EP2340898B1 - Rolling machine - Google Patents

Description

The invention relates to a rolling machine for forming a workpiece.

For forming workpieces from a starting shape into a desired intermediate shape (semifinished product, preforming) or final shape (finished product, finished forms), there are, among many other processes, also rolling processes which are counted among the pressure forming processes. During rolling, the workpiece (rolling stock) is placed between two rotating rolls and changed in shape by exerting a forming pressure by the rotating rolls. When profile rolling process tool profiles are arranged on the circumference of the rollers, which allow the production of corresponding profiles in the workpiece. In flat rolling, the cylindrical or tapered outer surfaces of the rollers act directly on the workpiece.

With regard to the relative movement of the tools or rollers on the one hand and the workpiece on the other hand, one divides rolling processes in longitudinal rolls, transverse rolls and oblique rolls. During longitudinal rolling, the workpiece is moved perpendicular to the axes of rotation of the rollers in a translatory movement and usually without rotation through the gap between the rollers (nip). During transverse rolling, the workpiece does not translate with respect to the rollers or their axes of rotation, but rotates only about its own axis, which is usually a main axis of inertia, in particular the axis of symmetry in a rotationally symmetrical workpiece. When combining both types of movement during longitudinal rolling and cross rolling one speaks of skew rolls. The rollers are usually at an angle to each other and to the workpiece, which is translationally and rotationally moved.

Profile transverse rolling machines, in which two rollers with wedge-shaped profile tools arranged on the outer circumference rotate in the same direction about axes of rotation parallel to one another, are sometimes referred to as transverse wedge rolling. The tools have a wedge-shaped or triangular in cross-section geometry and can increase along the circumference in their radial dimension in one direction and / or extend obliquely to the axis of rotation of the rollers.

These cross wedge or cross-profile rollers allow a variety of forming workpieces in high precision or dimensional accuracy. As a result of the compressive force exerted by the wedge-shaped tools on the workpiece while the material distribution in the workpiece during the rotation of the rollers is changed by a flow in the workpiece. The wedge-shaped tools can create circumferential grooves and other tapers in the rotating workpiece. By the axial offset in the circumferential direction or the oblique arrangement of the tool wedges relative to the axis of rotation, for example, axially changing structures and tapers can be produced in the workpiece to the rotation axis. By the increase or decrease of the outer diameter of the tool wedges when passing around the axis of rotation can be generated in combination with the oblique arrangement axially extending slopes and continuous transitions between two tapers of different diameters in the workpiece. The wedge shape of the tools allows the production of fine structures through the wedge outer edges or outer surfaces. Particularly suitable are cross wedge rollers for producing elongate, rotationally symmetrical workpieces with constrictions or elevations such as cams or ribs.

The forming pressure and the forming temperature depend on the material of which the workpiece is made, as well as the dimensional accuracy and surface quality requirements after forming. Especially In iron or steel materials, the forming is usually carried out at elevated temperatures during rolling, in order to achieve the formability or flowability of the material required for forming. These temperatures, in particular occurring during forging, can be in the range of room temperature in the case of so-called cold forming, or between 550 ° C. and 750 ° C. in the case of warm forging, and above 900 ° C. in the case of so-called hot forming. The forming or forging temperature is usually also placed in a temperature range in which run recovery and recrystallization processes in the material and unwanted phase transformations are avoided.

Cross wedge rolling machines are known, in which the workpieces at the beginning of the rolling process by means of a positioning device comprising two positioning supports (so-called guide rulers), in an initial position between the two rollers, which usually corresponds to the geometric center or the center of the nip , positioned. Now, the positioning carriers of the positioning device are withdrawn, so that the workpiece rotates freely between the rollers and is kneaded between the tools in the desired shape. After this rolling or kneading and the corresponding completion of the workpiece, the workpiece is detected via a recess in the rotating rolling tool and usgeworfen a.

Out DE 1 477 088 C is a cross wedge rolling machine for the transverse rolling of bodies of revolution or flat workpieces with two rotating in the same direction of rotation work rolls on the roll surfaces wedge tools are arranged interchangeable. The wedge tools each have wedge-shaped or triangular extending from the roll shell to a height adjusted to the produced workpiece end, by knurling or otherwise roughened reduction strips and extending at the same distance from the roll shell, wedge-shaped smooth form surfaces with calibration effect. The wedge tools are formed as deformation segments and extend only over a partial circumference of the associated roll surface. On the workpiece The mutually facing surfaces and tools of the two work rolls move in opposite directions or in opposite directions to each other.

