EP0233460B1 - Roll bending device for axially shifting rolls of a multiple rolling stand - Google Patents

Roll bending device for axially shifting rolls of a multiple rolling stand Download PDF

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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
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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
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German (de)
French (fr)
Other versions
EP0233460A3 (en
EP0233460A2 (en
Inventor
Johannes Jansen
Friedel Mogendorf
Karl-Heinz Simon
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SMS Siemag AG
Original Assignee
SMS Schloemann Siemag AG
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Filing date
Publication date
Priority claimed from DE19863601239 external-priority patent/DE3601239A1/en
Priority claimed from DE19863604133 external-priority patent/DE3604133A1/en
Application filed by SMS Schloemann Siemag AG filed Critical SMS Schloemann Siemag AG
Priority to AT87100220T priority Critical patent/ATE63241T1/en
Publication of EP0233460A2 publication Critical patent/EP0233460A2/en
Publication of EP0233460A3 publication Critical patent/EP0233460A3/en
Application granted granted Critical
Publication of EP0233460B1 publication Critical patent/EP0233460B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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.

Description

Die Erfindung betrifft eine Biegevorrichtung für axial verschiebbare Walzen eines Mehrwalzengerüstes mit vier oder mehr Walzen, wobei die Biegevorrichtung in ständerfesten, die Einbaustücke der Walzen horizontal und vertikal führenden Blöcken angeordnet ist und pro Block mindestens einem Biegezylinder mit hydraulisch beaufschlagtem Druckkolebn besteht, die die Biegekräfte auf ein Einbaustück, z.B. aus seitlich ausladende Pratzen desselben, übertragen. Sie geht damit aus von der EP-A- 59 4l7, soweit hierin ständerfeste Biegevorrichtungen beschrieben sind, die den axialen Verstellbewegungen der Walzen und ihrere Einbaustücke nicht zu folgen vermögen, also nicht "mitwandernd" bzw. walzenfixiert sind. Die Entwicklung ging in letzter Zeit in Richtung der walzenfixierten Biegevorrichtungen (EP-A- 26 903, 67 040, DE-A- 33 3l 055 und die vorgenannte EP-A- 59 4l7 in einigen Ausführungsbeispielen).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. It is based on EP-A-59 417, insofar as stand-fixed bending devices are described here which are unable to follow the axial adjustment movements of the rolls and their chocks, ie are not "moving along" or fixed to the rolls. The development has recently been in the direction of the roll-fixed bending devices (EP-A-26 903, 67 040, DE-A-33 3l 055 and the aforementioned EP-A-59 4l7 in some exemplary embodiments).

Walzenfixierte Biegevorrichtungen haben in erster Linie den Sinn, die Biegekräfte bei jeder möglichen Axialverstellung von Walzen, insbesondere Arbeitswalzen, mit stets gleichbleibender Wirkung an den Einbaustücken angreifen zu lassen. Ein weiterer Grund dafür, Biegevorrichtungen bei der Axialverschiebung von Walzung mitwandern zu lassen besteht darin, die Druckkolben von Querkräften freizuhalten, die bei der Relativbewegung zwischen den stößelartigen Kolben und den Einbaustücken bzw. deren seitlich ausladenden Pratzen entstehen würden, wenn diese ortsfest bzw. ständerfest sind. Die Entwicklung der walzenfixierten Biegevorrichtungen hat jedoch zu komplizierten und aufwendigen Konstruktionen geführt.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. However, the development of the roll-fixed bending devices has led to complicated and elaborate designs.

Der Erfindung liegt die Aufgabe zugrunde, die ursprüngliche Technik der ständerfesten Biegevorrichtung aufzugreifen und dahingehend weiterzuentwickeln, daß die ständerfest geführten Druckkolben von Biegevorrichtungen nicht nur von Querkräften freigehalten sind, sondern auch eine ständig gleichbleibende und einwandfreie Übertragung der Biegekräfte auf die mit den Walzen axial verschiebbaren Einbaustücken gewährleisten.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.

Die erfindungsgemäße Lösung dieser Aufgabe besteht gemäß Anspruch 1 darin, daß ausgehend von einer Biegevorrichtung nach dem Oberbegriff des Anspruchs 1, jedes Zwischenstück als stößelartige Wange oder als Druckbrücke ausgebildet ist und in Achsrichtung des oder der Druckkolben bzw. in der senkrechten Symmetrieebene S mehrerer nebeneinander liegender Druckkolben angeordnet ist und daß das Zwischenstück in der Achsrichtung des oder der Druckkolben bzw. in der Symmetrieebene S von dem oder den Druckkolben in den Blöcken höhenverschiebbar aber verkantungsfrei geführt ist.The solution to this problem according to the invention consists in claim 1, that starting from a bending device according to the preamble of claim 1, 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.

Durch die Zwischenstücke werden nicht nur ein oder mehr gleichsinnig wirkende Druckkolben an ihren stößelartigen Enden abgedeckt mit der Folge, daß beim Verschieben von Walzen und deren Einbaustücken Querkräfte von den Druckkolben ferngehalten sind, sondern es ist auch sichergestellt, daß bei jeder Relativbewegung einer einbaustückseitigen Gegendruckfläche gegenüber der ebenen Druckfläche eines Zwischenstückes die Biegekraft stets in der Quer-Mittenebene des Radiallagers eines Einbaustückes angreift. Liegt die Richtung der übertragenen Biegekraft außerhalb der senkrechten Symmetrieebene des oder der Druckkolben, so werden Kippmomente, die auf ein Zwischenstück einwirken, von dessen verkantungsfreien Führung aufgenommen.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.

Um der Durchbiegung der Walzen und der damit zusammenhängenden Kippbewegung von Einbaustücken Rechnung zu tragen, wird nach Anspruch 2 die Gegendruckfläche an jedem Einbaustück wie bekannt ballig ausgeführt und zweckmäßig als eine austauschbare Schleißleiste ausgebildet.In order to take into account the deflection of the rollers and the associated tilting movement of chocks, the counterpressure surface on each chock is designed to be spherical, as is known, and expediently designed as an exchangeable wear strip.

Wenn zur Aufbringung relativ geringer Biegekräfte ein Druckkolben pro ständerfestem Block genügt, empfiehlt es sich, zur verkantungsfreien Führung eines Zwischenstückes zwei symmetrisch zur Achse des Druckkolbens in Richtung der Walzenachsen voneinander entfernte Führungsabschnitte vorzusehen. Diese Führungsabschnitte bestehen bei einem als Druckbrücke ausgeführten Zwischenstück in Übereinstimmung mit Anspruch 4 vorteilhafterweise aus Rundbolzen, die ebenso wie ihre Führungsbohrungen sehr genau herstellbar sind und Kippmomente verkantungsfrei aufnehmen.If 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. In the case of an intermediate piece designed as a pressure bridge, these guide sections advantageously consist of round bolts which, like their guide bores, can be produced very precisely and absorb tilting moments without tilting.

