EP2858768B1 - Walzenanordnung - Google Patents

Walzenanordnung Download PDF

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Publication number
EP2858768B1
EP2858768B1 EP13727613.5A EP13727613A EP2858768B1 EP 2858768 B1 EP2858768 B1 EP 2858768B1 EP 13727613 A EP13727613 A EP 13727613A EP 2858768 B1 EP2858768 B1 EP 2858768B1
Authority
EP
European Patent Office
Prior art keywords
roll
pin
circumferential surface
bush
pin bushing
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
EP13727613.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2858768A1 (de
Inventor
Karl Keller
Johannes Alken
Konrad Roeingh
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
Publication of EP2858768A1 publication Critical patent/EP2858768A1/de
Application granted granted Critical
Publication of EP2858768B1 publication Critical patent/EP2858768B1/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
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • 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

Definitions

  • the invention relates to a roller assembly for use in metallurgical engineering, comprising a roller with a roll barrel and two roll neck, and at least one pin bushing for receiving one of the roll neck without radial play.
  • Roll arrangements are known from the prior art, in which the roll neck is received in a cylindrical or tapered pin bush.
  • oil film bearings are used in rolling mills to support back-up rollers that take over the rolling forces from pitching cylinders and transfer them to the work rolls.
  • These are highly loaded plain bearings, which usually work in the high summer field number range, ie at a relatively low speed and under high load.
  • An elastic deformation or flattening of the pressure-loaded surfaces takes place. This flattening in the elastic region results in a larger pressure-effective surface counter to the effective direction of the external force, which is applied for example by the adjusting cylinder.
  • the bearing can thus carry more load.
  • EHD Elastohydrodynamic
  • Morgoil KLX ® bearings which have a thin-walled, conical pin bushing as a tread, see also US 6,468,194 or EP 1 213 061 ,
  • a feather key is disposed between the pin bushing and the roll neck.
  • the DE 38 76 663 T2 describes a cylindrical bushing for supporting a rotating bearing on a hydrodynamic lubricant film.
  • the invention has for its object to further increase the carrying capacity of a roller assembly, without increasing the size or the installation size of the roller assembly.
  • the invention relates to a roller assembly for use in metallurgical engineering, comprising a roller with a roll barrel and two roll necks, and at least one pin bushing for non-rotatably receiving one of the roll neck without radial play.
  • the roller arrangement is particularly characterized in that in the unloaded state, a circumferential cavity between the pin bushing and the roll neck is formed.
  • the cavity is precisely pre-dimensioned as a function of the maximum bearing force.
  • the circumferential cavity is formed in the form of a rotationally symmetrical annular gap in the sense of a circumferential hollow profile in a plane perpendicular to the longitudinal axis of the roller assembly.
  • the cavity is enlarged and limited by a rotationally symmetrical concave expression on the lateral surface of the roll neck and / or on the inner circumferential surface of the neck bushing.
  • a further embodiment of the invention provides that the lateral surface of the roll neck and / or the inner surface of the neck bushing in the region of its concave expression - seen in longitudinal section of the roller assembly - at least in sections in the form of a straight line, a sine curve, a polygonal curve R (x) of the lowest degree or a combination of these.
  • the contour of the lateral surface of the roll neck or the contour of the inner circumferential surface of the pin bush in the region of its concave expression - seen in longitudinal section of the roller assembly - in Transition region between two adjacent profile sections is continuous and differentiable.
  • smooth transitions are thus created without edges between the individual profile sections of the profiling, so as to avoid the formation of indents, for example grooves, on the mutually acting lateral surfaces of the journal bushing and the roll neck, especially in the case of loading.
  • this also counteracts the disadvantages of a possible notch effect.
  • the contour of the lateral surface of the roll neck or the contour of the inner surface of the pin bushing in the region of its concave expression - seen in longitudinal section of the roller assembly - correlates with the distribution of the bearing force in the axial direction, so that under load locally as large as possible Flattening of the pin bushing is achieved in its elastic range, which leads to an increased load capacity of the roller assembly with unchanged size.
  • the invention provides that the lateral surface of the roll neck frustoconical and the inner circumferential surface of the pin bushing are complementary frusto-conical.
  • the pin bushing can be easily mounted on the roll neck via the cone or dismantled again.
  • the lateral surface of the roll neck are cylindrical in shape and the inner circumferential surface of the pin bushing are designed to be complementary cylindrical.
