EP0343440B1 - Rolling mill roll with a ring mounted on a roll shaft - Google Patents

Rolling mill roll with a ring mounted on a roll shaft Download PDF

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Publication number
EP0343440B1
EP0343440B1 EP89108513A EP89108513A EP0343440B1 EP 0343440 B1 EP0343440 B1 EP 0343440B1 EP 89108513 A EP89108513 A EP 89108513A EP 89108513 A EP89108513 A EP 89108513A EP 0343440 B1 EP0343440 B1 EP 0343440B1
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European Patent Office
Prior art keywords
ring
rolling
shaft
retaining
clamping
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EP89108513A
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German (de)
French (fr)
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EP0343440A1 (en
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Uwe Kark
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02—Shape or construction of rolls
    • B21B27/03—Sleeved rolls
    • B21B27/035—Rolls for bars, rods, rounds, tubes, wire or the like
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B2013/006—Multiple strand rolling mills; Mill stands with multiple caliber rolls

Definitions

  • the invention relates to a rolling device with a shaft, a rolling ring arranged on the shaft and an arrangement for securing a constant operating position of the rolling ring on the shaft.
  • a rolling device according to the preamble of claim 1 is already known from US-A-4117705.
  • the rolling ring is partly clamped radially via a conical sleeve and partly axially via a strong ring spring by means of a nut provided on a thread of the shaft.
  • the nut acts on a ring arranged between the conical sleeve and the spring, which can also be preloaded by a hydraulic force tensioning device which sits on the shaft thread on the side of the nut facing away from the rolling ring and whose force is applied to the ring radially outside the nut by means of a sleeve must be transferred.
  • This arrangement is expensive and bulky in the axial direction.
  • it is disadvantageous to use a nut the load-bearing number of thread turns is known to be limited, as an adjustable clamping element.
  • a threaded nut is also used for tensioning the rolling ring.
  • a hydraulic tensioning device is used to generate a hydraulic prestressing force, which has to be installed separately and comprises a tensioning sleeve surrounding the rolling ring.
  • This arrangement has the disadvantage that the hydraulic tensioning device is complex and cumbersome to use.
  • the clamping sleeve covers the outside of the rolling ring and therefore an optical control of the rolling ring is not possible during the clamping process.
  • it can only be used with overhung roller ring assemblies.
  • there are also the problems caused by the use of a threaded nut as a ring stop namely the fact that the load-bearing number of thread turns is limited.
  • the width of the compensation ring must be less than the width of the gap, because otherwise the compensation ring would not be mountable; moreover, compensation rings cannot be used continuously different axial dimensions are kept in stock. Therefore, the achievable axial operating clamping force is always considerably lower than in the case of devices which allow the clamping state achieved by the hydraulic clamping force to be infinitely fixed.
  • the invention relates to the known type of rolling device in which the securing of a constant operating position of the rolling ring on the shaft takes place essentially by means of an axial operating clamping force and in which the arrangement essentially comprises: two retaining rings axially fixed to the shaft on both sides of the rolling ring ; a hydraulic power clamping device for transferring the rolling device from the unclamped state into a preliminary clamping position in which the rolling ring is supported on the end face on one of the two retaining rings; a receiving space for a compensating ring between the other of the two retaining rings and the rolling ring; a compensation ring in the receiving space, which can be brought into the operating position in the provisional clamping position of the arrangement, in which its axial dimension is greater than the axial dimension of the receiving space in the untensioned state, such that the operating clamping force between the two after releasing the hydraulic force clamping device Retaining rings is transferred via the roller ring and the compensation ring in the operating position.
  • the object on which the invention is based is to improve this rolling device with regard to the space requirement, the manufacturing and operating effort and the clamping security.
  • the solution according to the invention is that, starting from a device according to the preamble of claim 1, the compensating ring and a ring adjacent to it can be rotated relative to one another and on their end faces with sawtooth-shaped, distributed over the circumference, complementary inclined surfaces with less in relation to the circumferential direction, far below the slope of the self-locking limit.
  • a rolling ring arrangement which comprises two rolling rings, the spacing of which is adjustable, for rolling H-shaped steel profiles.
  • They On the mutually facing end faces, they have sawtooth-shaped inclined surfaces distributed over the circumference, which interact with complementary inclined surfaces of an adjusting ring arranged between them.
  • This can be rotated by means of a hydraulic motor contained in the arrangement, as a result of which the roller rings are either pushed apart axially or are given the possibility of mutual approximation under the influence of a further hydraulic drive.
  • the slope of the inclined surfaces is relatively large and presumably not below the self-locking limit. This is possible because they are not intended to maintain the operating position of the roller rings.
  • conical sleeves are provided between the clamping rings and the shaft, which are tensioned by a spring in order to ensure the operational connection between the shaft and the rolling rings, and can be released by a hydraulic drive if the rolling rings are to be adjusted relative to one another.
  • This document does not contain the teaching that the operating clamping force for rolling rings can be generated under the very special design requirements of the invention by a ring with inclined faces at the end.
  • the one retaining ring which can be formed by a threaded nut on a shaft thread, is first set against the rolling ring as far as possible and without play, the complementary sawtooth surfaces of the retaining ring and the compensation ring are in deepest engagement.
  • the roll ring arrangement is then put under tension by the hydraulic power tensioning device. This loosens the mutual contact of the rings and creates axial play. Now the compensation ring is turned relative to the retaining ring until the axial play has disappeared. Then the hydraulic tension can be released.
  • the arrangement is extremely simple because the hydraulic power clamping device can be contained on or in the one retaining ring, expediently radially inside the compensating ring, so that it is easily accessible from the outside and without the need for a surrounding force-transmitting sleeve. Since the power clamping device is integrated in the adjustable retaining ring, the axial space requirement is small. In contrast to a nut, which must be relatively large for a given load, the compensating ring can transmit high axial forces even with small dimensions, because the entire contact surface of the complementary inclined surfaces can be regarded as load-bearing.
  • the shaft-fixed designed as a nut retaining ring with a view to the power transmission via the thread on the shaft must have a considerable cross-sectional dimension, not only the hydraulic power clamping device, but also the compensating ring can be accommodated in its cross section, which further reduces the space requirement and the arrangement is simplified.
  • the force clamping device and the compensating ring can then act parallel to one another on one and the same ring adjacent to the retaining ring, preferably even on the same end face of this ring.
  • the device according to the invention allows the transmission of unusually large axial forces, it is particularly suitable for arrangements in which the rolling ring or the Roll rings are predominantly or even axially clamped.
  • the application of the invention can be used both in the case of roll stands mounted on both sides of the roll ring and in the case of overhung use.
  • the invention is also applicable not only to rolling devices, but simply when in a clamping arrangement consisting of a bolt, an abutment connected to the bolt and a retaining ring, any parts located between the abutment and the retaining ring, preferably surrounding the bolt in an axial manner Direction must be set under compressive stress, whereby the bolt is stretched.
  • a tensioning arrangement according to the preamble of claim 4 is known from US-A-4117705.
  • the shaft 1 forms or carries a shaft-fixed collar 2 which, as a retaining ring on one side of the rolling ring, forms an abutment for the rolling ring tension and can be formed in one piece with the shaft, but need not be.
  • the roller rings 3 are mounted on the shaft 1 with intermediate rings 4 and centered either directly on the shaft circumference or by further means, not shown.
  • the shaft is provided with a thread 5 on which a nut 6 sits, which forms the other retaining ring.
  • a thread 5 on which a nut 6 sits, which forms the other retaining ring.
  • roller rings 3 are clamped axially between the retaining rings 2 and 6.
  • the nut 6 contains an annular piston 7, which can be acted upon via lines 8 with hydraulic medium.
  • the nut 6 contains on the outside and on its end facing the rolling ring arrangement 3, 4 a recess 9, which forms the receiving space for the compensating ring 10.
  • Both the hydraulic power tensioning device 7 and the compensating ring are thus accommodated in a space-saving manner in the longitudinal sectional area of the nut 6.
  • the shape of the elements involved, in particular also of the adjacent intermediate ring 4, on which the force clamping device and the compensating ring act, is very simple.
  • the cooperating end faces 11 of the nut 6 and the compensating ring 10 are, as can be seen in the lower half of the figure, sawtooth-shaped with a very low slope.
  • the slope of the flank must be very low, i.e. are very far below the self-locking limit, so that the clamping arrangement cannot be loosened by rotating forces acting on the roller ring. In extreme cases, it may be appropriate to choose the direction of the slope so that the axial tension is increased when the compensating ring 10 is rotated relative to the ring 6 by the drive torque.
  • the compensating ring is first rotated as far as possible so that the sawtooth surfaces 11 are in deepest engagement and the common axial length of the compensating ring 10 and the retaining ring 6 is minimal. Then the nut 6 is screwed on as tightly as possible, so that only a slight axial compression of the rolling ring arrangement 3, 4 is to be expected when the force clamping device is activated. If the annular piston 7 is then acted upon by hydraulic fluid, the rolling ring arrangement 3, 4 is pressed further together and the shaft is stretched. This loosens the arrangement and creates axial play.
  • the compensation ring 10 is rotated so that the Clearance is eliminated, whereby the tension state of the rolling ring arrangement remains fixed and the operating tension force is maintained even after the power tensioning device is released.
  • the proportion of the area in which the sawtooth flanks 11 of the compensating ring 10 and the nut 6 interact is reduced; however, these can easily be dimensioned so that they are still sufficient even after adjusting the compensating ring.
  • the design of these flanks of any size allows the transmission of any large axial forces evenly over the circumference. It goes without saying that the sawtooth surfaces 11 could also be provided between the compensating ring 10 and the intermediate ring 4 instead of between the compensating ring 10 and the retaining ring 6.

