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
  • B21B35/141—Rigid spindle couplings, e.g. coupling boxes placed on roll necks
• • 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

Definitions

• the invention relates to a roller drive according to the preamble of
• JP-60-37205 describes a rolling stand having upper and lower rollers, each having an independent drive in the form of a drive motor.
• a gear coupling is first arranged, followed - in the direction of
• Connecting shaft provided two radial rolling bearings.
• a rolling mill with a roller drive according to the preamble of claim 1 is disclosed in the Auslegeschrift DT 24 54 036 B2.
• Each roller drive has a propeller shaft, referred to here as articulated spindles, on which is connected on one side via a coupling, not shown, with the roller and on the other side remote from the cylinder via a coupling with axial length compensation with the motor shaft.
• a propeller shaft referred to here as articulated spindles
• Joint spindles are mounted in two bearings, supported. On one side, the support beams are connected to hydraulic supports, while on the other side they are mounted in bearing blocks.
• the European patent EP 0 822 872 B2 describes a rolling stand with two rollers forming a roller gap, which are drivable via drive spindles of their own drive motors.
• a drive train each with a toothed coupling combined with another joint coupling is provided for each roller, wherein the toothed coupling is located directly on the
• roller drive pin of the roller connects and allows axial length compensation.
• roller drive has considerably less of the aforementioned generic drive trains, that only a single drive train per pair of rollers an articulated coupling with two larger
• gear couplings each allow an angular position in the range between 0.5 and 1, 5 degrees, preferably an angular position of about 0.8 degrees
• drive shafts as they are generically provided in each drive train to each roller, angular displacements well beyond this range For example, greater than 5 degrees, 10 degrees or even 20 degrees, too.
• Propeller shafts in order to transmit high torques can, to a large cardan shaft weight, which in turn leads to relatively large forces acting on the connecting parts of the propeller shaft.
• the present invention has for its object to provide a roller drive and a rolling stand with such a roller drive, in which despite a small number of radial bearings optimum distribution of bending forces, weight forces and forces is achieved from the gimbal error and all in
• Powertrain provided components can be made relatively slim.
• the object of the invention is achieved by a roller drive with the
• roller drive according to the invention is based on a variety of
• Drive trains at least two drive trains, for the transmission of
• the two drive trains or the plurality of drive trains driven by one or more common drive motors, or to provide a plurality of drive motors per drive train.
• the propeller shafts can be driven by a so-called comb-rolling gear, which the
• a propeller shaft comprising a first, a greater angular deviation permitting joint, and a second, a greater angular deviation permitting joint. Accordingly, it is in the joints not to couplings or toothed couplings, which allow only the small angular deviations according to the introduction. Rather, angular deviations of more than 5 degrees, in particular more than 10 degrees, are possible between the two end parts of the propeller shaft, in particular even between each end part and the middle part of the propeller shaft.
• a roller-distal end part of each propeller shaft is assigned to each of the drive motors or the common drive motor and is from this
• roller distal end part directly to a
• a roller near end part of each PTO shaft is in each case one of the rollers
• the two end parts - ie the roller near end portion and the roller distal end portion - each cardan shaft via the two joints and a connecting the two joints middle part with each other.
• the central part is designed in particular without length compensation, that is, it advantageously has a fixed axial length.
• Drive shafts of the various drive trains can according to a
• Embodiment be designed with a different axial length.
• the joints themselves, for example, as a universal joint or as another, a corresponding angular deviation permitting joint coupling, for example, flat pin coupling executed.
• each propeller shaft is each connected to a toothed coupling with length compensation, wherein the
• Tooth coupling with length compensation for coaxial or substantially coaxial connection to a drive pin of one of the rollers is determined.
• the connection can be direct or indirect.
• a coupling half of the toothed coupling is advantageous, for example in the form of a sleeve or a pin, directly connected to the drive pin of the roller, for example, the drive pin rotationally enclosing or in the
• the toothed coupling according to the invention comprises two mutually displaceable in the longitudinal direction, via a toothed engagement with each other in one
• each PTO shaft and each toothed clutch is one over each
• the middle part of each propeller shaft is free of a radial bearing and / or free of any shaft bearing, which is arranged away from that joint between the central part and the roller-near end part.
• no bearing in the region of the axial center and / or at the distal end of the central part of the propeller shaft is provided, or a bearing support at both axial ends of the central part, which are merged into a common central part support, as is common in the prior art.
• the common radial bearing of the propeller shaft and the toothed coupling on the side of the central part of the propeller shaft is immediately adjacent to the relevant joint arranged so that it surrounds the middle part of the propeller shaft. This allows a particularly favorable length distribution based on the end of the
• PTO shaft can be achieved together with the toothed coupling and the cardan shaft middle part.
• the middle part can be made comparatively longer, resulting in smaller diffraction angles in the PTO shaft.
• the end portion together with the gear coupling can be made shorter, resulting in smaller bending moments, which are exerted by the drive train on the drive pin of the roller.
• Another advantage is that due to the greater distance between the longitudinal axes of the middle parts compared to the distance between the longitudinal axes of the toothed couplings of both rollers, in particular an upper roller and a lower roller, which together form the nip, the radial bearing with a larger outer diameter can be performed, which in particular its outer ring can be made more robust.
• the bearing interface that is the interface between rotating and stationary part of the bearing, in which particular rolling elements, for example in the form of cylindrical rollers, are positioned to a relatively larger diameter, whereby the possible power consumption is increased.
