Hertzian Theory of Contact

Christian Jäger, summer term 2019

In 1881 the German physicist Heinrich Hertz published a theory to compute the stresses and forces acting during the contact of two elastic bodies. Previously, it was only possible to calculate an idealized case in contact mechanics. The two interacting bodies were originally assumed to be curved and rigid. Therefore, in the idealized case one receives only a point-shaped area of contact if the interacting bodies are either both spheres or a sphere and a cylinder. If two cylinders are pressed together the area of contact is line-shaped.

Corresponding to real conditions of two bodies being compressed, the two interacting surfaces will be deformed, and a flattening will be visible. Hertz used his theory to describe the size and form of the contact zone as well as the distribution of stresses induced by the contact.

The Hertzian Contact theory plays a major role in the fields of non-destructive-testing, mainly in the Impact Echo and the Local Acoustic Resonance Spectroscopy (LARS).^2,3

Assumptions

To compute the contact mechanics, Hertz made several assumptions:

Firstly, the two interacting bodies are assumed to be of an elastic, isotropic and homogenous material. Secondly, the surface is assumed to be perfectly smooth such that no shear stresses occur in the interacting surfaces. And thirdly, it is assumed that only a relatively small part of the total surfaces is in contact.

The two bodies can thus be regarded as half-spaces and the half space theory is therefore applicable.

Static case

Hertz used his new theory to compute the size and form of the compressed area, the normal distribution of pressure between the two surfaces and the maximum pressure between the surfaces, from which the deformation of the two bodies depends. By computing all these parameters, he was finally able to compute the final approach of both bodies under the given load.

The tensile moduli and the form and size of the surfaces nearby the point of contact are known.

Hertz stated that the two surfaces meet in such a way that the surface normal in the contact point are orientated in the direction of compression and parallel to each other. An orthogonal cartesian coordinate system is defined with its origin placed exactly at the contact point (see Fig. 1). The two surfaces nearby the contact point can now be described as two paraboloids of the following form:¹

(1)	$\begin{array}{l}z_{1} = A_{1}x^2 + B_{1}y^2 + C_{1}xy \\ z_{2} = A_{2}x^2 + B_{2}y^2 + C_{2}xy\end{array}$

By the correct orientation of the axis of coordinates the xy-Terms will vanish. The two positive constants A and B can be computed from the principle radii of the surface curvatures:¹

(2)

$\begin{array}{l}B + A = \frac {1}{2} * (\frac{1}{R_{11}} + \frac{1}{R_{12}} + \frac{1}{R_{21}} + \frac{1}{R_{22}}) \\ (B - A) = \frac{1}{2} * [(\frac{1}{R_{11}} - \frac{1}{R_{12}})^2 + (\frac{1}{R_{21}} - \frac{1}{R_{22}})^2 + 2*(\frac{1}{R_{11}} - \frac{1}{R_{12}}) * (\frac{1}{R_{21}} - \frac{1}{R_{22}}) * \cos(2\beta)]^\frac{1}{2}\end{array}$


Fig. 1: Two bodies in Contact

The constant $\begin{array}{l}\beta\end{array}$ denotes the angle between the two normal planes containing the principal curvatures $\begin{array}{l}R_{11}\end{array}$ and $\begin{array}{l}R_{21}\end{array}$ . If body 1 is a sphere with radius $\begin{array}{l}R\end{array}$ , then $\begin{array}{l}R_{11} = R_{12} = R\end{array}$ . If one of the bodies is a cylinder with radius $\begin{array}{l}R\end{array}$ , then the first principal radius is set to $\begin{array}{l}R\end{array}$ and the second one equals $\begin{array}{l}\infty\end{array}$ . Those and further simplifications are shown in the following Table:¹

