Research Papers: Conduction

A Fundamental Study on the Heat Partition Ratio of Vehicle Disk Brakes

[+] Author and Article Information
Andreas Loizou

e-mail: loizou2@gmail.com

Andrew J. Day

School of Engineering,
Design and Technology,
University of Bradford,
Bradford BD7 1DP, UK

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received November 14, 2012; final manuscript received June 10, 2013; published online October 14, 2013. Assoc. Editor: Robert D. Tzou.

J. Heat Transfer 135(12), 121302 (Oct 14, 2013) (8 pages) Paper No: HT-12-1610; doi: 10.1115/1.4024840 History: Received November 14, 2012; Revised June 10, 2013

The interface tribolayer (ITL) in an automotive brake friction pair is a layer of material created from transfer films, wear particles, and surface transformations between the rotor and stator. Its presence in a brake friction interface has been proven, e.g., by the existence of a temperature “jump” across the friction interface. In this paper, two 1D static transient heat transfer models have been used to investigate the ITL behavior and obtain an equivalent thermal conductance value which will reduce computational requirements and software restrictions. The approach is developed into a more realistic 2D coupled temperature–displacement model using commercial finite element analysis (FEA) software (abaqus) that utilizes the contact pressure, real contact area, and the ITL equivalent thermal conductance to estimate the effective thermal conductance at the friction interface. Subsequently, the effective thermal conductance relationship is combined with the 2-D coupled temperature–displacement model to provide a new method of heat partition prediction in brake friction pairs where heat partition is neither uniform nor constant with time.

Copyright © 2013 by ASME
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Fig. 1

Static models with (right) and without (left) ITL

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Fig. 2

Temperatures with ITL physically modeled and with equivalent thermal resistance

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Fig. 3

2D coupled temperature–displacement model with frictional heating

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Fig. 4

Average contact pressure when f=1

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Fig. 5

Total thermal resistance at interface

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Fig. 6

Contact pressure and thermal conductance relationship for experiment 4

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Fig. 7

Pressure–conductance relationship for different contact areas

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Fig. 8

Average nodal contact pressure with different thermal contact resistance values

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Fig. 9

Resulting temperatures for experiment 4

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Fig. 10

Average nodal contact pressures for explicit and implicit solutions

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Fig. 11

Pad wear on leading edge due to higher contact pressure

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Fig. 12

(a) Leading and trailing pad temperatures and (b) temperatures with different f values




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