DE1527734A1 - Rolling mill with a constant roll gap - Google Patents

Description

PATENT ENGINEERS F. W. HEMMERICH · GERD MÜLLER · D. GROSSE DÜSSELDORF 1, BERLINER ALLEE 34-36

SSE 20,986 June 28, 1966 rm.se 1527734 - E 1 -

United Engineering and Foundry Comp., Pittsburgh / USA

Rolling mill with constant roll gap

The invention relates to a rolling mill and, more particularly, to a rolling mill for producing rolled material, such as strip, Sheet metal or heavy plate which has a thickness that is essentially constant over its longitudinal direction.

Although the invention in connection with all types of multi-roll rolling mills can only be used for the purpose of description and explanation Four-high strip mill selected.

Much attention has been paid in recent years to the development of rolling mills for strip rolling, particularly four-high mills which are capable of producing a strip within very close tolerances along its length. Prior to the invention, the rolling mills were controlled by an automatic thickness control system. Although this system has been developed in a number of different forms, the most common form currently used operates on the principle of screwing the screws. This corrected the roll gap between the work rolls for changes in the elongation of the mill parts caused by changes in roll pressure that may result from variations in the hardness or thickness of the incoming strip. This change in the elongation or the elastic jumping of the rolling mill is dependent on the module of the rolling mill. An algebraic expression of this system is T = S ₀ + jr, where T is the runout _{thickness, S 0 is} the original thickness setting of the rolling mill, P is the rolling pressure and Mjj is the module of the rolling mill.

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Although this method of correcting for variations in the longitudinal thickness of the material has been successful, practical experience has revealed several serious limitations and disadvantages. One of these drawbacks can be observed by considering the above formula, noting that in order to obtain a constant T it is assumed that the mill modulus (Mj |) is constant. Based on this assumption, when the value T changes, the value S ₀ changes in order to compensate for the change in the value P and thus to keep T constant. It is known, however, that the mill module is only approximately constant and fluctuates to a significant extent under rolling conditions over most of the entire range and to a far greater extent under low rolling pressure conditions. This automatic thickness control system is not only subject to the fluctuations in the module of the rolling mill. It has been shown that other fluctuations are of equal importance, such as dynamic influences as a result of the change in the speed of the rolling mill.

These limits in the automatic thickness control system As opposed to this, various attempts have been made to improve their results. Three well-known methods They are all aimed at increasing the rigidity of the rolling mill and, accordingly, increasing the rolling mill module. This is of course beneficial because it relieves the automatic thickness control system in order to achieve uniform thickness will. These attempts can be briefly identified as follows:

1. Increasing the robustness of the rolling mill by increasing the dimensions of the rolling mill parts, all the more so are the limits of the fluctuations due to the elastic change.

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2. Pre-tensioning the uprights, screws, nuts and back-up roll chocks, through their legs or an equivalent device, under a pressure that is greater than the expected rolling pressure, which means that the! these elements are prevented by the module ii. with the exception of the legs of the back-up roll chocks as well as

3. the application of a preload pressure to some of the rolling mill parts, such as the stands, back-up roll chocks, Adjusting screws and nuts, with an essentially constant ratio at the same time upright between the forefront pressure and the Walzo loads is obtained, i.e. keeping the distance between the axes of the backup rolls constant. With this method is a changing preload pressure of a lest standing Maintain the relationship between the. Preload pressure and the rolling pressure, which actually affects the above-listed parts of the influence of the rolling mill module withdrawn and consequently results in a more rigid V'alzwerkskonstruktion.

Even with the use of the most advantageous varieties, nmß it should be noted that none of them have cracking due to back-up roll journal deflection or compression turns off the rollers, both factors contributing significantly to the overall jumping of the rolling mill.

With regard to the deflection of the back-up roll journals, it should be pointed out that any measurement of the rolling pressures, especially with regard to the last-mentioned method, does not reflect the vertical displacement of the rolls that control the roll gap _f this vertical displacement being caused by the deflection of the journals of the back-up rolls and the Influence that this has on the chocks of the back-up rolls. This bending naturally changes with different rolling pressures. It should be noted that with support

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roll deflection in this sense does not mean the deflection of the roll body, which is also under the applied pressure changes.

