distribution along the seal ring inner surface on inner seal portion 13h facing rotor 11 all other pressures were identified in the two paragraphs above there will be a pressure drop across each tooth 14 of the seal using the known condition of flow continuity through each tooth with constant enthalpy expansions a relatively accurate distribution of pressure can be calculated using a series of constant area throttlings on some packing rings a high mach number will exist to complicate the calculation but this will be known and accounted for by those skilled in the art the radial pressure distribution is used to select the dimensions of seal ring 13 to achieve the appropriate resultant inward force on the seal ring 13 as discussed in reference u s pat nos 5 395 124 and 4 436 311 the design goal is to establish for seal ring 13 a force condition that will cause ring 13 to overcome its weight spring and friction forces so as to shift such seal ring to its inward or small clearance position shown in fig1 and 2 for the fluid pressure conditions which can be predicted to exist when the turbine is operating at a small but significant load such as 15 to 35 as will be recognized by those familiar with elastic fluid turbines the internal pressure at most locations throughout the turbine is approximately proportional to the load as the load and mass flow is increased local pressure is increased in approximately linear.