A calender for generating highest linear force, method for operating calender

Abstract

The invention relates to a calender (100) for calendering surface-shaped articles (10), preferably for producing electrodes, comprising a first roller (1) and a second roller (2), the rollers (1, 2) being displaceable relative to one another in an axial direction (A), the calender (100) having a first adjusting mechanism (7) for bending the first roller (1) by means of a torque input in a radial direction (R). The invention further relates to a method for operating a calender (100).

Description

Technical Field

[0001] This invention relates to a calender for calendering surface-shaped articles, preferably for manufacturing electrodes, the calender having a first roller and a second roller. Furthermore, this invention relates to a method for operating the calender. Background Technology

[0002] A calender typically has at least two work rolls that form a roll gap or pressure zone in which planar articles are processed. The planar articles travel through the roll gap and are pressure-loaded by the two rolls of the calender.

[0003] Modern applications of calenders demand the highest precision during operation. In particular, the precise dimensional determination of the roll gap is crucial. Special attention is paid to the defined settings, especially the constancy of the roll gap height along its entire width, i.e., along the axial direction of the calender rolls. The actual distribution curve of the roll gap height – hereinafter referred to as the gap height – corresponds to the desired distribution curve of the roll gap height, which encounters regular and inherently unfavorable factors during operation. For example, roll deflection is problematic when calendering planar articles. This deflection is typically attributed to the deformation of the rolls when force is input into the planar article. In calendering, the rolls deform through linear forces in the roll gap. But it is precisely when high precision is required that other effects become a focus of attention. For instance, the rolls expand as the temperature rises. It is in the heated rolls that a completely uniform temperature distribution is impossible. Typically, in the heated rolls, the temperature drops at the edges, for example, due to cooled bearings or through larger surfaces through which heat can be dissipated. The uneven temperature distribution of the heated rollers leads to uneven thermal expansion and thus, undesirable deviations in the gap height, resulting in deflection in the sense of the invention. Furthermore, undesirable effects occur in the roller gap at the edges of the calendered planar article, leading to deflection in the sense of the invention. Through the force input from the roller into the calendered planar article, flattening occurs in the areas where the roller is in contact with the material web. Outside these areas, the roller is not flattened through contact with the planar article. This generates shear stress in the roller at the edges of the calendered planar article, which deforms the roller and thus affects the roller gap. Through the effects described herein, the gap height decreases towards the edges of the calendered planar article, resulting in an undesirable increase in the linear force in the roller gap towards the edges of the calendered planar article.

[0004] The possibility of dealing with, avoiding, or compensating for roll deflection is known from existing technology. One possibility is to use a plunger-supported roll, in which a device is arranged inside the roll that compensates for the deflection of the roll sleeve by inputting a mechanical force that resists the deflection.

[0005] This technology has problems in applications requiring extremely high precision when applying very high linear forces. For example, the thin sleeves of plunger-supported rollers cannot be manufactured with arbitrary precision. Furthermore, the power of plunger-supported rollers is limited, which relates to the maximum linear force to be introduced. Finally, it is only possible to heat the plunger-supported rollers very uniformly with difficulty.

[0006] The growing application area for calenders is the fabrication of electrodes for battery manufacturing. Here, conductive films are coated and subsequently calendered. The calendering determines the electrode's density, porosity, adhesion strength, and these parameters also determine the electrode's conductivity and final electrochemical performance. Here, a gap height accuracy of 1µm is required across the entire width of the roll gap for linear forces exceeding 500 N / mm up to 10000 N / mm.

[0007] In existing technology, calenders are used to manufacture electrodes, typically with a width not exceeding 800 mm. Larger widths result in roller deflection, which cannot be satisfactorily compensated for using conventional methods. This makes the application of crown to the rollers inflexible, especially with varying linear forces. However, larger widths are desirable because they significantly improve electrode production efficiency. Summary of the Invention

[0008] Therefore, the object of the present invention is to provide a calender and a method for operating the calender, which does not have the disadvantages described in the prior art, but provides the possibility of very uniform adjustment of the roll gap at high linear forces and large widths.

[0009] This task is solved by the features of claims 1 and 11.

[0010] A calender according to the invention for calendering planar articles has a first roller and a second roller. Preferably, the calender is configured for counter-electrode calendering. The first roller and the second roller are the working rollers of the calender. For example, it is conceivable that the first roller is the upper roller of the calender and the second roller is the lower roller. However, it is also conceivable that the second roller is the upper roller and the first roller is the lower roller. Furthermore, it is possible that the first roller and the second roller are arranged side-by-side and the planar article is guided between the first roller and the second roller from above, from below, or obliquely. It is also conceivable that the first roller and the second roller are oblique, i.e., that the axial direction of the rollers is not horizontal. Finally, it is conceivable that the rollers of the calender are oriented such that the pressing plane is oblique, i.e., particularly not perpendicular. The invention is not limited to a calender having only two rollers. In addition to the first roller and the second roller, the calender according to the invention can have other rollers.

[0011] According to the invention, the first roller and the second roller are configured to move relative to each other in an axial direction. Specifically, to move the rollers relative to each other, the first roller may be moved in its axial direction, or the second roller may be moved in its axial direction, or both the first and second rollers may be moved in their respective axial directions. The axial direction here refers to the axial direction of the first roller or the second roller and is typically perpendicular to the direction in which the planar article is fed to the calender.

[0012] During operation, the corresponding rollers rotate about their axial direction. In the context of this invention, the pressure zone plane is the plane containing both axial directions. The radial direction, in the context of this invention, is orthogonal to the pressure zone plane.

[0013] Additionally, the calender according to the invention has a first adjustment mechanism for bending the first roller by inputting a torque in the radial direction.

[0014] The possibility of bending the first roller using a first adjusting mechanism by inputting a torque in the radial direction, i.e., by inputting a force parallel to the plane of the pressure zone, provides the possibility of adjusting the gap height along the pressure zone from one end of the roll gap, through the center of the roll gap, to the other end of the roll gap. If, for example, the roll gap is greater at the center than at the ends, the first roller can be bent toward the second roller at the center. The effect of bending is greater at the center of the first roller than at the ends. In particular, the convexity of the roll body of the first roller or the roll bodies of both rollers can be compensated for by the bending at the center and ends. However, at the position between the center and the outer end, especially after about one-eighth of the roll gap to one-quarter of the roll gap (referred to here as the quarter point), overcompensation by the bending of the first roller typically occurs.

[0015] To avoid undesirable deviations in the clearance height, even at the quarter-point, the rollers are moved relative to each other in the axial direction. This movement of the rollers alters the clearance height distribution curve along the axial direction. The combination of this axial movement of the rollers and the resulting adjustment of the clearance height distribution curve through the relative movement of the profiles, along with the bending of the first roller by a torque input in the radial direction, allows for high-precision and reliable adjustment of the clearance height even at very large widths, such as 1500 mm or more, and under very high linear forces. In particular, the combination of bending and axial movement can also specifically compensate for undesirable deviations in the clearance height caused by uneven roller temperatures.

[0016] The advantageous design and further configuration of the invention can be derived from the dependent claims and the description, with reference to the accompanying drawings.

[0017] According to a preferred embodiment of the invention, the first roller has a first profile, and the second roller has a second profile. The profile of the roller is the surface morphology of its peripheral surface and relates to a distribution curve of the roller extending orthogonally to the respective axial direction. The profile is preferably configured to generate a desired distribution curve of the gap height, particularly a uniform gap height between the rollers, through movement along the axial direction. Preferably, the first and second profiles are S-shaped. Alternatively or additionally, it is preferred that the first and second profiles have a 0.5S shape or multiple 0.5S shapes, particularly a 1.5S shape. Alternatively or additionally, it is preferred that the first and second profiles have a double S-shape. For this purpose, it is preferably configured that the first and second profiles have at least one, at least two, or at least three inflection points. That is, the first and second rollers are not implemented in a cylindrical or truncated conical shape, but rather as regions with different slopes along the roller width. This results in different roller diameters along the roller width, the roller diameters having a non-linear distribution curve along the axial direction. Nonlinear optimization also includes the adjacent arrangement of multiple non-parallel linear segments. The diameter deviations of the two rollers compensate for each other based on their relative positions along the axial direction, thus allowing the desired, especially uniform, gap height to be adjusted entirely according to existing needs without overcompensation. Besides the explicitly mentioned 0.5S-shape, S-shape, 1.5S-shape, and double S-shape, other profiles are conceivable, having other numbers, especially larger numbers, of S-shapes, such as 1.75S-shape, 2.5S-shape, 3S-shape, etc.

[0018] Specifically, the contours are configured such that they have polynomial distribution curves of at least or exactly three degrees, or at least or exactly four degrees, or at least or exactly five degrees. It is conceivable that convexity is superimposed on the 0.5S-shape, S-shape, 1.5S-shape, and / or double S-shape of the first roller. It is conceivable that convexity is alternatively or additionally superimposed on the S-shape, 1.5S-shape, and / or double S-shape of the second roller.

[0019] During axial movement, the area to be compensated can be freely selected by correspondingly adapting the profile. By selecting the corresponding profile, a large degree of freedom is obtained, so that the roll gap can be personalized to the greatest extent, especially regarding the number of affected locations, the position of the influence in the roll gap, and the width of the affected area.

[0020] The characteristic of a polynomial distribution curve or profile having a polynomial of at least or exactly a certain degree should not be interpreted rigidly mathematically. Rather, it should be considered as a description of the basic shape of the corresponding profile, conforming to the linguistic conventions of those skilled in the art in their daily work. Thus, it is conceivable that, in practice, the profile is described in place of a discrete table of values, including the corresponding rollers, extending radially and dependently in the axial direction, instead of mathematical functions. If the majority of the values ​​in the table can be approximated by a polynomial distribution curve within the error limits of technical practice, then the corresponding profile corresponds to that polynomial in the sense of the invention. If individual values ​​or small ranges in the table cannot be approximated by a polynomial distribution curve within the error limits of technical practice, this does not diminish the foregoing.

