EP3566789A1 - Hydraulikanordnung und verfahren zur regelung eines walzspalts eines walzgerüsts - Google Patents

Hydraulikanordnung und verfahren zur regelung eines walzspalts eines walzgerüsts Download PDF

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Publication number
EP3566789A1
EP3566789A1 EP18171953.5A EP18171953A EP3566789A1 EP 3566789 A1 EP3566789 A1 EP 3566789A1 EP 18171953 A EP18171953 A EP 18171953A EP 3566789 A1 EP3566789 A1 EP 3566789A1
Authority
EP
European Patent Office
Prior art keywords
valve
arrangement
valve arrangement
hydraulic
roll
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.)
Withdrawn
Application number
EP18171953.5A
Other languages
German (de)
English (en)
French (fr)
Inventor
Andre Feldmann
Harald Eichner
Alexander EICK
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.)
Muhr und Bender KG
Original Assignee
Muhr und Bender KG
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
Application filed by Muhr und Bender KG filed Critical Muhr und Bender KG
Priority to EP18171953.5A priority Critical patent/EP3566789A1/de
Priority to PL19721316.8T priority patent/PL3790674T3/pl
Priority to PCT/EP2019/061747 priority patent/WO2019215197A1/de
Priority to EP19721316.8A priority patent/EP3790674B1/de
Priority to CN201980031601.XA priority patent/CN112203782B/zh
Priority to ES19721316T priority patent/ES2913976T3/es
Priority to US17/053,388 priority patent/US11491523B2/en
Publication of EP3566789A1 publication Critical patent/EP3566789A1/de
Withdrawn legal-status Critical Current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
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/58—Roll-force control; Roll-gap control
    • B21B37/62—Roll-force control; Roll-gap control by control of a hydraulic adjusting device
    • 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
    • B21B31/32—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis by liquid pressure, e.g. hydromechanical adjusting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/16—Control of thickness, width, diameter or other transverse dimensions
    • B21B37/24—Automatic variation of thickness according to a predetermined programme
    • B21B37/26—Automatic variation of thickness according to a predetermined programme for obtaining one strip having successive lengths of different constant thickness
    • 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
    • B21B38/02—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product for measuring flatness or profile of strips
    • 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
    • B21B38/04—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product for measuring thickness, width, diameter or other transverse dimensions of the product

Definitions

  • the invention relates to a hydraulic arrangement and a method for controlling a roll gap of a roll stand, in particular for the flexible rolling of strip material.
  • strip material having an inlet thickness in a hot or cold state is rolled in one or more steps to a desired thickness.
  • the strip material is guided through a defined roll gap, which is formed by two work rolls.
  • the roll gap can be adjusted via a hydraulic adjustment unit in the rule, to control disturbances of the rolling process, such as changes in the initial thickness.
  • strip material is produced with a constant nominal thickness, so that after an initial setting of the nominal roll gap, only small deviations resulting from the influence of disturbance variables have to be readjusted.
  • strip material with a variable nominal thickness profile in the strip longitudinal direction is produced. In addition to compensating the deviations caused by disturbances, the roll gap must be tracked to the nominal thickness profile.
  • the necessary roll gap changes are usually many times greater than the conditional by the balancing of disturbances roll gap changes.
  • a device for controlling the roll gap In order to achieve high rolling speeds and thus high productivity in flexible rolling, a device for controlling the roll gap must allow relatively large stroke paths of the rolls in a short time while high precision setting of the roll gap.
  • From the DE 38 03 490 C2 is a device for the hydraulic control of a pressure roller by means of adjusting cylinders known.
  • the device For controlling pressure medium paths between the two chambers of an actuating cylinder, a pressure medium source and a Tank, the device each includes a switchable valve.
  • a disadvantage of this structure of the hydraulic control is that the one valve can either be designed so that this as fast as possible or as exactly as possible moves the actuating cylinder.
  • the invention has for its object to provide a hydraulic arrangement and a method for controlling a roll gap of a roll stand, which allows a variable, highly dynamic adjustment of the roll gap with high position accuracy and rolling at high rolling speeds.
  • a hydraulic arrangement for controlling a roll gap of a roll stand comprising: at least one hydraulic setting unit for setting the roll gap; a first double-acting valve arrangement for variably controlling the adjusting unit; and a second double-acting valve assembly for variable control of the Anstellech, which is connected in parallel to the first valve assembly and having a larger nominal volume flow than the first valve assembly.
