smt masta training manual - 캐드앤그래픽스 of masta.pdf · gear iso6336 safety factors input...
TRANSCRIPT
©SMT 2006
Slide 1
MASTA
MASTA
Th
e M
ost
Po
werf
ul S
oft
ware
fo
r T
he M
ost
Po
werf
ul S
oft
ware
fo
r
Tra
nsm
issio
n
Tra
nsm
issio
n
Desig
n/D
evelo
pm
en
t/M
an
ufa
ctu
rin
gD
esig
n/D
evelo
pm
en
t/M
an
ufa
ctu
rin
g
©SMT 2006
Slide 2Mission of MASTA System
Mission of MASTA System
Mission of MASTA System
1.1.able to identify and fix Design W
eakness as
able to identify and fix Design W
eakness as
early as possible
early as possible
2.2.able to reduce Development Tests as much
able to reduce Development Tests as much
as possible
as possible
3.3.able to identify design inherited
able to identify design inherited
Manufacturing Problems at design stage
Manufacturing Problems at design stage
4.4.able to fix Production Problems quickly
able to fix Production Problems quickly
5.5.easy to use and no need for full time user
easy to use and no need for full time user
Maximise Perform
ance at Minimum Cost & Time
©SMT 2006
Slide 3
Versions
Versions
Versions
��Automotive Version:
Automotive Version:
��Complete System from Drive Line Compatibility to Gear
Complete System from Drive Line Compatibility to Gear
Manufacturing
Manufacturing
��From Passenger Car application to Heavy Duty
From Passenger Car application to Heavy Duty
Application
Application
��Aerospace Version
Aerospace Version
��From Design to Gear Manufacturing
From Design to Gear Manufacturing
��Industrial Version
Industrial Version
��From High Speed Application to Low Speed Application
From High Speed Application to Low Speed Application
��Design for Ultra
Design for Ultra-- low Noise Application
low Noise Application
©SMT 2006
Slide 4
DLC M
odule
(Drive Line Compatibility)
Use existing transmission & axle due
to compatibility (Automotive version only)
Decide gear ratios to meet VP, cost &
fuel consumption (Automotive version only)
MASTA
MASTA
Modules of MASTA
Modules of MASTA
Modules of MASTA
VPS M
odule
(Vehicle Perform
ance Sim
ulation)
Design &
Analysis Modules
Modify existing transmission & axle
to achieve compatibility
Design new transmission & axle to
maximise the perform
ance at
minimum cost and time
NVH Modules
Gear Manufacturing
Modules
FMA ---Failure Mode Analysis for
major components
Achieve good gear quality at low
cost
©SMT 2006
Slide 5
Technologies of MASTA
Technologies of MASTA
Technologies of MASTA
System Technology
System Technology
��Complete System Static Analysis (Non
Complete System Static Analysis (Non-- Liner)
Liner)
��System Dynamics
System Dynamics
Component Technology
Component Technology
��Leading gear technology
Leading gear technology
��Advanced shaft technology
Advanced shaft technology
��FEA based casing technology
FEA based casing technology
��Latest bearing technology
Latest bearing technology
Unique Gear Manufacturing Technology
Unique Gear Manufacturing Technology
��For
For Hobbing
Hobbing/Shaping/Shaving process
/Shaping/Shaving process
��For
For Hobbing
Hobbing/Shaping/Grinding process
/Shaping/Grinding process
��For Spiral bevel and Hypoid gear manufacturing
For Spiral bevel and Hypoid gear manufacturing
©SMT 2006
Slide 6
Capability of MASTA
Capability of MASTA
Capability of MASTA
1.1.
Vehicle Perform
ance Simulation & Drive Line
Vehicle Perform
ance Simulation & Drive Line
Compatibility Check (for Automotive version only)
Compatibility Check (for Automotive version only)
2.2.
Transmission Design
Transmission Design
3.3.
Transmission Analysis and Optimisation
Transmission Analysis and Optimisation
4.4.
Gear Design for Manufacturing
Gear Design for Manufacturing
5.5.
