CN100579681C - Roll form regulating mechanism for twelve-roller controllable roll form roller mill - Google Patents

Abstract

The invention discloses an adjustment mechanism of roll forming used for 12 roll-controlled roller mill, which comprises a roller system and a intercross adjustment mechanism of a middle backup roller respectively arranged in upper and lower roller seat; the upper and lower roller system respectively comprises a middle backup roller system, two groups of external backup roller system, two middle rollers and a working roller; the intercross adjustment device of the middle backup roller is connected with the upper and lower middle backup roller; back-lining bearing of the external backup roller of each external backup roller system and that of the middle backup roller of the middle back up roller system are tangential with one middle roller simultaneously; two middle rollers are tangential with a working roller at the same time; the structures of arrangement and connection of two parts of the upper and lower roller systems are same, and the upper and the lower roller systems are symmetrically arranged. The purpose of control roller shape can be realized through adjusting the size of the angel formed by the upper and lower groups middle backup roller system crossed along horizontal surface, leading the middle rollers and the working roller to bend in different degree. The invention has simple structure, unique control structure and extensive application prospect.

Description

The roll forming guiding mechanism that is used for the controlled roll forming milling train of 12 rollers

Technical field

The invention belongs to the metallurgy rolling equipment technical field, relate to roll gap shape adjustments device in the multiple roll cold-strip steel rolling equipment, be specifically related to a kind of roll forming guiding mechanism that is used for the controlled roll forming milling train of 12 rollers.

Background technology

Early stage cold-rolled steel strip products is to adopt two rollers, four-high mill to be rolled, along with science and technology and industrial expansion, the band that demand is thinner, because the work roll diameter of two rollers, four-high mill is all bigger, roll itself produces serious elastic flattening when rolling, and the elastic flattening value is directly proportional with roller diameter, two rollers, four-high mill can't roll out thinner band, for this reason, just the six-high cluster mill that various structures occurred, it has good plate shape control ability, is widely used in the strip product of rolling general yield strength.But when rolling high-yield strength band or thinner strip product,, often adopt the multi-roll mill of the above littler work roll diameter of six rollers, as 12 rollers, 20 rollers, 32 rollers, 36 roller mills etc. in order further to reduce work roll diameter.

In order to obtain the straight plate shape and the band of broad ways consistency of thickness, the wide cut multi-roll mill all is furnished with the roll forming guiding mechanism at present, its structure and plate shape control mode are generally all very complicated, multi-roll mill roll forming guiding mechanism has two kinds of forms at present, a kind ofly be guiding mechanism radially, a kind of is mechanism for axial adjusting.

Radially guiding mechanism is in the saddle between each back lining bearing of backing roll, except the interior eccentric hoop of depressing guiding mechanism is housed, refill an outer eccentric hoop, respectively each outer eccentric hoop is rotated adjustment separately by worm and gear or hydraulic cylinder, tooth bar, gear, make backing roll group axle produce given flexural deformation, adjust purpose to reach whole roll forming.

Mechanism for axial adjusting is that two pairs of opposite two ends bodies of roll of intermediate calender rolls up and down are processed into taper, with its in opposite directions or opposite direction move axially, adjust the overlap length of its roll surface straight portion, reach roll forming and adjust purpose.

More than two kinds of frame for movement of adjusting modes and electrical control more complicated all, the manufacturing cost height, maintenance difficulty is big.Therefore, press for and adopt a kind of new roll forming to adjust mode, satisfy the requirement that roll forming is adjusted, to produce the band of thinner better plate shape and broad ways consistency of thickness.

Summary of the invention

The purpose of this invention is to provide a kind of roll forming guiding mechanism that is used for the controlled roll forming milling train of 12 rollers, solved the roll forming guiding mechanism device complexity of existing plate shape control, manufacturing cost height, the problem that maintenance difficulty is big.