  • the hydraulic arrangement according to the invention has the advantage that, for at least a part number of roll gap changes during rolling, a defined stroke between a start or actual roll position and a target roll position can be subdivided into a plurality of sections, wherein in a first section a large part of the Stroke can be realized by means of the second valve assembly with a large nominal volume flow and high speeds and in a second section, a highly accurate positioning of the rollers can be done by the first valve assembly with a smaller nominal volume flow and lower speeds.
  • the arrangement is particularly suitable for the flexible rolling of strip material, in which strip material with a variable thickness over the length is generated, since this allows a highly dynamic and fast control of the roll gap with high accuracy.
  • Nominal volumetric flow should be understood as meaning the maximum volumetric flow of the incoming or outgoing hydraulic fluid when fully opened by the respective valve arrangement, which results at a defined pressure difference.
  • the second valve arrangement may have a nominal volume flow which is at least 8 times, in particular at least 10 times, in particular at least 15 times, the nominal volume flow of the first valve arrangement. If one of the first and / or second valve arrangement comprises a plurality of individual valves, the specified nominal volume flow of the respective arrangement should relate to the sum of the respective nominal volume flows of the individual valves of this first or second valve arrangement.
  • a hydraulic adjusting unit is intended to include any unit which can convert a hydraulic energy which can be transmitted by the first and / or second valve arrangement into mechanical energy.
  • At least one hydraulic adjusting unit for roll gap control is provided in a rolling stand, which includes the possibility of two or more adjusting units.
  • an associated adjusting unit can be provided on each side of a work roll of a rolling stand. The two adjusters can be controlled synchronously in this case to move the work roll.
  • the at least one hydraulic adjusting unit may comprise a cylinder and an adjusting piston, wherein the adjusting piston movably divides the cylinder into a first chamber and a second chamber.
  • the Anstellech is in this case a double-acting cylinder and can also be referred to as a piston-cylinder unit.
  • the setting piston can move a chock, which is arranged so as to be vertically displaceable in a roll stand, in which a first work roll is rotatably mounted, or act upon it with a rolling force.
  • the first work roll can form a roll gap together with a second work roll, which is mounted rotatably and non-displaceably in the roll stand.
  • the roll gap can thus be adjusted variably by the adjusting unit and apply a defined rolling force to a strip material.
  • the respectively required volume flow into a chamber of the adjusting unit in and From the opposite chamber results from the stroke of the Anstellkolbens and each acting in the first chamber and the second chamber cross-sectional area.
  • the cross-sectional areas of the first chamber and the second chamber may differ.
  • one of the chambers may have an annular cross section with an outer diameter by a piston rod while the other chamber has a circular cross section with the same outer diameter.
  • the hydraulic adjusting unit can be acted upon by one or more pressure medium sources having a working pressure greater than 200 bar, in particular greater than 250 bar, in particular greater than 300 bar.
  • the high pressures ensure that high piston speeds can be achieved at the setting units and can be realized with fast switching times of less than 200 ms.
  • the high pressures allow sufficient rolling force to act on the work rolls. Overall, thus a highly dynamic roll gap control is achieved.
  • one of the one or more pressure medium sources may comprise a pump or a pressure medium reservoir with a connected pump.
  • the first and the second valve arrangement can be fed from a common pressure medium source or a part number of the pressure connections of the first and the second valve arrangement can be connected to a separate pressure medium source.
  • Double-acting valve arrangements are to be understood as meaning all valve arrangements by means of which the volume flows can be made so variable that a double-acting cylinder can be both extended and retracted.
  • the use of two valve arrangements with different volume flows makes it possible for the double-acting cylinder to be moved both quickly and slowly.
  • the adjusting unit of the hydraulic arrangement according to the invention can be extended and retracted independently of one another and / or in combination of both valve arrangements both by the first valve arrangement and by the second valve arrangement.
  • the first valve arrangement may control a volume flow of a first pressure medium path which is connected to the first chamber and a volume flow of a second pressure medium path which is connected to the second chamber.
  • the second valve arrangement can control a volume flow of a third pressure medium path, which is connected to the first chamber, and a volume flow of a fourth pressure medium path, which is connected to the second chamber.
