Title of Invention	A METHOD FOR OPERATING A DEVICE FOR LOADING GUIDE SURFACES OF BEARING CHOCKS SUPPORTED IN THE HOUSING WINDOWS OF ROLLING STANDS
Abstract	ABSTRACT A device for loading the guide surfaces of bearing chocks (LS) supported in the housing windows (SF) of rolling stands with pressure plates (DP) that can be placed on the guide surfaces and that can be loaded by a hydraulic piston (K) supported in the rolling stand housings (ST), wherein devices for measuring the pressure and devices (WM) for measuring the displacement of the piston are assigned to the hydraulic piston (K) , and wherein the frictional force is eliminated by adjusting well-defined clearances between the bearing chocks (LS) and the guide surfaces. Figure 1

Title of Invention

A METHOD FOR OPERATING A DEVICE FOR LOADING GUIDE SURFACES OF BEARING CHOCKS SUPPORTED IN THE HOUSING WINDOWS OF ROLLING STANDS

Abstract

ABSTRACT A device for loading the guide surfaces of bearing chocks (LS) supported in the housing windows (SF) of rolling stands with pressure plates (DP) that can be placed on the guide surfaces and that can be loaded by a hydraulic piston (K) supported in the rolling stand housings (ST), wherein devices for measuring the pressure and devices (WM) for measuring the displacement of the piston are assigned to the hydraulic piston (K) , and wherein the frictional force is eliminated by adjusting well-defined clearances between the bearing chocks (LS) and the guide surfaces. Figure 1

