EP0233460B1 - Dispositif pour fléchir les cylindres à déplacement axial d'une cage de laminoir - Google Patents

Dispositif pour fléchir les cylindres à déplacement axial d'une cage de laminoir Download PDF

Info

Publication number
EP0233460B1
EP0233460B1 EP87100220A EP87100220A EP0233460B1 EP 0233460 B1 EP0233460 B1 EP 0233460B1 EP 87100220 A EP87100220 A EP 87100220A EP 87100220 A EP87100220 A EP 87100220A EP 0233460 B1 EP0233460 B1 EP 0233460B1
Authority
EP
European Patent Office
Prior art keywords
pressure
bending
bending device
pistons
blocks
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP87100220A
Other languages
German (de)
English (en)
Other versions
EP0233460A3 (en
EP0233460A2 (fr
Inventor
Johannes Jansen
Friedel Mogendorf
Karl-Heinz Simon
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SMS Siemag AG
Original Assignee
SMS Schloemann Siemag AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19863601239 external-priority patent/DE3601239A1/de
Priority claimed from DE19863604133 external-priority patent/DE3604133A1/de
Application filed by SMS Schloemann Siemag AG filed Critical SMS Schloemann Siemag AG
Priority to AT87100220T priority Critical patent/ATE63241T1/de
Publication of EP0233460A2 publication Critical patent/EP0233460A2/fr
Publication of EP0233460A3 publication Critical patent/EP0233460A3/de
Application granted granted Critical
Publication of EP0233460B1 publication Critical patent/EP0233460B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B29/00—Counter-pressure devices acting on rolls to inhibit deflection of same under load, e.g. backing rolls ; Roll bending devices, e.g. hydraulic actuators acting on roll shaft ends
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2269/00—Roll bending or shifting
    • B21B2269/12—Axial shifting the rolls
    • B21B2269/14—Work rolls

