DRIVE DEVICE FOR AN ECCENTRIC BEARING AND A CORRESPONDING CALENDAR

Description

[0001] The invention relates to a drive device for an eccentric bearing for radially deflecting a roller mounted therein and a corresponding calender, wherein the eccentric bearing has an axially oriented bore for receiving a roller journal of a roller, and wherein the eccentric bearing has an outer eccentric bushing and an inner eccentric bushing, having the bore, which is inserted section by section into the outer eccentric bushing, so that the eccentric bushings have an axial overlap area.

[0002] A printing press bearing is known from the prior art, which has eccentric rings for axially displacing or tilting a cylinder mounted in the printing press bearing. These rings are pivotable relative to each other and / or around the cylinder. In the solution disclosed in the prior art, the adjustment of the eccentric rings is effected by means of pivotally mounted actuating elements in the form of pivot levers arranged on the outer face of the bearing. These pivot levers are displaceable in the tangential direction around the cylinder axis to set a desired eccentricity.

[0003] DE4143597 also discloses a drive device for an eccentric bearing for radially deflecting a roller mounted therein.

[0004] However, the device disclosed in the prior art has the disadvantage that, due to the front-side arrangement of the pivot levers extending away from the cylinder axis and their displacement in both horizontal and vertical directions, especially in the radial direction of the cylinder, it takes up a lot of space and is not suitable for tight installation spaces.

[0005] It is therefore the object of the present invention to improve a drive device for an eccentric bearing in such a way that it has a compact design.

[0006] The invention is solved by the features of the independent claims.

[0007] Advantageous embodiments are described in the dependent claims.

[0008] Accordingly, it is provided that at least one of the eccentric bushings has a free end outside the overlap area, which is coupled to a drive unit. This drive unit allows the at least one eccentric bushing to be rotated axially to adjust a radial axial deflection of the bore relative to the other eccentric bushing. Because at least one of the eccentric bushings has a free end, it is possible to drive the eccentric bushing not necessarily from its end face, but to introduce the force into the eccentric bushing in a space-saving manner via a tangentially arranged drive unit.

[0009] It may be provided that the inner eccentric bushing is rotatably mounted within the outer eccentric bushing. Accordingly, a radial bearing may be arranged in the axial overlap area between the outer surface of the inner eccentric bushing and the inner surface of the outer eccentric bushing. Furthermore, it may be provided that a roller journal, which can be received in the bore, is rotatably mounted within the inner eccentric bushing. Accordingly, another radial bearing may be arranged in the axial overlap area on the inner surface of the inner eccentric bushing. The eccentric bearing may be received in a bore or bushing provided in a calender frame and rotatably mounted therein. Accordingly, a radial bearing may also be arranged in the overlap area between the outer surface of the outer eccentric bushing and the inner surface of the bore or bushing.Thus, the outer eccentric bushing can be rotated relative to the bore or bushing, the inner eccentric bushing relative to the outer eccentric bushing, and the roller, if any, held in the inner eccentric bushing can be rotated relative to the inner eccentric bushing.

[0010] The inner bore of the outer eccentric bushing can be eccentric relative to its outer diameter. The inner eccentric bushing can be accommodated within the inner bore of the outer eccentric bushing. Furthermore, the inner bore of the inner eccentric bushing can be eccentric relative to its outer diameter. Simultaneously, in a starting position for both eccentric bushings, the inner bore of the inner eccentric bushing can be concentric with the outer diameter of the outer eccentric bushing. The inner and outer eccentric bushings can be rotated relative to each other or in the same direction, allowing the eccentricity of the inner bore of the inner eccentric bushing to be adjusted, with the direction and degree of eccentricity being variable. Each eccentric bushing can have a thick section and a thin section opposite the thick section.In the initial position described above, the thick section of the outer eccentric bushing and the thin section of the inner eccentric bushing can be close together, as can the thin section of the outer eccentric bushing and the thick section of the inner eccentric bushing. By rotating both eccentric bushings relative to each other by 180°, the maximum possible off-center deflection can be achieved. Furthermore, a linear deflection can be achieved by simultaneously rotating the inner and outer eccentric bushings in opposite directions. Additionally, a change in the direction of the deflection can be achieved by simultaneously rotating the inner and outer eccentric bushings in the same direction.

