DE3439269A1 - ROLLING MILL FOR AN UPstream, CONTINUOUSLY WORKING CASTING MACHINE FOR WIRE MANUFACTURING - Google Patents

Description

3439253

FRIED. KRUPP GESELLSCHAFT LIMITED LIABILITY

in food

Rolling mill for an upstream, continuously operating casting plant for wire production

The invention relates to a rolling train for an upstream, continuously operating casting plant for wire production with several horizontal and vertical roll stands, each having individually adjustable roll speeds as vario stands, and with horizontal and vertical roll stands, which have mutually rigid speed ratios in common are driven.

Casting and rolling plants in particular for the production of copper or steel wire - consisting essentially from a continuously operating casting machine along with a cooling equalizing section and driving unit as well from an adjoining rolling mill - are

usually to adapt to changing operating conditions and to avoid malfunctions with equipped with a number of independently variable-speed single stands, a multi-stand Rolling block with central drive are connected upstream or downstream.

The design of the last two roll stands as individual stands is therefore special desirable because even small, unavoidable temperature differences in the strand lead to differences lead in the wire diameter and therefore in EV 43/83 with regard to the required dimensional tolerances

must be caught. In addition, through appropriate speed setting, in particular care must be taken in the last roll stands that the strand has two adjacent ones Roll stands run through as far as possible without tensile and without compressive stress. The latter in particular leads to the fact that the strand backs up with the formation of a knot in front of the subsequent roll stand and eventually rips off.

So far, the strand in the area of the last roll stands was monitored by means of a loop control, that is, via the photoelectric scanning of a loop, its height by adjusting the speed of the roll stands is kept within a predetermined fluctuation range.

A group drive for several roll stands of a rolling train is already known from German patent specification 970 102. Starting from the basic speed of the group drive, the speed of each roll stand can be changed via an associated differential gear, which is equipped with a power take-off that can be regulated in terms of speed and acts on the summation gear.
The disadvantage of the prior art described is that the use of individual stands or group stands equipped with differential gears and auxiliary drives is associated with considerable effort.

The invention is based on the object of developing a rolling train as part of a casting and rolling plant, which can also be used for casting and rolling plants with a lower output at a reasonable cost, a Adaptation to changing operating conditions is permitted and based on the statement as to whether the strand is subjected to tension or compression, the risk of

Reduces operational disruptions and facilitates the production of a perfect product.

The problem posed is achieved by a rolling mill which essentially has the features of Claim 1 has.

The basic idea of the invention is to connect all of the rolling stands of the rolling train to a central drive to be connected, but at the same time the first two and the last two roll stands

TO be designed as variable scaffolding with individually variable speed; the entire rolling train thus forms a rolling block with four vario stands. To capture The second and third Vario stand (i.e. the one in Rolling direction second and penultimate roll stand) as well as the roll stand adjacent to it pivotably arranged chocks, which the associated pair of rollers together with drive elements adjustable and which are each supported on two pressure cells, which are in the rolling direction or are effectively held in the roll stand in the counter-rolling direction. In the case of tensile stress move the two adjacent chocks towards each other and claim the with respect to the Strand section internal pressure cells. The display of the applied pressure cells can therefore be used as an output signal for a change in the roller speed of the relevant Vario scaffolding can be used to set a draft-free state in the strand.

The speed-changing adjustment unit belonging to each Vario stand can be mechanical, hydraulic or

be electrically effective. It is preferably (regardless of its other configuration) designed in such a way that they allow a stepless speed change of the Vario stand rolls Fast or slow allows.

A PIV transmission is particularly suitable as the speed-changing adjustment unit (claim 2). It is a form-fitting gear, which essentially consists of two Conical pulley pairs with conical pulleys that can be displaced against each other and a chain as power transmission consists. Such transmissions are particularly suitable for small torques and high speeds and can therefore, without additional gear, especially on the last two in the rolling direction Vario stands of the rolling train are used.

In another embodiment of the subject matter of the invention, the Vario stands are via hydraulic adjustment gears, each consisting of a hydraulic pump with a downstream hydraulic motor to which Central drive connected. The hydraulic pump runs at the primary speed of the central drive driven; the output speed of the adjustment gear can be steplessly adjusted in a known manner change.

The invention can be implemented particularly well, provided that the rolling stands - the pivotally arranged Have chocks - equipped with overhung rollers, their employment over eccentric bushes held in the chocks can be changed (claim 4). A roll stand this one The type of construction is known from European patent specification 0 042 879, for example.

