Drive for an eccentric bearing and corresponding calendar

Abstract

The invention relates to a drive device for radially deflecting a roller mounted on an eccentric bearing, the eccentric bearing having an axially oriented bore intended to accommodate a roller journal of the roller, the eccentric bearing comprising an outer eccentric bush and an inner eccentric bush partially inserted in the outer eccentric bush and having a bore, the eccentric bushes being characterized in that they have an axial overlap area, at least one of the eccentric bushes having a free end outside the overlap area, said free end being coupled to a drive unit, via which at least one eccentric bush is rotatable about its axial direction in order to adjust the radial axial deflection of the bore relative to the other eccentric bush. The invention also relates to a corresponding calender.

Description

Technical Field

[0001] The present invention relates to a drive device for deflecting a roller mounted on an eccentric bearing in the radial direction, and to a corresponding calender. The eccentric bearing has an axially oriented bore for receiving the roller journal of the roller, and the eccentric bearing comprises an outer eccentric bush and an inner eccentric bush partially inserted into the outer eccentric bush and having a bore, and the eccentric bearing has an axial overlap region.

[0002] Printing press bearings have eccentric rings for axially displacing or obliquely arranging cylinders mounted on the printing press bearings, and it is known from the prior art that these rings can pivot relative to each other and / or around the cylinder. The adjustment of the eccentric rings according to the solutions disclosed in the prior art is carried out by actuating elements pivotally mounted in the form of pivot levers arranged on the front side outside the bearing, and these levers can be displaced tangentially around the cylinder to set the desired eccentricity.

[0003] However, the devices disclosed in the prior art have the disadvantage that the front arrangement of the pivot levers extends away from the cylinder axis and the pivot levers displace in both the horizontal and vertical directions, especially in the radial direction of the cylinder, occupying a lot of space and not being suitable for a compact installation space.

[0004] Therefore, the object of the present invention is to improve the drive device for the eccentric bearing to have a compact design.

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

[0006] Accordingly, at least one of the eccentric bushes has a free end outside the overlap region, and this free end is coupled to the drive unit. Through the drive unit, at least one eccentric bush can rotate about the axial direction to adjust the radial axial deflection of the bore with respect to the other eccentric bush. Since at least one eccentric bush has a free end, it is possible to avoid driving the corresponding eccentric bush from the front, and it is possible to introduce force to the eccentric bush in a space-saving way through a tangentially arranged drive unit.

[0007] It may be provided that the inner eccentric bush is rotatably attached to the outer eccentric bush. Accordingly, the radial bearing may be arranged in the axial overlap region between the outer surface of the inner eccentric bush and the inner surface of the outer eccentric bush. Further, it may be provided that a roller journal that can be accommodated in the bore can be rotatably attached to the inner eccentric bush. Accordingly, an additional radial bearing may be arranged in the axial overlap region of the inner surface of the inner eccentric bush. The eccentric bearing can be accommodated in a bore or bush provided in the calendar frame and rotatably attached therein. Accordingly, the radial bearing can also be arranged in the overlap region between the outer eccentric bush and the inner surface of the bore or bush. Accordingly, the outer eccentric bush can rotate with respect to the bore or bush, the inner eccentric bush can rotate with respect to the outer eccentric bush, and the roller that may be accommodated in the inner eccentric bush can rotate with respect to the inner eccentric bush.

[0008] The inner bore of the outer eccentric bush can be eccentric with respect to its outer diameter. The inner eccentric bush can be accommodated in the inner bore of the outer eccentric bush. Further, the inner bore of the inner eccentric bush can be eccentric with respect to the outer diameter of the inner eccentric bush. The inner bore of the inner eccentric bush may also be concentric with the outer diameter of the outer eccentric bush at the starting positions of both eccentric bushes. Since the inner eccentric bush and the outer eccentric bush can pivot relative to each other or in the same direction, the eccentricity of the inner bore of the inner eccentric bush can be adjusted, and the direction and degree of deflection are variable. Thereby, each eccentric bush has a thick portion and a thin portion on the side opposite to the thick portion. At the above starting position, the thick portion of the outer eccentric bush and the thin portion of the inner eccentric bush may be close to each other, and the thin portion of the outer eccentric bush and the thick portion of the inner eccentric bush may be close to each other. When both eccentric bushes rotate 180° relative to each other, the maximum possible deflection off-center can be achieved. Further, by simultaneously rotating the inner and outer eccentric bushes in opposite directions, a linear deflection can be achieved. Further, by simultaneously rotating the inner and outer eccentric bushes in the same rotation direction, changing the direction of deflection can be achieved.

