EP0366648B1 - Drive mechanism for cold pilger rolling mills - Google Patents

Drive mechanism for cold pilger rolling mills Download PDF

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Publication number
EP0366648B1
EP0366648B1 EP87903858A EP87903858A EP0366648B1 EP 0366648 B1 EP0366648 B1 EP 0366648B1 EP 87903858 A EP87903858 A EP 87903858A EP 87903858 A EP87903858 A EP 87903858A EP 0366648 B1 EP0366648 B1 EP 0366648B1
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EP
European Patent Office
Prior art keywords
crank
connecting rod
drive mechanism
mass
pinion
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP87903858A
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German (de)
French (fr)
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EP0366648A1 (en
Inventor
Hermann-Josef Klingen
Josef Gerretz
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Vodafone GmbH
Original Assignee
Mannesmann AG
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Application filed by Mannesmann AG filed Critical Mannesmann AG
Priority to AT87903858T priority Critical patent/ATE71315T1/en
Priority claimed from CA000540656A external-priority patent/CA1327134C/en
Priority to SU894742630A priority patent/RU1799299C/en
Publication of EP0366648A1 publication Critical patent/EP0366648A1/en
Application granted granted Critical
Publication of EP0366648B1 publication Critical patent/EP0366648B1/en
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    • 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 for a cold pilger rolling mill with mass and moment compensation according to the preamble of claim 1.
  • Such a cold pilger rolling mill is known from DE-AS-27 40 729, the crank mechanism being arranged laterally offset from the rolling mill.
  • the crank is connected via a crankshaft crank to the balancing mass for torque compensation arranged above the crank mechanism. This is 90 ° out of phase with the crank, and the reciprocating movement is made possible by parallel guides.
  • the rolling mill itself is coupled via a long connecting rod, which is supported on the crankshaft crank on one side.
  • the object of the invention is to develop a compact, cost-effective and as little stressed design for the drive from the existing knowledge about the mass and torque compensation of the double slide.
  • the overall vertical design makes it possible for the rolling stand to engage on one side and thus be guided over the entire gear unit. This eliminates the need for a connecting rod that connects the roll stand to the gear unit.
  • the paddock engages the slide directly below the roll stand.
  • the mass required for torque compensation is provided by the coupling itself.
  • the center of gravity of the paddock was placed beyond point D of the positive guidance.
  • the total mass of the coupling is reduced to point D, which in turn keeps the dimensions of the coupling small (flat design).
  • the paddock rotates with it and contributes with its moment of inertia ⁇ Ko to an improved uniformity of the overall system. Due to the design and arrangement of the coupling, the focal planes of torque compensation, mass compensation and the roll stand are brought together as closely as possible. This results in a compact design and a relatively low load within the gear unit.
  • the slide guide and positive guide are approximately in the same plane. This was made possible by an interruption in the forced operation.
  • the positive guidance is only required in the end positions in order to maintain the direction of rotation of the coupling and crank.
  • the embodiment according to claim 3 represents a modified embodiment, namely with a planetary crank gear (PKG).
  • the structure of the PKG is almost identical to the previously described first version of a double slide gear (DG).
  • the difference to the DG is that there is no forced guidance.
  • This is replaced by a planetary gear, which consists of a pinion and an internally toothed gear.
  • the pinion is firmly connected to the crank pin and rolls on the external internal teeth due to the rotating movement of the crank.
  • the superimposition of the rotational movement of the pinion and crank results in an exactly opposite direction of rotation of the coupling.
  • the rolling stand (WG) can be moved in a slide guide (Sch).
  • the roll stand is connected to the coupling (KO), which is arranged below the roll stand, and runs about a vertical axis via a pin.
  • the coupling (KO) has a cam roller (1), by means of which the coupling (KO) is guided in positive guides (2).
  • these positive guides (2) are only provided in the area of the end positions of the cam roller (1) or the coupling (KO).
  • the coupling (KO) is connected to the crank (KU) via the crank pin (3).
  • Figure lb shows the movements of the crank (KU), coupling (KO) and slide (4) (ie the rolling stand).
  • FIGS. 3a and b which show the coupling (KO) and the crank (KU) in different positions relative to one another, also serve for a better understanding of the movement sequence.
  • the crank (KU) is connected to the drive (8) (not shown) via a corresponding toothing (5-7).
  • the second embodiment shown in FIGS. 4a, b and 5 differs from the first embodiment in that a planetary crank arrangement is provided instead of the positive guides.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Metal Rolling (AREA)
  • Retarders (AREA)

Abstract

In a drive mechanism for cold pilger rolling mills with mass and torque balancing, the crank being driven is connected by a connecting rod to the roll stand. In order to obtain a drive mechanism which is compact, economical, and subjected to minimal stress, the roll stand (WG) is arranged directly above the crank drive (KU) and the connecting rod (KO) is mounted directly on the crank pin (3). Torque balancing is achieved by the total mass of the connecting rod (KO) and mass balancing by the total mass of the crank drive (KU).

