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G r o u p. Gisela Quintenz & Dr.Thomas Schneider. International CVT Conference September 2004. NOISE RADIATION. due to resonance oscillations. TABLE OF CONTENTS. SIMULATION PROCESS. DYNAMIC BEHAVIOR. OPTIMISATION. TEAM PLAY. 2. OVERVIEW. SIMULATION PROCESS. Sound pressure [dB].

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Presentation Transcript

G r o u p

Gisela Quintenz &

Dr.Thomas Schneider

International CVT Conference

September 2004

NOISE RADIATION

due to resonance oscillations


TABLE OF CONTENTS

SIMULATION

PROCESS

DYNAMIC

BEHAVIOR

OPTIMISATION

TEAM

PLAY

2


OVERVIEW

SIMULATION

PROCESS

Sound pressure [dB]

Incitation: bearing accelerations

1

2

3

4

FE-Model

1

2

3

4

3


SPL-CURVE

DYNAMIC

BEHAVIOR

2260 Hz

1600 Hz

1300 Hz

2150 Hz

1940 Hz

300 Hz

600 Hz

210 Hz

840 Hz

Operational condition “3rd gear“

4


VERTICAL BENDING

DYNAMIC

BEHAVIOR

214 Hz

5


BEARING OSCILLATION

DYNAMIC

BEHAVIOR

600 Hz

6


BEARING OSCILLATION

DYNAMIC

BEHAVIOR

600 Hz

7


BEARING OSCILLATION WITH ASSEMBLY INTERACTION

DYNAMIC

BEHAVIOR

8


BEARING BRACKET

DYNAMIC

BEHAVIOR

1300 Hz

9


FLANGE OSCILLATION

DYNAMIC

BEHAVIOR

1600 Hz

10


PULLEY TORSION

DYNAMIC

BEHAVIOR

1940 / 2150 Hz

11


SHAFT BENDING

DYNAMIC

BEHAVIOR

2260 Hz

12


MOVABLE SHEAVE

DYNAMIC

BEHAVIOR

3290 Hz

13


FIXED SHEAVE

DYNAMIC

BEHAVIOR

4150 Hz

14


DAMPING LAYER

____ Basis

____Damping Layer

OPTIMISATION

(broadband effect)

15


FLANGE DESIGN

SPL -5 dB

OPTIMISATION

1300 Hz

16


FLANGE DESIGN

SPL -6 dB

OPTIMISATION

1600 Hz

17


MOVABLE SHEAVE

OPTIMISATION

3290 Hz

18


FIXED SHEAVE

OPTIMISATION

4150 Hz

19


CAE & TEST:

VALIDATION RESULTS

TEAM

PLAY

5 dB

____ calculation results

____ test rig measurements

20


MEMBERS OF THE OPTIMISATION TEAM

TEAM

PLAY

DESIGN

CAE

TEST

21


G r o u p

Thank you for your attention!


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