EP4126408A1

EP4126408A1 - Roll stand

Info

Publication number: EP4126408A1
Application number: EP21712763.8A
Authority: EP
Inventors: Hans-Jürgen Bender; Achim Klein
Original assignee: SMS Group GmbH
Current assignee: SMS Group GmbH
Priority date: 2020-04-01
Filing date: 2021-03-15
Publication date: 2023-02-08
Also published as: JP7429304B2; DE102020204245A1; CN115362036A; WO2021197816A1; JP2023520411A

Abstract

The invention relates to a roll stand (1) for rolling a metal stock to be rolled, comprising a first roll housing (3), which is arranged on the drive side; a second roll housing (5), which is arranged on the operating side, each roll housing (3, 5) having at least one receiving opening (6, 7) for an installation piece (8, 9) for rotatably supporting a roll (10) which is provided with roll journals and which is not axially movable; and at least two locking plates (11, 12, 13, 14) for locking the installation pieces (8, 9), each locking plate (11, 12, 13, 14) being arranged on the respective roll housing (3, 5) end face remote from the roll and being connected to said housing via at least one axial load measuring bolt (15, 16, 17, 18) at least in a formfitting manner such that each of the locking plates (11, 12, 13, 14) overlaps with at least one part of the respective receiving opening (8, 9) such that an axial force which is produced during the rolling process and which is transmitted to at least one of the axial load measuring bolts (15, 16, 17, 18) via the roll journal, the installation piece (8, 9), and the locking plate (11, 12, 13, 14) can be detected by the respective axial load measuring bolt (15, 16, 17, 18).

Description

ROLLED FRAMEWORK

The present invention relates to a roll stand for rolling metallic rolling stock in a hot or cold rolling process.

Roll stands for rolling metallic rolling stock are known in principle from the prior art. In the case of roll stands that include non-axially displaceable rolls, each work roll is rotatably supported in an axial play-free manner via two roll journals in a chock, also called a bearing housing. In the ideal case, therefore, only forces should occur in the rolling process that extend transversely to the longitudinal axis of the work rolls.

The ideal case is hardly feasible in practice, however, since the work rolls are exposed to various disturbances from the rolling process. For example, asymmetries within the rolling stock to be rolled cause considerable disruptions in the rolling process. These disturbances lead to a compensating axial movement or force of the rollers. Because the work rolls are mounted axially free of play, this has a disadvantageous effect on the rolling quality of the rolling stock to be rolled and on the bearings installed in the chocks.

From CN 102327902 A, an operator-side roll stand with a work roll rotatably mounted in a chock is known. The chock arranged in the operator-side roll stand is locked against axial displacement by means of locking plates. The locking plates are screwed to the operator-side roller stand by means of pre-tensioned screws. The elongated screws have a strain gauge by means of which an axial force of the work roll extending only in the direction of the operator-side roll stand can be measured. Another device for measuring the axial force in an operator-side roll stand is also known from CN 205 413 924 U. The device comprises a bolt having a strain gauge, which is arranged in the roller stand with the operator side and is screwed to it in a pretensioned manner.

Against this background, the present invention is based on the object of providing a roll stand with which an improved product quality can be achieved in the rolled material and which requires less maintenance.

Description of the invention

According to the invention, the object is achieved by a roll stand with the features of claim 1. The roll stand according to the invention is provided for rolling a metallic rolling stock and comprises a first roll stand arranged on a drive side and a second roll stand arranged on an operating side. Each of the roll stands has at least one receiving opening for a chock for the rotatable mounting of an axially non-displaceable roll provided with roll journals. Furthermore, the roll stand comprises at least two locking plates for locking the chocks - and the rollers mounted therein - against axial displacement to the outside of the roll stand. In each case at least one locking plate is arranged on an end face of the respective roll stand remote from the roll. Furthermore, the roll stand comprises at least two axial force measuring pins. Each of the at least two locking plates is in an advanced position during the rolling operation, in which it covers at least part of the respective receiving opening for locking the chocks located - with the rollers rotatably mounted therein - against axial displacement. In this advanced position, the locking plates are each over at least an axial force measuring pin connected at least positively to the roll stand, so that an axial force generated during a rolling process and transmitted via the roll neck, the chock and the locking plate to at least one of the axial force measuring pins can be detected by the respective axial force measuring pin.