[0011] Furthermore, it can be provided that both eccentric bushings have a free end on opposite sides of the overlap area, each of which is coupled to a drive unit, via which the eccentric bushings can be rotated independently of each other about the axial direction to adjust the radial axis deflection of the bore.

[0012] Furthermore, the drive unit may include a gear output, for example an external gear, arranged at least partially on the outer circumference of the free end and coupled to it. The gear output may, for example, extend over half the circumference of the free end of the eccentric bushing, allowing it to pivot by 180°. The gear output can thus surround the eccentric bushing in a semicircular shape. The free ends may essentially be designed as cylindrical hollow bodies.

[0013] Furthermore, the drive unit can include a drive element coupled to the gearbox output, which is arranged perpendicular to the axial direction. The drive element can be driven rotaryally or translationally. For example, the drive element can be implemented as a rack and pinion. In particular, the drive element can include a worm shaft that engages with the gearbox output or the external gearing. When designed as a worm shaft, the drive element exhibits a rotary drive motion.

[0014] The drive units may be axially spaced apart. In particular, the drive elements may be axially spaced apart. This spacing may correspond to the distance between the gear outputs at their respective free ends. The drive elements may each be housed in a surrounding casing. The casings, like the drive elements, may extend perpendicular to the axial direction of the drive device. Each casing may have an interface with the bore or bushing in which the drive device is mounted. In the area of ​​the interfaces, the drive elements housed in the casings may engage with the gear outputs mounted in the bore or bushing at the free ends of the eccentric bushings.

[0015] The eccentric bearing can be mounted in a bushing or bore of a machine frame, or in particular a calender frame, with the drive element being driven by a motor located outside the bushing or bore. If two drive devices are provided on the eccentric bearing, the drive elements can be arranged on the same or different sides of the central bore axis and aligned parallel to each other. It can be provided that one of the motors is coupled to one of the drive elements via a first side, and the other motor is coupled to the other drive element via the opposite side. For example, with a horizontal bore or roller orientation, the drive elements can be arranged vertically, with one motor coupled to the top of one drive element and the other motor coupled to the bottom of the other drive element.

[0016] Furthermore, an angular offset between the drive element and the motor may be provided. This angular offset can be configured, for example, such that the motor is arranged perpendicular to the drive element. The angular offset can be achieved by a bevel gear unit coupling the drive element to the motor. This bevel gear unit can be, for example, a bevel gear unit, a bevel-planetary gear unit, or a hypoid gear unit. The motor can be, in particular, a servo motor. This allows the angular position of the motor shaft, as well as the rotational speed and acceleration, to be controlled. The servo motor can include a sensor for position determination.

[0017] Furthermore, the eccentric bushings can each be provided with an adjustment scale readable from the outside of the bushing. This scale allows the actual position of the eccentric bushings to be checked. It can be provided that the adjustment scale of one eccentric bushing points axially and the adjustment scale of the other eccentric bushing points radially, with the respective scales readable from their respective positions. For example, the scale of the eccentric bushing facing the outside of the roller can be designed to be readable from its end face. Alternatively, the adjustment scale of the eccentric bushing facing the center of the roller can be designed to be readable from either the top or bottom surface of the bushing that accommodates the drive device. The desired axis deflection values ​​are calculated using the angular function of the eccentric rotation. The increment can be read in 0.2 mm steps from 0 mm up to a maximum value of 4 mm.

