FI105799B - Guiding and controlling device for a roller rack for a paper web - Google Patents

Description

, 105799

BACKGROUND OF THE INVENTION The present invention relates to a control device for a web winder according to claim 1. The invention further relates to a position difference control apparatus according to the preamble of claim 6 in connection with a web reel control apparatus.

The web material rollers are used as a continuous web to wind the incoming material into a compact roll for transfer to further processing. The paper web reel rolls a continuous paper web from a paper machine, coating machine, or other similar paper handling equipment to roll onto a reel axis or reel. For example, the so-called. After the calender, the pope roller or the center-assisted pope roller rolls the finished paper around the roll-15 block axis. The web is introduced to the roll through a roller cylinder arranged to be rotatable, against which the loading axis is loaded with a loading device connected to the winding axis.

The web enters the winding shaft between the previous layers of the roll and the casing surface of the roll roll 20. At this point, where the web comes into contact with the previous layers of the roll, the web is affected by a certain nip load, line pressure, due to the above loading device. In current roller types, the winding shaft is also center driven, and the momentum of the winding shaft can also influence the circumferential force of the winding web.

25 The winding nip between the scroll cylinder and the roller is primarily used to prevent air from entering the roller. However, by controlling the load applied to the web, it is also possible to control the tightness of the resulting roll, and furthermore, it is sought to adjust the load during the roll to maintain the roll tightness at various locations within the roll radius. The winding event is controlled indirectly by adjusting the winding parameters (line load, track tension, circumferential force, and roll force.). The adjustment is usually made with a specific program.

The main purpose of the winding is to roll from a continuous paper web a roll that satisfies the conditions of the winding process and further processing in terms of hand-rollability and hence the roll structure as well as the paper quality. Paper machine speeds today are generally 20 m / s or more, and the goal is, of course, to achieve ever higher speeds.

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2 105799

The winding apparatus must operate continuously and receive continuous paper from the preceding parts of the paper machine.

When the old roll is full, the web must be cut and the web after the cut-off point 5 started to wrap around the new winding axis. In practice, this is done by moving the paper roll formed around the reel axis to its full size, usually simultaneously and from above the reel cylinder, with a new empty reel axis on the surface of the reel cylinder with the paper web between them.

10 The entire roll of paper is removed from the winding cylinder and then the paper money is cut off in some suitable manner and the end of the web after the cut-off point is guided to the periphery of the empty winding shaft, where new web begins to accumulate. The new winding shaft is then moved to a winding trolley over separate linear guides or over horizontal straight winding rails. For example, a full reel is moved by the transfer device along the reeling rails to the discharge station, and at the same time a new reeling shaft is introduced onto the reeling rails. During the initial winding, the load is controlled by the power units of the initial winding device, and when the winding shaft moves to the winding carriage, for example, the load is controlled by the power units connected to the winding carriage 20, usually by pressure medium cylinders.

For example, US 4634068 discloses a winding apparatus in which an empty roll is lowered onto a winding cylinder. In addition, the actuators of the starter winding device of U.S. Pat. No. 4,634,068, i.e., separate loading cylinder and relief cylinder, are specifically mentioned, and a loading cylinder which presses the shaft against the winding cylinders is located on the winding rails. The hydraulic cylinder used is connected, for example, to the pivoting pivoting pivoting pivots.

30

The properties of the web affect the quality of the roll. For example, the most common. the problem of winding caused by a poor track tension profile is the plucking of loose points on the track, usually the edges, in the winding nip or roll nip because the track is looser than tense. Loose edge edges also cause a poor edge area on the roller and, as a result, • poorly edged edges that are difficult to roll with winders and have problems with roller use, such as in printing presses. If the track tension profile is very variable or, for example, one-sided, it may lead to the use of high track tension for safety 5, which causes more stress on the track tension points and increases the number of track breaks.

In a roller control circuit disclosed in U.S. Patent No. 5,285,979, the load is applied to the roller body by means of 10 wagons moving along linear guides to which the power unit to be loaded is connected. In the publication, the winding shaft is arranged on the carriage pivotable on the pivoting pivot arm which, however, remains stationary during loading and is only used to remove the fully rolled pivot by rotating the pivoting arm in the discharge direction with special discharge cylinders. Em. the power unit 15 provides the desired loading force or displacement of the winding shaft further from the winding cylinder as the roll size increases. In the initial winding device, this can also be accomplished by means of separate lightening cylinders as disclosed in US 4,634,068. With the help of Keven nozzle cylinders, it is possible to compensate for the effect of the earth's pulling force on the winding cylinder, and thus they are used for so-called roller cylinders. profiling. It is also common for the initial winding device to handle the loading, lightening and adjustment of the position of the winding shaft relative to the winding cylinder by means of a single double-acting pressure medium cylinder.