Hobbing
Hobbing, Shaping, Shaving Cutter and Grinding Wheel
, Shaping, Shaving Cutter and Grinding Wheel
Design for Cylindrical Gears
Design for Cylindrical Gears
6.6.
Cutter Design and Machine Setting for Bevel/Hypoid
Cutter Design and Machine Setting for Bevel/Hypoid
Gears
Gears
7.7.
Simulation for Gear
Simulation for Gear Manufactruing
ManufactruingProcess
Process
Hobbing
Hobbing/Shaping/Shaving and
/Shaping/Shaving and
Hobbing
Hobbing/Shaping/Grinding Process
/Shaping/Grinding Process
©SMT 2006
Slide 7
VPS & DLC
VPS & DLC
VPS & DLC
©SMT 2006
Slide 8
ECE R 101 - urban and extra urban cycles
0
20
40
60
80
100
120
140
0200
400
600
800
1000
1200
Tim
e (s)
Speed (km/h)
engine
clutch
gearbox
final drive
fuel economy
vehicle
drive cycle
drive cycle
%
gradient
Predicted Acceleration From Rest
0
25
50
75
100
125
150
010
20
Tim
e (s)
Vehicle Speed (km/h)
Gearbox A
Gearbox B
Gearbox C
vehicle acceleration
vehicle acceleration
wheel
Model Structure
Model Structure
Model Structure
©SMT 2006
Slide 9
Inputs
Inputs
Inputs
��Evaluation of different options
Evaluation of different options
Driveline Ratios
0
2468
10
12
14
16
1st
2nd
3rd
4th
5th
Driveline Ratio
Gearbox A
Gearbox B
Gearbox C
©SMT 2006
Slide 10
Traction Diagram
Traction Diagram
Traction Diagram
Case Study Engine (2 litre) Curves
0
20
40
60
80
100
120
140
160
180
200
01000
2000
3000
4000
5000
6000
7000
Engine Speed (rpm)
Torque (Nm)
010
20
30
40
50
60
70
80
90
100
Power (kW)
Torque
PowerVehicle tractive effort and resistance
02468
10
050
100
150
200
Vehicle Speed (km/h)
Tractive Force (kN)
1st
2nd
3rd
4th
5th
Grade (0%)
Grade (5%)
Grade (10%)
Grade (15%)
Grade (20%)
Grade (25%)
Outputs
Outputs
Outputs
©SMT 2006
Slide 11
��Option C excluded as top speed too low
Option C excluded as top speed too low
Predicted Acceleration From Rest
0
25
50
75
100
125
150
175
010
20
30
40
50
60
Tim
e (s)
Vehicle Speed (km/h)
Gearbox A
Gearbox B
Gearbox C
Outputs
Outputs
Outputs
©SMT 2006
Slide 12
Drive Cycle Simulation
Drive Cycle Simulation
Drive Cycle Simulation
Outputs
Outputs
Outputs
©SMT 2006
Slide 13
Engine Map
Engine Map
Engine Map
Outputs
Outputs
Outputs
©SMT 2006
Slide 14
Fuel Economy
Fuel Economy
Fuel Economy
Fuel Economy over ECE R 101 Urban Drive Cycle
05
10
15
20
25
30
Land Rover, Discovery, (4.0)
Mazda M
PV (3.0)
Jaguar XJ6 (3.0)
Toyota Camry (2.4)
Ford Focus (1.6)
Peugeot 206 (1.6)
Peugeot 206 (1.4)
Ford Fiesta (1.4)
Toyota Prius (hy.)
Honda Insight (hy.)
