Journal of
Mechanical Engineering Research

  • Abbreviation: J. Mech. Eng. Res.
  • Language: English
  • ISSN: 2141-2383
  • DOI: 10.5897/JMER
  • Start Year: 2009
  • Published Articles: 112

Frictional effect on stress and displacement fields in contact region

Saeed Adibnazari
  • Saeed Adibnazari
  • Department of Mechanical and Aerospace Engineering, Science and Research Branch, Islamic Azad University, Tehran, Iran.
  • Google Scholar
Ali Anvari
  • Ali Anvari
  • Department of Mechanical and Aerospace Engineering, Science and Research Branch, Islamic Azad University, Tehran, Iran.
  • Google Scholar


  •  Received: 06 August 2017
  •  Accepted: 07 September 2017
  •  Published: 30 September 2017

 ABSTRACT

In this study, by applying Giannakopoulos and Pallot’s stress and displacement equations, and using the Goryacheva’s friction model, the stress and displacement equations are obtained. Finally, by applying analytical method, these equations are solved. By assuming that the roller is rigid and the substrate is almost homogeneous with constant Poisson ratio and constant elastic modulus, the results of frictional effect on stress and displacement fields are achieved and are shown in figures. Using different amounts of friction coefficient, the effect of friction coefficient on stress and displacement inside the contact region in the figures is observed. The new results achieved by the analytical method used in this study for obtaining tangential stress and displacement inside the contact region is compared with the results that were already achieved for obtaining tangential stress and displacement inside the contact region in another study. The comparison between the two analytical methods showed similarity in the results that are achieved by both methods. These results may be very advantageous in the design of suitable substrate and cylinder that are in contact, especially in the model that the substrate is almost homogeneous and the cylinder is rigid.

Key words: Friction, contact, stress field, displacement field.


 INTRODUCTION

The present study examines the frictional effect on stress and displacement fields in the contact region. It appears that friction is an undeniable phenomenon in contact with two or more materials. For calculating the amount of friction, many approaches are employed. One of the important contacts investigated in the presence of friction is the contact of roller with half space. Wheel with rail, as well as tire with road, contacts are examples of roller contact with half space. The contact region is the region where two or more materials are in contact and can be divided into three zones, viz; slip zone, partial slip zone, and stick zone. In a contact region, there is a possibility of the existence of one or more stick or slip zones.
 
It appears that friction can be very effective on stress and displacement fields and can cause increase and decrease in the stress and displacement amounts in contact region. Thus, the aim of this study is to investigate the frictional effect on stress and displacement fields because the numerical values of stress and displacement are required for selecting the contacting materials, since each contacting materials have specific friction coefficient. As a result, by selecting a material with suitable friction coefficient, the stress and displacement amounts may be controlled.
 
The method of complex variables developed by Muskhelishvili (1949), Galin (1953) and Kalandiya (1975) is mainly used to determine the stress distribution for the 2-D contact problems in the presence of friction. The linear form of the friction law is normally used in the problem formulations (Goryacheva, 1998).
 
Initial studies on the contact between two bodies took place near the end of the nineteenth century by German researcher, Heinrich Hertz (Hertz, 1882). An English researcher Carter, in the late nineteen-twenties was the first to evaluate the tangential forces between two rolling bodies (Carter, 1926). He aimed to evaluate locomotive railroad wheels in contact with the rail, considering only the longitudinal creep, and found the tangential forces in that direction. He was also the first to propose a model that considers the creep in the longitudinal direction. In addition, Johnson generalized Carter’s results to circular contacts as well as longitudinal and lateral creep (Johnson, 1958). Vermeulen and Johnson (1964) generalized this theory to elliptical contact areas. All of this work is Hertzian-based, giving contact solutions for a class of geometrical objects satisfying the half-space restriction (Vermeulen and Johnson, 1964).
 