Definitions

  • the invention relates to a bending device for axially displaceable rolls of a multi-roll stand with four or more rolls, the bending device being arranged in stationary blocks, the chocks of the rolls being arranged horizontally and vertically, and per block at least one bending cylinder having hydraulically actuated pressure pistons which apply the bending forces a chock, e.g. from laterally protruding claws of the same.
  • a chock e.g. from laterally protruding claws of the same.
  • Roll-fixed bending devices primarily have the purpose of having the bending forces act on the chocks with a constant effect with every possible axial adjustment of rolls, in particular work rolls. Another reason for bending devices in axial displacement Allowing rolling to move is to keep the pressure pistons free of transverse forces that would arise during the relative movement between the plunger-like pistons and the chocks or their laterally protruding claws if these are stationary or stationary.
  • the development of the roll-fixed bending devices has led to complicated and elaborate designs.
  • the invention has for its object to take up the original technique of the stationary bending device and to further develop that the stator-guided pressure pistons of bending devices are not only kept free from transverse forces, but also a constant and flawless transmission of the bending forces to the chocks axially displaceable with the rollers guarantee.
  • each intermediate piece is designed as a ram-like cheek or as a pressure bridge and in the axial direction of the pressure piston or pistons or in the vertical plane of symmetry S of several adjacent Pressure piston is arranged and that the intermediate piece in the axial direction of the pressure piston or in the plane of symmetry S of the pressure piston or pistons in the blocks is vertically displaceable but without tilting.
  • the intermediate pieces not only cover one or more pressure pistons acting in the same direction at their tappet-like ends, with the result that lateral forces are kept away from the pressure pistons when moving rollers and their chocks, but it is also ensured that a counterpressure surface on the chock side opposes each relative movement the flat printing surface an intermediate piece always acts on the bending force in the transverse center plane of the radial bearing of an installation piece. If the direction of the transmitted bending force lies outside the vertical plane of symmetry of the pressure piston (s), then tilting moments which act on an intermediate piece are absorbed by its tilt-free guidance.
  • the counterpressure surface on each chock is designed to be spherical, as is known, and expediently designed as an exchangeable wear strip.
  • one pressure piston per stand-fixed block is sufficient for the application of relatively low bending forces, it is advisable to provide two guide sections spaced apart symmetrically to the axis of the pressure piston in the direction of the roller axes for the tilt-free guidance of an intermediate piece.
  • these guide sections advantageously consist of round bolts which, like their guide bores, can be produced very precisely and absorb tilting moments without tilting.
  • each intermediate piece is coupled to a block at least on their distant guide sections or round bolts by means of a positive mechanical synchronizing device.
  • the form-fitting, mechanical synchronizing device consists of rack and pinion gears, in which the linear gears are formed on one functional part, while the rotating gears in the other, relatively displaceable functional part to store.
  • each synchronizing device consists of at least two pinions rotatably and coaxially connected by a shaft as well as meshing racks.
  • the pinions can be freely rotatable about their common shaft in the blocks, while the racks are fixed on the height-adjustable cheeks.
  • each cheek in the region of its spaced-apart guide sections has guide extensions directed backwards or into the blocks, which are guided past the bending cylinder within the blocks.
  • Another training option for a bending device according to the invention is according to claim l2 is that the hydraulically loaded piston of the bending cylinder on the Attack synchronous devices - i.e. indirectly - on the cheeks.
  • the synchronizing devices form a functional part of the bending device.
  • the shaft with the pinions of the synchronizing device is rotatably mounted in a slide, and each pinion is on the one hand with a rack on the sliding cheeks and on the other, diametrically opposite, with a rack in the stationary Blocks in positive engagement.
  • Such a design of the bending device is particularly suitable for use where it is desired to derive increased adjustment strokes for the cheeks from the bending cylinders with a relatively small adjustment stroke.
  • a hydraulic synchronous control for two pressure pistons acting in the same direction can also be used, in that the bending pressure for each intermediate piece (cheek or pressure bridge) associated pairs of pressure pistons acting in the same direction can be changed in opposite directions piston-wise, that in the event of a deviation of the center plane (M) of the radial bearing of a chock from the plane of symmetry (S) of the pressure piston as a result of an axial adjustment of a roller, the lateral guide sections or round bolts are guided without torque in the associated stationary block.
  • M center plane
  • S plane of symmetry
  • a form-fitting, mechanical synchronizing device 24 is installed between each cheek 2l and the block 16 accommodating it, which engages at least on the two guide sections of the cheek in question, which are at a distance from one another in the direction of the roller axes.
  • FIG. 1 of the drawing the basic structure of a four-roll (four-high) mill stand 1 is partially shown.
  • This roll stand comprises a pair of work rolls 1 and 2, each of which is mounted in two chocks 3 and 4, respectively.
  • it also has a pair of support rollers 5 and 6, each of which is in turn mounted in two chocks 7 and 8, respectively.
