EP3762161A1

EP3762161A1 - Rolling method with a step for adjusting the interspace between the side bearing roller and the support roller

Info

Publication number: EP3762161A1
Application number: EP19716463.5A
Authority: EP
Inventors: Conrad ERNST DE LA GRAETE
Original assignee: Fives DMS SA
Current assignee: Fives DMS SA
Priority date: 2018-03-05
Filing date: 2019-03-04
Publication date: 2021-01-13
Anticipated expiration: 2039-03-04
Also published as: US11654464B2; CN111989170B; FR3078494A1; FR3078494B1; EP3762161B1; CN111989170A; WO2019170994A1; US20200406323A1

Abstract

The invention relates to a rolling method suitable for a strip rolling mill (ST) comprising: - rolling of a strip by means of a pair of working rollers (WR), - transmitting a rolling force to the working rollers by means of a pair of support rollers (SR), - retaining each of the working rollers (WR) by means of a pair of side bearing rollers (SSR), - supporting each of the side bearing rollers by means of two rows formed by a plurality of followers (G) - supporting each of the two rows formed by the plurality of followers (G), by means of a bearing support (BS) supporting the two rows of followers, the bearing support is pivotally mounted along an articulated axis (A1), and wherein the dimensions of a first interspace (It1) defined between the side bearing roller (SSR) and the support roller (SR) and a second interspace (It2) defined between the strip (ST) and the side bearing roller (SSR)/bearing support (BS) assembly vary during the rolling process. According to the invention, the method comprises an adjustment step in which the dimension of the first interspace (It1) and of the second interspace (It2) is adjusted by adjusting the dimension separating the axis (ASR) of the support roller (SR) and the axis (ASSR) of the side bearing roller (SSR) defining, with the support roller, the first interspace (It1).

Description

METHOD OF ROLLING WITH RE-ADJUSTMENT STAGE OF THE INTERSPACE BETWEEN THE SIDE SUPPORT CYLINDER AND THE SUPPORT CYLINDER

The invention relates to a rolling method adapted to a rolling mill of a strip, and to a rolling mill as such.

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

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

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

A Sexto mill comprises two additional cylinders with respect to a Quarto, namely two intermediate cylinders interposed respectively between each working roll and the corresponding support roll, on either side of the metal band: the clamping force of each support cylinder is transmitted to the working cylinder only via the intermediate cylinder, the latter having a generatrix in contact with a generatrix of the support cylinder and a diametrically opposite generatrix in contact with a generatrix of the working cylinder .

In such rolling mills, each support cylinder and each intermediate cylinder, is rotatably mounted at its ends on chocks, by means of bearings, for example bearings or hydrostatic bearings. These chocks are supports that 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 displacement of the chocks of the intermediate rolls. These balancing cylinders allow 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 disassembly of the cylinders. These balancing cylinders can also help to arch the intermediate cylinders. An advantage of a Sexto cage mill is the ability to use smaller diameter work rolls compared to a Quarto cage, resulting in a greater reduction in the thickness of the product to be rolled. the same rolling force.

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

In a Sexto mill called "laterally supported", often the work rolls are not mounted on chocks, but instead provided floating. It is then necessary to maintain their axial position, by means of 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. else of the clamping plane.

For example, document ER 0 121 811 is known, in particular of the embodiment of FIG. 2, such a Sexto type mill which comprises two work rolls, two support rolls and two intermediate rolls interposed respectively between one of the working cylinders and the corresponding support cylinder. In this document, the work rolls, the intermediate rolls and the support rollers are all mounted on chocks.

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

In Figure 6 of this document, there are provided onboard nozzles on the support portion of the rollers, movable relative to the amount of the cage. For this purpose, hoses are used to supply the nozzles with cooling and / or lubrication products, the hoses making it possible to take account of displacements between the mobile support part and the amounts of the cage. These nozzles allow the lubrication and cooling of the rollers and the working roll, at the level of the support zone of the rollers.

No. 4,531,394 discloses another rolling mill design of the Sexto type supported laterally. Such a mill always 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 support cylinders and the intermediate cylinders are mounted at their ends on chocks, while the working rolls are provided floating. Each working cylinder is supported laterally, from 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 work roll, the two corresponding lateral support rollers are integral with the two chocks of said intermediate roll. Each lateral support cylinder and its support rollers are mounted on a support arm which extends between the two chocks of the intermediate cylinder, each support arm being pivotally mounted around a shaft whose ends are integral with the chocks. .

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, commonly called "cassette" or "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 open position of the cage.

Four force distribution beams extend rigidly between the two uprights of the cage, respectively, vis-à-vis each support arm. Each force distribution beam supports a beam, said preload, movable in translation relative to the corresponding force distribution beam, movable towards the interior of the cage in a substantially horizontal direction. Precharge cylinders make it possible to constrain the movable beam in contact with the pivoting support arm in order to precharge the lateral support cylinder on the working cylinder.

In such a mill, the cooling and lubrication of the working roll and the intermediate roll are performed by means of nozzles, respectively marked 73 and 72 in FIG. 2 of US 4,531,394, physically remote from the working roll, located outside G "insert" or "cassette". In Figure 2, these nozzles are secured to the force distribution beam or to the mobile precharge beam. So that the jet can reach the intermediate cylinder, the nozzles, marked 72 are opposite bores through the support arms. In practice and to the knowledge of the inventors, this solution of watering through bores of the support arms would not seem to be retained in the rolling mills implemented industrially.

According to the findings of the inventors, the spray nozzles, identified 73 are unable to properly cool the working roller because they are located too far from it, their jets coming too quickly in interference with the lateral support arms, rollers and rollers. side supports and therefore unable to trace the scroll of the band. On the other hand, according to the findings of the inventors, the nozzles identified 72 are unable to properly lubricate the contact between the working roller and the intermediate cylinder because they are located too far from it. In use, such insert mills have a limited life for the work roll, due to poor cooling.

No. 6,441,636 discloses another design of a laterally supported sexto type mill with "insert" or "cassette". As in the previous document, the intermediate cylinder assembly, chocks of the intermediate cylinder, support arm, (right and left), rollers and lateral bearing cylinders, right and left, form a self-supporting assembly that 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 rolls are mounted on bending blocks. The cylinders of the bending blocks allow, during operation, to bring the intermediate cylinders, in a working position illustrated in Figure 5 of this document, or to move the intermediate cylinders to a position, illustrated in FIG. 4, allowing the withdrawal of the inserts by sliding. These cylinders can also, in operation to arch the intermediate cylinder.

In this document, it is known to supply the bearings of the rollers of the support arms of the insert with lubricant from a source of lubricant. Connecting / disconnecting devices allow, 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 spaced vertically by the bending blocks. This automatic connection / disconnection is advantageous. No additional operation to connect / disconnect the lubricant source is required during maintenance, especially when the inserts are to be removed or inserted into the cage. For this purpose, each connecting device comprises a hollow element 57, designated "plunger", intended to conduct the lubricant, and which allows, in the working position of the intermediate cylinders, as illustrated in FIG. relatively tightly connect the bore of the chock via a joint. This element is movable, 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. mobile and up to the bore of the insert. The lubricant then flows from the bore of the chock, and up to the bearings through the hollow of the shaft, identified 17, on which the support arm is pivotally mounted.

