Squeezing roller having an internal drive for a cold rolling system

Abstract

The invention relates to a device (1) and a method for removing cooling lubricant during rolling of a rolled strip (100) in a cold rolling system having at least one roll stand. The device (1) comprises a squeezing roller (3) which is arranged between a first and a second roll rack (21, 21') of the roll stand. The squeezing roller (3) is mounted in a holder (2) to rotate about a rotational axis (R) and comprises a roller casing (15) and an internal electric rotary drive (5) which is designed as an internal rotor. By means of a positioning device (4), the squeezing roller (3) can be positioned against the rolled strip (100). An open- and closed-loop control device (30) actuates the rotary drive (5) synchronously to a current speed (v) of the rolled strip (100) behind the roll stand such that the roller casing (15) rolls on a surface (101) of the rolled strip (100) without slip and guides cooling lubricant from the rolled strip (100) in a lateral direction.

Description

[0001]202200161 1 Description Squeeze roll with internal drive for a cold rolling mill The invention relates to a device and a method for removing cooling lubricant during the rolling of a rolled strip in a cold rolling mill with at least one rolling stand. A cold rolling mill for rolling flat rolled stock - for example a tandem rolling mill - comprises at least one, preferably several rolling stands, through which the flat rolled stock passes successively. The cold rolling mill can also be a reversing rolling mill, which comprises one or more rolling stands through which the rolled strip passes in alternating directions. The flat rolled stock is usually a rolled strip made of steel. Each rolling stand of the cold rolling mill comprises at least two work rolls, which together form a roll gap through which the rolled strip is guided. For introducing ('threading') the initial section of a rolled strip (also known asWhen the strip is fed into the rolling stand (referred to as the 'strip head') the rolling stand is 'opened', i.e. the work rolls in the rolling stand are moved apart so far that the roll gap is greater than the strip thickness of the rolled strip to be threaded in. After threading has been completed, the rolling stand is 'closed' again, i.e. the roll gap is reduced so far that the work rolls contact the threaded strip. In addition, a tensile force (the so-called 'strip tension') is built up on the rolled strip behind the rolling stand, so that the rolled strip runs through the rolling stand along a so-called strip travel line during the rolling process. The strip travel line is essentially horizontally oriented immediately in front of and behind the roll gap of a rolling stand. During rolling in the rolling stand, the thickness of the rolled strip is reduced by the action of the work rolls to a predetermined exit thickness behind the 202200161 2 relevant rolling stand, whereby this exit thickness corresponds to the entry thickness of a possibly subsequentarranged rolling stand of the cold rolling mill. The area between two consecutively arranged rolling stands is also referred to as the inter-stand area. Furthermore, as the rolled strip passes through a rolling stand, a cooling lubricant is usually applied to the work rolls of the rolling stand and / or to the rolled strip in order to support the thickness reduction process of the rolled strip and to dissipate the resulting forming heat. The cooling lubricant is usually a lubricating emulsion, for example water with a proportion of up to 5% pure lubricant; alternatively, however, pure lubricant, for example pure rolling oil, can also be used. Below the work rolls, there is usually a collecting device for the applied cooling lubricant, which is subsequently collected and recycled. In cold rolling mills, so-called squeeze rolls are each arranged directly behind aA squeezing roller is used in a rolling stand, whereby a squeezing roller is positioned against the top side of the rolled strip with the aid of an associated adjustment mechanism, and guides or redirects the strip during the rolling process into a specific strip path through the rolling stand. This retains the cooling lubricant used during rolling, which accumulates on the top side of the rolled strip, preventing it from spreading into the intermediate stand area or entering the subsequent rolling stand. This is necessary because measuring instruments may be located in the intermediate stand area that would be disturbed without the removal of the cooling lubricant, or because visual inspection of the rolled strip is required. It may also be necessary to separate the different cooling and lubricant systems assigned to individual rolling stands. When the squeezing roller is positioned against the rolled strip, its lowest point is usually above a collecting device.202200161 3, so that cooling lubricant on the rolled strip is removed from the rolled strip by the squeeze roll in a direction transverse to the strip travel line and collected by the collecting device. Away from the immediate vicinity of the roll gap of a rolling stand - i.e. in the area from approximately 0.5 m in front of and behind the rolling stand in the inter-stand area - the strip travel line of a rolled strip does not necessarily run in a straight line, but is influenced, for example, by tension measuring or flatness measuring rolls. Furthermore, the strip travel line can be adjusted depending on the properties of the rolled strip in question or its production parameters with the help of additional rolls. For example, rolled strips of a certain product class must be rolled in a rolling stand with lubricant applied on the outlet side, which requires the adjustment of a corresponding squeeze roll in order to ensure the introduction of lubricant into thedownstream intermediate stand area. In contrast, the production of rolled strips of other product classes may require no or no significant application of lubricant, and therefore a squeeze roll does not need to be positioned against the rolled strip during rolling of such strips. Squeeze rolls are typically designed to be smooth-running – for example, in the form of a hollow cylinder with a low moment of inertia – and are driven by friction from the rolled strip, so that ideally no relative movement (slippage) occurs between the squeeze roll and the driving rolled strip. In practice, however, slippage frequently occurs with such passively driven squeeze rolls, especially when large quantities of emulsion or emulsions with a high lubricant content are used. In particular, slipping squeeze rolls behind the first rolling stands through which a rolled