  • a volume flow out of one of the chambers of the Anstellzylinders out and into one of the chambers of the Anstellzylinders be controlled.
  • the volume flows controlled in each case via the first and second valve arrangement can be made fully variable at a defined working pressure from an open position to a closed position.
  • a valve of the first valve arrangement and a valve of the second valve arrangement can each be configured as a continuous valve, in particular as a servo valve. In this case, pilot operated valves can be used.
  • the second valve arrangement may comprise at least one valve for controlling the hydraulic adjusting unit.
  • a valve has an actuator, for example a valve piston, by means of which the volume flow through the valve can be controlled.
  • the valve assembly can be driven with low control complexity.
  • a plurality of valves a plurality of kinematically decoupled valve actuators can be actuated and thus a highly variable actuation of the actuation unit can be realized.
  • the first valve arrangement may comprise at least one valve for controlling the hydraulic adjusting unit.
  • the first and the second valve arrangement can in each case comprise any number of valves connected in series and / or in parallel, which together allow a double-acting actuation of the adjusting unit, wherein the resulting nominal volume flow of the second valve arrangement is, in particular, many times greater than the resulting nominal volume flow first valve arrangement. If the first and / or the second valve arrangement has a plurality of individual valves, these can individual valves are designed to be single-acting or double-acting, that is, acting hydraulically on the Anstellech only in one operating direction or in both directions of actuation.
  • a first valve of the respective valve arrangement act on the adjusting unit such that it is retracted, while a second valve of the valve arrangement acts on the adjusting unit, that it is extended, in particular according to the so-called principle of the divided control edges.
  • the first and second valve thus form a double-acting valve arrangement.
  • one or both of the valve arrangements can also comprise one or more valves, which are each designed to be double-acting, that is, in which the respective valve can act on the adjustment unit in both directions. It is understood that the said options apply in each case to the first and / or the second valve arrangement.
  • the nominal volume flow of valve arrangements with a plurality of valves is intended to be the maximum flow which flows in or out through the valves of a valve arrangement at a certain pressure difference.
  • the valve arrangements may in particular be composed of 2/2, 3/2, 3/3, 4/2, 4/3, or 5/3 way valves.
  • a valve arrangement can be formed from a parallel connection of two 3/3-way valves or two 4/3-way valves.
  • the first valve assembly and the second valve assembly are hydraulically connected to a main tank.
  • the supply line (pressure line) between the main tank and the first and second valve arrangement may optionally be provided one or more pressure accumulator.
  • the at least one pressure accumulator is used in particular to ensure a steady supply of pressure oil to the first and / or second valve arrangement and to compensate for consumption peaks.
  • an intermediate tank may be arranged in a return line between the first valve arrangement and a main tank and / or between the second valve arrangement and the main tank. From the intermediate tank, the hydraulic fluid is then delivered to the main tank. Through the intermediate tank, the hydraulic fluid column can be relaxed early and pulsations in the return line between the valve and the main tank can be reduced, so that a faster discharge of the fluid flowing out of the adjusting unit hydraulic fluid can be realized. To damp the pulsations of the hydraulic fluid and pulsation damper in the return line between the valve assemblies and the main tank, especially in front of the intermediate tank, conceivable.
  • the intermediate tank may be arranged above the main tank.
  • the sub-tank can also be referred to as high tank.
  • the intermediate tank can be arranged at a vertical height with the first and the second valve arrangement and / or at a distance of less than three meters, in particular less than two meters, from the valve arrangements.
  • the object is further achieved by a method for controlling a roll gap of a roll stand, in particular by means of one of the hydraulic arrangements described above, comprising the steps of: determining an actual roll position of a work roll; Determining a desired roll position of the work roll; and controlling an opening degree of a first valve arrangement and an opening degree of a second valve arrangement for actuating the setting unit depending on the actual roll position and the target roll position, wherein the roll gap is changed during rolling, and wherein at least for a change in thickness of a rolling profile to be rolled during the Rolling the adjusting unit is controlled in a first portion of a stroke between the actual roller position and the target roller position by means of the first valve assembly and the second valve assembly and in a second portion of the stroke only from the first valve assembly.
  • Said first or second portion of the stroke can be in this context any Hubwegabroughe between the actual and the desired position.
