EP0351507A2 - Device for adjusting the interstice between rollers - Google Patents

Device for adjusting the interstice between rollers Download PDF

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Publication number
EP0351507A2
EP0351507A2 EP89108175A EP89108175A EP0351507A2 EP 0351507 A2 EP0351507 A2 EP 0351507A2 EP 89108175 A EP89108175 A EP 89108175A EP 89108175 A EP89108175 A EP 89108175A EP 0351507 A2 EP0351507 A2 EP 0351507A2
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EP
European Patent Office
Prior art keywords
roller
elements
supporting
actuating
roll
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Granted
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EP89108175A
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German (de)
French (fr)
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EP0351507B1 (en
EP0351507A3 (en
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Günther Alich
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ALICH, GUENTHER
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Individual
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05C—APPARATUS FOR APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05C1/00—Apparatus in which liquid or other fluent material is applied to the surface of the work by contact with a member carrying the liquid or other fluent material, e.g. a porous member loaded with a liquid to be applied as a coating
    • B05C1/04—Apparatus in which liquid or other fluent material is applied to the surface of the work by contact with a member carrying the liquid or other fluent material, e.g. a porous member loaded with a liquid to be applied as a coating for applying liquid or other fluent material to work of indefinite length
    • B05C1/08—Apparatus in which liquid or other fluent material is applied to the surface of the work by contact with a member carrying the liquid or other fluent material, e.g. a porous member loaded with a liquid to be applied as a coating for applying liquid or other fluent material to work of indefinite length using a roller or other rotating member which contacts the work along a generating line
    • B05C1/0826—Apparatus in which liquid or other fluent material is applied to the surface of the work by contact with a member carrying the liquid or other fluent material, e.g. a porous member loaded with a liquid to be applied as a coating for applying liquid or other fluent material to work of indefinite length using a roller or other rotating member which contacts the work along a generating line the work being a web or sheets
    • B05C1/0834—Apparatus in which liquid or other fluent material is applied to the surface of the work by contact with a member carrying the liquid or other fluent material, e.g. a porous member loaded with a liquid to be applied as a coating for applying liquid or other fluent material to work of indefinite length using a roller or other rotating member which contacts the work along a generating line the work being a web or sheets the coating roller co-operating with other rollers, e.g. dosing, transfer rollers