[0021] In another preferred embodiment of the invention, the two first roller necks of the first roller are supported in a first main bearing. A first adjusting mechanism acts on an additional first bending bearing, which also supports the first roller necks. The axial distance between the first main bearing and the adjacent first bending bearing is at least 0.8 times, preferably at least 1 time, and particularly preferably at least 1.2 times the diameter of the first roller. This significantly reduces the load on the main bearing when the first roller is bent by the first adjusting mechanism. Preferably, the main bearing is disposed axially between the bending bearing and the corresponding roller body. However, it is also conceivable that the bending bearing is disposed axially between the main bearing and the corresponding roller body. For this purpose, it is conceivable that a difference in the forces input on the bending bearing and the main bearing is generated, causing the rollers to bend away from each other at the center of the roller gap. Depending on the torque input on the bending bearing, it can be configured such that a force acts on the rollers on the main bearing, pulling the rollers toward each other or pressing them apart. Here, it is conceivable that at least one of the rollers has a crown. Typically, the crown is designed for a defined linear force or a defined material-induced deflection. It is conceivable that, especially in calendering with a smaller linear force than considered in the design of the convexity or with a smaller deflection caused by the material than considered in the design of the convexity, the convexity can be suppressed at least in part by bending.

[0022] To accommodate the bending of the roll neck, it is conceivable that, in particular, the first bending bearing, but also the first main bearing, has an auto-aligning bearing, such as an auto-aligning roller bearing, an auto-aligning ball bearing, or a cylindrical roller bearing comprising a spherical outer ring. It is conceivable that the first main bearing has a cylindrical roller bearing. This makes it possible to reliably accept large forces and reliably support the roll. It is conceivable that the first bending bearing also has a cylindrical roller bearing. Through the flexure or bending, both the first main bearing and the first bending bearing move at least partially.

[0023] Specifically, the first bending bearing and the first main bearing are configured to have outer rings. Furthermore, the first main bearing and the first bending bearing are kinematically decoupled from each other. Kinematic decoupling, in the sense of the invention, means that the outer ring of the first main bearing can be adapted to the bending of the roll neck in a way that is different from the inner ring of the first bending bearing and / or from the first bending bearing in terms of rotation about the radial direction. For this purpose, it is particularly conceivable that the first bending bearing and the first main bearing are housed in separate housings.

[0024] It is conceivable that both the first main bearing and the first bending bearing are cylindrical roller bearings. Furthermore, it is specifically designed that the first main bearing and the first bending bearing are kinematically decoupled from each other. Kinematic decoupling here means that the outer ring can be adapted to the bending of the roll neck in a different way about the radial direction. For this purpose, it is particularly conceivable that the first bending bearing and the first main bearing are housed in separate housings.

[0025] Preferably, the first adjusting mechanism is configured to press the first roller neck along the pressure plane away from the roller gap into the first main bearing. Alternatively or additionally, preferably, the first adjusting mechanism is configured to press the first roller neck along the pressure plane towards the roller gap into the first main bearing. It is conceivable that the first adjusting mechanism is configured to press the first roller neck, at least by the weight of the first roller, along the pressure plane away from the roller gap into the first main bearing. This advantageously ensures that the first roller is always tightly positioned within the first main bearing and that the bearing clearance of the first main bearing is suppressed. This ensures extremely accurate and stable adjustment of the roller gap during gap movement of the calender, especially during alternating thicknesses of the planar articles fed to the calender. Those skilled in the art understand "gap movement" to mean a predetermined gap height. This gap height is also maintained for different material parameters of the planar articles and results in varying linear forces before calendering, for example, during varying thicknesses of the planar articles. Alternatively, the calender can be moved "for pressure." Here, the linear force remains constant.

[0026] In another preferred embodiment of the invention, the first and second profiles are configured such that, in the relative positions of the first and second rollers, when the adjusting mechanism presses the first roller neck away from the roller gap into the first main bearing along the pressure plane, the roller gap has a uniform gap height in the axial direction. In other words, bending of the first roller caused by the first adjusting mechanism has been taken into account in the forming of the first and second profiles. This ensures, for example, that the first roller is tightly pressed into the first main bearing by the first adjusting mechanism, and the resulting bending of the first roller is detected in the geometry of the first and second profiles when correcting for expected deflection during the operation of the calender. For this purpose, it is preferably configured such that, in the relative positions of the first and second rollers, when the first adjusting mechanism presses the first roller neck away from the roller gap into the first main bearing radially, at least by the weight of the first roller, the roller gap has a uniform gap height in the axial direction.

[0027] Specifically, the calender is configured to have two first adjusting mechanisms, which act on the opposing first roll necks of the first roll in the axial direction. The two first adjusting mechanisms, according to the embodiment described herein, are configured to act on the opposing first roll necks to different degrees. In other words, according to this preferred embodiment, the first adjusting mechanisms act more strongly or less strongly on one axial end of the first roll than on the other axial end. This creates the possibility of asymmetrical bending and thus compensates for the asymmetrical deflection of the first roll. In asymmetrical bending, the maximum value of the bend produced by the bending of the corresponding roll moves from the center of the roll gap in the axial direction or opposite to it.

[0028] In addition to the first adjusting mechanism for bending the first roll, the calender is preferably configured to have a second adjusting mechanism for bending the second roll by inputting a torque in the radial direction. Preferably, the two second roll necks of the second roll are supported in a second main bearing, wherein the second adjusting mechanism acts in an additional second bending bearing, in which the second roll necks are supported. Particularly preferably, the second bending bearing and the second main bearing are spaced apart from each other by at least 0.8 times, more particularly preferably at least 1 times, and especially at least 1.2 times, the diameter of the second roll. The possibility of additional bending of the second roll allows for the use of a significantly greater diversity of compensation possibilities to establish a uniform roll gap. Thus, for example, symmetrical or even asymmetrical compensation of deflection can be achieved by adding bending of the first roll to the bending of the second roll. All the features, details, and advantages disclosed regarding the bending of the first roll using the first adjusting mechanism also relate to the bending of the second roll using the second adjusting mechanism.

[0029] It is conceivable that the second main bearing has cylindrical roller bearings. This allows for reliable acceptance of large forces and reliable support of the roller. It is also conceivable that the second bending bearing has cylindrical roller bearings. Through the aforementioned flexure or bending, both the second main bearing and the second bending bearing move at least partially. To accommodate the bending of the roller neck, it is conceivable, particularly the second bending bearing, but also the second main bearing, to have self-aligning bearings, such as self-aligning roller bearings or self-aligning ball bearings or cylindrical roller bearings comprising a spherical outer ring.

[0030] Specifically, the second bending bearing and the second main bearing are configured to have outer rings that are kinematically decoupled from each other. For this purpose, it is particularly conceivable that the second bending bearing and the second main bearing are housed in separate housings.

[0031] It is conceivable that the second adjustment mechanism is preferably configured to cause the second roll neck to be pressed into the second main bearing in the radial direction away from the roll gap, especially by the weight of the second roll or towards the roll gap.

[0032] In another preferred embodiment of the invention, the first and second profiles are configured such that, in the relative positions of the first and second rollers, during calendering, when the first adjusting mechanism presses the first roller neck along the pressure plane away from or toward the roller gap into the first main bearing and the second adjusting mechanism presses the second roller neck along the pressure plane away from or toward the roller gap into the second main bearing, the roller gap has a desired and, in particular, uniform gap height in the axial direction. In other words, bending of the first roller is induced by the first adjusting mechanism and bending of the second roller by the second adjusting mechanism during the forming of the first and second profiles. This, for example, ensures that the rollers are tightly pressed into the main bearings by the respective adjusting mechanisms, and that the resulting bending of the rollers is detected in the geometry of the first and second profiles when correcting for anticipated deflection during the operation of the calender. For this purpose, it is preferred that the first profile and the second profile are configured such that, in the relative positions of the first roller and the second roller, when the first adjusting mechanism presses the first roller neck into the first main bearing radially away from the roller gap at least by the weight of the first roller, the roller gap has a desired and especially uniform gap height in the calendering direction along the axial direction.

[0033] Furthermore, it is conceivable that the calender has two second adjustment mechanisms, which act on the axially opposed second roll necks of the second roll. The two second adjustment mechanisms are configured to act on the opposed second roll necks to varying degrees.

[0034] According to a preferred embodiment of the invention, the deflection at the center of the roll is fully compensated by the bending of the first and / or second rolls through a radial torque input, and the resulting overcompensation at the quarter point is compensated by the axial movement of the rolls relative to each other. For this purpose, it is preferably configured that the first and / or second profiles are double S-shaped. For example, the first and / or second profiles correspond to a polynomial of at least or exactly the fifth degree.

[0035] If the deflection is compensated solely by axial movement, it is conceivable that the first and second profiles are S-shaped and preferably correspond to polynomials of at least or exactly third degree.

[0036] Alternatively, the distribution of roll gap correction between bending and axial movement for a desired roll gap distribution curve can also be chosen differently. It is conceivable that the deflection is compensated only partially, for example, 2 / 3, by the bending of the first and / or second rolls, with the remaining compensation achieved through axial movement. It is conceivable that the first and / or second profiles are for this purpose only an S-shape. For example, the first and / or second profiles could be configured to correspond to a polynomial of at least or exactly third degree.

