Device for processing sheets and / or webs

Abstract

Apparatus for processing sheets and / or webs, having a pair of driven rollers forming a working gap, in which a transmission group connected to the rollers has a stationary gear that varies with respect to the working gap formed by the rollers and a second gear that moves together with one of the rollers and cooperates with the stationary gear, moreover, the axle distance between the two transmission gears is kept constant, and the axle distance is independent of the change of the working clearance.

Description

Field of the Invention

[0001] The present invention relates to an apparatus for processing sheets and / or webs according to the preamble of claim 1 and a method for processing sheets and / or webs according to the preamble of claim 10. Background Art

[0002] For processing sheets and / or webs, apparatuses are known having one or more pairs of cooperating cylindrical rollers. These rollers are oriented parallel to one another and together form a working gap. The working gap is arranged according to the thickness of the material sheet or web. The rollers are arranged transversely to the transport direction of the material to be processed.

[0003] For example, the roller pair may have an impression cylinder or a stamping cylinder as a working roller. The second roller is typically a counter-pressure roller that only resists the displacement of the sheet and / or web and, together with the working roller, assumes a transport function.

[0004] For the function of the roller pair, it is necessary to precisely coordinate the working gap with characteristics such as the thickness and elasticity of the material to be processed. For this purpose, feed devices are known.

[0005] At the same time, in the case where the working roller provides an image or a shape, the phase position of the working cylinder should be maintained at least when the working gap changes. For example, this is essential for a printing press having a plurality of printing mechanisms or combined with a rotary die.

[0006] For this purpose, a spur gear transmission set is known for driving at least the working cylinder. In an apparatus for processing hard materials such as corrugated paper, the working gap is adjusted by the movement of the rollers on the common side of the sheet or web. When processing on both sides by a plurality of roller pairs, this results in that at least one working roller must be moved for gap adjustment.

[0007] In order to maintain the phase position of the working roller, the change in the axle distance within one spur gear stage of the drive is tolerated. This solution is very simple in structure. On the other hand, the change in the working gap necessarily leads to a change in the clearance of the transmission set and thus to a less smooth operation of the apparatus and higher wear. In addition, the adjustment range is preset within a very narrow range. Summary of the Invention

[0008] Therefore, the object of the present invention is to provide an apparatus and a method that overcome at least one of the disadvantages disclosed in the prior art.

[0009] The above object is solved by the apparatus according to claim 1. Advantageous developments of the present invention are characterized by the features given in the dependent claims.

[0010] This device for processing a material sheet or web has a tool pair. The tool pair is formed by a working roll and a counterpressure roll. The two rolls are driven together. For this purpose, the device has a motor which is connected to the tool pair via a transmission group. At least the working roll has a predetermined phase position relative to the main axis of the device. The physical presence of the main axis is not necessary. It can also be a virtual axis simulated electronically.

[0011] The same motor can be connected to other operating units of the device and drive these operating units. These operating units can also have a predetermined phase position relative to the main axis. This phase position can be different from the phase position of the above-mentioned working roll.

[0012] The rolls of the tool pair are oriented parallel to each other. Their axes of rotation are oriented transversely to the transport direction of the material to be processed. The rolls are arranged relative to each other such that they together form a working gap through which the material to be processed is transported. The working gap can be adjusted to a predetermined size. Here, this size is determined by the thickness and mechanical properties (such as elasticity) of the material to be processed.

[0013] To adjust the working gap, the working roll is accommodated in a feed device. The feed movement is radially aligned relative to the working roll with respect to the axis of rotation of its counterpressure roll. Of course, the feed can be carried out in both directions.

[0014] The drive of the working roll has three or more drive elements, each of which has an axis parallel to the axis of rotation of the working roll. These drive elements can be gears or pulleys, etc. The first drive element among these drive elements is accommodated in the feed device together with the working roll. When changing the working gap, this first drive element moves its position together with the working roll. The second drive element is supported in an unchangeable position with respect to the change of the working gap.

[0015] The third drive element is used for the drive connection between the first drive element and the second drive element. It is accommodated in a pivot arm. The pivot axis of the arm having the third drive element either coincides with the axis of rotation of the first drive element or coincides with the axis of rotation of the second drive element.

