Issue 
Mechanics & Industry
Volume 20, Number 2, 2019



Article Number  201  
Number of page(s)  8  
DOI  https://doi.org/10.1051/meca/2019001  
Published online  08 April 2019 
Regular Article
Fluidsolid coupling characteristics analysis for tripod sliding universal joints
College of Mechanical and Electrical Engineering, Qingdao University of Science and Technology, Qingdao, Shandong, PR China
^{*} email: y_f_q@163.com
Received:
23
August
2018
Accepted:
6
January
2019
Fluidsolid coupling theory is introduced into tripod sliding universal joint design. The geometric models of the tripod sliding universal joint and lubricant film are established respectively and meshed. Fluidsolid coupling analyses of tripod sliding universal joints in unidirectional and bidirectional scenarios are performed to investigate sleeve and lubricant film coupling as well as sliding pin and lubricant film coupling under various differential pressures and frequencies. In the condition of unidirectional and bidirectional coupling, sleeve and sliding pin deformation and stress increase gradually with differential pressure and frequency. Under various differential pressures and frequencies, tripod sliding universal joint bidirectional coupling deformation and stress are greater than those of unidirectional coupling. The theory of fluidsolid coupling is combined with the tripod sliding universal joint for the first time in this paper. The fluidsolid coupling analysis results are of great significance and benefit to the design, application and marketing of tripod sliding universal joints.
Key words: Tripod sliding universal joint / hydrodynamic oil film / fluidsolid coupling / dynamic mesh technology
© AFM, EDP Sciences 2019
1 Introduction
Fluidsolid coupling is a crossdisciplinary science that combines higher mathematics, fluid mechanics and solid mechanics to investigate fluidsolid coupling. Research and applications of fluidsolid coupling date to the 19th century. Tziritas et al. employed the finitedifference method and Gauss–Seidel iterative method to solve the modified transient Reynolds equation [1]. Wodtke et al. employed the fluidsolid coupling method to analyze the thermal elastohydrodynamic lubrication of bearings and gears [2]. Tian et al. created a new rigidflexible multisystem model and employed a fluidsolid coupling method to calculate lubricant film pressure distribution [3]. Liu et al. performed numerical analysis for water turbines via fluidsolid coupling [4]. Xu investigated the bidirectional fluidsolid coupling dynamics modeling of aqueduct structure [5]. Zhang et al. solved fluidsolid thermal coupling system (bearing, lubricating oil and axial diameter) for turbogenerator journal bearings [6]. Mao et al. investigated and analyzed the dynamic characteristics of nonlinear oil films of sliding bearings based on fluidsolid coupling [7]. Shi et al. performed fluidsolid coupling simulation analyses for hydrodynamic journal bearings [8]. Yang et al. analyzed the dynamics characteristics of steam turbine bearings based on fluidsolid coupling [9]. These studies provide ideas and methods for the fluidsolid coupling analysis of tripod sliding universal joints.
The fluidsolid coupling analysis of the tripod sliding universal joint is carried out, which makes the analysis results closer to the reality. However, due to the complexity of fluidsolid coupling system, the long calculation period and the difficulty of calculation, previous study on lubrication characteristics of the joints did not take into account the deformation behavior of solids under the action of flow field and the reaction of the position and shape of solids to flow field [10,11]. In this paper, fluidsolid coupling analyses of sleeve and lubricant film coupling as well as sliding pin and lubricant film coupling in unidirectional and bidirectional scenarios are performed under different working conditions. The two coupling results are compared and analyzed.
2 Fluid domain analysis
2.1 Fluid control equation
Compared with the normal Reynolds equation, the fluid dynamics control equation simulates the lubricating characteristics of tripod sliding universal joints more accurately.
 1.
Mass conservation equation
According to mass conservation, control body internal mass increment equals the mass flowing into the control body:$$\frac{D\rho}{Dt}+\rho {\displaystyle \overrightarrow{\nabla}}\cdot {\displaystyle \overrightarrow{v}}=0$$(1)
In formula (1), $\frac{D}{Dt}$ is the particle derivative, ρ is the fluid density, $\overrightarrow{v}$ is the velocity vector and $\overrightarrow{\nabla}$ is the gradient vector.
