CN106294971A - A kind of oversize ring control surely rolls and embraces roller hydraulic design method - Google Patents

Abstract

The invention discloses a kind of oversize ring control and surely roll an armful roller hydraulic design method, comprise the steps: S1, set up based on radial-axial rolling rigidity condition and embrace a roller maximum guiding force mathematical model；S2, combine radial-axial ring rolling mill embrace roller mechanism set up embrace a roller hydraulic cylinder oil pressure cntrol mathematical model；S3, the comprehensive radial-axial rolling expanding Activity design of process ring embrace roller hydraulic cylinder oil pressure process control curve.The present invention can be that radial-axial rolling process embraces roller pressure control a kind of scientific and effective method for designing of offer, it is achieved the axial stable rolling in oversize ring footpath shapes.

Description

A kind of oversize ring control surely rolls and embraces roller hydraulic design method

Technical field

Present invention relates particularly to a kind of oversize ring control and surely roll an armful roller hydraulic design method.

Background technology

Large marine Wind turbines bearing, wind tower flange, harbour machinery tower crane pivoting support, heavy gas turbine group ring The important ring parts such as part, nuclear power generating sets ring, petrochemical industry pressure vessel, Large Launch Vehicle warehouse, are diameter 5 meters mostly Above oversize ring, classical production process is difficult to the manufacture requirements of this kind of part large-size and high performance.Ring footpath Axially rolled is a kind of advanced plasticity rotoforming technique manufacturing large-scale seamless ring.During radial-axial rolling, such as Fig. 1 Shown in, king roller 1 and core roller 2 constitute radially pass to be made ring wall thickness reduction, epicone roller 5 and lower cone roller 6 constitute axial pass to make Ring height reduces, thus promotes ring 7 enlarged-diameter and cross section profile to shape.

In ring growth process, as it is shown in figure 1, be arranged in a pair armful of roller (left armful of roller 3 and right armful of king roller 1 both sides Roller 4) under oil cylinder enclasping force effect, it is close to ring outer surface, it is ensured that ring stable rolling.When embracing, roller pressure is excessive, and ring is easy The plastic instability because of insufficient rigidity, causes ring to be crushed and scraps；When embracing, roller pressure is too small, and ring is easily because enclasping force is not enough Double swerve, ring time serious is as in irregular shape and scrap.Especially for this kind of oversize ring, its rigidity Relatively poor, that scraps because armful roller pressure control is improper is particularly problematic.Owing to operation of rolling DYNAMIC COMPLEX is changeable, how Rationally determine and embrace roller pressure, thus ensure that the operation of rolling is stably carried out, be a key issue urgently to be resolved hurrily.At present, roller is embraced The control of pressure is based primarily upon experience trial-and-error method, and this method is theoretically unsound, it is difficult to meet new product development requirement, and For oversize ring, usual experimental manufacturing cost is high.Therefore, set up a kind of oversize ring footpath and axially control steady rolling armful Roller hydraulic design method is particularly important.

Summary of the invention

It is an object of the invention to provide a kind of oversize ring control and surely roll an armful roller hydraulic design method, it is by rationally Design radial-axial rolling process embrace roller pressure, it is ensured that rolling is stable to be carried out, thus shapes high large-scale of dimensional accuracy Ring forging.

The technical solution adopted for the present invention to solve the technical problems is:

A kind of oversize ring control surely rolls and embraces roller hydraulic design method, it is characterised in that comprise the steps:

S1, based on radial-axial rolling rigidity condition set up embrace a roller maximum guiding force mathematical model, embrace roller guide power F_gCan not Exceed maximum guiding force F allowed_g-max, i.e.Wherein, B is ring axial height, H It is ring radial thickness, σ_sIt is material yield strength, R_aIt is the mean radius of ring,It it is the maximum section bending moment factor；

S2, combine radial-axial ring rolling mill embrace roller mechanism set up embrace a roller hydraulic cylinder oil pressure cntrol mathematical model, embrace a roller mechanism include Embrace roller, rotary swinging arm structure DGJ and embrace roller hydraulic cylinder EJ, embracing roller and be arranged at the G axle of rotary swinging arm structure DGJ, can rotate around G axle, Rotary swinging arm structure DGJ can rotate around D axle, embraces roller hydraulic cylinder EJ for embracing roller and provides enclasping force, its one end and rotary swinging arm structure DGJ J axle be connected, the other end can rotate around E axle, oil pressure in armful roller hydraulic cylinder Wherein, k_gBeing oil pressure adjustment factor, take 0.1～0.5, L is the length of bar DG, and γ is ∠ DGO₁Supplementary angle, O₁In ring The heart, r_hIt is to embrace roller hydraulic cylinder internal diameter, L₁Being the length of bar JD, δ is the angle of ∠ DJE；

