DE2757831A1 - METHOD AND DEVICE FOR REGULATING THE ROLLED THICKNESS DURING ROLLING - Google Patents

Description

Cheyabinsky Politechnichesky ρ 66 364-M-61 Institut imeni Leninskogo komsomola December 23, 1977 Chelyabinsk / USSR L / Br

METHOD AND DEVICE FOR * THICKNESS CONTROL IN

ROLLERS

The invention relates to the compression deformation of Metals and relates in particular to a method for stripping

called-

thickness control for rolling and a device for it Execution·

The invention is particularly suitable for rolling mills

Shape as well as simple form for the production of sheet metal and strips "

profiles and tubes *

There are ready methods of controlling the thickness h ^ a strip emerging from the rolls and devices for their implementation known, c.ie on the relocation the chocks of one of the rollers in the regulating process with the help of power devices around the oscillation magnitude of the elastic deformation of the framework are based "

These include, for example, the procedures and the

♦) Rolling stock thickness control - i »following briefly 809828/0629

directions for the automatic regulation of the thickness h * of a strip, which were developed by the firms "Davy and United ¹ *," Zowy Robertson "," JHJ ", ^H Schloemann mag" and others ·

On known methods is at the case

game of a procedure that is included in the

GB-PS 1,194,328

ben is «This s jek & r. '. te procedure is coming

closest to the subject of notification * »and is _Λ χ ₀ Pr ₀ -. to type taken.

Eb becomes a force for the displacement of the roller bearings generated, which of its size oereteigt the rolling force

You leave this force on the roller bearings in the Attack way that this overcomes the rolling force, the * alzenlagerungen by the difference between said Force and the rolling force are offset.

Proportionally to this displacement one develops a force which the approach of the roller bearings, between which the deformation of the strip takes place, and compensates for the difference between the force displacing the roller bearings and the rolling force

By calculating the force for the displacement of the roller bearings as a function of the signal Δ of the error,

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which compared τοη the change in shape of the roll stand and the displacement of the roller bearings is proportional Signals result, change, move the roller bearings as long as the signal Δ dee error equals Mull, at which the influence of the change in shape of the framework eliminated the thickness of the strip emerging from the rollers is·

The realization of this procedure includes the following operations

1 · Measure the change in shape of the rolling stand Nuter load · For the determination of the rolling force P is carried out (by means of a compression coil located below the electrical Ifießdobe) and the subsequent Lrrechnung animal Formendciung S h * of Walzgerüfctee according to the relation

where κ is the Cteifckeitszehl des Walzgerüetee and P is the whale force «

2 · The mutual displacement of the roller chocks is measured · This is done with the help of a kit consisting of an oil can and a spring by measuring with the mefidose (by means of a liquid · ». pressure transducer) / The force R the hydraulic cylinder is first and foremost by calculating the increase in force Q of the spring force

809828 / 062Θ

after the relationship AO 2757831 stung the Relocation of - ΔΡ (2) after which O ⁿ 2 ■ · Chocks after the relationship ^K 1 _s Δ ^Η * Δ ^Ρ (3)

is calculated in which

ζ
K ₁ the stiffness steel of the spring (it can be any, ä> er

be known in advance),

ήΡ and & R the increases in the rolling force P and the, respectively
Force R of the hydraulic cylinder.

The calculation of the change in shape £ h * according to (1) and the displacements £ h ₂ according to (3) are made on the basis of electrical impulses with the help of special electrical executions.

3. The signals proportional to the change in shape ^ h _{1 of} the framework and the ver-2 of the chocks are compared with one another, and the difference between them is calculated

Δ = OV ₁ - Sh ₂ = A ^ * AR -A P

K ₁
or Δ = ΔΡ ( 1 ♦ 1 ) -AR. 1 (5).

For this operation, use is made of a special comparison unit for comparing the issues concerned

tric signals, and this creates an electrical signal A given the error according to the formula (5).

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When regulating the thickness h ^ of the strip, the value £ P is used as a display of the electrical load cell located under the pressure calculating screw and the value

Δ Η as a display of an electrical pressure transducer, «elcher on the manifold is provided, which is the tree of the hydraulic cylinder the liquid feeds. In a special electrical block electrical signals are formed »which Summands

κ K ₁ K ₁

represent, which are then used to generate the Signalee Δ des errors according to (5) are added in a summing block «Das Signal Δ of the error is amplified and sent to the control circuit for controlling an electro-hydraulic relief valve directed "

This takes care of the size of the signal Δ of the error electro-hydraulic relief valve for regulation (the opening and closing) of the liquid supply from a constant pressure source to the tree of the hydraulic cylinder, which generates the force R, under the action of which the chocks of the movable roller are displaced «

So the signal Δ of the error due to the displacement the chocks has become equal to garbage, set the fluid supply to the hydraulic cylinder and the relocation of the chocks, and the thickness of the strip reaches the specified value

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Accordingly, the adjustment of the strip thickness Iu based on the known method runs on the generation of signals that the elastic deformation of the whale frame and the displacement of the chocks of the movable Roller proportion ^ are based on the comparison of these signals and the receipt of signals of the displacement error the relocation of the chocks of the movable orphan through a force device in the form of a signal as a displacement error out ·

Thus, the regulation of the strip thickness h ^ begins the process taken as a prototype only after it has emerged of the signal Δ of the defect, i.e. when there is a thickness difference 5 "h of the strip is present, which has to be fixed later «

This fact has an unfavorable effect on the control accuracy, that is to say on the quality of work of the control system the end·

The known method is carried out with a device which consists of electrical load cells arranged under the pressure screws for measuring the rolling force P, hydraulic cylinders which are connected to a constant pressure source and which are used to move the bearings of one of the work rolls, elastic elements (a beams, £ ugstäbe, a spring), the position of the bearings of the zz offsetting roller is determined with the aid of.

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a load cell to measure the size Q of the tension of the elastic elements mentioned and the force R of the hydraulic cylinder, potentiometers for the previous setting of _{the rolling gap β h Q} »wipe the orphans not burdened with the whale force as well as to set the desired strip thickness, a summation electricity circle on the generation of the Signal δ dee error, which characterizes the difference in thickness O h of the strip, an »amplifier for amplifying the error signal ^and an electrohydraulic one

Relief valve suh transforming the electrical signals Δ

£ -17

the error that controls the flow of the liquid coming from the pressurized liquid source, ^ consists ^

Ee eel now pointed out the complexity of the devices executing the method mentioned, because in In these devices, the Wals force P is transformed into a change in shape dea Walsgerüatee proportions-lee electrical Signal, the force Q of the tension of the elastic elements in a proportional to the displacement of the roller bearings

and
lee electrical signal the electrical signal Δ dee error, which characterizes the difference in thickness O h of the strip, converted into liquid flow (pressure) (of

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Presuppose oil) · This reduces the reliability of the systems _f complicates their operation and increases the cost of the control systems «

The purpose of the present invention is to provide a method which improves the accuracy of the adjustment and which can be carried out by means of simpler and cheaper devices can be realized.

The invention is based on the object by changing the relationship between the for the displacement of the roller bearings required force and the rolling parameter to be measured as well as a change the design of the mefidose and the pressure setting valve of the liquid agent in the space of the hydraulic cylinder, a method for the control of the strip thickness hu and a device for its implementation

that develop the accuracy of the scheme

to shape, with the

the thickness h ^ of a strip improve

^Ί should be,

in the direction of operational reliability and structurally simple

and operating resources result in a liquid production cost

(01) as it is for conventional hydraulic cylinders

is used, allowed to be used and should be operable by personnel who are not highly qualified.

The ^e task ^is solved in a method for regulating the strip thickness during rolling between the rollers built into the frame of a rolling mill

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a force to move the bearings of one of the rollers, is generated, which is greater than the rolling force and acts on the bearings of the rollers in such a way that they control the rolling force overcomes, and the difference between the said force and the rolling force ^ move ^ the bearings of the roller allows, in proportion to this displacement, a force is generated which increases the approach of the roller bearings, between which the deformation of a strip takes place, prevents, and the difference between the force for the Offset of the bearings of the roller and the rolling force compensates, with the proportionality factor for the proportionality between the displacement of the bearings of the roller and the force, which is the difference between the force for moving the bearings of the roll and the rolling force compensates, previously given in a certain ratio to the rigidity number of the rolling device and the Force for the displacement of the bearings of the roller when forming the strip to compensate for the fluctuations of the Roll column is changed, according to the invention, the force for the displacement of the bearings of the roll in the course of the Deformation of the strip proportional to the rolling force the formula

R »K ₂ P,

is changed, where
B is the force required to move the bearings of the

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Orphan is required
F is the whale force and

starting from the relationship

is chosen, where

K _{1 is} the proportionality factor for the proportionality between the displacement of the roller bearings and the force that prevents the roller bearings from approaching, and

K is the rigidity number of the roll stand *

In a device for carrying out the method, which is arranged in the frame of a rolling mill, the one Stand with a built-in pressure device and rollers with bearings that are located in the lateral openings of the

Stator are arranged such that at least one roller can move in the rolling direction, includes, and of two, attached to the two sides of the framework and parts formed according to the same scheme, each of which has a pressure transducer for receiving the rolling force, at least one hydraulic cylinder, the space of which is used to move the bearings of the roller during the rolling process a pressure source of the liquid agent is connected, elastic elements of the device, which are arranged so

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27S7831

that they are the difference between that made by the hydraulic cylinder generating force and the rolling force accommodate a valve for regulating the pressure of the liquid agent inside of the cavity of the hydraulic cylinder, according to

with

the Krfindung as a pressure transmitter hydraulic load cells at least One cavity is provided each time are located between the bearings of one of the rolls and the stand, and the valves are proportional to the rolling force len

