EP0059417B1 - Cage de laminoir - Google Patents

Cage de laminoir Download PDF

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Publication number
EP0059417B1
EP0059417B1 EP82101364A EP82101364A EP0059417B1 EP 0059417 B1 EP0059417 B1 EP 0059417B1 EP 82101364 A EP82101364 A EP 82101364A EP 82101364 A EP82101364 A EP 82101364A EP 0059417 B1 EP0059417 B1 EP 0059417B1
Authority
EP
European Patent Office
Prior art keywords
rolls
roll
pieces
adjusting means
guide
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
Application number
EP82101364A
Other languages
German (de)
English (en)
Other versions
EP0059417A1 (fr
Inventor
Hans Römmen
Erich Stoy
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 DE19813107693 external-priority patent/DE3107693A1/de
Priority claimed from DE19813122128 external-priority patent/DE3122128A1/de
Application filed by SMS Schloemann Siemag AG filed Critical SMS Schloemann Siemag AG
Publication of EP0059417A1 publication Critical patent/EP0059417A1/fr
Application granted granted Critical
Publication of EP0059417B1 publication Critical patent/EP0059417B1/fr
Expired legal-status Critical Current

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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
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/18—Adjusting or positioning rolls by moving rolls axially
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B21B13/145—Lateral support devices for rolls acting mainly in a direction parallel to the movement of the product
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B21B2013/028—Sixto, six-high stands
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B21B2031/206—Horizontal offset of work rolls

Definitions

  • the invention relates to a roll stand with two work rolls, two intermediate rolls and two backup rolls, i.e. a so-called six-roll roll stand, in which at least the support rolls and the intermediate rolls lie essentially one above the other in the same vertical plane, in which the intermediate rolls between the support rolls and the work rolls also lie axially are arranged displaceably and in which stand-fixed blocks are provided with vertical guide surfaces for the chocks of the work rolls and, on the other hand, carry vertical guide surfaces for the chocks of the intermediate rolls, in which adjustment means for balancing and bending the intermediate roll are also present, which act in the direction of action against the support rolls on the Installation pieces of the intermediate rolls can be brought into effect, and in which the adjusting means forming the bending devices for the intermediate rolls are displaced in the horizontal direction parallel to the roll axes.
  • a roll stand of this type already belongs to the state of the art according to Art. 54 (3) EPC due to EP-A-0 026 903. A similar roll stand is also known from BR-A-7 608 285.
  • the axially displaceable arrangement of the intermediate rolls makes it possible to use the known roll stands for rolling out strips of a wide range of widths.
  • the roll gap is influenced there by adjusting means acting as a roll bending device.
  • the adjustment means assigned to the chocks of the two intermediate rolls are installed between these chocks and together with these bars which can be displaced horizontally relative to the blocks. They therefore act directly on the chocks of the intermediate rolls and are therefore disadvantageously exposed to the horizontal forces which occur during the rolling operation or the roll change. Problems also arise with this known arrangement of the adjusting means for changing the support rollers.
  • the adjusting means which act as a roll bending device, sit in blocks which are fixed to the stand and engage the chocks of the work rolls in order to counteract the deflection of the free end sections of the work rolls which project beyond the rolling stock.
  • adjusting means for the upper intermediate roll are arranged in the blocks, which can act on the chocks.
  • a major disadvantage of the rolling stand according to BR-A-7 608 285 is that the adjusting means, which can also be used as bending devices for the upper intermediate roller, on the one hand have a very specific relative position to the blocks fixed to the stand and, on the other hand, directly attack the chocks which support the intermediate rollers.
  • the adjusting means assigned to the intermediate rolls as bending devices are provided in such a way that they come into direct contact with the chocks of the intermediate rolls and consequently the action exposed to lateral forces during rolling operation and when changing rolls.
  • a four-roll mill stand is also known, that is to say a roll stand containing two support rolls and two work rolls, in which the chocks of the work rolls are displaceably engaged in a horizontal direction parallel to the roll axes with guide pieces, which in turn are relative are arranged vertically displaceable to each other in blocks fixed to the stand.
  • Adjustment means provided as bending devices for the work rolls.
  • the horizontally displaceable operative connection between the chocks of the work rolls and the guide pieces which are vertically movable in the stationary blocks serves only for the purpose of being able to replace each work roll individually and quickly.
  • the invention is based on the object of not only designing a roll stand (six-roll stand) of the type specified at the outset which is suitable for rolling out strips of a wide range in such a way that it is suitable for all rollable strip widths with constant operating conditions with the smallest possible Hertz- ' pressure between the work rolls and the intermediate rolls and an optimal choice of diameter for the work and intermediate rolls - based on the rolling task and the mastery of the circumferential forces - but also that the horizontal lateral forces occurring during the rolling operation and during roll change are kept completely away from the bending devices as well as a trouble-free change of the work rolls and the intermediate rolls is guaranteed.