Abstract

A roll device is made with roll rings clamped axially between a shaft collar and an adjustable ring stop. The ring stop comprises a ring which is fixed to the shaft and which can be designed, for example, as a threaded nut, and an adjusting ring. The ring fixed to the shaft and the adjusting ring interact via sawtooth-shaped end faces.

Description

Die Erfindung bezieht sich auf eine Walzvorrichtung mit einer Welle, einem auf der Welle angeordneten Walzring und einer Anordnung zum Sichern einer gleichbleibenden Betriebsstellung des Walzrings auf der Welle. Eine Walzvorrichtung nach dem Oberbegriff des Anspruch 1 ist bereits aus der US-A-4117705 bekannt.The invention relates to a rolling device with a shaft, a rolling ring arranged on the shaft and an arrangement for securing a constant operating position of the rolling ring on the shaft. A rolling device according to the preamble of claim 1 is already known from US-A-4117705.

Es ist bekannt, Walzringe (insbesondere solche aus Hartmetall) kraftschlüssig durch eine radial und/oder axial wirkende Betriebsspannkraft derart festzuklemmen, daß eine gleichbleibende Betriebsstellung gewährleistet ist.It is known to clamp rolling rings (in particular those made of hard metal) in a force-locking manner by means of a radially and / or axially acting operating clamping force in such a way that a constant operating position is ensured.