The EP 1 256 399 A1 discloses a cross rolling machine with two parallel operated modules of two rollers rotating in the same direction of rotation, the half-shell-shaped tools having radially projecting tool wedges on its peripheral surface, wherein the deformation of a workpiece requires only the rotation of half the circumference of a pair of rollers. All four rollers are driven by only one drive motor via an interposed gear unit and drive shaft. From the DE 195 26 071 A1 is a device for rolling profiles in a workpiece, in particular transverse rolls, longitudinal rolls and helical rolls of threads, knurls, Zahnwalzprofile or the like, known with two forming rollers which are rotated about mutually parallel axes of rotation in the same direction of rotation and each driven by an associated drive with drive motor be, with each drive is assigned a braking device.

The DE 21 31 300 B discloses a cross rolling machine with two axially parallel horizontal superimposed profiled rollers for forming and cutting rotationally symmetrical workpieces, in which the profile rollers touch the workpieces diametrically opposite circumferential points and the lower profile roller has a recess for discharging the rolled and cut workpieces from the nip.

The JP H10 235416 discloses a rolling machine with two rolls for forming workpieces, each roll being associated with at least one drive for independently driving the rolls, each drive comprising at least one permanent magnet motor.

The invention is based on the object of specifying a new rolling machine.

This object is achieved with the features of claim 1.

The rolling machine according to claim 1 comprises an associated drive for each of the rollers, wherein the drives are independent of one another and comprise at least one permanent magnet motor, in particular a torque motor, for driving the rollers. The rolling machine is a cross wedge rolling machine and due to the speed controllable and reversible drive can also be used as a stretching roll machine or short stretch roll.

Advantageous embodiment and development of the rolling machine resulting from the dependent of claim 1 claims.

The permanent magnet motor preferably accelerates to the rated speed for operation of the rollers within a rotation angle of a maximum of 3 °, 2.2 °, 1 ° or 0.5 °. Furthermore, the permanent magnet motor preferably has a nominal torque between about 5,000 Nm and about 80,000 Nm, in particular between about 35,000 Nm and about 60,000 Nm, and / or a rated speed between about 20 U / min and 800 U / min, in particular about 30 U / min or 500 rpm.

In the independent drives for the rollers, however, the rollers are electronically synchronized or controlled, in particular via inverters, which convert, for example, a mains voltage of 400 V and 50 Hz in an AC voltage or an AC of suitable amplitude and frequency. Here is particularly advantageous that in cross wedge rollers, the force load on both motors because of the symmetrical structure of the tools / rollers and / or the symmetrical forming process is relatively low and thus the synchronization of the drives is favored.

FIG 1

eine Walzmaschine mit zwei Walzen und einem gemeinsamen Antrieb in einer teilweise geschnittenen Längsansicht,

FIG 2

die Walzmaschine gemäß FIG 1 in einer teilweise geschnittenen Draufsicht von oben,

FIG 3

die Walzmaschine gemäß FIG 1 und FIG 2 in einer Seitenansicht,

FIG 4

die beiden Arbeitswalzen einer Walzmaschine im Querschnitt vor Einbringen des Werkstückes,

FIG 5

die beiden Arbeitswalzen der Walzmaschine beim Einbringen des Werkstückes,

FIG 6

die Arbeitswalzen mit dem bearbeiteten Werkstück im Querschnitt,

FIG 7

die beiden Arbeitswalzen beim Auswerfen des Werkstückes und

FIG 8

eine mögliche Abhängigkeit der Winkelgeschwindigkeit einer Arbeitswalze vom Drehwinkel in einem Diagramm

FIG 9

eine weitere mögliche Abhängigkeit der Winkelgeschwindigkeit einer Arbeitswalze vom Drehwinkel in einem Diagramm

FIG 10

eine Ausführungsform einer Walzmaschine mit zwei Walzen und unabhängigen Antrieben für die Walzen in einer teilweise geschnitten Längsansicht und

FIG 11

die Walzmaschine gemäß FIG 10 in einer Seitenansicht.

