WO2014146792A1

WO2014146792A1 - Adjustment system

Info

Publication number: WO2014146792A1
Application number: PCT/EP2014/000760
Authority: WO
Inventors: Luigino Pozzo
Original assignee: PMP INDUSTRIES SpA
Current assignee: PMP INDUSTRIES SpA
Priority date: 2013-03-22
Filing date: 2014-03-20
Publication date: 2014-09-25
Anticipated expiration: 2015-09-22

Abstract

Adjustment system for adjusting the position of at least one rotation axis around which a first rolling cylinder or a second rolling cylinder of a pair of rolling cylinders comprising hinged mounting elements rotates.

Description

DESCRIPTION

ADJUSTMENT SYSTEM

Technical field

The present invention relates to a rolling station provided with an adjustment system for adjusting the reciprocal position of transmission slots adapted to put in rotation a pair if rolling cylinders according to the characteristics of the pre-characterizing part of claim 1.

The present invention also relates to a rolling mill plant according to the characteristics of the pre-characterizing part of claim 20.

Definitions

In the present description and in the appended claims the following terms must be understood according to the definitions given in the following.

In the present description by the term "bar" one means a generic product of metal material manufactured in the form of a product whose lengthwise development has much greater sizes with respect to the sizes of the section of the product itself measured on a section taken on an orthogonal plane with respect to the straight line defining its lengthwise development. Although in the terminology usually used in the specific sector of rolling one makes a distinction between "bar, "wire", "wire rod" according to the diameter, or, in general, to the sizes in section of the product of metal material, in the present description the term "bar" is meant to comprise the products usually identified by the terms "wire" and "wire rod" as well, that is to say, in general for the aim of the present description, comprising all the metal products obtained through a rolling process which may be wound in the form of bobbins or coils, or cut to an established length, packaged, and made available for final use or for following processing.

By the expression "profile" of a bar one means the shape of the bar along one of its sections orthogonal to its lengthwise development. Although in the description explicit reference is made to bars having a circular profile, by the expression "profile" one also means shapes other than the circular one, such as circular, oval, elliptic, quadrangular, square, hexagonal shape, flat, band or sheet, "L"-shape, "C"-shape, "H"-shape, etc. It will be evident, in the light of the following description, that the present invention is applicable to a profile corresponding to a generic section, with minimum corrections that will be obvious to a person skilled in the art. The term "bar" should be understood as also comprising different shapes in section as in the mentioned examples or other shapes suitable to be obtained by rolling.

In general one will use the expression "oblong metal material" to indicate said bars of any size in section, of any profile.

By the expression "rolling" one aims at indicating both hot rolling processes and cold rolling processes and by "rolled product" or "oblong metal material" one means a product resulting from rolling, both hot rolling and cold rolling.

The expressions roll/s and/or cylinder/s must be understood as substantially equivalent, as they are rotating elements of a cylindrical shape intended for the mechanical working of the rolled product, which mechanically work the rolled product. The rolled product is made to advance through a pair of rotating rollers or cylinders to undergo the mechanical deformation intended to progressively reduce the thickness of the rolled product by means of a following passage in one or more rolling stations. Although in the described embodiment the rollers or cylinders are shown as having a flat perimeter surface, by the expression rollers or cylinders one also means to include rollers or cylinders in which a first cylinder is provided with at least one first semi-channel and a second cylinder is provided with at least one second semi-channel, the reciprocal placing side-by-side of the cylinders causing the reciprocal placing side-by-side of the at least one first semi-channel and the at least one second semi-channel whose ensemble constitutes at least one rolling channel intended for the passage of the rolled product to be worked between said cylinders.

Prior art

The oblong metal material in the form of bars is generally obtained from a production line that by means of rolling or extrusion processes brings about some thermo-mechanical deformations on the metal material itself for the purpose of obtaining a bar with a determinate profile and with determinate sizes in section.

The production line generally comprises an initial portion of intermediate forging in which the oblong metal material of large sizes, usually indicated with billets, undergoes some initial treatments of thermo-mechanical deformation to turn it from a quadrangular section shape into an essentially round section shape. Afterwards, the production line includes an intermediate portion in which the oblong metal material generally, but not necessarily, undergoes successive thermo-mechanical deformations that turn it in sequence from essentially round section shapes into essentially ovoid section shapes with a progressive reduction in the size in section and extension of the oblong metal material. Finally, the production line includes one or more finishing portions intended to provide the oblong metal material with the final shape and sizes in section, if necessary with further working processes intended to obtain ribs or markings, division of the oblong metal material into two portions by means of "split lines", etc. Each portion of the production line includes one or more working stations and in each of the working stations a working phase of the oblong metal material occurs, that is to say, a thermo-mechanical transformation. For example in a first working station of the intermediate portion of the production line there may be a deformation of the oblong metal material from an essentially round section shape to an essentially ovoid section shape with a reduction in the sizes in section, while in a second working station downstream of the first working station according to the direction of advancement of the material on the line there may be a deformation of the oblong metal material from an essentially ovoid section shape to an essentially round section shape with a reduction in the sizes in section. The process continues in the sequence of working stations until obtaining an oblong metal product with a determinate size or surface area in section and a determinate profile, which can be, for example, circular, ovoid or elliptic, quadrangular, hexagonal, "L"-shaped, "C"-shaped, etc.

The working stations generally include rolling stands with a vertical axis and with a horizontal axis. The rolling stands with a vertical axis include a pair of working cylinders whose rotation axis is on a vertical axis. The rolling stands with a horizontal axis include a pair of working cylinders whose rotation axis is on a horizontal axis. In general the oblong metal material is worked thermo-mechanically within a working groove obtained by approaching the two working cylinders, wherein a first semi-portion of the working groove is obtained on a first cylinder and a second semi-portion of the working groove is obtained on a second cylinder. For example, in the case of a rolling stand that produces an oblong metal material with a round section, on the first cylinder a first groove portion of an essentially semicircular shape is obtained and on the second cylinder a second groove portion of an essentially semicircular shape is obtained, which is symmetrical with respect to the first groove portion present on the first cylinder. Although in the present description and in the enclosed figures reference is mainly made to a configuration relating to a horizontal rolling stand, the present invention is also applicable to the case of rolling stands with a vertical axis, with minimum and obvious adaptations that will be immediately clear to those skilled in the art.

In the rolling lines of more recent technology, the rolling stands are made up of a fixed part that constitutes the working station and a removable and interchangeable part, called cartridge, which includes a supporting structure of the cylinders that are pivotally supported by means of support and rotation bearings, the cartridge further including mechanical control means for the change in the reciprocal distance or distance between centres between the two cylinders, that is to say, for the change in the opening or gap of the rolling channel. The same cartridge can be equipped both as a cartridge for equipping rolling stands with a horizontal axis and as a cartridge for equipping rolling stands with a vertical axis, by means of the ninety-degree rotation of the body of the cartridge. The structure of the working lines without cartridges is similar except for the presence of a supporting removable and interchangeable part of the working cylinders. The present invention, although referred to the solution of rolling mill plants with removable and interchangeable cartridges, is applicable to both solutions.

In prior art the rolling cartridges (9) are operated by means of a control system (Fig. 34) made up of one single AC electric motor (25) with variable speed, operated by means of inverters, which usually has a maximum speed of 2000 rpm, a toothed joint (26) connecting the motor and the reduction gear, a speed reducer with two output shafts (27) with parallel or orthogonal axes, the two output shafts rotating mechanically synchronized. The transmission to the rolling cartridge occurs by means of a pair of adapters (28) generally of the Cardan type, each of which is connected to a respective rolling cylinder, namely a first rolling cylinder (31) and a second rolling cylinder (44). The adapters (28) are associated with an adapters supporting device (29) to realize the coupling with a rolling cartridge (9), which is provided with the first rolling cylinder (31) and with the second rolling cylinder (44). The first rolling cylinder (31) and the second rolling cylinder (44) are connected to the rolling cartridge (9) through the linings, two cylinders adjustment reduction gears (30). The coupling between each cylinder (31 , 44) and the corresponding adapter (28) occurs by means of a hub or a flange.

During the rolling of the oblong metal material, the rolling channel present on the rolling cylinders (31 , 44) wears out more or less rapidly depending on the type of rolled material and on other process parameters. Following the wear, the rolling channel progressively widens giving rise to an increase in the size in section of the oblong metal material. In that case it is possible to compensate at least partially for the wear of the channel by adjusting the distance between the first rolling cylinder (31) and the second rolling cylinder (44).

In some prior art solutions the rolling cylinders are applied to the frame of the cartridge by means of four or more screw tie-rods with transmissions in order to be able to obtain a symmetrical adjustment with respect to the rolling axis. Furthermore, some solutions provide a fine adjustment of the distance between the first rolling cylinder (31) and the second rolling cylinder (44) to compensate for the wear of the rolling channel. Such fine adjustment occurs by means of screw pressure devices acting both on the linings of the first cylinder and on the linings of the second cylinder, with the interposition between the linings of spring and/or hydraulic spacing means for the balancing of the cylinders.

In some prior art solutions the adjustment of the distance between the cylinders occurs by means of gear boxes having the purpose of enabling the correct adjustment of the distance by acting symmetrically on both sides of a same cylinder and/or symmetrically on both cylinders with respect to the rolling axis of the rolling line, which is a fixed axis.

In some prior art solutions the adjustment of the reciprocal position of the cylinders occurs by acting on the supporting bushes of said cylinders.

In order to compensate for such adjustment it is necessary to use universal joints to compensate for the change in the distance between the rolling cylinders (31 , 44) as well as for the change in the rolling channel. In fact, when a rolling channel is so worn out that one can no longer compensate for its wear, it is generally possible to resort to an additional rolling channel obtained on the same pair of rolling cylinders (31 , 44), next to the one subject to wear. This operation occurs by shifting the rolling cartridge in order to drive the new rolling channel in correspondence with the rolling line of the rolling mill plant, which is fixed. In the case of the horizontal rolling stands this occurs by translating the rolling cartridge horizontally, while in the case of the vertical rolling stands this occurs by translating the rolling cartridge vertically. The cylinders (31 , 44) must be replaced periodically and, to facilitate and fasten the change operation, the whole stand can be disengaged by being moved back, creating the conditions in which the whole rollers unit is extractable. In the case of the removable cartridges, on the other hand, they can be rapidly replaced as they are mobile on a system of rails, in such a way as to position in their place a cartridge already prearranged with the new cylinders. The connection between the cylinder neck and the hub of the universal joint is made by means of a shape coupling that is loose in such a way as to allow for the quick fitting of the cylinder on the hub. The hubs in this phase are supported by a mechanical device during the phase of change of the cylinders. As observed, the rolling cylinders can have several channels and, in order to be able to drive the desired rolling channel in correspondence with the rolling line of the plant, which is fixed, the flange holding carriage, too, must be mobile, horizontally in the case of the horizontal stands and vertically in the case of the vertical stands. The above applies to channels, but this reasoning must be extended also to other shapes and to the use of other rolls of different shapes including cylindrical shapes without rolling channels.