[0037] In particular, it is conceivable to additionally and specifically affect the quarter-point. For this purpose, it is configured to apply an alternative distribution of compensation through bending and axial movement. Preferably, this configuration involves the superposition of the S-shapes of the first and second profiles with a double S-shape. For this purpose, for example, the first and second profiles are configured to correspond to a polynomial of at least or exactly fifth degree. If, for example, the roll gap should be narrowed at the quarter-point, the share of compensation through bending increases and the share of compensation through axial movement decreases. Conversely, if the roll gap should be narrowed less drastically at the quarter-point, the share of compensation through axial movement increases, while the bending caused by the torque input in the radial direction decreases.

[0038] Furthermore, it is conceivable that the deflection is compensated for in such a manner by bending that overcompensation is just about to occur, particularly at the quarter point. The remaining deflection, especially at the center of the roll gap, is compensated for by axial movement. For this purpose, the first profile and / or the second profile has an S-shape. By varying the proportions of bending and axial movement, the gap height at the quarter point and at the roll center can be affected in a similarly different way.

[0039] It is also conceivable that, by means of a bend at the center of the roll gap, the deflection is specifically overcompensated, so that the distribution curve of the roll gap height from the center of the roll gap to the quarter point changes only slightly and remains essentially constant, solely by the bend, i.e., without the influence of axial movement. To compensate at the edge of the roll gap, i.e., outside the quarter point, an S-shape with an elongation of the S along the length of the roll gap is required.

[0040] That is, it is possible to completely influence the roll gap by different allocations of axial movement and bending proportions in compensation for deflection, and to consider in this way the given technical conditions that would otherwise be dictatedly not taken into account. The flexibility gained by the combination of axial movement and bending has significant advantages in extremely accurate calendering with the highest linear force necessary, as is required in calendering of electrodes.

[0041] This flexibility is further enhanced when, in addition to or alternative to axial movement and bending, asymmetrical pressure is applied to the first and / or second rolls. It is conceivable that this would cause at least one roll to tilt. The asymmetrical pressure application can be generated by unequal force inputs on the opposing main bearings of the rolls, particularly by force inputs on the opposing main bearings of the rolls that are independently adjusted from each other.

[0042] Five zones of the roll gap can be roughly distributed and influenced by a proportion of symmetrical pressure application, a proportion of symmetrical bending (i.e., by the same torque input on the opposite roll necks), a proportion of asymmetrical bending (i.e., by unequal torque input on the opposite roll necks), a proportion of asymmetrical pressure application, and a proportion of axial movement. These five zones are the two quarter points, the area at the center of the roll gap between the quarter points, and the edge of the roll gap, i.e., the area between the quarter points and the roll necks. In particular, the edge of the roll gap in contact with the planar article can also be influenced by a combination of axial movement, symmetrical and / or asymmetrical bending, and preferably asymmetrical pressure application. This is particularly advantageous because these areas often belong to critical areas in calendering, and planar articles outside the quarter points are often not calendered with satisfactory precision.

[0043] A significant increase in flexibility is achieved through asymmetrical bending and asymmetrical pressure application. The edges of the roll gap are thus affected in the same way by applying only symmetrical pressure or bending. Similarly, the quarter point is affected in the same way by applying only symmetrical pressure or bending. If bending and / or pressure application are applied asymmetrically, it is possible to decouple the influence on the geometry of the roll gap at the edges, quarter points, and center by affecting the edges and quarter points independently of each other, and thus, asymmetrical bending and / or asymmetrical pressure application helps to compensate for the asymmetrical proportion of deflection.

[0044] Particularly advantageous is the compensation for deflection by bending and axial movement in the edge regions of the calendered planar article. These edge regions can be the outer edge regions of the calendered planar article within the roll gap. However, it is also common in electrode calendering that the planar article is not coated across its entire width, but rather has uncoated longitudinal strips. These longitudinal strips can be externally positioned – with respect to the roll gap – i.e., adjacent only to the area of ​​the coating to be calendered on one side. Alternatively or additionally, the longitudinal strips can be internally positioned – also with respect to the roll gap – i.e., adjacent to the area of ​​the coating to be calendered on both sides. From these uncoated areas, for example, the contacts of the electrode can be manufactured in a later manufacturing step. The longitudinal strips have an extension transverse to the material travel path, i.e., along the roll gap, and a main extension direction along the material travel path, i.e., transverse to the roll gap. In the calendering of planar articles with longitudinal stripes, the roller does not contact the planar article in the region of the longitudinal stripes, thereby effectively setting the edge region of the calendered planar article on the longitudinal stripes. During calendering, the roller flattens the planar article by force input in the region where it directly contacts the calendered planar article. This flattening is similar to Hertzian pressing, except that, according to the theory of Hertzian pressing, no planar article is positioned between the cylinders being considered there. Outside the region where the roller contacts the planar article, no force input occurs onto the planar article. In the transition region between the Hertzian-like flattening and the unaffected region outside the edge region of the planar article, the difference between the flattened and unflattened shapes of the roller results in shear stress in the roller. The result is a narrowing of the roller gap towards the edge region and an increase in linear force towards the edge region. In the absence of internally arranged longitudinal strips, but for example with longitudinal strips not arranged externally, compensation for the effects described herein is possible only through a profile having a 0.5S-shape. If the planar article has the longitudinal strips, the axial movement of a roller with a corresponding profile can be used to specifically compensate for the portion of deflection in the edge region of the planar article caused by the shear stress of flattening by the roller. In the case of two longitudinal strips, i.e., three coating areas on the planar article, a 2.5S-shape profile is required for this purpose, for example. Because the roller does not contact the planar article in the region of the longitudinal strips, it becomes possible to adjust the profile segments here, which are not limited in shape, i.e., must be suitable for calendering. Thus, for example, a very steep distribution curve of the profile up to the step portion can be set. These areas unsuitable for calendering are not the parts of the S-shape and polynomial description of the profile in the sense of the present invention.If, for example, a step portion in the region of a longitudinal strip is provided for height compensation of the profile curve, the profile can be described in the sense of the invention by means of an S-shape and / or polynomial, as previously explained, without omitting the step portion. Functionally, at least similar, very steep regions are identical to the step portion.

[0045] It must be clearly emphasized that the number and location of areas affected by the roll gap can be influenced by the construction of the profile. The possibilities in constructing the profile, the possibility of asymmetrical bending, and the possibility of applying asymmetrical pressure thus provide degrees of freedom for influencing the geometry of the roll gap, degrees of freedom that can be achieved with excellent results in the calendering of the electrodes.

[0046] It should be noted that the calender can operate in both pressure and gap operation modes. The details and specifics described throughout the disclosure relate to both pressure and gap operation modes. In pressure operation mode, the calender is operated such that a uniform pressure is applied across the roll gap. In gap operation mode, the calender is operated such that the desired gap height is adjusted and readjusted, wherein, as in pressure operation mode, pressure is applied to the main bearing.

[0047] In another preferred embodiment of the invention, the movement of the first roller along the axial direction occurs simultaneously with the movement of the first roller neck through the first main bearing and preferably through the first bending bearing. It is also conceivable, alternatively or additionally, that the movement of the second roller along the axial direction occurs simultaneously with the movement of the second roller neck through the second main bearing and preferably through the second bending bearing. In other words, at least components of the main bearing or bending bearing remain fixed as the roller moves along the axial direction.

[0048] The axial movement of the first roller preferably causes movement of the inner ring of at least one of the first main bearings. Specifically, it is configured such that the rolling elements and / or outer rings of the at least one of the first main bearings do not move when the first roller moves axially. Furthermore, it is preferably configured such that the outer ring and / or rolling elements of the first curved bearing do not move when the first roller moves axially. The axial movement of the first roller preferably causes movement of the inner ring of at least one of the first curved bearings. Specifically, it is configured such that the rolling elements and / or outer rings of at least one of the first curved bearings do not move when the first roller moves axially. It is conceivable that the rolling elements of the first main bearing and / or the first curved bearing are guided only on the corresponding outer rings. This prevents the rolling elements from moving together. It is also conceivable that the rolling elements of the first main bearing and / or the first curved bearing are guided only on the corresponding inner rings. This causes the rolling elements to move together. Furthermore, it is conceivable that the inner ring of at least one of the first main bearings or the first curved bearing is formed by a first roller neck. For this purpose, the first roller neck is preferably hardened in the region of the corresponding bearing.

[0049] Preferably, a spacing mechanism is provided between the first main bearing of the first roller and the second main bearing of the second roller. It is conceivable that the spacing mechanism is configured to adjust a defined distance between the first and second main bearings and thereby influence the roller clearance. The spacing mechanism may, for example, include a spindle, a wedge, or a hydraulic cylinder.

[0050] Alternatively or additionally, the movement of the second roller in the axial direction causes movement of the inner ring of at least one of the second main bearings. In particular, it is configured that the rolling elements and / or outer rings of the at least one of the second main bearings do not move when the second roller moves in the axial direction. Furthermore, it is preferably configured that the outer ring and / or rolling elements of the second curved bearing do not move when the second roller moves in the axial direction. The movement of the second roller in the axial direction preferably causes movement of the inner ring of at least one of the second curved bearings. In particular, it is configured that the rolling elements and / or outer rings of at least one of the second curved bearings do not move when the second roller moves in the axial direction. It is conceivable that the rolling elements of the second main bearing and / or the second curved bearing are guided only on the corresponding outer rings. Thus, the rolling elements do not move together. It is also conceivable that the rolling elements of the second main bearing and / or the second curved bearing are guided only on the corresponding inner rings. Thus, the rolling elements move together. Furthermore, it is conceivable that the inner ring of at least one of the second main bearings or the second curved bearing is formed by a second roller neck. For this purpose, the second roller neck is preferably hardened in the region of the corresponding bearing.