 2.
Momentum conservation equation
According to the conservation of momentum, the control body momentum increment equals the sum of influent momentum, surface force impulse and volume force impulse. The differential form of fluid motion equation is:$$\rho \frac{D{\displaystyle \overrightarrow{\mathit{v}}}}{Dt}\rho {\displaystyle \overrightarrow{f}}{\displaystyle \overrightarrow{\nabla}}\times {\displaystyle \overrightarrow{\mathit{\iota}}}={\displaystyle \overrightarrow{\mathbf{0}}}$$(2)In formula (2), $\overrightarrow{\mathit{f}}$ is the body force, and $\overrightarrow{\mathit{\iota}}$ is the surface tension. In the rectangular coordinate system, stress tensor is as follows:$$\overrightarrow{\mathit{\iota}}}=\left[\begin{array}{ccc}\hfill {\mathit{\sigma}}_{x}\hfill & \hfill {\mathit{\iota}}_{xy}\hfill & \hfill {\mathit{\iota}}_{xz}\hfill \\ \hfill {\mathit{\iota}}_{yx}\hfill & \hfill {\mathit{\sigma}}_{y}\hfill & \hfill {\mathit{\iota}}_{yz}\hfill \\ \hfill {\mathit{\iota}}_{zx}\hfill & \hfill {\mathit{\iota}}_{zy}\hfill & \hfill {\mathit{\sigma}}_{z}\hfill \end{array}\right]$$
 3.
Energy conservation equation
Conservation of energy means that the sum of mechanical energy and all internal energy in a system is equal to the total energy of the system. According to the energy conservation equation, control body energy variation equals the sum of influent energy, surface force work, volume force work and influent heat:$$\frac{DE}{Dt}=\frac{DQ}{Dt}+\frac{DW}{Dt}$$(3)
In formula (3), E is the internal energy of the system, Q is the heat transferred into the system from the external environment and W is the external work on the system.
2.2 Threedimensional model and boundary condition
The Pro/E modeling system is used to build the model of the tripod sliding universal joint and lubricant film [12], as shown in Figure 1.
As the lubricant film between the tripod sleeve and sliding pin in the tripod sliding universal joint is very thin, the ratio between the lubricant film length and thin wall dimension is very large, which makes meshing difficult. Therefore, an unstructured mesh is created using the octree algorithm in ICEM (shown in Fig. 2a), which has superior robustness. Although unstructured mesh facilitates complex area meshing, when the unstructured mesh is imported into FLUENT for solving, the mesh may result in a significant expansion ratio that could affect calculation precision. Therefore, the unstructured mesh should be converted into a polyhedron mesh for calculation, as shown in Figure 2b.
FLUENT and ANSYS WORKBENCH are combined to analyze fluidsolid coupling [13,14]. The flow field is set as an incompressible flow field and the SIMPLE velocitypressure algorithm is employed to obtain a solution. The kɛ turbulent flow model is also employed. When solving the tripod sliding universal joint lubrication model, the outlet pressure is equal to atmospheric pressure and P100 lubricating oil is selected as the lubricant. The material attributes of the tripod sleeve and sliding pin are listed in Table 1. The characteristics of the lubricating oil are listed in Table 2.
Fig. 1 Threedimensional diagram of tripod sliding universal joint and lubricant film. 
Fig. 2 Lubricant film mesh. 
2.3 Flow field analysis results
2.3.1 Flow field analysis results under various differential pressures
Differential pressure is the difference between pressureinlet and pressureoutlet in lubricating area. According to the actual working condition of the joint, flow field distribution data of lubricant films are obtained via FLUENT under various differential pressures (5e + 7, 6.5e + 7, 8e + 7 and 1e + 8 Pa).
Figure 3a shows lubricant film pressure nephogram when the differential pressure is 5e + 7 Pa. The scatter diagram in Figure 3b shows the maximum fluid pressure under various differential pressures. Other parts are ignored and only the place with the thinnest lubricant film, i.e., the actual lubricating area of the lubricant film, is observed. Figure 3 shows that the maximum lubricant film pressure is at the inlet and the minimum pressure is at the outlet. Overall lubricant film pressure and the maximum fluid pressure increase with differential pressure. Negative pressure in the lubricant film means the lubricant film could rupture and cavitation could occur. In the pressure nephogram, the lubricant film rupture region has a negative value. However, the actual pressure is 0, and a rising negative pressure increases gasification. This reduces the mixture density of the lubricating oil, which is unfavorable to lubricant film bearing and affects the lubricating capability of the lubricant film.