  • the first solution principle is characterized in that the adjustment means provided as bending devices are located in the blocks fixed to the stand, that on each block a lower and an upper guide piece provided with guide surfaces for the chocks of the intermediate rolls is guided such that the chocks are relative in the horizontal direction to the effective position of the adjusting means and / or the effective position of the adjusting means within the guide pieces is varied in the horizontal direction, that each guide piece consists of a part on the stator side and a part assigned to the chock of the intermediate roller, that the two parts of the guide pieces can only be displaced relative to one another vertically that between them in each case two adjusting means lying one behind the other in the axial direction of the intermediate rollers act as a bending device, that the chocks of the intermediate rollers relative to the parts assigned to them d He guide pieces are arranged exclusively horizontally displaceable, and that the two adjusting means which are located one behind the other can be varied with respect to their actuating forces depending on the respective axial sliding position of the intermediate roller chocks.
  • the second solution principle of the invention is characterized in that the adjustment means provided as bending devices are located in the blocks fixed to the stand, that on each block a lower and an upper guide piece provided with guide surfaces for the chocks of the intermediate rolls is guided such that the horizontal displacement of the Adjustment means is carried out relative to the chocks and within the guide pieces, that each guide piece consists of a stator-side part and a part assigned to the chocks of the intermediate roller, that the two parts of the guide pieces are horizontally and vertically displaceable relative to each other, that between them one in the chock-side Part of the guide pieces built adjusting means is provided on the middle plane of the intermediate roller chocks that the chock-side part of the guide piece with the associated chock relative to the stator-side part horiz ontal is slidably connected, and that the stator-side part is connected to the chock-side part of the guide pieces via an intermediate part, which on the one hand has horizontal sliding guides to the stator-side part and on the other hand vertical sliding guides to the chock
  • the design of a six-roll mill stand according to the invention has on the one hand the significant advantage that there is little wear on the work rolls because they are not corrected around the edge of the intermediate rolls.
  • the shifting conditions for the intermediate rolls are also significantly improved because the actuating forces occurring here are completely kept away from the adjustment means serving as bending devices.
  • the measures according to the invention also prevent a mutual impairment of the available design spaces, so that with an optimal choice of diameter of work rolls and intermediate rolls there is no restriction with regard to the design of the effective force transmission systems for the bending correction forces, so that no dimensioning difficulties can arise.
  • the bending lever arm of the axially displaceable intermediate rollers can be kept constant for all rolling conditions according to the first-mentioned solution principle, because here the two adjusting means located one behind the other can be varied with regard to their actuating forces depending on the respective axial sliding position of the intermediate roller chocks.
  • the adjusting means forming the bending device are installed in the stator-side part of the guide pieces and on the chock-side part to grab.
  • the pressure medium supply to the adjustment means can then be effected with particularly little effort.
  • the adjusting means serving as a bending device consist of hydraulically actuatable piston-cylinder units which are installed in one part of the guide piece, while the piston rod acts on the other part.
  • piston-cylinder units are double-acting and engage between the two parts of the guide pieces in a tensile and compressive manner.
  • the design according to the invention is not only suitable for six-roll roll stands in which all the rolls - work rolls, intermediate rolls and backup rolls - lie on a common vertical plane; Rather, it can also be used in six-roll rolling stands of the type in which the work rolls are displaced from the vertical axis plane of the intermediate rolls and the support rolls and are supported on their bales in the direction of the displacement by intermediate rolls and / or support rolls mounted on support bridges, such as which is known per se from DE-B-2 522 213.
  • the guide pieces which are guided vertically displaceably in the blocks fixed to the stand and which contain the adjusting means forming the bending devices are advantageously positively connected to the chocks of the intermediate rolls by horizontal guides in the vertical direction, the horizontal guides for the roll change between the stands being continued parallel to the rolls.
  • the smallest diameter of the intermediate rolls is only limited by the height of their chocks or the guide pieces provided between them and the stand.
  • the roll stand according to the invention can be developed with simple means so that there is an effective expansion of the bending correction range, which enables an improvement in the strip profile quality and also the optimization of the joint pressures on the one hand at the contact points of the work rolls with the intermediate rolls and on the other hand at the contact points of the intermediate rolls with the support rollers.
  • This advantage can be achieved according to the invention in that the chocks of the two work rolls in the blocks are assigned adjusting means as bending devices which act on guide pieces, which in turn are held on the one hand by vertical guides in the blocks and on the other hand have horizontal guides for the chocks.
  • the particular advantage of such a measure is that by simultaneously engaging the bending devices separately assigned to the intermediate rolls and the work rolls, the strip profile quality can be increased, that the separate controllability of the joint pressures at the contact points of the work rolls and intermediate rolls as well as between the intermediate rolls and backup rolls results in a reduction of the roll wear and that the roll load and the roll bearing load is reduced.
  • the backing roll profile correction can be brought about by the bending of the intermediate rolls, while on the other hand the bending of the work rolls can be used for process interventions.