In a rolling mill with several main drive shafts, the speed-changing adjustment units are preferably driven via the free ends of the main drive shafts and the rollers of the Vario stands via hollow shafts which surround the main drive shaft in question and are coaxial with it. The adjustment unit is therefore connected on the drive side to the main drive shaft in question and on the output side via the hollow shaft ^to the associated vario frame.

For monitoring the line stress with a suitable Speed adjustment, the Vario stands are equipped with speed sensors (claim 6).

The invention is explained in detail below with reference to the drawing.
Show it:

1 shows the structure as a schematic diagram

a casting and rolling plant for the production of copper wire, which with the invention

Rolling mill is equipped,

Fig. 2 in a schematic representation

the mutual assignment of the successive ones in the rolling direction Horizontal and vertical

Roll stands with centrally arranged central drive,

3 schematically shows a section through

the first horizontal roll stand in the rolling direction, which over

a speed increase gear and

a PIV gearbox connected to the central drive of the rolling mill as a vario stand is,

4 apparently a section through the last horizontal roller in the rolling direction

rüst, which is connected to the central drive of the The rolling mill is connected,

Fig. 5 schematically shows a section through the last horizontal roll stand, which has a

Hydraulic adjustment gear with hydraulic pump and hydraulic motor as vario frame is connected to the central drive of the rolling mill,

Fig. 6 schematically shows a section through the last horizontal roll stand, which for Monitoring of the line stress a swiveling chock and two pressure cells having,

7 shows the interaction of the

last three roll stands for the purpose of strand monitoring and speed adjustment, and

Fig. 8 is a highly schematic drawing of a rolling train with six horizontal and vertical rolling stands, some of which are designed as Vario scaffolding, and with a central drive, which has an upstream Gearbox drives all rolling stands on the rolling train.

The casting and rolling plant shown as an example in Fig. 1 for the production of copper wire has the following

the main components: An intermediate container 1 for receiving liquid copper, which is supplied via a feed channel 2 is in connection with a casting machine 3, a cooling section 4 with a drive unit 5 for further conveyance of the strand 6 leaving the casting machine and an adjoining rolling train 7.

This consists - seen in the casting and rolling direction (arrow 8) - of twelve roll stands, namely the horizontal roll stands Hl, H3, H5, H7, H9 and H11 as well as the vertical roll stands V2, V4, V6, V8, V10 and V12; a horizontal roll stand a vertical roll stand is connected downstream in each case.

The rolling train 7 is formed into one via a centrally arranged central drive 9 common to all rolling stands Rolling block summarized. The central drive is located between the vertical roll stand V6 and the following one Horizontal mill stand H7.

The central drive 9, designed as a direct current motor, drives a downstream split gear via its shaft 9a 10 four main drive shafts 11 to 14 rotating at different speeds (Fig. 2). the Main drive shafts 11 and 12 to which the horizontal roll stands H1, H3 and H5 and the vertical roll stands, respectively V2, V4 and V6 are assigned, have a higher speed than the main drive shafts 13 and 14 the horizontal roll stands H7, H9 and H11 or V8, V10 and V12.

Apart from the first and last horizontal and vertical roll stands H1 in the rolling direction (arrow 8), V2 and H11, V12 are all known roll stands Way via bevel gear 15 rigidly to drive with the associated main drive shaft 11, 12, 13 or 14 connected: Your speed is therefore unchangeable on the speed of the shaft 9a.

5 In contrast, the first and second are as well

the penultimate and last roll stand with the interposition of a speed-changing adjustment unit 16, 17, 18 and 19 are driven by the respective associated main drive shaft 11 to 14. The adjustment unit is designed in such a way that the speed of the roll stands in question - the accordingly are referred to as Vario stands - can be steplessly changed regardless of the speed of the main drive shaft leaves.

All Vario stands H1, V2, H11, V12 have speed sensors 20 on. The second and penultimate Vario stand V2 and H11 as well as the roll stand adjacent to it H3 and V10 are each equipped with pressure cells 21L, 21R arranged in pairs, their task and operation will be described later.

In the case of the vario stand H1 shown in FIG. 3, there is an independent change in the rotational speed of the rolls 22 by interposing a PIV gear 23 made possible, which in a known manner consists of two pairs of conical pulleys 24, 25 with a chain 26 as a transmission element. The translation between the input shaft 27 and the output shaft 28 can be changed steplessly and without slippage by virtue of the fact that the conical disks each pair of cones are moved relative to each other.

