EP2942119A1 - Compression of a rolled product - Google Patents

Abstract

The invention relates to a compression device (10) and a method for compressing a rolling stock (1) moved along a rolling line. The compression device (10) comprises two upsetting tools (20) which can be moved along with the rolling stock (1) and can be pressed together with the rolling stock (1), and which can be pressed against the rolling stock (1), in each case transverse to the movement of the rolling stock (1) and depending on the upsetting tool (20) at least three independently controllable linear actuators (30), by means of which the respective upsetting tool (20) in a plane parallel to a surface of the rolling stock (1) working plane two-dimensionally in all directions and rotatable about an orthogonal to the working plane of rotation is.

Description

The invention relates to a compression device and a method for upsetting a moving along a rolling mill rolling stock.

Rolled products (slabs) rolled in hot rolling mills are widened during rolling. Frequently, the spreading of a rolling stock at least in sections exceeds a planned rolling stock width, so that in the rolling process, a reduction of the spreading is carried out by a so-called upsetting of the rolling stock. The upsetting of a rolling stock in hot rolling mills is often done in so-called compression mills whose width reduction is limited. For large compression decreases so-called compression presses are used, which make over a longer contact area, a reduction in width of a rolling stock and thereby allow better Durchstauchung of the rolling stock.

The invention has for its object to provide an improved compression device and an improved method for upsetting a moving along a rolling mill rolling stock.

The object is achieved with respect to the compression device by the features of claim 1 and with respect to the method by the features of claim 12.

Advantageous embodiments of the invention are the subject of the dependent claims.

An upsetting device according to the invention for compressing a rolling stock moved along a rolling line comprises two sides of the rolling stock which are arranged opposite each other transversely to the movement of the rolling stock and in each case with the rolling stock Mitbewegbare and pressed on the rolling stock upsetting tools and each upsetting tool at least three independently controllable or linear drives by means of which the respective upsetting tool in a parallel to a surface of the rolling work plane two-dimensionally in all directions and is rotatable about an orthogonal to the working plane of rotation axis.

An upsetting device according to the invention thus has upsetting tools which are displaceable and rotatable in all directions by linear drives in the working plane. As a result, almost any flat compression contours can be impressed on the rolling stock by means of the compression device. In particular, so occurring at the ends of rolling stock deformations, so-called crust contours (dog bones) can be avoided or reduced, which can lead to disruption of production in the further processing of the rolling stock and must therefore be removed.

An embodiment of the invention provides that the at least three linear drives of each compression tool form a parallel kinematic drive.

In this case, a parallel kinematic drive is understood to mean a drive which moves an object by means of a plurality of rod-like actuators which can be varied in their length and which can be controlled individually, and optionally by means of joints.

Such drives are advantageous because they allow high dynamics and a relatively uniform loading of the actuators because of the low mass of the actuators.

A further embodiment of the invention provides six independently controllable or controllable linear drives per upsetting tool, these six linear actuators are designed and arranged such that the respective compression tool by means of the six linear drives three-dimensionally displaceable in all directions and is freely rotatable.

The technical advantages of such drives are the complete programmability of the movements, the stiffnesses in all directions and the absence of any hinged guides. However, these drives require a relatively high control engineering effort and relatively complex (spherical) joints for connecting the linear drives with a compression tool.

An alternative to the aforementioned embodiment of the invention provides that each compression tool is held by a guide device in the working plane and each parallel kinematic drive has three linear drives for moving the respective upsetting tool in the working plane.

The guide device advantageously relieves the linear drives, so that the linear drives essentially only have to move the upsetting tool in the working plane, but do not have to hold it in the working plane. The technical background for this relief is on the one hand the weight of the compression tool and the linear drives themselves and on the other hand the fact that due to changing Walzgutdicken the resulting compression force can be slightly outside the working plane. This leads to transverse forces and bending moments acting on the drive system which, depending on the technical design, could stress components of the drive system too much or deform them out of the working plane.

