EP3762161B1 - Rolling method with a step for adjusting the interspace between the side bearing roller and the support roller - Google Patents

Description

The invention relates to a rolling process adapted to a strip rolling installation, as well as to a rolling installation as such.

The field of the invention is that of cold rolling a metal strip, and more particularly that of laterally supported Sexto cage rolling mills, and in particular the rolling mills known under the name “ ZHigh ”.

These rolling mills find their application, online, for example, in pickling annealing lines or, offline, as reversible rolling mills, for metal strip.

A Quarto stand rolling mill comprises a holding stand in which four rolls with parallel axes are provided, namely two working rolls, lower and upper, respectively, defining the air gap for the strip to be rolled, as well as two roll rolls. support, upper and lower, respectively bearing on the working rolls on the side opposite to that of the passage gap to transmit the rolling force.

A Sexto rolling mill includes two additional rolls compared to a Quarto, namely two intermediate rolls interposed respectively between each working roll and the corresponding support roll, on either side of the metal strip: the clamping force of each support cylinder is transmitted to the working cylinder, only via the intermediate cylinder, the latter having a generator in contact with a generator of the support cylinder and a diametrically opposite generator in contact with a generator of the working cylinder .

In such rolling mills, each support cylinder and each intermediate cylinder is rotatably mounted at its ends on chocks, via bearings, for example bearings or even hydrostatic bearings. These chocks are supports which can be moved in a vertical direction parallel to the clamping plane, along and between the two uprights of the cage.

Conventionally, balancing cylinders allow the movement of the chocks of the intermediate cylinders. These balancing cylinders make it possible to change the relative position of the chocks and their cylinder, allowing, among other things, to open the cage to facilitate the engagement of the product to be rolled, or to move these elements to facilitate the dismantling of the cylinders. These balancing cylinders can also allow the intermediate cylinders to be cambered. An advantage of a Sexto stand rolling mill is the possibility of using, compared to a Quarto stand, working rolls of smaller diameter, which makes it possible to obtain a greater reduction in thickness of the product to be rolled, for the same rolling force.

A Sexto rolling mill also offers the possibility of axially shifting the two intermediate rolls, and with the aim of applying the rolling force only to the width of the strip to be rolled, and not to the entire length of the working rolls.

In a so-called “ laterally supported ” Sexto rolling mill, very often the work rolls are not mounted on chocks, but on the contrary are designed to float. It is then necessary to maintain their axial position, via axial stops, but also to maintain their lateral position by means of lateral support members, such as rollers or lateral support rollers arranged on either side. other of the clamping plane.

We know, for example, from the document EP 0 121 811 , in particular of the mode of realization of the figure 2 , such a rolling mill of the Sexto type which comprises two working rolls, two support rolls and two intermediate rolls, interposed respectively between one of the work rolls and the corresponding support roll. In this document, the work rolls, intermediate rolls and support rolls are all mounted on chocks.

Each working cylinder is supported laterally, on either side of the working cylinder, by two pairs of rollers. The rollers of the same pair are provided at the two ends of each working roll, at the ends of the roll which are not in contact with the strip to be rolled. The rollers are pivotally mounted on forks that move in translation relative to the cage upright, under the action of hydraulic cylinders.

To the Figure 6 of this document, nozzles are provided on board the support part of the rollers, movable relative to the amount of the cage. For this purpose, flexibles are used to supply the nozzles with cooling and/or lubricating products, the flexibles making it possible to take into account the movements between the mobile support part and the uprights of the cage. These nozzles allow the lubrication and cooling of the rollers and the work cylinder, at the level of the roller support zone.

We still know of the document US 4,531,394 another rolling mill design, of the side-supported Sexto type. Such a rolling mill always includes two working rolls, two support rolls and two intermediate rolls, interposed respectively between one of the work rolls and the corresponding support roll. In this document, the support cylinders and the intermediate cylinders are mounted at their ends on chocks, while that the working cylinders are intended to be floating. Each working cylinder is supported laterally, on each side of the working cylinder, by a lateral support cylinder, itself resting on two rows of rollers arranged along the length of the cylinder.

In this rolling mill design, for each working roll, the two corresponding lateral support rolls are secured to the two chocks of said intermediate roll. Each lateral support cylinder, as well as its support rollers, are mounted on a support arm which extends between the two chocks of the intermediate cylinder, each support arm being mounted pivoting around a shaft whose ends are secured to the chocks .

The intermediate cylinder assembly, intermediate cylinder chocks, support arm (right and left), rollers and lateral support cylinders, right and left, form a self-supporting assembly, commonly called "cassette" or even "insert " which can be introduced into the cage, or removed from the cage, during maintenance, by sliding the assembly in the direction of the cylinders, in the cage opening position.

Four force distribution beams extend rigidly between the two uprights of the cage, respectively, opposite each support arm. Each force distribution beam supports a beam, called a preload beam, movable in translation relative to the corresponding force distribution beam, movable towards the inside of the cage in a substantially horizontal direction. Preload cylinders make it possible to force the mobile beam into contact with the pivoting support arm to preload the lateral support cylinder on the working cylinder.

In such a rolling mill, the cooling and lubrication of the working roll and the intermediate roll are carried out by means of nozzles, marked respectively 73 and 72 at the figure 2 of the document US 4,531,394 , physically distant from the working cylinder, located outside the “ insert ” or the “ cassette ”. On the figure 2 , these nozzles are secured to the force distribution beam, or even to the mobile preload beam. So that the jet can reach the intermediate cylinder, the nozzles, marked 72, face bores passing through the support arms. In practice and to the knowledge of the inventors, this watering solution via bores in the support arms would not appear to be retained in rolling mills used industrially.

According to the findings of the inventors, the spray nozzles, marked 73, are incapable of properly cooling the work roller because they are located too far from it, their jets coming too quickly in interference with the lateral support arms, rollers and rollers. lateral supports and therefore unable to move the tape up. On the other hand, according to the findings of the inventors, the nozzles marked 72 are incapable of properly lubricating the contact between the work roller and the intermediate cylinder because they are located too far from it. In use, such insert rolling mills have a limited lifespan for the working roll, due to its poor cooling.

We still know of the document US.6,041,636 another design of a sexto type rolling mill supported laterally, with “ insert” or “cassette”. As in the previous document, the intermediate cylinder assembly, intermediate cylinder chocks, support arm (right and left), rollers and lateral support cylinders, right and left, form a self-supporting assembly which can be introduced into the cage or removed from the cage during maintenance, by sliding the assembly in the direction of the cylinders.

In this document US.6,041,636 , the chocks of the intermediate cylinders are mounted on camber blocks. The cylinders of the cambering blocks allow, during operation, to bring the intermediate cylinders together, in a working position illustrated in figure 5 of this document, or to move the intermediate cylinders apart to a position, illustrated in figure 4 , allowing the removal of the inserts by sliding. These cylinders can also allow, in operation, to bend the intermediate cylinder.

In this document, it is known to supply lubricant to the roller bearings of the insert support arms, from a lubricant source. Connection/disconnect devices make it possible, in the working position of the cylinders, to connect the lubricant source to lubrication bores provided in the chocks, and to automatically disconnect the bores when the intermediate cylinders and their chocks are separated vertically by the chocks. camber blocks. This automatic connection/disconnection is advantageous. No additional operations to connect/disconnect the lubricant source are required during maintenance, especially when inserts need to be removed or introduced into the cage. For this purpose, each connection device comprises an element, marked 57 called " plunger ", hollow, intended to conduct the lubricant, and which allows, in the working position of the intermediate cylinders, as illustrated in the Figure 9 , to join the bore of the chock in a relatively watertight manner via a seal. This element is mobile, vertically in translation, forced towards its sealing position by means of a spring, marked 58. In the connection position, the lubricant flows from the lubricant source through the element movable and up to the bore of the insert. The lubricant then flows from the bore of the chock, and to the bearings via the hollow of the shaft, marked 17, on which the support arm is pivotally mounted.

When the intermediate cylinders are spaced apart by the bending blocks to their withdrawn position, the stroke of the movable element is limited, less than the displacement stroke of the bending blocks, thus making it possible to guarantee an inter-space between the moving element and the chock, as illustrated in figure 8 of the document US 6,041,636 . It is then possible to remove the insert, without friction between the chocks and the mobile element.

Such a connection/disconnect device allows the lubrication of the bearings of the support arms. However, this document does not address the problem of cooling the work rolls. To the knowledge of the inventors, and according to this design, the cooling of the intermediate and working cylinders and the lubrication of the intermediate cylinder/working cylinder contact is always carried out by providing nozzles physically at a distance from the cylinders.

However, we know of the document EP 1 721 685 a sexto type rolling mill laterally, perfecting the cooling of a working roll. This document aims to improve state-of-the-art “ cassette ” rolling mills, for which there would be no room to place cooling nozzles as close as possible to the rollers. There figure 2 illustrates the purpose of perfecting prior art EP 1 721 685 .

The rolling mill is now a unidirectional rolling mill (non-reversible) which includes, upstream, in the direction of travel of the strip, a lateral support cylinder, as previously described, supported by a support arm. Downstream, the support arm does not have a roller or support cylinder. This support cylinder is replaced by a pad called a “ support pad ” which can be made of bronze or a self-lubricating graphite material, intended to slide on the surface of the work roller, without exerting substantial force on it. this.

This skid support arm has several nozzles for a coolant which allow the work roller to be directly cooled on the downstream side. Downstream, the lubricant liquid is supplied to the nozzles via the hollow shaft of the corresponding support arm. Upstream, the hollow shaft of the support arm is used to convey the lubricant to the roller bearings supporting the side support cylinder. This document teaches how to improve the cooling of work rolls. However, this improvement comes at the expense of supporting the working roll on one of its sides, by removing a lateral support cylinder and replacing it with a shoe, the rolling mill then no longer being a reversible rolling mill.

We still know of the document EP 2 391 459 a method and a device for watering a rolling installation. This document focuses more particularly on the watering of working rolls each supported laterally by a pair of rolls, and comprising at least one pair of support rolls for transmitting a rolling force. This document is intended in particular as an improvement of the document EP 1 721 685 previously described, a solution which would remain prohibited for reversible rolling mills.

According to this document, direct spraying of at least part of the working cylinders is provided, on either side of said plane perpendicular to the direction of travel of the strip. According to this document, the nozzles are positioned on the supports of the lateral support cylinders in order to directly water the working cylinder on both sides, laterally on either side of the clamping plane.

However, the technology described in this document EP 2 391 459 is not a “cassette ” technology as taught by the documents US 4,531,394 , US.6,041,636 , EP 1,721,685 for which the intermediate cylinder assembly, chocks of the intermediate cylinder, support arm, (right and left), rollers and lateral support cylinders, right and left, form a self-supporting assembly, called " insert " which can be introduced into the cage or removed from the cage during maintenance, by sliding the assembly in the direction of the cylinders.

The real difficulty in improving the coolant of the work rolls in a cassette rolling mill is not in placing the coolant nozzles in the cassette, but in knowing how to supply them with lubricating/cooling fluid, and without increase the maintenance time during operations of removing or inserting the cassette into the rolling mill stand. For example, it is impossible to use flexible hoses between the cassette and the rolling mill stand to supply the nozzles, because these would need to be dismantled and reassembled during cassette removal or insertion operations, which would would considerably lengthen the time required for these maintenance operations.

As previously described, the document US.6,041,636 discloses automatic connection devices making it possible, in the working position of the cylinders, to connect the source of lubricant to lubrication bores provided in the chocks, and to automatically disconnect the bores when the intermediate cylinders are spaced apart vertically by the cambering blocks . However, such a device can only be used to supply lubricant, either only to the bearings of the rollers of the lateral support cylinder of a support arm, or only to supply fluid to the nozzles of a support arm. This is the reason why the nozzle support arm does not have a lateral support cylinder in the document EP 1 721 685 , this being replaced by a pad which does not require a bearing to be lubricated. Furthermore, the connection device in this prior art connects to the chocks which requires the fluid to be conveyed along a complex trajectory via the hollow shaft and to the lower end of the support arm. This complex fluid trajectory, from the chock to the support arm, via the hollow shaft, generates significant pressure losses, limiting flow rates.