When the intermediate rolls are moved apart by the bending blocks to their retracted position, the travel of the movable element is limited to less than the displacement stroke. bending blocks, thereby ensuring an inter-space between the movable member and the chock, as illustrated in Figure 8 of US 6,041,636. It is then possible to remove the insert, without friction between the chocks and the movable element.

Such a connection / disconnection 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 rolls and the lubrication of the intermediate roll / work roll contact is always carried out by providing nozzles physically away from the rolls.

However, document EP 1 721 685 discloses a sexto type mill laterally, improving the cooling of a working cylinder. This document proposes to improve the rolling mills of the state of the art "cassettes", for which there would be no place to place cooling nozzles closer to the rollers. FIG. 2 illustrates the object of the improvement of the prior art EP 1 721 685.

The rolling mill is now a unidirectional mill (non-reversible) which comprises, upstream, in the direction of travel of the web, a lateral support cylinder, as previously described, supported by a support arm. Downstream, the support arm is devoid of roller or support cylinder. This support cylinder is replaced by a pad called "support pad" which may be bronze or a self-lubricating graphite material, intended to slide on the surface of the working roller, without exerting substantial effort on it. this.

This pad support arm has several nozzles for a coolant that can directly cool the working roller 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 route the lubricant to the roller bearings supporting the lateral support cylinder. This document teaches how to improve the cooling of work rolls. However, this improvement is to the detriment of the support of the working cylinder on one of its sides, removing a lateral support cylinder and replacing it with a pad, the mill then no longer a reversible mill.

EP 2 391 459 discloses a method and a device for watering a rolling plant. This document is more particularly concerned with the watering of the working cylinders each laterally supported by a pair of rolls, and comprising at least one pair of support rollers for transmitting a rolling force. This document is In particular, it wishes to be an improvement of the document EP 1 721 685 previously described, a solution which would remain prohibited to reversing mills.

According to this document, there is provided a direct spray of at least a portion of the working rolls, on either side of said plane perpendicular to the running direction of the strip. According to this document, the nozzles are positioned on the supports of the lateral support cylinders so as 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 US Pat. Nos. 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 the maintenance, by sliding the assembly according to the direction of the cylinders.

The real difficulty in improving the watering of working cylinders in a cassette mill is not placing the spray nozzles in the cassette, but knowing how to feed them with lubricating / cooling fluid, and without increase maintenance time during removal or insertion of the cassette into the roll stand. For example, it is excluded to use hoses between the cassette and the roll stand to feed the nozzles, as these would need to be disassembled and reassembled during removal or insertion of the cassette, which considerably lengthen the time required for these maintenance operations.

As previously described, the document US.6, 041, 636 discloses automatic connection devices allowing, in the working position of the rolls, to connect the lubricant source to the lubrication bores provided in the chocks, and to automatically disconnect the bores when the intermediate cylinders are spaced vertically by the bending blocks. However, such a device can be used only to supply lubricant, or only the roller bearings 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 support arm of the nozzles 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 anteriority is connected to the chocks which requires to route the fluid along a complex path through the hollow shaft and to the lower end of the support arm. This fluid path, complex, from the chock to the support arm, through the hollow shaft, generates significant pressure losses, limiting flow rates. In summary, and according to the state of the art mentioned above, in the reversible mills of the sexto type laterally supported above, with cassettes, the cooling of the working rolls and the intermediate rolls are carried out by means of nozzles placed outside the cassette, physically remote from the working cylinders and intermediate cylinders and whose jets can not reach the working cylinders directly. In this type of rolling mill implemented industrially, it is conventional to place a spray boom, on each side of the clamping plane, embedded on the force distribution beam of the cage and whose jets are directed at the contact between the support cylinder and the intermediate cylinder. According to this arrangement, the lubrication of the working roll is thus obtained, indirectly, by the fact that the intermediate roll has been wet and that this roll carries this lubrication during its rotation by half a turn, to the work roll. . According to the findings of the inventors, this lubrication is insufficient, in particular for the cylinders placed under the band.

In addition, and as the speed of the 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 work roll.

Document WO 2015/011373 of the present Applicant, however, discloses a Cassette Technology of the Type Sexto supported, which provides a noticeable progress in cooling the working rolls, and with respect to the above-mentioned state of the art, in particular of a cassette rolling mill cage.

It is a laterally supported Sexto rolling mill which comprises:

a holding cage comprising two pairs of amounts spaced apart at the two ends of the cage, at least two posts of the same pair defining an access window,

two work rolls, capable of gripping a strip to be rolled, two support rolls, and two intermediate rolls, the support rolls and the intermediate rollers being rotatably mounted at their ends on chocks,

- Lateral support cylinders, able to support laterally the working rolls, each lateral support roll being carried by a support arm, pivotally mounted on an axis,

stress distribution beams extending between the corresponding uprights of each pair, and means for applying a preload force on each support arm intended to engage with one of the support arms at the level of a bearing surface, and comprising at least one preload jack 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 integral with the chocks of one of the intermediate cylinders, each intermediate cylinder, chocks of the intermediate cylinder, lateral bearing cylinders and corresponding support arms forming a self-supporting assembly, called insert (or "cassette"), which can be removed or slidably introduced through the access window during maintenance, in the open position of the cage.

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

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

a conduit of the support arm, intended to channel the fluid, having a feed opening opening on the bearing surface of the support arm intended to engage the means for applying a precharge force,

- A hollow portion, movable relative to the force distribution beam, movable relative to said force distribution beam 8 under the action of said means 9 for applying a precharge force.

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

In the first connection position, as illustrated in FIG. 2 of document WO 2015/011373, the cooling fluid can be channeled from the source to the said at least one marked nozzle 12 (illustrated) or until said at least one marked nozzle 12 '(not shown), via said connection / disconnection device. In the second disconnection position, the means for applying a precharge force are retracted, in the retracted position, said hollow portion being at a distance from the support arm.

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

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 US.6, 041, 636 To reach the nozzle or an insert type 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 substantially limit the pressure drops, and thus to obtain fluid flow rates much higher than those obtained in this state of the art, and thus to substantially improve the cooling of the work rolls by placing nozzles. cooling as close as possible to the lateral support cylinder.

Document WO 2011/107165 also discloses a Sexto-type rolling stand supported laterally with work rolls and intermediate rolls. The rolling stand comprises, according to the example of FIG. 5, lateral support rolls, and more particularly, for each working roll, a first lateral support roll and a second lateral support roll, located on the and else the clamping plane. Each lateral support cylinder is held by two rows of support rollers, the support rollers and the lateral support roll being carried by an arm pivotally mounted around a guide member marked 72 in FIG.