Control of the pressure of the liquid medium in the hydraulic cylinder

point
linderraum a housing with a slide housed therein, through which at least two cavities are formed, one of which is considered a valve control chamber, is connected to the cavity of the load cell and with this

while a closed bar with liquid medium forms, the other serves as a Ventlldrosselraum, with the hydraulic ^ linderraum and the t ^ ielle for the liquid funds in

flow connection stands and share a common space with the forms the means "

A rolling force occurs during rolling. As a result thereof turns out by the pumping system in the hydraulic cylinder, a pressure of the liquid agent A, which is proportional and also the rolling force ⁰¹ under the action of rolling force else pro-

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27S7831

proportional force for the displacement of the bearings of the movable roller is generated «Part of this force is expended for overcoming the rolling resistance, while the difference between the force of the hydraulic cylinder and The rolling force causes a change in the shape of the elastic elements mentioned of the device, so that the! «struggled move the movable roller by the amount of said change in shape · by applying the force of the hydraulic cylinder is adjusted so that the ratio between the deformation force of the elastic elements of the device and the rolling force is equal to the ratio between said number of rigidity of the elastic elements of the device and that of the elastic elements of the roll stand is, it is achieved that the elastic elements of the device to the deformation value of the elastic elements let deform the roll stand, so that the effect of the change in shape of the stand on the change the strip thickness is avoided when rolling between the work rolls

Such a technical solution, which implements the method ^{according to the invention, saves the electrical and electrical circuit in} the device, whereby the device is structurally simple and reliable,

and

low manufacturing costs are caused, the possibility of using a liquid agent (oil) with

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a degree of purification that is the same as for conventional hydraulic hydraulic cylinders is applied »is given and the

Perconal

direction of. with plate. · Qualification served can be"

Ee is here two-way that each hydraulic cylinder provided with a closed tree on the piston rod side is designed by the housing, cover, piston and piston rod and filled with liquid agent is, together with the elements of the hydraulic cylinder formed by said space, constitutes the elastic elements of the device that control the position of the bearings of the mobile orphan so that the device is more compact

It is also advantageous to design the slide of each valve for regulating the pressure of the liquid medium in the hydraulic cylinder chamber as a stepped slide valve which, together with the valve housing, forms an additional control chamber, and to connect the latter to the hydraulic cylinder chamber on the piston rod side, which is connected to the aforementioned

Control room forms a closed space, which mi ν

ge
the liquid agent is filled, which contributes to the rapid action of the device and an improved setting of the roll gap.

Ee is beneficial. in the closed piston rod side Hydraulic cylinder space to provide a spring,

098 28/06 29

which is supported with its ends against the piston of the hydraulic cylinder and against its cover and together ■ it the liquid funds as well as the closed piston rod side The elastic elements forming the hydraulic cylinder space and cooperating with the spring are the elastic elements Elements of the device represents what a desired stiffness number for the elastic elements of the Device allowed to choose

It is also expedient to connect the hydraulic load cell connected to the valve control chamber to the piston chamber of the hydraulic cylinder, which simplifies the device and contributes to its compact design

It is also advantageous to provide a spring in the piston chamber of the hydraulic cylinder, which is connected to the valve control and valve throttle chamber during the rolling process, which is supported against the piston and the housing of the hydraulic cylinder during the rolling process and to form an oil layer inside the piston chamber ¹ V, which is necessary for the actuation of the device, contributes

It is also useful to use the device with a to provide additional hydraulic cylinder with a cavity, which with the piston rodsvitigea hydraulic cylinder space is connected and with this forms a closed tree, which is filled with the liquid agent, and as

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elastic element of the device is used, so that there is the possibility of the desired ratio between the rigidity of the elastic elements of the device and that of the elastic elements of the roll stand au create"

further
UjB is appropriate »the piston chamber of the hydraulics ·

To connect the cylinder to the pressure source for the liquid medium via a control valve that has two end control chambers, of the soft one with the throttle chamber of the pressure valve and the source of oil for the liquid agent and the other with the constant pressure source in connection, what the Device easier and more compact to make «

The device is described below using the Regarding the

Exercise of exemplary embodiments explained with drawings, in shows

Fig «1 the roll stand of a rolling mill with the basic shell direction of the device}

2 shows the frame of a rolling mill on the operator's side with the control device according to the invention the strip thickness when rolling between the rolls with a section through the components of the device;

3 shows a section through the hydraulic load cell in its axial plane on an enlarged scale;

Fig. 4 with a Scmitt through the hydraulic cylinder two cylinder spaces in its axis plane on an enlarged scale j

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Fig. 5 is a section through the pressure control valve the liquid agent in the hydraulic cylinder space in its axis plane on an enlarged scale;

6 shows a section through a volume regulator in its axis plane on an enlarged scale;

7 shows the frame of a rolling mill on the operator's side with the device built into it to regulate the strip thickness when rolling between the rolls which of the slide of the valve is stepped, with a section through the components of the device;

8 shows a section through the valve for regulating the pressure of the liquid medium in the hydraulic cylinder space FIG. 6 in its achaenic plane on an enlarged scale; FIG.

Fig. 9 the hydraulic load cell and the hydraulic cylinder » designed as a hydraulic panel with a section through its axis plane

10 shows a modification of the hydraulic panel in which three hydraulic load cells and three hydraulic cylinders are provided with a section through the axis plane ι

11 shows a modification of the hydraulic panel with a Load cell and two hydraulic cylinders, in which the axis of the hydraulic load cell is in the axis of one of the hydraulic cylinders placed isu, with a cut through the plane of the common axis of the Mefldose and the hydraulic cylinder

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and through the plane of the axis of the "riding hydraulic cylinder"

12 shows a modification of the hydraulic panel with a Mefidoee in the middle and two hydraulic cylinders ie belt area Bit of a section through the axis plane of the hydraulic load cell and the hydraulic cylinder;

Pig · 13 the frame of a rolling mill on the operator's side ait the device built into it to regulate the strip thickness in the case of »rolls between the rolls, in which a reversing valve shown in longitudinal section is provided ι

Fig. 14 the reversing valve of Flg. 12 in enlarged « Mafistab;

Pig · 15 the frame of a rolling mill on the operator's side with the built-in device for regulating the strip dioke when rolling between the rollers that

provided with a hydraulic Mefidoee

is whose cavity with the piston chamber of the two-chamber hydraulic cylinder is united, and which has a hydraulically controlled reversing valve;

16 shows the valve for regulating the pressure of the liquid agent in the hydraulic cylinder space of FIG. 14 on an enlarged scale

17 shows the exchange valve of the Pig 14 on an enlarged scale

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The method according to the invention for strip thickness control is explained with the aid of a diagram shown in FIG Deformation of a strip takes place. The work rolls 3, 4 interact with support rolls 7t 8, which rest on the stand 2 via installation ^ -üoke 9t 10 and a pressure device 11. Hydraulic cylinders 12, 13 are provided for adjusting the upper work 3 and the upper support roller 7, each with the chock 5t 9. ^{A hydraulic cylinder 15t, which} has a movable housing 16, is used to move the chocks 10 of the lower support roller 8. Between the movable housing 16 and the stand 2 there are springs A which generate a force Q which prevents the approach of the rollers 3t ^ t between which the strip is deformed

Between the hydraulic measuring cell 14 and the hydraulic cylinder 15 there is a valve 17 for regulating the pressure of a liquid medium proportional to the force P, the flows from a pumping system 18 to the hydraulic cylinder 15

Invention when regulating the strip thickness II. after this

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- 19 -

According to the method, the rolling force F is from the cavity la "a" of the hydraulic Uefidoee 14 located liquid Medium (oil) added, with calibration the hydraulic Load cell 14 between the chock 9 egg upper support roller 7 and the pressure device 11 is »

The force R ₍ the 'secure chock 10 of the lower

4>

(movable) roller 8 can / shift is generated by the hydraulic cylinder 15, the space "b" with the pumping system 18, which converts the liquid under pressure, _communicates "To satisfy the relationship R = kgp is the pressure at the outlet of the Pump system and therefore the pressure of the fluid in the hydraulic cylinder chamber 13 proportionally to the rolling force P set by the valve 17. For this purpose, the "control chamber" d "of the valve 17 is connected to the ^{chamber" a n of} the hydraulic load cell 14 and the throttle chamber "θ" with the space "b" of the hydraulic cylinder 15 and the pumping system 18 ·

When rolling a strip developed in the control space ⁿ d ^N of the valve 17, a fluid pressure "q ^11, which from the equation

q = P (6)

is determined, where
Le area of the KoIb
The pressure "q" acts on the piston of the valve 17 _v "

F_ is the area of the piston of the hydraulic load cell 14

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.90.

A fluid pressure q ^ develops within the throttle space "e ^{H, which corresponds to the equation}

Q ₁ = q k ₃ (7)

met, where

Κχ Gain factor of valve 17 is «

As a result, the hydraulic cylinder 15 generates a force equal to R ag ^. F _fe is (8),

where Fw is the area of the piston chamber of the hydraulic cylinder let «

By using the values a for the pressures q and q * are used according to (6) and (7), one finds the Relationship between the forces R and P *

R a K _z . ^g b . P a K ₂ . P (9).

