EP1396292B1 - Drive system for a cold pilger mill - Google Patents

Drive system for a cold pilger mill Download PDF

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Publication number
EP1396292B1
EP1396292B1 EP03018510A EP03018510A EP1396292B1 EP 1396292 B1 EP1396292 B1 EP 1396292B1 EP 03018510 A EP03018510 A EP 03018510A EP 03018510 A EP03018510 A EP 03018510A EP 1396292 B1 EP1396292 B1 EP 1396292B1
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EP
European Patent Office
Prior art keywords
counterweight
crank mechanism
drive system
crank
shaft
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EP03018510A
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German (de)
French (fr)
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EP1396292A1 (en
Inventor
Michael Baensch
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SMS Group GmbH
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SMS Meer GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
    • B21B35/06—Drives for metal-rolling mills, e.g. hydraulic drives for non-continuously-operating mills or for single stands
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B21/00—Pilgrim-step tube-rolling, i.e. pilger mills
    • B21B21/005—Pilgrim-step tube-rolling, i.e. pilger mills with reciprocating stand, e.g. driving the stand

Definitions

  • the invention relates to a drive system for a cold pilger rolling mill, comprising a reciprocating roll stand, at least one driven by a drive crank mechanism having a crank arm with balance weight for at least partially balancing the mass forces generated by the rolling stand and a push rod, the rolling stand and the crank arm articulated to each other, and at least one counterweight which is eccentrically rotatably arranged for compensating mass forces and / or moments of inertia, and a transmission synchronizing the movement of the crank mechanism and the counterweight.
  • a drive for a cold pilger mill is known for example from DE 43 36 422 C2.
  • a mill stand equipped with a cold pilger roller pair is required, which is driven in an oscillating manner.
  • a crank mechanism is used, which is driven by a motor.
  • the crank mechanism is provided to compensate for the inertial forces of the roll stand with a balance weight.
  • crank drive via toothing drives further waves on which countermeasures are arranged eccentrically with respect to the center of gravity.
  • These countermeasures run in the same direction and in opposite directions upon rotation of the crank mechanism and are thus able to generate compensating mass forces or moments of inertia, so that the overall result is a balance of force in the entire drive system.
  • a disadvantage of the known embodiment that overall results in a rather complicated construction of the entire drive system, because a variety of machine elements - intermeshing intermeshing - are required. This also increases the cost of the drive system and thus of the cold pilger rolling mill, which means not only the investment costs for the system itself, but also the costs for the plant foundation, for spare and wearing parts and for maintenance and repair.
  • a drive system for a cold pilger rolling mill is known in which the crankshaft is equipped to drive the rolling mill with centrifugal weights and a vertically oscillating balance weight to compensate for the mass forces of the first order and the mass moments in the drive.
  • DE 36 13 036 C1 discloses a drive for the rolling stand of a cold pilger rolling mill, wherein a planetary drive for driving and balancing of inertial forces and moments of inertia is used.
  • this drive is only suitable for smaller cold pilger mills, because in larger systems, the size of such a drive system increases disproportionately and thus causes high costs.
  • crank mechanism consists of three parallel to each other and equally spaced waves, of which the middle formed as a crankshaft shaft is connected via its crank pin with the rolling stand coupling push rod and its crank by 180 degrees to the articulation point of the push rod offset a inertial forces of the rolling stand in half balancing main mass is arranged eccentrically to the axis of rotation of the crankshaft. Furthermore, there is provided that two equally large additional masses are arranged on the other two waves, which compensate for the other half of the inertial forces of the rolling stand.
  • the invention is therefore based on the object to design a drive system for a generic cold pilger rolling mill so that the simplest possible and therefore less expensive construction is given, the mass forces and inertia can be limited by such a structure, however, to a reasonable degree.
  • crank mechanism is assigned only a single counterweight, wherein the plane in which moves the balance weight of the crank mechanism during rotation, and the plane in which the counterweight moves during rotation, are identical, wherein the Crankshaft, the counterweight and the drive via gear transmission are interconnected, wherein the drive via the gear drive drives a shaft to which the counterweight is connected, and wherein the arranged on the shaft gear of the gear transmission via a gear drives a shaft with which the Crank drive is connected, and wherein the balance weight and / or the counterweight is arranged as an eccentrically arranged mass in one of the gears of the gear transmission.
  • the shaft of the crank mechanism, the shaft of the counterweight and the shaft of the drive lie in one plane, whereby a particularly simple and easily mountable structure can be realized.
  • the rolling stand and a single crank mechanism can be connected to each other by a single push rod. It is recommended in terms of a particularly simple structure, when the push rod is cantilevered on the crank mechanism.
  • the rolling stand and a single crank mechanism can be interconnected by two push rods, which are mounted on both sides of the crank mechanism flying.
  • the center plane (plane of symmetry) of the rolling stand and the center plane (plane of symmetry) of the crank mechanism are identical;
  • the center plane (plane of symmetry) of the crank mechanism and the center plane (plane of symmetry) of the counterweight are preferably identical.
  • a further alternative embodiment provides that the roll stand and two crank drives arranged on both sides of the crank mechanism arranged symmetrically to the center plane of the roll stand are connected to one another by two push rods.
  • the drive via gear transmission connects the two crank mechanisms and the two counterwebs assigned to them, the gear mechanisms being arranged laterally adjacent to a crank mechanism.
  • the shafts of the crank mechanism, the counterweight and the drive can be arranged horizontally or vertically.
  • the push rod is mounted on journals, wherein at least one bearing pin is provided with at least one bore for supplying the bearing between the thrust rod and journal with lubricating oil.
  • the masses of the roll stand, the balance weight (or the balance weights) and the counterweight (or counterweights) are selected so that the first-order framework mass forces are at least substantially equalized during operation of the drive system become.
  • the proposed drive system for a cold pilger mill is characterized by a simple structure, which ensures economical production and economic operation of the rolling mill.
  • the quality of the mass balance is sufficiently good, so that a good quality of the pipes to be produced is made possible.
  • the drive system therefore operates relatively low vibration, so that the foundation and the environment are treated gently.
  • the drive system works reliably and has a long service life; the costs for maintenance and repair are low.
  • the Kaltpilgerwalzrea is shown schematically. It is used for manufacturing or forming a tube 22 by means of a cold pilger roller pair 23, which is mounted in a rolling mill, not shown here.
  • the pipe 22 to be processed is guided on a rolling mandrel 24.
  • the rolling mill performs an oscillating motion during the rolling process, whereby stroke frequencies of up to 300 per minute and more are possible.
  • the tube 22 is moved in the conveying direction R during the rolling process.
  • the pre-stroke which is sketched schematically in FIG. 1a
  • the cold pilger-roller pair 23 rolls on the pipe 22 in the conveying direction R
  • the return stroke which is sketched in Fig. 1b
  • the rolling of the pair of rollers 23 on the tube 22 takes place counter to the conveying direction R (see arrows for the direction of rotation and direction of translation).
  • a drive system 1 is sketched for a rolling stand 2 in side view and top view, in which the roller pair 23 shown in Fig. 1a, 1b is mounted.
  • crank mechanism 4 which has a crank arm 5 with at least one offset and with a with respect to the bearing point eccentrically arranged balance weight 6.
  • Crankshaft 4 and rolling mill 2 are connected to a push rod 7, which is articulated both on the crank arm 5 and on the roll stand 2.
  • the oscillatory drive of the roll stand 2 proceeds as follows: In a common plane 25, three shafts 12, 13 and 14 are arranged and supported next to one another.
  • the shaft 14 is connected to a drive 3, which is not shown in detail; this can be an electric motor.
  • the shaft 12 supports in an eccentrically arranged counterweight 8.
  • the shaft 13 finally supports the crank mechanism 4, as explained above.
  • a spur gear 9, 10 and 11 are rotatably arranged in each case.
  • the gear 9 forms, together with the gear 10, a first gear transmission;
  • the gear 10 forms with the gear 11, a second gear transmission.
  • the toothed wheels 9, 10 and 11 are all in engagement, so that the drive 3 drives the shaft 13 and the counter mass 8 connected thereto when the shaft 14 rotates.
  • the shaft 12 drives via the gears 9 and 10 in turn the shaft 13 and thus the crank drive 4 at.
  • crank mechanism 4 is assigned only a single counterweight 8, wherein during rotation of the crank mechanism 4, the rotation of the counterweight 8 is synchronized. Further, the plane 26, s. Fig. 2b, in which the balance weight 6 of the crank mechanism 4 moves during rotation, and the plane 27, s. Fig. 2b, in which the counterweight 8 moves during rotation, identical.
  • crank mechanism 4, counterweight 8 and drive 3 via gear transmission 9, 10, 11 are interconnected.
  • the shaft 13 the crank drive 4, the shaft 12 of the counterweight 8 and the shaft 14 of the drive 3 are preferably in the common plane 25, s. Fig. 2a.
  • the balance weight 6 and the counterweight 8 are designed so that the mass forces of the first order for the system consisting of roll stand 2, balance weight 6 and counterweight 8 are compensated when the drive system 1 moves.
  • second and higher-order inertia forces arising from the oscillating movement of the roll stand 2 are not compensated.
  • the proposed drive concept has a deliberately lower quality of the mass balance, as it is usually the case in the solutions according to the prior art.
  • this disadvantage does not particularly affect smaller machines, since the amplitudes of the forces and moments emitted via the foundation are sufficiently low. Impairment of the environment is only possible in the case of installation sites with particularly sensitive vibration. In these cases, but also with the previously known solutions vibration analysis and, where appropriate, additional measures are required.
  • the solution according to FIG. 2 a or FIG. 2 b operates with a single push rod 7, which is mounted on the crank mechanism 4 in a flying manner.
  • the sketched arrangement of the push rod 7 in the center plane 15 of the rolling mill requires either a correspondingly low positioning of the system, consisting from crank drive 4, counterweight 8 and drive 3, or a suitable deflection of the produced tube from the roller center.
  • Fig. 2b only very schematically - outlined that extend through the crank of the crank mechanism 4 has two holes 20 and 21. Through these holes 20, 21, the bearings can be supplied with lubricating oil, which connect the bearing pins 18 and 19 to rolling stand 2 and crank mechanism 4 with the push rod 7.
  • FIGS. 3a and 3b show an embodiment of the drive system 1 according to the invention.
  • the center plane 15 of the roll stand 2, the center plane 16 of the crank mechanism 4 and the center plane 17 of the counterweight 8 are identical. This ensures that no unbalanced mass moments arise when the mass of the rolling stand 2 and the mass of the balance weight 6 and the counterweight 8 move relative to each other.
  • the gears 9, 10, 11 are below the roller center.
  • the balance weight 6 is arranged in the illustrated case as arranged eccentrically in the gear 9 mass; the balance weight 6 is thus in the gear 9 integrated.
  • the counterweight 8 is arranged as eccentrically arranged mass in the gear 10.
  • the push rods 7, 7' are here with two crank drives 4 and 4 'in FIG Connection.
  • the gear unit consisting of the gear drives 9, 10 and 10, 11 and the drive 3 is arranged.
  • Each crank mechanism 4 and 4 'with a balance weight 6 or 6' is assigned a counterweight 8 or 8 ', which is driven synchronized to balance the mass by means of the gears 9, 10, 11.
  • FIGS. 5a and 5b shows that a construction can also be realized in which the shafts 12, 13 and 14 are arranged vertically; in the solutions according to Figures 2, 3 and 4, however, these waves are positioned horizontally.
  • the proposed drive system 1 thus has a very simple structure, which causes only low investment costs. Furthermore, the maintenance costs are relatively low due to the simple machine concept. On the other hand, a good balance of inertial forces and mass moments is possible, so that a low-vibration operation of the cold pilger rolling mill is possible without much effort. The availability of the rolling mill is high. The production of low-cost manufactured high-quality cold piled pipes is thus ensured.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Metal Rolling (AREA)
  • Flow Control (AREA)
  • Control Of Velocity Or Acceleration (AREA)
  • Feedback Control In General (AREA)