Definitions

  • the invention relates to a roll stand with at least two corresponding rollers that are movably guided relative to one another in bilateral bearing arrangements, one roller being displaceable relative to the other by means of an adjusting mechanism for the purpose of adjusting the resulting roller gap.
  • the coating material is brought to the metering roller nip from a feed trough 105 which extends over the bale or coating width of the installation and is continuously transported to the film 106 via the roller system.
  • the decisive for the layer thickness roller gap above the pan 105 is formed with the help of the fixed to the stand frame 107 with the pillow block 107 '1 applicator roller 102 and on a load support bearing 108 on the stand 107 freely guided metering roller 101.
  • the size of the roller gap or the thickness of the more or less consistent material transported to the film can be adjusted with the aid of a screw spindle 110 articulated on the bearing slide 109 and an adjusting device consisting of nut 111 and fork bracket 112 and mounted on stand 107.
  • a screw spindle 110 articulated on the bearing slide 109 and an adjusting device consisting of nut 111 and fork bracket 112 and mounted on stand 107 As can easily be seen from the arrangement according to FIG. 1, the inner ring tolerances of the radial bearings 108, 107 'have a full effect on the nip accuracy, even in the case of a version free of play.
  • FIG. 1 the inner ring tolerances of the radial bearings 108, 107 'have a full effect on the nip accuracy, even in the case of a version free of play.
  • the roller gap formed by the roller pair 101, 102 and the roller axis spacing defined by the roller axes 101 ′, 102 ′ thanks to the non-positive and form-locking, mutually braced connecting elements of an actuating and supporting device 113, 114, 115, 116 unaffected by disturbances caused, for example, by inaccuracies in the roller support bearings 107 ', 108 in FIG. 1 and / or by deflections exerted by the spindle couplings on the roller journals.
  • the roller actuating unit consisting of the piston rod bearing 115 and the cylinder block bearing 116 guides the roller gap to zero during operation
  • the support unit consisting of the pair of support bearings 113, 113 'acts with pressure screws (spring elements) and adjusting gear housing 114 in the Support plane xx opposite.
  • the rollers become tap to a certain extent on bending, which is generally undesirable. 3 those bending lines of the roller axes 101 ', 102' generated by the arrangement of the adjusting and supporting elements according to FIG. 2 are shown exaggerated.
  • Fig. 4 shows a novel placement of the aforementioned actuating / support units, which is characterized by an arrangement lying in a common radial plane yy of the roll neck in the manner of a mutually interpenetrating construction of the actuating and supporting elements.
  • the roller journals 121, 122 of the metering and application roller 101, 102 are in this case also gripped and guided autonomously in a known manner with the aid of an actuating and supporting unit.
  • the actuating unit consists essentially of the bearing half-shell 131, 132 with four anchor bolts 133 held and guided by it and the actuating cylinder block 134 connected to it, together with the actuating piston 135 and the piston plate 136 and the identical anchor bolts 133 'screwed to it in the same way on the opposite side, which are also with the help of an identical half-shell 131 'closes the force circuit via the roll neck 122 on the other side of the application roller 102.
  • the adjusting unit designed in this way counteracts the supporting unit installed between the roller journals 121, 122; which consists essentially of the other, on the "inner" opposite side of the pins 121, 122 arranged play-free pair of bearing halves 141, 141 'and the compression spring bars 143.
