EP3519122B1 - Ring rolling mill with conformation rolls and process for controlling the position of a roll of such a rolling mill - Google Patents

Ring rolling mill with conformation rolls and process for controlling the position of a roll of such a rolling mill Download PDF

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Publication number
EP3519122B1
EP3519122B1 EP17777254.8A EP17777254A EP3519122B1 EP 3519122 B1 EP3519122 B1 EP 3519122B1 EP 17777254 A EP17777254 A EP 17777254A EP 3519122 B1 EP3519122 B1 EP 3519122B1
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EP
European Patent Office
Prior art keywords
rack
bar
rolling mill
roller
variable volume
Prior art date
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Application number
EP17777254.8A
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German (de)
French (fr)
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EP3519122A1 (en
Inventor
Peter Bierhalter
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Forge Pat GmbH
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Forge Pat GmbH
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Priority to PL17777254T priority Critical patent/PL3519122T3/en
Publication of EP3519122A1 publication Critical patent/EP3519122A1/en
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Publication of EP3519122B1 publication Critical patent/EP3519122B1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B21B31/32—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis by liquid pressure, e.g. hydromechanical adjusting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H1/00—Making articles shaped as bodies of revolution
    • B21H1/06—Making articles shaped as bodies of revolution rings of restricted axial length
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/08—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with differently-directed roll axes, e.g. for the so-called "universal" rolling process
    • B21B13/10—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with differently-directed roll axes, e.g. for the so-called "universal" rolling process all axes being arranged in one plane
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/48—Tension control; Compression control
    • B21B37/52—Tension control; Compression control by drive motor control

Definitions

  • the invention relates to a circular rolling mill which comprises two pairs of rollers intended to form radial faces and end faces of an annular part.
  • rollers In this type of rolling mill, it is known that the rollers must be moved, during operation of the rolling mill, to adapt their position to the dimensions of the part being shaped.
  • hydraulic cylinders can be used to move the rollers. This makes it necessary to have a large quantity of pressurized oil, to the point that a relatively large hydraulic unit must be provided near the rolling mill.
  • the invention more particularly intends to remedy by proposing a circular rolling mill in which the rollers can be moved by an electric gear motor, without it being necessary to install this electric gear motor on a swivel support.
  • the invention relates to a circular rolling mill comprising a fixed main frame, a pair of cylindrical rollers, internal and external respectively, intended to shape the internal and external radial faces of an annular part and supported by a first auxiliary frame mounted. on the main frame, and a pair of tapered rollers, upper and lower respectively, intended to shape opposite end faces of the part and supported by a second auxiliary frame mounted on the main frame.
  • a pinion-rack assembly for translational displacement of a roller relative to the auxiliary frame which supports it and at least one electric gear motor for driving the pinion of this pinion-rack assembly.
  • the electric gear motor is mounted fixedly relative to one of the auxiliary frames, while a fluidic discharge mechanism is interposed in a kinematic force transmission chain between the rack and the roller moved by this rack.
  • the fluidic discharge mechanism comprises at least one chamber of variable volume supplied with pressurized fluid and the volume of which varies according to the relative position of the roller and the rack.
  • the motor mounting mode makes it possible to constitute a fixed point, which allows precise control of the pinion-rack assembly, and therefore of the position of the associated roller.
  • the fluidic discharge mechanism makes it possible to absorb the transient overload transmitted to the kinematic chain, without the rack being moved, and therefore without risk of damaging the electric gear motor.
  • the rolling mill 2 shown in figures 1 to 10 comprises a fixed main frame 4 which defines a longitudinal axis X2 of the rolling mill 2.
  • the frame 2 supports a radial cage 6 which is fixedly mounted on this frame, as well as an axial cage 8 movable relative to the frame 4, according to l 'X2 axis.
  • a first auxiliary frame 46 is fixedly mounted on the main frame 4 and constitutes the frame of the radial cage 6.
  • a second auxiliary frame 48 is mounted on the main frame 4 while being movable along the axis X2 with respect to to this main frame.
  • the auxiliary frame 48 constitutes the frame of the axial cage 8.
  • P a part being shaped in the rolling mill 2. This part is centered on a vertical axis XP and perpendicular to the axis X2.
  • P2 and P4 of the inner and outer radial surfaces of the part P.
  • P6 and P8 of the upper and lower end surfaces of this part P, when it is in place in the rolling mill 2.
  • the frame 46 of the radial cage 6 supports a cylindrical main roller 62 rotatably mounted about a vertical axis Z62 and driven in rotation by a main electric motor 64.
  • the main roller 62 is mounted in the radial cage 6 to bear against the external radial surface P4 of the part P.
  • the frame 46 of the radial cage 6 also supports a cylindrical secondary roller or mandrel 66 rotatably mounted about a vertical axis Z66 parallel to the axis Z62.
  • the secondary roller 66 is supported by a cross member 68 which is movable, parallel to the axis X2, relative to the secondary frame 46 of the radial cage 6.
  • the cross member 68 is secured to two bars 72 and 74 which s 'each extend in a direction parallel to the axis X2.
  • the rollers 62 and 66 are solid and of circular section.
  • a plate 70 is mounted below the cross member 68 and provided with a housing 70A for receiving the lower part of the secondary roller 66.
  • This plate 70 is also movable relative to the auxiliary frame 46 by being supported by two. bars 76 and 78.
  • the radial cage 6 also comprises two centering arms of the part P, only one of these centering arms being visible at the figure 1 with the reference 65.
  • a rack-and-pinion lifting system 77 and 79 makes it possible to lift the crossbar 68 during the installation of the part P in the rolling mill 2, then to lower it to introduce the lower part of the secondary roller 66 into the housing 70A of the plate 70.
  • the gear motor 172 includes an electric motor 172A and a gearbox 172B.
  • the other geared motors have the same structure, each with an electric motor associated with a reduction gear.
  • the geared motor 174 is omitted, to allow viewing of the bar 74 and the associated pinion 273.
  • the bars 72 to 78 make it possible to transmit to the roller 66 a displacement movement, parallel to the axis X2 and to each of the axes X72 to X78, generated by the geared motors 172 to 178.
  • Each of the geared motors 172 to 178 is fixedly mounted relative to the auxiliary frame 46 of the radial cage 6.
  • the geared motor 172 is rigidly supported by a plate 46A belonging to the auxiliary frame 46.
  • the geared motor 174 is rigidly supported by a plate 46B belonging to the auxiliary frame 46.
  • the geared motors 176 and 178 are supported by plates 46C and 46D of the auxiliary frame 46.
  • the plates 46A and 46B are omitted. to the figures 3 to 7 . We notice at the figure 1 that they also support the 163 and 165 geared motors. This is not, however, compulsory.
  • the part P is compressed radially between the rollers 62 and 66 which are driven in rotation, around the axes Z62 and Z66, directly by the motor 64, for the roller 62, and indirectly through the part P, for the roller 66.
  • a pinion-rack assembly is used to transmit a movement of each geared motor 172 to 178 to the secondary roller or mandrel 66, in order to control the position of this roller in translation along the axis X2.
  • a pinion 273 is mounted on the output shaft of the reducer 172B. This pinion 273 cooperates with a rack 272 mounted on the bar 72.
  • the mounting of the rack 272 on the bar 72 is rigid in the normal configuration of use of the rolling mill 2.
  • This mounting however includes a degree of freedom, which can be implemented in the event of irregularity on the surface P2 of the part P , in a sense where a protruding relief present on this surface P2 tends to move the secondary roller or mandrel 66 in the direction of the axis XP.
  • a degree of freedom is implemented in mounting the rack 272 on the bar 72 when an irregularity results from a protruding relief on the surface P4 which tends to push the part P and the secondary roller 66 in the direction of the axis XP, by reaction against the main roller 62 whose axis Z62 is fixed relative to the auxiliary frame 46.
  • a fluidic discharge mechanism M72 is integrated in the bar 72 and makes it possible to authorize a relative displacement, along the axis X72, between the roller 62 and the rack 272, more precisely between the rack 272 and the bar 72 which is rigidly fixed to the roller 66, along the axis X2, by the intermediary of the crosspiece 68.
  • the mechanism M72 comprises a support 720 rigidly linked to the rack 272, for example by screws not shown.
  • This support 720 is received in a housing 722 formed inside the bar 72, with an axial length L722, measured parallel to the axis X72, which is greater than the axial length L720 of the support 720, also measured parallel to this. axis.
  • the mechanism M72 also comprises a piston 724 which is disposed in a terminal housing 726 formed at the level of the end 72A of the bar 72 which is opposite to the cross member 68, therefore to the secondary roller 66.
  • the terminal housing 726 is closed by a cover 728 rigidly fixed to bar 72.
  • the mechanism M72 also comprises a rod 723 for connecting the support 720 and the piston 724.
  • the compression of the rod 723 between the support 720 and the piston 724 makes it possible to create between the parts 720, 723 and 724 a rigid connection in translation parallel to the axis X72 when the support moves the piston to the right at the figure 5 or when the piston moves the support to the left in this figure.
  • the parts 72, 272, 720, 723 and 724 are made of metal, for example steel.
  • Guide pads 727 for example made of bronze, are provided on the support 720 to guide it inside the housing 722 and to facilitate its sliding.
  • guide rings 729 for example made of copper, are provided around the rod 723, inside the channel 725. As a variant, only the pads 727 or the pads 729 are provided.
  • the piston 724 is equipped with seals 724A which allow it to isolate a part of the terminal housing 726, located between its face 724B facing the cover 728 and this cover, of the channel 725.
  • seals 724A which allow it to isolate a part of the terminal housing 726, located between its face 724B facing the cover 728 and this cover, of the channel 725.
  • a chamber C72 of variable volume is defined in the terminal housing 726, between the face 724B of the piston 724 and the cover 728.
  • This variable volume chamber C72 is supplied with pressurized oil through an orifice 728A of the cover 728 and a conduit 732 which belongs to a system 73 for supplying the chamber C72 with pressurized oil, with a pressure greater than 100 bars.
  • the pressure delivered by the system 73 is chosen to be greater than 200 bars, preferably of the order of 250 bars.
  • System 73 may include, as shown schematically in figures 3 , 5 and 7 , a pump 734 which delivers the oil at the set pressure, drawing it from a tank 736, while a calibrated non-return valve 738 connects the pipe 732 to the tank 736.
  • the system 73 makes it possible to deliver oil to the interior of the chamber C72 at a pressure equal to the outlet pressure of the pump 734.
  • the valve 738 is preferably calibrated so that, if the pressure in the chamber C72 and in the duct 732 exceeds the outlet pressure of the pump 734, the oil present in the duct 732 is returned to the tank 736, through this valve.
  • System 73 is a system known in the hydraulic field. Taking into account the volume of oil that it contains, of the order of one or two liters, it is much easier to implement and much less expensive than the units conventionally used in rolling mills to supply jacks intended for move the shaping rollers.
  • the M72 discharge mechanism includes bar 72 as well as parts and volumes 720 through 729.
  • the pressure of the oil present in the chamber C72 is sufficient to stiffen the kinematic connection between the rack 272 and the bar 72, therefore between the rack 272 and the secondary roller 66, during normal operation of the rolling mill 2.
  • the bars 74, 76 and 78 are also connected to the motors 174, 176 and 178 by kinematic chains which each include a fluidic discharge mechanism of the type of the M72 mechanism, the M74 mechanism used for the bar 74 being visible at the bottom. figure 3 , while the corresponding mechanisms M76 and M78 used for the bars 76 and 78 are masked by the plates 46C and 46D.
  • the discharge mechanism M74 is inserted between, on the one hand, an assembly comprising a pinion 275 and a rack 274 and, on the other hand, the cross member 68, by means of the bar 74.
  • the mechanisms M76 and M78 are inserted between, on the one hand, the pinion-rack assemblies mounted at the foot of the geared motors 176 and 178 and, on the other hand, the plate 70.
  • the rolling mill is in the configuration of figures 3 to 5 .
  • a single power supply system 73 is shown.
  • a system can be provided for supplying the discharge mechanism M72, M74 or equivalent associated with each bar 74 to 78, or a system common to some or all of these mechanisms.
  • the secondary roller 66 In case of protruding relief on one of the radial surfaces P2 or P4 of the part P, the secondary roller 66 is temporarily moved towards the axis XP, which causes the displacement of the cross member 68 and the plate 70 in the same direction, to the left to the figure 2 .
  • the bar 72 Under the effect of the temporary displacement of the cross member 68, the bar 72 is moved abruptly in the direction of the axial cage 8, in the direction of the arrow F1 at the figure 7 . This movement should be prevented from being transmitted to the geared motor 172, to limit the risk of breakage and premature wear of this material.
  • This movement of the bar 72 is transmitted to the cover 728, which has the effect of increasing the oil pressure inside the variable volume chamber C72. This pressure increase results in the ejection of oil from chamber C72 to supply system 73, through orifice 728A.
  • the pressure of the oil leaving the chamber C72 is greater than the output pressure of the pump 734 and the oil, blocked by the non-return valve 739, flows back to the tank 736, through valve 738, as shown by arrow F2 at figure 7 .
  • the piston 724 which is rigidly fixed to the rack 272 through the rod 723 and the support 720, moves inside the housing 726 in a direction of reducing the volume of the chamber C72.
  • the unloading mechanism M72 allows a relative displacement of the rack 272 and the bar 72, which avoids transmitting to the pinion 273 and, through it, to the geared motor 172 a violent acceleration liable to damage the 172A motor and / or the 172B reducer.
  • the discharge mechanism M72 therefore constitutes a mechanism for protecting the electric motor 172A, the reducer 172B and the pinion-rack assembly 272-273 against violent accelerations that may result from surface irregularities of the part P in conformation course in the rolling mill 2.
  • the axial cage 8 comprises two conical rollers 82 and 84 intended to act respectively on the upper front surface P6 and on the lower front surface P8 of the part P.
  • the tapered rollers 82 and 84 are each rotated by an electric motor 86 or 88 and supported by the auxiliary frame 48.
  • the roller 82 is supported by a plate 90 which is movable vertically, along an axis Z90 parallel to the axes Z62 and Z66, relative to the secondary frame 48.
  • the plate 90 is rigidly fixed to a shoe 91, itself coupled to the lower end 92A of a bar or column 92.
  • the bar 92 makes it possible to transmit to the roller 82 a displacement movement in translation along its longitudinal axis X92 coincident with the axis Z90.
  • the movement of the bar 92 along the Z90 axis is controlled by a double-toothed rack 292, itself controlled by two geared motors 192 and 194 fixedly mounted on the frame 48.
  • Pinions 293 and 295 are respectively mounted on the output shafts of geared motors 192 and 194 and mesh simultaneously with the two toothings provided, on either side of axis Z90, on rack 292.
  • the rack is guided in translation along the axis Z90 by rails formed in guide plates 197 and 199, the plate 199 being partially torn away from the figure 8 and completely withdrawn from figures 9 and 10 , for clarity of the drawings.
  • the plates 197 and 199 form part of the auxiliary frame 48.
  • the geared motors 192 and 194 are attached to the frame 48 through the plate 197.
  • the upper end of the bar 92 forms a piston 924 which is engaged, in a sealed manner by virtue of a seal 924A, in a hollow housing 926 formed in the lower part of the rack 292, in the center thereof.
  • a duct 291 passes through the rack 292 over its entire height, from the housing 926, which makes it possible to connect the chamber.
  • C92 to a 93 power supply system this chamber in pressurized oil.
  • System 93 includes conduit 932, pump 934, drip tray 936, calibrated check valve 938, and check valve 739.
  • the supply system 93 may or may not be identical to the supply system 73. These systems may be confused.
  • the pressure in the chamber C92 is sufficient for the kinematic connection between the rack 292 and the upper conical roller 82 to be rigid, which makes it possible to precisely control the height of this roller.
  • the operation is here comparable to that mentioned previously with regard to the discharge mechanism M72.
  • a discharge mechanism M92 which makes it possible to precisely control the height of the conical roller 82 relative to the auxiliary frame 48, in normal operation of the rolling mill 2 and to accommodate any surface irregularity on the one of the front surfaces P6 or P8, without risking damage to the geared motors 192 and 194, while the latter are mounted rigidly with respect to the secondary frame 48.
  • the systems 73 and 93 can be replaced by other systems for supplying the chambers of variable volume C72, C74, C92, etc. with pressurized oil at a given pressure. It is in particular possible to use an accumulator tank loaded with oil at the desired pressure and associated with a calibrated discharge valve, or a booster chamber.
  • the rod 273 is rigidly linked to the support 720 and to the piston 724, which allows oil to be sucked into the booster chamber, like a syringe, before put the variable volume chamber C72 or equivalent under a pressure of the order of 250 bars by pushing back the piston 724, after having cut off the communication between this chamber and the booster chamber.
  • the invention is implemented to control the movement, in translation with respect to the frames 46 and 48, of the rollers 66 and 82. As a variant, it can be used for a single of these rolls.
  • the bars 72 and 74, on the one hand, and the bars 76 and 78, on the other hand can be interconnected by rear cross members arranged opposite the cross member. 68 and the plate 70.
  • a rack-and-pinion assembly driven by one or more geared motors can be provided to control the movement of each rear cross member along the axis X2.
  • the structure of the pinion-rack assembly mounted on the auxiliary frame 46 can be inspired by that shown in the figures for the axial cage 8, with an equivalent of the bar 92 which is arranged horizontally and which attacks each rear cross member, in one direction. distance from the axis Z62 of the main roller 62.
  • a single rack and pinion assembly is used to move the two rear cross members and, through them, the four columns.
  • a single cross member connects the four bars 72 to 78.
  • the number of traction bars used to control the translation of the roller 66 along the axis X2 may be different from four.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Crushing And Grinding (AREA)
  • Transmission Devices (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)
  • Press Drives And Press Lines (AREA)
  • Metal Rolling (AREA)

