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ArcelorMittal Research June 2008
Optimization of lubrication and cooling in cold rolling
from 17 mars to 12 September 2008
- RFCS Optcoolub -
Tutor: NGO Quang Tien
Project leader : Nicolas LEGRAND
03/09/10
2
Presentation
• Name : BOULECHFAR Kamal
• Age: 26
• Nationality : Moroccan.
• Engineering school: Polytechnic School of the University of Orleans - Polytech’Orléans. “numerical simulation of mechanics “
• Graduation : DUT Thermal-Energy Engineering.
• My aim objective: Researches engineer in energetic-mechanics.
03/09/10
3
Internship : Background
This internship is carried out under the project Optcoolub
Optimize cooling systems in cold rolling in order to reduce water
consumption.
Make better lubrication on cold rolling mills
03/09/10
4
Internship : involvement
Analysis and optimization of lubricationand cooling system in cold rolling
The second aim is: Study of 13 roll cooling trials to understand cooling mechanism in roll
and strip ( HTC, Flux, T°).
Brno collaboration.Propose an optimum mill cooling configuration and confirm by pilot
trials ARsa.
The primary aim is : Developing / completing a modeling of cooling system : simulator Avilès
HTCs ( coolant-strip and coolant-roll )Rheology
Identify actions increasing the efficiency of cooling
03/09/10
5
The primary aim :
Developing / completing a modeling cooling system :
simulator Avilès
1) HTCs
2) Rheology
03/09/10
6
Advantage:It takes into account:
the parameters: , and νf(T)
influence of speed V
Thermal simulator: HTC(x) strip-coolant
)(Tk f
Stand n
wipingroll
Stand n+1
work roll work roll
HTC(x)
strip
x
x
Stand n
wipingroll
Stand n+1
work roll work roll
HTC(x)
strip
x
x
Improvement Heat Transfer Coefficient of strip-coolant interface along mill interstand
Current situation
3 Pr..
...)(L
VkC
x
Lxh
ff
EM
ν=
Weakness:It does not take into account:
Strip temperature
The water flow “explicitly”.
)Pr(T
Not Adapted for high temperatures of strip
Forced convection:
03/09/10
7
Thermal simulator: HTC(x)
What happen in a high strip temperature “Typically Ts >100°C at least “ ?
20°C 300°C
Problem
the material-coolant interface: vapor ,HTC The first appearance of bubbles
promotes the exchange of heat.
Higher the temperature higher the agitation of water “convection"
03/09/10
8
Thermal simulator: HTC(x)
Improvement When T°<100° : natural convection When T°>100° : Hodgson model
Weakness: “ to verify”It does not take into account:
influence of speed V
Advantage:It takes into account:
Strip temperature
The water flow.
example of strip temperature evolution
Evolution of HTC and Temperature along the strip
5000
15000
25000
35000
45000
55000
65000
75000
85000
95000
0.01 0.11 0.21 0.31 0.41
X(m) strip
HT
C
60
80
100
120
140
160
180
200
220
240
Te
mp
eratu
re °C
HTC coupling Hodgson and currentmodel
current model in simulator
surface temperature
03/09/10
9
Thermal simulator: Rheology
Current situation
Strip heat transfers in the roll bite:
strip plastic yield stress
( ) ( ) ECeBA xDxx +−+= − )(
0 1 εεσWe use the SMATCH law
Weakness: “ to verify”Does not take into account
The strain rate
Temperature
Plastic deformation Frictional heat Heat conduction
03/09/10
10
Thermal simulator: Rheology
Problem : the graphics show that strip rheology depends on the strain rate
We made those experiences for 3 steel grades of AVILES.
To validate the LUCY-BALISTIK model.
Influence of speedOur experiment
Influence of temperatureLiterature data
03/09/10
11
Thermal simulator: Rheology
Advantage predicting precisely the evolution of metal hardness along the rolling mill
Improvement
Integrate LUCY-BALISYIK model in our simulator:
03/09/10
12
Second aim is:
Study of 13 roll cooling trials to understand cooling
mechanism in roll and strip ( HTC, Flux, T°).
Propose an optimized mill cooling configuration and
confirm by pilot trials ARsa.
03/09/10
13
Conditions defined for realization at stand #4 of Aviles TDM2
Brno has characterized 13 roll cooling configurations for Optcoolub project
03/09/10
14
Method of operating results
S∂
Heat flux variation as a function of time
A specific program was developed to extractFlux and temperature measured under thedirect spray during the tests.