Type of contact	A	B	A/B
Body 1: Sphere of radius $\begin{array}{l}R_{1}\end{array}$ Body 2: Sphere of radius $\begin{array}{l}R_{2}\end{array}$	$\begin{array}{l}\frac{1}{2R_{1}} + \frac{1}{2R_{2}}\end{array}$	$\begin{array}{l}\frac{1}{2R_{1}} + \frac{1}{2R_{2}}\end{array}$	$\begin{array}{l}1\end{array}$
Body 1: Sphere of radius $\begin{array}{l}R_{1}\end{array}$ Body 2: plane surface	$\begin{array}{l}\frac{1}{2R_{1}}\end{array}$	$\begin{array}{l}\frac{1}{2R_{2}}\end{array}$	$\begin{array}{l}1\end{array}$
Body 1: Cylinder of radius $\begin{array}{l}R_{1}\end{array}$ Body 2: Cylinder of radius $\begin{array}{l}R_{2}\end{array}$ , placed crosswise to body 1	$\begin{array}{l}\frac{1}{2R_{1}}\end{array}$	$\begin{array}{l}\frac{1}{2R_{2}}\end{array}$	$\begin{array}{l}\frac{R_{2}}{R_{1}}\end{array}$
Body 1: Sphere of radius $\begin{array}{l}R_{1}\end{array}$ Body 2: Cylinder of radius $\begin{array}{l}R_{2}\end{array}$	$\begin{array}{l}\frac{1}{2R_{1}}\end{array}$	$\begin{array}{l}\frac{1}{2R_{1}} + \frac{1}{2R_{2}}\end{array}$	$\begin{array}{l}\frac{R_{2}}{R_{1} + R_{2}}\end{array}$
Body 1: Sphere of radius $\begin{array}{l}R_{1}\end{array}$ Body 2: Cylindrical cup of radius $\begin{array}{l}R_{2}\end{array}$ ; $\begin{array}{l}R_{2} > R_{1}\end{array}$	$\begin{array}{l}\frac{1}{2R_{1}} - \frac{1}{2R_{2}}\end{array}$	$\begin{array}{l}\frac{1}{2R_{1}}\end{array}$	$\begin{array}{l}\frac {R_{2} - R_{1}}{R_{2}}\end{array}$
Body 1: Sphere of radius $\begin{array}{l}R_{1}\end{array}$ Body 2: Spherical cup of radius $\begin{array}{l}R_{2}\end{array}$ ; $\begin{array}{l}R_{2} > R_{1}\end{array}$	$\begin{array}{l}\frac{R_{2} - R_{1}}{2R_{1}R_{2}}\end{array}$	$\begin{array}{l}\frac{R_{2} - R_{1}}{2R_{1}R_{2}}\end{array}$	$\begin{array}{l}1\end{array}$
Body 1: Sphere of radius $\begin{array}{l}R_{1}\end{array}$ Body 2: Surface of rotation with principal radii $\begin{array}{l}R_{2}\end{array}$ and $\begin{array}{l}R_{3}\end{array}$ ; $\begin{array}{l}R_{2} > R_{1}\end{array}$	$\begin{array}{l}\frac{1}{2R_{1}} - \frac{1}{2R_{2}}\end{array}$	$\begin{array}{l}\frac{1}{2R_{1}} + \frac{1}{2R_{3}}\end{array}$	$\begin{array}{l}\frac{1-\frac{R_{1}}{R_{2}}}{1 - \frac{R_{1}}{R_{3}}}\end{array}$

The displacements of the two bodies can therefore be calculated as follows:¹

(3)	$\begin{array}{l}w_{1} + w_{2} = \alpha + Ax^2 + By^2 = \\ = [\frac{1-\mu_{1}^2}{E_{1}\pi} + \frac{1-\mu_{2}^2}{E_{2}\pi}] \iint \frac{p}{s} \mathrm {d}x \mathrm {d}y = [\delta_{1} + \delta_{2}] \iint \frac{p}{s} \mathrm {d}x \mathrm {d}y\end{array}$

The variables $\begin{array}{l}w_{1}\end{array}$ and $\begin{array}{l}w_{2}\end{array}$ represent the displacements of the two bodies, $\begin{array}{l}\alpha\end{array}$ is used to display the approach, $\begin{array}{l}s\end{array}$ equals the distance between any surface element in its initial position and the coordinate origin after the application of the pressure $\begin{array}{l}p\end{array}$ , which must be deduced.