Description

L'invention a trait à un laminoir circulaire qui comprend deux paires de rouleaux destinées à façonner des faces radiales et des faces frontales d'une pièce annulaire.The invention relates to a circular rolling mill which comprises two pairs of rollers intended to form radial faces and end faces of an annular part.

Dans ce type de laminoir, il est connu que les rouleaux doivent être déplacés, en cours de fonctionnement du laminoir, pour adapter leur position aux dimensions de la pièce en cours de conformation. De façon classique, des vérins hydrauliques peuvent être utilisés pour déplacer les rouleaux. Ceci impose de disposer d'huile sous pression en quantité importante, au point qu'une centrale hydraulique relativement volumineuse doit être prévue à proximité du laminoir.In this type of rolling mill, it is known that the rollers must be moved, during operation of the rolling mill, to adapt their position to the dimensions of the part being shaped. Conventionally, hydraulic cylinders can be used to move the rollers. This makes it necessary to have a large quantity of pressurized oil, to the point that a relatively large hydraulic unit must be provided near the rolling mill.

Pour pallier ce problème, il est connu de WO-A-2009/125102 , qui forme la base du préambule des revendications 1 et 15, d'utiliser, pour déplacer des rouleaux d'un laminoir circulaire, des ensembles pignons-crémaillères dont le pignon est entraîné en rotation par l'arbre de sortie d'un moto-réducteur électrique. Pour limiter les risques de casse en cas d'irrégularité de la surface avec laquelle interagit un rouleau, il est prévu de monter le moto-réducteur électrique sur un support, lui-même articulé autour de l'axe de rotation du pignon, par rapport à un châssis du laminoir. En outre, des moyens d'amortissement sont prévus pour amortir le pivotement du support. Le montage du moto-réducteur électrique sur un support articulé complexifie le laminoir, ce qui augmente son prix de revient et entraîne des opérations de maintenance supplémentaires.To overcome this problem, it is known to WO-A-2009/125102 , which forms the basis of the preamble of claims 1 and 15, to use, to move rollers of a circular rolling mill, rack and pinion assemblies, the pinion of which is driven in rotation by the output shaft of a motor. electric reducer. To limit the risk of breakage in the event of irregularity in the surface with which a roller interacts, it is planned to mount the electric geared motor on a support, itself articulated around the axis of rotation of the pinion, relative to to a rolling mill frame. In addition, damping means are provided to damp the pivoting of the support. Mounting the electric gear motor on an articulated support complicates the rolling mill, which increases its cost price and entails additional maintenance operations.

