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Research Papers: Hydrodynamic Lubrication

Systematical Analysis Method for the Mechanical Behaviors of Crankshaft-Bearing System

[+] Author and Article Information
Changlin Gui, Jun Sun

School of Mechanical and
Automotive Engineering,
Hefei University of Technology,
Hefei 230009, China

Zhixian He, Zhen Li

Department of Mechanical Engineering,
Anhui University of Technology and Science,
Wuhu 241000, China

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received October 29, 2015; final manuscript received March 21, 2016; published online August 11, 2016. Assoc. Editor: Joichi Sugimura.

J. Tribol 139(2), 021702 (Aug 11, 2016) (9 pages) Paper No: TRIB-15-1388; doi: 10.1115/1.4033362 History: Received October 29, 2015; Revised March 21, 2016

Various mechanical behaviors will happen at the same time when an engine operates. Based on this concept, in this paper, a systematical analysis method is presented to analyze the multiple mechanical behaviors (tribology, dynamics, stiffness, and strength) of the crankshaft-bearing system in an engine. By this method, the analyses of the tribology of bearing, the dynamics of crankshaft-bearing system and the dynamic stress of crankshaft can be accomplished simultaneously. For example, the effect of the journal misalignment of crankshaft and the elastic deformation of bearing bush on the dynamics of crankshaft-bearing system, the tribological performances of main bearings and the dynamic stress of crankshaft are analyzed emphatically. The results show that the journal misalignment of crankshaft and the elastic deformation of bearing bush have remarkable effect on the tribological performances of main bearings and the dynamic stress of crankshaft, but have little effect on the dynamics of crankshaft-bearing system.

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Figures

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Fig. 2

Crankshaft-bearing system

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Fig. 3

Beam-element finite element model of elastic crankshaft

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Fig. 5

The nodal force component acted on the journal surface of crankshaft at 30 deg crankshaft angle

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Fig. 9

The oil film pressure distributions at the moment of the maximum value of the maximum oil film pressure of No. 2 main bearing in an operating cycle of engine (a) not considering the journal misalignment and the deformation of bearing bush (the maximum oil film pressure pmax = 56.37 MPa, the crankshaft angle α = 68 °CA), (b) considering the journal misalignment (the maximum oil film pressure pmax = 80.03 MPa, the crankshaft angle α = 48 °CA, the angle of journal misalignment β = 0.033 deg), and (c) considering the deformation of bearing bush (the maximum oil film pressure pmax = 114.1 MPa, the crankshaft angle α = 46 °CA

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Fig. 8

The maximum oil film pressures of main bearings against the crankshaft angle in an operating cycle of engine (a) not considering the journal misalignment and the deformation of bearing bush, (b) considering the journal misalignment, and (c) considering the deformation of bearing bush

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Fig. 7

The minimum oil film thicknesses of main bearings against the crankshaft angle in an operating cycle of engine (a) not considering the journal misalignment and the deformation of bearing bush, (b) considering the journal misalignment, and (c) considering the deformation of bearing bush

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Fig. 6

The radial vibration responses of the main journal centers of crankshaft (a) not considering the journal misalignment and the deformation of bearing bush, (b) considering the journal misalignment, and (c) considering the deformation of bearing bush

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Fig. 4

Solid-element finite element model of crankshaft

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Fig. 10

The dynamic stress of crankshaft against the crankshaft angle in an operating cycle of engine

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