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Advances in Tribology
Volume 2017 (2017), Article ID 2509879, 12 pages
https://doi.org/10.1155/2017/2509879
Research Article

Dynamic Characterization of Rubber O-Rings: Squeeze and Size Effects

1Division of Production Engineering, Machine Design and Automation, KU Leuven, Leuven, Belgium
2Department of Mechanical and Aerospace Engineering, Politecnico di Torino, Torino, Italy
3Leuven Air Bearings, KU Leuven, Leuven, Belgium

Correspondence should be addressed to Federico Colombo

Received 2 May 2017; Accepted 13 June 2017; Published 12 July 2017

Academic Editor: Michel Fillon

Copyright © 2017 Farid Al-Bender 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.

Abstract

This paper concerns the dynamic characterization of rubber O-rings used to introduce damping in high speed gas bearing systems. O-shaped rubber rings composed of high temperature rubber compounds are characterized in terms of stiffness and damping coefficients in the frequency range 100–800 Hz. Simple formulas with frequency independent coefficients were identified to express the viscoelastic properties of the O-rings. The formulas proposed approximate the stiffness and damping coefficients of O-rings of general size.

1. Introduction

Air bearings at very high speeds can suffer the unstable whirl. A method to overcome this problem is to modify the bearings geometry and increase the stability threshold. An alternative method is to introduce external damping in the system by using a bush supported on rubber O-rings or other elastomeric material. The first experimental work in which the half-speed whirl was avoided by mounting the bushes flexibly goes back 50 years [1]. O-rings were used in gas bearings to improve the static stiffness [2], but in most cases their main function is to overcome the whirl instability in journal bearings [3, 4] or the pneumatic hammer [5]. In [6, 7] an analytical model is developed to predict the restoring and hysteresis characteristics of elastomer O-rings mounted in squeeze film dampers. Stiffness and damping coefficients of the elastic supports which ensure the stability of the rotor are theoretically studied in [8], where it is shown that it is possible to avoid the half-speed whirl. In order to select the support parameters in an optimal way, a stability study is performed in paper [9], in which design guidelines are given.

Literature shows that real viscoelastic materials have to be characterized by more than one relaxation time [12]. Anyway, for the sake of simplicity, a simple Kelvin Voigt model can be sufficiently accurate to predict the dynamic characteristics of rubber O-rings [13]. Finite element method can be used to predict characteristics of rubber rings in static conditions [1416]. However, the experimental characterization of these O-rings is essential for predicting the threshold speed and calculating the rotor runout in case they are used as damping supports.

The stiffness and damping coefficients of these rubber elements depend on several parameters: temperature, amplitude and frequency of the excitation, preload, material, and size of the O-ring [17]. In [18] axial forces transmitted by O-rings subjected to a reciprocating drag were measured for various amplitudes and frequencies. Papers [10, 19] describe some test benches used to measure the viscoelastic properties of O-rings. In paper [20] a simplified approach for the proper selection of elastomers is proposed.

In a previous work [11] dynamic stiffness and damping coefficients of O-rings composed of NBR and Viton® materials were measured. Analogous O-ring properties were found in [3]. In the present paper O-rings composed of high temperature resistant rubber are tested with a test rig for the purpose developed in University of Leuven. The aim is to identify stiffness and damping properties of O-rings of general size which could be used to study the stability of gas bearings, which are prone to whirl instability [21] or to pneumatic hammer instability. These coefficients could be inserted in lumped parameters models of gas bearings [2224] to evaluate their increased stability thanks to the use of the O-rings.

2. Materials and Methods

In literature two test methods can be found to measure the elastomer O-rings properties: the indirect method, named resonant mass method [17, 19], and the direct method.

In the first method (see [17]), the O-ring is compressed between a shaft, connected to the shaker base, and a bush, attached to a suspended mass. The displacements of the two elements that compress the O-ring are measured and no force transducers are needed.

The direct method, adopted in the present paper, consists in measuring directly the force transmitted by the O-ring. A test bench was set up as depicted in Figure 1. The O-ring under test () is compressed between bushing (), connected to the stinger of shaker (), and shaft (), fixed to support (). The load cell () is placed between support () and the fixed frame (). By means of the shaker a sinusoidal displacement is imposed to the bushing. This displacement is detected by sensors (), mounted on support (). The signals from the load cell and the displacement transducers are sent to a DAQ system and then elaborated. Table 1 shows a list of the instrumentation used and Figure 2 shows a photo of the test bench.