The main shaft 11 assigned to the Vario stand H1 is at a standstill Via a clutch 2 9 with the sun gear 30a of a planetary gear 30 in connection, which via a ring gear 30b, the sun gear 30a and a web 30c drives the input shaft 27 at increased speed. The output shaft 28 moved via a coupling 31, a spur gear 3 2a, b and a hollow shaft 32c; a cone

wheel gear 33a, b, another spur gear 34a, b two in engagement with one another via their external teeth standing ring gears 35a, b; The spur gears 3 6 of the drive shafts are connected in a known manner via their internal teeth 37 driven for the two co-operating rollers 22.

The mutual distance between the cantilevered rollers 22 can be steplessly adjusted by rotating two eccentric bushings 38 change in which the drive shafts 37 are mounted and which in turn are in a chock prop up. This is movable with the stationary stand via a pivot axis 40 and a guide pin 41 42 of the Vario scaffold H1 in connection. Because PIV gearboxes only work at relatively high speeds The Vario stands H1 and V2 - which are the slow-running main drive shafts - have to transmit high power 11 and 12 are assigned - in the manner mentioned with an additional gear to increase the input speed be fitted into the PIV gearbox.

The main drive shaft 11 is coaxial through the hollow shaft 32c passed through, which carries the spur gear 32b and the bevel gear 33a.

Due to the higher speed of the main drive shafts 13 and 14 for the rear roll stands in the rolling direction (cf. FIG. 2), the associated drive arrangement can be designed more simply than the one just described.
For example, the main drive shaft 13 - which

a hollow shaft 43c penetrates coaxially - via the coupling 29 directly to an input shaft 27 of the PIV gearbox 23 for the Vario stand H11 (last horizontal stand of the rolling mill) in Connection (see. Fig. 4). The output shaft 28 drives via the clutch 31, a neutral spur gear 43a, b, another clutch 44 and a bevel gear 45a, b in the already described Way (see. Fig. 3) the rollers 22; the design of the drive elements between the bevel gear 45b and the rollers 22 are therefore not shown.

The speed-changing adjustment unit 16 to 19 (see FIG. 2) can also consist of a hydraulic adjustment gear, which is connected to the main drive shaft in question, for example the main drive shaft 13 shown in FIG. 5.
This drives a variable-speed hydraulic motor 48 via a variable-volume hydraulic pump 46 with pressure line 47, the drive shaft 49 of which is drivingly connected to the spur gear 34a, b already described. The parts 46 and 48 are additionally connected to one another via a pressureless return line 50.

The hydraulic adjustment gear can, depending on the requirements, also be designed in this way be that only the hydraulic pump 46 or the hydraulic motor 48 for the purpose of changing the speed is adjustable.

The speed adjustment of the rolls 22 of the Vario stands H1, V2, H11 and V12 can also be done with others

speed-changing adjustment units are brought about. In particular, it is possible the Vario stands via a slip-controlled magnetic particle coupling to the associated main drive shaft 11 to 14 to be connected.

For the purpose of determining whether the strand 6 (see. Fig. 1) is subject to tension or compression is, with the possibility of a suitable speed adjustment are the horizontal roll stand H3 and the last Vario stand (or last horizontal roll stand) shown as an example in FIG. H11 - just like the vertical roll stands V2 and V10 - each with two pressure cells 21L and 21R equipped, on whose sensors 21a the chock 39 (which the eccentric bushes 38 and roller drive shafts 37 receives) is supported in the counter-rolling direction or in the rolling direction. Each pressure cell is in a mounting plate 51 and a base 52 in one Recess 4 2a is fastened in the roll stand 42.

The vertical roll stands V2 and V10 only differ from the illustrated embodiment in that the pivot axis 40, the chock 39 and the guide pin 41 not horizontal, but lie vertically.

The suspension of the chocks 39 should in any case - for example by using if possible Low-friction bearings - be designed in such a way that the pivoting movement is in the counter-rolling direction or in the rolling direction as little resistance as possible is opposed.

If, for example, the strand coming from the left (arrow 8 in FIG. 1) pushes the chock 39 to the right,

the load cell 21R becomes a related one Generate output signal. The same applies with regard to the load cell 21L, provided the chock to the left with respect to the roll stand 42 under the tensile action emanating from the strand is pivoted.

The method that can be carried out with the invention, with which the strand stress in the last three or monitor the first three roll stands and adjust the speed of the associated Vario stands H11, V12 or H1, V2 can be influenced in the following with reference to FIG. 7 in detail explained:

If the roll speed of the last roll stand V12 with respect to the penultimate roll stand H11 to is high, the strand section located in between experiences a tensile stress with the Risk of tearing off. The chock 39 of the roll stand H11 is supported on the pressure cell 21R, which shows the tensile stress on the strand section. By lowering the The roll speed of the Vario stand V12 can be used to reduce the tensile stress: the pressure load cell 21R of the roll stand H11 then shows lower values Stress values.

