EP3302836B1 - Walzenanordnung - Google Patents

Walzenanordnung Download PDF

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Publication number
EP3302836B1
EP3302836B1 EP16717404.4A EP16717404A EP3302836B1 EP 3302836 B1 EP3302836 B1 EP 3302836B1 EP 16717404 A EP16717404 A EP 16717404A EP 3302836 B1 EP3302836 B1 EP 3302836B1
Authority
EP
European Patent Office
Prior art keywords
roll
barrel
bearing bush
annular gap
pin
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.)
Active
Application number
EP16717404.4A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3302836A1 (de
Inventor
Johannes Alken
Ralf Seidel
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 Group 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 Group GmbH filed Critical SMS Group GmbH
Priority to PL16717404T priority Critical patent/PL3302836T3/pl
Publication of EP3302836A1 publication Critical patent/EP3302836A1/de
Application granted granted Critical
Publication of EP3302836B1 publication Critical patent/EP3302836B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/07—Adaptation of roll neck bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/07—Adaptation of roll neck bearings
    • B21B31/074—Oil film bearings, e.g. "Morgoil" bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/07—Adaptation of roll neck bearings
    • B21B31/078—Sealing devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2203/00—Auxiliary arrangements, devices or methods in combination with rolling mills or rolling methods
    • B21B2203/18—Rolls or rollers