US Patent 5,285,979 also discloses the use of a hydraulic cylinder separately, provided that the winding cylinder and the rising roller are kept at a desired distance from each other, thereby providing a photocell-generating signal. The actual load force is influenced by many factors, such as the friction caused by the movement of the power unit and, in addition, the frictional motion of the structure supporting the winding shaft during its movement. It should also be noted that the power regulating body functions as a ser. · A butterfly valve which controls a cylinder acting as a power unit which still controls only one wagon.

Also known are rollers as disclosed in EP 604558, corresponding to U.S. Patent 5,393,008. The patent discloses wagons arranged in linear motion on guides parallel to the winding rails, the position of which is determined by hydraulic cylinders coupled between the roller body and the wagons. These hydraulic blades thus also control the position of the winding shaft relative to the winding cylinder. The wagons are provided with separate printing devices which force-adjust the spacer bearings at the ends of the winding shaft, resting on the winding rails, to provide the necessary nip pressure in the direction of the winding cylinder. On the other side of the bearing housing, the carriages also have positioning devices which allow for more precise adjustment of the position of the reel shaft on the carriages.

10

In the cases described above, e.g. for controlling the winding carriage, the initial winding apparatus and the loading apparatus, hydraulic cylinders are typically used in pairs to control the different ends of the winding shaft. Here, the control of the ends is arranged, for example, by means of a continuous carriage or a carriage moving independently on each end 15. In addition, it is then possible to arrange the line loading between the machine roll and the winding cylinder also in the transverse direction of the paper web. From the foregoing, it is clear that for reliable operation, the control of power units must also be reliable and simple. The speed of the guide is important first and foremost in the case of fast web speeds in order to keep the paper roll quality as smooth as possible even in the control situation. However, the speed of control in the above examples depends on, for example, the operating delays of the valves used to control the pressure medium, which may be considerable due to the large number of valves and, for example, their mutual pressure control. In particular, delays occur when the roller shaft transfer equipment and the loading equipment are separate, requiring separate sensing and separate control valves for their functions.

30

In the case of pairs of roller cylinders from the same pressure source at the same time. when feeding and synchronizing them by dividing the volume flow into the cylinders by means of a distributor motor known per se or the like, there is a particular risk that leaks in the distributor motor, hydraulic cylinders, pipelines, fittings and control valves will cause misalignment of the cylinders. As a result, for example, the position of the different ends of the winding shaft differs with respect to the i 5 105799 winding cylinder, especially when these ends are controlled by separate carriages, which causes problems especially in position control. When switching to load pressure adjustment, this causes additional delays to compensate for position difference errors and 5 load pressure variations during adjustment. Particularly critical steps in winding in terms of loading pressure and position control include, for example, the transfer of the winding shaft from the initial winder to the actual winding station.

The object of the invention is to eliminate the drawbacks of the prior art and to provide a new control apparatus for use in connection with winding, for example the so-called nip-15 load, the so-called. winding nip open, controlled by pressure-driven cylinders. In addition, the position difference control circuit connected to the control apparatus enables more precise control of the difference in position between the movements of the cylinders arranged in pairs. The aim is to minimize the difference in position.

To accomplish this purpose, the control apparatus according to the invention is characterized in what is set forth in the characterizing part of the attached claim 1. With respect to other preferred embodiments, reference is made to the appended dependent claims 2 to 5. The position difference control apparatus according to Kek-25 is characterized by what is set forth in the characterizing part of the appended claim 6. For other preferred embodiments, reference is made to the appended dependent claims 7-14.

The invention has the advantage of simplicity in which the control apparatus is easy and reliable to operate. The control system avoids special • ·. the operation of the valves and the simple design of the system mean that delays in system operation are minimal. The required functions can be performed, for example, by means of a single pair of hydraulic cylinders, whereby separate control circuits, 35 control valves and a plurality of cylinder pairs are unnecessary. Particularly noteworthy is the ease of control of the double-acting cylinders of the control unit • · 6 105799, particularly with respect to the control of separate relief and load cylinders. Due to the back pressure applied to the control apparatus, the volume flow through the chokes is more easily controlled by closer control of the pressure difference across the chokes 5. Due to the maintained back pressure, the hydraulic fluid has a higher stiffness, thus reducing the operating delays caused by the compression.

A significant advantage of the control apparatus is that it is combined with pressure control and position control of the power cylinders 10. Pressure control controls the line loading of the winding in the nip and position control controls the winding nip open, as well as moving the winding carriage to the unloading station, for example. A further significant advantage of the steering system is that the steering is controlled in both directions of movement of the cylinders.

15

A significant advantage of the position difference control connected to the control apparatus is that when the position difference control circuit is connected to only one cylinder line, the adjustment can be carried out simply and without the detrimental effect of other control circuits, for example the control circuit connected to the other cylinder. An advantageous embodiment of the position difference adjusting circuit further has the advantage that, especially in the throttle, the flow occurs in both directions, thus reducing the risk of the throttle members being clogged. An additional advantage of the position difference control circuit is that the leakage requirements for the control equipment components can be reduced, thus avoiding the use of expensive special components. A further advantage is that the control of other components of the control apparatus, such as the components supplying volume flow to the cylinders, can be simplified, with separate position difference control taking into account, for example, the movement position caused by cylinder leaks. The pressure differences due to variable friction are then controlled by the control device.