  • each guide piece consists of a part on the upright side and a part assigned to the chock of the work roll, the adjusting means forming the bending device between them both parts are arranged.
  • the two parts of the guide pieces are exclusively vertically displaceable relative to one another, while the chocks of the work rolls are arranged only horizontally displaceable relative to the parts of the guide pieces assigned to them.
  • the adjusting means forming the bending device can be installed in the stator-side part of the guide pieces and can engage on the chock-side part thereof. It is also possible, however, for the adjusting means forming the bending devices to be seated in the chock-side part of the guide pieces and to engage the stator-side part thereof.
  • the adjustment means assigned to the chocks of the two work rolls consists of hydraulically actuatable piston-cylinder units which are installed in one part of the guide piece and whose piston rod acts on the other part.
  • These adjustment means are also designed to be double-acting and are provided with tensile and compressive strength between the two parts of the guide pieces.
  • the stand-side parts of the guide pieces for the chocks of the work rolls are expediently assigned abutments within the blocks of the roll stands, by means of which the relative position of the stand-side parts of the guide pieces to one another and / or to the blocks can be determined.
  • These adjustable abutments can consist of piston-cylinder units installed in the stator-side parts of the guide pieces.
  • the roll stand shown in FIG. 1 has in the usual way two roll stands 1 arranged at a distance from one another, of which only one is shown in FIG. 1.
  • two work rolls 2 and 3 two intermediate rolls 4 and 5 and two support rolls 6 and 7 are accommodated, so that a so-called six-high roll stand is formed.
  • the upper support roller 6 and the lower support roller 7 are held and guided directly via their chocks 8 and 9 in the stand windows 10 of the two roll stands 1, the adjusting devices 11 of the roll stand attacking the chocks 8 of the upper support roller 6.
  • the chocks 13 of the upper work roll 2 are positively connected in the vertical direction, but are horizontally displaceably connected for the changing process to guide pieces 17, which in turn are guided vertically displaceably in the blocks 12 fixed to the stand.
  • the chocks 14 of the lower work roll are connected to guide pieces 18, which are also guided vertically displaceably in the blocks 12 fixed to the stand.
  • the chocks 15 of the upper intermediate roller 4 are assigned guide pieces 19, with the chocks 15 also being in positive engagement with the guide pieces 19 in the vertical direction but being horizontally displaceable.
  • Guide pieces 20 of the same type and mode of operation are also assigned to the chocks 16 for the lower intermediate roller 5.
  • the horizontal guides 21 between the chocks 15 and 16 for the intermediate rolls 4 and 5 and the associated guide pieces 19 and 20 are designed so that they not only allow the change of the intermediate rolls 4 and 5 together with the work rolls 2 and 3, but that they also ensure an axial displacement of the intermediate rolls 4 and 5 relative to the work rolls 2 and 3 and to the support rolls 6 and 7 for the rolling operation.
  • the axial displacement of the intermediate rolls 4 and 5 is important for the rolling operation because this allows the rolling stand to be adjusted to the different widths of the strips to be rolled out. This setting prevents the rolling out of the rolled strips in the region of their longitudinal edges and the particularly high stress on the sections of the work rolls which act on the rolled material edges.
  • the mounting pieces 15 of the upper intermediate roll 4 and the corresponding mounting pieces 16 of the lower intermediate roll 5 in the area of the blocks 12 which are fixed to the stand are each adjusting means 22 in the form of hydraulically actuatable piston-cylinder Associated units, the arrangement and design of which clearly results from FIGS. 2 and 3.
  • These adjustment means or bending devices 22 for the intermediate rolls 4 and 5 are each in the block ken 12 associated guide pieces 19 and 20 installed.
  • the right guide piece 19 for the chocks 15 of the upper intermediate roller is shown.
  • All guide pieces 19 for the upper intermediate roll 4 and also all guide pieces 20 for the lower intermediate roll 5 have the same design; however, they are installed relative to each other in a mirror-image position in the roll stand 1, i. H. the left-hand guide pieces 19 and 20 are each mirror images of the right-hand guide pieces 19 and 20, while the upper guide pieces 19 in turn assume a mirror-image position to the lower guide pieces 20 in the roll stands 1.
  • each of the guide pieces 19 and 20 consists of a stator-side part 23 and a part 24 assigned to the chock 15 or 16 of the intermediate roller 4 or 5.
  • the adjustment means 22 forming the bending device for the intermediate roller 4 or 5 are installed, which in turn engage via their piston rod 25 on the chock-side part 24.
  • the operative connection between the piston rods 25 of the adjusting means 22 and the chock-side part 24 of each guide piece 19 or 20 is of such a type that with the help of the chocks 15 or 16 bending forces on the intermediate roller 4 or 5 at least in the direction against the Back-up roller 6 and 7 can be exercised.
