EP0698428B1 - Device for detecting the roll gap between two working rolls of a rolling stand - Google Patents

Device for detecting the roll gap between two working rolls of a rolling stand Download PDF

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Publication number
EP0698428B1
EP0698428B1 EP95109639A EP95109639A EP0698428B1 EP 0698428 B1 EP0698428 B1 EP 0698428B1 EP 95109639 A EP95109639 A EP 95109639A EP 95109639 A EP95109639 A EP 95109639A EP 0698428 B1 EP0698428 B1 EP 0698428B1
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EP
European Patent Office
Prior art keywords
hydraulic cylinders
roll
working
roller
distance
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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
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EP95109639A
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German (de)
French (fr)
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EP0698428A1 (en
Inventor
Ansgar Dipl.-Ing. Grüss
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Siemens AG
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Siemens AG
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B38/00—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product
    • B21B38/10—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product for measuring roll-gap, e.g. pass indicators
    • 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

Definitions

  • the invention relates to a device for detecting the Roll gap between two work rolls of a roll stand with a roll stand and a work roll bending device, where each of a total of four work roll chocks, which support the work rolls at their ends, over two each, on opposite sides of the hydraulic cylinders arranged directly on the respective work roll are adjustable relative to the roller stand.
  • the rolling stock thickness As a controlled variable of interest, cannot be measured in terms of control technology at the point of its creation, namely the roll gap, and therefore cannot be used for the direct correction of faults, such as eccentricities of the rolls can be used.
  • the invention has for its object a largely direct Detection of the roll gap between the work rolls to enable a roll stand, being a roll stand with a work roll bending device, as for example from "Handbook of Manufacturing Technology", Volume 2/1, Carl Hanser Verlag, 1983, page 453, picture 80 is.
  • the object is achieved in that position transmitters are installed in the hydraulic cylinders in the device of the type specified at the outset, and in that the position transmitters are followed by an evaluation device for determining the roll gap from the position values supplied by the position transmitters, the evaluation device being designed so that that it determines a common actual position value as a function of the position values s r and s l , the distance between the two hydraulic cylinders and the distance between the axis of the associated work roll and a line connecting the points of application of the hydraulic cylinders to the work roll chock .
  • Position sensors which are suitable for this measurement are disclosed in DE-A-1 602 195 or JP-A-61 199 506.
  • the roll stand shown in FIG. 1 consists of a roll stand 2, in which an upper and lower support roller 3 and 4 and two work rolls 5 and 6 are arranged.
  • the two Back-up rolls 3 and 4 are at their two ends via Morgoil bearings stored in backup roller chocks 7 and 8; the Both work rolls 5 and 6 are in corresponding work roll chocks 9 and 10 stored.
  • 1 shows that Roll stand 1 from its drive side, that is from the side, on which the rollers are driven so that only those on chocks 7 to 10 on this side can be seen.
  • the Back-up roll chocks 7 and 8 are in a window 11 of the roll stand 2 out.
  • a hydraulic adjusting device 13 is arranged between the upper crosshead 12 of the roller stand 2 and the chock 7 of the upper Back-up roller 3.
  • the chock 8 of the lower support roller 4 is via a wedge adjustment device 14 against the lower crosshead 15 of the roll stand 2 is supported.
  • each hydraulic cylinder 18 and 19 is a position transmitter 24 or 25 installed.
  • the axis 26 of the work roll 5 lies in the middle between the two hydraulic cylinders 18 and 19, the distance from each other designated x is.
  • the points of attack of the hydraulic cylinders 18 and 19 on the work roll chock 9 are designated 27 and 28.
  • FIG. 3 illustrates the geometric relationships on the work roll chock 9.
  • the distance r between the axis 26 of the work roll 5 and the connecting line 29 between the two points of attack 27 and 28 of the hydraulic cylinders 18 and 19 on the chock 9 is designated by r.
  • the position transmitter supplies a position value s l and the position transmitter 25 supplies a position value s r .
  • the block diagram in FIG. 4 shows a total of eight position transmitters 24, 25, 30, 31, 32, 33, 34 and 35, which are connected to an evaluation device 36.
  • the common position values s 01 to s 04 are calculated from the position values of two position transmitters and added to the values h A and h B for the roll gap.
  • the values h A and h B only have to take into account the comparatively small influences from the work roll back bend, the work roll eccentricity, the thermal work roll expansion and the elastic deformation of the work roll chocks.
  • the previously required additional calculations of the suspension of the back-up rolls and the eccentricity of the back-up rolls can be omitted.
  • the direct detection of the roll gap according to the invention enables a significantly more precise roll gap control to be implemented.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)

