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BALL JOINT TRIBOLOGY
Powers and Sons LLC
PURPOSE
• TO ISOLATE CONTRIBUTIONS TO WEAR IN A BALL JOINT AND IMPROVE WEAR LIFE– LUBRICATION– BEARING MATERIAL– INTERNAL PRESSURE– SURFACE FINISHES– BALL HARDNESS
COMPLAINT BY CUSTOMER CODE PASSENGER CAR TIE ROD ENDS, PITMAN, IDLER ARMS
MILEAGE > 36,000 (17,518 RECORDS-SWIS DATA)
OTHER19%
RIDE/HANDLING4%
FREEPLAY22%
NOISE55%
Complaint Codes by Verbatims >36000 miles 3a130
Squeak
Noise
loose
rubbing
play
grinding
clunk
groan
vibration
worn
whines
other/no comment
SqueakNoiselooserubbingplaygrindingclunkgroanvibrationwornwhinesother/no comment
CAUSAL FACTORS RETURNED PARTS ANALYSIS
>36000 MILES 79 PIECES
GREASE46%
SEAL/FORGING8%
SEAL/STUD19%
CAP/FORGING14%
GOOD PART13%
P-DIAGRAM
Tie Rod Ball Joints
Noise Factors
Signal Factor (M)
Customer turns the wheel
Response (Y) Ideal Function
Error States
Transmit motion / load uniformly
Control Factors•Seal / forging interface•Seal material•Spin Pressure (cap to forging)•Cap to forging interface•Bearing surface finish•Selection of lubricant•Dunnage
•Seal / stud interface•Rotating torque of joints•Geometry•Bearing Material
•Excessive free play•Squeaks•High initial rotating torque
•Plant Grease on steering stop•Customer usage- Police/Taxi; demographics•Contamination•Proximity to brake rotor•In plant handling damage•Misdiagnosis
Design Variables Which Affect Ball Joint Life
• Seal Effectiveness• Grease Type• Static Internal Pressure• Bearing Material• Ballstud Surface Finish• Bearing Surface Finish
Development Testing
• Current industry standards– Bench wear test– Vehicle durability tests– Vehicle fleet tests
• Current designs pass ES and Vehicle Tests meaning current test methods are inadequate for identifying High Mileage concerns
Identify Team• Powers & Sons - Gene Messenger Talon Harvey
Chris Fink August Rose• Ford R&VT- Lou Mastrofrancesco • Dow Corning- Dr. Chris Hsu Gary McIntyre • Dupont Automotive• BASF• Bayer Chemical• Freudenburg - NOK• CAM-CAR TEXTRON Townsend Engineered Products• Defiance
BASELINE WEAR TEST SMOOTH NYLON 6/6, CLIMAX GREASE, Ra32 BALL, 10N NORMAL LOAD
TRAVEL +/-1MM, 5 Hz
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
150 15150 30150 45150 60150 75150 90150 105150 120150 135150 150150 165150 180150 195150 210150 225150
CYCLES
DR
AG
(N)
POINT AT WHICH WEAR BEGINS
Development of Test • Goal
– Develop Key Life Test– Simulate interaction between component materials in a ball joint
• First inputs were developed– The Normal load to apply between surfaces – Length of path travel – Frequency of path travel
• Then wear test began with the following DOE variables:– Grease type– Ballstud surface finish– Bearing material type – Bearing material surface finish