Bei einer bekannten Walzvorrichtung (US-A-4208147, Fig. 2) wird der Walzring teils radial über eine Konushülse und teils axial über eine starke Ringfeder mittels einer auf einem Gewinde der Welle vorgesehenen Mutter gespannt. Die Mutter wirkt auf einen zwischen der Konushülse und der Feder angeordneten Ring, der außerdem von einer hydraulischen Kraftspanneinrichtung vorgespannt werden kann, die auf der dem Walzring abgewandten Seite der Mutter auf dem Wellengewinde sitzt und deren Kraft mittels einer Hülse radial außerhalb der Mutter auf den Ring übertragen werden muß. Diese Anordnung ist aufwendig und in Axialrichtung platzraubend. Außerdem ist es nachteilig, eine Mutter, deren tragende Zahl von Gewindewindungen bekanntlich begrenzt ist, als verstellbares Spannelement zu verwenden.In a known rolling device (US-A-4208147, FIG. 2), the rolling ring is partly clamped radially via a conical sleeve and partly axially via a strong ring spring by means of a nut provided on a thread of the shaft. The nut acts on a ring arranged between the conical sleeve and the spring, which can also be preloaded by a hydraulic force tensioning device which sits on the shaft thread on the side of the nut facing away from the rolling ring and whose force is applied to the ring radially outside the nut by means of a sleeve must be transferred. This arrangement is expensive and bulky in the axial direction. In addition, it is disadvantageous to use a nut, the load-bearing number of thread turns is known to be limited, as an adjustable clamping element.

Bei einer anderen bekannten Walzvorrichtung (DE-A-1948424) wird gleichfalls eine Gewindemutter zum Spannen des Walzrings verwendet. Zum Erzeugen einer hydraulischen Vorspannkraft wird eine hydraulische Spannvorrichtung benutzt, die gesondert montiert werden muß und eine den Walzring umgebende Spannhülse umfaßt. Diese Anordnung hat den Nachteil, daß die hydraulische Spannvorrichtung aufwendig und in der Benutzung umständlich ist. Ferner hat sie den Nachteil, daß die Spannhülse den Walzring außen abdeckt und daher eine optische Kontrolle des Walzrings während des Spannvorgangs nicht möglich ist. Außerdem kann sie nur bei fliegend gelagerten Walzringanordnungen verwendet werden. Hinzu kommen auch hier die Probleme, die durch die Verwendung einer Gewindemutter als Ringanschlag begründet sind, nämlich die Tatsache, daß die tragende Zahl von Gewindewindungen begrenzt ist.In another known rolling device (DE-A-1948424) a threaded nut is also used for tensioning the rolling ring. A hydraulic tensioning device is used to generate a hydraulic prestressing force, which has to be installed separately and comprises a tensioning sleeve surrounding the rolling ring. This arrangement has the disadvantage that the hydraulic tensioning device is complex and cumbersome to use. Furthermore, it has the disadvantage that the clamping sleeve covers the outside of the rolling ring and therefore an optical control of the rolling ring is not possible during the clamping process. In addition, it can only be used with overhung roller ring assemblies. In addition, there are also the problems caused by the use of a threaded nut as a ring stop, namely the fact that the load-bearing number of thread turns is limited.

Der Nachteil, der in der Verwendung einer Mutter als Spannelement liegt, wird bei einer weiteren bekannten Walzringanordnung vermieden (US-A-4117705; Ztschr. "Iron and Steel Engineer", Spt. 1978 S. 39-43), bei der ein wellenfester Haltering mit einem hydraulischen Ringkolben zusammenwirkt, durch dessen axiale Spannkraft ein Ringspalt zwischen der Walzringanordnung und dem Haltering erzeugt wird, der durch Einfügen eines Ausgleichsrings geschlossen wird. Dadurch soll der durch die hydraulische Spannkraft erreichte Spannzustand der Walzringanordnung nach Beendigung des hydraulischen Drucks als Betriesspannkraft fixiert werden. Dieses Ergebnis läßt sich aber nur dann erreichen, wenn die axiale Breite des Ausgleichsrings genau der Weite des Spalts gleicht. In der Praxis muß jedoch die Breite des Ausgleichsrings geringer sein als die Weite des Spalts, weil der Ausgleichsring sonst nicht montierbar wäre; außerdem können Ausgleichsringe nicht mit stufenlos unterschiedlichen axialen Abmessungen vorrätig gehalten werden. Daher ist die erzielbare axiale Betriebsspannkraft stets beträchtlich geringer als bei solchen Vorrichtungen, die eine stufenlose Fixierung des durch die hydraulische Spannkraft erreichten Spannzustands erlauben.The disadvantage that lies in the use of a nut as a clamping element is avoided in a further known rolling ring arrangement (US-A-4117705; Zschr. "Iron and Steel Engineer", Spt. 1978 pp. 39-43), in which a shaft-fixed Retaining ring cooperates with a hydraulic ring piston, an axial gap between the roller ring assembly and the retaining ring is generated by the axial clamping force, which is closed by inserting a compensating ring. This is intended to fix the clamping state of the rolling ring arrangement achieved by the hydraulic clamping force as the operating clamping force after the hydraulic pressure has ended. However, this result can only be achieved if the axial width of the compensating ring exactly matches the width of the gap. In practice, however, the width of the compensation ring must be less than the width of the gap, because otherwise the compensation ring would not be mountable; moreover, compensation rings cannot be used continuously different axial dimensions are kept in stock. Therefore, the achievable axial operating clamping force is always considerably lower than in the case of devices which allow the clamping state achieved by the hydraulic clamping force to be infinitely fixed.