It is important to note that although the foregoing variations appear theoretically capable of To improve the uniformity of the tape thickness along its length, they have been used in practice with certain Forms an automatic thickness control in order to give the best result.

It is an object of the invention to provide an improved one Rolling mill in which the module of the work roll units is completely independent or isolated from the module of the rolling mill itself, the back-up roll chocks, the adjusting screws, the back-up roll units, etc., so that when compensating of the elastic fluctuations under the rolling pressures, the work roll units are the only parts that are taken into account Need to become.

Another object of the invention is to provide a rolling mill including a pair of work rolls and a pair of backup rollers, a device for adjusting one of the backup rollers so as to meet a given printing condition to be established and maintained between the work rolls and a separate and independent facility to adjust the gap between the work rolls of the rolling mill.

Another object of the invention is to additionally provide an auxiliary adjusting device for the work rolls to a primary adjusting device as it is provided for one of the backup rolls of a four-high rolling mill, wherein the backup roll engagement includes a quick response device for rapid actuation of the engagement.

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Another feature of the invention is in connection with a four-high rolling mill, which has a first adjustment mechanism for one of the backup roll units and a second adjusting mechanism for the work roll units, in one Control system for the automatic control and coordination of the two adjustment systems in order to meet a given printing condition establish and maintain between the work roll units.

It is the object of the invention to provide in a rolling mill: a pair of work rolls and a pair of backup rolls for the aforesaid Work rolls, a device for measuring the rolling pressures between the work rolls, a device independent of work rolls for adjusting the gap between the work rolls, a device through which a vorbestimrater Pressure is established between the work rolls in accordance with the measurement by the measuring device, and thereby said pressure is constantly maintained at a value which by an amount corresponding to said predetermined Pressure above the rolling presses Ii ^ t, whereby so-called Roll gap adjustment is maintained regardless of the changing rolling pressures, the latter device by one of said backup rolls for moving the backup rolls and their associated work roll in Direction to the other work roll and is actuated away from this.

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The aforementioned objects and advantages will become apparent as the specification progresses in conjunction with the accompanying drawings more clear.

Fig. 1 is an elevational view, partially in section, of a four-high rolling mill incorporating the features of the invention contains.

FIG. 2 is a partial cross-sectional view of the lower work roll shown in FIG.

FIG. 3 is a partial cross-sectional view of the upper work roll shown in FIG.

FIG. 4 is a plan view of the deployment of that shown in FIG Rolling mill.

FIG. 5 is a schematic of the control system for the one shown in FIG. 1 illustrated rolling mill.

Fig. 6 is an elevation, partly in section a second embodiment of the invention.

1 shows one of the two identical stand posts 11 a four-high rolling mill for rolling strip material. Given this equality, unless otherwise necessary, only the elements associated with one post are described. This rolling mill has of course many conventional parts, so that in certain cases specific Details of certain components are not given. The stand post 11 is seen with a window 12 / in which a lower work roll 13 supports the üit an upper one Work roll 14 cooperates with the lower work roll in the conventional manner by t-ine lower backup roll 15 and the upper work roll 14 is supported by an upper backup roll 16. Fig. 1 also shows that the working

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roll 15 has a chock 17, the work roll 13 a chock 18, the back-up roll 15 a chock 19 and the back-up roll 16 a chock 21. The work rolls 13 and 14 are held apart in the usual manner by piston-cylinder units 22 for work roll balancing. The upper backup roll 16 is pressed against the top of the rolling mill in a conventional manner a piston-cylinder unit for balancing, which is not specifically shown in the drawings.

The chock 19 of the lower backup roll 15 rests on a support 24 which is on the inner, lower surface of the Stand post 11 is mounted. The upper backup roll chock 21 is at its upper part with a recess 25 provided, which receives a thrust bearing 26, the upper part is detected by the lower end of a screw 27. The adjustment screw runs in a conventional manner a nut 28 contained in the upright post 11 with the upper end of the screw pointing towards the The upper part of the stand post protrudes, to which part a worm wheel 29 is attached, which is also shown in FIG is shown. Fig. 4 illustrates the upper part of the rolling mill, with both upright posts being shown and showing that the worm wheels 29 of each post are driven by worms 32 on opposite sides of the Rolling mill are arranged. The screws protrude in the direction of the front part of the rolling mill, on which gears

33 are attached, which are driven by screws not specifically shown, the screws to large Adjusting motors 34 are connected and the motors themselves are connected to one another by a coupling 36. The aforementioned Elements enumerated between the main adjusting screws and the motors 34 form the main adjusting device of the rolling mill.

