EP3010662B1 - Rolling mill laying head - Google Patents

Rolling mill laying head Download PDF

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Publication number
EP3010662B1
EP3010662B1 EP14735721.4A EP14735721A EP3010662B1 EP 3010662 B1 EP3010662 B1 EP 3010662B1 EP 14735721 A EP14735721 A EP 14735721A EP 3010662 B1 EP3010662 B1 EP 3010662B1
Authority
EP
European Patent Office
Prior art keywords
laying head
quill
bushing
bearing
oil film
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.)
Revoked
Application number
EP14735721.4A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3010662A1 (en
Inventor
Thomas C. Wojtkowski Jr.
Peter N. Osgood
Kenneth R. Scheffler
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.)
Primetals Technologies USA LLC
Original Assignee
Primetals Technologies USA LLC
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=51063787&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP3010662(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Primetals Technologies USA LLC filed Critical Primetals Technologies USA LLC
Publication of EP3010662A1 publication Critical patent/EP3010662A1/en
Application granted granted Critical
Publication of EP3010662B1 publication Critical patent/EP3010662B1/en
Revoked 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
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C47/00—Winding-up, coiling or winding-off metal wire, metal band or other flexible metal material characterised by features relevant to metal processing only
    • B21C47/02—Winding-up or coiling
    • B21C47/10—Winding-up or coiling by means of a moving guide
    • B21C47/14—Winding-up or coiling by means of a moving guide by means of a rotating guide, e.g. laying the material around a stationary reel or drum
    • B21C47/143—Winding-up or coiling by means of a moving guide by means of a rotating guide, e.g. laying the material around a stationary reel or drum the guide being a tube
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C47/00—Winding-up, coiling or winding-off metal wire, metal band or other flexible metal material characterised by features relevant to metal processing only
    • B21C47/02—Winding-up or coiling
    • B21C47/10—Winding-up or coiling by means of a moving guide
    • B21C47/14—Winding-up or coiling by means of a moving guide by means of a rotating guide, e.g. laying the material around a stationary reel or drum