[0016] The axial distance from the first drive element to the third drive element and the axial distance from the second drive element to the third drive element are both independent of the working gap of the roll pair and its change. The first axial distance is determined by the design of the pivot arm. The second axial distance remains constant through the pivoting of the arm. Therefore, the drive elements can be designed respectively with a constant axial distance. Thus, the transmission group clearance can be kept small and is especially independent of the working gap. Thereby, an improved product quality is achieved and an improved running smoothness and durability of the device are achieved.

[0017] Here, it is advantageous to have a forced guidance of the pivot arm. In a first design, the forced guidance is achieved by a second arm. The second arm serves as a coupling between a third drive element on one side and a first drive element or a second drive element on the other side that does not form the pivot axis of the first pivot arm. In an alternative design, the pivot arm has an arcuate guide. The arcuate guide traces a circular arc around the first or second drive element that does not form the pivot axis of the pivot arm.

[0018] The feeding device is equipped with a controllable drive. The drive is connected to the electronic control device of the equipment via a data connection. The control device receives information about the material to be processed and determines the required working gap from this information.

[0019] The phase position of the working roller relative to the main shaft should not change due to the change of the working gap. Especially if the equipment has one or more additional processing devices, it is necessary to maintain the phase position.

[0020] According to the invention, the equipment has a second feeding device. The second feeding device is effectively connected to the working roller and determines its phase position relative to the physical or electronic main shaft of the equipment. Preferably, the second feeding device includes a controllable feeding drive. The feeding drive is connected to the electronic control device of the equipment by means of a device for data transmission.

[0021] A measuring device for detecting the phase position of the working roller relative to the main shaft is advantageous. The sensor of the measuring device is connected to the electronic control device by means of a device for data transmission. In this way, the control device receives information about the actual current phase position. Therefore, active adjustment of the phase position can be achieved in cooperation with the second feeding device. Thus, misregistration can be avoided.

[0022] Preferably, the equipment includes a second measuring device. The second measuring device detects the width of the working gap. The second measuring device has a sensor for directly detecting the width of the working gap or a characterization of the working gap. The characterization can be generated by means of a switching flag. However, data from the servo drive itself can also be used, so that an additional sensor can be omitted.

[0023] In an advantageous design, the electronic control device of the equipment has a data memory. In the data memory, the correspondence between the predetermined phase position and the width of the working gap or the corresponding characterization is stored. Thereby, when adjusting the working gap, the phase position of the working roller can be automatically tracked under permanent drive coupling without affecting the transmission group clearance. Description of the Drawings

[0024] The present invention will be described below with reference to the accompanying drawings by means of embodiments. All details not further mentioned in the description refer to the drawings.

[0025] In the figure:

[0026] Figure 1 A first embodiment of a pair of rollers with a variable working gap is schematically shown;

[0027] Figure 2 A second embodiment of a pair of rollers with a variable working gap is schematically shown;

[0028] Figure 3 A flexographic printing mechanism is shown in perspective view. Detailed implementation mode

[0029] In Figure 1 a first embodiment is schematically shown. Here, a counter-pressure roller 2 is arranged above the working roller 1. The working roller 1 is rotatably supported about a first rotation axis 201, while the counter-pressure roller can rotate about a second rotation axis 202. The two rotation axes 201, 202 are oriented parallel to each other. The two rollers 1, 2 act together on the material sheet 6. Instead of the sheet 6, a material web (not shown) can also be processed. The two rollers 1, 2 together form a working gap 4. The width of the working gap 4 is predetermined by the thickness of the material 6 to be processed.

[0030] Through the working gap 4, the material 6 moves in a horizontal conveying direction 200 transverse to the rollers 1, 2. Here, the working roller 1 rolls on the material 6 to be processed with a first rotational movement 101 and the counter-pressure roller 2 rolls on the material 6 to be processed with a second rotational movement 102.