S3, the comprehensive radial-axial rolling expanding Activity design of process ring embrace roller hydraulic cylinder oil pressure process control curve:

During S301, radial-axial rolling, ring change in size need to meet constant-volume principle, ring base size try to achieve ring Part outer radius R and inside radius r, and then obtain ring mean radius R_a,

In S302, the operation of rolling, ring radial thickness H and ring axial height B are calculated by following formula respectively:

$H=H_0-{\∫}_0^t{v}_{r}dt---\left(18\right)$

$B=B_0-{\∫}_0^t{v}_{a}dt---\left(19\right)$

Wherein, v_rFor radial feed speed, v_aFor axial feed velocity, t is rolling time；

S303, determine suitable feed speed after, calculate ring expanding during the change of each size, in conjunction with embracing a roller The each dimensional parameters of mechanism, obtains and embraces each angular relationship in roller mechanism, obtain the maximum section bending moment factor in conjunction with guide roller angle [alpha]The above results is substituted into formula (13), calculates armful roller hydraulic cylinder with the change of ring outer diameter D in the operation of rolling Interior oil pressure p process control curve, in radial-axial rolling production process, in conjunction with rolling ring apparatus measuring and control data, the most program control according to this Yeast production line conservative control embraces roller hydraulic cylinder oil pressure, to realize operation of rolling stability contorting.

By technique scheme, step S1 specifically includes following steps:

S101, assume ring radial direction pass and axially pass position retrained by fixing end, embrace the enclasping force of roller for referring to To the concentration power at ring center, calculate for simplifying, take 1/2nd models and carry out force analysis, solved by force method, available Ring section turn momentExpression formula:Wherein, F_gFor embracing the roller guiding force to ring,For The section turn moment factor, its expression formula is about embracing roller guide angle α and angle, ring sectional positionFunction:

S102, for meeting rigidity condition, cross section maximum stress in bend σ_maxShould be less than material permissible bending stress [σ], i.e.

Wherein, W_zIt is bending sections coefficient, for square-section, It is maximum section bending moment,And the maximum section bending moment factorCalculated by following expression formula:

[σ] is material permissible bending stress, yield strength σ of drawing materials_s, i.e. [σ]=σ_s；

S103, for ensureing to avoid ring to occur plastic instability to become because rigidity condition cannot be met during radial-axial rolling Shape, embraces roller guide power F_gNot can exceed that maximum guiding force F allowed_g-max。

By technique scheme, step S2 specifically includes following steps:

S201, for realizing statics balance, condition need to be met: F_pL₁Sin δ=F_gLsin γ (6), wherein, F_pIt it is hydraulic cylinder Pressure；

In conjunction with cylinder pressure computational methods, in obtaining hydraulic cylinder, oil pressure expression formula is:

According to geometrical relationship, the expression formula that solves of related angle γ and δ in armful roller mechanism can be calculated and be respectively as follows:

$\mathrm{\γ}=\mathrm{\π}-arccos\frac{L^2+{(R_g+R)}^2-{(R+R_m-x_D)}^2-{y_D}^2}{2L(R_g+R)}---\left(8\right)$

$\mathrm{\δ}=arccos\frac{{L_1}^2+{(x_D+L_1{\mathrm{sin\α}}_D-x_E)}^2+{(y_D-L_1{\mathrm{cos\α}}_D-y_E)}^2-{(x_D-x_E)}^2+{(y_D-y_E)}^2}{2L_1\sqrt{{(x_D+L_1{\mathrm{sin\α}}_D-x_E)}^2+{(y_D-L_1{\mathrm{cos\α}}_D-y_E)}^2}}---\left(9\right)$

Wherein, R_gIt is to embrace roller radius, R_mIt is king roller radius, x_DAnd y_DIt is the coordinate of rotary shaft D, x_EAnd y_EIt it is rotary shaft E Coordinate, α_DIt is the position angle of bar DG, α_DCalculated by following formula:

${\mathrm{\α}}_D=arctan\frac{R+R_m-x_D}{y_D}+arccos\frac{{y_D}^2+{(R+R_m-x_D)}^2+L^2-{(R_g+R)}^2}{2L\sqrt{{y_D}^2+{(R+R_m-x_D)}^2}}+arccos\frac{L^2+{L_1}^2-{L_2}^2}{2{\mathrm{LL}}_1}---\left(10\right)$

Wherein, L₂It is the length of bar JG；

Embrace roller guide angle α to be solved by following formula:

$\mathrm{\α}=\arctan \frac{y_D}{R+R_m-x_D}+\arccos \frac{{y_D}^2+{(R+R_m-x_D)}^2+{(R_g+R)}^2-L^2}{2(R_g+R)\sqrt{{y_D}^2+{(R+R_m-x_D)}^2}}---\left(11\right)$

According to equation (5) and (7), can show that embracing a roller hydraulic cylinder oil pressure p need to meet following condition:

During S202, radial-axial rolling, when embracing, roller pressure is excessive, and the ring easily plastic instability because of insufficient rigidity is made Becoming ring to be crushed to scrap, when embracing, roller pressure is too small, and the ring easily double swerve because enclasping force is not enough, time serious, ring also can Scrapping because of in irregular shape, therefore, suitable enclasping force is to ensure that the key of ring stable rolling, according to above-mentioned theory meter Calculating, in embracing roller hydraulic cylinder, oil pressure p is designed by following formula:

By technique scheme, in step S301, ring change in size need to meet constant-volume principle, i.e.

π(R²-r²) B=π (R₀ ²-r₀ ²)B₀ (14)

Wherein, R₀For ring base radius, r₀For ring base inside radius, B₀For ring base height, calculate according to formula (14) and obtain outside ring Radius R and inside radius r:

$R=({R_0}^2-{r_0}^2)\frac{B_0}{2BH}+\frac{H}{2}---\left(15\right)$

$r=({R_0}^2-{r_0}^2)\frac{B_0}{2BH}-\frac{H}{2}---\left(16\right)$

And then obtain ring mean radius R_a:

$R_a=\frac{R+r}{2}=({R_0}^2-{r_0}^2)\frac{B_0}{2BH}---\left(17\right)$

By technique scheme, in step s 302, nip for meeting and forge condition, radial feed speed v_rAxially Feed speed v_aNeed to meet following condition:

$\frac{6.55\×{10}^{-3}{v}_m}{2{\mathrm{\πRR}}_m}{(R-r)}^2(1+\frac{R_m}{R_i}+\frac{R_m}{R}-\frac{R_m}{r})\≤v_r\≤\frac{2{{\mathrm{\β}}_r}^2{v}_m{R}_m}{2\mathrm{\π}R{(1+R_m/R_i)}^2}(1+\frac{R_m}{R_i}+\frac{R_m}{R}-\frac{R_m}{r})---\left(20\right)$

$\frac{0.00655v_m{B}^2}{\mathrm{\π}RStan\mathrm{\γ}}\≤v_a\≤\frac{2{{\mathrm{\β}}_a}^2{v}_{m}Stan\mathrm{\γ}}{\mathrm{\π}R}---\left(21\right)$

Wherein, v_mIt is 800～1600mm/s for king roller linear velocity and span, R_iFor core roller radius, β_rAnd β_aPoint Not being 0.3～0.4 for radial and axial angle of friction and span, S is that cone roller summit is to itself and ring outer diameter contact point Distance, θ is the semi-cone angle of cone roller.

The method have the advantages that the present invention sets up based on radial-axial rolling rigidity condition and embrace roller maximum guiding force Mathematical model, embraces roller mechanism further combined with radial-axial ring rolling mill and sets up an armful roller hydraulic cylinder oil pressure cntrol mathematical model, comprehensively examine Consider the expanding Activity design of operation of rolling ring and embrace roller hydraulic cylinder oil pressure process control curve, can be that radial-axial rolling process embraces roller Stress control provides a kind of scientific and effective method for designing, it is achieved oversize ring stable rolling shapes.

Accompanying drawing explanation

Below in conjunction with drawings and Examples, the invention will be further described, in accompanying drawing:

Fig. 1 is radial-axial rolling principle schematic in the embodiment of the present invention；

Fig. 2 is the schematic cross-section of ring in the embodiment of the present invention；

Fig. 3 is radial-axial rolling stiffness analysis mechanical model schematic diagram in the embodiment of the present invention；

Fig. 4 is the structural representation that in the embodiment of the present invention, radial-axial ring rolling mill embraces roller mechanism；

Fig. 5 is that in the embodiment of the present invention, radial-axial ring rolling mill embraces roller hydraulic cylinder oil pressure p process control curve synoptic diagram.