Noticeably, and in this document WO 2011/107165 the support rollers and their support arm are pivotally mounted on the bending block, adapted to support a chock of intermediate cylinder, bending block which is able to move vertically by compared to the amount of the cage. During maintenance, it becomes possible to axially extract the intermediate cylinder, 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 through the support arm.

The invention is more particularly concerned, at least according to one embodiment, with the problem of cooling the work rolls, when each work roll is held laterally, by two rolls of a pair of lateral support rolls arranged from either side of the clamping plane, by direct spraying of the working roll, and as taught by EP 291 459 A1.

Notably, however, the invention is concerned with the resolution of this problem in the case where the two rows of support rollers ensuring the maintenance of each lateral support cylinder is pivotally mounted by means of 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 else to the camber block adapted to support the chock of the intermediate cylinder, embedded in the bending block, as taught by WO 2011/107165.

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

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

FIG. 1 shows such a configuration when the intermediate roll and the working roll are new, namely of maximum diameters, for example 355 mm for the intermediate roll and 140 mm for the work roll according to this example. Figure 4 shows this configuration when the intermediate cylinder and the working cylinder are worn and change, namely minimum diameters, for example 330 mm for the intermediate cylinder and 120 mm for the working cylinder.

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

It is also noted in Figure 1 (or in Figure 4) that it is possible to cool the working cylinder by a direct spray, on either side of the clamping plane of the roll stand: the first jet J1 generated by a first nozzle system, embossed on 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 working cylinder, close to intermediate cylinder contact / working cylinder WR.

a second jet J2, generated by a second nozzle system, embarked on the bearing support, passes through the inter-space between the lateral support cylinder SSR and the metal strip, before reaching directly the working cylinder, or even the metal strip at the level of the rolling right-of-way.

During operation, the surface condition of the working roll and the surface condition of the intermediate roll deteriorate. Periodically, and in known manner, one proceeds to rectifications of the working cylinder, and less frequently to rectifications of the intermediate cylinder, to restore their surface condition. These operations generate a decrease in diameter of the rectified cylinders.

As the diameter decrease of the work roll is thus faster than that of the intermediate roll, the inventors find that the support and position mechanism of the lateral support rolls (with a fixed pivot position relative to the axis of rotation of the intermediate cylinder, and a length of fixed arm) has drawbacks for certain configurations of diameters of the intermediate roll and the working roll: there is thus a risk of interference between the intermediate roll and the lateral support roll (or its bearing support), or a risk of obstruction of the passage opening for the sprinkler and lubrication jets of the intermediate cylinder / work roll contact, or the jets for lubrication of the rolling right-of-way.

Thus, and in FIG. 3, representing a configuration for which the diameter of the intermediate cylinder is maximum (355 mm) and the diameter of the working cylinder is minimal (120 mm), it is observed that the watering jets are interrupted (on the right ), the passage opening between the lateral support cylinder (right) and the intermediate cylinder no longer traversed by the jet Jl, the cooling of the working cylinder and the intermediate cylinder interface / working cylinder being compromised . There is still a very slight clearance of 0.7 mm between the bearing support (right) and the intermediate cylinder, with the risk of mechanical contact.

Similarly, in FIG. 4, for which the diameters of an intermediate cylinder with a minimum diameter and a working cylinder with a maximum diameter, it is observed 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 object of the present invention is to overcome the above-mentioned drawbacks by proposing a rolling method adapted to a rolling mill of a strip making it possible to avoid the aforementioned mechanical interferences between the metal strip and the lateral support cylinder assembly. bearing support, and also mechanical interference between the lateral support cylinder / bearing support assembly and the intermediate cylinder, when said bearing support is pivotally mounted along an axis of articulation, 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 document WO 2015/011373, or to the bending block adapted to support the chock the intermediate cylinder as taught by the document

WO 2011/107165.

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

Another object of the invention is to propose, at least according to one embodiment, such a method which ensures optimum cooling of the contact between the intermediate roll / work roll and / or the rolling grip between the working roll and the strip, throughout the operation of the rolling mill, and whatever the possible configurations of the diameters of the working roll and the intermediate roll.

Another object of the present invention is to propose a rolling installation as such, suitable for the implementation of the method.

Other purposes and advantages will become apparent from the foregoing description which is merely indicative and which is not intended to limit it.

Also the invention relates firstly to a rolling method suitable for a rolling mill of a strip comprising:

a rolling, by a pair of parallel axis working rolls, of said strip taken between said working rolls and moving 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 of a rolling force substantially normal to the strip, by a pair of support rolls, said work rolls and said rolls of support located on the same side of the web being in contact with each other along a common support generator to transmit said rolling force,

a plane perpendicular to a running direction of the strip, in which there are at least one contact generator and the axes of said working rolls,

holding each of said work rolls by a pair of lateral support rollers, located on either side of said perpendicular plane, each of the lateral support rolls being capable of exerting along a generator of support of said working cylinder, a force maintaining the axis of the working roll in a given position relative to a rolling stand of the installation and to said lateral bearing rolls,

a support of each of said lateral support cylinders by means of two rows formed of a plurality of rollers mounted side by side, making it possible to maintain in a given position the lateral support rolls with respect to the roll stand of the installation and said two rows of rollers,

a support of each of the two rows formed of said plurality of rollers, by means of a bearing support bearing the two rows of rollers, said bearing support being pivotally mounted along an axis of articulation, parallel to the cylinder of support, carried by an axis support, such as the chocks of the support cylinder, or the bending blocks for the cambering of the support cylinder, said axis support being fixed relative to the axis of the support cylinder and in which the dimensions of a first inter-space defined between the lateral support cylinder and the support cylinder and a second inter-space defined between the web and the lateral support / support cylinder assembly are made. Bearings vary during rolling due to reductions in diameters of the support roll and the work roll caused by the wear and the grinding of the rolls.

According to the invention, said method comprises a readjustment step for which the dimension of said first inter-space and the second inter-space is adjusted by the implementation of an adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder defining, with the support cylinder, said first inter-space.

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

said readjustment step consists in 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 Amin 1 and the dimension of the second space is at least equal one lower limit Dhiίh2, said lower limit Amin 1 and the lower limit Dhiίh2 being for example greater than or equal to 5 mm;

the diameter of the support roll being between a maximum diameter and a minimum diameter, in which method a nominal diameter is defined, smaller than the maximum diameter and greater than the minimum diameter, and in which:

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

a second rolling configuration is obtained, when the support roll is at the nominal diameter, by implementing said readjusting step with reduction of the dimension separating the axis of said support roll and the axis of said support roll; lateral SSR

said second configuration obtained by said readjustment step is maintained as long as the diameter of the support roll is between the nominal diameter and the minimum diameter;

the rolling installation has at least spray nozzles for spraying at least one fluid jet onto at least a portion of the strip and at least a portion of one of said rolls and in which one implements a watering step comprising at least direct spraying of at least a portion of the working rolls, on either side of said plane perpendicular to the running direction of the strip, said nozzles being configured to:

producing a jet directed towards the working roll, from at least one side of the plane perpendicular to the running direction, the jet passing through said first inter-space between the lateral support roll and the support roll, before to reach said work roll, and / or

producing a jet directed towards the working roll, 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 roll, before reaching said working cylinder and / or tape;

said bearing support is mounted detachably fixed on an arm, of adjustable position on the arm, said arm itself being articulated along said hinge axis, parallel to said support cylinder, ensuring the pivoting of said bearing support around of said articulation axis, and wherein 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 said bearing support on the arm; the installation comprises a detachable fixing means between said bearing support and said arm comprising a groove / key keying system, said key and the groove respectively carried 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 to the segment, perpendicular to the lateral support cylinder, joining the two axes 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 operated by a reversal step of said support bearings on the arm;

said bearing support being mounted fixed on an arm itself articulated along said axis of articulation parallel to said support cylinder ensuring the pivoting of said bearing support around said hinge 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 hinge axis relative to the support arm: for example an eccentric is provided between the axis of articulation and said arm, and wherein 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 performed 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 cylinder from lateral support implemented during the readjustment step is performed by a step of modifying the position of said hinge axis on said axis support: for example, said step of modifying the position of said hinge axis on said axis support is obtained by adding or removing shims between the axis support and said hinge axis, or alternatively, said step of modifying the position of said hinge axis on said axis support is obtained by rotating an eccentric provided between said hinge axis and said axis support;

said support cylinder is supported at its ends by chocks, and wherein 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 for cambering of the support cylinder;

said readjustment step is implemented during an interruption of the rolling, after grinding of the working roll and / or the support roll. The invention also relates to a rolling mill for a band comprising at least one cage comprising:

a pair of parallel-axis work rolls, between which the strip passes each of said work rolls having at least one contact generator with the strip,

a pair of support rollers, 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 one and the same side of the strip being in contact with the strip; with each 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 cylinder with parallel axes, said cylinders of one and the same pair being situated symmetrically on either side of one of said working cylinders, in a plane parallel to the strip, so that each of the cylinders lateral support of the same pair is able to transmit along a bearing generatrix of said working cylinder a force allowing a maintenance in a specific position relative to the support cylinder,

a support of each of said support rolls by means of two rows formed of a plurality of support rollers mounted side by side, making it possible to maintain the lateral support rolls in a determined position,

a support of each of the two rows formed of said plurality of support rollers, by means of a bearing support carrying the two rows, said bearing support being pivotally mounted along an axis of articulation, parallel to the cylinder; support, carried by a support axis, fixed relative to the axis of the support cylinder, such as the chocks of the support cylinder, or the bending blocks for the cambering of the support cylinder, in which the installation comprises, during the rolling of the metal strip, a first inter-space defined between the lateral support cylinder and the support cylinder and a second inter-space defined between the strip and the lateral support cylinder / support assembly. These bearings may vary during rolling due to reductions in the diameters of the support roll and the working roll caused by the wear or the grinding of the rolls.

According to the invention, said installation comprises an adjusting device configured to adjust the size of said first inter-space and the dimension of the second inter-space by setting implementing an adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder defining, with the support cylinder, said first inter-space.

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

the installation comprises a device configured for sprinkling at least one fluid jet onto at least a portion of the strip and at least a portion of one of said rolls comprising at least one nozzle system with nozzles configured for:

producing a jet directed towards the working roll, from at least one side of the plane perpendicular to the running direction, the jet passing through a first inter-space between the lateral support roll and the support roll, before to reach said work roll, and / or

producing a jet directed towards the working roll, from at least one side of the plane perpendicular to the direction of travel, passing through the inter-space between the lateral support roll and the strip, before reaching said working cylinder and / or tape;

the adjustment device comprises said bearing support which is mounted detachably fixed on an arm, of adjustable position on the arm, said arm being itself hinged along said axis of articulation parallel to the support cylinder ensuring pivoting; said bearing support about said hinge axis, and wherein 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 bearing support on the arm: for example, the adjustment device comprises a removable fixing means between said bearing support and said arm comprising a key / groove keying system, said key and the groove respectively carried by said bearing support and said arm, or vice versa, said key or the groove carried by the bearing support being offset according to the longitudinal irection of the arm, with respect 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 overturning said bearing support;

said bearing support being mounted fixed on an arm itself articulated along said axis of articulation parallel to said 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 implemented during the readjustment step is performed by adjusting the position of said axis articulation on the arm; for example, said adjustment device comprises an eccentric provided between the hinge axis and said arm, and wherein 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 hinge pin about which the bearing support is mounted, is supported and mounted on an axle 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 changing the position of said hinge axis on said axis support, for example, the adjustment device comprises shims, said adjustment device configured so that the changing the position of said hinge pin on said axle support either by adding or removing shims between the axle holder and said hinge pin, or alternatively, said adjusting device comprises an eccentric provided between said axis of articulation and said axis support and wherein said adjustment device is configured so that the modification of the position of said axis of articulation on said support of axis is obtained by rotation of the eccentric.

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

FIGS. 5 to 10 illustrate a first embodiment of the invention for which the readjustment step is obtained by inverting the bearing supports attached to the arms, the figures illustrating the rolling stand according to different configurations of diameters of the cylinder of working and diameters of the intermediate cylinder, as well as in different configurations of the position of the bearing support assembly / lateral support cylinder on the arm, namely respectively:

a configuration illustrated in FIG. 5 for which the working roll and the intermediate roll are of maximum diameters (348 mm maximum diameter for the intermediate roll and 140 mm maximum diameter for the working roll), and in a first position 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 respectively illustrated in Figures 6a and 6b for which the working roll is at its maximum diameter and the intermediate roll at its nominal diameter (342.5 mm nominal diameter for the intermediate roll and 140 mm maximum diameter for the cylinder 6a) illustrating the configuration according to 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, Figure 6b showing another configuration, after reversal of the bearing support on the arm, and in 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 pivot axis of the arm,

a configuration illustrated in FIG. 7 for which the working roll is at its minimum diameter and the intermediate roll at its maximum diameter (348 mm maximum diameter for the intermediate roll and 120 mm minimum diameter for the working roll) and according to 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,

a configuration illustrated in FIG. 8 for which the working roll is at its minimum diameter and the intermediate roll at its maximum diameter (348 mm maximum diameter for the intermediate roll and 120 mm minimum diameter for the working roll) and according to 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 respectively illustrated in Figures 9a and 9b for which the working roll is at its minimum diameter and the intermediate roll at its nominal diameter (342.5 mm nominal diameter for the intermediate roll and 120 mm minimum diameter for the roll 9a) illustrating the configuration according to 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, FIG. 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 l72mm from the pivot axis of the arm,

FIG. 10 is a view of a configuration for which the working roll is at its minimum diameter and the intermediate roll at its minimum diameter (330 mm maximum diameter for the intermediate roll and 120 mm minimum diameter for the roll of working) 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,

FIG. 11 is a view illustrating a second embodiment of the invention for which an eccentric is provided between the hinge axis and said arm, and wherein 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,

FIG. 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 step of readjustment is performed by a step of modifying the position of said axis of articulation on said axis support here constituted by the chocks of the support cylinder, said step of modifying the position of said axis of articulation on the chocks being obtained by the rotation of an eccentric provided between said articulation axis and the chocks,

FIG. 13 is a diagrammatic 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 the bending of the support cylinder, the cylinder assembly lateral support / bearing support being able to be moved according to the movement of the bending block and wherein said adjustment of the dimension separating the axis of said support cylinder and the axis of said lateral support cylinder implemented during of the readjustment step is performed by a step of modifying the position of said support cylinder with respect to the bending block intended for the bending of the support cylinder, operated for example by turning 180 ° asymmetrical chocks of the support cylinder.