Fuel Economy (km/litre)
Outputs
Outputs
Outputs
©SMT 2006
Slide 15
Acceleration
Acceleration
Acceleration
Acceleration & Elasticity Performances
02468
10
12
14
0-50
0-100
80-120,
5th
60-100,
5th
60-100,
4th
50-80, 4th
50-80,
3rd
Speeds km/h
Time (s)
Gearbox A
Gearbox B
Outputs
Outputs
Outputs
©SMT 2006
Slide 16
Model for AMT shift quality
Model for AMT shift quality
Outputs
Outputs
Outputs
©SMT 2006
Slide 17
Shift Simulation
Shift Simulation
Outputs
Outputs
Outputs
©SMT 2006
Slide 18
Transmission Design
Transmission Design
For any Arrangement
For any Arrangement
©SMT 2006
Slide 19
Truck Applications
Truck Applications
Truck Applications
Track Transmission with
Planetary Range Change
©SMT 2006
Slide 20
Truck Application
Truck Application
Truck Application
Track Transmission
with Range Change
©SMT 2006
Slide 21
Passenger Car Applications
Passenger Car Applications
Passenger Car Applications
Front Drive Transmission
©SMT 2006
Slide 22
Passenger Car Applications
Passenger Car Applications
Passenger Car Applications
Front Drive Transmission
©SMT 2006
Slide 23
Complex Automatic Transmission
Complex Automatic Transmission
Complex Automatic Transmission
©SMT 2006
Slide 24
Aerospace Applications
Aerospace
Aerospace Applications
Applications
Simplified demonstration models, client
confidentiality maintained
©SMT 2006
Slide 25
Track Applications
Track Applications
Track Applications
©SMT 2006
Slide 26
Marine Applications
Marine Applications
Marine Applications
Very wide and big helix angle gear
©SMT 2006
Slide 27
Analysis
Analysis
For any Arrangement
For any Arrangement
©SMT 2006
Slide 28
Analysis based on Actual Duty Cycle
Analysis based on Actual Duty Cycle
Analysis based on Actual Duty Cycle
©SMT 2006
Slide 29
�Component Stiffness and Masses
Underlying Analysis Model
Underlying Analysis Model
•Shafts –classic finite element beam model (or
derived from full FE model for complex 3-D shape,
e.g. to capture gear blank deflection)
•Bearings –stiffness derived from non-linear load-
deflection models (use Herztiancontact theory &
bearing internal geometry, ref T. Harris)
•Gears –mesh stiffness and line of action derived
from gear geometry
•Housing & complex shafts –reduced stiffness and
mass derived from full FE models
©SMT 2006
Slide 30
Underlying Analysis Model
Underlying Analysis Model
•Specialised Interface allows rapid
modelling of geared systems
•Component libraries and databases
•Fully integrated analysis & results display
©SMT 2006
Slide 31
�Powerflowanalysis to calculate all component speeds,
powers, torques
�System Finite Element Model created from Design Geometry
Underlying Analysis Model
Underlying Analysis Model
�System model retains all degrees of freedom, laterals, axial,
tilt, torsional
©SMT 2006
Slide 32
Validation MASTA vsMSC.NASTRAN
Shaft Deflection
Shaft Deflection
Shaft Deflection
Nominal X Bending Stress
05
10
15
20
25
30
35
050
100
150
200
250
300
Offset (mm)
Bending Stress (MPa)
MASTA X Bending Stress
Nastran |pt2 Bend Stress|
Nastran |pt4 Bend Stress|
Transaxle Input Shaft Deflection (x)
-250
-200
-150
-100
-500
50
100
150
050
100
150
200
250
300
350
Offset (m
m)
Displacement (um)
MSC-N
astran, spring m
odel
MASTA, full m
odel
MSC-N
astran, pinned
MASTA, pinned
©SMT 2006
Slide 33
Shaft Analysis
Shaft Analysis
Shaft Analysis
MASTA Shaft Forces and Fatigue Analysis
MASTA Shaft Forces and Fatigue Analysis
Qualitative Behaviour of Stresses in A Rotating
Shaft
Time
Stress
Bending Stress
Axial + Torsional S
tress
Total S
tress
Qualitative Behaviour of Stresses in A Rotating
Shaft
Tim
e
Stress
Equivalent Fully Reversing Stress
Goodman Diagram
vs Curves
Mean Stress
Alternating Stress
Yield Line (Langer)
Soderberg Line
Goodman Line
Gerber Curve
ASME Elliptic Curve
Bagci Curve
©SMT 2006
Slide 34
Fatigue/Lives/Scoring
Fatigue/Lives/Scoring
Fatigue/Lives/Scoring
•Various rating and lifingmethods
•Bearings, ISO + supplier
•Gears, ISO/AGMA +
experience/references/database
•Shafts, classic beam model fatigue
or use full FE
Gear ISO6336 Safety Factors
Input
Idler i/p
Idler o/p
PTO1
PTO2
Gen.
