Research Papers

Nonlinear System Identification and Modeling of a New Fatigue Testing Rig Based on Inertial Forces

[+] Author and Article Information
Michael Falco, Ming Liu, Son Hai Nguyen

Department of Mechanical,
Industrial and Systems Engineering,
University of Rhode Island,
Kingston, RI 02881

David Chelidze

Department of Mechanical,
Industrial and Systems Engineering,
University of Rhode Island,
Kingston, RI 02881
e-mail: chelidze@egr.uri.edu

R = σminmax, where σmin is the minimum peak stress and σmax is the maximum peak stress.

Currently, break of a specimen is indicated by the saturation of the eddy current sensor which usually happens after a crack reaches its fracture stage.

1Corresponding author.

Contributed by the Technical Committee on Vibration and Sound of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received April 17, 2013; final manuscript received March 23, 2014; published online April 18, 2014. Assoc. Editor: Jiong Tang.

J. Vib. Acoust 136(4), 041001 (Apr 18, 2014) (8 pages) Paper No: VIB-13-1113; doi: 10.1115/1.4027317 History: Received April 17, 2013; Revised March 23, 2014

A novel fatigue testing rig based on inertial forces is introduced. The test rig has capacity to mimic various loading conditions including high frequency loads. The rig design allows reconfigurations to accommodate a range of specimen sizes, and changes in structural elements and instrumentation. It is designed to be used as a platform to study the interaction between fatigue crack propagation and structural dynamics. As the first step to understand this interaction, a numerical model of testing rig is constructed using nonlinear system identification approaches. Some initial testing results also are reported.

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Fig. 4

Model of a specimen

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Fig. 3

Photograph of the system

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Fig. 2

Beam diagram with applied forces

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Fig. 1

Schematic of the fatigue testing apparatus. (1) Flexible connector, (2) slip table, (3) back cylinder, (4) rail, (5) back mass block, (6) specimen supports, (7) specimen, (8) front mass block, and (9) front cylinder.

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Fig. 5

(a) Phase space of the specimen under chaotic loading and (b) ACPD measurement and the specimen oscillations based damage estimate

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Fig. 6

Crack in the specimen at the end of an experiment

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Fig. 7

Frequency response function for different load levels

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Fig. 8

A simplified model for the fatigue testing rig

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Fig. 9

Left: distribution of data points and area used to generate RFS; right: generated RFS

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Fig. 10

Left: slice view of RFS when x·=0; right: slice view of RFS when x = 0

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Fig. 11

Left: surface generated using parameters from DPE; right: the error between the modeled surface and the generated RFS

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Fig. 12

Comparison between the measured base acceleration (thin light line) and the simulated base acceleration (thick dark line) for 0.1034 MPa in the cylinders

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Fig. 13

Relationship between nonlinearity and vibration amplitude



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