The present invention is based on the essential knowledge that by detecting the axial forces of the work rolls, not only one but in both axial directions, i.e. in the direction of the operating and drive side of the roll stand, process-related and / or system-related disturbances are better recognized and thus can be adjusted quantitatively. This has a particularly advantageous effect on the product quality of the rolled stock as well as the wear, which leads to reduced maintenance costs for the roll stand.

According to the invention, this is achieved in that the two roll stands are designed essentially identically, so that the axial force generated during a rolling process, regardless of the axial direction in which it acts, can be transmitted via the roll neck, the chock and the locking plate to at least one of the axial force measuring pins and is thus detectable.

The detected process-related and / or system-related disturbance variables can be adjusted manually by a worker, for example. However, it is advantageously provided that these are automatically regulated. For this purpose, the roll stand preferably has a control circuit comprising RAC (Roll Alignment Control) and / or TFC (Thrust Force Control) programming, which acts on the hydraulic actuators of the roll stand as a function of the values determined by the axial force measuring pin. Further advantageous refinements of the invention are specified in the dependent claims. The features listed individually in the dependently formulated claims can be combined with one another in a technologically meaningful manner and can define further embodiments of the invention. In the following, the features specified in the claims are specified and explained in more detail in the description, with further preferred embodiments of the invention being presented.

In a first advantageous embodiment variant, each of the at least two locking plates is positively connected to the roll stand via the at least one axial force measuring bolt in such a way that each of the axial force measuring bolts is not pretensioned. It has been shown here that this non-prestressing of the axial force measuring pins leads to a particularly high measurement resolution, since the entire axial force introduced can be measured. In this context, it has proven to be particularly advantageous if each of the axial force measuring bolts is connected to the roll stand in a form-fitting and material-locking manner. The axial force measuring bolt typically has a threaded section at each of its two ends. The axial force measuring bolt is screwed positively to the roll stand via a first thread section. The locking plate is fixed by means of a measuring bolt nut, preferably with an air gap, via a second threaded section. In order to ensure freedom from play in the two threads, these are z. B. additionally adhesively bonded by means of a thread adhesive. In a further preferred embodiment variant, the at least one locking plate arranged on the drive side is non-displaceable and the at least one locking plate arranged on the operating side is designed to be displaceable. A roll change can be carried out particularly easily via the horizontally displaceable locking plate. The locking plates, which normally secure a chock in the roll stand against axial displacement, are laterally displaced outward for a roll change and then release the respective chock for removal to the operating side of the roll stand. This variant is particularly advantageous when the axial force measuring pin is not clamped to the locking plate and the locking plate can then be freely displaced horizontally because the time-consuming removal of the axial force measuring pin to replace the rollers can then be saved. In this context, it is very particularly preferred that the at least one locking plate arranged on the operator side comprises an actuator by means of which it can be displaced so that the roll change can take place semi-automatically or fully automatically

The actuator can be designed, for example, in the form of a hydraulic cylinder or in the form of a threaded drive.

In a further preferred embodiment, the axial force measuring pin arranged on the operator side has a larger overall diameter compared to the axial force measuring pin arranged on the drive side. The larger dimensioning of the diameter compensates for the unfavorable lever arm on the at least one locking plate arranged on the operator side. In the context of the present invention, the term “overall diameter” is understood to mean a diameter averaged over the entire length of the axial force measuring pin.

It is particularly preferably provided that the roll stand comprises at least two, preferably four or eight locking plates, so that each of the chocks can be locked via at least two or even four locking plates.