Closest prior art documents which are relative to a rolling mill stand adapted to receive a rolling cartridge include patent applications US5941 1 15, US421001 1 , US4019360, RU2177846.

The Patent Application US5941 115 describes a rolling train which includes rolling stands which are provided with a drive side for the connection to drives by means of adapters or transmission shafts.

The Patent Application US4210011 describes an apparatus for the rolling of rod or light- section steel in which rolls are driven by means of adapters or transmission shafts connected to drives which are installed laterally with respect to the rolling line and the rolling stand.

The Patent Application US4019360 describes a wire rod rolling mill which has a plurality of rolling stands with individual drive shafts connected to at least one main drive shaft through respective couplings which are selectively disengagable to interrupt the drive of the corresponding roll stand.

The Patent Application RU2177846 describes a single-strand modular rolling mill for rolling elongated products in which the rolling mill includes gear mechanisms mounted removed out of rolling line for providing intervals in the whole rolling line and in which each gear mechanism is joined with a drive by means of adapters or transmission shafts.

The Patent Application DE 10 2011 018874 describes an arrangement of a cartridge with two rolls with an adjustment device for adjusting the distance between the rolls in which each of the two rolls is supported at each of the two longitudinal ends by a respective supporting block provided with hinged rigid levers that connect the supporting block of one of the two rolls with the supporting block of the other of the two rolls.

The Patent Application US 4156453 describes a supporting cartridge of two rolls mounted on a rocker structure and adapted to be used in a continuous casting plant as an extraction stand and if necessary as a reduction stand of the section of the material cast in the continuous casting plant. The Patent Application EP 1125648 describes a roll cartridge comprising: a support structure adapted to be fixed at a selected location along a rolling line in which the rolling cylinders are hinged to enable a rotation movement along an axis parallel to the rotation axis of the rolling cylinders.

The Patent Application DE 3317635 describes a hot rolling mill plant for progressively reducing the thickness of the rolled material in which the rolling cylinders are mounted in an adjustable symmetrical way by means of rockers and controlled hydraulic adjustment devices.

Problems of the prior art

As regards the adjustment of the distance between the cylinders, the prior art systems based on the coupling by means of screws and transmissions for the coordination of the movement of the two cylinders and/or for the coordination of the movement of the two ends of a same cylinder have many drawbacks with respect to the realization of the adjusting threads and in the coupling with threaded tie-rods. In addition to the complexity of the adjustment, with high costs, further problems derive from the positioning of the tie- rods which is necessarily made in end positions of the cartridge and which are therefore subject to heavy stresses also due to their spaced positioning with respect to the zones in which the rolling efforts are transmitted, obtaining anomalous distributions of the efforts with consequent lower reliability or need for oversizing.

Further drawbacks of the use of adjustments by means of threaded systems derive from the working environment that is much exposed to dirt and deposits of metal scales and that can lead to the jamming of the threaded couplings making difficult or preventing the adjustment.

The prior art solutions providing an adjustment of the reciprocal position of the cylinders acting on the supporting bushes of said cylinders, although apparently looking simpler, are actually very expensive from the point of view of construction because the working and the couplings must be very precise and furthermore the adjustment must occur with greater attention with respect to the other systems to obtain the correct positioning of the cylinders with respect to the rolling line.

As regards the rolling stations, the prior art solutions are particularly bulky to the extent that the rolling stands need considerable foundation works also considering the overall weight of the supporting structures of the rolling stands in which the rolling cartridges are inserted. As a consequence, also a plant with a reduced number of rolling passages needs a large space for its realization.

Furthermore, each rolling stand houses one single motor that, through a system of joints and reduction gears, controls both rolling cylinders installed on the cartridge, the motor having to be necessarily a motor of large sizes to be able to control both rolling cylinders and bear the rolling effort induced by the rolled product.

The mechanical transmission that is used to control the two rolling cylinders is complex and heavy.

Furthermore, also the fastening of the rolling cylinders onto the structure of the cartridge is complex, as well as the adjustment of the distance between the first rolling cylinder (31) and the second rolling cylinder (44).

Aim of the invention

The aim of the present invention is to provide a simplified adjustment system for adjusting the reciprocal distance between the rolling cylinders of a rolling stand or of a rolling cartridge.

A further aim of the present invention is to provide a rolling stand or a rolling cartridge with a simplified adjustment of the distance between the rolling cylinders.

A further aim of the present invention is to provide a rolling station with a simplified mechanical transmission between the driving means of the rotation of the rolling cylinders and the rolling cylinders or rolls themselves that can be adjusted correspondingly to the adjustment of the distance between the rolling cylinders.

Concept of the invention

The aim is achieved by the characteristics of the main claim. The sub-claims represent advantageous solutions. Advantageous effects of the invention

The solution according to the present invention, by the considerable creative contribution the effect of which constitutes an immediate and important technical progress, presents various advantages.

With reference to the rolling cartridge or rolling stand of the invention, the solution according to the present invention allows to obtain a simple and fast adjustment of the distance between the rolling cylinders of the cartridge.

Furthermore, by the solution according to the present invention it is possible to reduce the overall size of the rolling cartridge.

Advantageously, the adjustment of the reciprocal distance between the cylinders does not occur with screw systems, which are easily subject to jamming due to dirt or deformation.

Further advantageously, the solution according to the present invention enables an easy and fast symmetrical adjustment of the position of the rolling cylinders, allowing to maintain a rolling axis of the cartridge always coincident with the rolling axis of the rolling line.

Furthermore, in the solution according to the present invention maintenance operations are simplified.

With reference to the rolling station of the invention, the solution according to the present invention also allows to obtain a corresponding simple adjustment of the transmission of the rolling station for the purpose of obtaining a correspondence with the adjustment of the distance between the rolling cylinders of the cartridge.

The solution according to the present invention allows to reduce the number of components necessary for the transfer of the torque from the driving means of the rotation of the cylinders and the cylinders themselves also allowing to make the structure more compact.

Furthermore, the solution according to the present invention also allows to obtain a reduction in the weight of the machines and of the structures used, with advantages both in terms of the cost of the machines, and in terms of their transport, for example during the construction of a rolling mill plant. Moreover, the number of the moving parts is considerably reduced.

Furthermore, the solution according to the present invention also allows to reduce the costs of the foundations and to create a much more compact layout of the rolling mill plant, allowing to construct rolling mill plants with the same or better performances with respect to those of the prior art but with smaller overall dimensions and required space on the ground.

Furthermore, the present invention also allows to obtain rolling stations with greater performances and greater possibilities of control of the rolling process.

Furthermore, the solution according to the present invention advantageously allows for the application to existing plants as well, for example in an update phase of the latter or of part of the latter, in which case it is possible for example to maintain the existing rolling cartridges and update the rolling stations, reducing the space required by the rolling stations into which the existing cartridges are inserted, being able to use this space for other equipment.

Alternatively, one can also use the rolling cartridges of the present invention on existing rolling mill plants.

Finally, one can also provide new rolling mill plants comprising both the rolling stations of the present invention and the rolling cartridges of the present invention.

Finally, the present solution allows to obtain greater functionality, lower power consumption due to reduced friction and greater operating efficiency.

Description of the drawings

In the following a solution is described with reference to the enclosed drawings to be considered as a non-exhaustive example of the present invention in which:

Fig. 1 schematically represents a perspective view showing the coupling between a rolling station and a rolling cartridge made in accordance with the present invention relative to a rolling stand with a horizontal axis. Fig. 2 schematically represents the rolling station and the rolling cartridge of Fig. 1 according to a different point of view.

Fig. 3 schematically represents a front three-quarter view of the rolling station of Fig. 1. Fig. 4 schematically represents a front view of a rolling cartridge made in accordance with the present invention.

Fig. 5 schematically represents a back three-quarter view of the rolling cartridge of Fig. 4. Fig. 6 schematically represents a view of the rolling cartridge of Fig. 4 according to the point of view indicated by "A" in Fig. 4.

Fig. 7 schematically represents a front three-quarter perspective view of the rolling cartridge of Fig. 4 according to a first point of view.

Fig. 8 schematically represents a front three-quarter perspective view of the rolling cartridge of Fig. 4 according to a second point of view.

Fig. 9 represents an enlargement of one detail showing one possible adjustment solution. Fig. 10 represents an enlargement of the detail indicated by "E" in Fig. 8.

Fig. 11 schematically represents a front view showing the phase of reciprocal coupling between a cartridge of the present invention and a rolling station of the present invention. Fig. 12 represents a sectional view according to the section line indicated by "B-B" in Fig.11.

Fig. 13 represents a sectional view according to the section line indicated by "C-C" in Fig. 11.

Fig. 14 schematically represents a perspective view corresponding to the phase of reciprocal coupling between a cartridge of the present invention and a rolling station of the present invention that is represented in Fig. 11.

Fig. 15 schematically represents a front view showing the reciprocal coupling between a cartridge of the present invention and a rolling station of the present invention, in a first operating condition.

Fig. 16 schematically represents a view of the rolling station of the present invention coupled with the corresponding rolling cartridge of the present invention according to the point of view indicated by "F" in Fig. 15, in a first operating condition.

Fig. 17 represents a sectional view according to the section line indicated by "G-G" in Fig.

15, in a first operating condition.

Fig. 18 represents a sectional view according to the section line indicated by "H-H" in Fig. 15, in a first operating condition.

Fig. 19 schematically represents a front three-quarter perspective view of the rolling station of the present invention coupled with the corresponding rolling cartridge of the present invention, in a first operating condition.

Fig. 20 schematically represents a back three-quarter perspective view of the rolling station of the present invention coupled with the corresponding rolling cartridge of the present invention, in a first operating condition.

Fig. 21 schematically represents a front view showing the reciprocal coupling between a cartridge of the present invention with a rolling station of the present invention, in a second operating condition.