  • the chocks 7 and 8 of the support rollers 5 and 6 are guided directly between vertical guide surfaces 9 and 10 of the window cutouts 11 on the inside of the vertical bars l2 of the roller stands l3.
  • the chocks 3 and 4 of the two work rolls l and 2 are between vertical guide surfaces l5 and l4 of two blocks l6, which are held stationary on the inside of both uprights l2 and protrude into the window cutouts ll of the roll stand l3.
  • chocks 7 and 8 for the support rollers 5 and 6 can only be displaced in the vertical direction between the vertical guide surfaces 9 and 10 of the uprights 12, the chocks 3 and 4 of the two work rollers 1 and 2 can be moved relative to the vertical Shift the guide surfaces l5 of the blocks l6 parallel to the roller axes both in the vertical direction and in the horizontal direction.
  • the relative axial adjustment of the work rolls 1 and 2 is effected by shifting devices (not shown) assigned to the operating side of the roll stand.
  • Each of the bending devices l8 consists of at least one bending cylinder l9, with a hydraulically actuatable piston 20 guided therein, and a cheek 2l, on which the piston 20 of the bending cylinder l9 acts.
  • each bending device l8 is only vertically displaceable in the blocks l6.
  • Each cheek 2l of the bending devices l8 extends within the blocks l6 parallel to the axial direction of the work rolls 1 and 2 over a length which corresponds at least to the maximum possible axial displacement path of the work rolls 1 and 2 or the chocks 3 and 4 supporting them.
  • each cheek 2l has a pressure surface 22 which runs parallel to the roller axes and runs horizontally, with which the claws 3a and 4a of the chocks 3 and 4 respectively interact via a counter pressure surface 23.
  • the counter pressure surfaces 23 are designed such that they always absorb the bending forces in the area of the vertical transverse center plane of the radial bearings of the chocks.
  • the form-fitting, mechanical synchronizing device 24 consists of rack and pinion gears 25a, 25b, in which the linear toothings 26a and 26b sit or are formed on the cheek 2l, while the rotary toothings 27a and 27b each around a stationary axis 28 in the blocks l6 rotatably.
  • Each synchronizing device 24 consists, as shown in FIG. 4, of two pinions 27a and 27b, which are connected in a rotationally fixed and coaxial manner by a shaft 29, and toothed racks 26a and 26b which mesh with them.
  • the pinions 27a and 27b are freely rotatably supported via their common shaft 29 in the blocks l6, while the toothed racks 26a and 26b meshing with them are firmly attached to the height-displaceable cheeks 2l.
  • FIG. 1 While it can be seen from FIG. 1 that each cheek 2l of the bending device, which is displaceably guided in the same direction in the height direction, is assigned its own bending cylinder 19 with a piston 20 that can be displaced therein, FIG. 3 shows that there is also the possibility of the two in the same block 16 cheeks 2l to be assigned a common bending cylinder l9 with piston 20 displaceable therein.
  • the actual bending cylinder l9 is incorporated into the cheek 2l which can be moved upwards, the piston 20 which can be shifted therein having a downwardly directed piston rod 20a which has two pressure pans 20b which engage with spherical surfaces and a fixing plate 20c with the cheek 2l which can be moved downwards in block l6 is coupled.
  • a further structural simplification is achieved by the one according to FIG. 1
  • FIGS. 5 to 7 of the drawing show bending devices 18 for the work rolls 1 and 2, which basically differ from those according to FIGS. 2 to 4 only in that the two cheeks 2l arranged in the same block 16 do not have a bending cylinder l9 and a piston 20 work together, but are equipped with two parallel bending cylinders l9 and pistons slidable therein. These are arranged symmetrically on both sides of a transverse central plane of the block l6, and in between an additional guide bar 30, for example with a rectangular cross section, is installed in order to cooperate with both cheeks, which can relieve the piston rods 20a of lateral forces when the two Cheeks 2l are moved apart.
  • the design of the bending devices according to FIGS. 2 to 4 is particularly suitable for installation cases in which relatively small installation dimensions for the blocks l6 in the direction of the roller axes are important
  • the design according to FIGS. 5 to 7 can be used where the blocks l6 get a larger installation dimension in the direction of the roller axes can and relatively high bending forces must be exerted on the work rolls via the bending devices 18.
  • the installation dimensions of the blocks 16 parallel to the rolling direction in the construction according to FIGS. 5 to 7 can, however, easily match those of the construction according to FIGS. 2 to 4.
  • FIG. 8 of the drawing shows in a spatial representation and on a larger scale a bending device 18 installed in a block 16, the basic structure of which corresponds to that of FIG.
  • the positive mechanical synchronizing device 24 can be seen, which carries the two pinions 27a and 27b in a rotationally fixed manner on a shaft 29 which is rotatably mounted in the block 16.
  • each cheek 2l in the area of its spaced-apart guide sections i.e. in the area of the two racks 26a and 26b attached to you, has guide extensions 2la and 2lb directed backwards or into the block 16, which extend within the Block l6 are guided past the centrally arranged bending cylinder l9.
  • FIG. 9 shows a bending device 18 that is structurally modified compared to FIG. 8 in vertical section.
  • FIG. 10 shows a further design option for a bending device 18 according to the invention.
  • the arrangement is such that the hydraulically actuated piston 20 of the bending cylinder l9 acts on the cheek 2l, which is guided in a height-displaceable manner in block l6, via the positive mechanical synchronizing device 24.
