EP0734794A1 - Cage de laminoir à cylindres d'appui et de travail pour le laminage de tÔles et de bandes - Google Patents

Cage de laminoir à cylindres d'appui et de travail pour le laminage de tÔles et de bandes Download PDF

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Publication number
EP0734794A1
EP0734794A1 EP96250070A EP96250070A EP0734794A1 EP 0734794 A1 EP0734794 A1 EP 0734794A1 EP 96250070 A EP96250070 A EP 96250070A EP 96250070 A EP96250070 A EP 96250070A EP 0734794 A1 EP0734794 A1 EP 0734794A1
Authority
EP
European Patent Office
Prior art keywords
support
roll
rolls
work
strips
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.)
Granted
Application number
EP96250070A
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German (de)
English (en)
Other versions
EP0734794B1 (fr
Inventor
Dieter Dipl.-Ing. Figge
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.)
Vodafone GmbH
Original Assignee
Mannesmann AG
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Filing date
Publication date
Application filed by Mannesmann AG filed Critical Mannesmann AG
Publication of EP0734794A1 publication Critical patent/EP0734794A1/fr
Application granted granted Critical
Publication of EP0734794B1 publication Critical patent/EP0734794B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • B21B13/023—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally the axis of the rolls being other than perpendicular to the direction of movement of the product, e.g. cross-rolling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B21B31/22—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis mechanically, e.g. by thrust blocks, inserts for removal
    • B21B31/26—Adjusting eccentrically-mounted roll bearings