Full Text	DEVICE FOR LOADING THE GUIDE SURFACES OF BEARING CHOCKS SUPPORTED IN THE HOUSING WINDOWS OF ROLLING STANDS The invention concerns a device for loading the guide surfaces of bearing chocks supported in the housing windows of rolling stands with pressure plates that can be placed on the guide surfaces and that are loaded by hydraulic piston-cylinder units installed in the rolling stand housings. Devices of this type are disclosed, for example, in EP 1 036 605 and EP 1 281 449, in which the hydraulic piston-cylinder units are installed in recesses of the rolling stand housing, and each cylinder-piston supports a pressure plate on its end face that faces the housing window and the given lateral guide surface of the bearing chocks. This device makes it possible, by varying the hydraulic pressure loading of the piston, to produce well-defined contact forces and thus frictional forces on the bearing chocks while bridging the working clearance, i.e., to predetermine well-defined contact forces and frictional forces, independently of the rolling conditions. As described in the above-cited document EP Patent 1 036 605, the contact forces give rise to frictional forces, which have the same line of action as the rolling force. Even when the contact forces are held constant, there is no guarantee that the frictional forces also remain constant, because the coefficient of friction between the contact surfaces of the bearing chocks and the housing window changes due to the changes in the surface quality. The surface of the contact surfaces becomes rougher due to corrosion, cooling water, or other abrasive substances. The coefficient of friction rises, and therefore the frictional forces T also rise and thus can be determined only inexactly. Regardless of whether the frictional forces can be determined or not, they have an adverse effect on the ability to regulate or automatically control the rolling stands. Consequently, the rolling force acting directly in the roll gap cannot be exactly determined. However, the current strip thickness in the roll gap can be computed by the gage control equation only from this force that acts directly in the roll gap. As a result, the strip thickness tolerances and strip flatness tolerances are difficult to maintain. The design solution according to the documents cited above also does not make it possible to determine where the center planes of the bearing chocks in the housing window are located with respect to a fixed plane and how the position of the center planes varies relative to this fixed plane. This deficiency also means that unintended crossing of the rolls relative to one other cannot be determined. The objective of the invention is to eliminate these disadvantages that impair the rolling process. This objective is achieved by assigning pressure-measuring and position-measuring devices that can be controlled by automatic controlling devices to each hydraulic cylinder. These automatic controls can operate in such a way that the piston maintains a predetermined position regardless of the force acting on it or in such a way that at a certain force acting on the piston, the piston is displaced and enters a different, specific position. The automatic controls can also operate in such a way that the bearing chock is pressed against a fixed side of the housing window with a certain force. The displacement sensor then shows no further changes. If the piston of the cylinder is then moved a predetermined amount in the opposite direction, then a well-defined clearance of the bearing chocks in the housing window will be established. This type of clearance adjustment can compensate the production tolerances of the different bearing chocks, the wear, and the housing constriction due to the rolling forces to be expected. As the result of the adjustment of optimum clearance, no contact forces of the piston come into play, and no frictional forces are produced which have a negative effect on the automatic controllability of the process. With the position of the housing window sides known, the position of the bearing chocks relative to a selected plane can be determined by the pressing and simultaneous measurement of the piston stroke made on the drive side and on the tending side of the rolls. If this position measurement is compared with previously stored position measurements, the wear on the housing windows and their mounting parts can be determined. If, as described, the piston is installed in such a way that two pistons are present per roll and they press against a fixed surface via the bearing chocks, the crossing of the rolls can be determined in this way. Evaluation of the measured values makes it possible to determine the position of all of the rolls relative to one another. If a piston is provided for each bearing chock on each side, the run-in side and runout side and the drive side and tending side, the rolls can be systematically crossed relative to one another by means of this position measurement. For example, the upper work roll and the upper backup roll can be set parallel to each other and crossed with respect to the lower work roll and the lower backup roll, which are themselves set parallel to each other. This crossing of the upper roll relative to the lower roll can then be used to influence the profile and flatness. With the use of this integrated position measurement, which measures directly in or on the moving members, the rolls can be exactly positioned. The invention is explained in greater detail with reference to the specific embodiments illustrated in the drawings. -- Figure 1 shows a schematic partial section through a rolling stand in a side view. -- Figure 2 shows the same type of partial section as Figure 1 but through a different rolling stand. -- Figure 3 shows a control diagram. As Figure 1 shows, the bearing chock LS for the horizontal roll HW is supported in the housing window SF between the two housing posts STl and ST2 of a rolling stand. In the left housing post STl, there is a piston-cylinder unit, which has a guide cylinder FZ and a piston K with a piston rod KS that moves in the cylinder. A pressure plate DP is supported on the end face of the piston rod KS in the left housing post STl. The piston K and piston rod KS have a central recess AS, into which extends a displacement sensor WM, which is mounted on the outer rear wall of the guide cylinder FZ. Hydraulic pressure lines HD, which have a pressure-measuring device (not shown), open into the guide cylinder FZ on both sides of the piston K. In the design according to Figure 2, which shows a four-high rolling stand with horizontal backup rolls SWl and SW2 and their associated work rolls AWl and AW2, guide cylinders FZl, FZ2, FZ3, FZ4, FZ5, FZ6, FZ7 and FZ8, which have the same design as the guide cylinder FZ in Figure 1, are installed on both sides of the rolls in both housing posts STl and ST2. All of these guide cylinders have a piston K, piston rod KS, and displacement sensor WM and can be pressure-controlled and position-controlled by means of pressure lines (not shown), which correspond to the pressure lines HD in Figure 1. A clearance gap SP is provided between the pressure plates DPI, DP2 and the bearing chock LSI and between the pressure plates DP7, DP8 and the bearing chock LS4. In accordance with the control diagram in Figure 3, each cylinder is moved with a valve until it reaches the predetermined position set value. If the adjustable force limit is reached during this movement, the operation is interrupted. The rolling stand designs according to both Figure 1 and Figure 2 with automatic control systems according to Figure 3 make it possible, as explained above, to determine and evaluate the position of all of the rolls of the stand relative to one another by means of pressing the pressure plates and measurement of the stroke moved in each case in selected stand sections and comparison of these measured values with previously stored values. List of Reference Symbols SF housing window STl housing post (left) ST2 housing post (right) LS bearing chock HW horizontal rolls FZ guide cylinder K piston KS piston rod DP pressure plate AS recess WM displacement sensor ES adjustable clearance HD (hydraulic) pressure lines SWl backup roll SW2 backup roll AWl work roll AW2 work roll LSI bearing chock LS2 bearing chock LS3 bearing chock LS4 bearing chock FZl guide cylinder FZ2 guide cylinder FZ3 guide cylinder FZ4 guide cylinder FZ5 guide cylinder FZ6 guide cylinder FZ7 guide cylinder FZ8 guide cylinder DPI pressure plate DP2 pressure plate DP3 pressure plate DP4 pressure plate DPS pressure plate DP6 pressure plate DP7 pressure plate DP8 pressure plate SP clearance gap CLAIMS 1. A device for loading the guide surfaces of bearing chocks supported in the housing windows of rolling stands with pressure plates that can be placed on the guide surfaces and that can be loaded by hydraulic piston-cylinder units supported in the rolling stand housings, wherein devices for measuring the pressure and devices (WM) for measuring the displacement of the piston are assigned to the hydraulic piston. 2. A method for operating the device specified in Claim 1, wherein the frictional force is eliminated by adjusting well-defined clearances between the bearing chocks and the guide surfaces. 3. A method for operating the device specified in Claim 1, wherein, by pressing the pressure plates against the bearing chocks and measuring the piston stroke towards the bearing chocks on the tending side and the drive side of the roll, the position of the roll is determined and stored, and then the wear on the housing windows of the rolling stand is determined by comparing the values with previously stored values. 4. A method for operating the device specified in Claim 1, wherein, by controlled pressing of the pressure plates against the bearing chocks on the tending side and the drive side of the roll, a crossed position is produced or changed, and the values are compared with previously stored values.