  • connection between the piston rods 25 of the adjusting means 22 and the chock-side part 24 of the guide piece 19 in such a way that bending forces on the intermediate roller 4 or 5 both in the direction against the associated support roller 6 or 7 and also let exercise in the direction away from it.
  • the two parts 23 and 24 of the guide piece 19 are composed exclusively vertically displaceable relative to one another, that is to say secured against any horizontal displacement relative to one another.
  • the two adjustment means 22 installed in each guide piece 19 and serving as a bending device for the intermediate roller 4 or 5 have the purpose of keeping the bending lever arm of the intermediate roller 4 or 5 constant in any possible axial displacement position thereof. Therefore, the two adjustment means 22 are designed so that they can be varied depending on the instantaneous axial sliding position of the two intermediate roller chocks 15 and 16 relative to the guide piece 19 with respect to the actuating forces exerted by them. In the axial sliding position of the intermediate roller chock 15 shown in FIG. 3, the higher adjusting force is applied by the adjusting means 22 ′′ and the low adjusting force by the adjusting means 22 ′. The reverse is true if the intermediate roller chock 15 assumes the opposite extreme axial position Varying the actuating forces also ensures that all four individual forces acting on an intermediate roller act symmetrically with respect to their transfer to the backup roller to the center of the stand.
  • actuating forces are exerted by both adjusting means 22 'and 22 "when the intermediate roller chock 15 is in its central axial sliding position.
  • the actuating forces respectively applied by the adjusting means 22 thus change proportionally in relation to the extent of the axial displacement of the intermediate roller chock 15 Guide piece 19 in such a way that the bending lever arm for the intermediate roller 4 always engages in the central plane of the intermediate roller chocks 15 and 16 lying transversely to the roller axis and that the total effect of the actuating forces is symmetrical to the center of the stand at both ends of the intermediate rollers.
  • FIG. 4 of the drawing This mode of operation of the intermediate roll bending device is shown schematically in FIG. 4 of the drawing.
  • the force arrows 26, 27, 28 and 29 hereby indicate the position of the action of the four adjusting means 22 acting as an intermediate roller bending device.
  • the two double arrows 30 and 31 represent the central plane of the intermediate roller chocks and the two arrows 32 and 33 indicate the forces opposing the bending of the intermediate rollers, which emanate from the associated support roller.
  • the relative position of the double arrows 30 and 31 on the one hand to the force arrows 26 and 27 or 28 and 29 and on the other hand to the arrows 32 and 33 corresponds to the respective axial displacement position of the intermediate roller chocks and thus also the intermediate roller relative to the associated work roller and the associated backup roller.
  • the basic structure of the six-high roll stand shown in FIG. 5 corresponds entirely to that of the roll stand according to FIG. 1. However, the structure and mode of operation of the guide pieces 19 and 20 for the two intermediate rolls 4 and 5 are different here.
  • FIG. 6 it is shown with the aid of the upper right guide piece 19 that the guide pieces 19 and 20 in turn have a stator-side part 34 and a chock-side part 35, but that an intermediate part 36 is also present.
  • the stand-side part 34 is installed as a component of the block 12 in the roll stand 1. It interacts with the intermediate part 36 via horizontal guides 37 running parallel to the roll axis, in such a way that the intermediate part 36 is displaceable in the stator-side part 34 in the axial direction of the intermediate roll 4 or 5, but is supported in the vertical direction in a form-fitting manner.
  • the chock-side part 35 of the guide piece 19 or 20 engages only vertically displaceably, so that the intermediate part 36 and the chock-side part 35 can carry out the horizontal displacement relative to the stator-side part 34 together.
  • the form-fitting horizontal guidance in the vertical direction between the chock 15 or 16 of the intermediate roller 4 or 5 and the chock-side part 35 of the guide piece 19 is only useful here for changing the intermediate roller 4 or 5; the chock 15 or 16 and the chock-side part 35 of the guide piece 19 or 20 are thus locked together against horizontal displacement during the rolling operation.
  • the adjusting means 38 which forms the bending device for the intermediate roll 4 or 5 is installed in the form of a hydraulically actuatable piston-cylinder unit in the chock-side part 35 of the guide piece 19 or 20, and its piston rod 39 interacts with the intermediate part 36.
  • the adjusting means 38 can be double-acting and act on the intermediate part 36 with its piston rod 39 in a tensile and compressive manner.
  • the chock-side part 35 With each axial displacement of the intermediate roller 4 or 5, the chock-side part 35, together with the intermediate part 36, carries out a corresponding horizontal displacement relative to the stator-side part 34 without the effective plane of the adjusting means 38 changing relative to the intermediate roller chock 15 or 16. As a result, its bending lever arm remains unchanged in every axial sliding position of the intermediate roller 4 or 5.
  • the one according to FIG. 6 has a simplified structure in that it only requires one adjustment device 38 serving as a bending device.
  • a control for the bending device according to FIG. 6 can thus be made simpler because only the effect of the actuating forces of both intermediate roller ends has to be symmetrical to the center of the stand.
