EP1179373A2 - Cylindre à enveloppe creuse - Google Patents

Cylindre à enveloppe creuse Download PDF

Info

Publication number
EP1179373A2
EP1179373A2 EP01117980A EP01117980A EP1179373A2 EP 1179373 A2 EP1179373 A2 EP 1179373A2 EP 01117980 A EP01117980 A EP 01117980A EP 01117980 A EP01117980 A EP 01117980A EP 1179373 A2 EP1179373 A2 EP 1179373A2
Authority
EP
European Patent Office
Prior art keywords
core body
lubricant
core
hollow jacket
lubricant supply
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
EP01117980A
Other languages
German (de)
English (en)
Other versions
EP1179373A3 (fr
EP1179373B1 (fr
Inventor
Thorsten Bode
Helmut Kühn
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 Siemag AG
Original Assignee
SMS Demag 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 SMS Demag AG filed Critical SMS Demag AG
Publication of EP1179373A2 publication Critical patent/EP1179373A2/fr
Publication of EP1179373A3 publication Critical patent/EP1179373A3/fr
Application granted granted Critical
Publication of EP1179373B1 publication Critical patent/EP1179373B1/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
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02—Shape or construction of rolls
    • B21B27/03—Sleeved rolls
    • B21B27/05—Sleeved rolls with deflectable sleeves
    • 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 hollow jacket roller, which has a rotatable around the central axis, hydraulically supported core body as a slide bearing.
  • EP 0 937 515 A1 is based on the object of a to create a rigid roller that can be easily and quickly adapted to a Changing the rolling conditions, especially the strip width, allows.
  • the known roller consists of a rotating roller jacket with an inside of the roller shell arranged slide bearing in the form of a rotating body to influence the bending stiffness of the roll shell.
  • This rotating body should be a to the load zone of the roll shell generated by the rolling stock Counterforce in such a way that this counterforce is evenly over distributes the load zone of the rolling stock and thus the contour of the roll or the work roll in the load area is straight or adapted to the rolling stock profile becomes.
  • the known system is due to the hydrodynamic Pressure development that is not influenced by an external pressure supply can be called a passive system, which is this system not controllable under load.
  • Hollow-shell rollers are also known, which are arranged around an internal, stationary one Rotate the carrier.
  • DE 3119378 describes that between the Carrier and the roll shell a, sealed by sealing strips, hydrostatic Pressure chamber is located and additional stamp-like support elements are provided are connected to at least one pressure medium source and located in the Plane of symmetry of the pressure chamber. With such an arrangement can choose the pressures in the pressure chamber and the forces of the support elements the pressures in their cylinder spaces are determined independently of one another, and thus determine the deflection behavior.
  • the invention has for its object a generic hollow jacket roller to create with an inner core body as a plain bearing, in which the described Disadvantages are avoided and the profile and flatness Allow the rolled flat material to be influenced.
  • the core body is formed with a bale that is variable over the circumference and the core bale length.
  • the setting of a specific outer contour in the load area and under load can thus be achieved.
  • the core body has a crowning that is variable over the circumference and the core bale length, because it can be designed such that a contour is ground from the center of the core body over the core bale length, which in extreme cases can be any crowning n based on experience for normal use corresponds, whose size also depends on the angle of rotation ⁇ .
  • the crowning n generally corresponds to the bending line to be expected under rolling force, which can be pre-calculated; the angle of rotation ⁇ results from the change in position of the core body when it is rotated out of its original position about its central axis to set the crown n between 0 and n.
  • Such a core body can be produced mechanically, the angle of rotation ⁇ is additionally detected and a grinding wheel is set in the X and Y directions becomes.
  • the shape of the core body is freely selectable, for example in the form of an ellipsoid or paraboloides.
  • the core body is cylindrical towards the bearing journal educated.
  • An embodiment of the invention provides that in the core body Lubricant feed hole is provided, from the at least one channel to one leads on the circumference of the core body introduced distributor groove.
  • the channel or the channels between them Bore and the distributor groove introduced on the circumference of the core body can be Lubricant for lubrication in the gap between the load area Insert the hollow jacket and core body.
  • the distributor groove on the circumference is arranged so that the entire range from the minimum to the maximum core crowning is adjustable, the distributor groove in all cases outside the hydrodynamic The bearing area remains and therefore no impairment of the hydrodynamic principle of action occurs.