If the roll stand V12 with respect to the previous one Roll stand has too low a roll speed, the associated strand section is subject to a pressure load with the risk of congestion and knot formation. The pressure cell 21L of the roll stand H11 shows increased values. These

can be influenced by the fact that the roll speed of the last roll stand V1 2 is increased by intervening in the associated adjustment unit (cf. FIGS. 3 to 5).

By suitably setting the roll speed of the Vario stand V12 in relation to the previous one Roll stand H11 can therefore take care of this be that the associated strand section passes through without stress; this state is about it It can be seen that both pressure cells 21L and 21R of the penultimate rolling stand H11 have normal values Show.

The setting of a state in which the strand section between the roll stands V10 and H11 passes through without stress, could in principle be brought about in a corresponding manner as has just been described for the last two roll stands. The Vario stand H11 (like the last Vario stand V12 before) is the last roll stand view on which the required speed adjustment is made; the display of the status that of the continuous strand section takes place via the pressure cells 21L and 21R of the roll stand V10.

When monitoring the strand section between the roll stands V10 and H11, however, it is closed take into account that each speed adjustment on the roll stand H11 corresponds to the previously set, stress-free State of the strand section between the roll stands H11 and V12 again changes. So that the working conditions between the last two roll stands - regardless of a speed adjustment of the penultimate Vario stand H11

with regard to the third from last roll stand V10 - remain unchanged, every change in the roll speed of the roll stand H11 can be carried out simultaneously and in the same ratio on the last Vario stand Vl2.

Since the last-mentioned speed adjustment on the last roll stand V12 cannot be carried out by hand is, one measure of the procedure consists in the two in question to equip last (or first two) roll stands with speed sensors 20 and the means to process this acquired measurement signals with an electronic control unit, which comprises a computer and a comparison unit.

The computer calculates the change in speed of the Vario stand H11

Δη (11) = n (11) before - η (11) after into the following ratio E:

E = Δη (11) / η (11) before.

The output signal of the speed sensor 20 on the roll stand V12 corresponding to η (12) is previously also entered into the calculator, which has the value

η (12) after = E χ η (12) before

determined. To adjust the speed, control signals corresponding to this value are sent to the switching unit of the Vario stand V12 transmitted.

The already mentioned comparison unit, which during the adjustment of the roller speed of the Vario stand V12 continuously the difference value

Δη (12) = η (12) is - η (12) should

determined, indicates when the difference value ^{reaches zero J} and the speed adjustment on the Vario stand V12 is complete.

The process basically consists of first adjusting the speed of the last Vario stand V12 the operating status between the roll stands H11 and V12, then by adjusting the speed of the Vario stand H11 the operating status between this and the third from last roll stand V10 and with consideration of the speed change on the Vario stand H11 to maintain the operating state that has already been set between the last two roll stands a speed adjustment on the last roll stand in the same ratio Carry out V12.

The procedure described can be carried out accordingly on the first three roll stands H1, V2 and H3, where the speed adjustment between H1 and V2 is effected via the Vario stand H1 or the speed adjustment between V2 and H3 via the Vario stand V2.

The front roll stands H1 and V2 in question are also equipped with speed sensors 20, whose Measurement signals in the manner already described in an electronic control unit with a computer and a comparison unit are processed.

The operating state initially set between the two Vario stands H1 and V2 becomes even after a speed adjustment between the

Vario stand V2 and the subsequent roll stand H3 maintained by the fact that the roll speed of the first Vario stand Hl with the speed change on the second Vario stand V2 simultaneously and in the same Ratio is affected.

The invention is not limited to rolling mills with main drive shafts; rather, it can also be Use when all roll stands are driven by a central drive via a gear box are.

In the embodiment according to FIG. 8, the central drive 9 with the shaft 9a upstream of a gear box 53, from which the rolling direction (arrow 8) successive horizontal and vertical rolling stands h1, v2, h3, v4, h5 and v6 their drive energy obtain. The first two and last two roll stands h1, v2 and h5, v6 are vario stands designed with individually variable speed; the roll speed of the middle roll stands h3 and v4 invariably depends on the speed of the shaft 9a of the central drive 9.

With regard to their basic function and equipment, the roll stands correspond to h1, v2, h5 and v6 the previously described Vario stands H1, V2, H11 and V12, the middle roll stands h3, v4 the roll stands H3 and V10 (see Fig. 2).