Fig. 22 schematically represents a view of the rolling station of the present invention coupled with the corresponding rolling cartridge of the present invention according to the point of view indicated by "K" in Fig. 21 , in a second operating condition.

Fig. 23 represents a sectional view according to the section line indicated by "M-M" in

Fig.21 , in a second operating condition.

Fig. 24 represents a sectional view according to the section line indicated by "P-P" in Fig.

21 , in a second operating condition.

Fig. 25 schematically represents a front three-quarter perspective view of the rolling station of the present invention coupled with the corresponding rolling cartridge of the present invention, in a second operating condition.

Fig. 26 schematically represents a back three-quarter perspective view of the rolling station of the present invention coupled with the corresponding rolling cartridge of the present invention, in a second operating condition.

Fig. 27 schematically represents a perspective view of the transmission device relative to one of the two cylinders of the rolling cartridge.

Fig. 28 schematically represents a sectional view of the rolling station of Fig. 18 in which the sectional views indicated by R-R and S-S have been placed next to each other.

Fig. 29 schematically represents a sectional view of the initial portion of transmission from the motor to the transmission device of a rolling station made in accordance with the present invention.

Fig. 30 schematically represents an exploded view of a rolling cartridge made in accordance with the present invention.

Fig. 31 schematically represents a view showing the coupling between a rolling station and a rolling cartridge made in accordance with the present invention relating to a rolling stand with a vertical axis.

Fig. 32 schematically represents a view of a different embodiment of the rolling station of the present invention adapted for the use with prior art rolling cartridges, in a first operating condition.

Fig. 33 schematically represents a view of the rolling station of the present invention of Fig. 32, in a second operating condition.

Fig. 34 schematically represents a perspective view of a prior art rolling station relative to a rolling stand with a horizontal axis.

Fig. 35 and Fig. 36 schematically represent views showing the adjustment system of the cartridge of the present invention.

Description of the invention

The present invention relates to a rolling cartridge or stand (9) and a rolling station (20) that are structured and configured to couple with each other and that enable a coordinated action of adjustment of the reciprocal distance of the rolling cylinders (31 , 44) as well as a particularly innovative and advantageous structure for the transmission of motion to the rolling cylinders (31 , 44), as will be clear from the following of the present description.

With reference to the rolling station (20) and with reference to the Figures (Fig. 1 , Fig.

2, Fig. 3, Fig. 11 , Fig. 12, Fig. 14, Fig. 15, Fig. 16, Fig. 18, Fig. 19, Fig. 20, Fig. 21 , Fig. 22, Fig. 24, Fig. 25, Fig. 26) the present invention first of all relates to the control system of the rolling stand or rolling cartridge (9).

The oblong metal product is worked to obtain a determinate size or surface area in section and a determinate profile, which can be, for instance, circular, ovoid or elliptic, quadrangular, hexagonal, "L"-shaped, "C"-shaped, etc.

According to the invention (Fig. 1 , Fig. 2, Fig. 3, Fig. 15), each of the rolling cylinders, which are made up of a first cylinder (31) and a second cylinder (44), is controlled by a respective high-speed electric motor, indicatively but not exclusively between 3000 and 5000 RPM. The first motor (1) and the second motor (11) are preferably of the alternating current type. The rolling cylinders, that is to say, the first rolling cylinder (31) and the second rolling cylinder (44), are rotating opposite to each other, that is to say, according to opposite rotational directions. Each motor is provided with a respective control inverter that enables the independent control of the first motor (1) with respect to the second motor (11) and vice versa. A first rolling cylinder (31) is controlled by a first electric motor (1) and a second rolling cylinder (44) is controlled by a second electric motor (11). Each of the first electric motor (1 ) and second electric motor (1 1) is coupled (Fig. 3, Fig. 20, Fig. 24, Fig. 27, Fig. 28) with the respective rolling cylinder (31 , 44) by means of a transmission device, that is to say a first transmission device (3) for the first motor (1 ) and a second transmission device (33) for the second motor (11). The transmission device (3, 33) is provided (Fig. 3, Fig. 27, Fig. 28) with a shaft or first output pinion (17) equipped with a transmission slot (19) for the engagement of the hub (18) of the respective cylinder of the two cylinders (31 , 44) of the stand or cartridge (9). The shaft or first output pinion (17) is controlled in rotation by means of the combined and coordinated action of a second torque division pinion (16) integral with a first crown (15) by which it is put in rotation and of a third torque division pinion (22) integral with a second crown (21 ) by which it is put in rotation, the first crown (15) and the second crown (21) being put in rotation by means of a fourth self-compensated pinion (14) provided with a first gear (23) of transmission of the rotational motion to the first crown (15) and further provided with a second gear (24) of transmission of the rotational motion to the second crown (21). The fourth self- compensated pinion (14) in its turn receives the rotational motion from the motor (1 , 1 ) with the interposition of an epicyclic reduction gear (13).

The first output pinion (17) is controlled by a pair of pinions, that is to say, a second torque division pinion (16) and a third torque division pinion (22). As a consequence, with equal sizes of the overall gear (diameter, band, module) it is possible to transmit twice the torque with respect to the use of one pinion only. However, each of the two cylinders (31 , 44) must be controlled by one respective motor only, that is to say, the first motor (1) for the first rolling cylinder (31) and a second motor (11) for the second rolling cylinder (44). Therefore, for each of the two cylinders (31 , 44) a device is necessary that divides the torque of the respective motor in an exactly equal way onto two different chains of gears to transmit it to the only first output pinion (17) of the respective cylinder. For this purpose a fourth self-balanced pinion (14) is used, which is provided with a double toothed band with opposite screws, that is to say, provided with a first helical gear (23) and with a second helical gear (24) wherein the screw constituting the first helical gear (23) is made according to a shape opposite to the screw constituting the second helical gear (24). Therefore, the first gear (23) transmitting the rotational motion and the second gear (24) transmitting the rotational motion are respectively a first helical gear (23) shaped with a first screw and a second helical gear (24) shaped with a second screw, wherein the first screw constituting the first helical gear (23) is made according to a shape opposite to the second screw constituting the second helical gear (24). That is to say, the first screw has the respective teeth of the first helical gear (23) oriented according to an opposite orientation with respect to the orientation of the teeth of the second screw of the second helical gear (24). The division of the torque into an exactly equal value between the first helical gear (23) and the second helical gear (24) is ensured by the fact that the fourth self-balanced pinion (14) is not axially locked and, in order to keep in dynamic balance, the axial components of the meshing forces on the first helical gear (23) and on the second helical gear (24) must be exactly identical and contrary. Therefore, also the tangential meshing force on the first helical gear (23), to which the torque is directly linked, will be equal to the tangential meshing force on the second helical gear (24) and as a result the transmitted torques will be equal too.

The epicyclic reduction gear (13) is preferably made up (Fig. 29) of a first stage (36) onto which a first input shaft (35) engages that can be directly the output shaft of the motor (1 , 11) or a shaft of connection with the output shaft of the motor. The preferred solution is the one in which the first input shaft (35) is directly the output shaft of the motor (1 , 1 1), because the weight and rotating masses of the transmission system are minimized to the advantage of greater reliability and lower costs. The first input shaft (35) acts on first planetary gears (37) of the first stage (36), which are rotationally supported by a first planetary-gear support (38) which in its turn puts in rotation a second shaft (39). The second shaft (39) transmits the rotational motion from the first stage (36) to a second stage (40). The second shaft (39) acts on second planetary gears (41) of the second stage (40), which are rotationally supported by a second planetary-gear support (42) which in its turn puts in rotation a third shaft (43). The third shaft (43) in its turn is coupled with the fourth self-compensated pinion (14) of the first transmission device (3) in the case of the first motor (1) or of the second transmission device (33) in the case of the second motor (11).

The present invention provides the use of two transmission devices (3, 33) with divided torque for the purpose of reducing their weight and sizes. The application of transmission devices (3, 33) with divided torque determines a weight reduction, with respect to the current solutions, by about 30-35% only of the part relating to the transmission devices themselves, without considering the elimination (Fig. 34) of the adapters (28) of the prior art systems and the lower cost of the electric motors, that is to say, of the first electric motor (1) and of the second electric motor (11) with respect to the single motor (25) of the prior art solutions. Further benefits derive from the fact that, by adopting a more compact and lighter structure for the realization of the stand, thanks to the previously mentioned size and weight reductions, there is also a significant reduction in the construction needs of the plant and in particular as to the realization of the (Fig. 34) foundations (32) that may be reduced if not even eliminated. Furthermore, the plant as a whole will be considerably more compact, as is evident also from the comparison between the prior art solutions (Fig. 34) and the solution according to the present invention (Fig. 20) and considering that a rolling mill plant usually requires the presence of 14-16 rolling stands plus, if necessary, further finishing machines.

The two transmission devices (3, 33), that is to say, the first transmission device (3) and the second transmission device (33), are supported by a fixing structure (7) supporting the transmissions. The two transmission devices (3, 33) are movable on the transmissions fixing structure (7) by means of transmissions guides (4), which allow for their movement on the basis of the positioning of the rolling stand or of the rolling cartridge (9), for the purpose of adapting the position of the two transmission devices (3, 33) with respect to the position of the rolling cylinders (31 , 44) and/or with respect to the rolling line of the plant. For example in the case of a rolling station (20) intended to house a cartridge (9) according to a horizontal cylinders (31 , 44) configuration (Fig. 12, Fig. 17, Fig. 23), the two transmission devices (3, 33) must be able to perform a movement according to an essentially vertical direction. For example in the case of a rolling station (20) intended to house a cartridge (9) according to a vertical cylinders (31 , 44) configuration (Fig. 31), one or both of the two transmission devices (3, 33) must be able to perform a movement according to an essentially horizontal direction.