  • Hubwegabitese there are further Hubwegabitese conceivable, which can be before, between and / or nachlagert.
  • various control options with the first and second valve arrangement are conceivable, for example opening at least one valve of the first valve assembly, then opening at least one valve of the second valve assembly, re-closing the valve of the second valve assembly and then re-closing the valve of the first valve assembly.
  • the opening of the at least one valve of the first and the at least one valve of the second valve arrangement can also take place at the same time or in the reverse order.
  • the control described relates to at least one change in thickness during the rolling process for producing a particularly flexibly rolled strip material. That is, during the rolling of the strip material is at least a partial number of roll gap changes or strokes a hydraulic control of the adjusting unit (s) by means of the first and the second valve assembly.
  • a hydraulic control of the adjusting unit (s) by means of the first and the second valve assembly.
  • the desired roll gap can be adjusted quickly, whereby an accurate positioning can then be done by means of the designed on the smaller nominal volume flow valve assembly.
  • changes in thickness of profile sections to be produced can only be carried out by means of one of the two valve arrangements, in particular the small valve arrangement with smaller strokes.
  • the control of the adjusting unit takes place in the first portion of a stroke between the actual roller position and the target roller position by means of the first and / or second valve arrangement to achieve high actuating speeds, and in the second portion of the stroke, in particular the Target roller position comprises, carried out by the two valve assemblies solely by means of the first valve arrangement to achieve high positional accuracy.
  • the adjusting unit for roll gap changes of more than 10% deviation between actual and desired position, in particular of more than 5% of the rolling gap can be controlled by means of the first and second valve arrangement in the first section of the stroke (.DELTA.X).
  • An absolute value, in which both valve arrangements are controlled for actuating the setting unit can be indicated, for example, with a thickness change greater than 0.1 mm or roll gap.
  • the method has the advantages of the hydraulic arrangement according to the invention analogously. It is therefore to be understood that all features mentioned in connection with the arrangement are mutatis mutandis transferable to the method and, conversely, all mentioned in connection with the method features on the arrangement.
  • At least one manipulated variable for controlling the opening degree of the first valve arrangement and at least one manipulated variable for controlling the opening degree of the second valve arrangement can be offset in time be issued.
  • a first manipulated variable for a first valve of the first valve arrangement and a second controlled variable for a second valve of the first valve arrangement can be output with a time delay for controlling the opening degree of the first valve arrangement and / or for controlling the opening degree of the second valve arrangement first manipulated variable for a first valve of the second valve arrangement and a second manipulated variable for a second valve of the second valve arrangement are output with a time delay.
  • the desired roll position can be determined as a function of a desired thickness profile and at least one of a thickness measurement on the inlet side of the work roll and a profile thickness measurement on the outlet side of the work roll.
  • FIGS. 1 and 2a to 2d a hydraulic arrangement for controlling a roll gap 19 in a first embodiment is shown schematically.
  • incoming strip material 18 is rolled through the nip 19 from a constant nominal thickness to a variable thickness profile profile of the outgoing strip material 18 '.
  • the nip 19 is formed by two work rolls 6, 6 'of a four-high rolling stand.
  • the work rolls 6, 6 ' are each supported by a support roll 5, 5' to reduce the deflection of the work rolls 6, 6 '.
  • the work rolls 6, 6 'and the support rollers 5, 5' are each rotatably mounted in chocks, which are not shown in the figures.
  • the chocks are in turn housed in a rolling stand.
  • the chock of the lower work roll 6 'and the lower support roll 5' are fixed and the chock of the upper work roll 6 and the upper support roll 5 are mounted vertically displaceable in the rolling stand.
  • the chock of the upper work roll 6 and the upper support roller 5 can be positioned vertically via a Anstellech 1 or the Anstelltechnik 1 can exert on the chock a vertical rolling force.
  • the adjusting unit 1 comprises an adjusting piston 2 which divides a setting cylinder 17 movably into a first chamber 3 and a second chamber 4. If the first chamber 3 is acted upon by a higher pressure than the second chamber 4, the Anstellkolben 2 moves in the direction of the second chamber 4 and the nip 19 is reduced. If the second chamber 4 is acted upon by a higher pressure than the first chamber 3, the Anstellkolben 2 moves in the direction of the first chamber 3 and the nip 19 is increased.