Bei wieder einer anderen Walzvorrichtung (US-A-4008598) ist ausschließlich eine hydraulische Spannvorrichtung zur Fixierung der Walzringe vorgesehen. Dafür ist es erforderlich, den Hydraulikdruck auch im Betriebszustand aufrechtzuerhalten, was nicht mit der erforderlichen Sicherheit möglich ist.In yet another rolling device (US-A-4008598) only a hydraulic tensioning device is provided for fixing the rolling rings. This requires maintaining the hydraulic pressure even in the operating state, which is not possible with the necessary security.

Die Erfindung bezieht sich auf den bekannten Typ einer Walzvorrichtung, bei der die Sicherung einer gleichbleibenden Betriebsstellung des Walzrings auf der Welle im wesentlichen durch eine axiale Betriebsspannkraft erfolgt und in welcher die Anordnung im wesentlichen umfaßt: zwei beiderseits des Walzrings axial fest mit der Welle verbundene Halteringe; eine hydraulische Kraftspannvorrichtung zum Überführen der Walzvorrichtung aus dem ungespannten Zustand in eine vorläufige Spannstellung, in der der Walzring sich stirnseitig an dem einen der beiden Halteringe abstützt; einen Aufnahmeraum für einen Ausgleichsring zwischen dem anderen der beiden Halteringe und dem Walzring; einen Ausgleichsring in dem Aufnahmeraum, der in der vorläufigen Spannstellung der Anordnung in eine Betriebsstellung bringbar ist, in der seine axiale Abmessung größer ist als die axiale Abmessung des Aufnahmeraums im ungespannten Zustand, derart, daß nach dem Lösen der hydraulischen Kraftspanneinrichtung die Betriebsspannkraft zwischen den beiden Halteringen über den Walzring und den in Betriebsstellung befindlichen Ausgleichsring übertragen wird.The invention relates to the known type of rolling device in which the securing of a constant operating position of the rolling ring on the shaft takes place essentially by means of an axial operating clamping force and in which the arrangement essentially comprises: two retaining rings axially fixed to the shaft on both sides of the rolling ring ; a hydraulic power clamping device for transferring the rolling device from the unclamped state into a preliminary clamping position in which the rolling ring is supported on the end face on one of the two retaining rings; a receiving space for a compensating ring between the other of the two retaining rings and the rolling ring; a compensation ring in the receiving space, which can be brought into the operating position in the provisional clamping position of the arrangement, in which its axial dimension is greater than the axial dimension of the receiving space in the untensioned state, such that the operating clamping force between the two after releasing the hydraulic force clamping device Retaining rings is transferred via the roller ring and the compensation ring in the operating position.

Die der Erfindung zugrundeliegende Aufgabe besteht darin, diese Walzvorrichtung hinsichtlich des Platzbedarf, des Herstellungs- und Bedienungsaufwands und der Spannsicherheit zu verbessern.The object on which the invention is based is to improve this rolling device with regard to the space requirement, the manufacturing and operating effort and the clamping security.

Die erfindungsgemäße Lösung besteht darin, daß ausgehend von einer Vorrichtung nach dem oberbegriff des Anspruchs 1 der Ausgleichsring und ein ihm benachbarter Ring relativ zueinander verdrehbar sind und an ihren Stirnflächen mit sägezahnförmigen, über den Umfang verteilten, komplementären Schrägflächen mit gegenüber der Umfangsrichtung geringer, weit unter der Selbsthemmungsgrenze liegender Steigung zusammenwirken.The solution according to the invention is that, starting from a device according to the preamble of claim 1, the compensating ring and a ring adjacent to it can be rotated relative to one another and on their end faces with sawtooth-shaped, distributed over the circumference, complementary inclined surfaces with less in relation to the circumferential direction, far below the slope of the self-locking limit.

In diesem Zusammenhang sei erwähnt, daß eine Walzringanordnung bekannt ist (JP-A-60-127010), die zum Walzen von H-förmigen Stahlprofilen zwei Walzringe umfaßt, deren Abstand voneinander verstellbar ist. Auf den einander zugewendeten Stirnseiten weisen sie sägezahnförmige, über den Umfang verteilte Schrägflächen auf, die mit komplementären Schrägflächen eines zwischen ihnen angeordneten Verstellrings zusammenwirken. Dieser ist mittels eines in der Anordnung enthaltenen hydraulischen Motors verdrehbar, wodurch die Walzringe entweder axial auseinandergeschoben werden oder ihnen die Möglichkeit zu gegenseitiger Näherung unter dem Einfluß eines weiteren hydraulischen Antriebs gegeben wird. Die Steigung der Schrägflächen ist verhältnismäßig groß und vermutlich nicht unter der Selbsthemmungsgrenze. Dies ist möglich, weil sie nicht dazu vorgesehen sind, die Aufrechterhaltung der Betriebsstellung der Walzringe zu gewährleisten. Dazu sind vielmehr Konushülsen zwischen den Spannringen und der Welle vorgesehen, die durch eine Feder gespannt sind, um die Betriebsverbindung zwischen der Welle und den Walzringen zu gewährleisten, und durch einen hydraulischen Antrieb gelöst werden können, wenn die Walzringe gegeneinander verstellt werden sollen. Dieser Schrift läßt sich nicht die Lehre entnehmen, daß die Betriebsspannkraft für Walzringe unter den sehr speziellen konstruktiven Voraussetzungen der Erfindung durch einen Ring mit stirnseitigen Schrägflächen erzeugt werden kann.In this context, it should be mentioned that a rolling ring arrangement is known (JP-A-60-127010) which comprises two rolling rings, the spacing of which is adjustable, for rolling H-shaped steel profiles. On the mutually facing end faces, they have sawtooth-shaped inclined surfaces distributed over the circumference, which interact with complementary inclined surfaces of an adjusting ring arranged between them. This can be rotated by means of a hydraulic motor contained in the arrangement, as a result of which the roller rings are either pushed apart axially or are given the possibility of mutual approximation under the influence of a further hydraulic drive. The slope of the inclined surfaces is relatively large and presumably not below the self-locking limit. This is possible because they are not intended to maintain the operating position of the roller rings. Rather, conical sleeves are provided between the clamping rings and the shaft, which are tensioned by a spring in order to ensure the operational connection between the shaft and the rolling rings, and can be released by a hydraulic drive if the rolling rings are to be adjusted relative to one another. This document does not contain the teaching that the operating clamping force for rolling rings can be generated under the very special design requirements of the invention by a ring with inclined faces at the end.

