Viscous damper with rotor centering means

Claim 2

For turbine type power plant having a given thrust specific fuel consumption and having a rotor enclosed in a casing having a rotatable shaft supporting a plurality of compressor blades at one end and a plurality of turbine blades at an opposite end, at least three bearings axially spaced along said shaft for rotatably supporting said shaft and one of said bearings mounted intermediate said compressor blades and said turbine blades and the other two bearings, fluid damper means on said one of said bearings including a cavity adjacent said one bearing in which fluid is fed to support said bearing when in the rotating mode, said shaft being distortable as a function of the depth of said cavity and radially displacing said compressor blades a similar amount, the tips of said blades being sufficiently spaced to prevent touching of the inner diameter of said casing, means for improving the thrust specific fuel consumption by decreasing the distance of displacement of the tips of said blades including a spring means attached to said damper of said one bearing for preventing said one bearing from displacing the depth of said cavity and said spring being attached to said casing.

Claim 3

For turbine type power plant having a given thrust specific fuel consumption and having a rotor enclosed in a casing having a rotatable shaft supporting a plurality of compressor blades at one end and a plurality of turbine blades at an opposite end, at least two bearings axially spaced along said shaft for rotatably supporting said shaft and one of said bearings mounted intermediate said compressor blades and said turbine blades, fluid damper means on one of said bearings including a cavity adjacent said one bearing in which fluid is fed to support said bearing when in the rotating mode, said shaft being distortable as a function of the depth of said cavity and radially displacing said compressor blades a similar amount, the tips of said blades being sufficiently spaced to prevent touching of the inner diameter of said casing, means for improving the thrust specific fuel consumption by decreasing the distance of displacement of the tips of said blades including a spring means attached to said one bearing for preventing said one bearing from displacing the depth of said cavity wherein the rate of said spring is selected to minimize the deflection of said rotor relative to load manifested thereon by acceleration and gyroscopic forces when the shaft accelerates to its steady state operating speed where said spring rate is calculated in accordance with the formula ##EQU2## where: P=load Δ=deflection E=modulus of elasticity i=bending moment of inertia L=length of each rod of the spring N=number of rods.

Claim 4

For turbine type power plant having a given thrust specific fuel consumption and having a rotor enclosed in a casing having a rotatable shaft supporting a plurality of compressor blades at one end and a plurality of turbine blades at an opposite end, at least two bearings axially spaced along said shaft for rotatably supporting said shaft and one of said bearings mounted intermediate said compressor blades and said turbine blades, fluid damper means on one of said bearings including a cavity adjacent said one bearing in which fluid is fed to support said bearing when in the rotating mode, said shaft being distortable as a function of the depth of said cavity and radially displacing said compressor blades a similar amount, the tips of said blades being sufficiently spaced to prevent touching of the inner diameter of said casing, means for improving the thrust specific fuel consumption by decreasing the distance of displacement of the tips of said blades including a spring means attached to said one bearing for preventing said one bearing from displacing the depth of said cavity wherein the rate of said spring is selected to minimize the deflection of said rotor relative to load manifested thereon by acceleration and gyroscopic forces when the shaft accelerates to its steady state operating speed where said spring rate is calculated in accordance with the formula ##EQU2## where: P=load Δ=deflection E=modulus of elasticity i=bending moment of inertia L=length of each rod of the spring N=number of rods.