strip passes can cause unnoticed scratches and strip damage.202200161 4 which, due to the over-rolling in the subsequent rolling stands, are only discovered in a treatment plant downstream of the cold rolling mill. In such cases, large quantities of scrap material are produced without the possibility of early detection and prevention. Cooling lubricant remaining on the surface of the rolled strip reduces the friction between the squeezing roll and the rolled strip, thereby reducing the torque transmitted from the rolled strip to the squeezing roll. Under certain operating conditions (depending on the strip thickness, strip tension, and strip speed), this leads to slippage between the squeezing roll and the rolled strip, which in turn can cause damage to the strip surface in the form of slipping scratches. Squeezing rolls generally have neither their own drive nor is their rotational movement monitored during the rolling of a rolled strip. The problems described canTherefore, under these circumstances, they can only be identified in the form of quality defects in the final product and cannot be prevented early, as there are no reliable detection mechanisms or adjustment options to prevent non-synchronous behavior between the squeegee roll and the rolled strip. While an inspection of the strip surface in combination with speed monitoring of the squeegee roll can identify those operating conditions in which slippage occurs, it cannot be prevented. While a reduction in the moment of inertia of the squeegee roll leads to improved entrainment of the squeegee roll by the rolled strip, slippage cannot be ruled out for all operating conditions, especially not with a high lubricant content in the cooling lubricant. Even if the surface of the squeegee roll is modified (for example, by increasing its roughness), the squeegee roll cannot be permanently anduse reliably. 202200161 5 Another way to counteract the aforementioned slippage is to increase the contact pressure with which a squeeze roller is applied to a rolled strip: for example, US 4,323,122 A discloses rollers applied in pairs to a rolled strip for removing lubricant from a rolled strip, wherein the lower of the two rollers represents a counter-roller by means of which a corresponding contact pressure for the upper squeeze roller can be achieved. The counter-roller can be subjected to a pressurized liquid in order to adapt its surface contour, so that a uniform contact pressure is achieved along the contact line between the two rollers and the rolled strip. The disadvantages of this are, on the one hand, the increased construction effort for the lower counter-roller, and on the other hand, a separate control process is necessary to set the appropriate shape of the counter-roller to suit the respective production conditions.Alternatively, cooling lubricant remaining on a rolled strip can also be removed by blowing it off. In this context, EP 0513 632 A1 discloses a slot jet nozzle that is pressurized with a gas and whose outlet opening is oriented transversely to the strip travel direction. The direction of the emitted gas jet is directed at an inclination of 45° to 90° against the strip travel direction, and the exit velocity of the gas jet is in a range of 0.3 to 2 Mach. The disadvantage of this solution is the high energy requirement to achieve a gas jet with such a high exit velocity. In addition, there is a risk of contamination of the surroundings of the rolling mill by the cooling lubricant if it forms a liquid level of several millimeters on the rolled strip and is blown off with a high-pressure gas jet. Another measure to prevent slippagebetween a squeeze roller and the rolled strip can consist of a drive for the squeeze roller, so that it is not set in rotation by the rolled strip, or not exclusively by friction. However, a drive arranged outside the squeeze roller would not be feasible due to lack of space in a rolling stand, because a squeeze roller is usually arranged - viewed along its axial direction - between the columns of the rolling stand. DE 102017 214 412 A1 discloses an internally arranged electric motor with a rotor and a stator for a roller element for strip-shaped rolled material, wherein the rotor is connected directly to the roller element without the interposition of a clutch or gear, and the stator is connected directly to a frame on which the roller element is rotatably mounted. The rotary drive is designed as a so-called 'external rotor', in which a rotor rotates around a fixed electricStator rotates. In contrast, in an electric rotary drive referred to as an 'internal rotor', the rotor rotates – viewed in the radial direction – within a spatially stationary stator. A disadvantage of the drive disclosed in DE 102017 214 412 A1 is the fact that, for reasons of space, strong permanent magnets must be used for the stator in an electric rotary drive designed as an external rotor. The permanent magnets are arranged on the inside of the outer surface of the roller element and are thus in close proximity to its surface. Since, as a rule (among other things, for cost reasons), no magnetically shielding material is used for squeeze-out rollers, the magnetic fields of the permanent magnets penetrate the surface of the squeeze-out roller without attenuation and can lead to the adhesion of magnetic particles to it, so that strip-like patterns or impressions are formed on the rolled metal strip during rolling.The invention is therefore based on the object of overcoming the disadvantages of the solutions known from the prior art for removing cooling lubricant from a rolled strip and of providing a design solution that prevents the entry of cooling lubricant into the subsequent rolling stand during cold rolling of a rolled strip - even when the level is several centimeters on the rolled strip - and reliably prevents the occurrence of slippage between a squeeze-off roll and the rolled strip. A further aspect of the invention is that the proposed solution can be implemented in a simple manner and can also be used in confined spaces in the rolling stand area. This object is achieved according to the invention by a device according to claim 1. Preferred embodiments of the device according to the invention are the subject of the dependent device claims. A device according to the invention is used forThe device according to the invention comprises a squeezing roller which can be arranged between the first and second roll stands of the roll stand. The squeezing roller has a roller shell and an internal electric rotary drive. The rotary drive is fixedly (i.e., mechanically rigidly) connected to the roller shell, has a stator and a rotor, and is designed as an