Also, in 1949, M’Ewen evaluated the contact between two cylinders and calculated the stress field, taking into account the tangential load due to the friction on the contact area. His study was the first to include friction force on the model (M’Ewen, 1949). In the early nineteen-sixties, Haines and Ollerton (1963) came up with an approximated solution for shear stress distribution in an elliptic contact area. They also compared their results with photo elasticity experiments and found good agreement (Haines and Ollerton, 1963). Furthermore, in the late nineteen-sixties, Kalker (1967) presented his Ph.D. thesis in which he proposed a new revolutionary theory for contact between rolling bodies. He calculated all tangential forces and creep coefficients and also found the rigidity parameters involved in the analysis. His work, also based on the Hertz Theory, was used to develop several simplified algorithms (Fastism) and complete programs (Contact) to calculate the forces in the contact. His research provided an outstanding contribution to railroad research, because his theory explained and enabled the calculation of several parameters used in the wheel-rail modeling, like creep, yaw angle, spin and others (Kalker, 1967).
 
Sackfield and Hills (1983) put together the existing theories for circular and rectangular contact areas. They considered both the longitudinal and tangential loads and proposed a model to obtain the stress field for both cases, with each one  identified  using  the  axle  ratio,  k. The results obtained were similar to the ones calculated by other researchers before them (Sackfield and Hills, 1983). In addition, the theories: Linear theory, Simplified theory, Empirical theory, Strip theory and Exact three-dimensional rolling contact theory assume that the contact between the two bodies is non-conformal. Li and Kalker (1998) introduced an approach for numerical solution of the conformal contact between the wheel and the rail. Moreover, in 2000, Giannakopoulos and Pallot examined two-dimensional contact of a rigid cylinder on an elastic graded substrate. The normal, sliding and rolling types of contact along with effect of adhesion in frictionless contact are addressed and examined in this paper. The elastically graded substrate is modeled to be locally isotropic with constant Poisson ratio and elastic modulus that varies with depth, y, according to a power law, E = E0yk; 0 ≤ k < 1, y ≥ 0. Such variation covers a fairly broad class of graded materials. Exact results are derived within the context of small deformation linear elasticity. The results show that the power law elastic gradation can be very advantageous in the design of strong and wear resistance sliding surfaces (Giannakopoulos and Pallot, 2000). Furthermore, Santos et al. (2004) evaluated the stress field inside elastic rolling bodies with an ellipse area of contact. This kind of model can be applied to wheel-rail contact phenomena.
 
Also, Ke and Wang (2010) investigated the partial slip contact problem of two functionally graded material (FGM) coating/substrate systems by employing the Goodman approximation. The stress analysis showed that the FGM coating reduces the interface stress concentration that arises due to the elastic constant mismatch (Ke and Wang, 2010). In addition, in 2011, Ruderman and Bertram presented Modified Maxwell-slip model of pre-sliding friction (Ruderman and Bertram, 2011). An enhanced friction modeling for steady-state rolling tires is proposed by Rene van der Steen. In his modeling he proposed a friction coefficient model as a function of sliding velocity in a contact of cylinder with half space (Steen, 2010).
 
The tractive rolling contact problem between a rigid cylinder and a graded coating is investigated by Guler et al. (2011). The main objective of this study is to investigate the effect of the stiffness ratio, the coefficient of friction and the coating thickness on the surface contact tractions, the surface in-plane stress, the stick zone length and the creep ratio parameter that may have a bearing on the fatigue life of the component. Assuming that the shear modulus varies exponentially through the thickness of the coating, the governing integral equations associated with the rolling contact problem is constructed. Furthermore, it is supposed that the contact patch is controlled by a central stick zone accompanied by two slip zones. The conventional Goodman approximation is employed in order to decouple the governing singular integral equations. Finally, the numerical solution of the integral equations is obtained by applying the Gauss-Chebyshev integration method (Guler et al., 2011).
 
Furthermore, in the area of obtaining analytical evaluation methods for determining mechanical properties of different materials, a few works are submitted by Anvari (2014, 2016a, 2016b, 2017, 2017a, 2017b, 2017c,). Moreover, in the area of contact mechanics, a few publications are presented by Areias et al. (2014, 2015) and Timon and Huilong (2017).
 
As it appears, many efforts have been made in the field of contact mechanics to develop the equations for obtaining stress and displacement amounts inside the contact region, but the exact consideration of the relation between the friction and stress fields, and the relation between the friction and displacement fields in different contact zones like, slip and stick zones in contact of roller with a half space, is still required.
 