C'est à ces inconvénients qu'entend plus particulièrement remédier l'invention en proposant un laminoir circulaire dans lequel les rouleaux peuvent être déplacés par un moto-réducteur électrique, sans qu'il soit nécessaire d'installer ce mot-réducteur électrique sur un support pivotant.It is these drawbacks that the invention more particularly intends to remedy by proposing a circular rolling mill in which the rollers can be moved by an electric gear motor, without it being necessary to install this electric gear motor on a swivel support.

A cet effet, l'invention concerne un laminoir circulaire comprenant un châssis principal fixe, une paire de rouleaux cylindriques, respectivement interne et externe, destinés à façonner des faces radiales interne et externe d'une pièce annulaire et supportés par un premier châssis auxiliaire monté sur le châssis principal, et une paire de rouleaux coniques, respectivement supérieur et inférieur, destinés à façonner des faces frontales opposées de la pièce et supportés par un deuxième châssis auxiliaire monté sur le châssis principal. Il est prévu au moins un ensemble pignon-crémaillère de déplacement en translation d'un rouleau par rapport au châssis auxiliaire qui le supporte et au moins un moto-réducteur électrique d'entraînement du pignon de cet ensemble pignon-crémaillère. Conformément à l'invention, le moto-réducteur électrique est monté de façon fixe par rapport à l'un des châssis auxiliaires, alors qu'un mécanisme à décharge fluidique est intercalé dans une chaîne cinématique de transmission d'effort entre la crémaillère et le rouleau déplacé par cette crémaillère. En outre, le mécanisme à décharge fluidique comprend au moins une chambre de volume variable alimentée en fluide sous pression et dont le volume varie en fonction de la position relative du rouleau et de la crémaillère.To this end, the invention relates to a circular rolling mill comprising a fixed main frame, a pair of cylindrical rollers, internal and external respectively, intended to shape the internal and external radial faces of an annular part and supported by a first auxiliary frame mounted. on the main frame, and a pair of tapered rollers, upper and lower respectively, intended to shape opposite end faces of the part and supported by a second auxiliary frame mounted on the main frame. There is provided at least one pinion-rack assembly for translational displacement of a roller relative to the auxiliary frame which supports it and at least one electric gear motor for driving the pinion of this pinion-rack assembly. In accordance with the invention, the electric gear motor is mounted fixedly relative to one of the auxiliary frames, while a fluidic discharge mechanism is interposed in a kinematic force transmission chain between the rack and the roller moved by this rack. In addition, the fluidic discharge mechanism comprises at least one chamber of variable volume supplied with pressurized fluid and the volume of which varies according to the relative position of the roller and the rack.

Grâce à l'invention, le fait que le moto-réducteur électrique est monté de façon fixe par rapport au châssis principal ou secondaire simplifie la structure générale du laminoir. En fonctionnement normal, le mode de montage du moteur permet de constituer un point fixe, ce qui autorise un pilotage précis de l'ensemble pignon-crémaillère, donc de la position du rouleau associé. En cas d'irrégularité sur la surface façonnée par le rouleau, le mécanisme à décharge fluidique permet d'absorber la surcharge transitoire transmise à la chaîne cinématique, sans que la crémaillère soit déplacée, donc sans risque d'endommager le moto-réducteur électrique.Thanks to the invention, the fact that the electric gear motor is mounted in a fixed manner relative to the main or secondary frame simplifies the general structure of the rolling mill. In normal operation, the motor mounting mode makes it possible to constitute a fixed point, which allows precise control of the pinion-rack assembly, and therefore of the position of the associated roller. In the event of irregularity on the surface formed by the roller, the fluidic discharge mechanism makes it possible to absorb the transient overload transmitted to the kinematic chain, without the rack being moved, and therefore without risk of damaging the electric gear motor.

Selon des aspects avantageux mais non obligatoires de l'invention, un tel laminoir peut incorporer une ou plusieurs des caractéristiques suivantes, prises dans toute combinaison techniquement admissible :

  • La chaîne cinématique comprend une barre de transmission au rouleau d'un mouvement de déplacement de la crémaillère selon un axe longitudinal de la barre et la chambre de volume variable est définie entre
    • d'une part la barre ou une pièce solidarisée à la barre ; et
    • d'autre part, la crémaillère ou une pièce rigidement fixée à la crémaillère.
  • La chambre de volume variable est définie à l'intérieur de la barre.
  • En variante, la chambre de volume variable est définie, selon l'axe longitudinal de la barre, entre la crémaillère et la barre.
  • Le laminoir comprend un système d'alimentation de la chambre de volume variable en fluide sous une pression supérieure ou égale à 100 bars, de préférence supérieure ou égale à 200 bars, de préférence encore de l'ordre de 250 bars.
  • La chaîne cinématique est configurée pour que, en cas d'irrégularité en saillie sur la surface d'une pièce annulaire façonnée par le rouleau, le déplacement induit par cette irrégularité sur la barre tend à chasser le fluide sous pression de la chambre de volume variable, par réduction de son volume.
  • Le mécanisme à décharge fluidique comprend un piston solidarisé à la crémaillère et dont une face définit la chambre de volume variable.
  • Le piston est monté coulissant à l'intérieur de la barre, selon l'axe longitudinal de la barre.
  • Le piston est solidarisé à la crémaillère par l'intermédiaire d'un support de crémaillère et d'une tige de liaison entre le support de crémaillère et le piston, le support de crémaillère et la tige de liaison étant également montés coulissants à l'intérieur de la barre, selon l'axe longitudinal de la barre.
  • Le laminoir comprend des organes de guidage en translation, selon l'axe longitudinal de la barre, du support de crémaillère et/ou de la tige de liaison, à l'intérieur de la barre, notamment des patins de guidage.
  • La chambre de volume variable est définie entre la face du piston et un couvercle qui obture un volume interne de la barre, à l'opposé du rouleau.
  • En variante, une partie de la barre est reçue de façon étanche dans une cavité interne définie par la crémaillère et la chambre de volume variable est formée par la portion de cette cavité non occupée par la barre.
  • La chambre de volume variable est reliée au système d'alimentation en fluide sous pression par un conduit qui traverse la crémaillère.
  • Chaque rouleau mobile en translation par rapport à un châssis secondaire est déplacé par un ensemble pignon-crémaillère entraîné par un moto-réducteur électrique monté de façon fixe par rapport à ce châssis, avec interposition d'un mécanisme à décharge fluidique dans la chaîne cinématique de transmission d'effort entre chaque crémaillère et le rouleau entraîné par cette crémaillère.
According to advantageous but not mandatory aspects of the invention, such a rolling mill can incorporate one or more of the following characteristics, taken in any technically acceptable combination:
  • The kinematic chain comprises a bar for transmitting to the roller a movement of displacement of the rack along a longitudinal axis of the bar and the variable volume chamber is defined between
    • on the one hand the bar or a part secured to the bar; and
    • on the other hand, the rack or a part rigidly fixed to the rack.
  • The variable volume chamber is defined inside the bar.
  • As a variant, the variable volume chamber is defined, along the longitudinal axis of the bar, between the rack and the bar.
  • The rolling mill comprises a system for supplying the chamber of variable volume with fluid at a pressure greater than or equal to 100 bars, preferably greater than or equal to 200 bars, more preferably of the order of 250 bars.
  • The kinematic chain is configured so that, in the event of a protruding irregularity on the surface of an annular part formed by the roller, the displacement induced by this irregularity on the bar tends to expel the pressurized fluid from the chamber of variable volume. , by reducing its volume.
  • The fluidic discharge mechanism comprises a piston secured to the rack and one face of which defines the chamber of variable volume.
  • The piston is slidably mounted inside the bar, along the longitudinal axis of the bar.
  • The piston is secured to the rack by means of a rack support and a connecting rod between the rack support and the piston, the rack support and the connecting rod also being slidably mounted inside of the bar, along the longitudinal axis of the bar.
  • The rolling mill comprises guide members in translation, along the longitudinal axis of the bar, of the rack support and / or of the connecting rod, inside the bar, in particular of the guide shoes.
  • The variable volume chamber is defined between the face of the piston and a cover which closes an internal volume of the bar, opposite the roller.
  • As a variant, part of the bar is received in a sealed manner in an internal cavity defined by the rack and the variable volume chamber is formed by the portion of this cavity not occupied by the bar.
  • The variable volume chamber is connected to the pressurized fluid supply system by a conduit which passes through the rack.
  • Each roller movable in translation relative to a secondary frame is moved by a pinion-rack assembly driven by an electric gear motor mounted fixedly relative to this frame, with the interposition of a fluidic discharge mechanism in the kinematic chain of transmission of force between each rack and the roller driven by this rack.