Variation de flux et de température en fonction de temps
0
20
40
60
80
100
120
140
21950 22000 22050 22100 22150 22200 22250 22300 22350 22400
Température en (°C)
Pa
s d
e t
em
ps
0
200
400
600
800
1000
1200
1400
Flu
x c
ylin
dre
en
kW/m
²
temperaturePhi
study area
S∂ S∂ S∂
Time
Tem
pera
ture
03/09/10
15
Flux en fonction de la tmpérature Moyenne de surface de cylindre
0
500
1000
1500
2000
2500
0 50 100 150 200 250
Température moyenne de surface (°C)
flu
x (k
w/m
²)
Phi(T)
Logarithmique(Phi(T))
AV13-4
)(THTC
)(Tϕ
Evolution of Flux and HTC with a temperature of the cylinder
HTC mesuré et HTC Loi en fonction de la température moyenne de surface de cylindre
0
5000
10000
15000
20000
25000
0 50 100 150 200 250 300
Température moyenne de surface cyl °C
HT
C (
w/m
²K)
HTCmoy w /m ²K
Flux dependency to roll surface temperature is higher
03/09/10
16
Results with our analysis
Results with Brno analysis ±500: 13- 12- 8- 6 - 11
HTC average for each configuration “ position 4” at Twater = 0°c
Results obtained with Brno analysis
0
2000
4000
6000
8000
10000
12000
14000
16000
18000
20000
AV1
AV2
AV3
AV4
AV5
AV6
AV7
AV8
AV9
AV10
AV11
AV12
AV13
HT
C m
oy
en
ne
+- 200
+- 500
Results with Brno analysis ±200: 13- 6- 8- 12 - 9
Configuration common among all tests: 13-6-12
HTC average for each configuration
0
2000
4000
6000
8000
10000
12000
HT
C (
w/m
²K)
AV
4-1
AV
4-2
AV
4-3
AV
4-4
AV
4-5
AV
4-6
AV
4-7
AV
4-8
AV
4-9
AV
4-1
0
AV
4-1
1
AV
4-1
2
AV
4-1
3
HTC moyenne pour chaque essai position 4
HTC moyenne
03/09/10
17
)(Tϕ
If we use the flux as an indicator of the efficiency of cooling, somme differences in the classification are obtained(compared to classification with HTC)
However, we can conclud that config. N°6 is a good configuration as already concluded by Brno
Average flux for each configuration
0
200
400
600
800
1000
1200
1400
1600
1800
Flu
x m
oy
(w/m
²)
AV
4-1
AV
4-2
AV
4-3
AV
4-4
AV
4-5
AV
4-6
AV
4-7
AV
4-8
AV
4-9
AV
4-10
AV
4-11
AV
4-12
AV
4-13
Mean heat Flux for each test. Sensor n°4
Phi moyenne
03/09/10
18
-300 -250 -200 -150 -100 -50 0 50 100 150 200 250 300
Position [mm]
0
100
200
300
400
500
600
700
800
900
1000
1100
1200
1333.3
Liq
uid
lev
el [
l/m
in.m
]
Liquid level (VK=32.30%) Mean value (994.41 l/min.m)
Roll surface
Valeurs de HTC et Phi en fonction de la position du capteur sur la largeur
HT
C (
W/m
²°C
)
ou
P
hi (
10.k
W/m
²)
phi a 100°C
HTC à 100°C
N°13
Uniformity of HTC with distribution of flow
Conclusions : globally, when the flow is strongly heterogeneous, the HTC seems heterogeneous also,but HTC does not follow irregularities of the flow
Valeurs de HTC et Phi en fonction de la position du capteur sur la largeur
0
2000
4000
6000
8000
10000
12000
-250 -200 -150 -100 -50 0 50 100 150 200
HT
C (
W/m
²°C
) o
u P
hi (1
0.k
W/m
²)
-225
-150
-100
-50
0
50
100
150
HTC w/m²°C
03/09/10
19
Conclusion
1er aim : thermal simulator
Improvement of inter-stand heat transfer model
The rheology experiments have been done
2nd aim : optimized mill cooling configuration
Analysis of 13 roll cooling trials.
Experiment planning has been done.
03/09/10
20
In Progress……..
• Achievement of simulator• The second aim:
# To find out an optimized mill cooling configuration “pilot experiment” .
Comparison of 6 roll cooling configurations:
1test with HTRC 6 test with nozzles
The test plan : ready
Monitoring and analysis of tests : begin next week
Synthesis of testes and conclusion: next weeks