The technical solution adopted in the present invention is, a kind of roll forming guiding mechanism that is used for the controlled roll forming milling train of 12 rollers, be characterized in, comprise rack-mounted roller seat and the lower roller base gone up, between frame and last roller seat, be connected with the AGC hydraulic cylinder, backing roll intersection adjusting device and top roll system in one are installed in last roller seat, backing roll intersection adjusting device and lower roll system in one are installed in lower roller base, top roll system and lower roll system comprise backing roll roller system in a group separately, two groups of external support roller roller systems, two intermediate calender rolls, a working roll, backing roll intersection adjusting device is to be connected respectively with the middle backing roll roller of top roll system and lower roll system in described, the middle backing roll back lining bearing of the external support roller back lining bearing of each external support roller roller system and middle backing roll roller system is simultaneously tangent with an intermediate calender rolls, two intermediate calender rolls are simultaneously tangent with a working roll, each parts setting that top roll is fastened is identical with the structure that is connected with the setting of each parts that lower roll is fastened, and symmetry is installed up and down.

Middle backing roll intersection adjusting device comprises an intersection adjustment worm gear, the adjustment worm gear that intersects is a core structure, the worm gear external tooth of adjusting worm gear that intersects is connected with the worm screw of transmission device, intersection is adjusted the endoporus and the excircle eccentricity of worm gear, one homalocephalus axle is housed in the endoporus of worm gear sleeve, and the homalocephalus of homalocephalus axle is installed in the flat hole of middle backing roll saddle base plate.

In backing roll saddle base plate be arranged on roller system by bearing pin and adjust on the backing plate, roller system adjusts in the groove that backing plate is contained in roller seat and lower roller base middle part, and middle backing roll saddle is installed on the middle backing roll saddle base plate.

In backing roll roller system be installed in more than four by the middle backing roll back lining bearing more than three by middle backing roll axle is coaxial on the backing roll saddle.

Middle back-up roll bearing diameter is than an external support roller bearing young waiter in a wineshop or an inn/one.

The invention has the beneficial effects as follows that this rolling mill structure is greatly simplified, the roll forming method of adjustment is simple, can carry out the control of plate shape to rolling band effectively, and the device fabrication cost is low, is convenient to maintenance.

Description of drawings

Fig. 1 is a multi-roll mill roll forming guiding mechanism schematic diagram radially in the prior art;

Fig. 2 is a multi-roll mill roll forming guiding mechanism decomposing schematic representation radially in the prior art;

Fig. 3 is the structural representation of one embodiment of the invention;

Fig. 4 is the roll system structure schematic diagram of Fig. 3;

Fig. 5 a is lower roller base and the roll system structure schematic diagram of Fig. 4; Fig. 5 b is the middle backing roll partial schematic diagram of Fig. 3;

Fig. 6 is the structural representation of the middle backing roll saddle base plate of Fig. 5 embodiment;

Fig. 7 is the structural representation that the intersection of Fig. 6 embodiment is adjusted worm gear;

Fig. 8 is roller system and the roller seat force analysis figure when static load of Fig. 4;

Fig. 9 be Fig. 4 left intermediate calender rolls along its length each point with respect to X, the Y direction coordinate Calculation schematic diagram of external support roller center line;

Figure 10 is the schematic diagram that the backing roll along continuous straight runs rotates to an angle among the embodiment of Fig. 5, and a point is the center that horizontally rotates of middle backing roll.

Among the figure, 1, frame, 2, the AGC hydraulic cylinder, 3, last roller seat, 4, top roll system, 5, lower roll system, 6, lower roller base, 7, roller system adjusts backing plate, 8, middle backing roll intersection adjusting device, 9, middle backing roll saddle base plate, 10, middle backing roll saddle, 11, middle backing roll axle, 12, external support roller saddle, 13, external support roll centre axle, 14, external support roller back lining bearing, 15, working roll, 16, intermediate calender rolls, 17, middle backing roll back lining bearing, 18, bearing pin, 19, absolute altitude is adjusted piece, 20, intersect and adjust worm gear, 21, the homalocephalus axle, 22, flat hole, 23, interior eccentric hoop, 24, outer eccentric hoop, 25, the sector gear sheet, 26, eccentric sector, 27, the backing roll back lining bearing, 28, axle, 29, saddle, 30, two-sided tooth bar.

The specific embodiment

The present invention is described in detail below in conjunction with the drawings and specific embodiments.