Fig. 3 Lubricant film pressure. 
2.3.2 Flow field analysis results under various frequencies
With constant differential pressure, various frequencies are selected for flow field analysis to obtain lubricant film pressure nephograms and a scatter diagram (Fig. 4). Figure 4a shows lubricant film pressure nephogram when the frequency is 10 Hz. The scatter diagram in Figure 4b shows the maximum fluid pressure under various frequencies (10, 20, 30, 40 and 50 Hz).
From the analysis results, lubricant film pressure changes with frequency. Under constant differential pressure, lubricant film pressure increases with frequency and the probability of lubricant film rupture also increases. After lubricant film rupture, the rupture region increases with frequency. As shown in Figure 4b, when the frequency is in the range of 10–40 Hz, the amplitude of lubricant film pressure variation is moderate and the difference is insignificant. When frequency increases to 50 Hz, the amplitude of lubricant film pressure variation increases suddenly, and the increment is apparent.
Fig. 4 Lubricant film pressure. 
3 Unidirectional coupling
3.1 Fluidsolid coupling results under various differential pressures
3.1.1 Tripod sleeve
A tripod sliding universal joint under fluidsolid coupling is simulated to obtain overall tripod sleeve deformation under various differential pressures. The sleeve deformation nephogram when the differential pressure is 5e + 7 Pa and a scatter diagram are shown in Figure 5.
Figure 5 shows that sleeve deformation increases gradually with differential pressure. The maximum tripod sleeve deformation is close to input axis, where the coupling deformation effect of the lubricant film fluid domain and sleeve solid domain is the most apparent. Along the downward direction of the axis, sleeve deformation reduces gradually. Although such deformation is moderate for the sleeve, it is substantial compared with lubricant film thickness.
Figure 6a is sleeve stress diagram when the differential pressure is 5e + 7 Pa. A new path is created along the holes in the sleeve from top to bottom and a corresponding stress curve is generated, as shown in Figure 6b. Figure 6b shows that sleeve stress near the first ring bulge of the wearresistant structure close to inlet has a clear fluctuation; then, the fluctuations decline gradually and almost all fluctuations occur at the ring bulge. The maximum stress is at the junction between the first ring bulge and the sleeve, where stress concentration is likely to occur. When stress exceeds an allowed value, it could reduce the service life of the sleeve or cause accidents, such as fracture. The scatter diagram in Figure 6c shows that maximum sleeve stress increases with differential pressure and the variation rate is considerable. This means that differential pressure has a significant impact on sleeve stress.
Fig. 5 Overall deformation nephogram of sleeve. 
Fig. 6 Sleeve stress nephogram. 
3.1.2 Sliding pin
A tripod sliding universal joint under fluidsolid coupling is simulated to obtain overall tripod sliding pin deformation under various differential pressures. The sliding pin deformation nephogram when the differential pressure is 5e + 7 Pa and a scatter diagram are shown in Figure 7.
Figure 7 shows that the maximum deformation of the sliding pin occurs at the first thinnest lubricant film close to the end. Overall sliding pin deformation along the axis demonstrates the trend of gradual change, which results in local convergence and diffusion clearance and thus changes the structure of the lubricant film at the clearance of the tripod sliding universal joint and affects parameters in the lubricant film flow field. Sliding pin deformation gradually increases with differential pressure and becomes more substantial compared with sleeve deformation. This means that the sliding pin is more susceptible to the flow field, which is related to the sliding pin material and dimensions.
Figure 8a shows slide pin stress diagram under various differential pressures. Figure 8b shows a path created along the sliding pin from bottom to top and the corresponding stress curve. Figure 8a and b show that sliding pin stress declines gradually from top to bottom. Stress variation is not a smooth curve, but fluctuates. Fluctuating points concentrate at the ring bulge of the wearresistant structure. There are three changes from top to bottom. The first two have significant stress fluctuations and the last one is relatively smooth. Stress concentrates at the ring bulge of the sliding pin. These areas have the highest levels of stress and strain. Deformation or fracture is likely to occur, which affects the service life of the tripod sliding universal joint. Just like the sleeve, the scatter diagram in Figure 8c shows that maximum sliding pin stress increases with differential pressure and the variation rate is considerable.
