 Original Article
 Open Access
 Published:
Application of Fractal Contact Model in Dynamic Performance Analysis of Gas Face Seals
Chinese Journal of Mechanical Engineering volume 31, Article number: 27 (2018)
Abstract
Fractal theory provides scaleindependent asperity contact loads and assumes variable curvature radii in the contact analyses of rough surfaces, the current research for which mainly focuses on the mechanism study. The present study introduces the fractal theory into the dynamic research of gas face seals under facecontacting conditions. StructureFunction method is adopted to handle the surface profiles of typical carbongraphite rings, proving the fractal contact model can be used in the field of gas face seals. Using a numerical model established for the dynamic analyses of a spiral groove gas face seal with a flexibly mounted stator, a comparison of dynamic performance between the MajumdarBhushan (MB) fractal model and the ChangEtsionBogy (CEB) statistical model is performed. The result shows that the two approaches induce differences in terms of the occurrence and the level of face contact. Although the approach distinctions in film thickness and leakage rate can be tiny, the distinctions in contact mechanism and end face damage are obvious. An investigation of fractal parameters D and G shows that a proper D (nearly 1.5) and a small G are helpful in raising the proportion of elastic deformation to weaken the adhesive wear in the sealing dynamic performance. The proposed research provides a fractal approach to design gas face seals.
Introduction
Face contact is an important physical reality in a number of research fields [1,2,3]. In the field of face seals, for contacting face seals, face contact is inevitable during the opened operation. For noncontacting face seals such as spiral groove gas face seals as shown in Figure 1, they should possess a proper gas film thickness to avert face contact during the opened operation. Even so, face contact does occur during the startup and shutdown operations [4], and is also a risk from disturbances during the opened operation [5]. Therefore, it is imperative to choose an adequate asperity contact model in the analyses of face seals. With respect to asperity contact, Greenwood and Williamson (GW model) [6] have done a pioneering work, developing an elastic contact model between rough surfaces. McCool [7] and Bhushan [8] added asperity slope and curvature to capture rough surfaces. Chang et al. [9] proposed the CEB elasticplastic contact model based on volume conservation during plastic deformation to improve the GW model. Kogut and Etsion (KE model) [10, 11] developed a finite element method to investigate the contact between a deformable spherical asperity and a rigid flat, showing dimensionless contact load and contact area over the increase in the interference range from purely elastic through elasticplastic to fully plastic contact.
However, Sayles and Thomas [12] revealed that many engineered surfaces have the multiscale characteristic. Bhushan et al. [13] found that statistical parameters depend strongly on the resolution of measuring instruments, and are not unique for a surface because of the multiscale characteristic. It leads to the result that measurements with different resolutions and scanning lengths wouldn’t yield unique statistical parameters for a surface. Moreover, statistical contact models overlook the fact that the curvature radius of an asperity is a function of asperity size, and surely assume a constant curvature radius for all asperities. Majumdar and Bhushan [14] used the WeierstrassMandelbrot (WM) function to develop the first fractal contact model for real rough surfaces where the assumption of variable curvature radius was adopted. This fractal contact model has been of interest to many researchers, and has been applied to various applications. Wang and Komvopoulos [15, 16] researched the interfacial temperature factor in the fractal contact. Komvopoulos and Yan [17] generated a threedimensional fractal surface by the WM function and introduced it into the contact model. Sahoo and Chowdhury [18, 19] analyzed the friction and the wear of fractal surfaces. Ciavarella et al. [20] investigated the elastic contact stiffness and the contact resistance of fractal surfaces. Kogut and Jackson [21] used both statistical and fractal approaches to characterize simulated surfaces, and obtained substantial differences between the two. Morag and Etsion (ME model) [22] argued that a single asperity transferring from plastic to elastic when the load increases and the contact area becomes larger in the MB model is in contrast with classical contact mechanics. They suggested the real deformation is an independent parameter ranging from zero to full interference, and thus developed a revised elasticplastic contact model with respect to a single fractal asperity.
