DE102020204245A1 - Roll stand - Google Patents

Abstract

The present application relates to a roll stand (1) for rolling 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) ) has at least one receiving opening (6, 7) for a chock (8, 9) for the rotatable mounting of an axially non-displaceable roller (10) provided with roll journals, at least two locking plates (11, 12, 13, 14) for Locking of the chocks (8, 9), with a locking plate (11, 12, 13, 14) being arranged on an end face of the respective roll stand (3, 5) remote from the roll and with at least one axial force measuring pin (15, 16, 17, 18) this is at least positively connected, in such a way that each of the locking plates (11, 12, 13, 14) overlaps at least a part of the respective receiving opening (8, 9), 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 axial force measuring pins (15, 16, 17, 18) transmitted axial force from the respective axial force measuring pin (15, 16, 17, 18) is detectable.

Description

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 the 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 from the CN 205 413 924 U known. 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 at least positively connected to the roll stand via at least one axial force measuring bolt, so that an axial force generated during a rolling process and transmitted via the roll journal, the chock and the locking plate to at least one of the axial force measuring bolts can be detected by the respective axial force measuring bolt .

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, via the roll neck, the chock and the locking plate on at least one of the Axialkraftmessbolzen is transferable and 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 programming (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 plate arranged on the drive side is non-displaceable and the at least one locking plate 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 shifted laterally 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 at least in a form-fitting manner, particularly preferably form-fittingly and materially, via at least two axial force measuring bolts.

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 that opens into a central longitudinal bore of the axial force measuring pin and at least one on its outer one Jacket surface and spaced apart from the transverse bore, strain gauges.

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 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, care must be taken to ensure that the strain gauge is 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 list

• 1 eine Ausführungsvariante eines erfindungsgemäßen Walzgerüstes in einer schematischen horizontalen Querschnittsdarstellung,
• 2 eine Ausführungsvariante des in 1 gezeigten Axialkraftmessbolzens in einer Darstellung mit Hülse und Messbolzenmutter, und
• 3 eine Teilschnittdarstellung des im Walzgerüst angeordneten Axialkraftmessbolzens gemäß obiger Ausführungsvariante.

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 an embodiment variant of a roll stand according to the invention in a schematic horizontal cross-sectional view,
• 2 a variant of the in 1 Axialkraftmessbolzens shown in a representation with sleeve and measuring bolt nut, and
• 3 a partial sectional view of the axial force measuring pin arranged in the roll stand according to the above variant.

In 1 is a variant of the roll stand according to the invention 1 shown, which is provided for rolling a metallic rolling stock. The roll stand 1 comprises a first one on a drive side 2 arranged, roller stand 3 and a second, on one operating side 4th arranged, roller stand 5 . Each of the roll stands 3 , 5 has at least one receiving opening 6th , 7th for one chock each 8th , 9 on. The chocks 8th , 9 serve for the rotatable mounting of one with roll neck 8.1 , 9.1 provided, axially non-displaceable, roller 10 .

This in 1 Roll stand shown 1 comprises four locking plates in the embodiment variant shown here 11 , 12th , 13th , 14th for locking the chocks 8th , 9 - and thus the rollers - against axial displacement. For installing and removing the rollers from the roller stand, the rolls are pushed together with the chocks in the axial direction through the receiving opening of the roll stand. To do this, the receiving opening is opened by moving the locking plates 11-14 released transversely to the axial direction. Preferably there are two locking plates each 11 , 12th , 13th , 14th on an end face of the respective roll stand remote from the roll 3 , 5 at the height of the chocks 8th , 9 arranged. Each of the locking plates 11 , 12th , 13th , 14th is in the embodiment variant shown here via at least one axial force measuring pin 15th , 16 , 17th , 18th with the roller stand 1 tied together. Preferably, two axial force measuring bolts arranged vertically with respect to one another can also be provided per locking plate. Due to the horizontal cross-section is in the present 1 but only one axial force measuring pin 15th , 16 , 17th , 18th per locking plate 11 , 12th , 13th , 14th visible.