Description

Die Erfindung betrifft eine Einrichtung zur Erfassung des Walzspaltes zwischen zwei Arbeitswalzen eines Walzgerüsts mit einem Walzenständer und einer Arbeitswalzen-Biegevorrichtung, bei der jedes von insgesamt vier Arbeitswalzen-Einbaustücken, welche die Arbeitswalzen an ihren Enden lagern, über jeweils zwei, auf gegenüberliegenden Seiten der jeweiligen Arbeitswalze angeordnete Hydraulikzylinder unmittelbar gegenüber dem Walzenständer verstellbar sind.The invention relates to a device for detecting the Roll gap between two work rolls of a roll stand with a roll stand and a work roll bending device, where each of a total of four work roll chocks, which support the work rolls at their ends, over two each, on opposite sides of the hydraulic cylinders arranged directly on the respective work roll are adjustable relative to the roller stand.

Bei der Regelung der Walzgutdicke in einem Walzgerüst besteht die Schwierigkeit, daß die Walzgutdicke als interessierende Regelgröße nicht ohne weiteres regeltechnisch auswertbar am Ort ihrer Entstehung, nämlich dem Walzspalt, gemessen werden kann und daher nicht zur unmittelbaren Ausregelung von Störungen, wie z.B. Exzentrizitäten der Walzen, herangezogen werden kann. Nach dem sogenannten Gaugemeter-Prinzip kann jedoch die momentane Walzgutdicke ha im Bereich des Walzspaltes rechnerisch aus der Anstellposition s der Walzen, der Walzkraft FW und der Federkonstanten cG des Walzgerüstes zu ha+ΔR=s+FW/cG bestimmt werden, wobei ΔR die Störungen, also z.B. die Walzenexzentrizitäten, bezeichnet.When regulating the rolling stock thickness in a rolling stand, there is the difficulty that the rolling stock thickness, as a controlled variable of interest, cannot be measured in terms of control technology at the point of its creation, namely the roll gap, and therefore cannot be used for the direct correction of faults, such as eccentricities of the rolls can be used. According to the so-called gauge principle, however, the instantaneous rolling stock thickness h a in the area of the roll gap can be calculated from the setting position s of the rolls, the rolling force F W and the spring constant c G of the roll stand H a + ΔR = s + F W / c G are determined, where ΔR denotes the disturbances, for example the roll eccentricities.

Aus BBC-Nachrichten, 1976, Heft 1, Seiten 38 - 44, ist es bekannt, den Abstand zwischen den Einbaustücken der Stützwalzen zu erfassen und als Hilfsregelgröße bei der Dickenregelung zu verwenden. Aus dem gemessenen Abstand zwischen den Stützwalzen-Einbaustücken kann jedoch der Walzspalt zwischen den Arbeitswalzen nicht unmittelbar bestimmt werden, weil zusätzlich die Einflüsse der Lageraufschwemmung der Stützwalzenzapfen in den Morgoil-Lagern und die Exzentrizitäten der Stützwalzen berücksichtigt werden müssen. From BBC News, 1976, Issue 1, pages 38-44, it is known, the distance between the chocks of the backup rollers to record and as an auxiliary control variable in the thickness control to use. From the measured distance between the backing roll chocks, however, the roll gap between the work rolls are not determined directly, because in addition the influences of the flooding of the camp Back-up roll neck in the Morgoil bearings and the eccentricities of the backup rolls must be taken into account.