  • the shaft 29 with the two pinions 27a, 27b seated thereon in rotation is rotatably mounted in a slide 3l which is adjustable in the vertical direction, the pinions 27a, 27b meshing with the toothed racks 26a, 26b on the cheek 2l.
  • the pinions 27a, 27b at a diametrically opposite point on their circumference are also in positive engagement with racks 26c and 26d, which are rigidly arranged or fixed in the stationary blocks 16.
  • the form-fitting mechanical synchronizing device 24 is thus also used here as a differential gear which is switched on between the bending cylinders 19 or its piston 20 and the cheek 2l.
  • Such a design for the bending devices l8 is particularly recommended when bending cylinders l9 are to be used, which work with relatively small stroke lengths of their pistons, but have to produce larger stroke lengths of the cheeks 2l in the stationary blocks l6.
  • Such an embodiment can prove to be expedient, for example, if the bending cylinders 19 with their pistons 20 cannot be accommodated within the blocks 16 fixed to the stand, but instead have to be assigned to them on the outside of the roller stands 13.
  • the four-roll stand according to FIG. 11 corresponds to that according to FIG. 1 in the reference numerals.
  • one or two pairs of coaxial bending cylinders l9 are provided in a block l6, which is fixed to the stand, since these are bending devices for work rolls. It is understood that a bending device for intermediate rolls per stationary block l6 only one or a pair of in the same direction would have acting bending cylinders l9.
  • the bending devices shown in FIG. 11 are described in more detail with reference to FIGS. 12 to 15.
  • Fig. L2 the one end of the work rolls 1, 2 is shown with the claws 3a, 4a spanning a bending device.
  • Each stationary block l6 is provided with two pairs of coaxial, hydraulically actuated pressure pistons 42, 44 and 43, 45, respectively. the adjacent pressure pistons 42, 43 and 44, 45 have the same effect in pairs and jointly exert bending forces to counter-bend the work rolls.
  • Each pair of pressure pistons acting in the same direction is covered by a common pressure bridge 56, 57.
  • Each pressure bridge has an integrally formed round bolt 50 or 5l in the plane of symmetry S to the coaxial pressure pistons, which are guided in a common bore 32 with tight play, so that the pressure bridges are guided without tilting.
  • the pressure bridges 56, 57 - as shown in FIG. 12 for the pressure piston 42 - are connected to the pressure pistons via open snap rings 33 which engage in ring grooves 42a of the pressure pistons and are screwed to the pressure bridges.
  • the pressure bridge 56 (and likewise the lower pressure bridge 57) has a flat pressure transmission surface 34, whereas the counter pressure surface 35 of the claws 3a, 4a are designed spherically to the central plane M.
  • the center plane M defines the center plane of the radial bearings in the chocks, which is slightly offset to the right with respect to the stationary symmetry plane S, because the rollers 1, 2 and the claws 3a, 4a are adjusted slightly to the left from the middle axial position by an axial adjustment. It should be noted that, within the scope of the invention, primarily an opposite adjustment of the work rolls comes into question.
  • the counter pressure surface 35 is provided with a hardened wear strip 36. This also applies to the lower claw 4a.
  • the crowning of the counter pressure surfaces 35 and in particular the wear strips 36 ensures that the bending forces exerted by the piston pairs 42, 43 and 44, 45 acting in the same direction are always transmitted in the center plane M of the bearings, however, usually with the formation of one on the pressure bridges 56 and 57 acting tilting moment, which, however, is so far ineffective due to the precise round pin guidance of the pressure bridges in the stand-fixed block that the pressure bridges are to be regarded as tilt-free.
  • variable bending pressure is to be applied to each pair of pressure pistons with the same axis 42, 43 and 44, 45 piston-wise changeable in opposite directions in the sense that if the center plane M deviates from the plane of symmetry S due to an axial displacement of a roller, the round bolts 50, 5l are guided in the associated stationary block l6 without torque.
  • FIG. L3 differs from that of FIG. L2 solely in that only a pair of oppositely acting pressure pistons 52, 53 are provided in the plane of symmetry S in a block fixed to the stand, which are covered by pressure bridges 46, 47. Pairs of round bolts 48 and 49 are formed on these pressure bridges symmetrically to the plane of symmetry S.
  • the bending devices are the same as in FIG. 13, with the difference, however, that the round guide bolts 48 and 49 are provided with toothing 55 similar to a rack. Opposite the drawing plane, these toothed rack gears engage 55 pinion segments 60, as can be seen better from Fig. L5.
  • Each pair of coaxial pinion segments 60 is connected via a synchronous shaft 6l, so that the pair of round bolts 48 and the pair of round bolts 49 are mechanically synchronized among themselves in the sense of a synchronous control.
  • Each stationary block l6 has transverse recesses l6a (FIG. L5) which are large enough to be able to laterally install the synchronous shaft 6l with the two pinion segments 60 in a raised position.
  • transverse recesses l6a FIG. L5
  • the synchronous shaft 6l has at both ends of the bearing journal 6la, via which the synchronous shaft is supported in the covers 62 closing the recess 16a.
  • the rigid bending devices which allow hydraulic lines to be fixed, are designed in particular for relatively small axial adjustment paths of the work rolls. Such relatively small adjustment paths result in not too great differences in the width of the flat material to be rolled, in the axial adjustment of work rolls using Rolls with a bottle-shaped contour according to DE-A-30 38 865 or also in the case of cyclical counter-displacement of work rolls to avoid local roll wear in the area of the strip edges.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)