Also, the invention relates to a rolling method adapted to a rolling mill of an ST band comprising the following steps:

a rolling, by a pair of parallel axis working rollers WR, of said strip taken between said working rolls WR and moving between the pair of working rolls, each of said working rolls having at least one contact generator with the gang,

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

a holding of each of said working rolls WR by a pair of SSR lateral support rollers, situated on either side of said perpendicular plane, each of the SSR lateral bearing rolls being able to exert, along a support generatrix of said working cylinder WR, an effort now the axis of the working roll WR in a given position with respect to a rolling stand of the installation and to said lateral support rolls,

a support of 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 in a given position the SSR lateral support rolls,

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 a hinge axis A1, parallel to the cylinder; support SR carried by an axis support AS, such as the chocks Ep of the support cylinder, or else the bending blocks MB for the bending of the support cylinder, said axis support AS being fixed with respect to G support cylinder axis SR.

The rolling plant may be a rolling stand comprising the two work 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 roll stand of the Sexto type supported laterally.

According to an illustrated possibility according to FIGS. 1 to 12, said hinge axis Al around which the bearing support BS is mounted is supported and mounted integral with two chocks Ep of the support cylinder SR (otherwise the intermediate cylinder IR), the IR intermediate cylinder assembly, BS bearing supports, and two SSR lateral support cylinders, on either side of the perpendicular plane forming a self-supporting assembly adapted to be introduced or removed from the cage by sliding the assembly according to the direction of the cylinders, typically called "cassette" or "insert", and as known per se from WO 2015/011373.

According to another possibility illustrated in FIG. 13, said hinge axis Al, around which the bearing support BS is pivotally mounted, is supported and mounted onboard on a bending block MB (in English "Maes block" intended for cambering the IR intermediate cylinder, able to be moved vertically along the amounts of the cage and as known per se from WO 2011/107165.

During the implementation of the rolling method, the dimensions of a first inter-space It1 defined between the lateral support cylinder SSR and the support cylinder SR and a second inter-space It2 defined between the band ST and the SSR side bearing cylinder / BS bearing support vary during rolling due to reductions in diameters of the support roll and the work roll. The diameter reductions are caused by the wear and the rectifications of the cylinders. Periodically, and in a known manner, the working cylinders and the support rollers are removed from the cage: the work roll is rectified, and less frequently to the rectifications of the intermediate roll, in order to restore their surface condition.

The inventors observe that the support and position mechanism of the lateral support rollers with a fixed pivot position with respect to the axis of rotation of the intermediate roll, and a fixed arm length (as especially taught by the WO document 2011/107165 or WO 2015/011373) has drawbacks for certain configurations of diameters of the intermediate roll and the working roll: there is thus a risk of interference between the intermediate roll and the side support roll, or a risk of obstruction of the passage opening for the sprinkler and lubrication jets of the intermediate cylinder / work roll contact, or obstruction of the jets for lubrication of the rolling right-of-way.

Thus, and in FIG. 3 representing such a state of the art and in a configuration for which the diameter of the intermediate cylinder is maximum (355 mm) and the diameter of the working roll is minimal (l20 mm), it is observed that the jets of watering are interrupted (right), the opening of passage between the lateral support cylinder (right) and the intermediate cylinder is so restricted that it is no longer traversed by the jet Jl, the cooling of the working cylinder and the intermediate cylinder / work roll interface being compromised. There is still a very slight clearance of 0.7 mm between the bearing support (right) and the intermediate cylinder, with the risk of mechanical contact.

Similarly, in FIG. 4, for which the diameters of an intermediate cylinder with a minimum diameter and a working cylinder with a maximum diameter, it is observed 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 size of said first inter-space It1 and the second inter-space It2 is adjusted by the implementation of an adjustment the dimension separating the axis A _S R of said support cylinder SR and the axis A _S SR of said lateral support cylinder SSR defining, with the support cylinder, said first inter-space itl.

This readjustment step may advantageously be implemented during an interruption of the rolling, for example simultaneously with a rolling interruption for grinding the working roll and / or the support roll. This readjustment step consists in 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 Dhiίh 1 and the dimension of the second space It2 is at least equal to a lower limit Dhiίh2, whatever the configurations, namely as long as:

the diameter of the working roll WR is between a minimum diameter and a maximum diameter,

the diameter of the support roll SR is between a minimum diameter and a maximum diameter.

This lower limit Aminl and this lower limit Dhiίh2, which may be equal or distinct, may be greater than or equal to 5mm.

FIGS. 5 to 10 illustrate the various possible configurations of a Sexto-type rolling stand supported laterally with a cassette, like the state of the art shown in FIGS. 1 to 4.

In these FIGS. 5 to 10, the support cylinder SR is recognized which is the intermediate cylinder IR, and which transmits the rolling force to the working roll WR. The SR support cylinder is conventionally articulated at its ends to chocks.

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

According to this embodiment, said bearing support BS is mounted detachably fixed on an arm AR, of adjustable position on the arm, said arm AR being itself hinged along said hinge axis A1, parallel to said support cylinder , pivoting said bearing support about said hinge 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 stage is operated by a step modifying the position of said bearing support BS on the AR arm. More particularly, a removable fixing means may be provided between said bearing support BS and said AR arm comprising a groove / key keying system 1, said key and the groove carried respectively by said bearing support BS and said AR arm, Or vice versa.

As can be seen in FIG. 5, said key or the groove carried by the bearing support is noticeably offset in the longitudinal direction of the arm AR, 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 performed by a step of turning said bearing support BS on the arm.

This readjustment step performed by turning said bearing support BS 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 roll is at its minimum diameter and the intermediate roll at its nominal diameter (342.5 mm nominal diameter for the intermediate roll and 120 mm minimum diameter for the working cylinder).

FIG. 9a illustrates the configuration according to 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 hinge axis A1 of the arm, whereas the FIG. 9b illustrates another configuration along 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 transition from the first position P1 of the bearing support to the second position P2 of the bearing support is obtained simply by reversing 180 ° of said bearing support BS on the arm, during an interruption of the rolling.

This reversal effects a modification of the dimension separating the axis A _S R of said support cylinder SR and the axis A _S SR of said lateral support cylinder SSR defining, with the support cylinder, said first inter-space it1, and in this case a decrease in the dimension separating the axis A _S R of said support cylinder SR and the axis A _S SR of said lateral support cylinder SSR (of Figure 9a to Figure 9b).