Roll forming control of the present invention is applied on the controlled roll forming milling train of 12 rollers, its principle is that upper and lower two middle backing roll along continuous straight runs of the controlled roll forming milling train of 12 rollers are intersected adjustment mutually with given angle, under the effect of roll-force, make intermediate calender rolls and working roll produce flexural deformation, intersecting angle is big more, its flexural deformation is big more, thereby reaches the purpose that plate shape is adjusted.The frame of the controlled roll forming milling train of this kind 12 rollers adopts mill, Shuangpai County combining structure that is similar to six-high cluster mill, for the multi-roll mill of whole frame, structure is more simple, THICKNESS CONTROL adopts the AGC hydraulic cylinder directly to depress, similar to six-roll cold mill, in order to obtain desirable plate shape, the controlled roll forming milling train of this 12 roller has designed the novel roll forming guiding mechanism of a cover, and adopting a cover can be cross one another adjusting device with upper and lower two middle backing roll rollers.This milling train is not established radial and axial roll shape guiding mechanism, and structure is greatly simplified, and can carry out plate shape effectively and adjust.

Fig. 1 is the structural representation of existing radially guiding mechanism, and Fig. 2 is the local enlarged diagram of the backing roll of Fig. 1.Existing radially guiding mechanism operation principle is: 29 li of each saddles of depressing the backing roll group an interior eccentric hoop 23 and a roll forming of depressing usefulness is housed and regulates the outer eccentric hoop 24 of usefulness, eccentric sector 26 is fixed on the axle 28 by key with interior eccentric hoop 23, forms the guiding mechanism of depressing of milling train.Outer eccentric hoop 24 and two sector gear sheet 25 usefulness pins connect together, the radially roll forming guiding mechanism of forming milling train, radially the roll forming guiding mechanism is to make two-sided tooth bar 30 drive sector gear sheet 25 by worm and gear transmission or the direct transmission of servo hydraulic cylinder to rotate together with outer eccentric hoop 24, make axle 28 produce given flexural deformation, because of backing roll back lining bearing 27 is contained on the axle 28, backing roll back lining bearing 27 positions will change, and adjust purpose thereby reach whole roll forming.

Fig. 3 is the structural representation of the embodiment of the invention, comprise frame 1, frame 1 is the primary load bearing support that two enclosed memorial archway shapes are formed, roller seat 3 and lower roller base 6 are installed in the frame 1, top roll is 4 to be contained on the roller seat 3, lower roll is 5 to be contained on the lower roller base 6, between frame 1 and last roller seat 3, be connected with AGC hydraulic cylinder 2, AGC hydraulic cylinder 2 applies given downward roll-force for last roller seat 3, and with roll-force pass to top roll be 4 and lower roll be 5, top roll be 4 and lower roll be to realize the rolling of band during each roller of 5 rotates.It is on 5 the installed surface, when roller is to carry out roll line absolute altitude Compensation Regulation after the reconditioning diameter changes that the absolute altitude of roll line is adjusted lower roll that piece 19 is contained in lower roller base 6.

Fig. 4 is the roll system structure schematic diagram of the embodiment of the invention.Top roll of the present invention be 4 and lower roll to be that each parts on 5 are provided with identical with the structure of connection, be symmetrical arranged, simultaneously sheet material is rolled.Backing roll is installed in last roller seat 3 in one, and to intersect adjusting device 8 and top roll be 4, backing roll is installed in lower roller base 6 in one, and to intersect adjusting device 8 and lower roll be 5, middle backing roll intersect adjusting device 8 respectively with top roll be 4 and lower roll be that 5 middle backing roll roller system is connected.Top roll be 4 and lower roll be 5 backing roll roller system in the two groups of external support roller rollers system, a group, two intermediate calender rolls 16, a working roll 15 to be arranged respectively.Upper and lower each two external support roller roller system are respectively external support roll centre axle 13, external support roller back lining bearing 14 to be fixed in the plum blossom hole of roller seat 3 and lower roller base 6 by backing roll saddle 12; During backing roll roller system is arranged in upper and lower on the backing roll saddle 10, middle backing roll saddle 10 is separately fixed on separately the middle backing roll saddle base plate 9; Because middle backing roll is stressed littler than external support roller, in order to make compact conformation, middle backing roll back lining bearing 17 diameters are than external support roller back lining bearing 14 young waiters in a wineshop or an inn/about one, the roller system that middle backing roll saddle base plate 9 is arranged on separately adjusts on the backing plate 7, roller system adjusts the interior location of groove that backing plate 7 is contained in roller seat 3 and lower roller base 6 middle parts, the effect that roller system adjusts backing plate 7 be when roller be that the mutual alignment that pair roller was after the reconditioning diameter changed is rationally regulated, backing roll back lining bearing 17 can be done horizontal crisscross motion with middle backing roll saddle base plate 9 in two groups.Before middle backing roll roller was uncrossed, the middle backing roll back lining bearing 17 of the external support roller back lining bearing 14 of each external support roller roller system and middle backing roll roller system was simultaneously tangent with an intermediate calender rolls 16, and two intermediate calender rolls 16 are simultaneously tangent with a working roll 15.After central backing roll intersection adjusting device 8 makes angle of upper and lower middle backing roll roller system's intersection, under the effect of roll-force, the position that upper and lower roll system is in contact with one another along its length changes, upper and lower working roll 15 produces positive bending deformation, it will offset the flexural deformation of roller seat up and down, thereby the plate shape of realizing rolled strip is adjusted.