Each of the axial force measuring pins 15th , 16 , 17th , 18th is in the variant shown here with the respective roll stand 3 , 5 form-fitting and preferably also cohesively connected in such a way that each of the locking plates 11 , 12th , 13th , 14th at least part of the receiving opening 6th , 7th of the respective roll stand 3 , 5 covered, so that a chock caused during a rolling process and over the roll neck, the chock 8th , 9 and the locking plate 11 , 12th , 13th , 14th on at least one of the axial force measuring pins 15th , 16 , 17th , 18th transmitted axial force from the respective axial force measuring pin 15th , 16 , 17th , 18th is detectable. The axial force measuring pins arranged on the operator's side 17th , 18th In the embodiment variant shown here, have an axial force measuring pin arranged on the drive side 15th , 16 larger overall diameter.

The two locking plates on the drive side 11 , 12th are preferably not slidably connected to the roll stand, whereas the two locking plates arranged on the operator's side 13th , 14th are designed to be displaceable. This variant is particularly advantageous when the axial force measuring pins 13th , 14th do not have any bias against the locking plates, since a time-consuming loosening of the axial measuring bolts or the locking plates to replace the roller 10 can be saved. To this end, the two locking plates arranged on the operator's side have 13th , 14th an actuator (not shown), via which the two locking plates arranged on the operator's side 13th , 14th can be moved fully automatically.

In order to achieve a particularly high measurement resolution, they are in the roller stand 1 eight arranged axial force measuring pins 15th , 16 , 17th , 18th so positively and cohesively connected that they are not pretensioned. This is achieved in the present case that between a measuring bolt nut 19th of the axial force measuring pin 15th , 16 , 17th , 18th and the respective locking plate 11 , 12th , 13th , 14th an air game 35 is set ( 3 ). This non-pre-tensioning of the axial force measuring pins 15th , 16 , 17th , 18th a particularly high measurement resolution is achieved because the entire axial force introduced can be measured. This is supported by the fact that the axial force measuring pins 15th , 16 , 17th , 18th with the roller stand 3 , 5 on the one hand form-fitting and preferably also cohesively and on the other hand with the measuring bolt nut 19th are positively and preferably also firmly fixed. 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 roller 10 , i.e. in the direction of the operator and drive side 2 , 4th of the roll stand 1 a number of process and / or system-related disturbance variables occurring in the process are recognized so that they can be corrected quantitatively. 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 leads.

In 2 is a variant of one of the in 1 axial force measuring pin shown 17th in a representation with a sleeve 20th and measuring bolt nut 19th shown. The axial force measuring pin 17th is made, for example, of chrome-nickel steel 30CrNiMo8 and tempered ^{for a load of 1300 N / mm 2.}

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

Again 3 The axial force measuring pin is partially removable 17th two cross bores arranged radially opposite one another 25th in a central longitudinal bore 26th of the axial force measuring pin 17th open, as well as two, on its outer circumferential surface radially opposite and to the transverse bores 25th spaced apart strain gauges 27 on. Like the one in particular 2 the strain gauges are removable 27 as well as the cross hole 25th In the embodiment variant shown here, arranged on a common surface line.

The axial force measuring pin also has 17th in the embodiment variant shown here on each of the two transverse bores 25th two across to the longitudinal axis of the axial force measuring pin 17th extending pressure relief grooves 28 , 29 on. About the in the area of the cross bores 25th arranged pressure relief grooves 28 , 29 the loads that occur as a result of the axial forces introduced are further reduced and the quality of the measurement results improved.

The middle section 24 each has one in the area of the first and second threaded section 22nd , 23 arranged raised and circumferentially extending sealing seat surface 30th , 31 for the sleeve 20th up so the middle section 24 as well as the two on the outer jacket surface between the two sealing seat surfaces 30th , 31 arranged strain gauges 27 is hermetically sealed. Through the sleeve 20th become the strain gauges 27 Effectively protected from all environmental influences. To the air game 35 to be able to adjust optimally, shows the sleeve 20th one to the thickness of the locking plate 11 , 12th , 13th , 14th smaller axial extent.

In 3 is a partial sectional view of the in the roll stand 1 arranged axial force measuring pin 17th shown in a longitudinal section. The electrical connections can be seen here 32 of the respective strain gauges 27 going through the cross holes 25th and the central longitudinal bore 26th get lost. It can also be seen from the present illustration that the first thread section 22nd , the one with the roll stand 5 is positively and cohesively connected, one to the second threaded section 23 has a larger diameter. In addition, from the 3 recognizable that the sleeve 20th two radial grooves 33 , 34 has, are inserted into the O-rings (not shown).