Another advantage of the aforementioned embodiment is the simplification of the maintenance of the compression device. For example, a linear drive when using a guide device can be relatively easily replaced, since the upsetting tool by the guide device in the Working level is maintained and therefore does not need to be additionally supported when replacing a linear drive.

Preferably, each guide device is formed by a guide mechanism, which consists of at least two solid bodies and at least one rotary and / or at least one translational bearing. Preferably, the guide mechanism further comprises at least one planar branch joint.

In this case, a planar double joint is understood to mean a two-part guide element whose parts are pivotable relative to one another and together in a plane about axes orthogonal to the plane.

Such "arm-like" guide mechanisms are relatively easy and flexible together with linear actuators realized and are therefore particularly advantageous as guide devices for guiding the upsetting tools inventive compression devices.

Alternatively, the guide device may for example comprise at least one guide plate which holds a compression tool in the working plane. This realization of a guide device has the advantages of high rigidity and conceptual simplicity, but the disadvantages that the guide plate is close to the upsetting process and can be affected by the dirt of this harsh environment.

Furthermore, the guide device may alternatively comprise, for example, at least one cable or a deformable rod or chain or other "transversely flexible" mechanical element having high rigidity in its longitudinal direction but low rigidity in the transverse direction, this element being arranged substantially normal to the working plane and on the one hand with at least one compression tool and on the other hand with a fixed system (frame) is connected. The basic idea is, the To accommodate weights of the upsetting tools as well as parts of the linear drives by a substantially perpendicular, flexible element. It is therefore an elastic guide. Such elements may be thin rods, ropes, chains, bands of metals or high strength plastics. In this case, several such elements can be used.

Furthermore, at least one of the "transversely flexible" mechanical elements is preferably displaced in at least one of its end points with at least one component of a linear drive with respect to the fixed system or with respect to an upsetting tool. The technical background of this shift is that the upsetting movements typically have strokes of about 80 mm. These movements take place with relatively high operating frequencies of about 1 Hz. However, with changes in the rolling stock widths, further shifts in rolling stock width direction are added, typically a maximum of 800 mm per side. The latter, large displacements can be realistic from a "transversally flexible" element, i. H. with reasonable lengths of these elements, are difficult to absorb and only with no longer negligible height variations; on the other hand, periodic strokes of 80 mm can be picked up relatively easily and with small differences in height. Therefore, the articulation points of a transflexible member are preferably displaced either in the fixed system or in the tooling system with a drive (eg, a hydraulic cylinder) to substantially offset only the slow and large shifts to accommodate the width of the slab. The fast and short compression strokes, on the other hand, are absorbed by the "transversely flexible" element.

A further embodiment of the invention provides that at least one linear drive acts on the respective upsetting tool via at least one component of the guide device.

This embodiment allows on the one hand kinematic advantages, eg. B. that the force geometry varies less for the effect of a linear drive at different Walzgutbreiten, and can keep the linear drive on the other hand from the upsetting process with the high temperatures and pollution.

A particularly preferred embodiment of the invention provides that at least one linear drive is a hydraulic drive.

Hydraulic drives are particularly suitable as linear drives of the upsetting tools due to the high forces and powers required for upsetting a rolling stock.

A further embodiment of the invention provides that at least one linear drive is an open or closed hydrostatic drive with an adjustable hydraulic pump. Such drives are also referred to below as hydraulically primary-controlled drives.

By means of an adjustable hydraulic pump, a hydraulic linear drive can advantageously be set particularly precisely to the required compression force.

In the aforementioned embodiment, at least one adjustable hydraulic pump is preferably "pivotable through zero". A "pivotable by zero pump" advantageously allows direct and precise control of the drive in the dead centers. The alternative would be to switch at a dead center with valves, the conveying direction; However, this typically leads to rapid pressure equalization and jerky movements of the drives, which usually require complex circuitry and / or control engineering measures to avoid undesirable consequences.