In figure: 1-king roller；2-core roller；3-embraces roller in a left side；4-embraces roller in the right side；5-epicone roller；Roller is bored under 6-；7-ring；8-embraces Roller hydraulic cylinder.

Detailed description of the invention

In order to make the purpose of the present invention, technical scheme and advantage clearer, below in conjunction with drawings and Examples, right The present invention is further elaborated.Should be appreciated that specific embodiment described herein only in order to explain the present invention, not For limiting the present invention.

In the preferred embodiment, as Figure 1-Figure 5, a kind of oversize ring control surely rolls and embraces roller power and set Meter method, comprises the steps:

S1, based on radial-axial rolling rigidity condition set up embrace a roller maximum guiding force mathematical model, embrace roller guide power F_gCan not Exceed maximum guiding force F allowed_g-max, i.e.Wherein, B is ring axial height, H It is ring radial thickness, σ_sIt is material yield strength, R_aIt is the mean radius of ring,It it is the maximum section bending moment factor；

S2, combine radial-axial ring rolling mill embrace roller mechanism set up embrace a roller hydraulic cylinder oil pressure cntrol mathematical model, embrace roller mechanism position In king roller both sides, the operation of rolling is held ring tightly, it is ensured that ring stable rolling, as shown in Figure 4, embrace roller mechanism and include embracing roller (left armful of roller or right armful of roller), rotary swinging arm structure DGJ and armful roller hydraulic cylinder EJ, embrace roller and be arranged on the G axle of rotary swinging arm structure DGJ Place, can rotate around G axle, and rotary swinging arm structure DGJ can rotate around D axle, embraces roller hydraulic cylinder EJ for embracing roller and provides enclasping force, its one end Being connected with the J axle of rotary swinging arm structure DGJ, the other end can rotate around E axle, embraces oil pressure in roller hydraulic cylinder 8Wherein, k_gBeing oil pressure adjustment factor, take 0.1～0.5, L is bar DG Length, γ is ∠ DGO₁Supplementary angle, O₁It is the center of ring, r_hIt is to embrace roller hydraulic cylinder internal diameter, L₁Being the length of bar JD, δ is ∠ The angle of DJE；

S3, the comprehensive radial-axial rolling expanding Activity design of process ring embrace roller hydraulic cylinder oil pressure process control curve:

During S301, radial-axial rolling, ring change in size need to meet constant-volume principle, ring base size try to achieve ring Part outer radius R and inside radius r, and then obtain ring mean radius R_a,

In S302, the operation of rolling, ring radial thickness H and ring axial height B are calculated by following formula respectively:

$H=H_0-{\∫}_0^t{v}_{r}dt---\left(18\right)$

$B=B_0-{\∫}_0^t{v}_{a}dt---\left(19\right)$

Wherein, v_rFor radial feed speed, v_aFor axial feed velocity, t is rolling time；

S303, determine suitable feed speed after, calculate ring expanding during the change of each size, in conjunction with embracing a roller The each dimensional parameters of mechanism, obtains and embraces each angular relationship in roller mechanism, obtain the maximum section bending moment factor in conjunction with guide roller angle [alpha]The above results is substituted into formula (13), calculates in the operation of rolling and embrace roller with what ring outer diameter D (D=2R) changed Oil pressure p process control curve in hydraulic cylinder, in radial-axial rolling production process, in conjunction with rolling ring apparatus measuring and control data, according to this Process control curve conservative control embraces roller hydraulic cylinder oil pressure, to realize operation of rolling stability contorting.

In a preferred embodiment of the invention, step S1 specifically includes following steps:

S101 is as it is shown on figure 3, during radial-axial rolling, at radial direction pass, ring is by king roller and the footpath of core roller The wall thickness reduction to squeezing action, at axial pass, ring is by boring the axial compression effect of roller up and down and highly reducing, and arranges The a pair armful of roller in king roller both sides is close to ring outer surface under oil cylinder enclasping force effect, it is assumed that ring is at radial direction pass and axle Being retrained by fixing end to pass position, the enclasping force embracing roller is the concentration power pointing to ring center, calculates for simplifying, takes two points One of model carry out force analysis, solved by force method, available ring section turn momentExpression formula:(1), wherein, F_gFor embracing the roller guiding force to ring,For the section turn moment factor, its expression formula is to close In embracing roller guide angle α and angle, ring sectional positionFunction:

S102, for meeting rigidity condition, cross section maximum stress in bend σ_maxShould be less than material permissible bending stress [σ], i.e.