Für den Fall, daß wegen höherer Biegekräfte jeweils ein gleichsinnig beaufschlagbares Kolbenpaar pro ständerfestem Block vorzusehen ist, wird nach Anspruch 5 vorgeschlagen, an jedem der als Druckbrücke ausgeführten Zwischenstück einen in der Symmetrieebene der Kolben angeordneten Rundbolzen zur verkantungsfreien Führung der Druckbrücke vorzusehen.In the event that, due to higher bending forces, a piston pair which can be acted upon in the same direction is to be provided per block fixed to the stand, it is proposed according to claim 5 to provide a round pin arranged in the plane of symmetry of the pistons for tilt-free guidance of the pressure bridge on each of the intermediate pieces designed as a pressure bridge.

Um die verkantungsfreie Führung eines Zwischenstückes zu entlasten und damit einem überhöhten Verschleiß zu begegnen, sieht die Erfindung gemäß Anspruch 6 vor, daß jedes Zwischenstück wenigstens an ihren voneinander entfernten Führungsabschnitten oder Rundbolzen durch eine formschlüssige, mechanische Gleichlaufeinrichtung mit einem Block gekuppelt ist.In order to relieve the tilt-free guidance of an intermediate piece and thus to counter excessive wear, the invention provides according to claim 6 that 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.

Es hat sich nach der Erfindung besonders bewährt, eine Biegevorrichtung mit den Merkmalen des Anspruchs 7 auszustatten, wonach die formschlüssige, mechanische Gleichlaufeinrichtung aus Zahnstangengetrieben besteht, bei denen die Linearverzahnungen an einem Funktionsteil ausgebildet sind, während die Rotationsverzahnungen in dem anderen, dazu relativ verschiebbaren Funktionsteil lagern.It has proven particularly useful, according to the invention, to equip a bending device with the features of claim 7, according to which 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.

Nach Anspruch 8 liegt es dabei im Rahmen einer Weiterbildung der Erfindung, daß jede Gleichlaufeinrichtung aus mindestens zwei durch eine Welle drehfest und koaxial verbundenen Ritzeln sowie mit diesen kämmenden Zahnstangen besteht.According to claim 8, it is within the scope of a development of the invention that each synchronizing device consists of at least two pinions rotatably and coaxially connected by a shaft as well as meshing racks.

Es können dabei nach Anspruch 9 die Ritzel über ihre gemeinsame Welle in den Blöcken frei drehbar gelagert sein, während sich die Zahnstangen ortsfest an den höhenverschiebbaren Wangen befinden. Nach Anspruch l0 ist es aber ebenfalls möglich, die Ritzel über ihre gemeinsame Welle in den Wangen frei drehbar zu lagern, während die Zahnstangen ortsfest an den Blöcken sitzen.According to claim 9, the pinions can be freely rotatable about their common shaft in the blocks, while the racks are fixed on the height-adjustable cheeks. According to claim 10 it is also possible, however, to mount the pinions freely rotatably via their common shaft in the cheeks, while the racks are fixed in place on the blocks.

Als wichtig für eine optimale Führung hat es sich bei einer Biegevorrichtung nach der Erfindung erwiesen, daß gemäß Anspruch ll jede Wange im Bereich ihrer voneinander entfernten Führungsabschnitte nach hinten bzw. in die Blöcke hinein gerichtete Führungsverlängerungen aufweist, die innerhalb der Blöcke am Biegezylinder vorbeigeführt sind.It has proven to be important for optimal guidance in a bending device according to the invention that, according to claim 11, 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.

Eine andere Ausbildungsmöglichkeit für eine erfindungsgemäße Biegevorrichtung besteht nach Anspruch l2 darin, daß die hydraulisch beaufschlagbaren Kolben der Biegezylinder über die Gleichlaufeinrichtungen - also mittelbar - an den Wangen angreifen. Die Gleichlaufvorrichtungen bilden in diesem Falle einen Funktionsteil der Biegevorrichtung.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. In this case, the synchronizing devices form a functional part of the bending device.

Für eine Biegevorrichtung, bei welcher die Welle mit den Ritzeln der Gleichlaufeinrichtung in den Wangen drehbar lagert und die Zahnstangen sich ortsfest an den Blöcken befinden, ist nach Anspruch l3 die Möglichkeit gegeben, daß die hydraulisch beaufschlagbaren Kolben der Biegezylinder an einem mit der Welle drehfest verbundenen Hebelarm angreifen. Der Drehantrieb der Welle sichert damit nicht nur die Gleichlaufbewegung der Wange, sondern er übt auch die Biegekräfte auf die an den Wangen abgestützten Einbaustücke aus.For a bending device in which the shaft with the pinions of the synchronizing device is rotatably supported in the cheeks and the racks are stationary on the blocks, there is the possibility according to claim l3 that the hydraulically loadable piston of the bending cylinder is connected in a rotationally fixed manner to the shaft Attack the lever arm. The rotary drive of the shaft not only ensures the synchronous movement of the cheek, but also exerts the bending forces on the chocks supported on the cheeks.

Bei einer noch anderen Bauart einer erfindungsgemäßen Biegevorrichtung ist nach Anspruch l4 die Welle mit den Ritzeln der Gleichlaufeinrichtung in einem Schieber drehbar gelagert, und dabei steht jedes Ritzel einerseits mit einer Zahnstange an den verschiebbaren Wangen und andererseits, diametral gegenüberliegend, mit einer Zahnstange in den ortsfesten Blöcken in Formschlußeingriff.In yet another design of a bending device according to the invention, 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.

Sind die Zahnstangen einer mechanischen Gleichlaufeinrichtung an einem Paar von Rundbolzen einer Druckbrücke angeordnet, so empfiehlt sich deren gelenkiger Anschluß entsprechend dem Anspruch l5, um Zwänge und Biegespannungen in den Rundbolzen zu verhindern.If the racks of a mechanical synchronizing device are arranged on a pair of round bolts of a pressure bridge, their articulated connection according to claim 15 is recommended in order to prevent constraints and bending stresses in the round bolts.

Eine solche Ausbildung der Biegevorrichtung eignet sich besonders dort zum Einsatz, wo es erwünscht ist, aus den Biegezylindern mit relativ kleinem Stellhub vergrößerte Stellhübe für die Wangen abzuleiten.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.