In summary, and according to the aforementioned state of the art, in the aforementioned laterally supported sexto type reversible rolling mills, with cassettes, the cooling of the working rolls and the intermediate rolls is carried out by means of nozzles placed outside the cassette, physically distant from the work rolls and intermediate rolls and whose jets cannot directly reach the work rolls. In this type of rolling mill used industrially, it is conventional to place a spray ramp, on each side of the clamping plane, mounted on the force distribution beam of the cage and whose jets are directed at the contact level. between the support cylinder and the intermediate cylinder. According to this arrangement, the lubrication of the working cylinder is therefore obtained, indirectly, by the fact that the intermediate cylinder has been wetted and that this cylinder transports this lubrication during its half-turn rotation, up to the working cylinder . According to the inventors' findings, this lubrication is insufficient, in particular for the cylinders placed under the belt.

Furthermore, and when the speed of the rolling mill becomes large, the centrifugal force at the circumference of the intermediate roll tends to wring the roll so that little cooling fluid reaches the working roll.

However, we know of the document WO 2015/011373 of the present Applicant, a rolling mill of the Supported Sexto Type, with cassette technology which provides notable progress for the cooling of the working rolls, and compared to the aforementioned state of the art, in particular of the cassette rolling mill stand.

• une cage de maintien comprenant deux paires de montants écartées entre-elles aux deux extrémités de la cage, au moins deux montants d'une même paire définissant une fenêtre d'accès,
• deux cylindres de travail, aptes à enserrer une bande à laminer, deux cylindres d'appui, et deux cylindres intermédiaires, les cylindres d'appui et les cylindres intermédiaires étant montés rotatifs à leurs extrémités sur des empoises,
• des cylindres d'appui latéraux, aptes à supporter latéralement les cylindres de travail, chaque cylindre d'appui latéral étant porté par un bras support, monté pivotant sur un axe,
• des poutres de répartition d'effort s'étendant entre les montants correspondants de chaque paire, et des moyens d'application d'un effort de précharge sur chaque bras support, destinés à engager avec l'un des bras support au niveau d'une surface d'appui, et comprenant au moins un vérin de précharge solidaire de l'une des poutres de répartition d'effort,
• une ou plusieurs buses de pulvérisation pour un fluide lubrifiant/ refroidissant.

This is a laterally supported Sexto rolling mill which includes:

• a holding cage comprising two pairs of uprights spaced apart from each other at the two ends of the cage, at least two uprights of the same pair defining an access window,
• two working rolls, capable of gripping a strip to be rolled, two support rolls, and two intermediate rolls, the support rolls and the intermediate rolls being rotatably mounted at their ends on chocks,
• lateral support cylinders, capable of laterally supporting the working cylinders, each lateral support cylinder being carried by a support arm, pivotally mounted on an axis,
• force distribution beams extending between the corresponding uprights of each pair, and means for applying a preload force to each support arm, intended to engage with one of the support arms at the level of a support surface, and comprising at least one preload cylinder integral with one of the force distribution beams,
• one or more spray nozzles for a lubricating/cooling fluid.

Each support arm of a lateral support cylinder is pivotally mounted on said axis, constituted by a shaft secured to the chocks of one of the intermediate cylinders, each intermediate cylinder, chocks of the intermediate cylinder, lateral support cylinders and corresponding support arms forming a self-supporting assembly, called an insert (or “ cassette ”), which can be removed or inserted by sliding through the access window during maintenance, in the open position of the cage.

The hollow of the shaft can possibly be used, as in the state of the art (see US 6,041,636 ) to channel a fluid intended to lubricate the roller bearings (marked 52 on figure 1 ) laterally supporting the lateral support cylinder. According to the document WO 2015/011373 , at least one of the nozzles is mounted on one of the support arms in particular to allow the lubrication/cooling of the working cylinders and/or intermediate cylinders.

• une conduite du bras support, destinée à canaliser le fluide, présentant une ouverture d'alimentation débouchant sur la surface d'appui 10 du bras support 6 destinée à engager les moyens d'application d'un effort de précharge,
• une partie creuse, mobile par rapport à la poutre de répartition d'effort, déplaçable par rapport à ladite poutre de répartition d'effort 8 sous l'action desdits moyens 9 d'application d'un effort de précharge.

Advantageously, the fluid supply circuit of said at least one nozzle comprises a connection/disconnection device marked 13 having:

• a pipe of the support arm, intended to channel the fluid, having a supply opening opening onto the bearing surface 10 of the support arm 6 intended to engage the means for applying a preload force,
• a hollow part, mobile relative to the force distribution beam, movable relative to said force distribution beam 8 under the action of said means 9 for applying a preload force.

According to the document WO 2015/011373 , this hollow part is configured to make a watertight connection with the supply opening on the support surface in a first connection position, or on the contrary, retract into a second disconnection position, at a distance from the surface support.

In the first connection position, as shown in figure 2 of the document WO 2015/011373 , the cooling fluid can be channeled from the source to said at least one nozzle marked 12 (illustrated) or even to said at least one nozzle marked 12' (not illustrated), via said connection device /disconnect.

In the second disconnection position, the means for applying a preload force are retracted, in the retracted position, said hollow part being at a distance from the support arm.

This position allows, particularly when the design of the rolling mill is of the insert (or cassette) type, to be able to remove or introduce the insert, without requiring additional maintenance time to disconnect/connect the fluid source.

Another advantage of such a connection/disconnection device is that it connects directly to the support arm, and not to the chocks of the intermediate cylinder as taught in the state of the art known from the document US.6,041,636 . To reach the nozzle or in an insert type rolling mill WO 2015/011373 , the fluid does not need to pass through the hollow shaft on which the support arm is pivotally mounted. It is then possible to significantly limit the pressure losses, and thus to obtain fluid flow rates much higher than those obtained in this state of the art, and thus to significantly improve the cooling of the working cylinders by placing cooling nozzles. cooling as close as possible to the lateral support cylinder.

We still know of the document WO 2011/107165 (or US 2012324973A1 ) a Sexto type rolling stand supported laterally, with working rolls, intermediate rolls. The rolling stand comprises, according to the example of the figure 5 lateral support cylinders, and more particularly, for each working cylinder, a first lateral support cylinder and a second lateral support cylinder, located on either side of the clamping plane. Each lateral support cylinder is held by two rows of support rollers, the support rollers and the lateral support cylinder being carried by an arm mounted pivoting around a guide member marked 72 at the figure 5 .

Notably, and in this document WO 2011/107165 the support rollers and their support arm are pivotally mounted on the bending block, capable of supporting a chock of the intermediate cylinder, bending block which is capable of moving vertically relative to the amount of the cage. During maintenance, it becomes possible to extract the intermediate cylinder axially, by sliding its chocks relative to the bending blocks, and while the lateral support cylinder remains fixed in the cage, still connected to the bending block by via the support arm.

The invention is more particularly interested, at least according to one embodiment, in the problem of cooling the working cylinders, when each working cylinder is held laterally, by two cylinders of a pair of lateral support cylinders, arranged on either side of the clamping plane, by direct spraying of the working cylinder, and as taught by the document EP 291 459 A1 .

Notably, however, the invention is concerned with solving this problem in the case where the two rows of support rollers ensuring the maintenance of each lateral support cylinder is pivotally mounted via an arm support, that this support arm is articulated along a pivot axis to the chocks of the intermediate cylinder as taught by the document WO 2015/011373 , or even to the cambering block capable of supporting the chock of the intermediate cylinder, on board the cambering block, as taught by the document WO 2011/107165 .

THE figures 1 to 4 illustrate the standard configurations of a laterally supported Sexto type rolling mill, cassette type, for example taught according to the document WO 2015/011373 Or US.6,041,636 in which the support roll transmitting the rolling force to the working roll WR is an intermediate roll IR. This working cylinder is held laterally by the two cylinders of a pair of SSR lateral support cylinders, arranged on either side of the clamping plane of the cage.

Each lateral support cylinder SSR is itself held by two rows of support rollers G belonging to a bearing support, fixed to one of the ends of an arm Bs, the other end being articulated around a shaft fixed at its ends to the two chocks of the intermediate cylinder.

There figure 1 represents such a configuration when the intermediate cylinder and the working cylinder are new, namely of maximum diameters, for example 355 mm for the cylinder intermediate and 140 mm for the working cylinder according to this example. There Figure 4 represents this configuration when the intermediate cylinder and the working cylinder are worn and need to be changed, namely of minimum diameters, for example 330 mm for the intermediate cylinder and 120 mm for the working cylinder.

During the design, the position of the articulation axis between the support arm and the two chocks of the intermediate cylinder is chosen so that, when the working cylinder diameter WR and the intermediate cylinder diameter IR are maximum, it n there is no mechanical interference between the lateral support cylinder SSR and the intermediate cylinder IR (see figure 1 ), and so that, when the working roll diameter WR and the intermediate roll diameter IR are minimum, there is no interference between the lateral support roll and the rolled metal strip (see Figure 4 ).

• le premier jet J1 généré par un premier système de buses, embaqué au support de palier, traverse une ouverture de passage définie par l'inter-espace entre le cylindre d'appui latéral SSR et le cylindre intermédiaire IR, avant d'atteindre le cylindre de travail, à proximité du contact cylindre intermédiaire/cylindre de travail WR.
• un second jet J2, généré par un second système de buses, embarqué au support de palier traverse l'inter-espace entre le cylindre d'appui latéral SSR et la bande métallique, avant d'atteindre directement le cylindre de travail, voire même la bande métallique, au niveau de l'emprise de laminage.

We still notice at the figure 1 (or at Figure 4 ) that it is possible to cool the working roll by direct spraying, on either side of the clamping plane of the rolling mill stand:

• the first jet J1 generated by a first nozzle system, embedded in the bearing support, passes through a passage opening defined by the inter-space between the lateral support cylinder SSR and the intermediate cylinder IR, before reaching the cylinder working, near the intermediate cylinder/working cylinder contact WR.
• a second jet J2, generated by a second nozzle system, on board the bearing support crosses the inter-space between the lateral support cylinder SSR and the metal strip, before directly reaching the working cylinder, or even the metal strip, at the level of the rolling footprint.

During operation, the surface condition of the working roll and the surface condition of the intermediate roll deteriorate. Periodically, and in a known manner, grinding of the working cylinder is carried out, and less frequently grinding of the intermediate cylinder, in order to restore their surface condition. These operations lead to a reduction in the diameter of the ground cylinders.

The reduction in diameter of the working cylinder thus being faster than that of the intermediate cylinder, the inventors note that the mechanism for supporting and positioning the lateral support cylinders (with a fixed pivot position relative to the axis of rotation of the intermediate cylinder, and a fixed arm length) presents disadvantages for certain configurations of diameters of the intermediate cylinder and the working cylinder: we thus observe risks of interference between the intermediate cylinder and the lateral support cylinder (or its bearing support), or even a risk of obstruction of the passage opening for the jets for watering and lubricating the intermediate cylinder/working cylinder contact, or the jets for lubricating the rolling grip.

Thus and at Figure 3 , representing a configuration for which the diameter of the intermediate cylinder is maximum (355 mm) and the diameter of the working cylinder is minimum (120 mm), we observe that the watering jets are interrupted (on the right), the opening of passage between the lateral support cylinder (right) and the intermediate cylinder no longer crossed by the jet J1, the cooling of the working cylinder and the intermediate cylinder/working cylinder interface being compromised. We still observe a very small clearance of 0.7 mm between the bearing support (on the right) and the intermediate cylinder, with risk of mechanical contact.

