EP0455082B1 - Combined line for small sections and wire - Google Patents

Abstract

The invention proposes a combined line for small sections and wire, which consists essentially of so-called cantilever (CL stands) with floating roll rings and the special feature of which consists in the fact that a number of roll stands (7) with a modular unit (8, 8', 8") comprising roll rings (10) supported on both sides (double bearing) are arranged in the roughing line (1) and in the intermediate line (2) and/or the finishing line (3). The CL modular unit of the CL stands comprising floating roll rings can, if required, be replaceable by a modular unit comprising roll rings with double bearings. For this purpose, the second bearing (18) of the modular unit is arranged in a casing frame (19) which can be coupled to the gear casing (12) of the CL stand, and the roll ring can be mounted and demounted by means of an automatically actuated, preferably hydraulically acting, rapid clamping device (11), which has piston-cylinder units (25, 26) for clamping and releasing the roll ring on the shaft (14) in the axial and radial direction. The modular unit furthermore is a roll casing (40) of sandwich-type construction with casing plates (44) which can be separated from one another. <IMAGE>

Description

The invention relates to a combined, continuously working high-performance fine steel and wire mill, in the roughing mill and in the intermediate mill and / or in the finishing mill both CL stands with rolling rings supported on one side (overhung) and rolling stands with a module unit with double-sided (double) stored rolling rings are arranged.

In a rolling mill known per se from CL stands, the rolling pressure exerted by the rolling stock basically goes into the first bearings of the overhung rollers. This means that the rolling rings, the bearings and the housing have to be dimensioned appropriately large when rolling with high tapping cross sections and high forming resistances. With such large dimensions of the scaffolding components, there is a risk that the compact design of the CL scaffolding can be largely lost.

Large piercing cross sections and high rolling forces therefore lead to technological and constructive limits with the typical CL stands. A technical way out would be to use conventional stand-less scaffolding with rollers mounted on both sides in chocks, e.g. scaffolding with scaffolding stands and rollers with one or more calibres mounted on both sides in mounting pieces in chocks. These stands are expensive, take up a lot of space and are maintenance-intensive when converting the rolls to other calibers.

As a rule, the intermediate line or the finishing train of a wire and fine steel mill consisting of CL stands is not suitable for also rolling profiles, since this can generally lead to dimensional inaccuracies due to the flying bearing of the rollers. If you wanted to do this according to the current state of knowledge, separate conventional roll stands with double-sided roller bearings would have to be introduced into the rolling line. This is an expensive and complex solution since the rolling mill is primarily used for wire and round steel dimensions.

DE-B 2 025 640 shows a rolling mill with a plurality of roll stands, the individual roll stand being equipped with vertical and horizontal rolls which have roll rings mounted on one and two sides. The rolling mill consists of six stands. The first three roll stands are each equipped with a vertical and a horizontal pair of rolls, the vertical rolls of the first two roll stands being designed as guide rolls and the rolling stock resting against these rolls at least on sections of its outline, and the horizontal rolls of the first two roll stands being curved - Or V-shaped profiles are formed and are provided for the actual rolling of the rolling stock. The vertical rolls of the third roll stand are for rounding off the corners of the rolling stock and the horizontal rolls of the third roll stand are for the final profiling of the rolling stock to the final dimension or the final cross section provided. The arrangement of horizontal, overhung roller rings and of vertical, double-sided roller rings is used to produce electrical sector cables, the rollers of a pair of rollers having differently shaped profiles that are wider than the greatest width of the rolling stock in the direction of the roller axis. With such a rolling mill, it is not intended to roll profiles with high tapping cross sections and high forming resistances.