Abstract

Drive system, for a cold reciprocating rolling mill with a reciprocating roller stand (2), has at least one crank drive (4) from a drive (3). The crank arm has a balance weight (6) for at least a partial compensation of the mass forces generated by the roller stand, with a push rod (7) linking the crank arm and roller stand. At least one counter mass (8) with an eccentric rotation is synchronized with the crank drive movements, through a gearing (9,10), to compensate for the moving masses and/or the mass inertias. A single counter mass is used for the crank drive, with the movements of the balance weight and the counter mass on identical planes.

Description

Die Erfindung betrifft ein Antriebssystem für ein Kaltpilgerwalzwerk, mit einem hinund herbewegbaren Walzgerüst, mindestens einem von einem Antrieb angetriebenen Kurbeltrieb, der einen Kurbelarm mit Ausgleichsgewicht zum zumindest teilweisen Ausgleich der vom Walzgerüst erzeugten Massenkräfte und eine Schubstange aufweist, die Walzgerüst und Kurbelarm gelenkig miteinander verbindet, und mindestens einer zum Ausgleich von Massenkräften und/oder Massenmomenten exzentrisch drehbar angeordneten Gegenmasse und einem die Bewegung des Kurbeltriebs und der Gegenmasse synchronisierenden Getriebe.The invention relates to a drive system for a cold pilger rolling mill, comprising a reciprocating roll stand, at least one driven by a drive crank mechanism having a crank arm with balance weight for at least partially balancing the mass forces generated by the rolling stand and a push rod, the rolling stand and the crank arm articulated to each other, and at least one counterweight which is eccentrically rotatably arranged for compensating mass forces and / or moments of inertia, and a transmission synchronizing the movement of the crank mechanism and the counterweight.

Ein Antrieb für ein Kaltpilgerwalzwerk ist beispielsweise aus der DE 43 36 422 C2 bekannt. Zur Durchführung des Kaltpilgerprozesses ist ein mit einem Kaltpilgerwalzenpaar ausgestattetes Walzgerüst erforderlich, das oszillierend angetrieben wird. Hierzu wird ein Kurbeltrieb eingesetzt, der von einem Motor angetrieben wird. Der Kurbeltrieb ist zum Ausgleich der Massenkräfte des Walzgerüsts mit einem Ausgleichsgewicht versehen.A drive for a cold pilger mill is known for example from DE 43 36 422 C2. To carry out the cold pilgering process, a mill stand equipped with a cold pilger roller pair is required, which is driven in an oscillating manner. For this purpose, a crank mechanism is used, which is driven by a motor. The crank mechanism is provided to compensate for the inertial forces of the roll stand with a balance weight.

Die Produktivität eines Kaltpilgerwalzwerks ist direkt von der Hubzahl des Walzgerüsts pro Zeiteinheit abhängig, weshalb aus Wirtschaftlichkeitsgründen angestrebt werden muss, eine möglichst große Anzahl an Arbeitshüben pro Minute zu bewerkstelligen. Dies bedeutet jedoch auch große Massenkräfte, die sowohl das Antriebssystem und insbesondere dessen Lager als auch das Fundament und damit die Umgebung belasten.The productivity of a cold pilger mill is directly dependent on the number of strokes of the rolling stand per unit time, which is why it must be sought for reasons of economy, to achieve the largest possible number of strokes per minute. However, this also means large inertial forces that burden both the drive system and in particular its bearings as well as the foundation and thus the environment.