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From Fig. 1 and additionally Fig. 2 and 3 it can be seen that in the chock 17 of the upper work roll 14 is a nut 41 is present, which receives a vertically arranged adjusting screw 42, the screws at its upper End has a spur gear 43 which engages in a pinion 44 which in turn engages in an outer spur gear 45. The lower End of the screw 42 protrudes below the lower surface of the chock 17 of the upper work roll 14 and is in contact with a load cell 48 which is located in an opening 47 of the chock 18 of the lower work roll 14 lies. The LastzeHe can be one of several well-known types who are able to run a stream to send out, which fluctuates according to the different pressures applied. Directly below the load cell 46 there is a spring 48 which engages the lower surface of the load cell 46 at its top and at its bottom a filling block 49 is also located in opening 47.

Man k; recognize that the gearbox is the load cell and the Fu; k-.rur: G * - ^s ': hin! ig for the right side of the work roll installation style IV mid 18 and that, as mentioned before, οϊ ·. ■ ·' : ■> c .'-: - '' Ii the. Arrangement exists for the Arbei.tswalzen- '^ i · :: ■;> ^*: \ ΐ3ϊ.β the other stand, With regard to the left ->^;:' n -Jo: - ^ s.. , I ^^ erks in Fig, 1 the bevel gear 4 * 3 is driven you? "·"; .-: ot: i'B ¥ elle 51, which has a missed end, an «is. · Kvgelruu -iß rv. if ^ enommeri is, The "JeIIe 51 runs through '! s? ο · .--: ν · -, ^ tsTf-lE ^ aeiiibaustück 21 of the upper back-up roll 18 irdf -'- elo t -; \ asr üffaiiag 52, ^ obei this opening i / s. Upper part v <r ^ - ^ öii.ert ISt ₅ in a spring 53 aufzTHioSmen, -which presses the shaft 51 to «', if ^ ars. The shaft 31 is connected via a coupling 54 in a second connection mxt similar shaft 55 which dur. ^ H of Stäiiderpfosten 11 zue over part of the rolling mill passes. On the upper part of the rolling mill above the upper surface of the main adjustment motors 34, a worm wheel 56 is attached to the shaft 55, which is driven by a worm 57 to which a motor 58 is connected,

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with the motor and worm wheel above the rolling mill a common stage 59 are supported. As FIG. 4 shows, there is one motor for each of the two pairs the worm gear and shaft arrangement for each stator post. These four arrangements make up the work roll adjustment.

It can be seen that when the rear end of the tape leaves the rollers, there is a tendency for the work rollers to fall Pressure come into contact, whereby there is a risk that some of the parts of the work roll units break. at Rolling mills that roll very thin material, it is possible to measure the corresponding parts so that they have a sufficient Have strength against the load caused by the coming together of the work rolls, and that they are thus able to withstand or absorb the shock of springback of the rolling mill without that the parts involved are overloaded. However, in rolling mills that roll thicker material, it is a The feature of the invention is to engage the spring 48 between the load cell 46 and the filler block 49, thereby causing damage of the work roll parts is avoided when the trailing end of the strip leaves the rolling mill. Through this the work rolls come together and absorb the shock caused by the reaction of the rolling mill.

Before describing the operation of the rolling mill, it may be correct to present the theory behind the Invention stands, to the extent that it is understood the manner in which the invention is used to achieve the Results described here works yi e mentioned earlier, the formula below gives the relative dependence between ien factors involved in controlling the Jandci. Ke but The longitudinal direction in today's automatic Jiexen control systems plays a role:

T s

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In this formula, the individual elements of which are defined on page 2, it is assumed that the rolling mill module is constant and, as mentioned earlier, the degree of success achieved depends on the degree of equality of the rolling mill module. With this in mind, the novelty of the invention can be noticed by comparing the foregoing formula with the formula characterizing the factors involved in practicing the invention. the