  • first valve arrangement 9 and the second valve arrangement 10 each comprise precisely one valve 11, 12, the valve 12 of the second valve arrangement 10 having a larger nominal volume flow than the valve 11 of the first valve arrangement 9.
  • the valve 11 in the first embodiment of the hydraulic system as a 5/3-way valve, which controls a first Druckstoffweg 13 and a second Druckstoffweg 14, executed with an actuator 20.
  • the valve 11 is connected to a port A via the first Druckstoffweg 13 with the first chamber 3 and with a port B via the second Druckstoffweg 14 with the second chamber 4.
  • the valve 11 is connected via two ports P with a pressure medium source 27 and with a port T to a tank 28 which only in FIG. 1 are shown.
  • the valve 12 of the second valve arrangement 10 is likewise designed as a 5/3-way valve which controls a third pressure medium path 15 and a fourth pressure medium path 16 with an actuator 21.
  • the valve 12 is connected to a port A via the third Druckstoffweg 15 with the first chamber 3 and with a port B via the fourth Druckstoffweg 16 with the second chamber 4.
  • the valve 12 is connected via two ports P with a pressure medium source 27 and with a port T to a tank 28 which only in FIG. 1 are shown.
  • any arrangement is conceivable that a largely constant working pressure, which is greater than 200 bar, in particular greater than 250 bar, in particular greater than 300 bar, at a defined volume flow at the terminals P of the valve assemblies 9, 10 can provide.
  • a direct connection of one or more pumps to the ports P of the valve assemblies 9, 10 is possible or one or more pressure fluid accumulators can be arranged between the valve assemblies 9, 10 and a pump.
  • the ports P of the valve assemblies 9, 10 are fed from a common source of pressure medium.
  • at least a part number of the terminals P of the valve assemblies 9, 10 is connected to a separate pressure medium source.
  • any arrangement which allows a recording of the hydraulic fluid flowing out of the Anstelltechnik 1, and the pumps of the pressure medium source 27 feeds with hydraulic fluid.
  • the arrangement can be designed so that the outflowing hydraulic fluid can flow as quickly as possible.
  • pulsation dampers 30 can be arranged in the return line 31 between the valve arrangements 9, 10 and the main tank 28, in particular in front of the intermediate tank 29.
  • valve 11 of the first valve assembly 9 and the valve 12 of the second valve assembly 10 are in FIG. 2a shown in a first switching position, in which the first chamber 3 and the second chamber 4 are not acted upon by working pressure from the pressure medium source and the Anstellkolben 2 remains in the closed position.
  • the actuators 20, 21 are each positioned so that the two chambers 3, 4 of the Anstellzylinders 17 are hydraulically separated from both the pressure medium source and from the tank and thus an inflow and outflow of the hydraulic fluid in one of both chambers 3, 4 is suppressed.
  • FIG. 2b the valve 11 of the first valve assembly 9 and the valve 12 of the second valve assembly 10 are shown in a second switching position, in which the second chamber 4 is acted upon by the working pressure of the pressure medium source.
  • the Anstellkolben 2 moves in this switching position in the direction of the first chamber 3 and the nip 19 is increased.
  • the actuators 20, 21 are each positioned so that the first chamber 3 of the Anstellzylinders 17 is hydraulically connected to the tank and thus an outflow of the hydraulic fluid from the first chamber 3 can be carried in the direction of the tank.
  • the outflow of the hydraulic fluid is represented in the figures by white arrows with a black border.
  • the second chamber 4 of the Anstellzylinders 17 is hydraulically connected via the valves 11, 12 with the pressure medium source and there is an inflow of the hydraulic fluid under the working pressure in the second chamber 4.
  • the inflow of the hydraulic fluid is represented in the figures by solid arrows ,
  • valve 11 of the first valve assembly 9 and the valve 12 of the second valve assembly 10 are shown in a third switching position, in which the first chamber 3 is acted upon by the working pressure of the pressure medium source.
  • the Anstellkolben 2 moves in this switching position in the direction of the second chamber 4 and the nip is reduced or the rolling force is increased.
  • the actuators 20, 21 are each positioned so that the second chamber 4 is hydraulically connected to the tank and thus an outflow of the hydraulic fluid from the second chamber 4 can take place in the direction of the tank.