Pump.
Contact
Bending
Bearing Duty Cycle % Damages
Hyd
. Pum
p Le
ft
Hyd
. Pum
p Rig
ht
Gen
. Lef
t
Gen
. Right
Id
ler L
eft
Idler R
ight
Inpu
t Right
In
put L
eft
Upp
er P
TO1
Left
Upp
er P
TO1
Right
Upp
er P
TO2
Left
Upp
er P
TO2
Right
Description
Symbol
Wheel 2
Pinion
Description
Symbol
Wheel 2
Pinion
Torque (Nm)
T739.9309
265.2582
Speed (rpm)
n4301.8868
12000
Power (kW)
P333.3333
333.3333
Duration (hr)
100
100
Number of Cycles
NL
25811320.75
72000000
Description
Symbol
Wheel 2
Pinion
Percentage Damage
0%
0%
Factor Of Safety For Pitting
SH
1.36
1.26
Calculated Contact Stress (MPa)
σH
1187.5
1207.9
Nominal Contact Stress (MPa)
σH0
Description
Symbol
Wheel 2
Pinion
Percentage Damage
0%
0%
Factor Of Safety For Bending
SF
2.66
2.57
Tooth Root Stress (MPa)
σF
352.2
356.4
Nominal Tooth-Root Stress (MPa)
σF0
188.8
191.1
Bending Durability Results (ISO 6336-3)
Contact Durability Results (ISO 6336-2)
847.2461
Load Conditions & Inputs
Input Gear Train\W
heel to Pinion: ISO 6336 Rating Report
Load Case: Full Power In New Design State
©SMT 2006
Slide 35
�System Deflection
System Static Analysis
System Static Analysis
Calculation:
•Apply Input Torque
•Derived Gear Loads
•Calculate System Deflection
(non-linear force/load balance)
Results:
•Shaft loads and deflection
•Bearing loads,
misalignments & life
•Gear misalignment & life
Static deflection, zero to full load
©SMT 2006
Slide 36
System Deflections
System Deflections
System Deflections
•For lightweight aerospace transmission
it is important to include effects of
housing/support flexibility on internals
Gear Mesh Misalignment, FBetaX
Idler/I
nput
Inpu
t/PTO
1
PTO
1/PT
O2
IdlerO
utpu
t/Gen
. Gen
./Hyd
. Pum
p
Bearing Misalignment (mRad)
Hyd
. Pum
p Le
ft
Hyd
. Pum
p Rig
ht
Gen
. Lef
t
Gen
. Rig
ht
Idle
r Lef
t Id
ler R
ight
Inpu
t Right
In
put L
eft
Upp
er P
TO1
Left
Upp
er P
TO1
Rig
ht
Upp
er P
TO2
Left
Upp
er P
TO2
Rig
ht
•MASTA allows
inclusion of
housing flexibility
via reduced
stiffness imported
from housing FE
model
©SMT 2006
Slide 37
System Dynamics
System Dynamics
System Dynamics
Calculation:
•Static load condition provides
system stiffness
•Add mass to give dynamic model
•Solve multi-shaft system modes (or
single shaft if required)
•Forced excitation
Results:
•Modal Map, Mode shapes, Forced Response to Excitation,
Critical Speed Maps, Campbell Diagrams etc
System Dynamic Mode, full load condition
©SMT 2006
Slide 38
System Dynamics
System Dynamics
System Dynamics
Mode 2: torsionaldriveline
Mode 4: shaft bending mode
Fully Coupled Gearbox Modal Frequencies for
Cruise Condition
0
0.51
1.52
2.53
12
34
56
78
91011121314151617181920
Mode #
Frequency
Fully Coupled Gearbox Model Critical Speed
Map
00.5
11.5
22.5
3
1.0E+06
1.0E+07
1.0E+08
1.0E+09
1.0E+10
1.0E+11
Brg/Support Stiffness
Frequency
Mode1
Mode 2
Mode 3
Mode 4
Mode 5
Mode 6
Mode 7
Mode 8
•MASTA can run full coupled gearbox or
shafts in isolation
•Check excitations from shaft and gear
rotation speeds do not coincide with
modal frequencies
©SMT 2006
Slide 39
Advanced System Deflection
Advanced System Deflection
Advanced System Deflection
•Example showing use of MASTA
& FE for complex shaft shapes. A
truck planet carrier shaft.