In order to generate a symmetrical lever on the respective locking plates, it is advantageously provided that each of the locking plates is connected to the respective roller stand via at least two axial force measuring bolts is at least positively, particularly preferably positively and cohesively connected.

Preferably, each of the axial force measuring bolts has an essentially cylindrical base body with a first threaded section arranged at a first distal end and a second threaded section arranged at a second distal end and a central section with at least one between the first and second threaded sections radial transverse bore which opens into a central longitudinal bore of the axial force measuring pin and at least one strain gauge arranged on its outer surface and spaced from the transverse bore.

Due to the transverse bore, which is required for the electrical connection of the strain gauge, the axial force measuring pin and in particular the middle section are loaded asymmetrically by the axial force introduced. The direct area around the cross hole is exposed to particularly high loads. Surprisingly, it has been shown that an arrangement of the strain gauge that is axially spaced from the transverse bore has a particularly advantageous effect on the quality of the

Measurement results. In this context, it is particularly preferred if the strain gauge has a minimum distance from the transverse bore and the minimum distance is at least 1.5 times the diameter, particularly preferably at least 2 times the diameter, and very particularly preferably 3 to 5 times the diameter. times the

Corresponds to the diameter of the cross hole. The distance refers to the center of the cross hole to the center of the strain gauge. With regard to the positional arrangement, the at least one strain gauge with the transverse bore can be arranged on a common surface line, on a common circular line and / or on different surface and circular lines. When arranging the position, make sure that the strain gauge is to be positioned on the surface of the axial force measuring pin in such a way that it can detect the axial expansions that occur. The expansion or deformation changes the resistance of the strain gauge, which can then be converted into an axial force.

In a particularly preferred embodiment variant, the middle section has at least one pressure relief groove extending transversely to the longitudinal axis of the axial force measuring bolt on its surface in the region of the at least one transverse bore. In this context, it is advantageously provided that the at least one pressure relief groove has a minimum length and this is at least 2/10 of the diameter of the central section, more preferably at least 3/10 of the diameter of the central section, and particularly preferably at least 4/10 to a maximum of 6 / 10 of the diameter of the middle section. Via the at least one pressure relief groove arranged in the area of the transverse bore, the loads that occur as a result of the introduced axial forces are further reduced and the quality of the measurement results improved.

Furthermore, it is advantageously provided that the first thread section has a larger diameter than the second thread section. The axial force measuring bolt is connected to the roll stand of the roll stand with a positive fit, preferably a positive fit and material fit, via the first threaded section. The axial force measuring bolt can be fixed in a form-fitting and / or cohesive manner, preferably in a form-fitting and cohesive manner, by means of a measuring bolt nut via the second threaded section. The first thread section can be designed to be correspondingly long in order to enable an optimal introduction of force. If necessary, the first threaded section could be arranged in the roll stand via a separate threaded bushing. Figure description

The invention and the technical environment are explained in more detail below with reference to the figures. It should be pointed out that the invention is not intended to be restricted by the exemplary embodiments shown. In particular, unless explicitly stated otherwise, it is also possible to extract partial aspects of the facts explained in the figures and to combine them with other components and findings from the present description and / or figures. In particular, it should be pointed out that the figures and in particular the size relationships shown are only schematic. The same reference symbols denote the same objects, so that explanations from other figures can be used in addition, if necessary. Show it:

1 shows a variant of a roll stand according to the invention in a schematic horizontal cross-sectional view, FIG. 2 shows a variant of the axial force measuring pin shown in FIG. 1 in a representation with a sleeve and measuring bolt nut, and FIG. In Figure 1, a variant of the roll stand 1 according to the invention is shown, which is provided for rolling a metallic rolling stock. The roll stand 1 comprises a first roll stand 3 arranged on a drive side 2 and a second roll stand 5 arranged on an operating side 4. Each of the roll stands 3, 5 has at least one receiving opening 6, 7 for a respective chock 8, 9. The chocks 8, 9 serve for the rotatable mounting of an axially non-displaceable roller 10 provided with roller journals 8.1, 9.1.