^F a

According to the method according to the invention, the

Parameters for the hydraulic load cell 14, the hydraulic cylinder 15 and the valve 17 selected in such a way that

K ₂ * K _x . ^ b \ 1 (10)

1st. Here, the force R is greater than the rolling force P by the value (K ₂ - D.InfolEedeccen, the force H overcomes the force P when it increases by Δ Pi, the chocks 5t & the rollers 3, 4 / approach each other and thus compensates for the elastic change in shape of the roll stand 1, which is caused by the deviation of the rolling force from Δ P> 0. When the rolling force P decreases by the value Δ P> 0

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-21 -

The Hegelunge process runs in the same way, however in the opposite direction from "

The force Q _9, which prevents the bearings of the rollers 3, 4 from coming closer, is generated, for example, by means of a set of springs A ₁ located between the movable housing 16 of the hydraulic cylinder 15 and the stand 15, by compressing them during the displacement of the movable housing 16 of the hydraulic cylinder generated by the value ο hg

In the case of the coefficient of rigidity K ^ of the springs A, the force Q of the compression la course of the displacement of the chocks 10 of the orphans 8 changes by the amount S hg according to the law

q * K ₁ · Sh ₂ (11)

In order to avoid the influence of the elastic deformation of the roll stand 1 on the thickness h ^ of the strip, the coefficient K _{2 should be} the equation

K ₂ * * 1 ♦ 1 (12)

fulfill.

By applying the force (4 based on the deformation of the springs A. from the static equilibrium of the movable housing 16 of the hydraulic cylinder 15 without taking into account the losses by the friction of its moving parts after the relationship

Q »R- P * (K ₂ -D. P (13)

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is determined, one finds the displacement size of the installation pieces 10 of the movable roller 8 as follows

* ^R " ^F = P

Accordingly, shift in the inventive

the chock 10 would always be required during the regulation around the deformation value h «. of the frame 1, so that the Strip thickness h ,. constant in the event of deviations in the rolling force F; remain.

The aim of the invention, namely a better accuracy of the regulation of the strip thickness during the deformation with the aid of a simpler and cheaper device, the following is achieved.

A change in the deformation force P, for example, as a result of a change in the physicochemical properties of the strip and therefore a change in the force H a kg · P of the hydraulic cylinder 15 causes the displacement &? Chocks of the lower back-up roll 8. Complete here the displacement of the chocks 10 and the change in shape of the roll stand 1 at the same time, their Sizes are also the same. As a result of this, the strip thickness remains h «. unchangeable, i.e. the difference in thickness of the strip oh over the entire length is equal to zero

Various exemplary embodiments are given below

explained. Since the device calibrates from two

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composed of the same scheme executed parts, only a part of the device is described and shown in the drawings, which is arranged on one side of the stand 1 of a rolling mill which, as already mentioned, has a stand 2 (Fig. 2) in which seitrchen openings work orphan 5> 4- arranged which rotate in Einbaustükken 5, 6 and between which there is the deformation of a strip "the work rolls 3, 4 act bit support rollers 7 _t 8 together, which filnbaustücke 9i 10 and a pressure device 11 on rest on the stand 2 «For adjusting the upper work roll 3 and the lower back-up roll 7, there are two bits for each of the chocks 5 and 9, there are hydraulic cylinders 12, 13«

The device for regulating the strip thickness comprises a number of structural units

Such structural units include hydraulic keßdosen 14 with a cavity ⁿ a **, which is filled with a liquid agent for absorbing the rolling force P, for which they are located between a pressure screw 11 and the chock 9 of the support roller 7 (Fig «2); On the stand 2 is a two-chamber hydraulic cylinder 15 with a piston chamber "b" under the chock 10 of the support roller 8 for generating the force R, which is necessary for the displacement of the chock 10 together with the rollers 4, 8, and a closed one Rod-string tree ⁿ C ^w , with a liquid

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Means of developing the force q filled iat by which the displacement of the movable housing 16 of the hydraulic cylinder 15 is prevented, provided

Between the hydraulic load cell 14 and the hydraulic cylinder 15 there is a valve 17 for pressure control (Flow rate control) of the liquid medium, which is from a pumping system 18, which bycL il'ven electric motor

ta
19 is taken, the piston chamber ¹ V of the two-cylinder hydraulic cylinder 15 flows; the valve 17 has a control chamber ^N d ^H , a throttle chamber "e" and an evacuation chamber "f ^H.

The device also has oil volume regulators 20, 21, the cavities "g" and "i" of which each correspond to the piston chamber "b" and the piston rod side space "C" of the hydraulic cylinder 15 to adapt the stiffness number k ^ of the elements of the device (a more precise definition of this The assembly of the device is listed below) to the rigidity factor k ^ of the roll stand.

On the hydraulic lines of the device there are check valves 22, 23, shut-off valves 24, 25 for the air or Oil outlet into a container 26, a valve 27 for the two sides of the frame 1, which is used for limiting the

and

Minimum pressure of the pumping system 13 is a safety valve 28 intended to limit the maximum pressure of the pumping system 18 · Serve for both sides of the frame 1 the oil tank 26, a pumping system 29 with an electric

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Motor 30 and a valve 3I for maintaining a constant pre-pressure within the cavities ⁿ c ^{n of} the hydraulic cylinders 15.

The hydraulic load cell 14 (Fig. 3) includes a housing 32, a piston 33 and a cover 34, which is on the housing 32 by means of screws 35. Look is "The housing 32 and the piston 33 form ⁿ a cavity a ^H _v with a guided in the housing 32 to channel "a ^ ¹ * communicates · hermetic sealing is ensured by (in the drawing not shown) glands" the between the pressure device 11 and the chock 9 located hydraulic load cell 14 (Pig x 2) acts by its Piston 33 old of the pressure screw 11 "and through the housing 32 with the chock 9 of the upper support roller 7 together"

The hydraulic cylinder 15 (FIG. 4) has the housing 16, a piston 36 and a cover 37t which is fastened to the housing 16 by means of screws 38. The piston 36 together with the housing 16 forms the piston space "b" and together with the Housing 16, the cover 37 and the rod 39 of the piston 36 the piston rod-side space "c" · The trees "b" and "c" are in each case with the channel "b ^" and ¹¹ C ₁ "in connection. The closure of the spaces "b ^M and ⁿ c" is brought about by seals (not shown in the drawing). The hydraulic cylinder 15 (FIG. 2) is located under the chock 10 of the lower support roller 0 and acts through it

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Housing 16 "with the chock 10 of the lower support roller and together with the stator 2 through the piston 36 «

The valve 17 (Fig. 5) has a housing 40, a slide 41 and a cover 42, which is attached to the housing 40 by means of screws 43 «The slide 41 forms with the housing 40 a control space" d ^H , with the cover "+ 2 a throttle gap "y" and a cavity "e" and with the housing 40 and the cover 42 an emptying space "f ⁿ The cavities are each with the channels d ^, β * and tj. la connection "The closure of these cavities d, e, f is secured by means of seals (not shown in the drawing).

The oil volume regulator 20 urri 21 (Fig. 6) are designed according to their design equal · Each of the above-mentioned cones has a housing 44, inside which a piston 45 with a helical rod 46 is housed, and one

brush with screws 48 on housing 44, cover 47 « The piston 45 and the housing 44 form a cavity ** g " from which is connected to a channel "g ^ ** · The hermetic Sealing is achieved by means of seals (not shown in the drawing) «

The other components of the device, such as the valves 27 (Fig. 2) and 31, the shut-off valves 24, 25, the check valves 22, 23, the safety valve 28, the pumping systems 29, 18 bit the electric motors 30 and 19, the

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Containers 26 are common designs in the industry. · There-

required
their detailed description.

The hydraulic coupling between the on the roll stand 1 arranged assemblies is accomplished as follows «

The cavity "a ⁿ of the hydraulic Meädose 14 (j g x 2) is by means of a hydraulic line 49 to the control space" d "of the valve 17 in connection · For the filling of the cavities" a "and" d ⁿ with the Ol these are by means of a Hydraulic line 50 connected via the check valve 22 with the cavity "f ^{N of} the valve 17 * When the device is in operation, said cavities form the closed space" a - d " ₉ in which the oil pressure of the rolling force P is proportion 1 * This pressure acts on the Slide 41 of valve 17 on the side of cavity "d" a ·

The piston space "b ^{H of} the hydraulic cylinder 15 is connected at the same time with the aid of hydraulic lines 51, 52 with the pumping system 18 and the cavity" e ^{M of} the valve 17. The pressure within these cavities develops as a result of the resistance to the flow of the oil from the cavity "β" through the gap "y" into the emptying space "f" of the valve 17. This pressure acts on the slide 41 on the side of the cavity "a" and

from compensates for the pressure on slide 41 pages of the cavity "d" acts to change the stiffness number of the two-chamber hydraulic cylinder 15 and thus the steep

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figkeitszahl K of the roll stand 1 is the piston roughness "b of the hydraulic cylinder 15 by means of the hydraulic lines 51 and 53 with the cavity "g" of the oil volume regulator 20 tied together.

The piston rod side · space "c" of the two-chamber hydraulic cylinder 15 is connected by means of a hydraulic line 54; a cavity "i" of the oil volume space 21 "For the filling with the oil, these cavities are connected to a hydraulic line 55 via the check valve 23 to the pumping system 29" When the device is in operation, these cavities form a closed barely ^N C - i ", in to which the oil pressure of the displacement of the housing 16 of the two-chamber hydraulic cylinder 15 is proportional "

The elements of the two-chamber hydraulic cylinder 15, those of the oil volume regulator 21 and the hydraulic line 54 through which the closed space is formed _y as well as the oil contained therein form a group of elastic elements of the device with the stiffness number ¹¹ K ^ "when the device is in operation. the end"

The emptying space "f ^{H" of} the valve 17 is connected to the container 26 with the aid of hydraulic lines 5 & i 57 intended"

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The division of the device takes place as follows.

By actuating the electric motors 30, 19 of the pumping systems 29, 18, a pre-pressure builds up in the assemblies of the device Check valve 23 under a pressure "^ ₀ " in the tree * 'c - i ^N promoted · The pressure "o ^" is predetermined by the valve 31 and is always kept constant by this into the container 26, if necessary the air or oil is drained from the mentioned cavities and hydraulic lines into the container 26 via a hydraulic line (not shown in the drawing) by opening the shut-off valve 24.