Y Another particular advantage of the position difference control circuit is that by observing · * and comparing the cumulative operation times of the control circuit valves, one can determine which cylinder or cylinder line flows through 35. Thus, over a long period of time, monitoring can be used to monitor equipment wear and maintenance. Monitoring can easily be accomplished, for example, by means of a separate data processing equipment, which • · i 7 105799 collects information on the operating times of the valves by means of the electrical control signals they receive. The data processing equipment may be implemented, for example, in a control unit for a control circuit to be described later.

The invention will now be described in more detail with reference to the accompanying drawings, in which: Figure 1 is a side view of a prior art web winder; 10 Figure 2 is a simplified principle view of a control apparatus according to a preferred embodiment of the invention; and Fig. 4 is a simplified schematic view of a position difference adjusting apparatus according to a second preferred embodiment of the invention.

In the following description, a control apparatus according to a preferred embodiment of the invention is illustrated as applied to the reel winding axis 25. However, it will be apparent to those skilled in the art from the disclosure that the invention will also be applicable elsewhere on the reel, for example in conjunction with an alarms. Of course, the position difference control apparatus may also be applied to other control apparatuses to obtain the advantages previously described.

30

Figure 1 is a simplified principle view of itself: known from the side of a roll of paper web. The reel has ·· a well known rotatable winding cylinder C, which allows continuous paper web W from a paper machine, coating machine, or other paper handling equipment to be rolled around a winding axis T1 into a machine roll R. The roll R is mt 8 105799 Force F1. This provides a roll nip N1 between the roller R and the winding cylinder C, which has a certain nip pressure due to loading. Also, the reel axis T1 also has a center drive, in the case of a center drive assisted pop reel, whereby also the torque of the reel axis T1 can influence the quality of the resulting reel R. Figure 1 also shows the winding axis T2 introduced by the reel starter winding apparatus in connection with the winding cylinder C. The winding shaft T2 is loaded against the winding cylinder C by applying to the winding shaft T2 a desired force F2 towards the winding cylinder C. This provides a winding nip N2 with a certain nip pressure as a result of loading on the winding shaft T2 and the winding cylinder C. The nip pressure in this case is also influenced by the weight of the winding shaft T2.

The winding cylinder C is known per se to be mounted on a stationary reel body K1 with respect to the support base, e.g. The winding shaft T1, in turn, is known to be bearing-mounted on roller winding rails K2, on which the ends of the winding shaft T1 rest at their bearing housings, and which bear the weight of the roller R at the same time. In the guide K3 on the body K1, the support carriage V1, which is known per se, moves the roller shaft T1 and at the same time rolls R in the longitudinal direction of the roller (arrow X). The carriage V also moves in the longitudinal direction of the winder and is of a type such that, without listening to the weight lu-25 possibly received by the winding cylinder C, the winding rail K2 carries the full weight of the winding shaft T1 and the roller R. The carriage V is arranged in a manner known per se to move linear movement relative to the winding cylinder C to move the roller R, and there is a possibility of movement in both directions, i.e. the carriage V can be moved back and forth (arrow X) by double action cylinders.

30 Trolley V can move over fixed linear guides or guided by rails. The support V1 or parts thereof pivotally mounted on the carriage V for pivoting with respect to the pivot point therein may be moved further by separate hydraulic cylinders (not shown), for example to move the finished roller away from the carriage V.

Referring to Figs. 2. In a similar manner, the load force F2 is provided by the power units 11 and 12. The power units 1 and 2, one on each side of the roller 5R, as well as the power units 11 and 12, act in known manner on the bearing housings of the winding shaft T1. In the following, the actuator 11 or 12 is also referred to as the actuator 11 or 12. The roll rule shaft T1, in turn, moves farther from the winding cylinder C as the roll 10 R increases, i.e. the radius of the roll R increases. As the winding progresses, the power units 1 and 2 provide the desired nip load.

The force F1 provided by the loading power units 1 and 2, in the following description, by the double-acting cylinders 1 and 2, is adjustable.

15 The most typical power unit used in rollers with adjustable force and high loading forces is a pressure medium-acting power unit of variable length, such as a hydraulic cylinder. The hydraulic cylinder is connected to the pressure source of the hydraulic fluid, and the pressure acting on the hydraulic cylinder, which simultaneously determines a load force F1 of 20, can be adjusted in known ways. This is a case of so-called. pressure control and, on the other hand, the positioning of the hydraulic cylinder, for example, when moving the roller R or changing its position by controlling the volume flow of the hydraulic cylinder. During position adjustment, pressure is required to overcome the transmission friction and provide flow in the hydraulic fluid pipeline by differential pressure. Position adjustment is also discussed if the desired distance, i.e. nip gap, is desired between the roller R and the winding cylinder C, for example, during winding.