The roll stand 1 shown in FIG. 1 comprises, in the embodiment variant shown here, four locking plates 11, 12, 13, 14 for locking the chocks 8, 9 - and thus the rollers - against axial displacement. To the Installation and removal of the rolls from the roll stand, the rolls are pushed together with the chocks in the axial direction through the receiving opening of the roll stand. For this purpose, the receiving opening is released by moving the locking plates 11-14 transversely to the axial direction. Preferably, two locking plates 11, 12, 13, 14 are each arranged on an end face of the respective roll stand 3, 5 remote from the roll, at the level of the chocks 8, 9. Each of the locking plates 11, 12, 13, 14 is connected to the roll stand 1 via at least one axial force measuring bolt 15, 16, 17, 18 in the embodiment shown here. Due to the horizontal cross-section, however, there is only one in the present FIG

Axial force measuring pins 15, 16, 17, 18 per locking plate 11, 12, 13, 14 are visible.

Each of the axial force measuring bolts 15, 16, 17, 18 is connected in the embodiment variant shown here to the respective roll stand 3, 5 in a form-fitting and preferably also materially bonded, in such a way that each of the locking plates 11, 12, 13, 14 at least part of the receiving opening 6 , 7 of the respective roll stand 3, 5 covered, so that one during a

The axial force caused by the rolling process and transmitted via the roll neck, the chock 8, 9 and the locking plate 11, 12, 13, 14 to at least one of the axial force measuring pins 15, 16, 17, 18 can be detected by the respective axial force measuring pin 15, 16, 17, 18 . The axial force measuring pins 17, 18 arranged on the operator side have, in the embodiment variant shown here, a larger overall diameter than the axial force measuring pins 15, 16 arranged on the drive side.

The two locking plates 11, 12 arranged on the drive side are preferably connected to the roller stand in a non-displaceable manner, whereas the two locking plates 13, 14 arranged on the operating side are displaceable are executed. This embodiment variant is particularly advantageous when the axial force measuring bolts 13, 14 have no preload with respect to the locking plates, since time-consuming loosening of the axial measuring bolts or the locking plates to replace the roller 10 can be saved. For this purpose, the two locking plates 13, 14 arranged on the operator side have an actuator (not shown) by means of which the two locking plates 13, 14 arranged on the operator side can be displaced fully automatically.

In order to achieve a particularly high measurement resolution, the eight axial force measuring pins 15, 16, 17, 18 arranged in the roller stand 1 are connected in a form-fitting and material-locking manner in such a way that they are not pretensioned. In the present case, this is achieved in that an air gap 35 is set between a measuring bolt nut 19 of the axial force measuring bolt 15, 16, 17, 18 and the respective locking plate 11, 12, 13, 14 (FIG. 3). This non-prestressing of the axial force measuring pins 15, 16, 17, 18 achieves a particularly high measurement resolution, since the entire axial force introduced can be measured. This is supported by the fact that the axial force measuring bolts 15, 16, 17, 18 are fixed with the roll stand 3, 5 on the one hand in a form-fitting and preferably cohesive manner and on the other side with the measuring bolt nut 19 in a form-fitting and preferably also cohesively. The cohesive connection is achieved in the present case by means of an adhesive connection.

