A Method for Determining the Surface Contact Stresses Resulting From Interference Fits

Parsons, B.; Wilson, E. A.

doi:10.1115/1.3427710

Cited by 35 publications

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“…(4) In [18] the first 20 roots of (27) are given for r 0 = 0.5, 0.25, 0.125: they start from 6.393, 4.448, 3.999. For r 0 = 0 the first root is 3.8317 [24].…”

Section: U Z = (H'e+ + H'n'ze + + Hne_+ Hnze_)(do-] Yo )mentioning

confidence: 99%

“…Earlier investigations [25], [26] had used more substantial simplifications. In [27] a numericalanalytic procedure has been followed, adopting a finite element method for the sleeve and the Fourier integral method for the shaft. The same problem as in [9] is dealt with in [29] by potential methods: singularities are introduced to represent shrink fit dislocations and boundary loads, reducing to singular integral equations.…”

Section: Vi(h) = O Vi(c) = a 1 V2(c) + V2(h) =mentioning

confidence: 99%

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Analytic solutions of axisymmetric problems in elastic cylinders

Cicala

1985

Meccanica

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MECCANICA 20 (198'5), 43- , till recently subjected to numerous studies. The present paper, inspecting the conceptual outline of analytic investigations referred to, aims at facilitating the use of the abundant literature by engineers.Many deem that actual progress in numerical aids and availability of computation programs make these studies obsolete. On the contrary, it could be argued that, as these developments open to access by engineers a wider field of advanced problems, the need for analytic exploration becomes more and more impellent. Moreover, attention is called to the fact that the present diffusion of small computers makes more analytical approaches now practicable.Paper is incomplete: the important question of stress concentrations is not touched on, assuming that the analysis of these singularities is to be based on the study of the prevailing regular region of the stress field.Special attention is devoted to an investigation [3] being carried out in contact with the writer: its relevance in connection with literature is examined here.2. Generalities. The usual cylindric reference is adopted, denoting by Rr, Rz radial and axial coordinates, R being a reference length. Let V 2 be the axisymmetric Laplace operator 3 2 + r -1 a r + ~}z with d r = ~/br, a z = b/az. Material * Department of Structures, Politecnico di Torino. is assumed to be elastic isotropic, with tangential modulus G and Poisson's ratio v, both constant. The displacement field contains only radial and axial components, denoted by Ru r, Ru~. Let 2Ga r be the normal stress in radial direction: similar notation is used for circumferential o 0, axial a z and for the only tangential stress rrz. Non-dimensional variables are used without further notice.Homogeneous axisymmetric solutions are usually constructed by use of the biharmonic Love function • ([4], p. 276). From it, by differentiations, displacements and stresses are derived. Note that the expressions for the stresses can be obtained from the displacements through the elasticity relationships: moreover the stresses thus obtained comply with the equilibrium condition for radial forces. Therefore this formulation obeys the compatibility conditions and one ecluilibrium condition, for any choice of • whereas the equilibrium of axial forces requires that • be biharmonic. Therefore the denomination of stress function for • adopted by some Authors, is misleading as it suggests a false analogy with proper stress functions. These lead to an equilibrium configuration of stresses independently of their properties, which are dictated by compatibility of deformations(i). Distinction between stress and displacement functions is necessary when energy methods are adopted.A straightforward formulation is furnished by the equilibrium equations in terms of displacements. One of these may be written in the form V20 = 0 where 0 is the cubic dilatation, expressed for axisymmetric situations by the relation 0 = ~rUr -1" r'lu r 4" ~zUz.(The other equation writesConsider the solutions expressed by products o...