Fig. 5 a is that lower roller base and the roller of Fig. 4 embodiment is assembly structure figure.Lower roll is 5 to comprise left and right sides external support roller roller system, each external support roller roller system is by the external support roller back lining bearing 14 more than three, by an external support roll centre axle 13 coaxial being installed on four above external support roller saddles 12, in the plum blossom hole that external support roller saddle 12 is contained on the lower roller base 6, its fixed-site is constant.Left and right intermediate calender rolls 16 is tangent with external support roller back lining bearing 14 that contacts separately and middle backing roll back lining bearing 17 respectively, and working roll 15 is tangent with left and right sides intermediate calender rolls 16 respectively.

Fig. 5 b is that the backing roll roller is a partial schematic diagram in the lower roller base of Fig. 3 embodiment.In backing roll roller system be installed in more than four by the middle backing roll back lining bearing 17 more than three by a middle backing roll axle 11 is coaxial on the backing roll saddle 10, during being fixed on, middle backing roll saddle 10 on the backing roll saddle base plate 9, can horizontally rotate given angle with middle backing roll saddle base plate 9.

Fig. 6 is the structural representation of the middle backing roll saddle base plate of Fig. 5 embodiment.Middle backing roll saddle base plate 9 is adjusted backing plate 7 by bearing pin 18 with roller system and is movably hinged.Upper and lower two middle backing roll rollers are can intersect around bearing pin 18 levels with saddle base plate 9 to rotate given angle.Middle backing roll intersection adjusting device 8 adopts turbine and worm transmissions (not drawing among worm screw and the control servomotor figure), comprise an intersection adjustment worm gear 20, the adjustment worm gear 20 that intersects is a telescoping structure, the worm gear external tooth of adjusting worm gear 20 that intersects is connected with the worm screw that has servodrive, intersection is adjusted the endoporus and the excircle eccentricity of worm gear 20, a homalocephalus axle 21 is housed in the worm gear sleeve hole, during its homalocephalus inserts in the flat hole 22 at backing roll saddle base plate 9 two ends, when worm screw drives 20 rotations of intersection adjustment worm gear, backing roll saddle base plate 9 rotated a given adjustment angle around bearing pin 18 during homalocephalus axle 21 made in horizontal plane, like this, on, backing roll system produces and intersects down, just can realize the purpose that the present invention adjusts.

Fig. 7 is the structural representation that the intersection of Fig. 6 embodiment is adjusted worm gear 20, its endoporus and excircle eccentricity, and when worm screw drives the worm gear rotation, the homalocephalus axle 21 that is contained in its endoporus will produce displacement.

Roll forming control procedure of the present invention is, in the strip-rolling process, CCU receives the associated plate graphic data signal of the detected band of milling train exit detecting instrument of flatness, compare with the standard value of initial input, calculate the roll forming adjusted value, and intersect adjusting device 8 to middle backing roll and send instruction, two middle backing roll intersecting angles are up and down adjusted, thereby realized that controlled plate shape is rolling.Be simplified control system, above adjustment also can be adopted manually operated mode, according to the plate shape situation that observes, utilizes hand control to intersect and adjusts the angle that worm gear 20 rotates, and reaches the purpose of adjustment.Backing roll intersection adjusting device 8 can be that closed loop is adjusted automatically in of the present invention, also can be by the stochastic parameter adjustment manually is set.