AT-B 256 006 describes a rolling mill for wire or for profiled rolling stock. The core of the rolling mill is a roll stand with horizontal rolls mounted on both sides in stands, which are preceded by two stands that hold contact rolls and which is followed by an auxiliary stand. The auxiliary stand has vertical rollers. The auxiliary stand can serve a wide variety of purposes, for example as a pull-out driver, in order to pull the rolling stock that is running out of the rollers under tension. Furthermore, the auxiliary stand can be used for leveling the rolled profile, for which purpose it is then arranged with rolls offset by 90 ° to the rolls of the roll stand. The auxiliary scaffold should also make it possible to produce undercut profiles, for example profiles with a dovetail-shaped longitudinal groove. In this rolling mill, the rolling stock is regulated electrically brought to the desired rolling temperature before it enters the roll gap. In this way, the correct filling of the caliber of the rollers is to be ensured, so that the profile is fully developed and is true to size within narrow limits without burrs. At most, the auxiliary stand in this rolling mill is equipped with overhung roller rings. As the name of the auxiliary scaffold means, this scaffold is not suitable for rolling out rolling stock with large tapping cross sections and high forming resistances.

From DE-A 2 326 723 a rolling mill with several rolling stands standing in the rolling line for the production of rectangular, round or angular bars etc. is known. The rod material is reduced during rolling in the roll nips of the roll stands by pressure and in the gaps or spaces between two adjacent roll stands by reducing the elongation. The tensile stress of the bar between the roll stands is high and is in the order of the yield strength of the steel at the bar temperature and the rate of expansion. Each roll stand consists of a module version. Each module, which has one half of the roll stand, comprises a housing, a shaft, a main bearing and a rear bearing. The forces generated between the rolls are high during the rolling of flat profiles and angle profiles. These forces can cause the cantilever shafts to deflect. In order to prevent the shafts from bending, an external bearing is installed on certain intermediate rolling stands within the rolling mill. This bearing is preloaded by hand. The arrangement of a simple external bearing is in many cases not sufficient to absorb the high rolling forces if the reduction of the rolling stock is only to take place in the rolling stands and the reduction is not to be done by reducing the elongation.

The object of the invention is to further develop and improve a rolling mill consisting of CL stands in such a way that rolling stock with high tapping cross sections and high forming resistances and, if appropriate, rolling stock profiles can also be rolled with tolerable costs and short-time conversion measures. This task therefore also includes an improved device for storing and for the rapid and largely automated changing of the rolling rings of the stands. This task is solved with the measures of claims 1 to 7 in an exemplary manner.

The combined high-performance fine steel and wire mill of the type mentioned is characterized by the features of claim 1. If the rolling rings have to be replaced due to caliber wear or due to the rolling of another profile, this can be done in two ways: by exchanging the module unit known per se with an already pre-equipped module unit or, according to the invention, by changing the rolling rings, it being necessary to design the second bearing of the shaft carrying the roller ring in such a way that largely automatic removal of the roller rings is made possible with little maintenance. For this purpose, an automatically actuated, preferably hydraulically acting, quick-action clamping device for the double-bearing roller rings is proposed, with at least one piston-cylinder unit effective at least on one end face of the roller ring for clamping and releasing the same in the axial direction and at least one further piston acting on the roller ring. Cylinder unit for clamping and releasing in the radial direction of a cone bushing that supports the rolling ring and is arranged to be displaceable on its shaft axis. It is expedient that the module unit with double-bearing roller rings has a cassette bracket which contains the second bearing and is arranged on the transmission cassette which contains the first bearing and which consists of two bracket parts which can be connected by a quick-release coupling. The eccentric bush of the bearings of the shaft carrying the roller rings are positively connected with the aid of another connecting element, so that a synchronized turning of the eccentric bush is ensured. The new rollers and the new rolling fittings are adjusted to the new rolling line with the aid of the positively connected eccentric bushes.

The advantage of the structural design of the quick release device according to the invention for the double-bearing roller rings of the module unit is described below. Should the overhung rolling ring of the CL stands either counter in the roughing mill or in the finishing stands of the intermediate or finishing mill If a double-bearing roller ring has to be replaced, the entire module cassette is changed. With the proposed construction, the cassette change and the change of the roller rings can be carried out in a very short time and largely automatically. Depending on the application, the rolling mill can be most cost-effective completely with CL stands or in the roughing stand with some stands with module units with double rolling ring storage and in the intermediate line and finishing train either during initial equipment or later with modular units with double rolling ring storage for profile rolling or Separating rolling.