Table 1: List of instrumentation.
Figure 1: Test setup.
Figure 2: Photo of the test setup.

The fixed frame was designed with FEM software to avoid resonance in the frequency range of the tests. The first natural frequency of the fixed frame is about 1.2 kHz, which is above the frequency range of tests.

The O-rings were compressed with a small excitation amplitude (2.5 μm), so their behavior can be assumed to be linear. They were preloaded with various squeeze levels (5%, 10%, 15%, and 20%). The squeeze is defined bywhere is the cross section diameter of the O-ring and and are the inside diameter of bushing () and the external diameter of shaft (), respectively (see Figure 1).

2.1. O-Rings under Test

Rubber materials are used for different purposes, for example, vibration isolation, shock absorption, and sealing. Some compounds are designed for high temperatures, like Kalrez® and Viton. O-rings composed with such materials can be useful to increase the stability of high speed rotors supported by gas bearings. In literature it is difficult to find experimental data about O-rings of such compounds. For this reason, O-rings made in Viton, Kalrez 4079, and Kalrez 6375 were selected to be tested.

Viton is a fluoropolymer elastomer categorized under the ISO 1629 designation of FKM. Its density (1800 kg/m3) is significantly higher than that of most types of rubber. It is used in a broad range of applications for its low cost. Compounds of Shore hardness of 75 and 90 were designated in this paper.

Kalrez is a perfluoroelastomer material (FFKM) with high chemical resistance; it has a temperature stability comparable with that of PTFE. It is mostly used in highly aggressive chemical processing, pharmaceutical, and aerospace applications. In particular, Kalrez 4079 is a carbon black filled compound with a maximum operating temperature of 315°C. Kalrez 6375 has maximum operating temperature of 275°C. Their Shore hardness is 75.

Table 2 shows details of the O-rings tested. The maximum temperature of the materials, the inner diameter , and the cross section diameter are indicated.

Table 2: Details of the O-rings under test.
2.2. Test Procedure

In this section the procedure used to measure the dynamic stiffness of the O-rings is described. All tests were performed at constant ambient temperature of 20°C. Each O-ring was tested at different frequencies by imposing the sinusoidal displacement (the input) and measuring the transmitted force (the output). For each frequency, the shaker amplitude was adjusted in open loop until displacement sensors indicated the required value (small displacement). On the base of the time functions and acquired at several frequencies the experimental transfer functions were obtained. The transfer function is defined as ratio:where is the cross power spectral density of and and is the power spectral density of . Using a Kelvin Voigt model the transfer function can be written as follows:

Stiffness and damping coefficients were calculated with the following formulas:

Finally, a least square procedure (see Appendix A) was adopted to find a best fit for the experimental data. This brought expressions for stiffness and damping in the exponential form

In these relations the pulsation is expressed in rad/s.

3. Results and Discussion

An example of Bode diagram is shown in Figure 3. It can be noticed that, approaching the resonance frequency of the test bench, the Bode diagram has a peak in the amplitude. Also the phase changes abruptly. For this reason, data at frequencies over 850 Hz are neglected.

Figure 3: Body diagram of transfer function in case of Viton 75,  mm,  mm.
3.1. Frequency Dependence

The results are summarized in Tables 35 for Viton 75, Viton 90, and Kalrez, respectively. They are presented in the form of coefficients A, B, , and . Stiffness and damping coefficients at a frequency of 200 Hz are also given in the tables. These are more representative than the previous coefficients as they are less affected by measuring errors.

Table 3: Summary of the results for Viton 75 O-ring.
Table 4: Summary of the results for Viton 90 O-ring.
Table 5: Summary of the results for Kalrez O-ring ( mm,  mm).

In Figures 47, the experimental points of stiffness and damping coefficients are plotted with the fitted power law lines.

Figure 4
Figure 5
Figure 6
Figure 7

Figures 47 show the squeeze effect on and coefficients for a selected size of the O-ring and the size influence on and at a medium squeeze level (15%).

Figure 4(a) shows the effect of squeeze on the stiffness coefficient of Viton 75 O-rings of size  mm,  mm. It can be seen that stiffness increases with frequency and with the squeeze level.