The theoretical validation that one embodiment of the present of invention intersecting angle is adjusted is as follows:

Setting the roller owner wants parameter as follows:

External support roller bearing 14 diameters: φ 260mm; Left and right external support roller bearing centre-to-centre spacing: 410mm;

Middle back-up roll bearing 17 diameters: φ 139mm; Intermediate calender rolls 16 diameters: φ 100mm;

Working roll 15 diameters: φ 50mm, length: 800mm;

Middle backing roll centre-height (left and right relatively backing roll) :-10.16234mm.

Controlled roll forming roller system of rolling mill of 12 rollers and roller seat force analysis are:

Fig. 8 is roller system and the roller seat force analysis figure when static load of Fig. 4, and P is a roll-force, and P3, P4, P5 are the component that roller system passes to the roller seat vertical direction:

General rolling force P=P3+P4+P5.

T1, T2 are the internal force that roller system passes to the roller seat horizontal direction.T1=T2, its value is about 57% of roll-force.

By the graphing method pair roller is force analysis, if roll-force is P, about 73% (P3+P4) of roll-force passes to roller seat up and down by the external support roller bearing, and middle supporting roller holding capacity P5 is less, its value has only 27% of roll-force, and it is very favourable that this centering backing roll intersection roll forming is regulated.

The calculating demonstration of the controlled roll forming milling train of 12 rollers roll forming controlling value is as follows:

The angle of middle backing roll rotation is adjusted at any time according to band template situation, and the middle backing roll anglec of rotation is big more, and the roll forming adjusted value is big more.Calculate the roll forming changing value of working roll, must calculate the function numerical value of the roll forming of two intermediate calender rolls earlier respectively with middle backing roll feathering angle variation.

Fig. 9 be Fig. 4 left intermediate calender rolls along its length the arbitrfary point with respect to X, the Y direction coordinate Calculation schematic diagram of external support roller center line.

Extrapolate below left intermediate calender rolls along its length each point with respect to the coordinate function value of X, the Y of external support roller center line:

D1 is the external support roller diameter, and D2 is middle backing roll diameter,

D3 is the intermediate calender rolls diameter, and D4 is a work roll diameter,

H is that middle backing roll center is poor with respect to external support roller centre-height,

Y be left intermediate calender rolls along length Z direction any section center with respect to external support roller centre-height coordinate,

X be left intermediate calender rolls along length Z direction any section center with respect to external support roller central horizontal coordinate,

B is the horizontal range of middle backing roll middle part with respect to external support roller center,

θ be middle backing roll around the middle part along the horizontal plane anglec of rotation,

λ be middle backing roll behind anglec of rotation θ angle, middle part, along the horizontal displacement distance of roller length Z direction any section, middle part front end Z value is for just on the roller, rear end Z value is to bear, λ is with different variation of coordinate position Z on the size at θ angle and the roller.Very little because of the θ angle, the λ value can be represented by the formula:

λ＝Ztanθ

B+ λ be middle backing roll along arbitrfary point, length Z direction axle center with respect to external support roller central horizontal distance.

L is middle backing roll any section kernel of section and external support centre distance.

$L=\sqrt{{\mathrm{<figure-callout\; id="2"\; label="h"\; filenames="C2008100173990018H1.png"\; state="\{\{state\}\}">h</figure-callout>}}^2+{(B+\mathrm{\&lambda;})}^2}$

Each point is as follows with respect to X, the Y equation in coordinates of external support roller center line along its length for left side intermediate calender rolls axis:

$Y=\frac{{\mathrm{<figure-callout\; id="1"\; label="D"\; filenames="C2008100173990018H1.png"\; state="\{\{state\}\}">D</figure-callout>}}_1+{\mathrm{<figure-callout\; id="3"\; label="D"\; filenames="C2008100173990018H1.png,C2008100173990018H2.png"\; state="\{\{state\}\}">D</figure-callout>}}_3}{2}\&times;\mathrm{San}(\mathrm{\&beta;}-\mathrm{\&alpha;})---\left(1\right)$