Wherein, W_zIt is bending sections coefficient, for square-section, It is maximum section bending moment,And the maximum section bending moment factorCalculated by following expression formula:

[σ] is material permissible bending stress, yield strength σ of drawing materials_s, i.e. [σ]=σ_s；

S103, for ensureing to avoid ring to occur plastic instability to become because rigidity condition cannot be met during radial-axial rolling Shape, embraces roller guide power F_gNot can exceed that maximum guiding force F allowed_g-max。

In a preferred embodiment of the invention, step S2 specifically includes following steps:

S201, for realizing statics balance, condition need to be met: F_pL₁Sin δ=F_gLsin γ (6), wherein, F_pIt it is hydraulic cylinder Pressure；

In conjunction with cylinder pressure computational methods, in obtaining hydraulic cylinder, oil pressure expression formula is:

According to geometrical relationship, the expression formula that solves of related angle γ and δ in armful roller mechanism can be calculated and be respectively as follows:

$\mathrm{\γ}=\mathrm{\π}-arccos\frac{L^2+{(R_g+R)}^2-{(R+R_m-x_D)}^2-{y_D}^2}{2L(R_g+R)}---\left(8\right)$

$\mathrm{\δ}=arccos\frac{{L_1}^2+{(x_D+L_1{\mathrm{sin\α}}_D-x_E)}^2+{(y_D-L_1{\mathrm{cos\α}}_D-y_E)}^2-{(x_D-x_E)}^2+{(y_D-y_E)}^2}{2L_1\sqrt{{(x_D+L_1{\mathrm{sin\α}}_D-x_E)}^2+{(y_D-L_1{\mathrm{cos\α}}_D-y_E)}^2}}---\left(9\right)$

Wherein, R_gIt is to embrace roller radius, R_mIt is king roller radius, x_DAnd y_DIt is the coordinate of rotary shaft D, x_EAnd y_EIt it is rotary shaft E Coordinate, α_DIt is the position angle of bar DG, α_DCalculated by following formula:

${\mathrm{\α}}_D=arc\tan \frac{R+R_m-x_D}{y_D}+arccos\frac{{y_D}^2+{(R+R_m-x_D)}^2+L^2-{(R_g+R)}^2}{2L\sqrt{{y_D}^2+{(R+R_m-x_D)}^2}}+arccos\frac{L^2+{L_1}^2-{L_2}^2}{2{\mathrm{LL}}_1}---\left(10\right)$

Wherein, L₂It is the length of bar JG；

Embrace roller guide angle α to be solved by following formula:

$\mathrm{\α}=arctan\frac{y_D}{R+R_m-x_D}+arccos\frac{{y_D}^2+{(R+R_m-x_D)}^2+{(R_g+R)}^2-L^2}{2(R_g+R)\sqrt{{y_D}^2+{(R+R_m-x_D)}^2}}---\left(11\right)$

According to equation (5) and (7), can show that embracing a roller hydraulic cylinder oil pressure p need to meet following condition:

During S202, radial-axial rolling, when embracing, roller pressure is excessive, and the ring easily plastic instability because of insufficient rigidity is made Becoming ring to be crushed to scrap, when embracing, roller pressure is too small, and the ring easily double swerve because enclasping force is not enough, time serious, ring also can Scrapping because of in irregular shape, therefore, suitable enclasping force is to ensure that the key of ring stable rolling, according to above-mentioned theory meter Calculating, in embracing roller hydraulic cylinder, oil pressure p is designed by following formula:

In a preferred embodiment of the invention, in step S301, ring change in size need to meet constant-volume principle, i.e.