In the present research, the frictional effect on stress and displacement fields for contact of roller with half space is investigated. As mentioned in the study, the results shown in the figures, indicate the relation between the stress and friction coefficient and the relation between the displacement and friction coefficient inside the contact region. Since the amounts of stress and displacement are required in many of the proper designs, these results may be used in designing process of solid mechanics.


 PROBLEM FORMULATION

Friction model
 
In order to describe the friction model and associated stress in the contact region, some assumptions are required to be considered. These assumptions are defined by Goryacheva (1998) and Giannakopoulos and Pallot (2000). Definition of this method may contribute to the explanation of the equations in friction model that determine the relation between normal and tangential load, etc.
 
“For a contact of roller with half space, if a tangential force Q applied to the body satisfies the inequality Q < µP, where P is the normal force and µ is the friction coefficient, then partial slip occurs; this is characterized by the friction. If Q = µP, there is limiting friction, and the condition of full slip occurs in the contact region. This case is also called sliding friction. The case Q = 0 corresponds to pure rolling” (Goryacheva, 1998). In Figures 1 and 2 the contact between rigid roller with half space under the normal load P is shown. In Figure 1, Q is the tangential load, a is the half of the contact length, R is the cylinder radius, and v is the velocity in x direction.
 
 
“For cylinder in rolling contact under normal load with torque transmission, slipping may take place over part of the contact where the limiting value of traction is reached, while over the rest of the contact area (where the tangential traction is less than the limiting value), the contacting surfaces are locked and no slipping takes place” (Giannakopoulos and Pallot, 2000). In Figure 3, tangential and normal stress in contact of roller with half space is illustrated.
 
 
Muskhelishvili method
 
One of the attempts that is performed in order to obtain stress inside the contact region is mechanics of elastic contacts (Hills et al., 1993). In this method, the Muskhelishvili potential function is applied to obtain stress inside the contact region. Whereas Equation 1 is the Muskhelishvili potential function, Equation 2 is the Muskhelishvili potential function by taking the conjugate of both sides. Equations 3, 4, and 5 are the equations to obtain stress inside the contact region. In the following equations, z is a complex variable, f is friction coefficient, and P(x) is the function of normal load in contact region. In Figure 4, p0 is the normal load in unit of length and q is the tangential load in unit of length inside the contact region.
 
 
 
In Muskhelishvili’s closed-form expression (Hills et al., 1993), the tangential stress in unit of length inside the partial slip contact region is indicated. Muskhelishvili’s closed-form expression involves the tangential stress in contact region in unit of length of cylinder with substrate (Hills et al., 1993). In this expression, the points 1 to 12 will be used to compare the results of this study (Figure 7) and the results of the book (Hills et al., 1993).
 
 
Also, by following the solution method, there is:  
 
 
Giannakopoulos and Pallot’s method
 
Here, the parameters and variables that are used in Giannakopoulos and Pallot’s method to obtain stress and displacement inside the contact region are introduced. Furthermore, the method to solve the Giannakopoulos and Pallot’s stress equations are explained.
 
In Equation 12, Ґ is a function that defines the substrate stiffness ratio (Guler et al., 2011). The substrate is assumed almost homogeneous and its stiffness is constant, therefore Γ = 1. In Equation 13, ν is the Poisson ratio and in the following equations β, Ik, k, and Jk are the parameters reflecting the material properties of the substrate. In the homogeneous limit, k→0, and in the elastic limit, k→1 (Giannakopoulos and Pallot, 2000). As mentioned in the previous paragraph, because the substrate is almost homogeneous, k = 0.1.
 
 
In this study, the numerical values indicated in Table 1 are used for different parameters and unknown quantities. All the numerical values in order to obtain the stress are available in Table 1. Only by having the stress equations and substituting the above numerical values in the stress equations can they be obtained. It is noticeable that the aim is to obtain the frictional effect on stress fields. So by changing the µ in stress equations, the frictional effect on stress fields can be achieved. Equation 17 illustrates a stress equation that is dependent on friction coefficient.
 
 
 
From Equation 17, by using the partial integral solution method,  the numerical values mentioned in Table 1, assuming h = y = 0.0053 m, and substituting the numerical values of x between the range 0.0178 m to 0.0178 m (-a, a) may be solved.
 