ρ
the latter formula can be expressed with T = S ₀ - ^ = ,

^M wr where T is the strip thickness, S _{0 is} the original setting of the work roll adjustment, P is the load on the work _{roll units and M wr is} the module of the work roll journals of a part of the work roll barrel, the work roll chocks, the work roll adjustment parts and load cells and springs. The use of the spring allows, in addition to the protective effect when springing back, the choice of such a module that the. most desirable control system can be used. Since the invention intends to keep ρ at a constant value, the formula can be expressed _{in a simplified form as T = S 0 -.}

Examination of the immediately preceding formula reveals one of the most important and novel features of the invention, namely that the module of the rolling mill itself "the back-up roll chocks, the roll deflection, the alzenaoilachung, not the module of the work roll parts My ₁ . It influences, but that they are independent of one another. This also means that the _{working rollers contained in M M} ^. \ e "i ht; u ^ bien-Kungen an leir. Main module of his rolling mill he, -ngen, with the exception of 'uni ^ er very -int-rgeo; dneter -eLund.s c · ';·>", -ϋ ^ s is also of importance' estzuste s len a *: · * - n.ihire les module« M _wr . the lurch ^r application ier? r 'n> is Ae ; ; i ■ · - iigesef-yt en ieder ',>ew> .rkt νινύ m- e. ι on the folding unit module Mm. % llgemeiß ögeuru »kr -ruhL the --r" olgreichrich operation of the here ies <hi *; ea «rt *" a. / works

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in the following: First of all, by turning the screws 42 in order to achieve the Desired measure for setting the original roll gap of the working rolls 13 and 14 by the working roll adjustment system, then in the application of a vernier pressure the load cells 46 through the adjustment for the back-up roll 16, which is the final roll gap of the work rolls established and thereafter in maintaining this nominal Pressure regardless of changes in the Walzdruek, by actuating the adjustment for the work roll that in turn keeps the roll gap of the work rolls constant. Thus, in this arrangement, the modulus affects the components of the rolling mill with the exception of the work roll unit and its adjustment in no way the control of the roll gap, which of course controls the uniformity of the strip to be produced. The effect is that of one almost infinitely rigid rolling mill, which in a real sense allows the roll gap between the work rolls to be kept constant. Because every change in the roll gap is precisely corrected the ribbon produced has a substantially uniform thickness over its longitudinal direction.

Fig. 3 shows a control system for the interrelation in Operation of the two adjustment systems, namely the adjustment system, which is assigned to the upper support roller 16 and the adjustment system, that cooperates with the upper work roll 14. The major parts of the rolling mill shown in Fig. 1 have been carried over to Fig. 5, although not in all of them Cases are marked as such, it being seen that the load cells 46 a signal via a line Lj with a; Generate value ρ. The signal from line Li will be one: Amplifier 61 is supplied, which sends a signal to a line L2 gives away. With regard to the line L2, it can be seen that the amplifier 61 converts the signal ρ into a signal which is indicative of a value S- that is sent to an amplifier 62 is transmitted. The amplifier 62 also includes

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a signal indicative of the factor "- which is generated by an amplifier 83, which receives an electrical signal indicative against a potentiometer 64 for the value of pi. As shown in FIG. 5, the potentiometer 64 is set manually, for example from the main control desk of the rolling mill.

YyLe signals §- and ~ - are carried to the amplifier 62 ^ «, where they are withdrawn and generate a signal,

the liennaeiehaead is for jr- ^, which has a line L4

¹⁰ Wr
eiaesi Servoyent.il 85 is supplied «The servo valve is at a standstill

ir .. YerüiiL-dung. or a hydraulic line L5 with a KoI-beriSylirnrfereiiüieit 66. which in turn moves the screws 32 and rotates the Zabiiradcr 33, what makes the main position "27 a triage" and thus the vb -; - rB Ä ^ 'jsitKwaiae 14 move vertically wis-d. Although the loj.he & tty lindere :; Jifeöii; 66 211 Fig., I cattle 4 "light shown :,: ./ ,. - verü.cehi Q> i siefc that aa j« aer Seh.neckenwelie 32 the • '■ -. ". ::: & €: ϊΐύ & der SolbfriiEylindereißhoit similar unit ββ '.-..-- ■ r - v, xi-j; t ±; ^ t Vi: rl da £ - the Well ^ ü relatively ku the gears ■: ·': * : j -.ii ^ r: - --z-ri'a'is köimt-B., against Bsi ^ egmiQ; in axial hich

€ _>"U'ih" η- 5 ^ h-

'-', The "Yy *; sign ■ • 'Wfc becomes, · '-. Bas • - / i! Found f. ' 67 .iuf- 1 oiißs a for youngsters '. J. '/ -f
• α _ ' . ·

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Value Tj, which is also fed to switch 69. Of the The purpose of the signal T ^ is the rapid separation of the work rolls to compensate when the front end of the belt enters the roller engagement, which will be explained in more detail later is explained.

