GKN Driveline is the world’s leading manufacturer of automotive driveline components like CVJ Systems, AWD Systems, Trans Axle Solutions and eDrive Systems. The global acting company has 22,000 people at 56 facilities in 22 countries working in partnership with vehicle manufacturers to develop driveshaft and geared component technologies for the future.
For all transmission systems, the task of the development is to satisfy customer requirements which partly act against each other. Systematically separate and balance design parameters regarding durability, NVH and efficiency to achieve biggest benefit at acceptable cost level. These various requirements and demands leads to challenging optimization work. Traditionally this challenge has been determine using existing designs or ideas based on experience and testing using simulation after design to verify changes.
The introduction of numerical optimization methods has significantly changed the way of transmission development. Best concept design that meets design requirements replacing time consuming and costly design iterations. This presentation will show how GKN Driveline, has integrated optimization techniques showing examples of recent development.
Speakers
Amelin Begovic, GKN Driveline Köping AB
4. 4
GKN Driveline – product segments
CVJ Systems AWD Systems Trans Axle Solutions eDrive Systems
CV Joints
Sideshafts
Propshafts
Transfer Units
AWD Couplings
Disconnects
Final Drive Units
Differentials
Limited Slip &
Locking Differentials
eAxles
eTransmissions
eMotors
5. 5
AWD Systems – global manufacturing
GKN Driveline Bowling Green
GKN Driveline Bruneck
GKN Driveline Köping
GKN Driveline Newton
GKN Driveline Tochigi
GKN Driveline Nagoya
GKN Driveline Shanghai
Europe
Americas
Asia Pacific
6. 6
AWD products
Rear Drive Unit
− Distributes the torque to the rearwheels
− Ratio > 1 = Reduces speed and increases torque
Rear Drive Module
Coupling
− Distributes the torque to the Rear Drive Unit
− Controlled by the vehicle via the ECU
Power Take off Unit
− Connected to the gearbox, normally to the differential carrier
− Ratio < 1 = Reduces torque and increases speed
8. 8
Solution – Dynamic Thinking
System approach
Proactive product development
Virtual analysis and simulation of complete driveline
Customer involvement
Design maturity
Shorter lead time
9. 9
Optimization work
Yesterday
New design start from existing ideas considering..
− Extreme torque requirements
− Packaging constrained enviroment
− Light weight requiremnts
− Design response
− … CAE done after CAD
Today
New design start from new enviroment with new ideas considering directly
− Extreme torque requirements
− Packaging constrained enviroment
− Light weight requirement
− Design response
− … CAE done before CAD Get new ideas
10. 10
Optimization analyzes – Workflow
Shorter lead time
Faster and more design loops
Design maturity
The optimization process speeds up
and make the product development
more efficient regarding time & cost
Best concept design that meets design
requirements replacing time
consuming and costly design iterations
Topology optimization towards variables
− Stiffness
− Eigen frequency
− Mobility
Generation of machining and manufactural design constraints
Design
Space
Stiffness opt
11. 11
OEM1: Frequency Response Analysis
Corrective action:
After evaluation of optimized FE Model, improvement of PTU fixation was identified
− By: Mobility analysis, Modal anlaysis, Strain energy evaluation
Implementation of additional fixation point between PTU cover and bracket
Issue:
Eigen frequency of the PTU due to the weakness of the PTU support
Firing frequency of customer diesel engine as a excitation
PTU propshaft connection producing resonance frequency
Software:
HyperMesh, OptiStruct
12. 12
Five accelerometers located at different positions, measuring the mobility
Each location is measured in x, y, z direction
Modal hammer test
FE model: 116 Hz Rig test: 114 Hz
Correlation with rig testing
1
23
4
5
Y X
Z
14. 14
Improvement and results
Requirement
First bending mode > 250Hz
Improvements
Implemented proposal as stiffener, supports
Vehicle validation showed improvement potential up to 264Hz
PTU (incl. internal parts)
Engine block
Transmission
Oil pan
1st eigenmode: 161Hz < 250Hz
PTU (incl. internal parts)
Improvements on bracket/cover
Engine block
Transmission
Oil pan
1st eigenmode: = 𝟏𝟔𝟏 × 𝟏. 𝟔𝟖 ≈ 𝟐𝟕𝟎𝐇𝐳 > 𝟐𝟓𝟎𝐇𝐳
15. 15
OEM 2: Weight reduction
Corrective action:
Material savings
Material distribution and balancing
Task:
Reduce the weight with equivalent or increased stiffness of torque tube
Software:
HyperWorks, OptiStruct
16. 16
Improvement and results
Baseline
− Weight: ~3500 gr
− Requirement: Eigen Frequency >148 Hz
Design space
− Considering manufacturing constraints
Topology optimization
Final design
− Weight: ~3200 gr
− Eigen Frequency: 541 Hz
Mass saving cca 12% considering manufacturubility, cost
Eigen Frequency requirement fullfiled
17. 17
OEM 3: Topology optimization
Corrective action:
Stiffer and robust structure
Task:
Increase stiffness
Fulfill mobility requirement
Increase dynamic performance of the housing
Investigate housing senstivity to torsional loading
Software:
HyperMesh, OptiStruct
18. 18
Mounting Mobility
The velocity response per unit force through a specified frequency range
Analysis used for the dynamic performance of housing stiffness
The force is measured in (m/s/N) at each mount and in each vehicle
translational direction
RBE2 (rigid) links
Nodesinthesplitplaneonboth
housingandcoverarefixatedinallDOF´s
FLH
FRH
RRH
RLH
19. 19
Mount support stiffness
Prediction of the FDU/RDU housing stiffness
Determination of static stiffness for each vehicle axis and at each mount
− General requirement for resulting displacement:
− Mount stiffness must be 10 times higher compared to static bushing stiffness
− Mount stiffness must be 5 times higher compared to dynamic bushing stiffness
BC (locked in x, y, z)
FRH RRH
RLHForce (FX, 1N) @ FLH mount
20. 20
Torsional sensitivity
Prediction of the FDU/RDU sensitivity to torsional loading
Determination of mount accelerations in all vehicle directions at all mounts
RBE2 (rigid) links
StubshaftslockedinrotationalDOF’s
Moment (1Nmm) @ pinion
FLH
FRH
RRH
RLH
21. 21
Tomorrow.. Start early
Customer involvement
Proactive product development risk management
Virtual analysis and simulation of complete driveline
Understand how design respons and transfer vibration further
Understand and consider manufacturing variation initially
Virtual and Physical Testing collaboration (2 Functions = 1 Discipline)