internal rotor. An internally arranged rotary drive – i.e., in the interior of the squeezing roller – advantageously enables a small structural space requirement for the squeezing roller between the respective roll stands of the roll stand. The rotary drive can be designed such that only the fixedThe stator is supplied with electrical drive energy, while the rotor is set in rotation due to the electromagnetic currents induced by the stator. This advantageously avoids the need for wear-prone sliding contacts in the rotary drive. Furthermore, an internal rotary drive enables a compact and maintenance-friendly design because, in the event of damage, the squeeze roller, including the rotary drive, can be replaced as a whole; the separate replacement of the drive module (as in the case of a squeeze roller with an externally mounted drive) or a coupling between the drive and squeeze roller, as well as the alignment of the latter, is eliminated. Furthermore, a rotary drive designed as an internal rotor offers the advantage that any permanent magnets of the internal rotor are arranged at a sufficient distance from the surface of the squeeze roller, and that magnetically shielding material can be used for the stator if necessary.This advantageously prevents any disruptive magnetic field penetration of the electric rotary drive to the surface of the squeeze roller. The device according to the invention further comprises a holder in which the squeeze roller is rotatably mounted about a rotation axis R, wherein the rotation axis R runs essentially transversely to a strip travel line. In addition, the device according to the invention comprises an adjusting device for adjusting the squeeze roller against the rolled strip and a control and regulating device for controlling the rotary drive and the adjusting device. In this context, 'control' is understood to mean both the output of control signals or control commands to the respective unit without feedback (pre-control) and the repeated issuing of the same in conjunction with a control loop. Furthermore, the control and regulating device knows the current speed v of the rolled strip behind the respective rolling stand.This is the instantaneous value of the strip speed of the rolled strip along a strip travel line behind the rolling stand and relative to the rolling stand. This speed can be measured, for example, using a tension measuring roll or a contactless speed measuring device (e.g., based on the laser Doppler 202200161 9 principle) and transmitted to the control and regulation system. The instantaneous speed v of the rolled strip behind the rolling stand exactly matches the rotational speed of the surfaces of its work rolls only at the so-called 'neutral point' within the roll gap. With respect to the rotating work roll surfaces, the rolled strip entering the rolling stand lags, and the rolled strip leaving the rolling stand leads. The speeds of the rolled strip before and behind the rolling stand are related to each other via the continuity conditionassuming constant volume of the rolled stock during the rolling process (see, for example, equation (3.9) on page 112 in H. Hoffmann, R. Neugebauer and G. Spur (eds.), "Handbuch Umformen", 2nd edition, Carl Hanser Verlag, 2012, ISBN 978-3-446-42778-5). Due to the aforementioned lag and lead of the rolled strip relative to the rotating work rolls, the control and regulating device is designed according to the invention to control the rotary drive of the squeeze-out roll synchronously with the current speed of the rolled strip behind the rolling stand. This means that the control and regulation device, based on the current rolling strip speed v behind the rolling stand, specifies or controls an angular speed for the rotary drive of the squeeze roll (which is identical to the angular speed ^ of the squeeze roll itself due to the rigid connection between the roll drive and the roll shell) in such a way (ie controls or regulates in the above-mentioned sense) that theThe roller shell rolls on the rolled strip with essentially no slippage. 'Essentially no slippage' in this context means that a relative speed between the rolled strip surface and the surface of the roller shell in the range of 0-1% of the rolled strip speed v behind the rolling stand can occur or is tolerated by the control and regulation device. 202200161 10 The aforementioned design of the control and regulation device enables particularly precise speed control of the squeeze-out roll and, as a result, particularly reliable prevention of slipping scratches, regardless of the current friction conditions between the squeeze-out roll and the rolled strip - and thus also when using cooling lubricants with a particularly high lubricant content of more than 10%. This advantageously prevents the unintentional production of material that would otherwise have to be scrapped at a later date. In addition, theThe energy requirement of such a synchronously driven squeeze roller, which in continuous operation, for example, amounts to a power of 0.5 to 1 kW, is significantly lower than, for example, that of a blow-off device for emulsion residues. Furthermore, the adjusting device is designed to move or pivot the holder with the squeeze roller between a starting position A and an end position E. The starting position A and the end position E are arranged with respect to the rolling stand and the diameter of the squeeze roller in such a way that during the rolling of a rolled strip in the rolling stand (i.e., with the rolling stand closed), the roller shell of the squeeze roller in the starting position A does not touch the rolled strip, so that the rolled strip passes through the rolling stand in a first strip travel line B1. In contrast, the roller shell of the squeeze roller in the end position E contacts the rolled strip on its upper side during rolling and deflects it in the processbottom into a second strip travel line B2, whereby cooling lubricant located on the rolled strip is drained laterally from the top side of the rolled strip. The squeeze roller is moved between the starting position A and the end position E, normal to a strip travel line of the rolled strip. The roller shell extends transversely beyond the rolled strip and has, for example, a cylindrical shape and a length of up to two meters along the rotation axis R of the squeeze roller. In a preferred embodiment of the invention, the holder is designed in two pieces, consisting of a first and a second holder part. 