[0018] The invention further relates to a calender with at least two parallel rollers mounted in a calender frame, between which a roller gap is formed, wherein the rollers each have a roller journal mounted in the calender frame at their opposite ends, and wherein at least two adjacent roller journals have a drive device according to one of the preceding claims. Because a drive device according to the invention is provided on each of two adjacent roller journals for driving the eccentric bearings, only a small amount of installation space is available, particularly for the motors for driving the drive elements. The advantageous force transmission for adjusting the eccentric bushings made possible by the drive device according to the invention allows for space-saving adjustment of the eccentric bushings.

[0019] Furthermore, it can be provided that in the calender all roller journals of the two rollers each have a drive device according to one of claims 1 to 13.

[0020] It may be specifically provided that the drive elements of the adjacent drive devices are aligned parallel to each other. For example, they may be aligned perpendicularly if the bore or roller axis is horizontally oriented. Both drive elements may be arranged either on the same side or on opposite sides of the bore or roller axis. For example, both drive elements may be arranged to the right or left of the roller axis, or on different sides, i.e., to the right and left, of the roller axis.

[0021] The motors of the adjacent drive devices can be arranged so that they are either parallel to the roller axes or point away from the respective adjacent drive device. For example, a first motor of a drive device can be arranged parallel to the roller axis, and a second motor of the drive device can be arranged perpendicular to the roller axis and pointing away from the adjacent drive device. The motors of the adjacent drive devices can be oriented accordingly.

[0022] It can be provided that a first backup roll is arranged adjacent to a first roll, and a second backup roll is arranged adjacent to a second roll, each rotating in the opposite direction. The backup rolls can each have a larger diameter than the rolls. The rolls and backup rolls can each have the same diameter. The rolls can each have a diameter of 200 mm. The backup rolls can each have a diameter of 700 mm. The axes of the rolls and backup rolls can be aligned in the same plane. The first roll and the first backup roll can roll against each other, and a roll gap can be formed between the second roll and the second backup roll.

[0023] Further details of the invention are explained with reference to the figures below. These show: Figure 1 shows an actuating mechanism known from the prior art for adjusting eccentric rings of a printing press bearing; Figure 2 shows a schematic front view of an eccentric bearing for radially deflecting a bearing journal; Figure 3 shows a perspective view of an embodiment of the drive device according to the invention; Figure 4 shows a perspective sectional view of a roller journal mounted in an eccentric bearing; Figure 5 shows a perspective front view of a roller calender equipped with drive devices; Figure 6 shows a perspective overall view of a roller calender equipped with drive devices; and Figure 7 shows a top view of a calender equipped with drive devices for producing an electrode film from a powdered electrode precursor material.

[0024] The in Figure 1The illustration shows a printing press bearing known from the prior art, which has eccentric rings for axially displacing or tilting a printing cylinder mounted therein. These rings are pivotable relative to each other and / or about the cylinder axis. The eccentric rings have the same axial thickness and are aligned with each other so that they overlap over their entire thickness. As can be seen, in the solution disclosed in the prior art, the adjustment of the eccentric rings is achieved by means of pivot levers arranged on the outside of the bearing, which are pivotally mounted and can be displaced tangentially around the cylinder to set the required eccentricity.However, the solution shown has the disadvantage that, due to the necessary length of the levers and their displacement in both horizontal and vertical directions, especially in the radial direction of the cylinder, it takes up a lot of space and is not suitable for tight installation spaces.

[0025] Figure 2Figure 1 shows an exemplary eccentric bearing 99, which serves to deflect a roller journal 205 in any direction orthogonal to the central axis of the respective roller 201, 202 and to an adjustable degree. The eccentric bearing 99 has an outer eccentric bushing 101, the inner bore of which is eccentric with respect to the outer diameter of the outer eccentric bushing 101. The eccentric bearing 99 also has an inner eccentric bushing 102, the inner bore 105 of which is concentric to the outer diameter of the outer eccentric bushing 101 in a starting position. The inner and outer eccentric bushings 102, 101 are rotatable relative to each other or in the same direction, so that the eccentricity of the inner bore 105 of the inner eccentric bushing 102 is adjustable, with the direction and degree of deflection being variable. Each of the eccentric bushings 101, 102 has a thick section and a thin section opposite the thick section.In the initial position described above, the thick section of the outer eccentric bushing 101 and the thin section of the inner eccentric bushing 102 are close together, as are the thin section of the outer eccentric bushing 101 and the thick section of the inner eccentric bushing 102. Accordingly, by rotating both eccentric bushings 101, 102 relative to each other by 180°, the greatest possible off-center deflection can be achieved.