Selon un autre aspect, l'invention concerne un procédé de contrôle de la position d'au moins un rouleau de façonnage d'une face d'une pièce à conformer au sein d'un laminoir circulaire qui comprend un châssis principal fixe, une paire de rouleaux, respectivement interne et externe, destinés à façonner des faces radiales interne et externe de cette pièce et supportés par un premier châssis auxiliaire monté sur le châssis principal, ainsi qu'une paire de rouleaux coniques, respectivement supérieur et inférieur, destinée à façonner des faces frontales opposées de la pièce et supportés par un second châssis auxiliaire monté sur le châssis principal, ce laminoir comprenant également au moins un ensemble pignon-crémaillère de déplacement d'un rouleau par rapport au châssis auxiliaire qui le supporte et au moins un moto-réducteur électrique d'entraînement du pignon de cet ensemble pignon-crémaillère. Conformément à l'invention, ce procédé comprend des étapes consistant à ;

  1. a) alimenter en fluide sous pression une chambre de volume variable intégrée à un mécanisme de décharge intercalé dans une chaîne cinématique de transmission d'effort entre la crémaillère et le rouleau déplacé par cette crémaillère, pour rigidifier cette chaîne cinématique en fonctionnement normal du laminoir, et
  2. b) évacuer une partie au moins du fluide sous pression de la chambre de volume variable, grâce à une variation dimensionnelle de la chaîne cinématique, en cas d'irrégularité sur la face de la pièce à conformer façonnée par le rouleau.
According to another aspect, the invention relates to a method for controlling the position of at least one shaping roller of a face of a workpiece to be shaped within a circular rolling mill which comprises a fixed main frame, a pair of rollers, internal and external respectively, intended to shape the internal and external radial faces of this part and supported by a first auxiliary frame mounted on the main frame, as well as a pair of tapered rollers, upper and lower respectively, intended to shape opposite end faces of the part and supported by a second auxiliary frame mounted on the main frame, this rolling mill also comprising at least one pinion-rack assembly for moving a roller relative to the auxiliary frame which supports it and at least one motorbike -Electric gearbox for driving the pinion of this pinion-rack assembly. According to the invention, this method comprises steps consisting in;
  1. a) supplying pressurized fluid to a chamber of variable volume integrated into a discharge mechanism interposed in a kinematic transmission chain force between the rack and the roller moved by this rack, to stiffen this kinematic chain in normal operation of the rolling mill, and
  2. b) evacuating at least part of the pressurized fluid from the variable volume chamber, thanks to a dimensional variation of the kinematic chain, in the event of irregularity on the face of the part to be shaped shaped by the roller.

L'invention sera mieux comprise et d'autres avantages de celle-ci apparaîtront plus clairement à la lumière de la description qui va suivre, d'un mode de réalisation d'un laminoir et d'un procédé de contrôle conformes à son principe, donnée uniquement à titre d'exemple et faite en référence aux dessins annexés, dans lesquels :

  • la figure 1 est une vue en perspective d'un laminoir conforme à l'invention ;
  • la figure 2 est une coupe longitudinale de principe du laminoir, selon le plan II à la figure 1 ;
  • la figure 3 est une vue à plus grande échelle du détail III à la figure 1 lorsque le laminoir est dans première une configuration de fonctionnement normal ; pour la clarté du dessin, certaines plaques supports et un moto-réducteur sont omis sur cette figure 3 et certaines barres sont représentées partiellement arrachées ;
  • la figure 4 est une vue à plus grande échelle du détail IV à la figure 3 ;
  • la figure 5 est une vue de dessus correspondant au détail IV ;
  • la figure 6 est une vue analogue à la figure 4 lorsque le laminoir est dans une deuxième configuration de fonctionnement, en cas d'irrégularité sur une surface radiale d'une pièce en cours de façonnage au sein du laminoir ;
  • la figure 7 est une vue de dessus correspondant au détail de la figure 6 ;
  • la figure 8 est une vue à plus grande échelle du détail VIII à la figure 1 dans laquelle une plaque de guidage est partiellement omise pour la clarté du dessin ;
  • la figure 9 est une vue en élévation dans le sens de la flèche IX à la figure 8 lorsque le laminoir est dans une première configuration normale de fonctionnement ; pour la clarté du dessin, la plaque de guidage est totalement omise et
  • la figure 10 est vue analogue à la figure 9 lorsque le laminoir est dans une troisième configuration de fonctionnement, en cas d'irrégularité sur une surface frontale d'une pièce en cours de conformation dans le laminoir.
The invention will be better understood and other advantages thereof will appear more clearly in the light of the description which follows, of an embodiment of a rolling mill and of a control method in accordance with its principle, given by way of example only and made with reference to the accompanying drawings, in which:
  • the figure 1 is a perspective view of a rolling mill according to the invention;
  • the figure 2 is a longitudinal section of the rolling mill in principle, according to plane II at figure 1 ;
  • the figure 3 is a view on a larger scale of detail III at the figure 1 when the rolling mill is in a normal operating configuration; for clarity of the drawing, some support plates and a gear motor are omitted on this figure 3 and some bars are shown partially broken away;
  • the figure 4 is a view on a larger scale of detail IV at the figure 3 ;
  • the figure 5 is a top view corresponding to detail IV;
  • the figure 6 is a view similar to the figure 4 when the rolling mill is in a second operating configuration, in the event of irregularity on a radial surface of a part being shaped within the rolling mill;
  • the figure 7 is a top view corresponding to the detail of the figure 6 ;
  • the figure 8 is a view on a larger scale of detail VIII at the figure 1 in which a guide plate is partially omitted for clarity of the drawing;
  • the figure 9 is a view in elevation in the direction of arrow IX at the figure 8 when the rolling mill is in a first normal operating configuration; for clarity of the drawing, the guide plate is completely omitted and
  • the figure 10 is seen analogous to figure 9 when the rolling mill is in a third operating configuration, in the event of irregularity on a front surface of a part being shaped in the rolling mill.

Le laminoir 2 représenté sur les figures 1 à 10 comprend un châssis principal fixe 4 qui définit un axe longitudinal X2 du laminoir 2. Le châssis 2 supporte une cage radiale 6 qui est montée de façon fixe sur ce châssis, ainsi qu'une cage axiale 8 mobile par rapport au châssis 4, selon l'axe X2.The rolling mill 2 shown in figures 1 to 10 comprises a fixed main frame 4 which defines a longitudinal axis X2 of the rolling mill 2. The frame 2 supports a radial cage 6 which is fixedly mounted on this frame, as well as an axial cage 8 movable relative to the frame 4, according to l 'X2 axis.

Un premier châssis auxiliaire 46 est monté de façon fixe sur le châssis principal 4 et constitue l'armature de la cage radiale 6. Un deuxième châssis auxiliaire 48 est monté sur le châssis principal 4 en étant mobile le long de l'axe X2 par rapport à ce châssis principal. Le châssis auxiliaire 48 constitue l'armature de la cage axiale 8.A first auxiliary frame 46 is fixedly mounted on the main frame 4 and constitutes the frame of the radial cage 6. A second auxiliary frame 48 is mounted on the main frame 4 while being movable along the axis X2 with respect to to this main frame. The auxiliary frame 48 constitutes the frame of the axial cage 8.

On note P une pièce en cours de conformation dans le laminoir 2. Cette pièce est centrée sur un axe XP vertical et perpendiculaire à l'axe X2. On note respectivement P2 et P4 des surfaces radiales interne et externe de la pièce P. De la même façon, on note P6 et P8 des surfaces frontales supérieure et inférieure de cette pièce P, lorsqu'elle est en place dans le laminoir 2.We denote by P a part being shaped in the rolling mill 2. This part is centered on a vertical axis XP and perpendicular to the axis X2. We denote respectively P2 and P4 of the inner and outer radial surfaces of the part P. In the same way, we denote P6 and P8 of the upper and lower end surfaces of this part P, when it is in place in the rolling mill 2.

Le châssis 46 de la cage radiale 6 supporte un rouleau principal cylindrique 62 monté rotatif autour d'un axe vertical Z62 et entraîné en rotation par un moteur électrique principal 64. Le rouleau principal 62 est monté dans la cage radiale 6 pour venir en appui contre la surface radiale externe P4 de la pièce P.The frame 46 of the radial cage 6 supports a cylindrical main roller 62 rotatably mounted about a vertical axis Z62 and driven in rotation by a main electric motor 64. The main roller 62 is mounted in the radial cage 6 to bear against the external radial surface P4 of the part P.

Le châssis 46 de la cage radiale 6 supporte également un rouleau secondaire cylindrique ou mandrin 66 monté rotatif autour d'un axe vertical Z66 parallèle à l'axe Z62. Le rouleau secondaire 66 est supporté par une traverse 68 qui est mobile, parallèlement à l'axe X2, par rapport au châssis secondaire 46 de la cage radiale 6. Pour ce faire, la traverse 68 est solidaire de deux barres 72 et 74 qui s'étendent chacune selon une direction parallèle à l'axe X2.The frame 46 of the radial cage 6 also supports a cylindrical secondary roller or mandrel 66 rotatably mounted about a vertical axis Z66 parallel to the axis Z62. The secondary roller 66 is supported by a cross member 68 which is movable, parallel to the axis X2, relative to the secondary frame 46 of the radial cage 6. To do this, the cross member 68 is secured to two bars 72 and 74 which s 'each extend in a direction parallel to the axis X2.

Les rouleaux 62 et 66 sont pleins et à section circulaire.The rollers 62 and 66 are solid and of circular section.

Par ailleurs, un plateau 70 est monté en-dessous de la traverse 68 et pourvu d'un logement 70A de réception de la partie inférieure du rouleau secondaire 66. Ce plateau 70 est également mobile par rapport au châssis auxiliaire 46 en étant supporté par deux barres 76 et 78.Furthermore, a plate 70 is mounted below the cross member 68 and provided with a housing 70A for receiving the lower part of the secondary roller 66. This plate 70 is also movable relative to the auxiliary frame 46 by being supported by two. bars 76 and 78.

On note respectivement X78, X74, X76 et X78 les axes longitudinaux des barres 74 à 78 qui sont parallèles à l'axe X2.We denote respectively X78, X74, X76 and X78 the longitudinal axes of the bars 74 to 78 which are parallel to the axis X2.

La cage radiale 6 comprend également deux bras de centrage de la pièce P, un seul de ces bras de centrage étant visible à la figure 1 avec la référence 65.The radial cage 6 also comprises two centering arms of the part P, only one of these centering arms being visible at the figure 1 with the reference 65.

Un système de levage à crémaillères 77 et 79 permet de soulever la traverse 68 lors de la mise en place de la pièce P dans le laminoir 2, puis de l'abaisser pour introduire la partie inférieure du rouleau secondaire 66 dans le logement 70A du plateau 70.A rack-and-pinion lifting system 77 and 79 makes it possible to lift the crossbar 68 during the installation of the part P in the rolling mill 2, then to lower it to introduce the lower part of the secondary roller 66 into the housing 70A of the plate 70.