'Two-piece' in this context means that the first and second holder parts represent two separate sections that are not directly connected to one another, for example by screwing, welding, or any other rigid connection. The squeeze roller also has a first and asecond roller journal, wherein the first roller journal is rigidly connected to the first support part and the second roller journal is rigidly connected to the second support part. The rotor is rotatably mounted within the stator relative to the latter. Furthermore, the rotor is firmly connected to a rigid shaft, wherein the rigid shaft in turn is firmly connected to the roller shell via a flexible drive shaft. In the described two-piece design of the holder, the first and second support parts are indirectly connected to one another via the squeeze roller. The rotary movement of the rotor arranged inside the squeeze roller is mechanically transmitted directly to the roller shell via the flexible shaft. This design allows the entire electrical rotary drive to be arranged inside the squeeze roller. In concrete terms, this means that both the entire rotor and the entire stator - especially with respect to the longitudinal axis of theSqueeze roller - are arranged in the interior of the squeeze roller, so that only electrical connection cables for the electric rotary drive lead out of the squeeze roller. This advantageously allows the use of a squeeze roller according to the invention as a retrofit solution or replacement for a squeeze roller without a rotary drive, since the outer dimensions of the - essentially cylindrical - squeeze roller can remain unchanged. Furthermore, an electric rotary drive located entirely in the interior of the squeeze roller advantageously minimizes the space required by the squeeze roller in the axial direction when installed between the two rolling stands of the rolling stand. The flexible drive shaft also enables the compensation of small deviations in the mechanical alignment between the first and second mounting parts (alignment errors). In a preferred embodiment of the device according to the invention, the firstThe roller journal is firmly connected to a cooling jacket for the stator, whereby the cooling jacket surrounds the stator and is firmly connected to it. The heat generated by the electric rotary drive can be dissipated via the cooling jacket, for example by passing coolant through the cooling jacket. The squeeze roller preferably has a diameter of 300-500 mm. This allows emulsion residues to be reliably removed from the rolled strip even when applying larger quantities of emulsion of up to 2000 liters per minute. The first roller journal and the cooling jacket surrounding the stator preferably have at least one cooling channel for the passage of a cooling medium. The cooling medium can be water, for example. Since the first roller journal is rigidly connected to the first mounting part, no rotary feedthrough for introducing a cooling medium into the first roller journal is necessary, so that a mechanicallyRobust active cooling for the electric rotary drive of the squeeze roller is enabled. In a further preferred embodiment of the device according to the invention, the first and / or the second roller journal have a passage for introducing a gaseous medium under overpressure into the interior of the squeeze roller. 'Overpressure' here refers to a pressure level that is higher than the ambient pressure of the squeeze roller. Since the first and second roller journals are rigidly connected to the first and second mounting parts, respectively, the generation of overpressure inside the squeeze roller is again made possible with little effort by means of a simple and robust mechanical passage. Gaseous media under overpressure with a very low water content - such as dried air, nitrogen, or argon - can be provided cost-effectively and protect the internal electric rotary drive of theSqueeze roller against corrosion and the penetration of moisture or dust and abrasion particles. The introduction of a gaseous medium with a higher thermal conductivity than air - such as helium - also advantageously results in a correspondingly higher heat dissipation from the electric rotary drive to the roller shell or to the environment. In a further preferred embodiment of the device according to the invention, the first and second mounting parts extend along the rotational axis R of the squeeze roller over 50-70 mm and have chamfers, for example, with an angle ^ of 1-2°, on a respective contact surface to the adjusting device. At the respective contact surfaces, the first and second mounting parts are connected to the adjusting device via detachable fastening means, for example via screw connections. The adjusting device comprises, for example, two hydraulic actuators, each of whichassigned to and connected to it. To move the squeeze roller to the starting position A or to the end position E, the two hydraulic actuators must be moved synchronously, whereby irregularities in the movement of the actuators cannot be completely avoided. Since the first and second support parts are essentially mechanically rigidly connected to each other via the squeeze roller, tilting moments can occur on the support parts. The chamfers therefore allow a slight tilting of the support parts relative to the adjusting device or its actuators and thus a dissipation of the induced tilting moments. In addition, the dimensions of the support parts allow optimal utilization of the available space between the roll stands, so that the roll shell has a large extension in relation to the width of the rolled strip and can reliably remove cooling lubricant even from rolled strips with a maximum possible width.in relation to the rolling stand. In a further preferred embodiment of the device according to the invention, the control and regulating device is configured to pre-control an angular velocity ^ of the squeeze-out roll based on a torque characteristic ^ of the electric rotary drive. In a cold rolling mill, for example, different rolled strips are joined (welded) to one another and successively rolled as a so-called 'endless strip' by the individual rolling stands of the cold rolling mill. The individual rolled strips generally have different properties - such as deformation resistance or strip thickness - which make it necessary, when changing successive rolled strips, to change the roll gap of a rolling stand on which the device according to the invention is used and / or the speed at which the different rolled strips are rolled. In order to ensure that the transition sections on the respective rolled stripsTo keep the time required for the squeezing roll to be as short as possible, such changes must be made relatively quickly, e.g., within 20 to 50 meters relative to the rolled strip length. Pre-control of the speed of the squeezing roll based on its torque characteristic ^ ^ advantageously enables rapid adjustment of the rotational speed of the squeezing roll, whereas with purely speed-based control of the squeezing roll, its speed would lag behind that of the rolled strip over a certain period of time during a speed change due to the inherent delay in the control loop (control delay). This, in turn, would result in undesirable slippage between the squeezing roll and the strip surface. 