Statt einer mechanischen Gleichlaufeinrichtung kann zur Entlastung der verkantungsfreien Führung von Zwischenstücken auch eine hydraulische Gleichlaufsteuerung für jeweils zwei gleichsinnig beaufschlagte Druckkolben angewendet werden, indem der Biegedruck für jedem Zwischenstück (Wange oder Druckbrücke) zugeordnete Paare von gleichsinnig wirkenden Druckkolben kolbenweise gegenläufig veränderbar ist in dem Sinne, daß bei einer Abweichung der Mittenebene (M) des Radiallagers eines Einbaustückes von der Symmetrieebene (S) der Druckkolben infolge einer Axialverstellung einer Walze die seitlichen Führungsabschnitte bzw. Rundbolzen in dem zugehörigen ständerfesten Block momentenfrei geführt sind.Instead of a mechanical synchronizing device, to relieve the tilt-free guidance of intermediate pieces, 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.

Zur Ausbalancierung der Arbeitswalzen l und 2 sowie auch der zur Profilbeeinflussung des zwischen ihnen gebildeten Walzspaltes l7 sind besondere Biegevorrichtungen l8 erforderlich, die jeweils in den beiden ortsfesten Blöcken l6 sitzen und an seitwärts auskragenden Pratzen 3a bzw. 4a der Einbaustücke 3 bzw. 4 für die Arbeitswalzen l und 2 angreifen, wie das der Figur l entnommen werden kann.In order to balance the work rolls l and 2 and also to influence the profile of the roll gap l7 formed between them, special bending devices l8 are required, each of which is located in the two stationary blocks l6 and on cantilevered claws 3a and 4a of the chocks 3 and 4 for the Attack work rolls 1 and 2, as can be seen in Figure 1.

In der Zeichnung sind verschiedene Ausführungsbeispiele einer erfindungsgemäßen Biegevorrichtung dargestellt. Es zeigen

Figur l
eine axiale Seitenansicht des wesentlichen Aufbaus eines Vierwalzen-Walzgerüstes, teilweise im Schnitt mit Wangen als höhenverschieblichen Zwischenstücken,
Figur 2
den in Figur l mit II gekennzeichneten Bereich in größerem Maßstab,
Figur 3
einen Schnitt entlang der Linie III-III in Figur 2,
Figur 4
einen Schnitt entlang der Linie IV-IV in Figur 2,
Figur 5
eine der Figur 2 entsprechende Darstellung einer abgewandelten Bauart der Biegevorrichtung,
Figur 6
einen Schnitt entlang der Linie VI-VI in Figur 5,
Figur 7
einen Schnitt entlang der Linie VII-VII in Figur 5,
Figur 8
in schematisch vereinfachter, räumlicher Durchsichtdarstellung den oberen Teil des in Figur l mit VIII gekennzeichneten, ständerseitigen Blockes mit der darin befindlichen Biegevorrichtung,
Figur 9
einen Vertikalschnitt durch den in Figur 8 gezeigten Bereich eines Blockes mit abgewandelter Bauart der darin befindlichen Biegevorrichtung,
Figur l0
in einer der Figur 9 entsprechenden Darstellung eine wieder abgewandelte Bauart für eine ArbeitswalzenBiegevorrichtung.
Figur ll
eine Ansicht ähnlich Fig. l mit Druckbrücken als höhenverschiebbaren Zwischenstücken,
Figur l2
die Situation an einem Ende zweier Arbeitswalzen mit senkrechtem Schnitt durch die Biegevorrichtungen für diese Walzen nach einem Ausführungsbeispiel,
Figur l3
eine Darstellung ähnlich Fig. l2 für ein anderes Ausführungsbeispiel,
Figur l4
eine Darstellung ähnlich Fig. l3 mit Gleichlaufeinrichtung im senkrechten Schnitt nach der Linie XIV-XIV in Fig. l5, und
Figur l5
einen waagerechten Schnitt nach der Linie XV-XV in Fig. l4.
Various exemplary embodiments of a bending device according to the invention are shown in the drawing. Show it
Figure l
an axial side view of the essential structure of a four-roll stand, partially in section with cheeks as height-adjustable intermediate pieces,
Figure 2
the area marked II in FIG. 1 on a larger scale,
Figure 3
2 shows a section along the line III-III in FIG. 2,
Figure 4
3 shows a section along the line IV-IV in FIG. 2,
Figure 5
2 shows a representation of a modified type of bending device,
Figure 6
4 shows a section along the line VI-VI in FIG. 5,
Figure 7
4 shows a section along the line VII-VII in FIG. 5,
Figure 8
in a schematically simplified, spatial see-through representation, the upper part of the stand-side block identified by VIII in FIG. 1 with the bending device located therein,
Figure 9
8 shows a vertical section through the area of a block shown in FIG. 8 with a modified design of the bending device located therein,
Figure l0
in a representation corresponding to FIG. 9, a modified type for a work roll bending device.
Figure ll
1 with pressure bridges as height-displaceable intermediate pieces,
Figure l2
the situation at one end of two work rolls with a vertical section through the bending devices for these rolls according to one embodiment,
Figure l3
a representation similar to Fig. l2 for another embodiment,
Figure l4
a representation similar to Fig. L3 with synchronizer in vertical section along the line XIV-XIV in Fig. l5, and
Figure l5
a horizontal section along the line XV-XV in Fig. l4.

Um diese Wirkungsweise dauerhaft sicherstellen zu können, ist zwischen jeder Wange 2l und dem sie aufnehmenden Block l6 eine formschlüssige, mechanische Gleichlaufeinrichtung 24 eingebaut, die wenigstens an den in Richtung der Walzenachsen voneinander entfernten beiden Führungsabschnitten der betreffenden Wange angreift.In order to be able to permanently ensure this mode of operation, 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.

In Figur l der Zeichnung ist der grundsätzliche Aufbau eines Vierwalzen-(Quarto-)Walzgerüstes l teilweise dargestellt. Dabei umfaßt dieses Walzgerüst ein Paar von Arbeitswalzen l und 2, von denen jede in zwei Einbaustücken 3 bzw. 4 gelagert ist. Darüberhinaus weist es auch ein Paar von Stützwalzen 5 und 6 auf, deren jede wiederum in zwei Einbaustücken 7 bzw. 8 gelagert ist.In Figure 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. In addition, 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.

Die Einbaustücke 7 und 8 der Stützwalzen 5 und 6 sind unmittelbar zwischen vertikalen Führungsflächen 9 bzw. l0 der Fensterausschnitte ll an der Innenseite der vertikalen Holme l2 der Walzenständer l3 geführt. Hingegen befinden sich die Einbaustücke 3 bzw. 4 der beiden Arbeitswalzen l und 2 zwischen vertikalen Führungsflächen l5 bzw. l4 zweier Blöcke l6, die an der Innenseite beider Ständerholme l2 ortsfest gehalten sind und in die Fensterausschnitte ll der Walzenständer l3 hineinragen.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. On the other hand, 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.