Fig. 7 Overall deformation nephogram of tripod sliding pin. 
Fig. 8 Stress nephogram of sliding pin. 
3.2 Fluidsolid coupling results under various frequencies
3.2.1 Tripod sleeve
Figure 9 shows sleeve deformation nephogram when the frequency is 10 Hz and a scatter diagram. Figure 9 shows that the maximum sleeve deformation is at the inlet and then gradually reduces along the direction toward the interior. Sleeve deformation also gradually increases with frequency. When the differential pressure increases, the sleeve deformation changes significantly. However, in contrast to the differential pressure, the frequency variation induced deformation variation is relatively small, and the deformation growth rate is stable.
Figure 10 shows sleeve stress nephogram when the frequency is 10 Hz and a scatter diagram. As shown in Figure 10, the maximum sleeve stress increases with frequency and the range of the maximum stress gradually expands. In the range of 20–40 Hz, the stress variation rate is moderate and stable; however, at 10 Hz or 50 Hz, the curve variation rate has an apparent significant change. This means that when frequency is too high or too low, stress change is apparent.
Fig. 9 Overall sleeve deformation nephogram. 
Fig. 10 Sleeve stress nephogram. 
3.2.2 Sliding pin
Figure 11 shows sliding pin deformation nephogram when the frequency is 10 Hz and a scatter diagram. As shown in Figure 11, the overall deformation of the sliding pin in the tripod sliding universal joint gradually increases with frequency; deformation at the ring bulge is greater than that of the sliding bar. When the frequency is low, deformation variation is small. As frequency increases, deformation increases significantly. When the frequency grows to a certain level, the deformation increment slows; however, the overall trend grows. The trend of deformation variation rate initially increases and subsequently decreases.
Figure 12 shows sliding pin stress nephogram when the frequency is 10 Hz and a scatter diagram. As shown in Figure 12, the sliding pin stress variation trend is similar to the deformation variation trend. Both increase initially and subsequently decrease. Stress also increases with frequency. In the midrange of frequency, stress variation rate is stable and stress increases quickly. When frequency reaches 50 Hz, the increasing trend slows down significantly. Compared with the tripod sleeve, the sliding pin is more susceptible to equivalent stress. Additionally, higher velocity results in higher fluid dynamic pressure and a higher peak value of equivalent stress. Consequently, the sliding pin exceeds the allowed stress, which results in wear deformation or fracture.
Fig. 11 Overall deformation nephogram of sliding pin. 
Fig. 12 Stress nephogram of sliding pin. 
4 Bidirectional coupling
A dynamic mesh is defined by the Profile and UDF macros in FLUENT [15]. Coupling data are configured based on the parameters in Tables 1 and 2. The time step is defined as 0.001 s and the solution stop time is 0.2 s. The initial loop sequence starts from the flow field calculation [16].
Figure 13 shows a lubricant film pressure diagram. Figure 13 shows that, compared with unidirectional coupling, the highpressure range in bidirectional coupling expands significantly. This is because, in unidirectional coupling, the fluid domain only transfers pressure to the solid domain and the solid domain cannot feed data back to the fluid. In bidirectional coupling, however, the solid is under flow field pressure and displacement is fed back to the flow field. Based on the mesh node diffusion model, the flow field starts to calculate displacement diffusion, then generates new fluid mesh after deformation.
Material attributes.
Characteristics of P100 lubricating oil at 295 K (temperature).
Fig. 13 Lubricant film pressure. 
4.1 Fluidsolid coupling results under various differential pressures