Beim Spannen des Walzrings bzw. der Walzringe wird zunächst der eine Haltering, der von einer Gewindemutter auf einem Wellengewinde gebildet sein kann, so weit wie möglich und spielfrei gegen den Walzring angestellt, wobei sich die komplementären Sägezahnflächen des Halterings und des Ausgleichsrings in tiefstem Eingriff befinden. Sodann wird die Walzringanordnung durch die hydraulische Kraftspanneinrichtung unter Spannung gesetzt. Dabei lockert sich die gegenseitige Anlage der Ringe und es entsteht axiales Spiel. Nun wird der Ausgleichsring gegenüber dem Haltering verdreht, bis das axiale Spiel verschwunden ist. Danach kann die hydraulische Spannung gelöst werden.When tensioning the rolling ring or the rolling rings, the one retaining ring, which can be formed by a threaded nut on a shaft thread, is first set against the rolling ring as far as possible and without play, the complementary sawtooth surfaces of the retaining ring and the compensation ring are in deepest engagement. The roll ring arrangement is then put under tension by the hydraulic power tensioning device. This loosens the mutual contact of the rings and creates axial play. Now the compensation ring is turned relative to the retaining ring until the axial play has disappeared. Then the hydraulic tension can be released.

Die Anordnung ist höchst einfach, weil die hydraulische Kraftspanneinrichtung an oder in dem einen Haltering enthalten sein kann, und zwar zweckmäßigerweise radial innerhalb des Ausgleichsrings, so daß dieser von außen ohne weiteres und ohne die Notwendigkeit einer ihn umgebenden, kraftübertragenden Hülse zugänglich ist. Da dabei die Kraftspanneinrichtung in den verstellbaren Haltering integriert ist, ist der axiale Platzbedarf gering. Im Gegensatz zu einer Mutter, die bei einer gegebenen Belastung verhältnismäßig groß sein muß, kann der Ausgleichsring hohe Axialkräfte auch bei geringen Abmessungen übertragen, weil die gesamte Anlagefläche der komplementären Schrägflächen als tragend betrachtet werden kann.The arrangement is extremely simple because the hydraulic power clamping device can be contained on or in the one retaining ring, expediently radially inside the compensating ring, so that it is easily accessible from the outside and without the need for a surrounding force-transmitting sleeve. Since the power clamping device is integrated in the adjustable retaining ring, the axial space requirement is small. In contrast to a nut, which must be relatively large for a given load, the compensating ring can transmit high axial forces even with small dimensions, because the entire contact surface of the complementary inclined surfaces can be regarded as load-bearing.

Da der wellenfeste, als Mutter ausgebildete Haltering mit Rücksicht auf die Kraftübertragung über das Gewinde auf die Welle eine beträchtliche Querschnittsausdehnung haben muß, kann nicht nur die hydraulische Kraftspanneinrichtung, sondern auch der Ausgleichsring in ihrem Querschnitt untergebracht werden, wodurch der Raumbedarf weiter verringert und die Anordnung vereinfacht wird. Die Kraftspanneinrichtung und der Ausgleichsring können dann parallel zueinander auf ein und denselben, dem Haltering benachbarten Ring, vorzugsweise sogar auf dieselbe Stirnfläche dieses Rings, einwirken.Since the shaft-fixed, designed as a nut retaining ring with a view to the power transmission via the thread on the shaft must have a considerable cross-sectional dimension, not only the hydraulic power clamping device, but also the compensating ring can be accommodated in its cross section, which further reduces the space requirement and the arrangement is simplified. The force clamping device and the compensating ring can then act parallel to one another on one and the same ring adjacent to the retaining ring, preferably even on the same end face of this ring.

Da die erfindungsgemäße Vorrichtung die Übertragung ungewöhnlich großer Axialkräfte gestattet, ist sie insbesondere für solche Anordnungen geeignet, bei denen der Walzring bzw. die Walzringe überwiegend oder gar ausschließlich axial gespannt werden.Since the device according to the invention allows the transmission of unusually large axial forces, it is particularly suitable for arrangements in which the rolling ring or the Roll rings are predominantly or even axially clamped.

Die Anwendung der Erfindung kann sowohl bei beidseitig vom Walzring gelagerten Walzgerüsten als auch bei fliegend gelagerten Verwendung finden.The application of the invention can be used both in the case of roll stands mounted on both sides of the roll ring and in the case of overhung use.

Die Erfindung ist ferner nicht nur bei Walzvorrichtungen anwendbar, sondern schlechthin dann, wenn in einer Spannanordnung, bestehend aus einem Bolzen, einem mit dem Bolzen verbundenen Widerlager und einem Haltering irgendwelche zwischen dem Widerlager und dem Haltering befindliche, vorzugsweise den Bolzen ringförmig umgebende Teile in axialer Richtung unter Druckspannung zu setzen sind, wobei der Bolzen gedehnt wird. Eine Spannanordnung gemäß dem Oberbegriff des Anspruchs 4 ist aus der US-A-4117705 bekannt.The invention is also applicable not only to rolling devices, but simply when in a clamping arrangement consisting of a bolt, an abutment connected to the bolt and a retaining ring, any parts located between the abutment and the retaining ring, preferably surrounding the bolt in an axial manner Direction must be set under compressive stress, whereby the bolt is stretched. A tensioning arrangement according to the preamble of claim 4 is known from US-A-4117705.