• the radial bearing can advantageously be hinged to compensate for angular movements of the middle part.
• a lifting mechanism for the radial bearing, in particular jointly for the radial bearings of both propeller shafts can advantageously be designed such that it is synchronized with a movement of one of the two rollers forming the nip, in particular the work roll, for example in the axial direction, always at a small deflection angle, in particular constant Bend angle, to ensure the gear couplings. Furthermore, it is possible to carry out the gear coupling free of its own radial bearing, so that the two coupling halves only by the drive pin the roller and the propeller shaft or its roll-near end portion are supported.
• the two toothed couplings associated with a roller pair forming the roller gap may have different axial lengths relative to one another. Overall, both gear couplings can be made relatively short, although they allow axial length compensation. Thus, it is not necessary to provide an axial distance in the toothed couplings for this length compensation, which prevents a collision with a stationary radial bearing.
• a pressing device may be provided which at least the roller-side
• Coupling halves in the toothed engagement over a multiple of the teeth of the other coupling half For example, an internal toothing extends over a multiple in the direction of the longitudinal axis of an external toothing or vice versa.
• a rolling stand according to the invention has at least two rolls forming a roll gap, which are driven by two drive motors via a roll drive, which is designed in accordance with the roll drive according to the invention. At least one roller of the roller pair is advantageous in
• Figure 1 is a side view and a plan view of an inventive
• FIG. 1 shows a schematic section through the roller drive according to the invention
• FIG. 1 a shows a schematic side view and in FIG. 1 b a plan view of a rolling mill designed according to the invention
• Drive motor 2 to a first roller 3 and a second lower drive train 2 for transmitting drive power from a second drive motor 4 to a second roller 5.
• the first roller 3 and the second roller 5 together form a roller gap 13.
• both drive trains 1, 2 each have a propeller shaft 6, comprising a first, a greater angular deviation permitting joint 7, and a second, a greater angular deviation permitting joint 8.
• the distal end part 6.1 each articulated shaft 6 is one of the
• each propeller shaft 6 is assigned to one of the rollers 3, 5 in order to drive them with the interposition of a toothed coupling 9 with length compensation.
• the roller-distal first joint 8 of the propeller shaft 6 and the second roller-near joint 8 of the propeller shaft 6 are interconnected via a central portion 6.3 of the propeller shaft 6, wherein in the present case the middle part 6.3 is composed of three sections, namely a comparatively long central portion, on which both sides in each case a part is flanged with a yoke.
• Each central part 6.3 of the propeller shaft is supported directly by a radial bearing 11 positioned next to the second joint 8. Due to the provided flanges at both ends of the middle part 6.3 and its middle section, the bearing 11 is designed as a circumferentially split bearing, comprising two or more segments, in particular circular ring segments, which are connected to each other to form a closed bearing ring.
• a pressing device is quantified, which is provided to press the toothed coupling 9 in the direction of the rollers 3, 5.
• the longitudinal axes 12 of the middle parts 6.3 of the cardan shafts 6 diverge from one another.
• the roller-distant coupling halves of the toothed coupling 9 due to the
• the radial bearing 11, which is assigned to the first drive train 1, has, as indicated by the dimension lines, a smaller distance from the first roller 3 than the radial bearing 11, which is assigned to the second drive train 2.
• FIG. 2 further details of the toothed couplings 9 are shown schematically.
• the second roller near coupling half 9.2 connects, which has an internal toothing 9.3.
• the external teeth 9.4 of the first coupling half 9.1 has a spherical shape, as you can see, that is, a curvature extending in the axial direction in the toothed coupling 9 extends.
• the first coupling half 9.1 is connected via a flange 17 with the end part 6.2 of the propeller shaft 6. This flange connection 17 is also shown in FIG. It can also be seen, both in the figure 1 and in Figure 2, a second flange 19, with which the second
• Coupling half 9.2 is connected to the roll neck enclosing sleeve 16.
• the axial length compensation in the toothed clutch 9 is achieved here by the toothed engagement 10, in the figure 2 with the internal toothing 9.4 and the external toothing 9.3.
• the radial bearings 11 each enclose a central part 6.3 of the propeller shaft 6 and are positioned directly next to the joint 8.
• the positioning is selected directly adjacent to the flange 20, which is the roller distal half 21 of the second joint 8, you could also say the roller distant yoke, with the one-piece, here cylindrical central portion of the middle part 6.3, which, as stated, at its remote from the roller End has a corresponding flange, connects. Therefore, an even closer positioning of the radial bearing 11 in the direction of the axis of rotation of the second joint 8 is not possible or only with difficulty.
• the positioning of the radial bearing 11 is deviating from a central part 6.3 ausbalancierenden bearing in the middle of the middle part 6.3 or two support points in the region of both ends of the middle part 6.3.
• the radial bearing 11 does not extend to the axial center of the propeller shaft 6 or the middle part 6.3 of the propeller shaft 6.
• the radial bearing 11 in the outer third or in the outer quarter of the axial
• PTO shaft 6 is arranged.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Friction Gearing (AREA)
• Gear Transmission (AREA)
• Rolls And Other Rotary Bodies (AREA)

Applications Claiming Priority (2)

Publications (2)

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ID=42096721

Family Applications (1)

Country Status (7)

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• 2009
  • 2009-06-30 DE DE102009031324A patent/DE102009031324A1/de not_active Withdrawn
  • 2009-12-10 CN CN200980132021.6A patent/CN102123799B/zh active Active
  • 2009-12-10 WO PCT/EP2009/008818 patent/WO2011000397A1/fr active Application Filing
  • 2009-12-10 AT AT09774636T patent/ATE554864T1/de active
  • 2009-12-10 US US12/734,689 patent/US8904841B2/en not_active Expired - Fee Related
  • 2009-12-10 JP JP2012516519A patent/JP5636425B2/ja active Active
  • 2009-12-10 EP EP09774636A patent/EP2385882B1/fr active Active

Non-Patent Citations (1)

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