Figur 1

das Layout der Walzstraße

Figur 2

die Schnellspannvorrichtung für die doppelt gelagerten Walzringe einer Modul-Einheit

Figur 3

die Moduleinheit als Walzenkassette in Sandwich-Bauweise

Figur 4

einen Teilausschnitt der Walzenkassette nach Figur 3, teilweise im Schnitt.

The invention is described with the aid of partially schematic drawings for a combined fine steel and wire mill. Show it

Figure 1

the layout of the rolling mill

Figure 2

the quick release device for the double-bearing roller rings of a module unit

Figure 3

the module unit as a roller cassette in sandwich construction

Figure 4

a partial section of the roller cassette according to Figure 3, partly in section.

In Figure 1 is the combined and continuously working high performance fine steel and. Wire mill shown, with roughing train 1, which consists of roll stands arranged side by side in the rolling line with the stand sequence horizontal (H) / vertical (V), followed by intermediate line 2, which also consists of roll stands arranged side by side with the stand sequence horizontal (H) / vertical (V), which is followed by a finishing train 3. The finishing train 3, which is the intermediate line in the wire production, is followed by the finishing block 4 with the cooling device 5 (not shown in more detail), usually consisting of a water cooling section with driver / winding layer and the Stelmor system. In the case of rolling rod production or profile production, the finishing train 3 is followed by a cooling or storage bed 6. The entire rolling train essentially exists from so-called cantilever stands, abbreviated to CL stands, that means stands with one-sided (overhung roller rings). The peculiarity of the rolling mill now consists in the fact that primarily the first CL stands in the roughing mill contain interchangeable cassette units which can be exchanged for those with double-sided rolling rings. All gear, drive and housing units (not shown in detail) of the CL stands in the rolling mill can be taken over for the cassette with double-bearing roller rings. With rolling rings mounted in this way, the possibility is opened in the first stands of the roughing mill to roll out a rolling stock with high tapping cross sections and high forming resistances with impeccable quality. In the intermediate line 2 or in the finishing train 3, some roll stands can be arranged with a module unit 8 ', 8' with double-bearing roller rings 10 for the production of profiles as required. Since all gear, drive and housing units of the CL stands in the rolling mill can also be taken over in the intermediate line or finishing train, the module unit 8 ', 8' for profile production does not have to be part of the original equipment of the rolling train, but it If necessary, the CL module unit with overhung roller rings can be replaced with a module unit 8 ', 8' with double roller rings 10.

FIG. 2 shows the quick-clamping device for the double-bearing roller rings 10 of a corresponding module unit in the roughing mill and in the intermediate mill or in the finishing mill. The quick release device 11 is arranged on the transmission cassette 12. The first bearing 13, preferably a multi-layer slide bearing of the shaft 14 of the rolling ring 10, is seated in an eccentric bushing 15, which also has an adjusting spindle (not shown) Worm thread 16 is rotatable. As a result, the caliber opening of the rolling rings is adjustable. With the help of a spur gear 17, 17 'driven by a pilot gear, not shown, the roller rings 10, 10' carrying shafts 14, 14 'are driven. The second bearing 18 of the rolling ring 10 is also a multi-layer plain bearing, which is arranged in an eccentric bush 15 '. The second bearing 18 and the eccentric bushing 15 'are located in a cassette bracket 19 which is connected to the gearbox 12, for example by means of a screw connection. The cassette bracket 19 consists of two bracket parts, which are held together by a quick-release coupling 20. The eccentric bushes 15 and 15 'of the first bearing 13 and the second bearing 18 are, as is known per se, positively connected, so that a synchronized rotation of the eccentric bushes is ensured with the aid of the meshing screw in the worm thread 16.