[0051] In another preferred embodiment of the invention, the calender has a first axial adjustment mechanism for moving the first roller in the axial direction. It is conceivable that the first axial adjustment mechanism has a first annular cylinder. This advantageously ensures that the axial force required for this axial movement acts centrally. The corresponding axial bearing is thus uniformly loaded, which in turn results in a uniform load on the roller. Finally, the central action of the axial force and the resulting uniform loading prevent undesirable influence on the curvature, i.e., geometry, of the roller gap.

[0052] In another preferred embodiment of the invention, the first annular cylinder has a first expansion chamber configured to be filled with an expansion medium, preferably hydraulic oil. This advantageously allows the first annular cylinder to be moved by introducing the expansion medium. The use of hydraulic oil is particularly advantageous because hydraulic oil, as a liquid, is virtually incompressible and the expansion path of the first expansion chamber is thus highly defined.

[0053] Preferably, the first expansion chamber is closed by a fixed first portion and an axially movable first annular piston. The first expansion chamber increases axially by introducing an expansion medium. Here, the first annular piston moves axially. Using the fixed first portion and the defined axially movable first annular piston allows the introduction of the expansion medium into the first expansion chamber to be very precisely translated into movement of the first axial adjustment mechanism. Preferably, the fixed first portion and the first annular piston each have L-shaped sections in their cross-sections with respect to the axial direction. The legs of the L-shaped sections of the movable first portion are offset along the legs of the L-shaped sections of the first annular piston. The first expansion chamber formed between the L-shaped sections is preferably sealed outwards by a sealing device.

[0054] For this purpose, it is preferably configured such that the first annular piston is operatively connected to the first roller, and particularly to one of the first roller necks, to receive axial forces. In other words, the axial force is transmitted from the first annular piston to the first roller, and particularly to one of the first roller necks. Thus, advantageously, the movement of the first annular piston can be directly converted into the movement of the first roller. Preferably, the first annular piston is supported on the first roller neck by a first axial bearing. In particular, the first axial bearing is a rolling bearing, especially preferably an axial cylindrical roller bearing. This enables easy operation of the first roller.

[0055] In another preferred embodiment of the invention, the calender has a further first axial adjustment mechanism for moving the first roller in the opposite axial direction. This further first axial adjustment mechanism has a further first annular cylinder, which preferably has a further first expansion chamber configured to be filled with an expansion medium, particularly hydraulic oil. This allows for advantageous movement of the first roller not only in the axial direction but also in the opposite direction, and centrally applies the necessary axial force. Furthermore, it is conceivable that the first expansion chamber and the further first expansion chamber are filled under pressure, so that the axial position of the first roller can be fixedly maintained by the first axial adjustment mechanism and the further first axial adjustment mechanism.

[0056] It is conceivable that the additional first axial adjustment mechanism is disposed on the same first roller neck as the first roller, where the first axial adjustment mechanism is also disposed. The additional first expansion chamber is closed by an additional fixed first portion and an additional first annular piston movable in the opposite axial direction. The additional first expansion chamber increases in the opposite axial direction by introducing an expansion medium, wherein the additional first annular piston moves in the opposite axial direction. The additional first annular piston is operatively connected to the first roller neck for receiving axial forces. Preferably, the additional first annular piston is supported on the first roller neck by an additional first axial bearing, particularly a rolling bearing. In other words, the additional first axial adjustment mechanism is disposed on the same roller neck as the first axial adjustment mechanism. Therefore, axial adjustment of the first roller can advantageously be caused from only one side in a simple manner, enabling, for example, technical synergies involving the arrangement of control or supply lines. It is conceivable that the first and second axial bearings have a common ring, with the rolling elements of the first axial bearing running through one side of the ring and the rolling elements of the second axial bearing running through the other side of the ring, and the ring being fixedly connected to the roller neck in the axial direction.

[0057] Alternatively, the additional first axial adjustment mechanism is disposed on the first roll neck of the first roll, while the first axial adjustment mechanism is not disposed on the first roll neck. The two first roll necks of the first roll are opposite to each other. The additional first expansion chamber is closed by a fixed additional first portion and an additional first annular piston movable in the opposite axial direction. By introducing an expansion medium, the additional first expansion chamber increases in the opposite axial direction, wherein the additional first annular piston moves in the opposite axial direction. The additional first annular piston is operatively connected to the first roll neck for receiving axial forces, wherein the additional first annular piston is preferably supported on the first roll neck by an additional first axial bearing, in particular a rolling bearing. In other words, the first axial adjustment mechanism is disposed on one side of the first roll and the additional first axial adjustment mechanism is disposed on the other side of the first roll. The embodiment described herein has the advantage that the calender is symmetrically constructed, which is structurally simpler to construct and provides the possibility of implementing the first and second axial adjustment mechanisms at least partially structurally identical. Furthermore, the arrangement of the axial adjustment mechanisms on different sides of the roll provides the advantage of a smaller overall width of the calender.

[0058] However, it is also conceivable that the first axial adjustment mechanism and / or the second axial adjustment mechanism and / or the additional first axial adjustment mechanism and / or the additional second axial adjustment mechanism act on the axial bearings of the main bearing and / or the axial bearings of the bending bearing. For this purpose, it is conceivable that the main bearing and / or the bending bearing have combined radial-axial bearings. Thus, it is conceivable that the main bearing and / or the bending bearing have angular contact ball bearings, angular contact roller bearings, and / or self-aligning roller bearings. Furthermore, it is conceivable that the axial adjustment mechanism causes axial movement of the roller through the housing of the main bearing and / or the bending bearing. To introduce axial force for axial movement, the axial adjustment mechanism may, for example, have a spindle, a pneumatic mechanism, an electric motor, and / or a hydraulic mechanism.

[0059] In another preferred embodiment of the invention, the fixed first portion is supported on a first main bearing in the opposite axial direction. The first main bearing is configured to support a first roll neck of the first roll. The first main bearing is capable of receiving the axial force of the first axial adjustment mechanism. This results in an advantageously simple method for fixing the fixed first portion. It is conceivable that the first main bearing has a cylindrical roller bearing. This enables reliable acceptance of large forces and reliable support of the roll. The distribution of deflection compensation described herein also relates to the method according to the invention, which is further explained below.

[0060] In another preferred embodiment of the invention, the calender is configured to have a mechanism for temperature control of the first and / or second rollers. This temperature control mechanism can be used to heat or cool the first or second rollers. An optimized temperature range is often present in calendering, particularly in the calendering of electrodes, within which calendering is performed. The temperature used for calendering must be increased or decreased depending on the temperature of the planar article entering the calender. To achieve the optimized temperature range directly in the calendering region, heat can be transferred from the planar article to the rollers, i.e., the planar article can be cooled. Furthermore, heat can be released from the rollers onto the planar article. To generate this heat flow, a temperature difference is required between the planar article and the roller surfaces. The transferred heat power depends on the temperature difference, which can be adjusted such that the temperature of the first and / or second rollers is controlled, i.e., the temperature of the roller surfaces of the first or second rollers is increased or decreased as needed. To increase the temperature, the first and / or second rollers are heated; to decrease the temperature, the first and / or second rollers are cooled. It is conceivable that the first and / or second rollers are heated to input heat into the planar article. However, it is also conceivable that the first and / or second rollers are heated to remove heat from the planar article. This is, for example, when the temperature difference between the roller surface and the planar article is so large that excessive heat removal from the planar article would occur without heating the rollers. Similarly, it is conceivable that the first and / or second rollers are cooled to remove heat from the planar article. However, it is also conceivable that the first and / or second rollers are cooled to input heat from the rollers into the planar article. This is when the rollers are hotter than the planar article, and the temperature difference is so large that it would result in excessive heat input into the planar article.

[0061] Preferably, the first and / or second rolls of the calender are heated to increase the temperature of the respective roll surfaces. This also makes the calender well-suited for use in electrode manufacturing. The first and / or second rolls can be heated electrically or inductively, for example, by induction coils. However, it is also conceivable to heat the first and / or second rolls with steam, which is guided, for example, through a central hole or through peripheral holes. Preferably, the first and / or second rolls are configured for oil heating, with the oil flowing through the peripheral holes. The roll surfaces of the first and / or second rolls are preferably heated to at least 80°C and more particularly preferably at least 100°C. It is also conceivable to heat the roll surfaces of the first and / or second rolls, for example, by providing electric heating elements in the peripheral holes of the first or second roll.

[0062] Preferably, the first and / or second rollers of the calender are cooled to reduce the temperature of the corresponding roller surfaces. This also better suits the calender for use in the manufacture of electrodes that must be calendered within a defined temperature range. If the planar article to be calendered is conveyed at a temperature above said temperature range, the temperature can be reduced to an optimized range by the cooled rollers.

[0063] The first and / or second rollers may be cooled, for example, with a coolant, which is preferably guided through a central hole or through a peripheral hole.