A further embodiment of the invention provides that at least one of the hydraulic linear drives more than a hydraulic cylinder, wherein a plurality of displacement volumes of the hydraulic cylinders in the movement of the pistons in the hydraulic cylinders compensate each other by the effluent from at least one displacement volume hydraulic fluid flows compensate for the flows into at least one displacement volume hydraulic fluid flows.

This embodiment of the invention advantageously allows on the one hand to avoid or at least reduce tank volumes for supply and removal of hydraulic fluid from the hydraulic system, and on the other hand to realize closed, pressure-biased hydrostatic drives. The latter drives are advantageous for reasons of control technology to achieve high accuracies. High compressive stress ensures high rigidity of the hydraulic fluid columns everywhere. On the other hand, if low pressures occur, the outgassing of dissolved air can significantly reduce the effective hydraulic fluid rigidity, with negative effects on control quality and stability.

A further embodiment of the invention provides that at least one linear drive is a combination of an open or closed hydrostatic drive with an adjustable hydraulic pump and a switching drive, wherein in the switching drive in at least one displacement chamber at least one additional hydraulic cylinder by means of a switching valve, a pressure optionally is adjustable to one of at least two different discrete values.

Such a "switchable" pressure for an additional hydraulic cylinder can be advantageously provided by a remote system pressure source, so that suburb, ie in the region of the rolling stock, no corresponding pumps or motors and the space required for it are needed. By the at least one additional hydraulic cylinder Furthermore, the primary controlled hydraulic cylinder is relieved, so that only a fraction of the total hydraulic power has to be provided by it and has to be generated on site. As a result, only relatively small and simple hydraulic pumps and drive motors are needed on site.

Preferably, at least one of the hydraulic linear drives has at least one differential hydraulic cylinder whose piston-side cylinder chamber is connected to at least one first connection of at least one adjustable hydraulic pump, and at least one cylinder chamber of at least one further hydraulic cylinder is connected to a second connection of this at least one hydraulic pump.

The purpose and advantage of this embodiment of the invention is, in particular, to realize a hydrostatic linear drive which acts in both directions of movement, d. H. for upsetting and in Rückhubrichtung. The movement of the system can thus be controlled in first order by a flow adjustment of the hydraulic pumps. The control then only has to compensate for more errors as a consequence of the compressibility of the hydraulic fluid or other compliances in the system (eg the frame structure).

In the aforementioned embodiment of the invention, an even number of adjustable hydraulic pumps for the hydrostatic linear drive is preferably provided, wherein first connections of all these pumps hydraulically combined on the piston side of a first differential hydraulic cylinder and second ports of the pump are connected to a total of two hydraulically completely separate lines, said one half of the pumps are connected to a first of these lines and the second half of the pumps are connected to the second of these lines and each of these lines is connected to one side of a bar at least one another hydraulic cylinder is connected, the piston surface is operated switching (see. FIG. 6 ).

The purpose and advantage of this embodiment of the invention is to make a balance of moments on the linear drive with the adjustable pump. Such moments are caused by an upsetting force, which acts somewhat off-center on the drive, and / or by the weight of the tool.

A further embodiment of the invention provides at least one redundant linear drive in order to replace or support, if necessary, a linear drive for moving a compression tool.

This embodiment of the invention is particularly advantageous when several small linear drives are less expensive than a larger linear drive or other technical or economic advantages, such as redundancy, ease of installation and / or maintainability, standardization or use of drive technologies in the representable force or power are limited.

A further embodiment of the invention provides that to relieve linear drives, bearings or components of the guide device are impressed on at least one upsetting tool by means of a device forces that substantially compensate for the weight forces of the upsetting tools and / or components of the linear drives at least partially.

This embodiment of the invention advantageously enables a reduction of stresses and deformations in the linear drives as a result of weight forces of the upsetting tools and / or components of the linear drives.

In the method according to the invention for upsetting a rolling stock moved along a rolling line, the rolling stock is impressed by placing two upsetting tools of a compressing device at sides of the rolling stock which are transverse to the movement of the rolling stock and are respectively pressed or controlled by the linear drives against the rolling stock.