  • the journal bush is shrunk onto the roll neck to produce a frictional connection without radial play.
  • the invention provides that the roll is a back-up roll or an intermediate roll or a work roll for use in a roll stand.
  • the arrangement comprises at least one chock with a bearing bush in which the pin bushing is slidably mounted with the roll neck or with the roller using a bearing oil film between the bearing bush and the pin bushing.
  • a roll assembly 100 is shown for use, for example in the field of metallurgical technology, with a roll with a roll barrel 11 and at least one cylindrical roll neck 10.
  • the roll neck 10 is rotatably mounted in a complementary to the roll neck 10 receiving bore of the pin bushing 20 and at least without radial play ,
  • the journal bush 20 is shrunk onto the roll neck 10, for example.
  • it is provided between the roll neck 10 and the pin bushing 20 to arrange at least one driver element 23, for example in the form of a feather key or a correspondingly specially designed sliding block.
  • the inner circumferential surface 21 of the pin bushing 20 and / or the outer surface of the roll neck are provided with a concave contour, hereinafter also referred to as profiling 40, which is produced for example by turning and / or grinding.
  • the profiling 40 is in the region of its concave shape - seen in longitudinal section of the pin bushing 20 - at least partially contoured in the form of a straight line, a sine curve, a polygonal curve R (x) nth degree or a combination of these.
  • the Profiling 40 can also describe a simple parabolic waveform.
  • the cavity 12 is designed in the form of an annular gap in the sense of a circumferential rotationally symmetrical hollow profile.
  • the outer circumferential surface 22 of the pin bushing 20 and the lateral surface 13 of the roll neck 10 are shown in the illustration shown FIG. 1 designed as an example cylindrical.
  • profiling 40 can be provided to arrange the above-described profiling 40 on the lateral surface 13 of the roll neck 10 and to form the inner circumferential surface 21 of the journal bush 20 in a cylindrical manner.
  • the profilings 40 described above can also be formed simultaneously both on the inner circumferential surface of the journal bushing and on the outer circumferential surface of the roll neck, preferably opposite one another.
  • a spacer ring 28 is arranged with a stop 25 between the end face of the roll bale 11 and the pin bushing 20.
  • the roll bale 11 may be provided with a projection (not shown) at the front end as a stop 25, which is formed integrally with the roll bale.
  • the pin bushing 20 is stretched after being pushed onto the roll neck 10 with a pressure shoulder ring 17 via a thrust bearing, which is optionally arranged to support the roll neck 10, and a nut 18 in the axial direction x against the spacer ring 28 and secured against axial displacement, the Roll neck at its end for receiving the pressure shoulder ring 17 with a hub shoulder 26 and then with a threaded pin 27 is provided for receiving the nut 18.
  • a thrust bearing which is optionally arranged to support the roll neck 10 and a nut 18 in the axial direction x against the spacer ring 28 and secured against axial displacement
  • the Roll neck at its end for receiving the pressure shoulder ring 17 with a hub shoulder 26 and then with a threaded pin 27 is provided for receiving the nut 18.
  • FIGS. 1 and 2 is merely schematically the axial bearing inner ring 16 between the pressure shoulder ring 17 and the nut 18 shown.
  • the nut 18 may additionally be secured against loosening with an anti-twist device 19, for example a lock
  • the depth t of the profiling 40 or the size of the resulting cavity 12 between the pin bushing 20 and the roll neck 10 is adjusted in dependence on the maximum occurring bearing force F and the modulus of elasticity of the pin bushing 20 so that the volume of the cavity 12 is greater is formed, the greater the maximum bearing force F in the loaded state, the deformation of the pin bushing 20 remains exclusively in the elastic range.
  • the actual tread depths t are in the micrometer ( ⁇ m) range, preferably up to 1000 ⁇ m.
  • the wall thickness d of the cylindrical pin bushing is between 10 mm to 75 mm without consideration of an optional rotationally symmetric concave characteristic described below.
  • At least one chock 50 is provided with a bearing bushing 51 for receiving the pin bushing 20 with the roll neck 10, wherein between the bearing bush 51 of the chock 50 and the outer circumferential surface 22 of the pin bushing 20, a supporting oil film 30 is provided.
  • This arrangement is also referred to as oil film storage.
  • the inner circumferential surface of the bearing bush 51 is coated with a bearing metal lining, for example with white metal.
  • the roll neck 10 is frusto-conical.
  • the inner circumferential surface 21 of the pin bushing 20 is formed complementary to the ideal line (without profiling) of the frusto-conical roll neck 10. It is As described above, a profiling 40 on the inner circumferential surface of the pin bushing 21 and / or on the outer circumferential surface of the roll neck 13 is provided.
  • the pin bushing 20 is pushed onto the roll neck 10 until the radial clearance between the pin bushing 20 and roll neck 10 is eliminated. Subsequently, the pin bushing 20, as before for FIG. 1 described, biased and secured against displacement.