  • the intermediate part 36 is required as an additional element in the exemplary embodiment according to FIG. 6, which, however, can be implemented inexpensively as a mechanically simple component.
  • FIG. 7 shows a six-high mill stand, which differs in its basic structure from the mill stands according to FIGS. 1 and 5.
  • 1 and 5 the work rolls 2, 3, the intermediate rolls 4, 5 and the backup rolls 6, 7 lie on a common vertical axis plane, in the roll stand according to FIG. 7 this essentially common axis plane is of a certain size shifted from the vertical.
  • the work rolls 2 and 3 are supported on their bale circumference by intermediate rolls 42 and 43 and / or support rolls 44, 45 mounted on support bridges 40 and 41.
  • the chocks 15, 16 of the intermediate rolls 4 and 5 intermediate roll bending devices of the embodiment shown in FIGS. 2 and 6 can be assigned and consequently the advantages of the intermediate roll bending can be optimally used.
  • a work roll bending device in addition to the intermediate roll bending device, a work roll bending device can be seen in which the Guide pieces 117 and 118 for the chocks 13 and 14 of the two work rolls 2 and 3 basically have the same structure as the guide pieces 19 and 20 for the two intermediate rolls 4 and 5. Also, their relative position to one another in the roll stand basically corresponds to that of the guide pieces 19 and 20 for the intermediate rolls 4 and 5.
  • each of the guide pieces 117 and 118 consists of a stator-side part 53 and a part 54 assigned to the chock 13 and 14 respectively.
  • the adjusting means 55 which form the bending device for the work rolls 2 and 3 are installed, which are designed as piston-cylinder units and engage via their piston rod 56 on the chock-side part 54.
  • the operative connection between the piston rods 56 of the adjusting means 55 and the chock-side part 54 of each guide piece 117 and 118 is of such a type that with the help of the guide pieces 117 and 118 bending forces on the work roll 2 and 3 both in the direction against the associated intermediate roller 4 or 5 and exercise in the direction away from it.
  • stator-side parts 53 of the guide pieces 117 and 118 are expediently supported via abutments against the blocks 12 and / or against one another in such a way that their chock-side parts 54 and thus also the chocks 13 and 14 for the work rolls 2 and 3 are formed by the bending device Adjustment means 55 can be shifted independently of the respective support position of the stand-side parts 53 for work roll bending.
  • piston-cylinder units 57 are provided as abutments, for example, which hold the stator-side parts 53 of the guide pieces 117 and 118 in connection with one another in such a way that they enable a basic setting of the roll gap between the work rolls 2 and 3, but a common, Allow vertical relative displacement of the guide pieces 117 and 118 relative to the blocks 12 to an unlimited extent. Regardless of this possible relative displacement of the work roll set 2, 3 in the vertical direction to the blocks 12, the two work rolls 2 and 3 can be bent individually in each of the two possible directions in the vertical plane by the adjusting means 55 in order to make the respectively desirable interventions in the rolling process enable.
  • the basic structure of the six-high mill stand shown in FIG. 10 corresponds entirely to that of the roll stand according to FIG. 8.
  • the construction and mode of operation of the guide pieces 19 and 20 for the intermediate roll chocks 15 and 16 on the one hand and the structure on the other hand are different of the guide pieces 117 and 118 for the work roll chocks 13 and 14.
  • FIG. 11 shows, in addition to the intermediate roll bending already described in connection with FIG. 6, the right guide piece 117 for the chocks 13 of the upper work roll 2 shown in FIG. 10. It should also be pointed out here that all guide pieces 117 for the upper work roll 2 as well all the guide pieces 118 for the lower work roll 3 have the same design with respect to one another and that they differ from one another only with regard to their installation position in the roll stands 1.
  • the guide pieces 117 and 118 also have a stator-side part 58 and a chock-side part 59.
  • the adjusting means 60 forming the bending device for the work roll 2 or 3 is in the form of a hydraulically loadable device Piston-cylinder unit with the chock-side parts 59 of the guide pieces 117 and 118 installed and its piston rod 61 cooperates with the stator-side part 58.
  • the adjusting means 60 is double-acting and is fastened with its piston rod 39 to the part 58 on the stator side in a tensile and compressive manner.
  • piston-cylinder units 62 and 63 can be formed in the upright part 58 of the guide pieces 117 and 118 for forming these abutments to be built in.
  • the piston rods 64 and 65 of the two piston-cylinder units 62 and 63 are supported on the one hand against one another or can be coupled to one another, while on the other hand they come to rest against horizontally running support surfaces of the blocks 12.