[0026] Figure 2Figure 1 shows an embodiment of the drive device 1 according to the invention. An eccentric bearing 99 is received in a bushing 520 that can be connected to a machine frame 500. The bearing 99 has an inner and an outer eccentric bushing 101, 102, which are rotatable relative to each other about an X-axis, or relative to the bushing 520 and relative to a roller journal 205 that can be received in an inner bore 105 of the inner eccentric bushing 102, respectively. A first drive unit 300 is provided to drive the eccentric bushing facing the center of the roller. This drive unit has a drive element 302 arranged perpendicular to the X-axis, which is received in a housing 306.The housing 306 has an interface with the bushing 520, via which the drive element 302 is coupled to a gear output in the form of an external toothing 301, which is arranged on the outer circumference of a free end 104 of the eccentric bushing, the drive element 302 being tangentially connected to the external toothing 301. A servo motor 304 driving the drive element 302 is coupled to the drive element 302 via a bevel gear 305, the motor 304 being arranged perpendicular to the drive element 302 and parallel to the X-axis above the bushing 520. A second drive unit 300 is provided for driving the eccentric bushing facing away from the center of the roller, which is designed accordingly to the first drive unit 300, the drive element 302 being coupled to the free end 104 of the eccentric bushing facing away from the center of the roller in the housing 306. The housings 306 orThe drive elements 302 are arranged parallel to each other to the right of the X-axis. In contrast to the first drive unit 300, in the second drive unit 300 the motor 304 is arranged on the underside of the bushing 520, also perpendicular to the drive element 302, but not parallel to the X-axis, rather perpendicular to it, intersecting the bushing 520. To read the setting of the eccentric bushing facing the center of the roller, the bushing 520 has a viewing window on its upper side, through which the setting scale 400 provided at the free end 104 can be read. To read the setting of the eccentric bushing facing away from the center of the roller, the end face of the free end 104 of the eccentric bushing has a scale ring with a further setting scale 400, so that this can be read from the front.

[0027] Figure 4Figure 1 shows a sectional view through a roller 201 and an eccentric bearing 99 mounted on the roller journal 205 of the roller 201. The roller 201 is mounted in a machine frame 500, which has a bushing 520 in which the roller journal 205, together with the eccentric bearing 99, is received. The eccentric bearing 99 essentially comprises an inner eccentric bushing 102 and an outer eccentric bushing 101, wherein the roller journal 205 is received in a bore 105 of the inner eccentric bushing 102. The inner eccentric bushing 102 is partially inserted into the outer eccentric bushing 101, so that they have an axial overlap area 103. The outer eccentric bushing 101 is axially rotatable in the cylindrical bushing via a first radial bearing 110. The inner eccentric bushing 102 is mounted in the outer eccentric bushing 101 via a second axially rotatable radial bearing 120.The roller journal 205 is in turn mounted axially rotatably in the inner eccentric bushing 130 via a third radial bearing 130. In the illustrated orientation, the eccentric bearing 99 is in its initial position, in which the thick section of the outer eccentric bushing 101 is close to the thin section of the inner eccentric bushing 102, and the thin section of the outer eccentric bushing 101 is close to the thick section of the inner eccentric bushing 102, so that the roller journal 205 is centered and not deflected. The eccentric bushings 101 and 102 are adjustable independently of each other by means of separate drive units 300. For this purpose, the eccentric bushings 101, 102 each have free ends 104 extending away from the overlap area 103 opposite each other, each of which has a gear output in the form of an external toothing 301, via which the eccentric bushings 101, 102 can be adjusted independently of each other.On the front side, the inner eccentric bushing 102, facing away from the center of the roller, has an adjustment scale 400 that can be read from the end face. On the rear side, the outer eccentric bushing 101, facing towards the center of the roller, has an adjustment scale 400 that can be read from the circumference.