Face contact can affect sealing performance, such as dynamic behavior, thermodynamics, friction, wear. The dynamics of face seals has been an active area since the works by Etsion [23,24,25]. In the aspect of gas face seals, direct numerical method [26,27,28,29,30] is detailed but computationally intensive, whilst semianalytical method including perturbation method [31,32,33,34] and step jump method [35], on the other hand, is a more practical and efficient alternative but intensively depends on small displacement precondition. Before the introduction of asperity contact, stability and tracking have been used to illustrate the potential menace of face contact. Variables such as minimum film thickness, axial relative displacement and angular transmissibility are regarded as the indirect evaluation indexes of face contact. With the development of simulation, asperity contact models have been involved to directly gauge their influence on sealing dynamic performance. Harp and Salant [36] developed an axial dynamic model including the AbbottFirestone plastic asperity contact model. Green [37] researched the transient performance of coned gas face seals during the startup operation by using the CEB model. Ruan [38] also used the CEB model to investigate the transient performance of spiral groove gas face seals during the startup and shutdown operations.
The above dynamic works all used the statistical contact models, while the fractal contact theory has not been applied. The present study is an attempt to involve the fractal theory in the dynamic research of gas face seals. And a comparison of dynamic performance between statistical and fractal approaches is performed. The widely used, original contact models (i.e., the MB and the CEB models) are selected, respectively, as the representatives of fractal and statistical asperity contact models accounting for excluding extra factors (such as the impact of work hardening, the influence of neighboring asperities, the introduction of new biGaussian stratified surface parameters [39,40,41,42,43,44,45], the revision of contact mechanic in ME model) involved in advanced statistical or fractal models.
Model
MB Model
In the MB model, the surface profile z(x), as shown in Figure 2, is random, multiscale and statistically selfaffine. The WM function is used to describe the surface profile. Its power spectrum is [14]
where S is the power spectrum, ω is the frequency that is the reciprocal of the wavelength of roughness, D is the fractal dimension, G is the fractal roughness parameter, γ determines the frequency spectrum of surface roughness where γ = 1.5 is found to be a suitable value for high spectral density and phase randomization [46]. In a loglog plot of S(ω) ~ ω, the power law behavior of Eq. (1) transforms into a straight line. The slope k_{p} is related to the fractal dimension D and the intercept B_{p} is related to the fractal roughness parameter G. In practical experiments, one needs to obtain the power spectrum of a real surface profile in a loglog plot. If the relation is linear and k_{p} satisfies (− 3, − 1), it reveals the real surface profile owns fractal characteristic. Then, D and G can be calculated referring to k_{p} and B_{p}.
The critical contact area of an asperity is [14]
where E is the Hertz elastic modulus, H is the hardness of softer material, and the maximum contact pressure coefficient K = 0.454 + 0.41υ (υ is the Poisson ratio). If the area of a contact spot a < a_{c}, the asperity is in plastic contact; if a > a_{c}, the asperity is in elastic contact. The total contact load between a rough surface and a smooth plate P_{c} is [14]
where the first term corresponds to elastic deformation and the second term corresponds to plastic deformation. a_{l} is the area of the largest contact spot. n(a) is the sizedistribution of a [14]:
The real contact area A_{r} is [14]
If a_{l} < a_{c}, the elastic and plastic deformation can be simply rendered as [14]
If a_{l} > a_{c}, the elastic and plastic deformation can be calculated as [14]
Application of MB Model in Sealing Dynamics
The dynamic schematic of the two mated rings and the geometry of the rotor are depicted in Figure 3. A total of N spiral grooves are processed on the rotor at a depth of δ_{g}. The ratio of groove width to the land width is captured by λ = W_{g}/(W_{g} + W_{l}), and the ratio of groove length to the dam length is characterized by β = (r_{g }− r_{i})/(r_{o }− r_{i}). α is the spiral angle varying from 0 to 180°. r_{o}, r_{i} and r_{g} are outer radius, inner radius and the boundary between groove region and dam region. The gas film thickness of any point (x, y) on the stator h(x, y) is given by h(x, y) = c + <δ_{g}>, where c is the central gas film thickness between the coupling rings, and <δ_{g}> indicates a δ_{g}deep groove in the groove region. Considering the stiffness and damping properties of springs and the secondary seal, the 1D axial dynamic equation is rendered by [27, 35]