Claims (16)

  1. Dispositif de flexion de cylindres d'une cage de laminoir à quatre ou à plus de quatre cylindres, qui peuvent se déplacer dans le sens axial, qui est monté dans des blocs (16) qui sont solidaires de montants et guident horizontalement et verticalement les empoises (3, 4) des cylindres mobiles (1, 2) et qui comprend, pour chaque bloc, au moins un vérin de flexion (19) associé à un piston de compression hydraulique (20) qui transmet les forces de flexion à une empoise (3, 4), des pièces intermédiaires (21, 46, 56; 47, 57) étant intercalées entre le piston de compression (20) et l'empoise (3, 4) et ces pièces intermédiaires (21, 46, 56, 47, 57) comportant, à chacune de leurs extrémités dépassant les blocs (16), une surface de compression horizontale plane qui est orientée parallèlement aux axes des cylindres (1, 2) et qui s'étend au moins sur le trajet de déplacement axial minimal du cylindre (1, 2) et, par ailleurs, l'empoise (3, 4) comportant, pour l'absorption de la force de pression, une surface de contre-pression (23) qui se trouve au moins dans la zone du plan médian transversal (M) de son palier radial, caractérisé en ce que chaque pièce intermédiaire est une plaque constituée par un poussoir (21) ou par un pont de compression (46, 56 ou 47, 57) et orientée dans la direction de l'axe du ou des pistons de compression (20, 52, 53) ou située dans le plan de symétrie vertical (S) de plusieurs pistons de compression (20, 42, 43) disposés les uns à côté des autres et en ce que lapièce intermédiaire est guidée dans les blocs (16) de manière à pouvoir être réglée en hauteur sans possibilité de coincement dans la direction du ou des axes du ou des pistons de compression ou dans le plan de symétrie (S) du ou des pistons de compression.
  2. Dispositif de flexion selon la revendication 1, caractérisé en ce que la surface de contre-pression (23, 35), au niveau de l'empoise, est bombée et constituée par une bande d'usure amovible (36).
  3. Dispositif de flexion selon la revendication 1, comportant un piston de compression dans chaque bloc solidaire d'un montant, caractérisé en ce que chaque pièce intermédiaire (21, 46 ou 47) comporte deux zones de guidage (21a, 48 ou 49) symétriques par rapport à l'axe du piston de compression (20, 52) et situées à une certaine distance l'une de l'autre dans la direction des axes de cylindres.
  4. Dispositif de flexion selon la revendication 3, comportant une pièce intermédiaire constituée par un pont de compression, caractérisé en ce que les pièces de guidage sont des boulons ronds (48, 49)
  5. Dispositif de flexion selon la revendication 1, comportant, dans chaque bloc solidaire d'un montant, une paire de pistons de compression synchronisés, caractérisé en ce que chaque pièce intermédiaire constituée par un pont de compression (56, 57) comporte un boulon rond (50 ou 51) placé dans le plan de symétrie (S) des pistons de compression (20; 42, 43 ou 44, 45).
  6. Dispositif de flexion selon l'une des revendications 3 ou 5, caractérisé en ce que chaque pièce intermédiaire (21; 46 ou 47) est, au moins au niveau de ses zones de guidage situées à une certaine distance l'une de l'autre ou des boulons ronds, accouplée à un bloc (16) par un mécanisme de synchronisation (24, 25a, 25b, 26a, 27a, 27b, 28, 29, 60, 61, 62) comportant une adaptation des formes.
  7. Dispositif de flexion selon la revendication 6, caractérisé en ce que le mécanisme de synchronisation relié avec adaptation des formes est constitué par des engrenages à crémaillères (25a, 25b) dans lesquels les séries de dents linéaires (26a, 26b, 55) sont montées sur une partie intervenant dans le fonctionnement (plaque 21 ou boulons ronds (48, 49), tandis que les séries de dents rotatives (27a, 27b, 60) sont montées sur une autre partie intervenant dans le fonctionnement (bloc 16) qui peut se déplacer par translation par rapport à la première.