From the pumping system 18, the oil that reaches there under its own weight via the hydraulic line 60 from the container 26 is conveyed via the hydraulic lines 52, 51 to the piston chamber "b" of the two-chamber hydraulic cylinder 15 and to the throttle chamber "e ^{n of} the valve 17 flows through the gap "y ^M between the slide 41 and the cover 42 into the emptying space" f "and then comes via the hydraulic lines 56, 50 and the check valve 22 into the bar between the cavity ** a - d" and the Hydraulic line 49 is formed.Sin excess oil flows through valve 27

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and the hydraulic line 57 into the container 26. in the If necessary, the air and the oil from the specified Cavities and hydraulic lines are drained into the container 26 via a hydraulic line (not shown in the drawing) by opening the shut-off valve 25 The safety valve 28 is set to the highest possible pressure value of the pumping system 18

The pressure value ^M q ^ ^H is pre-determined by the valve 27 and selected so that the piston 33 of the hydraulic load cell 14 and the piston 36 of the two-chamber hydraulic cylinder 15 Ib are locked in the starting position (in front of the rollers).

Accordingly, the pressure "oV * should have the following relationship

q ₀ Jc _> <l ₁ > Jo (15),

^F b ² * a

meet, where

H _{Q is} the pressing force of the upper backup roll 3 and the upper work roll 7 on the hydraulic load cell 14 thanks to the hydraulic cylinders 12, 13,

F is the area of the piston 33 of a hydraulic load cell 14, Fx. the surface of the piston 36 of the hydraulic cylinder 15

the side of the hydraulic cylinder space (b) and F the surface of the piston 36 of the hydraulic cylinder 15 the side of the hydraulic cylinder space "c".

The print size "^" corresponds to the lower limit value

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the rolling force, after which the device begins to regulate the strip thickness "

By changing the position of the piston 45 (FIG. 6) with respect to the housing 44 in the oil volume regulator 20, the desired stiffness number "K" is set for the roll stand 1 (* 'ig · 2), which depends on the elastic behavior of the stand 1 of a rolling mill as well as that of the assemblies of the device, such as hydraulic drainage box 14 including the oil and hydraulic cylinder 15 in the cavities "b", ⁿ g ^M , "e ⁿ and hydraulic lines 51 ^{located in the cavity" ad w and the hydraulic line 49} , 52, 53 depends on the oil.

The rigidity number "K ₁ " for the elastic assembly of the device, consisting of the elements of the hydraulic cylinder 15 and the elements of the oil volume regulator 21, as well as the hydraulic line 54 with the oil contained therein, is predetermined by the oil volume regulator 21 «The rigidity number" K ₁ " one brings with the stiffness number of the framework according to the following equation

K ₁ a K. (K ₂ - 1) (16)

in line, being

the proportionality factor for the proportionality between the changes in the rolling force P and the force R of the hydraulic cylinder 15 1st, which emerges from the Glein » decision for the scheme

■ AP - AR - AP a 0 (17) XE ₁

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- 32 -

results

The consequence of the pre-pressure in the assemblies of the device is that the piston 33 (* 'ig · 3) of the hydraulic measuring doses · 14 on the cover 34 thanks to the difference between the force generated by the pressure "q ^" in the cavity " a ^{H of} the hydraulic load cell 14, and the pressure force "^ ₀ " of the pressure of the chock 9 (Fig. 2) on the hydraulic let socket 14 by means of the hydraulic cylinder 12, 13t ^and the piston 36 of the two-space hydraulic cylinder 15 at the bottom of the housing 16 thanks of force 5J ₀ ♦ G-IL ₁ , where

= q ₀ . F ₀ (18) and

aq _v F ₀ (19)

are where

G is the weight of all rollers including the film components, taking into account the thrust of the hydraulic cylinders 12, 13,
stay pressed.

Thus, the lower rolls 4, 8, which rest on the hydraulic cylinder 15 via the chock 10, and the upper malts 3 »7» those over the lüinbuuatück 9 on the hydraulic load cell 14, locked in the starting position

The pressure device 11 is used to adjust the original gap "h ₀ " between the waI- «e * 3i 4.

This roll gap is according to the equation

R O Π B 2 Π / O 6 2 Π

M ₀ «h - ² * o * V ^g (2 °)

determined, where

when exiting from the Ht the desired thickness of the strip is rolling

The device works as follows »

By posting a strip in the gap between the rolls 3 and 4 (Fig. 2) of the stand 1 of a rolling mill a rolling force develops P

As a result of this rolling force experience the elements of the frame 1 including the hydraulic load cell 14 and of the hydraulic cylinder 15 "an elastic change in shape, whereby the roll gap is changed"

The size of the roll gap increase S h _Q as a result of the deformation of the stand 1 depends on the gate pressure size "q ₀ ^{H of} the oil in the cavity" c - i "and is equal to the size of the change in shape of the Uerüstes 1, which is caused by the rolling force P, which the Oil pressure "q ^" in the hydraulic keßdose 14 corresponds, is caused «

(21).

The further increase S h ^ in the change in shape of the frame 1, which is caused by a change a P of the pressure P of the metal against the rollers with respect to the size 2q _Q. F _& G can be caused by the displacement of the chock x 10 of the orphan 8, hereinafter referred to as displacement

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of the housing 16 of the hydraulic cylinder 15 designated, balanced , ·

Correspondingly, the thickness is «Ines from the framework 1 the exiting strip

n. * h. + _ ο a _{(22) β}

? At the time of the rise d 3 oil pressure in the cavity ^w a ⁿ of the hydraulic load cell 14 as well as in Steuerraua » 'i of the valve ⁿ 17 closes the check valve 22 and forms a closed space" cavity "a" of the hydraulic load cell 14 - control space "d "of the valve 17 (the cavities a - d) with an oil pressure" q "which is the rolling force F propertiofia-l, thus

9, ■ P ♦ ^M o (23).

Due to the effect of this pressure within the control chamber "d ^{w of} the valve 17, the slide 41 (FIG. 5) is out of balance. It moves in the direction of the cover 42 and leaves the gap" y "between the slide 41 and the Reduce cover 42 _# Here the resistance of the oil flow from the throttle space "e" through the gap "y ^N to the evacuation space" f ^H increases and consequently the pressure of the pumping system 18 increases (FIG. 2).

As soon as the pressure of the pump system 18 has become higher than the value “q ^ **, a force Rs q ₂ · Έ · ^ _{9 develops in the piston chamber“ b ”of the two-chamber hydraulic ayliner 15}

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on the piston 36 and the housing 16 acts «A part of this force (q · 2F _& ) serves as the rolling force F and for balancing the weight“ G ^{n of} the rollers and the chock ”, while the difference in force (RPG) at the Group of elastic elements of the device engages

As soon as R has exceeded the rolling force P and the force ^ ₀ , which is generated by the oil pressure "q" in the piston rod-side space "c" of the hydraulic cylinder 15, the displacement of the housing 16 with respect to the piston 36 begins piston rod side space ** e ^H , which compresses the oil located therein and consequently an increase in the oil pressure within the piston rod side space ^M c "of the hydraulic cylinder 15 and within the cavity" i "of the oil volume regulator 21 causes« As a result, the check valve closes 23 and forms an enclosed space *.

- Space c on the piston rod side of the hydraulic cylinder 15 * Cavity i of the oil volume regulator 21 (the spaces c- i)

To the size of the oil compression in the said

one ..
closed space, displacement of the housing 16 of the hydraulic cylinder 15 takes place together with the chock 10 of the lower support roller 8.

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The pressure increase of the pumping system 18 during the control of the strip thickness when rolling between the rolls can be explained by two reasons "

First, the pressure corresponds to the pumping system 18

and

not the pressure in the closed barely "a- d", secondly, there is a resistance to the rolling force P and the force Q of the oil compression in the closed space "c - i **, the one displacement of the piston under the action of the

at the pressure of the pump system 18 prevents proportional force R

The housing 16 therefore moves with respect to the piston 36 until the slide 41 is caused by the oil pressure in the control chamber “d ⁿ and in the throttle chamber“ e ”of the valve 1? And the housing 16 of the hydraulic cylinder 15 is caused by the force acting on one side R as well as by the rolling force P acting on the other side and the force Q of the oil compression in the closed space "c - i" are brought into equilibrium

one

Waltzes) due to its equilibrium in stiffness a number K ^ of the closed space "c - i", according to the formula

8 * 2 " RP -So - ^G (24)

^K 1
determine.

By substituting the value for ^ in equation (24)

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is the "is determined moment of the onset of the rolling force" where ^{p is} ₀ ^{5 2} I ₀ · ^F _a "starting from de · balance of the housing of the hydraulic cylinder 15 i ^G and ^the force ^R _o = ² <lo * ^F t>^{are" aleo}

Q ₀ ^{a fi} o - ^P o - ^G <25>

one sets the replacement of the housing 16 of the hydraulic cylinder 15 depending on the increases Δ Β and δ Ρ after the equation

8 * 2 * AH - AP (26)

Ej

Ej

Here, the general change in the roll gap es and consequently the change in the strip thickness ^with regard to the displacement quantity Sh _{2 can be given} by the equation (17) <5 * »- ^A? AR - AP . ₀ (17)

KK ₁

describe, while the thickness h «. of the emerging from the frame 1 titreifens through the transfer

Β Ρ ₍₂₇₎

KKK ₁

is expressed "

In realizing the relation (16) between K

and K ₁ is the right part of equation (17) equal to Mull

a t-

Consequently, there remains a change in the roll gap and the

Stripe _{thickness h 1} when shaping the framework <| locked out"

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When operating the device according to equation (17), an absolute mechanical rigidity value of the system "scaffolding device" is achieved at Sh = 0, whereby the influence of the elastic deformation of the scaffolding 1 on the strip diclce Vei the change in the whale force la range

P> 2q ₀ . F _a - G (23)

is completely switched off

When the slide 41 of the valve 17 is in equilibrium, the oil that is conveyed by the pumping system 18 flows out of the throttle chamber "β" through the gap "y" (FIG. 5) in the fiitleerungsraum "f" and then on via the valve 2 ? in the container 26 (Fig. 2).