$X=\frac{{\mathrm{<figure-callout\; id="1"\; label="D"\; filenames="C2008100173990018H1.png"\; state="\{\{state\}\}">D</figure-callout>}}_1+{\mathrm{<figure-callout\; id="3"\; label="D"\; filenames="C2008100173990018H1.png,C2008100173990018H2.png"\; state="\{\{state\}\}">D</figure-callout>}}_3}{2}\&times;\mathrm{Cos}(\mathrm{\&beta;}-\mathrm{\&alpha;})---\left(2\right)$

Wherein:

$\mathrm{\&beta;}=\mathrm{arcCos}[{\left(\frac{{\mathrm{<figure-callout\; id="1"\; label="D"\; filenames="C2008100173990018H1.png"\; state="\{\{state\}\}">D</figure-callout>}}_1+{\mathrm{<figure-callout\; id="3"\; label="D"\; filenames="C2008100173990018H1.png,C2008100173990018H2.png"\; state="\{\{state\}\}">D</figure-callout>}}_3}{2}\right)}^2+L^2-{\left(\frac{{\mathrm{<figure-callout\; id="2"\; label="D"\; filenames="C2008100173990018H1.png"\; state="\{\{state\}\}">D</figure-callout>}}_2+{\mathrm{<figure-callout\; id="3"\; label="D"\; filenames="C2008100173990018H1.png,C2008100173990018H2.png"\; state="\{\{state\}\}">D</figure-callout>}}_3}{2}\right)}^2]\&divide;[2\&times;\left(\frac{{\mathrm{<figure-callout\; id="1"\; label="D"\; filenames="C2008100173990018H1.png"\; state="\{\{state\}\}">D</figure-callout>}}_1+{\mathrm{<figure-callout\; id="3"\; label="D"\; filenames="C2008100173990018H1.png,C2008100173990018H2.png"\; state="\{\{state\}\}">D</figure-callout>}}_3}{2}\right)\&times;\left(\frac{{\mathrm{<figure-callout\; id="2"\; label="D"\; filenames="C2008100173990018H1.png"\; state="\{\{state\}\}">D</figure-callout>}}_2+{\mathrm{<figure-callout\; id="3"\; label="D"\; filenames="C2008100173990018H1.png,C2008100173990018H2.png"\; state="\{\{state\}\}">D</figure-callout>}}_3}{2}\right)]$

$\mathrm{\&alpha;}=\arctan \left(\frac{h}{B+\mathrm{\&lambda;}}\right)$

Because under the certain situation of angle θ, middle backing roll is different along the λ value of each point on the axis, and its value changes with the distance at backing roll middle part in the distance, so the value of β and α also just changes with the λ size.Can find out from last (1), (2) equation, intermediate calender rolls axial line Y coordinate figure along its length in a left side is with (β-α) value is sinusoidal variation with respect to external support roller center, directions X is with (β-α) value is the cosine curve variation, be that left intermediate calender rolls axial line produces sinusoidal curve in the Y direction, produce the cosine curve bending at directions X.

Simultaneously, λ also changes with the size of middle backing roll around middle part anglec of rotation θ, thereby can regulate the degree of crook of roll forming by the size of regulating the θ angle, reaches the controlled purpose of roll forming.

In like manner can calculate right intermediate calender rolls axis along its length each point with respect to X, the Y coordinate of external support roller center line.

According to the left and right intermediate calender rolls axis coordinate position of each point along its length, promptly available same method is obtained the working roll coordinate position of each point along its length.

Because the roller of upper and lower roller seat system is identical, the horizontal rotatio direction of just middle backing roll is opposite, therefore need only carry out computational analysis to the roller system of lower roller base below.

The schematic diagram that Figure 10 rotates a certain angle for backing roll along continuous straight runs in the present embodiment.A point among the figure is the center that horizontally rotates of middle backing roll, on middle supporting saddle roller seat 10 by middle backing roll axle 11 serials be equipped with some in backing roll back lining bearing 17, middle supporting saddle roller seat 10 drives each parts with this and adjusts accordingly action along with middle backing roll saddle base plate 9 horizontally rotates according to certain angle.