Der Erfindung liegt die Aufgabe zugrunde, eine weitgehend direkte Erfassung des Walzspaltes zwischen den Arbeitswalzen eines Walzgerüstes zu ermöglichen, wobei von einen Walzgerüst mit einer Arbeitswalzen-Biegevorrichtung ausgegangen wird, wie sie beispielsweise aus "Handbuch der Fertigungstechnik", Band 2/1, Carl Hanser Verlag, 1983, Seite 453, Bild 80, bekannt ist.The invention has for its object a largely direct Detection of the roll gap between the work rolls to enable a roll stand, being a roll stand with a work roll bending device, as for example from "Handbook of Manufacturing Technology", Volume 2/1, Carl Hanser Verlag, 1983, page 453, picture 80 is.

Gemäß der Erfindung wird die Aufgabe dadurch gelöst, daß bei der Einrichtung der eingangs angegebenen Art in den Hydraulikzylindern Postionsgeber eingebaut sind und daß den Positionsgebern eine Auswerteeinrichtung zur Bestimmung des Walzspaltes aus den von den Positionsgebern gelieferten Positionswerten nachgeordnet ist, wobei die Auswerteeinrichtung so ausgelegt ist, daß sie einen gemeinsamen Positions-Istwert in Abhängigkeit von den Positionswerten sr und sl, dem Abstand zwischen den beiden Hydraulikzylindern und dem Abstand zwischen der Achse der zugehörigen Arbeitswalze und einer Linie, die die Angriffspunkte der Hydraulikzylinder an dem Arbeitswalzen-Einbaustück verbindet, bestimmt. Positionsgeber, die für diese Messung in Frage kommen sind in der DE-A-1 602 195 oder der JP-A-61 199 506 offenbart.According to the invention, the object is achieved in that position transmitters are installed in the hydraulic cylinders in the device of the type specified at the outset, and in that the position transmitters are followed by an evaluation device for determining the roll gap from the position values supplied by the position transmitters, the evaluation device being designed so that that it determines a common actual position value as a function of the position values s r and s l , the distance between the two hydraulic cylinders and the distance between the axis of the associated work roll and a line connecting the points of application of the hydraulic cylinders to the work roll chock . Position sensors which are suitable for this measurement are disclosed in DE-A-1 602 195 or JP-A-61 199 506.

Dabei bestimmt die Auswerteeinrichtung vorzugsweise aus den Positionswerten sr und sl der Positionsgeber in den jeweils beiden zur Verstellung eines Arbeitswalzen-Einbaustücks dienenden Hydraulikzylindern einen gemeinsamen Positions-Istwert so=½(sr+sl)-[(sr-sl)·r/x]·tan[½ arctan ((sr-sl/x)], wobei x den Abstand zwischen den beiden Hydraulikzylindern und r den Abstand zwischen der Achse der zugehörigen Arbeitswalze und einer Linie bezeichnet, die die Angriffspunkte der Hydraulikzylinder an dem Arbeitswalzen-Einbaustück verbindet. In this case, the evaluation device preferably determines a common actual position value from the position values s r and s l of the position transmitters in the two hydraulic cylinders used to adjust a work roll chock s O = ½ (s r + s l ) - [(s r -s l ) R / x] tan [½ arctan ((s r -s l / x)] , where x is the distance between the two hydraulic cylinders and r is the distance between the axis of the associated work roll and a line connecting the points of engagement of the hydraulic cylinders on the work roll chock.