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

Claims (14)

1. Cage de laminoir avec deux cylindres de travail (2, 3), deux cylindres intermédiaires (4, 5) et deux cylindres de soutien (6,7) (cage de laminoir sexto), dans laquelle au moins les cylindres de soutien (6, 7) et les cylindres intermédiaires (4, 5) sont situés sensiblement dans un même plan vertical, dans laquelle en outre les cylindres intermédiaires (4, 5) sont disposés avec possibilité de déplacement axial entre les cylindres de soutien (6, 7) et les cylindres de travail (2, 3) et dans laquelle des blocs (12) fixés aux colonnes d'une part sont munis de faces de guidage verticales pour les empoises (13,14) des cylindres de travail (2,3) et, d'autre part, portent des faces de guidage verticales pour les empoises (15,16) des cylindres intermédiaires (4, 5), dans laquelle en outre il existe, pour équilibrer et fair fléchir les cylindres intermédiaires (4, 5), des moyens de déplacement (22) qui, avec une direction effective contre les cylindres de soutien (6, 7), peuvent être mis en action sur les empoises (15, 16) des cylindres intermédiaires (4, 5), et dans laquelle les moyens de déplacement (22) formant les dispositifs de flexion pour les cylindres intermédiaires (4, 5) sont déplacés en direction horizontale parallelement aux axes des cylindres, caractérisée en ce
que les moyens de déplacement (22) prévus en tant que dispositifs de flexion sont installés dans les blocs (12) fixés aux colonnes,
que sur chaque bloc (12) peut être déplacée en direction verticale une pièce de guidage (20, 19) inférieure (20) et supérieure (19) de faces de guidage pour les empoises (16 resp. 15) des cylindres intermédiaires (5 resp. 4),
que les empoises (15, 16 sont déplacées en direction horizontale par rapport à la position active des moyens de déplacement (22), et/ou que la position active des moyens de déplacement
(22) est modifiée (20', 22') en direction horizontale dans les guidages (19, 20),
que chaque guidage (19, 20) se compose d'une partie (23) côté colonne et d'une partie (24) affectée à l'empoise (15, 16) du cylindre intermédiaire (4,5),
que les deux parties (23, 24) des guidages (19, 20) peuvent être déplacées exclusivement verticalement relativement l'une à l'autre,
qu'entre elles attaquent, en tant que dispositif de flexion, deux moyens de déplacement (22; 22', 22") situés à distance l'un derrière l'autre dans la direction axiale des cylindres intermédiaires (4, 5),
que les empoises (15, 16) des cylindres intermédiaires (4,5) sont, par rapport aux parties (24) des guidages (19, 20) qui leur sont affectées, disposées avec possibilité de déplacement exclusivement horizontalement (21 ; fig. 1 à 3),
et que les deux moyens de déplacement (22; 22', 22") situés à distance l'un derrière l'autre peuvent, en ce qui concerne leurs de déplacement, être modifiés en fonction de la position de déplacement axiale des empoises des cylindres intermédiaires.
2. Cage de laminoir avec deux cylindres de travail (2, 3), deux cylindres intermédiaires (4, 5) et deux cylindres de soutien (6, 7) (cage de laminoir sexto), dans laquelle au moins les cylindres de soutien (6, 7) et les cylindres intermédiaires (4, 5) sont situés sensiblement dans un même plan vertical, dans laquelle en outre les cylindres intermédiaires (4, 5) sont disposés avec possibilité de déplacement axial entre les cylindres de soutien (6, 7) et les cylindres de travail (2, 3), et dans laquelle des blocs (12) fixés aux colonnes d'une part sont munis de faces de guidage verticales pour les empoises (13, 14) des cylindres de travail (2, 3) et, d'autre part, portent des faces de guidage verticales pour les empoises (15,16) des cylindres intermédiaires (4, 5), dans laquelle en outre il existe, pour équilibrer et faire fléchir les cylindres intermédiaires (4, 5), des moyens de déplacement (38) qui, avec une direction effective contre les cylindres de soutien (6, 7), peuvent être mis en action surles empoises (15, 16) des cylindres intermédiaires (4, 5), et dans laquelle les moyens de déplacement (38) formant les dispositifs de flexion pour les cylindres intermédiaires (4, 5) sont déplacés en direction horizontale parallèlement aux axes des cylindres, caractérisée en ce
que les moyens de déplacement (38) prévus en tant que dispositifs de flexion sont installés dans les blocs (12) fixés aux colonnes,
que sur chaque bloc (12) peut être déplacée en direction verticale une pièce de guidage (20, 19) inférieure (20) et supérieure (19) munie de faces de guidage pour les empoises (16 resp. 15) des cylindres intermédiaires (5 resp. 4),
que le déplacement horizontal des moyens de déplacement (38) est effectué par rapport aux empoises (15, 16) et dans les guidages (19, 20), que chaque guidage (19, 20) se compose d'une partie (34) côté colonne et d'une partie (35) affectée à l'empoise (15, 16) du cylindre intermédiaire (4,5),
que les deux parties (34, 35) des guidages (19,20) peuvent être déplacées horizontalement et verticalement relativement l'une à l'autre (36),
qu'entre elles est prévu, sur le pla médian des empoises (15, 16) des cylindres intermédiaires, un moyen de déplacement (38) installé dans la partie (35) des guidages (19,20) côté empoises, que la partie (35) du guidage (19, 20) côté empoises est reliée à l'empoise correspondante (15, 16) avec possibilité de déplacement horizontal (21) relativement à la partie (34) côté colonne,
et que la partie (34) côté colonne est reliée à la partie côté empoise (35) des guidages (19, 20) par une partie intermédiaire qui a d'une part des guidages coulissants horizontaux (37) pour la partie côté colonne (34) et d'autre part des guidages coulissants verticaux pour la partie côté empoise (35) (fig. 5 et 6).
