EP0707901A1 - Mécanisme à manivelle pour un laminoir à pas de pélerin à froid - Google Patents

Mécanisme à manivelle pour un laminoir à pas de pélerin à froid Download PDF

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Publication number
EP0707901A1
EP0707901A1 EP94250236A EP94250236A EP0707901A1 EP 0707901 A1 EP0707901 A1 EP 0707901A1 EP 94250236 A EP94250236 A EP 94250236A EP 94250236 A EP94250236 A EP 94250236A EP 0707901 A1 EP0707901 A1 EP 0707901A1
Authority
EP
European Patent Office
Prior art keywords
crank
cold pilger
cranks
rolling mill
drive
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.)
Granted
Application number
EP94250236A
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German (de)
English (en)
Other versions
EP0707901B1 (fr
Inventor
Michael Baensch
Ralf Bonsels
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.)
Vodafone GmbH
Original Assignee
Mannesmann AG
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 Mannesmann AG filed Critical Mannesmann AG
Publication of EP0707901A1 publication Critical patent/EP0707901A1/fr
Application granted granted Critical
Publication of EP0707901B1 publication Critical patent/EP0707901B1/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
    • 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 cold pilger rolling mill with a reciprocating roll stand, which is coupled to the crank pin of two cranks by means of two push rods, and whose inertial forces can be at least partially compensated for by counterweights, which in the form of centrifugal weights are eccentric to the axis of rotation of the cranks by 180 degrees to the articulation point of the Push rods are offset on the cranks.
  • the back and forth movement of the mill stand of conventional cold pilger rolling mills is generated by different crank drive designs.
  • the large moving inertial masses of the roll stands with the rollers generate very large inertial forces, which make countermeasures necessary to reduce the vibration emission.
  • the countermeasures are limited to attaching counterweights to the crank of the crank mechanism, which, however, only result in poor mass balancing and are not suitable for preventing the vibration emission.
  • crank mechanism of a cold pilger rolling mill in that it consists of three shafts arranged parallel to one another and equidistant from one another, of which the middle shaft, which is designed as a crankshaft, has its crank pin with the push rod that can be coupled to the roll stand connected is.
  • a main mass is offset eccentrically on the crank, while there are additional masses on the other two shafts, which are to compensate for the total inertia mass of the roll stand.
  • the transmission formed from crank operation and counterweights is divided into two mirror-inverted transmission parts arranged in a plane perpendicular to the rolling axis, which are connected to one another via the shaft of a common drive train consisting of a motor, clutch and bevel gear transmission arranged below the rolling plane are connected, wherein the axes of rotation of the gear parts are arranged parallel to one another and horizontally and the cranks of the two gear parts have an opposite direction of rotation.
  • a crank operation which consists of two partial transmissions arranged on the right and left of the rolling center, the axes of rotation of the shafts of the partial transmissions lying horizontally, with the exception of the drive shaft preferably in a common plane.
  • the division into two gear parts enables free passage for the rolled tube, even of large dimensions, the drives being arranged below or above the roller plane. This means that only flat foundations are required.
  • crank drive arrangement allows the use of non-offset thrust cranks as a rolling stand drive, which was not possible with previous drives, for example of the MEER type, because the tube produced in the cold pilger process had to be passed over the crankshaft.
  • the drive of the cold pilger rolling mill has a drive motor arranged below the roll plane with a drive shaft parallel to the roll axis, which is connected with the interposition of a clutch to a transfer case, the halves of the output shaft of which run perpendicular to the roll axis and horizontally running, the drive torque in initiate the transmission parts.
  • the pipe produced only has to be guided over the lower-lying drive, while the crank drives are arranged half on both sides of the pipe.
  • centrifugal weights are arranged on shafts parallel to the axis of rotation of the cranks of each transmission part to compensate for remaining inertia forces, which are intermeshed via spur gears with spur gears arranged on the crank mechanism in such a way that the centrifugal weights of the cranks and the circulate additional counterweights in opposite directions.
  • the centrifugal weights on the cranks of the gear parts balance the centrifugal forces of the rotating masses of the crank mechanism and push rod.