Zur weiteren Erläuterung der Erfindung wird im folgenden auf die Figuren der Zeichnung Bezug genommen; im einzelnen zeigen

FIG 1
ein Walzgerüst mit einer Arbeitswalzen-Biegevorrichtung,
FIG 2
einen Ausschnitt aus der Arbeitswalzen-Biegevorrichtung mit zwei, an einem Arbeitswalzen-Einbaustück angreifenden Hydraulikzylindern,
FIG 3
eine schematische Darstellung der geometrischen Verhältnisse im Bereich der in FIG 2 gezeigten Arbeitswalzen-Biegevorrichtung und
FIG 4
ein schematisches Blockschaltbild mit Positionsgebern und einer Auswerteeinrichtung zur Walzspaltbestimmung.
To further explain the invention, reference is made below to the figures of the drawing; show in detail
FIG. 1
a roll stand with a work roll bending device,
FIG 2
a section of the work roll bending device with two hydraulic cylinders acting on a work roll chock,
FIG 3
a schematic representation of the geometric relationships in the area of the work roll bending device shown in FIG
FIG 4
a schematic block diagram with position sensors and an evaluation device for determining the roll gap.

Das in FIG 1 gezeigte Walzgerüst besteht aus einem Walzenständer 2, in dem eine obere und untere Stützwalze 3 bzw. 4 sowie zwei Arbeitswalzen 5 und 6 angeordnet sind. Die beiden Stützwalzen 3 und 4 sind an ihren beiden Enden über Morgoil-Lager in Stützwalzen-Einbaustücken 7 und 8 gelagert; die beiden Arbeitswalzen 5 und 6 sind in entsprechenden Arbeitswalzen-Einbaustücken 9 und 10 gelagert. FIG 1 zeigt das Walzgerüst 1 von seiner Antriebsseite, also von der Seite, auf der der Antrieb der Walzen erfolgt, so daß nur die auf dieser Seite liegenden Einbaustücke 7 bis 10 zu sehen sind. Auf der rückwärtigen Bedienseite des Walzgerüsts, auf der die einzelnen Walzen ausgewechselt werden können, sind entsprechende Einbaustücke in gleicher Anordnung vorhanden. Die Stützwalzen-Einbaustücke 7 und 8 sind in einem Fenster 11 des Walzenständers 2 geführt. Zwischen dem oberen Querhaupt 12 des Walzenständers 2 und dem Einbaustück 7 der oberen Stützwalze 3 ist eine hydraulische Anstellvorrichtung 13 angeordnet. Das Einbaustück 8 der unteren Stützwalze 4 ist über eine Keilverstelleinrichtung 14 gegen das untere Querhaupt 15 des Walzenständers 2 abgestützt.The roll stand shown in FIG. 1 consists of a roll stand 2, in which an upper and lower support roller 3 and 4 and two work rolls 5 and 6 are arranged. The two Back-up rolls 3 and 4 are at their two ends via Morgoil bearings stored in backup roller chocks 7 and 8; the Both work rolls 5 and 6 are in corresponding work roll chocks 9 and 10 stored. 1 shows that Roll stand 1 from its drive side, that is from the side, on which the rollers are driven so that only those on chocks 7 to 10 on this side can be seen. On the rear operating side of the roll stand, on the the individual rollers can be replaced are corresponding Chocks available in the same arrangement. The Back-up roll chocks 7 and 8 are in a window 11 of the roll stand 2 out. Between the upper crosshead 12 of the roller stand 2 and the chock 7 of the upper Back-up roller 3, a hydraulic adjusting device 13 is arranged. The chock 8 of the lower support roller 4 is via a wedge adjustment device 14 against the lower crosshead 15 of the roll stand 2 is supported.