With reference to the rolling cartridge (9) of the present invention (Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 8, Fig. 9, Fig. 10, Fig. 13, Fig. 17, Fig. 23) at least one rolling cylinder (31 , 44) is supported by a pair of respective mounting elements (47, 48). For example, with reference to the first rolling cylinder (31), this is supported by a pair of first mounting elements (47) essentially parallel to each other, which are shaped with a central portion (59) which is provided with coupling seats (62) for the insertion of corresponding protrusions present at opposite head ends of the first cylinder (31). For example, with reference to the second rolling cylinder (44), this is supported by a pair of second mounting elements (48) essentially parallel to each other, which are shaped with a central portion (59) which is provided (Fig. 7) with circular coupling seats (62) for the insertion of corresponding protrusions present at opposite head ends of the second cylinder (44). By opposite head ends of the cylinder one means the base ends of the cylindrical shape. In practice the first cylinder (31), and likewise the second cylinder (44), are provided with a central body having an essentially cylindrical shape. In correspondence with the central body the semi-portions of the working groove are obtained, which, following the assembly of the first cylinder (31) and of the second cylinder (44) on the frame (46) of the cartridge (9), are approached to each other to form a working groove made by approaching a first semi-portion of the working groove that is obtained on the first cylinder (31) and a second semi-portion of the working groove that is obtained on the second cylinder (44). From the reciprocally opposite base ends of the cylindrical shape the protrusions branch off, which are intended to enter the coupling seats present on the central portion (59) of the mounting elements, that is to say, on the pair of first mounting elements (47) as regards the first cylinder (31) and on the pair of second mounting elements (48) as regards the second cylinder (44). The coupling between the first cylinder (31) and the pair of first mounting elements (47) can occur for instance by means of bearings and likewise the coupling between the second cylinder (44) and the pair of second mounting elements (48) can occur for instance by means of bearings so that the first cylinder (31 ) and the second cylinder (44) constitute a pair of idle cylinders rotating on (Fig. 6) a first rotation axis (63). The first cylinder (31) and the second cylinder (44) are controllable in rotation in an independent way of each other by means of the hubs (18) that are present at one of the head ends of the rolling cylinders themselves. The mounting element (47, 48) is shaped with the previously described central portion (59) for fixing a head of the rolling cylinders (31 , 44). From the central portion (59) at least one first arm (60) branches off (Fig. 6), which develops according to an essentially radial direction with respect to the circular coupling seat (62). At a first end (52) of the mounting element (47, 48), that is to say in correspondence with the first arm (60), pairs of first rings (72) are obtained which are intended to couple with hinging means (50, 51) intended for the rotation of the mounting element (47, 48) around a second rotation axis (64) that is in an eccentric position with respect to the first rotation axis (63) around which the respective rolling cylinder (31 , 44) supported by the mounting element itself (47, 48) is put in rotation. As a consequence, at least one cylinder (31 , 44) is supported by a pair of mounting elements (47, 48) essentially parallel to each other, each of which is provided with a circular coupling seat (62) for the insertion of corresponding protrusions present at opposite head ends of the cylinder (31 , 44) and each mounting element (47, 48) of the pair of mounting elements that support the cylinder (31 , 44) is provided with first rings (72) intended to couple with hinging means (50, 51) intended for the coordinated rotation of the pair of mounting elements (47, 48) around a second rotation axis (64) essentially parallel to the first rotation axis (63). The hinging means (Fig. 30) comprise a first hole (73) obtained on a first plate (65), which will be described in following, and a first coupling pin (71) that enters the first hole (73) and the first rings (72). The second rotation axis (64) is placed in an eccentric position with respect to the first rotation axis (63) around which the respective rolling cylinder (31 , 44) is put in rotation. Preferably both cylinders (31 , 44) are supported by means of the described system, namely:

- the first rolling cylinder (31) is supported by a pair of first mounting elements (47) essentially parallel to each other, each of which is provided with a circular coupling seat (62) for the insertion of corresponding protrusions present at opposite head ends of the first cylinder (31) and each first mounting element (47) of the pair of mounting elements that support the first cylinder (31) is provided with a pair of first rings (72) intended to couple with first hinging means (50) intended for the coordinated rotation of the pair of first mounting elements (47) around a second rotation axis (64) essentially parallel to the first rotation axis (63), said second rotation axis (64) being placed in an eccentric position with respect to the first rotation axis (63) around which the respective first rolling cylinder (31) is put in rotation;

- the second rolling cylinder (44) is supported by a pair of second mounting elements (48) essentially parallel to each other, each of which is provided with a circular coupling seat (62) for the insertion of corresponding protrusions present at opposite head ends of the second cylinder (44) and each second mounting element (48) of the pair of mounting elements that support the second cylinder (44) is provided with a pair of first rings (72) intended to couple with second hinging means (51) intended for the coordinated rotation of the pair of second mounting elements (48) around a second rotation axis (64) essentially parallel to the first rotation axis (63), said second rotation axis (64) being placed in an eccentric position with respect to the first rotation axis (63) around which the respective second rolling cylinder (44) is put in rotation.

In this way it is possible to obtain a simple and fast adjustment of the reciprocal distance between the first rolling cylinder (31) and the second rolling cylinder (44) without complex and delicate adjustment transmission systems being necessary to transmit in a coordinated and corresponding way the adjustment on all four sides of the mounting elements of the cylinders as occurs in the prior art solutions.

In the preferred solution of the present invention both cylinders are supported and are adjustable in their position with respect to the rolling axis by means of the described system. However, in less preferred solutions of the present invention one can also have hybrid solutions in which only one of the two cylinders (31 , 44) is supported by the system of the present invention while the other of the two cylinders (31 , 44) is supported by a system similar to a traditional system for supporting the rolling cylinders.

The mounting elements (47, 48) couple (Fig. 10) with the cartridge frame (46) by means of a first fixing interface (54) made up of a first supporting element integral with the cartridge frame (46) and of a second element that is screwed on the first element. The second element is provided with a first plate (65) having a pair of first holes (73) of which: - one hole of said first holes (73) is a first hole (73) intended to couple with the first hinging means (50) intended for the coordinated rotation of the pair of first mounting elements (47), in particular it is a first hole (73) intended to couple with the first pin (71);

- another hole of said first holes (73) is a first hole (73) intended to couple with the second hinging means (51) intended for the coordinated rotation of the pair of second mounting elements (48), in particular it is a first hole (73) intended to couple with the first pin (71).

The first plate (65) and the second element form one single hinging body for hinging the mounting elements (47, 48).

It will be evident that in different embodiments there may be common hinging means (50, 51) for the first mounting elements (47) and second mounting elements (48), as well as there may be separate first fixing interfaces (54) for the first mounting elements (47) and second mounting elements (48).

The adjustment of the reciprocal distance between the first rolling cylinder (31) and the second rolling cylinder (44) preferably occurs by means of adjustment means (49) which perform a pushing or traction action at a point of application of the force that is placed in an eccentric position with respect to the first rotation axis (63) around which the respective second rolling cylinder (44) is put in rotation and that furthermore is preferably at a location essentially symmetrical with respect to the second rotation axis (64) according to a central symmetry with respect to the first rotation axis (63). In this way a lever configuration is obtained that also allows to reduce the efforts necessary both for the movement of the cylinders and for their maintenance in a lock position during the rolling process. Preferably the adjustment means (49) act (Fig. 6) in correspondence with a second arm (61) which branches off the central portion (59) of the mounting element (47, 48). The second arm (61 ) develops according to an essentially radial direction with respect to the circular coupling seat (62) and preferably according to a radial direction that is essentially opposite with respect to the radial direction with reference to which the previously described first arm (60) branches off. At a first end (52) of the mounting element (47, 48), that is to say, in correspondence with the second arm (61 ), there is a pair of second rings (76) intended to couple with further hinging means (57, 58) intended for the coupling with the adjustment means (49). More precisely:

- the first rolling cylinder (31) is supported by a pair of first mounting elements (47) essentially parallel to each other, each of which is provided with a circular coupling seat (62) for the insertion of corresponding protrusions present at opposite head ends of the first cylinder (31) and each first mounting element (47) of the pair of mounting elements that support the first cylinder (31) is provided with a pair of second rings (76) intended to couple by means of a second pin (78) with adjustment means (49) intended to perform a pushing or traction action on the first mounting elements (47) to control the coordinated rotation of the pair of first mounting elements (47) around the second rotation axis (64), said adjustment means (49) performing the described pushing or traction action with respect to the frame of the rolling cartridge or stand (9) and acting on the first mounting elements (47) in correspondence with a third hinging means (57);

- the second rolling cylinder (44) is supported by a pair of second mounting elements (48) essentially parallel to each other, each of which is provided with a circular coupling seat (62) for the insertion of corresponding protrusions present at opposite head ends of the second cylinder (44) and each second mounting element (48) of the pair of mounting elements that support the second cylinder (31) is provided with a pair of second rings (76) intended to couple by means of a second pin (78) with adjustment means (49) intended to perform a pushing or traction action on the second mounting elements (48) to control the coordinated rotation of the pair of second mounting elements (48) around the second rotation axis (64), said adjustment means (49) performing the described pushing or traction action with respect to the frame of the rolling cartridge or stand (9) and acting on the second mounting elements (48) in correspondence with a fourth hinging means (58).

To sum up, with reference to the rolling cartridge or stand, the present invention relates (Fig. 6) to an adjustment system (47, 48, 49, 54, 55, 67, 68) for adjusting the position of at least one first cylinder (31) of a pair of rolling cylinders (31 , 44) of a rolling stand or of a rolling cartridge (9), wherein the adjustment system (47, 48, 49, 54, 55, 67, 68) is intended to adjust the reciprocal position between:

- a first rotation axis (63) around which the first rolling cylinder (31) is put in rotation;

- a first rotation axis (63) around which the second rolling cylinder (44) is put in rotation. The reciprocal adjustment between said first rotation axes (63) causes (Fig. 4, Fig. 21) an adjustment of the reciprocal distance between the rolling cylinders (31 , 44). The adjustment system (47, 48, 49, 54, 55, 67, 68) comprises (Fig. 6, Fig. 7) at least one pair of mounting elements (47, 48) supporting one between the first cylinder (31 ) and the second cylinder (44) on opposite sides with respect to the longitudinal development of the cylinder (31 , 44). The pair of mounting elements (47, 48) is hinged (Fig. 6) in correspondence with a second rotation axis (64) that is in an eccentric position with respect to the first rotation axis (63). The adjustment of the reciprocal distance between the rolling cylinders (31 , 44) occurs by means of a rotation (Fig. 17, Fig. 23) of the first rotation axis (63) of the cylinder supported by the pair of mounting elements (47, 48) around the second rotation axis (64) according to approaching or spacing directions between the first cylinder (31 ) and the second cylinder (44) of the pair of rolling cylinders (31 , 44). Preferably the second rotation axis (64) is essentially parallel to the first rotation axis (63).