202200161 15 Furthermore, a torque characteristic ^ for the electric rotary drive of the squeezing roll can be determined empirically, for example, by installing a rolling mill when the squeezing roll is first installed on the respective roll stand.The strip is rolled at several different speeds, with the squeeze roller in its final position against the rolled strip and the electric rotary drive being operated purely with speed control. If the respective torque of the electric rotary drive is determined at which the angular velocity of the squeeze roller corresponds to the respective strip speed behind the rolling stand (i.e., when the speed control has adjusted to the respective strip speed), then the torque values ​​thus determined represent the torque characteristic ^ as a function of the strip speed v (or the corresponding angular velocity ^ of the squeeze roller). Therefore, knowledge of the torque characteristic ^ makes it possible to directly specify the corresponding torque of the electric rotary drive when the speed v of the rolled strip changes, which is also referred to as 'feed-forward control'. ThisAdvantageously, the angular velocity ^ of the squeeze roller is adapted more quickly to a changed belt speed v. In a further preferred embodiment of the device according to the invention, the electric rotary drive is designed as an asynchronous motor with the rotor as a squirrel-cage rotor and has a measuring device for detecting an instantaneous angular velocity ^' of the squeeze roller (or of its roller shell). In particular, the measured angular velocity ^' can be an angular velocity that is repeatedly determined by measurement over short time intervals of, for example, 10-100 milliseconds. This measuring device can, for example, comprise a magnet wheel rotating with the roller shell and a rotary sensor arranged on the holder of the squeeze roller, which detects the rotary movement of the magnet wheel without contact. A particularly advantageous feature of such an embodiment is the fact thatPermanent magnets in the roller drive can be completely dispensed with, thus preventing unwanted deposits of magnetizable particles on the surface of the squeeze roller. Furthermore, contactless detection of the rotational movement of the magnet wheel is particularly wear-resistant and – in the case of an inductively operating rotary sensor – also independent of dust and metallic particles. A further advantage of the described embodiment is that the rotary sensor 12 generating a measurement signal is arranged in a fixed position on the first and / or second support part 20, 20', thus eliminating the need for a rotary feedthrough for corresponding signal lines to the rotating squeeze roller 3. Alternatively, according to a further preferred embodiment, the rotary drive is designed as a synchronous motor. In this case, sensor-based detection of the angular velocity ^ of the squeeze roller can be dispensed with, since the rotational speed of aSynchronous motor is coupled to its drive frequency and therefore the angular velocity ^, which must be specified for the squeeze roller in order to achieve slip-free rolling on the rolled strip, can be determined directly from this without additional sensors. This makes it possible, for example, to omit a pole wheel and a rotation sensor and achieve an even more compact design for the device according to the invention. Furthermore, the object is achieved according to the invention by a method for removing cooling lubricant during the rolling of a rolled strip in a cold rolling mill mentioned above, on which a device according to the invention is arranged. In the method according to the invention - in a first step before threading a strip head of the rolled strip into the rolling stand, the control and 202200161 17 regulating device controls the adjusting device such that the squeeze roller is moved to a starting position A, - in a second step after threadingof the rolled strip into the rolling stand, the control and regulating device controls the adjusting device in such a way that the squeeze-off roll is moved to the end position E and the rolled strip is deflected downwards into a second strip running line B2, and - in a third step, the rolled strip is rolled in the rolling stand, wherein cooling lubricant is applied to the rolled strip and the instantaneous speed v of the rolled strip behind the rolling stand is measured and fed to the control and regulating device, wherein the control and regulating device controls the rotary drive in such a way that the roller shell rolls essentially without slippage on an upper side of the rolled strip and in the process diverts the cooling lubricant laterally from the upper side of the rolled strip. The advantageous effects of the method according to the invention correspond to those of the device according to the invention. The properties, features and advantages of the invention described above as well as the manner in whichthese are achieved, will become clearer and more easily understandable in connection with the description of the following exemplary embodiment of the invention, which is explained in more detail in connection with the figures. Identical parts and sections in the figures are each provided with the same designations. They show: Figure 1 (FIG 1) a cross-section through a squeeze roller according to the exemplary embodiment of the device according to the invention; Figure 2A (FIG 2A) a squeeze roller pivoted into the starting position A on the rolling stand according to the exemplary embodiment; Figure 2B (FIG 2B) a squeeze roller pivoted into the end position E on the rolling stand according to the exemplary embodiment; 202200161 18 Figure 2C (FIG 2C) the squeeze roller arranged on the rolling stand from FIGS. 2A, 2B with adjusting device seen opposite a first or second strip running line B1 or B2; Figure 3 (FIG 3) shows a support part for the squeeze roller according to the embodiment; and Figure 4 (FIG 4) shows a block diagram of theDevice according to the invention. FIG. 1 shows a cross-section through a squeeze roller 3 of an embodiment of the device 1 according to the invention. The squeeze roller 3 (specifically: its roller shell 15, designed, for example, as a hollow cylinder) is rotatably mounted about