EP1396292B1 - Système d'entraînement pour un laminoir à pas de pèlerin à froid - Google Patents

Système d'entraînement pour un laminoir à pas de pèlerin à froid 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
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03018510A
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German (de)
English (en)
Other versions
EP1396292A1 (fr
Inventor
Michael Baensch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SMS Group GmbH
Original Assignee
SMS Meer GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SMS Meer GmbH filed Critical SMS Meer GmbH
Publication of EP1396292A1 publication Critical patent/EP1396292A1/fr
Application granted granted Critical
Publication of EP1396292B1 publication Critical patent/EP1396292B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • 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)

Claims (9)

  1. Système d'entraînement (1) pour un laminoir à pas de pèlerin à froid, avec
    - une cage de laminoir (2) déplacable en va-et-vient,
    - au moins une commande par bielle-manivelle (4, 4') comportant un bras de manivelle (5) avec contrepoids (6, 6') pour la compensation au moins partielle des forces inertielles générées par la cage de laminoir (2) et une bielle (7, 7') reliant entre eux de façon articulée la cage de laminoir (2) et le bras de manivelle (5),
    - au moins une contre-masse (8, 8') disposée de façon rotative excentrique pour la compensation de forces inertielles et/ou de moments d'inertie, et une transmission (9, 10) synchronisant le déplacement de la bielle-manivelle (4, 4') et de la contre-masse, (8, 8'),
    caractérisé en ce que seule une contre-masse (8, 8') unique est associée à la bielle-manivelle (4, 4'),
    le plan dans lequel le contrepoids (6, 6') de la bielle-manivelle (4, 4') se déplace en rotation et le plan dans lequel la contre-masse (8, 8') se déplace étant identiques,
    la bielle-manivelle (4, 4'), la contre-masse (8, 8') et l'entraînement (3) étant reliés entre eux par des transmissions par engrenage (9, 10, 11), l'entraînement (3) entraînant un arbre (12) par l'intermédiaire de la transmission par engrenage (10, 11), et la roue dentée (10) de la transmission par engrenage (10, 11) disposée sur l'arbre (12) entraînant par l'intermédiaire d'une roue dentée (9) un arbre (13), avec lequel est reliée la bielle-manivelle (4, 4'), et
    le contrepoids (6, 6') et/ou la contre-masse (8, 8') étant disposé en tant que masse placée de façon excentrique dans l'une des roues dentées (9, 10) des transmissions par engrenage (9, 10, 11).
  2. Système d'entraînement selon la revendication 1,
    caractérisé en ce que l'arbre (13) de la bielle-manivelle (4, 4'), l'arbre (12) de la contre-masse (8, 8') et un arbre (14) de l'entraînement (3) sont situés dans un plan.
  3. Système d'entraînement selon la revendication 1 ou 2,
    caractérisé en ce que le plan central (15) de la cage de laminoir (2) et le plan central (16) de la bielle-manivelle (4, 4') sont identiques.
  4. Système d'entraînement selon la revendication 3,
    caractérisé en ce que le plan central (16) de la bielle-manivelle (4, 4') et le plan central (17) de la contre-masse (8, 8') sont identiques.
  5. Système d'entraînement selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que la cage de laminoir (2) et deux bielles-manivelles (4, 4') disposées de part et d'autre du plan central (15) de la cage de laminoir (2) et symétriquement à cette dernière sont reliées entre elles par deux bielles (7, 7').
  6. Système d'entraînement selon la revendication 5,
    caractérisé en ce que l'entraînement (3) relie les deux bielles-manivelles (4, 4') et les deux contre-masses (8, 8') associées à ces dernières par l'intermédiaire de transmissions par engrenage (9, 10, 11), les transmissions par engrenage (9, 10, 11) étant disposées au voisinage latéral de l'une des bielles-manivelles (4).
  7. Système d'entraînement selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que les arbres (12, 13, 14) de la bielle-manivelle (4, 4'), de la contre-masse (8, 8') et de l'entraînement (3) sont disposés à l'horizontale.
  8. Système d'entraînement selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que les arbres (12, 13, 14) de la bielle-manivelle (4, 4'), de la contre-masse (8, 8') et de l'entraînement (3) sont disposés à la verticale.
  9. Système d'entraînement selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce que les bielles (7, 7') sont logées sur des tourillons bouts d'arbre (18, 19), au moins un tourillon bout d'arbre (18, 19) étant muni d'au moins un alésage (20, 21) pour l'alimentation de la zone d'appui entre la bielle (7, 7') et le tourillon bout d'arbre (18, 19) avec de l'huile lubrifiante.
EP03018510A 2002-09-07 2003-08-16 Système d'entraînement pour un laminoir à pas de pèlerin à froid Expired - Lifetime EP1396292B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10241612A DE10241612B3 (de) 2002-09-07 2002-09-07 Antriebssystem für ein Kaltpilgerwalzwerk
DE10241612 2002-09-07