  • Computer systems for profile and flatness control can be the core crowning also adjust under load. Thus lies with regard to symmetrical flatness errors an active actuator.
  • the Core body In one-way operation, i.e. H. with a certain direction of rotation of the hollow shell, the Core body from its initial position by the twist angle ⁇ from 0 ° to 180 ° twisted out until the core body takes up a position with its spherical contour, which is adapted to the expected bending line.
  • the core body depends on the different Sense of rotation either by the angle of rotation ⁇ from 0 ° to -120 ° or ⁇ by Is rotated 0 ° to + 120 ° out of its original position.
  • An embodiment of the invention provides that the core body over the core bale length is divided into several zones, and in these zones the extent can be divided into several lubricant supply areas.
  • This up and down Subdivision can in particular optimize the hydrostatic bearing principle and due to the individual zones on the one hand an ideal adaptation of the contour of the core body to the existing bending line and on the other hand also a zone-wise Influencing the roll gap and thus the rolling stock profile and the Achieve rolling flatness.
  • an embodiment of the invention provides that the core body for each Zone and lubricant supply holes running to each lubricant supply area which is assigned a channel to one in each zone placed on the circumference of the core body in each lubricant area Distributor groove leads.
  • This configuration of the invention allows one to be targeted effective influencing of the gap of the load area between the core body and achieve the hollow jacket through the selectively switchable lubricant pressure, whereby a desired zone-wise impact on the roll gap and thereby on the rolled profile and on the rolling flatness is possible.
  • the selected switchable Lubricant pressure and the required flow rate can be via known higher-level computer systems for profile and flatness control determine. This computer system controls valves in the connecting lines between a lubricant source and the lubricant supply holes are mounted.
  • Lubricant feed areas are provided in return channels which, on the one hand, in Lubricant collecting pockets delimiting the lubricant supply area and on the other hand to at least one lubricant return hole arranged in the core body are connected, the lubricant over the Return channels and the lubricant return hole can be sucked off.
  • both axial bearings and spherical ones Have the bearing installed.
  • the core body can thereby be rotated under load adjust because a tilt-free storage of the core body is achieved.
  • the angle of twist for setting the crown is determined using known computer systems determined that a control signal to access units for rotating the core body to transfer.
  • the proposed hollow jacket roller is advantageously used as a backup roller, preferably used in four-high and other multi-roll stands.
  • a core body 2 of a hollow jacket roller 1, e.g. as a backup roller in a four-high scaffold, has a circular shape in the middle (see section A - A in FIG. 1) Form on, with the center of the circle on the axis of the cylindrical core body ends 3 lies. Starting from the middle is symmetrical towards both ends over the core bale length 4 of the core body 2 a contour 5 ground in Extreme case corresponds to a crowning n (cf. section BB in FIG. 1), its size on the one hand from the expected bending line under rolling force, and on the other hand also depends on the angle of rotation ⁇ .
  • the expected bending line below Rolling force is based on empirical values, and the twist angle ⁇ results resulting from the change in position of the core body when this to adjust the effective crowning between 0 and n from its original position to its Center axis is rotated.
  • the core body 2 shown in Figure 1 has been manufactured mechanically, for which purpose the angle of rotation ⁇ was also detected and the grinding wheel 6 in the x and y directions was employed accordingly.
  • FIG. 2 shows the core body 2, which is not rotationally symmetrical, in one Hollow jacket 7 existing hollow jacket roller 1 as a backup roller of a four-high stand. It supports a work roll 8 which bears against the rolling stock 9. The Roll arrangement is shown in the unloaded state.
  • FIG. 3 shows the rolling arrangement according to FIG. 2 in the loaded state.
  • the Core body 2 was here adapted to an expected pre-calculated maximum bending line, by twisting by the twist angle ⁇ set so that the core body 2 with its maximum ground Contour 5, i.e. counteracts the crowning n of the maximum bending line.
  • the possible setting range 10 of the core body 2 by the twist angle ⁇ of In FIG. 4a, 0 ° to 180 ° is for the load case of the so-called one-way operation, as a section through the circular center of the core body 1 (see section A-A shown in Figure 1).