π(R²-r²) B=π (R₀ ²-r₀ ²)B₀ (14)

Wherein, R₀For ring base radius, r₀For ring base inside radius, B₀For ring base height, calculate according to formula (14) and obtain outside ring Radius R and inside radius r:

$R=({R_0}^2-{r_0}^2)\frac{B_0}{2BH}+\frac{H}{2}---\left(15\right)$

$r=({R_0}^2-{r_0}^2)\frac{B_0}{2BH}-\frac{H}{2}---\left(16\right)$

And then obtain ring mean radius R_a:

$R_a=\frac{R+r}{2}=({R_0}^2-{r_0}^2)\frac{B_0}{2BH}---\left(17\right)$

In a preferred embodiment of the invention, in step s 302, nip for meeting and forge condition, radial feed speed v_rWith axial feed velocity v_aNeed to meet following condition:

$\frac{6.55\×{10}^{-3}{v}_m}{2{\mathrm{\πRR}}_m}{(R-r)}^2(1+\frac{R_m}{R_i}+\frac{R_m}{R}-\frac{R_m}{r})\≤v_r\≤\frac{2{{\mathrm{\β}}_r}^2{v}_m{R}_m}{2\mathrm{\π}R{(1+R_m/R_i)}^2}(1+\frac{R_m}{R_i}+\frac{R_m}{R}-\frac{R_m}{r})---\left(20\right)$

$\frac{0.00655v_m{B}^2}{\mathrm{\π}RStan\mathrm{\γ}}\≤v_a\≤\frac{2{{\mathrm{\β}}_a}^2{v}_{m}Stan\mathrm{\γ}}{\mathrm{\π}R}---\left(21\right)$

Wherein, v_mIt is 800～1600mm/s for king roller linear velocity and span, R_iFor core roller radius, β_rAnd β_aPoint Not being 0.3～0.4 for radial and axial angle of friction and span, S is that cone roller summit is to itself and ring outer diameter contact point Distance, θ is the semi-cone angle of cone roller.

As Figure 1-Figure 5, as a example by a certain 5m oversize 42CrMo ring radial-axial rolling, ring external diameter 5018mm, internal diameter 4498mm, highly 252mm, ring base external diameter 1900mm, internal diameter 900mm, highly 446mm.

Machine for rolling ring relevant parameter is: king roller radius R_m=675mm, core roller radius R_i=300mm, guide roller radius R_g= 250mm, semi-cone angle θ=17.5 ° of cone roller, distance S=1100mm on cone roller summit to itself and ring outer diameter contact point, king roller Linear velocity v_m=1600mm/s, radial and axial friction angle beta_rAnd β_aAll take 0.3；The coordinate of rotary shaft D is (-1200,925) mm, Coordinate (-2800, the 1825) mm of rotary shaft E, length L of bar JD₁=1200mm, length L of bar JG₂=1500mm, the length of bar DG Degree L=2250mm, hydraulic cylinder internal diameter r_h=150mm.

According to formula (19) and (20), owing to ring change in size is big, use segmentation feeding pattern, ring external diameter 3000mm with In, radial feed speed v_rControl at 3mm/s, axial feed velocity v_aControl at 2.5mm/s；Ring external diameter 3000～4200mm Within, radial feed speed v_rControl at 2mm/s, axial feed velocity v_aControl at 1.6mm/s；Ring external diameter 4200～ Within 5018mm, radial feed speed v_rControl at 1mm/s, axial feed velocity v_aControl at 0.8mm/s；Advise according to this feeding Journey, parameter is substituted into formula (15)～(19) can calculate ring expanding during the change of each size.

In conjunction with the above-mentioned armful of each dimensional parameters of roller mechanism, substitute into formula (8)～(11), obtain and embrace each angular relationship in roller mechanism； It is directed to roller angle [alpha] substitution formula (4) again and obtains the maximum section bending moment factorTake under 42CrMo high temperature low strain rate Yield strength σ_s=40MPa, takes oil pressure adjustment factor k_g=0.2, finally the above results is substituted into formula (13) can calculate as The operation of rolling shown in Fig. 5 embraces roller hydraulic cylinder oil pressure p process control curve, in conjunction with rolling with what ring outer diameter D (D=2R) changed Ring apparatus measuring and control data, embraces roller hydraulic cylinder oil pressure according to this curve conservative control, can realize operation of rolling stability contorting.

It should be appreciated that for those of ordinary skills, can be improved according to the above description or be converted, And all these modifications and variations all should belong to the protection domain of claims of the present invention.

