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Research Papers

Dynamic Performance of an Oil Starved Squeeze Film Damper Combined With a Cylindrical Roller Bearing

[+] Author and Article Information
H. Meeus

Department of Mechanical Engineering,
Vrije Universiteit Brussel,
Pleinlaan 2,
Brussels, 1050, Belgium
e-mail: hans.meeus@vub.be

J. Fiszer, W. Desmet

Department of Mechanical Engineering,
KU Leuven,
Celestijnenlaan 300B,
Leuven, 3001, Belgium

G. Van De Velde, B. Verrelst, D. Lefeber, P. Guillaume

Department of Mechanical Engineering,
Vrije Universiteit Brussel,
Pleinlaan 2,
Brussels, 1050, Belgium

1Corresponding author.

Manuscript received July 9, 2018; final manuscript received December 27, 2018; published online February 6, 2019. Editor: Jerzy T. Sawicki.

J. Eng. Gas Turbines Power 141(7), 071009 (Feb 06, 2019) (12 pages) Paper No: GTP-18-1468; doi: 10.1115/1.4042418 History: Received July 09, 2018; Revised December 27, 2018

Squeeze film dampers (SFDs) are widely used to dissipate mechanical energy caused by rotor vibrations as well as to improve overall stability of the rotor system. Especially turbomachine rotors, supported on little damped rolling element bearings (REBs), are primarily sensitive to unbalance excitation and thus high amplitude vibrations. To ensure safe operation, potential failure modes, such as an oil starved damper state, need to be well examined prior to the introduction in the ultimate industrial application. Hence, the aim of this research project is to evaluate the performance of the rotor support for a complete oil starvation of the SFD. An academic rotor dynamic test bench has been developed and briefly presented. Experimental testing has been conducted for two static radial load cases resembling the full load and idle condition of a certain turbomachine. Evidently, the measurement results exposed severe vibration problems. Even a split first whirl mode arises due to a pronounced anisotropic bearing stiffness. Moreover, for the least radially loaded bearing, highly nonlinear behavior emerged at elevated unbalance excitation. Consequently, the rollers start to rattle which will have a negative effect on the overall bearing lifetime. To explain the nature of the nonlinear behavior, advanced quasi-static bearing simulations are exploited. A number of possible solutions are proposed in order to help mitigate the vibration issues.

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References

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Figures

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Fig. 1

Technical drawing of the novel rotor dynamic test rig

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Fig. 2

Discretized rotor dynamic model

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Fig. 3

Results of the performed damped eigenvalue analysis for the 1050 N load case: (a) damped natural frequency map for the 1050 N load case, (b) first forward whirl mode, and (c) first backward whirl mode

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Fig. 4

Results of the performed damped eigenvalue analysis for the 2380 N load case: (a) damped natural frequency map for the 2380 N load case, (b) first forward whirl mode, and (c) first backward whirl mode

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Fig. 5

Positions of the inductive proximity probes (dimensions in mm)

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Fig. 6

Measurements of the starved damper condition for the 2380 N static load case with gradually increasing unbalance excitation. The top graph resembles the virtual probe A in the vertical direction and the bottom graph depicts the virtual probe B in the horizontal direction.

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Fig. 7

Orbital relative phase plot between virtual probes A and B

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Fig. 8

Color map of the starved damper condition for the 2380 N static load case with 12 gmm unbalance excitation

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Fig. 9

Damping estimation using the single DOF peak picking method for the 2380 N static load case with 24 gmm unbalance excitation. Both the original and the virtual probe measurement results are presented in the top graph. In the bottom graph, the orbit plots at, respectively, 4000 rpm, 5000 rpm, 5500 rpm, 6000 rpm, 6500 rpm, and 7000 rpm are shown.

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Fig. 10

Measurements of the starved damper condition for the 1050 N static load case with gradually increasing unbalance excitation. The top graph resembles the virtual probe A in the vertical direction and the bottom graph depicts the virtual probe B in the horizontal direction.

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Fig. 11

Color map of the starved damper condition for the 1050 N static load case with 12 gmm unbalance excitation

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Fig. 12

Color map of the starved damper condition for the 1050 N static load case with 120 gmm unbalance excitation

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Fig. 13

Load-displacement plot of the CRB's vertical direction

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Fig. 14

Load distribution for a combined loading condition of an upwards facing 1050 N static load superimposed by a rotating unbalance force of 500 N (direction specified in subcaptions): (a) up, (b) right, (c) down, and (d) left

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Fig. 15

Stiffness values as a function of the unbalance loading for the 1050 N and 2380 N static load cases

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