In the preferred solution of the present invention, the adjustment system (47, 48, 49, 54, 55, 67, 68) comprises (Fig. 6) two pairs of mounting elements (47, 48):

- one pair of first mounting elements (47) supporting the first cylinder (31 ), said pair of first mounting elements (47) being hinged in correspondence with the second rotation axis (64) that is in an eccentric position with respect to the first rotation axis (63) of the first cylinder (31);

- one pair of second mounting elements (48) supporting the second cylinder (44), said pair of second mounting elements (48) being hinged in correspondence with the second rotation axis (64) that is in an eccentric position with respect to the first rotation axis (63) of the second cylinder (44).

The adjustment of the reciprocal distance between the rolling cylinders (31 , 44) can occur, in general, by means of:

- a rotation of the first rotation axis (63) of the first cylinder (31 ) around the second rotation axis (64) of the pair of first mounting elements (47);

or - a rotation of the first rotation axis (63) of the second cylinder (44) around the second rotation axis (64) of the pair of second mounting elements (48);

or

- a reciprocally coordinated rotation of the first rotation axis (63) of the first cylinder (31) around the second rotation axis (64) of the pair of first mounting elements (47) and of the second cylinder (44) around the second rotation axis (64) of the pair of second mounting elements (48).

In one embodiment (not shown but whose implementation will be immediately clear to those skilled in the art) the second rotation axis (64) of the pair of first mounting elements (47) coincides with the second rotation axis (64) of the pair of second mounting elements (48).

In a different embodiment (Fig. 6) the second rotation axis (64) of the pair of first mounting elements (47) is different and spaced with respect to the second rotation axis (64) of the pair of second mounting elements (48).

In a first solution (not shown) the adjustment means (49) can be fixed on a second plate (66) of a second coupling interface (55) by means of a hinging means intended to enable the rotation of an end of the adjustment means (49).

In a different embodiment (Fig. 6), the adjustment means (49) act on the mounting elements (47, 48) on the one side and are fixed to the frame (46) of the rolling cartridge or stand (9) on the opposite side by means of a second coupling interface (55) which comprises a second plate (66) which is equipped with eyelets (56) or dovetail joints intended to enable (Fig. 9) an advancing or backing guided sliding of the second plate with respect to the frame (46). The sliding is a sliding coordinated with the adjustment performed by the adjustment means (49) on the mounting elements (47, 48). In fact, since the first mounting element (47) and the second mounting element (48) are fixed to the frame (46) of the rolling cartridge or stand (9) by eccentric fixing with respect to the first rotation axis (63) of the respective cylinders (31 , 44), the movement of opening and closing of the gap between the cylinders (31 , 44) is a circular movement and, therefore, causes an advancing or backing translation of the second end (53) with respect to the frame (46) of the rolling cartridge or stand (9). Said translation is guided by the sliding of the second plate (66) that compensates for said translation.

Advantageously the adjustment means (49) that act on the first mounting element (47) and the adjustment means (49) that act on the second mounting element (48) are fixed to the frame (46) of the rolling cartridge or stand (9) by means of a second plate (66) which is common both to the adjustment means (49) that act on the first mounting element (47) and to the adjustment means (49) that act on the second mounting element (48). In this way one advantageously also obtains a synchronization function that is translated into a symmetry of the action of opening and closing of one of the two rolling cylinders (31 , 44) with respect to the other of the two rolling cylinders (31 , 44), because the pushing or traction action controlled by means of the adjustment means (49) that act on the first mounting element (47) and the adjustment means (49) that act on the second mounting element (48) is constrained to produce a symmetrical effect of movement with respect to the rolling axis thanks to the guiding action obtained by means of the sliding of the second plate (66) that is common both to the adjustment means (49) that act on the first mounting element (47) and to the adjustment means (49) that act on the second mounting element (48).

The adjustment means (49) are controlled by means of a control device (70) mounted on the cartridge itself. Preferably there are:

- a first control device (70) that acts on a control unit (49, 66) relative to a first side (74) of the rolling cartridge or stand (9);

- a second control device (70) that acts on a control unit (49, 66) relative to a second side (75) of the rolling cartridge or stand (9);

the first side (74) and second side (75) being the opposite sides of the rolling cartridge or stand (9) in correspondence with which (Fig. 4) the fixing of the rolling cylinders (31 , 44) on the frame (46) of the rolling cartridge occurs.

Preferably the adjustment means (49) are hydraulic pistons and the control device (70) is a hydraulic motor that acts as a control of the adjustment unit made up of the adjustment means (49) and of the second plate (66).

In the preferred embodiment of the present invention (Fig. 35, Fig. 36) the control device (70) is a hydraulic motor that acts on a worm screw (80) which in its turn puts in rotation a gear wheel (79) that:

- in correspondence with its first side operates a first left-hand nut screw (81) associated with a first left-hand screw (83) intended to perform the translation of the adjustment means (49) in correspondence with said first side of the gear wheel (79), the first left-hand screw (83) comprising at one end the third hinging means (57) for fixing the first mounting elements (47);

- in correspondence with a second side operates a second right-hand nut screw (82) associated with a second right-hand screw (84) intended to perform the translation of the adjustment means (49) in correspondence with said second side of the gear wheel (79), the second right-hand screw (84) comprising at one end the fourth hinging means (58) for fixing the second mounting elements (48).

Therefore, the control devices (70) for performing the adjustments are two and move in a synchronized way, through a pulse sensor or an encoder, to allow the two rolls to keep the same reciprocal distance over their entire width. To sum up, the adjustment system (47, 48, 49, 54, 55, 67, 68) preferably comprises two control devices (70) placed spaced from each other by a distance essentially corresponding to the distance between the opposite ends of the rolling cylinders (31 , 44), said two control devices (70) being controlled in a reciprocally synchronized way, the synchronization being obtained by means of control means that detect the position of the control devices (70) or of the cylinders or of actuation means between the control devices and said cylinders through pulse sensors or encoders, the synchronization being intended to maintain the reciprocal distance between the first cylinder and second cylinder essentially constant over the entire length of the cylinders.

The first screw (83) and the second screw (84) are preferably screws with a trapezoidal section thread.

Each system of nut screw (81 , 82) and corresponding screw (83, 84) is enclosed within a protection tube (85) provided with a scraper (86).

The control of the synchronization between the movement of the first mounting element (47) that supports the first rolling cylinder (31) and of the second mounting element (48) that supports the second rolling cylinder (44), as well as by the previously described action of the fixing constraint on the second plate (66), can also occur by means of position transducers, which, if necessary, can also be provided with a transmission system for transmitting the data relative to the position of the first mounting element (47) and of the second mounting element (48). The data transmission system can interface with a control unit of the rolling mill or station (20) in order to coordinate the movement of the first mounting element (47) and of the second mounting element (48) in such a way as to obtain a correspondence between the reciprocal position of the first mounting element (47) and of the second mounting element (48) and the reciprocal position of the first transmission device (3) and of the second transmission device (33). In this way, by said synchronization between the described elements, the transmission slots (19) of the transmission devices (3) and the hubs (18) of the rolling cylinders (31 , 44) will be driven in a condition of reciprocal alignment.

Likewise, one can also provide a reciprocal coordination system of the mechanical type of the reciprocal opening of the first transmission device (3) and second transmission device (33) and/or one can provide position transducers for the detection of the position of the first transmission device (3) and of the second transmission device (33). In fact, the first transmission device (3) and the second transmission device (33) can be provided with an adjustment of the position of the transmission devices (3, 33) according to a rotational movement around (Fig. 12, Fig. 24) a second rotation axis (64) in correspondence with a fifth hinging means (69) that is placed in an eccentric position with respect to the first rotation axis (63) around which the respective rolling cylinder (31 , 44) is put in rotation and that is aligned with the second rotation axis (64) around which the rotation of the respective mounting elements (47, 48) of the cylinders occurs. As a consequence, in this solution the first transmission device (3) and the second transmission device (33) can each be rotated around a respective second rotation axis (64) in correspondence with a fifth hinging means (69) as will be explained in the following of the present description.

The advantages provided by the solution of the transmission system of the rolling station (20) of the present invention can be applied:

- to the rolling cartridges or stands (Fig. 1 , Fig. 2, Fig. 3, Fig. 1 1 , Fig. 12, Fig. 14, Fig. 15, Fig. 16, Fig. 18, Fig. 19, Fig. 20, Fig. 21 , Fig. 22, Fig. 24, Fig. 25, Fig. 26) of the present invention with the mounting elements (47, 48) that can be rotated around the second rotation axis (64) that is placed at an eccentric location with respect to the first rotation axis (63) around which the respective rolling cylinder (31 , 44) is put in rotation;

- to existing rolling cartridges or stands (Fig. 32, Fig. 33) with the mounting elements (47, 48) of the cylinders that can be translated vertically according to prior art solutions.

With particular reference to the case in which the advantages provided by the solution of the transmission system of the rolling station (20) of the present invention are applied to existing rolling cartridges or stands (Fig. 32, Fig. 33) with the mounting elements (47, 48) of the cylinders that can be translated vertically according to prior art solutions (Fig. 32), the two transmission devices (3, 33) must be sliding vertically. In that case the movement of the two transmission devices (3, 33) occurs by means of respective transmission locking means (5) preferably of the hydraulic type, which maintain the position set during the rolling process. For example the described adjustment can be used for the adjustment of the reciprocal distance between the cylinders (31 , 44) according to the wear conditions of the latter. As a consequence, in case of need for adjustment, the procedure provides (Fig. 32, Fig. 33) that:

- one unlocks the transmission locking means (5);

- one controls the adjustment of the position of the transmission devices (3, 33), during this phase the transmission devices (3, 33) being suspended with a transmission supporting compensator (6) that enables a self-compensation in such a way that the transmission devices (3, 33) can be moved with some drives that can be hydraulic or mechanical, but that must overcome only the friction of the guide mechanism (4) of the transmission;

- one locks the transmission locking means (5).

For example, from a reciprocally close position (Fig. 32) of the two cylinders (31 , 44), by acting as previously described, one can reach (Fig. 33) a reciprocally spaced position of the two cylinders (31 , 44). The supporting compensator (6) is preferably made up of three levers, of which:

- a central lever hinged on the transmissions fixing and supporting structure (7) at an intermediate point between a first end and a second end of the central lever itself;

- a first transmission lever hinged at the first end of the central lever and on which a first element of the reduction gear locking means (5) acts;

- a second transmission lever hinged at the second end of the central lever and on which a second element of the reduction gear locking means (5) acts.