  • An additional proportion of centrifugal weight on each crank and this proportion of equal centrifugal weights on intermediate shafts rotating in opposite directions with the speed of the cranks enable the oscillating first-order proportion of inertia force of the roll stand and the push rod to be completely balanced.
  • the additional flyweights of each gear part can also be distributed over two parallel shafts, which are arranged synchronously on both sides of the divided crank drive of each gear part via spur gears.
  • crank mechanism solves the problem by the following effects for compensating the mass effects:
  • the centrifugal weights on the cranks initially balance the centrifugal forces of the rotating masses of the crank mechanism and push rod.
  • the special arrangement of the gear parts prevents the creation of mass moments due to the centrifugal weights, since the mass moments remaining in the crank drive parts compensate each other.
  • cranks The opposite movement of the cranks has the effect that the mass moments of the push rods are compensated for.
  • Eccentric flywheels arranged eccentrically on the shafts connecting the drive train with the transmission parts compensate for the oscillating inertial forces of the second order.
  • a flywheel can be provided on the drive shaft, which smoothes the speed curve of the crankshaft and thus the crank mechanism.
  • 1 denotes the reciprocating roll stand in which the cold pilger roll pair 2 is received.
  • a push rod 4 is arranged on both sides at 3 on both sides, the opposite side of which is mounted at 5 on the crank pin 6, each with a crank 7, which in turn is mounted at 8 and 9 on the housing (not shown).
  • two mirror-image gear parts are to be provided on both sides of an imaginary plane running perpendicularly through the rolling axis 10, which include both the crank 7 and the other drive parts.
  • a flyweight 11 On each crank of each gear part sits 180 degrees to the crank pin 6 offset eccentrically, a flyweight 11, which is so large in the sum of both flyweights 11 of both gear parts that all rotating and oscillating inertia forces of the first order are balanced.
  • the drive train consists, as the lower half of the drawing of Figure 1, of the motor 12, the clutch 13 and the bevel gear 14, which distributes the drive torque to the two aligned half shafts 15a and 15b, which run perpendicular to the drive train and horizontally.
  • Each of the half shafts 15a, 15b carries a flywheel mass in the form of a flywheel 16 for smoothing the speed curve of the crankshaft.
  • the half shafts 15a and 15b are mounted at 17 and each carry a spur gear 18 which, in the exemplary embodiment, meshes with a spur gear 19 with a ratio of 4: 1 on the crank mechanism 7 and sets it in rotation.
  • the flywheels 16 and the flyweights 11 rotate in the direction of the arrow at synchronized speeds and in this way enable compensation.
  • crank drive arrangement shown in Figure 2 allows an even better compensation by additional centrifugal weights 20, which together with the centrifugal weights 11 on the two cranks 7, the centrifugal forces of the rotating masses of crank and push rod and the oscillating Compensate for the first order inertia force component of the roll stand and push rod.
  • the additional flyweights 20 are arranged on shafts 21 which are arranged parallel to the axis of rotation of the cranks 7 in the same horizontal plane and at the same time each carry a spur gear 22 which on the one hand with the spur gears 18 of the drive half-shafts 15a and 15b and on the other hand with the spur gears 19th Comb on the cranks 7 and transfer the drive torque with the appropriate gear ratio.
  • the flywheels 16 arranged on the drive shafts 15a and 15b are arranged eccentrically in such a way that they compensate for the second-order oscillating inertial forces when the speed is doubled compared to the crank drive speed. Similar components are identified in the same way in FIG.
  • FIG. 3 shows a mechanism which, even with the same direction of rotation of the two cranks 7, enables a complete compensation of the mass forces and moments of inertia of the first order, but then does not have any compensation of the mass moments of the push rods.
  • the additional flyweights 20a and 20b are divided into two shafts 21a and 21b, which are arranged on both sides and parallel to the axis of rotation of the cranks 7. Both flyweights 20a and 20b rotate in the opposite direction to the crank rotation direction, the driving torque being distributed over the spur gears 18, 22a, 19 and 22b.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Retarders (AREA)
  • Metal Rolling (AREA)
EP94250236A 1993-10-20 1994-09-28 Mécanisme à manivelle pour un laminoir à pas de pélerin à froid Expired - Lifetime EP0707901B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4336422 1993-10-20
DE4336422A DE4336422C2 (de) 1993-10-20 1993-10-20 Kurbeltrieb für ein Kaltpilgerwalzwerk