  • the wall thickness d of the conical bushing 20 is at its thin end between 10 mm and 75 mm.
  • a lubricating film 31 is disposed between the pin bushing 20 and the roll neck 10 to avoid micro-cold micro-welding.
  • the profiles 40 on the roll neck 10 or on the pin bushing 20 are in this conical embodiment as before to the FIG. 1 described, executed.
  • FIGS. 3a and 3b describe in principle the roller assembly 100 with the roller and at least one pin bushing 20 for play-free and rotationally fixed receiving one of the roll neck 10.
  • the lateral surface 13 of the roll neck 10 and the inner circumferential surface 21 of the pin bushing 20 may be cylindrical or frusto-conical, wherein the respective lateral surfaces 13th , 21 are complementary to each other and adjoin each other without radial play.
  • the profiles 40 of the inner circumferential surface 21 of the pin bushing 20 and / or the lateral surface 13 of the roll neck 10 as shown in the Figure 3c describe by way of example various possibilities of mathematical functions R (x) of the nth degree which, depending on the load case, can also be used in combination with other profilings.
  • R (x) mathematical functions of the nth degree which, depending on the load case, can also be used in combination with other profilings.
  • the profiling 40 in the transition region between two adjacent profile sections is formed continuously and differentially. It should be mentioned that in the Figure 3c shown curves do not describe the actually practicable profilings.
  • the illustrated plurality of curve or profile sections is merely a schematic representation of different possible Profiltechnikssectionn.
  • the at least substantially vertical upward rolling force F w is exerted on the upper (supporting) roll, while at the same time exerting an at least substantially vertically downward rolling force F w on the lower (supporting) roll becomes.
  • These rolling forces are transmitted from the roll bales half on the Rolling pin, which presses down the roll pins in the upper chock and down in the lower chock.
  • the rolling forces are transmitted according to an action chain from the roll neck on the journal, the bearing oil film between the journal and bearing bush and the bearing bush on the chock. From the chock, the rolling forces are further derived in the rolling mill, in which the chock is stored.
  • the chock and also mounted in the chock bearing bush should ideally be regarded as relentless and incompressible to the rolling forces. That is, the chock and the bushing catch the acting on them each half rolling forces F w / 2 (Aktio) completely by holding each the same amount, but oppositely directed bearing forces F L (Reactio).
  • the pin bushing 20 itself, in conjunction with the cavity 12 according to the invention, towards the roll neck 10, is the weakest link in the above-described chain of effects of the (rolling) force.
  • journal bushing 20 can not escape the rolling force, in the event of loading during elastic rolling operation, the journal bushing 20 elastically deforms.
  • the journal bushing 20 is replaced by the rolling force F w / 2 or the opposing bearing force F L into the original cavity 12 deformed into it and is flattened.
  • the flattening takes place at the maximum extent until the pin bushing 20 presses on the roll neck 10 and is supported by this.
  • the pin bushing 20 adapts locally elastically to the profiling 40 of the roll neck and deforms after discharge back into the original state.
  • the pressure-effective area between the pin bushing 20 and the bearing bush 51 is increased.
  • the supporting oil film 30 is arranged, which forms a so-called hydrodynamic oil film storage. Due to the enlargement of the pressure-effective surface, the roller arrangement according to the invention leads to an increase in the load bearing capacity of the hydrodynamic oil film bearing between the journal bush and the bearing bush.
  • the rolling force or the bearing force is not punctiform or linear, but in the form of a force mountain.
  • the power mountains have a surface extent in the circumferential direction and in the axial direction. Due to the flattening of the pin bushing and the associated enlargement of the pressure-effective surface a significant increase in load capacity of the roller assembly is achieved for the area extended power mountains.
  • the roller assembly according to the invention also carries significantly more compared to a roller assembly in which the pin bushing is already connected in the unloaded state non-positively with bias, for example by shrinking, with the roll neck.
  • the force required for the elastic flattening of the pin bushing force is lower due to the cavity according to the invention as in constructions with bias between Bearing bush and pin. For prestressed structures, greater forces are required to achieve the same deformation of the pin bushing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Rolling Contact Bearings (AREA)
  • Sliding-Contact Bearings (AREA)
EP13727613.5A 2012-06-12 2013-06-07 Walzenanordnung Active EP2858768B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012209831A DE102012209831A1 (de) 2012-06-12 2012-06-12 Walzenanordnung
PCT/EP2013/061822 WO2013186142A1 (de) 2012-06-12 2013-06-07 Walzenanordnung