[0009] Further, both eccentric bushes may have free ends on the opposite side of the overlap region, and the free ends are respectively coupled to drive units, and through the drive units, the eccentric bushes can be rotated independently of each other about the axial direction to adjust the radial axial deflection of the bore.

[0010] Further, the drive unit may be provided with a transmission output such as an external gear, etc., and is at least partially disposed on the outer periphery of the free end and coupled to the free end. The transmission output can extend, for example, over a semi-circumference of the free end of the eccentric bush, so that the eccentric bush can be pivoted up to 180°. Therefore, the transmission output can surround the eccentric bush along a semi-circle. The free end can basically be designed as a cylindrical hollow body.

[0011] Furthermore, the drive unit can have a drive element coupled to the transmission output, and the drive element is arranged perpendicular to the axial direction. The drive element can be driven rotationally or translationally. For example, the drive element can be formed by a rack. In particular, the drive element can have a worm shaft that engages with the transmission output or an external gear. The drive element designed as a worm shaft performs a rotational drive movement.

[0012] The drive units may be provided to be axially spaced from each other. In particular, the drive elements can be axially separated from each other. The distance may in particular correspond to the distance between the transmission outputs on their respective free ends. The drive elements may each be provided to be accommodated within a housing surrounding them. The housing, like the drive element, can extend perpendicular to the axial direction of the drive device. Each housing can have a boundary surface to a bore or bush in which the drive device is accommodated. In the region of the boundary surface, the drive element accommodated in the housing can engage with the gear output accommodated in the bore or bush at the free end of the eccentric bush.

[0013] The eccentric bearing can be attached to a bush or bore of the machine frame, in particular the calendar frame, and the drive element is driven by a motor arranged outside the bush or bore. When two drive devices are provided on the eccentric bearing, the drive elements can be arranged on the same side or different sides of the central bore axis and aligned parallel to each other. It may be provided that one of the motors is coupled to one of the drive elements via the first side, and the other motor is coupled to the other drive element via the opposite side. For example, when the bore or roller is horizontally oriented, the drive element may be arranged vertically, one motor may be coupled to the top of one drive element, and the other motor may be coupled to the bottom of the other drive element.

[0014] Furthermore, it can also be provided that an angular offset is provided between the drive element and the motor. The angular offset can be designed, for example, such that the motor is arranged perpendicular to the drive element. The angular offset can be realized by an angular gear that couples the drive element to the motor. The angular gear can be, for example, a bevel gear, a bevel planetary gear, or a hypoid gear. The motor can particularly be a servo motor. Thereby, it becomes possible to control the angular position, as well as the rotational speed and acceleration of the motor shaft. The servo motor can have a sensor for determining the position.

[0015] Furthermore, each of the eccentric bushes can be provided with an adjustment scale that can be read from the outside of the bush. This can be used to check the actual position of the eccentric bush. An adjustment scale for one eccentric bush point in the axial direction, and an adjustment scale for the other eccentric bush point in the radial direction, and it can be provided that the adjustment scale can be read therefrom. For example, the scale of the eccentric bush facing the outside of the roller can be designed to be readable from the front side. Furthermore, the adjustment scale of the eccentric bush towards the center of the roller can be designed to be readable from the upper or lower side of the bush that houses the drive device. The desired axial offset amount is converted using the angular function of the eccentricity rotation. The increments can be read in 0.2 mm steps from 0 mm to a maximum value of 4 mm.

[0016] The present invention further relates to a calendar in which at least two rollers are arranged in parallel, attached to a calendar frame, and a roller gap is formed therebetween, each roller having a roller journal attached to the calendar frame at its opposite end, and at least two adjacent roller journals having the drive device according to any one of the preceding claims. The drive device according to the present invention is provided for each of two adjacent roller journals for driving the eccentric bearing, so that only a small installation space is available, particularly for the motor for driving the drive element. By the advantageous introduction of the force for adjusting the eccentric bush made possible by the drive device according to the present invention, it is possible to adjust the eccentric bush in a space-saving manner.

[0017] Furthermore, in the calendar, it may be provided that all the roller journals of the two rollers each have the drive device according to any one of claims 1 to 13.

[0018] Specifically, it may be provided that the drive elements of adjacent drive devices are aligned parallel to each other. For example, when the bores or roller shafts are aligned horizontally, they can be oriented vertically. Both drive elements can be arranged on either the same side or the opposite side of the bore or roller shaft. For example, both drive elements may be arranged on the right or left side of the roller shaft, or on different sides of the roller shaft, i.e., right and left.