Description

Die Erfindung betrifft einen Antrieb für ein Kaltpilgerwalzwerk mit Massen- und Momentenausgleich gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a drive for a cold pilger rolling mill with mass and moment compensation according to the preamble of claim 1.

Aus der DE-AS-27 40 729 ist ein derartiges Kaltpilgerwalzwerk bekannt, wobei der Kurbeltrieb seitlich versetzt zum Walzwerk angeordnet ist. Die Kurbel ist dabei über eine Kurbelwellenkröpfung mit der über dem Kurbeltrieb angeordneten Ausgleichsmasse für den Momentenausgleich verbunden. Diese ist um 90° phasenverschoben mit der Kurbel angeordnet, und die hinund hergehende Bewegung wird durch parallele Führungen ermöglicht. Das Walzwerk selbst ist über eine lange Verbindungsstange, an der einen Seite an der Kurbelwellenkröpfung gelagert, gekoppelt.Such a cold pilger rolling mill is known from DE-AS-27 40 729, the crank mechanism being arranged laterally offset from the rolling mill. The crank is connected via a crankshaft crank to the balancing mass for torque compensation arranged above the crank mechanism. This is 90 ° out of phase with the crank, and the reciprocating movement is made possible by parallel guides. The rolling mill itself is coupled via a long connecting rod, which is supported on the crankshaft crank on one side.

Aufgabe der Erfindung ist es, aus den bereits vorhandenen Erkenntnissen über den Massen- und Momentenausgleich des Doppelschiebers eine kompakte, kostengünstige und möglichst gering beanspruchte Bauweise für den Antrieb zu entwickeln.The object of the invention is to develop a compact, cost-effective and as little stressed design for the drive from the existing knowledge about the mass and torque compensation of the double slide.

Gelöst wird diese Aufgabe erfindungsgemäß mit den Merkmalen im Kennzeichen des Anspruchs 1.This object is achieved according to the invention with the features in the characterizing part of claim 1.

Vorzugsweise Weiterbildungen ergeben sich aus den Unteransprüchen.Further developments preferably result from the subclaims.

Die insgesamt vertikale Bauweise macht es möglich, daß das Walzgerüst einseitig angreifen und somit auf der gesamten Getriebeeinheit geführt werden kann. Dadurch kann eine Verbindungsstange, die das Walzgerüst mit der Getriebeeinheit verbindet, entfallen.The overall vertical design makes it possible for the rolling stand to engage on one side and thus be guided over the entire gear unit. This eliminates the need for a connecting rod that connects the roll stand to the gear unit.

Die Koppel greift direkt unterhalb des Walzgerüstes am Schieber an.The paddock engages the slide directly below the roll stand.

Die für den Momentenausgleich benötigte Masse wird durch die Koppel selbst gestellt. Dabei wurde der Schwerpunkt der Koppel über den Punkt D der Zwangsführung hinaus gelegt. Die Gesamtmasse der Koppel wird auf den Punkt D reduziert, wodurch die Abmessungen der Koppel wiederum klein gehalten werden (flache Bauweise).The mass required for torque compensation is provided by the coupling itself. The center of gravity of the paddock was placed beyond point D of the positive guidance. The total mass of the coupling is reduced to point D, which in turn keeps the dimensions of the coupling small (flat design).

Die Koppel dreht sich mit

Figure imgb0001
und trägt mit ihrem Massenträgheitsmoment ⊖Ko zu einer verbesserten Gleichförmigkeit des Gesamtsystems bei. Durch die Ausführung und Anordnung der Koppel werden die Schwerpunktebenen des Momentenausgleichs, des Massenausgleichs und des Walzgerüstes möglichst nahe zusammengebracht. Damit erreicht man eine kompakte Bauweise und eine relativ geringe Belastung innerhalb der Getriebeeinheit.The paddock rotates with it
Figure imgb0001
and contributes with its moment of inertia ⊖ Ko to an improved uniformity of the overall system. Due to the design and arrangement of the coupling, the focal planes of torque compensation, mass compensation and the roll stand are brought together as closely as possible. This results in a compact design and a relatively low load within the gear unit.