  • a sectional view jj Fig. 4a of the actuating / supporting elements according to Fig. 4 makes it clear that the actuating and supporting elements of the construction are interlocked and positively guided in such a way that their centrally centered actuating or supporting forces are always in the same radial plane yy of the roll neck 121, 122 attack. As a result, it is the support 4 / 4a to address both radially and axially as completely autonomous.
  • roller journals 121, 122 are pressed apart with the aid of the compression springs 143 in connection with the pair of bearing half shells 141, 141 'against the actuating unit 131, 131', 133, 134, 135, 136 and how in the case of Fig. 4 / 4a acting as a pressure compensator with the aid of a regulating pump 138, the roll gap is set.
  • the actuating piston 135 of the actuating cylinder block 134 is hollow and takes over two tasks, namely the actual one as an actuator and a second one for guiding a displacement measuring device 161, 162, 163, 164, 165.
  • One in the piston 135 is free and independent of its actuating direction with the help of a longitudinal bearing 139 embedded and guided path sensor 161 in a tappet housing 162 is supported by means of a compression spring 163 and stops 164, 165 on the support bearing half-shells 151, 151 'which are supported on the roller journals without play.
  • the roll spacing or (in the case of a centrically ground roll roll) the roll gap which is proportional to it can be measured in a reliable manner or controlled with the aid of a control device - comprising a set / actual value comparator 167, 168 and a servo valve 130; see Fig. 7.
  • a control device - comprising a set / actual value comparator 167, 168 and a servo valve 130; see Fig. 7.
  • a valve-free actuating force control practiced with the aid of a regulating pump 138 can be used.
  • a more precise actuating force control will, however, use a suitable servo valve 130, a pressure measuring device 166 and a comparator 167, 168, as indicated in FIGS. 5 and 7.
  • three alternative sensors are available as actual sensors, namely one each for a roller distance measurement 161 and signal pressure measurement 166 and, as a further variant, an actuating force measurement with the aid of a load cell 147.
  • the compression spring bars 143 are supported indirectly by means of an intermediate plate 146 via the load cell 147 on the support bearing half-shell 141 '.

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Abstract

Bei Walzenspalteinstellvorrichtungen für Walzenpaare (101, 102) eines Walzengerüstes mit Stellelementen (131, 131′, 133, 133′, 134, 135, 136) und Stützelementen (141, 141′ 143), wie sie beispielsweise zur Beschichtung von Kunst­stoff-Folien oder Metallbändern mit Stoffen, die nicht oder nur mässig auf den Dosierwalzenspalt zurückwirken, gebräuchlich sind, sollen jene mechanischen, die Schicht­dickengenauigkeit beeinträchtigenden Störungen eliminiert werden, die von "äusseren" Störquellen, etwa von Lagerfeh­lern und Ständerkopplungen herrühren, wie auch solche, die durch "innere" (systemimmanente) Walzenbiegekräfte zufolge der in einer radialen Stellebene und einer mit ihr korre­spondierenden radialen Stützebene positionierten Stell- und Stützelemente verursacht werden.
Dies gelingt mit Hilfe von an den Walzenzapfen (121, 122) von "äusseren", dem Ständer und den Antrieben zugehörigen Konstruktionsteilen unabhängig geführten Halbschalen-La­gern (131, 131′, 141, 141′), mit an den Walzenzapfen (121, 122) beidseitig spielfrei angreifenden Stell- und Stütz­kräften der Stellelemente (133, 134, 135, 136, 133′) und Stützelemente (143) in einer zu den Walzenachsen recht­winkligen gleichen radialen Ebene.
Darüber hinaus bietet diese Anordnung u.a. die Möglichkeit eines vorteilhaften Einbaus einer in der Stelleinheit (134, 135) zentrisch geführten Walzenabstandsmesseinrichtung.