Figure 14 shows deformation diagrams under various differential pressures. Figure 15 shows stress diagrams under various differential pressures. When the fluid domain exterior wall and solid domain interior wall are coupled and other conditions are identical, sleeve deformation and stress increase with differential pressure; the results for bidirectional coupling are larger than those for unidirectional coupling. Additionally, higher differential pressure induces a more significant difference between the results in unidirectional coupling and those in bidirectional coupling. Compared with unidirectional coupling analysis, bidirectional coupling analysis is more complex because both convergence and computing cost need to be considered. However, the lubricant film in the tripod sliding universal joint is very thin (less than 1 μm) and extremely thin lubricant film has the following consequence: slight solid deformation results in significant changes in the lubricant film. In terms of numerical precision, bidirectional coupling is superior.
Figures 14 and 15 show that, when the fluid domain interior wall and solid domain exterior wall are coupled and other conditions are identical, sliding pin deformation and stress increase with differential pressure. The line chart shows that bidirectional coupling shows more significant deformation and stress than unidirectional coupling. Compared with the sleeve, the sliding pin has a more significant difference between unidirectional coupling and bidirectional coupling. In general, stronger unidirectional coupling results in a more significant calculation deviation. The comparisons in Figures 7, 8 and Figures 11, 12 show that unidirectional coupling has a more significant impact on the sliding pin, which means sliding pin unidirectional coupling has a larger error.
Fig. 14 Deformation diagrams under various differential pressures. 
Fig. 15 Stress diagrams under various differential pressures. 
4.2 Fluidsolid coupling results under various frequencies
As shown in Figure 16a and c, a path curve from 1 to 2 is set up to observe the variation of the deformations of the sleeve and the sliding pin on the specified path under various frequencies and to record the data in Figure 16b and d.
The sleeve and sliding pin deformation analysis results are shown in Figure 16. Figure 16 shows that the sleeve has less severe deformation than the sliding pin. When frequency increases, the deformation diagrams of both the sliding pin and the sleeve increase. The sleeve deformation variation rate is more apparent than the sliding pin variation rate. The difference between unidirectional coupling and bidirectional coupling is smaller at low frequencies. As frequency rises, the difference between deformation variation rates under unidirectional coupling and bidirectional coupling gradually increase. The difference between the sliding pin deformations under unidirectional coupling and bidirectional coupling is significant; however, the deformation variation rates are relatively gentle and the growth trends are similar. As frequency rises, the bidirectional variation rate is more apparent than the unidirectional variation rate.
As shown in the Figure 17a and c, a path curve from 1 to 2 is set up to observe the variation of the stresses of the sleeve and the sliding pin on the specified path under various frequencies and to record the data in Figure 17b and d.
The sleeve and sliding pin stress analysis results are shown in Figure 17. Similar to the trend of the deformation curve, sleeve and sliding pin stress variations also increase with frequency. For the sliding pin, the difference between the results for unidirectional coupling and those for bidirectional coupling is greater than that for the sleeve. Figure 17 shows that when the frequency is low, the difference in sleeve stress variations between unidirectional and bidirectional coupling is moderate. However, as frequency increases, the sleeve stress variation rate is significantly larger than the deformation variation rate. Higher frequency results in a more significant difference between the unidirectional coupling result and the bidirectional coupling result. The sliding pin stress variation rate is moderate; however, the overall stress difference is significant. Based on the unidirectional coupling analysis in Section 2, despite various differential pressures and frequencies, unidirectional coupling and bidirectional coupling have a more significant impact for the sliding pin; the sliding pin is more susceptible to stress concentration and is likely to develop bending, which affects the service life of the joint.
Fig. 16 Deformation diagrams under various frequencies. 
Fig. 17 Stress diagrams under various frequencies. 
5 Conclusions