Definitions

  • Embodiments of the present invention relate to laying heads of the type employed in rolling mills to form hot rolled products into helical formations of rings.
  • a stationary support structure contains a hollow quill rotatably supported between axially spaced bearings.
  • the quill is equipped with a guide pathway, which may typically comprise a curved guide pipe having an entry end aligned with the rotational axis of the quill, and a curved intermediate section projecting in a cantilever fashion from the quill to an exit end spaced radially from the quill axis.
  • the quill is rotatably driven by known means, with the guide pipe being configured to receive a product at its entry end and to form the product into a helical formation of rings emerging from its exit end.
  • Roller bearings are typically employed to rotatably support the quill. Under high speed operating conditions, e.g., when handling products traveling at speeds exceeding 100m/sec, experience has shown that the roller bearings are prone to producing vibrations that disturb operation of the laying head.
  • the rotating member forms a single pressure field "P" as a result of a combination of parameters, including the rotational speed of the rotating member, the applied load, the diametrical clearance between the rotating member and bushing, and the viscosity of the oil.
  • the force integrated from the pressure field exactly balances out the applied load, with the centerline 18 of the rotating member 10 being offset from the centerline 20 of the bushing 12, resulting in an eccentricity "E” that is a function of the aforesaid parameters.
  • a typical laying head application might require a 600 mm diameter bearing.
  • a conventional hydrodynamic bearing would have an L/D ratio of not less than 0.25 and a typical clearance of 0.60 mm.
  • the bearing would have a predicted peak oil film temperature as a function of speed as follows: Peak Peak RPM Temp F. Temp, C 750 155.7 68.7 1000 164.7 73.7 1250 172.3 77.9 1500 179 81.7 1750 185 85.0 2000 190.5 88.1 2250 195.6 90.9 2500 200.3 93.5
  • the helical formation of rings exiting from the laying head is typically deposited in an overlapping pattern on a conveyor.
  • the rings are subjected to controlled cooling while being transported by the conveyor to a reforming station where they are gathered into coils.
  • the speed of the laying head may be controlled to implement so called “wobble" and "tail end speed up” functions.
  • the wobble control function is typically employed with larger product sizes, e.g., 10.0 mm and larger, and serves to cyclically alter the speed of the laying head above and below nominal speed to produce differently sized rings that nest inside each other in the reforming chamber, resulting in a denser coil of reduced height.
  • the tail end speed up function is achieved by accelerating the rotational speed of the laying head once the tail end of the product exits from and is no longer being propelled by the laying head pinch roll.
  • An objective of the present invention is to provide a rolling mill laying head equipped with a novel and improved hydrostatic oil film bearing that overcomes or at least substantially mitigates the problems associated with mechanical roller bearings and hydrodynamic oil film bearings.
  • the quill of the laying head is rotatably supported by multiple bearings, with at least the bearing at the delivery end of the laying head being a hydrostatic oil film bearing.
  • the hydrostatic oil film bearing of the present invention provides a plurality of discrete pressure fields formed by high pressure oil being actively pumped into angularly spaced recesses in the bushing.
  • the recesses are arranged in a manner such that their associated pressure fields urge the quill into concentric alignment with the bushing where it is held during continued operation of the laying head, thus minimizing and ideally eliminating vibration due to eccentricity.
  • the multiple pressure fields also serve to separate the quill from the bushing surface prior to the start of quill rotation, which makes it unnecessary to provide a drive train with a higher starting torque.
  • the overall stability of a hydrostatic bearing is not a function of the rotational speed of the bearing, i.e., the hydrostatic bearing does not rely on a speed/geometry dependent wedge to lift and center the rotating mass. Because the inherent design of a hydrostatic bearing allows for centering of the rotating mass regardless of the applied load or speed, the bearing has a significant operational advantage over hydrodynamic bearings, particularly during a wobble cycle.
  • a laying head 22 comprises a quill 24 rotatable about a central axis "X".
  • the quill is equipped with a guide passageway, one non limiting example being a guide pipe 26.
  • the guide pipe has an entry end 26a aligned with axis X, and a curved intermediate section 26b leading to an exit end 26c spaced radially from axis X.
  • the quill is contained within a stationary support structure 28 and is supported for rotation about axis X by axially spaced bearings 30, 32.
  • Bearing 30 may comprise a back to back combination of two angular roller bearings, with bearing 32 at the delivery end of the laying head being a hydrostatic oil film bearing in accordance with an exemplary embodiment of the present invention.
  • the quill is rotatable driven by a conventional drive train including meshed gears 34, 36 powered by a gear box and motor (not shown).
  • the hydrostatic oil film bearing comprises a bushing 38 surrounding the journal surface of the quill 24.
  • a plurality of angularly separated recesses 40 are provided in the interior surface of the bushing.
  • the recesses 40 are connected via supply conduits 42 to a distribution header 44, which in turn is connected to a primary supply means which may comprise a high pressure pump 46.
  • the high pressure oil supplied to the recesses 40 creates discrete pressure fields 48 acting during static conditions prior to start up to lift the journal surface of the quill from the bushing surface, and thereafter during operation of the laying head, to urge the quill into concentric alignment with the bushing, where it is held, irrespective of the speed at which the quill is driven. Eccentricity is thus eliminated, or at least minimized to tolerable levels. By lifting the journal surface of the quill from the bushing surface prior to start up, friction is reduced, thus eliminating the need for increased starting torque.
  • the internal diameter D of the bushing 38 is relatively large, typically ranging from about 500 mm to 1000 mm.
  • the loads are relatively light, with a rotating mass of 40 kw or less.
  • the length L of the bearing is purposely shortened to provide an L/D ratio less than 0.25, with L/D ratios as low as 0.15 being shown by tests to be particularly advantageous.
  • bearing temperatures were measured during tests of a laying head equipped with a hydrostatic oil film bearing in accordance with an exemplary embodiment of the present invention.
  • the hydrostatic oil film bearing had dimensions comparable to those of the previously described hydrodynamic oil film bearing. Its design was similar to that depicted in Fig. 2 except that the bushing had eight rather than five equally spaced pressure pads. As can be seen in Fig. 3 , in comparison to the predicted temperatures of the hydrodynamic oil film bearing, the measured temperatures of the hydrostatic oil film bearing were substantially lower.
  • an auxiliary supply means serves to store high pressure oil in a stand-by mode.
  • the auxiliary supply means may comprise an accumulator 50 charged with high pressure oil supplied by the high pressure pump 46.
  • a check valve 52 isolates the accumulator 50 from the pump 46, and a normally open valve 54 is provided between the accumulator 50 and the header 44.
  • An electrically operated solenoid closes the valve 54 during normal operation. In the event of a power outage, the solenoid will open the valve 54 automatically to connect the accumulator 50 to the header 44, thus insuring that the bearing 32 maintains its hydrostatic function during coast-down.
  • the quill can be maintained in substantially constant concentric alignment with the bushing, and this can be achieved independently of the speed at which the laying head is being operated.
  • vibration problems due to whirl in hydrodynamic bearings and clearances in mechanical roller bearings are eliminated or at the very least, significantly minimized to an extent that they no longer impede high speed operation of the laying head. This is achieved with the added benefits of lower operating temperatures, reductions in oil consumption and power loss, and relatively low starting torques.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • General Engineering & Computer Science (AREA)
  • Rolling Contact Bearings (AREA)
  • Sliding-Contact Bearings (AREA)
  • Winding, Rewinding, Material Storage Devices (AREA)
  • Guides For Winding Or Rewinding, Or Guides For Filamentary Materials (AREA)
  • Milling Processes (AREA)
EP14735721.4A 2013-06-20 2014-05-21 Rolling mill laying head Revoked EP3010662B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US13/922,668 US20140374526A1 (en) 2013-06-20 2013-06-20 Rolling mill laying head
PCT/US2014/038968 WO2014204609A1 (en) 2013-06-20 2014-05-21 Rolling mill laying head