By detecting the axial forces in both axial directions of the roll 10, i.e. in the direction of the operating and drive side 2, 4 of the roll stand 1, a number of process and / or system-related disturbances occurring in the process are detected so that they can be quantitatively corrected. This has a particularly advantageous effect on the product quality of the rolled stock as well as the wear, which leads to a reduced maintenance effort for the roll stand 1. FIG. 2 shows an embodiment variant of one of the axial force measuring bolts 17 shown in FIG. 1 in a representation with a sleeve 20 and measuring bolt nut 19. The axial force measuring bolt 17 is made, for example, of chromium-nickel steel 30CrNiMo8 and tempered ^{for a load of 1300 N / mm 2.}

The axial force measuring bolt 17 has an essentially cylindrical base body 21 with a first threaded section 22 arranged at a first distal end and a second threaded section 23 arranged at a second distal end and one between the first and second threaded sections 22, 23 middle section 24 on.

As can be seen in part from FIG. 3, the axial force measuring bolt 17 has two radially opposite transverse bores 25, which open into a central longitudinal bore 26 of the axial force measuring bolt 17, as well as two strain gauges 27, which are arranged radially opposite on its outer circumferential surface and spaced from the transverse bores 25 . As can be seen in particular from FIG. 2, the strain gauge 27 and the transverse bore 25 are arranged on a common surface line in the embodiment variant shown here.

Furthermore, in the embodiment variant shown here, the axial force measuring pin 17 has two pressure relief grooves 28, 29 extending transversely to the longitudinal axis of the axial force measuring pin 17 on each of the two transverse bores 25. About the arranged in the area of the transverse bores 25

Pressure relief grooves 28, 29, the loads occurring as a result of the introduced axial forces are reduced again and the quality of the measurement results is improved. The middle section 24 has in each case a raised design and circumferentially arranged in the area of the first and second threaded sections 22, 23 running sealing seat surface 30, 31 for the sleeve 20, so that the middle section 24 and the two strain gauges 27 arranged on the outer jacket surface between the two sealing seat surfaces 30, 31 are hermetically encapsulated. The strain gauges 27 are effectively protected from all environmental influences by the sleeve 20. In order to be able to optimally adjust the air gap 35, the sleeve 20 has an axial extent that is smaller than the thickness of the locking plate 11, 12, 13, 14.

In FIG. 3, a partial sectional illustration of the axial force measuring pin 17 arranged in the roll stand 1 is shown in a longitudinal section. The electrical connections 32 of the respective strain gauges 27, which run through the transverse bores 25 and the central longitudinal bore 26, can be seen here. Furthermore, it can be seen from the present illustration that the first threaded section 22, which is connected to the roll stand 5 in a form-fitting and material-locking manner, has a larger diameter than the second threaded section 23. In addition, it can be seen from FIG. 3 that the sleeve 20 has two radially extending grooves 33, 34 into which O-rings are inserted (not shown).

List of reference symbols

1 roll stand

2 drive side

3 first roller stand 4 operating side

5 second roll stand

6 receiving opening

7 receiving opening

8 Chock 8.1 Roll neck

9 chock

9.1 Roll neck

10 roller

11 locking plate 12 locking plate

13 locking plate

14 locking plate

15 axial force measuring pins

16 axial force measuring pins 17 axial force measuring pins

18 axial force measuring pins

19 measuring bolt nut

20 sleeve

21 cylindrical body 22 first threaded portion

23 second thread section

24 middle section

25 cross hole

26 Longitudinal bore 27 Strain gauges

28 Pressure relief groove 29 Pressure relief groove

30 sealing seat

31 sealing seat

32 electrical connections 33 grooves

34 grooves

35 air game

Claims

1 . Roll stand (1) for rolling a metallic rolling stock, comprising a first roll stand (3) arranged on a drive side and a second roll stand (5) arranged on an operating side, each of the roll stands (3, 5) having at least one receiving opening ( 6, 7) for a chock (8, 9) for the rotatable mounting of an axially non-displaceable roll (10) provided with roll journals, at least two locking plates (11, 12, 13, 14) for locking the chocks (8, 9) ), wherein in each case one of the locking plates (11, 12, 13, 14) is arranged on the end face of the respective roll stand (3, 5) remote from the roll that they (11, 12, 13, 14) at least part of it

Receiving opening (8, 9) covered, and at least one axial force measuring pin (15, 16, 17, 18) with the roll stand is at least positively connected so that a generated during a rolling process and over the roll neck, the chock (8, 9) and the locking plate (11, 12, 13, 14) on at least one of the

Axialkraftmessbolzen (15, 16, 17, 18) transmitted axial force from the respective axial force measuring bolt (15, 16, 17, 18) can be detected.