Definitions

  • the invention relates to a roll stand with support and work rolls for rolling sheets and strips, in which the upper and lower work rolls together with the support rolls assigned to them by pairwise horizontal displacement in pairs of the stand windows formed between the stand columns of the roll stands in chocks by means of the Installation pieces of effectively assigned displacement drives can be moved out of the common vertical plane into positions in which the vertical planes running through the roller axes of the upper work and backup rolls and the lower work and backup rolls intersect,
  • pair cross-rolling systems Systems in which the upper and lower rolls of a four-high roll stand are pivoted in pairs and in opposite directions are also known as pair cross-rolling systems.
  • the profile of the rolling stock can be adjusted without having to apply high work roll bending forces as is otherwise necessary.
  • a resultant advantage is a larger adjustment range when setting the rolling stock profile.
  • Patent application 0 525 552 A1 proposes common sliding blocks for the chocks of the work and back-up rolls, which are arranged between the chocks and the roller stand and have wedge surfaces on their sides facing away from the chocks, which correspond to vertically adjustable displacement drives with the same wedge surfaces. At the Adjustment of these displacement drives cause the wedge surfaces sliding on one another to cause the displacement blocks to be displaced horizontally, as a result of which they adjust the chocks lying on the side.
  • the known pair-cross-rolling systems are very complex, they usually require special work roll bearings;
  • the roller sets must be provided with axial locks in order to be able to absorb the axial forces caused by the system-related inclination of the rollers.
  • Another disadvantage is the fact that adjustment components are arranged in the area of the frame guides, which hinder the roll change.
  • the object of the present invention is to design a roll stand of the generic type with little mechanical outlay in such a way that with simple displacement drives and high system stability, the rolls are entangled with conventional bearings is possible, whereby the installation and removal of the work rolls is not hindered compared to conventional roll stands.
  • each roll neck of the work rolls is mounted in an eccentric bushing receiving the roller bearing designed as a self-aligning bearing, each eccentric bushing being rotatable in opposite directions to the other eccentric bushing and that each roll neck of the support rollers can be horizontally displaced horizontally within the mounting piece in a sliding frame receiving the roller bearing, the set angles of the upper work and support rollers and the lower work and support rollers being the same.
  • the proposed solution has the essential advantage over the prior art that all adjustment means, both for the work and the backup rolls, are arranged within the chocks and can be installed and removed with them in a conventional manner.
  • the proposal of the invention enables the use of conventional work roll bending devices in the roll stands, for example in the form of known bending blocks which are supported in the stand window.
  • Adjusting the work and backup rolls with different adjustment means has advantages when changing the rolls - the work rolls can be changed independently of the backup rolls - and takes into account the different loading of the work and backup rolls from the rolling forces. Adapted to the loads occurring, the respective roller bearings can be built very small, which on the one hand reduces the price of the roll stands and on the other hand the space requirement. The latter advantage makes it possible to retrofit the invention into existing roll stands.
  • the eccentric bushes on the outside of the work rolls are provided with circumferential toothing in which the correspondingly formed toothing of a rotary drive engages and that the two eccentric bushes of a work roll are mechanically coupled to one another when the direction of rotation is reversed.
  • rotary drives are provided, with which the roller journals, which are mounted extremely stably in the eccentrics, are horizontally displaced in opposite directions on both sides of the roll stand.
  • the roller axis moves with respect to the center of the chock, which itself only has to be adjusted vertically with respect to the required height in the roll stand. Since the bearings of the work rolls are designed as self-aligning bearings, the work rolls can easily be set from their central position.
  • the rotary drives engaging in the external toothings on the eccentric bushes are structurally simple and reliable, in particular if, according to a further feature of the invention, the rotary drive for the eccentric bushes on the work rolls is designed as a geared motor with planetary gear provided on the operating side of the roll stand, the drive pinion of which is on the operating side combs directly and on the drive side via a drive shaft connecting the drive pinion with one another parallel to the work roll and with the interposition of an intermediate wheel with the interlocking of the eccentric bushings, with different directions of rotation of the eccentric bushings the spur gear ratios on both sides is the same.
  • a larger eccentric bushing can be accommodated on the operating side of the roll stand, as can the actuator for the roller crossing.
  • the cardan shaft transmits the drive power to the drive side of the roll stand, where a smaller eccentric bushing can be provided, which is connected to the drive via an idler gear to reverse the direction of rotation.
  • Cylindrical roller bearings or tapered roller bearings with spherical outer rings and spherical roller bearings with cylindrical outer rings that absorb axial forces on the drive side are preferably installed as self-aligning bearings on the operating side of the roll stand. Such bearings are small in size and still able to safely absorb the forces that occur.
  • the expansion of the working rollers in the storage according to the invention is possible without any problems on the operator side, because the drive-side chock with its adjustment mechanism for the eccentric bushing can easily fit through the stand window even with bending blocks permanently installed on the roller stand.
  • the rotary drive is preferably integrated in one of the corners of the chock.
  • the storage of the support rollers is characterized according to a feature of the invention in that the sliding frame accommodating the roller bearing is displaceable by means of wedge strips vertically arranged on both sides of each sliding frame and can simultaneously be pivoted about a vertical axis running in the center of the bearing, the rear sides of the roller in the longitudinal direction of the roller Rising wedge-shaped wedge strips abut the inside of the box-shaped chock and pressure pieces are provided between the sliding frame and the wedge strips, which on the one hand have corresponding wedge surfaces on the wedge surfaces of the wedge strips and on the other hand for pivoting the sliding frame with their spherically designed rear sides on spherically formed parts of the sliding frame invest.
  • the invention provides a particularly stable construction for the support roller storage because the support rollers have to absorb particularly high radial forming forces from the work rollers in their storage (approx. 2000 to 3000 t).