When the strip emerges from the rollers of the stand, the oil pressure inside the closed tree ⁿ a - d "drops to the original value q *. The pumping system 18 also develops the same pressure.

Here come the piston 36 of the hydraulic load cell 14 and the housing 16 of the two-room hydraulic cylinders 15 back to the starting position «The pressure within the closed itaumes "c- i" is also equal to V ",

The device is now ready for the following work.

To increase the rigidity of the elastic elements of the device is inside the closed piston rod

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mutual space "c ^{n of} the hydraulic cylinder 15 a spring 61 (Fig. 4) is provided, which is supported with its ends against the piston 36 and against the cover 37 and together with the liquid agent and the closed piston rod-side space" c "forming elements represents the elastic elements of the device "

The guide 61 present in the space "c" on the piston rod side helps _{to select the desired stiffness number S 1 of} the elastic elements of the device. Otherwise, the mode of operation of the device remains unchanged.

The in Figs. 7 and 8 illustrated modified device to the strip thickness control in the rolling differs from that in Fig. 2 through 6, device characterized from that whose valve 17a (Fig · 7) »it an additional control chamber is provided" 1 ^H, which means of the hydraulic lines 62 and 54 is ^{in communication with the space formed by the cavities H} c "and" i "

The assemblies of the device, such as the hydraulic Load cell 14, the two-room hydraulic cylinder 15 »the pumping systems 18, 29 with the electric motors 19, 30, the oil volume control 20, 21, the valves 2 ?, 31 »the safety valve 28, the check valves 22, 23, the shut-off valves 24, 25, the container 26 and the hydraulic lines 49 to 60 perform the same functions as in the first embodiment of the device and are with the same

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Reference sign denotes «

As far as the modified valve 17a is concerned, its cavities and channels fulfill the same functions as in the first embodiment of the device (Fig. 2, 5) and are denoted by ^the same reference numerals, in the construction elements are the same reference signs, but with Ir. riex a uses
The valve 17a (Fig. 8) comprises a housing 40a, a

Step valve 41a with a step 63 and a cover 42a,

bra that is attached to the housing 40a with screws 43a

The slide 41a together with the housing 40a forms a (* kupt ~) control chamber "d", which is in connection with a channel d ^, with its step 63 and the cover 42a a control chamber "1", which is connected to a channel "I ₁ ¹ * is connected, and a throttle chamber "e", which is connected to a

as

Channel "e ^" is connected, by means of the housing 40a and the cover 42a an emptying space "f" which is in communication with a channel f ^. The slide 41a and the cover 42a form a throttle gap ″ y ^M.

The hermetic seal of said cavities is accomplished by means of ζ seals (not shown in the drawing) «

The hydraulic coupling of the cavities "d", "e", "f", to the other assemblies of the device is ensured in the same way as in the first embodiment «The control

B 0 9020/0629

raun "1" of the valve 17a is connected to the space "c - i ^{M" with the aid of the hydraulic lines 62, 54 (FIG. 7).}

Such a connection allows the oil pressure and the oil throughput in the piston chamber "b" of the two-chamber hydraulic cylinder 15 to be proportional to the tension force of the group of elastic elements of the device, consisting of the tree "c" of the two-chamber hydraulic cylinder 15t near the piston rod to ^the cavity ^H i ^{n of} the oil volume governor 21 and the

Control chamber "1" of the valve 17a (the cavities c - i - 1),

at

control, thereby increasing the rapid action of the device of this embodiment compared to the previously mentioned one

Embodiment is improved «

In fact, the amount of oil ΔV that flows into the piston chamber ** b ^{N of} the hydraulic cylinder 15 according to the first variant is as follows «

Δ? » K ₄ . Δ Ρ (29),

where K ^ is the proportionality factor for the proportionality between the change in the rolling force and the amount of oil supplied to the piston chamber "b" of the hydraulic cylinder 15 is is.

Let us _{now determine} the relationship between the values & V and & P of the device which is designed according to the second variant.

As a result of the inertia of the device when the rolling force us changes, the value δ P experiences the exact 16 des

809828/0629

Hydraulic cylinder 15 a lowering due to the deformation & hz of the oil in the piston roughness "b ⁿ among other things the size, which is the same

£ ^h 3 "(50)

K ₅ ♦ K ₁

is, where Kc is the rigidity number of the oil that is in the piston chamber "b" of the hydraulic cylinder 151 een hydraulic lines 51 to 53 and the cavities ¹ V, ^M e ^M. Here, the change in the amount of tension of the group of elastic members of the device is as follows

a <4 a £ hj. K ₁ (3D.

By substituting expression (30) in equation (31) one finds the relationship between the value δ <4 for changing the tension of the elastic elements of the device and the * ert δ Ρ for changing the rolling force

Taking expression (32) into account, the resulting signal that controls the Olflufi is the same ♦ AQ ■ A Ρ «(1 + 1

1+

When the rolling force fluctuates by the magnitude δ? to the Hydraulic cylinder 15, the amount of oil flowing in is the same

^{ci +} —i—- ⁾ (3 *).

1 +

*1

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By comparing the expressions (29) and it is easy to see that in the second embodiment sform when the rolling force P changes by the magnitude λ Ρ the amount of oil flowing into the hydraulic cylinder chamber by the value

¹ Z " ^K 4 · Δ ^ρ · 3 (35)

1+

is larger and therefore the part-time is less «

It is not difficult to prove that the control accuracy also improves in the second embodiment will·

Assuming the case that in the device of the first embodiment, the between the movable elements

ungs of the hydraulic cylinder 15 occurring clamping force F ₁ acts on the size of the displacement, then it can be shown that the elastic elements of the device a force

Α <ί- Δ ^Η - Δ? ± ^ ₁ (36)

and the transfer itself is the same

hg »^ L. = A »- A ^r ± * 1 (37) K ₁ K ₁

and that the displacement error in the displacement of the housing 16 of the hydraulic cylinder 15 in the first embodiment of the device is equal to the value + ^F 1

In the second embodiment, the hydraulic

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cylinder 15 to an amount of oil that corresponds to the change Λ Ρ of the rolling force P and the change α q of the deformation force Q according to the equation

8th (38)

- AQ

proportion al is "

As soon as the equation ^ E- "^ - is satisfied i _stl poses

the oil feed line to the hydraulic cylinder 15 is connected »

The displacement of the housing 16 of the hydraulic cylinder 15 is the same in this case

³ ΔΡ (39)

and depends on the frictional forces in the moving parts of hydraulic cylinder 15 not from *

Adjusting the device before rolling one Strip as well as its actuation during the task of the strip to the scaffolding 1 are carried out in the same way as made in the first embodiment *

It is _{now au} f <ii _e effective as of the device

when rolling, when the thickness of the strip in entry ^into

the

Rolling of the stand 1 increases, received.

With the increase in thickness of the strip to be rolled, the rolling force P increases by the amount δP and consequently increases / increases by the value Aqyier oil pressure within the closed tree "a - d ^M / indes the pressure in the closed space ^N c - i - 1" decreases «As a result

809828/0629

If the slide 41a (FIG. 6) is out of equilibrium, Sr shifts and thereby reduces the gap "y" between the slide 41a and the cover 42a, but increases the resistance of the oil flowing from the pump system 18 and consequently an increase of the pressure fq ₂ ^{n of} this pumping system by the magnitude q ₂ «As a result of the pressure increase by ^ q _{2 , an additional force δ Η« q 2} · F ^ develops in piston space "b" of the hydraulic cylinder 15, part of which acts as a resistance to the increase ΔΡ the rolling force P makes, while the difference between the force E, which is generated by the hydraulic cylinder 15 under the action of the oil pressure within the piston space "b ^M , and the rolling force P- the oil in the closed space ^M c - i - 1 ^H compresses. to effected the size of the Olzusammendrückung in this closed tree $ ^ine displacement of the housing 16 of the hydraulic cylinder 15 and the Einbaustüclces 10 of the lower backup roll 8 *

The displacement of the housing 16 with respect to the piston 36 (Fig. 4) of the hydraulic cylinder 15 takes place as a result of a Change in oil pressure in piston chamber "b" and consequently des Pressure of the pumping system 18 instead of

The change in the pressure of the pumping system 18 continues as long as the slide 41a (FIG. 8) of the valve 17a due to the oil pressure in the closed trees ⁿ ad ^tt and ^M ci «l ^M as well as the bridge of the pumping system 18 (FIG. 7) and the

809828/0629

Housing 16 of the Zweiraum- ^ ydraulikzylinders 15 by the force R, generated by the hydraulic cylinder 15 under the action of the pressure in the piston chamber ** b ** _t as well as by the force Q of the oil compression in the closed barely "ci-1" and the rolling force P ins Are brought into balance.