Die Schieberführung und Zwangsführung liegen annähernd in der gleichen Ebene. Dies wurde durch eine Unterbrechung der Zwangsführung ermöglicht. Die Zwangsführung wird nur in den Endlagen benötigt, um den Drehsinn von Koppel und Kurbel aufrechtzuerhalten. Durch die Lagerung der Koppel auf der Kurbel wurde eine Optimaleinstellung für die geometrische Anordnung und die Belastung der Lager und Zapfen gefunden.The slide guide and positive guide are approximately in the same plane. This was made possible by an interruption in the forced operation. The positive guidance is only required in the end positions in order to maintain the direction of rotation of the coupling and crank. By mounting the coupler on the crank, an optimal setting for the geometric arrangement and the load on the bearings and pins was found.

Die Ausführung nach Anspruch 3 stellt eine abgewandelte Ausführung dar, und zwar mit einem Planeten-Kurbel-Getriebe (PKG). Der Aufbau des PKG ist nahezu identisch mit der vorher beschriebenen ersten Ausführung eines Doppelschiebergetriebes (DG). Der Unterschied zum DG liegt darin, daß die Zwangsführung entfällt. Diese wird durch ein Planetengetriebe ersetzt, das aus einem Ritzel und einem innenverzahnten Zahnrad besteht. Das Ritzel sitzt fest verbunden auf dem Kurbelzapfen und wälzt sich durch die Drehbewegung der Kurbel auf die außenliegende Innenverzahnung ab. Durch die Überlagerung der Drehbewegung von Ritzel und Kurbel kommt es zu einem genau entgegengesetzten Drehsinn der Koppel. Diese entgegengesetzten Drehbewegungen mit der Winkelgeschwindigkeit

Figure imgb0002
und unter Einhaltung der vorliegenden geometrischen Bedingungen haben eine Schiebung des Punktes B (Walzgerüst) zur Folge.The embodiment according to claim 3 represents a modified embodiment, namely with a planetary crank gear (PKG). The structure of the PKG is almost identical to the previously described first version of a double slide gear (DG). The The difference to the DG is that there is no forced guidance. This is replaced by a planetary gear, which consists of a pinion and an internally toothed gear. The pinion is firmly connected to the crank pin and rolls on the external internal teeth due to the rotating movement of the crank. The superimposition of the rotational movement of the pinion and crank results in an exactly opposite direction of rotation of the coupling. These opposite rotational movements with the angular velocity
Figure imgb0002
and in compliance with the existing geometrical conditions result in a shift of point B (roll stand).

Folgend werden die Nachteile des herkömmlichen DG und die Vorteile des erfindungsgemäßen DG und des PKG stichwortartig gegenübergestellt.

Figure imgb0003
Figure imgb0004
 The disadvantages of the conventional DG and the advantages of the DG and the PKG according to the invention are compared in brief.
Figure imgb0003
Figure imgb0004

Die Erfindung soll nachfolgend anhand der Zeichnungen erläutert werden, die zwei Ausführungsbeispiele darstellen. Dabei zeigt:

  • Figur 1a, b schematisch einen Schnitt auf eine Aufsicht auf die erste Ausführung des erfindungsgemäßen Antriebes (Doppelschiebergetriebe),
  • Figur 2 einen Querschnitt durch eine konstruktive Ausführung dieses ersten Antriebes,
  • Figur 3a, b die Bewegung von Koppel und Kurbel in zwei Stellungen,
  • Figur 4a, b schematisch einen Schnitt und eine Aufsicht auf eine zweite Ausführung des erfindungsgemäßen Antriebes (Planeten-Kurbel-Getriebe) und
  • Figur 5 einen Querschnitt durch eine konstruktive Ausführung dieses zweiten Antriebes.
The invention will be explained below with reference to the drawings which show two exemplary embodiments. It shows:
  • Figure 1a, b schematically shows a section of a top view of the first embodiment of the drive according to the invention (double slide transmission),
  • FIG. 2 shows a cross section through a design of this first drive,
  • 3a, b the movement of the coupling and crank in two positions,
  • Figure 4a, b schematically shows a section and a plan view of a second embodiment of the drive according to the invention (planetary crank gear) and
  • Figure 5 shows a cross section through a design of this second drive.