where m is the stator mass. k_{sz} is the stiffness of springs. c_{sz} is the damping of flexible support. F_{closing} is the total load of the pressuredropgenerated fluid load and the spring support load at equilibrium. F_{closing} is applied on the back of the stator, balancing the gas film opening load F_{g} and the face contact load F_{c}. F_{g} can be obtained by integrating the gas film pressure p over the nominal sealing area A_{n}, rendered as \(F_{g} = \int_{{A_{n} }} {p{\text{d}}A}\). The gas pressure distribution p is governed by the lubrication equation. Assuming the gas flow is ideal and isothermal, and the effect of surface texture is ignored, the compressible Reynolds equation is adopted as [36,37,38]
where μ is the gas viscosity, r is the radius, i_{θ} is the unit vector in θ direction, and Ω is the shaft speed. The boundary conditions to Eq. (9) are
For a given gas face seal, the film thickness h measured from the mean plane of asperity height is easily obtained. Majumdar and Bhushan [14] proposed that if the asperity height of a surface follows a Gaussian distribution, h respects the relation as below
Then Eq. (11) can be deduced as
The value of \({{\int_{  \infty }^{{{h \mathord{\left/ {\vphantom {h \sigma }} \right. \kern0pt} \sigma }}} {{{e}}^{{  {{x^{2} } \mathord{\left/ {\vphantom {{x^{2} } 2}} \right. \kern0pt} 2}}} } {\text{d}}x} \mathord{\left/ {\vphantom {{\int_{  \infty }^{{{h \mathord{\left/ {\vphantom {h \sigma }} \right. \kern0pt} \sigma }}} {{\text{e}}^{{  {{x^{2} } \mathord{\left/ {\vphantom {{x^{2} } 2}} \right. \kern0pt} 2}}} } {\text{d}}x} {\sqrt {2\uppi} }}} \right. \kern0pt} {\sqrt {2\uppi} }}\) can be calculated by using an error function erf
Therefore, the value of Eq. (11) finally becomes
The relation between h and a_{l} can be obtained from Eqs. (5) and (14)
Therefore, for a gas face seal, if h is known, a_{l} can be calculated according to Eq. (15). Substituting n(a) from Eq. (4) in Eq. (3), P_{c} finally becomes
Note the special condition that if a_{l} < a_{c}, all the contact spots are in plastic contact and P_{c} can be simplified as
Then, the resulting P_{c} can be used in the sealing dynamics to take the place of F_{c} in Eq. (8).
All in all, the calculation scheme can be summarized as Figure 4.
Results and Discussion
Test of Fractal Characteristic in Gas Face Seals
As not all rough surfaces own fractal characteristic [46], the precondition for using the MB model in gas face seals is to determine whether the surface of sealing rings own fractal characteristic. Ganti and Bhushan [47] proposed that for an isotropic fractal surface, the study of a section provides complete information about the surface because the fractal dimension D of the rough profile and that of the surface D_{s} are related as D = D_{s} + 1, and the profile and surface spectral densities are also related. Therefore, a surface can be characterized by fractal parameters D and G. Here, structure–function method [47] is adopted to analyze the properties of surface profiles. In the structure–function method, structure function S(τ) is defined as
where τ is an increment of x, and <·> means the space average. Substituting S(ω) from Eq. (1) in Eq. (18) and integrating to yield
where
and Γ is the Gamma function. As the structure function also follows a power law relation, Eq. (19) will transform into a line in the loglog plot of S(τ) ~ τ. If its slope k_{s} satisfies the interval of (0, 2), it reveals that the real surface owns fractal characteristic. Then, the fractal dimension D and the fractal roughness parameter G can be calculated by
where B_{s} is the intercept.
The surface of an isotropic carbongraphite ring, serving in an industrial spiral gasfaceseal product, is tested by the Talysuf surface topography measurement system. Three rough profiles spaced 120° apart are tested from inner radius to outer radius. The corresponding loglog plot of S(τ) ~ τ is displayed in Figure 5. The slopes of these three profiles are, respectively, 1.5933, 1.5905 and 1.5823, satisfying the interval of (0, 2) and verifying that the measured surface owns fractal characteristic. Therefore, the MB model can be used in this typical gas face seal. Using Eqs. (20) and (21), the fractal dimension D of the three profiles are, respectively, 1.2034, 1.2048 and 1.2089, and the fractal roughness parameter G are 2.9961 × 10^{−13} m, 2.1073 × 10^{−13} m and 3.5568 × 10^{−13} m, respectively.