Figure imgaf001
In nip setting devices for roller pairs (101, 102) of a roll stand with actuating elements (131, 131 ', 133, 133', 134, 135, 136) and support elements (141, 141 '143), such as those used for coating plastic films or Metal belts with substances that do not, or only moderately, react to the metering roller gap are to be used to eliminate those mechanical disturbances which impair the layer thickness accuracy and which result from "external" sources of interference, for example from bearing errors and stator couplings, as well as those caused by "internal""(System-inherent) roll bending forces are caused by the positioning and supporting elements positioned in a radial setting plane and a corresponding radial supporting plane.
This is achieved with the aid of half-shell bearings (131, 131 ', 141, 141') which are independently guided on the roller journals (121, 122) by "outer" structural parts associated with the stand and the drives, and on the roller journals (121, 122 ) Actuating and supporting forces of the adjusting elements (133, 134, 135, 136, 133 ') and supporting elements (143), which act on both sides without play, in a same radial plane perpendicular to the roller axes.
In addition, this arrangement offers, inter alia, the possibility of advantageously installing a roller distance measuring device which is guided centrally in the adjusting unit (134, 135).
Figure imgaf001

Description

Die Erfindung betrifft ein Walzengerüst mit mindestens zwei miteinander korrespondierenden, relativ zueinander in beidseitigen Lageranordnungen beweglich geführten Wal­zen, wobei eine Walze, zwecks Einstellung des sich erge­benden Walzenspaltes, gegenüber der anderen mittels einem Stellmechanismus verschiebbar ist.The invention relates to a roll stand with at least two corresponding rollers that are movably guided relative to one another in bilateral bearing arrangements, one roller being displaceable relative to the other by means of an adjusting mechanism for the purpose of adjusting the resulting roller gap.

Verfahren zur Lösung jener Aufgabe - wie sie sich bei­spielsweise beim Betrieb einer Folien-Beschichtungsma­schine zur Verarbeitung nicht-reaktiver Stoffe, wie Lak­ke u. dgl stellt - sind aus der EP-A2-0242783 bekannt. Eine nach Massgabe jener Vorschläge ausgebildete autonome Walzenspalt-Einstellvorrichtung eliminiert den bei kon­ventionellen Maschinen die Walzenspaltgenauigkeit beein­trächtigenden Radialschlag der Laststützlager-Innenringe. Infolge einer gewissen Hebelwirkung der im Kraft- und Formschluss-Verbund auf die Walzenzapfen wirkenden Stell- und Stützelemente kann dabei u.U. ein Walzenbiegemoment erzeugt werden, das die Walzenspalt-Parallelität nachtei­lig beeinflusst.
Aufgabe der vorliegenden Erfindung zur Walzenspalteinstel­lung eines Walzenpaares mit Hilfe von Stell- und Stützele­menten ist es, Walzenbiegemomente zu vermeiden. Das Prinzip der Erfindung wird anhand von Zeichnungen schematisch und detailliert beschrieben, wobei sich die Darstellungen und Erläuterungen (mit Ausnahme von Fig. 3) jeweils auf eines der beidseitig nahezu identisch ausge­führten Walzenenden beschränkt. Es stellen dar

  • Fig. 1 ein konventionelles Verfahren zur Dosierwalzen­spalt-Einstellung eines Auftragswerkes;
  • Fig. 2 einen kraft- und formschlüssigen Walzenverbund mit Hilfe autonom gelagerter Stell- und Stützele­mente gem. EP-A2-242783;
  • Fig. 3 ein Schema der Walzenachsen-Biegelinien bei einer Geräteanordnung gemäss Fig. 2;
  • Fig. 4 eine Anordnung und das Prinzip einer biegemoment­freien Walzen-Stell/Stützeinheit;
  • Fig. 4a eine Schnitt-Seitenansicht j-j der Anordnung gem. Fig. 4 mit Darstellung der gemeinsamen Symmetrie- und Stell/Stützachsen y-y und s-s;
  • Fig. 4b eine für grosse Stellwege (Walzenspalte) mit äu­sserem Stellkraftangriff ausgebildete Anordnung der Stellelemente;
  • Fig. 5 ein detailliertes Ausführungsbeispiel einer Kom­pakt-Stell/Stützeinheit;
  • Fig. 6 eine Variante eines Stützelement-Details mit ei­ner Kraftmessdose;
  • Fig. 7 eine schematische Darstellung eines Walzenspalt-­Regelkreises mit Hilfe von drei alternativen Ist­wertgebern.
Process for solving that task - as is the case, for example, when operating a film coating machine for processing non-reactive substances, such as Lakke u. The like represents - are known from EP-A2-0242783. An autonomous roll gap setting device designed in accordance with those suggestions eliminates the radial runout of the load support bearing inner rings which affects the roll gap accuracy in conventional machines. As a result of a certain leverage effect of the actuating and supporting elements acting in a force-locking and positive-locking connection on the roll neck, a roll bending moment can be generated which adversely affects the roll gap parallelism.
The object of the present invention for setting the nip of a pair of rolls with the aid of adjusting and supporting elements is to avoid roll bending moments. The principle of the invention is described schematically and in detail with reference to drawings, the illustrations and explanations (with the exception of FIG. 3) each limited to one of the roller ends that are almost identical on both sides. It represent
  • 1 shows a conventional method for setting the metering roll gap of an application unit;
  • Fig. 2 shows a non-positive and positive roller composite with the help of autonomously mounted actuating and supporting elements. EP-A2-242783;
  • 3 shows a diagram of the roll axis bending lines in a device arrangement according to FIG. 2;
  • 4 shows an arrangement and the principle of a roll actuation / support unit free of bending moment;
  • Fig. 4a is a sectional side view jj of the arrangement. 4 shows the common symmetry and positioning / support axes yy and ss;
  • 4b shows an arrangement of the actuating elements designed for long actuating paths (nips) with an external actuating force attack;
  • Fig. 5 shows a detailed embodiment of a compact actuator / support unit;
  • 6 shows a variant of a support element detail with a load cell;
  • Fig. 7 is a schematic representation of a roll gap control circuit using three alternative actual value transmitters.