Figure 4(b) shows the effect of squeeze on the damping coefficient of Viton 75 O-rings of size  mm,  mm. Damping decreases with frequency and increases with the squeeze level.

Figures 5(a) and 5(b) show the influence of the size on the stiffness and damping coefficients at a 15% squeeze level. Stiffness and damping coefficients increase both with diameter and cross diameter , although the influence of is almost negligible when is high. This is in accordance with data of paper [10], in which the influence of the cross section diameter is negligible with an O-ring of internal diameter of about 73 mm.

Figures 6(a) and 6(b) show the effect of squeeze on stiffness and damping coefficients of Viton 90 O-rings of size  mm,  mm. It can be noticed that Viton 90 is more rigid and has also a greater damping capability.

Similar trends are shown in Figures 7(a) and 7(b) presenting the influence of the size on the stiffness and damping coefficients at a 15% squeeze level for Viton 90 O-rings. Both stiffness and damping are greater in Viton 90 with respect to Viton 70.

Literature data on these coefficients are very difficult to be found. Table 6 shows details about O-rings from [10, 11] tested with the mass resonant method. Figure 8 compares these results with that of the present paper, with Viton material and a squeeze level of 15%. Considering that stiffness and damping should increase with the Shore hardness and with both and , coefficients from [11] are compatible with that of  mm, as their Shore hardness and their cross section diameter are lower. Furthermore the coefficients from [10] are greater than that of  mm and squeeze 15% and also this comparison is good.

Table 6: Dimensions of the O-rings tested in [10, 11].
Figure 8: Comparison of the results of Viton 75, squeeze level 15%, with those from [10, 11].

Considering that the sensitivity of rubber properties on temperature is very high, the discrepancies on the data from different test benches are acceptable. Also, as noticed in [19], the O-rings can easily be twisted during mounting and this fact could influence the test results. To avoid this problem the O-rings could be lubricated, but the presence of a lubricant could be another source of uncertainty.

3.2. Dependence on the Squeeze

The relationship between the stiffness and damping coefficients and the squeeze is approximately linear. Figures 9 to 11 show the coefficients at frequency of 200 Hz.

Figure 9: and versus for Viton 75.
Figure 10: and versus for Viton 90.
Figure 11: and versus for Kalrez O-rings.
3.3. Dependence on O-Ring Size

The effects of the inner diameter and of the cross section diameter can be evaluated plotting the coefficients obtained with the following ratios:

The results are depicted in Figures 12 and 13. In first approximation it is possible to collapse the four trends into one curve. In this way the properties of the O-rings can be identified independently of their size:

Figure 12: and versus for Viton 75.
Figure 13: and versus for Viton 90.

The least squares procedure was adopted to fit the linear trends to experimental data (see Appendix B). In these equations the squeeze is expressed in percentage form (, 10, 15, and 20). Table 7 summarizes the results.

Table 7: Coefficients for the identification of and .

4. Conclusions

In the present work the dynamic properties of rubber O-rings are provided. The following conclusions can be made:(i)Stiffness increases with frequency, while damping decreases.(ii)Stiffness and damping coefficients increase both with the size of the O-ring (internal diameter and cross-sectional diameter ) and with the squeeze level.(iii)A material with higher Shore hardness has higher stiffness and damping.

Formulas are provided to identify as a first approximation the stiffness and damping coefficients of O-rings of general size. These formulas can be inserted in lumped parameters models of gas bearings to evaluate their increased stability with the use of the O-rings.

Future interesting investigations could concern the verification of these formulas with O-rings of different size. Also the effect of temperature could be taken into account setting up a temperature control.

Appendix

A. Interpolating Coefficients

Coefficients and are calculated solving the following linear system by least squares procedure:

The pulsation vector is expressed in rad/s.

Similar procedure was adopted for coefficients and :

B. Extrapolating Coefficients

Coefficients and are calculated solving the following linear system by least squares procedure:

The squeeze is expressed in percentage form.

Similar procedure was adopted for coefficients and :

Conflicts of Interest

The authors declare that they have no conflicts of interest.

Acknowledgments

The authors wish to acknowledge KU Leuven and Politecnico di Torino for the financial support to this work.

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