Stress equation solution method
 
The assumption of Goryacheva Q = µP, means that in stress equations, µP instead of Q can be substituted. Thus, stress equation that is dependent on friction coefficient may be obtained. In this method, by changing the numerical value of µ in the range, 0 ˂ µ ˂ 1, in stress equations, the effect of friction coefficient on stress inside the contact region of roller with half space can be achieved. In order to explain the solution method, the following procedure is explained. The following equation is the stress equation in x direction.
 
 
It can be observed that Equation 19 is dependent on µ, and with changing µ, changes, which is the aim of this study; the effect of friction on stress field. By substituting µP instead of Q in stress equations and , the exact same thing occurred. It is noticeable that in this solution for stress equations, only the first two partial integrals terms are used. Using more than two partial integrals terms in the solution of the stress integral equations is not necessary. 
 
 
By substituting µP instead of Q in stress equation, and by applying the partial integral solution method, the tangential stress integral equation is solved and is shown in Equation 21.
 
 
Figure 7 is used to prove that the method is used in this study seems correct, because Figure 7 has results similar to Muskhelishvili’s closed-form expression.
 
Displacement equation solution method
 
Since all stress equations are solved and the results are observable in Figures 5 to 8, the displacement equations that are dependent on stress can be solved. In this part of study, the method that is used to solve the displacement equations is explained, and finally the results that are obtained by using the numerical values of Table 1 are shown in Figures 9 and 10. Finally, the displacement results that are obtained in this study are compared with the results that are already obtained by another analytical method. The equation for substrate tangential displacement is:
 
 
 
 
 
 
 
By substituting the amounts of  and in the Equation 27 and applying partial integral solution method to solve the normal displacement integral equation, Equation 30 is obtained.
 
 
Figure 10 illustrates the tangential displacement inside the contact region of rigid cylinder with substrate (Giannakopoulos and Pallot 2000).


 RESULTS AND DISCUSSION

Table 2 indicates the comparison of numerical values of points 1 to 12 between Muskhelishvili’s closed-form expression (Hills et al., 1993) and Figure 7 (The analytical method that is used in this study). These figures show the tangential stress in unit of length in partial slip contact region. A comparison of the results of Figures 4 and 8 indicated in Table 2 obviously revealed that the results in most of the coordinates are similar whereas in some coordinates are identical. Therefore, by considering a proper safety factor, the results of this study can be used to obtain stress inside the contact region and to design contacting materials in many mechanical processes.
 
 
Obviously, according to Table 3, the numerical results obtained from this study have lower numerical amounts in comparison with results obtained from Giannakopoulos and Pallot’s method. It can be concluded that thedifference between the results is due to the fact that in this study, only the first two terms of partial integrals solution is considered, but in Giannakopoulos and Pallot’s method, the whole integral equation is used to obtain the results.
 


 CONCLUSIONS

One of the important results achieved in this research is that, in slip region, it seems that with increasing friction coefficient, tangential stress and shear stress are increased, but normal stress in almost all of contact zone is constant. The figure of tangential stress (Figure 7) inside the contact region is symmetrical because the numerical values of tangential stress in both posterior and anterior halves of the contact region are equal. In addition, the figure of shear stress (Figure 6) and especially the normal stress (Figure 5) are asymmetrical because in posterior half of the contact region numerical values are greater than in the anterior half of the contact region. It appears that by increasing the friction coefficient, the tangential and normal displacements are increased. The figure of tangential displacement (Figure 8) inside the contact region is asymmetrical because the numerical values of tangential displacement in posterior half of the contact region are greater than anterior half of the contact region. The figure of normal displacement (Figure 9) inside the contact region is symmetrical because the numerical values of normal  displacement  in  both posterior and anterior halves of the contact region are equal.
 
Applications of the present research are broad in the field of contact mechanics; the contact of tire with road and the contact of wheel with rail, and so on. By identifying the effect of friction on stress and displacement fields inside the contact region, the design can be done by an appropriate safety factor. In circumstances that a high friction can make the stress or displacement to pass the valid numerical value of design, decreasing the friction coefficient by selecting the materials with proper numerical values of friction coefficient in order to decrease the numerical values of the stress and displacement is possible. For the future work, the investigation of friction coefficient as a function of time inside the contact region is proposed.


 CONFLICT OF INTERESTS

The authors have not declared any conflict of interests.



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