Full Text

DEVICE FOR LOADING THE GUIDE SURFACES OF BEARING CHOCKS SUPPORTED IN THE HOUSING WINDOWS OF ROLLING STANDS
The invention concerns a device for loading the guide surfaces of bearing chocks supported in the housing windows of rolling stands with pressure plates that can be placed on the guide surfaces and that are loaded by hydraulic piston-cylinder units installed in the rolling stand housings. Devices of this type are disclosed, for example, in EP 1 036 605 and EP 1 281 449, in which the hydraulic piston-cylinder units are installed in recesses of the rolling stand housing, and each cylinder-piston supports a pressure plate on its end face that faces the housing window and the given lateral guide surface of the bearing chocks. This device makes it possible, by varying the hydraulic pressure loading of the piston, to produce well-defined contact forces and thus frictional forces on the bearing chocks while bridging the working clearance, i.e., to predetermine well-defined contact forces and frictional forces, independently of the rolling conditions. As described in the above-cited document EP Patent 1 036 605, the contact forces

give rise to frictional forces, which have the same line of action as the rolling force. Even when the contact forces are held constant, there is no guarantee that the frictional forces also remain constant, because the coefficient of friction between the contact surfaces of the bearing chocks and the housing window changes due to the changes in the surface quality. The surface of the contact surfaces becomes rougher due to corrosion, cooling water, or other abrasive substances. The coefficient of friction rises, and therefore the frictional forces T also rise and thus can be determined only inexactly. Regardless of whether the frictional forces can be determined or not, they have an adverse effect on the ability to regulate or automatically control the rolling stands. Consequently, the rolling force acting directly in the roll gap cannot be exactly determined. However, the current strip thickness in the roll gap can be computed by the gage control equation only from this force that acts directly in the roll gap. As a result, the strip thickness tolerances and strip flatness tolerances are difficult to maintain. The design solution according to the documents cited above also does not make it possible to determine where the center planes of the bearing chocks in the housing window are located with respect to a fixed plane and how

the position of the center planes varies relative to this fixed plane. This deficiency also means that unintended crossing of the rolls relative to one other cannot be determined.
The objective of the invention is to eliminate these disadvantages that impair the rolling process. This objective is achieved by assigning pressure-measuring and position-measuring devices that can be controlled by automatic controlling devices to each hydraulic cylinder. These automatic controls can operate in such a way that the piston maintains a predetermined position regardless of the force acting on it or in such a way that at a certain force acting on the piston, the piston is displaced and enters a different, specific position. The automatic controls can also operate in such a way that the bearing chock is pressed against a fixed side of the housing window with a certain force. The displacement sensor then shows no further changes. If the piston of the cylinder is then moved a predetermined amount in the opposite direction, then a well-defined clearance of the bearing chocks in the housing window will be established. This type of clearance adjustment can compensate the production tolerances of the different bearing chocks, the wear, and the housing constriction due to the rolling forces to be expected. As the result of the adjustment