In this way one can control the adjustment of the position of the transmission devices (3, 33), with the transmission devices (3, 33) which are suspended by means of the transmission supporting compensator (6). The adjustment of the position of the first transmission device (3) and of the second transmission device (33) is reciprocally coordinated by means of the supporting compensator (6), the first transmission device (3) and the second transmission device (33) being suspended on the transmissions fixing and supporting structure (7) by means of said transmission supporting compensator (6).

On the contrary, the adjustment of the position of the transmission devices (3, 33) will have to occur with an adjustment system similar to the one described with reference to the cartridge of the present invention in the case in which the advantages provided by the solution of the transmission system of the rolling station (20) of the present inventions are applied to the rolling cartridges or stands of the present invention (Fig. 1 , Fig. 2, Fig. 3, Fig. 11 , Fig. 12, Fig. 14, Fig. 15, Fig. 16, Fig. 18, Fig. 19, Fig. 20, Fig. 21 , Fig. 22, Fig. 24, Fig. 25, Fig. 26) with the mounting elements (47, 48) that can be rotated around the second rotation axis (64) that is placed in an eccentric position with respect to the first rotation axis (63) around which the respective rolling cylinder (31 , 44) is put in rotation.

In this case, too, it is necessary to adopt an adjustment of the position of the transmission devices (3, 33) according to a rotational movement around (Fig. 12, Fig. 24) a second rotation axis (64) in correspondence with a fifth hinging means (69) that is placed in an eccentric position with respect to the first rotation axis (63) around which the respective rolling cylinder (31 , 44) is put in rotation and that is aligned with the second rotation axis (64) around which the rotation of the respective mounting elements (47, 48) of the cylinders occurs. As a consequence, in this solution the first transmission device (3) can be rotated around a second rotation axis (64) in correspondence with a fifth hinging means (69) that is placed in an eccentric position with respect to the first rotation axis (63) around which the first rolling cylinder (31) is put in rotation, said second rotation axis (64) in correspondence with the fifth hinging means (69) being aligned with the second rotation axis (64) around which the rotation of the first mounting elements (47) of the first rolling cylinder (31) occurs. Likewise, the second transmission device (33) can be rotated around a second rotation axis (64) in correspondence with a fifth hinging means (69) that is placed in an eccentric position with respect to the first rotation axis (63) around which the second rolling cylinder (44) is put in rotation, said second rotation axis (64) in correspondence with the fifth hinging means (69) being aligned with the second rotation axis (64) around which the rotation of the second mounting elements (48) of the second rolling cylinder (44) occurs.

The movement of the transmission devices (3, 33) is controlled by means of transmission movement means (68) that couple with a corresponding mounting element (47, 48) of the transmissions (3, 33) by means of a coupling (67) which is placed in an eccentric position with respect to the first rotation axis (63) around which the respective rolling cylinder (31 , 44) is put in rotation. Preferably the coupling (67) is in correspondence with a prolongation of the straight line joining the second rotation axis (64) and the first rotation axis (63), said coupling (67) lying on the prolongation of said straight line in correspondence with a position essentially opposite to the second rotation axis (64) with respect to the first rotation axis (63). In this way a lever configuration is obtained, which also allows to reduce the efforts necessary both for the movement of the transmissions (3, 33) and for their maintenance in a lock position during the rolling process. The coupling (67) is made up (Fig. 19) of a pair of reciprocally parallel arms on which hinging holes are obtained, which are reciprocally aligned according to a direction of insertion of a hinging pin, the direction of insertion being essentially coincident with the second rotation axis (64). In the movement induced by the movement means (68), the coupling (67) is guided by means of transmission guides (4) obtained on the transmissions fixing and supporting structure (7).

Furthermore, adjustments are provided to allow to carry out the channel change. In fact, each rolling cylinder can be provided with several rolling channels for the purpose of enabling a fast channel change for example in case of wear of the channel being used with a new channel or to change the channel being used with another channel having different characteristics. For example, it can be provided that the transmissions fixing and supporting structure (7) is mobile with respect to the anchorage base (10) for the adjustment of the position of the rolling channel obtained on the cylinders (31 , 44). Furthermore (Fig. 11 , Fig. 14, Fig. 15) the rolling cartridge (9) can be sliding on own cartridge guides (34) to enable its insertion or extraction with respect to the rolling station (20). As a consequence, the rolling station (20) is preferably provided with an anchorage base (10) for being fixed to the floor. The anchorage base (10) is provided with the base guides (8) intended to enable the movement of the transmissions fixing and supporting structure (7). Furthermore, stand guides (34) may be present. The base guides (8) and the stand guides (34) can be made in the superimposed configuration (the solution shown) or in line one after the other (solution not shown) on the rolling plane on which the rolling stations (20) and the cartridges (9) are installed or according to further configurations, according to the plant layout. The cartridges (9) can be provided with hooking means (45) for the movement of the cartridges as well as with means for the coupling with lifting hooks of the cartridges, such as insertion holes obtained on the frame (46).

The two rolling cylinders (31 , 44) are controlled in an independent way and, through their own inverter and management system, the adjustments necessary to obtain a perfect synchrony of the system can be made. This is a great advantage with respect to the present state of the art, which is bound by one single transmission of the two cylinders.

By the present invention it is not necessary to realize the foundation for the support of the reduction gear and of the motor, obtaining a considerable saving in the realization of the civil works. Moreover, the necessary space is considerably reduced and therefore the sizes of the shed can be reduced as well. Therefore, the saving achieved by the application of the present invention is not only linked to the transmission system, but in particular to the simplification that is introduced to the whole structure of the plant. In fact, as shown in the Figures and as described, the rolling station (20) of the present invention comprises an adjustment system (47, 48, 49, 54, 55, 67, 68) provided with two mounting elements (47, 48) of which a first mounting element (47) supports in an overhanging way on the rolling station (20) the first transmission device (3) that is a gear transmission device coupled with the respective first motor (1) and of which a second mounting element (48) supports in an overhanging way on the rolling station (20) the second transmission device (33) that is a gear transmission device coupled with the respective said second motor (11) according to a configuration without adapters or transmission shafts in which the transmission devices (3, 33) are supported by the fixing structure (7) of the transmission devices (3, 33) that supports the transmission devices (3, 33) in an overhanging way on the rolling station (20), which is a single block rolling station which includes in a single block the supporting structure of the equipments of the rolling station itself which supporting structure supports in a single operative block also the transmission slots, the gear transmission devices, the motors, constituting a single block structure according to a configuration without adapters or transmission shafts.

In particular, the resort to two motors, that is to say, a first electric motor (1) for a first rolling cylinder and a second electric motor (11 ) for a second rolling cylinder of the rolling stand allows to use smaller motors with respect to the single motor used in the prior art solutions, with lower costs and better performances in terms of control. Furthermore, the possibility to control in an independent way the rotation of each of the two rolling cylinders allows to obtain benefits in terms of the quality of the material. In fact, in this way one obtains the possibility to modify the peripheral speeds of the rolling cylinders in an independent way of each other also during the rolling process, that is to say, in load conditions. For example one can change the rotation speed of one cylinder with respect to the other according to the load and to the effort detected on each rolling cylinder to compensate for possible differences which may be the sign of the wear of one cylinder with respect to the other or of unevenness of the material, such as unevenness in the section, unevenness in the temperature, unevenness at the head and/or at the tail of the oblong metal material, etc. In this way such problems can be solved by varying the speed of one cylinder with respect to the speed of the other cylinder of the same rolling stand, obtaining on the oblong metal material a different condition of balance between the sliding and the mechanical action of deformation in correspondence with the portion in contact with the first rolling cylinder controlled by the first motor (1) with respect to the conditions in correspondence with the portion in contact with the second rolling cylinder controlled by the second motor (1 1 ), to the advantage of the quality and of the mechanical characteristics of the finished product. For example, in addition to the compensation for the wear of the channel of the cylinders that is obtained by the variation in the reciprocal distance of the cylinders, there may be a compensation for the wear of the channel of the cylinders obtained by means of the introduction of a difference in the rotation speed of one cylinder with respect to the other, which is not possible with the prior art rolling stands, provided with one single motor, and which is instead possible with the solution according to the present invention in which each cylinder is controllable in an independent way by means of the respective motor. As a consequence, there may also be an extension of the useful life cycle of the rolling cylinders thanks to the increased possibilities of compensation provided by the solution according to the present invention.

Therefore, the solution according to the present invention provides a rolling station (20) intended to couple with a respective rolling cartridge or stand (9) which is provided with two rolling cylinders (31 , 44) identical to each other, a first cylinder (31) being provided with at least one first semi-channel and a second cylinder (44) being provided with at least one second semi-channel, the reciprocal placing side-by-side of the cylinders (31 , 44) causing the reciprocal placing side-by-side of the at least one first semi-channel and of the at least one second semi-channel whose ensemble constitutes at least one rolling channel of the cartridge or stand (9), wherein the rolling station (20) includes a transmissions fixing and supporting frame (7) intended to house a pair of transmission devices of which a first transmission device (3) is intended to couple with a first rolling cylinder of the cartridge or stand (9) and a second transmission device (33) is intended to couple with a second rolling cylinder of the cartridge or stand (9), the first rolling cylinder being put in rotation by a first motor (1) by means of the first transmission device (3) and the second rolling cylinder being put in rotation by a second motor (11) by means of the second transmission device (33).

The first motor (1) and the second motor (1 1) can be controllable in an independent way of each other and/or in a coordinated way with each other. For example one can provide an independent control of one motor with respect to the other, or one can provide the control of one motor only with the other motor following the control performed on the first motor with the introduction of a possible speed difference between the first motor (1) and the second motor (11), which can be null or assume a determined difference value calculated in an absolute way or in a percentage way with respect to the speed of the first motor (1). In general the first motor (1) and the second motor (11 ) are controllable in an independent way of each other with different rotation speeds, the rotation speed difference of the first motor (1) and of the second motor (11) corresponding to a difference in the rotation speed of the first cylinder (31) with respect to the rotation speed of the second cylinder (44) of the stand or cartridge (9). For example, the rotation speed difference of the first motor (1) and of the second motor (11) is controllable in a manually and/or automatically controlled way according to rolling parameters, such as:

- temperature of the oblong metal material;

- temperature differences between a first oblong metal material rolled in the rolling line and a second oblong metal material rolled in the rolling line after the first;

- temperature differences of the cylinders following the progressive heating of the latter following the rolling process;

- temperature of a portion of the oblong metal material detected by means of temperature detection means in order to compensate for the greater rolling effort required in correspondence with portions having a lower temperature and/or for the lower rolling effort required in correspondence with portions having a greater temperature with respect to adjacent portions along a same bar of oblong metal material;

- unevenness of the oblong metal material, such as temperature, section, mechanical structure unevenness, etc.;

- unevenness of the oblong metal material detected by means of the input power of the first motor (1) and/or second motor (11) and/or differences between them;

- physical and/or mechanical characteristics of the head and/or of the tail of the oblong metal material;

- material constituting the oblong metal material that is rolled;

- material for making the cylinders (31 , 44);

- wear of the rolling channel;

- one or more measurements of the section of the oblong metal material taken in one or more points of the rolling line;

- tension applied to the oblong metal material between a pair of rolling stations (20);

- combination of one or more of the described parameters.