With reference to Figure 2, a preferred embodiment of the control apparatus according to the invention will be described in more detail below. By way of example, the control circuit used for controlling the hydraulic cylinders, known per se, is used to control the roller carriages V. The carriages V are shown in simplified form as well as the power units 1 and 2. It will be apparent to those skilled in the art from the description that the control apparatus is to be applied, for example, to the starter winding apparatus.

• »10 105799

The control circuit is connected to a pressure source P known per se and to a return line T. The pressure source P provides a pressurized pressure medium, preferably hydraulic fluid, which is typically higher than the pressure of the control circuit of the invention. The pressure medium return flow 5 is directed to a return connection T, which is typically lower than the pressure of the control circuit to direct the return flow, for example, to a container. It will be understood that, with reference to Figures 2 and 3, the separate pressure sources P may be interconnected. Of course, the control circuit line can also be used as a pressure source P, which has a sufficient pressure level or volume flow and does not interfere with other operation of the circuit.

As is known for the synchronization of the cylinders 1 and 2, current control means 8 and, in addition, apparatus formed by means corresponding to the distribution means 3 are used. Then, as is known, the return flow 15 from the cylinders 1 and 2 is connected via the flow control means 8 to the return line T. Referring to FIG. 2, in the control circuit and 2a are coupled to a pressure source P20 via distribution means 3. The distributor members 3, preferably a structure comprising a distributor motor 3 or interconnected motors 3, divide the volume flow of the pressure medium from the pressure source P to the cylinders 1 (outlet 3a) and 2 (outlet 3b) by L1 and L2 and L3 and L4 to synchronously move arrows VS1 and VS2).

Typically, the split ratio is 1/1, whereby the components controlling the ends of the roller R in the branching lines 3 in the lines L1 and L2 have the same dimension and characteristics. The roller R can be moved either towards or away from the winding cylinder C (arrow VS1 and VS2). The direction is selected by means of the directional elements 4 connected to the line L1 and the directional means 30 5 connected to the line L2 to control the volume flow from the distributor motor 3 alternatively to the other cylindrical volumes 1b and 2b of the cylinders 1b and 2b. Through the directional means 4 and 5, preferably a 2-way 4-way valve, i.e. a 4/2-way valve, a flow of volume from the second tapering 35 cylindrical volumes of cylinder 1 and 2 is also simultaneously directed to the return line T. Cylinder volume 1 or 2 to which the volume flow is directed can be changed by means of the directional elements 4 and 5, whereby position control

»• I

According to the invention, H 105799 can be performed in both directions of motion (arrow VS1 and VS2). It is clear that the directional members 4 and 5 can operate independently of each other, but when operated in synchrony, their operation is typically simultaneous. For example, in pressure control, the direction of loading may change and, with the initial winding device moving from relief to loading, the loads on cylinders 11 and 12 may be different.

Line L7 and line L8 are connected to return line T and pressure source P by pressure control means 6 and 7. For example, the function of the pressure control member 6, preferably the pressure relief proportional valve 6 shown in Fig. 2, is to provide the desired pressure to the cylinder volume 1a or 1b of cylinder 1 to which it is connected by line L7, directional member 4 and L3 or L5. The pressure is applied to either sy-15 cylinder volume 1a by line L3 or cylinder volume 1b by line L5. By means of the pressure control means 6 and 7, during the position adjustment, a counter-pressure is obtained against the movement of the cylinder 1 and 2, whereby a controlled pressure difference also controls the volume flow over the throttles. By means of the pressure control means 6 and 7, an effective pressure is also provided during the pressure control in the cylinders 1 and 20 2 to form the load force previously described and further the nip load. For example, the pressure adjusting member 6 is connected during the position adjustment to the shrinking cylinder volume of the cylinder 1 and during the pressure adjustment to the cylinder volume of the cylinder 1 which causes the roller R to push against the winding cylinder C.

25

Current control means 8 are connected to line L9 from the pressure source P to the distribution means 3 for controlling the volume flow of the pressure medium from the pressure source P to the distribution means 3. The flow control means 8, preferably the directional proportional valve 8, controls the speed of movement 30 of the cylinders 1 and 2 during position adjustment. The direction of movement of the cylinders 1 and 2 (arrow VS1 and VS2) is then controlled by the directional elements 4 and 5. During pressure adjustment - ·. the current control means 8 close the line L9, whereby the volume flow does not pass through the distribution means 3 and the line L9 to the return line T connected to the flow control means 8. travel.

12 105799 These act as inputs to the valve which are proportional to a given volume flow or pressure. This means stepless adjustment of speed or force. The directional elements 4 and 5 are also preferably electrically controlled, but may also comprise a hydraulically actuated pre-steering stage which is electrically controlled in a manner known per se.