jeweils schematisch dargestellt sind. Einander entsprechende Teile und Größen sind in den FIG 1 bis 11 mit denselben Bezugszeichen versehen.The invention will be explained below with reference to exemplary embodiments. Reference is made to the drawings, in which

FIG. 1

a rolling machine with two rolls and a common drive in a partially sectioned longitudinal view,

FIG. 2

the rolling machine according to FIG. 1 in a partially sectioned top view from above,

FIG. 3

the rolling machine according to 1 and FIG. 2 in a side view,

FIG. 4

the two work rolls of a rolling machine in cross section before introduction of the workpiece,

FIG. 5

the two work rolls of the rolling machine when introducing the workpiece,

FIG. 6

the work rolls with the machined workpiece in cross section,

FIG. 7

the two work rolls when ejecting the workpiece and

FIG. 8

a possible dependence of the angular velocity of a work roll on the angle of rotation in a diagram

FIG. 9

Another possible dependence of the angular velocity of a work roll from the angle of rotation in a diagram

FIG. 10

an embodiment of a rolling machine with two rolls and independent drives for the rolls in a partially cut longitudinal view and

FIG. 11

the rolling machine according to FIG. 10 in a side view.

are each shown schematically. Corresponding parts and sizes are in the 1 to 11 provided with the same reference numerals.

The in the 1 to 3 illustrated embodiment of a designed as a cross wedge roller or cross wedge rolling machine 1 comprises a first work roll 2 which is rotatable about an axis of rotation A or rotating and a second work roll 3, which is rotatable about a rotational axis B or rotating. The sense of rotation of both work rolls 2 and 3 is illustrated and the same with the arrows shown. The axes of rotation A and B are arranged substantially parallel to each other, in the example of 1 to 3 seen in the direction of gravity on top of each other, so that the work rolls 2 and 3 are arranged one above the other. The work rolls have a substantially cylindrical outer surface. The distance between the cylindrical outer surfaces of the two work rolls 2 and 3 is designated by W.

On the outer surface or lateral surface of the work rolls 2 and 3, wedge-shaped tools 20 and 21 or 30 and 31 are respectively fastened in cross-section, especially tense. In the illustrated embodiment, the tools 20 and 21 of the first work roll 2 and the tools 30 and 31 of the second work roll 3 are each disposed obliquely and at an angle to the respective rotation axis A and B, the tools 20 and 21 of the work roll 2 with respect to between the two rollers parallel to the axes of rotation extending, the geometric center defining central axis M are arranged axially in the substantially same positions. The tools 20 and 21 and 30 and 31 take in the circumferential direction seen in its cross section, wherein the increase of the cross section in the tools 20 and 21 in the same direction of rotation or orientation and in the tools 30 and 31 of the second work roll 3 opposite or opposite directions to which the tools 20 and 21 of the first work roll 2 is.

Each work roll 2 and 3 is releasably held in a two-part holding device and can be removed from the holding device in its unlocked state to replace the tools 20 and 21 or 30 and 31 or the entire work rolls 2 and 3 with the tools 20 and 21 and 30 and 31. The holding device for the work roll 2 is denoted by 12 and the holding device for the work roll 3 with 13. A in 1 and 2 The left-hand arranged first part 12A of the holding device 12 comprises a conical receptacle 14 for receiving a axially to the rotation axis A outwardly from the work roll 2 extending frusto-conical extension 24 (stub shaft). The second part 12B accordingly comprises a receptacle 15 for receiving a corresponding conically tapered away from the work roll 2 and axially to the axis of rotation A extending extension 25 of the work roll 2. Under the resulting wedge and clamping action, the work roll 2 is fixed in the receptacles 14 and 15 of the holding device 12 clamped, wherein the axial force is generated on the receptacle 15 in the direction of the axis of rotation A to the work roll 2 towards the support of the work roll 2 by a spring 16 or other an axial force-exerting element. The receptacles 14 and 15 are rotationally symmetrical to the axis of rotation A and stored in unspecified pivot bearings.