We then observe a readjustment (a modification) of the dimension of said first inter-space It1 and the second inter space it2: in FIG. 9a, and according to the first position Pl of the bearing support BS on the arm, the first gap between the lateral support cylinder SSR (left) and the support cylinder SR is 17 mm and the first inter-space between the SSR lateral support cylinder (right) and the SR support cylinder is 15.1 mm, on the one hand, the second inter-space between the strip and the bearing support / cylinder assembly. the lateral (left) support is 8.7 mm and the second inter-space between the band and the bearing support / lateral support cylinder (right) is 8.9 mm

in FIG. 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 band and the bearing support / cylinder assembly Lateral support (left) is 18 mm, the second inter gap between the band and the bearing support assembly / lateral support cylinder (right) is 16.3 mm.

Note that at this nominal diameter of the support cylinder SR (here in this case equal to 342.5 mm) and while the working roll 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, retaining, before (FIG. 9a) and after (FIG. 9b) the readjustment step a value of the first inter-space It1 and a It2 inter-space value sufficient to avoid the risk of mechanical interference.

Note that this change to operate by turning the bearing support when the support cylinder is at its nominal diameter (342.5mm), but that the working cylinder is at its maximum diameter (l40mm) poses no difficulty in that the first inter-space It1 and the second inter-space It2 are even more comfortable values in terms of mechanical interference risks, and as visible in Figures 6a and 6b.

Understandably 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 hinge axis A1 of the arm) can be retained without risk of mechanical interference as long as the diameter of the support roll SR is between the maximum diameter and the nominal diameter and whatever the diameter of the working roll between the minimum diameter and the maximum diameter, and as particularly understandable 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 hinge axis A1 of the arm) can be preserved without risk of mechanical interference, as long as the diameter of the support roll SR is between the nominal diameter and the minimum diameter and whatever the diameter of the work roll between the minimum diameter and the maximum diameter, and as particularly understandable Figures 6b and 9b.

The problems of mechanical interference and jet obstruction identified in FIGS. 3 and 4 representing the state of the prior art are solved:

the comparison between FIG. 3 (prior art) and FIG. 8 according to the invention, both of which represent the case where the diameter of the support roll is maximal, the diameter of the minimum working roll, shows that the interference problems mechanical and jet obstructions are resolved.

the comparison between FIG. 4 (prior art) and FIG. 10 (according to the invention) both representing the case where the diameter of the support roll is minimal, the diameter of the minimum work roll, shows that the problems of risk of mechanical interference are diminished.

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

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

a second rolling configuration is obtained when the support roll is of nominal diameter, with a tolerance, by the implementation of the readjustment step with reduction of the dimension separating the axis A _S R from said roll of SR support and the axis A _S SR of said lateral support cylinder SSR,

said second configuration obtained by the readjustment step is maintained as long as the diameter of the support roll is between the nominal diameter and the minimum diameter.

It should be noted 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 between the bearing support assembly / lateral support cylinder and support cylinder, on the other hand. As shown in FIGS. 5 to 10, and keeping G inter-space Itl between the support cylinder and the lateral support cylinder greater than or equal to the value of a lower limit Amin1, the invention still makes it possible to ensure optimized cooling. of the SR support cylinder / working cylinder by direct spraying of the working cylinder, throughout the operation, regardless of the diameter of the working roll and the diameter of the support roll, and without risk of total interruption of the jet during this operation.

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

producing 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 passing through said first inter-space It1 between the lateral support cylinder SSR and the cylinder SR, before reaching said work 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 inter-space between the strip and the lateral support roll, before reaching said work roll and / or the band.

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

FIGS. 5 to 10 show an example for which the readjustment step is performed 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 _SSR axis A of said lateral support cylinder SSR.

Other technical solutions are conceivable 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 _S SR of said cylinder of SSR lateral support.

According to another embodiment, said bearing support BS being mounted fixed on an arm AR itself hinged along said axis of articulation Al parallel to said support cylinder ensuring the pivoting of said bearing support about said hinge axis A1, and in said setting 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 axis of articulation Al on the support arm AR.

For example, an eccentric Ex1 may be provided between the hinge axis Al and said arm AR, and wherein said adjustment of the dimension separating the axis A _S R of said support cylinder SR and the axis A _S SR of said cylinder SSR lateral support implemented during the readjustment step is performed by a step of rotating said eccentric Exl.

Such an embodiment is illustrated in FIG. 11, respectively showing in full line and dashed line the change of position of the arm and of the bearing support according to two positions of the eccentric Exl. It is found that during the rotation of the eccentric Exl, the position of the axis Al remains unchanged, and while the arm AR and the bearing support BS deviate from the axis of the support cylinder SR.

According to another embodiment, said hinge axis Al around which the bearing support BS is mounted is supported and mounted on said axis support AS and in which method said adjustment of the dimension separating the axis A _{SR of} said cylinder SR support and _SSR axis A of said _SSR lateral support cylinder implemented during the readjustment step is operated by a step of changing the position of said axis of articulation A1 on said AS axis support.

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

This last embodiment with eccentric Ex2 is illustrated in Figure 12 respectively showing solid line and dotted line the change of position of the arm and the bearing support in two positions of the eccentric Ex2. According to this schematic example, the support cylinder SR is rotatably mounted to chocks Ep, said hinge axis Al 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 axis Al and the chock Ep. As shown in FIG. 12, the rotation of the eccentric Ex2 makes it possible to modify the position of the hinge axis Al on the AS axis support

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 SSR lateral support cylinder implemented during the readjustment step is operated by a step of modifying the position of the axis A _S R of said support cylinder relative to the bending blocks MB for the cambering of the support cylinder.

For example and according to the embodiment illustrated in Figure 13, the support roller 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 articulated arm AR following Tax Al to the axis support AS here constituted by the bending block MB.

It is also noted that the chocks Ep are asymmetrical, in that they make it possible to obtain two mounting positions of the support cylinder, with a tax A offset _SR of the support cylinder according to whether the chock is mounted in a first direction. mounting in the bending block, or in a second direction of assembly, obtained by turning the chock Ep.

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

The invention also relates to a rolling installation of an ST band suitable for implementing the method.

Said rolling installation comprises at least one cage comprising:

a pair of parallel axis working rollers WR, between which the band ST passes each of said working rolls having at least one contact generator with the band,

a plane perpendicular to a running direction of the strip, in which there are at least one contact generator and the axes of said working rolls WR,

a pair of support rollers SR, with axes parallel to the plane of the band and located on either side of said band, said support rolls and working rolls situated on one and the same side of the band being in contact with each other; with each other along a common support generator to transmit to the work rolls a rolling force substantially normal to the web,

two pairs of lateral support cylinder with parallel axes, said cylinders of one and the same pair being situated symmetrically on either side of one of said working cylinders, in a plane parallel to the strip, so that each of the cylinders lateral support SSR of the same pair is able to transmit along a bearing generatrix of said working cylinder WR a force allowing a maintenance in a given position relative to the support cylinder SR, a support of 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 bearing cylinders SSR in a given position,

a support of each of the two rows formed of said plurality of support rollers, by means of a bearing support BS carrying the two rows of rollers, said bearing support BS being pivotally mounted along an axis of articulation Al, parallel to the support cylinder, carried by a support axis AS, fixed relative to the axis of the support cylinder, such as the chocks Ep support cylinder, or the bending blocks MB for cambering of the support cylinder.