In dem Fenster 11 des Walzenständers 2 befinden sich fest installierte Zylinderblöcke (Mae-West-Blöcke) 16 und 17, in denen Hydraulikzylinder 18 bis 21 zur positiven Arbeitswalzenbiegung eingebaut sind. Dabei greifen jeweils zwei Hydraulikzylinder, z.B. 18 und 19, auf gegenüberliegenden Seiten der Arbeitswalzen, hier der Arbeitswalze 5, an dem zugehörigen Arbeitswalzen-Einbaustück 9 an, wie dies in FIG 2 näher dargestellt ist. Zur Erzielung einer negativen Arbeitswalzenbiegung sind in den Stützwalzen-Einbaustücken 7 und 8 weitere Hydraulikzylinder 22 eingebaut, die ebenfalls gegen die Arbeitswalzen-Einbaustücke 9 und 10 wirken. In the window 11 of the roller stand 2 are fixed installed cylinder blocks (Mae West blocks) 16 and 17, in which hydraulic cylinders 18 to 21 for positive work roll bending are installed. Two hydraulic cylinders each grip e.g. 18 and 19, on opposite sides the work rolls, here the work roll 5, on the associated one Work roll chock 9 as shown in FIG. 2 is shown in more detail. To achieve a negative work roll bend are in the support roller chocks 7 and 8 other hydraulic cylinders 22 installed, which also act against the work roll chocks 9 and 10.

Zur Messung des Walzspaltes 23 zwischen den beiden Arbeitswalzen 5 und 6 sind in den Hydraulikzylindern 18 bis 21 in den Zylinderblöcken 16 und 17 hier nicht gezeigte Positionsgeber eingebaut. Durch den Einbau der Positionsgeber in den Hydraulikzylindern 18 bis 21 wird eine Beschädigung oder Verschmutzung der Positionsgeber während des Walzbetriebs verhindert.To measure the roll gap 23 between the two work rolls 5 and 6 are in the hydraulic cylinders 18 to 21 in the cylinder blocks 16 and 17 position sensors, not shown here built-in. By installing the position transmitter in the hydraulic cylinders 18 to 21 will damage or Contamination of the position sensors during rolling operation prevented.

FIG 2 zeigt das Arbeitswalzen-Einbaustück 9 mit der darin gelagerten Arbeitswalze 5 und den beiden Hydraulikzylindern 18 und 19 in den Zylinderblöcken 16 und 17. In jedem der beiden Hydraulikzylinder 18 und 19 ist jeweils ein Positionsgeber 24 bzw. 25 eingebaut. Die Achse 26 der Arbeitswalze 5 liegt in der Mitte zwischen den beiden Hydraulikzylindern 18 und 19, deren Abstand zueinander mit x bezeichnet ist. Die Angriffspunkte der Hydraulikzylinder 18 und 19 an dem Arbeitswalzen-Einbaustück 9 sind mit 27 und 28 bezeichnet.2 shows the work roll chock 9 with the one in it mounted work roll 5 and the two hydraulic cylinders 18 and 19 in cylinder blocks 16 and 17. In each of the each hydraulic cylinder 18 and 19 is a position transmitter 24 or 25 installed. The axis 26 of the work roll 5 lies in the middle between the two hydraulic cylinders 18 and 19, the distance from each other designated x is. The points of attack of the hydraulic cylinders 18 and 19 on the work roll chock 9 are designated 27 and 28.

FIG 3 verdeutlicht die geometrischen Verhältnisse an dem Arbeitswalzen-Einbaustück 9. Dabei ist mit r der Abstand zwischen der Achse 26 der Arbeitswalze 5 und der Verbindungslinie 29 zwischen den beiden Angriffspunkten 27 und 28 der Hydraulikzylinder 18 und 19 an dem Einbaustück 9 bezeichnet. Bei Schräglage des Einbaustücks 9 liefert der Positionsgeber einen Positionswert sl und der Positionsgeber 25 einen Positionswert sr. Aus den beiden Positionswerten sr und sl wird ein gemeinsamer Positionswert s0 berechnet, der bei waagrechter Lage des Einbaustücks 9 von beiden Positionsgebern 18 und 19 geliefert wird; dabei gilt so=½(sr+sl)-[(sr-sl)·r/x]·tan[½ arctan ((sr-sl)/x)]. 3 illustrates the geometric relationships on the work roll chock 9. The distance r between the axis 26 of the work roll 5 and the connecting line 29 between the two points of attack 27 and 28 of the hydraulic cylinders 18 and 19 on the chock 9 is designated by r. When the chock 9 is in an inclined position, the position transmitter supplies a position value s l and the position transmitter 25 supplies a position value s r . A common position value s 0 is calculated from the two position values s r and s l and is supplied by both position transmitters 18 and 19 when the chock 9 is in a horizontal position; applies s O = ½ (s r + s l ) - [(s r -s l ) R / x] tan [½ arctan ((s r -s l ) / x)].

