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Research Papers

Reduced-Order Modeling of Preloaded Bolted Structures in Multibody Systems by the Use of Trial Vector Derivatives

[+] Author and Article Information
Florian Pichler

Faculty of Engineering,
University of Applied Sciences Upper Austria,
Stelzhamerstraße 23,
Wels 4600, Austria
e-mail: Florian.Pichler@fh-wels.at

Wolfgang Witteveen

Faculty of Engineering,
University of Applied Sciences Upper Austria,
Stelzhamerstraße 23,
Wels 4600, Austria
e-mail: Wolfgang.Witteveen@fh-wels.at

Peter Fischer

Institute of Automotive Engineering,
Graz University of Technology,
Inffeldgasse 11/II, Graz 8010, Austria

1Corresponding author.

Contributed by the Design Engineering Division of ASME for publication in the JOURNAL OF COMPUTATIONAL AND NONLINEAR DYNAMICS. Manuscript received February 6, 2017; final manuscript received May 24, 2017; published online July 18, 2017. Assoc. Editor: Javier Cuadrado.

J. Comput. Nonlinear Dynam 12(5), 051032 (Jul 18, 2017) (12 pages) Paper No: CND-17-1055; doi: 10.1115/1.4036989 History: Received February 06, 2017; Revised May 24, 2017

In order to achieve a correct representation of jointed structures within multibody dynamic simulations, an accurate computation of the nonlinear contact and friction forces between the contact surfaces is required. In recent history, trial vectors based on trial vector derivatives, the so-called joint modes, have been presented, which allow an accurate and efficient representation of this joint contact. In this paper, a systematic adaption of this method for preloaded bolted joints is presented. The new strategy leads to a lower number of additional joint modes required for accurate results and hence to lower computational time. Further, a major reduction of the computational effort for joint modes can be achieved. The potential and also possible limitations of the method are investigated using two numerical examples of a preloaded friction bar and a bolted piston rod bearing cap.

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Figures

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Fig. 1

Schematic draft and FE model of the friction bar

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Fig. 4

Deflection of the force application point: (a) load case fext+ and (b) load case fext−

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Fig. 5

Contact pressure at PL1 due to fext+: (a) 25 joint modes only PLM TVDs, (b) 25 joint modes all TVDs, (c) 25 joint modes no PLM, and (d) abaqus

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Fig. 6

Single cylinder with flexible bolted piston rod: (a) schematic draft of MBS model, (b) FE model of the piston rod, and (c) screw preload modeling

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Fig. 7

Three free–free modes of the piston rod: (a) mode 1— φCB,1, (b) mode 2— φCB,2, and (c) mode 3— φCB,3

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Fig. 8

Three joint modes of the piston rod

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Fig. 9

Normal stress (Syy) in the joint area: (a) with PLM—only PLM derivatives, (b) with PLM—all TVDs, (c) no PLM, and (d) no PLM—additional normal modes instead of joint modes

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Fig. 10

Dynamic convergence study: (a) PLM—only PLM derivatives, (b) PLM—all TVDs, and (c) no PLM

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Fig. 11

Deflection of the force application point: (a) load case fext+ and (b) load case fext−

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Fig. 12

Convergence at different dynamic levels: (a) nc = 1000 min−1 and (b) nc = 10,000 min−1

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Fig. 13

Normal stress (Syy) in the joint area with modified contact parameters

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Fig. 2

Preload mode for the friction bar

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Fig. 3

Contact pressure due to preload at PL1: (a) Φ = [ΦCB], (b) Φ = [ΦCBΦPL], and (c) abaqus

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