The displacement distance for the roller up to the equilibrium position of the slide Ma (Fig. 6) of the valve 17a and up to the equilibrium position of the housing 16 of the hydraulic cylinder 15 is the same

- A ^ (37),

at * ¹

where ^ Q is the amount of change in compression of the closed Tree "c-i-1" is *

Here is the total change in the roll gap between the rolls 3, 4 and therefore the change in the strip thickness taking into account the displacement of the extension pieces 10 of the lower roller 8 is equal to the displacement amount

Sh = AP - Au (38)

T ^ I

where the strip thickness at the exit of the framework 1 is given by the equation

' ^F a - ^G ♦ Δ ^ρ -

KKK ₁

results. ·

In realizing the relationship (16) is the

right part of equation (38) is zero · Thus, a

809828/0629

Change dea roll gap and thus a change in the Stripe thickness h ^ in the exit of the framework as a result of the Change in shape of the latter excluded "

At equilibrium of the slide 41a (Fig. 8) of the valve 17a and when the housing 16 (FIG. 7) of the hydraulic cylinder 15 is in equilibrium and after the strip has emerged from the rollers 3, 4 of the frame 1, the device works just like the first embodiment »

The hydraulic load cell is beneficial here 14 and the hydraulic cylinder 15 in the form of a hydraulic panel 64 (Fig. 9) «This means that the devices described above are more compact are executed "

In Fig. 9 the lower part is the opening of the stand 2 is shown, in which between the Feinbau-8tück 10 of the lower support roller 8 and the stand 2 the hydraulic panel b4 is provided

The elements of the hydraulic Moßdosa 14 (J? 'Ig. 3) (the piston 33 »the cover 34, the screws 35) and the elements of the hydraulic cylinder 15 (Fig. 4) (the piston 3b with the rod 39, the cover 37 and the screws 38), which belong to the construction of the hydraulic panel 64 (FIG. 9), as well as their cavities "a", "b" and ⁿ c ^M exercise the same functions au3 and are in FIG. 9 with the same reference numerals as in FIG 3 and 4 denotes «

809828/0629

D _a 8 Hydraulikpaneel 64 has a housing 65 is formed with a piston 33, which by the latter two hydraulic load cell 14 with the cavity "a", which communicates with the channel "B _1" in compound and is filled with oil, a cover 34, which is angular by means of screws 38 on the housing 65. The piston 36 and its rod 39 together with the housing 65 and the cover 37 form a two-space JiydraUlik cylinder 15 with a piston space "b ⁿ and a tree on the piston rod side ⁿ c ⁿ where the mentioned cavities are connected to channels "b ^" and "o ⁿ *

The hydraulic panel 64 acts by means of the piston 33 of the hydraulic load cell 14 with the chock 10 de? lower Support roller θ and by means of the rod 39 of the piston 36 of the two-space hydraulic cylinder 15 with the crosshead of the stand 2 together »

In order to reduce the height of the hydraulic panel 64, the latter can be equipped with several hydraulic load cells 14 and several two-chamber hydraulic. ⁴ .l: cylinders 15 are executed.

In Fig. 10 is an embodiment of the hydraulic panel reproduced, which is provided with three hydraulic load boxes 14 and three hydraulic cylinders 15 ii.it. ^ s it is quite possible that the number of hydraulic load cells 14 and that of hydraulic cylinders 15 in the device is more or less than three.

0 9 828/0629

The elements of the hydraulic panel illustrated in Fig. 10 e are ait the same reference numerals as in Fig. 9, but marked with index a «

The hydraulic panel 64a (FIG. 10) has three pistons 33a, which together with the housing 66 form hydraulic drain boxes 14- with cavities a, which are connected to one another and to a channel "a * ⁿ " guided in the housing 66, a cover 34 * which is fastened to the housing 66 by means of screws 35 *, three pistons 36a and a cover 3? a, which is fastened to ^{the housing 66 by means of screws 38a.} Hydraulic cylinder 13 with piston chambers "b ⁿ and trees ** c" on the piston side from · The trees of the same name of the two-chamber hydraulic cylinders 13 are connected to each other and to the channels ** b ^ ⁿ and ⁿ c ^ ⁿ provided in the housing 66 ·

The hydraulic panel 64a of this variant acts by means of all pistons 33a of the hydraulic let cans 1t- with the Chock 10 of the lower support roller 8 and by means of all rods 39a of the piston 36a of the two-chamber hydraulic cylinder? 13 together with the crosshead of the stand 2 «

In the described embodiments of the hydraulic panel the axes of the hydraulic load cells 14 and those of the hydraulic cylinders 15 are in alignment with one another.

Ia Fig. 11 is the shape of the hydraulic

809828/0629

panels only / with a hydraulic load cell 14 and two Hydraulic cylinders 15 shown, in which calibrate the axis of the hydraulic measuring device 14 with the axis of a the hydraulic cylinder 15 covers »Such an embodiment is moderately simpler in construction ·

The hydraulic panel 64b has a housing 67 with a * Pin 68, a piston 23b, which together with the housing 67 a hydraulic measuring device 14 with a cavity "a", connected to a channel "a *" forms one

Cover 34b, which by means of screws 35b on the housing 67

close eight, two pistons 36b, a cover 37b which is fastened to the housing 67 by means of screws 38b. The pistons 36b and their rods 39b, together with the housing 67 and the cover 37b, form hydraulic cylinders 15 with a piston space "b" and a space ** c ^{n on the} piston rod side. The trees of the same name in the hydraulic cylinders 15 are connected to each other and to the channels "b .." and "c ^ ¹¹ .

The hydraulic panel 64b works with the component 10 of the support roller 8 by means of the piston 33b of the hydraulic load cell 14 and by means of the pin 68 of the housing 67 and with the lower crosshead of the stand 2 by means of the rods 39b the pistons 36b of the hydraulic cylinders 15 together·

In the case of orphans, the hydraulic measuring device takes 14 in the same way

809828/0629

one

as in the described embodiments of the rolling force F proportional force to · Such an execution of the hydraulic panel allows the construction of the device to be simplified »

The hydraulic panel can also be equipped with a hydraulic load cell 14 and several hydraulic cylinders 15 are arranged around the hydraulic measuring box. «With such a structure, the hydraulic panel be provided between the pressure screw 11 (Fig. 2) and the chock 9 of the upper support roller 7

Fig. 12 shows a further embodiment of the hydraulic panel 64c_nur] with a hydraulic load cell 14 and two hydraulic cylinders 15 ·

This hydraulic panel has a housing 69, a piston 33c, which together with the housing 69 has a hydraulic load cell 14 with a cavity ^M a ^H , which is connected to a channel "a,." is in communication, forms a cover 34c, the

br is eight by means of screws 35c on the housing 69, two and

Piston 36c, cover 37c, which is attached to the housing by means of screws 38c 69 are attached · The piston 36c and its rod

39c together with the housing 69 and the cover 37c form a
Two-chamber hydraulic cylinder 15 with a piston chamber "b" and a piston rod-side barely "c" · The chambers of the same name in the hydraulic cylinders 15 are connected to each other and to the channels "b *" and ^η ο _Λ ^η ·

809828/0629

The hydraulic panel 64c works by means of the piston 33c with the pressure screw 11 and by means of the rods 39c with the chock 9 of the upper support roller 7 together *

The hermetic seal of the cavities "a", "b" and ¹¹ C ¹ * of the hydraulic panels shown in Fig. 9 to 12 is secured with the aid of seals (not shown in the drawings), while the hydraulic coupling de?

Cavities on the assemblies of the device - as in the described embodiments of the device - in each case via the channels "a ^", "b ,," and ¹¹ C ₁ "takes place.

The variant of the device shown in Fig. 13, 14 for strip thickness control when rolling between the rolls of the stand of a rolling mill differs from the devices shown in Fig. 2 to 6 and 7-8 in that it has a reversing valve 70 (Fig. I3) which ensures the connection of the piston chamber "b ^{N of} the hydraulic cylinder 15 with the pumping system 18 when the device is started up and the container 26 when the strip emerges from the rollers.

The insertion of the reversing valve 70 in the hydraulic arrangement of the device contributes to the simplification of the device. In particular, assemblies such as the pump system 29 with the electric motor 30, the valve 31 and the hydraulic lines 58, 59 are saved. _The ^ _06- ren assemblies of the device, namely the hydraulic

809828/0629

Meßdoee 14, the two-room hydraulic cylinder 15, the pump system 18 with the electric motor 19ι the oil volume regulator 20, 21, the valve 27, the safety valve 28, the check valves 22, 23, the shut-off valves 24, 25, the container 26 and the hydraulic lines 49 to 57 and 60, 62 the same functions as in the first and second »embodiment of the device and are with the same Labeled "

The reversing valve 70 (FIG. 14) comprises a housing 71 in which there is a piston 72 which, on the side of the valve stem 73 "with a spring 74, is supported against the cover 75 fastened to the housing 71 by means of the screws 76, is loaded * The piston 72 and the housing 71 form a cavity V, which is connected to channels "m ^" and "B ₂ ¹ *, an annular cavity" n "which is connected to a channel" η ^ ^Η , and together with the housing 71 and the deodorant 75 a cavity "p" which is in communication ^{with a channel N} p ^ ^{M ·}

The hydraulic coupling of the reversing valve 70 (FIG. 13) is achieved as follows. The cavity "m" stands above the channel "m" ** (FIG. 14) by means of the hydraulic line 77 (FIG. 13) which is connected to the Hydraulic line 52 is connected, with the pump system 18 and via the channel Xm ₂ ″ by means of the hydraulic line 51 (FIG. 13) with the piston chamber ** b ^{M of} the hydraulic cylinder 15 in connection,

809828/0629

while the cavity "p ^M " is coupled to the hydraulic line 56 via the channel ¹¹ P ₁ "(FIG. 14) by means of the hydraulic line 78 (FIG. 13). The annular cavity "n ^{n of} the reversing valve 70 is connected _{to the container 26 (FIG. 13) via the channel" H 1} "(FIG. 14) and with the aid of the hydraulic lines 78a and 57.