Plusieurs moto-réducteurs électriques sont prévus dans la cage radiale 6, à savoir :

  • deux moto-réducteurs électriques 172 et 174 d'entraînement des barres 72 et 74, selon leurs axes longitudinaux respectifs X72 et X74,
  • deux moto-réducteurs électriques 176 et 178 d'entraînement des barres 76 et 78, selon leurs axes longitudinaux respectifs X76 et X78,
  • deux moto-réducteurs électriques 163 et 165 d'entraînement en rotation des bras de centrage 65 et équivalent, autour d'axes verticaux Z63 et Z65.
Several electric geared motors are provided in the radial cage 6, namely:
  • two electric gear motors 172 and 174 for driving the bars 72 and 74, along their respective longitudinal axes X72 and X74,
  • two electric gear motors 176 and 178 for driving the bars 76 and 78, along their respective longitudinal axes X76 and X78,
  • two electric gear motors 163 and 165 for rotating the centering arms 65 and the like, around vertical axes Z63 and Z65.

Le moto-réducteur 172 comprend un moteur électrique 172A et un réducteur 172B. Les autres moto-réducteurs ont la même structure, avec chacun un moteur électrique associé à un réducteur.The gear motor 172 includes an electric motor 172A and a gearbox 172B. The other geared motors have the same structure, each with an electric motor associated with a reduction gear.

A la figure 3, le moto-réducteur 174 est omis, pour permettre la visualisation de la barre 74 et du pignon 273 associé.To the figure 3 , the geared motor 174 is omitted, to allow viewing of the bar 74 and the associated pinion 273.

Les barres 72 à 78 permettent de transmettre au rouleau 66 un mouvement de déplacement, parallèle à l'axe X2 et à chacun des axes X72 à X78, généré par les moto-réducteurs 172 à 178.The bars 72 to 78 make it possible to transmit to the roller 66 a displacement movement, parallel to the axis X2 and to each of the axes X72 to X78, generated by the geared motors 172 to 178.

Chacun des moto-réducteurs 172 à 178 est monté de façon fixe par rapport au châssis auxiliaire 46 de la cage radiale 6. Par exemple, le moto-réducteur 172 est supporté rigidement par une plaque 46A appartenant au châssis auxiliaire 46. De même, le moto-réducteur 174 est supporté rigidement par une plaque 46B appartenant au châssis auxiliaire 46. Les moto-réducteurs 176 et 178 sont supportés par des plaques 46C et 46D du châssis auxiliaire 46. Pour la clarté du dessin, les plaques 46A et 46B sont omises aux figures 3 à 7. On remarque à la figure 1 qu'elles supportent également les moto-réducteurs 163 et 165. Ceci n'est toutefois pas obligatoire.Each of the geared motors 172 to 178 is fixedly mounted relative to the auxiliary frame 46 of the radial cage 6. For example, the geared motor 172 is rigidly supported by a plate 46A belonging to the auxiliary frame 46. Likewise, the geared motor 174 is rigidly supported by a plate 46B belonging to the auxiliary frame 46. The geared motors 176 and 178 are supported by plates 46C and 46D of the auxiliary frame 46. For clarity of the drawing, the plates 46A and 46B are omitted. to the figures 3 to 7 . We notice at the figure 1 that they also support the 163 and 165 geared motors. This is not, however, compulsory.

En fonctionnement normal du laminoir 2, la pièce P est comprimée radialement entre les rouleaux 62 et 66 qui sont entraînés en rotation, autour des axes Z62 et Z66, de façon directe par le moteur 64, pour le rouleau 62, et indirecte à travers la pièce P, pour le rouleau 66.In normal operation of the rolling mill 2, the part P is compressed radially between the rollers 62 and 66 which are driven in rotation, around the axes Z62 and Z66, directly by the motor 64, for the roller 62, and indirectly through the part P, for the roller 66.

Un ensemble pignon-crémaillère est utilisé pour transmettre un mouvement de chaque moto-réducteur 172 à 178 vers le rouleau secondaire ou mandrin 66, afin de contrôler la position de ce rouleau en translation selon l'axe X2.A pinion-rack assembly is used to transmit a movement of each geared motor 172 to 178 to the secondary roller or mandrel 66, in order to control the position of this roller in translation along the axis X2.

Ainsi, un pignon 273 est monté sur l'arbre de sortie du réducteur 172B. Ce pignon 273 coopère avec une crémaillère 272 montée sur la barre 72.Thus, a pinion 273 is mounted on the output shaft of the reducer 172B. This pinion 273 cooperates with a rack 272 mounted on the bar 72.

Le montage de la crémaillère 272 sur la barre 72 est rigide en configuration normale d'utilisation du laminoir 2. Ce montage comprend toutefois un degré de liberté, qui peut être mis en œuvre en cas d'irrégularité sur la surface P2 de la pièce P, dans un sens où un relief en saillie présent sur cette surface P2 tend à déplacer le rouleau secondaire ou mandrin 66 en direction de l'axe XP. De même, un degré de liberté est mis en œuvre dans le montage de la crémaillère 272 sur la barre 72 lorsqu'une irrégularité résulte d'un relief en saillie sur la surface P4 qui tend à repousser la pièce P et le rouleau secondaire 66 en direction de l'axe XP, par réaction contre le rouleau principal 62 dont l'axe Z62 est fixe par rapport au châssis auxiliaire 46.The mounting of the rack 272 on the bar 72 is rigid in the normal configuration of use of the rolling mill 2. This mounting however includes a degree of freedom, which can be implemented in the event of irregularity on the surface P2 of the part P , in a sense where a protruding relief present on this surface P2 tends to move the secondary roller or mandrel 66 in the direction of the axis XP. Likewise, a degree of freedom is implemented in mounting the rack 272 on the bar 72 when an irregularity results from a protruding relief on the surface P4 which tends to push the part P and the secondary roller 66 in the direction of the axis XP, by reaction against the main roller 62 whose axis Z62 is fixed relative to the auxiliary frame 46.

Pour ce faire, et comme visible aux figures 3 à 7, un mécanisme à décharge fluidique M72 est intégré dans la barre 72 et permet d'autoriser un déplacement relatif, selon l'axe X72, entre le rouleau 62 et la crémaillère 272, plus précisément entre la crémaillère 272 et la barre 72 qui est rigidement fixée au rouleau 66, le long de l'axe X2, par l'intermédiaire de la traverse 68.To do this, and as visible to figures 3 to 7 , a fluidic discharge mechanism M72 is integrated in the bar 72 and makes it possible to authorize a relative displacement, along the axis X72, between the roller 62 and the rack 272, more precisely between the rack 272 and the bar 72 which is rigidly fixed to the roller 66, along the axis X2, by the intermediary of the crosspiece 68.

A la figure 3, les capots 46A et 46B sont omis et les barres 72 et 74 sont représentées à moitié arrachées selon un plan horizontal. Ceci permet de visualiser le mécanisme M72 et le mécanisme équivalent M74 associé à la barre 74.To the figure 3 , the covers 46A and 46B are omitted and the bars 72 and 74 are shown half cut away in a horizontal plane. This makes it possible to visualize the mechanism M72 and the equivalent mechanism M74 associated with the bar 74.

Le mécanisme M72 comprend un support 720 rigidement lié à la crémaillère 272, par exemple par des vis non représentées. Ce support 720 est reçu dans un logement 722 ménagé à l'intérieur de la barre 72, avec une longueur axiale L722, mesurée parallèlement à l'axe X72, qui est supérieure à la longueur axiale L720 du support 720, également mesurée parallèlement à cet axe. Ainsi, le support 720 peut coulisser à l'intérieur du logement 722, parallèlement à l'axe X72. Le mécanisme M72 comprend également un piston 724 qui est disposé dans un logement terminal 726 ménagé au niveau de l'extrémité 72A de la barre 72 qui est opposée à la traverse 68, donc au rouleau secondaire 66. Le logement terminal 726 est obturé par un couvercle 728 rigidement fixé à la barre 72.The mechanism M72 comprises a support 720 rigidly linked to the rack 272, for example by screws not shown. This support 720 is received in a housing 722 formed inside the bar 72, with an axial length L722, measured parallel to the axis X72, which is greater than the axial length L720 of the support 720, also measured parallel to this. axis. Thus, the support 720 can slide inside the housing 722, parallel to the axis X72. The mechanism M72 also comprises a piston 724 which is disposed in a terminal housing 726 formed at the level of the end 72A of the bar 72 which is opposite to the cross member 68, therefore to the secondary roller 66. The terminal housing 726 is closed by a cover 728 rigidly fixed to bar 72.

Le mécanisme M72 comprend également une tige 723 de liaison entre le support 720 et le piston 724. La tige 723, qui est par exemple en appui simple contre le support 720 et le piston 724, est disposée dans un canal central et longitudinal 725 de la tige 72 qui relie entre eux les logements 722 et 726. La compression de la tige 723 entre le support 720 et le piston 724 permet de créer entre les pièces 720, 723 et 724 une liaison rigide en translation parallèle à l'axe X72 lorsque le support déplace le piston vers la droite à la figure 5 ou lorsque le piston déplace le support vers la gauche sur cette figure.The mechanism M72 also comprises a rod 723 for connecting the support 720 and the piston 724. The rod 723, which is for example in simple abutment against the support 720 and the piston 724, is arranged in a central and longitudinal channel 725 of the rod 72 which interconnects the housings 722 and 726. The compression of the rod 723 between the support 720 and the piston 724 makes it possible to create between the parts 720, 723 and 724 a rigid connection in translation parallel to the axis X72 when the support moves the piston to the right at the figure 5 or when the piston moves the support to the left in this figure.

Les pièces 72, 272, 720, 723 et 724 sont réalisées en métal, par exemple en acier. Des patins de guidage 727, par exemple en bronze, sont prévus sur le support 720 pour le guider à l'intérieur du logement 722 et faciliter son coulissement. De la même façon, des bagues de guidage 729, par exemple en cuivre, sont prévues autour de la tige 723, à l'intérieur du canal 725. En variante, seuls les patins 727 ou les patins 729 sont prévus.The parts 72, 272, 720, 723 and 724 are made of metal, for example steel. Guide pads 727, for example made of bronze, are provided on the support 720 to guide it inside the housing 722 and to facilitate its sliding. Likewise, guide rings 729, for example made of copper, are provided around the rod 723, inside the channel 725. As a variant, only the pads 727 or the pads 729 are provided.