In der genannten DE 43 36 422 C2 ist daher vorgesehen, dass der Kurbeltrieb über Verzahnungen weitere Wellen antreibt, auf denen Gegenmassen hinsichtlich des Schwerpunkts exzentrisch angeordnet sind. Diese Gegenmassen laufen bei Drehung des Kurbeltriebs gleich- und gegensinnig um und sind so in der Lage, ausgleichende Massenkräfte bzw. Massenmomente zu erzeugen, so dass sich insgesamt ein Massenkraftausgleich im gesamten Antriebssystem ergibt.In the cited DE 43 36 422 C2 it is therefore provided that the crank drive via toothing drives further waves on which countermeasures are arranged eccentrically with respect to the center of gravity. These countermeasures run in the same direction and in opposite directions upon rotation of the crank mechanism and are thus able to generate compensating mass forces or moments of inertia, so that the overall result is a balance of force in the entire drive system.

Nachteilig ist bei der bekannten Ausgestaltung, dass sich insgesamt eine recht aufwendige Konstruktion des gesamten Antriebssystems ergibt, weil eine Vielzahl von Maschinenelementen - über Verzahnungen ineinander eingreifend - erforderlich sind. Damit steigen auch die Kosten des Antriebssystems und damit des Kaltpilgerwalzwerks, wobei hierunter nicht nur die Investitionskosten für die Anlage selber zu verstehen sind, sondern auch die Kosten für das Anlagenfundament, für Ersatz- und Verschleißteile und für Wartung und Reparatur.A disadvantage of the known embodiment that overall results in a rather complicated construction of the entire drive system, because a variety of machine elements - intermeshing intermeshing - are required. This also increases the cost of the drive system and thus of the cold pilger rolling mill, which means not only the investment costs for the system itself, but also the costs for the plant foundation, for spare and wearing parts and for maintenance and repair.

Aus der DE-PS 962 062 ist ein Antriebssystem für ein Kaltpilgerwalzwerk bekannt, bei dem die Kurbelwelle zum Antrieb des Walzgerüsts mit Fliehgewichten und einem vertikal oszillierenden Ausgleichsgewicht zum Ausgleich der Massenkräfte erster Ordnung sowie der Massenmomente im Antrieb ausgestattet ist.From DE-PS 962 062 a drive system for a cold pilger rolling mill is known in which the crankshaft is equipped to drive the rolling mill with centrifugal weights and a vertically oscillating balance weight to compensate for the mass forces of the first order and the mass moments in the drive.

Nachteilig ist bei dieser Lösung, dass das Fundament des Walzwerks sehr aufwendig und damit teuer ausgestaltet ist, da für das vertikale Eintauchen des Ausgleichsgewichts in das Fundament gesorgt werden muss. Es wird hierbei ein großer und tiefer Keller benötigt, was die Kosten des Walzwerks entsprechend steigen lässt.The disadvantage of this solution is that the foundation of the rolling mill is very complicated and therefore expensive designed, since it must be ensured for the vertical immersion of the balance weight in the foundation. This requires a large and deep basement, which increases the costs of the rolling mill accordingly.

Die DE 36 13 036 C1 offenbart einen Antrieb für das Walzgerüst eines Kaltpilgerwalzwerks, wobei ein Planetkurbeltrieb zum Antrieb und Ausgleich von Massenkräften und Massenmomenten zum Einsatz kommt.DE 36 13 036 C1 discloses a drive for the rolling stand of a cold pilger rolling mill, wherein a planetary drive for driving and balancing of inertial forces and moments of inertia is used.

Wenngleich mit dieser Lösung ein optimaler Massenausgleich erfolgen kann, eignet sich dieser Antrieb nur bei kleineren Kaltpilgerwalzwerken, weil bei größeren Anlagen die Baugröße eines solchen Antriebsystems überproportional steigt und damit hohe Kosten verursacht.Although with this solution, an optimal mass balance can be done, this drive is only suitable for smaller cold pilger mills, because in larger systems, the size of such a drive system increases disproportionately and thus causes high costs.

Auch aus der DE 41 24 691 C1 (& EP-A-0524711) ist ein gattungsgemäßes Antriebssystem für ein Kaltpilgerwalzwerk bekannt. Dieses zeichnet sich dadurch aus, dass der Kurbeltrieb aus drei parallel zueinander und gleich beabstandet angeordneten Wellen besteht, von denen die mittlere als Kurbelwelle ausgebildete Welle über ihren Kurbelzapfen mit der das Walzgerüst koppelnden Schubstange verbunden ist und auf deren Kurbel um 180 Grad zum Anlenkpunkt der Schubstange versetzt eine die Trägheitskräfte des Walzgerüsts zur Hälfte ausgleichende Hauptmasse exzentrisch zur Drehachse der Kurbelwelle angeordnet ist. Weiterhin ist dort vorgesehen, dass auf den beiden anderen Wellen zwei gleich große Zusatzmassen angeordnet sind, die die andere Hälfte der Trägheitskräfte des Walzgerüstes ausgleichen.Also from DE 41 24 691 C1 (& EP-A-0524711) a generic drive system for a cold pilger rolling mill is known. This is characterized by the fact that the crank mechanism consists of three parallel to each other and equally spaced waves, of which the middle formed as a crankshaft shaft is connected via its crank pin with the rolling stand coupling push rod and its crank by 180 degrees to the articulation point of the push rod offset a inertial forces of the rolling stand in half balancing main mass is arranged eccentrically to the axis of rotation of the crankshaft. Furthermore, there is provided that two equally large additional masses are arranged on the other two waves, which compensate for the other half of the inertial forces of the rolling stand.

Alle bekannten Antriebssysteme für Kaltpilgerwalzwerke haben daher den gravierenden Nachteil, daß ein recht hoher Aufwand zur Reduzierung der Massenkräfte bzw. Massenmomente betrieben wird, so dass hohe Investitions- bzw. Fundamentkosten und/oder eine aufwendige Montage bei der Fertigung bzw. bei der Reparatur und Instandhaltung des Walzwerks bedingt sind.All known drive systems for cold pilger mills therefore have the serious disadvantage that quite a lot of effort to reduce the mass forces or moments of inertia is operated, so that high investment or foundation costs and / or a complex assembly during manufacture or during repair and maintenance of the rolling mill are conditional.

Es hat sich herausgestellt, dass die vorbekannten, teilweise recht aufwendig konzipierten Systeme für den Ausgleich von Massenkräften und Massenmomenten manchmal gar nicht erforderlich sind, wenn die Umgebung nicht ausgesprochen schwingungsempfindlich ist.It has been found that the previously known, sometimes quite elaborately designed systems for the compensation of inertial forces and moments of inertia are sometimes not necessary if the environment is not very sensitive to vibrations.

Der Erfindung liegt daher die Aufgabe zugrunde, ein Antriebssystem für ein gattungsgemäßes Kaltpilgerwalzwerk so zu gestalten, dass ein möglichst einfacher und damit kostengünstiger Aufbau gegeben ist, die Massenkräfte und Massenmomente durch einen solchen Aufbau jedoch auf ein vernünftiges Maß beschränkt werden können.The invention is therefore based on the object to design a drive system for a generic cold pilger rolling mill so that the simplest possible and therefore less expensive construction is given, the mass forces and inertia can be limited by such a structure, however, to a reasonable degree.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, dass dem Kurbeltrieb nur eine einzige Gegenmasse zugeordnet ist, wobei die Ebene, in der sich bei Rotation das Ausgleichsgewicht des Kurbeltriebs bewegt, und die Ebene, in der sich bei Rotation die Gegenmasse bewegt, identisch sind, wobei der Kurbeltrieb, die Gegenmasse und der Antrieb über Zahnradgetriebe miteinander verbunden sind, wobei der Antrieb über das Zahnradgetriebe eine Welle antreibt, mit der die Gegenmasse verbunden ist, und wobei das auf der Welle angeordnete Zahnrad des Zahnradgetriebes über ein Zahnrad eine Welle antreibt, mit der der Kurbeltrieb verbunden ist, und wobei das Ausgleichsgewicht und/oder die Gegenmasse als exzentrisch angeordnete Masse in einem der Zahnräder der Zahnradgetriebe angeordnet ist.This object is achieved in that the crank mechanism is assigned only a single counterweight, wherein the plane in which moves the balance weight of the crank mechanism during rotation, and the plane in which the counterweight moves during rotation, are identical, wherein the Crankshaft, the counterweight and the drive via gear transmission are interconnected, wherein the drive via the gear drive drives a shaft to which the counterweight is connected, and wherein the arranged on the shaft gear of the gear transmission via a gear drives a shaft with which the Crank drive is connected, and wherein the balance weight and / or the counterweight is arranged as an eccentrically arranged mass in one of the gears of the gear transmission.