To compute the final pressure distribution, which Hertz assumed to be in a potential form, the following equilibrium conditions need to be fulfilled:

The equilibrium of forces must be met. Therefore, the applied force F must equal the vertical component of the pressure inside the contact area.
For the bodies’ interiors outside within the region of contact the equations of motion must be zero. The stresses are assumed to decrease rapidly with increasing distance from the area of contact
The components of displacement vanish at infinity, since here our coordinate systems are rigidly attached to the bodies.
The shear stresses $\begin{array}{l}\tau_{xz}\end{array}$ and $\begin{array}{l}\tau_{yz}\end{array}$ have to disappear along the surfaces, as well as the normal stresses acting on surface elements outside the region of contact. The normal stresses acting on the two bodies within the contact zone must balance as well.

The pressure potential was assumed to be a quadratic function of $\begin{array}{l}x\end{array}$ and $\begin{array}{l}y\end{array}$ and an ellipsoid with a certain mass density. By assuming $\begin{array}{l}F\end{array}$ as the total mass of the ellipsoid the formula for the pressure distribution reduces to the following:⁷

(4)	$\begin{array}{l}\displaystyle p = p_{0}\sqrt{1 - \frac{x^2}{a} - \frac{y^2}{b}} = \frac{3F}{2\pi ab} \sqrt{1 - \frac{x^2}{a} - \frac{y^2}{b}}\end{array}$

The two constants $\begin{array}{l}a\end{array}$ and $\begin{array}{l}b\end{array}$ constitue the length of the two semiaxes of the elliptic compression area. Including the evaluation of means of Legendre polynomials the length of those semiaxes can be computed as:¹

(5)	$\begin{array}{l}a = q_{a} \sqrt[3]{\frac{3F(\delta_{1} + \delta_{2})}{4(A + B)}} \\ b = q_{b} \sqrt[3]{\frac{3F(\delta_{1} + \delta_{2})}{4(A + B)}}\end{array}$

And the total Force $\begin{array}{l}F\end{array}$ calculates as:¹

(6)	$\begin{array}{l}\displaystyle F =\frac{4q_{k}}{3(\delta_{1} + \delta_{2}) \sqrt{(A+B)}} = k_{2}a^\frac{3}{2}\end{array}$

The next table shows some values for the constants $\begin{array}{l}q_{a}\end{array}$ , $\begin{array}{l}q_{b}\end{array}$ and $\begin{array}{l}q_{k}\end{array}$ depending on the ratio^{$\begin{array}{l}\frac{A}{B}\end{array}$} or the auxiliary angle $\begin{array}{l}\theta = \arccos(\frac{B-A}{B+A})\end{array}$ :¹

$\begin{array}{l}\theta\end{array}$	$\begin{array}{l}\frac{A}{B}\end{array}$	$\begin{array}{l}q_{a}\end{array}$	$\begin{array}{l}q_{b}\end{array}$	$\begin{array}{l}q_{k}\end{array}$
90°	1.000	1.4645	1.4645	0.3180
80°	0.7041	1.6517	1.3074	0.3215
70°	0.4903	1.8797	1.1741	0.3322
60°	0.3333	2.1759	1.0502	0.3505
50°	0.2174	2.5690	0.9383	0.3819
40°	0.1325	3.1277	0.8308	0.4300
30°	0.0718	3.9991	0.7220	0.5132
20°	0.0311	5.5327	0.5974	0.6662
10°	0.00765	9.6833	0.4666	1.1450
0°	0	$\begin{array}{l}\infty\end{array}$	0	-