Während die Einbaustücke 7 und 8 für die Stützwalzen 5 und 6 jeweils nur in Vertikalrichtung verlagerbar zwischen den vertikalen Führungsflächen 9 bzw. l0 der Ständerholme l2 verlagert werden können, lassen sich die Einbaustücke 3 bzw. 4 der beiden Arbeitswalzen l und 2 relativ zu den vertikalen Führungsflächen l5 der Blöcke l6 sowohl in Vertikalrichtung als auch in Horizontalrichtung parallel zu den Walzenachsen verlagern.While the 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.

Durch die horizontale Verlagerung der Einbaustücke 3 und 4 ist es möglich, die Arbeitswalzen l und 2 relativ zueinander wie auch relativ zu den Stützwalzen 5 bzw. 6 in Axialrichtung zu verschieben und dadurch das Walzgerüst auf die Bearbeitung unterschiedlicher Walzbandbreiten und/oder zur Beeinflussung der Walzbandprofile einzustellen.Due to the horizontal displacement of the chocks 3 and 4, it is possible to move the work rolls 1 and 2 relative to each other as well as relative to the support rolls 5 and 6 in the axial direction and thereby the roll stand to process different strip widths and / or to influence the strip profiles adjust.

Die relative Axialverstellung der Arbeitswalzen l und 2 wird durch der Bedienungsseite des Walzgerüstes zugeordnete (nicht dargestellte) Verschiebevorrichtungen bewirkt.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.

Jede der Biegevorrichtungen l8 besteht dabei aus mindestens einem Biegezylinder l9, mit darin geführtem, hydraulisch beaufschlagbarem Kolben 20, und einer Wange 2l, auf die der Kolben 20 des Biegezylinders l9 einwirkt.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.

Wie der Kolben 20 im Biegezylinder l9 so ist auch die Wange 2l jeder Biegevorrichtung l8 lediglich höhenverschiebbar in den Blöcken l6 geführt.Like the piston 20 in the bending cylinder l9, the cheek 2l of each bending device l8 is only vertically displaceable in the blocks l6.

Jede Wange 2l der Biegevorrichtungen l8 erstreckt sich dabei innerhalb der Blöcke l6 parallel zur Achsrichtung der Arbeitswalzen l und 2 über eine Länge, die mindestens dem maximal möglichen axialen Verschiebeweg der Arbeitswalzen l und 2 bzw. der sie lagernden Einbaustücke 3 bzw. 4 entspricht.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.

An ihrem freien bzw. aus den Blöcken l6 herausragenden Ende weist jede Wange 2l eine parallel zu den Walzenachsen gerichtete und horizontal verlaufende Druckfläche 22 auf, mit der die Pratzen 3a bzw. 4a der Einbaustücke 3 bzw. 4 jeweils über eine Gegendruckfläche 23 zusammenwirken. Die Gegendruckflächen 23 sind dabei so ausgebildet, daß sie die Biegekräfte stets im Bereich der vertikalen Quer-Mittenebene der Radiallager der Einbaustücke aufnehmen.At its free end or protruding from the blocks l6, 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.

Ein wichtiges Ausbildungskriterium der Biegevorrichtungen l8 liegt darin, daß die die Druckflächen 22 aufweisenden Wangen 2l bei jedem möglichen Betriebszustand des Walzgerüstes über ihre ganze Länge exakt in einer Lage gehalten werden, bei der die Druckfläche 22 in jeder Richtung und ständig ihre exakte Horizontallage beibehält.An important design criterion of the bending devices 18 is that the cheeks 2l, which have the pressure surfaces 22, are held in their position over their entire length in every possible operating state of the roll stand, in which the pressure surface 22 maintains its exact horizontal position in every direction and constantly.

Besonders deutlich ist aus den Figuren 2 und 4 ersichtlich, daß die formschlüssige, mechanische Gleichlaufeinrichtung 24 aus Zahnstangengetrieben 25a, 25b besteht, bei denen die Linearverzahnungen 26a und 26b an der Wange 2l sitzen bzw. ausgebildet sind, während die Rotationsverzahnungen 27a und 27b jeweils um eine ortsfeste Achse 28 in den Blöcken l6 drehbar lagern.It can be seen particularly clearly from FIGS. 2 and 4 that 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.

Jede Gleichlaufeinrichtung 24 besteht dabei, wie Figur 4 zeigt, aus zwei durch eine Welle 29 drehfest und koaxial verbundenen Ritzeln 27a und 27b sowie mit diesen kämmenden Zahnstangen 26a und 26b.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.

Die Ritzel 27a und 27b sind dabei über ihre gemeinsame Welle 29 in den Blöcken l6 frei drehbar gelagert, während sich die mit ihnen kämmenden Zahnstangen 26a und 26b fest an den höhenverschiebbaren Wangen 2l befinden.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.

Während aus Figur l hervorgeht, daß jeder im gleichen Block l6 in Höhenrichtiung verschiebbar geführten Wange 2l der Biegevorrichtung ein eigener Biegezylinder l9 mit darin verschiebbarem Kolben 20 zugeordnet ist, kann der Figur 3 entnommen werden, daß auch die Möglichkeit besteht, den beiden im gleichen Block l6 geführten Wangen 2l einen gemeinsamen Biegezylinder l9 mit darin verschiebbarem Kolben 20 zuzuordnen.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.

Der eigentliche Biegezylinder l9 ist dabei in die autwärts verschiebbare Wange 2l eingearbeitet, wobei der darin verschiebbare Kolben 20 eine nach unten gerichtete Kolbenstange 20a hat, die über zwei mit Kugelflächen ineinandergreifende Druckpfannen 20b und eine Fixierplatte 20c mit der nach abwärts verschiebbaren Wange 2l im Block l6 gekuppelt ist. Gegenüber der Bauart einer Biegevorrichtung nach Figur l wird durch diejenige nach Figur 3 eine weitere bauliche Vereinfachung erzielt.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. Compared to the construction of a bending device according to FIG. 1, a further structural simplification is achieved by the one according to FIG.

Der Figur 4 ist zu entnehmen, daß der Biegezylinder l9 und der zugehörige Kolben 20 den beiden Wangen 2l im Kreuzungsbereich ihrer Längs- und Querebenen zugeordnet sind und somit eine Symmetrielage zu den formschlüssigen, mechanischen Gleichlaufeinrichtungen 24 einnehmen.It can be seen from FIG. 4 that the bending cylinder 19 and the associated piston 20 are assigned to the two cheeks 2l in the area of intersection of their longitudinal and transverse planes and thus assume a symmetrical position with the form-fitting, mechanical synchronizing devices 24.