In einem gemäss Fig. 1 mit einer Dosierwalze 101, einer Auftragswalze 102 sowie einer Schichtübertragungswalze 103 ausgestatteten Auftragswerk einer Folienbeschichtungsanlage wird der Beschichtungsstoff aus einer sich über die Bal­len- bzw Beschichtunsbreite der Anlage erstreckenden Speisewanne 105 an den Dosierwalzenspalt herangetragen und über das Walzensystem kontinuierlich zur Folie 106 transportiert. Der für die Schichtdicke massgebende Wal­zenspalt oberhalb der Speisewanne 105 wird dabei mit Hil­fe der am Ständerrahmen 107 mit dem Stehlager 107′ 1 fixier­ten Auftragswalze 102 und der auf einem Last-Stützlager 108 am Ständer 107 frei beweglich geführten Dosierwalze 101 gebildet. Die Grösse des Walzenspaltes bzw. die Dicke des zur Folie transportierten mehr oder minder konsistenten Stoffes lässt sich mit Hilfe einer am Lagerschlitten 109 angelenkten Schraubenspindel 110 und einer am Ständer 107 montierten, aus Mutter 111 und Gabelbock 112 bestehenden Stellvorrichtung justieren.
Wie die Anordnung nach Fig. 1 unschwer erkennen lässt, wirken sich u.a. die Innenring-Toleranzen der Radiallager 108, 107′, selbst bei solchen in spielfrei verspannter Ausführung, voll auf die Walzenspaltgenauigkeit aus. Demgegenüber ist gemäss Fig. 2 der durch das Walzenpaar 101, 102 gebildete Walzenspalt und der durch den mit den Walzenachsen 101′, 102′ definierte Walzenachsenabstand dank den kraft- und formschlüssigen, gegenseitig verspann­ten Verbindungselementen einer Stell- und Stützeinrichtung 113, 114, 115, 116 von Störungen unbeeinflusst, die z.B. durch Ungenauigkeiten der Walzenstützlager 107′, 108 in Fig. 1 und/oder durch von den Spindelkupplungen auf die Walzenzapfen ausgeübten Auslenkungen verursacht werden. Während dabei in der Stellebene z-z des Walzenpaares die aus dem Kolbenstangenlager 115 und dem Zylinderblocklager 116 bestehende Walzenstelleinheit den Walzenspalt betriebs­mässig gegen null führt, wirkt ihr die Stützeinheit, be­stehend aus dem Stützlagerpaar 113, 113′ mit Druckschrau­ben (Federelementen) und Einstellgetriebegehäuse 114, in der Stützebene x-x entgegen.
Zufolge der in den Ebenen x-x und z-z an den Walzen 101, 102 angreifenden Stütz- und Stellkräfte werden die Walzen­ zapfen in gewissem Ausmass auf Biegung beansprucht, was im allgemeinen unerwünscht ist.
In Fig. 3 sind jene, durch die Anordnung der Stell- und Stützelemente gemäss Fig. 2 generierten Biegelinien der Walzenachsen 101′, 102′ überspitzt dargestellt. Es leuch­tet ein, dass das Mass für solche unvermeidbaren Walzen­durchbiegungen von dem Abstand zwischen x-x und z-z sowie von den Grössen für Stellkraft und Zapfen-Widerstandsmo­ment abhängt.
Fig. 4 zeigt eine neuartige Placierung der vorerwähnten Stell/Stützeinheiten, die durch eine in einer gemeinsamen radialen Ebene y-y der Walzenzapfen liegenden Anordnung in der Art einer sich wechselseitig durchdringenden Kon­struktion der Stell- und Stützelemente gekennzeichnet ist. Die Walzenzapfen 121, 122 der Dosier- und Auftragswalze 101, 102 werden auch hierbei in bekannter Weise mit Hilfe einer Stell- und Stützeinheit gefasst und autonom geführt. Konstruktiv besteht die Stelleinheit im wesentlichen aus der Lagerhalbschale 131, 132 mit vier von ihr gehaltenen und geführten Ankerschrauben 133 und dem damit verbundenen Stellzylinderblock 134 nebst dem Stellkolben 135 und der Kolbenplatte 136 sowie den an ihr gleichartig angeschraub­ten identischen Ankerschrauben 133′ der Gegenseite, die ebenfalls mit Hilfe einer identischen Lagerhalbschale 131′ den Stellkraftkreis über den jenseitigen Walzenzapfen 122 der Auftragswalze 102 schliesst. Der dergestalt konzipier­ten Stelleinheit wirkt die zwischen den Walzenzapfen 121, 122 eingebaute Stützeinheit entgegen; die im wesentlichen aus dem anderen, auf der "inneren" Gegenseite der Zapfen 121, 122 angeordnetem spielfreiem Lagerhälftenpaar 141, 141′ und den Druckfederstäben 143 besteht.
Ein Schnittbild j-j Fig. 4a der Stell/Stützelemente gemäss Fig. 4 macht deutlich, dass die Stell- und Stützelemente der Konstruktion derart ineinander gekammert und zwangsge­führt sind, dass ihre mittig zentrierten Stell- bzw. Stütz­kräfte stets in der gleichen radialen Ebene y-y der Walzen­zapfen 121, 122 angreifen. Demzufolge ist das Stell/Stütz­ system nach Fig. 4/4a sowohl radial, als auch axial als vollständig autonom anzusprechen; "äussere" (auf den Stän­der) oder "längs" 11 (auf die Walzenachsen) wirkende Kräfte oder Momente werden hierbei nicht erzeugt.
Eine Variante der in Fig. 4/4a dargestellten und erläuter­ten Anordnung des aus Stell- und Stützeinheiten bestehen­den Walzenverbundsystems zeigt Fig. 4b. In funktionell gleicher Weise wie zuvor werden auch in dieser Gerätean­ordnung die Walzenzapfen 121, 122 mit Hilfe der Druckfe­dern 143 in Verbindung mit dem Lagerhalbschalenpaar 141, 141′ auseinander gegen die Stelleinheit 131, 131′, 133, 134, 135, 136 gedrückt und, wie im Fall von Fig. 4/4a mit Hilfe einer Regelpumpe 138 als Druckwaage wirkend, der Walzenspalt eingestellt.