Mit dieser Ausgestaltung wird insgesamt ein sehr einfacher Aufbau des Antriebssystems für ein Kaltpilgerwalzwerk erreicht. Trotzdem ist sichergestellt, dass ein hinreichender Massenkraft- und Massenmomentausgleich erfolgt, so dass ein akzeptabler Betriebszustand des Walzwerks gegeben ist.With this configuration, a very simple construction of the drive system for a cold pilger mill is achieved overall. Nevertheless, it is ensured that a sufficient Massenkraft- and mass moment compensation takes place, so that an acceptable operating condition of the rolling mill is given.

Mit Vorteil ist dabei vorgesehen, dass die Welle des Kurbeltriebs, die Welle der Gegenmasse und die Welle des Antriebs in einer Ebene liegen, wodurch ein besonders einfacher und leicht montierbarer Aufbau realisiert werden kann.Advantageously, it is provided that the shaft of the crank mechanism, the shaft of the counterweight and the shaft of the drive lie in one plane, whereby a particularly simple and easily mountable structure can be realized.

Gemäß einer ersten konstruktiven Ausgestaltung des Antriebssystems können das Walzgerüst und ein einziger Kurbeltrieb durch eine einzige Schubstange miteinander verbunden sein. Dabei empfiehlt es sich im Sinne eines besonders einfachen Aufbaus, wenn die Schubstange am Kurbeltrieb fliegend gelagert ist.According to a first structural embodiment of the drive system, the rolling stand and a single crank mechanism can be connected to each other by a single push rod. It is recommended in terms of a particularly simple structure, when the push rod is cantilevered on the crank mechanism.

Bei einer alternativen Ausführungsform können das Walzgerüst und ein einziger Kurbeltrieb durch zwei Schubstangen miteinander verbunden werden, die beiderseits des Kurbeltriebs fliegend gelagert sind. Hier kann mit Vorteil vorgesehen werden, dass die Mittenebene (Symmetrieebene) des Walzgerüsts und die Mittenebene (Symmetrieebene) des Kurbeltriebs identisch sind; bevorzugt sind ferner die Mittenebene (Symmetrieebene) des Kurbeltriebs und die Mittenebene (Symmetrieebene) der Gegenmasse identisch.In an alternative embodiment, the rolling stand and a single crank mechanism can be interconnected by two push rods, which are mounted on both sides of the crank mechanism flying. Here can be provided with advantage that the center plane (plane of symmetry) of the rolling stand and the center plane (plane of symmetry) of the crank mechanism are identical; Furthermore, the center plane (plane of symmetry) of the crank mechanism and the center plane (plane of symmetry) of the counterweight are preferably identical.

Eine weitere alternative Ausgestaltung sieht vor, dass das Walzgerüst und zwei beiderseits der und symmetrisch zur Mittenebene des Walzgerüsts angeordnete Kurbeltriebe durch zwei Schubstangen miteinander verbunden sind. Dabei kann ferner vorgesehen werden, dass der Antrieb über Zahnradgetriebe die beiden Kurbeltriebe und die beiden diesen zugeordneten Gegenmassen verbindet, wobei die Zahnradgetriebe seitlich benachbart zu einem Kurbeltrieb angeordnet sind.A further alternative embodiment provides that the roll stand and two crank drives arranged on both sides of the crank mechanism arranged symmetrically to the center plane of the roll stand are connected to one another by two push rods. In this case, it can further be provided that the drive via gear transmission connects the two crank mechanisms and the two counterwebs assigned to them, the gear mechanisms being arranged laterally adjacent to a crank mechanism.

Die Wellen des Kurbeltriebs, der Gegenmasse und des Antriebs können horizontal oder vertikal angeordnet sein.The shafts of the crank mechanism, the counterweight and the drive can be arranged horizontally or vertically.

Der ökonomischen und effizienten, möglichst automatischen Versorgung der Schubstangenlager und der Lager der Arbeitswalzen im Walzgerüst kommt eine wesentliche Bedeutung zu. Daher ist gemäß einer Weiterbildung vorgesehen, dass die Schubstange auf Lagerzapfen gelagert ist, wobei zumindest ein Lagerzapfen mit mindestens einer Bohrung zur Versorgung der Lagerstelle zwischen Schubstange und Lagerzapfen mit Schmieröl versehen ist.The economic and efficient, as automatic as possible supply of the push rod bearings and the bearings of the work rolls in the rolling mill is of major importance. It is therefore provided according to a development that the push rod is mounted on journals, wherein at least one bearing pin is provided with at least one bore for supplying the bearing between the thrust rod and journal with lubricating oil.

Für einen optimalen Betrieb des Antriebssystems wird hierbei vorgeschlagen, dass die Massen des Walzgerüsts, des Ausgleichsgewichts (bzw. der Ausgleichsgewichte) und der Gegenmasse (bzw. der Gegenmassen) so gewählt sind, dass die Gerüstmassenkräfte erster Ordnung im Betrieb des Antriebssystems zumindest im wesentlichen ausgeglichen werden.For optimal operation of the drive system, it is proposed here that the masses of the roll stand, the balance weight (or the balance weights) and the counterweight (or counterweights) are selected so that the first-order framework mass forces are at least substantially equalized during operation of the drive system become.

Das vorgeschlagene Antriebssystem für ein Kaltpilgerwalzwerk zeichnet sich durch einen einfachen Aufbau aus, der eine wirtschaftliche Herstellung und einen wirtschaftlichen Betrieb des Walzwerks sicherstellt. Die Qualität des Massenausgleichs ist dabei hinreichend gut, so dass eine gute Qualität der zu produzierenden Rohre ermöglicht wird. Das Antriebssystem arbeitet daher relativ erschütterungsarm, so dass das Fundament und die Umgebung schonend behandelt werden. Das Antriebssystem arbeitet zuverlässig und hat eine hohe Lebensdauer; die Kosten für Wartung und Reparatur sind gering.The proposed drive system for a cold pilger mill is characterized by a simple structure, which ensures economical production and economic operation of the rolling mill. The quality of the mass balance is sufficiently good, so that a good quality of the pipes to be produced is made possible. The drive system therefore operates relatively low vibration, so that the foundation and the environment are treated gently. The drive system works reliably and has a long service life; the costs for maintenance and repair are low.

Auch die Montagekosten des Antriebssystems sind durch den vorgeschlagenen Aufbau des Systems niedrig. Gleichermaßen werden keine besonderen Ansprüche an das Fundament gestellt.The assembly costs of the drive system are low due to the proposed structure of the system. Likewise, no special demands are placed on the foundation.

