Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21B—ROLLING OF METAL
  • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
  • B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21B—ROLLING OF METAL
  • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
  • B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills
  • B21B35/142—Yielding spindle couplings; Universal joints for spindles
  • B21B35/143—Yielding spindle couplings; Universal joints for spindles having slidably-interengaging teeth, e.g. gear-type couplings
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21B—ROLLING OF METAL
  • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
  • B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills
  • B21B35/148—Spindle carriers or balancers
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21B—ROLLING OF METAL
  • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
  • B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills
  • B21B35/142—Yielding spindle couplings; Universal joints for spindles
  • B21B35/145—Hooke's joints or the like with each coupling part pivoted with respect to an intermediate member

Definitions

• the invention relates to a roll stand with two rolls forming a roll gap, which can be driven by drive spindles each with their own drive motors, in particular a four-high stand, a toothed coupling combined with a larger angular shaft displacement permitting joint coupling being used.
• twin drive - In the case of a roll stand, the arrangement of two drive motors - a so-called twin drive - requires large deflection angles of the drive spindles due to the large center-to-center distance of the motor drive shafts or, if one wishes to avoid them, correspondingly long drive spindles, but this would result in a smooth drive. This problem arises particularly in the case of four-high reversing stands, in which the vertical adjustment path of the upper work roll is large.
• a roll stand of the type described in the introduction is known, the rolls each having a first tooth coupling with a first shaft and a second tooth coupling with a connecting shaft and further via a universal joint with an articulated shaft and a further universal joint is connected to a drive motor or another drive shaft.
• the connecting shafts are mounted in an adjustable guide in a parallel arrangement.
• relatively large angles must be taken up by the toothed couplings, because a sufficiently greater distance must be created between the universal joints arranged on the connecting shafts. This significantly increases the wear on the tooth clutches.
• Another disadvantage of the known roll stand is that the distance between the motor and the roll stand is very large, which results in a space-consuming drive arrangement.
• the invention aims to avoid these disadvantages and difficulties and has as its object to provide a roll stand in which drive spindles can also be provided with rollers with small diameters and a relatively large center distance of the motor drive shafts, which have a large diffraction angle - and thus relatively short overall length - can be arranged, but nevertheless very high drive torques can be transmitted, for example for rolling high-strength rolling stock and for rolling with large pass reductions.
• each drive spindle is formed by a maximum of two mutually inclinable parts and that at least one of the drive spindles, which is formed by two parts, a single tooth coupling for connection to a roller and at the other two articulation points between its parts and has articulated couplings towards the drive motor, in particular universal joints.
• a particularly space-saving construction which enables dimensioning that is optimal in terms of torque even with very narrow center distances of the rollers, is characterized in that only one of the drive spindles consists of two parts which are connected to one another by an articulated coupling, part of which is connected to the drive motor via an articulated coupling, is formed and the other drive spindle extends as a one-piece toothed spindle from the tooth coupling to a coupling arranged on the drive shaft of the motor and permitting angular shaft displacements, preferably also a tooth coupling.
• the dimensioning of the cardan shaft and also the toothed spindles can be improved if the axes of the toothed spindles diverge in the direction of the drive motors.
• the toothed couplings expediently have spherical external toothings, the internal toothings of the toothed couplings extending in the axial direction over a multiple of the external toothing in order to achieve axial mobility of the driven rollers.
• the part that is movable relative to a roller is the Tooth coupling of the toothed spindle, which is connected to the cardan shaft, is supported by a compensating device for maintaining a predetermined angular position on the foundation, the compensating device advantageously being formed by a parallel guide designed as a lever system.
• the toothed spindles are advantageously supported against the foundation by means of rotary bearings by means of laterally guided spindle balancings.
• FIG. 1 shows an oblique view
• FIG. 2 shows a vertical section through the axes of the drive spindles of a detail of FIG. 1 of a first embodiment
• Fig. 3 shows a schematic representation of another embodiment in side view.
• Two work rolls 1, 2 of a quarto heavy-plate stand, the center distance 3 of which can be adjusted to the desired plate thickness, are supported on the roll stand 7 with their drive pins 4, 5 via bearings, which are generally designated 6, according to FIG. 1.
• support rolls 8 are provided, which are also rotatably mounted on the roll stand 7 via bearings 9.
• the arrangement of the drive motors 13, 14 is such that the center distance 15 of the drive shafts 16 of the drive motors 13, 14 is as small as possible.
• the drive spindles 11, 12 are arranged inclined to one another.
• each drive pin 4, 5 of the work rolls 1, 2 is rotatably connected to a sleeve 17 which has an internal toothing 18.
• a spherical external toothing 19 engages in this internal toothing 18 and is arranged on the outside on a further sleeve 20.