Comparison of Steadystate and Transient Sealing Performance
Since face contact occurs under lowspeed conditions such as the startup and shutdown operations, and may take place during disturbances [4, 5], the following dynamic simulation is classified into two groups: the steadystate response under lowspeed conditions and the transient response to disturbances. Here, the typical operation condition parameter, pressure drop, is taken as the variable. The organized simulation cases are listed in Table 1. Table 2 illustrates the parameters of a spiral groove gas face seal. Table 3 shows the parameters of the CEB and the MB models with respect to the above three profiles. The total contact load of the CEB model is calculated by [9, 48]
where R is the mean summit radius, y_{s} is the distance between the mean of summit height and that of asperity height, ω_{c} is the critical elastic deformation of an asperity, and ϕ is the distribution function of summit height which is assumed to respect a Gaussian distribution. Note that the surface parameters used in the CEB model, as shown in Table 3 and Eq. (22), are calculated referring to Eqs. (A4, A9–A13) in the appendix of Ref. [48] based on three variables m_{0}, m_{2} and m_{4}. In Ref. [48], m_{0}, m_{2} and m_{4} are, respectively, defined as
Figure 6(a) displays the dimensionless contact area A ^{*}_{r} as a function of the dimensionless contact load P ^{*}_{c} using the MB and the CEB approaches, where P ^{*}_{c} = P_{c}/(A_{n}E) and A ^{*}_{r} = A_{r}/A_{n}. The contact area obtained by the CEB model is greater than that obtained by the MB model at the same contact load. The deviation between the two is in the same order of magnitude with the results of simulated surfaces in Figure 2 of Ref. [21]. It can be seen that the results obtained by the CEB model have fine distinctions, while those obtained by the MB model are overlapped. It is because that the dimensionless critical area of the asperity a ^{*}_{c} (a ^{*}_{c} = a_{c}/A_{n}) in the MB model is about 10^{−1} under current fractal parameters. When P ^{*}_{c} increases from 10^{−7} to 10^{−3}, the dimensionless largest area a ^{*}_{l} (a ^{*}_{l} = a_{l}/A_{n}) in the MB model increases from about 10^{−6} to 10^{−2}. In the MB model, it means that all the contact spots are smaller than the critical contact area, leading to full plastic contact. Thus, only the second term of Eq. (16) for plastic contact is available, and the distinction of G in Table 3 is not involved. One may wonder the explanation about the full plastic deformation, yet this phenomenon has also occurred in the case with D = 1.1 in Figure 10 of Ref. [14], and explained by Majumdar and Bhushan that the loadarea relation and the fraction of the contact area in elastic and plastic deformation are quite sensitive to fractal parameters [14]. This difference between the MB and the CEB approaches shows that the two approaches have distinctions in contact mechanism and end face damage regardless of the degree of distinctions in dynamic performance including film thickness, leakage rate and face contact load. Figure 6(b) shows the dimensionless gas film thickness h/σ as a function of the dimensionless contact load P ^{*}_{c} . It is obvious that the gas film thickness of the CEB model is smaller than that of the MB model at the same contact load. When P ^{*}_{c} is about 10^{−7}, the face contact load is too small to be considered. By this, h/σ is about 4.0 in the CEB model and 6.6 in the MB model. It means that if h/σ was in the interval of (4.0, 6.6), the MB model would provide a face contact load in the dynamic analysis whilst the CEB model would not. Therefore, it can be expected that there will be an apparent difference between the two approaches in the occurrence of face contact, which will be shown in the subsequent simulation under lowspeed conditions.
Profile 3 is selected to gauge the differences of sealing performance between the MB and the CEB approaches. A wholering numerical model is established for the dynamic analyses of a spiral groove gas face seal with a flexibly mounted stator using the finite element method. In regards to the accuracy and stability of a complex dynamic system, a very fine mesh and a very small time step would be ideal. Yet, a balance should be struck between accuracy and computing time. After experiments, it is determined that a time step of 1 × 10^{−6} s with a 3160finite element mesh is adopted. The simulation is carried out on a 2.3 GHz workstation.