  • the first chamber 3 of the Anstellzylinders 17 is hydraulically connected via the valves 11, 12 with the pressure medium source and there is an inflow of the hydraulic fluid under the working pressure in the first chamber.
  • a stroke volume must be the product of the acting cross-sectional area of the Anstellzylinders 17 and the stroke .DELTA.X in the second chamber 4 in and simultaneously conveyed out of the first chamber 3 out.
  • the effective cross-sectional area of the second Chamber 4 due to the piston rod is annular and smaller than the acting cross-sectional area of the first chamber 3.
  • the second valve arrangement 10 has a larger nominal volume flow than the first valve arrangement 9. Upon complete opening of the valve assemblies 9, 10, thus a greater part of the stroke volume is conveyed through the second valve assembly 10 into the second chamber than through the first valve assembly.
  • valve assemblies 9, 10 may be designed so that in the first portion of the stroke .DELTA.X both valve assemblies 9, 10 are opened to allow the largest possible volume flow, as in the FIGS. 2b and 2c shown. In the second area, the second valve arrangement 10 is closed and the resulting volume flow corresponds to the nominal volume flow of the first valve arrangement 9.
  • valve 11 of the first valve assembly 9 and the valve 12 of the second valve assembly 10 are shown in a fourth shift position, in which-as previously in FIG Figure 2c -
  • the first chamber 3 is acted upon by the working pressure of the pressure medium source.
  • the Anstellkolben 2 moves in this switching position in the direction of the second chamber 4 and the nip is reduced or the rolling force is increased.
  • the actuator 21 of the valve 10 is in a closed position, so that an inflow of the hydraulic fluid into the first chamber 3 and an outflow of the hydraulic fluid from the second chamber 4 takes place only via the first valve 9.
  • the resulting volume flow and thus also the actuating speed of the Anstellkolbens 2 thus decrease with respect to the third switching position.
  • a more accurate positioning of the adjusting unit or the work roll 6 is made possible.
  • the control of the valve assemblies 9, 10 takes place in each case via a manipulated variable output by a controller 25.
  • the valves 11, 12 are each designed as a continuous valve, in particular as a servo valve or servo valves with pilot control, so that the two valves 11, 12 can be set continuously between an open position with nominal volume flow and a closed position without flow on the manipulated variable.
  • By varying the opening degrees of the valves 11, 12, the resulting Volumetric flow and thus the stroke speed of the actuating piston 2 can be adjusted specifically over the stroke .DELTA.X.
  • the controller 25 can be supplied with the actual roller position as a control variable and, by a process controller, with the desired roller position as a reference variable.
  • the desired roll position can be specified by the process control as a function of a nominal thickness profile. It is also conceivable that the target roller position is determined as a function of an actual thickness profile of the outgoing strip material 18 'received by the measuring unit 8 and / or a thickness profile of the incoming strip material 18 recorded by the measuring unit 7.
  • FIG. 3 a hydraulic system according to the invention in a second embodiment is shown schematically, which differs from the hydraulic arrangement in FIG. 1 only distinguished by the alternative embodiment of the second valve assembly 10 '.
  • Identical elements of the hydraulic systems are provided with the same reference numerals. For the similarities is therefore at this point to the comments on the FIGS. 1 and 2a to 2d directed.
  • the second valve arrangement 10 'in the second embodiment comprises a first valve 12' and a second valve 12 ".
  • the first valve 12 ' controls, with an actuator 21', the third pressure medium path 15 'and an additional fifth pressure medium path 22.
  • the first valve 12 ' is hydraulically connected to a port A via the third fluid path 15' to the first chamber 3 and to a port B via the fifth fluid path 22 to the second chamber 4.
  • the valve 12 ' is connected via a port P to an unillustrated port
  • the second valve 12 "controls with an actuator 21, the fourth Druckstoffweg 16 'and an additional sixth Druckstoffweg 23.
  • the second valve 12" is connected to a port B via the fourth Druckstoffweg sixteenth 'hydraulically verbun with the second chamber 4 and with a port A via the sixth Druckstoffweg 23 with the first chamber 3 hydraulically the.
  • the two actuators 21 ', 21 "of the valves 12', 12" are kinematically decoupled, so that the valve 12 'and the valve 12 "can be set independently by a regulator 25.