Likewise at the figure 4 for which the diameters of an intermediate cylinder at the minimum diameter and a working cylinder at the maximum diameter, we observe that the distance between the metal strip and each bearing support (left) is small, with only 7.3 mm, representing a significant risk of contact.

The aim of the present invention is to overcome the aforementioned drawbacks by proposing a rolling process adapted to a strip rolling installation making it possible to avoid the aforementioned mechanical interferences between the metal strip and the lateral support cylinder/assembly. bearing support, and or even mechanical interference between the lateral support cylinder/bearing support assembly and the intermediate cylinder, when said bearing support is pivotally mounted along an articulation axis, parallel to the support cylinder, that the bearing support is articulated along a pivot axis to the chocks of the intermediate cylinder as taught by way of example in the document WO 2015/011373 , or even to the bending block capable of supporting the chock of the intermediate cylinder as taught by the document WO 2011/107165 .

More particularly the aim of the present invention is to propose such a method making it possible to avoid the aforementioned interferences throughout the operation of the rolling installation, and whatever the possible configurations of the diameters of the working cylinder and the intermediate cylinder which are respectively caused to decrease in diameter, from a maximum diameter and to a minimum diameter.

Another aim of the invention is to propose, at least according to one embodiment, such a method which ensures optimal cooling of the intermediate cylinder/cylinder contact. work and/or the rolling footprint between the work roll and the strip, throughout the operation of the rolling installation, and whatever the possible configurations of the diameters of the work roll and the intermediate roll .

Another aim of the present invention is to propose a rolling installation as such, suitable for carrying out the process.

Other purposes and advantages will appear during the aforementioned description which is given for information purposes only and which is not intended to limit it.

Also the invention firstly concerns a rolling process adapted to an installation for rolling a strip according to claim 1.

• ladite étape de réajustement consiste à régler la dimension séparant l'axe dudit cylindre soutien et l'axe dudit cylindre d'appui latéral de sorte que la dimension du premier inter-espace est au moins égale une limite inférieure Δmin1 et la dimension du deuxième espace est au moins égale une limite inférieure Δmin2, ladite limite inférieure Δmin1 et la limite inférieure Δmin2 étant par exemple supérieure ou égale à 5 mm ;
• le diamètre du cylindre de soutien étant compris entre un diamètre maximal et un diamètre minimal, procédé dans lequel on définit un diamètre nominal, inférieur au diamètre maximal et supérieur au diamètre minimal et dans lequel :
  • on maintient une première configuration de laminage sans étape de réajustement tant que le diamètre du cylindre de soutien est compris entre le diamètre maximal et le diamètre nominal,
  • on obtient une deuxième configuration de laminage, lorsque le cylindre de soutien est au diamètre nominal, par la mise en oeuvre de ladite étape de réajustement avec réduction de la dimension séparant l'axe dudit cylindre soutien et l'axe dudit cylindre d'appui latéral SSR
  • on maintient ladite deuxième configuration obtenue par ladite étape de réajustement tant que le diamètre du cylindre de soutien est compris entre le diamètre nominal et le diamètre minimal ;
• l'installation de laminage présente au moins des buses d'aspersion permettant l'arrosage par aspersion d'au moins un jet de fluide sur au moins une partie de la bande et au moins une partie d'un desdits cylindres et dans lequel on met en oeuvre une étape d'arrosage comprenant au moins une aspersion directe d'au moins une partie des cylindres de travail, de part et d'autre dudit plan perpendiculaire à la direction de défilement de la bande, lesdites buses étant configurées pour :
  • produire un jet dirigé vers le cylindre de travail, à partir d'au moins un côté du plan perpendiculaire à la direction de défilement, le jet traversant ledit première inter-espace entre le cylindre d'appui latéral et le cylindre de soutien, avant d'atteindre ledit cylindre de travail, et/ou
  • produire un jet dirigé vers le cylindre de travail, à partir d'au moins un côté du plan perpendiculaire à la direction de défilement, traversant l'inter-espace entre la bande et le cylindre d'appui latéral, avant d'atteindre ledit cylindre de travail et/ou la bande ;
• ledit support de paliers est monté fixé de manière amovible sur un bras, de position réglable sur le bras, ledit bras étant lui-même articulé suivant ledit axe d'articulation , parallèle audit cylindre de soutien, assurant le pivotement dudit support de paliers autour dudit axe d'articulation, et dans lequel ledit réglage de la dimension séparant l'axe dudit cylindre soutien et l'axe dudit cylindre d'appui latéral mis en oeuvre lors de l'étape de réajustement est opéré par une étape de modification de la position dudit support de paliers sur le bras ;
• l'installation comprend un moyen de fixation amovible entre ledit support de paliers et ledit bras comprenant un système de détrompeur rainure/clavette, ladite clavette et la rainure portées respectivement par ledit support de paliers et ledit bras, ou inversement, ladite clavette ou la rainure portée par le support de paliers étant désaxée suivant la direction longitudinale du bras, par rapport au plan, parallèle à l'axe cylindre d'appui, passant par la médiane au segment, perpendiculaire au cylindre d'appui latéral, joignant les deux axes des deux rangées de galets, et dans ledit réglage de la dimension séparant l'axe dudit cylindre de soutien et l'axe dudit cylindre d'appui latéral mis en oeuvre lors de l'étape de réajustement est opéré par une étape de retournement dudit support de paliers sur le bras ;
• ledit support de paliers étant monté fixé sur un bras lui-même articulé suivant ledit axe d'articulation parallèle audit cylindre de soutien assurant le pivotement dudit support de paliers autour dudit axe d'articulation, et dans ledit réglage de la dimension séparant l'axe dudit cylindre soutien et l'axe dudit cylindre d'appui latéral mis en oeuvre lors de l'étape de réajustement est opéré par une étape de réglage de la position dudit axe d'articulation par rapport au bras support : par exemple un excentrique est prévu entre l'axe d'articulation et ledit bras , et dans lequel ledit réglage de la dimension séparant l'axe dudit cylindre de soutien et l'axe dudit cylindre d'appui latéral mis en oeuvre lors de l'étape de réajustement est opéré par une étape de mise en rotation dudit excentrique ;
• ledit axe d'articulation, autour duquel est monté le support de paliers, est soutenu et monté sur ledit support d'axe et dans lequel ledit réglage de la dimension séparant l'axe dudit cylindre de soutien et l'axe dudit cylindre d'appui latéral mis en oeuvre lors de l'étape de réajustement est opéré par une étape de modification de la position dudit axe d'articulation sur ledit support d'axe : par exemple, ladite étape de modification de la position dudit axe d'articulation sur ledit support d'axe est obtenue par l'ajout ou le retrait de cales entre le support d'axe et ledit axe d'articulation, ou alternativement, ladite étape de modification de la position dudit axe d'articulation sur ledit support d'axe est obtenue par la rotation d'un excentrique prévu entre ledit axe d'articulation et ledit support d'axe ;
• ledit cylindre de soutien est supporté à ses extrémités par des empoises, et dans lequel ledit réglage de la dimension séparant l'axe dudit cylindre de soutien et l'axe dudit cylindre d'appui latéral mis en oeuvre lors de l'étape de réajustement est opéré par une étape de modification de la position de l'axe dudit cylindre de soutien par rapport aux blocs de cambrage destinés au cambrage du cylindre de soutien ;
• ladite étape de réajustement est mise en oeuvre lors d'une interruption du laminage, après rectification du cylindre de travail et/ou du cylindre de soutien.

According to optional characteristics of the invention, taken alone or in combination:

• said readjustment step consists of adjusting the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder so that the dimension of the first inter-space is at least equal to a lower limit Δmin1 and the dimension of the second space is at least equal to a lower limit Δmin2, said lower limit Δmin1 and the lower limit Δmin2 being for example greater than or equal to 5 mm;
• the diameter of the support cylinder being between a maximum diameter and a minimum diameter, process in which a nominal diameter is defined, less than the maximum diameter and greater than the minimum diameter and in which:
  • a first rolling configuration is maintained without readjustment step as long as the diameter of the support cylinder is between the maximum diameter and the nominal diameter,
  • a second rolling configuration is obtained, when the support cylinder is at the nominal diameter, by implementing said readjustment step with reduction of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder SSR
  • said second configuration obtained by said readjustment step is maintained as long as the diameter of the support cylinder is between the nominal diameter and the minimum diameter;
• the rolling installation has at least spray nozzles allowing watering by spraying at least one jet of fluid on at least part of the strip and at least part of one of said cylinders and in which we put implements a watering step comprising at least one direct spraying of at least part of the working cylinders, on either side of said plane perpendicular to the direction of travel of the strip, said nozzles being configured to:
  • produce a jet directed towards the working cylinder, from at least one side of the plane perpendicular to the direction of travel, the jet crossing said first inter-space between the lateral support cylinder and the support cylinder, before 'reach said working cylinder, and/or
  • produce a jet directed towards the working cylinder, from at least one side of the plane perpendicular to the direction of travel, crossing the interspace between the strip and the lateral support cylinder, before reaching said cylinder work and/or band;
• said bearing support is mounted removably fixed on an arm, of adjustable position on the arm, said arm itself being articulated along said articulation axis, parallel to said support cylinder, ensuring the pivoting of said bearing support around said articulation axis, and in which said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during the readjustment step is carried out by a step of modifying the position of said bearing support on the arm;
• the installation comprises a removable fixing means between said bearing support and said arm comprising a groove/key key system, said key and the groove carried respectively by said bearing support and said arm, or conversely, said key or the groove carried by the bearing support being offset in the longitudinal direction of the arm, relative to the plane, parallel to the support cylinder axis, passing through the median of the segment, perpendicular to the lateral support cylinder, joining the two axes of the two rows of rollers, and in said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during the readjustment step is carried out by a step of turning over said support of bearings on the arm;
• said bearing support being mounted fixed on an arm itself articulated along said articulation axis parallel to said support cylinder ensuring the pivoting of said bearing support around said articulation axis, and in said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during the readjustment step is operated by a step of adjusting the position of said articulation axis by relative to the support arm: for example an eccentric is provided between the articulation axis and said arm, and in which said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented implemented during the readjustment step is carried out by a step of rotating said eccentric;
• said articulation axis, around which the bearing support is mounted, is supported and mounted on said axis support and in which said adjustment of the dimension separating the axis of said support cylinder and the axis of said support cylinder lateral implemented during the readjustment step is carried out by a step of modifying the position of said articulation axis on said axis support: for example, said step of modifying the position of said articulation axis on said axle support is obtained by adding or removing shims between the axle support and said articulation axle, or alternatively, said step of modifying the position of said articulation axle on said axle support is obtained by the rotation of an eccentric provided between said articulation axis and said axis support;
• said support cylinder is supported at its ends by chocks, and in which said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during the readjustment step is operated by a step of modifying the position of the axis of said support cylinder relative to the bending blocks intended for the bending of the support cylinder;
• said readjustment step is implemented during an interruption of rolling, after rectification of the working roll and/or the support roll.

The invention also relates to an installation for rolling a strip according to claim 13.