In den Figuren 5 bis 7 der Zeichnung sind Biegevorrichtungen l8 für die Arbeitswalzen l und 2 dargestellt, welche sich von denjenigen nach den Figuren 2 bis 4 im Grunde genommen nur dadurch unterscheiden, daß die im gleichen Block l6 angeordneten beiden Wangen 2l nicht über einen Biegezylinder l9 und einen Kolben 20 zusammenarbeiten, sondern mit zwei parallelen Biegezylindern l9 und darin verschiebbaren Kolben ausgestattet sind. Diese sind dabei symmetrisch zu beiden Seiten einer Quer-Mittelebene des Blocks l6 angeordnet, und dazwischen ist zum Zusammenwirken mit beiden Wangen 2l noch ein zusätzlicher Führungsholm 30, bspw. mit Rechteckquerschnitt, eingebaut, der die Kolbenstangen 20a von Seitenkräften entlasten kann, wenn die beiden Wangen 2l auseinandergefahren werden.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.

Während die Ausgestaltung der Biegevorrichtungen nach den Figuren 2 bis 4 sich besonders für Einbaufälle eignet, bei denen es auf relativ kleine Einbauabmessungen für die Blöcke l6 in Richtung der Walzenachsen ankommt, ist die Bauform nach den Figuren 5 bis 7 dort benutzbar, wo die Blöcke l6 in Richtung der Walzenachsen eine größere Einbauabmessung erhalten können und über die Biegevorrichtungen l8 auf die Arbeitswalzen relativ hohe Biegekräfte ausgeübt werden müssen. Die Einbauabmessungen der Blöcke l6 parallel zur Walzrichtung können bei der Bauform nach den Figuren 5 bis 7 jedoch mit denjenigen der Bauform nach den Figuren 2 bis 4 ohne weiteres übereinstimmen.While 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.

In Figur 8 der Zeichnung ist in räumlicher Darstellung und größerem Maßstab eine in einen Block l6 eingebaute Biegevorrichtung l8 gezeigt, deren Grundaufbau mit dem nach Figur l übereinstimmt. Dabei ist die formschlüssige, mechanische Gleichlaufeinrichtung 24 zu sehen, welche auf einer im Block l6 drehbar gelagerten Welle 29 drehfest die beiden Ritzel 27a und 27b trägt. Diese kämmen dauernd mit den beiden Zahnstangen 26a und 26b, die fest mit der Wange 2l verbunden sind, die ausschließlich vertikal verschiebbar im Block l6 geführt wird.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. These mesh continuously with the two toothed racks 26a and 26b, which are firmly connected to the cheek 2l, which is guided in the block l6 exclusively in a vertically displaceable manner.

Aus Figur 8 ist dabei ersichtlich, daß jede Wange 2l im Bereich ihrer voneinander entfernten Führungsabschnitte, also im Bereich der beiden an Ihnen befestigten Zahnstangen 26a und 26b, nach hinten bzw. in den Block l6 hinein gerichtete Führungsverlängerungen 2la und 2lb aufweist, die innerhalb des Blockes l6 am mittig angeordneten Biegezylinder l9 vorbeigeführt sind.From Figure 8 it can be seen that 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.

Auf diese Art und Weise wird unter bestmöglicher Ausnutzung des verfügbaren Einbauraums das Führungsverhalten der Wange 2l wesentlich verbessert.In this way, the guide behavior of the cheek 2l is significantly improved while making the best possible use of the available installation space.

In Figur 8 ist desweiteren noch angedeutet, daß die Gegendruckfläche 23 des Einbaustückes 3 eine mit der vertikalen Quer-Mittelebene des Lagers desselben zusammenfallende ballige Erhöhung aufweist, welche zweckmäßigerweise von einer austauschbaren Schleißleiste gebildet wird. Auf diese Art und Weise ist sichergestellt, daß sich die Lage der Einbaustücke 3 bzw. 4 für die Arbeitswalzen l bzw. 2 entsprechend der jeweiligen Biegeverformung der Arbeitswalzen l bzw. 2 gegenüber den Blöcken l6 und/oder den Wangen 2l einstellen kann.In Figure 8 is further indicated that the counter-pressure surface 23 of the chock 3 has a spherical elevation coinciding with the vertical transverse center plane of the bearing, which is expediently formed by an exchangeable wear strip. In this way it is ensured that the position of the chocks 3 or 4 for the work rolls l or 2 according to the respective bending deformation of the work rolls l or 2 relative to the blocks l6 and / or the cheeks 2l.

In Figur 9 ist eine gegenüber der Figur 8 baulich abgewandelte Biegevorrichtung l8 im Vertikalschnitt gezeigt.FIG. 9 shows a bending device 18 that is structurally modified compared to FIG. 8 in vertical section.

Der Unterschied gegenüber der Bauart nach Figur 8 liegt darin, daß die Ritzel 27a, 27b der formschlüssigen, mechanischen Gleichlaufvorrichtung 24 über die sie drehfest miteinander verbindende Welle 29 frei drehbar in der Wange 2l gelagert sind, während die zugehörigen Zahnstangen 26a und 26b jeweils ortsfest im Block l6 montiert sind.The difference compared to the design according to Figure 8 lies in the fact that the pinions 27a, 27b of the form-fitting, mechanical synchronizing device 24 are rotatably mounted in the cheek 2l via the shaft 29 connecting them to one another in a rotationally fixed manner, while the associated toothed racks 26a and 26b are each stationary in the Block l6 are mounted.

Es ergibt sich hierdurch eine kinematisch umgekehrte Anordnung der die Gleichlaufvorrichtung 24 bildenden Funktionselemente gegenüber der Bauform nach Figur 8. Die grundsätzliche Wirkungsweise der Ausführungsform nach Figur 9 ist jedoch die gleiche wie bei der Ausführungsform nach Figur 8.This results in a kinematically reversed arrangement of the functional elements forming the synchronizing device 24 compared to the design according to FIG. 8. However, the basic mode of operation of the embodiment according to FIG. 9 is the same as that of the embodiment according to FIG. 8.

Die Figur l0 zeigt in einer der Figur 9 entsprechenden Darstellung eine weitere Ausbildungsmöglichkeit für eine erfindungsgemäße Biegevorrichtung l8. In diesem Falle ist die Anordnung so getroffen, daß der hydraulisch beaufschlagbare Kolben 20 des Biegezylinders l9 über die formschlüssige mechanische Gleichlaufeinrichtung 24 auf die im Block l6 höhenverschiebbar geführte Wange 2l einwirkt.In a representation corresponding to FIG. 9, FIG. 10 shows a further design option for a bending device 18 according to the invention. In this case, 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.