Lines L1 and L2 are connected by means of switching means 9, preferably a 4/2-way valve, to line L12, which is further connected to pressure source P by means of pressure control means 10. Lines L1 and L2 are arranged such that they are not interconnected when the switching means 9 closes the connection of these lines L1 and L2 to line L12. The switching elements 9 close the connection during the previously described position control and the connection is engaged during the pressure control. Thus, during positioning, the volume flow, preferably the hydraulic fluid acting as pressure medium 15, does not pass between the lines L1 and L2 by interruption, thereby disturbing the synchronization of the cylinders 1 and 2. In addition, the volume flow and the pressure level thereof coming from the distribution means 3 and further through the flow control means 8 during pressure control do not interfere with the pressure control of the cylinders 1 and 2. In this case, the distribution means 3 are also inoperative. The function of the Pai-20 regulating means 10, preferably the pressure-reducing proportional valve 10, shown in Fig. 2, is to provide a back pressure affecting line L12, further lines L1 and L2, and further affecting cylinder volumes of cylinders 1 and 2 during pressure control. This back pressure affects a cylinder volume different from the pressure control 25 itself. The pressure control pressure is provided by the pressure control means 6 and 7. through. By means of the directional elements 4 and 5, the cylinder volumes of the back pressure and the pressure control pressure can be interchanged, so that the pressure control can be carried out in both directions of movement according to the invention.

The operation of the control apparatus for controlling the pressure control and the position control in both directions of movement of the cylinders 1 and 2 will be further described below. In the position control, the direction of movement of the cylinders 1 and 2 (arrow VS1 and VS2) r is selected by the directional elements 4 and 5. The previously described roller driving nip open is possible with the desired position difference 35 of the rollers R with respect to the roller cylinder C. synchronizing the dividing means 3 to maintain the desired position difference at both ends of the roller R 105799. In this case, the switching elements 9 also close the connection of lines L10 and L11 to line L12. The substantially constant back pressure used during position adjustment is provided by the pressure adjusting members 6 and 7. The back pressure of the piston 5 of the cylinder 1 is 80 mm on the piston side, i.e. 50 bar, and the piston rod side 1 or cylinder 1b. In this case, the movement of the piston of the cylinder 1 is about 3 mm per second at a flow rate of 1 dm3 per minute.

During pressure control, the substantially opposite back pressure is applied to the opposite cylinder volume of cylinder 1 and 2, and the pressure control elements 6 and 7 serve to control the load pressure. In one step, in cylinder 1, during the position adjustment, the volume flow is supplied to the cylinder volume 1a and at the same time the back pressure is supplied to the cylinder-15 blade volume 1b, during pressure control the loading pressure is applied to the cylinder volume 1a and simultaneously. The back pressure used in the pressure control, i.e. the winding, during the adjustment of the line load of the roller, which is now controlled by the pressure control elements 10, is controlled by the switching elements 9. In this case, the switches 20 connect the lines L10 and L11 to the line L12. The pressure control may also be asymmetric since the cylinders 1 and 2 each have their own pressure control elements 6 and 7 in the preferred embodiment of the invention.

The control apparatus according to the invention can also be applied in connection with the cylinders of the starter roller, with reference to FIG. 2, the cylinders 11 and 12 of FIG. 1 correspond to the cylinders 1 and 2 during initial rotation (arrow VS3). var-30 blue for pressure control. Thus, in a cylinder volume acting as a relief chamber for the cylinders 11 and 12, the back pressure is initially greater than the pressure in the load chamber. As the swinging motion of the initial winding device progresses, the situation reverses until the pressure of the cylinder volumes of the cylinder 11 and 12 is the same as a result of the adjustment. Subsequently, the members corresponding to the directional members 4 and 5 change the effective back pressure to affect the second cylinder volume and the load pressure coupled by the members corresponding to the pressure control members 6 and 7 105799 14 to the opposite cylinder volume. With equal pressures, sudden pressure drops or elevations that interfere with the control of the rolling event are avoided. By means of the cylinders 1 and 2, the carriages V can be brought into contact with the winding shaft T2 and the initial winding apparatus lowers the winding shaft T2, on which the paper web W has begun to accumulate, onto the winding rails K2. Thereafter, the operation will continue as described above. It will be appreciated that the control apparatus can also be applied to pressure control and position control of other cylinders arranged in pairs to operate on the basis of the above description.

Referring to Figure 2, the positions of the cylinders 1 and 2 are determined by known position sensors 13 and 14, preferably linear potentiometers 13 and 14. The position sensors are shown in the figure as a simplified concept view of the principle, and it is clear that other sensors based on electrical, inductive, capacitive, photoelectric or mechanical action can also be used to determine the position of the cylinders, which may also be based on rotary motion. The signal from the position of the cylinders 1 and 2 is fed to a control unit 15 which provides control of the various elements of the control apparatus and their mutual operating sequence, for example by means of electrical control signals. The operation of the control unit 15 can be influenced, for example, by the user. The control unit 15 can also be supplied with signals from the elements regarding their state and position, as well as system pressures and state currents in a manner known per se.