DOE - Full Factorial 32 runs (4x2x2x2) for Cameron Plint studyLoad of 10N, speed of 5 Hz, and stroke of +/- .5mm
Run Grease 0,1,2,3 Plastic 0,1 Stud finish 0,1 Bearing finish 0,11 Climax Nylon Ra32 smooth2 Climax Nylon Ra32 fine3 Climax Nylon Ra5 smooth4 Climax Nylon Ra5 fine5 Climax Acetal Ra32 smooth6 Climax Acetal Ra32 fine7 Climax Acetal Ra5 smooth8 Climax Acetal Ra5 fine9 Nye Nylon Ra32 smooth10 Nye Nylon Ra32 fine11 Nye Nylon Ra5 smooth12 Nye Nylon Ra5 fine13 Nye Acetal Ra32 smooth14 Nye Acetal Ra32 fine15 Nye Acetal Ra5 smooth16 Nye Acetal Ra5 fine17 LT278 Nylon Ra32 smooth18 LT278 Nylon Ra32 fine19 LT278 Nylon Ra5 smooth20 LT278 Nylon Ra5 fine21 LT278 Acetal Ra32 smooth22 LT278 Acetal Ra32 fine23 LT278 Acetal Ra5 smooth24 LT278 Acetal Ra5 fine25 PG75 Nylon Ra32 smooth26 PG75 Nylon Ra32 fine27 PG75 Nylon Ra5 smooth28 PG75 Nylon Ra5 fine29 PG75 Acetal Ra32 smooth30 PG75 Acetal Ra32 fine31 PG75 Acetal Ra5 smooth32 PG75 Acetal Ra5 fine
STATIC INTERNAL JOINT PRESSURE
• MEASURED JOINT ROT. TORQUE = .56 N-M• BEARING/BALL SURFACE CONTACT = 938 SQ. MM• EFFECTIVE TORQUE RADIUS = 9.44 MM• DRAG = TORQUE/RADIUS = .56/.00944 = 59N• NORMAL LOAD = DRAG/COEFF. OF FRICTION = 59/.02=2950N• STATIC INTERNAL JOINT PRESSURE= NORMAL
LOAD/SURFACE CONTACT AREA = 2950/938 = 3.15 N/SQ. MM
WORKING PRESSURE UNDER LOAD
• WORKING RADIAL LOAD = 600N• PROJECTED BALL AREA = 270 SQ.
MM.• PRESSURE = LOAD/AREA = 600/270 =
2.22N/SQ. MM.
NORMAL LOAD DETERMINATION
• TOTAL PRESSURE = STATIC + WORKING = 3.15+2.22 = 5.37 N/SQ. MM.
• CAMERON PLINT MEASURED CONTACT AREA = 2 SQ. MM
• NORMAL LOAD = PRESSURE * AREA = 5.37*2 = 10.74 N
• C-P WEAR TESTING RUN @ 10N NORMAL LOAD
TRAVEL DETERMINATION
• 90TH PERCENTILE ARTICULATION/ ROTATION TRAVEL < 6 DEGREES
• LINEAR TRAVEL FOR 22MM BALL AT 6 DEGREES = 1.17 MM
• C-P WEAR TESTING RUN AT +/- 1 MM TRAVEL
Climax Grease Failure Modes
• Oxidation instability• Poor moisture resistance• Reacts adversely under static design and
road load pressure
Oxidized Climax
CAMERON PLINT WEAR TEST NYLON 6/6, SMOOTH BEARING, Ra5 BALL STUD,
10N LOAD, +/- 1 MM TRAVEL, 5 HZ
0
0.5
1
1.5
2
2.5
3
3.5
0
3750
0
7500
0
1125
00
1500
00
1875
00
2250
00
2625
00
3000
00
3375
00
3750
00
4125
00
4500
00
4875
00
CYCLES
DR
AG
(N
)
LT2/78
CLIMAX
NYE 880
PG75
EFFECT OF BEARING MATERIAL ON WEAR LIFE CLIMAX GREASE SMOOTH NYLON 6/6 BEARING
Ra5 BALL STUD, 10N LOAD, +/- 1MM TRAVEL, 5HZ
0
0.2
0.4
0.6
0.8
1
1.2
0 75000 150000 225000 300000
CYCLES
DR
AG
(N
)
NYLON 6/6
ACETEL
EFFECT OF BALL SURFACE FINISH ON COEFFICIENT OF FRICTION CLIMAX GREASE, SMOOTH NYLON 6/6 PLATE,
10N NORMAL LOAD, +/- 1MM TRAVEL, 5HZ
0
0.2
0.4
0.6
0.8
1
1.2
0 60000 120000 180000 240000 300000 360000 420000