[0019] The motors of adjacent drive devices can be aligned parallel to the roller shaft or arranged to face away from the adjacent drive device. For example, the first motor of the drive device may be arranged parallel to the roller shaft, and the second motor of the drive device may be arranged perpendicular to the roller shaft and facing away from the adjacent drive device. The motors of adjacent drive devices can also be oriented accordingly.

[0020] The first support roller may be arranged adjacent to the first roller, and the second support roller may be arranged adjacent to the second roller, and each may be provided to rotate in a direction opposite to that of the latter. Each of the support rollers can have a diameter larger than that of the roller. Each of the rollers can have the same diameter, and the support rollers can also have the same diameter. Each of the rollers can have a diameter of 200 mm. Each of the support rollers can have a diameter of 700 mm. The axes of the rollers and the support rollers can be oriented in one plane. The first roller and the first support roller can roll against each other, and a roller gap can be formed between the second roller and the second support roller.

[0021] Further details of the present invention are described using the following figures.

Brief Description of the Drawings

[0022]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

[0023] The figure shown in FIG. 1 shows a printing press bearing known from the prior art, which has an eccentric ring for axially displacing or obliquely positioning a printing cylinder mounted therein, and these are each pivotable relative to one another and / or about the cylinder axis. The eccentric rings have the same axial thickness and are arranged aligned with one another such that the eccentric rings overlap one another over their entire thickness. As can be seen from the figure, the adjustment of the eccentric rings according to the solutions disclosed in the prior art is carried out by pivotably mounted levers arranged outside the bearing, and these levers can be displaced tangentially in sequence around the cylinder to set the required eccentricity. However, the illustrated solution has the disadvantage that it requires a large amount of space for the required length of the levers and in both the horizontal and vertical directions, especially for the radial displacement of the cylinder, and is not suitable for a compact installation space.

[0024] FIG. 2 shows an exemplary eccentric bearing 99 used to deflect the roller journal 205 in an adjustable magnitude in any direction orthogonal to the central axes of the respective rollers 201, 202. The eccentric bearing 99 comprises an outer eccentric bush 101, the inner bore of which is eccentric with respect to the outer diameter of the outer eccentric bush 101. The eccentric bearing 99 also includes an inner eccentric bush 102, the inner bore 105 of which is concentric with the outer diameter of the outer eccentric bush 101 in the starting position. Since the inner eccentric bush 102 and the outer eccentric bush 101 are pivotable relative to one another or in the same direction, the eccentricity of the inner bore 105 of the inner eccentric bush 102 is adjustable, and the direction and degree of deflection are variable. Each of the eccentric bushes 101, 102 has a thick portion and a thin portion on the side opposite the thick portion. In the above-mentioned starting position, the thick portion of the outer eccentric bush 101 and the thin portion of the inner eccentric bush 102 are close to each other, and the thin portion of the outer eccentric bush 101 and the thick portion of the inner eccentric bush 102 are close to each other. When both eccentric bushes 101, 102 rotate 180° relative to one another, the maximum possible deflection off-center can be achieved.

[0025] Figure 2 shows an embodiment of the drive device 1 according to the present invention. In a bush 520 that can be connected to the machine frame 500, an eccentric bearing 99 is accommodated. The eccentric bearing 99 has inner and outer eccentric bushes 101 and 102 that are rotatable relative to each other about the X-axis, or rotatable relative to the bush 520, or rotatable relative to a roller journal 205 that can be accommodated in the inner bore 105 of the inner eccentric bush 102. To drive the eccentric bush facing the center of the roller, a first drive unit 300 is provided. The first drive unit 300 has a drive element 302 arranged perpendicular to the X-axis, and the drive element 302 is accommodated in a housing 306. The housing 306 has an interface surface with the bush 520, whereby the drive element 302 is coupled to a transmission output in the form of an external gear 301 arranged on the outer circumference of the free end 104 of the eccentric bush, and the drive element 302 is tangentially linked to the external gear 301. A servo motor 304 for driving the drive element 302 is coupled to the drive element 302 via an angle gear 305. The motor 304 is perpendicular to the drive element 302 and is arranged parallel to the X-axis above the bush 520. To drive the eccentric bush facing outward from the center of the roller, a second drive unit 300 designed corresponding to the first drive unit 300 is provided. The drive element 302 accommodated in the housing 306 is coupled to the free end 104 of the eccentric bush facing outward from the center of the roller. The housing 306 and the drive element 302 are arranged parallel to each other on the right side of the X-axis. In contrast to the first drive unit 300, in the second drive unit 300, the motor 304 is arranged below the bush 520, is also perpendicular to the drive element 302, is not parallel to the X-axis, but rather is arranged vertically and intersects the bush 520. To read the setting of the eccentric bush facing the center of the roller, the bush 520 has, on its upper side, an observation window through which the adjustment scale 400 provided at the free end 104 can be read. To read the setting of the eccentric bush facing outward from the center of the roller, there is a scaling ring with an additional adjustment scale 400 on the front side of the free end 104 of the eccentric bush, which can be read from the front.