Lubricant film pressure increases with differential pressure and frequency.

In unidirectional coupling, tripod sleeve and sliding pin deformations and stresses increase with differential pressure and frequency. Sliding pin deformation and stress variations are more apparent.

In bidirectional coupling, sleeve and sliding pin deformations and stresses increase with differential pressure and frequency.

Under various differential pressures and frequencies, the deformation and stress in bidirectional coupling are greater than those for unidirectional coupling; the differences in sleeve deformations and stresses between unidirectional coupling and bidirectional coupling increase gradually with differential pressure and frequency. Differences in sliding pin deformations and stresses between unidirectional and bidirectional coupling are relatively stable; however, they are significantly larger for the sleeve.
Nomenclature
$\overrightarrow{v}$ : Velocity vector
$\overrightarrow{\nabla}$ : Gradient vector
$\overrightarrow{f}$ : Body force
$\overrightarrow{\mathit{\iota}}$ : Surface tension
E : Internal energy of the system
Q : Heat transferred into the system from the external environment
W : External work on the system
Acknowledgement
This paper was supported by the key research and development project (Science and technology for public welfare) program of Shandong Province (Grant NO.2018GGX103015).
References
 G. Tziritas, Recursive and iterative estimation of the twodimensional velocity field and reconstruction of threedimensional motion, Signal Process. 16 (1989) 53–72 [CrossRef] [Google Scholar]
 M. Wodtke, A. Olszewski, M. Wasilczuk, Application of the fluidstructure interaction technique for the analysis of hydrodynamic lubrication problems, Proc. Inst. Mech. Eng. Part J J. Eng. Tribol. 227 (2013) 888–897 [CrossRef] [Google Scholar]
 Q. Tian, Y. Sun, C. Liu et al., Elastohydrodynamic lubricated cylindrical joints for rigidflexible multibody dynamics, Comput. Struct. 114–115 (2013) 106–120. [CrossRef] [Google Scholar]
 D. Liu, S. Liu, Y. Wu et al., Numerical simulation of hydraulic turbine based on fluidstructure coupling, Chin. J. Hydrodyn. (2008) 345–351. [Google Scholar]
 J.G. Xu, H. Chen, B. Wang et al., Dynamic modeling study of aqueduct structure with fluidstructure coupling, J. Nanjing Univ. Sci. Technol. 2005. [Google Scholar]
 P.L. Zhang, H. Zhang, Z.D. Wu et al., Application of the fluidsolidheat interaction method to study the lubrication of a 1000MW turbine generator journal bearing, Large Electr. Mach. Hydraulic Turbine 05 (2013) 30–33. [Google Scholar]
 W.G. Mao, X. Han, G.P. Liu, Research on the dynamic characteristics of nonlinear slide bearing oil films based on fluidsolid interaction, China Mech. Eng. 25 (2014). [Google Scholar]
 Y.X. Shi, Y. Yang, Y.Z. Wang, Simulation analysis of fluidsolid coupling for hydrodynamic sliding bearings, Process Equip. Piping 51 (2014) 43–46 [Google Scholar]
 J.G. Yang, T. Cai, M. Gao, Threedimensional fluidsolid analytical model of steam turbine bearings, Proc. Chin. Soc. Electr. Eng. 24 (2004) 147–151 [Google Scholar]
 X.F. Wang, D.G. Chang, J.Z. Wang, Kinematic investigation of tripod sliding universal joint based on coordinate transformation, Multibody Syst. Dyn. 22 (2009) 97–113 [CrossRef] [Google Scholar]
 Y. Zhou, D.G. Chang, S.M. Li, Analysis on grease lubrication properties of the tripod sliding universal coupling in automotive transmission shaft, Ind. Lubr. Tribol. 69 (2017) 598–604 [CrossRef] [Google Scholar]
 Y. Zhou, Study on the dual automotive universal joint friction and lubrication, Qingdao University of Science and Technology, 2017. [Google Scholar]
 S. Zhang, L.J. Xiao, Q. Liu et al, Tribology performance testing and fluidsolidthermal coupling simulation of automotive ventilated disc brakes, Automot. Eng. 39 (2017) 675–682. [Google Scholar]
 L.D. Li, S. Li, Numerical simulation technology based on CFX and Workbench software, China Measur. Test 36 (2010) 79–80+ 83. [Google Scholar]
 T. Li, Study on the transient characteristics of hydrodynamic mechanical seal multifield interaction, Jiangsu University, 2017. [Google Scholar]
 S.J. Zheng, Liquidsolidthermal coupling analysis and flow visualization of cartridge poppet valves, Taiyuan University of Technology, 2015. [Google Scholar]
Cite this article as: F. Yang, X. Liu, S. Zhao, L. Sun, Fluidsolid coupling characteristics analysis for tripod sliding universal joints, Mechanics & Industry 20, 201 (2019)
All Tables
All Figures
Fig. 1 Threedimensional diagram of tripod sliding universal joint and lubricant film. 

In the text 
Fig. 2 Lubricant film mesh. 

In the text 
Fig. 3 Lubricant film pressure. 

In the text 
Fig. 4 Lubricant film pressure. 

In the text 
Fig. 5 Overall deformation nephogram of sleeve. 

In the text 
Fig. 6 Sleeve stress nephogram. 

In the text 
Fig. 7 Overall deformation nephogram of tripod sliding pin. 

In the text 
Fig. 8 Stress nephogram of sliding pin. 

In the text 
Fig. 9 Overall sleeve deformation nephogram. 

In the text 
Fig. 10 Sleeve stress nephogram. 

In the text 
Fig. 11 Overall deformation nephogram of sliding pin. 

In the text 
Fig. 12 Stress nephogram of sliding pin. 

In the text 
Fig. 13 Lubricant film pressure. 

In the text 
Fig. 14 Deformation diagrams under various differential pressures. 

In the text 
Fig. 15 Stress diagrams under various differential pressures. 

In the text 
Fig. 16 Deformation diagrams under various frequencies. 

In the text 
Fig. 17 Stress diagrams under various frequencies. 

In the text 
Current usage metrics show cumulative count of Article Views (fulltext article views including HTML views, PDF and ePub downloads, according to the available data) and Abstracts Views on Vision4Press platform.
Data correspond to usage on the plateform after 2015. The current usage metrics is available 4896 hours after online publication and is updated daily on week days.
Initial download of the metrics may take a while.