Zunächst soll die erste Ausführung mit dem sog. Doppelschiebergetriebe erläutert werden.First, the first version with the so-called double slide gear is to be explained.

Das Walzgerüst (WG) ist in einer Schieberführung (Sch) bewegbar. Über einen Zapfen ist das Walzgerüst mit der Koppel (KO) verbunden, die unterhalb des Walzgerüstes angeordnet ist, und um eine vertikale Achse läuft.The rolling stand (WG) can be moved in a slide guide (Sch). The roll stand is connected to the coupling (KO), which is arranged below the roll stand, and runs about a vertical axis via a pin.

Wie sich aus den Figuren 1a, b und 2 ergibt, weist die Koppel (KO) eine Kurvenrolle (1) auf, mittels der die Koppel (KO) in Zwangsführungen (2) geführt ist. Diese Zwangsführungen (2) sind allerdings nur im Bereich der Endstellungen der Kurvenrolle (1) bzw. der Koppel (KO) vorgesehen. Über den Kurbelzapfen (3) ist die Koppel (KO) mit der Kurbel (KU) verbunden. Die Figur lb zeigt die Bewegungen von Kurbel (KU), Koppel (KO) und Schieber (4) (d.h. des Walzgerüstes). In diesen Figuren 1a, b sowie den folgenden Figuren 3a- 4b bedeuten:
x und y die Verschiebekoordinaten,
SWG, SKo und SAG die Schwerpunkte des Walzgerüstes
WG, der Koppel KO und der Ausgleichsmasse MA,

Figure imgb0005
und φ die Drehrichtungen von WG, KO und KU,
R die Radien der Anlenkungen zwischen den Verbindungen WG, KO und KU,
Sch die Führung für das Walzgerüst WG und
Z die vertikale Achse, in der Walzwerk, Koppel und Kurbel liegen.As can be seen from FIGS. 1a, b and 2, the coupling (KO) has a cam roller (1), by means of which the coupling (KO) is guided in positive guides (2). However, these positive guides (2) are only provided in the area of the end positions of the cam roller (1) or the coupling (KO). The coupling (KO) is connected to the crank (KU) via the crank pin (3). Figure lb shows the movements of the crank (KU), coupling (KO) and slide (4) (ie the rolling stand). In these figures 1a, b and the following figures 3a-4b:
x and y the displacement coordinates,
S WG , S Ko and S AG focus on the rolling stand
WG, the Koppel KO and the balancing mass MA,
Figure imgb0005
and φ the directions of rotation of WG, KO and KU,
R the radii of the linkages between the connections WG, KO and KU,
Sch the guide for the WG and mill stands
Z the vertical axis in which the rolling mill, coupling and crank lie.

Zum besseren Verständnis des Bewegungsablaufes dienen auch die Figuren 3a und b, die die Koppel(KO) und die Kurbel (KU) in verschiedenen Stellungen zueinander zeigen. Die Kurbel (KU) ist - wie die Figur 2 zeigt -über eine entsprechende Verzahnung (5-7) mit dem nicht dargestellten Antrieb (8) verbunden.FIGS. 3a and b, which show the coupling (KO) and the crank (KU) in different positions relative to one another, also serve for a better understanding of the movement sequence. As shown in FIG. 2, the crank (KU) is connected to the drive (8) (not shown) via a corresponding toothing (5-7).

Die zweite - in den Figuren 4a, b und 5 dargestellte - Ausführung weicht insoweit von der ersten Ausführung ab, als anstelle der Zwangsführungen eine Planeten-Kurbel-Anordnung vorgesehen ist.The second embodiment shown in FIGS. 4a, b and 5 differs from the first embodiment in that a planetary crank arrangement is provided instead of the positive guides.

Auf dem Kurbelzapfen (3) der Kurbel (KU) ist fest ein Ritzel (9) angeordnet, das sich an einem, die Kurbel (KU) umgebenden, innenverzahnten Zahnrad (10) abwälzt. Wie die Figur 4b zeigt, wird durch diese Anordnung erreicht, daß infolge der Überlagerungsbewegung von Kurbel (KU) und Ritzel (9) die Koppel (KO) eine gegenläufige Bewegung ausführt.
Die Schiebung des Punktes B am Walzgerüst erfolgt aus der kinematischen Betrachtung für gleich große, entgegengesetzte Drehbewegungen unter Berücksichtigung der auf Figur 4b vorliegenden Geometrie.On the crank pin (3) of the crank (KU) there is a fixed pinion (9) which rolls on an internally toothed gear (10) surrounding the crank (KU). As shown in FIG. 4b, this arrangement ensures that the coupling (KO) executes an opposite movement as a result of the superimposed movement of the crank (KU) and pinion (9).
The point B on the roll stand is shifted from the kinematic consideration for the same, opposite rotary movements taking into account the geometry present in FIG. 4b.