of optimum clearance, no contact forces of the piston come into play, and no frictional forces are produced which have a negative effect on the automatic controllability of the process.
With the position of the housing window sides known, the position of the bearing chocks relative to a selected plane can be determined by the pressing and simultaneous measurement of the piston stroke made on the drive side and on the tending side of the rolls. If this position measurement is compared with previously stored position measurements, the wear on the housing windows and their mounting parts can be determined. If, as described, the piston is installed in such a way that two pistons are present per roll and they press against a fixed surface via the bearing chocks, the crossing of the rolls can be determined in this way. Evaluation of the measured values makes it possible to determine the position of all of the rolls relative to one another. If a piston is provided for each bearing chock on each side, the run-in side and runout side and the drive side and tending side, the rolls can be systematically crossed relative to one another by means of this position measurement. For example, the upper work roll and the upper backup roll can be set parallel to each other and crossed with respect to the lower work roll and the lower backup roll, which

are themselves set parallel to each other. This crossing of the upper roll relative to the lower roll can then be used to influence the profile and flatness. With the use of this integrated position measurement, which measures directly in or on the moving members, the rolls can be exactly positioned.
The invention is explained in greater detail with reference to the specific embodiments illustrated in the drawings.
-- Figure 1 shows a schematic partial section through a rolling stand in a side view.
-- Figure 2 shows the same type of partial section as Figure 1 but through a different rolling stand.
-- Figure 3 shows a control diagram.
As Figure 1 shows, the bearing chock LS for the horizontal roll HW is supported in the housing window SF between the two housing posts STl and ST2 of a rolling stand. In the left housing post STl, there is a piston-cylinder unit, which has a guide cylinder FZ and a piston K with a piston rod KS that moves in the cylinder. A pressure plate DP is supported on the end face of the piston rod KS in the left housing post STl. The piston K and piston rod KS have a central recess AS, into which extends a displacement sensor WM, which is mounted on the outer rear wall of the guide cylinder FZ. Hydraulic pressure lines

HD, which have a pressure-measuring device (not shown), open into the guide cylinder FZ on both sides of the piston K.
In the design according to Figure 2, which shows a four-high rolling stand with horizontal backup rolls SWl and SW2 and their associated work rolls AWl and AW2, guide cylinders FZl, FZ2, FZ3, FZ4, FZ5, FZ6, FZ7 and FZ8, which have the same design as the guide cylinder FZ in Figure 1, are installed on both sides of the rolls in both housing posts STl and ST2. All of these guide cylinders have a piston K, piston rod KS, and displacement sensor WM and can be pressure-controlled and position-controlled by means of pressure lines (not shown), which correspond to the pressure lines HD in Figure 1. A clearance gap SP is provided between the pressure plates DPI, DP2 and the bearing chock LSI and between the pressure plates DP7, DP8 and the bearing chock LS4.
In accordance with the control diagram in Figure 3, each cylinder is moved with a valve until it reaches the predetermined position set value. If the adjustable force limit is reached during this movement, the operation is interrupted.
The rolling stand designs according to both Figure 1 and Figure 2 with automatic control systems according to Figure 3 make it possible, as explained above, to determine and evaluate

the position of all of the rolls of the stand relative to one another by means of pressing the pressure plates and measurement of the stroke moved in each case in selected stand sections and comparison of these measured values with previously stored values.

List of Reference Symbols
SF housing window
STl housing post (left)
ST2 housing post (right)
LS bearing chock
HW horizontal rolls
FZ guide cylinder
K piston
KS piston rod
DP pressure plate
AS recess
WM displacement sensor
ES adjustable clearance
HD (hydraulic) pressure lines
SWl backup roll
SW2 backup roll
AWl work roll
AW2 work roll
LSI bearing chock
LS2 bearing chock
LS3 bearing chock

LS4 bearing chock
FZl guide cylinder
FZ2 guide cylinder
FZ3 guide cylinder
FZ4 guide cylinder
FZ5 guide cylinder
FZ6 guide cylinder
FZ7 guide cylinder
FZ8 guide cylinder
DPI pressure plate
DP2 pressure plate
DP3 pressure plate
DP4 pressure plate
DPS pressure plate
DP6 pressure plate
DP7 pressure plate
DP8 pressure plate
SP clearance gap