The receptacle 14 continues as a hollow shaft axially to the axis of rotation A and has in its end remote from the work roll 2 end a gear 18 which, like a corresponding gear 19 which is associated with the second work roll 3, with a control gear (pinion, drive gear ) 5 is engaged. The gear 18, which serves to drive the first work roll 2 via the holding device 12, engages from above into the control gear 5 and the gear 19, which is coupled to the second work roll 3 via the holding device 13, engages from below into the control gear fifth ,

The control gear 5 is now coupled via an output shaft 45 with a drive motor 4. The control gear 5, the output shaft 45 and the - not shown - rotor of the drive motor 4 are rotatable about a common axis of rotation R or rotating. The built-up of the drive motor 4, the output shaft 45 and the control gear 5 drive for the gears (roller gears) 18 and 19 and thus the synchronously with the gears 18 and 19 rotating work rolls 2 and 3 is thus a direct drive.

The mechanical power supplied by the drive motor 4 corresponds to the product of torque and angular velocity or angular frequency ω, the angular frequency ω being equal to the product of 2π and the rotational speed n. The drive motor 4 is preferably a torque motor and has a high torque even at a comparatively low speed n of the drive motor 4 for generating the required drive power for the drive rollers 2 and 3.

The transmission ratio of the control gear 5 to the gears 18 and 19 can thus be selected in the range of 1, in particular between about 1: 1 and about 1: 2. At a transmission ratio of 2, the drive rollers 2 and 3 rotate twice as fast as that Control gear 5 and the drive motor 4, at a transmission ratio of 1: 1 just as fast. Typical speeds of work rolls 2 and 3 are between about 10 revolutions per minute (RPM) and about 40 RPM, typically at 15 RPM.

With such a low-speed or low-speed rotating drive motor 4, a very dynamic adaptation or control or regulation of the speed of the work rolls 2 and 3 can now be realized.

A preferred embodiment of the drive motor 4 is a permanent magnet motor, in which, usually on the rotor, permanent magnets (permanent magnets) are arranged, which generate a magnetic flux generated in the induction field generated by electromagnets or windings of the stator, wherein by interaction of the magnetic flux of the permanent magnets and the induction field, the rotation of the rotor on the basis of the induction principle or electromotive principle arises. In general, a torque motor is a synchronous motor, that is, the rotor rotates synchronously with the rotating magnetic flux. The induction windings of the stator are usually connected to the phases of a three-phase connection and arranged offset by 120 ° to each other. Preferably, permanent magnets are used with the highest possible energy product, such as rare earth cobalt magnets. The stator usually has an iron core with the three-phase winding package, while the rotor has a cylindrical iron core with the permanent magnets. Such a torque motor can have a torque of up to 80,000 Nm. The high torque also causes a very fast spin. In particular, the permanent magnet motor or torque motor can accelerate the rollers within a rotation angle of only 1 °, preferably even only 0.5 °, to the rated speed, for example 30 rpm. This high dynamics or rotational acceleration of the torque motor allows a very dynamic control of the speed.

The control or regulation of the speed n of each other and synchronously rotating work rolls 2 and 3 is adapted to the rolling process by a special control method or control method. For this purpose, the rotational speed n or angular velocity ω of the work rolls 2 and 3 to the respective rotational position or angular position φ of the work rolls. 2 and 3 are adjusted and controlled in response to this rotational position φ. Thus, depending on the respective process, the respective rolling machine and, above all, depending on the workpiece to be machined, the deformation by the work rolls 2 and 3 can be optimized by controlling the rotational speed n or the angular velocity ω = dφ / dt.

The 4 to 7 Now show a possible sequence of a rolling process with such a rotational position-dependent speed control or regulation in a workpiece 10. A positioning device for the workpiece 10 is designated 60 and comprises two relatively movable positioning parts (guide rulers) 61 and 62nd

FIG. 4 shows a position of the work rolls 2 and 3 before the introduction of the workpiece. The same direction of rotation of the two rollers 2 and 3 about the respective axes of rotation A and B are marked with corresponding arrows. In the tool 20, which extends in segments around the outer surface of the work roll 2 and about the axis of rotation A, a recess 23 is provided. In the second work roll 3, a further recess 33 is also provided in the segment-like tool 30.

The workpiece 10 is now taught by means of two guide ruler of a positioning device not shown in a position between the work rolls 2 and 3, in which it is detected by the recess 23 in the tool 20 of the first work roll 2. This process phase with incorporated tool 10 in the starting position shows FIG. 5 , On the workpiece 10, the mutually facing surfaces of the work rolls 2 and 3 move in opposite directions or opposite to each other.