  • the one centrally located in the core body 2 lubricant supply hole 11, and branching outwards from this to an outside on the circumference of the Core body 2 provided distributor groove 12 has leading channels 13.
  • the fed Lubricant can be determined by the direction of rotation D of the hollow jacket 7 in Lubricant flow direction 14 to the gap of the load area 15 between Conduct core body 2 and hollow jacket 7.
  • FIG. 4 b shows the course of the distributor groove 12 with the core bale length 4 of the core body 2 distributed several, the lubricant supply bore 11 with the Distribution groove 12 connecting spaced on one side of of the lubricant supply bore 11 branching channels 13 in perspective Longitudinal section of the core body 2.
  • Lubricant supply system in cross section of the core body 2 for the so-called One-way operation shown.
  • the core body 2 for one-way operation can be from a here also shown in Figure 4a for the lubricant supply there underlying neutral position 16 by the angle of rotation ⁇ up to 180 ° accordingly Turn arrow 17 continuously to position 18.
  • the crowning n is infinitely variable between 0 and n.
  • FIG. 5a shows a cross section comparable through a roller arrangement that according to Figures 4a, 4b with the difference that here the load case of so-called reversing operation is shown.
  • the lubricant to the gap of the load area 15 between the core body Promote 2 and 7 hollow jacket.
  • the core body 2 Starting from a neutral starting position 19 can the core body 2 either around the twist angle range ⁇ from 0 ° to Turn + 120 ° to position 20 or around the angle of rotation ⁇ of Turn 0 ° to -120 ° to position 21.
  • the lubricant flow direction 14a or 14b in the gap of the load area 29 between the core body 2 and Hollow jacket 7 corresponds to the direction of rotation D or D '.
  • FIG. 5b shows the arrangement in a perspective longitudinal section of the core body 2 the distribution groove 12 with lubricant supply bore 11 and the channels 13 for the Reversing operation shown (see also section B-B).
  • the core body 2 for the Reversing operation is in accordance with the respective direction of rotation D or D ' Starting position 19 by the angle of rotation ⁇ up to + 120 ° in position 20 or the angle of rotation ⁇ is continuously rotated up to -120 ° to position 21. simultaneously here again the crowning n can be steplessly between 0 and n to adjust.
  • FIG. 6 shows a possible division of the core body 2 into successive ones Zones 2a to 2g, with a lubricant collection pocket 22a in each zone to 22g is arranged, the return channels 23a to 23g with a central Lubricant return bore 24 which contains the lubricant from all zones collects and returns, is connected.
  • lubricant collecting pockets 22a to 22g delimiting the lubricant supply area, which are connected to a lubricant return hole 24 via return channels 23a to 23g.
  • the supply of lubricant can be implemented via a lubricant supply bore 11a to 11g which is separately introduced for each zone 2a to 2g and for each lubricant supply area I to IV.
  • the lubricant pressure that can thus be selected can be used to set, for example in the lubricant supply area I, a minimum core crowning designated as I 1 . If additional lubricant, triggered by the higher-level profile and flatness control, is now applied to the lubricant supply area I through the lubricant supply bores 11a to 11g, the core crowning increases in this area in a targeted manner. In this and each other zone, the individual influence of the lubricant supply areas I to IV formed there can directly influence the roll gap 25 and thus have a direct effect on the rolling stock profile and the rolling stock flatness.
  • FIG. 8 shows a configuration of the lubricant disposal that differs from FIG. 7.
  • the lubricant supply areas I to IV in the circumferential direction of each zone 2a to 2g delimiting lubricant collecting pockets 22a to 22g and the return channels 23a to 23g opening here is a separate one Lubricant return hole 24a to 24g assigned, through which the Lubricant triggered by the higher-level profile and flatness control can be suctioned off separately.
  • An embodiment of a storage of the hollow jacket roller 1 is in longitudinal section represented by the backup roller and a chock 26 in Figure 9.
  • This has on the drive side an axial bearing 27, a spherical bearing 28, sealing devices 29, a lubricant return hole 30 for returning the after Figures 4a, 4b, 5a and 5b supplied lubricant and a device 31 for deriving the lubricant collected in the chock 26.
  • the backup roller can be firmly clamped on both sides by the axial bearing 27, at the same time but the core body 2 rotate at its ends 3 due to the spherical bearing 28 and adjust under load.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Rolling Contact Bearings (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Friction Gearing (AREA)
  • Delivering By Means Of Belts And Rollers (AREA)
EP01117980A 2000-08-10 2001-07-25 Cylindre à enveloppe creuse Expired - Lifetime EP1179373B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10039000 2000-08-10
DE10039000A DE10039000A1 (de) 2000-08-10 2000-08-10 Hohlmantelwalze