Le piston 724 est équipé de joints d'étanchéité 724A qui lui permettent d'isoler une partie du logement terminale 726, située entre sa face 724B tournée vers le couvercle 728 et ce couvercle, du canal 725. Ainsi, une chambre C72 de volume variable est définie dans le logement terminal 726, entre la face 724B du piston 724 et le couvercle 728.The piston 724 is equipped with seals 724A which allow it to isolate a part of the terminal housing 726, located between its face 724B facing the cover 728 and this cover, of the channel 725. Thus, a chamber C72 of variable volume is defined in the terminal housing 726, between the face 724B of the piston 724 and the cover 728.

Cette chambre de volume variable C72 est alimentée en huile sous pression à travers un orifice 728A du couvercle 728 et un conduit 732 qui appartient à un système 73 d'alimentation de la chambre C72 en huile sous pression, avec une pression supérieure à 100 bars. En pratique, la pression délivrée par le système 73 est choisie supérieure à 200 bars, de préférence de l'ordre de 250 bars. Le système 73 peut comprendre, comme cela est représenté schématiquement aux figures 3, 5 et 7, une pompe 734 qui délivre l'huile à la pression de consigne, en la puisant dans un bac 736, alors qu'un clapet anti-retour taré 738 relie le conduit 732 au bac 736. Un autre clapet anti-retour 739, monté en sens inverse du clapet anti-retour 738, à la sortie de la pompe 732, évite que de l'huile circule à travers la pompe, en sens inverse, c'est-à-dire de sa sortie vers son entrée.This variable volume chamber C72 is supplied with pressurized oil through an orifice 728A of the cover 728 and a conduit 732 which belongs to a system 73 for supplying the chamber C72 with pressurized oil, with a pressure greater than 100 bars. In practice, the pressure delivered by the system 73 is chosen to be greater than 200 bars, preferably of the order of 250 bars. System 73 may include, as shown schematically in figures 3 , 5 and 7 , a pump 734 which delivers the oil at the set pressure, drawing it from a tank 736, while a calibrated non-return valve 738 connects the pipe 732 to the tank 736. Another non-return valve 739, mounted in the opposite direction of the non-return valve 738, at the outlet of the pump 732, prevents oil from circulating through the pump, in the opposite direction, that is to say from its outlet to its inlet.

Ainsi, le système 73 permet de délivrer à l'intérieur de la chambre C72 de l'huile à une pression égale à la pression de sortie de la pompe 734. Le clapet 738 est, de préférence, taré de telle sorte que, si la pression dans la chambre C72 et dans le conduit 732 dépasse la pression de sortie de la pompe 734, l'huile présente dans le conduit 732 est renvoyée vers le bac 736, à travers ce clapet.Thus, the system 73 makes it possible to deliver oil to the interior of the chamber C72 at a pressure equal to the outlet pressure of the pump 734. The valve 738 is preferably calibrated so that, if the pressure in the chamber C72 and in the duct 732 exceeds the outlet pressure of the pump 734, the oil present in the duct 732 is returned to the tank 736, through this valve.

Le système 73 est un système connu dans le domaine hydraulique. Compte tenu du volume d'huile qu'il contient, de l'ordre d'un ou deux litres, il est beaucoup plus facile à mettre en œuvre et beaucoup moins onéreux que les centrales utilisées classiquement dans les laminoirs pour alimenter des vérins prévus pour déplacer les rouleaux de conformation.System 73 is a system known in the hydraulic field. Taking into account the volume of oil that it contains, of the order of one or two liters, it is much easier to implement and much less expensive than the units conventionally used in rolling mills to supply jacks intended for move the shaping rollers.

Le mécanisme à décharge M72 comprend la barre 72 ainsi que les pièces et volumes 720 à 729.The M72 discharge mechanism includes bar 72 as well as parts and volumes 720 through 729.

Par défaut, la pression de l'huile présente dans la chambre C72, de l'ordre de 250 bars, est suffisante pour rigidifier la liaison cinématique entre la crémaillère 272 et la barre 72, donc entre la crémaillère 272 et le rouleau secondaire 66, en fonctionnement normal du laminoir 2.By default, the pressure of the oil present in the chamber C72, of the order of 250 bars, is sufficient to stiffen the kinematic connection between the rack 272 and the bar 72, therefore between the rack 272 and the secondary roller 66, during normal operation of the rolling mill 2.

Les barres 74, 76 et 78 sont également reliées aux moteurs 174, 176 et 178 par des chaînes cinématiques qui incluent chacune un mécanisme à décharge fluidique du type du mécanisme M72, le mécanisme M74 utilisé pour la barre 74 étant visible à la figure 3, alors que les mécanismes correspondants M76 et M78 utilisés pour les barres 76 et 78 sont masqués par les plaques 46C et 46D. Le mécanisme à décharge M74 est inséré entre, d'une part, un ensemble comprenant un pignon 275 et une crémaillère 274 et, d'autre part, la traverse 68, par l'intermédiaire de la barre 74. Les mécanismes M76 et M78 sont insérés entre, d'une part, les ensembles pignons-crémaillères montés en pied des moto-réducteurs 176 et 178 et, d'autre part, le plateau 70.The bars 74, 76 and 78 are also connected to the motors 174, 176 and 178 by kinematic chains which each include a fluidic discharge mechanism of the type of the M72 mechanism, the M74 mechanism used for the bar 74 being visible at the bottom. figure 3 , while the corresponding mechanisms M76 and M78 used for the bars 76 and 78 are masked by the plates 46C and 46D. The discharge mechanism M74 is inserted between, on the one hand, an assembly comprising a pinion 275 and a rack 274 and, on the other hand, the cross member 68, by means of the bar 74. The mechanisms M76 and M78 are inserted between, on the one hand, the pinion-rack assemblies mounted at the foot of the geared motors 176 and 178 and, on the other hand, the plate 70.

Par défaut, le laminoir est dans la configuration des figures 3 à 5.By default, the rolling mill is in the configuration of figures 3 to 5 .

A la figure 3, un seul système d'alimentation 73 est représenté. En pratique, on peut prévoir un tel système pour alimenter le mécanisme à décharge M72, M74 ou équivalent associé à chaque barre 74 à 78, ou un système commun à certains ou à tous ces mécanismes.To the figure 3 , a single power supply system 73 is shown. In practice, such a system can be provided for supplying the discharge mechanism M72, M74 or equivalent associated with each bar 74 to 78, or a system common to some or all of these mechanisms.

En cas de relief en saillie sur l'une des surfaces radiales P2 ou P4 de la pièce P, le rouleau secondaire 66 est déplacé temporairement vers l'axe XP, ce qui entraîne le déplacement de la traverse 68 et du plateau 70 dans le même sens, vers la gauche à la figure 2.In case of protruding relief on one of the radial surfaces P2 or P4 of the part P, the secondary roller 66 is temporarily moved towards the axis XP, which causes the displacement of the cross member 68 and the plate 70 in the same direction, to the left to the figure 2 .

Ce déplacement est transmis aux barres 72 à 78 qui sont rigidement liées aux pièces 68 et 70.This movement is transmitted to the bars 72 to 78 which are rigidly linked to the parts 68 and 70.

Dans ce qui suit, on considère ce qui se passe au niveau de la barre 72, étant entendu que le fonctionnement est le même au niveau des barres 74 à 78.In what follows, we consider what happens at bar 72, it being understood that the operation is the same at bars 74 to 78.

Sous l'effet du déplacement temporaire de la traverse 68, la barre 72 est déplacée brutalement en direction de la cage axiale 8, dans le sens de la flèche F1 à la figure 7. Il convient d'éviter que ce mouvement ne soit transmis au moto-réducteur 172, pour limiter les risques de casse et l'usure prématurée de ce matériel. Ce déplacement de la barre 72 est transmis au couvercle 728, ce qui a pour effet d'augmenter la pression d'huile à l'intérieur de la chambre de volume variable C72. Cette augmentation de pression se traduit par l'éjection de l'huile de la chambre C72 vers le système d'alimentation 73, à travers l'orifice 728A. Dans ce cas, la pression de l'huile sortant de la chambre C72 est supérieure à la pression de sortie de la pompe 734 et l'huile, bloquée par le clapet anti-retour 739, s'écoule en retour vers le bac 736, à travers le clapet 738, comme représenté par la flèche F2 à la figure 7.Under the effect of the temporary displacement of the cross member 68, the bar 72 is moved abruptly in the direction of the axial cage 8, in the direction of the arrow F1 at the figure 7 . This movement should be prevented from being transmitted to the geared motor 172, to limit the risk of breakage and premature wear of this material. This movement of the bar 72 is transmitted to the cover 728, which has the effect of increasing the oil pressure inside the variable volume chamber C72. This pressure increase results in the ejection of oil from chamber C72 to supply system 73, through orifice 728A. In this case, the pressure of the oil leaving the chamber C72 is greater than the output pressure of the pump 734 and the oil, blocked by the non-return valve 739, flows back to the tank 736, through valve 738, as shown by arrow F2 at figure 7 .