Insgesamt werden vier solcher gemeinsamen Positionswerte s01, s02, s03 und s04 ermittelt, wobei für die obere Arbeitswalze 5 auf der Antriebsseite der Wert s01 und auf der Bedienseite der Wert s02 und für die untere Arbeitswalze 6 auf der Antriebsseite der Wert s03 und auf der Bedienseite der Wert s04 bestimmt wird. Unter der Annahme, daß bei geschlossenem Leerwalzspalt gilt s01=s02=s03=s04=0 ergibt sich der Walzspalt auf der Antriebsseite zu hA=s01+s03 und auf der Bedienseite hB=s02+s04 .A total of four such common position values s 01 , s 02 , s 03 and s 04 are determined, the value s 01 for the upper work roll 5 on the drive side and the value s 02 on the operator side and for the lower work roll 6 on the drive side Value s 03 and the value s 04 is determined on the operating side. Assuming that applies when the blank gap is closed s 01 = s 02 = s 03 = s 04 = 0 the roll gap on the drive side results H A = s 01 + s 03 and on the operator side H B = s 02 + s 04 .

Das Blockschaltbild in FIG 4 zeigt die insgesamt acht Positionsgeber 24, 25, 30, 31, 32, 33, 34 und 35, die an einer Auswerteeinrichtung 36 angeschlossen sind. Innerhalb der Auswerteeinrichtung 36 werden aus den Positionswerten jeweils zweier Positionsgeber die gemeinsamen Positionswerte s01 bis s04 berechnet und zu den Werten hA und hB für den Walzspalt addiert. Um die tatsächliche Größe des Walzspaltes 23 zu erhalten, müssen in die Werte hA und hB nur noch die vergleichsweise geringen Einflüsse aus der Arbeitswalzenrückbiegung, der Arbeitswalzenexzentrizität, der thermischen Arbeitswalzendehnung und der elastischen Verformung der Arbeitswalzen-Einbaustücke eingerechnet werden. Demgegenüber können jedoch die bisher erforderlichen Zusatzberechnungen der Lageraufschwemmung der Stützwalzen und der Exzentrizität der Stützwalzen entfallen. Durch die erfindungsgemäße direkte Erfassung des Walzspaltes kann eine wesentlich exaktere Walzspaltregelung verwirklicht werden.The block diagram in FIG. 4 shows a total of eight position transmitters 24, 25, 30, 31, 32, 33, 34 and 35, which are connected to an evaluation device 36. Within the evaluation device 36, the common position values s 01 to s 04 are calculated from the position values of two position transmitters and added to the values h A and h B for the roll gap. In order to obtain the actual size of the roll gap 23, the values h A and h B only have to take into account the comparatively small influences from the work roll back bend, the work roll eccentricity, the thermal work roll expansion and the elastic deformation of the work roll chocks. In contrast, however, the previously required additional calculations of the suspension of the back-up rolls and the eccentricity of the back-up rolls can be omitted. The direct detection of the roll gap according to the invention enables a significantly more precise roll gap control to be implemented.