• l'installation comprend un dispositif configuré pour l'arrosage par aspersion d'au moins un jet de fluide sur au moins une partie de la bande et au moins une partie d'un desdites cylindres comprenant au moins un système de buses avec des buses configurées pour :
  • produire un jet dirigé vers le cylindre de travail, à partir d'au moins un côté du plan perpendiculaire à la direction de défilement, le jet traversant un premier inter-espace entre le cylindre d'appui latéral et le cylindre de soutien, avant d'atteindre ledit cylindre de travail, et/ou
  • produire un jet dirigé vers le cylindre de travail, à partir d'au moins un côté du plan perpendiculaire à la direction de défilement, traversant l'inter-espace entre le cylindre d'appui latéral et la bande, avant d'atteindre ledit cylindre de travail et/ou la bande ;
• le dispositif d'ajustement comprend ledit support de paliers qui est monté fixé de manière amovible sur un bras , de position réglable sur le bras, ledit bras étant lui-même articulé suivant ledit axe d'articulation parallèle au cylindre de soutien assurant le pivotement dudit support de paliers autour dudit axe d'articulation, et dans laquelle le dispositif d'ajustement est configuré pour que le réglage de la dimension séparant l'axe dudit cylindre soutien et l'axe dudit cylindre d'appui latéral est opéré par modification de la position dudit support de paliers sur le bras: par exemple, le dispositif d'ajustement comprend un moyen de fixation amovible entre ledit support de paliers et ledit bras comprenant un système de détrompeur rainure/clavette, ladite clavette et la rainure portées respectivement par ledit support de palier et ledit bras, ou inversement, ladite clavette ou la rainure portée par le support de paliers étant désaxée suivant la direction longitudinale du bras, par rapport au plan, parallèle au cylindre d'appui latéral, passant par la médiane au segment perpendiculaire au cylindre d'appui latéral joignant les deux axes de deux rangées de galets, et dans laquelle le dispositif d'ajustement est configuré pour que ledit réglage de la dimension séparant l'axe dudit cylindre de soutien et l'axe dudit cylindre d'appui latéral est opéré par retournement dudit support de paliers ;
• ledit support de paliers étant monté fixé sur un bras lui-même articulé suivant ledit axe d'articulation parallèle audit cylindre de soutien assurant le pivotement dudit support de paliers autour dudit axe d'articulation, et dans lequel le dispositif d'ajustement est configuré pour que le réglage de la dimension séparant l'axe dudit cylindre de soutien et l'axe dudit cylindre d'appui latéral mise en oeuvre lors de l'étape de réajustement est opéré par réglage de la position dudit axe d'articulation sur le bras ; par exemple ledit dispositif d'ajustement comprend un excentrique prévu entre l'axe d'articulation et ledit bras, et dans lequel le dispositif d'ajustement est configuré pour que ledit réglage de la dimension séparant l'axe dudit cylindre soutien et l'axe dudit cylindre d'appui latéral soit opéré par une étape de mise en rotation dudit excentrique ;
• ledit axe d'articulation autour duquel, est monté le support de paliers, est soutenu et monté sur un support d'axe et dans laquelle le dispositif d'ajustement est configuré pour que le réglage de la dimension séparant l'axe dudit cylindre soutien et l'axe dudit cylindre d'appui latéral est opéré par modification de la position dudit axe d'articulation sur ledit support d'axe par exemple, le dispositif d'ajustement comprend des cales, ledit dispositif d'ajustement configuré pour que la modification de la position dudit axe d'articulation sur ledit support d'axe soit obtenue par l'ajout ou le retrait de cales entre le support d'axe et ledit axe d'articulation, ou alternativement, ledit dispositif d'ajustement comprend un excentrique prévu entre ledit axe d'articulation et ledit support d'axe et dans lequel ledit dispositif d'ajustement est configuré pour que la modification de la position dudit axe d'articulation sur ledit support d'axe soit obtenue par la rotation de l'excentrique.

According to optional characteristics of the invention taken alone or in combination:

• the installation comprises a device configured for watering by spraying at least one jet of fluid onto at least part of the strip and at least part of one of said cylinders comprising at least one nozzle system with configured nozzles For :
  • produce a jet directed towards the working cylinder, from at least one side of the plane perpendicular to the direction of travel, the jet crossing a first inter-space between the lateral support cylinder and the support cylinder, before 'reach said working cylinder, and/or
  • produce a jet directed towards the working cylinder, from at least one side of the plane perpendicular to the direction of travel, crossing the inter-space between the lateral support cylinder and the strip, before reaching said cylinder work and/or band;
• the adjustment device comprises said bearing support which is mounted removably fixed on an arm, with an adjustable position on the arm, said arm itself being articulated along said articulation axis parallel to the support cylinder ensuring the pivoting of said bearing support around said articulation axis, and in which the adjustment device is configured so that the adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder is carried out by modification of the position of said bearing support on the arm: for example, the adjustment device comprises a removable fixing means between said bearing support and said arm comprising a groove/key key system, said key and the groove carried respectively by said support bearing and said arm, or vice versa, said key or the groove carried by the bearing support being offset in the longitudinal direction of the arm, relative to the plane, parallel to the lateral support cylinder, passing through the median to the segment perpendicular to the lateral support cylinder joining the two axes of two rows of rollers, and in which the adjustment device is configured so that said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder is operated by reversing said bearing support;
• said bearing support being mounted fixed on an arm itself articulated along said articulation axis parallel to said support cylinder ensuring the pivoting of said bearing support around said articulation axis, and in which the adjustment device is configured to that the adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during the readjustment step is carried out by adjusting the position of said articulation axis on the arm; for example said adjustment device comprises an eccentric provided between the articulation axis and said arm, and in which the adjustment device is configured so that said adjustment of the dimension separating the axis of said support cylinder and the axis said lateral support cylinder is operated by a step of rotating said eccentric;
• said articulation axis around which the bearing support is mounted, is supported and mounted on an axis support and in which the adjustment device is configured so that the adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder is operated by modification of the position of said articulation axis on said axis support for example, the adjustment device comprises shims, said adjustment device configured so that the modification of the position of said articulation axis on said axis support is obtained by the addition or removal of shims between the axle support and said articulation axle, or alternatively, said adjustment device comprises an eccentric provided between said articulation axle and said axle support and in which said adjustment device is configured so that the modification of the position of said articulation axis on said axis support is obtained by the rotation of the eccentric.

• Les figures 5 à 10 illustrent un premier mode de réalisation de l'invention pour lequel l'étape de réajustement est obtenue par retournement des supports de paliers fixés aux bras, les figures illustrant la cage de laminoir selon différentes configurations de diamètres du cylindre de travail et de diamètres du cylindre intermédiaire, ainsi que selon différentes configurations de la position de l'ensemble support de paliers/ cylindre d'appui latéral sur le bras, à savoir respectivement :
  • une configuration illustrée à la figure 5 pour laquelle le cylindre de travail et le cylindre intermédiaire sont de diamètres maximum (348 mm de diamètre maximal pour le cylindre intermédiaire et 140 mm de diamètre maximal pour le cylindre de travail), et suivant une première position du support de palier sur le bras pour laquelle l'axe des galets de la première rangée est à une distance de 180 mm de l'axe de pivot du bras,
  • deux configuration illustrées respectivement aux figures 6a et 6b pour lesquelles le cylindre de travail est à son diamètre maximal et le cylindre intermédiaire à son diamètre nominal (342,5 mm de diamètre nominal pour le cylindre intermédiaire et 140 mm de diamètre maximal pour le cylindre de travail), la figure 6a illustrant la configuration suivant la première position du support de palier sur le bras pour laquelle l'axe des galets de la première rangée est à une distance de 180 mm de l'axe de pivot du bras, la figure 6b illustrant une autre configuration, après retournement du support de paliers sur le bras, et suivant une deuxième position du support de paliers sur le bras pour laquelle l'axe des galets de la première rangée est à une distance de 172 mm de l'axe de pivot du bras,
  • une configuration illustrée à la figure 7 pour laquelle le cylindre de travail est à son diamètre minimal et le cylindre intermédiaire à son diamètre maximal (330 mm de diamètre maximal pour le cylindre intermédiaire et 140 mm de diamètre minimal pour le cylindre de travail) et suivant la première position du support de palier sur le bras pour laquelle l'axe des galets de la première rangée est à une distance de 172 mm de l'axe de pivot du bras,
  • une configuration illustrée à la figure 8 pour laquelle le cylindre de travail est à son diamètre minimal et le cylindre intermédiaire à son diamètre maximal (348 mm de diamètre maximal pour le cylindre intermédiaire et 120 mm de diamètre minimal pour le cylindre de travail) et suivant la première position du support de palier sur le bras pour laquelle l'axe des galets de la première rangée est à une distance de 180 mm de l'axe de pivot du bras,
  • deux configurations illustrées respectivement aux figures 9a et 9b pour lesquelles le cylindre de travail est à son diamètre minimal et le cylindre intermédiaire à son diamètre nominal (342,5 mm de diamètre nominal pour le cylindre intermédiaire et 120 mm de diamètre minimal pour le cylindre de travail), la figure 9a illustrant la configuration suivant la première position du support de paliers sur le bras pour laquelle l'axe des galets de la première rangée est à une distance de 180 mm de l'axe de pivot du bras, la figure 9b illustrant une autre configuration suivant une deuxième position du support de paliers sur le bras pour laquelle l'axe des galets de la première rangée est à une distance de 172mm de l'axe de pivot du bras,
• La figure 10 est une vue d'une configuration pour laquelle le cylindre de travail est à son diamètre minimal et le cylindre intermédiaire à son diamètre minimal (330 mm de diamètre maximal pour le cylindre intermédiaire et 120 mm de diamètre minimal pour le cylindre de travail) et suivant la deuxième position du support de palier sur le bras pour laquelle l'axe des galets de la première rangée est à 172 mm de l'axe de pivot du bras,
• La figure 11 est une vue illustrant un second mode de réalisation de l'invention pour lequel un excentrique est prévu entre l'axe d'articulation et ledit bras, et dans lequel ledit réglage de la dimension séparant l'axe dudit cylindre soutien et l'axe dudit cylindre d'appui latéral mis en oeuvre lors de l'étape de réajustement est opéré par une étape de mise en rotation dudit excentrique,
• La figure 12 est une vue illustrant un troisième mode de réalisation de l'invention pour lequel ledit réglage de la dimension séparant l'axe dudit cylindre de soutien et l'axe dudit cylindre d'appui latéral mis en oeuvre lors de l'étape de réajustement est opéré par une étape de modification de la position dudit axe d'articulation sur ledit support d'axe constitué ici par les empoises du cylindre de soutien, ladite étape de modification de la position dudit axe d'articulation sur les empoises étant obtenue par la rotation d'un excentrique prévu entre ledit axe d'articulation et les empoises,
• La figure 13 est une vue schématique d'un quatrième mode de réalisation pour lequel l'ensemble cylindre d'appui latéral/support de paliers est articulé via un bras au bloc de cambrage destiné au cambrage du cylindre de soutien, l'ensemble cylindre d'appui latéral/support de paliers étant apte à être déplacé suivant le déplacement du bloc de cambrage et dans lequel ledit réglage de la dimension séparant l'axe dudit cylindre de soutien et l'axe dudit cylindre d'appui latéral mis en oeuvre lors de l'étape de réajustement est opéré par une étape de modification de la position dudit cylindre de soutien par rapport au bloc de cambrage destiné au cambrage du cylindre de soutien, opéré par exemple par retournement à 180° des empoises asymétriques du cylindre de soutien.