3. Cage de laminoir selon la revendication 1, caractérisée en ce que les moyens de déplacement (22) formant le dispositif de flexion sont installés dans la partie côté colonne (23) des guidages (19, 20) et attaquent (25; fig. 1 et 2) la partie côté empoise (24).
4. Cage de laminoir selon une des revendications 1 à 3, caractérisée en ce que les moyens de déplacement (22 resp. 38) se composent de vérins hydrauliques qui sont installés dans une partie (23 resp. 35) du guidage (19, 20) et dont la tige de piston (25 resp. 39) attaque l'autre partie (24 resp. 36, 34).
5. Cage de laminoir selon une des revendications 1 à 4, caractérisée en ce que les moyens de déplacement (22 resp. 38) sont à double effet et attaquent entre les guidages (19, 20) de manière rigide à la traction et à la compression.
6. Cage de laminoir selon une des revendications 1 à 5, caractérisée en ce qu'également aux empoises (13,14) des deux cylindres de travail (2, 3) sont affectés des moyens de déplacement (55; 60) prévus dans les blocs (12), ces moyens attaquant des pièces de guidage (117 resp. 118) qui, à leur tour, d'une part sont maintenues dans les blocs (12) par l'intermédiaire de guidages verticaux (53, 54 resp. 58, 59) et, d'autre part, comportent des guidages horizontaux (54 resp. 59) pour les empoises (13,14) (fig. 8 à 11).
7. Cage de laminoirsselon la revendication 6, caractérisée en ce que chaque pièce de guidage (117 resp. 118) se compose d'une partie côté colonne (53 resp. 58) et d'une partie (54 resp. 59) affectée à l'empoise (13 resp. 14) du cylindre de travail (2 resp. 3), les moyens de déplacement (55 resp. 60) qui forment le dispositif de flexion étant disposés entre ces deux parties (53, 54 resp. 58, 59) (fig. 9 resp. 11).
8. Cage de laminoir selon la revendication 6 ou 7, caractérisée en ce que les deux parties (53, 54, resp. 58, 59) des pièces de guidage (117, 118) peuvent être déplacées l'une par rapport à l'autre exclusivement verticalement et les empoises (13, 14) des cylindres de travail (2, 3) sont disposées de manière à pouvoir être déplacées exclusivement horizontalement par rapport aux parties (54, 59) des pièces de guidage (17, 18) qui leur sont affectées (fig. 9 resp. 10).
9. Cage de laminoir selon une des revendications 6 à 8, caractérisée en ce que les moyens de déplacement (55) qui forment le dispositif de flexion sont installés dans la partie côté colonne (53) des pièces de guidage (117, 118) et attaquent (56; fig. 9) la partie côté empoise (54).
10. Cage de laminoir selon une des revendications 6 à 8, caractérisée en ce que les moyens de déplacement (60) qui forment le dispositif de flexion sont installés dans la partie côté empoise (59) des pièces de guidage (117, 118) et attaquent (61; fig. 11) la partie côté colonne (58).
11. Cage de laminoir selon une des revendications 6 à 10, caractérisée en ce que les moyens de déplacement (55 resp. 60) se composent de vérins hydrauliques installés dans une partie (53, resp. 59) des pièces de guidage (117 resp. 118), leur tige de piston (56 resp. 61) attaquant l'autre partie (54 resp. 58) (fig. 9 resp. 11).
12. Cage de laminoir selon une des revendications 6 à 11, caractérisée en ce que les moyens de déplacement sont à double effet et attaquent entre les pièces de guidage (117,118) de manière rigide à la traction et à la compression.
13. Cage de laminoir selon une des revendications 6 à 12 caractérisée en ce qu'aux parties côté colonne (53 resp. 58) des pièces de guidage (117,118) à l'intérieur des blocs (12) des colonnes (1) sont affectées des butées (57 resp. 62, 63) par l'intermédiaire desquelles la position relative des parties côté colonnes (53 resp. 58) des pièces de guidage (117 et 118) les unes par rapport aux autres et/ou aux blocs (12) peut être déterminée.
14. Cage de laminoir selon la revendication 13, caractérisée en ce que les butées déplaçables (57 resp. 62, 63) se composent de vérins hydrauliques installés dans les parties côté colonnes (53 resp. 58) des pièces de guidage (117,118).