The shaft 9a stands on spur gears 54a, b or 55a, b, c drivingly connected to a roll drive shaft 56 or 57 of the roll stands h3 and v4. The roller drive shafts 56 and 57 in turn drive a hollow shaft 60 or 61 and from there, via spur gears 6 2a, b and 63a, b, a further hollow shaft 64 and 65, respectively.

Each hollow shaft is via an additional gear (which, for the sake of simplicity, corresponds to 66 is) connected to the input shaft 27 of a speed-changing adjustment unit 16, 17, 18 or 19, whose output shaft 28 with continuously variable speed, the rollers 22 of the Vario stand in question h1, v2, h5 or v6 set in rotation. The roller drive shaft coupled to the output shaft 28 67, 68, 69 or 70 is passed through the hollow shaft 64, 60, 61 or 65 in question.

The previously mentioned PIV gear units are used as the speed-changing adjustment units (cf. FIGS. 3 and 4) in question.

The advantage achieved with the invention is that in the area of the first roll stands (H1, V2 and H3 or h1, v2 and h3) in spite of the large strand cross-sections available there (which require the use of a Exclude loop control with optical observation) can set an operating state in which the The strand sections between the roll stands concerned are not subject to any stress.

Since the rolling train has only one common central drive, the one required for casting rolling can Adjustment between casting machine and rolling train made by engaging in a single drive although some roll stands (H1, V2, H11, V12 or h1, v2, h5, v6) are included as Vario stands individually variable roll speeds are formed · the roll speeds of all roll stands of the rolling mill be changed together.

During cast rolling, the deformation conditions cannot therefore be kept constant to the desired extent because the strand temperature fluctuates to an unavoidable extent. The rolling mill can therefore

can be adapted to the fluctuations in question via the vario stands in the front in the rolling direction.
By suitably setting the operating conditions in the last roll stands, tight tolerances can be maintained in the manufacture of the wire rod, for any finished wire diameter.

The proposed solution is also interesting from an economic point of view because instead of several individual drives and additional equipment, only one central drive is used.

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Claims (6)

3 1 O O ι Γ Π 4 j J .L O J Claims 1. Rolling mill for an upstream, continuous. ^: -.-: for wire production, Lending casting plant / with several horizontal and Vertxkal roll stands, which as vario stands each have individually adjustable roll speeds have, and with horizontal and vertical "rolling stands, which with each other rigid speed ratios are driven jointly, characterized in that that the first, second, penultimate and last roll stand (Hl, V2, H11 or V12) as Vario scaffold each with its own speed-changing adjustment units (16, 17, 18 or 19) to a centrally arranged central drive (9) for all roll stands (H1, V2, H3, V4, H5, V6, H7, V8, H9, V10, H11 and V12) are connected and that for recording the tensile stress in the rolling stock the second and third Vario stand (V2 or = HVlJ as well as the one adjacent to it Roll stand (HJ or, VlO) have pivotably arranged chocks (39, i, which the Associated pair of rollers (22) together with drive elements employable record and which each support on two pressure cans (2 IL, 21R), in the rolling direction (arrow 8) or in counter-rolling 2S direction effective in: Roll stand (42) held sj nd. 2. Wa'zstraße after. Addressed 1, characterized in that the Vdiκ frames (H1, V2, H11 and V12) are each connected to the central drive (9j) via a PIV gear (23). ^ /, Q α 9 ρ α · Λ 3. Rolling train according to one of claims 1 to 2, characterized in that the Vario stands (H1, V2, H11 or V12) via hydraulic adjustment gear, each consisting of a hydraulic pump (46) with a downstream hydraulic motor (48) connected to the central drive (9) are. 4. Rolling train according to one of claims 1 to 3, characterized in that the roll stands (V2, H3, V10, H11) with pivotable Chocks (39) have cantilevered rollers (22), the employment of which over into the Chocks held eccentric bushes (38) can be changed. 5. rolling train with several main drive shafts according to one of claims 1 to 4, characterized characterized in that the adjustment units (16, 17, 18 or 19) via the free Shaft ends of the main drive shafts (12, 13, 14 or 15) and the rollers (22) of the Vario stands (H1, V2, H11 or V12) are driven via hollow shafts (32c or 43c), which the relevant Hauptantrxebswelle (11 or 13) encompassing this lie coaxially. 6. Rolling train according to one of claims 1 to 5, characterized in that the Vario stands (H1, V2, H11 or V12) equipped with speed sensors (20) are.