The invention will be better understood on reading the description accompanied by the appended figures, representing the invention, among which:

• THE figures 5 to 10 illustrate a first embodiment of the invention for which the readjustment step is obtained by reversing the bearing supports fixed to the arms, the figures illustrating the rolling mill stand according to different configurations of diameters of the working roll and diameters of the roll intermediate, as well as according to different configurations of the position of the bearing support/lateral support cylinder assembly on the arm, namely respectively:
  • a configuration illustrated in figure 5 for which the working cylinder and the intermediate cylinder have maximum diameters (348 mm maximum diameter for the intermediate cylinder and 140 mm maximum diameter for the working cylinder), and following a first position of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 180 mm from the pivot axis of the arm,
  • two configurations illustrated respectively in figures 6a And 6b for which the working cylinder is at its maximum diameter and the intermediate cylinder at its nominal diameter (342.5 mm nominal diameter for the intermediate cylinder and 140 mm maximum diameter for the working cylinder), the figure 6a illustrating the configuration following the first position of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 180 mm from the pivot axis of the arm, the figure 6b illustrating another configuration, after turning the bearing support on the arm, and following a second position of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 172 mm from the axis of arm pivot,
  • a configuration illustrated in Figure 7 for which the working cylinder is at its minimum diameter and the intermediate cylinder at its maximum diameter (330 mm maximum diameter for the intermediate cylinder and 140 mm minimum diameter for the working cylinder) and following the first position of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 172 mm from the pivot axis of the arm,
  • a configuration illustrated in figure 8 for which the working cylinder is at its minimum diameter and the intermediate cylinder at its maximum diameter (348 mm maximum diameter for the intermediate cylinder and 120 mm minimum diameter for the working cylinder) and following the first position of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 180 mm from the pivot axis of the arm,
  • two configurations illustrated respectively in figures 9a And 9b for which the working cylinder is at its minimum diameter and the intermediate cylinder at its nominal diameter (342.5 mm nominal diameter for the intermediate cylinder and 120 mm minimum diameter for the working cylinder), the figure 9a illustrating the configuration following the first position of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 180 mm from the pivot axis of the arm, the figure 9b illustrating another configuration according to a second position of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 172mm from the pivot axis of the arm,
• There Figure 10 is a view of a configuration for which the working cylinder is at its minimum diameter and the intermediate cylinder is at its minimum diameter (330 mm maximum diameter for the intermediate cylinder and 120 mm minimum diameter for the working cylinder) and following the second position of the bearing support on the arm for which the axis of the rollers of the first row is 172 mm from the pivot axis of the arm,
• There Figure 11 is a view illustrating a second embodiment of the invention for which an eccentric is provided between the hinge pin and said arm, and in which said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during the readjustment step is operated by a step of rotating said eccentric,
• There Figure 12 is a view illustrating a third embodiment of the invention for which said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during the readjustment step is carried out by a step of modifying the position of said articulation axis on said axis support constituted here by the chocks of the support cylinder, said step of modifying the position of said axis articulation on the chocks being obtained by the rotation of an eccentric provided between said articulation axis and the chocks,
• There Figure 13 is a schematic view of a fourth embodiment for which the lateral support cylinder/bearing support assembly is articulated via an arm to the bending block intended for bending the support cylinder, the lateral support cylinder assembly /bearing support being able to be moved following the movement of the bending block and in which said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during the step readjustment is carried out by a step of modifying the position of said support cylinder relative to the bending block intended for the bending of the support cylinder, operated for example by reversing 180° of the asymmetrical chocks of the support cylinder.

• un laminage, par une paire de cylindres de travail WR à axes parallèles, de ladite bande prise entre lesdits cylindres de travail WR et défilant entre la paire de cylindres de travail, chacun desdits cylindres de travail ayant au moins une génératrice de contact avec la bande,
• une transmission auxdits cylindres de travail WR d'un effort de laminage sensiblement normal à la bande, par une paire de cylindres de soutien SR, lesdits cylindres de travail WR et lesdits cylindres de soutien SR situés du même côté de la bande étant en contact l'un avec l'autre le long d'une génératrice de soutien commune afin de transmettre ledit effort de laminage,
• un plan perpendiculaire à une direction de défilement de la bande, dans lequel se trouvent au moins une génératrice de contact et les axes desdits cylindres de travail,
• un maintien de chacun desdits cylindres de travail WR par une paire de cylindres d'appui latéraux SSR, situés de part et d'autre dudit plan perpendiculaire, chacun des cylindres d'appui latéral SSR étant, apte à exercer, le long d'une génératrice d'appui dudit cylindre de travail WR, un effort maintenant l'axe du cylindre de travail WR dans une position déterminée par rapport à une cage de laminage de l'installation et auxdits cylindres d'appui latéraux,
• un soutien de chacun des dits cylindres d'appui latéral au moyen de deux rangées formées d'une pluralité de galets G montés côte à côte, permettant de maintenir dans une position déterminée les cylindres d'appui latéraux SSR,
• un soutien de chacune des deux rangées formées de ladite pluralité de galets G, par l'intermédiaire d'un support de paliers BS portant les deux rangées, ledit support de paliers étant monté pivotant suivant un axe d'articulation A1, parallèle au cylindre de soutien SR, porté par un support d'axe AS, tel que les empoises Ep du cylindre de soutien, ou encore les blocs de cambrage MB destinés au cambrage du cylindre de soutien, ledit support d'axe AS étant fixe par rapport à l'axe du cylindre de soutien SR.

Also, the invention relates to a rolling process adapted to an installation for rolling an ST strip comprising the following steps:

• rolling, by a pair of WR working rolls with parallel axes, of said strip taken between said WR working rolls and passing between the pair of working rolls, each of said working rolls having at least one contact generator with the strip ,
• a transmission to said working rolls WR of a rolling force substantially normal to the strip, by a pair of support rolls SR, said working rolls WR and said support rolls SR located on the same side of the strip being in contact 'one with the other along a common support generator in order to transmit said rolling force,
• a plane perpendicular to a direction of travel of the strip, in which there are at least one contact generator and the axes of said working cylinders,
• maintaining each of said working cylinders WR by a pair of lateral support cylinders SSR, located on either side of said perpendicular plane, each of the lateral support cylinders SSR being, capable of exerting, along a support generator of said working roll WR, a force maintaining the axis of the working roll WR in a determined position relative to a rolling stand of the installation and to said lateral support rolls,
• supporting each of said lateral support cylinders by means of two rows formed of a plurality of rollers G mounted side by side, making it possible to maintain the lateral support cylinders SSR in a determined position,
• a support of each of the two rows formed of said plurality of rollers G, via a bearing support BS carrying the two rows, said bearing support being pivotally mounted along an articulation axis A1, parallel to the cylinder of support SR, carried by an axis support AS, such as the chocks Ep of the support cylinder, or the bending blocks MB intended for the bending of the support cylinder, said axis support AS being fixed relative to the SR support cylinder axis.

The rolling installation can be a rolling stand comprising the two working rolls, the two support rolls, and the two support rolls, each support roll being intermediate between said support roll and said work roll, namely a Sexto type rolling mill stand supported laterally.

According to a possibility illustrated following the figures 1 to 12 , said articulation axis A1 around which the bearing support BS is mounted is supported and mounted integrally with two chocks Ep of the support cylinder SR (otherwise the intermediate cylinder IR), the intermediate cylinder assembly IR, bearing supports BS, and two of the lateral support cylinders SSR, on either side of the perpendicular plane forming a self-supporting assembly capable of being introduced into or removed from the cage by sliding of the assembly in the direction of the cylinders, typically called a "cassette" or “insert”, and as known per se from the document WO 2015/011373 .

According to another possibility illustrated in Figure 13 , said articulation axis A1, around which the bearing support BS is pivotally mounted, is supported and mounted on board a bending block MB (in English “ Maes block ” intended for the bending of the intermediate cylinder IR, capable of being moved vertically along the uprights of the cage and as known per se from the document WO 2011/107165 .

During the implementation of the rolling process, the dimensions of a first inter-space It1 defined between the lateral support cylinder SSR and the support cylinder SR and of a second inter-space It2 defined between the strip ST and the SSR side support roll/BS bearing support assembly vary during rolling due to reductions in the diameters of the support roll and the work roll.

Reductions in diameter are caused by wear and grinding of the cylinders. Periodically, and in a known manner, the working rolls and the support rolls are removed from the cage: grinding of the working roll is carried out, and less frequently grinding of the intermediate roll, in order to restore their surface condition.

The inventors note that the mechanism for supporting and positioning the lateral support cylinders with a fixed pivot position relative to the axis of rotation of the intermediate cylinder, and a fixed arm length (as in particular taught by the document WO 2011/107165 or WO 2015/011373 ) presents disadvantages for certain configurations of diameters of the intermediate cylinder and the working cylinder: we thus observe risks of interference between the intermediate cylinder and the lateral support cylinder, or even a risk of obstruction of the opening of passage for the watering and lubricating jets of the intermediate roll/working roll contact, or for blocking the jets for the lubrication of the rolling gap.

Thus and at Figure 3 representing such a state of the art and according to a configuration for which the diameter of the intermediate cylinder is maximum (355 mm) and the diameter of the working cylinder is minimum (120mm), we observe that the watering jets are interrupted (on the right ), the passage opening between the lateral support cylinder (right) and the intermediate cylinder is so restricted that it is no longer crossed by the jet J1, the cooling of the working cylinder and the intermediate cylinder interface /working cylinder being compromised. We still observe a very small clearance of 0.7 mm between the bearing support (right) and the intermediate cylinder, with a risk of mechanical contact.

Likewise at the Figure 4 for which the diameters of an intermediate cylinder at the minimum diameter and a working cylinder at the maximum diameter, we observe that the distance between the metal strip and each bearing support (left) is small, with only 7.3 mm, representing a significant risk of contact.

The invention advantageously makes it possible to avoid such mechanical interference by implementing a readjustment step for which the dimension of said first inter-space It1 and the second inter-space It2 is adjusted by implementing an adjustment of the dimension separating the axis A _SR of said support cylinder SR and the axis A _SSR of said lateral support cylinder SSR defining, with the support cylinder, said first inter-space it1.

This readjustment step can advantageously be implemented during an interruption of rolling, for example simultaneously with an interruption of rolling for rectification of the working roll and/or the support roll.

• le diamètre du cylindre de travail WR est compris entre un diamètre minimal et un diamètre maximal,
• le diamètre du cylindre de soutien SR est compris entre un diamètre minimal et un diamètre maximal.

This readjustment step consists of adjusting the dimension separating the axis of said support cylinder SR and the axis of said lateral support cylinder SSR so that the dimension of the first inter-space It1 is at least equal to a lower limit Δmin1 and the dimension of the second space It2 is at less equals a lower limit Δmin2, whatever the configurations, namely as long as:

• the diameter of the working cylinder WR is between a minimum diameter and a maximum diameter,
• the diameter of the support cylinder SR is between a minimum diameter and a maximum diameter.

This lower limit Δmin1 and this lower limit Δmin2, which may be equal or distinct, may be greater than or equal to 5mm.

THE figures 5 to 10 illustrate the different possible configurations of a Sexto type rolling mill stand supported laterally, with cassette, like the state of the art represented in figures 1 to 4 .

On these figures 5 to 10 , we recognize the support cylinder SR which is the intermediate cylinder IR, and which transmits the rolling force to the working cylinder WR. The SR support cylinder is conventionally hinged at its ends to chocks.

On either side of the clamping plane, each lateral support cylinder SSR is held by two rows of rollers G of a bearing support BS pivotally mounted via an AR arm following the articulation axis A1 to a support axis formed by the chocks of the support cylinder SR. The SR support cylinder with its chocks, the AR arms, the BS bearing supports and the pair of lateral support cylinders form a self-supporting assembly which can be removed when opening the cage, and in a manner known per se of the state of the art.

According to this embodiment, said BS bearing support is mounted removably fixed on an AR arm, with an adjustable position on the arm, said AR arm itself being articulated along said articulation axis A1, parallel to said support cylinder , ensuring the pivoting of said bearing support around said articulation axis A1.

Notably, and according to this embodiment, said adjustment of the dimension separating the axis of said support cylinder SR and the axis of said lateral support cylinder SSR implemented during the readjustment step is carried out by a step modification of the position of said BS bearing support on the AR arm.

More particularly, a removable fixing means can be provided between said BS bearing support and said AR arm comprising a groove/key key system 1, said key and the groove carried respectively by said bearing support BS and said AR arm, or vice versa.

As visible on the figure 5 , said key or the groove carried by the bearing support is significantly offset in the longitudinal direction of the AR arm, relative to the plane, parallel to the axis of the support cylinder, passing through the median Md to the segment, perpendicular to the lateral support cylinder, joining the two axes of the two rows of rollers G.

The adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during the readjustment step is carried out by a step of turning over said BS bearing support on the arm.