The method realizes the above-mentioned advantages of the compression device according to the invention when upsetting a rolling stock.

In this case, preferably at least one linear drive is designed as a hybrid hydraulic linear drive with a primary-controlled hydraulic cylinder and at least one adjustable hydraulic pump and / or at least one optionally switchable digitally controlled additional hydraulic cylinder.

Preferably, at least one linear drive is regulated, in particular by means of a position control and / or speed control and / or pressure control and / or force control.

A position control of linear drives advantageously allows in particular to make Triftkorrekturen for movements of the upsetting tools. A speed control advantageously makes it possible to control, in particular, rapid movement components of these movements. A pressure and / or force control in the direction of the compression movement allows both sides of the rolling undergo the same compression force and consequently no resultant force acts on the rolling stock, which could displace the rolling stock.

Furthermore, for example, at least two linear drives are controlled by means of an impedance control of a compression tool or both upsetting tools in combination with one another. This embodiment of the invention takes into account that the events relevant to the upsetting process are determined by the upsetting tools. When upsetting there is the upsetting direction in Walzgutbreitenrichtung and the feed motion in the longitudinal direction. When upsetting the tool longitudinal movement should be synchronous to the rolling stock movement; The easiest way is to let the upsetting tools by frictional forces this longitudinal movement easily and thus largely avoid constraining forces of the upsetting tools on the rolling stock in this direction. Mechanically or control technically this means to control the tool forces in this direction largely to zero. In compression direction, however, the required compression at each compression stroke is achieved before upsetting tools lift off again.

A further embodiment of the invention provides that at least one controller for at least one of the linear drives uses an observer for an unknown compression force.

This embodiment takes into account that an up-to-date compression force can be interpreted as a disturbance in terms of regulation, provided that it is not known about upsetting force models or a direct measurement. In particular, the compression force substantially determines the "deflection" of relatively soft hydraulic drives. In order to compensate this as well as possible in terms of control technology, an at least approximate knowledge of the current compression force is helpful. This can advantageously be done by an observer.

FIG 1

schematisch und ausschnittsweise eine Draufsicht auf ein Walzgut und eine Stauchvorrichtung zum Stauchen des Walzgutes,

FIG 2

eine perspektivische Darstellung eines Stauchwerkzeuges und einer Führungsvorrichtung mit einem einfachen Führungsmechanismus zur Führung des Stauchwerkzeuges in einer Arbeitsebene,

FIG 3

ein Stauchwerkzeug, jeweils drei Hydraulikzylinder und Kolben zum Bewegen des Stauchwerkzeuges und eine Führungsvorrichtung mit einem zweifachen Führungsmechanismus zur Führung des Stauchwerkzeuges in einer Arbeitsebene,

FIG 4

in einer perspektivischen Darstellung ein Stauchwerkzeug und fünf Hydraulikzylinder zum Bewegen des Stauchwerkzeuges,

FIG 5

einen hybriden hydraulischen Linearantrieb mit einem primärgesteuerten Hydraulikzylinder, einer verstellbaren Hydraulikpumpe und vier bedarfsweise durch eine digitale Steuerung zuschaltbaren Zusatz-Hydraulikzylindern, und

FIG 6

einen hybriden hydraulischen Linearantrieb mit einem primärgesteuerten Hydraulikzylinder, zwei verstellbaren Hydraulikpumpen und zwei bedarfsweise zuschaltbaren digital gesteuerten Zusatz-Hydraulikzylindern.