Die Erfindung wird im folgenden näher unter Bezugnahme auf die Zeichnung erläutert, die ein vorteilhaftes Ausführungsbeispiel in einer Figur veranschaulicht, die in der oberen Hälfte einen Längsschnitt und in der unteren Hälfte eine Seitenansicht zeigt.The invention is explained in more detail below with reference to the drawing which illustrates an advantageous embodiment in a figure which shows a longitudinal section in the upper half and a side view in the lower half.

Die Welle 1 bildet oder trägt einen wellenfesten Bund 2, der als Haltering auf einer Seite des Walzrings ein Widerlager für die Walzringspannung bildet und einstückig mit der Welle ausgebildet sein kann aber nicht sein muß. Auf die Welle 1 sind die Walzringe 3 mit Zwischenringen 4 aufgezogen und entweder direkt auf dem Wellenumfang oder durch weitere, nicht dargestellte Mittel zentriert.The shaft 1 forms or carries a shaft-fixed collar 2 which, as a retaining ring on one side of the rolling ring, forms an abutment for the rolling ring tension and can be formed in one piece with the shaft, but need not be. The roller rings 3 are mounted on the shaft 1 with intermediate rings 4 and centered either directly on the shaft circumference or by further means, not shown.

Jenseits ihres die Walzringe 3 tragenden Abschnitts ist die Welle mit einem Gewinde 5 versehen, auf dem eine Mutter 6 sitzt, die den anderen Haltering bildet. Obwohl sie verstellbar und lösbar ist, ist sie im erfindungsgemäßen Zusammenhang insofern axial fest mit der Welle verbunden, als sie während und nach der hydraulischen Vorspannung nicht verstellt wird.Beyond its section carrying the roller rings 3, the shaft is provided with a thread 5 on which a nut 6 sits, which forms the other retaining ring. Although it is adjustable and detachable, it is axially fixed to the shaft in the context according to the invention insofar as it is not adjusted during and after the hydraulic preload.

Zwischen den Halteringen 2 und 6 werden die Walzringe 3 axial festgespannt.The roller rings 3 are clamped axially between the retaining rings 2 and 6.

Die Mutter 6 enthält einen Ringkolben 7, der über Leitungen 8 mit Hydraulikmedium beaufschlagt werden kann. Außerdem enthält die Mutter 6 außen und an ihrer der Walzringanordnung 3, 4 zugewandten Stirnseite eine Ausdrehung 9, die den Aufnahmeraum für den Ausgleichsring 10 bildet. Sowohl die hydraulische Kraftspanneinrichtung 7 als auch der Ausgleichsring sind somit platzsparend in der Längsschnittfläche der Mutter 6 untergebracht. Außerdem ist die Form der beteiligten Elemente, insbesondere auch des benachbarten Zwischenrings 4, auf den die Kraftspanneinrichtung und der Ausgleichsring einwirken, sehr einfach. Die zusammenwirkenden Stirnflächen 11 der Mutter 6 und des Ausgleichsrings 10 sind, wie in der unteren Hälfte der Figur zu erkennen ist, sägezahnförmig mit sehr geringer Flankenneigung ausgeführt. Die Flankenneigung muß sehr gering sein, d.h. sehr weit unter der Selbsthemmungsgrenze liegen, damit die Spannanordnung nicht durch drehend auf den Walzring einwirkende Kräfte gelockert werden kann. In extremen Fällen kann es zweckmäßig sein, die Richtung der Schrägung so zu wählen, daß die Axialspannung erhöht wird, wenn der Ausgleichsring 10 gegenüber dem Ring 6 durch das Antriebsdrehmoment verdreht wird.The nut 6 contains an annular piston 7, which can be acted upon via lines 8 with hydraulic medium. In addition, the nut 6 contains on the outside and on its end facing the rolling ring arrangement 3, 4 a recess 9, which forms the receiving space for the compensating ring 10. Both the hydraulic power tensioning device 7 and the compensating ring are thus accommodated in a space-saving manner in the longitudinal sectional area of the nut 6. In addition, the shape of the elements involved, in particular also of the adjacent intermediate ring 4, on which the force clamping device and the compensating ring act, is very simple. The cooperating end faces 11 of the nut 6 and the compensating ring 10 are, as can be seen in the lower half of the figure, sawtooth-shaped with a very low slope. The slope of the flank must be very low, i.e. are very far below the self-locking limit, so that the clamping arrangement cannot be loosened by rotating forces acting on the roller ring. In extreme cases, it may be appropriate to choose the direction of the slope so that the axial tension is increased when the compensating ring 10 is rotated relative to the ring 6 by the drive torque.