a rotation axis R at both axial ends by means of bearings 19 and spacer bushings 39 via a first and second roller pin 14, 14' in a first and second holding part 20, 20' of a holder 2, respectively. The first and second roller pin 14, 14' are each rigidly connected to the first and second holding part 20, 20', respectively, and each has a media connection 24 for introducing a gaseous medium into the interior of the squeeze roller 3, whereby a higher pressure level is created there in relation to the ambient pressure and the penetration of moisture and dust particles is advantageously prevented. In addition, the first roller pin 14 has media connections 25for the supply and discharge of a cooling liquid. The cooling liquid - for example water - is introduced into or discharged from cooling channels 16 through the first roller pin 14 via feedthroughs 17 into cooling channels 16' of a motor housing 13 of the electric rotary drive 5 of the squeeze roller 3. The motor housing 13 is firmly connected to the first roller pin 14 and encloses the electric rotary drive 5. The rotary drive 5 is designed as an internal rotor and comprises an internal rotor 7 and an external stator 6 - viewed in the axial direction. The stator 6 has, for example, coil windings for generating an electromagnetic rotating field (not shown in FIG. 1) and is firmly connected to the motor housing 13. The introduced coolant flows from the cooling channels 16' of the motor housing 13 into corresponding cooling channels 16" in or on the stator 6 and absorbs waste heat generated by the rotary drive 5 as it flows through.Cooling channels 16" are designed in the present embodiment as one or more spiral channels on the outer surface of the stator 6. The first and second roller journals 14, 14', the motor housing 13, and the stator 6 form the stationary parts of the squeeze roller 3 with respect to the first and second support parts 20, 20'. Furthermore, sealing rings 18 are arranged between the bearing seats of the bearings 19 and the parts of the squeeze roller 3 that are rotatable relative thereto in order to prevent the penetration of fine particles into the bearings 19 or into the interior of the squeeze roller 3. The rotor 7 is connected to a rigid output shaft 8, which protrudes axially from the motor housing 13 and is connected to the roller shell 15 of the squeeze roller 3 via a flexible drive shaft 9. The flexibility of the drive shaft 9 allows a certain mechanical offset normal to its axial direction. (Misalignment), however, the drive shaft 9 behaves rigidlywith respect to its circumferential direction. Furthermore, the device 1 according to the invention comprises a measuring device 10 for detecting a current angular velocity ^' of the squeeze roller 3. According to the illustrated embodiment, the measuring device 10 is designed as a magnet wheel 11 fixedly arranged on the roller shell 15 in conjunction with a rotation sensor 12. The rotation sensor 12 is fastened to the first mounting part 20 as a non-contact measuring device and is designed to generate a signal corresponding to a relative movement of the magnet wheel 11 rotating with the roller shell. For redundancy reasons, such a measuring device can also be arranged at both axial ends of the squeeze roller 3 (not shown in FIG. 1). FIG 2A shows a view of the embodiment of FIG 1 along the rotation axis R of the squeeze roller 3. The thick solid line represents a flat rolled strip 100, which is arranged along a firstStrip travel line B1 (running from right to left in FIG 2A) in front of a first roll stand 21 of the roll stand and moves through it. Of the first roll stand 21, only the central region in relation to its height with the stand window is shown in FIG 2A, but without work rolls and any other rolls. The roll stand is closed, i.e. the upper and lower work rolls 40 of the roll stand are each positioned against the rolled strip 100, which passes through the roll stand along a first strip travel line B1. In the immediate vicinity of the roll gap, the first strip travel line B1 runs essentially horizontally - i.e. within a range of 5° - wherein a slight deflection is visible in FIG 2A, which is caused by rollers (not shown in FIG 2A) arranged upstream and downstream of the roll stand. The squeeze roller 3 or its roller casing 15 are shown in the perspective shown in front of the first support part 20 and are rotatably attached thereto.The first support member 20 is attached via screws 29 to a base 27, which in turn is rigidly connected to a pivotable platform 28. The platform 28 is rotatably attached to the first rolling stand 21 by means of a first pivoting attachment 26. Below the platform 28, a first actuator 4' (in the illustrated embodiment in the form of a hydraulic cylinder) of an adjusting device 4 is also rotatably attached to the first rolling stand 21 at its lower end via a second pivoting attachment 26'. The actuator 4' is rotatably mounted on the base 27 at the end opposite the second rotary mounting 26' by means of a third rotary mounting 26". In FIG. 2A, the adjusting device 4 or its first actuator 4' is adjusted (hydraulic cylinder extended) such that the squeeze roller 3 is positioned above the rolled strip 100 in the starting position A and therefore does not touch the upper side 101 of the rolled strip 100. FIG. 2Bshows the same view of the exemplary embodiment as FIG 2A with the difference that the adjusting device 4 or its first actuator 4' is set such (hydraulic cylinder retracted) that the squeeze-off roller 3 is positioned in the end position E, wherein the roller shell 15 touches the upper side 101 of the rolled strip 100 and thereby deflects the rolled strip 100 downwards so that the rolled strip 100 passes through the rolling stand along a second strip running line B2. In the depression caused by the deflection, excess cooling lubricant (not shown in FIG 2B) collects on the inlet side - ie to the right of the squeeze-off roller 3 in FIG 2B - which is subsequently drained off from the rolled strip 100 in a lateral direction transverse to the second strip running line B2 (ie normal to the plane of the drawing in FIG 2B). FIG 2C shows a view of the embodiment from FIG 1 parallel to the rotation axis R of the squeeze roller 3 and opposite a first or second strip running line B1 orB2, wherein the squeeze roller 3 is located in the starting position A above the end position E. It is further shown that the squeeze roller 3 is arranged between the first and second roll stands 21, 21' of the roll stand in the direction of its rotation axis R and is rotatably mounted at its two axial ends in the first and second holding parts 20, 20', respectively. The first and second