In der Zeichnungen 3a und 3b ist ein Ausführungsbeispiel der Erfindung dargestellt, wobei es sich bei den in den Fig. 2 a, 2 b, 4 a, 4 b und 5 a, 5 b gezeigten Ausführungsbeispielen nicht um Ausführungsbeispiele der Erfindung sondern um Beispiele handelt, die das Verständnis der Erfindung erleichtern. Es zeigen:

Fig. 1a
schematisch die Seitenansicht eines Kaltpilgerwalzenpaars während des Vorhubs des Kaltpilgerwalzprozesses;
Fig. 1b
die entsprechende Ansicht gemäß Fig. 1a während des Rückhubes;
Fig. 2a
eine Seitenansicht und
Fig. 2b
die zugehörige Draufsicht auf ein Antriebssystem für ein Kaltpilgerwalzwerk;
Fig. 3a
eine Seitenansicht und
Fig. 3b
die zugehörige Draufsicht auf eine Ausführungsform des Antriebssystem gemäß der Erfindung;
Fig. 4a
eine Seitenansicht und
Fig. 4b
die zugehörige Draufsicht auf ein Antriebssystem; und
Fig. 5a
eine Seitenansicht und
Fig. 5b
die zugehörige Draufsicht auf eine Ausführungsform eines Antriebssystems.
In the drawings 3a and 3b, an embodiment of the invention is shown, wherein the embodiments shown in FIGS. 2 a, 2 b, 4 a, 4 b and 5 a, 5 b are not exemplary embodiments of the invention but are examples which facilitate the understanding of the invention. Show it:
Fig. 1a
schematically the side view of a pair of cold pilger rollers during the Vorhubs the cold pilger rolling process;
Fig. 1b
the corresponding view of Figure 1a during the return stroke.
Fig. 2a
a side view and
Fig. 2b
the associated plan view of a drive system for a cold pilgering mill;
Fig. 3a
a side view and
Fig. 3b
the associated plan view of an embodiment of the drive system according to the invention;
Fig. 4a
a side view and
Fig. 4b
the associated plan view of a drive system; and
Fig. 5a
a side view and
Fig. 5b
the corresponding plan view of an embodiment of a drive system.

In Fig. 1a und Fig. 1b ist schematisch der Kaltpilgerwalzprozess dargestellt. Er dient zur Fertigung bzw. Umformung eines Rohres 22 mittels eines Kaltpilgerwalzenpaares 23, das in einem hier nicht dargestellten Walzgerüst gelagert ist. Das zu bearbeitende Rohr 22 ist auf einem Walzdorn 24 geführt. Das Walzgerüst vollzieht während des Walzprozesses eine oszillierende Bewegung, wobei Hubfrequenzen bis zu 300 pro Minute und mehr möglich sind.In Fig. 1a and Fig. 1b, the Kaltpilgerwalzprozess is shown schematically. It is used for manufacturing or forming a tube 22 by means of a cold pilger roller pair 23, which is mounted in a rolling mill, not shown here. The pipe 22 to be processed is guided on a rolling mandrel 24. The rolling mill performs an oscillating motion during the rolling process, whereby stroke frequencies of up to 300 per minute and more are possible.

Das Rohr 22 wird während des Walzprozesses in Förderrichtung R bewegt. Während des Vorhubs, der in Fig. 1a schematisch skizziert ist, rollt das Kaltpilgerwalzenpaar 23 in Förderrichtung R auf dem Rohr 22 ab; während des Rückhubes, der in Fig. 1b skizziert ist, erfolgt das Abrollen des Walzenpaares 23 auf dem Rohr 22 entgegen Förderrichtung R (s. Pfeile für Drehrichtung und Translationsrichtung).The tube 22 is moved in the conveying direction R during the rolling process. During the pre-stroke, which is sketched schematically in FIG. 1a, the cold pilger-roller pair 23 rolls on the pipe 22 in the conveying direction R; during the return stroke, which is sketched in Fig. 1b, the rolling of the pair of rollers 23 on the tube 22 takes place counter to the conveying direction R (see arrows for the direction of rotation and direction of translation).

In Fig. 2a und Fig. 2b ist ein Antriebssystem 1 für ein Walzgerüst 2 in Seitenansicht und Draufsicht skizziert, in dem das in Fig. 1a,1b dargestellte Walzenpaar 23 gelagert ist.In Fig. 2a and Fig. 2b, a drive system 1 is sketched for a rolling stand 2 in side view and top view, in which the roller pair 23 shown in Fig. 1a, 1b is mounted.

Zum Durchführen des Kaltpilger-Walzprozesses muss das Walzgerüst 2 eine oszillierende Bewegung - also eine hin- und hergehende Bewegung - ausführen. Zu diesem Zweck ist ein Kurbeltrieb 4 vorgesehen, der einen Kurbelarm 5 mit mindestens einer Kröpfung und mit einem in Bezug auf den Lagerpunkt exzentrisch angeordneten Ausgleichsgewicht 6 aufweist. Kurbeltrieb 4 und Walzgerüst 2 sind mit einer Schubstange 7 verbunden, die sowohl am Kurbelarm 5 als auch am Walzgerüst 2 gelenkig angeordnet ist.To carry out the cold pilger rolling process, the rolling stand 2 must perform an oscillating movement - ie a reciprocating movement. For this purpose, a crank mechanism 4 is provided, which has a crank arm 5 with at least one offset and with a with respect to the bearing point eccentrically arranged balance weight 6. Crankshaft 4 and rolling mill 2 are connected to a push rod 7, which is articulated both on the crank arm 5 and on the roll stand 2.

Der oszillatorische Antrieb des Walzgerüsts 2 verläuft wie folgt: In einer gemeinsamen Ebene 25 sind nebeneinander drei Wellen 12, 13 und 14 angeordnet und gelagert. Die Welle 14 ist mit einem Antrieb 3 verbunden, der nicht näher dargestellt ist; es kann sich hierbei um einen Elektromotor handeln. Die Welle 12 lagert in einer exzentrisch angeordneten Gegenmasse 8. Die Welle 13 lagert schließlich den Kurbeltrieb 4, wie er oben erläutert wurde. Auf jeder der drei Wellen 12, 13 und 14 ist jeweils ein Stirnzahnrad 9, 10 bzw. 11 drehfest angeordnet. Das Zahnrad 9 bildet zusammen mit dem Zahnrad 10 ein erstes Zahnradgetriebe; gleichermaßen bildet das Zahnrad 10 mit dem Zahnrad 11 ein zweites Zahnradgetriebe. Wie Fig. 2b zu entnehmen ist, befinden sich die Zahnräder 9, 10 und 11 sämtlich im Eingriff, so dass der Antrieb 3 bei Drehung der Welle 14 die Welle 13 und die mit dieser verbundenen Gegenmasse 8 antreibt. Die Welle 12 treibt über die Zahnräder 9 und 10 ihrerseits die Welle 13 und damit den Kurbeltrieb 4 an.The oscillatory drive of the roll stand 2 proceeds as follows: In a common plane 25, three shafts 12, 13 and 14 are arranged and supported next to one another. The shaft 14 is connected to a drive 3, which is not shown in detail; this can be an electric motor. The shaft 12 supports in an eccentrically arranged counterweight 8. The shaft 13 finally supports the crank mechanism 4, as explained above. On each of the three shafts 12, 13 and 14, a spur gear 9, 10 and 11 are rotatably arranged in each case. The gear 9 forms, together with the gear 10, a first gear transmission; Similarly, the gear 10 forms with the gear 11, a second gear transmission. As can be seen from FIG. 2 b, the toothed wheels 9, 10 and 11 are all in engagement, so that the drive 3 drives the shaft 13 and the counter mass 8 connected thereto when the shaft 14 rotates. The shaft 12 drives via the gears 9 and 10 in turn the shaft 13 and thus the crank drive 4 at.

Im Betrieb des Antriebssystems 1 dreht die Welle 12 und mit ihr die Gegenmasse 8 gegenläufig mit Kurbeldrehzahl zum Kurbeltrieb 4, wodurch der Massenausgleich erreicht wird.In operation of the drive system 1, the shaft 12 and with it the counterweight 8 rotates in opposite directions with crank speed to the crank mechanism 4, whereby the mass balance is achieved.