EP82101364A 1981-02-28 1982-02-23 Cage de laminoir Expired EP0059417B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19813107693 DE3107693A1 (de) 1981-02-28 1981-02-28 Walzgeruest
DE3107693 1981-02-28
DE19813122128 DE3122128A1 (de) 1981-06-04 1981-06-04 Walzgeruest
DE3122128 1981-06-04

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EP0059417A1 EP0059417A1 (fr) 1982-09-08
EP0059417B1 true EP0059417B1 (fr) 1985-01-02

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DE (1) DE3261730D1 (fr)

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DE3503756A1 (de) * 1984-03-13 1985-09-19 SMS Schloemann-Siemag AG, 4000 Düsseldorf Sechswalzengeruest
JPH0620561B2 (ja) * 1985-04-03 1994-03-23 株式会社日立製作所 圧延機のロ−ルベンデイング装置
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DE3769809D1 (de) * 1986-01-17 1991-06-13 Schloemann Siemag Ag Staenderfeste biegevorrichtung fuer axial verschiebbare walzen eines mehrwalzengeruestes.
DE3603693A1 (de) * 1986-02-06 1987-08-13 Schloemann Siemag Ag Vorrichtung zum axialen verschieben der arbeitswalzen eines walzgeruestes zum walzen von flachmaterial
DE3627690A1 (de) * 1986-08-14 1988-02-25 Schloemann Siemag Ag Biege- und ausbalanciervorrichtung fuer axial verschiebbare arbeitswalzen eines quartowalzgeruestes
DE3627692A1 (de) * 1986-08-14 1988-02-25 Schloemann Siemag Ag Biege- und ausbalanciervorrichtung fuer axial verschiebbare arbeitswalzen eines quartowalzgeruestes
DE3634367A1 (de) * 1986-10-09 1988-04-21 Schloemann Siemag Ag Walzen-anordnung zur verformungsfreien behandlung von bewegten bandfoermigen erzeugnissen
DE3638331C2 (de) * 1986-11-10 1995-07-13 Schloemann Siemag Ag Walzgerüst zum Walzen von Flachmaterial mit einem Paar von axial verschiebbaren Arbeitswalzen
DE3707560A1 (de) * 1987-03-10 1988-09-22 Schloemann Siemag Ag Walzgeruest
DE3815454A1 (de) * 1988-05-06 1989-11-16 Schloemann Siemag Ag Biege- und ausbalanciervorrichtung fuer axial verschiebbare walzen eines walzgeruestes
DE3822821A1 (de) * 1988-07-06 1990-01-18 Schloemann Siemag Ag Walzwerk zur herstellung eines walzgutes
US4898014A (en) * 1988-12-23 1990-02-06 United Engineering, Inc. Roll shifting system for rolling mills
DE3843387A1 (de) * 1988-12-23 1990-07-05 Schloemann Siemag Ag Vorrichtung zum walzenwechsel insbesondere der horizontal verschieblichen arbeitswalzen in einem walzgeruest
DE4041290A1 (de) * 1990-12-21 1992-07-02 Achenbach Buschhuetten Gmbh Vorrichtung zum ausbalancieren und vertikalen biegen der arbeitswalzen eines quartowalzgeruestes
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FR2733171B1 (fr) * 1995-04-19 1997-07-04 Clecim Sa Laminoir a grande ouverture
DE19922373A1 (de) * 1999-05-14 2000-11-16 Sms Demag Ag Biegevorrichtung für die Arbeitswalzen eines Warmwalzgerüstes
DE10257971A1 (de) * 2002-12-12 2004-06-24 Sms Demag Ag Mehrwalzengerüst zum Walzen eines Metallbandes
DE102009058876A1 (de) * 2009-01-23 2010-07-29 Sms Siemag Ag Biege- und Ausbalanciervorrichtung für axial verschiebbare Arbeitswalzen eines Walzgerüstes
DE102009060641A1 (de) 2009-07-07 2011-01-13 Sms Siemag Ag Vorrichtung zur Arretierung des Einbaustückes und des Axiallagergehäuse eines Walzensatzes sowie des Walzenwechselwagen
CN103157666B (zh) * 2013-04-11 2015-05-20 中冶赛迪工程技术股份有限公司 板带轧机轧辊调节装置
FR3006211B1 (fr) 2013-05-28 2015-05-15 Fives Dms Procede de changement de configuration d'un laminoir et laminoir pour la mise en oeuvre du procede.
FR3048899B1 (fr) * 2016-03-17 2019-05-31 Fives Dms Laminoir pour bande metallique
IT201900000713A1 (it) * 2019-01-17 2020-07-17 Danieli Off Mecc Sistema di bending e shifting per gabbie di laminazione

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EP0059417A1 (fr) 1982-09-08
US4543810A (en) 1985-10-01
DE3261730D1 (en) 1985-02-14
US4615202A (en) 1986-10-07

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