During present embodiment is given backing roll horizontally rotate 0.573 ° (total length 800mm two ends displacement: λ for ± 4mm) time, calculate X, the Y coordinate figure of each roller, converting then draws the distortion numerical value of each roller with respect to self middle part.Result of calculation is as follows:

1, middle backing roll is horizontally rotated 0.573 ° after, the position calculation in the relative stage casing of left each section of intermediate calender rolls the results are shown in Table 1:

Table 1: each of left intermediate calender rolls section relative coordinate (centre is 0, to the right for just, upwards for just)

The measuring position	(front end λ) 400	(front end λ) 200	Middle part 0	(rear end λ)-200	(rear end λ)-400	Utilize the graphing method analysis
							Horizontal direction	0.98182	0.48655	0	-0.47755	-0.94583	Horizontal direction integral inclination 1.92765.Horizontal direction is bent into+and 0.018.
Vertical direction	-1.55637	-0.76686	0	0.74446	1.46673	Vertical direction integral inclination 3.0231.The body of roll is for just bending+0.0448.

Left side intermediate calender rolls roll shape result of variations is analyzed as follows:

1), the horizontal direction anglec of rotation is approximately: α=0.1381 ° (tg α=1.92765/800), horizontally rotating angle is 24% of the middle backing roll anglec of rotation.

2), horizontal direction is bent into+0.018 (inwardly), it is just curved to help working roll.

3), the vertical direction inclination angle is approximately: 0.2165 ° (tg β=3.0231/800).

4), vertical direction bending+0.0448 is for just curved.

2, middle backing roll is horizontally rotated 0.573 ° after, the position calculation in the relative stage casing of right each section of intermediate calender rolls the results are shown in Table 2:

Table 2: each of right intermediate calender rolls section relative coordinate (centre is 0, to the right for just, upwards for just)

The measuring position	(front end λ) 400	(front end λ) 200	(middle part) 0	(rear end λ)-200	(rear end λ)-400	Utilize the graphing method analysis
							Horizontal direction	-0.94583	-0.47755	0	0.48655	0.98182	Horizontal direction integral inclination 1.92765.Horizontal direction is bent into-0.018.
Vertical direction	1.46673	0.74446	0	-0.76686	-1.55637	Vertical direction integral inclination 3.0231.The body of roll is for just bending+0.0448.

Right intermediate calender rolls roll shape result of variations is analyzed as follows:

1), the horizontal direction anglec of rotation is approximately: α=0.1381 °, (tg α=1.92765/800), direction is opposite with left intermediate calender rolls, the anglec of rotation is 24% of the middle backing roll anglec of rotation.

2), horizontal direction was bent into for-0.018 (inwardly), it is just curved to help working roll.

3), the vertical direction inclination angle is approximately: β=0.2165 ° (tg β=3.0231/800), direction is opposite with left intermediate calender rolls.

4), vertical direction bending+0.0448 is for just curved.

Table 3: each of working roll section relative coordinate (centre is 0, to the right for just, upwards for just)

The measuring position	(front end λ) 400	(front end λ) 200	(middle part) 0	(rear end λ)-200	(rear end λ)-400	Utilize the graphing method analysis
							Horizontal direction	0.53495	0.26730	0	-0.26730	-0.53495	Horizontal direction integral inclination 1.0699.Horizontal direction is crooked hardly.
Vertical direction	-0.06958	-0.01739	0	-0.01739	-0.06958	Vertical direction has only bending, does not produce inclination.Just bend 0.06958

When 3, middle backing roll being horizontally rotated 0.573 °, the position calculation in the relative stage casing of each section of working roll the results are shown in Table 3.

The working roller result of variations is analyzed as follows:

1), the horizontal direction anglec of rotation is approximately: 0.0766 °, (tg α=1.0699/800) anglec of rotation is very little.

2), the relative intersecting angle of upper working rolls and lower working rolls is approximately: 0.1532 ° (0.0766 ° * 2)

3), horizontal direction is bent into 0.00018, numerical value very I is ignored.

4), vertical direction do not tilt, and has only bending, is just curved+0.06958 (sine curve).

4, can reach a conclusion from above-mentioned analysis: this example, the roll forming regulated quantity that working roll is obtained by flexural deformation is 0.13916mm (0.06958mm * 2).The roll forming regulated quantity that the working roll intersection obtains is 0.01145mm (calculates and omit).

In this example, total roll forming regulated quantity is: 0.13916+0.01145=0.15061mm.