•Complex geometry done in industry
standard CAD tools
©SMT 2006
Slide 40
Advanced System Deflection
Advanced System Deflection
Advanced System Deflection
•Example showing use of MASTA
& FE for complex shaft shapes. A
truck planet carrier shaft.
•Complex FEA done in industry standard
tools, e.g. NASTRAN or ANSYS
©SMT 2006
Slide 41
Advanced System Deflection
Advanced System Deflection
Advanced System Deflection
•MASTA interface to NASTRAN & ANSYSFE
©SMT 2006
Slide 42
Advanced System Deflection
Advanced System Deflection
Advanced System Deflection
•MASTA interface to NASTRAN & ANSYS FE
©SMT 2006
Slide 43
Gear Optimisation for High Perform
ance and Low Cost
Gear Optimisation for High Perform
ance and Low Cost
Gear Optimisation for High Perform
ance and Low Cost
©SMT 2006
Slide 44
Very Accurate Gear Rating for Life
Very Accurate Gear Rating for Life
Very Accurate Gear Rating for Life
Internal dynamic factor: method B & C
Face load factor: Method A & B
Nominal tooth-root stress: Method B & C
All other factors: Method B
©SMT 2006
Slide 45
Gear Rating to Scuffing
Gear Rating to Scuffing
Gear Rating to Scuffing
©SMT 2006
Slide 46
Gear Micro Modification
Gear Micro Modification
Gear Micro Modification
Define Micro Geometry
Lead
Profile
Bias
Total
©SMT 2006
Slide 47
Gear Micro Modification
Gear Micro Modification
Gear Micro Modification
Transmission Error & Contact Pattern (Predicted)
T.E. for all Load Case
C.P. @ 100% Load
C.P. @ 50% Load
C.P. @ 10% Load
©SMT 2006
Slide 48LTCA for Ultra-low Noise Gear
LTCA for Ultra
LTCA for Ultra-- low Noise Gear
low Noise Gear
High contact ratio: Industrial Gear
High contact ratio: Industrial Gear --set
set
©SMT 2006
Slide 49
Minimise
Minimise
Manufacturing Cost
Manufacturing Cost
©SMT 2006
Slide 50
Failure Mode Analysis for Major Components
Failure Mode Analysis for Major Components
Failure Mode Analysis for Major Components
Sort the major components by design lives to guide the investm
en
Sort the major components by design lives to guide the investm
ent of
t of
manufacturing process
manufacturing process
©SMT 2006
Slide 51
Design Gears for existing Hobs/Shapers
Design Gears for existing Hobs/Shapers
Design Gears for existing Hobs/Shapers
©SMT 2006
Slide 52
Gear Hob/Shaper Design
Gear Hob/Shaper Design
Gear Hob/Shaper Design
Maximise gear bending strength by
optimising cutter tip
©SMT 2006
Slide 53
HobbingCutter Simulation
Hobbing
HobbingCutter Simulation
Cutter Simulation
Gear rating based on the actual gear fillet
generated by the hobs
©SMT 2006
Slide 54
Shaping Cutter Simulation
Shaping Cutter Simulation
Shaping Cutter Simulation
Gear rating based on the actual gear fillet
generated by the shapers
©SMT 2006
Slide 55
Shaping/HobbingProcess
Shaping/
Shaping/ Hobbing
HobbingProcess
Process
Rapidly identify root causes and solutions to poor
Shaping/Hobbingquality
Profile
Lead
Pitch
©SMT 2006
Slide 56
Plunge Shaving Dynamics Simulation
Plunge Shaving Dynamics Simulation
Plunge Shaving Dynamics Simulation
To
fin
d o
ut
if t
he
ge
ar
is d
iffi
cu
lt t
o s
ha
ve
an
d a
lso
pro
vid
e
so
luti
on
if
the
re is
dif
fic
ult
y a
t g
ear
de
sig
n s
tag
e
Go
od
dy
na
mic
s:
no
dif
ficu
lty
in
sh
avin
g
©SMT 2006
Slide 57
Plunge Shaving Dynamics Simulation