Wie das Konzept gemäss Fig. 4b erkennen lässt, ermöglicht eine solche ausserhalb des (inneren) Walzenzapfenbereiches angeordnete Stelleinheit 133, 134, 135, 136 eine allenfalls sehr grosse Walzenspalteinstellung, die in bestimmten Fäl­len nicht zuletzt im Hinblick auf einen unerlässlichen SPALT-NOT-AUF-Betrieb der Maschine von Bedeutung sein kann.In a coating unit equipped with a metering roller 101, an application roller 102 and a layer transfer roller 103 as shown in FIG. 1 the coating material is brought to the metering roller nip from a feed trough 105 which extends over the bale or coating width of the installation and is continuously transported to the film 106 via the roller system. The decisive for the layer thickness roller gap above the pan 105 is formed with the help of the fixed to the stand frame 107 with the pillow block 107 '1 applicator roller 102 and on a load support bearing 108 on the stand 107 freely guided metering roller 101. The size of the roller gap or the thickness of the more or less consistent material transported to the film can be adjusted with the aid of a screw spindle 110 articulated on the bearing slide 109 and an adjusting device consisting of nut 111 and fork bracket 112 and mounted on stand 107.
As can easily be seen from the arrangement according to FIG. 1, the inner ring tolerances of the radial bearings 108, 107 'have a full effect on the nip accuracy, even in the case of a version free of play. In contrast, according to FIG. 2, the roller gap formed by the roller pair 101, 102 and the roller axis spacing defined by the roller axes 101 ′, 102 ′, thanks to the non-positive and form-locking, mutually braced connecting elements of an actuating and supporting device 113, 114, 115, 116 unaffected by disturbances caused, for example, by inaccuracies in the roller support bearings 107 ', 108 in FIG. 1 and / or by deflections exerted by the spindle couplings on the roller journals. While in the position plane zz of the pair of rollers, the roller actuating unit consisting of the piston rod bearing 115 and the cylinder block bearing 116 guides the roller gap to zero during operation, the support unit consisting of the pair of support bearings 113, 113 'acts with pressure screws (spring elements) and adjusting gear housing 114 in the Support plane xx opposite.
As a result of the supporting and actuating forces acting on the rollers 101, 102 in the levels xx and zz, the rollers become tap to a certain extent on bending, which is generally undesirable.
3, those bending lines of the roller axes 101 ', 102' generated by the arrangement of the adjusting and supporting elements according to FIG. 2 are shown exaggerated. It is obvious that the measure of such unavoidable roll deflections depends on the distance between xx and zz as well as on the sizes for actuating force and pin resistance moment.
Fig. 4 shows a novel placement of the aforementioned actuating / support units, which is characterized by an arrangement lying in a common radial plane yy of the roll neck in the manner of a mutually interpenetrating construction of the actuating and supporting elements. The roller journals 121, 122 of the metering and application roller 101, 102 are in this case also gripped and guided autonomously in a known manner with the aid of an actuating and supporting unit. Structurally, the actuating unit consists essentially of the bearing half-shell 131, 132 with four anchor bolts 133 held and guided by it and the actuating cylinder block 134 connected to it, together with the actuating piston 135 and the piston plate 136 and the identical anchor bolts 133 'screwed to it in the same way on the opposite side, which are also with the help of an identical half-shell 131 'closes the force circuit via the roll neck 122 on the other side of the application roller 102. The adjusting unit designed in this way counteracts the supporting unit installed between the roller journals 121, 122; which consists essentially of the other, on the "inner" opposite side of the pins 121, 122 arranged play-free pair of bearing halves 141, 141 'and the compression spring bars 143.
A sectional view jj Fig. 4a of the actuating / supporting elements according to Fig. 4 makes it clear that the actuating and supporting elements of the construction are interlocked and positively guided in such a way that their centrally centered actuating or supporting forces are always in the same radial plane yy of the roll neck 121, 122 attack. As a result, it is the support 4 / 4a to address both radially and axially as completely autonomous. "Outer" (on the stand) or "longitudinal" 11 (on the roller axes) forces or moments are not generated.
4b shows a variant of the arrangement of the roller composite system consisting of actuating and supporting units shown and explained in FIG. 4 / 4a. In a functionally the same way as before, the roller journals 121, 122 are pressed apart with the aid of the compression springs 143 in connection with the pair of bearing half shells 141, 141 'against the actuating unit 131, 131', 133, 134, 135, 136 and how in the case of Fig. 4 / 4a acting as a pressure compensator with the aid of a regulating pump 138, the roll gap is set.
As can be seen from the concept according to FIG. 4b, such an actuating unit 133, 134, 135, 136 arranged outside the (inner) roll neck area enables a very large roll gap setting, which in certain cases not least with regard to an indispensable GAP EMERGENCY OPENING -Operation of the machine can be important.