• the sleeves 17 and 20 thus each form a tooth coupling.
• the length of the internal toothing 18 is many times longer than the teeth of the external toothing 19, so that axial mobility is possible.
• the work rolls 1, 2 can be moved in the axial direction with respect to the roll stand 7. Different axial positions of the work rolls 1, 2 are shown in FIG. 2.
• the sleeves 20 provided with the external toothing 19 are each mounted non-rotatably on a spindle 21 or 22 and together with this spindle 21 or 22 form a so-called toothed spindle.
• the drive spindle 12 of the upper work roll 2 is formed by the toothed spindle 20, 22 and an adjoining cardan shaft 23, which is connected via its universal joints 24 on the one hand to the toothed spindle 20, 22 and on the other hand to the drive shaft 16 of the upper drive motor 14 .
• the universal joints 24 instead of the universal joints 24, other articulated couplings that are suitable for transmitting high torques, for example flat pin couplings, could also be provided.
• the drive spindle 11 of the lower work roll 1 is rigid up to the drive shaft 16 of the lower drive motor 13 - albeit in several parts if necessary - and coupled to the drive shaft 16 of the lower drive motor 13 via a toothed coupling 24 '.
• the axial positions of the toothed spindles 20, 21 and 20, 22 are chosen so that their axes form an angle between 0.5 and 1.5 °, preferably an angle of approximately 0.8 °, with the axes of the associated work rolls 1, 2 .
• the toothed spindles 20, 22 must be supported against the foundation 26 by means of a compensating device designed as a parallel guide 25 in order to maintain the optimum angular range.
• the parallel guide 25 is formed by an articulated lever system, etc. engage approximately vertically directed tabs 27 on a housing 29 surrounding the upper toothed spindle 20, 22 and supported with respect to the toothed spindle 20, 22 by means of rotary bearings 28, which housing 29 is secured against rotation with respect to the foundation 26.
• the tabs 27 are each articulated on an angle lever 30, the knee joint 31 of which is rotatably supported on the foundation 26.
• the further lever arms 32 of the angle lever 30 are connected via a tab 33 absorbing tensile or compressive forces. In this way, the toothed spindle 20, 22 of the upper work roll 2 can be adjusted together with it in the vertical direction parallel to itself, for example for setting differently high roll gaps 34.
• the toothed spindles 20, 21 and 20, 22 are opposite the foundation 26 by means of spindle balancings 35, 36 supported on a lateral guide 26 ', which are only shown in FIG. 2 supported.
• the inventive design of the roll stand enables the universal joints 24 of the cardan shaft 23 to be made very large despite the very small diameter 10 of the work rolls 1, 2, etc. as a result of the provision of the tooth clutches 17, 20 and the tooth spindles 20, 21 and 20, 22.
• the arrangement of the toothed spindles 20, 21 and 20, 22 is such that they diverge in the direction of the drive motors 13, 14, which makes it possible to design the universal joint 24 connecting the cardan shaft 23 with the toothed spindle 20, 22 with the maximum size .
• This is important insofar as the torque to be transmitted increases with the third power of the diameter of the universal joints 24 or the cardan shaft 23.
• toothed clutches 17, 20 means that only a small displacement force is required to move the work rolls 1, 2. This is far below the displacement force that is necessary, for example, to move a work roll driven by means of a conventional cardan shaft with length compensation.
• a further advantage results from the installation of a spring-damper element designed as a spring cup 37 in the lever system of the parallel guide 25.
• a spring-damper element designed as a spring cup 37 in the lever system of the parallel guide 25.
• the spring cup 37 can be provided on any lever of the lever system.
• the spring-damper element is preferably adjustable as a function of force.
• the upper work roll 2 with the drive motor 14 assigned to it can be driven in the same way as illustrated in FIG. 1, ie via a sleeve 17 forming a tooth coupling, a spindle 22, a universal joint 24, and a cardan shaft 23 and another universal joint 24 connected to the drive motor 14.
• the universal joints 24 instead of the universal joints 24, other high-torque articulated couplings could be provided, for example flat-pin couplings.
• the lower work roll 1 is coupled in the same way to the drive motor 13 assigned to it, that is to say via a sleeve 17 forming a tooth coupling, a spindle 22, a universal joint 24, a cardan shaft 23 and another universal joint 24.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Gear Transmission (AREA)
• Buildings Adapted To Withstand Abnormal External Influences (AREA)
• Iron Core Of Rotating Electric Machines (AREA)
• Transmission Devices (AREA)
• Manipulator (AREA)
• Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
• Machines For Manufacturing Corrugated Board In Mechanical Paper-Making Processes (AREA)
• Bending Of Plates, Rods, And Pipes (AREA)
• Crushing And Grinding (AREA)
• Straightening Metal Sheet-Like Bodies (AREA)

Applications Claiming Priority (4)

Publications (3)

Family

ID=3497792

Family Applications (1)

Country Status (7)

Families Citing this family (10)

Family Cites Families (13)

• 1995
  • 1995-04-25 AT AT0071195A patent/AT405619B/de not_active IP Right Cessation
• 1996
  • 1996-04-23 US US08/945,478 patent/US6062058A/en not_active Expired - Lifetime
  • 1996-04-23 AT AT96910844T patent/ATE181520T1/de not_active IP Right Cessation
  • 1996-04-23 DE DE59602284T patent/DE59602284D1/de not_active Expired - Lifetime
  • 1996-04-23 WO PCT/AT1996/000078 patent/WO1996033823A1/fr not_active Ceased
  • 1996-04-23 KR KR1019970707322A patent/KR19990007799A/ko not_active Withdrawn
  • 1996-04-23 EP EP96910844A patent/EP0822872B2/fr not_active Expired - Lifetime
  • 1996-04-23 JP JP8532029A patent/JPH11503975A/ja active Pending

Non-Patent Citations (1)

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