Upon further rotation of the work rolls 2 and 3 to each other, the workpiece 10 is now placed between the tools 20 and 30 and under the pressure of the tools 20 and 30, which have a smaller distance w to each other than the original diameter of the workpiece 10 in a smaller diameter spent. The resulting after forming reduced Diameter (puncture) of the workpiece 10 at the point shown in cross section largely corresponds to the minimum distance w between the tools 20 and 30 of the work rolls 2 and 3. A position of the work rolls 2 and 3 with the intermediate kneaded workpiece 10 during the actual rolling process is in FIG. 6 shown.

In FIG. 7 Finally, the position of the work rolls 2 and 3 is illustrated, in which the workpiece 10 falls into the recess 33 of the tool 30 of the second work roll 3 and, upon further rotation of the work roll 3, is ejected from the gap between work rolls 2 and 3.

Thus, in the rolling process, it is fundamentally possible to distinguish three process phases, namely a first process phase for preparing the rolling process and positioning the workpiece in the starting position, that is to say a process phase which occurs in the process 4 and 5 is shown, further a second process phase, during which the actual rolling process takes place and the workpiece is formed between tools of the two work rolls, according to FIG. 6 , and finally a third process phase, during which the workpiece is removed again from the tools, accordingly FIG. 7 ,

FIG. 8 now shows a diagram in which the speed n of the work rolls 2 and 3 as a direct measure of the rotational speed in the unit Hertz (Hz) = 1 / s or in revolutions per second (or: revolutions per minute) on the rotational position or the angle of rotation φ of the work roll 2 is applied. There are nine consecutive angular positions φ1 to φ9 drawn on the φ-axis and between the angular positions φ1 and φ9 the rotational speed n as a function of n (φ) of the rotational angle φ plotted. The resulting curve is labeled K. This curve K is in turn subdivided into seven sub-curves K1 to K7, the first sub-curve K1 between the angular positions φ1 and φ2, the second sub-curve K2 between the angular positions φ2 and φ3, the third sub-curve K3 between the angular positions φ3 and φ4, the fourth sub-curve K4 between the angular positions φ4 and φ5, the fifth sub-curve K5 between the angular positions φ5 and φ6, the sixth sub-curve K6 between the angular positions φ6 and φ7 and the seventh sub-curve K7 between the angular positions φ7 and φ8. The first part curve K1 and the second part curve K2 show a possible time profile of the rotational speed n of the work rolls 2 and 3 in the first process phase between the angular positions φ1 and φ3 for the preparation and positioning of the workpiece 10. Between the angular positions φ1 and φ2 is in a quite steep rise according to the sub-curve K1 increases the speed from 0 to a first speed n1> 0 and then held substantially constant between the angular positions φ2 and φ3, corresponding to the part curve K2. In the period between φ2 and φ3, corresponding to the part curve K2, the workpiece 10 is positioned between the work rolls 2 and 3 and finally detected at approximately the angular position φ3 of the recess 23 of the tool 20 of the first work roll 2.

The angular position φ3 is now the angular position of the first rotary roller 2, in which the workpiece 10 is fixed in the recess 23 and the rolling process can begin. It should be noted that the angular position or rotational position of the second work roll 3 is directly correlated with the angular position of the work roll 2 and changes synchronously, but in opposite directions with the angular position of the first work roll, wherein the rotation of the work rolls 2 and 3 takes place in the same direction. Therefore, it is sufficient to consider the rotational position of the first work roll 2. Of course, it could just as the angular position of the second work roll 3 are taken as a variable or parameter, of which the speed n is made dependent. In any case, it is sufficient to provide on one of the two work rolls 2 or 3 a position detection device for determining the angle of rotation φ relative to a reference or zero position φ0, which in the 4 to 7 is selected down and drawn.

