Research Papers: Gas Turbines: Structures and Dynamics

Criteria for Best Performance of Pre-Optimized Solid Dampers

[+] Author and Article Information
Chiara Gastaldi

Department of Mechanical and
Aerospace Engineering,
Politecnico di Torino,
Torino 10129, Italy
e-mail: chiara.gastaldi@polito.it

Muzio M. Gola

Department of Mechanical and
Aerospace Engineering,
Politecnico di Torino,
Torino 10129, Italy
e-mail: muzio.gola@polito.it

1Corresponding author.

Contributed by the Structures and Dynamics Committee of ASME for publication in the JOURNAL OF ENGINEERING FOR GAS TURBINES AND POWER. Manuscript received June 26, 2018; final manuscript received July 2, 2018; published online November 16, 2018. Editor: Jerzy T. Sawicki.

J. Eng. Gas Turbines Power 141(4), 042502 (Nov 16, 2018) (9 pages) Paper No: GTP-18-1379; doi: 10.1115/1.4040820 History: Received June 26, 2018; Revised July 02, 2018

This paper furthers recent research by these authors. The starting point is the pre-optimization of solid dampers, which ensures that all dampers bound to “misbehave” are excluded since the early design stage. The authors now enlarge the scope of their investigations to explore those damper configurations selected inside the admissible design area. The purpose of the paper is to present a set of criteria apt to select a damper configuration which not only avoids unwanted situations, but in addition guarantees high performance under different design conditions. The analysis starts with the definition of a set of requirements a high performance damper should meet. In detail, the present investigation seeks to answer the following questions: in the low excitation regime, what is the frequency shift and the stiffening effect each damper can provide? for increasing excitation levels, which damper will start slipping sooner? in the high excitation regime, which damper provides the maximum dissipation? Like pre-optimization, it does not involve nonlinear finite element calculations, and unlike existing optimization procedures, is not linked to a specific set of blades the damper may be coupled to. The numerical prediction of the blade-damper coupled dynamics is here used only for validation purposes. The approach on which this paper rests is fully numerical; however, real contact parameters are taken from extensive experimental investigations made possible by those purposely developed test rigs which are the distinctive mark of the AERMEC Lab of Politecnico di Torino.

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Fig. 1

(a) Bladed disk close up on two adjacent blades and (b) curved-flat damper configuration. Parameters θR, θL, and h are the design variables of the pre-optimization process and of the subsequent high performance investigation.

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Fig. 2

Top: example of IP and OOP pre-optimization maps for residual radius h = 50%r and friction coefficients μL = μR = 0.3. Design areas are indicated on each map. Bottom left: intersection of IP and OOP design areas. Bottom right: representation of forbidden areas and limit lines identified on maps.

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Fig. 3

(a) Absolute platform kinematics for IP motion of the blades shown in Fig. 1(a) and (b) relative platform kinematics (right platform considered still) for IP motion

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Fig. 4

Mind map of the CHP of solid dampers procedure

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Fig. 5

Representation of the numerical model of a solid damper between a set of platforms

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Fig. 6

(a) Representative scheme of KW in the case of pure IP motion. (b) Representative scheme of KU in case of pure OOP motion.

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Fig. 7

Damper performance maps: ((a) and (b)) IP and OOP vertical and horizontal stiffness in full stick, ((c) and (d)) IP and OOP minimum displacement to reach gross slip, ((e) and (f)) IP and OOP dissipation parameter at advanced gross slip

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Fig. 8

(a) Example of IP full stick blade-damper coupled response for damper configurations with different KW values and (b) relationship between vertical stiffness KW and corresponding IP frequency increase (represented in blue) and amplitude reduction (represented in black)

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Fig. 9

(a) Damper force and moments equilibrium for IP motion and bilateral slip and (b) platform-to-platform hysteresis cycle in the case of IP motion and its relation to the damper force equilibrium

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Fig. 10

(a) (θR, θL) two-dimensional space where the high performance areas coming from the three CHP steps are shown. In yellow, their intersection. (b) Numerical prediction of the blade-damper coupled response for increasing excitation levels: three dampers, termed A1, A2, and B, also shown in Fig. 10(a) are considered.



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