Claims (5)

1. an oversize ring control surely rolls and embraces roller hydraulic design method, it is characterised in that comprise the steps:

S1, based on radial-axial rolling rigidity condition set up embrace a roller maximum guiding force mathematical model, embrace roller guide power F_gNot can exceed that institute Maximum guiding force F allowed_g-max, i.e.Wherein, B is ring axial height, and H is ring Radial thickness, σ_sIt is material yield strength, R_aIt is the mean radius of ring,It it is the maximum section bending moment factor；

S2, combine radial-axial ring rolling mill embrace roller mechanism set up embrace a roller hydraulic cylinder oil pressure cntrol mathematical model, embrace a roller mechanism include embrace Roller, rotary swinging arm structure DGJ and armful roller hydraulic cylinder EJ, embrace a roller and be arranged at the G axle of rotary swinging arm structure DGJ, can revolve around G axle Turning, rotary swinging arm structure DGJ can rotate around D axle, embraces roller hydraulic cylinder EJ for embracing roller and provides enclasping force,

Its one end is connected with the J axle of rotary swinging arm structure DGJ, and the other end can rotate around E axle, embraces oil pressure in roller hydraulic cylinderWherein, k_gBeing oil pressure adjustment factor, take 0.1～0.5, L is bar DG Length, γ is ∠ DGO₁Supplementary angle, O₁It is the center of ring, r_hIt is to embrace roller hydraulic cylinder internal diameter, L₁Being the length of bar JD, δ is ∠ The angle of DJE；

S3, the comprehensive radial-axial rolling expanding Activity design of process ring embrace roller hydraulic cylinder oil pressure process control curve:

During S301, radial-axial rolling, ring change in size need to meet constant-volume principle, ring base size try to achieve outside ring Radius R and inside radius r, and then obtain ring mean radius R_a,

In S302, the operation of rolling, ring radial thickness H and ring axial height B are calculated by following formula respectively:

$H=H_0-{\∫}_0^t{v}_{r}dt---\left(18\right)$

$B=B_0-{\∫}_0^t{v}_{a}dt---\left(19\right)$

Wherein, v_rFor radial feed speed, v_aFor axial feed velocity, t is rolling time；

S303, determine suitable feed speed after, calculate ring expanding during the change of each size, in conjunction with embracing a roller mechanism Each dimensional parameters, obtains and embraces each angular relationship in roller mechanism, obtain the maximum section bending moment factor in conjunction with guide roller angle [alpha]The above results is substituted into formula (13), calculates armful roller hydraulic cylinder with the change of ring outer diameter D in the operation of rolling Interior oil pressure p process control curve, in radial-axial rolling production process, in conjunction with rolling ring apparatus measuring and control data, the most program control according to this Yeast production line conservative control embraces roller hydraulic cylinder oil pressure, to realize operation of rolling stability contorting.

The most according to claim 1 armful of roller hydraulic design method, it is characterised in that step S1 specifically includes following steps:

S101, assume ring radial direction pass and axially pass position retrained by fixing end, embrace the enclasping force of roller for pointing to ring The concentration power at part center, is calculated for simplifying, takes 1/2nd models and carry out force analysis, solved by force method, available ring Section turn momentExpression formula:Wherein, F_gFor embracing the roller guiding force to ring,For cross section The moment of flexure factor, its expression formula is about embracing roller guide angle α and angle, ring sectional positionFunction:

S102, for meeting rigidity condition, cross section maximum stress in bend σ_maxShould be less than material permissible bending stress [σ], i.e.

Wherein, W_zIt is bending sections coefficient, for square-section, It is maximum section bending moment,And the maximum section bending moment factorCalculated by following expression formula:

[σ] is material permissible bending stress, yield strength σ of drawing materials_s, i.e. [σ]=σ_s；

S103, for ensureing to avoid ring to occur plastic instability to deform because rigidity condition cannot be met during radial-axial rolling, Embrace roller guide power F_gNot can exceed that maximum guiding force F allowed_g-max。

The most according to claim 1 armful of roller hydraulic design method, it is characterised in that step S2 specifically includes following steps:

S201, for realizing statics balance, condition need to be met: F_pL₁Sin δ=F_gLsin γ (6), wherein, F_pIt it is cylinder pressure；

In conjunction with cylinder pressure computational methods, in obtaining hydraulic cylinder, oil pressure expression formula is:

According to geometrical relationship, the expression formula that solves of related angle γ and δ in armful roller mechanism can be calculated and be respectively as follows:

$\mathrm{\γ}=\mathrm{\π}-\arccos \frac{L^2+{(R_g+R)}^2-{(R+R_m-x_D)}^2-{y_D}^2}{2L(R_g+R)}---\left(8\right)$