The above-described characteristics, features, and advantages of this invention, as well as the manner in which they will be achieved, will become clearer and more clearly understood in connection with the following description of exemplary embodiments which will be described in detail in conjunction with the drawings. Showing:

FIG. 1

schematically and partially a plan view of a rolling stock and a compression device for compressing the rolling stock,

FIG. 2

a perspective view of a compression tool and a guide device with a simple guide mechanism for guiding the upsetting tool in a working plane,

FIG. 3

a compression tool, three hydraulic cylinders and pistons for moving the compression tool and a guide device with a double guide mechanism for guiding the compression tool in a working plane,

FIG. 4

in a perspective view of an upsetting tool and five hydraulic cylinders for moving the upsetting tool,

FIG. 5

a hybrid hydraulic linear drive with a primary controlled hydraulic cylinder, an adjustable hydraulic pump and four as needed by a digital control switchable additional hydraulic cylinders, and

FIG. 6

a hybrid hydraulic linear drive with a primary-controlled hydraulic cylinder, two adjustable hydraulic pumps and two on-demand digitally controlled additional hydraulic cylinders.

Corresponding parts are provided in all figures with the same reference numerals.

FIG. 1 shows schematically and partially a plan view of a rolling stock 1, which is moved along a rolling line in a direction of movement 2, and a Stuffering device 10 for upsetting the rolling stock 1. It shows FIG. 1 only one half of the compressing device 10 arranged on a first side of the rolling stock 1, comprising an upsetting tool 20, three linear drives 30 and a hydraulic accumulator 40. The other half (not shown) of the stuffering device 10 is transverse to its movement at one of the first side of the rolling stock 1 lying (not shown) side of the rolling stock 1 and formed as the illustrated half of the compression device 10, that is, the non-illustrated half of the compression device 10 includes a compression tool 20, three linear actuators 30 and a hydraulic accumulator 40. The compression device 10 is connected to the rolling stock. 1 moved in the direction of movement 2.

Each compression tool 20 comprises a head part 21 for contacting the rolling stock 1 and a body part 21 carrying the body part 22nd

Each linear drive 30 comprises a hydraulic cylinder 31, a piston 32 guided in the hydraulic cylinder 31, a hydraulic pump 33 adjustable in volume flow for generating a pressure driving the piston 32, and an electric drive motor 34 for the hydraulic pump 33. The hydraulic pump 33 is on the one hand connected to the hydraulic cylinder 31 of the linear actuator 30 and on the other hand connected to the respective hydraulic accumulator 40.

In the hydraulic accumulator 40 there is a pressure substantially exceeding an ambient pressure, which is preferably about half the maximum working pressure of a hydraulic cylinder 31. As a result, the power of the electric drive motors 34 can be reduced, since in the largely powerless return stroke energy flows into the hydraulic accumulator 40, which provides a higher pressure during the exhaustive Stauchhub on the suction side, the required engine torque to produce a high pressure in the hydraulic cylinders 31 is reduced. Thus, the drive motors 34 can be dimensioned lower compared to a version without hydraulic accumulator 40 by about 50%.

Shown is also a supply unit 41 with a supply tank 42 for hydraulic fluid, which is supplied to the hydraulic system, if necessary.

The body part 22 of each compression tool 20 is coupled to the pistons 32 of three linear drives 30. The linear actuators 30 are individually and independently controllable or controllable and arranged such that each upsetting tool 20 via three linear actuators 30 in a working plane to a surface of the rolling stock 1 and the plane of the FIG. 1 is parallel, two-dimensionally displaceable in all directions and is rotatable about an axis of rotation orthogonal to the working plane. The three an upsetting tool 20 driving linear drives 30 thus form a parallel kinematic drive of the upsetting tool 20th

The head portion 21 of each upsetting tool 20 is in the form of a straight prism having a base plane parallel to the working plane, which has the shape of a convex pentagon with two sides facing the rolling stock 1, enclosing an obtuse interior angle. As a result, the surface of the head part 21 facing the rolling stock 1 can act like a ramp for swaging the rolling stock 1.