Figure 7 shows the differences of steadystate performance using the MB and the CEB approaches under different pressure drops where the shaft speed Ω maintains at 31.4 rad/s. The leakage rate Q_{i} is r = (r_{i} + r_{g})/2 referring to the relationship
M_{gas} is the molar mass set to 29 g/mol, R_{gas} is the gas constant set to 8.314 J mol^{−1} K^{−1}, and T_{gas} is gas temperature set to 293 K. There is no difference under the nonpressuredrop condition (p_{o} = p_{i} = 0.1 MPa) because the gas film opening load F_{g} are able to balance the closing load F_{closing} at equilibrium and the face contact load F_{c} is zero. When p_{o} increases in Figure 7(b), F_{c} transforms into a nonzero value and its proportion in the total opening load rises. The larger the proportion of F_{c}, the more apparently the deviations display in the central film thickness at equilibrium and face contact load. However, after p_{o} reaching 5 MPa, the deviations of the two approaches in the central film thickness at equilibrium and face contact load start to decrease because the proportion of F_{c} obtained by the MB model starts to decrease, accounting for F_{g} becoming the dominant component of the total opening load again. The deviation in leakage rate still increases monotonically because the leakage rate is related to not only the film thickness but also the pressure drop. Moreover, it should be emphasized that before p_{o} arriving at 1 MPa, F_{c} obtained by the MB model starts to transform into a value of 40 N whilst F_{c} obtained by the CEB model is still maintains at nearly zero, which is in accordance with the prediction in Figure 6(b). It is concluded that the two approaches will induce differences in terms of the occurrence and the level of face contact.
Figure 8 illustrates the differences of transient performance using the MB and the CEB approaches during a fluctuation of pressure drop (i.e., p_{o}, instantaneously, raises from 1 to 2 MPa at 0.01 s) where shaft speed Ω maintains at 104.7 rad/s. The value of 104.7 rad/s is large enough to guarantee the completely opened state of the two mated rings. From the simulation case without the contact model, it can be seen that the fluctuation of pressure drop induces oscillations in the central film thickness and leakage rate. After coupling the contact model, face contact occurs. In Figure 8(b), the face contact load obtained by the MB model is greater than that obtained by the CEB model at the same film thickness under current sealing parameters, which is in accordance with Figure 6(b). When c decreases with an instantaneous increase of p_{o}, F_{c} obtained by the MB model occurs earlier and is greater at the same film thickness than that obtained by the CEB model. These lead to a result that the stator in the MB approach returns to a stable state faster and its oscillation amplitude is smaller. Moreover, though the distinctions of the two approaches about the oscillation amplitude and oscillation time are tiny in terms of film thickness and leakage rate, the distinction in the face contact load is apparent. A greater face contact load obtained by the MB model indicates that the surface of the seal would undergo much more severe wear during the fluctuation. Therefore, here, the dynamics using the CEB model will offer a more optimistic consideration of face wear than the dynamics using the MB model.
To sum up, the MB and the CEB approaches induce different steadystate and transient performance in the dynamic simulation. In particular, under current sealing parameters, even if the distinctions of the two approaches in film thickness and leakage rate are tiny, the two approaches will induce apparent differences in the occurrence and the level of face contact, which affect contact mechanism and end face damage. In addition, since not all surfaces own fractal characteristic, it should be emphasized that the use of the MB model in other types of seals or other fields has an extra limitation.
Investigation of Fractal Characteristic
Adhesive wear is a significant physical phenomenon in the dynamic analyses of gas face seals for its effect on the end face damage and service life. As adhesive wear is more easily caused by plastic deformation, it is better to raise the proportion of elastic deformation in the face contact. In the MB model, a feasible approach to raise the proportion of elastic deformation is to control the fractal parameters D and G. Therefore, a parametric investigation of D and G is performed. Note that the present study focuses on the influence of D and G on the proportion of elastic deformation. The detailed approach to realize the control of D and G should be researched in the manufactureprocess field.