[0064] In another preferred embodiment of the invention, a region is provided in the roll gap through which the planar article to be calendered is guided and calendered, and this region is also referred to as the calendering region within the scope of this disclosure. Furthermore, the calender is configured to have mechanisms for cooling the roll surface of a first roll and / or for cooling the roll surface of a second roll, these mechanisms preferably acting from outside the roll and cooling the roll surface outside this region (also referred to herein as the non-calendering region) and preferably partially within this region. The non-calendering region also includes, in particular, the region through which the aforementioned longitudinal strip passes through the roll gap. In addition to heat release through air, the roll surface of the heated roll releases heat to the planar article being calendered, while the roll surface of the heated roll releases heat only to the air to the left and right of the calendering region. This effect is further enhanced in rolls heated by means of peripheral holes. On the left and right sides of the planar article, due to the reversal of the heat medium in this region of the roller, a significantly higher temperature can exist on the roller surface compared to the region of the roller that comes into contact with the planar article. Therefore, particularly in the edge regions of the planar article, undesirable changes in roller geometry and thus undesirable effects on the roller gap can occur, resulting in distortion of linear forces. To prevent the region of the roller that does not come into contact with the planar article from expanding intensely due to stronger heating, causing undesirable effects in the roller gap, until the first and second rollers come into contact outside the area through which the planar article is guided, the cooling mechanism cools the heated rollers in these critical regions. Furthermore, this cooling ensures that the temperature profile in the roller gap remains constant, especially that the rollers are not hotter in the edge regions of the planar article than, for example, in the center of the roller gap. Axial movement of the rollers relative to each other further intensifies the temperature gradient and the accompanying negative effects. The portion of the roller that protrudes beyond the planar article to be calendered is heated even more intensely. This results in a situation where the area where the roller is introduced but does not receive heat through the planar configuration is larger than on the opposing side. The less protruding portion of the roller is less hot. In particular, a temperature difference is also achieved between the first and second rollers at the opposing positions in the roller gap. To prevent undesirable effects on the geometry of the roller gap, it is preferable that the cooling mechanisms are independently adaptable to each other and, in particular, asymmetrically operate in terms of their respective cooling power. This allows for a direct and targeted solution to the problem and provides cooling as required. Furthermore, it is conceivable that the cooling mechanisms can move independently of each other in the axial direction. This allows the cooling mechanisms to be individually and precisely positioned at the locations where heat must be dissipated from the rollers.Finally, it can be envisioned that the temperature distribution of the rolls and thus the geometry of the roll gap are specifically affected by different degrees of cooling, for example by different degrees of cooling on both sides of the rolls and / or by different cooling of the first and second rolls.

[0065] It is also conceivable that the calender has mechanisms for heating the surface of the first roll and / or for heating the surface of the second roll, preferably acting from outside the roll and heating the roll surface in the non-calendered area and preferably partially in the calendered area. The non-calendered area particularly includes the area where the longitudinal strips pass through the roll gap as described above. The cooled roll receives heat from the calendered planar article in addition to heat from the air, while the surface of the cooled roll receives heat only from the air on the left and right sides of the calendered area. This effect is further enhanced in rolls cooled by means of peripheral holes. On the left and right sides of the planar article, due to the reversal of the coolant in this area of ​​the roll, a significantly lower temperature of the roll surface can exist compared to the area of ​​the roll that comes into contact with the planar article. Therefore, particularly at the edge areas of the planar article, undesirable changes in roll geometry and thus undesirable effects of the roll gap can occur, resulting in distortion of linear force. To prevent the areas of the rollers not in contact with the planar article from undergoing intense deformation due to stronger cooling, thus preventing undesirable effects in the roller gap, the heating mechanism heats the cooled rollers in these critical areas. Furthermore, this heating ensures a constant temperature profile in the roller gap, particularly that the rollers are not colder in the edge regions of the planar article than, for example, in the center of the roller gap. The temperature gradient and associated negative effects are further amplified by the axial movement of the rollers relative to each other. The portions of the rollers that protrude beyond the planar article to be calendered are cooled more intensely. This results in a larger area where heat is extracted from but not input through the planar article than on the opposing side. The less protruding portions of the rollers are less cold. Therefore, a temperature difference is achieved, particularly at the opposing positions in the roller gap, between the first and second rollers. To prevent undesirable effects on the geometry of the roller gap, it is preferably configured such that the heating mechanism can be independently adaptable to each other in terms of their respective heating power, and especially asymmetrically. This allows for direct and targeted solutions to the problem and reheating as needed. Furthermore, it is conceivable that the heating mechanisms can move independently of each other along the axial direction. Thus, the heating mechanisms can be individually and precisely positioned at locations where heat must be extracted from the rollers. Finally, it is conceivable that the temperature distribution of the rollers, and therefore also the geometry of the roller gap, can be specifically influenced by varying degrees of heating, for example, by varying degrees of heating on both sides of a roller and / or by varying degrees of heating on the first and second rollers. For example, it is conceivable that the heating mechanisms are configured for induction heating of the roller surface.

[0066] In another preferred embodiment of the invention, the first profile is introduced by grinding the surface of a first roll, wherein the first roll is heated to a temperature set for operation during grinding. This enables extremely high precision of the first profile during operation of the calender. This can at least partially compensate for temperature-induced changes in the roll geometry. Similarly, it is conceivable that the second profile is introduced by grinding the surface of a second roll, wherein the second roll is heated to a temperature set for operation during grinding. In particular, the polygonal effect, which occurs when the first roll is heated by means of the peripheral holes, can be compensated by the thermal grinding described herein. The temperature gradient of the roll between positions near and further away from the peripheral holes results in different thermally induced expansions of the roll body, which forms the calendered area. Through thermal grinding, the roll is ground in such a way that the different thermally induced expansions result in the desired peripheral shape during operation of the ground roll and, in particular, avoid the polygonal effect.

[0067] Particularly preferred is that the surface of the roll body of the first roll and / or the second roll is plated with hard chrome. It is also conceivable that the surface of the roll body of the first roll and / or the second roll is coated with tungsten carbide. Furthermore, it is preferably additionally or alternatively configured that the surface of the roll body of the first roll and / or the second roll is subjected to inductive edge layer hardening.

[0068] Another subject for addressing the task presented at the beginning is a method for operating a calender, particularly a calender according to the invention. The deflection of the first roller, particularly the deflection generated during the operation of the calender, is compensated by the axial movement of the roller and the bending of the first roller by means of a first adjusting mechanism via a torque input in the radial direction, such that the roller gap of the calender has a defined height distribution curve in the axial direction. The method according to the invention advantageously enables the high-precision calendering of planar articles, such as in the manufacture of electrodes, with a very high linear force over a large bandwidth. Even with widths significantly exceeding one meter, the gap height can be adjusted with a precision of 1 µm and a small margin across the entire width while simultaneously calendering with a linear force up to 10,000 N / mm.

[0069] Preferably, the first roller neck is pressed into the first main bearing in a direction away from or toward the roller gap by the first adjusting mechanism, thereby suppressing the bearing clearance of the first main bearing and / or the second roller neck is pressed into the second main bearing in a radial direction away from or toward the roller gap by the second adjusting mechanism, thereby suppressing the bearing clearance of the second main bearing.

[0070] The features, details, and advantages previously mentioned in connection with the calender according to the invention also apply to the method according to the invention.

[0071] In another preferred embodiment of the invention, the deformation caused by temperature of the first and / or second rolls of the calender is compensated for by axial movement of the rolls and bending of the first or second rolls by a torque input in the radial direction via a first or second adjusting mechanism, such that the roll gap has a desired gap height distribution curve in the axial direction. In particular, the deformation of the rolls can be compensated by axial movement and bending of the rolls by a torque input in the radial direction, the deformation arising from locally different temperatures and therefore locally different thermal expansion of the rolls. Attached Figure Description

[0072] Further details, features, and advantages of the invention will become apparent from the accompanying drawings and the subsequent description of preferred embodiments with the aid of the drawings. The drawings herein illustrate only exemplary embodiments of the invention and do not limit the inventive concept.

[0073] It is shown that:

[0074] Figure 1 A schematic view of a calender according to an exemplary embodiment of the invention, shown in an unloaded state, for implementing a method according to an exemplary embodiment of the invention;

[0075] Figure 2 A schematic view of a calender according to another exemplary embodiment of the invention is shown for implementing a method according to one exemplary embodiment of the invention;

[0076] Figure 3 A schematic view of a calender according to another exemplary embodiment of the invention is shown for implementing a method according to one exemplary embodiment of the invention;

[0077] Figure 4 A schematic view of the first and second rollers of a calender according to an exemplary embodiment of the invention, in different relative positions along the axial direction;

[0078] Figure 5 A schematic view of a calender according to another exemplary embodiment of the invention, shown in an unloaded state, for implementing a method according to one exemplary embodiment of the invention;

[0079] Figure 6 (a)-(d) show schematic views of the main bearing of a calender according to an exemplary embodiment of the invention;

[0080] Figure 7 A schematic view showing details of a calender according to another exemplary embodiment of the invention;

[0081] Figure 8 A schematic view showing details of a calender according to another exemplary embodiment of the invention;

[0082] Figure 9 A schematic view showing details of a calender according to another exemplary embodiment of the invention;

[0083] Figure 10 (a)-(b) show detailed views of prior art calenders and

[0084] Figure 11 (a)-(c) show detailed views of calenders according to different exemplary embodiments of the invention. Detailed Implementation

[0085] Figure 1 , 2 Figures 3, 5, 9, and 10 respectively illustrate calenders 100 according to different embodiments of the invention. As long as it relates not only to... Figure 1 The calender 100 shown in the figure and in Figure 2 , Figure 3 , Figure 5 and Figure 9 The features and details implemented in the calender 100 shown are then described together with the calender 100 shown. The differences between the calenders 100 shown are further explained below. Figure 11 The calender 100 shown is depicted with less detail for clarity, so that attention can be drawn to the details emphasized therein. Therefore Figure 11 Further explanation follows separately. However, with the help of... Figure 1 , 2 The same features and details discussed in points 3, 5, and 9 apply to... Figure 11 The calender 100.

[0086] Figure 1 Shown in the unloaded state Figure 2 A calender 100 is provided. The calender 100 is configured for calendering surface-shaped articles 10, particularly for manufacturing electrodes. For this purpose, the calender 100 has a first roller 1 and a second roller 2. It is conceivable that the calender 100 may have other rollers. However, the following description will be limited to the first roller 1 and the second roller 2 forming the working rollers of the embodiment shown.