Publications (2)

Publication Number Publication Date
EP3010662A1 EP3010662A1 (en) 2016-04-27
EP3010662B1 true EP3010662B1 (en) 2019-07-03

Family

ID=51063787

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14735721.4A Revoked EP3010662B1 (en) 2013-06-20 2014-05-21 Rolling mill laying head

Country Status (11)

Country Link
US (1) US20140374526A1 (ja)
EP (1) EP3010662B1 (ja)
JP (1) JP2016526485A (ja)
KR (1) KR20160021864A (ja)
CN (1) CN105705262B (ja)
AR (1) AR096653A1 (ja)
BR (1) BR112015032073B1 (ja)
MX (1) MX368517B (ja)
RU (1) RU2651552C2 (ja)
TW (1) TWI619562B (ja)
WO (1) WO2014204609A1 (ja)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109704143B (zh) * 2019-01-28 2020-10-09 浙江康盛股份有限公司 一种金属管收卷机控制系统及方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3661432A (en) 1970-02-26 1972-05-09 Ikegai Tekko Kk Ikegai Iron Wo Hydrostatic bearing assembly
US3761149A (en) 1970-10-15 1973-09-25 E Ferguson Hydrostatic radial bearing
US4122772A (en) 1971-12-13 1978-10-31 Dahlgren Harold P Hydrostatic bearer for printing press
US7086783B2 (en) 2001-12-14 2006-08-08 Morgan Construction Company Laying head bearing with offset preloading
US20110108652A1 (en) 2009-11-12 2011-05-12 Morgan Construction Company Rolling mill laying head
US20110168495A1 (en) 2010-01-11 2011-07-14 General Electric Company Lubrication of fluid turbine gearbox during idling or loss of electric grid