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

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

The installation may comprise a device configured for sprinkling at least one fluid jet onto at least a portion of the strip and at least a portion of one of said rolls comprising at least one nozzle system with nozzles SN 1, SN2 configured for:

producing 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 inter-space It1 between the lateral support roll SSR and the roll of SR support, before reaching said WR working cylinder, and / or

producing 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 inter-space between the lateral support roll SSR and the band ST, before reaching said work roll and / or the web.

According to one embodiment, the adjustment device comprises said bearing support BS which is mounted detachably fixed on an arm AR, of adjustable position on the arm, said arm being itself hinged along said axis of articulation parallel to the support cylinder SR ensuring the pivoting of said bearing support BS about said hinge axis. The adjustment device is configured so that the adjustment of the dimension separating the axis A _S R of said support cylinder SR and the axis A _S SR of said lateral support cylinder SSR is operated by modifying the position of said support of BS bearings on the AR arm.

For example, and according to the example of Figures 5 to 15, the adjustment device comprises a removable fastening means between said bearing support and said arm comprising a groove / feather keying 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 operated by turning said bearing support BS.

According to another embodiment illustrated for information purposes in FIG. 11, said bearing support BS being mounted fixed on an arm AR itself hinged along said hinge axis Al parallel to said support cylinder ensuring the pivoting of said bearing support BS about said axis of articulation, and wherein the adjustment device is configured so that the adjustment of the dimension separating the axis A _S R of said support cylinder SR and the axis A _S SR of said lateral support cylinder SSR is operated by adjusting the position of said hinge axis A1 on the AR arm.

Said adjustment device may comprise an eccentric Exl provided between the hinge axis A1 and said AR arm, said adjustment device being configured so that said adjustment of the dimension separating the axis A _S R of said support cylinder SR and the axis A _S SR of said lateral support cylinder SSR is operated by a step of rotating said eccentric Exl.

According to another embodiment illustrated for information purposes in FIG. 12, said hinge axis Al 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 _S SR of said lateral support cylinder SSR is operated by modifying the position of said axis of articulation Al on said support of AS axis.

The adjustment device may then comprise shims, said adjustment device being configured so that the modification of the position of said hinge axis on said axis support is obtained by adding or removing shims between the support axis and said hinge axis. Alternatively, said adjustment device comprises the eccentric Ex2 provided between said hinge axis and said AS axis support: said adjustment device is configured so that the position of said hinge axis A1 on said support is modified. AS axis is obtained by the rotation of the eccentric Ex2.

NOMENCLATURE

Al. Hinge pin (between the BS bearing support and the AS axis support),

A _sr . Support cylinder axis,

At _S SR. Axis of the lateral support cylinder

AR. Arms

AS. Axis support

BS. Bearing support,

Ep. Empoise

Ex1, Ex2. eccentrics

G. Rollers (bearing support),

IR. Intermediate cylinder (support cylinder)

Itl. 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. Jl. First throw,

J2. Second throw,

MB. Block of bending (in English "Maes block")

Median

SR. Support cylinder,

SSR. Lateral support cylinder

ST. Gang

WR. Work rolls,

1. key / groove keying system

Claims

2. Claims

A method of rolling adapted to a strip rolling mill (ST) comprising:

a rolling, by a pair of parallel axis working rolls (WR), of said strip taken between said working rolls (WR) and moving between the pair of working rolls, each of said working rolls having at least one generator contact with the band,

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 in the same side of the web being in contact with each other along a common support generator to transmit said rolling force,

holding each of said work rolls (WR) by a pair of lateral support rollers (SSR) situated on either side of said perpendicular plane, each of the lateral support rolls (SSR) being suitable for exerting, along a supporting generatrix of said working cylinder (WR), a force maintaining the axis of the work roll (WR) in a determined position with respect to a rolling stand of the installation and to said rolls of lateral support,

a support of 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 of rollers, said bearing support is pivotally mounted along an axis of articulation (Al), parallel to the support cylinder (SR), carried by an axis support (AS), such as the chocks (Ep) of the support cylinder, or else the bending blocks (MB) intended for cambering the support cylinder, said axis support being fixed relative to the support cylinder axis (SR) and in which method the dimensions of a first inter-space (It1) defined between the lateral support cylinder (SSR) and the support cylinder (SR) and a second inter-space (It2) defined between the belt (ST) and the lateral bearing cylinder (SSR) / bearing support (BS) vary during the rolling in. because of reductions in diameters of the support cylinder and the working cylinder caused by the wear and the grinding of the cylinders s characterized in that said method comprises 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 _S R) of said support cylinder (SR) and the axis (A _S SR) of said lateral support cylinder (SSR) defining, with the support cylinder, said first inter-space (Itl).

The method of claim 1, wherein said readjusting step comprises 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 interstage space is at least equal to a lower limit Amin1 and the dimension of the second space is at least equal to a lower limit Amin2, said lower limit Amin1 and the lower limit Amin2 being greater than or equal to 5 mm.

3. A rolling method according to one of claims 1 or 2 wherein the diameter of the support roller (SR) being between a maximum diameter and a minimum diameter, wherein method defines a nominal diameter less than the maximum diameter and greater than the minimum diameter and in which:

a second rolling configuration is obtained, when the support roll is at the nominal diameter, by implementing said readjusting step with reduction of the dimension separating the axis (A _SR ) from said support roll (SR) and the axis (A _SSR ) of said lateral support cylinder SSR

said second configuration obtained by said readjustment step is maintained as long as the diameter of the support roll is between the nominal diameter and the minimum diameter.

4. The rolling method according to one of claims 1 to 3, wherein the rolling installation has at least spray nozzles (SN1, SN2) for sprinkling-spraying at least one jet of fluid on at least a portion of the strip (ST) and at least a portion of one of said rolls and wherein a sprinkling step is implemented comprising at least direct spraying of at least part of the working rolls ( WR), on either side of said plane perpendicular to the running direction of the strip, said nozzles ((SN1, SN2) being configured to:

producing 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 passing through said first inter-space (It1) between the support cylinder side (SSR) and the support cylinder (SR), before reaching said working cylinder (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 inter-space between the strip and the lateral support roll before reaching said work roll and / or the web.

5. Method according to one of claims 1 to 4, wherein said bearing support (BS) is mounted removably attached to an arm (AR), of adjustable position on the arm, said arm (AR) being itself same articulated along said hinge axis (Al), parallel to said support cylinder, ensuring the pivoting of said bearing support about said hinge axis (Al), and wherein 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 operated by a step of changing the position of said bearing support (BS) on the arm (AR).