The removal and assembly elements of the quick-action clamping device 11 for the rolling rings 10, including the inlet and outlet guide fittings, which are not shown in detail, are to be designated as follows, starting at the end of the shaft 14:
A compression nut 21 with a union nut 22. A retaining ring 23 which is arranged between the union nut 22 and a cylinder part 24. In the cylinder part 24, two annular pistons 25, 26 are arranged, namely a clamping piston 25 for the rolling ring 10 and a release piston 26 for the conical sleeve 27 on which the rolling ring 10 is seated. The cylinder part 24 is positively and non-positively connected to a support sleeve, on the support surface 29 of which one end face 30 of the rolling ring 10 rests. The second multilayer plain bearing 18 is arranged on the support sleeve 28 and from the eccentric bushing 15 'surrounded. The eccentric bush 15 'is arranged in the cassette bracket 19, as I said. There is a stop ring 32 with a stop surface 33 between the first slide bearing 13 and the eccentric bush 15 and the other end face 31 of the rolling ring 10. Between the supporting surfaces of the support sleeve 28 and the rolling ring 10 and between the supporting surfaces of the stop ring 32, thin friction disks 38 are inserted for torque transmission . The stop ring 32, the cone bushing 27 and the support sleeve 28 are arranged in a form-fitting manner in the circumferential direction, preferably by means of a longitudinal toothing 34, 35 or the stop ring with a feather key 36 on the shaft 14 carrying the rolling ring 10. In the support sleeve 28 there is an annular piston 37 which is supported against the conical sleeve 27 for the purpose of clamping the conical sleeve against the rolling ring.

To dismantle the rolling ring 10, the cassette bracket 19 is first unlocked from the transmission cassette with the aid of the coupling 20. Centering units arranged on the gearbox cassette are hydraulically tensioned and the centering bolts retained for compression by means of compression springs are advanced and then the bolts are swiveled out of the centering bolts by hand (not shown in more detail).

Now the clamping piston 25 for the rolling ring is hydraulically tensioned higher and the pressure nut 22 loosened and screwed back. The clamping piston 25 is then relaxed. The release piston 26 for the cone sleeve 27 is hydraulically tensioned, whereby the element unit consisting of the cylinder part 24, support sleeve 28, cone sleeve 27 and walrzing 10 is pulled off the shaft 14. A separate puller is therefore not necessary. Since the rolling fittings, not shown, are also attached to the cassette bracket 19, the entire unit can Corresponding to the resulting center of gravity 9 of a crane unit, for example, by means of a transport bracket arranged on the cassette bracket 19, it is moved from the stand to a construction site on which new roller rings 10 are mounted and new fittings are attached and completely adjusted.

To assemble the new rolling rings with the newly adjusted fittings, the assembly is moved from the construction site to the rolling stand 7 with the aid of a crane or a quick-change device and is pulled onto the roller shaft 14. The assembly is carried out as follows: the pressure nut 21 is rotated in the closing direction and the assembly is pushed onto the shaft 14 centering. The annular clamping piston 37 for clamping the cone sleeve 27 and the annular release piston 26 for the cone sleeve 27 are hydraulically relaxed. Now the clamping piston 25 is tensioned for the rolling ring, so that the rolling ring is pressed against the stop surface 30 of the stop ring 32 via the support surface 29 of the support sleeve 28.

The ring piston 37 for clamping the conical sleeve 27 is hydraulically preloaded and inserted. The clamping piston 25 for the rolling ring 10 is then pretensioned to maximum pressure and the union nut 22 is tightened by hand to the stop.

The cassette bracket 19 is locked by means of the latch pivoted into the centering bolt by hand. Now the centering unit is hydraulically relaxed, whereby the centering bolts are pushed back with the help of the compression springs and thus take over the clamping of the cassette bracket.

The new rollers and the new rolling fittings are adjusted to the new caliber opening with the aid of the positively connected eccentric bushes 15, 15 '.

