16 c the enlarged portions including the portion 16 f project radially outwardly from the plane of the latter portions although the enlarged portion 16 f is shown slightly spaced from the corresponding inner surfaces of the housing 20 in fig1 in the interest of clarity the enlarged portions actually engage the latter surfaces in an interference fit to prevent the leakage of oil from the clearance c also the axial lengths of the enlarged portions including the portion 16 f are designed to minimize contact stresses between the cage 16 and the housing 20 1 a relatively low clamping force acts on the bearing housing 20 to eliminate the risk of deformation and leakage 2 no deformation of the inside of the cage 16 occurs where the tilt pads 18 contact the cage allowing a much better control of the tilt pad bearing geometry 3 there is less sensitivity to temperature effects on the housing 20 resulting in minimum deleterious effects on the interference fit between the enlarged portions including portion 16 f of the cantilevered portions 16 c and 16 d and the corresponding surfaces of the housing 20 4 the presence of the oil in the clearance c provides additional damping of the bearing assembly 10 in general thus significantly increasing the damping provided to the rotor 12 referring to fig3 the reference numeral 30 refers in general to the bearing assembly according to another embodiment of the invention the bearing assembly 30 surrounds a rotor 32 which is rotated about its axis and forms part of an assembly that includes a driving system for imparting torque to the rotor in a conventional manner an annular bearing cage 36 extends around the rotor 32 and has an internal recess formed.