Wesentlich ist, dass dem Kurbeltrieb 4 nur eine einzige Gegenmasse 8 zugeordnet ist, wobei bei Rotation des Kurbeltriebs 4 die Rotation der Gegenmasse 8 synchronisiert erfolgt. Ferner ist die Ebene 26, s. Fig. 2b, in der sich bei Rotation das Ausgleichsgewicht 6 des Kurbeltriebs 4 bewegt, und die Ebene 27, s. Fig. 2b, in der sich bei Rotation die Gegenmasse 8 bewegt, identisch.It is essential that the crank mechanism 4 is assigned only a single counterweight 8, wherein during rotation of the crank mechanism 4, the rotation of the counterweight 8 is synchronized. Further, the plane 26, s. Fig. 2b, in which the balance weight 6 of the crank mechanism 4 moves during rotation, and the plane 27, s. Fig. 2b, in which the counterweight 8 moves during rotation, identical.

Ein einfacher konstruktiver Aufbau wird erreicht, weil Kurbeltrieb 4, Gegenmasse 8 und Antrieb 3 über Zahnradgetriebe 9, 10, 11 miteinander verbunden sind. Wie bereits erwähnt, treibt dabei der Antrieb 3 über ein Zahnradgetriebe 10, 11 die Welle 12 an, mit der die Gegenmasse 8 verbunden ist; andererseits treibt das auf der Welle 12 angeordnete Zahnrad 10 des Zahnradgetriebes 10, 11 über das Zahnrad 9 die Welle 13 an, mit der der Kurbeltrieb 4 verbunden ist. Die Welle 13 des Kurbeltriebs 4, die Welle 12 der Gegenmasse 8 und die Welle 14 des Antriebs 3 liegen dabei bevorzugt in der gemeinsamen Ebene 25, s. Fig. 2a.A simple structural design is achieved because crank mechanism 4, counterweight 8 and drive 3 via gear transmission 9, 10, 11 are interconnected. As already mentioned, drives the drive 3 via a gear transmission 10, 11, the shaft 12 to which the counterweight 8 is connected; on the other hand drives the arranged on the shaft 12 gear 10 of the gear transmission 10, 11 via the gear 9, the shaft 13 to which the crank mechanism 4 is connected. The shaft 13 the crank drive 4, the shaft 12 of the counterweight 8 and the shaft 14 of the drive 3 are preferably in the common plane 25, s. Fig. 2a.

Das Ausgleichsgewicht 6 und die Gegenmasse 8 sind so ausgelegt, dass die Massenkräfte erster Ordnung für das System bestehend aus Walzgerüst 2, Ausgleichsgewicht 6 und Gegenmasse 8 ausgeglichen werden, wenn sich das Antriebssystem 1 bewegt. Massenkräfte zweiter und höherer Ordnung, die durch die oszillierende Bewegung des Walzgerüsts 2 entstehen, werden hingegen nicht ausgeglichen. Auch werden keine Vorkehrungen getroffen, das Moment zu kompensieren, das die senkrecht zur Schubrichtung des Walzgerüsts wirkende Fliehkraftkomponenten der Ausgleichsgewichte erzeugt. Das Gleiche gilt für die Momente, die entstehen, weil die Resultierende der Trägheitskräfte der Ausgleichsgewichte nicht auf derselben Wirkungslinie liegt wie die auszugleichende Trägheitskraft des Walzgerüsts.The balance weight 6 and the counterweight 8 are designed so that the mass forces of the first order for the system consisting of roll stand 2, balance weight 6 and counterweight 8 are compensated when the drive system 1 moves. On the other hand, second and higher-order inertia forces arising from the oscillating movement of the roll stand 2 are not compensated. Also, no provision is made to compensate for the moment which produces the centrifugal force components of the counterweights acting perpendicular to the thrust direction of the rolling stand. The same applies to the moments that arise because the resultant of the inertial forces of the balance weights is not on the same line of action as the inertial force of the roll stand to be compensated.

Das vorgeschlagene Antriebskonzept weist insofern eine bewusst geringere Qualität des Massenausgleichs auf, als es bei den Lösungen gemäß dem Stand der Technik zumeist der Fall ist. Dieser Nachteil wirkt sich jedoch insbesondere an kleineren Maschinen nicht aus, da die Amplituden der über das Fundament emittierten Kräfte und Momente hinreichend gering sind. Nur im Falle von Installationsorten mit schwingungstechnisch besonders sensiblem Untergrund sind Beeinträchtigungen der Umgebung möglich. In diesen Fällen sind aber auch mit den vorbekannten Lösungen schwingungstechnische Analysen und gegebenenfalls Zusatzmaßnahmen erforderlich.The proposed drive concept has a deliberately lower quality of the mass balance, as it is usually the case in the solutions according to the prior art. However, this disadvantage does not particularly affect smaller machines, since the amplitudes of the forces and moments emitted via the foundation are sufficiently low. Impairment of the environment is only possible in the case of installation sites with particularly sensitive vibration. In these cases, but also with the previously known solutions vibration analysis and, where appropriate, additional measures are required.

In besonders vorteilhafter Weise arbeitet die Lösung gemäß den Fig. 2a bzw. Fig. 2b mit einer einzigen Schubstange 7, die fliegend am Kurbeltrieb 4 gelagert ist. Die skizzierte Anordnung der Schubstange 7 in der Mittenebene 15 des Walzgerüsts bedingt entweder eine entsprechend tiefe Positionierung des Systems, bestehend aus Kurbeltrieb 4, Gegenmasse 8 und Antrieb 3, oder eine geeignete Auslenkung des produzierten Rohres aus der Walzmitte.In a particularly advantageous manner, the solution according to FIG. 2 a or FIG. 2 b operates with a single push rod 7, which is mounted on the crank mechanism 4 in a flying manner. The sketched arrangement of the push rod 7 in the center plane 15 of the rolling mill requires either a correspondingly low positioning of the system, consisting from crank drive 4, counterweight 8 and drive 3, or a suitable deflection of the produced tube from the roller center.

Wichtig für einen ökonomischen Betrieb des Kaltpilger-Walzwerks ist es auch, dass eine automatische Schmierung der Lager der Schubstange und der Lager der Arbeitswalzen im Walzgerüst erfolgen kann. Hierfür ist in Fig. 2b - nur sehr schematisch - skizziert, dass sich durch die Kurbel des Kurbeltriebs 4 zwei Bohrungen 20 und 21 erstrecken. Durch diese Bohrungen 20, 21 können die Lagerstellen mit Schmieröl versorgt werden, die die Lagerzapfen 18 bzw. 19 an Walzgerüst 2 bzw. Kurbeltrieb 4 mit der Schubstange 7 verbinden.It is also important for an economical operation of the cold pilger rolling mill that automatic lubrication of the bearings of the push rod and the bearings of the work rolls in the rolling stand can take place. For this purpose, in Fig. 2b - only very schematically - outlined that extend through the crank of the crank mechanism 4 has two holes 20 and 21. Through these holes 20, 21, the bearings can be supplied with lubricating oil, which connect the bearing pins 18 and 19 to rolling stand 2 and crank mechanism 4 with the push rod 7.

Durch die Schmierölversorgung über die Bohrungen 20, 21 kann auf einen Produktionsstop zwecks Nachschmieren der Lager verzichtet werden; das Nachschmieren kann vielmehr während des Betriebs des Antriebssystems erfolgen. Ein weiterer besonderer Vorteil, der mit dieser Ausgestaltung erreicht werden kann, ist der, dass eine zuverlässige Trennung von Schmieröl und Kühlschmierstoff erreicht werden kann.Through the supply of lubricating oil through the holes 20, 21 can be dispensed with a production stop for relubrication of the bearings; relubrication can rather be done during operation of the drive system. Another particular advantage that can be achieved with this embodiment is that a reliable separation of lubricating oil and coolant can be achieved.