Plunge Shaving Dynamics Simulation
Plunge Shaving Dynamics Simulation
Ve
ry b
ad
dyn
am
ics
, h
en
ce
very
po
or
sh
av
ing
qu
ality
To
fin
d o
ut
if t
he
ge
ar
is d
iffi
cu
lt t
o s
ha
ve
an
d a
lso
pro
vid
e
so
luti
on
if
the
re is
dif
fic
ult
y a
t g
ear
de
sig
n s
tag
e
©SMT 2006
Slide 58
Shaving cutter micro modification
Shaving cutter micro modification
Shaving cutter micro modification
A p
ow
erf
ul to
ol fo
r g
ea
r m
icro
mo
dif
ica
tio
n a
nd
he
at
tre
atm
en
t
dis
tort
ion
co
mp
en
sati
on
Profile
Lead
©SMT 2006
Slide 59
Spiral/Hypoid Gear Contact pattern
Spiral/Hypoid Gear Contact pattern
Spiral/Hypoid Gear Contact pattern
Contact pattern after assembly
Contact pattern in-service
Predict the contact pattern for given machine setting
©SMT 2006
Slide 60
Spiral/Hypoid Gear Ease off
Spiral/Hypoid Gear Ease off
Spiral/Hypoid Gear Ease off
Predict the actual gear tooth topology accurately
©SMT 2006
Slide 61
Spiral/Hypoid Pinion Finish Stock Distribution
Spiral/Hypoid Pinion Finish Stock Distribution
Even finish stock distribution makes cutter life longer,
connection between rough/finish fillet smoother, and …
…
©SMT 2006
Slide 62
Heat Treatment Distortion compensation
Heat Treatment Distortion compensation
Pinion flank is designed based on heat treated wheel
©SMT 2006
Slide 63
3D Simulation of Pinion cutting
3D Simulation of Pinion cutting
Connection
between rough
root and finish
filet
Check the gears
before starting any
machining
©SMT 2006
Slide 64
Summary
Summary
Summary
��Maximise/Upgrade the ratio=load/volume of transmission at minimu
Maximise/Upgrade the ratio=load/volume of transmission at minimum
m
cost and time cycle
cost and time cycle
��Improve Gear Contact Pattern and System Response to Improve
Improve Gear Contact Pattern and System Response to Improve
Noise/Vibration
Noise/Vibration
��Optimise Major Component Design to Maximise Life and Perform
ance
Optimise Major Component Design to Maximise Life and Perform
ance
��Minimise Manufacturing Cost
Minimise Manufacturing Cost
��Design gears using existing hobs and Shapers
Design gears using existing hobs and Shapers
��Predict failure modes of the major components at design stage
Predict failure modes of the major components at design stage
��Predict and fix potential gear manufacturing problems at design
Predict and fix potential gear manufacturing problems at design stage
stage
��Optimise gear cutter design at design stage (for cylindrical and
Optimise gear cutter design at design stage (for cylindrical and
bevel/hypoid gears)
bevel/hypoid gears)
��Simulate Manufacturing Process to identify and fix the root cau
Simulate Manufacturing Process to identify and fix the root causes of Gear
ses of Gear
quality in no time (for cylindrical and bevel/hypoid gears)
quality in no time (for cylindrical and bevel/hypoid gears)
MASTA has been used to
©SMT 2006
Slide 65
How to contact us?
How to contact us?
EE-- mails:
mails: [email protected]
Website:
Website: www.smartmt.com
www.smartmt.com
SMT Limited
SMT Limited
14 Regent Street
14 Regent Street
Nottingham
Nottingham
NG1 5BQ
NG1 5BQ
Tel: +44 (0) 115 941 9839
Tel: +44 (0) 115 941 9839
Fax: +44 (0) 115 950 9278
Fax: +44 (0) 115 950 9278