Die Welle 29 mit den drehfest darauf sitzenden beiden Ritzeln 27a, 27b ist hierbei in einem in Höhenrichtung verstellbaren Schieber 3l drehbar gelagert, wobei die Ritzel 27a, 27b einerseits mit den Zahnstangen 26a, 26b an der Wange 2l kämmen. Andererseits stehen jedoch die Ritzel 27a, 27b an einer diametral gegenüberliegenden Stelle ihres Umfangs auch noch mit Zahnstangen 26c und 26d in Formschlußeingriff, welche starr in den ortsfesten Blöcken l6 angeordnet bzw. befestigt sind.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. On the other hand, however, 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.

Die formschlüssige mechanische Gleichlaufvorrichtung 24 wird hier also zugleich als Differentialgetriebe benutzt, welches zwischen den Biegezylindern l9 bzw. dessen Kolben 20 und die Wange 2l eingeschaltet ist.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.

Eine solche Bauart für die Biegevorrichtungen l8 ist besonders dann empfehlenswert, wenn Biegezylinder l9 benutzt werden sollen, die mit relativ kleinen Hubstrecken ihres Kolbens arbeiten, dabei jedoch größere Hubwege der Wangen 2l in den ständerfesten Blöcken l6 hervorbringen müssen.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.

Selbstverständlich wäre es auch denkbar, Biegevorrichtungen l8, bei denen die Welle 29 mit den beiden Ritzeln 27a, 27b der Gleichlaufeinrichtung 24 gemäß Figur 9 in den Wangen 2l drehbar lagert, während die Zahnstangen 26a, 26b sich ortsfest an den Blöcken l6 befinden, die hydraulisch beaufschlagbaren Kolben 20 der Biegezylinder l9 an einem mit der Welle 29 drehfest verbundenen Hebelarm angreifen zu lassen und auf diese Art und Weise die Hubbewegung der Wangen 2l zu erzeugen.Of course, it would also be conceivable to use bending devices 18, in which the shaft 29 with the two pinions 27a, 27b of the synchronizing device 24 according to FIG. 9 is rotatably supported in the cheeks 2l, while the toothed racks 26a, 26b are stationary on the blocks 16, which are hydraulic to act upon piston 20 of the bending cylinder l9 on a lever arm connected to the shaft 29 in a rotationally fixed manner and in this way to generate the lifting movement of the cheeks 2l.

Eine solche Ausgestaltung kann sich bspw. dann als zweckmäßig erweisen, wenn die Biegezylinder l9 mit ihren Kolben 20 nicht innerhalb der ständerfesten Blöcke l6 untergebracht werden können, sondern diesen stattdessen an der Außenseite der Walzenständer l3 zugeordnet werden müssen.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.

Das Vierwalzengerüst nach Fig. ll entspricht in den Bezugsziffern demjenigen nach Fig. l. Auch hier sind in jeweils einerm ständerfesten Block l6 ein oder zwei Paare von gleichachsigen Biegezylindern l9 vorgesehen, da es sich um Biegevorrichtungen für Arbeitswalzen handelt. Es versteht sich, daß eine Biegevorrichtung für Zwischenwalzen pro ständerfestem Block l6 lediglich einen oder ein Paar von gleichsinnig wirkenden Biegezylindern l9 aufweisen würde. Die in Fig. ll dargestellten Biegevorrichtungen werden im einzelnen anhand Fig. l2 bis l5 näher beschrieben.The four-roll stand according to FIG. 11 corresponds to that according to FIG. 1 in the reference numerals. Here too, 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.

In Fig. l2 ist das eine Ende der Arbeitswalzen l, 2 mit den eine Biegevorrichtung übergreifenden Pratzen 3a, 4a dargestellt. Ein jeder ständerfester Block l6 ist mit zwei Paaren von gleichachsigen, hydraulisch beaufschlagten Druckkolebn 42, 44 bzw. 43, 45 versehen, d h. die nebeneinanderliegenden Druckkolben 42, 43 bzw. 44, 45 sind paarweise gleichwirkend und üben gemeinschaftlich Biegekräfte zum Gegenbiegen der Arbeitswalzen aus. Jedes Paar von gleichsinnig wirkenden Druckkolben ist von einer gemeinsamen Druckbrücke 56, 57 abgedeckt. Jede Druckbrücke weist in der Symmetrieebene S zu den gleichachsigen Druckkolben einen angeformten Rundbolzen 50 bzw. 5l auf, die in einer gemeinsamen Bohrung 32 mit engem Spiel geführt sind, so daß die Druckbrücken verkantungsfrei geführt sind. Die Druckbrücken 56, 57 sind - wie Fig. l2 für den Druckkolben 42 zwigt - über offene Sprengringe 33, die in Ringnuten 42a der Druckkolben eingreifen und an den Druckbrücken festgeschraubt sind, mit den Druckkolben verbunden.In 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.

Die Druckbrücke 56 (und ebenso die untere Druckbrücke 57) hat eine ebene Druckübertragungsfläche 34, wogegen die Gegendruckfläche 35 der Pratzen 3a, 4a symmetrisch zur Mittenebene M ballig ausgeführt sind. Die Mittenebene M definiert die Mittenebene der Radiallager in den Einbaustücken, die gegenüber der ortsfesten Symmetrieebene S etwas nach rechts versetzt ist, weil die Walzen l, 2 und die Pratzen 3a, 4a durch eine Axialverstellung etwas aus der mittleren Axiallage nach links verstellt sind. Zu bemerken ist, daß tatsächlich im Rahmen der Erfindung vorrangig eine gegenläufige Verstellung der Arbeitswalzen infrage kommt.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.

In der Mittenebene M ist die Gegendruckfläche 35 mit einer gehärteten Schleißleiste 36 versehen. Dies gilt ebenso für die untere Pratze 4a. Die Balligkeit der Gegendruckflächen 35 und insbesondere der Schleißleisten 36 stellt sicher, daß die von den gleichsinnig wirkenden Kolbenpaaren 42, 43 bzw. 44, 45 ausgeübten Biegekräfte stets in der Mittenebene M der Lager übertragen werden, allerdings meist unter Entstehung eines auf die Druckbrücken 56 und 57 einwirkenden Kippmomentes, das jedoch durch die exakte Rundbolzen-Führung der Druckbrücken in dem ständerfesten Block soweit unwirksam ist, daß die Druckbrücken als verkantungsfrei geführt anzusehen sind. Um bei großen Abweichungen zwischen der ortsfesten Symmetrieebene S und der Lager-Mittenebene M die Rund-Führungsbolzen 50, 5l von ihrer Aufgabe der verkantungsfreien Fürhung der Druckbrücken 56, 57 weitgehend zu entlasten, ist der veränderliche Biegedruck zum Beaufschlagen eines jeden Paares von gleichachsig wirkenden Druckkolben 42, 43 bzw. 44, 45 kolbenweise gegenläufig veränderbar in dem Sinne, daß bei einer Abweichung der Mittenebene M von der Symmetrieebene S infolge einer Axialverschiebung einer Walze die Rundbolzen 50, 5l in dem zugehörigen ständerfesten Block l6 momentenfrei geführt sind.In the center plane M, 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. In order to largely relieve the round guide bolts 50, 5l of their task of not tilting the pressure bridges 56, 57 in the event of large deviations between the stationary symmetry plane S and the bearing center plane M, the 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.