  • the sliding frame is particularly suitable for this.
  • the radial rolling forces are conducted through the large contact surface into the chock via the bearings and the sliding frame.
  • the adjustment to the misalignment with setting is done by the spherical pressure pieces in contact with corresponding radii on the sliding frame; the radii have their center in the middle of the bearing.
  • Hydraulic cylinders are preferably arranged in the support rollers for adjusting the sliding frame between each of the two wedge bars and the chock receiving the sliding frame, which act on one of the wedge bars and adjust them opposite to the other wedge bar, the movements being hydraulically synchronized and with the sliding frame in the rolling position can be determined in the chock if hydraulic cylinders are blocked. Since the hydraulic cylinders engage the chock, they can be removed together with it. The entire adjustment mechanism remains limited to the chock. Because of the steep taper of the wedge strips, there is no self-locking.
  • each roll neck of the support rolls is mounted in a preferably 4-row cylindrical or tapered roller bearing in the sliding frame.
  • the bearings can be conventional bearings.
  • the axial bearing of the support roller must also be able to adapt to the restricted position. It is therefore provided that additional tapered roller bearings are fixed on the extended roller journal on one side of the support rollers, the outer bearing rings of which, together with the roller, can be pivoted in a separate housing to support the axial forces acting on the support rollers and are supported on the chock in the axial direction of the roller. As a result, the support rollers can be held in the axial direction without impeding the pivoting.
  • the stand columns of the roll stand (not designated in any more detail) are designated by 1, in the stand windows 2 in which are formed between two stand columns 1 Chocks 3 the work rolls 4 are mounted on their roll journals 5 and 6.
  • the roll neck 6 on the drive side 7 of the roll stand is extended at 8 and can be coupled at 9 to the drive of the work roll 4.
  • each roll neck 5, the work roll 4 is mounted in an eccentric bush 10 in a self-aligning bearing 11.
  • the eccentric bushing on the operating side 12 of the roll stand is larger than the eccentric bushing 10 on the drive side 7 of the roll stand and is provided with an externally toothed collar 13, in the outer toothing of which the drive pinion 14 of a rotary drive 15 engages.
  • the pinion shaft of the drive pinion 14 is connected via the intermediate shaft 16 to an articulated shaft 17, via which the drive torque of the rotary drive 15 can be transferred via the pinion shaft 16 to the drive pinion 18 on the drive side of the roll stand, which meshes with the intermediate wheel 19, the eccentric bushing 10, which is toothed on its outer circumference, drives.
  • the eccentric bushing 10 on the operating side 12 is driven in one direction and the eccentric bushing 10 on the drive side 7 in the other direction of rotation, as a result of which the center points of the roller journals 5 and 6 move in the horizontal direction (in the plane of the drawing) ) in the stand window 2.
  • the roller pivots about its center point 20.
  • the outer rings of the self-aligning bearings 11 are formed on the operating side 12 as cylindrical roller bearings with a spherical outer ring, which enables an inclined position within the eccentric bushing 10.
  • the bearing is designed as a spherical roller bearing with a cylindrical outer ring that absorbs axial forces.
  • the bending cylinders designated with 21 can also be seen, which are provided in bending blocks 22 installed on the stand side 1 and allow an additional bending of the work rolls.
  • the position of the bending blocks 22 can be seen in the side view of the roll stand, as can the bearing of the roll journals in the eccentric bushings 10.
  • the drive side is shown in the upper half and the operating side of the roll stand in the lower half.
  • the eccentricity of the eccentric bush 10 is indicated at 23, starting from the center 24 of the set work roll 4.
  • the intermediate gear 19 can be seen, which meshes with the drive pinion 18, which is connected via the propeller shaft 17 to the drive pinion 14 of the geared motor, not shown here.
  • the support roller 25 is indicated in FIG. 2 in connection with the lower work roller 4.
  • the bearing of the support roller 25 can be seen according to the invention.
  • a mounting piece 28 which receives the roll journals 26 and 27 and which can be displaced in a known manner in the stand window 2 between the stand columns 1 in the vertical direction.
  • the chock of the left half of the roller is omitted for the sake of simplicity.
  • the chock 28 is box-shaped and accommodates a sliding frame 29 inside, in which the roll neck 26 or 27 of the support roll 25 is mounted in the roll bearing 30.
  • the sliding frame 29 is spherical in the area of its corners, as can be seen in the lower illustration of the drawing figure 4, with a center of radius in the middle of the roller bearing 30.
  • the center of the radius is designated by 31.
  • the wedge strip 34 is flat on the side opposite the wedge surface and, as can be seen at 35, lies flat against the inside of the chock 28.
  • the wedge strips 34 on both sides of the sliding frame 29 are coupled to hydraulic cylinders 36, one of which is shown in the drawing figure 4 below.
  • the hydraulic cylinder 36 moves the wedge ledge 34 in the longitudinal direction, the hydraulic cylinders arranged on both sides of the sliding frame 29 being acted upon in opposite directions by hydraulic fluid, so that the wedge ledges are displaced in opposite directions (one in the drawing up and the other down).
  • the roll neck 26 or 27 of the support roller 25 moves in one direction or the other within the chock 28 and causes the support roller 25 to be set to the same extent as the work roller 6, 7 rotated in the eccentrics 10.
  • the angular position of the frame 29 is adjusted via the spherical contact surfaces on the sliding frame 29 and the pressure piece 33, with its wedge surface resting on the wedge bar 34.
  • the radial rolling forces are conducted over a large area from the sliding frame 29 via a wear plate 44 into the chock 28 and from there via employment into the stator columns 1.
  • the axial bearing also has to adapt to the restricted position of the roller, it can be seen in FIG. 3 on the right-hand side of the drawing that the housing 40 of an axial bearing 41 designed as a tapered roller bearing is supported by a linkage 38 and a pressure ring 39, namely on Pressure ring 39 formed spherical pin 42.
  • the pressure ring 39 is adjustably attached to a parallel guide at 43 and can perform a movement in the pivoting direction of the roller pin 27. The associated slight movement in the transverse direction is irrelevant for the function.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Support Of The Bearing (AREA)
  • Straightening Metal Sheet-Like Bodies (AREA)
EP19960250070 1995-03-30 1996-03-28 Cage de laminoir à cylindres d'appui et de travail pour le laminage de tÔles et de bandes Expired - Lifetime EP0734794B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19512929 1995-03-30
DE1995112929 DE19512929C1 (de) 1995-03-30 1995-03-30 Walzgerüst mit Stütz-und Arbeitszwalzen zum Walzen von Blechen und Bändern