  8. Dispositif de flexion selon la revendication 7, caractérisé en ce que chaque mécanisme de synchronisation 24 comporte deux pignons (27a, 27b, 60) reliés l'un à l'autre sans possibilité de rotation relative et coaxialement par un arbre (29, 61) ainsi que des cremaillères (26a, 26b, 55) qui sont en prise avec les pignons.
  9. Dispositif de flexion selon la revendication 8, caractérisé en ce que les pignons (27a, 27b) sont montés, par l'intermédiaire de leur arbre commun (29, 61), dans des blocs (16) ou ils peuvent tourner librement, tandis que les cremaillères (26a, 26b, 60) sont solidaires des pièces (21) ou des boulons ronds (48, 49).
  10. Dispositif de flexion selon la revendication 6, caractérisé en ce que les pignons (27a, 27b) sont montés sur les plaques (21) de manière à pouvoir tourner librement sur leur axe commun (29) tandis que les cremaillères (26a, 26b) sont solidaires des blocs (16).
  11. Dispositif de flexion selon la revendication 9, caractérisé en ce que chaque plaque (21) comporte, au niveau de ses zones de guidage situées à une certaine distance l'une de l'autre, des prolongements de guidage (21a, 21b) qui sont dirigés vers l'arrière ou pénètrent dans les blocs (16) etqui, à l'intérieur des blocs (16), passent devant le vérin de flexion (19).
  12. Dispositif de flexion selon la revendication 8, caractérisé en ce que les pistons (20) des vérins de flexion hydrauliques (19) agissent sur les plaques (21) par l'intermédiaire des mécanismes de synchronisation (24).
  13. Dispositif de flexion selon la revendication 12, dans lequel les arbres associés aux pignons du mécanisme de synchronisation sont montés sur les plaques de manière à pouvoir tourner et dans lequel les crémaillères sont montées à poste fixe dans les blocs, caractérisé en ce que les pistons (20) des vérins de flexion hydrauliques (19) agissent chacun sur un bras de levier relié sans possibilité de rotation relative à l'arbre (29).
  14. Dispositif de flexion selon la revendication 12, caractérisé en ce que l'abre (29) associé aux pignons du mécanisme de synchronisation (24) est monté de manière à pouvoir tourner dans une pièce coulissante (31) et que chaque pignon (27a, 27b) est en prise, avec adaptation des formes, d'une part avec une cremaillère (26a, 26b) au niveau des plaques (21) et, d'autre part, à un emplacement diamétralement opposé avec une crémaillère (26c, 26d) montée sur les blocs fixes (16).
  15. Dispositif de flexion selon les revendications 3, 4 et 9, comportant des crémaillères associées aux boulons ronds d'un pont de compression, caractérisé en ce que le pont de compression (46, 47) est relié aux boulons ronds (48, 49) par une articulation (48a, 49a).
  16. Dispositif de flexion selon la revendication 5, dans lequel des pistons de compression sont soumis à une pression de flexion variable, caractérisé en ce que la pression de flexion pour des paires de pistons de compression associés à chaque pièce intermédiaire (plaque 21 en forme de poussoir ou ponts de compression 56, 57) et agissant dans le même sens est modifiable en sens inverse au niveau des pistons du fait que, lorsque, par suite du déplacement d'un cylindre (1, 2) dans le sens axial, le plan médian (M) du palier radial d'une empoise s'écarte du plan de symétrie (S) des pistons de compression, les zones de guidage ou boulons ronds (50, 51) sont guidés sans aucun moment dans le bloc (16) correspondant solidaire d'un montant.
EP87100220A 1986-01-17 1987-01-09 Dispositif pour fléchir les cylindres à déplacement axial d'une cage de laminoir Expired - Lifetime EP0233460B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87100220T ATE63241T1 (de) 1986-01-17 1987-01-09 Staenderfeste biegevorrichtung fuer axial verschiebbare walzen eines mehrwalzengeruestes.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3601239 1986-01-17
DE19863601239 DE3601239A1 (de) 1986-01-17 1986-01-17 Biegevorrichtung fuer die axial verschiebbaren arbeitswalzen eines vierwalzen-walzgeruestes
DE19863604133 DE3604133A1 (de) 1986-02-10 1986-02-10 Staenderfeste biegevorrichtung fuer axial verschiebbare arbeitswalzen eines walzgeruestes
DE3604133 1986-02-10