2. Roll stand (1) according to claim 1, wherein each of the at least two

Locking plates (11, 12, 13, 14) over the at least one

Axialkraftmessbolzen (15, 16, 17, 18) is positively connected to the roll stand (3, 5) in such a way that each of the axial force measurement bolts (15, 16, 17, 18) is not pretensioned.

3. Roll stand (1) according to claim 1 or 2, wherein the at least one locking plate (11, 12) arranged on the drive side is not slidable with the roll stand on the drive side and the at least one locking plate (13, 14) arranged on the operating side is slidable.

4. Roll stand (1) according to claim 3, wherein the at least one locking plate (13, 14) arranged on the operator's side is assigned an actuator via which the at least one locking plate (13, 14) can be displaced.

5. Roll stand (1) according to one of the preceding claims, wherein the axial force measuring pin (17, 18) arranged on the operator side has a larger overall diameter compared to the axial force measuring pin (15, 16) arranged on the drive side.

6. Roll stand (1) according to one of the preceding claims, comprising at least four locking plates (11, 12, 13, 14), so that each of the chocks (8, 9) can be locked via at least two locking plates (11, 12, 13, 14) is.

7. Roll stand (1) according to one of the preceding claims, wherein at least one of the locking plates (11, 12, 13, 14) via two or more axial force measuring bolts (15, 16, 17, 18) with the respective roll stand (3, 5) is at least positively connected.

8. roll stand (1) according to any one of the preceding claims, wherein each of the

Axial force measuring pin (15, 16, 17, 18) an essentially cylindrical base body (21) with a first threaded section (22) arranged at a first distal end, with a second threaded section (23) arranged at a second distal end , as well as having a central section (24) arranged between the first and the second threaded section (22, 23), the central section having at least one radial transverse bore (25) which is in a central longitudinal bore (26) of the axial force measuring pin (15, 16, 17, 18) opens and at least one strain gauge (27) is provided on its outer lateral surface and spaced from the at least one transverse bore (25).

9. Roll stand (1) according to claim 8, wherein the at least one strain gauge (27) each has a minimum distance from the at least one transverse bore (25) and the minimum distance corresponds to at least 1.5 times the diameter of the transverse bore (25).

10. Roll stand (1) according to one of the preceding claims 8 or 9, wherein the at least one strain gauge (27) with the at least one transverse bore (25) is arranged on a common surface line, on a common circular line and / or on different surface and circular lines is.

11. Roll stand (1) according to one of the preceding claims 8 to 10, wherein the middle section (24) in the region of the at least one transverse bore (25) has a pressure relief groove (28, 29) running transversely to the longitudinal axis.

12. Roll stand (1) according to claim 11, wherein the pressure relief groove (28, 29) has a minimum length and this corresponds to at least 2/10 of the diameter of the central section.

13. Roll stand (1) according to one of the preceding claims 8 to 12, wherein the axial force measuring pin (15, 16, 17, 18) comprises a sleeve (20) which is mounted on two spaced apart and circumferentially extending sealing seat surfaces (30, 31 ) is arranged so that the at least one strain gauge (27) arranged on the outer jacket surface between the two sealing seat surfaces (30, 31) is hermetically encapsulated.

14. Roll stand (1) according to one of the preceding claims 8 to 13, wherein the axial force measuring pin (15, 16, 17, 18) is formed from a chrome-nickel steel.

15. Roll stand (1) according to one of the preceding claims 8 to 14, wherein the first threaded section (22) has a diameter larger than the second threaded section (23).