CLAIMS
1. A device for loading the guide surfaces of bearing chocks supported in the housing windows of rolling stands with pressure plates that can be placed on the guide surfaces and that can be loaded by hydraulic piston-cylinder units supported in the rolling stand housings, wherein devices for measuring the pressure and devices (WM) for measuring the displacement of the piston are assigned to the hydraulic piston.
2. A method for operating the device specified in Claim 1, wherein the frictional force is eliminated by adjusting well-defined clearances between the bearing chocks and the guide surfaces.
3. A method for operating the device specified in Claim 1, wherein, by pressing the pressure plates against the bearing chocks and measuring the piston stroke towards the bearing chocks on the tending side and the drive side of the roll, the position of the roll is determined and stored, and then the wear on the housing windows of the rolling stand is determined by comparing the values with previously stored values.

4. A method for operating the device specified in Claim 1, wherein, by controlled pressing of the pressure plates against the bearing chocks on the tending side and the drive side of the roll, a crossed position is produced or changed, and the values are compared with previously stored values.

Documents:

0117-chenp-2008 abstract.jpg

0117-chenp-2008 abstract.pdf

0117-chenp-2008 claims.pdf

0117-chenp-2008 correspondence-others.pdf

0117-chenp-2008 description (complete).pdf

0117-chenp-2008 drawings.pdf

0117-chenp-2008 form-1.pdf

0117-chenp-2008 form-26.pdf

0117-chenp-2008 form-3.pdf

0117-chenp-2008 form-5.pdf

117-CHENP-2008 AMENDED PAGES OF SPECIFICATION 13-11-2014.pdf

117-CHENP-2008 AMENDED CLAIMS 13-11-2014.pdf

117-CHENP-2008 AMENDED PAGES OF SPECIFICATION 22-01-2015.pdf

117-CHENP-2008 CORRESPONDENCE OTHERS 12-09-2014.pdf

117-CHENP-2008 EXAMINATION REPORT REPLY RECEIVED 22-01-2015.pdf

117-CHENP-2008 EXAMINATION REPORT REPLY RECEIVED. 13-11-2014.pdf

117-CHENP-2008 FORM-1. 13-11-2014.pdf

117-CHENP-2008 CORRESPONDENCE OTHERS 08-09-2014.pdf

117-CHENP-2008 CORRESPONDENCE OTHERS 15-09-2014.pdf

117-CHENP-2008 CORRESPONDENCE OTHERS 02-09-2014.pdf

117-CHENP-2008 CORRESPONDENCE OTHERS 18-03-2014.pdf

117-CHENP-2008 CORRESPONDENCE OTHERS 18-08-2014.pdf

117-CHENP-2008 FORM-3 18-03-2014.pdf

117-CHENP-2008 FORM-3 18-08-2014.pdf

117-CHENP-2008 CORRESPONDENCE OTHERS 28-08-2014.pdf

117-CHENP-2008 FORM-13-19-08-2009.pdf

117CHENP2008-Petition for Form 3.pdf

117CHENP2008-Petition for POR.pdf

117CHENP2008-Petition for VET.pdf

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Patent Number

266045

Indian Patent Application Number

117/CHENP/2008

PG Journal Number

14/2015

Publication Date

03-Apr-2015

Grant Date

30-Mar-2015

Date of Filing

08-Jan-2008

Name of Patentee

SMS SIEMAG AKTIENGESELLSCHAFT

Applicant Address

EDUARD-SCHLOEMANN-STRASSE 4, 40237 DUSSELDORF,

Inventors:

#	Inventor's Name	Inventor's Address
1	BRANDENFELS, PETER,	AUF DER HUTTE 13, 57271 HILCHENBACH, GERMNY
2	BENFER, FRANK,	DITZRODER WEG 23,57334 BAD LAASPHE, GERMANY, GERMAN CITIZEN
3	KIPPING, MATTHIAS,	AUGUSTASTRASSE 10, 57562 HERDOFG, GERMANY

PCT International Classification Number

B21ZB3/02

PCT International Application Number

PCT/EP06/05485

PCT International Filing date

2006-06-08

PCT Conventions:

#	PCT Application Number	Date of Convention	Priority Country
1	102005026257.0	2005-06-08	Germany