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A Study on Prediction of Wear A Study on Prediction of Wear Progress of Railway WheelProgress of Railway Wheel
“Long-term endurance test” running at 240 km/h(from Sept. 1983 till Sept. 1984)
Morioka
Omiya
on Tohoku Shinkansen line
(465 km long)
Open on 1982(JNR)
Ueno
1
Background
Katsuya Tanifuji Niigata University
Japan
Test trainTest train((Type 925 electric and track inspection train)
q
2
6-car train
Test runningPeriod: 1 yearRunning distance:
total 268 000 km
Bogie features○ with side bearers○ wheel of 1/40 conical tread
Niigata University
Wheel shape and object parameters Wheel shape and object parameters
Tread wear
Flange wearδ, (WF)Flange angleαF
New
Neutral point
Worn WT Tread shape
3
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Comparison of flange wear Comparison of flange wear among wheelset positionsamong wheelset positions
4
=268x103 km
30x103 km
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Tread wearWT
Flange wear
ρT
Radius of curvatureWF
New
Flange wearFlange wear
WF at the height of HF=21 mm
Flan
ge w
ear
WF
mm
5
δ
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Tread wearWT
ρT
Radius of curvatureFlange angleαF
New
Flange angleFlange angle
Mean value of 48 wheels
6
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Profile of Profile of tread weartread wear
ρTFlange angleαF
Tread wear shape
ρT
Radius of curvatureFlange angleαF
New
Mean value of 48 wheelsW
T
7
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ρTFlange angleαF
Tread wearWT
ρT
Radius of curvatureFlange angleαF
New Tread wearTread wearat neutral pointat neutral point
WT
8
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Flow chart for wear predictionFlow chart for wear prediction
Start
End
SIMPACK
Vehicle model
Simulation onmain line & cross-over
Wear process fortread & flange
Reach to target distance?
Update ofwheel profile
Data ofvehicle & track
Data ofwheel profile
Yes
No every 10000 km
9
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268000km走行後
新品形状NewWorn
( )1 1 2 2T TWI k T Tγ γ= +・ Tread wear(Elkins & Eickoff)
T1,T2: Creep force: Creepage1 2,γ γ
Wear indicesWear indices
・ Flange wear(Heumann)
( )F F F FWI k Fμ ψ= : Coefficient of friction : Flange force: Attack angle
FμFFψ
10
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Wear process on treadWear process on tread
Running simulationwith SIMPACK
① Contact position and wear index
30
40
50
60
70
80
90
100
-5 0 5 10 15 20 25 30Time [s]
Posi
tion o
n w
heel [m
]
Contact position
0
5
0 5 10 15 20 25 30Time [s]
WI FW
I T
Wear index
Whe
el
11
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[ ][ ]
( ) [ ]
0.25 / : 100
25.0 / :100 200
1.19 154 / : 200
T
T
T
F D F
F D F
F D F
δ
δ
δ
= <
= ≤ <
= − ≥
N
N
N
where F=T1γ1+T2γ2, D: Wheel diameter [mm]
: Interim wear thickness [mm] Tδ
Interim wear based on Pearce, et al.