As shown in Fig. 5, the amplifier 67 receives either a signal from the potentiometer 68 or 71 as a function on the position of the switch 69. The amplifier 67 adds those from the potentiometers 68 and 71 and from the line L3 values obtained and generated in a line

P P

neither a value T ₀ + «- or Ti + -n -. Each of these signals

^M wr * wr

is transmitted to an amplifier 72, which is a feedback signal received via a line L7, which is indicative of the actual roll gap setting of the work roll unit. The feedback signal is generated by a potentiometer 70 associated with one of the worm gear sets 56-57 which actuate the motors 58 of the work roll adjustment, thereby raising or lowering the screws and cause a change in the pressure reading of cells 46, which allows a corrective adjustment of the roll gap over the Back-up roll adjustment causes. It can be seen that when an X-ray system is used, it is completely automatic Control the switch system 69 is not used. Likewise, when the switch system 69 is used, there is no further change by the auxiliary control circuit as soon as the Signal Ti once caused a change in the roll gap.

A brief explanation of the operation of the one shown in FIG Rolling mill is now to be given. For the sake of completeness, a quick separation of the rollers should be used can be assumed through the leading end of the tape. Let us assume that there is no strip in the rolling mill, then the adjustment for the work rolls 13 and 14 actuated so that the upper work roll 14 relative to the lower roll is brought into a position in which the desired roll gap is obtained, in which the rolls are in contact with one another.

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tion may or may not exist. This adjustment of the upper work roll 14 is made possible by prior movement of the upper back-up roll 16. Although in this case the screws 42 abut against the cells 46, the pressure generated is nominal, the pressure initially on these cells being due to the adjustment of the back-up rolls is delivered. The backup roll adjustment then applies pressure to the load cells 46, operating the adjustment screw 27 until the load reading of a predetermined nominal reading is in about 50,000 pound ranges on each load cell. Before doing this, the potentiometers 64, 60 and 71 are set to the correct reading of the values P ^, T _Q and T ₁ . The switch Qd is enabled to receive the signal T ₀ which is set to anticipate the fact that the leading end of the strip will need a slight decrease in the roll gap in order to produce a substantially constant strip thickness at the leading end of the strip obtain. As soon as the front end engages the work rolls and pushes the rolls apart, the load cells 46 indicate a pressure drop and the signal ρ is picked up via the line L ^ by the amplifier 61, which generates a value ^ - by offsetting which is fed to the amplifier 62 via lines L2. here

pi

this value is offset against the value .JL., whereby

MwF

If χ is generated, a PIr ₈ S or minus value or

% r

May be zero, and when a signal is generated it is fed to servo motor 65 to actuate cylinder 66, causing the backup roll adjustment to bring the upper work roll toward the lower work roll, thereby providing the preselected nominal pressure of 50,000 pounds in each load cell is increased and restored. As soon as the order end of the strip enters the rolling mill, wj.rd Jer Ichalter 6 $ actuated and generates a signal T ^ in place of the signal T ₀ , whereby the signal ~ - the signal Ti lurch

^M wr ler; Amplifier 67 is added. This should result in a slight opening of the roll gap, caused by the one? *. Χ of the support roll adjustment.

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If the strip is thinner than the one that ran through the rolling mill during operation, the Load cells 46 cause an increase in the pressure reading, which as previously explained the employment for the back-up roll 16 upper work roll moved away from lower work roll restoring the preselected pressure reading. Fluctuations in the signal ρ on line L ^ like this from that

ρ amplifier 61 for generating a value -g- were received,

P Μ «» γ ·

are compared in amplifier 62 with the signal ^ A_, where ~

ρ% r

is generated - by a signal _B. The signal is transmitted

^M wr
device L4 to the servo valve 65, whereby the operation of the piston-cylinder unit 66 is triggered and the main or backup roller adjustment and the screws 27 are operated so that the backup roller is raised, whereby the initial pressure setting is maintained and a compensation is made for the running-in of a thinner strip into the rolling mill. In order to avoid any inaccuracy in the initial roll gap setting, the primary control for keeping the pressure constant can be monitored by a secondary control system. This could take the form of a thickness control system, but is not shown.