The present invention and the controlled roll shape milling train of described 12 rollers thereof have following characteristics, and 1, external support roller and middle backing roll all adopt saddle structure, takes full advantage of the high rigidity of upper and lower roller seat, is conducive to the plate shape control of band. 2, adopt with backing roll intersection in the Worm wheel transmission mechanism realization of eccentric orfice, it is reliable to make roll forming adjust Stability Analysis of Structures, has avoided the simultaneously baroque shortcoming of Integral cross of PC milling train (the paired cross rolling mill of roll) upper and lower backing roll and working roll bearing block. 3, roll forming of the roll is simple, and reconditioning is easy, reduces spare part quantity, is convenient to spare parts management. 4, by the intersection of middle backing roll, it is certain just curved that intermediate calender rolls is produced, and the inclination angle is very little, is conducive to adopt the transmission of universal connecting shaft. 5, the middle backing roll roll-force of bearing is less, is conducive to when rolling on-load and intersects and adjust. 6, the intersecting angle of working roll is very little, and the suffered axial force of working roll is little, has overcome the PC cross rolling mill because the working roll intersecting angle is large, causes the large weakness of suffered axial force. 7, working roller bending is symmetrical, and is just curved for sine, is comparatively desirable roll shape adjustment distortion. 8, upper and lower roll system is installed in respectively on the upper and lower roller seat, and roll change is convenient, for ease of maintenaince. 9, Double-memorial arch formula combined rack adopts the hydraulic AGC oil cylinder directly to depress, and makes the thickness of slab control structure simple. 10, for whole closed frame, the opening degree of roll is large, is easy to threading operation and accident treatment.

In sum, the controlled roll shape Control Structure of Rolling Mill of 12 rollers of the present invention is unique, and adjusting operation is simple, the device fabrication cost is low, be convenient to maintenance, can effectively control the plate shape of band, have broad application prospects at the accurate strip of rolling stainless steel and other high-yield strength material.

Claims (3)

1, a kind of roll forming guiding mechanism that is used for the controlled roll forming milling train of 12 rollers, it is characterized in that, comprise the last roller seat (3) and the lower roller base (6) that are installed on the frame (1), between frame (1) and last roller seat (3), be connected with AGC hydraulic cylinder (2), backing roll intersection adjusting device (8) and top roll system (4) in one are installed in last roller seat (3), backing roll intersection adjusting device (8) and lower roll system (5) in one are installed in lower roller base (6), top roll system (4) and lower roll system (5) comprise backing roll roller system in a group separately, two groups of external support roller roller systems, two intermediate calender rolls (16), a working roll (15), backing roll intersection adjusting device (8) is to be connected respectively with the middle backing roll roller of top roll system (4) and lower roll system (5) in described, the middle backing roll back lining bearing (17) of the external support roller back lining bearing (14) of each external support roller roller system and middle backing roll roller system is simultaneously tangent with an intermediate calender rolls (16), two intermediate calender rolls (16) are simultaneously tangent with a working roll (15)

Each parts in the top roll system (4) be provided with and lower roll system (5) on the setting of each parts identical with the structure that is connected, symmetrical up and down installation;

Backing roll intersection adjusting device (8) comprises an intersection adjustment worm gear (20) in described, the adjustment worm gear (20) that intersects is a core structure, the worm gear external tooth of adjusting worm gear (20) that intersects is connected with the worm screw of transmission device, intersection is adjusted the endoporus and the excircle eccentricity of worm gear (20), one homalocephalus axle (21) is housed in the endoporus of worm gear sleeve, and the homalocephalus of homalocephalus axle (21) is installed in the flat hole (22) of middle backing roll saddle base plate (9);

Backing roll saddle base plate (9) is arranged on roller system's adjustment backing plate (7) by bearing pin (18) in described, roller system's adjustment backing plate (7) is contained in the groove at roller seat (3) and lower roller base (6) middle part, backing roll saddle (10) in being equipped with on the middle backing roll saddle base plate (9).

2, roll forming guiding mechanism as claimed in claim 1 is characterized in that, described in backing roll roller system be installed in more than four on the middle backing roll saddle (10) by a middle backing roll axle (11) is coaxial by the middle backing roll back lining bearing (17) more than three.

3, roll forming guiding mechanism as claimed in claim 1 is characterized in that, described middle back-up roll bearing (17) diameter is than external support roller bearing (a 14) young waiter in a wineshop or an inn/one.

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