In correspondence with the first motor (1 ) a first safety joint (2) is installed and in correspondence with the second motor (11) a second safety joint (12) is installed.

The safety joints have the function of protecting the mechanical transmission in case of cobbles, that is to say, when the rolled product gets jammed inside the rolling cartridge due to operation errors or to problems of various nature that can occur above all during the starting of the plant, that is to say, when the plant is in a test phase. In case of a sudden stop of the stand, the mechanical transmission may undergo such high shocks as to damage some components. For this reason a joint with a device is usually introduced, set at a predetermined torque value, which is released when the safety threshold is reached disconnecting the motor from the rest of the transmission. The release device can be of various nature, such as with elements that break, with friction discs, of the hydraulic type, etc. In the prior art solutions said function is performed (Fig. 34) by the toothed joint (26). Advantageously in the solution according to the present invention the safety joint is applied in a more protected position.

The present invention also relates to a rolling mill plant for the production of oblong metal products comprising at least one rolling station (20) as previously described.

Furthermore, the present invention relates to a rolling process for the production of oblong metal products by means of successive passages in a sequence of rolling cartridges or stands (9) of a rolling line comprising rolling stations (20) each of which is intended to house a rolling cartridge or stand (9), in which at least one rolling cartridge or stand (9) is provided with two rolling cylinders (31 , 44), a first rolling cylinder (31) being provided with at least one first semi-channel and a second rolling cylinder (44) being provided with at least one second semi-channel, the reciprocal placing side-by-side of the two rolling cylinders (31 , 44) causing the reciprocal placing side-by-side of the at least one first semi-channel and the at least one second semi-channel, which together in their side- by-side configuration form at least one rolling channel of the cartridge or stand (9) intended for the mechanical working by rolling of an oblong metal product passing in said at least one rolling channel, wherein the rolling process comprises at least one phase of adjustment of the rotation speed difference between the first cylinder (31) and the second cylinder (44) installed on a same rolling cartridge or stand (9), the first cylinder (31) and the second cylinder (44) being controllable in rotation in an independent way of each other by means of a pair of transmission devices of which a first transmission device (3) is intended to couple with the first rolling cylinder of the cartridge or stand (9) and a second transmission device (33) is intended to couple with the second rolling cylinder of the cartridge or stand (9), the first rolling cylinder (31) being put in rotation by a first motor (1) by means of the first transmission device (3) and the second rolling cylinder (44) being put in rotation by a second motor (11) by means of the second transmission device (33). Furthermore, said rotation speed difference between the first cylinder and second cylinder is controllable in a manually and/or automatically controlled way according to rolling parameters.

Of course all this must be understood as further advantageous as it is well known that the wear of the materials, in particular of the opposite cylinders, occurs, although imperceptibly, in a different way. Therefore, even very small diameter variations between the cylinders due to the natural and continuously variable wear cause different peripheral speeds, therefore by the present invention, by obtaining the possibility of variation in the angular speed of one cylinder with respect to the other, an extremely optimal rolling is obtained with an increase in quality, profitability and productivity.

In general, both for the cartridge and for the rolling station, the present invention relates to an adjustment system (47, 48, 49, 54, 55, 67, 68) for adjusting the position of at least one first rotation axis (63) around which a first rolling cylinder (31) or a second rolling cylinder (44) of a pair of rolling cylinders (31 , 44) applied on a frame (46) of a rolling stand or a rolling cartridge (9) rotates. The rolling stand or rolling cartridge (9) is intended to couple with at least one rolling station (20) provided with at least one transmission device (3, 33) intended to transmit the rotational motion from rotation means (1 , 1 1) to at least one of the rolling cylinders (31 , 44) of the pair of rolling cylinders (31 , 44), the adjustment system (47, 48, 49, 54, 55, 67, 68) being intended to adjust the reciprocal position between:

- the first rotation axis (63) around which the first rolling cylinder (31) is intended to be put in rotation; - the first rotation axis (63) around which the second rolling cylinder (44) is intended to be put in rotation.

The reciprocal adjustment between the first rotation axes (63) causes an adjustment of the reciprocal distance between the rolling cylinders (31 , 44). The adjustment system (47, 48, 49, 54, 55, 67, 68) comprises at least mounting elements (47, 48) adapted to support one between the first rolling cylinder (31) and the second rolling cylinder (44), or adapted to support one between a first transmission device (3) and a second transmission device (33) which are intended to transmit the rotational motion to the pair of rolling cylinders (31 , 44). The mounting elements (47, 48) are hinged in correspondence with a second rotation axis (64) that is in an eccentric position with respect to the first rotation axis (63). The adjustment of the reciprocal distance between the rolling cylinders (31 , 44) occurs by means of a rotation of the first rotation axis (63) of the cylinder (31 , 44) around the second rotation axis (64) according to approaching or spacing directions between the first cylinder (31) and the second cylinder (44).

In general, as regards the rolling station (20), the adjustment system (47, 48, 49, 54, 55, 67, 68) comprises at least one of the mounting elements (47, 48), which supports one between a first transmission device (3) and a second transmission device (33) which are intended to transmit the rotational motion to at least one of the rolling cylinders (31 , 44) of the pair of rolling cylinders (31 , 44). The at least one of the mounting elements (47, 48) is hinged in correspondence with the second rotation axis (64) that is in an eccentric position with respect to the first rotation axis (63), the adjustment of the reciprocal distance between the rolling cylinders (31 , 44) further including an adjustment of the reciprocal distance between a first transmission slot (19) adapted for the engagement of a hub (18) of a respective cylinder selected from the cylinders of the pair of rolling cylinders (31 , 44) and a second transmission slot (19) adapted for the engagement of a hub (18) of a respective other cylinder selected from the pair of rolling cylinders (31 , 44). The mounting elements (47, 48) are shaped with a central body which is provided with insertion seats for one of the transmission devices (3, 33). Therefore, the movement means (68) of the transmission (3, 33) are intended to perform the action of adjustment of the reciprocal distance between the first transmission slot (19) and the second transmission slot (19) by means of an adjustment force acting between one of the mounting elements (47, 48) and a transmissions fixing and supporting structure (7).

Preferably the adjustment system (47, 48, 49, 54, 55, 67, 68) comprises two movement means (68) of which one is intended for the movement of the first transmission device (3) and of which another is intended for the movement of the second transmission device (33). The two movement means (68) are controlled in a reciprocally synchronized way, the synchronization being obtained by means of control means that detect the position of the two movement means (68) or of the transmission devices (3, 33) or of actuation means between the movement means (68) and the transmission devices (3, 33) themselves through pulse sensors or encoders.

In general, with reference to the rolling station, the adjustment system (47, 48, 49, 54, 55, 67, 68) comprises (Fig.19) two mounting elements (47, 48):

- a first mounting element (47) supporting the first transmission device (3), the first mounting element (47) being hinged (Fig. 22) in correspondence with the second rotation axis (64) that is (Fig. 24) in an eccentric position with respect to the first rotation axis (63) relative to the first rolling cylinder (31);

- a second mounting element (48) supporting the second transmission device (33), the second mounting element (48) being hinged (Fig. 22) in correspondence with the second rotation axis (64) that is (Fig. 24) in an eccentric position with respect to the first rotation axis (63) relative to the second rolling cylinder (44).

Correspondingly such adjustment corresponds to the adjustment of the reciprocal distance between the first transmission slot (19) and the second transmission slot (19), which occurs, therefore, by means of:

- a rotation (Fig. 24) of the first mounting element (47) with a corresponding rotation of the first axis (63) around the second rotation axis (64);

or - a rotation (Fig. 24) of the second mounting element (48) with a corresponding rotation of the first axis (63) around the second rotation axis (64);

or

- a reciprocally coordinated rotation of the first mounting element (47) around the second rotation axis (64) and of the second mounting element (48) around the second rotation axis (64).

Similarly to what explained with reference to the application of the system of the present invention to the rolling cartridge, the second rotation axis (64) of the first mounting element (47) relative to the mounting of the first transmission device (3) coincides with the second rotation axis (64) of the second mounting element (48) relative to the mounting of the second transmission device (33). As an alternative, the second rotation axis (64) of the first mounting element (47) relative to the mounting of the first transmission device (3) can be different and spaced with respect to the second rotation axis (64) of the second mounting element (48) relative to the mounting of the second transmission device (33). The description of the present invention has been made with reference to the enclosed figures in a preferred embodiment, but it is evident that many possible changes, modifications and variations will be immediately clear to those skilled in the art in the light of the previous description. Thus, it must be underlined that the invention is not limited to the previous description, but includes all the changes, modifications and variations in accordance with the appended claims.