En d'autres termes, du fait du mouvement de la barre 72 dans le sens de la flèche F1, le piston 724 qui est rigidement fixé à la crémaillère 272 à travers la tige 723 et le support 720, se déplace à l'intérieur du logement 726 dans un sens de réduction du volume de la chambre C72. Ceci permet que, dans le référentiel du châssis secondaire 46, le piston 724, la tige 723, le support 720 et la crémaillère 272 demeurent fixes, alors que la barre 72 se déplace dans le sens de la flèche F1. En d'autres termes, le mécanisme de décharge M72 permet un déplacement relatif de la crémaillère 272 et de la barre 72, ce qui évite de transmettre au pignon 273 et, à travers lui, au moto-réducteur 172 une accélération violente susceptible d'endommager le moteur 172A et/ou le réducteur 172B. Le mécanisme de décharge M72 constitue donc un mécanisme de protection du moteur électrique 172A, du réducteur 172B et de l'ensemble pignon-crémaillère 272-273 à l'encontre d'accélérations violentes pouvant résulter d'irrégularités de surface de la pièce P en cours de conformation dans le laminoir 2.In other words, due to the movement of the bar 72 in the direction of the arrow F1, the piston 724 which is rigidly fixed to the rack 272 through the rod 723 and the support 720, moves inside the housing 726 in a direction of reducing the volume of the chamber C72. This allows, in the frame of reference of the secondary frame 46, the piston 724, the rod 723, the support 720 and the rack 272 remain fixed, while the bar 72 moves in the direction of the arrow F1. In other words, the unloading mechanism M72 allows a relative displacement of the rack 272 and the bar 72, which avoids transmitting to the pinion 273 and, through it, to the geared motor 172 a violent acceleration liable to damage the 172A motor and / or the 172B reducer. The discharge mechanism M72 therefore constitutes a mechanism for protecting the electric motor 172A, the reducer 172B and the pinion-rack assembly 272-273 against violent accelerations that may result from surface irregularities of the part P in conformation course in the rolling mill 2.

La comparaison des figures 5 et 7 permet de remarquer que, même si la barre 71 s'est déplacée vers la gauche, dans le sens de la flèche F1, la crémaillère 272 et le pignon 273 ont conservé leurs positions, du fait de la réduction du volume de la chambre C72.The comparison of figures 5 and 7 makes it possible to notice that, even if the bar 71 has moved to the left, in the direction of the arrow F1, the rack 272 and the pinion 273 have retained their positions, due to the reduction in the volume of the chamber C72.

La cage axiale 8 comprend deux rouleaux coniques 82 et 84 destinés à agir respectivement sur la surface frontale supérieure P6 et sur la surface frontale inférieure P8 de la pièce P.The axial cage 8 comprises two conical rollers 82 and 84 intended to act respectively on the upper front surface P6 and on the lower front surface P8 of the part P.

Les rouleaux coniques 82 et 84 sont chacun entraînés en rotation par un moteur électrique 86 ou 88 et supportés par le châssis auxiliaire 48.The tapered rollers 82 and 84 are each rotated by an electric motor 86 or 88 and supported by the auxiliary frame 48.

Le rouleau 82 est supporté par une platine 90 qui est mobile verticalement, le long d'un axe Z90 parallèle aux axes Z62 et Z66, par rapport au châssis secondaire 48.The roller 82 is supported by a plate 90 which is movable vertically, along an axis Z90 parallel to the axes Z62 and Z66, relative to the secondary frame 48.

Pour ce faire, la platine 90 est rigidement fixée à un sabot 91, lui-même attelé à l'extrémité inférieure 92A d'une barre ou colonne 92. Comme les barres 72 à 78, la barre 92 permet de transmettre au rouleau 82 un mouvement de déplacement en translation selon son axe longitudinal X92 confondu avec l'axe Z90.To do this, the plate 90 is rigidly fixed to a shoe 91, itself coupled to the lower end 92A of a bar or column 92. Like the bars 72 to 78, the bar 92 makes it possible to transmit to the roller 82 a displacement movement in translation along its longitudinal axis X92 coincident with the axis Z90.

Le déplacement de la barre 92 selon l'axe Z90 est contrôlé par une crémaillère à double denture 292, elle-même pilotée par deux moto-réducteurs 192 et 194 montés fixes sur le châssis 48. Des pignons 293 et 295 sont respectivement montés sur les arbres de sortie des moto-réducteurs 192 et 194 et engrènent simultanément avec les deux dentures prévues, de part et d'autre de l'axe Z90, sur la crémaillère 292.The movement of the bar 92 along the Z90 axis is controlled by a double-toothed rack 292, itself controlled by two geared motors 192 and 194 fixedly mounted on the frame 48. Pinions 293 and 295 are respectively mounted on the output shafts of geared motors 192 and 194 and mesh simultaneously with the two toothings provided, on either side of axis Z90, on rack 292.

La crémaillère est guidée en translation selon l'axe Z90 par des rails formés dans des plaques de guidage 197 et 199, la plaque 199 étant partiellement arrachée à la figure 8 et complètement retirée aux figures 9 et 10, pour la clarté des dessins. Les plaques 197 et 199 font partie du châssis auxiliaire 48. Les moto-réducteurs 192 et 194 sont rapportés sur le châssis 48 à travers la plaque 197.The rack is guided in translation along the axis Z90 by rails formed in guide plates 197 and 199, the plate 199 being partially torn away from the figure 8 and completely withdrawn from figures 9 and 10 , for clarity of the drawings. The plates 197 and 199 form part of the auxiliary frame 48. The geared motors 192 and 194 are attached to the frame 48 through the plate 197.

L'extrémité supérieure de la barre 92 forme un piston 924 qui est engagé, de façon étanche grâce à un joint 924A, dans un logement creux 926 ménagé en partie basse de la crémaillère 292, au centre de celle-ci. Ceci constitue une chambre C92 de volume variable définie entre la surface supérieure 924B du piston 924 et le fond 926B du logement 926. Un conduit 291 traverse la crémaillère 292 sur toute sa hauteur, à partir du logement 926, ce qui permet de relier la chambre C92 à un système 93 d'alimentation de cette chambre en huile sous pression. Le système 93 comprend un conduit 932, une pompe 934, un bac de récupération 936, un clapet anti-retour taré 938 et un clapet anti-retour 739.The upper end of the bar 92 forms a piston 924 which is engaged, in a sealed manner by virtue of a seal 924A, in a hollow housing 926 formed in the lower part of the rack 292, in the center thereof. This constitutes a chamber C92 of variable volume defined between the upper surface 924B of the piston 924 and the bottom 926B of the housing 926. A duct 291 passes through the rack 292 over its entire height, from the housing 926, which makes it possible to connect the chamber. C92 to a 93 power supply system this chamber in pressurized oil. System 93 includes conduit 932, pump 934, drip tray 936, calibrated check valve 938, and check valve 739.

En pratique, le système d'alimentation 93 peut être identique ou non au système d'alimentation 73. Ces systèmes peuvent être confondus.In practice, the supply system 93 may or may not be identical to the supply system 73. These systems may be confused.

En fonctionnement normal du laminoir 2 représenté aux figures 8 et 9, la pression dans la chambre C92 est suffisante pour que la liaison cinématique entre la crémaillère 292 et le rouleau conique supérieur 82 soient rigide, ce qui permet de piloter de façon précise la hauteur de ce rouleau.In normal operation of the rolling mill 2 shown in figures 8 and 9 , the pressure in the chamber C92 is sufficient for the kinematic connection between the rack 292 and the upper conical roller 82 to be rigid, which makes it possible to precisely control the height of this roller.

En cas d'irrégularité en saillie sur la surface frontale supérieure P6 ou sur la surface frontale inférieure, le rouleau 82 est déplacé vers le haut, dans le sens de la flèche F3 à la figure 10, ce qui se traduit par une translation verticale vers le haut de la platine 90, du sabot 91 et de la barre 92. Ceci a pour effet de chasser l'huile présente dans la chambre C92 vers le système 93, donc vers le bac 936 à travers le clapet 938, comme expliqué ci-dessus au sujet de la barre 72 et du système d'alimentation 73, ce que représente la flèche F4.In the event of a protruding irregularity on the upper front surface P6 or on the lower front surface, the roller 82 is moved upwards, in the direction of the arrow F3 at the figure 10 , which results in a vertical translation upwards of the plate 90, of the shoe 91 and of the bar 92. This has the effect of expelling the oil present in the chamber C92 towards the system 93, therefore towards the tank 936 through the valve 938, as explained above with regard to the bar 72 and the supply system 73, which is represented by the arrow F4.

Le fonctionnement est ici comparable à celui mentionné précédemment au sujet du mécanisme à décharge M72. Il est donc formé dans la cage axiale 8 un mécanisme à décharge M92 qui permet de piloter précisément la hauteur du rouleau conique 82 par rapport au châssis auxiliaire 48, en fonctionnement normal du laminoir 2 et d'accommoder une éventuelle irrégularité de surface sur l'une des surfaces frontales P6 ou P8, sans risquer d'endommager les moto-réducteurs 192 et 194, alors que ceux-ci sont montés de façon rigide par rapport au châssis secondaire 48.The operation is here comparable to that mentioned previously with regard to the discharge mechanism M72. There is therefore formed in the axial cage 8 a discharge mechanism M92 which makes it possible to precisely control the height of the conical roller 82 relative to the auxiliary frame 48, in normal operation of the rolling mill 2 and to accommodate any surface irregularity on the one of the front surfaces P6 or P8, without risking damage to the geared motors 192 and 194, while the latter are mounted rigidly with respect to the secondary frame 48.

En variante, les systèmes 73 et 93 peuvent être remplacés par d'autres systèmes d'alimentation des chambres de volume variable C72, C74, C92, ... en huile sous pression à une pression donnée. On peut notamment utiliser un réservoir accumulateur chargé en huile à la pression souhaitée et associé à une soupape de décharge tarée, ou une chambre de gavage. Dans le cas d'une chambre de gavage, la tige 273 est rigidement liée au support 720 et au piston 724, ce qui permet d'aspirer de l'huile dans la chambre de gavage, à la façon d'une seringue, avant de mettre la chambre de volume variable C72 ou équivalente sous une pression de l'ordre de 250 bars en repoussant le piston 724, après avoir coupé la communication entre cette chambre et la chambre de gavage..As a variant, the systems 73 and 93 can be replaced by other systems for supplying the chambers of variable volume C72, C74, C92, etc. with pressurized oil at a given pressure. It is in particular possible to use an accumulator tank loaded with oil at the desired pressure and associated with a calibrated discharge valve, or a booster chamber. In the case of a booster chamber, the rod 273 is rigidly linked to the support 720 and to the piston 724, which allows oil to be sucked into the booster chamber, like a syringe, before put the variable volume chamber C72 or equivalent under a pressure of the order of 250 bars by pushing back the piston 724, after having cut off the communication between this chamber and the booster chamber.