[0087] The first roller 1 is supported in the first main bearing 5 by the first roller neck 3. The first main bearing 5 may include, for example, a rolling bearing, particularly a cylindrical roller bearing. In the embodiment shown here, rollers 1 and 2 are heated.

[0088] In the calendering of the electrode, the coated conductive film is rolled to a thickness of 40µm to 400µm with a linear force of 500N / mm to 10000N / mm. Precision here plays a crucial role in the subsequent functionality of the electrode. Thus, the porosity of the electrode is determined, for example, by calendering. Deviations in gap height of 2µm to 3µm have already resulted in almost unacceptable inaccuracies in the electrode manufacturing process. The calendering machine and method according to the invention enable compensation for undesirable deflection with deviations of 1µm or better.

[0089] If the coated film is calendered between the first roller 1 and the second roller 2, deformation of rollers 1 and 2 is forcibly caused. Rollers 1 and 2 flex. Similarly, rollers 1 and 2 deform due to the temperature difference that occurs along the rollers. Here, temperature inhomogeneity of several degrees Celsius can already cause an undesirable deviation in the gap height. This leads to an unacceptable deviation in the gap height, especially in calendering with a large width. To compensate for these deviations and achieve the desired, especially uniform, gap height, the calender 100 has a first adjusting mechanism 7 for bending the first roller 1 under a torque input in the radial direction R. Furthermore, the calender 100 shown here has a second adjusting mechanism 8 for bending the second roller 2 under a torque input in the radial direction R. The first adjusting mechanism 7 acts on the first bending bearings 11 and loads these first bending bearings with a force along the pressure zone plane, which in the illustrated embodiment is in the paper surface. The second adjusting mechanism 8 acts on the second bending bearings 12 and similarly loads these second bending bearings with a force along the pressure zone plane. Figure 2 In the state of compensated flexural deformation, it is shown Figure 1 The calender 100. For clarity, the effect of bending is shown in a strongly exaggerated manner. The first roller 1 is attached to the first main bearing 5 by the first roller neck 3 and is also supported in the first bending bearing 11. The second roller 2 is attached to the second main bearing 6 by the second roller neck 4 and is also supported in the second bending bearing 12. The bending bearings 11, 12 and the main bearings 5, 6 are spaced apart in the axial direction A by at least 0.8 times the roller diameter. Furthermore, the outer rings of the bending bearings 11, 12 and the main bearings 5, 6 (see...) Figure 6 , 7 8) Kinematic decoupling. Here, main bearings 5 ​​and 6 are shown positioned along axial direction A between bending bearings 7 and 8 and the corresponding roller body (not shown). However, it is also conceivable that bending bearings 11 and 12 are positioned along axial direction A between main bearings 5 ​​and 6 and the corresponding roller body.

[0090] exist Figure 6 Parts of the calender 100 are shown in (a) to (d), and one of the first main bearings 5 ​​is visible in said part. The first main bearing 5 is implemented here as a cylindrical roller bearing comprising an outer ring 5.1, an inner ring 5.2, and rolling elements 5.3. Figure 6In the embodiments shown in (a) and (b), the rolling element 5.3 is laterally guided by a rolling element guide device 5.4, which is connected to the outer ring 5.1. When the roller neck 3 moves in the axial direction A via the first axial adjustment mechanism 13 (see...), Figure 1 , 7 8), the inner ring 5.2 moves together, while the rolling element 5.3 is held in place by the rolling element guide 5.4 about the axial direction A and fixed to the outer ring 5.1. Figure 6 (c) shows an exemplary embodiment in which the rolling element guide 5.4 is fastened to the inner ring 5.2. Thus, as the inner ring 5.2 moves in the axial direction A, the rolling element 5.3 also moves. Figure 6 (d) shows an exemplary embodiment in which the inner ring 5.2 is formed by the roller neck 3 itself. For this purpose, the edge layer of the roller neck 3 is hardened. The rolling element guide 5.4 is here secured to the outer ring 5.1, so that the rolling element 5.4 does not move together in the axial direction A. The details shown here for the first main bearing 5 also apply to the second main bearing 6 and preferably to the first and second bending bearings 11, 12, the inner ring of the second main bearing moving with or without rolling elements.

[0091] In the embodiment shown here, the first adjusting mechanism 7 and the second adjusting mechanism 8 induce a torque input in the radial direction R via corresponding bending bearings 11 and 12, thereby pressing the rollers 1 and 2 away from the roller gap 9. The force input of the adjusting mechanisms 7 and 8 is indicated by arrows on the corresponding adjusting mechanisms 7 and 8. This force input causes the rollers 1 and 2 to bend such that the height of the roller gap 9 decreases at the center of the rollers 1 and 2.

[0092] The bending of rollers 1 and 2 via adjusting mechanisms 7 and 8 has another positive effect on calendering quality, in addition to its effect on adjusting roller gap 9. Thus, by adjusting mechanisms 7 and 8, a force input to the bending bearings 11 and 12, preferably at least the weight of the corresponding rollers 1 and 2, ensures that roller necks 3 and 4 are tightly seated in the main bearings 5 ​​and 6 and that bearing gaps are suppressed. The arrows indicate the forces acting on the main bearings 5 ​​and 6 here. It is precisely in the calendering of the planar article 10, with its alternating layer thickness prior to calendering, that the suppression of bearing gaps results in a significantly higher quality outcome in the intermittent operation mode of the calender 100.

[0093] The shape of the roll gap 9 is influenced by the bending of rolls 1 and 2 in the radial direction R, where, typically, the undesired deviation in the gap height at the center of the roll gap is overcompensated at the position between the center and the outer end. To eliminate this overcompensation, the first roll 1 has a first profile P1 and the second roll 2 has a second profile P2. Profiles P1 and P2 are ground into the roll bodies of the respective rolls 1 and 2 and are designed to achieve different roll diameters in the axial direction A. The figures show profiles P1 and P2 in a strongly magnified manner. Preferably, profiles P1 and P2 are thermally ground, i.e., during the grinding of profiles P1 and P2, the respective rolls are heated to a temperature corresponding to the temperature at which the rolls should operate in the calender 100.

[0094] In the embodiment shown here, contours P1 and P2 have different slopes and three inflection points are shown. The distribution curve of the height of the roll gap 9 along the axial direction can be adjusted by moving the first roll 1 and the second roll 2 relative to each other in the axial direction A. This is in Figure 4 As shown in [the image]. Figure 4 In the diagram, the first roll 1 and the second roll 2 are seen in three different relative positions along the axial direction A. In the uppermost relative position, the profiles P1 and P2 extend parallel to each other without load, i.e., without calendering of the planar article 10. Once the planar article 10 is calendered, this is changed by the force input generated during the rolling of the planar article 10. To compensate for this, the first roll 1 and the second roll 2 can move relative to each other along the axial direction A.

[0095] That is, the desired roll gap 9 is adjusted by a combination of bending and axial movement to compensate for the deflection. It is conceivable that the deflection is entirely compensated by the bending of the first roller 1 and the second roller 2 through a torque input in the radial direction R, and the resulting overcompensation at the quarter point is compensated by the movement of rollers 1 and 2 relative to each other in the axial direction A. For this purpose, the first profile P1 and the second profile P2 each have a double S-shape with a fifth-order polynomial structure. However, it is also possible to adjust the desired roll gap 9 by only partially, for example, 2 / 3, compensating for the deflection by the bending of the first roller 1 and the second roller 2, and the remaining compensation by movement in the axial direction A. For this purpose, profiles P1 and P2 are provided with only an S-shape with a cubic polynomial structure.

[0096] Alternatively, it can be configured to specifically affect the quarter point through axial movement. This can be achieved by varying the proportion of compensation for deflection, which is attributed to both axial movement and bending. For such a combination, one can envision the superposition of the S-shape with a double S-shape of the first contour P1 and the superposition of the S-shape with a double S-shape of the second contour P2, wherein the first contour P1 and the second contour P2 have a fifth-order polynomial structure.

[0097] Overall, a very flexible possibility of adjusting the desired roll gap 9 is achieved through a combination of symmetrical pressure applied in the main bearings 5 ​​and 6 by axial movement and bending. Additionally, it is also possible to influence the roll gap 9 by applying asymmetrical pressure. For this purpose, for example, different magnitudes of force can be introduced into the opposing main bearings 5 ​​and 6 of the rolls 1 and 2. Depending on the compensation for deflection to axial movement, symmetrical and asymmetrical bending, and the selective allocation of symmetrical and asymmetrical pressure application, the area of ​​the roll gap 9 can be adjusted specifically, and taking into account other effects of axial movement and bending, such as more or less pressure in the main bearings 5 ​​and 6 by stronger or weaker bending, i.e., particularly the area between the roll necks 3 and 4 and the quarter point, and the area between the quarter point and the quarter point.

[0098] Furthermore, it is possible to compensate for deflection by bending as much as possible until overcompensation occurs, especially at the quarter point. The remaining deflection, particularly at the center of the roll gap 9, is compensated by movement along the axial direction A. For this purpose, profiles P1 and P2 have an S-shape.

[0099] In the relative positions shown in the center, the first roller 1 moves to the left and the second roller 2 moves to the right. The relative positions of the first roller 1 moving to the right and the second roller 2 moving to the left are shown below. In the relative positions shown here, it is clear how the distribution curve of the height of the roller gap 9 changes due to the movement along the axial direction A. In particular, this can affect the region of the roller gap 9 between the outer end and the center.

[0100] It is preferable to monitor and adjust the position of the first roller 1 and / or the second roller 2 along the axial direction A when there is a deviation from the theoretical value.

