Research Article | Open Access
Center Impedance Method for Damping Measurement
Damping materials are used extensively for reduction of vibration and noise. These damping materials have viscoelastic characteristics and are used by automotive and other industries. Testing of these materials is important in order to predict their performance and traditionally the damping properties are measured by the Oberst method. This paper discusses an alternate method called the Center Impedance method where force and response are measured directly and the damping properties are obtained. The Center Impedance method is easy to use requiring only standard vibration equipment for excitation, namely, shaker, and is easy to control the experiment for repeatability. Results of beams tested by both Oberst and Center Impedance methods are presented in order to validate this test method.
Damping is of the utmost importance for noise and vibration harshness issues related to the automotive industry . Traditionally the Oberst method is the method of choice recommended by both ASME  and SAE . Other innovative methods, such as inverted shaker, have been proposed [4, 5] but did not gain acceptance due to its limitation of applicability in low frequency ranges. However, the Oberst method poses two problems: only viscoelastic materials sprayed or coated onto beams made of magnetic materials can be tested, and heavily damped beams cannot be tested since the force and response sensors are non contacting magnetic sensors. The Oberst method is suitable primarily for narrow samples and wider samples requiring shaker use. This has led to various industrial standards [6, 7]. The Center Impedance method , while based on the same theory as Oberst, overcomes both limitations associated with Oberst testing. The Center Impedance method does not require presence of a magnetic material and it provides direct measurement of force and response that permits the user to apply the necessary exciting force. It may be noted that the Center Impedance method is slowly gaining recognition [8–10] but a comprehensive study comparing the Center Impedance method and the Oberst method is so far lacking. Dowling and Saha  have studied loss factors by the Oberst and the Center Impedance methods (only at room temperature). They did not study the Young’s moduli and, consequently, could not compare the accuracy of these methods based on comparison of predicted and measured natural frequencies. It may be noted that a plate-based method called Giger Plate method  has existed in the industry. However, this method is not very useful  because it provides output only at one frequency (around 160?Hz) and the measurement is based on a 6?mm thick plate which is uncommon in many industries, including automotive industry.
The Oberst method uses a cantilever specimen and two magnetic sensors (one placed close to the fixed end and the other placed close to the free end) are used for excitation and response (Figure 1). The Center Impedance method (Figure 2) typically uses an impedance head (force and acceleration sensor combined) to measure applied force and response acceleration of the free-free beam driven at the center. Since almost all laboratories involved with vibration testing have shakers and impedance heads (or separate force sensor and accelerometer), the Center Impedance method does not require any special apparatus whereas the Oberst method requires a specialized Oberst fixture. Since the properties of the damping material are highly temperature sensitive, tests at temperatures higher than room temperature are performed inside an oven as shown in Figure 3.
Since the above equations are applicable for a bar damped on one side, the same equations are applied for Oberst and Center Impedance methods (the effects of different boundary conditions are taken care of by natural frequencies of bare bars as well as damped bars).
Theoretical calculations to determine the natural frequencies for bare or undamped beams are based on the following equations: where = the modal eigenvalue parameter and its magnitude depends on the boundary conditions of the beam .
The natural frequencies measured by the Center Impedance method are compared with the theoretical values in Table 1. The first mode shape obtained numerically (by Finite Element software Ansys displayed on left) and by Center Impedance method (displayed on right) is shown in Figure 4. Similarly third bending mode (theoretical and experimental) is shown in Figure 5.
It may be noted that the Oberst setup involves fixed-free or cantilevered boundary conditions; whereas the Center Impedance method involves free-free boundary conditions. Since cantilevered boundary conditions are difficult to achieve, it is suggested to ignore the results involving the first mode . The Center Impedance method, on the other hand, involves a boundary condition easier to simulate in experiment but only odd number modes are excited (due to placement of a stinger at the center). Natural frequencies by either method are obtained by the location of peaks of the transfer functions. Damping properties (loss factors) may be estimated by one of the three methods: Half power method, Schroeder integration (decay method), and power injection method . In this study half-power method is used because it works well for transfer functions with well-separated peaks and it is simpler than the Schroeder method. The power injection method has not been used because the previous studies [16, 17] have shown that the power injection method may produce erroneous results.
Steel beams coated with liquid sprayable dampers with specifications, as shown in Table 2, were used for this study. Figures 6, 7 and 8 show the composite loss factors of the beams measured at room temperature, and
It may be noted that at any given frequency such as 200?Hz, as expected thicker coating of damping material (bar R690-64 S.No2) will provide larger loss factor than that by bar with thinner coating (bar R690-64 S.No1) for a particular temperature as shown in Figure 12.
Since the loss factors as obtained by the Center Impedance method are consistently higher than those measured by the Oberst method, next Young’s moduli of the materials were computed which would then be used to estimate the natural frequencies of thick coated bars and compare with the frequencies obtained by the experiment. Young’s moduli of the material were computed using (1) and they are plotted in Figures 13, 14 and 15.
Next, these moduli were used to compute the natural frequencies of bars coated with the same material but of different thicknesses (0.0059?m to 0.0062?m nominal) and were compared with experimentally observed values as shown in Table 3.
4. Conclusion and Discussion
This paper shows the measurement of loss factor and Young’s modulus of damping materials using the Center Impedance method. The Center Impedance method not only provided the loss factors which are higher, but more importantly provided Young’s moduli which were in better agreement with experimentally observed values in terms of predicting the natural frequencies of the beams with thicker coating. It may again be noted that the Oberst method does not permit testing of damping material coated onto nonmagnetic materials or use thick coating whether attached to magnetic or nonmagnetic beams. The Center Impedance method does not have these limitations. One limitation of Center Impedance method is that results are available at only odd numbered modes because this method involves excitation of a free-free beam at the center. Also care should be taken to place the shaker stinger at the center properly in order to avoid excitation of torsional modes. Considering the importance of accurately measuring the properties of damping materials, it is suggested that new damping measurement standards be established based on the Center Impedance instead of the Oberst method. Future work is suggested to use this technique for several more types of damping materials and also utilize the properties obtained through this method to predict behavior of plates or more complicated structures.
|:||Area of the beam,|
|:||Young’s modulus of bare bar, N/m2|
|:||Young’s modulus of damping material, N/m2|
|:||Thickness of bare bar, m|
|:||Thickness of damping material, m|
|:||Moment of inertia of the beam,|
|:||E1 /E, Young’s modulus ratio|
|:||/H, thickness ratio|
|:||Loss factor of visco-elastic material, dimensionless|
|:||loss factor of composite bar, dimensionless|
|:||Density of Oberst bar,|
|:||Density of damping material,|
|:||Half-power bandwidth for mode of composite bar, Hz|
|:||Resonance frequency for mode of bare bar, Hz|
|:||Resonance frequency for mode of composite bar, Hz|
|:||Index number: 1, 2,|
|:||Length of bar, m.|
The supports from US Department of Education Grant no. P116-Z08-0102,? the Dean of NIU College of Engineering and Engineering Technology, and Daubert Chemicals are acknowledged.
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Copyright © 2009 D. Malogi et al. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.