In swing pad bearing, the pad is supported by curved layers of a l t m t e luminates of elastomer and metul. The hydrodynamic wedge is formed by the swing of the pad about the center of curvature of the laminate as a result of fluid fi-iction force. This paper extends the previous analysis (Dawson, (1)) by including the stiffi~esses of the laminates under the pad in the equilibrium analysis of the pad and metal shim. The deformation of the curved elastomer layers is assumed to consist of compression, bending and shearing of the curved layer. The latter two contribute to the swing of pad surface. Each of the deformation mode has been formulated and the deflections have been calculated in the form of Fourier series. An example is given using water as lubricant. Presented at the 43rd Annual Meeting in Cleveland, Ohio May 9-12, 1988 Final manuscript approved January 25, 1988 B = length of pad in direction of sliding C,, = bending sliffness of the elastomer layer C, = shearing stiffness E = Young's modulus of elastomers G = shear modulus of elastomer H = thickness of layer in laminate hl = inlet thickness of lubricant film h2 = exit film thickness, minimum thickness Fy = applied normal load d = local layer deflection (or change in thickness) in layer do = pad normal deflection p = pressure in fluid film bearing, or layers P , = pressure along the centerline 6 = 0) of pad L = (axial) width of pad r, 0, z = cylindrical coordinates for the laminates x, y = cartesian coordinate on pad surface M = moment R, = distance from pad sliding surface to curvature center (Oc) of the curved layers in laminates