Zum axialen Spannen der Walzringanordnung 3, 4 wird zunächst der Ausgleichsring weitestmöglich so gedreht, daß sich die Sägezahnflächen 11 in tiefstem Eingriff befinden und die gemeinsame axiale Länge des Ausgleichsrings 10 und des Halterings 6 minimal ist. Dann wird die Mutter 6 möglichst fest angedreht, so daß nur noch eine geringe axiale Zusammenpressung der Walzringanordnung 3, 4 beim Tätigwerden der Kraftspanneinrichtung zu erwarten ist. Wenn danach der Ringkolben 7 von Druckflüssigkeit beaufschlagt ist, wird die Walzringanordnung 3, 4 weiter zusammengepreßt und die Welle gedehnt. Dadurch lockert sich die Anordnung und es entsteht axiales Spiel. Sodann wird der Ausgleichsring 10 so gedreht, daß das Spiel beseitigt wird, wodurch auch nach dem Lösen der Kraftspanneinrichtung der Spannzustand der Walzringanordnung fixiert bleibt und die Betriebsspannkraft erhalten bleibt. Zwar wird durch die Verstellung des Ausgleichsrings der Flächenanteil verringert, in welchem die Sägezahnflanken 11 des Ausgleichsrings 10 und der Mutter 6 zusammenwirken; jedoch können diese leicht so bemessen werden, daß sie auch nach dem Nachstellen des Ausgleichsrings noch ausreichen. Die beliebig großflächige Ausführung dieser Flanken erlaubt die Übertragung beliebig großer Axialkräfte gleichmäßig über den Umfang. Es versteht sich, daß die Sägezahnflächen 11 statt zwischen Ausgleichsring 10 und Haltering 6 auch zwischen Ausgleichsring 10 und Zwischenring 4 vorgesehen sein könnten.For axial tensioning of the roller ring arrangement 3, 4, the compensating ring is first rotated as far as possible so that the sawtooth surfaces 11 are in deepest engagement and the common axial length of the compensating ring 10 and the retaining ring 6 is minimal. Then the nut 6 is screwed on as tightly as possible, so that only a slight axial compression of the rolling ring arrangement 3, 4 is to be expected when the force clamping device is activated. If the annular piston 7 is then acted upon by hydraulic fluid, the rolling ring arrangement 3, 4 is pressed further together and the shaft is stretched. This loosens the arrangement and creates axial play. Then the compensation ring 10 is rotated so that the Clearance is eliminated, whereby the tension state of the rolling ring arrangement remains fixed and the operating tension force is maintained even after the power tensioning device is released. By adjusting the compensating ring, the proportion of the area in which the sawtooth flanks 11 of the compensating ring 10 and the nut 6 interact is reduced; however, these can easily be dimensioned so that they are still sufficient even after adjusting the compensating ring. The design of these flanks of any size allows the transmission of any large axial forces evenly over the circumference. It goes without saying that the sawtooth surfaces 11 could also be provided between the compensating ring 10 and the intermediate ring 4 instead of between the compensating ring 10 and the retaining ring 6.

Claims (4)

1. A rolling apparatus with a shaft (1), at least one rolling ring (3) mounted on the shaft and with an assembly for ensuring a constant operating position of the rolling ring (3) on the shaft (1) substantially by an axial operational clamping force, wherein said assembly comprises: two retaining rings (2, 6) connected axially securely to the shaft (1) on either side of the rolling ring (3); a hydraulic chucking means (7) for converting the rolling apparatus from an unclamped condition into a preliminary clamping position, in which the rolling ring (3) bears at the end face against one of the two retaining rings (2); a space for accommodating a spacer ring (10) between the other of the two retaining rings (6) and the rolling ring (3); a spacer ring in the accommodating space, which in the preliminary clamping position of the rolling ring assembly can be brought into an operating position in which its axial dimension is larger than the axial dimension of the accommodating space in the unclamped condition in such a way that, after the hydraulic chucking means has been released, the operational clamping force is transmitted between the two retaining rings (2, 6) via the rolling ring (3) and the spacer ring (10) situated in the operating position, characterised in that the spacer ring (10) and a ring (6) adjacent to it are rotatable relative to one another and at their end faces they interact along sawtooth-like complementary inclined surfaces (11) peripherally disposed with an inclination decreasing peripherally and considerably below the self-locking limit.
2. A rolling apparatus according to Claim 1, characterised in that the retaining ring (6) adjacent the spacer ring includes the hydraulic chucking means (7) and the outer diameter of the hydraulic chucking means (7) is not greater than the inner diameter of the spacer ring (10).
3. A rolling apparatus according to Claim 2, characterised in that the spacer ring (10) and the chucking means (7) act on the same ring (4) adjacent the associated retaining ring (6).
4. A clamping assembly, comprising a shaft (1), an abutment (2) connected to the shaft, a retaining ring (6) at the end of the shaft (1) remote from the abutment (2), and also members (3, 4) to be clamped axially and situated between the abutment (2) and the retaining ring (6); and also with a hydraulic chucking means for converting the clamping assembly from an unclamped condition into a preliminary clamping position, in which the members (3, 4) bear at the end face against the abutment (2); a space for accommodating a spacer ring (10) between the retaining ring (6) and the members (3, 4); a spacer ring in the accommodating space, which in the preliminary clamping position of the clamping assembly can be brought into an operating position in which its axial dimension is larger than the axial dimension of the accommodating space in the unclamped condition in such a way that; after the hydraulic chucking means has been released, the operational clamping force is transmitted between the abutment (2) and the retaining ring (6) via the members (3, 4) and the spacer ring (10) situated in the operating position, characterised in that the spacer ring (10) and a ring (6) adjacent to it are rotatable relative to one another and at their end faces they interact along sawtooth-like complementary inclined peripherally disposed surfaces (11) with an inclination decreasing peripherally and considerably below the self-locking limit.
EP89108513A 1988-05-27 1989-05-11 Rolling mill roll with a ring mounted on a roll shaft Expired - Lifetime EP0343440B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89108513T ATE66836T1 (en) 1988-05-27 1989-05-11 ROLLING DEVICE WITH A ROLLING RING DISPOSED ON A SHAFT.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8806968U DE8806968U1 (en) 1988-05-27 1988-05-27
DE8806968U 1988-05-27