Dans l'exemple décrit ci-dessus, l'invention est mise en œuvre pour contrôler le déplacement, en translation vis-à-vis des châssis 46 et 48, des rouleaux 66 et 82. En variante, elle peut être utilisée pour un seul de ces rouleaux.In the example described above, the invention is implemented to control the movement, in translation with respect to the frames 46 and 48, of the rollers 66 and 82. As a variant, it can be used for a single of these rolls.

Selon une variante non représentée de l'invention, les barres 72 et 74, d'une part, et les barres 76 et 78, d'autre part, peuvent être reliées entre elles par des traverses arrière disposées à l'opposé de la traverse 68 et du plateau 70. Dans ce cas, un ensemble pignon-crémaillère entraîné par un ou plusieurs moto-réducteurs peut être prévu pour contrôler le déplacement de chaque traverse arrière selon l'axe X2. La structure de l'ensemble pignon-crémaillère montée sur le châssis auxiliaire 46 peut être inspirée de celle représentée aux figures pour la cage axiale 8, avec un équivalent de la barre 92 qui est disposé horizontalement et qui attaque chaque traverse arrière, dans un sens d'écartement par rapport à l'axe Z62 du rouleau principal 62.According to a variant not shown of the invention, the bars 72 and 74, on the one hand, and the bars 76 and 78, on the other hand, can be interconnected by rear cross members arranged opposite the cross member. 68 and the plate 70. In this case, a rack-and-pinion assembly driven by one or more geared motors can be provided to control the movement of each rear cross member along the axis X2. The structure of the pinion-rack assembly mounted on the auxiliary frame 46 can be inspired by that shown in the figures for the axial cage 8, with an equivalent of the bar 92 which is arranged horizontally and which attacks each rear cross member, in one direction. distance from the axis Z62 of the main roller 62.

Selon une autre variante, un seul ensemble pignon-crémaillère est utilisé pour déplacer les deux traverses arrière et, à travers elles, les quatre colonnes. Selon encore une autre variante, une unique traverse relie les quatre barres 72 à 78.According to another variant, a single rack and pinion assembly is used to move the two rear cross members and, through them, the four columns. According to yet another variant, a single cross member connects the four bars 72 to 78.

Le nombre de barres de traction utilisées pour contrôler la translation du rouleau 66 le long de l'axe X2 peut être différent de quatre.The number of traction bars used to control the translation of the roller 66 along the axis X2 may be different from four.

Le mode de réalisation et les variantes envisagées ci-dessus peuvent être combinés pour générer de nouveaux modes de réalisation de l'invention.The embodiment and the variations contemplated above can be combined to generate new embodiments of the invention.

Claims (15)

  1. A circular rolling mill (2) comprising
    - a fixed main frame (4);
    - a pair of cylindrical rollers (62, 66), respectively internal and external, intended to shape internal and external radial faces (P2, P4) of an annular part (P) and supported by a first auxiliary frame (46) mounted on the main frame;
    - a pair of conical rollers (82, 84), respectively upper and lower, intended to shape opposite front faces (P6, P8) of the part and supported by a second auxiliary frame (48) mounted on the main frame;
    - at least one rack and pinion assembly (272-273, 274-275, 292-293-295) to move a roller (68, 82) in translation relative to the auxiliary frame that supports it; and
    - at least one electric geared motor (172-178, 192, 194) to drive the pinion (273, 275, 293, 295) of the pinion and rack assembly
    characterized in that:
    - the electric geared motor (172-178, 192, 194) is fixedly mounted relative to one of the auxiliary frames (46, 48);
    - a fluid discharge mechanism (M72, M74, M76, M78, M92) is interposed in a kinematic chain for transmitting force between the rack (272, 274, 292) and the roller (66, 82) moved by this rack;
    - the fluid discharge mechanism comprises at least one variable volume chamber (C72, C74, C92) supplied with pressurized fluid and the volume of which varies as a function of the relative position of the roller (66, 82) and of the rack (272, 274, 292).
  2. The rolling mill according to claim 1, characterized in that the kinematic chain comprises a transmission bar (72-78, 92) for transmitting a movement to the roller (66, 82) for moving the rack (272, 274, 292) along a longitudinal axis (X72-X78, X92) of the bar and in that the variable volume chamber (C72, C74, C92) is defined between
    - on the one hand, the bar (92) or a part (728) secured to the bar (72); and
    - on the other hand, the rack (292) or a part (724) rigidly fastened to the rack (272).
  3. The rolling mill according to claim 2, characterized in that the variable volume chamber (C72, C74) is defined inside the bar (72-78).
  4. The rolling mill according to claim 2, characterized in that the variable volume chamber (C92) is defined, along the longitudinal axis (X92) of the bar (92), between the rack (292) and the bar.
  5. The rolling mill according to one of the preceding claims, characterized in that it comprises a system (73, 93) for supplying the variable volume chamber (C72, C74, C92) with fluid under a pressure greater than or equal to 100 bars, preferably greater than or equal to 200 bars, still more preferably of about 250 bars.
  6. The rolling mill according to one of the preceding claims, characterized in that the kinematic chain is configured so that, in case of irregularity protruding on the surface (P2, P4, P6, P8) of an annular part (P) shaped by the roller (66, 82), the movement (F1, F3) caused by this irregularity on the bar (72-78, 92) tends to drive (F2, F4) the pressurized fluid from the variable volume chamber (C72, C74, C92), by reducing its volume.
  7. The rolling mill according to one of the preceding claims, characterized in that the fluid discharge mechanism (M72, M74, M76, M78) comprises a piston (724) secured to the rack (272) and one face (724B) of which defines the variable volume chamber (C72, C74).
  8. The rolling mill according to claim 2 and claim 7, characterized in that the piston (724) is mounted sliding inside the bar (72), along the longitudinal axis (X72) of the bar.
  9. The rolling mill according to claim 8, characterized in that the piston (724) is secured to the rack (272) via a rack support (720) and a connecting rod (723) between the rack support and the piston, the rack support and the connecting rod also being mounted sliding inside the bar (72), along the longitudinal axis (X72) of the bar.
  10. The rolling mill according to claim 9, characterized in that it comprises members (727, 729) for guiding the translation, along the longitudinal axis of the bar (X72), of the rack support (720) and/or the connecting bar (723), inside the bar, in particular of guiding skids.
  11. The rolling mill according to one of claims 8 to 10, characterized in that the variable volume chamber (C72, C74) is defined between the face (724B) of the piston (724) and a cover (728) that closes off an internal volume (726) of the bar, opposite the roller (66).
  12. The rolling mill according to claim 2, characterized in that part (924) of the bar (92) is received sealably in an internal cavity (926) defined by the rack (292) and in that the variable volume chamber (C92) is formed by the portion of this cavity not occupied by the bar.
  13. The rolling mill according to claim 5 and claim 12, characterized in that the variable volume chamber (C92) is connected to the pressurized fluid supply system (93) by a pipe (291) that passes through the rack (292).
  14. The rolling mill according to one of the preceding claims, characterized in that each roller (66, 82) translatable relative to a secondary frame (46, 48) is moved by a pinion and rack assembly (272-273, 274-275, 292-293-295) driven by an electric geared motor (172-178, 192, 194) mounted fixedly relative to said frame, with insertion of a fluid discharge mechanism (M72, M74, M76, M78, M92) in the kinematic force transmission chain between each rack (272, 274, 292) and the roller (66, 82) driven by said rack.
  15. A method for controlling the position of at least one roller (66, 82) for shaping a face (P2-P8) of a part (P) to be shaped within a circular rolling mill (2) that comprises:
    - a fixed main frame (4);
    - a pair of rollers (62, 66), respectively internal and external, intended to shape internal and external radial faces (P2, P4) of the part and supported by a first auxiliary frame (46) mounted on the main frame;
    - a pair of conical rollers (82, 84), respectively upper and lower, intended to shape opposite front faces (P6, P8) of the part and supported by a second auxiliary frame (48) mounted on the main frame;
    - at least one rack and pinion assembly (272-273, 274-275, 292-293-295) to move a roller (66, 82) relative to the main frame; and
    - at least one electric geared motor (172-178, 192, 194) to drive the pinion (273, 275, 293, 295) of the pinion and rack assembly,
    this method being characterized in that it comprises the following steps:
    a) supplying pressurized fluid to a variable volume chamber (C72, C74, C92) integrated into a discharge mechanism (M72, M74, M76, M78, M92) interposed in a kinematic force transmission chain between the rack (272, 274, 292) and the roller (66, 82) moved by this rack, to stiffen this kinematic chain during normal operation of the rolling mill (2), and
    b) discharging (F2, F4) at least part of the pressurized fluid from the variable volume chamber (C72, C74, C92), owing to a dimensional variation of the kinematic chain, in case of irregularity on the face (P2-P8) of the part (P) that is shaped by the roller.
EP17777254.8A 2016-09-30 2017-09-29 Ring rolling mill with conformation rolls and process for controlling the position of a roll of such a rolling mill Active EP3519122B1 (en)

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EP16306289.6A EP3300814A1 (en) 2016-09-30 2016-09-30 Ring rolling mill with conformation rolls and process for controlling the position of a roll of such a rolling mill
PCT/EP2017/074736 WO2018060399A1 (en) 2016-09-30 2017-09-29 Circular rolling mill with shaping rollers and method for controlling the position of a roller of such a rolling mill

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CN109843467B (en) 2020-08-21
PL3519122T3 (en) 2021-10-25
CN109843467A (en) 2019-06-04
ES2876162T3 (en) 2021-11-12
KR20190055110A (en) 2019-05-22
JP6722359B2 (en) 2020-07-15
RU2019108707A3 (en) 2020-11-24
EP3300814A1 (en) 2018-04-04
EP3519122A1 (en) 2019-08-07
BR112019006291A2 (en) 2019-07-02
US11110499B2 (en) 2021-09-07
JP2019531198A (en) 2019-10-31
RU2019108707A (en) 2020-09-28
KR102460419B1 (en) 2022-10-31
RU2742986C2 (en) 2021-02-12
BR112019006291B1 (en) 2023-04-18
WO2018060399A1 (en) 2018-04-05
US20190232348A1 (en) 2019-08-01

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