The dimensionless form of total contact load in the MB model is rendered as [14]
where
Therefore, the proportion of elastic deformation can be deduced from Eqs. (2), (5), (7), (24) and (25)
The values of D and G^{*} are assumed within a common range, and other material properties are still selected from Table 2. Figure 9(a) shows the influence of D on the asperity contact where G^{*} maintains at 10^{−10}. The case with D = 1.5 has the greatest proportion of elastic contact area at the same A ^{*}_{r} . In the MB model, contact spots will be in plastic deformation when a < a_{c}. When D increases from 1.3 to 1.5, a_{c} decreases according to Eq. (2). It leads to the result that more and more contact spots transform from plastic deformation into elastic deformation. However, after D reaching 1.5, the positive effect caused by the decrease of a_{c} is surpassed by the negative effect caused by the refining of surface topography, leading to more spots in plastic deformation. With respect to the above negative effect, Majumdar and Bhushan [14] found that with the increase of D, the number of contact spots below the critical size increases and the contribution of these contact spots to the total contact area is significant. Figure 9(b) shows the influence of G^{*} on the asperity contact when D maintains at 1.5. It can be seen that the proportion of elastic contact area increases as G^{*} decreases because a_{c} decreases with a decrease of G^{*} according to Eq. (2). Since a_{c} decreases, a large amount of contact spots transform from plastic deformation into elastic deformation. It is concluded that a proper D (nearly 1.5) and a small G are helpful for maximizing the proportion of elastic deformation.
Conclusions

(1)
Fractal asperity contact model can provide an asperity contact load out of the influence of measuring instruments or sample length for its scaleindependence. It also uses an assumption of variable curvature radius. The MB fractal contact model is selected as the representative of fractal contact models in the attempt of incorporating the fractal theory into the dynamic research of gas face seals.

(2)
StructureFunction method is adopted to process the surface profiles of a typical carbongraphite ring which is an industrial product, proving the MB model can be utilized in the typical gas face seals.

(3)
The CEB statistical model is selected to compare with the MB model to gauge the differences of the two approaches in dynamic performance. The MB and the CEB approaches will induce differences in terms of the occurrence and the level of face contact. Although the distinctions in film thickness and leakage rate may be tiny, the distinctions in contact mechanism and end face damage are apparent. The CEB approach offers a more optimistic consideration of face contact.

(4)
An investigation of fractal parameters D and G is performed to explore a feasible approach to raise the proportion of elastic deformation to weaken adhesive wear in the sealing dynamic performance.
References
R Tong, G Liu, T Liu. Two dimensional nanoscale reciprocating sliding contacts of textured surfaces. Chinese Journal of Mechanical Engineering, 2016, 29(6): 531–538.
X Han, L Hua, S Deng. Influence of alignment errors on contact pressure during straight bevel gear meshing process. Chinese Journal of Mechanical Engineering, 2015, 28(6): 1089–1099.
Y Zhao, C Xia, H Wang, et al. Analysis and numerical simulation of rolling contact between sphere and cone. Chinese Journal of Mechanical Engineering, 2015, 28(3): 521–529.
W Huang, Y Lin, Z Gao, et al. An acoustic emission study on the starting and stopping processes of a dry gas seal for pumps. Tribology Letters, 2013, 49(2): 379–384.
W Huang, Y Lin, Y Liu, et al. Face rubimpact monitoring of a dry gas seal using acoustic emission. Tribology Letters, 2013, 52(2): 253–259.
J A Greenwood, J B P Williamson. Contact of nominally flat surfaces. Proceedings of the Royal Society, 1966, 295(1442): 300–319.
J I Mccool. Comparison of models for the contact of rough surfaces. Wear, 1986, 107(1): 37–60.
B Bhushan, M T Dugger. Real contact area measurements on magnetic rigid disks. Wear, 1990, 137(1): 41–50.
W R Chang, I Etsion, D B Bogy. An elasticplastic model for the contact of rough surfaces. Journal of Tribology, 1987, 109(2): 257–263.
L Kogut, I Etsion. ElasticPlastic contact analysis of a sphere and a rigid flat. Journal of Applied Mechanics, 2002, 69(5): 657–662.