Publications (2)

Publication Number Publication Date
EP0734794A1 true EP0734794A1 (fr) 1996-10-02
EP0734794B1 EP0734794B1 (fr) 1999-01-27

Family

ID=7758961

Family Applications (1)

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EP19960250070 Expired - Lifetime EP0734794B1 (fr) 1995-03-30 1996-03-28 Cage de laminoir à cylindres d'appui et de travail pour le laminage de tÔles et de bandes

Country Status (2)

Country Link
EP (1) EP0734794B1 (fr)
DE (1) DE19512929C1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114144289A (zh) * 2019-08-21 2022-03-04 柯尔布斯有限责任两合公司 用于生产书封皮、盒盖或者游戏板的设备
WO2023217309A1 (fr) * 2022-05-12 2023-11-16 Matthews International GmbH Dispositif d'entraînement pour un palier excentré, et calandre correspondante

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1288931B1 (it) * 1996-06-24 1998-09-25 Danieli Off Mecc Dispositivo di compensazione per guarniture in gabbie di laminazione a quarto con movimentazione incrociata dei cilindri

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2965920A (en) * 1958-01-09 1960-12-27 Farrel Birmingham Co Inc Calender or like device
JPS53127353A (en) * 1977-04-13 1978-11-07 Ishikawajima Harima Heavy Ind Co Ltd Method and apparatus for rolling by multistage rolling mill
JPS5449960A (en) * 1977-09-29 1979-04-19 Masao Kubota Rolling mill
JPS574307A (en) * 1980-06-10 1982-01-09 Nippon Steel Corp Cross roll rolling mill
JPS57190704A (en) * 1981-05-20 1982-11-24 Mitsubishi Heavy Ind Ltd Cross rolling mill
JPS60118309A (ja) * 1983-11-30 1985-06-25 Mitsubishi Heavy Ind Ltd クロスロール圧延機におけるバックアップロールチョック装置
EP0525552A1 (fr) * 1991-07-30 1993-02-03 Mitsubishi Jukogyo Kabushiki Kaisha Dispositif de croisement de cylindres pour un laminoir à cylindres obliques
JPH0663619A (ja) * 1992-08-17 1994-03-08 Ishikawajima Harima Heavy Ind Co Ltd 圧延ロールの支持構造

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2965920A (en) * 1958-01-09 1960-12-27 Farrel Birmingham Co Inc Calender or like device
JPS53127353A (en) * 1977-04-13 1978-11-07 Ishikawajima Harima Heavy Ind Co Ltd Method and apparatus for rolling by multistage rolling mill
JPS5449960A (en) * 1977-09-29 1979-04-19 Masao Kubota Rolling mill
JPS574307A (en) * 1980-06-10 1982-01-09 Nippon Steel Corp Cross roll rolling mill
JPS57190704A (en) * 1981-05-20 1982-11-24 Mitsubishi Heavy Ind Ltd Cross rolling mill
JPS60118309A (ja) * 1983-11-30 1985-06-25 Mitsubishi Heavy Ind Ltd クロスロール圧延機におけるバックアップロールチョック装置
EP0525552A1 (fr) * 1991-07-30 1993-02-03 Mitsubishi Jukogyo Kabushiki Kaisha Dispositif de croisement de cylindres pour un laminoir à cylindres obliques
JPH0663619A (ja) * 1992-08-17 1994-03-08 Ishikawajima Harima Heavy Ind Co Ltd 圧延ロールの支持構造

Non-Patent Citations (6)

* Cited by examiner, † Cited by third party
Title
DATABASE WPI Section Ch Week 7922, Derwent World Patents Index; Class M21, AN 79-41355B [22], XP002008473 *
PATENT ABSTRACTS OF JAPAN vol. 003, no. 003 (C - 033) 16 January 1979 (1979-01-16) *
PATENT ABSTRACTS OF JAPAN vol. 006, no. 061 (M - 123) 20 April 1982 (1982-04-20) *
PATENT ABSTRACTS OF JAPAN vol. 007, no. 041 (M - 194) 18 February 1983 (1983-02-18) *
PATENT ABSTRACTS OF JAPAN vol. 009, no. 272 (M - 425) 30 October 1985 (1985-10-30) *
PATENT ABSTRACTS OF JAPAN vol. 018, no. 302 (M - 1618) 9 June 1994 (1994-06-09) *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114144289A (zh) * 2019-08-21 2022-03-04 柯尔布斯有限责任两合公司 用于生产书封皮、盒盖或者游戏板的设备
CN114144289B (zh) * 2019-08-21 2024-05-10 柯尔布斯有限责任两合公司 用于生产书封皮、盒盖或者游戏板的设备
WO2023217309A1 (fr) * 2022-05-12 2023-11-16 Matthews International GmbH Dispositif d'entraînement pour un palier excentré, et calandre correspondante

Also Published As

Publication number Publication date
DE19512929C1 (de) 1996-05-15
EP0734794B1 (fr) 1999-01-27

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