This readjustment step carried out by reversing said BS bearing support on the AR arm is illustrated by way of example in figures 9a And 9b .

The two configurations illustrated respectively in figures 9a And 9b are configurations for which the working cylinder is at its minimum diameter and the intermediate cylinder at its nominal diameter (342.5 mm nominal diameter for the intermediate cylinder and 120 mm minimum diameter for the working cylinder).

There figure 9a illustrates the configuration following the first position P1 of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 180 mm from the articulation axis A1 of the arm, while the figure 9b illustrates another configuration according to a second position P2 of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 172 mm from the pivot axis of the arm.

The passage from the first position P1 of the bearing support to the second position P2 of the bearing support is obtained by simple turning 180° of said bearing support BS on the arm, during an interruption in rolling.

This reversal causes a modification of the dimension separating the axis A _SR of said support cylinder SR and the axis A _SSR of said lateral support cylinder SSR defining, with the support cylinder, said first inter-space it1, and in l 'species a reduction in the dimension separating the axis A _SR of said support cylinder SR and the axis A _SSR of said lateral support cylinder SSR (of the figure 9a around the figure 9b ) .

• à la figure 9a, et selon la première position P1 du support de paliers BS sur le bras, le premier inter- espace entre le cylindre d'appui latéral SSR (gauche) et le cylindre de soutien SR est de 17 mm et le premier inter-espace entre le cylindre d'appui latéral SSR (droite) et le cylindre de soutien SR est de 15,1 mm, d'une part, le second inter-espace entre la bande et l'ensemble support de paliers/cylindre d'appui latéral (gauche) est de 8,7 mm et le second inter-espace entre la bande et l'ensemble support de paliers/cylindre d'appui latéral (droite) est de 8,9 mm
• à la figure 9b, et selon la deuxième configuration P2 du support de paliers BS sur la bras le premier inter-espace entre le cylindre d'appui latéral SSR (gauche) et le cylindre de soutien SR est de 10,5 mm, et le premier inter-espace entre le cylindre d'appui latéral SSR (droite) et le cylindre de soutien SR est de 9 mm, d'une part, le second inter espace entre la bande et l'ensemble support de paliers/cylindre d'appui latéral (gauche) est de 18 mm, le second inter espace entre la bande et l'ensemble support de paliers/cylindre d'appui latéral (droite) est de 16,3 mm.

We then observe a readjustment (a modification) of the dimension of said first inter-space It1 and of the second inter-space it2:

• to the figure 9a , and according to the first position P1 of the bearing support BS on the arm, the first interspace between the lateral support cylinder SSR (left) and the support cylinder SR is 17 mm and the first interspace between the side support cylinder SSR (right) and the support cylinder SR is 15.1 mm, on the one hand, the second inter-space between the strip and the bearing support/side support cylinder assembly (left ) is 8.7 mm and the second interspace between the strip and the bearing support/lateral support cylinder assembly (right) is 8.9 mm
• to the figure 9b , and according to the second configuration P2 of the bearing support BS on the arm the first inter-space between the lateral support cylinder SSR (left) and the support cylinder SR is 10.5 mm, and the first inter-space between the lateral support cylinder SSR (right) and the support cylinder SR is 9 mm, on the one hand, the second inter space between the strip and the bearing support/lateral support cylinder assembly (left) is 18 mm, the second interspace between the strip and the bearing support/lateral support cylinder assembly (right) is 16.3 mm.

We note that at this nominal diameter of the support cylinder SR (here in this case equal to 342.5 mm) and while the working cylinder is of minimum diameter (here in this case 120 mm), the most critical case in terms of risks of mechanical interference, it is possible to proceed to the readjustment step, while retaining, before ( figure 9a ) and after ( figure 9b ) the step of readjusting a value of the first inter-space It1 and an inter-space value It2 sufficient to avoid the risk of mechanical interference.

We note that this change to be made by reversing the bearing support when the support cylinder is at its nominal diameter (342.5mm), but the working cylinder is at its maximum diameter (140mm) does not pose any difficulty in that the first inter-space It1 and the second inter-space It2 are of even more comfortable values in terms of risks of mechanical interference, and as visible to figures 6a And 6b .

• la première configuration de laminage (première position P1 du support de paliers sur le bras pour laquelle l'axe des galets de la première rangée est à une distance de 180 mm de l'axe d'articulation A1 du bras) peut être conservé sans risque d'interférence mécanique tant que le diamètre du cylindre de soutien SR est compris entre le diamètre maximal et le diamètre nominal et quel que soit le diamètre du cylindre de travail compris entre le diamètre minimal et le diamètre maximal, et comme plus particulièrement compréhensible des figures 6a et 9a,
• la deuxième configuration de laminage (seconde position P2 du support de paliers sur le bras pour laquelle l'axe des galets de la première rangée est à une distance de 172 mm de l'axe d'articulation A1 du bras) peut être conservé sans risque d'interférence mécanique, tant que le diamètre du cylindre de soutien SR est compris entre le diamètre nominal et le diamètre minimal et quel que soit le diamètre du cylindre de travail compris entre le diamètre minimal et le diamètre maximal, et comme plus particulièrement compréhensible des figures 6b et 9b.

In an understandable way figures 5 to 10 :

• the first rolling configuration (first position P1 of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 180 mm from the articulation axis A1 of the arm) can be retained without risk of mechanical interference as long as the diameter of the support cylinder SR is between the maximum diameter and the nominal diameter and whatever the diameter of the working cylinder between the minimum diameter and the maximum diameter, and as more particularly understandable from figures 6a And 9a ,
• the second rolling configuration (second position P2 of the bearing support on the arm for which the axis of the rollers of the first row is at a distance of 172 mm from the articulation axis A1 of the arm) can be retained without risk of mechanical interference, as long as the diameter of the support cylinder SR is between the nominal diameter and the minimum diameter and whatever the diameter of the working cylinder between the minimum diameter and the maximum diameter, and as more particularly understandable from figures 6b And 9b .

• la comparaison entre la figure 3 (art antérieur) et la figure 8 selon l'invention représentant toutes les deux le cas où le diamètre du cylindre de soutien est maximal, le diamètre du cylindre de travail minimal, montre que les problèmes d'interférence mécanique et d'obstructions de jet sont résolus.
• la comparaison entre la figure 4 (art antérieur) et la figure 10 (selon l'invention) représentant toutes les deux le cas où le diamètre du cylindre de soutien est minimal, le diamètre du cylindre de travail minimal, montre que les problèmes de risque d'interférence mécanique sont diminués.

The problems of mechanical interference and jet obstruction identified in figures 3 And 4 representing the state of the prior art are resolved:

• the comparison between the Figure 3 (prior art) and the figure 8 according to the invention both representing the case where the diameter of the support cylinder is maximum, the diameter of the minimum working cylinder, shows that the problems of mechanical interference and jet obstructions are solved.
• the comparison between the Figure 4 (prior art) and the Figure 10 (according to the invention) both representing the case where the diameter of the support cylinder is minimal, the diameter of the minimum working cylinder, shows that the problems of risk of mechanical interference are reduced.

• on maintient une première configuration de laminage (sans étape de réajustement) tant que le diamètre du cylindre de soutien est compris entre le diamètre maximal et le diamètre nominal,
• on obtient une deuxième configuration de laminage, lorsque le cylindre de soutien est au diamètre nominal, à une tolérance près, par la mise en oeuvre de l'étape de réajustement avec réduction de la dimension séparant l'axe A_SR dudit cylindre de soutien SR et l'axe A_SSR dudit cylindre d'appui latéral SSR,
• on maintient ladite deuxième configuration obtenue par l'étape de réajustement tant que le diamètre du cylindre de soutien est compris entre le diamètre nominal et le diamètre minimal.

Thus and in general and according to an advantageous embodiment, the diameter of the support cylinder SR being between a maximum diameter and a minimum diameter, process in which a nominal diameter is defined, less than the maximum diameter and greater than the minimum diameter and in which :

• a first rolling configuration is maintained (without readjustment step) as long as the diameter of the support cylinder is between the maximum diameter and the nominal diameter,
• a second rolling configuration is obtained, when the support cylinder is at the nominal diameter, within a tolerance, by implementing the readjustment step with reduction of the dimension separating the axis A _SR from said support cylinder SR and the axis A _SSR of said lateral support cylinder SSR,
• said second configuration obtained by the readjustment step is maintained as long as the diameter of the support cylinder is between the nominal diameter and the minimum diameter.

We note that the invention thus makes it possible to considerably reduce the risks of mechanical interference between the strip and the bearing support/lateral support cylinder assembly on the one hand, or even, and between the bearing support/ lateral support cylinder and the support cylinder, on the other hand.

As visible from figures 5 to 10 , and by maintaining the inter-space It1 between the support cylinder and the lateral support cylinder greater than or equal to the value a lower limit Δmin1, the invention still makes it possible to ensure optimized cooling of the support cylinder contact SR / working cylinder by direct spraying of the working cylinder, throughout operation, whatever the diameter of the working cylinder and the diameter of the support cylinder, and without risk of total interruption of the jet during this exploitation.

• produire un jet J1 dirigé vers le cylindre de travail WR, à partir d'au moins un côté du plan perpendiculaire à la direction de défilement, le jet traversant ledit premier inter-espace It1 entre le cylindre d'appui latéral SSR et le cylindre de soutien SR, avant d'atteindre ledit cylindre de travail WR, et/ou
• produire un jet J2 dirigé vers le cylindre de travail WR, à partir d'au moins un côté du plan perpendiculaire à la direction de défilement, traversant l'inter-espace entre la bande et le cylindre d'appui latéral, avant d'atteindre ledit cylindre de travail et/ou la bande.

Advantageously, the rolling installation can thus have at least spray nozzles SN1, SN2 allowing watering by spraying at least one jet of fluid on at least part of the strip ST and at least part of said cylinders and in which method a watering step is implemented comprising at least one direct spraying of at least part of the working cylinders WR, on either side of said plane perpendicular to the direction of travel of the strip, said nozzles SN1, SN2 being configured for:

• produce a jet J1 directed towards the working cylinder WR, from at least one side of the plane perpendicular to the direction of travel, the jet crossing said first inter-space It1 between the lateral support cylinder SSR and the cylinder of support SR, before reaching said working cylinder WR, and/or
• produce a jet J2 directed towards the working cylinder WR, from at least one side of the plane perpendicular to the direction of travel, crossing the inter-space between the strip and the lateral support cylinder, before reaching said working cylinder and/or the strip.

For each working cylinder, direct spraying can thus be implemented on either side of the clamping plane. The SN1 and SN2 nozzles can be carried by the A.R arm and/or the B.S bearing support.

THE figures 5 to 10 show an example for which the readjustment step is carried out by changing the position of the bearing support BS on the arm AR, and in order to modify (adjust) the dimension separating the axis A _SR of said support cylinder SR and the axis A _SSR of said SSR lateral support cylinder.

Other technical solutions are possible without departing from the scope of the invention, and always with the objective of modifying (adjusting) the dimension separating the axis A _SR of said support cylinder SR and the axis A _SSR of said support cylinder. SSR lateral support.

According to another embodiment, said bearing support BS being mounted fixed on an AR arm itself articulated along said articulation axis A1 parallel to said support cylinder ensuring the pivoting of said bearing support around said articulation axis A1, and in said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during the readjustment step is carried out by a step of adjusting the position of said articulation axis A1 on the rear support arm.

For example, an eccentric Ex1 can be provided between the articulation axis A1 and said arm AR, and in which said adjustment of the dimension separating the axis A _SR of said support cylinder SR and the axis A _SSR of said cylinder SSR lateral support implemented during the readjustment step is operated by a step of rotating said eccentric Ex1.

Such an embodiment is illustrated in Figure 11 , respectively illustrating in solid lines and dotted lines the change in position of the arm and the bearing support following two positions of the eccentric Ex1. It can be seen that during the rotation of the eccentric Ex1, the position of the axis A1 remains unchanged, and while the arm AR and the bearing support BS move away from the axis of the support cylinder SR.