Publications (3)

Publication Number Publication Date
EP0233460A2 EP0233460A2 (fr) 1987-08-26
EP0233460A3 EP0233460A3 (en) 1988-09-14
EP0233460B1 true EP0233460B1 (fr) 1991-05-08

Family

ID=25840188

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87100220A Expired - Lifetime EP0233460B1 (fr) 1986-01-17 1987-01-09 Dispositif pour fléchir les cylindres à déplacement axial d'une cage de laminoir

Country Status (2)

Country Link
EP (1) EP0233460B1 (fr)
DE (1) DE3769809D1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2611541B1 (fr) * 1987-02-27 1994-04-29 Clecim Sa Dispositif de reglage du profil et de repartition d'usure de cylindres dans un laminoir a cylindres deplacables axialement
GB2202173B (en) * 1987-03-19 1991-08-14 Davy Mckee Rolling mill
AT504208B1 (de) 2006-04-21 2008-04-15 Siemens Vai Metals Tech Gmbh Biegevorrichtung für zwei arbeitswalzen eines walzgerüstes
CN102284502B (zh) * 2011-08-11 2013-06-05 二重集团（德阳）重型装备股份有限公司 轧机的弯窜辊装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2024682B (en) * 1978-07-07 1982-06-23 Davy Loewy Ltd Roll bending assembly for a rolling mill
JPS5666307A (en) * 1979-10-04 1981-06-04 Hitachi Ltd Rolling mill
EP0059417B1 (fr) * 1981-02-28 1985-01-02 Sms Schloemann-Siemag Aktiengesellschaft Cage de laminoir
JPS57199505A (en) * 1981-06-03 1982-12-07 Hitachi Ltd Work roll moving type rolling mill
JPS5956910A (ja) * 1982-09-27 1984-04-02 Kawasaki Steel Corp ロ−ルベンデイング押力制御方法
DE3331055C2 (de) * 1983-08-29 1994-11-03 Schloemann Siemag Ag Walzgerüst mit axial verschieblichen Arbeitswalzen
GB8528848D0 (en) * 1985-11-22 1985-12-24 Davy Mckee Poole Rolling mills