As mentioned earlier, Fig. 6 shows a second embodiment of the invention. It is considered unnecessary such Specify elements that correspond to the elements shown in FIG. 1. The embodiment of FIG. 6 differs from that of FIG. 1 in that instead of the mechanical adjustment for the support roller in FIG. 6 There is a hydraulic adjustment in the lower part of the rolling mill, which controls the movement of the lower back-up roll controls. In Fig. 6, for the purpose of description, the back-up rolls are identified by 74 and 75, the upper back-up roll 74 touches the upper work roll 76 and the lower backup roll 75 contacts the lower work roll 77. The lower backup roll 75 is provided with a chock 78, the lower surface of which is penetrated by the piston 79 of the piston-cylinder unit 81

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is detected with the cylinder 81 supported on the stand 82 will. The operation and results of the embodiment shown in FIG. 6 are similar to those obtained with the embodiment shown in FIG shown rolling mill are described. The embodiment of FIG. 6, however, has certain features that are common to certain Applications can be very desirable. A characteristic is the speed of action of the hydraulic arrangement, this being fast enough to accommodate a large percentage of the thickness variations due to rapid separation of the work rolls due to the penetration of the front end of the strip. The hydraulic arrangement can sense the increased rolling pressure and apply a corresponding pressure, resulting in a constant thickness Restoring the set value of the load cells is obtained.

Another feature resides in the fact that in the arrangement of Fig. 1 the work rolls by the pitch are loaded and therefore the operation is position-dependent, since to compensate for the fluctuations in the rolling mill elongation Movement of the screws is required. In the arrangement of FIG. 6, this influence is completely eliminated. There the hydraulic load on the work roll parts and the load on the cells depend only on the hydraulic pressure and since this pressure is independent of the position, the jumping of the rolling mill is automatically compensated for. Also depends Load on the cells from hydraulic pressure, which is a very fine control compared to the mechanical System enables, which is dependent on the control of the adjusting screw position, to keep the load on the cells constant to keep. Another feature of the embodiment in Fig. 6 is that the risk of cracking of the work roll parts reduced or eliminated as a result of their reaction when the trailing end of the tape passes through the intervention is. A hydraulic arrangement, as a result of its inherent rapid response, is fast enough to at least partially the rebound effect of the rolling mill on the working

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to reduce drum parts. However, as explained above, j protects a spring introduced into the work roll system protects the work roll parts against damage.

In accordance with the patent statutes, the principle and mode of operation of the invention was explained and illustrated and described, which is considered to be the best forms of training. It should be understood, however, that the invention should otherwise be within the scope of the appended claims can be realized than specifically illustrated and described herein.

-Al-

909805 / Ö002

Claims (13)