[0031] The counter-pressure roller 2 is fixedly received in the machine frame 5, while the working roller 1 is supported in the feeding device 10. The feeding device 10 presets a vertical feeding direction 103 for the working roller 1. For this purpose, the feeding device 10 is arranged to be movable relative to the machine frame 5 by a linear guide 11. As a feeding device, the feeding device 10 has an eccentric wheel 16 embedded in a fork. The eccentric wheel is driven by a feeding drive 15.

[0032] The feeding device 10 has a sensor 18. The sensor detects the distance characterizing the width 210 of the working gap 4. The sensor 18 is connected to the control device 7 of the equipment through a line 80 as a device for data transmission. The feeding drive 15 is likewise connected to the same control device 7 through another line 81 as a device for data transmission. Thereby, the control device 7 can adjust the width 210 of the working gap 4 according to a preset rated value.

[0033] The working roll 1 and its counter-pressure roll 2 are both driven by the same motor (not shown). Their rotational directions 101, 102 during processing are marked in the figure. The drive connection includes a plurality of spur gears 31, 32, 33, 34, 41, 42. Among them, the first set 30 is used to drive the working roll 1. The first set includes a plurality of gears 31, 32, 33, 34. Among them, the first spur gear 31 and the second spur gear 32 connected to the first spur gear through an intermediate gear are accommodated in the feeding device 10 for the working gap 4 together with the working roll 1.

[0034] The second spur gear 32 meshes with the third gear 33. Among them, the third spur gear 33 is accommodated in an arm 13 that can pivot around a pivot axis 203. The pivot axis 203 of the pivot arm 13 is arranged in the frame 5 of the device and is fixedly arranged relative to the feeding movement of the working gap 4. It coincides with the rotational axis of the fourth spur gear 34 fixed to the frame and supported in the frame 5. The fourth spur gear 34 also meshes with the pivotally arranged third gear 33.

[0035] The axial distance between the first spur gear 31 and the second gear 32 and the axial distance 204 between the third gear 33 and the fourth spur gear 34 are preset to be fixed by their arrangement. Even when adjusting the working gap 4 through the guide part 12, the axial distance between the second spur gear 32 and the third spur gear 33 moving together with the working roll 1 remains constant. The guide part 12 imposes the movement form for the corresponding feeding movement on the arm 13 with the third gear 33 supported therein. The feeding movement is designed as an arc concentric with the second spur gear 32.

[0036] The second feeding device 20 is used to adapt the phase position of the working roll 1 to the physical or electronic analog spindle of the device (not shown). It includes a feeding driver 21, which is effectively connected to the working roll 1 through a differential 22. The feeding driver 21 is connected to the control device 7 of the device through a line 71 as a data transmission device.

[0037] The relationship between the gap width 210 and the resulting phase position deviation is stored in the data memory 90 of the control device 7. This mathematical function can be stored as a table or an equation. Therefore, the phase shift occurring due to the adjustment of the working gap 4 can be corrected.

[0038] Therefore, this makes it possible to adjust the working gap 4 in the permanent drive connection of the working roll 1 and even during continuous processing by the roll pair 1, 2 without changing the phase position of the working roll 1 relative to the physical or electronic spindle of the device.

[0039] Alternatively or additionally, a sensor 23 is provided which detects the phase position of the working roll 1 or a corresponding representation. It is likewise connected to the same control device 7 via a line 70 serving as a data transmission means. Thus, an active adjustment of the phase position to a predetermined nominal value can be achieved.

[0040] A second embodiment is shown in Figure 2 . Here, the impression cylinder as the working roll 1 cooperates with the counter-impression cylinder as the counter-pressure roll 2. Together they form a nip 4. Different from the example shown in Figure 1 , the arcuate guide 12 of the pivoting arm 13 is replaced by a second arm 14. The pivot axis 203 of the second arm 14 coincides with the axis of rotation of the spur gear 32 which moves together with the working roll 1 relative to the working nip 4.

[0041] Furthermore, a screw drive 17 is used instead of the above-mentioned eccentric 16 as the adjusting means of the feed device 10 for changing the working nip 4. An additional sensor for detecting the width 210 of the working nip 4 is dispensed with. Instead, the data returned by the feed drive 15 via a means 80 for data transmission is used as a representation of the nip width 210.