In Fig. 5/5a ist ein Ausführungsbeispiel einer kompakten biegemomentfreien Stell/Stützeinheit mit integrierter Weg­messeinrichtung für eine Walzenzapfenabstandsmessung sowie (alternativ) eine Druckmessdose für eine Stellkraftmessung dargestellt.
Gegenüber den in der Prinzipdarstellung (Fig. 4/4a) verwen­deten vier Druckfederstäben 143 wird hier ein Stützsystem als statisch bestimmtes 'Dreibein' dergestalt ausgebildet und angeordnet, dass die einzelnen Druckfederstäbe 143, 143′, 143˝ die gleichen spezifischen Stützmomente [=Stütz­abstand vom Zentrum x Federsteife] aufweisen. Ferner ist der Stellkolben 135 des Stellzylinderblocks 134 hohl aus­gebildet und übernimmt derart zwei Aufgaben, nämlich jene eigentliche als Stellglied sowie eine zweite zur Führung einer Wegmesseinrichtung 161, 162, 163, 164, 165. Ein im Kolben 135 frei und von dessen Stellrichtung unabhängig mit Hilfe von einem Längslager 139 in einem Stösselgehäu­se 162 eingebetteter und geführter Wegtaster 161 stützt sich mittels einer Druckfeder 163 und Anschlägen 164, 165 an den an den Walzenzapfen spielfrei gelagerten Stützlager-­Halbschalen 151, 151′ ab.
Dank einer solchen Messanordnung kann der Walzenabstand bzw. (bei zentrisch geschliffenem Walzenballen) der ihm propor­tionale Walzenspalt in zuverlässiger Weise gemessen oder mit Hilfe einer Regeleinrichtung - bestehend aus Soll/Ist­wert-Vergleicher 167, 168 und Servoventil 130 - geregelt werden; siehe Fig. 7. Für weniger hohe Ansprüche an die Schichtdickengenauigkeit lässt sich - wie in Fig. 4 ange­deutet - eine ventilfreie, mit Hilfe einer Regelpumpe 138 praktizierte Stellkraftregelung anwenden.
Eine präzisere Stellkraftregelung wird sich indes eines ge­eigneten Servoventils 130, einer Druckmesseinrichtung 166 und eines Vergleichers 167, 168 bedienen, wie in den Fig.5 und 7 angedeutet ist.
Eine im übrigen meistens erforderliche mechanisch/elektri­sche (Null-) Kalibrierung des Walzenspaltes mit Hilfe der distanzbestimmenden Stützeinheit - deren Kennlinie (im Hooke'schen Bereich) im wesentlichen durch die Steifigkeit der Druckfederstäbe 143, 143′, 143˝ vorgegeben ist - lässt sich in einfacher Weise gemäss Anordnung nach Fig. 5 mit Hilfe einer feingängigen Justiereinrichtung 145 bewerkstelligen. Für eine betriebsmässige Walzenspaltregulierung sind in Fig.6 und 7 weitere Mess- und Regelelemente skizziert bzw.schema­tisch dargestellt. Während in Fig.7 dem Vergleicher 167 ein Sollwertgeber 168 zugeordnet ist, stehen als Istwertgeber drei alternative Aufnehmer zur Verfügung, nämlich je einer für eine Walzenabstandsmessung 161 und Stelldruckmessung 166 sowie als weitere Variante eine Stellkraftmessung mit Hilfe einer Kraftmessdose 147.
Wie aus Fig. 6 ersichtlich ist, stützen sich, im Fall einer Stellkraftregelung, die Druckfederstäbe 143 mittelbar mit Hilfe einer Zwischenplatte 146 über die Kraftmessdose 147 an der Stützlager-Halbschale 141′ ab.In Fig. 5 / 5a an embodiment of a compact bending moment-free actuator / support unit with an integrated displacement measuring device for a roll neck distance measurement and (alternatively) a pressure cell for a positioning force measurement is shown.
Compared to the four compression spring bars 143 used in the schematic diagram (Fig. 4 / 4a), a support system is designed and arranged as a statically determined 'tripod' in such a way that the individual compression spring bars 143, 143 ', 143˝ have the same specific support moments [= support distance from Center x spring stiffness]. Furthermore, the actuating piston 135 of the actuating cylinder block 134 is hollow and takes over two tasks, namely the actual one as an actuator and a second one for guiding a displacement measuring device 161, 162, 163, 164, 165. One in the piston 135 is free and independent of its actuating direction with the help of a longitudinal bearing 139 embedded and guided path sensor 161 in a tappet housing 162 is supported by means of a compression spring 163 and stops 164, 165 on the support bearing half-shells 151, 151 'which are supported on the roller journals without play.
Thanks to such a measuring arrangement, the roll spacing or (in the case of a centrically ground roll roll) the roll gap which is proportional to it can be measured in a reliable manner or controlled with the aid of a control device - comprising a set / actual value comparator 167, 168 and a servo valve 130; see Fig. 7. For less stringent layer thickness accuracy requirements, as indicated in Fig. 4, a valve-free actuating force control practiced with the aid of a regulating pump 138 can be used.
A more precise actuating force control will, however, use a suitable servo valve 130, a pressure measuring device 166 and a comparator 167, 168, as indicated in FIGS. 5 and 7.
An otherwise usually required mechanical / electrical (zero) calibration of the nip with the aid of the distance-determining support unit - whose characteristic (in Hooke's area) is essentially determined by the rigidity of the compression spring bars 143, 143 ', 143' - can be in 5 in a simple manner according to the arrangement according to FIG. 5 with the aid of a fine adjustment device 145. For operational roll gap regulation, further measuring and control elements are sketched or schematically shown in Fig. 6 and 7. While a comparator 167 is assigned a comparator 167 in FIG. 7, three alternative sensors are available as actual sensors, namely one each for a roller distance measurement 161 and signal pressure measurement 166 and, as a further variant, an actuating force measurement with the aid of a load cell 147.
As can be seen from Fig. 6, in the case of actuating force control, the compression spring bars 143 are supported indirectly by means of an intermediate plate 146 via the load cell 147 on the support bearing half-shell 141 '.