[0026] Figure 4 shows a cross-sectional view through roller 201 and the eccentric bearing 99 attached to roller journal 205 of roller 201. Roller 201 is attached to machine frame 500, which has a bush 520 that houses roller journal 205 together with eccentric bearing 99. Eccentric bearing 99 basically includes an inner eccentric bush 102 and an outer eccentric bush 101, and roller journal 205 is housed in the bore 105 of inner eccentric bush 102. Inner eccentric bush 102 is partially inserted into outer eccentric bush 101 and has an axial overlap region 103. Outer eccentric bush 101 is attached to the cylinder bush via a first radial bearing 110 in a manner rotatable axially relative thereto. Inner eccentric bush 102 is attached to outer eccentric bush 101 via a second axially rotatable radial bearing 120. Roller journal 205 is attached to inner eccentric bush 130 via a third radial bearing 130 in a manner rotatable axially relative thereto. In the illustrated orientation, eccentric bearing 99 is in its starting position, in which case the thick part of outer eccentric bush 101 is close to the thin part of inner eccentric bush 102 and the thin part of outer eccentric bush 101 is close to the thick part of inner eccentric bush 102, so that roller journal 205 is centered and not deflected. Eccentric bushes 101 and 102 can be adjusted independently of each other by a separate drive unit 300. For this purpose, eccentric bushes 101, 102 each have a free end 104 extending outward from the overlap region 103, and the free ends 104 each have a transmission output in the form of an external external gear 301, via which eccentric bushes 101, 102 can be adjusted independently of each other. On the front side, inner eccentric bush 102 facing outward from the center of the roller has an adjustment scale 400 that can be read from the front side. On the rear side, outer eccentric bush 101 facing the center of the roller has an adjustment scale 400 that can be read on the circumference.

[0027] Figure 5 shows a perspective front view of the calendar 2 having two rollers 201 mounted horizontally and parallel to the machine frame 500. These rollers form a roller gap 220 and are thus arranged very close to each other. A drive device 1 equipped with two drive units 300 each is attached to the roller journals 205 protruding from the machine frame respectively. As shown in the figure, the drive elements 302 each have a worm shaft 303 that engages with each external gear 301. All the drive elements 302 are respectively arranged vertically on the side of the roller 201 facing outward from the roller gap 220. One motor 304 of each drive device 1 is respectively arranged above each roller 201, and one motor 304 of each drive device 1 is arranged below each roller 201. At the same time, all the motors are aligned perpendicular to the drive elements 302 and parallel to the roller axis X.

[0028] Figure 6 shows an overall view of the calendar 2 shown in Figure 5. This shows the attachment of a basic mirror image of the roller journals 205 provided at both ends of the roller 201 within the machine frame 500. A drive device 1 equipped with one eccentric bearing 99 and two drive units 300 each is attached to each roller journal 205. The roller gap 220 of several millimeters formed between the rollers 201 can be clearly seen. This requires a very compact design of the connecting elements such as the front drive unit 300 for the roller 201. All the motors 304 are attached to the side of the roller 201 facing outward from the roller gap 220. One motor 304 is attached to the upper part respectively, one motor 304 is attached to the bottom of the roller 201, and is attached parallel to the roller axis.

[0029] FIG. 7 shows a top view of a multi-roller calendar 3 showing the apparatus of roller 201 in relation to support roller 210 in an integrated roller system according to an embodiment. The multi-roller calendar 2 is used to produce a separator film (not shown) coated on both sides using electrode films 601, 602. The apparatus has two calendar devices 2 arranged side by side in the front, and these calendar devices 2 have main transport directions Y1, Y2 in opposite directions. Each of the calendar devices 2 has eight rollers 201, 210, 310 mounted within a machine frame 500. On the input side, the apparatus has two rollers 201 laterally supported by support rollers 210, and the two rollers 201 are used as powder mills for producing electrode films 601, 602 from a powder electrode precursor material. Following the support rollers, there are four conveyor rollers 310 each, and the four conveyor rollers 310 impart a desired width and thickness to the electrode film and homogenize it. The input side end roller 210 is designed as a support roller 210, and the support roller 210 is directly wound onto the first roller 201. The output side conveyor rollers 310 form a common end roller gap 13, and in the common end roller gap 13, the electrode films 601, 602 are applied to the separator film.