Publications (3)

Publication Number Publication Date
EP1179373A2 true EP1179373A2 (fr) 2002-02-13
EP1179373A3 EP1179373A3 (fr) 2004-03-24
EP1179373B1 EP1179373B1 (fr) 2005-06-08

Family

ID=7651936

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01117980A Expired - Lifetime EP1179373B1 (fr) 2000-08-10 2001-07-25 Cylindre à enveloppe creuse

Country Status (3)

Country Link
EP (1) EP1179373B1 (fr)
AT (1) ATE297267T1 (fr)
DE (2) DE10039000A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015058896A1 (fr) * 2013-10-24 2015-04-30 Robert Bosch Gmbh Machine à pistons axiaux

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57127507A (en) * 1981-01-30 1982-08-07 Ishikawajima Harima Heavy Ind Co Ltd Rolling mill
DE3119387A1 (de) * 1981-05-06 1982-11-25 Escher Wyss AG, Zürich Walze fuer eine walzvorrichtung
JPH0299206A (ja) * 1988-09-30 1990-04-11 Kobe Steel Ltd ４段圧延機
EP0937515A1 (fr) * 1998-02-20 1999-08-25 Sms Schloemann-Siemag Aktiengesellschaft Cylindre pour influencer la planéité

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57127507A (en) * 1981-01-30 1982-08-07 Ishikawajima Harima Heavy Ind Co Ltd Rolling mill
DE3119387A1 (de) * 1981-05-06 1982-11-25 Escher Wyss AG, Zürich Walze fuer eine walzvorrichtung
JPH0299206A (ja) * 1988-09-30 1990-04-11 Kobe Steel Ltd ４段圧延機
EP0937515A1 (fr) * 1998-02-20 1999-08-25 Sms Schloemann-Siemag Aktiengesellschaft Cylindre pour influencer la planéité

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 006, no. 224 (M-170), 9. November 1982 (1982-11-09) -& JP 57 127507 A (ISHIKAWAJIMA HARIMA JUKOGYO KK), 7. August 1982 (1982-08-07) *
PATENT ABSTRACTS OF JAPAN vol. 014, no. 305 (M-0992), 29. Juni 1990 (1990-06-29) -& JP 02 099206 A (KOBE STEEL LTD), 11. April 1990 (1990-04-11) *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015058896A1 (fr) * 2013-10-24 2015-04-30 Robert Bosch Gmbh Machine à pistons axiaux
CN105683561A (zh) * 2013-10-24 2016-06-15 罗伯特·博世有限公司 轴向活塞机
CN105683561B (zh) * 2013-10-24 2018-09-21 罗伯特·博世有限公司 轴向活塞机

Also Published As

Publication number Publication date
EP1179373A3 (fr) 2004-03-24
ATE297267T1 (de) 2005-06-15
EP1179373B1 (fr) 2005-06-08
DE10039000A1 (de) 2002-02-21
DE50106434D1 (de) 2005-07-14

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