Definitions

  • the invention relates to a roller arrangement for rolling rolling in a rolling mill according to the preamble of patent claim 1.
  • a roll neck rotates in a stationary bearing bush, wherein the bearing bush is arranged in a chock.
  • the diameter difference between the roll neck and the bearing bush is usually in the range of 1 ⁇ of the bearing diameter, i. H. about 1 mm clearance at 1 m bearing diameter, which is why a corresponding annular gap between the roll neck and the bearing bush is formed.
  • the annular gap is typically with lubricants, z. B. oil filled, so that forms an oil film in the annular gap.
  • an external force for. B. the rolling force applied to the storage, so first shifts the rotating roll neck eccentrically to the bearing bush in the radial direction against the outer direction of force.
  • the annular gap between the roll neck and the bearing bush then has on one side a minimum cross section and exactly opposite a maximum cross section.
  • the oil which is supplied via hydrodynamic pockets the annular gap is transported by the adhesive condition on the rotating surface of the roll neck in the region of the narrowest cross-section. As the cross-section of the gap narrows to the narrowest point, the oil is squeezed out to the side of the bearing. At the same time, however, the pressure in the oil film increases, whereby the bearing is able to carry an external larger force.
  • the oil, which is pushed out to the two bearing sides usually referred to as the side flow of the camp.
  • EP 1 699 575 B1 and DE 198 31 301 A1 describe sealing devices for rolls in rolling mills.
  • the oil film between the roll neck and the roll neck receiving bearing surface is hereinafter also referred to as a lubricating film.
  • a disadvantage of systems with a completely sealed annular gap without drain possibility for the lubricant is, inter alia, that the operating temperature of the lubricant and the roll neck increases, especially at higher speeds and therefore expensive cooling systems are required to limit the increase in temperature or to keep uniform. Due to the increase in temperature, the viscosity of the lubricant decreases. Consequently, the lubricant pressure also decreases and it reduces the bearing capacity of the storage. Most are closed Systems integrated check valves to prevent running of the cooling circuit.
  • the German patent DE 690 07 079 T2 discloses a roller assembly according to the preamble of claim 1.
  • the roller assembly disclosed therein comprises: a roller having a roll barrel and at least one roll neck; a chock with a rotatably mounted bushing, which has a receiving opening for receiving the roll neck, wherein the inner diameter of the receiving opening relative to the outer diameter of the roll neck is formed so larger that between the bearing bush and the roll neck an annular gap for receiving a lubricant remains; a sealing ring arranged on the roll barrel-side end face of the receiving opening for sealing the annular gap there; and a arranged on the roller bale far end face of the receiving opening sealing ring for local sealing of the annular gap.
  • the object of the invention is to develop a known roll order to the effect that their carrying capacity or the rolling force can be increased while maintaining or reducing their size, without overheating the roll assembly.
  • the roller assembly according to the invention should also be easy to install and retrofit in existing systems.
  • Characteristic of the roller assembly according to the invention is that the bearing bush - seen in the circumferential direction - is divided into a flow angle range and Absperrwinkel Scheme; in that the bearing bush has at least one outflow channel in the passage angle region for deriving the lubricant from the Annular gap in an oil receiving space; that the flow angle range extends adjacent to the Absperrwinkel Scheme over an angular range of 360 ° minus Absperrwinkel Anlagen; and that the Absperrwinkel Quarry a, starting from A + y with -10 ° ⁇ ⁇ 25 °, extending against the direction of rotation of the roller by a maximum of 270 °, where A defines a support load point, which by the angular position A of the narrowest gap (h min ) is represented in the load case between roll neck and chock. where A defines a support load point, which is represented by the angular position A of the narrowest gap (h min ) in the load case between roll neck and chock.
  • the roller assembly according to the invention initially, due to the blocking of the side flow of the lubricant by means of the sealing rings, leads to an increase in pressure of the lubricant in the annular gap in the region of the support load point and thus to a load capacity increase or rolling force increase of the roller assembly.
  • the thickness of the lubricating film is increased in the region of the support load point and thus improves the reliability, for example with respect to edge runners and with respect to the startup behavior.
  • the pressure build-up can be realized simply and advantageously by providing the sealing rings.
  • the invention advantageously allows easy retrofitting in existing facilities. Without enlarging the space, for example, in the course of Modernization measures on existing rolling mills the rolling force and thus the efficiency of the existing rolling mill can be increased by up to 40%.
  • Existing plants can increase in rolling demands, z. B. be converted by the processing of other material grades or material thicknesses, easily and inexpensively.
  • a previous bushing can be easily replaced by a bearing bush according to the invention.
  • the ball-side and bale-distant sealing ring can be retrofitted to existing roller assemblies.
  • roller arrangement in new systems in advance can be made smaller overall to ensure the same load capacity as before. This saves above all space, material costs and production time.
  • a pin bushing is provided for mounting on the roll neck.
  • the pin bushing can advantageously be easily and inexpensively replaced in case of wear.
  • the annular gap is then formed between the bearing bush and the pin bushing.
  • the bearing bush in the flow angle region at least one ball-side drainage channel for fluid-conducting connection of the annular gap with a ball-side oil receiving space and at least one balefernen drainage channel for fluid-conducting connection of the annular gap with a ballenfernen ⁇ lseeraum.
  • the two drainage channels advantageously allow a radial and lateral outflow of oil from the annular gap of the bearing bush. With the effluent oil is dissipated more heat from the annular gap than an already existing collecting return in the chock, and so overheating of the annular gap or in particular the pin bushing and the roll neck is reliably prevented even at increased load.
  • the particular radial outflow channels are advantageously arranged distributed in the circumferential angular range of the pin bushing in the circumferential direction or extend in the circumferential direction.
  • they may have a slit-shaped cross-section which extends in the circumferential direction within the flow angle range, or a plurality of drainage channels may be provided which are arranged side by side on the ball side or on the ball-distal side in the flow angle region of the bearing bush.
  • the bearing bush can have an oil pocket in the passage angle region on its inner side facing the roll neck, and the at least one drain channel is then preferably arranged so that it can discharge the oil from the oil pocket into the oil receiving space.
  • the roller of the roller arrangement according to the invention may be a work roll, a support roll or an intermediate roll.
  • FIG. 1 shows the roller assembly 100 according to the invention according to a first embodiment.
  • the roll arrangement 100 comprises a roll 110 with a roll bale 112 and a roll neck 114.
  • the roll is rotatably mounted in a chock 120, more precisely in a bearing bush 130 arranged rotationally fixed in the chock.
  • the bearing bush 130 has a receiving opening for receiving the roll neck 114, wherein the inner diameter of the receiving opening relative to the outer diameter of the roll neck or on this mounted pin bushing 116 is formed so larger that between the bearing bush and the roll neck or the pin bushing 116 an annular gap 180 for receiving a lubricant, typically oil remains; please refer FIG. 2 ,
  • a sealing ring 140 is arranged for sealing the annular gap there with respect to a Roller box-side receiving space 160.
  • a further sealing ring 150 is arranged for local sealing of the annular gap 180 relative to the local roller barrel remote oil receiving chamber 170 at the roller bale remote end face of the receiving opening.
  • the bearing bush 130 at least one outflow channel 132, for discharging the lubricant from the annular gap 180 in one of the oil receiving chambers 160, 170.
  • a balejonberger outflow channel 132-1 and a ballenferner outflow channel 132-2 is provided for discharging oil from the annular gap 180.
  • the drainage channels 132-1, 132-2 are fluid-conducting with the annular gap and the respective oil receiving space 160, 170 connected.
  • the drainage channels extend by way of example in sections in the radial and axial directions.
  • FIG. 2 shows a cross section through the roller assembly according to the invention under the load of the rolling force F, which acts here for example in the direction of the center plane y. Due to the interaction of the action and the reaction of the rolling force F, the roll pin 114 optionally displaces eccentrically within the bearing bush 130 together with the pin bushing 116, so that an asymmetric annular gap 180 or an asymmetric oil film is produced.
  • the minimum height or thickness h min assumes the annular gap 180 at the position of the support load point A.
  • the bearing bush 130 is divided, as seen in the circumferential direction, into a passage angle range ⁇ and a shut-off angle range a, which is understood as the difference between 360 ° and the flow angle range ⁇ .
  • the Absperrwinkel Scheme a extends, starting from A + y with - 10 ° ⁇ ⁇ + 35 ° against the direction of rotation of the roller by a maximum of 270 °. Accordingly, the flow area is defined as the complement angle range to the Absperrwinkel Suite, ie to 360 ° - the Absperrwinkel Scheme ⁇ .
  • FIG. 3 shows a second embodiment of the roller assembly, more precisely for a possible guidance of the drainage channels 132.
  • the second embodiment provides that the ball-side and the baleferne spillway 132-1, 132-2 not only - starting from the annular gap 180 - in radial Direction through the bearing bush 130, but from this further through the chock 120 is guided to exit at the end faces in the respective oil receiving chambers 160, 170, preferably in the axial direction.
  • FIG. 4 shows a third embodiment of the inventive arrangement, in particular for a possible guidance of the drainage channels.
  • the bearing bush 130 has a collecting oil pocket 136 on its inner side facing the roll neck 114 and that the at least one outflow channel 132-1, 132-2 is in fluid-conducting connection with the oil pocket 136.
  • the oil pocket is a local recess on the inside of the bushing and so the oil bag acts as a local volume enlargement of the annular gap; in the area of the collecting oil pocket, the thickness of the annular gap 180 and thus the thickness of the oil film therein is increased.
  • the outflow channels 132, 132-1, 132-2 according to the invention are always formed only in the passage angle range ⁇ , but never in the Absperrwinkel Scheme ⁇ .
  • FIG. 5 shows possible arrangements and cross-sectional shapes for the drainage channels.
  • the cross-sectional shapes shown therein, slit-shaped, round or rectangular are to be understood merely as examples;
  • the drainage channels can have any cross-sectional shape. It is advantageous if the drainage channels extend in the circumferential direction of the bearing bush, be it slot-shaped, for example, as in the left in FIG FIG. 5 shown or in the form of a plurality of circumferentially distributed singular drainage channels, as shown right in FIG. 5 shown.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Rolls And Other Rotary Bodies (AREA)
EP16717404.4A 2015-05-26 2016-04-21 Walzenanordnung Active EP3302836B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL16717404T PL3302836T3 (pl) 2015-05-26 2016-04-21 Układ walców