Claims (2)

  1. Device for detecting the roll gap (23) between two working rollers (5, 6) of a roll stand (1) with a roll housing (2) and a working-roller bending arrangement, where each of a total of four working-roller chocks (9, 10), which support the working rollers (5, 6) at their ends, is adjustable directly opposite the roll housing (2) by way of two respective hydraulic cylinders (18, 19, 20, 21) which are arranged on opposite sides of the respective working rollers (5, 6), characterized in that locators (24, 25, 30 to 35) are installed in the hydraulic cylinders (18, 19, 20, 21) and in that downstream of the locators (24, 25, 30 to 35) there is an evaluation device (36) for determining the roll gap from the position values (sl, sr) supplied by the locators (24, 25, 30 to 35), wherein the evaluation device (36) is designed in such a way that it determines a common actual position value in dependence upon the position values sr and sl, the distance between the two hydraulic cylinders (18, 19) and the distance between the axis (26) of the associated working roller (5) and a line (29) which connects the contact points (27, 28) of the hydraulic cylinders (18, 19) at the working-roller chock (9).
  2. Device according to claim 1, characterized in that the evaluation device (36) determines from the position values sr and sl of the locators (24, 25) in the respective two hydraulic cylinders (18, 19), used for adjusting a working-roller chock, for example (9), a common actual position value so=½(sr+sl)-[(sr-sl)·r/x]·tan[½ arctan ((sr-sl)/x)], with x denoting the distance between the two hydraulic cylinders (18, 19) and r the distance between the axis (26) of the associated working roller (5) and a line (29) which connects the contact points (27, 28) of the hydraulic cylinders (18, 19) at the working-roller chock (9).
EP95109639A 1994-07-08 1995-06-21 Device for detecting the roll gap between two working rolls of a rolling stand Expired - Lifetime EP0698428B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4424153 1994-07-08
DE4424153 1994-07-08

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EP0698428A1 EP0698428A1 (en) 1996-02-28
EP0698428B1 true EP0698428B1 (en) 1999-03-31

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Cited By (1)

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WO2022243425A1 (en) 2021-05-21 2022-11-24 Sms Group Gmbh Method for operating a roll stand

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Publication number Priority date Publication date Assignee Title
DE50214899D1 (en) 2001-12-12 2011-03-17 Sms Siemag Ag DEVICE FOR MEASURING THE ROLL OF THE ROLL BETWEEN WORKING ROLLERS OF A COLD OR WARM ROLLING SCAFFOLD
DE102005042837A1 (en) * 2005-08-26 2007-03-08 Sms Demag Ag Method for thickness control during hot rolling
DE102009060642A1 (en) * 2009-07-07 2011-01-13 Sms Siemag Ag 4-roll - / - rolls / 18HS roll rolling mill in cassette construction
DE102011078139A1 (en) 2011-06-07 2012-12-13 Sms Siemag Ag Measuring device, rolling stand and method for detecting the height of a roll gap
CN104741385B (en) * 2015-04-14 2017-02-01 中冶赛迪工程技术股份有限公司 Working roller bending device for double-roller rolling machine and roller bending force control method
DE102022125630A1 (en) 2022-10-05 2024-04-11 Karlsruher Institut für Technologie, Körperschaft des öffentlichen Rechts Arrangement with two rollers spaced apart to form a gap with a gap width measuring system

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GB1190738A (en) * 1966-08-16 1970-05-06 United Eng Foundry Co Means for indicating the Roll Pass Opening in a Rolling Mill or Calender
US3733875A (en) * 1971-07-12 1973-05-22 Mesta Machine Co Work roll sensing and/or balancing arrangements
JPS57209710A (en) * 1981-06-16 1982-12-23 Sumitomo Metal Ind Ltd Plate thickness controlling method
JPS61199506A (en) * 1985-02-28 1986-09-04 Ishikawajima Harima Heavy Ind Co Ltd Rolling mill

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022243425A1 (en) 2021-05-21 2022-11-24 Sms Group Gmbh Method for operating a roll stand
DE102021205275A1 (en) 2021-05-21 2022-11-24 Sms Group Gmbh Method for operating a roll stand

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EP0698428A1 (en) 1996-02-28

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