Abstract
When two rough bodies slide against each other, asperities on the opposing surfaces interact with each other, defining a transient contact and heat conduction problem. We represent each body by a Greenwood and Williamson asperity model with a Gaussian height distribution of identical spherical asperities. The heat transfer during a typical asperity interaction is analyzed, and the results are combined with the height distributions to determine the mean heat flux and the mean normal contact pressure as functions of the separation between reference planes in the two surfaces. We find that the effective thermal conductance is an approximately linear function of nominal contact pressure, but it also increases with the square root of the sliding speed and decreases with the 3/4 power of the combined RMS roughness. The results can be used to define an effective thermal contact resistance and division of frictional heat in macroscale (e.g., finite element) models of engineering components, requiring as input only the measured roughness and material properties.
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Abbreviations
- \(a\) :
-
Contact radius
- \(a_0\) :
-
Maximum contact radius
- \(A_{{\mathrm{nom}}}\) :
-
Nominal contact area
- \(b\) :
-
Nearest approach
- \(b_0\) :
-
Maximum value of \(b\) for contact
- \(d\) :
-
Maximum interference
- \(d_0\) :
-
See Eq. (5)
- \(D\) :
-
Fractal dimension of the profile
- \(E^{{*}}\) :
-
Composite elastic modulus
- \(h_i\) :
-
Asperity height above a datum
- \(h_0\) :
-
Mean plane separation
- \(k\) :
-
Thermal diffusivity
- \(K\) :
-
Thermal conductivity
- \(m_{0,2,4}\) :
-
Moments of the power spectral density
- \(N_i\) :
-
Surface density of summits
- \(p\) :
-
Contact pressure
- \(P\) :
-
Normal contact force
- \(Pe\) :
-
Peclet number
- \(q\) :
-
Heat flux per unit area
- \(Q\) :
-
Total heat transfer
- \(R_i\) :
-
Radius of asperity summit
- \(R^{{*}}\) :
-
Composite radius
- \(S\) :
-
Sliding distance
- \(t\) :
-
Time
- \(t_0\) :
-
Half of the duration of contact
- \(T_i\) :
-
Bulk temperatures
- \(T_0\) :
-
Flash temperature
- \(\bar{T}_0\) :
-
Average flash temperature
- \(V\) :
-
Relative velocity
- \(x,y\) :
-
Cartesian coordinates
- \(\alpha\) :
-
Bandwidth parameter
- \(\theta\) :
-
Temperature difference \(T_1-T_2\)
- \(\phi _i\) :
-
Height distribution of asperities
- \(\varPhi _i\) :
-
Probability distribution for asperity interaction
- \(\mu\) :
-
Coefficient of friction
- \(\sigma _i\) :
-
Summit height standard deviation
- \(\omega _h\) :
-
Upper cut-off frequency
- \(c\) :
-
Heat flux due to temperature difference
- \(f\) :
-
Heat generated by friction
- \(i=1,2\) :
-
Bodies 1, 2
- nom:
-
Nominal contact
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Appendices
Appendix 1
1.1 Effect of Relative Motion
We consider the case where \(C_2\gg C_1\), so that points on the surface of body 2 can be assumed to remain at temperature \(T_2\) throughout the contact, and for simplicity we assume that \(R_1=R_2=R\)—i.e. the asperities on the two surfaces have the same summit radius \(R\).
A representative point \((x,y)\) on the surface of body 1 will make contact as long as it remains within the appropriate contact circle in Fig. 2a—i.e. if \(\xi ^2+\eta ^2\le a(t)^2\), where \(\xi ,\eta\) and the time-varying contact radius \(a(t)\) are defined in Eqs. (2, 7) respectively. Using these relations, the inequality can be written in terms of \(x,y,t\) as
and hence
where we define dimensionless time and coordinates through
The times \(\tau _1,\tau _2\) at which contact begins and ends at a given point \((X,Y)\) are defined by taking the equality in (48), giving
It follows that the period of contact at this point is
Notice that by setting \(\Delta \tau =0\), we define the envelope of the contact regions in Fig. 2a, which is
using (49). Points outside this ellipse never experience contact. The total heat exchanged per unit area at \((X,Y)\) is given by Eq. (8) with \(C_2\rightarrow \infty\) as
and hence the total heat exchange during the interaction is
where the integration domain \(\mathcal {A}\) comprises the ellipse of Eq. (52). We obtain
which exceeds Eq. (13) [with \(R_1=R_2\)] by a factor of \(\root 4 \of {3}\approx 1.32\).
Appendix 2
1.1 Evaluation of Gaussian Integrals
Consider the integral
We define dimensionless parameters
and then perform the linear transformation
This preserves the condition
so that the Jacobean of the transformation is unity. We also have
and the domain of integration in \(J(\gamma )\) is \(\xi >\hat{h}_0\), giving
The integral with respect to \(\eta\) evaluates to \(\sqrt{\pi }\) so that finally we obtain
where
writing \(y=\xi -\hat{h}_0\). The integral \(I(\hat{h}_0,\gamma )\) can be evaluated in terms of special functions (for example using Mathematica or Maple) for integer and fractional values of \(\gamma\).
1.2 Frictional Heating
Substituting \(Q_f, \varPhi (b), \phi _1(h_1), \phi _2(h_2)\) from Eqs. (9, 22, 23) respectively into Eq. (24), we obtain
where
Evaluating the integral with respect to \(b\) and substituting for \(b_0\) from (5), we have
Substituting this result in (58) and using (56) we obtain
1.3 Heat Exchange Due to a Temperature Difference
Substituting \(Q_c, \varPhi (b), \phi _1(h_1), \phi _2(h_2)\) from Eqs. (13, 22, 23) respectively into Eq. (27), we obtain
where
after evaluating the integral with respect to \(b\). We therefore have
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Liu, Y., Barber, J.R. Transient Heat Conduction Between Rough Sliding Surfaces. Tribol Lett 55, 23–33 (2014). https://doi.org/10.1007/s11249-014-0328-x
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DOI: https://doi.org/10.1007/s11249-014-0328-x