L Kogut, I Etsion. A finite element based elasticplastic model for the contact of rough surfaces. Tribology Transactions, 2003, 46(3): 383–390.
R S Sayles, T R Thomas. Surface topography as a nonstationary random process. Nature, 1978, 271(5644): 431–434.
B Bhushan, J C Wyant, J Meiling. A new threedimensional non–contact digital optical profiler. Wear, 1988, 122(3): 301–312.
A Majumdar, B Bhushan. Fractal model of elasticplastic contact between rough surfaces. Journal of Tribology, 1991, 113(1): 1–11.
S Wang, K Komvopoulos. A fractal theory of the interfacial temperature distribution in the slow sliding regime: part Ielastic contact and heat transfer analysis. Journal of Tribology, 1994, 116(4): 812–822.
S Wang, K Komvopoulos. A fractal theory of the interfacial temperature distribution in the slow sliding regime: part IImultiple domains, elastoplastic contacts and applications. Journal of Tribology, 1994, 116(4): 824–832.
K Komvopoulos, W Yan. Contact analysis of elasticplastic fractal surfaces. Journal of Applied Physics, 1998, 84(7): 3617–3624.
P Sahoo, S K R Chowdhury. A fractal analysis of adhesive friction between rough solids in gentle sliding. Proceedings of the Institution of Mechanical Engineers Part J: Journal of Engineering Tribology, 2000, 124(6): 583–595.
P Sahoo, S K R Chowdhury. A fractal analysis of adhesive wear at the contact between rough solids. Wear, 2002, 253(9): 924–934.
M Ciavarella, G Muroloa, G Demelioa, et al. Elastic contact stiffness and contact resistance for the Weierstrass profile. Journal of the Mechanics and Physics of Solids, 2004, 52(6): 1247–1265.
L Kogut, R L Jackson. A comparison of contact modeling utilizing statistical and fractal approaches. Journal of Tribology, 2006, 128(1): 213–217.
Y Morag, I Etsion. Resolving the contradiction of asperities plastic to elastic mode transition in current contact models of fractal rough surfaces. Wear, 2007, 262(5, 6): 624–629.
I Etsion. A review of mechanical face seal dynamic. Shock and Vibration, 1982, 14(3): 9–14.
I Etsion. Mechanical face seal dynamics update. Shock and Vibration, 1985, 17(4): 11–16.
I Etsion. Mechanical face seal dynamics 1985–1989. Shock and Vibration, 1991, 23(4): 3–7.
W Shapiro, R Colsher. Steadystate and dynamic analysis of a jet engine, gas lubricated shaft seal. ASLE Transactions, 1974, 17(3): 190–200.
B A Miller, I Green. Numerical formulation for the dynamic analysis of spiralgrooved gas face seal. Journal of Tribology, 2001, 123(2): 395–403.
I Green, R M Barnsby. A simultaneous numerical solution for the lubrication and dynamic stability of noncontacting gas face seals. Journal of Tribology, 2001, 123(2): 388–394.
I Green, R M Barnsby. A parametric analysis of the transient forced response of noncontacting conedface gas seals. Journal of Tribology, 2002, 124(1): 151–157.
S Hu, W Huang, X Liu, et al. Influence analysis of secondary Oring seals in dynamic behavior of spiral groove gas face seals. Chinese Journal of Mechanical Engineering, 2016, 29(3): 505–514.
N Zirkelback, S Andresl. Effect of frequency excitation on force coefficients of spiral groove gas seals. Journal of Tribology, 1999, 121(4): 853–863.
N Zirkelback. Parametric study of spiral groove gas face seals. Tribology Transactions, 2000, 43(2): 337–343.
B Ruan. A semianalytical solution to the dynamic tracking of non–contacting gas face seals. Journal of Tribology, 2002, 124(1): 196–202.
S Hu, W Huang, X Liu, et al. Stability and tracking analysis of gas face seals under lowparameter conditions considering slip flow. Journal of Vibroengineering, 2017, 19(3): 2126–2141.
B A Miller, I Green. Semianalytical dynamic analysis of spiralgrooved mechanical gas face seals. Journal of Tribology, 2003, 125(3): 403–413.
