gap being formed between the rollers, wherein the rollers (201) each have a roller journal (205) mounted in the frame (500) of the calender at opposite ends thereof, wherein at least two adjacent roller journals of the roller journals (205) have a drive device (1) as claimed in any one of claims 1 to 13.

15. Calender (2) according to claim 14, wherein all roller journals (205) of the two rollers (201) each have a drive device (1) according to any one of claims 1 to 13.

16. The calender (2) according to claim 14, wherein the drive components (302) of adjacent drive devices (1) are oriented parallel to each other.

17. Calender (2) according to claim 14 or 15, wherein the motor (304) of the adjacent drive device (1) is arranged to be either oriented parallel to the roller axis (X) or away from the associated adjacent drive device (1).

18. The calender (2) according to any one of claims 14 to 16, wherein a first support roller (210) is adjacent to a first roller among the rollers (201), and a second support roller (210) is adjacent to a second roller among the rollers (201), and the support rollers rotate in opposite directions to the rollers respectively.

19. Calender (2) according to claim 17, wherein the support rollers (210) each have a larger diameter than the rollers.

20. Calender (1) according to any one of claims 17 or 18, wherein the axes of the roller (201) and the support roller (210) are aligned in one plane.

21. The calender according to any one of claims 14 to 20, wherein the first roller (201) and the first support roller (210) roll on each other, forming a roller gap (220) between the second roller (201) and the second support roller (210).

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