Upon reaching the angular position φ3 and the engagement of the workpiece 10 in the recess 23, the rotational speed n between the angular position φ3 and a subsequent angular position φ4 is now increased rapidly in the curve section K3 with a correspondingly high rotational acceleration or slope of the characteristic K. The angular position φ4 is then reaches a higher speed n2, on which the rotational speed n is kept during the sub-curve K4 up to a new angular position φ6. This partial curve K4 between the angular positions φ4 and φ6 marks the actual rolling process. The FIG. 6 shows a snapshot of this rolling cut to the angular position φ5 of the work roll second

Just before the recess 33 of the tool 30 of the second work roll 3 reaches the workpiece 10, the rotational speed n is reduced again during the part curve K5 to an angle φ6 of the first work roll 2 in front of the associated angular position φ7 of the first work roll 2, preferably again with one high braking acceleration and then with a lower braking acceleration, corresponding to a flatter slope in the sub-curve K6 between the angular positions φ7 and φ8 further lowered. It is therefore carried out the ejection of the workpiece at a lower speed n and a lower spin to gently eject the workpiece. The ejection of the workpiece is completed at the end of the part curve K6 at the angular position φ8 of the first work roll 2 and the rotational speed n is now at the termination of the machining process of this workpiece 10 between the rotation angles φ8 and φ9 corresponding to the part curve K7 back to speed n = 0 Hz scaled back. A work cycle or a forming process is thus completed.

Of course, other angular position-dependent profiles of the speed n can be driven. So it is also possible to rotate the two work rolls 2 and 3 during partial phases of the process with mutually different speeds or even different directions of rotation. Further, depending on the number and arrangement of the tools on the work rolls, the profile n (φ) can be controlled.

FIG. 9 shows a dependence n (φ), during which a more complicated profile is driven during the forming process. First, starting from the angular position φ0 and a rotational speed n = n2, decelerated to a rotational speed n1 at an angular position φ1. This speed n1 is up to an angular position φ2 maintained and then is again accelerated to the rotational speed n2 at the angular position φ3 and maintain this speed n2 to the angular position φ4. This reduction in the speed n is when threading or gripping the workpiece 10 is advantageous. For a first forming phase with a first tool is now accelerated between the angular positions φ4 and φ5 of a speed n2 to a higher speed n8 and maintain this speed n8 up to an angular position φ6. Then is braked again from the speed n8 to a speed n5 between the angular positions φ6 and φ7. The rotational speed n5 is maintained between the angular positions φ7 and φ8 and then accelerated again between φ8 and φ9 to a rotational speed n7, which is maintained again during a plateau phase between φ9 and φ10. This plateau phase between φ9 and φ10 with the speed n7 corresponds to another forming phase with another tool. Finally, braked again by the rotational speed n7 to a rotational speed n4 between the angular positions φ10 and φ11, the rotational speed n4 up to the angular position φ12 maintained and then accelerated again to a rotational speed n6 in the interval between φ12 and φ13. The speed n6 is kept constant up to the angular position φ14. Then it is again accelerated to a maximum speed n9 between the angular positions φ14 and φ16 and the speed n9 is maintained during a final forming phase between φ16 and φ17. Finally, at the end of the forming process, between φ17 and φ18 is decelerated to the original speed n2. We have 0 <n1 <n2 <n3 <n4 <n5 <n6 <n7 <n8 <n9.

Like the profiles according to FIG. 8 and 9 show, the angle-dependent speed control allows a variety of adapted rolling rotational movements for different processes, tools and workpieces.

FIG. 1 and 3 further show a worm wheel 9, which is coupled to the gear 18 for the work roll 2 and allows adjustment or adjustment of the relative angular position of the work roll 2 relative to the work roll 3. This allows customization to different tools or even for correction the angular positions of the work rolls 2 and 3 are adjusted relative to each other.

For adjusting or correcting the backlash or tooth engagement between the rolling gears 18 and 19 and the central control gear 5 may also be provided an adjusting drive, not shown, the rotational drive with the permanent magnet motor 4 and the transmission to the output shaft 45 and the control gear 5 relative to can move the two roller gears 18 and 19. As a result, an asymmetric engagement or backlash can be corrected. Furthermore, it is also possible to provide separate drives for adjusting the rollers 2 and 3 with their roller gears 18 and 19, so that the meshing of the roller gears 18 and 19 can be set to the central control gear 5 each independently.