In this embodiment of the device, the connection of the space .. which is formed by the piston rod-side space "c ^{M of} the two-chamber hydraulic cylinder 15, the cavity" i "of the oil volume regulator 21 and the control space ⁿ l" of the pressure valve 17a, with the source for the liquid agent (01) changed «This connection is made by means of the hydraulic line 55a and via the check valve 23 with the hydraulic line 56, in which pressure is generated by means of the valve 27 when the oil flows through and is always kept constant ·

The setting of the device described before rolling, its actuation and operation during regulation the strip thickness when rolling is carried out on a similar basis Way as with the first two embodiments of the device «

The embodiment of the device shown in Fig. 15 to 17 differs from the device corresponding to the second variant (Fig. 7) in that the cavity "a" of the hydraulic measuring cell 14 with the cavity "b ⁿ dee two-

809828/0629

Raum-Hydraulikzylinaers 15 (Fig · 15) is united, whereby a considerable simplification of the device is achieved «

For the purpose of automatic start-up of this device, a reversing valve 79 with hydraulic is in its arrangement Control added “The design of valve 17, that of the two-chamber hydraulic cylinder, is also used for the same purpose 15 and the hydraulic coupling of the assemblies of the device changed · The assemblies of the device, namely the pumping systems 18, 29 with the. Electric motors 19, 30, the oil volume regulator 21, 20, the valves 27, 31, the safety valve 28 the check valves 22, 23, the shut-off valves 24, 25 and the container 26 are unchanged, play the same role as in the device according to the second embodiment and have the same function

Regarding the hydraulic cylinder 15b and the valve 17b, which have undergone a partial change in constructive terms, it should be said that Beuelemente as well as their Cavities and channels that perform the same functions as in the exercise second embodiment of the device, with the

b the same reference number, and additionally provided with an index

The valve 17b (FIG. 16) comprises a housing 40b in which a stepped slide valve 41b with a step 63 is located floating piston 80 loaded with a spring 81,

809828/0629

br and a eighth by means of screws 43b on the housing 40b

Cover 42b are "

The step valve 41b and the housing 40b form a control space which is divided into two cavities "d" and ^H r ^H «These two cavities are each associated with

the end
housing 40b led channels "d ^" and ¹ V ₁ "in connection.

Together with the cover 42b, the stepped valve 41b forms two cavities _t that is, a control chamber "l '* ₍ which is connected to a channel ¹¹ I ^", and a throttle chamber "e ^H , which is connected to a channel" e,. ""As well as a throttle gap" y "· The evacuation space" f "is through the

Stepped valve 41b designed and with one in the housing

the end
40b led channel "f ^" connected ·

The reversing valve 79 (fig. 17) has a housing 82, in which coaxially a slide 83 loaded with a spring 84 and a plunger loaded with a spring 86, which is against one by means of screws. 8ö on housing 82 attached cover 87 supports, are arranged · On the side of the slide 83 is the reversing valve with an I-ecl · /. " 89 completed, which by means of screws 90 on the housing 82 is attached.

The slide 83 forms together with the housing 82 and

the cover 89 has a cavity "s", which is connected to a channel "s * ¹ *

and
connected to the housing 82 annular cavities "t"

and ¹¹ U ", which are each connected to channels" t ,, "and ¹¹ U ₁ "

' ^J 8 09828/0629

dun ^ stand

The plunger 85 forms an annular cavity "v" with the housing 82 and a cavity V with the housing 82 and the cover 87, the two cavities with each other by means of channels ¹¹ V ^ "and" w * "and with the annular cavity" u "are connected by channel ¹¹ U ₁ " «

Between the slide 85 and the plunger 85 there is an annular cavity ⁿ z ⁿ which is connected to the cavity ⁿ t "by means of the channels ⁿ s ^ ^N and ⁿ t ^ ^M «

Continue in the housing 82 of the reversing valve 79 Bind Channels "Sg" and "tg" planned «

The hydraulic connection of the assemblies of the device is achieved as follows. The space formed by the piston space "b ** of the hydraulic cylinder 15 (FIG. 15) and the space" g "of the oil volume regulator 20 is by means of the hydraulic line 51 via the channel ¹¹ S ₁ " alt the cavity ^H s "and via the check valve 22 with the hydraulic lines 51a and 51b with the valve 27 and the ring-shaped barely ^M in connection. and the throttle space "< 'of the valve 17b and the pumping system 18 are connected by means of the hydraulic lines 52, 52a, 52b to the channel ^M s ₂ ^{H of} the reversing valve 79, which in the orphan has the cavity" s "and in the absence of a strip between the lalxea of the framework bit the ring-shaped hollow

809828/0629 ⁸ ^ ORIGINAL

space "t" is in communication, and connected via the channel "t ^. ** by means of the hydraulic lines 51h and 91 with the container 26" The cavity "r" of the valve 17b is connected to the channel "t ₂ " by means of the hydraulic line 92 in connection, which during rolling over the annular cavity "t", the channel "t ^" by means of the hydraulic lines i? 1b, 91 with the container 26 and in the absence of a strip between the rolls over the annular cavity V, the channels ¹¹ U ₁ "and" V ₁ ", the hydraulic lines 93, 95 with the pump line 29, which is responsible for a constant oil pressure, is connected. In the Mullstellung of the slider 83 (i'ig. 17) of the channel remains "t ₂ ^M inhibited. The cavities" γ "and ¹ V ** are by means of hydraulic lines 93 (FjLg ₀ 15), and 55 n, the pumping system 29 is connected .

The hydraulic coupling of the remaining assemblies of the device, namely the piston rod side space "c ^N of the hydraulic cylinder 15b of the cavity" i ", Olvolumenreglers 21, the second control chamber dee" 1 ^H of the valves 17b, the JSntleerungsraumes "f" is similar to the Device according to the second embodiment (Fig. 7).

The setting of the device is carried out in a manner similar to that of the device according to the second embodiment performed. The only difference here is that the force of the spring 84 (FIG. 17) is smaller than that

809828/0629

the spring ö6 is attached

By operation of the pumping systems 18 and 29 (FIG · 15) generates a pilot pressure in the modules of the device * This occurs in the Raun, "hich through the cavities" oil "of the pump system 29 is formed, a pressure q _o on * The The same pressure is in the cavities ¹ V ¹ , "w ^N and" u "of the reversing valve 79 as well as in the cavity" r "of the valve 17b and the hydraulic lines 55, 92, 93 through which the pump system 29 is connected to the named cavities, detectable · Ea should be noted that the plunger is 85 (FIG · 17) in the left Endsteilung and supports the piston against the housing 82 while the slider 83 also the left l & dstellurg occupies and braces against the cover 89 '

This results in the annular cavity

and "u ^n" connects the channels ^w t ₂ ^H and ⁿ u ^ ^{N to} one another the annular cavity "t" connects the channels ¹¹ S ₂ "and" U ₁ "to one another _f where the pumping system 18 (FIG. 15), the first control chamber • • d "and the throttle ^{space" e M of} the valve 17b are connected to the container 26 by means of the annular cavity "t", the hydraulic lines 51b and 91 and the valve 27. The pressure q,. inside these cavities and the hydraulic lines 52, 52a, 52b lies above atmospheric pressure and is preset with the aid of the valve 27

«0Ü828 / 0629

the magnitude of this pressure based on the relationship

Vl _<e \ J- (40),

^F s
whereby

F _{1 is} the force generated by the spring 84 (Fig. 17) and F _{0 is} the face of the piston 83 is ^ ohlrauK "β" is »

as well as the relationship

<Io · - ^ S-. C ^ D

^F b

f and F ^

In each of whose trees "c ^M and ¹ V are,

where f and F ^ are the areas of the piston of the hydraulic cylinder

chosen"

Under the action of the form "q _o ⁿ in the voids" 1 "and" r "and the upstream pressure in the cavities in the cavities q ,." d "and" β "as well as due to the force of the spring 81 remains (Fig x 16) the slide 41b of the valve 17b is pressed against the cover by the floating piston 80

The balance of the spool 41b of the valve 17b can be as follows

^ o · ^F l ⁺ Vl- ^F e ^{+ T} - ⁽ Mo ♦ ^{F) s0 (42)} write, from which the force T of the pressure pushes the slide 41b on the cover 42b

T »q ₀ (F _r - F ₁ ) ♦ F
is derived _t where

8 0 9828/0629

F is the area of floating piston 80 in cavity "r" r

Under the action of this force, there is a gap "y" between the slide 41b and the cover 42b equal zero *

The piston of the hydraulic cylinder stands up by the spring 95 (FIG · 15) against the Boc.en of the housing 16, and I "between the end face of the piston 26 and d * r of the housing 16 forms an oil layer" Thus Alxa ours rollers 4 , 8 * which rest on the housing 16 of the hydraulic cylinder 15b via the chock 10, locked in a certain position «

The desired gap between the work rolls 3, 4 is set by means of the pressure screw 11 «

The device works in the following way.

As a result of the abandonment of a strip in the gap between The rollers of the stand 1 of a rolling mill produce a rolling force which <fcich> the elements of the stand 1 and the hydraulic cylinder 15b can be deformed.

Here, the oil pressure rises within the piston chamber "b ^N due to the approach of the end face of the piston 6 and that of the housing 16, which also leads to an increase in the oil pressure in the cavity" β "of the reversing valve 79 *

As soon as the oil pressure "q" is in the piston chamber ** b ^{N of the hydraulic cylinder 15b.} so

809828/0629 BAD original

enters, the slide 82 (Fig. 17) begins to move and ^{connects the channel M} Sp ^H with the cavity "s **. This closes the channel" tp "» whereby the piston chamber "b" of the two-chamber hydraulic Zylindere 15b (Fig. 15) to the pumping system 18 and the cavities "d" and "e" of the Ve / will connect itils 17b. This guessed a pressure increase in the pumping system 18 and in Kclbenrauc ¹ V of the hydraulic cylinder 15b and into said Hoh. .räui: et of the valve 17b (the gap ^M y ^M is equal to Hull, an outflow of the oil from the throttle space ⁿ e "in the i ^ ntleerungaraua" f "does not take place).