In den Figuren 3a und 3b ist eine Ausführungsform des Antriebssystems 1 gemäß der Erfindung gezeigt. Hier sind am Walzgerüst 2 seitlich zwei Schubstangen 7 und 7' angeordnet, die ebenfalls seitlich und fliegend am Kurbeltrieb 4 gelagert sind. Die Mittenebene 15 des Walzgerüsts 2, die Mittenebene 16 des Kurbeltriebs 4 und die Mittenebene 17 der Gegenmasse 8 sind identisch. Damit wird erreicht, dass keine nicht ausgeglichenen Massenmomente entstehen, wenn sich die Masse des Walzgerüsts 2 bzw. die Masse des Ausgleichsgewichts 6 und die Gegenmasse 8 relativ zueinander bewegen.FIGS. 3a and 3b show an embodiment of the drive system 1 according to the invention. Here are the rolling stand 2 side two push rods 7 and 7 'are arranged, which are also mounted laterally and flying on the crank mechanism 4. The center plane 15 of the roll stand 2, the center plane 16 of the crank mechanism 4 and the center plane 17 of the counterweight 8 are identical. This ensures that no unbalanced mass moments arise when the mass of the rolling stand 2 and the mass of the balance weight 6 and the counterweight 8 move relative to each other.

Wie in Fig. 3a zu sehen ist, befinden sich die Zahnräder 9, 10, 11 unterhalb der Walzmitte. Das Ausgleichsgewicht 6 ist im dargestellten Fall als exzentrisch im Zahnrad 9 angeordnete Masse angeordnet; das Ausgleichsgewicht 6 ist somit in das Zahnrad 9 integriert. In gleicher Weise ist die Gegenmasse 8 als exzentrisch angeordnete Masse im Zahnrad 10 angeordnet.As can be seen in Fig. 3a, the gears 9, 10, 11 are below the roller center. The balance weight 6 is arranged in the illustrated case as arranged eccentrically in the gear 9 mass; the balance weight 6 is thus in the gear 9 integrated. In the same way, the counterweight 8 is arranged as eccentrically arranged mass in the gear 10.

Bei der Ausgestaltung gemäß Fig. 4a bzw. Fig. 4b ist zu sehen, dass das Prinzip der fliegend am Kurbeltrieb 4 gelagerten Schubstangen 7 bzw. 7' verlassen ist: Die Schubstangen 7, 7' stehen hier mit zwei Kurbeltrieben 4 und 4' in Verbindung. An der Seite des einen Kurbeltriebs 4 ist die Getriebeeinheit bestehend aus den Zahnradgetrieben 9, 10 und 10, 11 sowie der Antrieb 3 angeordnet. Jedem Kurbeltrieb 4 und 4' mit einem Ausgleichsgewicht 6 bzw. 6' ist eine Gegenmasse 8 bzw. 8' zugeordnet, die zum Massenausgleich mittels der Zahnräder 9, 10, 11 synchronisiert angetrieben wird.In the embodiment according to FIG. 4a or FIG. 4b, it can be seen that the principle of the push rods 7 or 7 'mounted on the crank mechanism 4 has been abandoned: the push rods 7, 7' are here with two crank drives 4 and 4 'in FIG Connection. On the side of a crank mechanism 4, the gear unit consisting of the gear drives 9, 10 and 10, 11 and the drive 3 is arranged. Each crank mechanism 4 and 4 'with a balance weight 6 or 6' is assigned a counterweight 8 or 8 ', which is driven synchronized to balance the mass by means of the gears 9, 10, 11.

Die Resultierende der Fliehkräfte alle Ausgleichsgewichte 6, 6' bzw. Gegengewichte 8, 8' befinden sich durch den symmetrischen Aufbau in der Mittenebene 15 des Walzgerüsts, so dass die ebenfalls in der Mittenebene 15 liegende Massenkraft des Walzgerüsts 2 optimal ausgeglichen werden kann.The resultant of the centrifugal forces all balancing weights 6, 6 'and counterweights 8, 8' are due to the symmetrical structure in the center plane 15 of the rolling stand, so that the also lying in the center plane 15 mass force of the roll stand 2 can be optimally balanced.

Der alternativen Ausgestaltung gemäß den Fig. 5a bzw. 5b ist zu entnehmen, dass auch ein Aufbau realisiert werden kann, bei dem die Wellen 12, 13 und 14 vertikal angeordnet sind; bei den Lösungen gemäß den Figuren 2, 3 und 4 sind diese Wellen hingegen horizontal positioniert.The alternative embodiment according to FIGS. 5a and 5b shows that a construction can also be realized in which the shafts 12, 13 and 14 are arranged vertically; in the solutions according to Figures 2, 3 and 4, however, these waves are positioned horizontally.

Das vorgeschlagene Antriebssystem 1 hat damit einen sehr einfachen Aufbau, was nur geringe Investitionskosten verursacht. Femer sind die Instandhaltungsaufwendungen infolge des einfachen Maschinenkonzepts relativ gering. Andererseits ist auch ein guter Ausgleich von Massenkräften und Massenmomenten möglich, so dass ein schwingungsarmer Betrieb des Kaltpilgerwalzwerks ohne hohen Aufwand möglich ist. Die Verfügbarkeit des Walzwerks ist hoch. Die Herstellung kostengünstig gefertigter kaltgepilgerter Rohre in guter Qualität ist somit sichergestellt.The proposed drive system 1 thus has a very simple structure, which causes only low investment costs. Furthermore, the maintenance costs are relatively low due to the simple machine concept. On the other hand, a good balance of inertial forces and mass moments is possible, so that a low-vibration operation of the cold pilger rolling mill is possible without much effort. The availability of the rolling mill is high. The production of low-cost manufactured high-quality cold piled pipes is thus ensured.

Bezugszeichenliste:LIST OF REFERENCE NUMBERS

11
Antriebssystemdrive system
22
Walzgerüstrolling mill
33
Antriebdrive
44
Kurbeltriebcrankshaft
4'4 '
Kurbeltriebcrankshaft
55
Kurbelarmcrank
66
Ausgleichsgewichtcounterweight
6'6 '
Ausgleichsgewichtcounterweight
77
Schubstangepushrod
7'7 '
Schubstangepushrod
88th
Gegenmasseto ground
8'8th'
Gegenmasseto ground
9, 109, 10
Getriebe (Zahnradgetriebe)Transmission (gear transmission)
10,1110.11
Getriebe (Zahnradgetriebe)Transmission (gear transmission)
99
Zahnradgear
1010
Zahnradgear
1111
Zahnradgear
1212
Wellewave
1313
Wellewave
1414
Wellewave
1515
Mittenebene (Symmetrieebene) des WalzgerüstsCenter plane (symmetry plane) of the roll stand
1616
Mittenebene (Symmetrieebene) des KurbeltriebsCenter plane (symmetry plane) of the crank mechanism
1717
Mittenebene (Symmetrieebene) der GegenmasseCenter plane (symmetry plane) of the countermass
1818
Lagerzapfenpivot
1919
Lagerzapfenpivot
2020
Bohrungdrilling
2121
Bohrungdrilling
2222
Rohrpipe
2323
KaltpilgerwalzenpaarCold pilger roll pair
2424
Walzdornrolling mandrel
2525
Ebenelevel
2626
Ebenelevel
2727
Ebenelevel
RR
Förderrichtungconveying direction

Claims (9)