Das Ausführungsbeispiel nach Fig. l3 unterscheidet sich gegenüber demjenigen nach Fig. l2 allein dadurch, daß in einem ständerfesten Block lediglich ein Paar von gegenläufig wirkenden Druckkolben 52, 53 in der Symmetrieebene S vorgesehen sind, die von Druckbrücken 46, 47 abgedeckt sind. An diesen Druckbrücken sind symmetrisch zu der Symmetrieebene S jeweils Paare von Rundbolzen 48 und 49 angeformt.The embodiment of 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.

Bei dem Ausführungsbeispiel nach Fig. l4 handelt es sich um die gleichen Biegevorrichtungen wie nach Fig. l3 mit dem Unterschied jedoch, daß die Führungs-Rundbolzen 48 und 49 mit zahnstangenähnlichen Verzahnungen 55 versehen sind. Gegenüber der Zeichenebene vorgelagert greifen in diese Zahnstangenverzahnungen 55 Ritzelsegmente 60 ein, wie besser aus Fig. l5 zu ersehen ist.Jeweils ein Paar von gleichachsigen Ritzelsegmenten 60 ist über eine Sychronwelle 6l verbunden, so daß das Rundbolzenpaar 48 und das Rundbolzenpaar 49 unter sich im Sinne einer Gleichlaufsteuerung mechanisch synchronisiert ist. Auch dies entlastet die Rundbolzen 48, 49 hinsichtlich der Annahme von Kippmomenten die je nach der axialen Einstellung der Arbeitswalzen l, 2 der einbaustückseitigen Pratzen 3a, 4a auf die Druckbrücken 46, 47 einwirken könnten. Da die Gleichlaufeinrichtung zu einer Torsion der Sychronwelle 6l führt, ist es zur Vermeidung von Zwängen erforderlich, die Verbindung zwischen den Druckbrücken und der Rundbolzen gelenkig zu gestalten, was durch die Ausbildung der Rundbolzen mit Kugelköpfen 48a bzw. 49a schematisch dargestellt ist, die in entsprechende Kugelpfannen der Druckbrücken eingreifen. Selbstverständlich können die Druckbrücken 46, 47 auch über Gelenkbolzen mit dem Rundbolzen 48, 49 verbunden sein.In the exemplary embodiment according to FIG. 14, 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. This also relieves the round bolts 48, 49 with regard to the assumption of tilting moments which, depending on the axial setting of the work rolls 1, 2 of the claws 3a, 4a on the chock side, could act on the pressure bridges 46, 47. Since the synchronizing device leads to a torsion of the synchronous shaft 6l, it is necessary to avoid the necessity to design the connection between the pressure bridges and the round bolts in an articulated manner, which is illustrated schematically by the design of the round bolts with ball heads 48a and 49a, respectively, which correspond to Engage ball pans of the pressure bridges. Of course, the pressure bridges 46, 47 can also be connected to the round bolt 48, 49 via hinge bolts.

Ein jeder ständerfester Block l6 hat quergerichtete Ausnehmungen l6a (Fig. l5), die groß genug sind, um die Synchronwelle 6l mit den beiden Ritzelsegmenten 60 in hochgestellter Lage seitlich einbauen zu können. Mit der Einführung der Rundbolzen 48 werden deren Zahnstangenverzahnungen 55 durch Drehen der Sychronwelle 6l mit den Verzahnungen der Ritzelsegmente 60 in Eingriff gebracht. Die Sychronwelle 6l hat an beiden Enden der Lagerzapfen 6la, über die die Sychronwelle in den die Ausnehmung l6a verschließenden Deckeln 62 gelagert ist.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. With the introduction of the round bolts 48, their rack teeth 55 are brought into engagement with the teeth of the pinion segments 60 by rotating the synchronous shaft 61. 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.

Es ist zu bemerken, daß die ständerfesten Biegevorrichtungen, die es erlauben, hydraulische Leitungen fest zu verlegen, insbesondere für relativ kleine axiale Verstellwege der Arbeitswalzen ausgelegt sind. Solche relativ kleinen Verstellwege ergeben sich bei nicht zu großen Unterschieden in der Breite des zu walzenden Flachmaterials, bei der Axialverstellung von Arbeitswalzen unter Verwendung von Walzen mit flaschenförmiger Kontur nach der DE-A- 30 38 865 oder auch beim zyklischen gegenläufigen Verschieben von Arbeitswalzen zur Vermeidung von örtlichem Walzenverschleiß im Bereich der Bandkanten.It should be noted that 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.

Claims (16)