S R Harp, R F Salant. Analysis of mechanical seal behavior during transient operation. Journal of Tribology, 1998, 120(2): 191–197.
I Green. A transient dynamic analysis of mechanical seals including asperity contact and face deformation. Tribology Transactions, 2002, 45(3): 284–293.
B Ruan. Numerical modeling of dynamic sealing behaviors of spiral groove gas face seals. Journal of Tribology, 2002, 124(1): 186–195.
S Hu, N Brunetiere, W Huang, et al. Stratified revised asperity contact model for worn surfaces. Journal of Tribology, 2017, 139(2): 021403.
S Hu, N Brunetiere, W Huang, et al. Continuous separating method for characterizing and reconstructing biGaussian stratified surfaces. Tribology International, 2016, 102: 454–462.
S Hu, N Brunetiere, W Huang, et al. Stratified effect of continuous biGaussian rough surface on lubrication and asperity contact. Tribology International, 2016, 104: 328–341.
S Hu, N Brunetiere, W Huang, et al. BiGaussian surface identification and reconstruction with revised autocorrelation functions. Tribology International, 2017, 110: 185–194.
S Hu, N Brunetiere, W Huang, et al. Evolution of biGaussian surface parameters of siliconcarbide and carbongraphite discs in a dry sliding wear process. Tribology International, 2017, 112: 75–85.
S Hu, N Brunetiere, W Huang, et al. The biGaussian theory to understand sliding wear and friction. Tribology International, 2017, 114: 186–191.
S Hu, W Huang, N Brunetiere, et al. Truncated separation method for characterizing and reconstructing biGaussian stratified surfaces. Friction, 2017, 5(1): 32–44.
A Majumdar, C L Tien. Fractal characterization and simulation of rough surfaces. Wear, 1990, 136(2): 313–327.
S Ganti, B Bhushan. Generalized fractal analysis and its applications to engineering surfaces. Wear, 1995, 180(1): 17–34.
I Etsion, I Front. A model for static sealing performance of end face seals. Tribology Transactions, 1994, 37(1): 111–119.
Authors’ Contributions
STH was in charge of the whole trial; STH wrote the manuscript; WFH, XFL and YMW assisted with sampling and laboratory analyses. All authors have read and approved the final manuscript.
Authors’ Information
SongTao Hu, born in 1989, is currently a postdoctoral fellow at State Key Laboratory of Mechanical System and Vibration, Shanghai Jiao Tong University, China. He received his doctorate degree from State Key Laboratory of Tribology, Tsinghua University, China, in 2017, and received his bachelor degree from Northwestern Polytechnical University, China, in 2012. His research interests include mechanical face seals. Tel: +8618221229658; Email: hsttaotao@sjtu.edu.cn.
WeiFeng Huang, born in 1978, is currently an associate professor at State Key Laboratory of Tribology, Tsinghua University, China. His research interests include mechanical face seals. Tel: +861062795124; Email: huangwf@tsinghua.edu.cn.
XiangFeng Liu, born in 1961, is currently a professor at State Key Laboratory of Tribology, Tsinghua University, China. His research interests are machine design and mechanical face seals. Tel: +861062795122; Email: liuxf@tsinghua.edu.cn.
YuMing Wang, born in 1941, is currently a professor at State Key Laboratory of Tribology, Tsinghua University, China, and an academician of Chinese Academy of Engineering. His research interest is fluid sealing technology. Tel: +861062771865; Email: yumingwang@tsinghua.edu.cn.
Competing Interests
The authors declare no competing financial interests.
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Funding
Supported by China Postdoctoral Science Foundation (Grant No. 2017M621458), National Science and Technology Support Plan Projects (Grant No. 2015BAA08B02), National Natural Science Foundation of China (Grant No. 11632011), and National Natural Science Foundation of China (Grant No. 11372183).
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Hu, ST., Huang, WF., Liu, XF. et al. Application of Fractal Contact Model in Dynamic Performance Analysis of Gas Face Seals. Chin. J. Mech. Eng. 31, 27 (2018). https://doi.org/10.1186/s1003301802247
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DOI: https://doi.org/10.1186/s1003301802247
Keywords
 Fractal theory
 Asperity contact
 Gas face seal
 Dynamic performance