Figure 3 and Figure 4 show a further module unit 8, 8 ', 8˝ with an exchangeable roller cassette 40, which is designed in a sandwich construction. The roller cassette consists of two cassette plates 44 with coupling pieces 45 which end at one end and point towards one another. The rolling ring shafts 41 are supported in bearings 42 in the cassette plates. The shaft ends of the rolling ring shafts 41 can be inserted into the transmission cassette 47, which is no longer shown. At the other shaft end of the rolling ring shafts 41, the hydraulic nut 50 can be seen, with which the rolling ring 46 is fastened on the shaft 41 in the radial direction with the aid of a conical bush 49 pushed onto the rolling ring shaft. On the outer sides of the cassette plates 44, the adjusting unit 43 for adjusting the roller rings 46 to the respective caliber opening is arranged. The pinion 54 shown in FIG. 3, which can be rotated by a handwheel (not shown) that can be pushed onto the split shaft 55, acts on the eccentric bushing 57 provided with external teeth 56 via at least one intermediate spur gear (not shown) (FIG. 4). The bearing units for the rolling ring shaft, in this case spherical roller bearings, are arranged in the eccentric bushing 57. The eccentric bushing 57 is forcibly connected on the transmission side by means of the connecting shaft 55 to the other actuating unit 43 which is arranged on the cassette plate 44 which faces the transmission cassette 47. For the sake of simplicity, only the further bearing unit 42, consisting of spherical roller bearings, is drawn in FIG. 4; the spherical roller bearings 42 receiving eccentric bushing is identical to that, eccentric bushing 57, which is shown with reference to the cassette front plate 44.

FIG. 3 also shows that the entire roller cassette 40 can be pulled off the gear cassette 47 and can be exchanged for a new cassette, possibly for a different cassette type or a different cassette size with different center distances. Figure 3 also shows that the cassette front plate 44 of the roller cassette 40 can be replaced separately if necessary, if necessary with the roller rings 46 and / or the roller fittings. For this purpose, the screws of the coupling piece 45 are loosened or removed and the hydraulic nut 50 is relaxed and loosened. Since the roller ring 46 is seated on the taper bush 49, this is also pulled off the roller ring shaft when the cassette front plate is removed. Then the rolling ring 46 is easily accessible and can be easily removed from the taper bush 49 and exchanged for a new rolling ring. The maintenance times for the roller cassette and the changing times for the roller rings are thereby reduced considerably, in particular when the roller ring cooling 48 and other hydraulic connections remain on the cassette plate 44 which can be connected to the gear cassette 47 (FIG. 3). Different diameters of, for example, exchanged rolling rings are identified by the reference numerals 46 'and 46˝.

As previously described, the roller rings 46 are seated on a conical sleeve 49 pushed onto the roller ring shaft 41, which is acted upon in the radial direction by clamping and releasing the roller rings with the axial pressure of the hydraulic nut 50, the mode of operation of which is assumed to be known. So that the rolling rings 46 not only in in the radial direction on the rolling ring shaft 41, but also axially and in the circumferential direction, the rolling rings are held between annular clamping pieces 51, friction discs 52 being inserted as connecting elements between the clamping pieces 51 and the side flanks 53 of the rolling rings, and furthermore the clamping pieces 51 with the Taper bush 49 or on the other side are splined with the rolling ring shaft 41.

The measures described above are not only limited to the illustrated embodiment, but also relate to all such constructive solutions that fall under the claims.