Publications (2)

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

Family

ID=29719542

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03018510A Expired - Lifetime EP1396292B1 (fr) 2002-09-07 2003-08-16 Système d'entraînement pour un laminoir à pas de pèlerin à froid

Country Status (7)

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

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009007465B3 (de) * 2009-02-04 2010-09-30 Sms Meer Gmbh Antriebssystem für ein Walzwerk, insbesondere für ein Kaltpilgerwalzwerk
CN101590504B (zh) * 2009-05-05 2012-05-23 西北工业大学 一种用于大型数控弯管机的加强拉杆装置
DE102009003172A1 (de) 2009-05-15 2010-12-02 Sandvik Materials Technology Deutschland Gmbh Spannfutter für eine Kaltpilgerwalzanlage
DE102009003175A1 (de) * 2009-05-15 2010-11-18 Sandvik Materials Technology Deutschland Gmbh Vorschubantrieb für eine Kaltpilgerwalzanlage
DE102009047049A1 (de) 2009-11-24 2011-05-26 Sandvik Materials Technology Deutschland Gmbh Antrieb für eine Pilgerwalzanlage
RU2481163C1 (ru) * 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") Привод клети стана холодной прокатки труб
DE102012112398B4 (de) * 2012-12-17 2018-05-30 Sandvik Materials Technology Deutschland Gmbh Pilgerwalzanlage mit einem Kurbeltrieb
RU2578883C1 (ru) * 2014-10-07 2016-03-27 Открытое акционерное общество "Электростальский завод тяжелого машиностроения" Стан холодной прокатки труб
CN109351777B (zh) * 2018-11-21 2024-10-11 杭州淳通新材料科技有限公司 旋转滚压式生产加工无缝锥形管设备及其生产加工方法
RU2721251C1 (ru) * 2019-03-22 2020-05-18 Открытое акционерное общество "Электростальский завод тяжелого машиностроения" Стан холодной прокатки труб
DE102022208236A1 (de) 2022-08-08 2024-02-08 Sms Group Gmbh Walzwerk, insbesondere Kaltpilgerwalzgerüst, Überlastsicherung an einem Walzwerk sowie Verfahren zur Bereitstellung einer Überlastsicherung an einem Walzgerüst

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE962062C (de) * 1955-07-15 1957-04-18 Mannesmann Meer Ag Antrieb fuer Walzwerke, insbesondere Kaltpilgerwalzwerke
DE3010526A1 (de) * 1980-03-17 1981-09-24 Mannesmann AG, 4000 Düsseldorf Pilgerschrittwalzwerk
SU1258536A1 (ru) * 1985-04-17 1986-09-23 Ереванский Ордена Трудового Красного Знамени Политехнический Институт Им.К.Маркса Привод перемещени клети стана холодной прокатки труб
DE3613036C1 (en) * 1986-04-15 1987-08-13 Mannesmann Ag Drive for cold pilger roll mill
DE3706129C1 (de) * 1987-02-23 1988-03-10 Mannesmann Ag Antrieb fuer ein Kaltpilgerwalzwerk mit Massen- und Momentenausgleich
US5076088A (en) * 1986-04-15 1991-12-31 Mannesmann Ag Drive for a pilger cold rolling mill
DE4124691C1 (fr) * 1991-07-22 1992-02-27 Mannesmann Ag, 4000 Duesseldorf, De
DE4336422C2 (de) * 1993-10-20 1996-10-24 Mannesmann Ag Kurbeltrieb für ein Kaltpilgerwalzwerk
ES2173546T3 (es) * 1997-10-08 2002-10-16 Sms Demag Ag Procedimiento y dispositivo para la fabricacion de tubos segun el procedimiento de paso de peregrino en frio.

Also Published As

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

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