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU1140847A1 (ru) * 1982-12-24 1985-02-23 Всесоюзный ордена Ленина научно-исследовательский и проектно-конструкторский институт металлургического машиностроения Проволочна моталка
US5312065A (en) * 1992-02-05 1994-05-17 Morgan Construction Company Rod laying head with front and tail end ring control
CA2145459C (en) * 1994-04-26 1999-01-12 Terence M. Shore High speed laying head
JPH0919717A (ja) * 1995-07-06 1997-01-21 Kobe Steel Ltd レーイング式線材巻取機
JP3744973B2 (ja) * 1995-07-19 2006-02-15 東芝機械株式会社 静圧軸受の油圧装置
US6010088A (en) * 1998-07-21 2000-01-04 Morgan Construction Company Apparatus for centralizing rings being deposited in an overlapping pattern on a cooling conveyor
CN2427285Y (zh) * 2000-04-28 2001-04-25 太原重型机械(集团)有限公司 一种带快速锁紧装置的油膜轴承
JP2003307195A (ja) * 2002-04-11 2003-10-31 Ebara Corp 静圧軸受を備えた流体機械
ITMI20040308A1 (it) 2004-02-24 2004-05-24 Danieli Off Mecc Testa formaspire con dispositivo di smorzamento delle vibrazioni
CN102218447B (zh) * 2011-05-05 2013-04-03 安阳市合力高速冷轧有限公司 高延性冷轧带肋钢筋生产线
US8556517B1 (en) * 2012-09-19 2013-10-15 Siemens Industry, Inc. Bushing for oil film bearing

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3661432A (en) 1970-02-26 1972-05-09 Ikegai Tekko Kk Ikegai Iron Wo Hydrostatic bearing assembly
US3761149A (en) 1970-10-15 1973-09-25 E Ferguson Hydrostatic radial bearing
US4122772A (en) 1971-12-13 1978-10-31 Dahlgren Harold P Hydrostatic bearer for printing press
US7086783B2 (en) 2001-12-14 2006-08-08 Morgan Construction Company Laying head bearing with offset preloading
US20110108652A1 (en) 2009-11-12 2011-05-12 Morgan Construction Company Rolling mill laying head
US20110168495A1 (en) 2010-01-11 2011-07-14 General Electric Company Lubrication of fluid turbine gearbox during idling or loss of electric grid

Non-Patent Citations (4)

* Cited by examiner, † Cited by third party
Title
EL SHERBINYT M., ET AL.: "Optimum design of hydrostatic journal bearings Part I: Maximum load capacity", TRIBOLOGY INTERNATIONAL, vol. 17, no. 3, June 1984 (1984-06-01), pages 155 - 161, XP055705270
J.K. MARTIN: "Industrial Lubrication and Tribology", DESIGN GUIDELINES FOR HYDROSTATIC JOURNAL BEARINGS, 2006, pages 135 - 138, XP055705303
M.K. GHOSH ET AL.: "Design of multirecess hydrostatic oil journal bearings", TRIBOLOGY INTERNATIONAL, 1980, pages 73 - 78, XP055705283
R. BASSANI ET AL.: "Hydrostatic Lubrication - Tribology series 22", 1992, article R. BASSANI ET AL.: "Chapter 1 and Chapter 8", pages: 1-14 - 236-251, XP055705276

Also Published As

Publication number Publication date
CN105705262A (zh) 2016-06-22
CN105705262B (zh) 2018-11-13
EP3010662A1 (en) 2016-04-27
MX2015017764A (es) 2016-08-03
RU2016101352A (ru) 2017-07-25
MX368517B (es) 2019-10-07
TWI619562B (zh) 2018-04-01
JP2016526485A (ja) 2016-09-05
TW201511858A (zh) 2015-04-01
RU2016101352A3 (ja) 2018-03-23
BR112015032073A2 (pt) 2017-07-25
KR20160021864A (ko) 2016-02-26
US20140374526A1 (en) 2014-12-25
WO2014204609A1 (en) 2014-12-24
BR112015032073B1 (pt) 2020-10-20
AR096653A1 (es) 2016-01-27
RU2651552C2 (ru) 2018-04-20

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