$\mathrm{\δ}=\arccos \frac{{L_1}^2+{\left(x_D+L_1{\mathrm{sin\α}}_D-x_E\right)}^2+{\left(y_D-L_1{\mathrm{cos\α}}_D-y_E\right)}^2-{\left(x_D-x_E\right)}^2+{\left(y_D-y_E\right)}^2}{2L_1\sqrt{{\left(x_D+L_1{\mathrm{sin\α}}_D-x_E\right)}^2+{\left(y_D-L_1{\mathrm{cos\α}}_D-y_E\right)}^2}}---\left(9\right)$

Wherein, R_gIt is to embrace roller radius, R_mIt is king roller radius, x_DAnd y_DIt is the coordinate of rotary shaft D, x_EAnd y_EIt it is the seat of rotary shaft E Mark, α_DIt is the position angle of bar DG, α_DCalculated by following formula:

${\mathrm{\α}}_D=\arctan \frac{R+R_m-x_D}{y_D}+\arccos \frac{{y_D}^2+{(R+R_m-x_D)}^2+L^2-{(R_g+R)}^2}{2L\sqrt{{y_D}^2+{(R+R_m-x_D)}^2}}+\arccos \frac{L^2+{L_1}^2-{L_2}^2}{2{\mathrm{LL}}_1}---\left(10\right)$

Wherein, L₂It is the length of bar JG；

Embrace roller guide angle α to be solved by following formula:

$\mathrm{\α}=\arctan \frac{y_D}{R+R_m-x_D}+\arccos \frac{{y_D}^2+{(R+R_m-x_D)}^2+{(R_g+R)}^2-L^2}{2(R_g+R)\sqrt{{y_D}^2+{(R+R_m-x_D)}^2}}---\left(11\right)$

According to equation (5) and (7), can show that embracing a roller hydraulic cylinder oil pressure p need to meet following condition:

During S202, radial-axial rolling, when embracing, roller pressure is excessive, the ring easily plastic instability because of insufficient rigidity,

Causing ring to be crushed to scrap, when embracing, roller pressure is too small, ring easily double swerve, ring time serious because enclasping force is not enough Part is as in irregular shape and scrap, and therefore, suitable enclasping force is to ensure that the key of ring stable rolling, according to above-mentioned Theoretical Calculation, in embracing roller hydraulic cylinder, oil pressure p is designed by following formula:

The most according to claim 1 armful of roller hydraulic design method, it is characterised in that in step S301, ring change in size Constant-volume principle need to be met, i.e.

π(R²-r²) B=π (R₀ ²-r₀ ²)B₀ (14)

Wherein, R₀For ring base radius, r₀For ring base inside radius, B₀For ring base height, calculate according to formula (14) and obtain ring outer radius R and inside radius r:

$R=({R_0}^2-{r_0}^2)\frac{B_0}{2BH}+\frac{H}{2}---\left(15\right)$

$r=({R_0}^2-{r_0}^2)\frac{B_0}{2BH}-\frac{H}{2}---\left(16\right)$

And then obtain ring mean radius R_a:

$R_a=\frac{R+r}{2}=\left({R_0}^2-{r_0}^2\right)\frac{B_0}{2BH}---\left(17\right)$

The most according to claim 1 armful of roller hydraulic design method, it is characterised in that in step s 302, for meet nip and Forge condition, radial feed speed v_rWith axial feed velocity v_aNeed to meet following condition:

$\frac{6.55\×{10}^{-3}{v}_m}{2{\mathrm{\πRR}}_m}{\left(R-r\right)}^2\left(1+\frac{R_m}{R_i}+\frac{R_m}{R}-\frac{R_m}{r}\right)\≤v_r\≤\frac{2{{\mathrm{\β}}_r}^2{v}_m{R}_m}{2\mathrm{\π}R{\left(1+R_m/R_i\right)}^2}\left(1+\frac{R_m}{R_i}+\frac{R_m}{R}-\frac{R_m}{r}\right)---\left(20\right)$

$\frac{0.00655v_m{B}^2}{\mathrm{\π}RStan\mathrm{\γ}}\≤v_a\≤\frac{2{{\mathrm{\β}}_a}^2{v}_{m}Stan\mathrm{\γ}}{\mathrm{\π}R}---\left(21\right)$

Wherein, v_mIt is 800～1600mm/s for king roller linear velocity and span, R_iFor core roller radius, β_rAnd β_aIt is respectively footpath Being 0.3～0.4 to axial rub angle and span, S is the cone roller summit distance to itself and ring outer diameter contact point, θ It it is the semi-cone angle of cone roller.