[0028] Figure 5Figure 1 shows a perspective frontal view of a calender 2 with two rolls 201 mounted horizontally and parallel within a machine frame 500. These rolls form a roll gap 220 and are therefore arranged very close together. A drive device 1, each with two drive units 300, is mounted on the roll journals 205 projecting from the machine frame. As shown, the drive elements 302 each have a worm shaft 303, which engages with the respective external gears 301. The drive elements 302 are all arranged vertically on the sides of the rolls 201 facing away from the roll gap 220. One motor 304 of each drive device 1 is located above the respective roll 201, and one motor 304 of each drive device 1 is located below the respective roll 201. All motors are aligned perpendicular to the drive elements 302 and parallel to the roll axes X.

[0029] Figure 6 shows an overall view of the in Figure 5 The calender 2 shown in the illustration depicts the essentially mirror-image mounting of the roller journals 205, located at opposite ends of the rollers 201, within the machine frame 500. Each roller journal 205 is fitted with a drive device 1, comprising an eccentric bearing 99 and two drive units 300. The roller gap 220, a few millimeters wide, between the rollers 201 is clearly visible. This gap necessitates a very compact design for the end faces of the rollers 201, including connecting elements such as the drive units 300. All motors 304 are mounted on the side of the rollers 201 facing away from the roller gap 220. One motor 304 is mounted on the top and one on the bottom of each roller 201, parallel to the roller axes X.

[0030] Figure 7Figure 2 shows a top view of a multi-roll calender 3, which illustrates the arrangement of the rolls 201 relative to the backup rolls 210 in an integrated rolling system according to one embodiment. The multi-roll calender 2 is used to produce a separator film (not shown) coated on both sides with electrode films 601, 602. The arrangement comprises two calender assemblies 2 positioned end-to-end, which have opposing main conveying directions Y1, Y2. Each calender assemblies 2 has eight rolls 201, 210, 310 mounted in a machine frame 500. On the inlet side, each arrangement has two rolls 201 laterally supported by backup rolls 210, which serve as a powder mill for producing the electrode films 601, 602 from a powdered electrode precursor material.Four feed rollers 310 follow each backup roller, bringing the electrode film to the desired width and thickness and homogenizing it. The input-side end roller 210 is designed as a backup roller 210 that rolls directly on the first roller 201. The output-side feed rollers 310 form a common end roller gap 13 in which the electrode films 601, 602 are applied to the separator film.

[0031] The features of the invention disclosed in the foregoing description, in the drawings and in the claims may be essential for the realization of the invention, both individually and in any combination. Reference symbol list

[0032] 1 Drive device 2 Calender 13 End roll gap 99 Eccentric bearing 100 Preload device 101 Outer eccentric bushing 102 Inner eccentric bushing 103 Axial overlap area 104 Free end 105 Inner eccentric bushing bore 110 First radial bearing 120 Second radial bearing 130 Third radial bearing 201 Roll 205 Roll journal 210 Support roll 220 Roll gap 300 Drive unit 301 External gearing 302 Drive element 303 Worm shaft 304 Motor 305 Bevel gear 310 Conveyor rolls 400 Adjustment scale 500 Calender frame 501 Bearing 520 Bore / bushing 601 First electrode film 602 Second electrode film X Axial direction Y1 Conveying direction of the first electrode film Y2 Conveying direction of the second electrode film

Claims

1. A drive device (1) for an eccentric bearing (99) for radially deflecting a roller (205) mounted therein, wherein the eccentric bearing (99) has a bore (105) oriented in an axial direction (X) for receiving a roller journal (205) of a roller (201), and wherein the eccentric bearing (99) has an outer eccentric bush (101) and an inner eccentric bush (102) which is inserted in sections into the outer eccentric bush (101) and has the bore (105), such that the eccentric bushes (101, 102) have an axial overlap region (103), characterized in that at least one of the eccentric bushes (101, 102) has a free end (104) outside the axial overlap region (103), which is coupled to a drive unit (300) via which the at least one eccentric bush (101, 102) is rotatable about the axial direction (X) for adjusting a radial axis deflection of the bore (105) relative to the other eccentric bush (101, 102).