Publications (2)

Publication Number Publication Date
EP2858768A1 EP2858768A1 (de) 2015-04-15
EP2858768B1 true EP2858768B1 (de) 2016-09-14

Family

ID=48577762

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13727613.5A Active EP2858768B1 (de) 2012-06-12 2013-06-07 Walzenanordnung

Country Status (9)

Country Link
US (1) US9180501B1 (ru)
EP (1) EP2858768B1 (ru)
JP (1) JP5823654B2 (ru)
KR (1) KR101700210B1 (ru)
CN (1) CN104540608B (ru)
BR (1) BR112014031004A2 (ru)
DE (1) DE102012209831A1 (ru)
RU (1) RU2604545C2 (ru)
WO (1) WO2013186142A1 (ru)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012209828A1 (de) * 2012-06-12 2013-12-12 Sms Siemag Ag Walzenanordnung
DE102017216547A1 (de) 2017-09-19 2019-03-21 Sms Group Gmbh Walzgerüst

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2955002A (en) 1957-12-26 1960-10-04 Morgan Construction Co Bearing
US4159152A (en) 1977-10-11 1979-06-26 Morgan Construction Company Means for lubricating the roll neck/sleeve interface of an oil film bearing
JPS5893508A (ja) * 1981-11-30 1983-06-03 Mitsubishi Heavy Ind Ltd 撓み制御ロ−ル
DE3150496A1 (de) * 1981-12-19 1983-11-24 Mannesmann AG, 4000 Düsseldorf Oelfilmlager
SU1210928A1 (ru) * 1984-07-30 1986-02-15 Всесоюзный Ордена Ленина Научно-Исследовательский И Проектно-Конструкторский Институт Металлургического Машиностроения "Внииметмаш" Подшипникова опора прокатного валка
US4772137A (en) 1987-03-30 1988-09-20 Morgan Construction Company Oil film bearing and bushing
US4944609A (en) 1987-03-30 1990-07-31 Morgan Construction Company Oil film bearing and bushing
DE19816602C1 (de) * 1998-04-15 1999-05-27 Schloemann Siemag Ag Walzgerüst mit axial verschiebbaren Walzen
US5934131A (en) * 1998-08-10 1999-08-10 Morgan Construction Company Overhung roll assembly
US6149309A (en) * 1999-07-13 2000-11-21 Morgan Construction Company Bushing for oil film bearing
US6468194B2 (en) 2000-12-08 2002-10-22 Morgan Construction Company Sleeve for rolling mill oil film bearing
US6604859B1 (en) * 2002-01-23 2003-08-12 Morgan Construction Company Bushing for oil film bearing
DE10336894A1 (de) 2003-08-08 2005-03-10 Sms Demag Ag Ölfilmlager für Walzenzapfen mit hydrostatischer Unterstützung
US7380431B2 (en) * 2005-07-18 2008-06-03 Morgan Construction Company Oil film bearing with compact hydraulic mount
DE102006016714A1 (de) * 2006-04-08 2007-10-11 Sms Demag Ag Einbaustück zur Aufnahme eines Walzenzapfens
US7857522B2 (en) * 2007-01-31 2010-12-28 Siemens Industry, Inc. Rolling mill oil film bearing
US8246250B2 (en) * 2008-01-11 2012-08-21 Sms Siemag Aktiengesellschaft Bearing arrangement
US20110075956A1 (en) * 2009-09-28 2011-03-31 Morgan Construction Company Sleeve for Oil Film Bearing

Also Published As

Publication number Publication date
DE102012209831A1 (de) 2013-12-12
WO2013186142A1 (de) 2013-12-19
US9180501B1 (en) 2015-11-10
CN104540608B (zh) 2017-01-18
KR20150023682A (ko) 2015-03-05
EP2858768A1 (de) 2015-04-15
RU2604545C2 (ru) 2016-12-10
CN104540608A (zh) 2015-04-22
JP2015519207A (ja) 2015-07-09
KR101700210B1 (ko) 2017-01-26
RU2014153914A (ru) 2016-07-27
US20150343504A1 (en) 2015-12-03
BR112014031004A2 (pt) 2017-08-08
JP5823654B2 (ja) 2015-11-25

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