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015209637.8A DE102015209637A1 (de) 2015-05-26 2015-05-26 Walzenanordnung
PCT/EP2016/058873 WO2016188681A1 (de) 2015-05-26 2016-04-21 Walzenanordnung

Publications (2)

Publication Number Publication Date
EP3302836A1 EP3302836A1 (de) 2018-04-11
EP3302836B1 true EP3302836B1 (de) 2018-10-24

Family

ID=55794992

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16717404.4A Active EP3302836B1 (de) 2015-05-26 2016-04-21 Walzenanordnung

Country Status (12)

Country Link
US (1) US10710131B2 (ko)
EP (1) EP3302836B1 (ko)
JP (1) JP6633649B2 (ko)
KR (1) KR101990391B1 (ko)
CN (1) CN107645973B (ko)
BR (1) BR112017025033B1 (ko)
DE (1) DE102015209637A1 (ko)
PL (1) PL3302836T3 (ko)
RU (1) RU2675881C1 (ko)
TR (1) TR201900282T4 (ko)
TW (1) TWI617371B (ko)
WO (1) WO2016188681A1 (ko)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1052488C (zh) * 1996-01-18 2000-05-17 沈阳药科大学 一步合成美欧卡霉素生产工艺
DE102017219935A1 (de) 2017-11-09 2019-05-09 Sms Group Gmbh Dichtung gegen einen Austritt von Schmiermittel und Walzgerüst mit der Dichtung
NL2023659B1 (en) * 2019-08-19 2021-10-13 Pelleting Tech Nederland B V Pellet press with cooling system and method of manufacturing pellets
KR102294083B1 (ko) 2021-03-31 2021-08-26 디에스케이아이 주식회사 이종 금속 접합체 부품을 포함하는 압연기 롤