[0042] Likewise, the information detected by the feed drive 21 for changing the phase position is used as a representation of the actual phase position. This data is returned to the control device 7 via a means 71 for data transmission. As explained in the previous example, in the second example an additional sensor can be dispensed with without loss of function.

[0043] Figure 3 A partial section of a flexographic printing mechanism is shown as another embodiment. It is a variant of the first example shown in Figure 1 . The impression cylinder as the working roll 1 cooperates with the counter-impression cylinder as the counter-pressure roll 2. In this case, the impression cylinder 1 is arranged above the counter-impression cylinder 2. Together they form a nip 4.

[0044] In order to adapt the nip 4 to the substrate, the impression cylinder 1 is adjustably accommodated in the machine frame 5 in the vertical direction 103.

[0045] The counter-impression cylinder is fixedly supported in the machine frame 5, while the feed device 10 receives the impression cylinder 1. The feed device 10 has a linear guide 11. The linear guide 11 prescribes a vertical feed direction 103 for the impression cylinder 1 which is rotatable about its axis 201. The feed is effected by means (such as a screw or an eccentric) of a known type not shown further.

[0046] The driving of the rollers 1 and 2 is carried out by a transmission group 3 composed of a plurality of spur gears 31, 32, 33, 34. In order to achieve a transmission clearance independent of the width of the joint, all the shaft distances of the spur gears 31, 32, 33, 34 that mesh with each other are constant with respect to the width of the joint.

[0047] For this purpose, an intermediate gear 33 is provided, which meshes not only with the spur gear 34 fixed to the machine frame but also with the spur gear 32 that can be vertically adjusted together with the impression cylinder 1. The intermediate gear 33 is accommodated in the pivot arm 13. Contrary to the example shown in Figure 1 , according to Figure 3 , the pivot axis 203 coincides here with the axis of rotation of the spur gear 32 that can be adjusted together with the impression cylinder 1.

[0048] The end of the pivot arm 13 that houses the intermediate gear 33 is guided in a curved manner. For this purpose, an arcuate guide 12 is provided. The chute position of the arcuate guide 12 is fixedly mounted on the machine frame 5. A curve roller arranged concentrically with the intermediate gear 33 moves in this chute. The arcuate guide 12 is determined by an arc concentric with the spur gear 34 that meshes with the intermediate gear 33 fixed to the machine frame.

[0049] Therefore, as the width of the joint changes, the intermediate gear 33 moves on a concentric track around the spur gear 34 fixed to the machine frame. The shaft distance between the intermediate gear 33 and the spur gear 34 fixed to the machine frame that meshes with it, as well as the shaft distance between the intermediate gear 33 and the spur gear 32 that can be fed together with the impression cylinder 1, remain constant, regardless of the width of the joint.

[0050] Therefore, the change of the joint causes an undesired change in the phase position of the impression cylinder 1 relative to the main shaft of the entire machine. To compensate for this undesired adjustment, another feeding device 20 is provided. The feeding drive 21 of this feeding device is connected to the impression cylinder 1 by means of a differential 22 in such a way that it is suitable for adjusting the phase position of the impression cylinder 1 relative to the virtual main shaft of the machine to a predetermined value.

[0051] As shown in Figure 2 , the feeding drive 21 for the phase position is connected to the machine control device 7 by means of devices 70, 71 for data transmission. Here, a data line 71 is provided to transmit the control signal of the machine control device 7. Another data line 70 returns this information obtained in the feeding drive 21 to the control device 7, and these information are used as a characterization of the phase position.

[0052] In this way, the phase position can not only be actively adjusted to a predetermined value during steady-state operation. Instead, it can also compensate for the undesired change in the phase position that occurs due to the adjustment of the joint 4 or correct the phase position.

[0053] Even during continuous production, it is possible to prevent a loss of the desired phase position or register accuracy due to a desired change in the nip 4 (for example, to adapt the color transfer from the printing cylinder 1 to the substrate 6).

[0054] As an alternative to the illustrated embodiment, the spur gear can be replaced by a belt pulley.