holding parts 20, 20' are each connected to a first and second actuator 4', 4" of the adjusting device 4, as described in connection with FIG. 2A. To move the squeeze roller 3 between the starting position A and the end position E, the first and second actuators 4', 4" are moved synchronously with one another. FIG 3 shows a support part 20 for the squeeze roller 3. The squeeze roller 3 is rotatably mounted in the first support part 20 via the first roller pin 14. Between the rotation sensor 12 arranged on the first support part 20 and theAn air gap, for example of a few millimeters, remains between the pole wheel 11 fastened to the roller shell 15. A media connection 24' for introducing the gaseous medium and media connections 25' for introducing and discharging coolant into the squeeze roller 3 are arranged on the upper bevel of the first mounting part 20. Corresponding media channels in the first mounting part 20 open into the corresponding media connections 24, 25 in the first roller journal 14. The media connection 24 or 24' also serves to feed through the connections of the electric rotary drive 5. Since the first roller journal 14 is non-rotatable and firmly connected to the first mounting part 20, the corresponding transition points can be reliably sealed against the escape of coolant or gaseous medium. The media are thus passed through the first support part 20 into the squeeze roller 3, with the media connections 24', 25' on a surfaceof the first holding part 20 are arranged, the normal vector of which is oriented perpendicular to the axis of rotation R of the squeeze roller 3. This advantageously allows good utilization of the space available between the first and second rolling stands 21, 21' for the device 1 according to the invention. Furthermore, FIG. 3 shows that the first holding part 20 has a flat contact surface 23 on its underside in the region of the screw connection 29 for contact with the base 27 (this is not shown in FIG. 3). Transversely to this, ie in the direction of rotation R of the squeeze roller 3, the underside of the first holding part 20 has chamfers 22 in the form of beveled surfaces, the angle ^ between the contact surface 23 and the chamfers 22 being a few degrees in each case, for example 1-2°. The second support part 20' has similar chamfers 22. The chamfers 22 allow a slight tiltingbetween the first and second support parts 20, 20' on the one hand and the respective associated base 27, so that when moving the squeeze roller 3 between the starting and end positions A and E, slight asynchronies between the individual actuators 4' and 4" of the adjusting device 4 can be compensated. FIG. 4 shows a block diagram of the individual sections of the device 1 according to the invention: the rotary drive 5 of the squeeze roller 3, which has a stator 6 and a rotor 7, is firmly connected to the roller shell 15, which is symbolized by hatching. When the squeeze roller 3 is positioned against the rolled strip 100 (end position E), a control and regulating device 30 controls the rotary drive 5 or specifies an angular velocity ^ for the squeeze roller 3, which corresponds to a current speed v of the rolled strip 100 behind the rolling stand (not shown in FIG. 4). placed) so that the roller shell 15 can be moved without slippage on the rolled strip100 rolls off. A current speed v of the rolled strip 100 behind the rolling stand is continuously measured and fed to the control and regulating device 30. The control and regulating device 30 determines the specified angular speed ^ in the case of a rotary drive 5 designed as a synchronous motor based on the current speed v and the diameter of the roll shell 15, since in this case the angular speed of the electric rotating field generated by the stator 6 of the rotary drive 5 always corresponds to that of the rotor 7. In the case of a rotary drive 5 designed as an asynchronous motor, the control and regulating device 30 determines the angular speed ^, which is specified to the rotary drive 5, with the additional inclusion of the angular speed ^' of the roller shell 15 determined with the aid of the measuring device 10 (dashed arrow in FIG. 4), since in this case the electric rotating field generated by the stator 6 of theAngular velocity of the rotor 7 - depending on the instantaneous torque load of the rotary drive 5 - leads. In both cases (rotary drive 5 as a synchronous or asynchronous motor), the determination of the specified angular velocity ^ can be carried out by the control and regulating device 30 taking into account a torque characteristic curve ^ in order to adapt the angular velocity ^ of the squeeze roller 3 more quickly to these changes in the event of changes in the speed v of the rolled strip 100 behind the rolling stand. Furthermore, the control and regulating device 30 controls the adjusting device 4 in accordance with external control data S supplied to the control and regulating device 30 such that the squeeze roller 3 is moved between a starting position (A) and an end position E. With regard to the embodiment shown in FIG. 2C, the control and regulating device 30 controls the two actuators 4', 4" synchronously, so that the first andsecond support part 20, 20' of the support 2 executes a synchronous movement for moving / pivoting the squeeze roller 3. The control data S depend essentially on the state of the rolled strip 100 rolled in the respective rolling stand (if, for example, no rolled strip 100 or only the beginning of the strip is currently moving through the rolling stand, then the squeeze roller 3 must be moved to the starting position A in order to enable undisturbed threading of the rolled strip 100) and specify to the control and regulating device 30 at what point in time the squeeze roller 3 is to be positioned against the rolled strip 100 passing through the rolling stand or moved away from it. 202200161 25 List of reference symbols 1 Device 2 Holder 3 Squeeze roller 4, 4', 4" Adjusting device, actuator 5 Electric rotary drive 6 Stator 7 Rotor 8 Output shaft 9 Flexible drive shaft 10 Measuring device 11 Pole wheel 12 Rotation sensor 13 Motor housing 14, 14' Roller journal 15 Roller shell 16, 16', 16" Cooling channel 17Feedthrough 18 Sealing ring 19 Bearing 20, 20' Supporting part 21, 21' Roll stand 22 Chamfer 23 Contact surface 24, 24' Media connection gas 25, 25' Media connection coolant 26, 26', 26" Rotating fastening 27 Base 28 Platform 29 Screw 30 Control and regulation device 39 Spacer bush 40 Work roll 100 Rolled strip 101 Top side Rolled strip A Starting position B1, B2 First, second strip running line 202200161 26 E End position R Rotation axis S Control data v Speed ​​Rolled strip ^ Angle ^, ^' Angular speed