Each control member may consist of a plurality of valves, e.g., the pressure control means 10 may alternatively comprise a check valve or a pressure relief valve to achieve the desired function. Preferably, however, the oh-30 distribution member is as simple as possible. It will be appreciated that the valve functions of the members described above and shown in Figure 2 may be implemented, for example, for drilling of a block made of metal material: · by means of cartridge valves disposed, which can additionally be combined in a minimum space using standard components. This is possible in particular for the position difference control circuit which will be described later. In addition, it is clear that the above functions of the various elements of i 1K 105799 may be accomplished within the scope of the claims by means of the same valve construction, but for purposes of clarity these functions are illustrated by means of individual valves. Further, it is possible that, for example, the pressure control means 10 comprise 5 separate members for each cylinder 1 and 2, but preferably the pressure control means 10 is a single pressure reduction proportional valve whose connection to the lines L1 and L2 is closed by the genital means 9. However, the functions of the genital organs 9 may be combined with those of the directional members 4 and 5, in particular when the operation of the pressure control members 10 is divided into different valves 10.

Figure 3 shows a position difference control apparatus S, i.e. a position difference control circuit S, in accordance with a preferred embodiment, which is connected to line L2 with reference to Figure 2. Alternatively, circuit S can be connected to line L1.

Adjustment of the position difference is important especially when the roller roller shaft T1 or T2 is moved towards the roller cylinder C, with reference to Fig. 2, the movement directions of the cylinders 1 and 2 are VS6 and VS7, and connected so that their total length increases The position difference control circuit S is connected to the control line L2 by means of lin-20 and L15, which is further connected to the pressure source P by the pressure control means 16 and the return line T by the pressure control means 17. The pressure regulating member 16, preferably the pressure relief valve 16, shown in a pre-controlled manner, is connected to the line L13, to which the closing members 19 are also connected. The closing members 19, preferably a cartridge type 2/2 directional valve, close and open the line L13. The pressure regulating member 17, preferably the pressure limiting valve 17, is connected to the line L14, to which also the closing members 20 are connected. The closing members 20, preferably a cartridge type 2/2-directional valve, close and open the L14 line. In addition, lines L13 and L14 are connected to each other.

30

To control the volume flow through a differential pressure, a throttling member - · · · 18, preferably a throttle 18, is provided, with a throttle orifice diameter of 0.6: 1 * mm providing a flow of about 0.6 dm 3 per minute over the choke 18. With low flow rates, the control is hel-35 more bouncy and more stable and can be easily influenced by the pressure settings of the ie 105799 pressure regulating members 16 and 17 and further by the differential pressure acting over the choke 18. The flow can also be influenced by closing and opening the closing members 19 and 20 which are closed during pressure adjustment of the cylinder 2. In this case, the pressures 16 and 17 cannot be influenced by the pressures prevailing in the control apparatus described earlier during the pressure control. In addition, during position adjustment, the pressure control means 16 and 17 can only be actuated by means of the genital means 19 and 20 when a position difference to be corrected is detected between the cylinders 1 and 2. The position 10 of the cylinders 1 and 2 is monitored by means of position sensors 13 and 14, for example. The position of the stationary winding cylinder C relative to the position sensors 13 and 14 is known whereby the information they provide to the control unit 15 can control the operation of the position difference control circuit, for example by electrical signals acting on the control magnets of the valve bodies and further by their forces. The valves can also be pre-controlled by pressure medium.

The operation of the position difference control circuit S will now be described and, in the description, it is coupled to cylinder 2 in a line L2. During the position adjustment 20, the back pressure of the cylinders 1 and 2 is adjusted by the pressure control means 6 and 7, and the flow control means 8 feeds volume flow to the cylinders 1 and 2. The direction of movement of the cylinders 1 and 2 is also determines the roller carriage instead of V, the cylinders are synchronized as follows. If cylinder 2 is lagging behind cylinder 1, additional volume flow is supplied to cylinder 2 via circuit S When, for example, the piston side, as well as line L2, is pressurized to 30 bar, the pressure adjusting member 16 is adjusted to 40 bar. differential pressure and flow direction 30 cylinders towards 2 (arrow VS4). The volume flow is then directed to the piston side, i.e. to the cylinder volume 2a. At the same time, the closing means 19 must be in a position which allows the hydraulic fluid to flow from L13 to L15 and further to L2. At the same time, the closing means 20 must also be in a position which prevents the flow of hydraulic fluid in line 35 L15 and line 13 to line L14, thereby also preventing the action of the pressure regulating means 17.

17 105799

If the cylinder 2 has advanced further than the cylinder 1, i.e., the cylinder 1 is left behind, then the circuit is used to direct the volume flow away from line L2. The cylinder 2 is then slowed down by this decrease in volume flow. For example, when the pressure 5 on the piston side, and thus also on line L2, is adjusted to 30 bar, the pressure regulating member 17 is adjusted to 20 bar, with a 10 bar differential pressure across the throttle member 18 and flow direction away from cylinder 2 (arrow VS5). At the same time, the genitalia 20 must be in a position that allows the hydraulic fluid to flow in a line L15 to a line L14.

