Research Papers

On Force Control of an Engine Order–Type Excitation Applied to a Bladed Disk With Underplatform Dampers

[+] Author and Article Information
Christian M. Firrone

e-mail: christian.firrone@polito.it

Teresa M. Berruti

e-mail: teresa.berruti@polito.it

Muzio M. Gola

e-mail: muzio.gola@polito.it
Dept. of Mechanical and Aerospace Engineering,
Politecnico di Torino,
Corso Duca degli Abruzzi, 24,
10129 Turin, Italy

Contributed by the Design Engineering Division of ASME for publication in the JOURNAL OF VIBRATION AND ACOUSTICS. Manuscript received May 20, 2011; final manuscript received February 20, 2013; published online June 6, 2013. Assoc. Editor: Bogdan Epureanu.

J. Vib. Acoust 135(4), 041103 (Jun 06, 2013) (9 pages) Paper No: VIB-11-1112; doi: 10.1115/1.4023899 History: Received May 20, 2011; Revised February 20, 2013

The paper presents an original multiple excitation system based on electromagnets with force control. The system is specifically designed in order to investigate the dynamics of bladed disks, since it mimics the excitation existing in a real engine. Moreover, the system is suitable for forced response tests of bladed disks with nonlinear dynamic response, like in the case of presence of friction contacts, since the amplitude of the exciting force is known with good precision. For this purpose, a device called force-measuring electromagnet (FMEM) was designed and employed during the system calibration. The excitation system is applied to the test rig Octopus, which includes underplatform dampers (UPDs). Tests were carried out under different excitation force amplitude values. The tests put in evidence the presence of mistuning and the UPDs' capability of attenuating the mistuning phenomena.

Copyright © 2013 by ASME
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Fig. 1

The test rig “Octopus”

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Fig. 2

The cyclical excitation system

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Fig. 3

(a) The electromagnet (EM). (b) The force-measuring electromagnet (FMEM).

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Fig. 4

Different support solutions for the measuring electromagnet (FMEM): (a) solution 1; (b) solution 2; (c) final solution

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Fig. 5

The FMEM calibration curve

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Fig. 6

The FMEM mounted under the disk

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Fig. 7

Feeding voltage amplitude versus electrical frequency for different excitation force amplitudes

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Fig. 8

Feeding voltage amplitude versus the square root of the excitation force amplitude for different electrical frequencies

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Fig. 9

Comparison of the feeding voltage trends amplitude versus electrical frequency

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Fig. 10

FRF of the first blade of the blisk without UPDs. Hammer test.

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Fig. 11

Operating deflection shapes (ODSs) of the bladed disk for different nodal diameters: (a) ND = 0; (b) ND = 2; (c) ND = 3. Hammer test.

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Fig. 12

Operating deflection shapes (ODSs) of the repeated modes. Hammer test.

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Fig. 13

FRF of the first blade of the bladed disk with UPDs. Hammer test.

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Fig. 14

Blade absolute velocity values for different excitation force amplitudes: (a) excitation electrical frequency 75 Hz; (b) excitation electrical frequency 150 Hz

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Fig. 15

FRF of the bladed disk (free and with UPDs) for different excitation force amplitude values. CF = 50 N. EO = 2. fm = 2fel.

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Fig. 16

Optimization curves at ND = 2

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Fig. 17

FRF of the bladed disk (free and with UPDs) for different excitation force amplitude values. CF = 50 N. EO = 4. fm = 2fel.

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Fig. 18

Imaginary part of the mobility for the different blades at 316 Hz (solid line), 345 Hz (dotted line). FAnom = 0.1 N, EO = 4.




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