According to another embodiment, said articulation axis A1 around which the bearing support BS is mounted is supported and mounted on said axis support AS and in which said adjustment of the dimension separating the axis A _SR from said cylinder is carried out. support SR and the axis A _SSR of said lateral support cylinder SSR implemented during the readjustment step is operated by a step of modification of the position of said articulation axis A1 on said axis support AS.

For example, said step of modifying the position of said articulation axis on said axis support AS is obtained by adding or removing shims between the axis support and said articulation axis (example not illustrated) , or else said step of modifying the position of said articulation axis on said axis support is obtained by the rotation of an eccentric Ex2 provided between said articulation axis A1 and said axis support AS.

This last embodiment with eccentric Ex2 is illustrated in Figure 12 respectively illustrating in solid lines and dotted lines the change in position of the arm and the bearing support following two positions of the eccentric Ex2. According to this schematic example, the support cylinder SR is rotatably mounted on chocks Ep, said hinge pin A1 being fixed at its ends to the two chocks of the support cylinder which constitute the axis support AS. An eccentric Ex2 is provided between each end of the hinge pin A1 and the chock Ep. As visible in the Figure 12 , the rotation of the eccentric Ex2 makes it possible to modify the position of the hinge pin A1 on the pin support AS

Again, and according to a fourth possible embodiment, said support cylinder SR is supported at its ends by chocks Ep, and which process said adjustment of the dimension separating the axis A _SR of said support cylinder SR and the axis A _SSR of said lateral support cylinder SSR implemented during the readjustment step is operated by a step of modification of the position of the axis A _SR of said support cylinder relative to the bending blocks MB intended for the bending of the support cylinder .

For example and according to the embodiment illustrated in Figure 13 , the support cylinder SR rotatably mounted on chocks Ep, each of the chocks being engaged with a bending block MB. Each bearing support BS is mounted on an AR arm articulated along the axis A1 to the axis support AS constituted here by the bending block MB.

We also note that the chocks Ep are asymmetrical, in the sense that they make it possible to obtain two mounting positions of the support cylinder, with offset of the axis A _SR of the support cylinder depending on whether the chock is mounted in a first direction of assembly in the bending block, or in a second direction of assembly, obtained by reversing the chock Ep.

According to this embodiment, the adjustment during the readjustment step is obtained by reversing the chock 180°.

The invention also relates to an installation for rolling an ST strip suitable for implementing the process.

• une paire de cylindres de travail WR à axes parallèles, entre lesquels défile la bande ST chacun desdits cylindres de travail ayant au moins une génératrice de contact avec la bande,
• un plan perpendiculaire à une direction de défilement de la bande, dans lequel se trouvent au moins une génératrice de contact et les axes desdits cylindres de travail WR,
• une paire de cylindres de soutien SR, à axes parallèles au plan de la bande et situés de part et d'autre de ladite bande, lesdits cylindres de soutien et cylindres de travail situés d'un même côté de la bande étant en contact l'un avec l'autre le long d'une génératrice de soutien commune afin de transmettre aux cylindres de travail un effort de laminage sensiblement normal à la bande,
• deux paires de cylindre d'appui latéral à axes parallèles, lesdits cylindres d'une même paire étant situés symétriquement de part et d'autre d'un desdits cylindres de travail, dans un plan parallèle à la bande, afin que chacun des cylindres d'appui latéral SSR d'une même paire soit apte à transmettre le long d'une génératrice d'appui dudit cylindre de travail WR un effort permettant un maintien dans une position déterminée relativement au cylindre de soutien SR,
• un soutien de chacun desdits cylindres d'appui au moyen de deux rangées formées d'une pluralité de galets G d'appui montés côte à côte, permettant de maintenir dans une position déterminée les cylindres d'appui latéral SSR,
• un soutien de chacune des deux rangées formées de ladite pluralité de galets d'appui, par l'intermédiaire d'un support de paliers BS portant les deux rangées de galets, ledit support de paliers BS étant monté pivotant suivant un axe d'articulation A1, parallèle au cylindre de soutien, porté par un support d'axe AS, fixe par rapport à l'axe du cylindre de soutien, tel que les empoises Ep du cylindre de soutien, ou encore les blocs de cambrage MB destinés au cambrage du cylindre de soutien.

Said rolling installation comprises at least one cage comprising:

• a pair of working cylinders WR with parallel axes, between which the strip ST passes, each of said working cylinders having at least one contact generator with the strip,
• a plane perpendicular to a direction of travel of the strip, in which there are at least one contact generator and the axes of said working cylinders WR,
• a pair of support rolls SR, with axes parallel to the plane of the strip and located on either side of said strip, said support rolls and working rolls located on the same side of the strip being in contact with each other one with the other along a common support generator in order to transmit to the working rolls a rolling force substantially normal to the strip,
• two pairs of lateral support cylinders with parallel axes, said cylinders of the same pair being located symmetrically on either side of one of said working cylinders, in a plane parallel to the strip, so that each of the lateral support cylinders SSR of the same pair is capable of transmitting along a support generator of said working cylinder WR a force allowing maintenance in a determined position relative to the cylinder SR support,
• supporting each of said support cylinders by means of two rows formed of a plurality of support rollers G mounted side by side, making it possible to maintain the lateral support cylinders SSR in a determined position,
• a support for each of the two rows formed of said plurality of support rollers, via a bearing support BS carrying the two rows of rollers, said bearing support BS being pivotally mounted along an articulation axis A1 , parallel to the support cylinder, carried by an axis support AS, fixed relative to the axis of the support cylinder, such as the chocks Ep of the support cylinder, or the bending blocks MB intended for the bending of the cylinder Support.

Such an installation comprises, during rolling of the metal strip, a first inter-space It1 defined between the lateral support cylinder SSR and the support cylinder S and a second inter-space It2 defined between the strip ST and the assembly side support roll SSR/bearing support BS likely to vary during rolling due to reductions in diameters of the support roll and work roll caused by wear or grinding of the rolls.

According to the invention, said installation comprises an adjustment device configured to adjust the dimension of said first inter-space It1 and the dimension of the second inter-space It2 by implementing an adjustment of the dimension separating the axis A _SR of said support cylinder SR and the axis A _SSR of said lateral support cylinder SSR defining, with the support cylinder, said first inter-space It1.

• produire un jet J1 dirigé vers le cylindre de travail, à partir d'au moins un côté du plan perpendiculaire à la direction de défilement, le jet traversant un premier inter-espace It1 entre le cylindre d'appui latéral SSR et le cylindre de soutien SR, avant d'atteindre ledit cylindre de travail WR, et/ou
• produire un jet J2 dirigé vers le cylindre de travail, à partir d'au moins un côté du plan perpendiculaire à la direction de défilement, traversant l'inter-espace entre le cylindre d'appui latéral SSR et la bande ST, avant d'atteindre ledit cylindre de travail et/ou la bande.

The installation may comprise a device configured for watering by spraying at least one jet of fluid onto at least part of the strip and at least part of one of said cylinders comprising at least one nozzle system with nozzles SN1, SN2 configured for:

• produce a jet J1 directed towards the working cylinder, from at least one side of the plane perpendicular to the direction of travel, the jet crossing a first inter-space It1 between the lateral support cylinder SSR and the support cylinder SR, before reaching said working cylinder WR, and/or
• produce a jet J2 directed towards the working cylinder, from at least one side of the plane perpendicular to the direction of travel, crossing the inter-space between the cylinder lateral support SSR and the strip ST, before reaching said working cylinder and/or the strip.

According to one embodiment, the adjustment device comprises said bearing support BS which is mounted removably fixed on an AR arm, with an adjustable position on the arm, said arm itself being articulated along said parallel articulation axis to the support cylinder SR ensuring the pivoting of said bearing support BS around said articulation axis. The adjustment device is configured so that the adjustment of the dimension separating the axis A _SR of said support cylinder SR and the axis A _SSR of said lateral support cylinder SSR is carried out by modification of the position of said bearing support BS on the rear arm.

For example, and according to the example of Figures 5 to 15, the adjustment device comprises a removable fixing means between said bearing support and said arm comprising a groove/key key system 1, said key and the groove carried respectively by said bearing support and said arm, or vice versa, said key or the groove carried by the bearing support BS being offset in the longitudinal direction of the arm, relative to the plane, parallel to the lateral support cylinder, passing through the median Md to the segment perpendicular to the lateral support cylinder joining the two axes of two rows of rollers. The adjustment device is configured so that said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder is carried out by inversion of said BS bearing support.

According to another embodiment illustrated for information purposes only in Figure 11 , said BS bearing support being mounted fixed on an AR arm itself articulated along said articulation axis A1 parallel to said support cylinder ensuring the pivoting of said BS bearing support around said articulation axis, and in which the device d The adjustment is configured so that the adjustment of the dimension separating the axis A _SR of said support cylinder SR and the axis A _SSR of said lateral support cylinder SSR is carried out by adjusting the position of said articulation axis A1 on the rear arm.

Said adjustment device may comprise an eccentric Ex1 provided between the articulation axis A1 and said arm AR, said adjustment device being configured so that said adjustment of the dimension separating the axis A _SR from said support cylinder SR and the The axis A _SSR of said lateral support cylinder SSR is operated by a step of rotating said eccentric Ex1.

According to another embodiment illustrated for information purposes only in Figure 12 , said articulation axis A1 around which the bearing support BS is mounted is supported and mounted on an axis support AS and in which the adjustment device is configured so that the adjustment of the dimension separating the axis A _S of said support cylinder SR and the axis A _SSR of said lateral support cylinder SSR is operated by modifying the position of said articulation axis A1 on said axis support AS.

The adjustment device can then comprise shims, said adjustment device being configured so that the modification of the position of said articulation axis on said axis support is obtained by the addition or removal of shims between the support axis and said articulation axis.

Alternatively, said adjustment device comprises the eccentric Ex2 provided between said articulation axis and said axis support AS: said adjustment device is configured so that the position of said articulation axis A1 on said support d is modified. The axis AS is obtained by the rotation of the eccentric Ex2.