Family Cites Families (22)

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Publication number Priority date Publication date Assignee Title
US3453031A (en) * 1967-04-06 1969-07-01 Morgan Construction Co Bearing assembly
SU801918A1 (ru) * 1979-03-19 1981-02-07 Предприятие П/Я В-2869 Гидродинамическа опора валковпРОКАТНыХ CTAHOB
DE3117746A1 (de) 1981-05-05 1982-12-09 Krupp Polysius Ag, 4720 Beckum Hydrodynamisches radial-gleitlager
DE3150496A1 (de) * 1981-12-19 1983-11-24 Mannesmann AG, 4000 Düsseldorf Oelfilmlager
SU1442288A1 (ru) * 1986-11-26 1988-12-07 Предприятие П/Я В-2869 Опорный узел прокатного валка
DE3721265A1 (de) * 1987-06-27 1989-01-12 Schloemann Siemag Ag Dichtungsvorrichtung fuer walzenlager in dressiergeruesten
US5000584A (en) * 1990-03-02 1991-03-19 Morgan Construction Company Bushing for oil film bearing
US5678931A (en) * 1995-10-17 1997-10-21 Morgan Construction Company Hydrodynamically lubricated eccentrically adjustable bearing
JPH1162946A (ja) * 1997-08-19 1999-03-05 Nippon Seiko Kk ロール支持装置
DE19831301B4 (de) 1998-07-13 2006-02-23 Skf Gmbh Abdichtung für Walzen in Walzwerken
US6146020A (en) 1999-02-26 2000-11-14 Morgan Construction Company Seal assembly for rolling mill oil film bearing
US6149309A (en) * 1999-07-13 2000-11-21 Morgan Construction Company Bushing for oil film bearing
JP2002155946A (ja) * 2000-11-20 2002-05-31 Daido Metal Co Ltd 軸支承部材
US6468194B2 (en) * 2000-12-08 2002-10-22 Morgan Construction Company Sleeve for rolling mill oil film bearing
EP1522751A1 (en) * 2003-10-09 2005-04-13 Corus UK Limited Method and apparatus for lubricating a bearing assembly by supplying grease and gas
ES2293369T3 (es) 2004-01-03 2008-03-16 Sms Demag Ag Dispositivo de obturacion para cojinetes de cilindro laminador.
US8246250B2 (en) * 2008-01-11 2012-08-21 Sms Siemag Aktiengesellschaft Bearing arrangement
DE102008054715A1 (de) * 2008-12-16 2010-06-17 Voith Patent Gmbh Lagerung für eine rotierbare und durch Schwingungsanregung in Richtung iher Rotationsachse bewegbare Walze, insbesondere Brustwalze und Verfahren zur Steuerung der Betriebsweise einer derartigen Walze
JP5048028B2 (ja) * 2009-09-08 2012-10-17 新日本製鐵株式会社 圧延ロール軸受部に供給する潤滑油の冷却方法
US8500332B2 (en) * 2010-05-05 2013-08-06 Siemens Industry, Inc. Self pumping oil film bearing
DE102011087605A1 (de) * 2011-12-01 2013-06-06 Sms Siemag Ag Einbaustück und Verfahren zu dessen Herstellung
CN203635622U (zh) * 2013-12-31 2014-06-11 一重集团大连设计研究院有限公司 一种二十辊轧机的油气润滑连接装置

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Also Published As

Publication number Publication date
PL3302836T3 (pl) 2019-03-29
CN107645973B (zh) 2019-05-17
KR20170122806A (ko) 2017-11-06
JP2018513023A (ja) 2018-05-24
BR112017025033B1 (pt) 2022-07-05
KR101990391B1 (ko) 2019-06-18
EP3302836A1 (de) 2018-04-11
TWI617371B (zh) 2018-03-11
TW201703891A (zh) 2017-02-01
TR201900282T4 (tr) 2019-02-21
DE102015209637A1 (de) 2016-12-01
WO2016188681A1 (de) 2016-12-01
US10710131B2 (en) 2020-07-14
JP6633649B2 (ja) 2020-01-22
RU2675881C1 (ru) 2018-12-25
US20180297093A1 (en) 2018-10-18
CN107645973A (zh) 2018-01-30
BR112017025033A2 (pt) 2018-08-07

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