Also Published As

Publication number Publication date
EP0233460A3 (en) 1988-09-14
DE3769809D1 (de) 1991-06-13
EP0233460A2 (fr) 1987-08-26

Similar Documents

Publication Publication Date Title
EP2390017B1 (fr) Machine de cintrage à trois rouleaux
EP0267420B1 (fr) Cage de laminoir avec un dispositif pour déplacer axialement les cylindres ajustables
DE3331055C2 (de) Walzgerüst mit axial verschieblichen Arbeitswalzen
EP0233460B1 (fr) Dispositif pour fléchir les cylindres à déplacement axial d'une cage de laminoir
DE1558220C3 (de) Lagerung von Walzen für die Formänderung eines aus einer Stranggießkokille kommenden metallischen Stranges
AT507110B1 (de) Presse zum umformen von material
EP0154896B1 (fr) Laminoir à six cylindres
DE2540403B2 (fr)
DE2122204B2 (de) Gewichtsentlastungseinrichtung an werkzeugmaschinen, insbesondere karusselldrehmaschinen
EP0483599B1 (fr) Cage de laminoir comprenant des dispositifs pour supporter à distance le cylindre de travail supérieur
EP0118812B1 (fr) Cage de laminoir à plusieurs cylindres
DE3008203A1 (de) Stauchgeruest mit kraftbetrieben anstellbaren walzen
EP0233597B1 (fr) Cage de laminoir aux empoises ajustables verticalement dans le bâti
DE3335857A1 (de) Walzgeruest mit mittels stuetzrollen abstuetzbarer arbeitswalzen
EP0231875A2 (fr) Dispositif de déplacement axial des cylindres d'une cage de laminoir
DE3627692A1 (de) Biege- und ausbalanciervorrichtung fuer axial verschiebbare arbeitswalzen eines quartowalzgeruestes
DE1940414B2 (de) Walzgerüst mit einer Einrichtung zum Walzenwechsel
AT390902B (de) Schmiedemaschine zum durchlaufschmieden strangfoermigen gutes, insbesondere stranggegossener brammen
DE3601239A1 (de) Biegevorrichtung fuer die axial verschiebbaren arbeitswalzen eines vierwalzen-walzgeruestes
DE2932115A1 (de) Richtmaschine
DE2129376A1 (de) Walzwerk
DE3807628C2 (de) Walzgerüst mit Verschiebeeinrichtung
DE907884C (de) Walzenanstellvorrichtung zum Hoehenverstellen und/oder Seitenverstellen der Walzen
EP0326805B1 (fr) Cage de laminoir avec un dispositif de déplacement
DE3811875A1 (de) Fuehrungsvorrichtung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19870126

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE DE FR GB IT

17Q First examination report despatched

Effective date: 19881215

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE DE FR GB IT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRE;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.SCRIBED TIME-LIMIT

Effective date: 19910508

Ref country code: GB

Effective date: 19910508

Ref country code: BE

Effective date: 19910508

REF Corresponds to:

Ref document number: 63241

Country of ref document: AT

Date of ref document: 19910515

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3769809

Country of ref document: DE

Date of ref document: 19910613

EN Fr: translation not filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19910927

GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19920109

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19950321

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19961001