By means of the linear drives 30, the head parts 21 of the two upsetting tools 20 are pressed against the rolling stock 1 for upsetting the rolling stock 1 from its opposite sides simultaneously. Due to the fact that the upsetting tools 20 are displaceable and rotatable in all directions by the linear drives 30 in the working plane, any desired flat upsetting contours can be impressed on the rolling stock 1 by means of the upsetting device 10. FIG. 1 shows an example of a force 3 of a force, the rolling stock 1 on a Upset tool 20 exerts when the upsetting tool 20 is pressed against the rolling stock 1 to the upsetting.

FIG. 2 shows a perspective view of a compression tool 20 and a guide device 50 with a simple guide mechanism for guiding the compression tool 20 in a working plane. The simple guide mechanism consists of a pair of two sub-arms 51, 52 which are interconnected by a first hinge 53. Furthermore, a first partial arm 51 via a second guide joint 56 with the body part 22 of the upsetting tool 20 and the second

Part arm 52 via a third pivot joint 54 movably connected to a fixing member 55 for fixing the guide device 50. By means of the guide joints 53, 54, 56, the partial arms 51, 52 are pivotable relative to each other and to the fixing member 55 about pivot axes orthogonal to the working plane, so that the simple guide mechanism forms a flat Zweelenk that allows movements of the upsetting tool 20 in the working plane. The upsetting tool 20 is by means of in FIG. 2 not shown linear actuators 30 moves (see. FIG. 3 ). The guide device 50 serves to relieve the linear drives 30, so that the linear drives 30 essentially have to move the upsetting tool 20 only in the working plane, but do not have to hold it in the working plane.

FIG. 3 shows a compression tool 20, three hydraulic cylinders 31 and piston 32 for moving the upsetting tool 20 and one to the in FIG. 2 illustrated guide device 50 alternative guide device 50 with a dual guide mechanism for guiding the upsetting tool 20 in a working plane. This guide mechanism consists of two simple guide mechanisms, each one like the one in FIG. 2 illustrated simple guide mechanism are formed, wherein the first partial arms 51 of these two simple Guide mechanisms are connected to different ends of the body portion 22 of the upsetting tool 20 and allow both simple guide mechanisms movements of the upsetting tool 20 in a common working plane. The hydraulic cylinders 31 and pistons 32 are components of three linear drives 30 to move the upsetting tool 20 in the working plane. The pistons 32 of two linear drives 30 are as in FIG FIG. 1 connected to the body portion 22 of the upsetting tool 20, while the piston 32 of the third linear actuator 30 is connected to the first hinge 53 of one of the simple guide mechanisms and acts via this guide joint 53 via the first arm 51 on the upsetting tool 20.

FIG. 4 shows in a perspective view of an upsetting tool 20 and five of a total of six hydraulic cylinders 31 for moving the upsetting tool 20, wherein the sixth hydraulic cylinder 31 is not shown for clarity. Each of the six hydraulic cylinders 31 and a piston 32 guided therein are components of a linear drive 30 for moving the upsetting tool 20. The pistons 32 are each connected to the body part 22 of the upsetting tool 20. In this case, the six linear drives 30 are arranged on the body part 22 in such a way that the upsetting tool 20 can be displaced three-dimensionally in all directions by means of the six linear drives 31 and rotated as desired. The six linear drives 31 thus form a three-dimensional parallel kinematic Hexapodenantrieb the compression tool 20, which is an alternative to one of the basis of the FIGS. 1 to 3 described planar drives a compression tool 20 is.

FIG. 5 shows a "hybrid" hydraulic linear actuator 30, comprising a primary controlled hydraulic cylinder 31 with a piston 32, an adjustable hydraulic pump 33, four as needed by a digital control switchable additional hydraulic cylinder 35 with each a piston 32, a piston connecting element 36 connected to all the pistons 32 and two switching valves 37 in order to switch on additional hydraulic cylinders 35 as required.