Publications (2)

Publication Number Publication Date
EP0707901A1 true EP0707901A1 (fr) 1996-04-24
EP0707901B1 EP0707901B1 (fr) 1998-12-23

Family

ID=6500999

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94250236A Expired - Lifetime EP0707901B1 (fr) 1993-10-20 1994-09-28 Mécanisme à manivelle pour un laminoir à pas de pélerin à froid

Country Status (7)

Country Link
US (1) US5540076A (fr)
EP (1) EP0707901B1 (fr)
JP (1) JPH07164024A (fr)
KR (1) KR100295951B1 (fr)
CN (1) CN1052926C (fr)
DE (2) DE4336422C2 (fr)
RU (1) RU2107565C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101228003B (zh) * 2005-07-07 2011-04-27 德国索菲纳有限公司 用于磨削和/或精加工工件的装置

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE217550T1 (de) * 1997-10-08 2002-06-15 Sms Demag Ag Verfahren und vorrichtung zur herstellung von rohren nach dem kaltpilgerschrittverfahren
DE10147046C2 (de) 2001-09-25 2003-10-02 Sms Meer Gmbh Antriebssystem für ein Walzwerk
DE10241612B3 (de) * 2002-09-07 2004-01-08 Sms Meer Gmbh Antriebssystem für ein Kaltpilgerwalzwerk
DE10248136B3 (de) * 2002-10-12 2004-05-06 Sms Meer Gmbh Verfahren und Vorrichtung zum Herstellen eines sich längserstreckenden Körpers
JP2004195574A (ja) * 2002-12-17 2004-07-15 Jon Zen 食肉スライサ
DE10311144B3 (de) * 2003-03-14 2004-10-28 Sms Meer Gmbh Verfahren zum Herstellen eines Rohres mit einer Innenprofilierung und Vorrichtung zur Durchführung des Verfahrens
CN101234399B (zh) * 2008-03-06 2012-05-30 中国重型机械研究院 冷轧管机的曲轴-双偏心质量水平平衡方法
CN101722189B (zh) * 2008-10-31 2013-05-08 扬州诚德钢管有限公司 大型冷轧无缝钢管机及轧制方法
DE102009007465B3 (de) 2009-02-04 2010-09-30 Sms Meer Gmbh Antriebssystem für ein Walzwerk, insbesondere für ein Kaltpilgerwalzwerk
RU2385779C1 (ru) * 2009-05-14 2010-04-10 Открытое акционерное общество "Электростальский завод тяжелого машиностроения" Стан холодной прокатки труб
DE102009003175A1 (de) 2009-05-15 2010-11-18 Sandvik Materials Technology Deutschland Gmbh Vorschubantrieb für eine Kaltpilgerwalzanlage
DE102009003172A1 (de) 2009-05-15 2010-12-02 Sandvik Materials Technology Deutschland Gmbh Spannfutter für eine Kaltpilgerwalzanlage
DE102009047049A1 (de) * 2009-11-24 2011-05-26 Sandvik Materials Technology Deutschland Gmbh Antrieb für eine Pilgerwalzanlage
RU2441723C1 (ru) * 2010-09-07 2012-02-10 Галина Ивановна Гусева Рабочая клеть холодно-пильгерного стана
DE102011052739B4 (de) * 2011-08-16 2017-03-02 Sandvik Materials Technology Deutschland Gmbh 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
RU2539882C1 (ru) * 2013-06-19 2015-01-27 Владислав Архипович Мироненко Рабочая линия холодно-пильгерного стана
JP6369836B2 (ja) * 2014-10-15 2018-08-08 株式会社三益 圧延装置及び圧延方法
CN104889172A (zh) * 2015-05-28 2015-09-09 潘益忠 一种左右独立对称式冷轧管轧管机轧制中减速机构
CN105964705A (zh) * 2016-07-08 2016-09-28 中国重型机械研究院股份公司 一种大型冷轧管机的送进同步机构及其同步方法
CN110722003B (zh) * 2018-07-17 2024-11-22 韩静涛 一种复合锻轧金属管成形机
RU2721251C1 (ru) * 2019-03-22 2020-05-18 Открытое акционерное общество "Электростальский завод тяжелого машиностроения" Стан холодной прокатки труб
CN118080569B (zh) * 2024-04-18 2024-08-20 中国重型机械研究院股份公司 一种冷轧管机用三齿双扇曲柄连杆机构及使用方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2057351A (en) * 1933-12-11 1936-10-13 Smith Corp A O Frame transferring mechanism and drive therefor
US3030835A (en) * 1958-06-06 1962-04-24 Blaw Knox Co Tube rolling machine
FR2477912A1 (fr) * 1980-03-17 1981-09-18 Mannesmann Ag Laminoir a pas de pelerin a encombrement reduit
DE4124691C1 (fr) * 1991-07-22 1992-02-27 Mannesmann Ag, 4000 Duesseldorf, De

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1555869A (fr) * 1967-12-20 1969-01-31

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2057351A (en) * 1933-12-11 1936-10-13 Smith Corp A O Frame transferring mechanism and drive therefor
US3030835A (en) * 1958-06-06 1962-04-24 Blaw Knox Co Tube rolling machine
FR2477912A1 (fr) * 1980-03-17 1981-09-18 Mannesmann Ag Laminoir a pas de pelerin a encombrement reduit
DE4124691C1 (fr) * 1991-07-22 1992-02-27 Mannesmann Ag, 4000 Duesseldorf, De

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"Maschinen und Anlagen zur Herstellung von Rohren nach dem Kaltpilgerverfahren", 2 October 1988, MANNESMANN DEMAG HÜTTENTECHNIK, MÖNCHENGLADBACH, DE *
SOVIET INVENTIONS ILLUSTRATED Derwent World Patents Index; AN 171831 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101228003B (zh) * 2005-07-07 2011-04-27 德国索菲纳有限公司 用于磨削和/或精加工工件的装置

Also Published As

Publication number Publication date
DE4336422A1 (de) 1995-04-27
US5540076A (en) 1996-07-30
DE59407543D1 (de) 1999-02-04
CN1104940A (zh) 1995-07-12
RU2107565C1 (ru) 1998-03-27
DE4336422C2 (de) 1996-10-24
CN1052926C (zh) 2000-05-31
KR950010980A (ko) 1995-05-15
EP0707901B1 (fr) 1998-12-23
JPH07164024A (ja) 1995-06-27
KR100295951B1 (ko) 2001-10-24
RU94045828A (ru) 1997-02-27

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