CYCLES
DR
AG
(N
)
Ra 5 BALL
Ra 32 BALL
EFFECT OF BEARING SURFACE FINISH ON WEAR LIFE ACETEL BEARING, Ra32 BALL, CLIMAX GREASE
10N LOAD, +/- 1MM, 5 Hz
0
0.05
0.1
0.15
0.2
0.25
0.3
0.35
0.4
0.45
150 60150 120150 180150 240150 300150
CYCLES
DR
AG
(N
)
FINE BEARING
SMOOTH BEARING
EFFECT OF NORMAL LOAD ON DRAG CLIMAX GREASE, SMOOTH NYLON 6/6 PLATE, Ra32 BALL
+/-1MM STROKE, 5 Hz
0
1
2
3
4
5
6
7
0 60000 120000 180000 240000 300000
CYCLES
DR
AG
(N
)50N NORMAL LOAD
10N NORMAL LOAD
BASELINE TO BEST 10N NORMAL LOAD, +/- 1MM STROKE, 5Hz
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
0
1500
00
3000
00
4500
00
6000
00
7500
00
9000
00
1E+0
6
1E+0
6
1E+0
6
2E+0
6
2E+0
6
2E+0
6
2E+0
6
2E+0
6
2E+0
6
CYCLES
DR
AG
(N
)
BASELINE GREASE, Ra32 BALL, SMOOTH NYLON 6/6 BEARING
PG75, Ra5 BALL, FINE ACETAL BEARING
39
CONTRIBUTION TO WEAR LIFE IMPROVEMENTSBASED UPON F DISTRIBUTION WITH TEST SUSPENDED AT 4000
MINUTES OR FAILURE
BEARING MATERIAL
STUD FINISH
BEARING FINISH
GREASE
Coefficient of Friction with Nylon 6/6 bearing and Ra32 ball stud at full temperature range measured on Cameron Plint at Dow
0
0.2
0.4
0.6
0.8
1
1.2
-60 -50 -40 -30 -20 -15 -5 0 15 25 30 40 50 65 75 85 95 10
Temperature (degrees Farenheit)
Co
effi
cien
t of F
rict
ion
ClimaxPG75LT 2/78NO-lube
Operating Temperature Range Rotating Torque on 2000 M.Y. Windstar Tie Rod Ends
0
20
40
60
80
100
120
140
160
-40 -20 0 20 40 80 100 120 140
Temperature (deg. Fahrenheit)
Ro
tati
ng
To
rqu
e (i
n. l
bs.
)
LT278
Climax
LT278/Climax
PG75/Climax
PG75
no grease
Climax grease, 10N load, 5Hz, Ra 32 on Smooth Nylon
0
1
2
3
4
5
6
7
8
9
10
0 10 20 30 40 50 60
time, min
For
ce, N
-70
-60
-50
-40
-30
-20
-10
0
Tem
pera
ture
, C
Frictional force, N
Temp, degree C
Point to fail
Conclusions from Cameron Plint
• Grease is primary constituent to improving joint life– Grease of choice is Dow Corning PG75
• Minor improvement is found with:– Acetel vs. Nylon 6/6– Polished ballstud surface – Fine texture bearing surface vs. current smooth
texture
• Lowering Ball Joint Internal Static Pressure will add to joint life
42
PN96 PITMAN ARM (3590) WARRANTY VS DATE OF PRODUCTION
0
5
10
15
20
25
30
35
Apr-9
6Jun
-96Au
g-96
Oct-96
Dec-96
Feb-97
Apr-9
7Jun
-97Au
g-97
Oct-97
Dec-9
7Feb
-98Ap
r-98
Jun-98
Aug-9
8Oct-9
8
DATE OF PRODUCTION
R/1
000
12MIS
18MIS
24MIS
REVISED GREASE FROM CLIMAX TO NYE 880
INTERIM GREASES VS BASELINE CLIMAX
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
400000 800000 1200000
CYCLES
DR
AG
(N
)
LT278/CLIMAX BLEND
92A/CLIMAX BLEND
CLIMAX GREASE
Design Solutions
• New Joint- bearings, grease, and ballstuddeveloped through:– Benchmarking– Cameron Plint Testing– ES Bench Testing– 150K mile AEMS fleet test