6. The method of claim 5, wherein the installation comprises a removable fixing means between said bearing support (BS) and said arm (AR) comprising a key / groove keying system (1), said key and the groove. carried respectively by said bearing support (BS) and said arm (AR), or vice versa, said key or the groove carried by the bearing support being offset in the longitudinal direction of the arm (AR), with respect to the plane, parallel to the support cylinder axis, 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), and in said adjustment of the dimension separating the axis said support cylinder and the axis of said lateral support cylinder implemented during the readjustment step is operated by a step of reversing said bearing support (BS) on the arm.

7. Method according to one of claims 1 to 4, wherein said bearing support (BS) being mounted fixed on an arm (AR) itself hinged along said hinge axis (Al) parallel to said support cylinder ensuring pivoting said bearing support about said hinge axis (Al), 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 hinge axis (Al) relative to the support arm (AR).

The method of claim 7, wherein an eccentric (Ex1) is provided between the hinge axis (Al) and said arm (AR), and wherein 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 operated by a step of rotating said eccentric (Exl).

9. Method according to one of claims 1 to 4, wherein said hinge axis (Al), around which is mounted the bearing support (BS), is supported and mounted on said axis support (AS) and wherein 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 said hinge axis (Al) on said axis support (AS).

The method of claim 9, wherein said step of changing the position of said hinge axis on said axis support (AS) is achieved by adding or removing shims between the axis support and said hinge axis, or alternatively, said step of modifying the position of said hinge axis on said axis support is obtained by the rotation of an eccentric (Ex2) provided between said hinge axis (Al) and said Axis support (AS).

11. The method according to one of claims 1 to 4, wherein said support cylinder (SR) is supported at its ends by chocks (Ep), and wherein 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 (A _SR ) of said support cylinder relative to the camber blocks (MB ) for the bending of the support cylinder.

12. Method according to one of claims 1 to 11, wherein said readjustment step is carried out during an interruption of the rolling, after grinding of the working roll and / or the support roll.

13. A strip rolling mill (ST) comprising at least one cage comprising:

a pair of parallel axis working rolls (WR), between which the strip (ST) moves each of said working rolls having at least one contact generator with the strip,

a plane perpendicular to a running direction of the strip, in which there are at least one contact generator and the axes of said working rolls (WR),

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

two pairs of lateral support cylinder with parallel axes, said cylinders of one and the same pair being situated symmetrically on either side of one of said working cylinders, in a plane parallel to the strip, so that each of the cylinders lateral support device (SSR) of the same pair is able to transmit along a bearing generatrix of said working cylinder (WR) a force allowing a maintenance in a given position relative to the support cylinder (SR), a support of 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 of each of the two rows formed of said plurality of support rollers, by means of a bearing support (BS) carrying the two rows, said bearing support (BS) being pivotally mounted along an axis of articulation (Al), parallel to the support cylinder, carried by an axis support (AS), fixed with respect to the axis of the support cylinder, such as the chocks (Ep) of the support cylinder, or the bending blocks (MB) for cambering the support cylinder in which the installation comprises, during the rolling of the metal strip, a first inter-space (It1) defined between the lateral support cylinder (SSR) and the cylinder of support (SR) and a second inter-space (It2) defined between the belt (ST) and the lateral bearing cylinder (SSR) / bearing support (BS) which may vary during rolling due to the reductions. diameters of the support cylinder and the working cylinder caused by wear or ation of the cylinders, characterized in that it comprises an adjusting device configured to adjust the dimension of said first inter-space (It1) and the dimension of the second inter-space (It2) by the implementation of a adjusting the dimension separating the axis (A _S R) of said support cylinder (SR) and the axis (A _S SR) of said lateral support cylinder (SSR) defining, with the support cylinder, said first inter-space (Itl).

14. Installation according to claim 13 comprising a device configured for sprinkling at least one fluid jet on at least a portion of the strip and at least a portion of one of said cylinders comprising at least one nozzle system. with nozzles (SN1, SN2) configured for:

- producing a jet (Jl) directed towards the working cylinder, from at least one side of the plane perpendicular to the direction of travel, the jet passing through a first inter-space (It1) between the lateral support cylinder ( SSR) and the support cylinder (SR), before reaching said working cylinder (WR), and / or

- producing a jet (J2) directed towards the working roll, from at least one side of the plane perpendicular to the direction of travel, crossing the inter-space between the lateral support roll (SSR) and the strip (ST) before reaching said work roll and / or the web.

15. Installation according to claim 13 or 14, wherein the adjustment device comprises said bearing support (BS) which is mounted removably attached to an arm (AR), of adjustable position on the arm, said arm being even articulated along said axis of articulation parallel to the support cylinder (SR) pivoting said bearing support (BS) around said hinge axis, and in which the adjustment device is configured so that the adjustment of the dimension separating the axis (A _S R) of said support cylinder (SR) and the axis (A _S SR) of said lateral support cylinder (SSR) is operated by modifying the position of said bearing support (BS) on the arm (AR).

16. Installation according to claim 15, wherein the adjustment device comprises a removable fastening means between said bearing support and said arm comprising a key / groove keying 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, and wherein 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 reversal of said bearing support (BS).

17. Installation according to claim 13, wherein said bearing support (BS) being mounted fixed on an arm (AR) itself hinged along said hinge axis (Al) parallel to said support cylinder pivoting said support bracket. bearings (BS) about said hinge axis, and wherein the adjustment device is configured to adjust the dimension separating the axis (A _S R) of said support cylinder (SR) and the axis (A _S SR) of said lateral support cylinder (SSR) implemented during the readjustment step is operated by adjusting the position of said hinge axis (Al) on the arm (AR).

The apparatus of claim 17, wherein said adjustment device comprises an eccentric (Ex1) provided between the hinge axis (Al) and said arm (AR), and wherein the adjustment device is configured to that said adjustment of the dimension separating the axis (A _S R) of said support cylinder (SR) and the axis (A _S SR) of said lateral support cylinder (SSR) is operated by a step of rotating said eccentric (Exl).

19. Installation according to claim 13, wherein said hinge axis (Al) around which is mounted the bearing support (BS), is supported and mounted on an axis support (AS) and wherein the device of adjustment is configured so that the adjustment of the dimension separating the axis (A _S R) of said support cylinder (SR) and the axis (A _S SR) of said lateral support cylinder (SSR) is operated by changing the position of said articulation axis (Al) on said axis support (AS).

20. Installation according to claim 19, wherein the adjustment device comprises wedges, said adjustment device configured so that the modification of the position of said axis of articulation on said axis support is obtained by the addition or removing shims between the axis support and said hinge axis, or alternatively, said adjustment device comprises an eccentric (Ex2) provided between said hinge axis and said axis support (AS) and wherein said adjustment device is configured to change the position of said hinge axis (Al) on said axis support (AS) by rotation of the eccentric (Ex2).