By means of each switching valve 37 is in each case two of the auxiliary hydraulic cylinder 35, a pressure selectively adjustable to one of two different discrete values. Such a "switchable" pressure for the auxiliary hydraulic cylinder 35 can be advantageously provided by a remote system pressure source 44, so that suburb, d. H. in the area of the rolling stock 1, no corresponding pumps or motors and the space required for it are needed. Due to the additional hydraulic cylinder 35, the primary-controlled hydraulic cylinder 31 is further relieved, so that only a fraction of the total hydraulic power has to be provided by it and has to be generated on site. As a result, only relatively small and simple hydraulic pumps 33 and drive motors 34 are required in the region of the rolling stock 1. The use of several additional hydraulic cylinders 35 advantageously allows the use of auxiliary hydraulic cylinders 35 of relatively small cylinder sizes and avoids the use or development of large special cylinders.

In this case, the primary-controlled hydraulic cylinder 31 and the auxiliary hydraulic cylinder 35 are formed and hydraulically connected to each other that a primary hydraulic cylinder 31 on the underside, that is, from a piston connecting member 36 remote end, supplied hydraulic fluid quantity compensates that amount of hydraulic fluid from the primary controlled hydraulic cylinder 31 and the Additional hydraulic cylinders 35 on the upper side, that is discharged from the piston connecting element 36 ends, a total, and that correspondingly compensated from the primary controlled hydraulic cylinder 31 under discharged hydraulic fluid quantity that amount of hydraulic fluid that the primary controlled hydraulic cylinder 31 and the auxiliary hydraulic cylinders 35 top side is supplied in total. To this end, the underside cross-sectional area of the piston 32 of the primary-controlled hydraulic cylinder 31 corresponds to the sum of all upper-side annular surfaces of the primary-controlled hydraulic cylinder 31 and auxiliary hydraulic cylinders 35, the upper-side annular surface of a hydraulic cylinder 31, 35 being the difference in cross-sectional areas of the interior of the hydraulic cylinders 31, 35 and whose upper-side piston 32 is defined.

FIG. 5 also shows a recirculation tank 45 which receives hydraulic fluid returned from the auxiliary hydraulic cylinders 35 and is drawn from the hydraulic fluid upon extension of the pistons 32. Further shows FIG. 5 a hydraulic accumulator 40 and a minimum pressure source 46 for generating a minimum pressure for the primary-controlled hydraulic cylinder 31, wherein the hydraulic accumulator 40 and the minimum pressure source 46 are connected via check valves 47 to the primary-controlled hydraulic cylinder 31 and the hydraulic pump 33.

FIG. 6 shows a "hybrid" hydraulic linear actuator 30, which is an alternative to the in FIG. 5 shown linear actuator 30, and a primary-controlled hydraulic cylinder 31 with a piston 32, two adjustable hydraulic pumps 33, two, if necessary, switchable digitally controlled additional hydraulic cylinder 35, each with a piston 32 and a switching valve 37 to switch additional hydraulic cylinder 35, if necessary. Unlike the in FIG. 5 shown linear actuator 30 has the in FIG. 6 illustrated linear actuator 30 two independently adjustable hydraulic pumps 33, according to FIG. 6 are each connected to the primary controlled hydraulic cylinder 31 and one of the auxiliary hydraulic cylinder 35. As a result, off-center forces can advantageously be compensated for the piston connecting element 36.

Everyone in FIG. 5 and 6 illustrated "hybrid" hydraulic linear actuators 30 can one of the in the FIGS. 1 . 3 and 4 replace shown linear actuators 30. This results in various embodiments of compression devices 10 according to the invention. For example, an upsetting tool 20 as in FIG FIG. 3 be connected to a two simple guide mechanisms having guide device 50 and three linear drives 30, but with the two directly connected to the upsetting tool 20 linear actuators 30 each as a in FIG. 5 or FIG. 6 illustrated "hybrid" hydraulic linear actuator 30 are formed.

While the invention has been further illustrated and described in detail by way of preferred embodiments, the invention is not limited by the disclosed examples, and other variations can be derived therefrom by those skilled in the art without departing from the scope of the invention.