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“…(4) In [18] the first 20 roots of (27) are given for r 0 = 0.5, 0.25, 0.125: they start from 6.393, 4.448, 3.999. For r 0 = 0 the first root is 3.8317 [24].…”

Section: U Z = (H'e+ + H'n'ze + + Hne_+ Hnze_)(do-] Yo )mentioning

confidence: 99%

Section: Vi(h) = O Vi(c) = a 1 V2(c) + V2(h) =mentioning

confidence: 99%

Analytic solutions of axisymmetric problems in elastic cylinders

Cicala

1985

Meccanica

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“…For the finite element approach, Parson and Wilson (1970) suggested a method for determining the contact-stresses between any two elastic bodies, ignoring the effects of friction at the contact surfaces. There are few analyses for the reduction of the contact-stress concentrations between two bodies.…”

Section: Introductionmentioning

confidence: 99%

A method for producing a uniform contact stress distribution in composite bodies with interference

Oda

Sakamoto

San

1991

Structural Optimization

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Abstract. One of the most important problems in the design of press-and shrink-fitted assemblies is to avoid stress concentrations at the contact of two bodies. A method is presented whereby the contact-stresses can be made uniform by using variable interferences. In the proposed method the finite element technique is applied to determine the stresses of composite bodies, ignoring the effects of friction at the contact surfaces. A method of optimum structural design is used to obtain a uniform contact stress within the limit of the contraction force. In this method, interferences at contact nodal points are used as design variables. Some simple examples are presented and the effectiveness of the proposed approach is also demonstrated. ement methods. Some numerically controlled machines have been developed which can produce any shape of the component with great accuracy. Thus, the opportunity to consider variable interference allowances for composite bodies is available.Considering these points, the authors propose a method for determining the uniform stress distribution between contact surfaces of composite bodies with variable interferences, by using the finite element method. Some example problems are solved analytically for uniform tangential or normal stress at the contact surfaces. The results of the uniform stresses demonstrate the efficiency of the method.

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“…The stress distribution was investigated for the elastic steady state along the shrink-fitted region. Parson and Wilson [9] suggested a method for determining the contact stresses between any two elastic bodies but ignored the effects of friction at the contact surface. Tsuta and Yamaji [10] found irreversible nonlinearity caused by frictional forces at the contact surfaces and proposed a new method based on incremental theory.…”

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confidence: 99%

Numerical simulation of contact problems in vane machinery by a parametric quadratic programming method

Zhang

Liao

2006

Arch Appl Mech

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Interference fits are widely used for connecting impeller and shaft assembly that are forced together slowly by pressing. The interference fit design ensures stable balance behavior and allows for positive contact between the impeller and shaft assembly throughout the range of operating speeds. In addition to maintaining radial contact, sufficient net radial interface pressure must remain in order to transmit torque when the rotational speed is very high. Therefore, the interference fit between the impeller and the shaft assembly is one of the most important factors influencing the performance of the turbo unit in the design of turbocharger compressor. A suitable fit tolerance needs to be considered in the structural design.A locomotive-type turbocharger compressor with 24 blades under combined centrifugal and interference fit loading is used for the analysis. The finite-element (FE) parametric quadratic programming (PQP) method developed based on the parametric variational principle (PVP) is used for the analysis of the stress distribution in the three-dimensional (3D) contact problem of impeller. The advantages of the parametric programming method compared with conventional approaches are that the penalty factors can be canceled and that solutions can be obtained directly without tedious iterative procedures such as the general incremental iterative method. To save time in the computation, a multi-substructure technique is adopted for structural modeling. This not only simplifies the calculation, but also provides a convenient service for process computer-aided design (CAD) by means of FE simulation. The effects of the fit tolerance, coefficient of friction and rotational speed (centrifugal force), wall thickness of the shaft sleeve and the contact stress on the interference-fitting surfaces are studied in detail in the numerical computation. It is found that a nonuniform initial amount of interference in the structural design avoids the relative displacement generated and ensures uniformity of the contact stress. To assure quality of press-fitting, the amount of interference between the shaft sleeve and shaft should be strictly controlled to avoid the rapid increase of the contact stress. The numerical results demonstrate the high accuracy and good convergence of the algorithm presented here, which provides an effective approach that achieves more-reliable interference-fitted connections and more-precise assembly accuracy with lower manufacturing cost in the structural design.

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A Method for Determining the Surface Contact Stresses Resulting From Interference Fits

Cited by 35 publications

References 0 publications

Analytic solutions of axisymmetric problems in elastic cylinders

Analytic solutions of axisymmetric problems in elastic cylinders

A method for producing a uniform contact stress distribution in composite bodies with interference

Numerical simulation of contact problems in vane machinery by a parametric quadratic programming method

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