List of reference numbers

1

Vorstrasse

2nd

Intermediate street

3rd

Finishing train

4th

Finished block

5

Water cooling section

6

Storage bed

7

CL framework

8, 8 ′, 8˝

Module unit

9

main emphasis

10, 10 ′

Roll rings

11

Quick release device

12th

Gearbox

13

first camp

14, 14 ′

wave

15, 15 ′

Eccentric bushes

16

Worm thread

17, 17 ′

Spur gears

18th

second camp

19th

Cassette bracket

20th

clutch

21

Pressure nut

22

Cap nut

23

Retaining ring

24th

Cylinder part

25th

ring-shaped clamping piston

26

ring-shaped release piston

27

Taper bush

28

Support sleeve

29

Support surface

30th

Roll ring end face

31

Roll ring end face

32

Stop ring

33

Abutment surface

34

Longitudinal teeth

35

Longitudinal teeth

36

adjusting spring

37

Ring piston

38

Friction disc

39

Front side support sleeve

40

Exchange cassette

41

Roll ring shaft

42

Storage unit

43

Instead of

44

Cassette plate, cassette front plate

45

Coupling piece

46

Rolling ring

47

Gearbox

48

Roll ring cooling

49

Taper bush

50

Hydraulic nut

51

Clamp

52

Friction discs

53

Side flanks

54

pinion

55

Connecting shaft

56

External teeth

57

Eccentric bushing

Claims (7)

1. Combined continuously operating high-output roll train for small sections and wire, in the roughing train (1) of which as well as in the intermediate train (2) of which and/or in the finishing train (3) of which there are arranged not only cantilever stands (7) with ring rolls mounted at one end (cantilever) but also roll stands with a modular unit (8, 8′, 8˝) with ring rolls (10) mounted at both ends (doubly), characterised thereby that the modular unit (8, 8′, 8˝) with ring rolls (10) mounted doubly has a cassette yoke (19) which contains the second bearing (18) and is arranged at the transmission cassette (12) containing the first bearing (13) and which consists of two yoke parts (19′, 19˝) connectible by a quick-release coupling (20), and that there is provided an automatically actuable, preferably hydraulically operating quick-acting device (11) for the ring rolls (10) mounted doubly, with at least one piston-cylinder unit (25, 26), which acts at least on an end face (30) of the ring roll (10), for the clamping and release of the same in axial direction and with at least one further piston-cylinder unit (37), which acts on the ring roll (10), for the clamping and release in radial direction of a collet (27) carrying the ring roll (10) and displaceably arranged on the shaft (14) thereof.
2. Roll train for small sections and wire according to claim 1, characterised thereby that the collet (27) stands in connection at its end and by means of the piston-cylinder unit (37) with a support sleeve (28) displaceably arranged on the shaft (14) of the ring roll (10) and carrying the second bearing (18) of the ring roll (10), and that the support sleeve (28) is supported in force-locking manner at the one end face (30) of the ring roll (10).
3. Roll train for small sections and wire according to claim 1 or 2, characterised thereby that the other end face (31) of the ring roll (10) is supported in force-locking manner at an abutment ring (32) surrounding the shaft (14) of the ring roll (10).
4. Roll train for small sections and wire according to claim 1, 2 or 3, characterised thereby that a respective friction disc (38) is arranged between the support surfaces (29, 30) of support sleeve (28) and ring roll (10) and between the support surfaces (33, 31) of abutment ring (32) and ring roll (10).
5. Roll train for small sections and wire according to at least one of the preceding claims 1 to 4, characterised thereby that the other end face (29) of the support sleeve (28) is connected with a cylinder part (24), in which the piston (25) for the clamping of the roll ring (10) and the piston (26) for the release of the collet (27) are slidingly arranged, wherein the pistons (25, 26) are constructed as annular pistons and are seated on the shaft (14) carrying the ring roll (10).
6. Roll train for small sections and wire according to at least one of claims 1 to 5, characterised thereby that the cylinder part (24) is tightenable, in a given case with interposition of a retaining ring (23), by a pressure nut (21), especially a box nut (22), in direction of the shaft (14) against the support sleeve (28) and against the collet, wherein the box nut (22) is rotatable in the shaft (14) by means of screw-threading for the application of the tightening forces.
7. Roll train for small sections and wire according to at least one of the preceding claims, characterised thereby that the abutment ring (32), the collet (27) and the support sleeve (28) are arranged on the shaft (14), which carries the ring roll (10), to be shape-locking in circumferential direction, preferably by means of longitudinal toothing (34, 35) or adjusting springs (36).

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