  • the two valves 12', 12" are in particular identical In sum, they have a rated volumetric flow which is greater than the nominal volumetric flow rate of the first valve arrangement 9. It is understood that the individual valves can also be designed or controlled differently, for example as only in one direction acting on the Anstelltechnik 1 valves, which together form the double-acting valve arrangement for actuating the adjusting unit 1 in both directions together control technology.
  • the first valve arrangement 9 may comprise two or more valves, which may be designed analogously to the two valves 12 ', 12 "of the second valve arrangement 10', as described above.
  • FIGS. 4a to 4d show the switching positions of the second embodiment analogous to the switching positions of the first embodiment in the FIGS. 2a to 2d , Wherein the respective volume flows belonging to the switch positions are additionally realized by the two pressure medium passages 22, 23. It is therefore at this point to the explanations to the FIGS. 2a to 2d directed.
  • Figure 4e is an intermediate switching position between the switch positions of Figure 4c , in which by a maximum volume flow, a large lifting speed is realized, and the switching position of the FIG. 4d , in which a small flow velocity is realized for exact positioning by means of a small volume flow.
  • the second valve 12 "of the second valve arrangement 10 ' is closed so that a volume flow into the first chamber 3 and out of the second chamber 4 is realized only by the valves 11 and 12' the Indian Figure 4c realized volume flow and larger than that in the FIG. 4d realized volume flow.
  • the second valve arrangement can be represented by any number of in series and / or parallel valves, which together allow a double-acting control of Anstellzylinders 17 with a larger nominal volume flow than the nominal volume flow of the first valve assembly.
  • 2/2, 3/2, 3/3, 4/2, 4/3, or 5/3 way valves can be used.
  • the first valve assembly 9 can be composed analogously by a plurality of valves and thus the variability of the control of the adjusting unit 1 can be further increased.
  • FIG. 5 an inventive method for controlling a roll gap 19 is shown in a flow chart.
  • a starting roll position of a work roll 6 is determined.
  • a desired roll position of the work roll 6 is determined, so that a stroke ⁇ X between the start roll position and the target roll position can be determined. This can be done by a control unit 24 in response to a desired thickness profile and a thickness measurement 7 on the inlet side of the work roll 6 and a profile thickness measurement 8 on the outlet side of the work roll.
  • an actual roll position is measured by a position sensor 26.
  • a process decision VE10 is subsequently checked whether the actual roll position coincides with the target roll position. If the actual roll position coincides with the target roll position, the process is stopped in a process step S and the roll position is held. If the actual roller position and the target roller position are different from one another, a degree of opening of a first valve arrangement 9 and an opening degree of a second valve arrangement 10, 10 'are controlled in a process step V40 to provide a setting unit connected to the work roll 6 as a function of Actual roll position and the target roll position to control.
  • the second valve arrangement 10, 10 ' has a larger nominal volume flow than the first valve arrangement 9.
  • the control of the adjusting unit in a first section of a stroke between the actual roller position and the target roller position by means of the second valve arrangement.
  • the control of the adjusting unit can thus be effected solely by the second adjusting unit or by the second valve arrangement together with the first valve arrangement. It can thus be made large volume flows, which lead to a high actuating speed of Anstelltechnik.