List of reference symbols

1

Roll stand

2

Drive side

3

first roll stand

4th

Operating side

5

second roll stand

6th

Receiving opening

7th

Receiving opening

8th

Chock

8.1

Roll neck

9

Chock

9.1

Roll neck

10

roller

11

Locking plate

12th

Locking plate

13th

Locking plate

14th

Locking plate

15th

Axial force measuring pins

16

Axial force measuring pins

17th

Axial force measuring pins

18th

Axial force measuring pins

19th

Measuring bolt nut

20th

Sleeve

21

cylindrical body

22nd

first thread section

23

second thread section

24

middle section

25th

Cross hole

26th

Longitudinal bore

27

Strain gauges

28

Pressure relief groove

29

Pressure relief groove

30th

Sealing seat

31

Sealing seat

32

electrical connections

33

Grooves

34

Grooves

35

Air game

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• CN 102327902 A [0004]
• CN 205413924 U [0005]

Claims (15)

Roll stand (1) for rolling a metallic rolling stock, comprising a first roller stand (3) arranged on a drive side and a second roller stand (5) arranged on an operating side, each of the roller 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 roller (10) provided with roller journals, at least two locking plates (11, 12, 13, 14) for locking the chocks (8, 9), one of the locking plates (11, 12, 13, 14) being arranged in this way on the end face of the respective roll stand (3, 5) remote from the roll is that it (11, 12, 13, 14) covers at least part of its receiving opening (8, 9), and is connected to the roll stand via at least one axial force measuring pin (15, 16, 17, 18) at least positively so that an axial force generated during a 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) from the respective axial force measuring pin (15, 16, 17, 18) is detectable. Roll stand (1) after Claim 1 , wherein each of the at least two locking plates (11, 12, 13, 14) is positively connected to the roll stand (3, 5) via the at least one axial force measuring bolt (15, 16, 17, 18) in such a way that each of the axial force measuring bolts (15, 16, 17, 18) is not preloaded. Roll stand (1) after Claim 1 or 2 wherein the at least one locking plate (11, 12) arranged on the drive side is designed to be non-displaceable with the drive-side roller stand and the at least one locking plate (13, 14) arranged on the operating side is designed to be displaceable. Roll stand (1) after 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. 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 than the axial force measuring pin (15, 16) arranged on the drive side. 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). 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) at least positively connected is. Roll stand (1) according to one of the preceding claims, wherein each of the axial force measuring bolts (15, 16, 17, 18) has a substantially cylindrical base body (21) with a first threaded section (22) arranged at a first distal end, with a , a second threaded section (23) arranged at a second distal end, as well as having a middle section (24) arranged between the first and the second threaded section (22, 23), the middle section having at least one radial transverse bore (25), which opens into a central longitudinal bore (26) of the axial force measuring pin (15, 16, 17, 18) and is provided with at least one strain gauge (27) on its outer surface and spaced from the at least one transverse bore (25). Roll stand (1) after Claim 8 wherein the at least one strain gauge (27) 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). 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. Roll stand (1) according to one of the preceding Claims 8 until 10 wherein the middle section (24) has a pressure relief groove (28, 29) running transversely to the longitudinal axis in the region of the at least one transverse bore (25). Roll stand (1) after 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. Roll stand (1) according to one of the preceding Claims 8 until 12th , wherein the axial force measuring pin (15, 16, 17, 18) comprises a sleeve (20) which is arranged on two spaced apart and circumferentially extending sealing seat surfaces (30, 31) so that the at least one on the outer circumferential surface between the two sealing seat surfaces (30, 31) arranged strain gauges (27) is hermetically encapsulated. Roll stand (1) according to one of the preceding Claims 8 until 13th , wherein the axial force measuring pin (15, 16, 17, 18) is formed from a chrome-nickel steel. Roll stand (1) according to one of the preceding Claims 8 until 14th wherein the first threaded section (22) has a larger diameter than the second threaded section (23).

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