[0055] Reference numerals:

[0056] 1 Working roller 33 Intermediate gear

[0057] 2 Counter-pressure roller 34 Upstream spur gear

[0058] 3 Drive 35 Brake

[0059] 4 Working gap 37 Coupler

[0060] 5 Frame 40 Transmission group of the counter-pressure roller

[0061] 6 Material sheet 41 Spur gear

[0062] 7 Control device 42 Spur gear

[0063] 10 Feeding device 70 Data line

[0064] 11 Linear guide 71 Data line

[0065] 12 Arc guide 80 Data line

[0066] 13 First lever 81 Data line

[0067] 14 Second lever 90 Data memory

[0068] 15 Feeding drive 101 Rotational movement of the working roller

[0069] 16 Eccentric wheel

[0070] 17 Screw drive 102 Rotational movement of the counter-pressure roller

[0071] 18 Sensor for the gap width

[0072] 20 Register adjustment unit 103 Feeding movement of the nip

[0073] 21 Feeding drive for the phase position 104 Pivoting movement of the arm

[0074] 22 Differential 105 Rolling of the intermediate gear

[0075] 23 Sensor for the phase position 200 Transport direction

[0076] 30 Transmission group of the work roll 201 Rotation axis of the work roll

[0077] 31 Spur gear 202 Rotation axis of the counter-pressure roll

[0078] 32 Downstream spur gear 203 Pivot axis

[0079] 204 Axle distance

[0080] 210 Width of the working gap

Claims

1. An apparatus for processing sheet-like and / or web-like substrates (6), such as paper, cardboard, corrugated cardboard or similar materials, the apparatus having at least · A work roll (1) rotatable about its axis (201), wherein, The working roll (1) extends substantially transversely to the transport direction (200) of the substrate (6) to be processed; · A counter-pressure roll (202) assigned to and cooperating with the at least one working roll (1) and rotatable about its axis (202), wherein the counter-pressure roll (2) is oriented substantially parallel to the at least one working roll (1) assigned thereto, and the at least one counter-pressure roll (2) and the at least one working roll (1) assigned thereto together form a working gap (4), and the substrate (6) to be processed is transported through the working gap in the transport direction (200) and the substrate (6) is processed at least by the working roll (1) in the working gap; · A drive having a motor and a transmission group (30, 40), wherein the transmission group (30, 40) forms a drive connection between the motor and the working roll (1) and the counter-pressure roll (2); · A first feed device (10) assigned to the at least one working roll (1) and / or the at least one counter-pressure roll (2), wherein the at least one first feed device (10) is connected to the at least one working roll (1) and / or the at least one counter-pressure roll (2) such that the at least one first feed device (10) is adapted to adjust the working gap (4) between the working roll (1) and the counter-pressure roll (2) to a predetermined dimension (210) and · A second feed device (20) assigned to the at least one working roll (1), wherein the second feed device (20) is connected to the working roll (1) such that the at least one second feed device (20) is adapted to adjust the phase position of the working roll (1) relative to the physical and / or virtual main axis of the apparatus to a predetermined dimension; Characterized in that at least one controllable feed drive (21) and an electronic control device (7) of the second feed device (20), wherein the at least one feed drive (21) and the at least one control device (7) are connected to each other by at least one first device (71) for data transmission.

2. The device according to claim 1, wherein At least one first measuring device (23) for receiving the phase position of the working roll (1), wherein the at least one first measuring device (23) is connected to the at least one control device (7) of the at least one feed drive (21) by at least one second device (70) for data transmission.

3. The device according to one of the above claims, characterized in that At least one second measuring device (18) for receiving the gap dimension (210) between the working roll (1) and the corresponding counter-pressure roll (2) or a representation of the gap dimension (210), wherein the at least one second measuring device (18) is connected to the at least one control device (7) by at least one third device (80) for data transmission.

4. The device according to one of the above claims, characterized in that, The at least one control device (7) is provided with at least one data memory (90), which has a relationship between the phase position of the working drum (1) relative to the physical and / or virtual main axis of the device and the dimension of the working gap (210), wherein the relationship is stored in the data memory (90) as a mathematical equation and / or a numerical table.

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