Publications (2)

Publication Number Publication Date
EP0343440A1 EP0343440A1 (en) 1989-11-29
EP0343440B1 true EP0343440B1 (en) 1991-09-04

Family

ID=6824488

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89108513A Expired - Lifetime EP0343440B1 (en) 1988-05-27 1989-05-11 Rolling mill roll with a ring mounted on a roll shaft

Country Status (8)

Country Link
US (2) US4841612A (en)
EP (1) EP0343440B1 (en)
JP (1) JPH0235213A (en)
AT (1) ATE66836T1 (en)
DD (1) DD286977A5 (en)
DE (2) DE8806968U1 (en)
ES (1) ES2026288T3 (en)
SU (1) SU1715199A3 (en)

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US5109585A (en) * 1990-10-24 1992-05-05 Uwe Kark Roll for a roll stand having an exchangeable roll ring and a divided roll body
WO2000074869A1 (en) * 1999-06-07 2000-12-14 Uwe Kark Assembly for changing the nut that retains a roll ring
US7572215B2 (en) 2005-06-17 2009-08-11 Sandvik Intellectual Property Ab Roll
US7582046B2 (en) 2005-06-17 2009-09-01 Sandvik Intellectual Property Ab Roll as well as a spacer ring therefor
DE10302660B4 (en) * 2002-04-24 2011-04-07 Köllges, Ralf Apparatus and method for tensioning a rolling ring on a shaft of a rolling stand
US8133162B2 (en) 2005-06-17 2012-03-13 Sandvik Intellectual Property Ab Roll, as well as a ring for such a roll
EP3378577A1 (en) 2017-03-22 2018-09-26 Ralf Köllges Hydraulic clamping device for demountable, frictionally engaged connection between two components

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DE3834606A1 (en) * 1988-10-11 1990-04-12 Voest Alpine Ind Anlagen Device for fixing a roll ring
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US5483812A (en) * 1994-02-08 1996-01-16 Asko, Inc. Roll apparatus for reducing work
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US6666804B2 (en) * 2001-12-11 2003-12-23 Mario Fabris Two stage clamping pinion
DE20212838U1 (en) * 2002-08-21 2002-12-12 Kark Ag Ring holder for rolling ring
US20050091821A1 (en) * 2003-11-03 2005-05-05 Best Scott D. Method of manufacturing an article having a radio frequency identification (RFID) device
KR100578468B1 (en) * 2004-05-20 2006-05-10 대한동방 주식회사 Adiabatic Roll
SE529027C2 (en) * 2005-06-17 2007-04-10 Sandvik Intellectual Property Roller and spring for roller with annular end surfaces
MX2011000634A (en) * 2010-01-18 2011-11-04 Basf Se Strand guide assembly and method of controlling a flow of molten thermoplastic.
CN102205347B (en) * 2011-04-28 2013-03-20 株洲硬质合金集团有限公司 Combined hydraulic pre-tightening locking device and hard alloy compound roller
US9334890B2 (en) 2012-01-24 2016-05-10 Kennametal India Limited Hardmetal roll clamping system onto the shaft and the method thereof
DE102014005331B3 (en) 2014-02-11 2015-05-21 Sms Meer Gmbh Tool change system and method as well as stretching roller
KR101595376B1 (en) * 2016-01-14 2016-02-26 박은수 Assembly Structure Of Roller
CN113714298B (en) * 2017-12-11 2023-03-28 株洲硬质合金集团有限公司 Combined roller, nut locking device and combined roller with nut locking device
CN110340150B (en) * 2019-07-31 2021-06-25 安徽川岳机械有限公司 Composite roll collar

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5109585A (en) * 1990-10-24 1992-05-05 Uwe Kark Roll for a roll stand having an exchangeable roll ring and a divided roll body
WO1992007668A1 (en) * 1990-10-24 1992-05-14 Uwe Kark Roller for a roll stand with an interchangeable roller ring and a divided roller body
WO2000074869A1 (en) * 1999-06-07 2000-12-14 Uwe Kark Assembly for changing the nut that retains a roll ring
EP1066890A1 (en) * 1999-06-07 2001-01-10 Uwe Kark Arrangement for changing the nut securing a rolling ring
US6286394B1 (en) 1999-06-07 2001-09-11 Uwe Kark Arrangement for changing the nut holding a roll ring
DE10302660B4 (en) * 2002-04-24 2011-04-07 Köllges, Ralf Apparatus and method for tensioning a rolling ring on a shaft of a rolling stand
US7572215B2 (en) 2005-06-17 2009-08-11 Sandvik Intellectual Property Ab Roll
US7582046B2 (en) 2005-06-17 2009-09-01 Sandvik Intellectual Property Ab Roll as well as a spacer ring therefor
US8133162B2 (en) 2005-06-17 2012-03-13 Sandvik Intellectual Property Ab Roll, as well as a ring for such a roll
EP3378577A1 (en) 2017-03-22 2018-09-26 Ralf Köllges Hydraulic clamping device for demountable, frictionally engaged connection between two components

Also Published As

Publication number Publication date
ATE66836T1 (en) 1991-09-15
DD286977A5 (en) 1991-02-14
ES2026288T3 (en) 1992-04-16
US4841612A (en) 1989-06-27
US4932111A (en) 1990-06-12
EP0343440A1 (en) 1989-11-29
DE58900255D1 (en) 1991-10-10
SU1715199A3 (en) 1992-02-23
JPH0235213A (en) 1990-02-05
JPH0517405B2 (en) 1993-03-09
DE8806968U1 (en) 1988-07-28

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