2. The drive device (1) according to claim 1, wherein (i) both eccentric bushes (101, 102) have a free end (104) on opposite sides of the axial overlap region (103), each of which is coupled to a drive unit (300) via which the eccentric bushes (101, 102) are rotatable about the axial direction (X) independently of one another for adjusting the radial axis deflection of the bore (105), and / or (ii) the drive unit (300) has a gear output, for example external teeth (301), arranged at least in sections on the outer circumference of the free end (104) and coupled to the free end.

3. The drive device (1) according to alternative (ii) of claim 2, wherein the drive unit (1) has a drive element (302) coupled to the gear output, which is arranged perpendicular to the axial direction (X), wherein optionally the drive element (302) has a worm shaft (303) in engagement with the gear output or the external teeth (301).

4. The drive device (1) according to any one of the preceding claims 2 to 3, wherein the drive units (300) are spaced apart from one another in the axial direction (X).

5. The drive device (1) according to any one of claims 3 to 4, wherein (i) the eccentric bearing (99) is mounted in a bush (520) of a machine frame (500), wherein the drive element (302) is driven via a motor (304) arranged outside the bush (520), and / or (ii) an angular offset is provided between the drive element (302) and the motor (304), wherein optionally the angular offset is designed such that the motor (304) is arranged perpendicular to the drive element (302) and / or the angular offset is realized by an angular gear (305) coupling the drive element (302) to the motor (304).

6. The drive device (1) according to claim 5, wherein the motor (304) is a servomotor.

7. The drive device (1) according to any one of the preceding claims, wherein the eccentric bushes (101, 102) each have an adjustment scale (400) readable from the outside of the bush (520), wherein optionally the adjustment scale (400) of one eccentric bush (101, 102) points in the axial direction and the adjustment scale (400) of the other eccentric bush (101, 102) points in a radial direction (Y) and the adjustment scales (400) are each readable from there.

8. A calender (2) with at least two rollers (201) arranged in parallel and mounted in a calender frame (500), between which a roller nip is formed, wherein the rollers (201) each have at their opposite ends a roller journal (205) mounted in the calender frame (500), wherein at least two adjacent ones of the roller journals (205) have a drive device (1) according to any one of the preceding claims.

9. The calender (2) according to claim 8, wherein all roller journals (205) of the two rollers (201) each have a drive device (1) according to any one of claims 1 to 7.

10. The calender (2) according to claim 8, wherein the drive elements (302) of the adjacent drive devices (1) are aligned parallel to one another.

11. The calender (2) according to claim 8 or 9, wherein the motors (304) of the adjacent drive devices (1) are arranged such that they are either aligned parallel to the roller axes or point away from the respective adjacent drive device (1).

12. The calender (2) according to any one of claims 8 to 10, wherein a first support roller (210) is arranged adjacent to a first one of the rollers (201) and a second support roller (210) is arranged adjacent to a second one of the rollers (201), which each rotate in opposite directions thereto.

13. The calender (2) according to claim 11, wherein the support rollers (210) each have a larger diameter than the rollers.

14. The calender (2) according to any one of claims 11 or 12, wherein the axes of the rollers (201) and the support rollers (210) are aligned with one another in one plane.

15. The calender (2) according to any one of claims 8 to 14, wherein the first roller (201) and the first support roller (210) roll on one another and a roller nip (220) is formed between the second roller (201) and the second support roller (210).