Nomenclature used

With reference to the identification numbers in the enclosed figures, the following nomenclature has been used:

1. First electric motor

2. First safety joint

3. First transmission device

4. Transmission guide

5. Locking means . Transmission supporting compensator

7. Transmissions fixing and supporting structure

8. Base guides

9. Rolling cartridge

10. Anchorage base

11. Second electric motor

12. Second safety joint

13. Epicyclic reduction gear

14. Fourth self-compensated pinion

15. First crown

16. Second torque division pinion

17. First output pinion

18. Hub

19. Transmission slot

20. Rolling station

21. Second crown

22. Third torque division pinion

23. First helical gear

24. Second helical gear

25. Single motor

26. Toothed joint

27. Speed reducer with two output shafts

28. Adapter

29. Adapters supporting device

30. Cylinders adjustment reduction gear

31. First cylinder

32. Foundations

33. Second transmission device 34. Stand guides

35. First input shaft

36. First stage

37. First planetary gear

38. First planetary-gear support

39. Second shaft

40. Second stage

41. Second planetary gear

42. Second planetary-gear support

43. Third shaft

44. Second cylinder

45. Hooking means

46. Cartridge frame

47. First mounting element

48. Second mounting element

49. Adjustment means or cylinders adjustment means

50. First hinging means

51. Second hinging means

52. First end

53. Second end

54. First fixing interface

55. Second fixing interface

56. Eyelet

57. Third hinging means

58. Fourth hinging means

59. Central portion

60. First arm

61. Second arm 62. Coupling seat

63. First axis

64. Second axis

65. First plate

66. Second plate

67. Coupling

68. Movement means or transmission movement means

69. Fifth hinging means

70. Control device

71. First pin

72. First ring

73. Hole

74. First side

75. Second side

76. Second ring

77. Second hole

78. Second pin

79. Gear wheel

80. Worm screw

81. First nut screw

82. Second nut screw

83. First screw

84. Second screw

85. Protection tube

86. Scraper

Claims

1. Rolling station (20) intended to couple with a respective rolling cartridge or stand (9), said rolling cartridge or stand (9) being provided with rolling cylinders (31 , 44), respectively a first rolling cylinder (31 ) and a second rolling cylinder (44) which are opposite rolling cylinders (31 , 44) rotating around a respective first rotation axis (63), wherein said first rolling cylinder (31) is put in rotation by a first motor (1) by means of a first transmission device (3) and said second rolling cylinder (44) is put in rotation by a second motor (11) by means of a second transmission device (33), characterised in that said rolling station (20) includes an adjustment system (47, 48, 49, 54, 55, 67, 68) provided with two mounting elements (47, 48) of which a first mounting element (47) is intended to support in an overhanging way on said rolling station (20) said first transmission device (3) which is a gear transmission device coupled with the respective first motor (1) and of which a second mounting element (48) is intended to support in an overhanging way on said rolling station (20) said second transmission device (33) which is a gear transmission device coupled with said respective second motor ( 1) according to a single-block configuration without adapters or transmission shafts in which said transmission devices (3, 33) are supported by a fixing structure (7) of said transmission devices (3, 33) that supports said transmission devices (3, 33) in an overhanging way on said rolling station (20)

and further characterised in that said adjustment system (47, 48, 49, 54, 55, 67, 68) is intended for the adjustment of the reciprocal distance between a first transmission slot (19) rotating around said respective first rotation axis (63) and adapted for the engagement of a hub (18) of a respective cylinder selected from said pair of rolling cylinders (31 , 44) and a second transmission slot (19) rotating around said respective first rotation axis (63) and adapted for the engagement of a hub (18) of a respective other cylinder selected from said pair of rolling cylinders (31 , 44), said mounting elements (47, 48) of said adjustment system (47, 48, 49, 54, 55, 67, 68) being hinged in correspondence with a respective second rotation axis (64) that is in an eccentric position with respect to said first rotation axis (63), said adjustment of the reciprocal distance between said first and second transmission slots (19) occurring by means of a rotation of said first axis (63) around said second rotation axis (64) according to approaching or spacing directions between said first and said second transmission slots (19), said rolling station constituting a single block station incorporating in a configuration without adapters or transmission shafts said transmission slots (19), said transmission devices (3, 33), said motors (1 , 11).

2. Rolling station (20) according to claim 1 , characterised in that said second rotation axis (64) around which the rotation of said at least one of said mounting elements (47, 48), which supports one between said first transmission device (3) and said second transmission device (33), occurs, is a second rotation axis (64) essentially parallel to said first rotation axis (63).

3. Rolling station (20) according to claim 2, characterised in that said second rotation axis (64) around which the rotation of said at least one of said mounting elements (47, 48), which supports one between said first transmission device (3) and said second transmission device (33), occurs, is essentially coincident with the second rotation axis (64) around which the rotation of corresponding mounting elements (47, 48) supporting one between said first cylinder (31) and said second cylinder (44) on said rolling cartridge or stand (9) occurs.

4. Rolling station (20) according to any of the previous claims, characterised in that it includes movement means (68) of one of said transmission devices (3, 33), said movement means (68) being intended to perform said action of adjustment of the reciprocal distance between said first transmission slot (19) and said second transmission slot (19) by means of an adjustment force acting between one of said mounting elements (47, 48) and a transmissions fixing and supporting structure (7), preferably comprising two of said movement means (68) of which one is intended for the movement of said first transmission device (3) and of which another is intended for the movement of said second transmission device (33), said two movement means (68) being controlled in a reciprocally synchronized way, the synchronization being obtained by means of control means that detect the position of said two movement means (68) or of the transmission devices (3, 33) or of actuation means between the movement means (68) and the transmission devices (3, 33) themselves through pulse sensors or encoders.

5. Rolling station (20) according to any of the previous claims, characterised in that said mounting elements (47, 48) are shaped with a central body which is provided with insertion seats for the insertion of one of said transmission devices (3, 33).

6. Rolling station (20) according to claim 5 and according to claim 4, characterised in that said transmission movement means (68) couple with said central body of one of said mounting elements (47, 48) of the transmissions (3, 33) by means of a coupling (67) which is placed in an eccentric position with respect to said first rotation axis (63) around which the respective rolling cylinder (31 , 44) is put in rotation.

7. Rolling station (20) according to claim 6, characterised in that in the movement induced by said movement means (68) said coupling (67) is guided by means of transmission guides (4) which are obtained on said transmissions fixing and supporting structure (7).

8. Rolling station (20) according to any of the previous claims 6 to 7, characterised in that said coupling (67) is positioned in correspondence with a prolongation of a straight line joining the second rotation axis (64) and the first rotation axis (63), said coupling (67) lying on said prolongation of said straight line in correspondence with a position which is essentially opposite to said second rotation axis (64) with respect to said first rotation axis (63).

9. Rolling station (20) according to any of the previous claims 1 to 8, characterised in that said adjustment of the reciprocal distance between said first transmission slot (19) and said second transmission slot (19) occurs by means of:

- a rotation of said first mounting element (47) with a corresponding rotation of said first axis (63) around said second rotation axis (64);

or

- a rotation of said second mounting element (48) with a corresponding rotation of said first axis (63) around said second rotation axis (64); or

- a reciprocally coordinated rotation of said first mounting element (47) around said second rotation axis (64) and of said second mounting element (48) around said second rotation axis (64).

10. Rolling station (20) according to any of the previous claims 1 to 9, characterised in that said second rotation axis (64) of said first mounting element (47) which is relative to the mounting of said first transmission device (3) coincides with said second rotation axis (64) of said second mounting element (48) which is relative to the mounting of said second of transmission device (33)

or characterised in that said second rotation axis (64) of said first mounting element (47) which is relative to the mounting of said first transmission device (3) is different and spaced with respect to said second rotation axis (64) of said second mounting element (48) which is relative to the mounting of said second transmission device (33).

11. Rolling station (20) according to any of the previous claims 1 to 10, characterised in that said adjustment system (47, 48, 49, 54, 55, 67, 68) includes at least second position transducers which are intended to detect a second detected position of at least one between said first transmission device (3) and said second transmission device (33) in order to transmit data relative to said second detected position of at least one between said first transmission device (3) and said second transmission device (33).

12. Rolling station (20) according to any of the previous claims 1 to 11 , characterised in that said first motor (1) and said second motor (11) are controllable in an independent way of each other and/or in a coordinated way with respect to each other.

13. Rolling station (20) according to claim 12, characterised in that said first motor (1) and said second motor (11) are controllable in an independent way of each other with different rotation speeds, the rotation speed difference of said first motor (1) and said second motor (11) corresponding to a difference in the rotation speed of said first cylinder (31) with respect to the rotation speed of said second cylinder (44).

14. Rolling station (20) according to claim 13, characterised in that said rotation speed difference of said first motor (1) and said second motor (11 ) is controllable in a manually and/or automatically controlled way according to rolling parameters.

15. Rolling station (20) according to any of the previous claims 1 to 14, characterised in that said first transmission (3) or said second transmission (33) include a first output pinion (17) provided with said transmission slot (19) for the engagement of said hub (18) of a respective cylinder selected from said two cylinders (31 , 44) of said stand or cartridge (9), said first output pinion (17) being controlled in rotation by means of the combined and coordinated action of a second torque division pinion (16) integral with a first crown (15) by which it is put in rotation and of a third torque division pinion (22) integral with a second crown (21) by which it is put in rotation.

16. Rolling station (20) according to claim 15, characterised in that said first crown (15) and said second crown (21) are put in rotation by means of a fourth self-compensated pinion (14) which is provided with a double toothed band in which a first toothed band constitutes a first gear (23) transmitting the rotational motion to said first crown ( 5) and in which a second toothed band constitutes a second gear (24) transmitting the rotational motion to said second crown (21).

17. Rolling station (20) according to claim 16, characterised in that said rotational motion transmission first gear (23) and said rotational motion transmission second gear (24) are respectively a first helical gear (23) shaped with a first screw and a second helical gear (24) shaped with a second screw, in which the first screw constituting the first helical gear (23) is made according to a shape opposite to the second screw constituting the second helical gear (24), said first screw having the respective teeth of said first helical gear (23) oriented according to an opposite orientation with respect to the orientation of the teeth of said second screw of said second helical gear (24).

18. Rolling station (20) according to any of the previous claims 16 to 17, characterised in that said fourth self-compensated pinion (14) receives the rotational motion from one of said first motor (1) or second motor (11) with the interposition of an epicyclic reduction gear (13).

19. Rolling station (20) according to claim 18, characterised in that said epicyclic reduction gear (13) is made up of a first stage (36) on which a first input shaft (35) engages, preferably consisting of the output shaft of said first motor (1) or second motor (1 1), said first input shaft (35) acting on first planetary gears (37) of said first stage (36) which are rotationally supported by a first planetary-gear support (38) which in turn puts in rotation a second shaft (39), said second shaft (39) transmitting the rotational motion from said first stage (36) to a second stage (40), said second shaft (39) acting on second planetary gears (41) of said second stage (40), which are rotationally supported by a second planetary-gear support (42) which in turn puts in rotation a third shaft (43), said third shaft (43) in turn coupling with said fourth self-compensated pinion (14).

20. Rolling mill plant for the manufacture of oblong metal products, characterised in that it includes at least one rolling station (20) made according to any of the previous claims 1 to 19.