Dynamic case

To compute the occurring forces for the dynamic contact of two bodies, a calculation of the contact time of both bodies is necessary. By integration of Newton’s second law of motion¹

(7)	$\begin{array}{l}\displaystyle F = -m_{1}\ddot{w_{1}} = -m_{2}\ddot{w_{2}} = - \frac{m_{1}m_{2}}{m_{1}+m_{2}}\ddot{\alpha}\end{array}$

where $\begin{array}{l}\alpha\end{array}$ marks the compression of the two colliding elements and substituting Equation (6), the following correlation of the initial conditions $\begin{array}{l}\alpha_{0} = 0\end{array}$ and $\begin{array}{l}\dot{\alpha_{0}} = v_{0}\end{array}$ is compiled¹.

(8)	$\begin{array}{l}\displaystyle \frac{1}{2}(\dot{\alpha}^2-v_{0}^2) = -\frac{2}{5}k_{1}k_{2}\alpha^\frac{5}{2}\end{array}$

For the closest approach of the colliding bodies $\begin{array}{l}\dot{\alpha}=0\end{array}$ and the maximum compression computes as:⁴

(9)	$\begin{array}{l}\displaystyle \alpha_{m} = (\frac{5v_{0}^2}{4k_{1}k_{2}})^\frac{2}{5}\end{array}$

The total duration of contact can therefore be calculated as⁴

(10)	$\begin{array}{l}\displaystyle T = 2t = 2 \int \limits_0^{\alpha_{m}}\frac{1}{\sqrt{v_{0}^2-\frac{4}{5}k_{1}k_{2}\alpha^\frac{5}{2}}}\mathrm{d}\alpha = 2\eta\frac{\alpha_{m}}{v_{0}}\end{array}$

where⁴

(11)	$\begin{array}{l}\displaystyle \eta = \int \limits_0^1 \frac{1}{\sqrt{1-\epsilon^\frac{5}{2}}}\mathrm{d}\epsilon = 1.4716\end{array}$

Compression as a function of time can therefore be determined as follows:⁵

(12)	$\begin{array}{l}\displaystyle \alpha = \alpha_{m}\sin{\frac{1.068v_{0}t}{\alpha_{m}}}\end{array}$

The force-time-correlation can thus be approximated as:¹

(13)	$\begin{array}{l}F =\begin{cases} \frac{1.140}{k_{1}\alpha_{m}}\sin{\frac{1.068v_{0}t}{\alpha_{m}}} \quad \text{for } 0\leq t \leq \frac{\pi\alpha_{m}}{1.068v_{0}}\\ 0 \quad \text{for } t > \frac{\pi\alpha_{m}}{1.068v_{0}} \end{cases}\end{array}$

The shape and size of the compression-figure can now be computed analogue to the static case.

Literature

Goldsmith, W. (1960). Impact - The Theory and Physical Behaviour of Colliding solids. London: Edward Arnold Publishers.
Gregory C. McLaskey, S. D. (2010). Hertzian Impact: Experimental study of the force pulse and resulting stress waves. Accoustical Society of America, 1087-1096.
Große, C. (2018). Grundlagen der Zerstörungsfreien Prüfung. München: Lehrstuhl für Zerstörungsfreie Prüfung. (Date: 07.08.2019)
Hertz, H. (1881). Über die Berührung fester elastischer Körper. Journal für reine und angewandte Mathematik, S. 156-171.
Hunter, S. C. (1957). Energy absorbed by Elastic Waves during Impact. Journal of the Mechanics and Physics of Solids, 162-171.
Johnson, K. L. (1982). One Hundred Years of Hertz Contact. Proceedings of the Institution of Mechanical Engineers, 363-378.
Popov, V. L. (2009). Kontaktmechanik und Reibung. Berlin: Springer.

Seitenhierarchie

Hertzian Theory of Contact

Assumptions

Static case

Dynamic case

Literature