Claims (8)

1. Walzenspalteinstellvorrichtung eines Walzengerüstes mit auf den Walzenzapfen (121, 122) gelagerten, gegen­einander wirkenden Walzenstell- und Stützelementen auf jeder Walzenseite, dadurch gekennzeichnet, dass die Stellelemente (133, 134, 135, 136, 133′) sich zwischen - bezogen auf den Walzenspalt - aussenliegenden Stell­lager-Halbschalen (131, 131′) und die Stützelemente 143 sich zwischen innenliegende Stützlager-Halbschalen 141, 141′) der Walzenzapfen (121, 122) jeder Walzenseite derart abstützen und geführt sind, dass die erzeugten Stell- und Stützkräfte in der selben, zu den Achsen der Walzen (101, 102) rechtwinkligen Ebene (y-y) wirken.1. nip setting device of a roll stand with on the roll neck (121, 122) mounted, counteracting roll setting and supporting elements on each roll side, characterized in that the control elements (133, 134, 135, 136, 133 ') between - based on the Roll nip - outer positioning bearing half-shells (131, 131 ') and the support elements 143 between the inner supporting bearing half-shells 141, 141') of the roller journals (121, 122) of each roller side are supported and guided in such a way that the actuating and supporting forces generated in the same plane (yy) acting at right angles to the axes of the rollers (101, 102). 2. Walzenspalteinstellvorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass drei auf die zentrische Stellachse (s-s) bezogenen Stützelemente (143, 143′ 143˝) die glei­chen spezifischen Stützmomente [ = Stützabstand x Feder­steife] aufweisen.2. nip setting device according to claim 1, characterized in that three on the central adjusting axis (s-s) related support elements (143, 143 '143˝) have the same specific support moments [= support distance x spring stiffness]. 3. Walzenspalteinstellvorrichtung nach Ansprüchen 1 oder 2, dadurch gekennzeichnet, dass die Kraft/Weg-Kennlinie mindestens eines der federnden Stützelemente (143) mit Hilfe einer Justiereinrichtung (145) einstellbar ist.3. nip setting device according to claims 1 or 2, characterized in that the force / displacement characteristic of at least one of the resilient support elements (143) is adjustable with the aid of an adjusting device (145). 4. Walzenspalteinstellvorrichtung nach den Ansprüchen 1, 2 oder 3, dadurch gekennzeichnet, dass die Stützelemen­te (143, 143′, 143˝) durch Längsführungen (144) in dem Stellelement (134) gehalten und geführt sind.4. nip setting device according to claims 1, 2 or 3, characterized in that the supporting elements (143, 143 ', 143˝) are held and guided by longitudinal guides (144) in the adjusting element (134). 5. Walzenspalteinstellvorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Stellkraft eines Stellzylin­ders (134, 135) durch eine Pumpe (138) mit einstellba­rem Förderdruck erzeugt wird.5. nip setting device according to claim 1, characterized in that the actuating force of an actuating cylinder (134, 135) is generated by a pump (138) with adjustable delivery pressure. 6. Walzenspalteinstellvorrichtung nach einem der Ansprü­che 1 bis 5, dadurch gekennzeichnet, dass mittels eines rohrförmigen Stellkolbens (135) und eines Längslagers (139) eine axial frei beweglich geführte Wegmessein­richtung, bestehend aus Stösselgehäuse (162), Druckfe­der (163) und Wegmessgerät (161), mit Hilfe von An­schlägen (164, 165) an den Stützlager-Halbschalen (151, 151′) abgestützt ist.6. nip setting device according to one of claims 1 to 5, characterized in that by means of a tubular adjusting piston (135) and a longitudinal bearing (139) an axially freely guided displacement measuring device, consisting of plunger housing (162), compression spring (163) and displacement measuring device (161 ), with the help of stops (164, 165) on the support bearing half-shells (151, 151 ') is supported. 7. Walzenspalteinstellvorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Stelldruck eines Stellzylinders (134, 135) mit Hilfe eines Druck­aufnehmers (166) gemessen und mittels einer Regelein­richtung (167, 168, 130) geregelt ist.7. nip setting device according to one of claims 1 to 5, characterized in that the signal pressure of an actuating cylinder (134, 135) is measured with the aid of a pressure sensor (166) and is regulated by means of a regulating device (167, 168, 130). 8. Walzenspalteinstellvorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Stützkraft der Stützelemente (143) mit Hilfe einer zwischen einer Stützplatte (146) und einer Stützlager-Halbschale (141′) angeordneten Kraftmessdose (147) gemessen und unter Mitwirkung eines Reglers (167, 168) und eines Regelven­tils (130) eingestellt wird.8. nip setting device according to one of claims 1 to 5, characterized in that the supporting force of the support elements (143) with the aid of a between a support plate (146) and a support bearing half-shell (141 ') arranged load cell (147) measured and with the participation of a Regulator (167, 168) and a control valve (130) is set.
EP89108175A 1988-07-16 1989-05-05 Device for adjusting the interstice between rollers Expired - Lifetime EP0351507B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2689/88A CH672082A5 (en) 1988-07-16 1988-07-16
CH2689/88 1988-07-16

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EP0351507A2 true EP0351507A2 (en) 1990-01-24
EP0351507A3 EP0351507A3 (en) 1990-12-27
EP0351507B1 EP0351507B1 (en) 1994-06-22

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EP (1) EP0351507B1 (en)
CH (1) CH672082A5 (en)
DE (1) DE58907933D1 (en)

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Also Published As

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CH672082A5 (en) 1989-10-31
US5022318A (en) 1991-06-11
EP0351507B1 (en) 1994-06-22
DE58907933D1 (en) 1994-07-28
EP0351507A3 (en) 1990-12-27

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