Wear process on treadWear process on tread
Accumulationinto 5 mm partitions
Hi
Position on wheel [mm]
② Conversion to wear & accumulation
12
・ Wear thickness Ti T icΔ Η= ⋅
Tc :Coefficient determined from measured data at running distance 60 000 km
・ Smoothing of distribution
(2) Smoothing ofby polynomial
TiΔ ′
Wear process on treadWear process on tread
( )1 1 3Ti Ti Ti TiΔ Δ Δ Δ− +′ = + +(1) Averaging among 3 partitions
Position on wheel [mm]95~10085~9075~8065~7055~6045~50
バック面からの距離 [mm]45 50 55 60 65 70 75 80 85 90 95 100
③ Distribution of wear thickness
13
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Wear process on Wear process on flangeflange
Wear index
F F FWI Fμ ψ=
100 5 15Time [s]
0
50
100
150
WI F
100 5 15
0
10
-10
[mra
d]
Left wheelRight wheel
Simulation on cross-over section
14
Wear process on flangeWear process on flange
Position on wheel X
① Wear index in unit area wF
F Fw WI A=
A:Contact area
Accumulation of wF into partitions
FiWConversion to wear thickness
Fi F Fic WΔ = ⋅
:Fc Coefficient determined from measured data at running
distance 60 000 km
Wheel
FWI
Fw
Δx mm
Fw
Contact area
i②
15
③ Distribution of wear ΔFiNiigata University
Wear process on flangeWear process on flange
30
Wear distribution of WFi
30 35 45
25
20
15
Position on wheel [mm]
Hei
ght f
rom
flan
ge to
p [
mm
] Updated worn shape
Before update
Wear distributionaround flange root
Envelope of arcs with the radius of rail edge
representing ΔFi
Wear distribution of WFi
R13
16
Envelope of arcsrepresenting ΔFi
・With alignment irregularities・New rail of Type 60-kg
Main line
Sharp curve (cross-over section)
・ Straight track ・・・85%・ Curved track (R 4 000 m) ・・・15%
Running speed 40 km/h
5 m
R200 m
R200 m
65 m
Track conditions for simulationTrack conditions for simulation
Running speed 240 km/h
17
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Comparison of worn profiles between Comparison of worn profiles between prediction and measurement (wheel tread) prediction and measurement (wheel tread)
18
29.5
30.0
30.5
31.0
31.5
32.0
40 50 60 70 80 90 100Position on wheel [mm]
Heig
ht
from
fla
nge
top [
mm
]
1/40 Initial Profile
270 000 km180 000 km120 000 km 60 000 km
MeasuredCalculatedMeasuredPredicted
268 000
Initial profile
Comparison of worn profiles between Comparison of worn profiles between prediction and measurement (wheel flange) prediction and measurement (wheel flange)
25 30 35 40 45Position on wheel [mm]
25
30
20
15
10
5
0
Hei
ght f
rom
flan
ge to
p [m
m]
Initial profile60000km120000km268000km
PredictedMeasured
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Composition of wear profiles in equal scalesComposition of wear profiles in equal scales20
30
0
29.5
30.0
30.5
31.0
31.5
32.0
40 50 60 70 80 90 100Position on wheel [mm]
Height from flange top [mm]
1/40 Initial Profile
270 000 km180 000 km120 000 km 60 000 km
MeasuredCalculated
20
10
32
25 35 45
55 65 8575 10595
Position on wheel X [mm]Hei
ght f
rom
flan
ge to
p [m
m]
Flangewear
Treadwear
PredictedMeasured
Predicted flange shape in case ofPredicted flange shape in case ofworn outer rail in sharp curveworn outer rail in sharp curve
25 30 35 40 45Position on wheel [mm]
25
30
20
15
10
5
0
Hei
ght f
rom
flan
ge to
p [m
m]
60000 km
PredictedMeasured
New Worn
Outer rail in curved track
80°R10R30
Initial profile
268000 km
120000 km
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A wear progress of railway wheel was compared with measured data in a field test.
(1) For the tread wear, the general tendency is predictable although the wear is limited within the narrower region. It is thought that the difference comes from the rail profile and switch structure which are not considered in the simulation.
(2) For the flange wear, the predicted profile greatly depends on the inner side shape of the outer rail and tends to follow the worn rail shape in sharp curves.
Concluding remarksConcluding remarks22
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(3) This prediction can be useful, however, if we are interestedin the comparison of influences between bogie structures or between railway line conditions such as the rate of contained curved section.
Such examples are as follows:
Concluding remarksConcluding remarks23
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As mentioned above, it is perceived that practical rail profile is necessary to predict the real wear profile of wheel.
30
25 30 35 40 45
25
20
15
10
5
0
Position on wheel [mm]
Hei
ght f
rom
flan
ge to
p [m
m] Truck with bolster
and side bearers
Bolster-less truck
270000kmInitial profile
Initial profile(Arc profiled)60000km120000km270000km
Comparison of flange wears Comparison of flange wears between bogie structuresbetween bogie structures
(Conical)
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29.5
30.0
30.5
31.0
31.5
32.0
40 50 60 70 80 90 100Position on wheel [mm]
Heig
ht
from
fla
nge
top
[mm
]
0%15%30%
Initial Profile
270 000 km
180 000 km
60 000 km1/40
・ Rate of contained curved section (R4000 m )
Comparison of tread wears Comparison of tread wears between the rates of contained curved section between the rates of contained curved section
Initial profile
25
30 %
15 %0 %
Thank you for your kind attention
Niigata University