June 28, 1966 rm.se United Engineering and Foundry Comp., Pittsburgh / USA patent claims 1. In a rolling mill with a pair of work rolls forming a nip, at least one of which is of one Support roller is supported: Bearing chock units for the rotatable support of the ends of the said Rolling in the said rolling mill, a 'Talzspalteinstellvorrichtung, which between the bearing chock units of said work rolls is located and their bearing chock units detected and is able to an original Roll gap between the work rolls to produce a separate device from that mentioned Rolling mill is carried and through which one of the said support rolls to change the original Roll gap is adjusted, as well as a drive device carried by said rolling mill and by means of which said roll gap adjustment device is adjusted. - A 2 - 909085/0 062 20,986 June 28, 1966 _ rm.se 2. In a rolling mill according to claim 1, the pine backup roll for each work roll and wherein said device for changing the original roll gap consists of a mechanical adjustment which engages the bearing chock units of the uppermost backup roll. 3. In a rolling mill according to claim 1 having a backup roll for each work roll and wherein said roll Device for changing the original roll gap consists of a piston-cylinder unit, which is the bearing chock unit the lowest support roller detected. 4. In a rolling mill according to claim 1, wherein said adjustable nip device comprises: a A pair of screws rotatably mounted in the bearing chock units of one of said work rolls; the outer end of said screws being arranged to interfere with the bearing chock units of the others Work roll detected so as to establish the initial roll gap between the work rolls. 5. In a rolling mill according to claim 2, wherein said separate device is a fast response power device includes, which is operatively assigned to said mechanical employment. 6. In a rolling mill according to claim 1, wherein said roll gap adjustment means comprises: pressure sensing means to detect a change in the rolling pressure developed between the work rolls Control system for receiving a signal from the pressure oo filling device and wherein said control system of he. named separate device for the effective Q position of the support roller mentioned for maintenance ° a given printing condition between those mentioned fvj is assigned to work rolls. - A 3 - 20,986 6/28/1966 £ 0 Fm, se 7. In a rolling mill according to claim 4 including egg « ner pressure sensing device which is arranged in said bearing chock units of the other work roll and which can be detected by said screws and which shows a change in that between the work rolls developed rolling pressure, as well as a control system for the reception of a signal from the pressure sensing device, said control system of said separate device for the effective Adjusting said backup roller to maintain a given printing condition between said ones Is assigned to work rolls. S. In a rolling mill according to claim 4, wherein a pair of said screws are rotatable in each of the bearing chock units the uppermost work roll with a pair of pressure sensing devices on each of the bearing chock units the lowermost work roll is attached and can be grasped by the said screws, a A pair of gear sets mounted in each of the uppermost work roll bearing chock units and which cause the rotation of the screw with which they are associated, with a drive shaft passing through for each gear set the bearing chock units of the back-up roll runs, as well as a power device for the simultaneous drive of the called drive shafts. 9. In a rolling mill according to claim 7 including an elastic element for each Druckftih! Device that Mounted in the bearing chock units in the other work roll and through the pressure sensing device can be detected on the opposite sides of the screws mentioned. 909885/0062 -A4- 20 986 June 28, 1966 Z / l ^rm - ^se 10. In a rolling mill comprising: a stand, a window in said stand, a pair of work rolls with bearing chock units for rotatable mounting of the opposite ends of the work rolls in said window, a pair of backup rolls for each work roll with chock units for rotatably supporting their opposite ends in said window Window, a device between the work roll chock units for sensing a change in the rolling pressure developed between the work rolls during rolling, a device developed by is segregated from said backup roll-bearing chock units and that with the bearing chock units one of said work rolls for adjusting the gap between the work rolls can be detected, a Device between said upright and one of the bearing chock units of one of said back-up rolls, whereby a change in the gap between the work rolls can be effected by applying a pressure, by compressing the bearing chock units of said work rolls in such a way that at least a portion of the pressure is sensed by said sensing device, and a device for varying said pressure in response to a sensed change in rolling pressure, such that the pressure always exceeds the rolling pressure by a predetermined amount. 11. In a rolling mill having a pair of work rolls, said work rolls being rotatably supported in bearing chock units, one backup roll for each Work roll, said backup rolls being rotatably mounted in bearing chock units, a pressure sensing element between the bearing chock units of 909885 / Q062 - A 5 - 20,986 June 28, 1966 rm.ste Work rolls, which is a change in that between the Work rolls developed rolling pressure tracks, with the construction and the ratio of the rolling mill parts with regard to the location and operation of said pressure sensing device is such that depending on the elastic change of the rolling mill parts, the pressure sensing device is only subject to the elastic change of the work rolls and their bearing chock units. 12. In a rolling mill according to claim 10 including a pressurizing device by which a pressure is applied which constantly exceeds the rolling pressure by a given amount, and a control system for actuating said pressurizing device whereby said relationship between that applied Pressure and the rolling pressure when the rolling pressure changes is kept essentially constant. 13. In a rolling mill according to claim 10 comprising: an adjusting mechanism for adjusting the gap between the work rolls, a portion of which is included in the bearing chock units of the work rolls, said pitch mechanism being a resilient one There is a device by which the elastic stiffness of the work roll chock units is reduced is, the construction being such that the pressure sensing element also the elastic change of said Part of the adjusting mechanism and the elastic device is subject. - Kiule - 909885/0062 L e r s e i t e