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TORSIONAL DISTORSION ANALYSIS
1806 RPOA COLD TEST-NEW SOLID TIP
| STUDY
Ra’uf Tailony
05/10/2017
ORIGINAL DESIGN
Figure 1: New Driveline tip.
NODAL ANALYSIS
Figure 2: Vibration nodes locations on driveline.
Mode 2,3Mode 4,5
2
Figure 3: Torque and speed signatures (ramping 0-2000 rpm).
MODELING ASSUMPTIONS
Homogeneous material along the driveline (AISI 4130 steel Annealed at 860 0
C).
All parts are rotating at the same speed (relative angular velocity=0).
Electrical motor slipping is neglected.
Residual friction is neglected.
All considered bearings are ball bearing type with zero lateral forces.
Center of gravity is assumed to be static on a dynamic assembly.
Geometry is treated as a fixed-free structure.
Rayleigh’s equations solution is exact with no iteration.
Ramping up speed = 1500 rpm Ramping down speed = 1500 rpm
- 1500 rpm is a critical speed.
- Critical Frequency = 230 - 280
Hz.
- Critical Modes are 1, 2 and/or
3.
- Critical Excitation order is 12th
order (Engine and E-motor 12th
orders are coinciding).
OBSERVATIONS
3
INITIAL CONDITIONS
Input torque = 300 N.m.
Rotational speed range = 0 - 2000 rpm.
Centrifugal force is proportional to the driveline’s speed.
Excitation diagram is dependent on a standard V8 engine specifications.
FREQUENCY ANALYSIS RESULTS
Figure 4: Mode shape vs. Frequency with and without E-motor bearing.
4
INTERFERENCE DIAGRAMS AND CRITICAL SPEEDS
Figure 5: Campbell diagram for mode1 (bearing considered) and mode3 (bearing ignored).
NARROWING ROOT CAUSE PROBLEM
Figure 6: Original driveline components nodal effects.
Mode 1 effect
Mode 2,3 effect
5
Mode “E-motor bearing
ignored”
Freq. [Hz]
“E-motor bearing
considered”
Freq. [Hz]
1 104 2301
2 120 600
3 280 615
4 815 1050
5 816 1080
Table 1: Frequencies vs. modes.
1
Highlighted frequencies are found in the torque signatures.

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Cold test nodal and distorsion analysis

  • 1. 1 TORSIONAL DISTORSION ANALYSIS 1806 RPOA COLD TEST-NEW SOLID TIP | STUDY Ra’uf Tailony 05/10/2017 ORIGINAL DESIGN Figure 1: New Driveline tip. NODAL ANALYSIS Figure 2: Vibration nodes locations on driveline. Mode 2,3Mode 4,5
  • 2. 2 Figure 3: Torque and speed signatures (ramping 0-2000 rpm). MODELING ASSUMPTIONS Homogeneous material along the driveline (AISI 4130 steel Annealed at 860 0 C). All parts are rotating at the same speed (relative angular velocity=0). Electrical motor slipping is neglected. Residual friction is neglected. All considered bearings are ball bearing type with zero lateral forces. Center of gravity is assumed to be static on a dynamic assembly. Geometry is treated as a fixed-free structure. Rayleigh’s equations solution is exact with no iteration. Ramping up speed = 1500 rpm Ramping down speed = 1500 rpm - 1500 rpm is a critical speed. - Critical Frequency = 230 - 280 Hz. - Critical Modes are 1, 2 and/or 3. - Critical Excitation order is 12th order (Engine and E-motor 12th orders are coinciding). OBSERVATIONS
  • 3. 3 INITIAL CONDITIONS Input torque = 300 N.m. Rotational speed range = 0 - 2000 rpm. Centrifugal force is proportional to the driveline’s speed. Excitation diagram is dependent on a standard V8 engine specifications. FREQUENCY ANALYSIS RESULTS Figure 4: Mode shape vs. Frequency with and without E-motor bearing.
  • 4. 4 INTERFERENCE DIAGRAMS AND CRITICAL SPEEDS Figure 5: Campbell diagram for mode1 (bearing considered) and mode3 (bearing ignored). NARROWING ROOT CAUSE PROBLEM Figure 6: Original driveline components nodal effects. Mode 1 effect Mode 2,3 effect
  • 5. 5 Mode “E-motor bearing ignored” Freq. [Hz] “E-motor bearing considered” Freq. [Hz] 1 104 2301 2 120 600 3 280 615 4 815 1050 5 816 1080 Table 1: Frequencies vs. modes. 1 Highlighted frequencies are found in the torque signatures.