[0101] In the calender 100 Figure 2 In the embodiment shown, rollers 1 and 2 are additionally provided with a convexity. This is achieved by considering... Figure 4 The polynomial shaping and superposition of the convexity of the contours P1 and P2 shown in the figure can be well adapted to the rollers 1 and 2 at high linear forces, precisely to match the desired load and the resulting deflection. Such superposition in Figure 3 As shown in the diagram, the contours P1 and P2 of rollers 1 and 2 have convexity in addition to the aforementioned double S-shape. To suppress this convexity, adjusting mechanisms 7 and 8 correct the deflection by inputting force along the pressure zone plane, thereby giving the roller gap 9 a desired gap height distribution curve.

[0102] What all the embodiments shown have in common is that they have a first axial adjustment mechanism 13, which is detailed in... Figure 7 and 8The following are different embodiments of the invention. A first axial adjustment mechanism 13 is provided for moving the first roller 1 in the axial direction A. For this purpose, the first axial adjustment mechanism 13 has a first annular cylinder 31. The first annular cylinder 31 has a first expansion chamber 32, which can be filled with an expansion medium, such as hydraulic oil. The first annular cylinder 31 is arranged along the entire periphery of the first roller neck 3 of the first roller 1. By introducing the expansion medium into the first expansion chamber 32, a first annular piston 34 moves in the axial direction A. Here, the first annular piston 34 presses against a first axial bearing 35 in the axial direction A. The first axial bearing is implemented in the form of a rolling bearing, with the first annular piston 34 abutting against a ring on the roller body side of the rolling bearing. A ring of the first axial bearing 35 disposed away from the roller body is fixedly connected to the first roller neck 3. Therefore, the movement of the first annular piston 34 in the axial direction A causes the first roller neck 3 to move in the axial direction A. By arranging the first expansion chamber 32 along the entire periphery of the first roller neck 5, the axial force for moving the first roller 1 in the axial direction A can be centrally applied, thereby generating uniform loading on the first axial bearing 3 and consequently on the first roller 1. Furthermore, undesirable effects on the roller gap 9 due to the off-center action of the axial force are avoided.

[0103] exist Figure 7 As can be seen, the fixed first portion 33 is supported on the first main bearing 5 opposite to the axial direction A. The first expansion chamber 32 is formed through the gap between the fixed first portion 33 and the first annular piston 34. To prevent leakage, the first expansion chamber 32 is sealed with an surrounding sealing device 36, through which the expansion medium may be discharged.

[0104] exist Figure 7 In the exemplary embodiment shown, the first axial adjustment mechanism 13 is disposed between the first main bearing 5 and the first bending bearing 11. It is not apparent that the additional first axial adjustment mechanism 13' is present. Figure 7 In the exemplary embodiment shown, the first roller 1 is positioned on the opposite side of the first roller 1 on another first roller neck 3, which can cause the first roller 1 to move in the opposite direction to the axial direction A. According to this exemplary embodiment, the additional first axial adjustment mechanism 13' is implemented completely symmetrically to the first axial adjustment mechanism 13, and therefore is omitted from the illustration here.

[0105] Different from In Figure 7 The exemplary implementation shown in [the document] is... Figure 8In the exemplary embodiment shown, not only the first axial adjustment mechanism 13 but also the additional first axial adjustment mechanism 13' is disposed on the same first roller neck 3 of the first roller 1. Both the first axial adjustment mechanism 13 and the additional first axial adjustment mechanism 13' are disposed here between the first main bearing 5 and the first bending bearing 11. The fixed first portion 33 of the first axial adjustment mechanism 13 is supported on the first main bearing 5 opposite to the axial direction A. Furthermore, the fixed first portion 33 forms the sidewall of the first expansion chamber 32 and the upper wall of the expansion chamber 32 and the upper wall of the additional expansion chamber 32' of the additional first axial adjustment mechanism 13'. That is, the fixed first portion 33 bridging the first axial adjustment mechanism 13 and at least partially the additional first axial adjustment mechanism 13'. In addition to the first expansion chamber 32 of the first axial adjustment mechanism 13, the additional first expansion chamber 32' of the additional first axial adjustment mechanism 13' can also be seen. Like the first expansion chamber 32, the additional first expansion chamber 32' is also provided for filling with an expansion medium. When the expansion medium is introduced into the additional first expansion chamber 32', the movable additional first annular piston 34' of the additional first axial adjustment mechanism 3' moves in the opposite direction of axial direction A. Here, the additional first annular piston 34' presses against the additional first axial bearing 35' in the opposite direction of axial direction A, and the ring on the roller body side of the additional first axial bearing is fixedly connected to the first roller neck 5. Thus, the filling of the additional first expansion chamber 32' causes the first roller 1 to move in the opposite direction of axial direction A. The ring on the roller body side of the additional first axial bearing 35' and the ring of the first axial bearing 35 that is opposite to the roller body of the first roller 1 are integrally connected to each other. However, it is also conceivable that these rings are separate.

[0106] In the present invention Figure 8 In the exemplary embodiment shown, the fixed additional first portion 33' forms at least a portion of the housing of the first bending bearing 11. The fixed first portion 33 and the fixed additional first portion 33' are screwed together. To achieve kinematic decoupling between the first bending bearing 11 and the first main bearing 5, the fixed first portion 33 is pivotally connected to the first main bearing 5. Therefore, the movement of the first bending bearing 11 in the radial direction R is not transmitted to the first main bearing 6 through the first axial adjustment mechanism 13.

[0107] Details of the second axial adjustment mechanism 14 and the additional second axial adjustment mechanism 14' are not shown, but these details correspond exactly to those of the first axial adjustment mechanism 13 and the additional first axial adjustment mechanism 13' shown herein, and both have a second annular cylinder or additional second annular cylinder including a second expansion chamber or additional second expansion chamber formed between a fixed second portion and a movable second annular piston or between a fixed additional second portion and a movable additional second annular piston. The movable second portion of the second axial adjustment mechanism 14 is supported on a second axial bearing. The movable additional second portion of the additional second axial adjustment mechanism 14' is supported on an additional second axial bearing.

[0108] The axial position adjustment of the first roller 1 and the second roller 2 is performed by servo hydraulic pressure. For this purpose, the axial position of the first roller 1 and the second roller 2 is measured and the pressure in the expansion chambers 32, 32' is adjusted so that the axial position corresponds to the theoretical value.

[0109] Specifically, for the purpose of calendering the electrodes, the rollers 1 and 2 are temperature-controlled. This is achieved by heating the rollers 1 and 2, for example, through peripheral holes (not shown), in which a heat carrier is disposed or guided. The heat carrier can be, for example, oil, steam, or the like. It is also conceivable to place heating elements in the peripheral holes or to inductively heat the rollers 1 and 2. The heat input through heating is released from the roller surface into the ambient air, but is also received by the calendered planar article 10. This results in a temperature gradient on the rollers 1 and 2 between the area where the roller surface of the rollers 1 and 2 comes into contact with the planar article 10, the so-called calendered area 92, and the areas to the left and right of these areas, the so-called uncalendered area 93. This temperature gradient can be further enhanced by the peripheral holes at the outer ends of the roller body, which can be redirected by a 180° rotation, thereby allowing more heat to be transferred from the heat carrier to the rollers 1 and 2. The temperature gradient affects the geometry of rollers 1 and 2 to varying degrees of thermal expansion along the axial direction A, and thus also affects the geometry and curvature of the roller gap 9, and can lead to undesirable effects, such as deviations from the geometry of the roller gap 9, until the first roller 1 and the second roller 2 come into contact outside the area where the faceted article 10 is calendered.

[0110] To prevent this, a mechanism for cooling the first roller 1 and the second roller 2 is provided outside rollers 1 and 2, as shown in... Figure 1 , 2As can be seen in sections 3 and 5, the cooling mechanism 15 is configured such that it receives heat from the roller surfaces of rollers 1 and 2 in areas not in contact with the planar article 10, and simultaneously from the areas of the roller surfaces of rollers 1 and 2 that are in direct contact with the planar article 10. For this purpose, the cooling mechanism 15 can move in the axial direction A. By receiving heat via the cooling mechanism 15, the temperature of the roller surfaces of rollers 1 and 2 is homogenized along the roller gap 9, thus preventing undesirable effects caused by temperature gradients. Through this cooling, it is even possible to specifically influence the thermal expansion of rollers 1 and 2 and actively change the geometry of the roller gap 9.

[0111] However, it is also conceivable to cool rollers 1 and 2. This is particularly advantageous when the planar article 10 is fed to the calender 100 at a temperature above the optimal temperature for calendering the planar article 10. This cooling can be achieved, for example, through peripheral holes (not shown) through which coolant is provided or guided. The heat removed by cooling is partially reintroduced into rollers 1 and 2 by the calendered planar article 10 during calendering. This results in a temperature gradient on rollers 1 and 2 between the calendered region 92 and the non-calendered region 93. This temperature gradient can be further enhanced by redirecting the peripheral holes for cooling at the outer ends of the rollers at a 180° turn, thereby allowing more heat to be drawn from the coolant there. This temperature gradient affects the geometry of rollers 1 and 2 by varying degrees of thermal expansion of rollers 1 and 2 along the axial direction A, and therefore also affects the geometry and curvature of the roller gap 9, potentially leading to undesirable effects such as deviations from the geometry of the roller gap 9.