The holding devices 12 and 13 of the two work rolls 2 and 3 are supported by a support means 6 and stored or anchored in this. The support means 6 comprises four columnar support members 6A to 6D arranged in a rectangular arrangement and mounted or fixed on a common floor panel 6E supported on the floor 50. In each of the support members 6A to 6D, an associated tie rod 7A to 7B is vertically arranged in the longitudinal direction of the respective support member which is fixed to the bottom of the support plate 6E and above by means of an associated lock nut, preferably a hydraulically operated lock nut (9B, 9C in FIG. 3 ) is biased. In this case, a slotted Unterlagringsegment is placed under the hydraulic nut when the hydraulic nut is in the released state and then pressed by applying the hydraulic pressure, the nut on the Unterlagsringsegment. Thereby, the support means forming the frame of the rolling machine can be set under a certain tension. This leads to a stiffening of the roll stand.

FIG. 10 and 11 show a further embodiment of a cross wedge rolling machine 1, in which unlike the embodiment according to FIG 1 to 3 one first drive 42 for the first work roll 2 and a second, independent of the first drive 42 drive 43 for the second work roll 3. Each drive 42 and 43 includes an associated permanent magnet motor 44 and 45 and a - not shown - gear, for example a , in particular three-stage, gear transmission, for transmitting the torque of the motor to the associated work roll 2 and 3. The reduction ratio of each transmission, for example, be 1:35. In the illustrated embodiment according to FIG. 10 and 11 are the rotation axis C of the output shaft of the permanent magnet motor 44 of the first drive 42 and the rotation axis D of the output shaft of the permanent magnet motor 45 of the second drive 43 orthogonal to the axes of rotation A and B of the respective work rolls 2 and 3 directed and the motors accordingly laterally Roll stand arranged.

Each of the permanent magnet motors 44 and 45 is controlled electronically, in particular via a converter. As a result, the work rolls 2 and 3 can be driven either electronically synchronously or asynchronously.

LIST OF REFERENCE NUMBERS

1

rolling machine

2.3

Stripper

4

drive motor

5

timing gear

6

support means

6A to 6D

support element

6E

baseplate

7A to 7D

tie rods

8A to 8D

guide

9

worm

9B, 9C

locknut

10

workpiece

12

holder

12A, 12B

part

13

holder

13A, 13B

part

14, 15

admission

16

feather

18, 19

gear

20, 21

Tool

23

recess

24, 25

extension

30, 31

Tool

33

recess

42, 43

rotary drive

45

output shaft

46, 47

Rotary drive gear

50

ground

60

positioning

61, 62

positioning parts

A, B

axis of rotation

C, D

drive axle

G

gravitational force

M

central axis

P

positioning

R

axis of rotation

w

tool clearance

W

Platen Gap

Claims (6)

1. Rolling machine

   a) comprising at least two rotatable or rotating rollers (2, 3), which can be fitted or are fitted with tools, for forming a workpiece (10) which can be arranged or is arranged between the rollers,

   b) wherein at least one drive is associated with each roller for independently driving the rollers,

   c) wherein the at least one drive comprises a permanent-magnet motor (4) and the rotation speed of the said drive can be controlled and the said drive is reversible,

   d) wherein the rolling machine is in the form of a cross-wedge rolling machine and can also be used as a stretch rolling machine on account of the reversible drive of which the rotation speed can be controlled.
2. Rolling machine according to Claim 1, in which each permanent-magnet motor is accelerated or decelerated to the nominal rotation speed for operation of the roller(s) within a maximum rotation angle interval of at most 3° or of at most 2.2° or at most 1° or even at most 0.5°.
3. Rolling machine according to Claim 1 or Claim 2, in which at least one or each permanent-magnet motor has a nominal torque of between approximately 5000 Nm and approximately 80,000 Nm or between approximately 35,000 Nm and approximately 60,000 Nm, and/or in which at least one or each permanent-magnet motor has a nominal rotation speed of between approximately 20 rev/min and 800 rev/min or between approximately 30 rev/min and 500 rev/min.
4. Rolling machine according to one or more of Claims 1 to 3, in which at least one drive has a converter for supplying electrical energy to the motor.
5. Rolling machine according to one or more of Claims 1 to 4, comprising at least one position detection device for detecting or determining the rotation position of at least one of the rollers.
6. Rolling machine according to one or more of Claims 1 to 5, in which the rollers have wedge-shaped or triangular profiled tools in cross section, the radial dimension of the said profiled tools increasing in one direction along the circumference and/or running obliquely to the rotation axis of the associated roller.

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