[0030] The elements of the invention disclosed in the above description, figures, and claims may be essential for the implementation of the invention, either individually or in any combination.

[0031]

Description of Reference Numerals

[0032] 1 Drive device 2 Calendar 13 End roller gap 99 Eccentric bearing 100 Pretensioning device 101 Outer eccentric bush 102 Inner eccentric bush 103 Axial overlap region 104 Free end Bore of the inner eccentric bush 110 First radial bearing 120 Second radial bearing 130 Third radial bearing 201 Roller 205 Roller journal 210 Support roller 220 Roller gap 300 Drive unit 301 External gear 302 Drive element 303 Worm shaft 304 Motor 305 Angular gear 310 Conveyor roller 400 Adjustment scale 500 Calendar frame 501 Bearing 520 Bore / bush 601 First electrode film 602 Second electrode film X-axis direction Y1 Conveying direction of the first electrode film Y2 Conveying direction of the second electrode film

Claims

1. A drive (1) for radially deflecting a roller (205) mounted in an eccentric bearing (99), said eccentric bearing (99) having an axially (X) oriented bore (105) for receiving a roller journal (205) of a roller (201), said eccentric bearing (99) having an outer eccentric bush (101) and an inner eccentric bush (102) partially inserted in said outer eccentric bush (101) and having said bore (105), said eccentric bushes (101, 102) being arranged in an axially overlapping manner. the drive device (1) having a bore (105) and a free end (104) outside the axial overlap region (103), the free end being coupled to a drive unit (300) via which at least one of the eccentric bushes (101, 102) is rotatable about the axial direction (X) to adjust a radial axial deflection of the bore (105) relative to the other eccentric bush (101, 102).

2. 2. The drive device (1) according to claim 1, wherein both eccentric bushes (101, 102) have free ends (104) on opposite sides of the axial overlap region (103), said free ends being respectively coupled to said drive unit (300) via which said eccentric bushes (101, 102) can be rotated independently of one another about said axial direction (X) in order to adjust the deflection of the radial axis of said bore (105).

3. 3. The drive device (1) according to claim 1 or 2, wherein the drive unit (300) has a transmission output, e.g. an external gear (301), and is arranged at least partially on the outer periphery of the free end (104) and coupled to the free end.

4. 4. The drive arrangement (1) according to claim 3, wherein the drive unit (1) has a drive element (302) coupled to the transmission output, the drive element (302) being arranged perpendicular to the axial direction (X).

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

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

7. The drive device (1) according to any one of claims 4 to 6, wherein the eccentric bearing (99) is mounted in a bush (520) of a machine frame (500) and the drive element (302) is driven by a motor (304) arranged outside the bush (520).

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

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

10. 10. The drive arrangement (1) according to claim 8 or 9, wherein the angular offset is provided by an angular gear (305) coupling the drive element (302) to the motor (304).

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

12. 10. The drive device (1) according to any one of the preceding claims, wherein the eccentric bushes (101, 102) each have an adjustment scale (400) which can be read from outside the bush (520).

13. 12. The drive device (1) according to claim 11, wherein the adjustment scale (400) of one of the eccentric bushes (101, 102) points in the axial direction and the setting scale (400) of the other of the eccentric bushes (101, 102) points in the radial direction (Y), and the adjustment scales (400) can be read therefrom.

14. A calender (2) having at least two rollers (201) arranged in parallel and mounted in a calender frame (500) forming a roller gap therebetween, each said roller (201) having a roller journal (205) mounted at its opposite ends in the calender frame (500), at least two adjacent roller journals (205) having a drive device (1) according to any one of the preceding claims.

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

16. 15. The calender (2) according to claim 14, wherein the drive elements (302) of adjacent drive devices (1) are oriented parallel to one another.

17. 16. The calender (2) according to claim 14 or 15, wherein the motors (304) of adjacent drives (1) are oriented parallel to the roller axis (X) or are arranged to point away from the respective adjacent drive (1).

18. 17. The calender (2) according to any one of claims 14 to 16, wherein a first support roller (210) is arranged adjacent to the first said roller (201) and a second support roller (210) is arranged adjacent to the second said roller (201), each rotating in an opposite direction to the latter.

19. 18. The calender (2) according to claim 17, wherein each of said support rollers (210) is larger than the diameter of said roller.

20. 19. A calender (1) according to claim 17 or 18, wherein the axes of the rollers (201) and the support rollers (210) are aligned in a plane with respect to each other.

21. 21. The calender according to claim 14, wherein the first roller (201) and the first support roller (210) roll against each other and a roller gap (220) is formed between the second roller (201) and the second support roller (210).

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