LIST OF REFERENCE NUMBERS

1

rolling

2

movement direction

3

direction of force

10

clincher

20

upsetting tool

21

headboard

22

body part

30

linear actuator

31

hydraulic cylinders

32

piston

33

hydraulic pump

34

drive motor

35

Auxiliary hydraulic cylinder

36

Piston connecting element

37

switching valve

40

hydraulic accumulator

41

supply unit

42

supply tank

44

System pressure source

45

Recycle tank

46

Minimum pressure source

47

check valve

50

guiding device

51, 52

partial arm

53, 54, 56

joint

55

fixing member

Claims (15)

Compressing device (10) for compressing a rolling stock (1) moved along a rolling line - two upright to the movement of the rolling stock (1) opposite sides of the rolling stock (1) arranged and each with the rolling stock (1) mitbewegbare and to the rolling stock (1) can be pressed up compression tools (20) - And each upsetting tool (20) at least three independently controllable or controllable linear actuators (30), by means of which the respective upsetting tool (20) in a plane parallel to a surface of the rolling stock (1) working plane two-dimensionally displaceable in all directions and one to the Working plane orthogonal axis of rotation is rotatable. A compression device (10) according to claim 1,
characterized in that the at least three linear drives (30) of each compression tool (20) form a parallel kinematic drive. A compression device (10) according to claim 1 or 2,
characterized by six independently controllable or controllable linear drives (30) per compression tool (20), these six linear drives (30) are designed and arranged such that the respective compression tool (20) by means of the six linear drives (30) three-dimensionally displaceable in all directions and is rotatable arbitrarily. Compressing device (10) according to claim 2,
characterized in that each compression tool (20) by means of a guide device (50) is held in the working plane and each parallel kinematic drive has three linear drives (30) for moving the respective compression tool (20) in the working plane. Compressing device (10) according to claim 4,
characterized in that each guide device (50) is formed by a guide mechanism consisting of at least two solid bodies and at least one rotatory and / or at least one translational bearing. A compression device (10) according to claim 5,
characterized in that the guide mechanism comprises at least one planar double joint. A compression device (10) according to any one of claims 4 to 6,
characterized in that at least one linear drive (30) acts on the respective upsetting tool (20) via at least one component of the guide device (50). Compression device (10) according to one of the preceding claims,
characterized in that at least one linear drive (30) is a hydraulic drive. A compression device (10) according to claim 8,
characterized in that at least one linear drive (30) is an open or closed hydrostatic drive with an adjustable hydraulic pump (33). Compressing device (10) according to claim 8 or 9,
characterized in that at least one linear drive (30) is a combination of an open or closed hydrostatic drive with an adjustable hydraulic pump (33) and a switching drive, wherein in the switching drive in at least one displacement space of at least one additional hydraulic cylinder (35) by means of a Switching valve (37), a pressure is selectively adjustable to one of at least two different discrete values. Compression device (10) according to one of the preceding claims,
characterized by at least one redundant linear drive (30) to replace or support, if necessary, a linear drive (30) for moving a compression tool (20). Method for compressing a rolling stock (1) moved along a rolling line by means of an upsetting device (10) with two upsetting tools (20), wherein - The rolling stock (1) Stauchkonturen be impressed by the upsetting tools (20) disposed transversely to the movement of the rolling stock (1) opposite sides of the rolling stock (1) and in each case by means of at least one linear drive (30) controlled or controlled to the rolling stock (1) are pressed. Method according to claim 12,
characterized in that at least one linear drive (30) is designed as a hybrid hydraulic linear drive with a primary controlled hydraulic cylinder (31) and at least one adjustable hydraulic pump (33) and / or at least one optionally switchable digitally controlled additional hydraulic cylinder (35). Method according to claim 12 or 13,
characterized in that at least one linear drive (30) is controlled by means of a position control and / or speed control and / or pressure control and / or force control. Method according to claim 12 or 13,
characterized in that at least two linear drives (30) are controlled by means of an impedance control of a compression tool (20) or both upsetting tools (20) in combination with each other.

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