Claims (3)

1. A drive mechanism for a cold pilger rolling mill with mass and torque balancing, wherein the driven crank is connected to the roller stand by a connecting rod,
characterised in that
the roller stand (WG) is located directly above the crank mechanism (KU) and the connecting rod (KO) is mounted directly on the crank pin (3), the total mass of the connecting rod (KO) taking on the torque balancing and the total mass of the crank (KU) assuming the mass balancing.
2. A drive mechanism according to Claim 1,
characterised in that
the connecting rod (KO) is guided in restraint guides in the region of its extreme positions of movement.
3. A drive mechanism according to Claim 1,
characterised in that
the crank (KU) is constructed as part of a planet gear, that a pinion (9) is located on the crank pin (3) and connected securely thereto, which pinion rolls on an internal-toothed gear wheel (10) surrounding the crank (KU) in such a manner that the superposition of the rotational motion of the pinion and crank (KU) imparts to the connecting rod (KO) an opposing rotational motion.
EP87903858A 1986-04-15 1987-06-18 Drive mechanism for cold pilger rolling mills Expired - Lifetime EP0366648B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AT87903858T ATE71315T1 (en) 1986-04-15 1987-06-18 DRIVE FOR A COLD PILING ROLLING MILL.
SU894742630A RU1799299C (en) 1987-06-18 1989-12-15 Cold tube-rolling mill

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE3613036A DE3613036C1 (en) 1986-04-15 1986-04-15 Drive for cold pilger roll mill
PCT/DE1987/000277 WO1988010160A1 (en) 1986-04-15 1987-06-18 Drive mechanism for cold pilger rolling mills
CA000540656A CA1327134C (en) 1986-04-15 1987-06-26 Drive system for a cold pilger rolling mill

Publications (2)

Publication Number Publication Date
EP0366648A1 EP0366648A1 (en) 1990-05-09
EP0366648B1 true EP0366648B1 (en) 1992-01-08

Family

ID=25671397

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87903858A Expired - Lifetime EP0366648B1 (en) 1986-04-15 1987-06-18 Drive mechanism for cold pilger rolling mills

Country Status (5)

Country Link
EP (1) EP0366648B1 (en)
JP (1) JPH07108407B2 (en)
AT (1) ATE71315T1 (en)
DE (1) DE3613036C1 (en)
WO (1) WO1988010160A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3706129C1 (en) * 1987-02-23 1988-03-10 Mannesmann Ag Drive for a cold pilger rolling mill with mass and torque compensation
DE3613036C1 (en) * 1986-04-15 1987-08-13 Mannesmann Ag Drive for cold pilger roll mill
DE10147046C2 (en) * 2001-09-25 2003-10-02 Sms Meer Gmbh Drive system for a rolling mill
DE10241612B3 (en) * 2002-09-07 2004-01-08 Sms Meer Gmbh Drive system for a cold pilger rolling mill
DE10311144B3 (en) * 2003-03-14 2004-10-28 Sms Meer Gmbh Method for producing a tube with an internal profile and device for carrying out the method
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

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2541324A (en) * 1945-04-20 1951-02-13 Bell Telephone Labor Inc Motion translating mechanism
US4052898A (en) * 1976-09-13 1977-10-11 Wean United, Inc. Crank drive system for cold pilger mills drive or the like
SU735342A1 (en) * 1977-01-28 1980-05-27 Днепропетровский Ордена Трудового Красного Знамени Металлургический Институт Cold tube-rolling mill stand drive
SU956081A1 (en) * 1980-12-11 1982-09-07 Уральский ордена Трудового Красного Знамени политехнический институт им.С.М.Кирова Drive for moving rolling stand of tube cold rolling mill
DE3613036C1 (en) * 1986-04-15 1987-08-13 Mannesmann Ag Drive for cold pilger roll mill

Also Published As

Publication number Publication date
JPH07108407B2 (en) 1995-11-22
WO1988010160A1 (en) 1988-12-29
EP0366648A1 (en) 1990-05-09
JPH03501362A (en) 1991-03-28
ATE71315T1 (en) 1992-01-15
DE3613036C1 (en) 1987-08-13

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