10

In the operation of the position difference control circuit S, it should be noted that the cylinders 1 and 2 can be driven synchronously if desired, while maintaining their desired position difference. Advantageously, this is taken care of by a control unit 15 which controls the operation of the valves of the various means and ensures that their operation is synchronized.

15

Figure 4 shows another preferred embodiment of the position difference control circuit S. The position difference control circuit S comprises current control means 23, preferably a directional proportional valve 23, through which line L1 and / or line L2 is connected to a pressure source P and return line T via line L16 and / or 20 via line L17. In addition, lineage 21 is connected to line L16 and lineage 22 is connected to line L17. The genitalia are preferably cartridge type 2/2 directional valves. By means of the genitals 21 and 22 it is chosen whether the two lines L1, L2 are affected or only one of them.

Referring still to Figure 4, when the genital 21 is active, i.e., open, the flow control means 23 can be used to deflect a volume flow from line L1 to the return line T, or T, or to conduct a volume flow to line L2 from a pressure source P. - The valve acting as a flow control member 23 may also be provided with a closed central position where no flow occurs in lines · ·: L16 and L17. While the genitals 21 and 22 are simultaneously active, a flow of space 35 can be discharged from another line, for example L1, and a flow of flow into another line, for example L2. In this case, especially in the case of a large difference in position, 105799 18 will shorten the adjustment and repair time compared to the situation where only one of the L1 or L2 lines is affected.

It is clear from the foregoing that the operation of the genitalia 21 and 22 can also be accomplished by means of a single multidirectional directional valve. It is further understood that one of the genera 21, 22 and / or the line L16, L17 of one of the lines L1, L2 may be completely absent. In this context, it should also be noted that when the position difference control circuit S provides sufficient control of the volume flow of the lines L1 and L2, each of the lines L1 and L2 can also be independently supplied with two separate flow control means 8, e.g. . When the position difference control circuit S provides control of the volume flow supplied to the actuators 1 and 2 to control the position difference, the distribution means 3 can also be greatly simplified, whereby only branching of line L9 to lines L1 and L2 may be involved. The position difference control devices shown in Figures 3 and 4 can be used in conjunction with the control device shown in Figure 2.

It will be apparent to one skilled in the art that the invention is not limited to the above preferred embodiment, but may vary within the scope of the claims. Furthermore, it will be apparent to one skilled in the art that the cylinders 1 and 2 described above can be used in a wide variety of roller applications. Here, the transfer and force action of the cylinders at different ends of the winding shaft 25 can be transmitted, for example, by means of various transmission mechanisms such as pivoting means, carriages and guides as previously described. In this case, the Motion or Movement Track of the said cylinders is typically different from, for example, the motion or the path of the scroll axis.

30 • i

Claims (14)