Claims

202200161 27 claims 1. Device (1) for removing cooling lubricant during the rolling of a rolled strip (100) in a cold rolling mill with at least one rolling stand, comprising - a squeeze roller (3) which can be arranged between a first and a second rolling stand (21, 21') of the rolling stand and has a roller shell (15) and an internal electric rotary drive (5), - a holder (2) in which the squeeze roller (3) is rotatably mounted about a rotation axis (R), - an adjusting device (4) for adjusting the squeeze roller (3) against the rolled strip (100), and - a control and regulating device (30) for controlling the rotary drive (5) and the adjusting device (4), - wherein the rotary drive (5) is fixedly connected to the roller shell (15), a stator (6) and a rotor (7) and is designed as an internal rotor,- wherein the control and regulating device (30) knows a current speed (v) of the rolled strip (100) behind the rolling stand, and the control and regulating device (30) is configured to control the rotary drive (5) synchronously with the current speed (v) of the rolled strip (100) behind the rolling stand, - wherein the adjusting device (4) is configured to move the holder (2) with the squeeze-out roller (3) between a starting position (A) and an end position (E), - wherein during the rolling of the rolled strip (100) in the rolling stand, the roller shell (15) -- in the starting position (A) does not touch the rolled strip (100), so that the rolled strip (100) passes through the rolling stand in a first strip travel line (B1), and -- in the end position (E) contacts the rolled strip (100) on an upper side (11) and thereby deflects downwards into a second strip running line (B2).

2. Device (1) according to claim 1, 202200161 28 - wherein the holder (2) is designed in two pieces from a first and a second holder part (20, 20') and the squeeze-out roller (3) has a first and a second roller pin (14, 14'), - wherein the first roller pin (14) is rigidly connected to the first holder part (20) and the second roller pin (14') is rigidly connected to the second holder part (20'), - wherein the rotor (7) is firmly connected to a rigid shaft (8) which is firmly connected to the roller shell (15) via a flexible drive shaft (9).

3. Device (1) according to claim 2, wherein the first roller pin (14) is firmly connected to a cooling jacket (13) for the stator (6), which encloses the stator (6) and is firmly connected to it.

4. Device (1) according to one of the preceding claims, wherein the diameter of the squeezing roller (3) is 300-500 mm. 5.Device (1) according to one of the preceding claims, wherein the first roller journal (14) and the cooling jacket (13) have at least one cooling channel (16) for the passage of a cooling medium.

6. Device (1) according to one of the preceding claims, wherein the first and / or the second roller journal (14, 14') have a passage (17) for introducing a gaseous medium under excess pressure into the interior of the squeeze-out roller (3).

7. Device (1) according to one of the preceding claims, wherein the first and the second holding part (14, 14') extend along the axis of rotation (R) over 50-70 mm and have chamfers (22) on a respective contact surface (23) with the adjusting device (4). 202200161 29 8. Device (1) according to one of the preceding claims, wherein the control and regulating device (30) is configured to pre-control an angular velocity ( ^) of the squeeze roller (3) on the basis of a torque characteristic ( ^) of the electric rotary drive (5).

9. Device (1) according to one of the preceding claims, wherein the electric rotary drive (5) is designed as an asynchronous motor with the rotor (7) as a squirrel-cage rotor and has a measuring device (10) for detecting an instantaneous angular velocity ( ^') of the squeeze roller (3).

10. Device (1) according to claim 9, wherein the measuring device (10) comprises a pole wheel (11) arranged on the squeeze roller (3) and a rotation sensor (12) arranged on the holder (2).

11. Device (1) according to one of claims 1 to 8, wherein the electric rotary drive (5) is designed as a synchronous motor. 12.Method for removing cooling lubricant during the rolling of a rolled strip (100) in a cold rolling mill with at least one rolling stand on which a device (1) according to one of the preceding claims is arranged, wherein - in a first step, before threading a strip head of the rolled strip (100) into the rolling stand, the control and regulating device (30) controls the adjusting device (4) such that the squeeze roller (3) is moved into an initial position (A), - in a second step, after threading the rolled strip (100) into the rolling stand, the control and regulating device (30) controls the adjusting device (4) such that the squeeze roller (3) is moved into the end position (E) and the rolled strip (100) is deflected downwards into a second strip running line (B2), and - in a third step, the rolled strip (100) in the Rolling stand is rolled, with cooling lubricant being applied to the rolled strip. 202200161 30 is applied and the instantaneous speed (v) of the rolled strip (100) behind the rolling stand is measured and fed to the control and regulating device (30), wherein the control and regulating device (30) controls the rotary drive (5) in such a way that the roller shell (15) rolls essentially without slippage on an upper side (101) of the rolled strip and in the process diverts the cooling lubricant laterally from the upper side (101).

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