  1. Bending device, for axially displaceable rolls of a cluster stand with four or more rolls, which is arranged in blocks (16), which are fast with the standard and guide the chocks (3, 4) of the displaceable rolls (1, 2) horizontally and vertically, and consists for each block of at least one bending cylinder (19) with hydraulically loadable pressure piston (20), which transmit the bending forces to a chock (3, 4), wherein intermediate members (21; 46, 56; 47, 57) are arranged between the pressure pistons (20) and the chocks (3, 4) and the intermediate members (21; 46, 56; 47, 57) at their ends projecting out of the blocks (16) each display a respective horizontal planar pressure surface, which is oriented parallelly to the roll axes (1, 2) and extends over at least the maximum axial displacement path of the roll (1, 2), and wherein furthermore the chock (3, 4) is provided with a counterpressure surface (23), which is arranged at least in the region of the transverse centre plane (M) of its radial bearing, for the reception of the bending force, characterised thereby, that each intermediate member is constructed as ramlike cheek (21) or as pressure bridge (46, 56 or 47, 57) and arranged either in axial direction of the pressure piston or pistons (20, 52, 53) or in the vertical symmetry plane (S) of several pressure pistons (20, 42, 43) arranged one beside the other and that the intermediate member is guided in the blocks (16) to be displaceable vertically, but free of canting, either in the axial direction of the pressure piston or pistons or in the symmetry plane (S) of the pressure piston or pistons.
  2. Bending device according to claim 1, characterised thereby, that the counterpressure surface (23, 35) at the chock is constructed to be cambered and expediently consists of an exchangeable strip (36) subject to wear.
  3. Bending device according to claim 1 with a respective pressure piston for each block fast with the standard, characterised by two guide portions (21a, 48 or 49), which are arranged symmetrically to the axis of the pressure piston (20, 52) and each spaced from the other in the direction of the roll axes, at each intermediate member (21, 46 or 47).
  4. Bending device according to claim 3 with a pressure bridge as intermediate member, characterised thereby, that the guide portions consist of round bolts (48, 49).
  5. Bending device according to claim 1 with a respective pressure piston pair loaded in like sense for each block fast with the standard, characterised by a round bolt (50 or 51), which is arranged in the symmetry plane (S) of the pressure pistons (20; 42, 43 or 44, 45) at each intermediate member constructed as pressure bridge (56, 57).
  6. Bending device according to claim 3 or 5, characterised thereby, that each intermediate member (21, 46 or 47) is coupled with a block (16), at least at its mutually spaced guide portions or round bolts, by a shape-looking mechanical synchronising equipment (24, 25a, 25b, 26a, 26b, 27a, 27b, 28, 29, 60, 61, 62).
  7. Bending device according to claim 6, characterised thereby, that the shape-looking mechanical synchronising equipment (24) consists of toothed rack drives (25a, 25b), in which the linear toothings (26a, 26b, 55) are formed at a functional part (cheek 21 or round bolt 48, 49), while the rotary toothings (27a, 27b, 60) are borne in the other functional part (block 16) displaceable relatively thereto.
  8. Bending device according to claim 7, characterised thereby, that each synchronising equipment (24) consists of at least two pinions (27a, 27b, 60), which are connected co-axially and secure against rotation by a shaft (29, 61) as well as toothed racks (26a, 26b, 55) meshing with these.
  9. Bending device according to claim 8, characterised thereby, that the pinions (27a, 27b) are borne by way of their common shaft (29, 61) to be freely rotatable in the blocks (16), while the toothed racks (26a, 26b, 55) are rigidly disposed either at the cheeks (21) or at the round bolts (48, 49).
  10. Bending device according to claim 6, characterised thereby, that the pinions (27a, 27b) are borne by way of their common shaft (29) to be freely rotatable in the cheeks (21), while the toothed racks (26a, 26b) sit rigidly at the blocks (16).
  11. Bending device according to claim 9, characterised thereby, that each cheek (21) in the region of its mutually spaced guide portions displays guide prolongations (21a, 21b), which are directed rearwardly or into the blocks (16) and are led past the bending cylinder (19) within the blocks (16).
  12. Bending device according to claim 8, characterised thereby, that the hydraulically loadable pistons (20) of the bending cylinders (19) engage at the cheeks (21) by way of the synchronising equipments (24).
  13. Bending device according to claim 12, in which the shafts with the pinions of the synchronising equipment are borne to be rotatable in the cheeks and the toothed racks are disposed fixed in location at the blocks, characterised thereby, that the hydraulically loadable pistons (20) of the bending cylinders (19) engage at a lever arm connected secure against rotation with the shaft (29).
  14. Bending device according to claim 12, characterised thereby, that the shaft (29) with the pinions of the synchronising equipment (24) is borne to be rotatable in a slide (31) and each pinion (27a, 27b) in that case stands in shape-locking engagement on the one hand with a toothed rack (26a, 26b) at the displaceable cheeks (21) and on the other hand, diametrally opposite, with a toothed rack (26c, 26d) in the fixedly located blocks (16).
  15. Bending device according to claims 3, 4 and 9 with toothed racks arranged at the round belts of a pressure bridge, characterised thereby, that the pressure bridge (46, 47) is articulatedly (48a, 49a) connected with the round bolts (48, 49).
  16. Bending device according to claim 5 with a variable bending pressure loading the pressure pistons, characterised thereby, that the bending pressure for pairs of pressure pistons (42, 43 or 44, 45), acting in like sense and associated with each intermediate member (ramlike cheeks 21 or pressure bridges 56, 57), is variable in opposite sense by way of the piston in the sense that, on a deviation of the centre plane (M) of the radial bearing of a chock from the symmetry plane (S) of the pressure piston in consequence of the axial adjustment of a roll (1, 2), either the guide portions or the round bolts (50, 51) are guided free of moment in the associated block (16) fast with the standard.
EP87100220A 1986-01-17 1987-01-09 Roll bending device for axially shifting rolls of a multiple rolling stand Expired - Lifetime EP0233460B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87100220T ATE63241T1 (en) 1986-01-17 1987-01-09 STATION-FIXED BENDING DEVICE FOR AXIALLY MOVABLE ROLLERS OF A MULTI-ROLLER ROLLER.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3601239 1986-01-17
DE19863601239 DE3601239A1 (en) 1986-01-17 1986-01-17 Bending device for the axially displaceable working rolls of a four-high stand
DE19863604133 DE3604133A1 (en) 1986-02-10 1986-02-10 Bending device, fixed to the housing, for axially displaceable work rolls of a rolling stand
DE3604133 1986-02-10

Publications (3)

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

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EP87100220A Expired - Lifetime EP0233460B1 (en) 1986-01-17 1987-01-09 Roll bending device for axially shifting rolls of a multiple rolling stand

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DE (1) DE3769809D1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2611541B1 (en) * 1987-02-27 1994-04-29 Clecim Sa DEVICE FOR ADJUSTING THE PROFILE AND DISTRIBUTION OF WEAR OF CYLINDERS IN A ROLLER WITH AXIALLY MOVABLE CYLINDERS
GB2202173B (en) * 1987-03-19 1991-08-14 Davy Mckee Rolling mill
AT504208B1 (en) 2006-04-21 2008-04-15 Siemens Vai Metals Tech Gmbh BENDING DEVICE FOR TWO WORKING ROLLERS OF A ROLLING MILL
CN102284502B (en) * 2011-08-11 2013-06-05 二重集团（德阳）重型装备股份有限公司 Bending roll-shifting device of rolling mill

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
DE3261730D1 (en) * 1981-02-28 1985-02-14 Schloemann Siemag Ag Roll stand
JPS57199505A (en) * 1981-06-03 1982-12-07 Hitachi Ltd Work roll moving type rolling mill
JPS5956910A (en) * 1982-09-27 1984-04-02 Kawasaki Steel Corp Method for controlling pressing force for roll bending
DE3331055C2 (en) * 1983-08-29 1994-11-03 Schloemann Siemag Ag Roll stand with axially movable work rolls
GB8528848D0 (en) * 1985-11-22 1985-12-24 Davy Mckee Poole Rolling mills

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EP0233460A3 (en) 1988-09-14
EP0233460A2 (en) 1987-08-26
DE3769809D1 (en) 1991-06-13

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