  1. A drive system (1) for a cold rolling pilger mill, with
    - a rolling stand (2) that is movable back and forth,
    - at least one crank mechanism (4, 4') that is driven by a drive unit (3) and is equipped with a crank arm (5) having a balancing weight (6, 6') to at least partly balance the inertial forces generated by the rolling stand (2) and a driving rod (7, 7') that connects the rolling stand (2) and the crank arm (5) to each other in articulated manner,
    - at least one counterweight (8, 8') disposed rotatably and eccentrically to balance inertial forces and/or inertial moments, and a transmission (9, 10) that synchronizes the movement of the crank mechanism (4, 4') and the counterweight (8, 8')
    characterised in that
    only one counterweight (8, 8') is attached to the crank mechanism (4, 4')
    wherein the plane in which the balancing weight (6, 6') of the crank mechanism (4, 4') moves during rotation and the plane in which the counterweight (8, 8') moves during rotation are identical,
    wherein the crank mechanism (4, 4'), the counterweight (8, 8') and the drive unit (3) are connected to each other via gear mechanisms (9, 10, 11), wherein the drive unit (3) drives a shaft (12) via the gear mechanism (10, 11), the shaft being connected to the counterwight (8, 8'), and wherein the gearwheel (10) of the gear mechanism (10, 11) that is disposed on the shaft (12) drives a shaft (13) via a gearwheel (9), the shaft being connected to the crank mechanism (4, 4'),
    wherein the balancing weight (6, 6') and/or the counterweight (8, 8') is/are disposed as an eccentrically situated mass in one of the gearwheels (9, 10) of the gear mechanisms (9, 10, 11).
  2. The drive system as recited in claim 1,
    characterised in that
    the shaft (13) of the crank mechanism (4, 4'), the shaft (12) of the counterweight (8, 8'), and a shaft (14) of the drive unit (3) lie in one plane.
  3. The drive system as recited in claim 1 or 2,
    characterised in that
    the midplane (15) of the rolling stand (2) and the midplane (16) of the crank mechanism (4, 4') are identical.
  4. The drive system as recited in claim 3,
    characterised in that
    the midplane (16) of the crank mechanism (4, 4') and the midplane (17) of the counterweight (8, 8') are identical.
  5. The drive system as recited in any of claims 1 to 3,
    characterised in that
    the rolling stand (2) and two crank mechanisms (4, 4') situated symmetrically about the midplane (15) of the rolling stand (2) and on either side thereof are connected to one another via two driving rods (7, 7').
  6. The drive system as recited in claim 5,
    characterised in that
    the drive unit (3) connects the two crank mechanisms (4, 4') and the two counterweights (8, 8') attached thereto via gear mechanisms (9, 10, 11), wherein the gear mechanisms (9, 10, 11) are laterally adjacent a crank mechanism (4).
  7. The drive system as recited in any of claims 1 to 6,
    characterised in that
    the shafts (12, 13, 14) of the crank mechanism (4, 4'), of the counterweight (8, 8'), and of the drive unit (3) are disposed horizontally.
  8. The drive system as recited in any of claims 1 to 6,
    characterised in that
    the shafts (12, 13, 14) of the crank mechanism (4, 4'), of the counterweight (8, 8'), and of the drive unit (3) are disposed vertically.
  9. The drive system as recited in any of claims 1 to 6,
    characterised in that,
    the driving rod (7, 7') is supported on bearing journals (18, 19), wherein at least one bearing journal (18, 19) is provided with at least one bore hole (20, 21) for supplying the bearing point between the driving rod (7, 7') and the bearing journal (18, 19) with lubricating oil.
EP03018510A 2002-09-07 2003-08-16 Drive system for a cold pilger mill Expired - Lifetime EP1396292B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10241612A DE10241612B3 (en) 2002-09-07 2002-09-07 Drive system for a cold pilger rolling mill
DE10241612 2002-09-07

Publications (2)

Publication Number Publication Date
EP1396292A1 EP1396292A1 (en) 2004-03-10
EP1396292B1 true EP1396292B1 (en) 2006-10-04

Family

ID=29719542

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03018510A Expired - Lifetime EP1396292B1 (en) 2002-09-07 2003-08-16 Drive system for a cold pilger mill

Country Status (7)

Country Link
US (1) US7073362B2 (en)
EP (1) EP1396292B1 (en)
CN (1) CN1240495C (en)
AT (1) ATE341406T1 (en)
DE (2) DE10241612B3 (en)
ES (1) ES2272866T3 (en)
RU (1) RU2247613C1 (en)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009007465B3 (en) * 2009-02-04 2010-09-30 Sms Meer Gmbh Drive system for a rolling mill, in particular for a cold pilger rolling mill
CN101590504B (en) * 2009-05-05 2012-05-23 西北工业大学 Reinforced pull rod for large computer numerical control pipe bender
DE102009003175A1 (en) * 2009-05-15 2010-11-18 Sandvik Materials Technology Deutschland Gmbh Feed drive for a cold pilger rolling mill
DE102009003172A1 (en) 2009-05-15 2010-12-02 Sandvik Materials Technology Deutschland Gmbh Chuck for a cold pilger rolling mill
DE102009047049A1 (en) 2009-11-24 2011-05-26 Sandvik Materials Technology Deutschland Gmbh Drive for a pilgrim rolling mill
RU2481163C1 (en) * 2011-10-07 2013-05-10 Открытое акционерное общество Акционерная холдинговая компания "Всероссийский научно-исследовательский и проектно-конструкторский институт металлургического машиностроения имени академика Целикова" (ОАО АХК "ВНИИМЕТМАШ") Tube cold-rolling mill stand drive
DE102012112398B4 (en) * 2012-12-17 2018-05-30 Sandvik Materials Technology Deutschland Gmbh Pilger rolling mill with a crank mechanism
RU2578883C1 (en) * 2014-10-07 2016-03-27 Открытое акционерное общество "Электростальский завод тяжелого машиностроения" Pipes cold rolling mill
CN109351777A (en) * 2018-11-21 2019-02-19 杭州淳通新材料科技有限公司 Revolving-rolling type produces and processes seamless conical pipe equipment and its production and processing method
RU2721251C1 (en) * 2019-03-22 2020-05-18 Открытое акционерное общество "Электростальский завод тяжелого машиностроения" Cold rolling mill
DE102022208236A1 (en) 2022-08-08 2024-02-08 Sms Group Gmbh Rolling mill, in particular cold pilgrim rolling mill, overload protection on a rolling mill and method for providing overload protection on a rolling mill

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
DE962062C (en) * 1955-07-15 1957-04-18 Mannesmann Meer Ag Drive for rolling mills, especially cold pilger mills
DE3010526A1 (en) * 1980-03-17 1981-09-24 Mannesmann AG, 4000 Düsseldorf PILGRIM STEP MILL
SU1258536A1 (en) * 1985-04-17 1986-09-23 Ереванский Ордена Трудового Красного Знамени Политехнический Институт Им.К.Маркса Drive for moving tube cold rolling mill working stand
DE3613036C1 (en) * 1986-04-15 1987-08-13 Mannesmann Ag Drive for cold pilger roll mill
DE3706129C1 (en) * 1987-02-23 1988-03-10 Mannesmann Ag Drive for a cold pilger rolling mill with mass and torque compensation
US5076088A (en) * 1986-04-15 1991-12-31 Mannesmann Ag Drive for a pilger cold rolling mill
DE4124691C1 (en) * 1991-07-22 1992-02-27 Mannesmann Ag, 4000 Duesseldorf, De
DE4336422C2 (en) * 1993-10-20 1996-10-24 Mannesmann Ag Crank drive for a cold pilger rolling mill
ATE217550T1 (en) * 1997-10-08 2002-06-15 Sms Demag Ag METHOD AND DEVICE FOR PRODUCING PIPES USING THE COLD PILGRIM STEP METHOD

Also Published As

Publication number Publication date
US20040045334A1 (en) 2004-03-11
DE50305235D1 (en) 2006-11-16
CN1488451A (en) 2004-04-14
ES2272866T3 (en) 2007-05-01
RU2247613C1 (en) 2005-03-10
EP1396292A1 (en) 2004-03-10
US7073362B2 (en) 2006-07-11
DE10241612B3 (en) 2004-01-08
ATE341406T1 (en) 2006-10-15
CN1240495C (en) 2006-02-08

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