[0112] To prevent this, a mechanism (not shown, similar to reference numeral 15) for heating the first roller 1 and the second roller 2 is provided outside the rollers 1 and 2. This heating mechanism is configured such that it inputs heat from the roller surfaces of the rollers 1 and 2 into areas that do not directly contact the planar article 10, and simultaneously inputs heat into the areas of the roller surfaces of the rollers 1 and 2 that directly contact the planar article 10. For this purpose, the heating mechanism can move in the axial direction A. Through the heat input via the heating mechanism, it is possible to homogenize the temperature of the roller surfaces of the rollers 1 and 2 along the roller gap 9, thus preventing undesirable effects caused by temperature gradients. By this heating, it is even possible to specifically influence the thermal expansion of the rollers 1 and 2 and actively change the geometry of the roller gap 9. It is conceivable that the heating mechanism is for induction heating.

[0113] exist Figure 10(a) and (b) illustrate the effects produced on the edge region 95 of the calendered planar article 10 during calendering. In the calendering region 92 of rollers 1 and 2, i.e., the region where rollers 1 and 2 are in direct contact with the planar article 10 during calendering, rollers 1 and 2 flatten by force input. Further, outside the calendering region 92 to the left and right, in the non-calendering region 93, no flattening by force input occurs. This difference results in shear stress in rollers 1 and 2. As a result, the roller gap 9 narrows towards the edge region 95 in the transition region 94 between the calendering region 92 and the non-calendering region 93, and generates an increase in linear force 91 (shown here as an arrow) towards the edge region 95.

[0114] The effect occurs not only at the left and right edges of the roll gap 9. If thinner regions, such as uncoated regions, are provided in the planar article 10, the uncalendered region 93 is also located in these regions. Figure 11 (b) and (c) show a planar configuration article 10 comprising three such regions, which are shown as longitudinal strips on the planar configuration article 10. Shear stress and thus deformation of rollers 1 and 2 also occur on the edge regions 95 adjacent to the longitudinal strips of the planar configuration article 10.

[0115] In the absence of longitudinal strips in the planar configuration article 10, compensation for the effects described herein is possible solely through the contours P1 and P2 having a 0.5S shape. This is in Figure 11 As shown in (a). By axially moving the rollers 1 and 2 with the shown contours P1 and P2, the narrowing of the roller gap 9 caused by flattening in the transition region 94 between the calendering region 92 and the non-calendering region 93 can be compensated.

[0116] If the planar article 10 has the longitudinal strip, the portion of deflection can be specifically compensated by the axial movement of rollers 1 and 2 with corresponding contours P1 and P2, the deflection being generated at the edge region 95 of the planar article 10 by shear stress due to the flattening of rollers 1 and 2. This is exemplarily demonstrated in Figure 11 As shown in (b) and (c). In Figure 11 The planar configuration article 10 shown in (b) has three coated areas and therefore (in addition to the uncoated areas on the outer edges of the planar configuration article 10) two longitudinal stripes. To compensate for the effects caused by shear stress, the contours P1 and P2 are set in a 2.5S shape here. Figure 11 (b) The particular shapes of the outlines P1, P2 of the exemplary embodiment result in the coated areas extending offset from each other along the direction of the linear force.

[0117] As in Figure 11As shown in (c), this can be prevented by the step portion 96 in the contours P1, P2. The step portion 96 is formed into the contours P1, P2 in the non-calendered region 93. Here, the roller surface does not contact the calendered planar configuration article 10, thus as in Figure 11 As shown in (b), the height difference between the calendered regions 92 can be compensated.

[0118] List of reference numerals

[0119] 1 First roller

[0120] 2 Second Roller

[0121] 3 First roll neck

[0122] 4 Second roll neck

[0123] 5 First main bearing

[0124] 5.1 Outer Ring

[0125] 5.2 Inner Ring

[0126] 5.3 Rolling elements

[0127] 5.4 Rolling element guide device

[0128] 6 Second main bearing

[0129] 7. First Regulatory Agency

[0130] 8. Second Regulation Mechanism

[0131] 9-roll gap

[0132] 10-sided structure items

[0133] 11 First Bending Bearing

[0134] 12 Second Bending Bearing

[0135] 13 First Axial Adjustment Mechanism

[0136] 13' Another first axial adjustment mechanism

[0137] 14 Second Axial Adjustment Mechanism

[0138] 14' Additional second axial adjustment mechanism

[0139] 15. Cooling mechanism

[0140] 31 First annular cylinder

[0141] 31' Another first annular cylinder

[0142] 32 First Expansion Chamber

[0143] 32' Another first expansion chamber

[0144] 33 Fixed First Part

[0145] 33' Fixed other first part

[0146] 34 First Ring Piston

[0147] 34' Another first annular piston

[0148] 35 First Axial Bearing

[0149] 35' additional first axial bearing

[0150] 36 Sealing Device

[0151] 91 linear force

[0152] 92-coated area

[0153] 93 non-pressurized areas

[0154] 94 Transition Zone

[0155] 95 edge area

[0156] 96 steps

[0157] 100 calender

[0158] Axial direction

[0159] P1 First Outline

[0160] P2 Second Outline

[0161] R radial direction

Claims

1. A calender (100) for calendering a surface-shaped article (10), preferably for manufacturing electrodes, said calender having a first roller (1) and a second roller (2), wherein, The rollers (1, 2) are movable relative to each other in the axial direction (A), wherein the calender (100) has a first adjustment mechanism (7) for bending the first roller (1) by a torque input in the radial direction (R).

2. The calender (100) according to claim 1, characterized in that, The first roller (1) has a first profile (P1) and the second roller (2) has a second profile (P2), wherein the first profile (P1) has a 0.5S shape or multiple 0.5S shapes, preferably a 1.0S shape or a 1.5S shape, particularly preferably a double S shape, and more particularly preferably a 2.5S shape, and the second profile (P2) has a 0.5S shape or multiple 0.5S shapes, preferably a 1.0S shape or a 1.5S shape, particularly preferably a double S shape, and more particularly preferably a 2.5S shape.

3. The calender (100) according to any one of the preceding claims, characterized in that, The two first roller necks (3) of the first roller (1) are supported in the first main bearing (5), wherein the first adjustment mechanism (7) acts on the additional first bending bearing (11), in which the first roller necks (3) are supported, wherein the first bending bearing (11) and the first main bearing (5) are preferably spaced apart by at least 0.8 times the diameter of the first roller (1), particularly preferably by at least 1 times the diameter and especially by at least 1.2 times the diameter.

4. The calender (100) according to claim 3, characterized in that, The first adjustment mechanism (7) is configured to press the first roller neck (3) away from the roller gap (9) in the radial direction (R) into the first main bearing (5) or towards the roller gap (9) into the first main bearing (5), wherein the first adjustment mechanism (7) is preferably configured to press the first roller neck (3) away from the roller gap (9) into the first main bearing (5) at least by the weight of the first roller (1) in the radial direction (R).

5. The calender (100) according to any one of claims 3 to 4, characterized in that, The first profile (P1) and the second profile (P2) are configured such that, in the relative positions of the first roller and the second roller (1, 2), when the adjusting mechanism (7) presses the first roller neck (3) away from the roller gap (9) in the radial direction (R) into the first main bearing (5), the roller gap (9) has a uniform gap height in the axial direction (A), wherein, the first profile (P1) and the second profile (P2) are preferably configured such that, in the relative positions of the first roller and the second roller (1, 2), when the first adjusting mechanism (7) presses the first roller neck (3) away from the roller gap (9) in the radial direction (R) into the first main bearing (5) at least by the weight of the first roller (1), the roller gap (9) has a uniform gap height in the axial direction (A).

6. The calender (100) according to any one of the preceding claims, characterized in that, The calender (100) has two first adjustment mechanisms (7), wherein the two first adjustment mechanisms (7) act on the first roller neck (3) opposite each other in the axial direction (A) of the first roller (1), wherein the two first adjustment mechanisms (7) are configured to act on the opposite first roller neck (3) to different degrees respectively.

7. The calender (100) according to any one of the preceding claims, characterized in that, The calender (100) has a second adjustment mechanism (8) for bending the second roller (2) along the radial direction (R), wherein, preferably, the two second roller necks (4) of the second roller (2) are supported in a second main bearing (6), wherein the second adjustment mechanism (8) acts in an additional second bending bearing (12), the second roller necks (4) being supported in the second bending bearing, wherein the second bending bearing (12) and the second main bearing (6) are particularly preferably spaced apart from each other at least 0.8 times the diameter of the second roller (2), more particularly preferably at least 1 time the diameter, and especially at least 1.2 times the diameter.

8. The calender (100) according to any one of claims 3 to 7, characterized in that, The movement of the first roller (1) along the axial direction (A) occurs together with the movement of the first roller neck (3) through the first main bearing (5) and preferably through the first bending bearing (11).

9. The calender (100) according to claim 8, characterized in that, The first bending bearing (11) is a rolling bearing, preferably a cylindrical roller bearing, wherein the movement of the first roller (1) along the axial direction (A) is caused by the movement of the inner ring of at least one of the first bending bearings (11), wherein, in particular, the rolling elements and / or outer rings of the at least one of the first bending bearings (11) do not move when the first roller (1) moves along the axial direction (A).

10. The calender (100) according to any one of the preceding claims, characterized in that, Heating the first roller (1) and / or the second roller (2).

11. A method for operating a calender (100), particularly a calender (100) according to any one of the preceding claims, wherein, The deflection of the first roller (1) of the calender (100) is compensated by the movement of the rollers (1, 2) in the axial direction (A) and the bending of the first roller (1) by the torque input in the radial direction (R) via the first adjustment mechanism (8), so that the roller gap (9) has a desired gap height distribution curve in the axial direction (A).

12. The method according to claim 11, wherein, The first roller neck (3) is pressed into the first main bearing (5) by the first adjustment mechanism (7) away from or toward the roller gap (9), thereby suppressing the bearing gap of the first main bearing (5).

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