The pressure of the pump q> q is _0, the slider come 8} (Fig. 17) and the plunger 85 in the right hndstellung · at Here the plunger against the lid 87 and the slider 83 against the plunger 85 'while the cavity ^M based r "of the valve 17b is connected to the container 26 via the channel" tg "and the annular cavity" t "*

The piston 80 (Fig. 16) of the valve 17b pushes away from the slide 41b and is against the bottom of the recess pressed in the housing 40b .. The slide 41b of the valve 17b is attached to the cover 42b by the force

T »q (F _d - F _e ) -q ₀ . F ₁ (45)

pressed, where F _d , F ₆ , F _{1 are} the surfaces of the slide 41b in the cavities "d ^N ," e "and ⁿ l ^{H of} the valve 17b«

809828/0629

The throttle gap "y ⁿ " therefore remains closed, and no oil flows through it into the container 26 (FIG. 15) *

The pressure of the pump system 18 increases until

under the action of the pressure q of the pumping system

the resulting force R can move the housing 16 with respect to the Kolbexis 36. Here, a part of the force R _v, which is generated by the hydraulic cylinder 15 under the action of the pressure within the piston chamber "b", provides one: Resistance to the rolling force P, while the difference between the force B and the rolling force P on the closed building » , formed by the cavities "ctl", acted

The relocation of the housing continues

R - P> O ₄₀ . F _e (46)

Here, the oil pressure in the said space rises as a result of its compression (reduction)

As soon as the slide 41b (Fig. 16) of the valve 17b has ^{been brought into equilibrium by the oil pressure in the cavity, 1} M "," β "and" 1 ", the gap" y "between the slide 41b and the »Lid 42b opened, and the 01, which is conveyed by the pumping system 18 (FIG. 15), flows completely through the gap" y "from the throttle space" e "to the emptying space" f " ₉ from where it is fed to the container 26 WiTd ₁ what makes the housing 16 of the hydraulic cylinder 15 stop

8 (H) H 2 8/0 6 2 9

BATH

The path covered through the housing is the same

With this shift in mind, the mean change in strip thickness is the same

fr * - AH - AQ . AQ (48)

1
and the strip thickness _a * is the same as the exit of the framework

When the relationship (16) between K ₁ and K is satisfied, the right-hand part of equation (48) is equal to zero, consequently a change in the gap between the rolls and a change in the strip thickness is ^a m exit

one
Rolling of the stand due to changes in the shape of the latter excluded "

Now that the strip has left the rollers, the device takes its starting position and is for the the following work cycle ready

manure
In this way, the inventor increases a *

Accuracy of the regulation and its execution with
a simpler and cheaper device,

achieved by using the strip thickness control the strength for the transfer

of the bearings c.er roller la course of the deformation of the

Strip between the rolls proportional to the rolling force can change, including the hydraulic load cells with the device for performing this method

the cavity filled with the liquid agent for replenishing

and
would take from the rolling force the valves for regulating the pressure of the liquid agent with the control chamber, which is connected to the cavity of the hydraulic load cell, and the throttle chamber, which is connected to the hydraulic cylinder and which is connected to the liquid agent

809828/0629

Claims (1)

P 66 364-Μ-61 December 23, 1977 L / Br PATENT CLAIMS 2 7 B 7 8 3 1 [1 ·] Method for strip thickness control during rolling between rolls installed in the stand of a rolling mill, in which a force; one of W _a is generated lzen for displacement of the bearings, which is greater than the rolling force and on the bearings of the rollers engages such that it overcomes the rolling force and the difference η clipboard this force and the rolling force ^ iclT> the bearings of the <£ -? and Can be offset roller, which is proportional to this offset a force is generated which causes the approach of the bearings of the rolls between which the forming of a strip takes place, prevents, and the difference between the force for the displacement of the bearings of the Malts and the rolling force balances, with the proportionality factor for the proportionality between the displacement of the bearings of the orphan and the force that the Difference between the force for the displacement of the bearings on the Wulze and the rolling force compensates, previously In a certain ratio to the stiffness number of the roll stand it is given and the force for the dislocation dei The roller bearings are changed when the strip is formed to compensate for the fluctuations in the gap, characterized in that the force for the displacement of the bearings (10) of the roller (8) in the course of the deformation 809828/0629 ORIGINAL INSPECTEP -9f- of the strip proportional to the rolling force according to the formula E = K ₂ P, is changed, where
B is the force required to move the bearings of the Roller is required, and
P is the rolling force; and K ₂ is based on the relationship K ₂ = ^K 1 + 1
K is chosen, where K ^ the proportionality factor for the proportionality ■ wipe the displacement of the roller bearings and the force that prevents the roller bearings from approaching, and K is the rigidity number of the roll stand « Implementation 2 · device for the procedure according to Claim 1, which is arranged in the frame of a rolling mill, which has a stand with a pressure device built into it and rollers with bearings which are arranged in the side openings of the stator in such a way that that at least one roller can move in the rolling direction, includes, and attached from two ah the two sides of the stand and parts formed according to the same scheme, each of which has a pressure transducer for receiving the rolling force, at least one hydraulic cylinder, 809828/0629 sen cylinder space for relocating the bearings of the roller in the Rolling process is connected to a pressure source for liquid agent, elastic elements of the device, which are so arranged are that aie is the difference between the by to
the hydraulic cylinder generating the force and the rolling force, has a valve for regulating the pressure of the liquid medium within the hydraulic cylinder space, characterized in that hydraulic measuring cells (14) with at least one cavity (a) each are provided as pressure transducers, which are located between the Bearings (7, 9 or, 8, 10) of one of the rollers (3 or «4) and the stand (2) are located, and the valves (17 or 17a or« 17b) for regulating the pressure of the liquid cement proportional to the rolling force in the hydraulic cylinder space (13) a housing (40 or 40a or 40b) with a slide (41 or 41a) inserted therein exhibit,
or «41b) through which at least two cavities are formed, one of which is the valve control chamber of the valve (17 or, 17a or 17b) (d), is connected to the cavity (a) of the hydraulic keypad (14) and with this forms a closed fluff with a liquid medium, and the other serves as the throttle belly (e) of the valve (17 or «17a or« 17b),. with the hydraulic cylinder space (b) and the <4ielle for the liquid agent is in connection and forms a common tree with liquid agent 809828/0629 3. Device according to claim 2, characterized in that each hydraulic cylinder (15) NIIT a closed piston rod side chamber (c) provided iüt, the through housing (16), cover (37) _t piston rod (39) and piston (36) designed and is filled with liquid agent, which, together with the elements of the hydraulic cylinder (15) ι by which said tree (o) is formed, forms elastic elements of the device, which with a corresponding. · Force the position of the bearings (6, 10) of the determine the movable roller (4). 4. Apparatus according to claim 2 and 3t, characterized in that that the slide (41a or 41b) of each valve (17a or, 17b) to regulate the pressure of the liquid agent in the Hydraulic cylinder chamber (b) is designed as a stepped piston, which together with the housing (40a or 40b) of the Valve (17a or «17b) an additional control room (b) whereby forms »the latter with the hydraulic cylinder space on the piston rod side (c) is connected, which forms a closed space with said control space (b), which se
is filled with liquid funds 5 · Device according to claim 3ι characterized in that that in the closed piston rod-side hydraulic Small cylinder space (c), which fills with the liquid agent is, a spring (61) is provided, the ends of which are against the piston (36 * and against the cover (37) 809828/0629 - £ 27 7,834 supports and together with the liquid agent as well as the closed piston rod-side hydraulic cylinder space Cc) forming and with the spring (61) cooperating elements of the hydraulic cylinder X.15) elastic elements of the Device forms. 6. The device according to claim 2, characterized in that the cavity (a) is the hydraulic. Load cell (14), the with the control chamber (d) of the valve (17 or 17a or 17b) for regulating the pressure of the liquid medium in the hydraulic cylinder chamber (b) is connected with the piston chamber (6) of the hydraulic cylinder (15b). 7. Device according to claim 6, characterized in that that in the piston chamber (b) of the hydraulic cylinder (15) t the in the rolling process with the control chamber (d) and the throttle chamber (e) of the valve (17b) to regulate the pressure of the liquid agent in the Cavity (b) of the hydraulic cylinder (15b) is connected, a spring (95) is provided, which in the absence of it a strip between the rollers against the piston (3 &) and against the housing (16) of the hydraulic cylinder (15b) and prevents the bearings of the rollers (3t Ό from moving apart . 8. Device according to claims 3, 4, 5, 6, 7, characterized in that that they have additional oil volume space (21) contains a cavity (i), which is connected to the piston 809828/0629 stan _{6 is} connected to the hydraulic cylinder space (c) and with this hardly forms a closed one, which with with the liquid funds replenished, these two Cylinder spaces as an elastic element of the device works. or 9 · Device according to claim 2, 4 6, characterized characterized in that the Kolbea.rß / (b) of the hydraulic cylinder (15) is connected to the pressure source (16) for the liquid medium via a control valve (70 or 79), that has two customer control spaces (m and «β), (ρ and · w), of which one (m) with the throttle chamber (s) of the valve (17 or «17a or« 17b) to regulate the pressure of the liquid Means in the hydraulic cylinder-rough * (b), with the piston chamber (B) the hydraulic cylinder (15 or, 15b) and the pressure source for the liquid agent when folding and the other (p or w) is connected to the constant pressure source 809828/0629