  • the control of the adjusting unit in a second section of the stroke between the actual roller position and the target roller position, which includes the target roller position, is effected solely by means of the first valve arrangement. Due to the smaller nominal volume flow of the first valve arrangement, the adjusting unit can be positioned more accurately, although smaller actuating speeds can be achieved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
EP18171953.5A 2018-05-11 2018-05-11 Hydraulikanordnung und verfahren zur regelung eines walzspalts eines walzgerüsts Withdrawn EP3566789A1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP18171953.5A EP3566789A1 (de) 2018-05-11 2018-05-11 Hydraulikanordnung und verfahren zur regelung eines walzspalts eines walzgerüsts
PL19721316.8T PL3790674T3 (pl) 2018-05-11 2019-05-07 Klatka walcownicza z układem hydraulicznym do regulacji szczeliny walcowniczej i sposób jej regulacji
PCT/EP2019/061747 WO2019215197A1 (de) 2018-05-11 2019-05-07 Walzgerüst mit einer hydraulikanordnung zur regelung des walzspalts und verfahren hierfür
EP19721316.8A EP3790674B1 (de) 2018-05-11 2019-05-07 Walzgerüst mit einer hydraulikanordnung zur regelung des walzspalts und verfahren hierfür
CN201980031601.XA CN112203782B (zh) 2018-05-11 2019-05-07 带有用于调节轧辊间隙的液压组件的轧辊机架及其方法
ES19721316T ES2913976T3 (es) 2018-05-11 2019-05-07 Tren de laminación con un dispositivo hidráulico para la regulación de la hendidura entre cilindros y procedimiento para ello
US17/053,388 US11491523B2 (en) 2018-05-11 2019-05-07 Hydraulic control of a roll gap for a roll stand

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18171953.5A EP3566789A1 (de) 2018-05-11 2018-05-11 Hydraulikanordnung und verfahren zur regelung eines walzspalts eines walzgerüsts

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EP3566789A1 true EP3566789A1 (de) 2019-11-13

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EP18171953.5A Withdrawn EP3566789A1 (de) 2018-05-11 2018-05-11 Hydraulikanordnung und verfahren zur regelung eines walzspalts eines walzgerüsts
EP19721316.8A Active EP3790674B1 (de) 2018-05-11 2019-05-07 Walzgerüst mit einer hydraulikanordnung zur regelung des walzspalts und verfahren hierfür

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US (1) US11491523B2 (zh)
EP (2) EP3566789A1 (zh)
CN (1) CN112203782B (zh)
ES (1) ES2913976T3 (zh)
PL (1) PL3790674T3 (zh)
WO (1) WO2019215197A1 (zh)

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DE102020211770A1 (de) 2020-03-06 2021-09-09 Sms Group Gmbh Walzgerüst

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JPH0552202A (ja) * 1991-08-20 1993-03-02 Sumitomo Metal Ind Ltd 油圧式サーボ装置
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JP2001311401A (ja) * 1999-12-03 2001-11-09 Amada Eng Center Co Ltd 液圧サーボバルブの制御方法および装置並びに液圧シリンダの駆動方法および装置
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WO2007093333A1 (de) * 2006-02-13 2007-08-23 Iba Ag Verfahren und vorrichtung zur identifizierung eines teilstücks eines halbzeugs

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Publication number Priority date Publication date Assignee Title
JPS5114593A (en) * 1974-07-24 1976-02-05 Komatsu Mfg Co Ltd Kensetsusharyono shiagebetsujidoseigyosochi
DE3803490A1 (de) 1988-02-05 1989-08-17 Rexroth Mannesmann Gmbh Sicherheitsanordnung fuer stellzylinder, insbesondere fuer kalander mit verstellbaren walzen
JPH0552202A (ja) * 1991-08-20 1993-03-02 Sumitomo Metal Ind Ltd 油圧式サーボ装置
JPH0911000A (ja) * 1995-06-22 1997-01-14 Amada Co Ltd 油圧装置
JP2001311401A (ja) * 1999-12-03 2001-11-09 Amada Eng Center Co Ltd 液圧サーボバルブの制御方法および装置並びに液圧シリンダの駆動方法および装置
DE10254958A1 (de) * 2002-11-26 2004-06-03 Sms Demag Ag Einrichtung zur Regelung des Walzspaltes beim Walzverfahren für Metalle, insbesondere für Stahlwerkstoffe, unter sich schnell ändernden Parametern
JP2004251331A (ja) * 2003-02-19 2004-09-09 Hitachi Zosen Corp 流体駆動装置および流体駆動装置における流体制御方法
EP1459813A2 (de) * 2003-03-21 2004-09-22 Sundwig GmbH Anstellzylinder für Walzgerüste zum Walzen von Stahl oder Nichteisenmetall
WO2007093333A1 (de) * 2006-02-13 2007-08-23 Iba Ag Verfahren und vorrichtung zur identifizierung eines teilstücks eines halbzeugs

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US11491523B2 (en) 2022-11-08
EP3790674A1 (de) 2021-03-17
CN112203782B (zh) 2023-08-18
PL3790674T3 (pl) 2022-08-08
ES2913976T3 (es) 2022-06-07
CN112203782A (zh) 2021-01-08
EP3790674B1 (de) 2022-04-20
WO2019215197A1 (de) 2019-11-14
US20210229151A1 (en) 2021-07-29

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