NOMENCLATURE

• A1. Articulation axis (between the bearing support BS and the axis support AS),
• A _SR . Support cylinder axis,
• A _SSR . Axis of the side support cylinder
• AR. Arm
• AS. Axle support
• B.S. Bearing support,
• Ep. Empoise
• Ex1, Ex2. Eccentrics
• G. Rollers (bearing support),
• IR. Intermediate cylinder (support cylinder)
• It1. First inter-space between the lateral support cylinder and the support cylinder,
• It2. Second inter-space between the lateral support cylinder/bearing support assembly and the belt.
• J1. First draft,
• J2. Second draft,
• MB. Bending block (English “Maes block”)
• Md. Median
• SR. Support cylinder,
• SSR. Lateral support cylinder
• ST. Band
• WR. Working cylinders,

Claims (13)

1. Rolling method adapted to a mill for rolling a strip (ST), comprising:

   - a rolling, by a pair of working rolls (WR) with parallel axes, of said strip taken between said working rolls (WR) and travelling between the pair of working rolls, each of said working rolls having at least one generatrix of contact with the strip,

   - a transmission to said working rolls (WR) of a rolling force substantially normal to the strip, by a pair of support rolls (SR), said working rolls (WR) and said support rolls (SR) situated on the same side of the strip being in contact with each other along a common support generatrix in order to transmit said rolling force,

   - a plane perpendicular to a direction of travel of the strip, in which the at least one contact generatrix and the axes of said working rolls are situated,

   - holding of each of said working rolls (WR) by a pair of side support rollers (SSR), situated on either side of said perpendicular plane, each of the side support rollers (SSR) being able to exert, along a bearing generatrix of said working roll (WR), a force holding the axis of the working roll (WR) in a given position with respect to a rolling cage of the mill and with respect to said side support rollers,

   - support of each of said side support rollers by means of two rows formed by a plurality of rollers (G) mounted side by side, for holding the side support rollers (SSR) in a given position,

   - a support of each of the two rows formed by said plurality of rollers (G), by means of a bearing support (BS) carrying the two rows of rollers, said bearing support is mounted pivotably by a support arm (AR) on an articulation axis (A1), parallel to the support roll (SR), carried by an axis support (AS), formed by chocks (Ep) of the support roll, or cambering blocks (MB) intended for cambering the support roll, said axis support being fixed with respect to the axis of the support roll (SR),

   and in which method the dimensions of a first interspace (It1) defined between the side support roller (SSR) and the support roll (SR) and a second interspace (It2) defined between the strip (ST) and the assembly consisting of the side support roller (SSR) and the bearing support (BS) vary during rolling because of the reductions in diameters of the support roll and working roll caused by wear and planing of the rolls,

   characterised in that said method comprises a readjustment stepfor which the dimension of said first interspace (It1) and of the second interspace (It2) is adjusted by carrying out an adjustment of the dimension separating the axis (A_SR) of said support roll (SR) and the axis (A_SSR) of said side support roller (SSR) defining, with the support roll, said first interspace (It1), and wherein :

   /1/ according to a first possibility, said bearing support (BS) is fixedly mounted removably on said support arm (AR), with an adjustable position on the support arm, said support arm (AR) itself being articulated on said articulation axis (A1), parallel to said support roll, providing the pivoting of said bearing support about said articulation axis (A1), and wherein said adjustment of the dimension separating the axis of said support roll (SR) and the axis of said side support roller (SSR) implemented during the readjustment step is performed by a step of modifying the position of said bearing support (BS) on the support arm (AR),

   /2/ according to a second possibility, said bearing support (BS) being mounted fixed on said support arm (AR) itself articulated on said articulation axis (A1) parallel to said support roll providing the pivoting of said bearing support about said articulation axis (A1), and wherein said adjustment of the dimension separating the axis of said support roll and the axis of said side support roller implemented during the readjustment step is performed by a step of adjusting the position of said articulation axis (A1) with respect to the support arm (AR),

   /3/ according to a third possibility, said articulation axis (A1), around which the bearing support (BS) is mounted, is supported and mounted on said axis support (AS) and wherein said adjustment of the dimension separating the axis of said support roll and the axis of said side support roller implemented during the readjustment step is performed by a step of modifying the position of said articulation axis (A1) on said axis support (AS),

   /4/ according to a fourth possibility, wherein said support roll (SR) is supported at the ends thereof by chocks (Ep), and wherein said adjustment of the dimension separating the axis of said support roll and the axis of said side support roller implemented during the readjustment step is performed by a step of modifying the position of the axis (A_SR) of said support roll with respect to the cambering blocks (MB) intended for cambering the support roll.
2. Method according to claim 1, wherein said readjustment step consists of adjusting the dimension separating the axis of said support roll (SR) and the axis of said side support roller (SSR) so that the dimension of the first interspace is at least equal to a lower limit Δmin1 and the dimension of the second interspace is at least equal to a lower limit Δmin2, said lower limit Δmin1 and the lower limit Δmin2 being greater than or equal to 5 mm;
3. Method according to any one of claims 1 or 2, wherein the diameter of the support roll (SR) lying between a maximum diameter and a minimum diameter, a method wherein a nominal diameter is defined, smaller than the maximum diameter and larger than the minimum diameter, and wherein:

   - a first rolling configuration is maintained without a readjustment step so long as the diameter of the support roll lies between the maximum diameter and the nominal diameter,

   - a second rolling configuration is obtained, when the support roll is at the nominal diameter, by performing said readjustment step with reduction of the dimension separating the axis (A_SR) of said support roll (SR) and the axis (A_SSR) of said side support roller (SSR),

   - said second configuration obtained by said readjustment step is maintained as long as the diameter of the support roll lies between the nominal diameter and the minimum diameter.
4. Rolling method according to one of claims 1 to 3, wherein the rolling mill has at least spray nozzles (SN1, SN2) allowing watering by spraying of at least one jet of fluid onto at least part of the strip (ST) and at least part of one of said rolls and wherein a watering step is implemented comprising at least one direct spraying of at least part of the working rolls (WR), on either side of said plane perpendicular to the direction of travel of the strip, said nozzles (SN1, SN2) being configured to:

   - produce a jet (J1) directed towards the working roll (WR), from at least one side of the plane perpendicular to the direction of travel, the jet passing through said first interspace (111) between the side support roller (SSR) and the support roll (SR), before reaching said working roll (WR), and/or

   - producing a jet (J2) directed towards the working roll (WR), from at least one side of the plane perpendicular to the direction of travel, passing through the interspace between the strip and the side support roller, before reaching said working roll and/or said strip;
5. Method according to the first possibility of claim 1, wherein the mill comprises a removable means of fixing between said bearing support (BS) and said support arm (AR) comprising a groove/key positive-location system (1), said key and the groove carried respectively by said bearing support (BS) and said arm support (AR), or vice versa, said key or the groove carried by the bearing support being offset in the longitudinal direction of the arm support (AR), with respect to the plane, parallel to the backup-roll axis, passing through the median line (Md) to the segment, perpendicular to the side support roller, joining two axes of the two rows of rollers (G),
   and in said adjustment of the dimensions separating the axis of said support roll and the axis of said side support roller implemented during the readjustment step is performed by a step of turning over said bearing support (BS) on the arm.
6. Method according to the seconde possibility of claim 1, wherein an eccentric (Ex1) is provided between the articulation axis (A1) and said support arm (AR), and wherein said adjustment of the dimension separating the axis of said support roll (SR) and the axis of said side support roller (SSR) implemented during the readjustment step is performed by a step of rotation of said eccentric (Ex1).
7. Method according to the third possibility of claim 1, wherein said step of modifying the position of said articulation axis on said axis support (AS) is obtained by adding or removing shims between the axis support and said articulation axis, or alternatively said step of modifying the position of said articulation axis on said axis support is obtained by rotating an eccentric (Ex2) provided between said articulation axis (A1) and said axis support (AS).
8. Method according to any one of claims 1 to 7, wherein said readjustment step is implemented when rolling is interrupted, after planing of the working roll and/or of the support roll.
9. Mill for rolling a strip (ST) including at least one cage, comprising:

   - a pair of working rolls (WR) with parallel axes, between which the strip (ST) passes, each of said working rolls having at least one generatrix of contact with the strip,

   - a plane perpendicular to a direction of travel of the strip, wherein at least one contact generatrix and the axes of said working rolls (WR) are situated,

   - a pair of support rolls (SR), with axes parallel to the plane of the strip and situated on either side of said strip, said support rolls and working rolls situated on the same side of the strip being in contact with each other along a common support generatrix in order to transmit to the working rolls a rolling force substantially normal to the strip,

   - two pairs of side support rollers with parallel axes, said rolls in the same pair being situated symmetrically on either side of one of said working rolls, in a plane parallel to the strip, so that each of the side support rollers (SSR) in the same pair is able to transmit, along a bearing generatrix of said working roll (WR), a force affording holding in a given position in relation to the support roll (SR),

   - a support for each of said support rollers by means of two rows formed by a plurality of support rollers (G) mounted side by side, for holding the side support rollers (SSR) in a given position,

   - support of each of the two rows formed by said plurality of support rollers, by means of a bearing support (BS) carrying the two rows, said bearing support (BS) being mounted pivotally by a support arm (AR) on an articulation axis (A1), parallel to the support roll, carried by an axis support (AS), fixed with respect to the axis of the support roll, formed by the chocks (Ep) of the support roll, or the cambering blocks (MB) intended for cambering the support roll,

   wherein the mill comprises, during the rolling of the metal strip, a first interspace (It1) defined between the side support roller (SSR) and the support roll (SR) and a second interspace (It2) defined between the strip (ST) and the assembly consisting of side support roller (SSR) and bearing support (BS) liable to vary during rolling because of the reductions in diameters of the support roll and of the working roll caused by wear or planing of the rolls,

   characterised in that it comprises an adjustment device configured to adjust the dimension of said first interspace (111) and the dimension of the second interspace (It2) using an adjustment of the dimension separating the axis (A_SR) of said support roll (SR) and the axis (A_SSR) of said side support roller (SSR) defining, with the support roll, said first interspace (It1), and wherein

   /1/ according to a first possibility, the adjustment device comprises said bearing support (BS) that is fixedly mounted removably on ths support arm (AR), with a position adjustable on the support arm, said support arm being itself articulated on said articulation axis parallel to the support roll (SR) providing the pivoting of said bearing support (BS) about said articulation axis, and wherein the adjustment device is configured so that the adjustment of the dimension separating the axis (A_SR) of said support roll (SR) and the axis (A_SSR) of said side support roller (SSR) is performed by modifying the position of said bearing support (BS) on the support arm (AR),

   /2/ according to a second possibility said bearing support (BS) being mounted fixedly on the support arm (AR) itself articulated on said articulation axis (A1) parallel to said support roll providing the pivoting of said bearing support (BS) about said articulation axis, and wherein the adjustment device is configured so that the adjustment of the dimension separating the axis (A_SR) of said support roll (SR) and the axis (A_SSR) of said side support roller (SSR) implemented during the readjustment step is performed by adjusting the position of said articulation axis (A1) on the support arm (AR)

   /3/ according to a third possibility, said articulation axis (A1) around which the bearing support (BS) is mounted is supported and mounted on an axis support (AS) and wherein the adjustment device is configured so that the adjustment of the dimension separating the axis (A_SR) of said support roll (SR) and the axis (A_SSR) of said side support roller (SSR) is performed by modifying the position of said articulation axis (A1) on said axis support (AS).
10. Mill according to claim 9, comprising a device configured for cooling by spraying at least one jet of fluid on at least part of the strip and at least part of one of said rolls, comprising at least one system of nozzles with nozzles (SN1, SN2) configured to:

    - produce a jet (J1) directed towards the working roll, from at least one side of the plane perpendicular to the direction of travel, the jet passing through a first interspace (It1) between the side support roller (SSR) and the support roll (SR), before reaching said working roll (WR), and/or

    - produce a jet (J2) directed towards the working roll, from at least one side of the plane perpendicular to the direction of travel, passing through the interspace between the side support roller (SSR) and the strip (ST), before reaching said working roll and/or the strip.
11. Mill according to the first possibility claim 9, wherein the adjustment device comprises a removable means of fixing between said bearing support and said support arm comprising a groove/key positive-location system (1), said key and the groove carried respectively by said bearing support and said support arm, or vice versa, said key or the groove carried by the bearing support (BS) being offset in the longitudinal direction of the support arm, with respect to the plane, parallel to the side support roller, passing through the median line (Md) to the segment perpendicular to the side support roller joining two axes of two rows of rollers.
    and wherein the adjustment device is configured so that said adjustment of the dimension separating the axis of said support roll and the axis of said side support roller is performed by turning over said bearing support (BS).
12. Mill according to the second possibility of claim 9, wherein said adjustment device comprises an eccentric (Ex1) provided between the articulation axis (A1) and said support arm (AR), and wherein the adjustment device is configured so that said adjustment of the dimension separating the axis (A_SR) of said support roll (SR) and the axis (A_SSR) of said side support roller (SSR) is performed by a step of rotating said eccentric (Ex1).
13. Mill according to the thid possibility of claim 9, wherein the adjustment device comprises shims, said adjustment device configured so that the modification of the position of said articulation axis on said axis support is obtained by adding or removing shims between the axis support and said articulation axis, or alternatively said adjustment device comprises an eccentric (Ex2) provided between said articulation axis and said axis support (AS) and wherein said adjustment device is configured so that the modification of the position of said articulation axis (A1) on said axis support (AS) is obtained by rotating the eccentric (Ex2).

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