A control device at a wheelchair of a paper web, comprising: 5 - at least one first actuator (1, 11) and a second actuator (2, 12) for controlling the position of a rolling shaft (T1, T2) by means of of position adjustment and / or to adjust the load (F1, F2) between the rolling shaft (T1, T2) and a roll-up roller (C) by means of pressure control, 10. current control means (8) to control the volume flow of a pressure medium to be measured from a pressure source (P) to the actuators (1, 2, 11, 12) at least during the position adjustment, - a first line (L1, L3, L5) for feeding the pressure medium from the pressure regulating means (8) to the first actuator - the actuator (1, 11) and a second line (L2, L4, L6) for feeding the pressure medium supplied from the current control means (8) to the second actuator (2,12), characterized in that the control device further comprises: pressure control means (10) to control the pressure of the pressure medium to be measured from the pressure source (P) to the first cylinder volumes (1a, 2a) of the actuator (1, 2, 11, 12) at least during the pressure control, - other pressure control means (6) to regulating the pressure of the pressure medium to be measured from the pressure source (P) to the second cylinder volume (1b) of the first actuator (1, 11) during pressure control and position adjustment; P) to the second cylinder volume (2b) of the second actuator (2) during pressure control and position adjustment, - first directing means (4) for coupling the pressure regulated by the first pressure regulating means (10) or alternatively to the first actuator (1, 11) ) second cylinder volume (1b) and to simultaneously copy the pressure regulated by the second pressure regulating means (6) or alternatively to the first actuator ( 1, 11) first cylinder volume (1a), - second directing means (5) for coupling the pressure regulated by the first pressure regulating means (10) or alternatively to the second cylinder volume (2b) of the second actuator (2, 12) and for simultaneously copy the pressure regulated by the third pressure regulating means (7) or alternatively to the first cylinder volume (2a) of the second actuator (2,12), and - that the first line (L1, L3, L5) has through a third line 10 (L10, L12 ) contact also with the first pressure control means (10), and - that the second line (L2, L4, L6) has contact with the first pressure control means (10) through a fourth line (L11, L12). 15 Control device according to claim 1, characterized in that the control device comprises additional coupling means (9) for closing the mutual contact between the first line (L1, L3, L5) and the second line (L2, L4, L6). and their contact to the first pressure regulating means 20 (10) at least during the position adjustment. Control device according to claim 1, characterized in that the first pressure regulating means (10), the second pressure regulating means (6) and the third pressure regulating means (7) comprise a proportional pressure reducing valve which is T contact with the pressure source (P) and the return line (T) to control the pressure in the line (L1-L8, L10-L12) which is in contact with the cylinder volume (1a, 1b, 2a, 2b) of the actuator (i, 2,11,12). Control device according to any one of claims 1 to 3, characterized in that the flow control means (8) are also arranged to stop the volume flow of the pressure medium to be measured from the pressure source (P) to distribution means (3) at least during the pressure control. . Control device according to any of claims 1-4, characterized in that the control device comprises distributing means (3) for distributing the pressure medium coming from the current control means (8) in a selected relation to a first leading to the first actuator (1, 11). line 26 105799 (L1, L3, L5) and to a second line leading to the second actuator (2, 12) (L2, L4, L6). A position difference control device in conjunction with a control device 5 at a wheelchair of a paper web, the control device comprising: - at least one first actuator (1, 11) and a second actuator (2,12) for controlling the position of an exchange shaft σΐ.Τ2) Current control means (8) for controlling the volume flow of a pressure medium to be measured from a pressure source (P) to the actuators (1,2,11,12), - a first line (L1, L3, L5) for feeding it from the pressure regulating means (8) fed the pressure medium to the first actuator (1, 11) and a second line (L2, L4, L6) to feed the pressure medium from the current regulating means (8) to the second actuator (2.12) , characterized in that the 20. position difference control device (S) comprises at least means (18, 17, 20, 21-23) for conducting pressure medium from a first line (L1, L3, L5), from a second line (L2, L4, L6) or out of both these lines (L1 – L6), and means (18, 16, 19, 21-23) for feeding print media to the first line (L1, L3, L5), the second line (L2, L4, L6) or both of these lines (L1 -: L6), and - the means (18, 17, 20, 21-23) are arranged to control and maintain the reciprocal position of the actuators (1,2,11,12). 30 The position difference control device (S) according to claim 6, characterized in that the device (S) further comprises: - throttling means (18) in contact with the first line (L1, L3, L5) or the second line (L2, L4, L6) ) to control the volume flow of a pressure medium coming from or to be measured at the line (L1 – L6); • in first pressure regulating means (16) to control the pressure of the pressure medium to be measured from a pressure source (P) through the throttling means ( 18) to the line (L1-L6), * - second pressure regulating means (17) for controlling the pressure of the pressure medium coming from the line (L1-L6) through throttling means (18), and - first blocking means (20) for blocking the contact (L13, L15) between the first pressure regulating means (16) and the second pressure regulating means (17) and for blocking the contact 10 (L14, L15) between the throttling means (18) and the second pressure regulating means (17). The position difference control device (S) according to claim 6 or 7, characterized in that it comprises further second blocking means (19) for blocking the contact (L13, L15) between the first pressure regulating means (16) and the throttling means (18). The position difference control device (S) according to any of claims 6 to 8, characterized in that the first pressure control means (16) comprise a proportional pressure reducing valve which contacts the pressure source (P) and the return line (T) to control the pressure. in the position difference control device (S), and that the other pressure control means (17) comprise a pressure reducing valve which is in contact with the return line (T) to control the pressure in the position difference control device (S). 25 A position difference control device (S) according to any of claims 6 to 9, characterized in that the first locking means (20) and the second locking means (19) comprise separate cartridge-type control valves, or the functions of the locking means (19, 20) are integrated in the same control valve design. 11. Position difference control device (S) according to any of claims 6 to 10, characterized in that the pressure regulated by the first pressure regulating means (16) is higher than the pressure of the line (L1 - L6), and that by the second pressure regulating means (17) the regulated pressure is lower than the pressure in the line (L1 - L6). m 28 105799 The position difference control device (S) according to any of claims 6 to 11, characterized in that its function is arranged to be controlled by means of a control unit (15), which control unit (15) is in contact with the actuator (1,2). 11, 12) position sensors (13, 14) for determining the position of the actuators (1, 2,11,12). The position difference control device (S) according to claim 6, characterized in that said means (18,17, 20, 21-23) comprise at least: 10. current control means (23) in contact with the first line (L1, L3, L5 ), the second line (L2, L4, L6) or both of these lines (L1 – L6), to control the volume flow of the pressure medium coming from or to be measured at the line (L1—6), and 15. blocking means (21, 22) to block the contact (L16, L17) to the first line (L1, L3, L5), the second line (L2, L4, L6) or both of these lines (L1 - L6). The position difference control device (S) according to claim 13, characterized in that the current control means (23) comprise a proportional control valve which is in contact with the pressure source (P) and the return line (T). in