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5.6 Rotor Shaft Dynamics Figure 5-26 shows an engineering drawing of the rotor shaft connected to the compressor (right) and the motor-assist turbine (left). The rotor is supported by two gas foil journal bearings located near the compressor and turbine wheels. The thrust bearing is the disk that is located next to the compressor wheel. The rotor uses Sm/Co for the permanent magnet, and holds these magnets in place by using a pre- stressed Inconel 718 shroud. The rotor is approximately 2” in diameter, which makes it much larger than the diameter of the compressor wheel (~ 1.5”). Figure 5-26: Engineering schematic of the Sm-Co Permanent Magnet rotor with gas foil journal and thrust bearings. The thrust bearing is on the right next to the compressor wheel. The moment of inertia is 7.53 lbs/in2 in the current design. The “red” disk is the thrust bearing surface, but was increased in size to allow for greater thrust load capability and for the inclusion of magnetic thrust bearings. Rotor dynamics were investigated for the ball bearing supported shaft and for the gas-foil bearing supported shaft. Figure 5-27 shows the discretization used to estimate the rotor dynamics with the ball bearings providing support on both ends. The stiffness of the ball bearings using flex-mounts is estimated to be about 34,000 lb/in. Figure 5-28 shows a plot of the critical speed for the first three modes of vibration as a function of bearing stiffness. For the expected design, it is seen that the shaft will be operating between the second and third fundamental modes. The first and second vibration modes are often considered to be the rigid body modes, while the third mode has two zero crossings representing the “U” shaped bending mode. The first and second modes occur at approximately 17,000 and 32,000 rpm, while the third mode does not occur until 104,000 rpm. A vibration analysis was performed to assure that the vibrations would be acceptable within BNI’s ability to balance the rotor shaft. Stress strain calculations were also performed on the compressor wheel to assure that the loads imposed by the CO2 were within limits. The peak stress levels were located in the compressor blade and were approximately 7,000 psi which is well within the limits of Aluminum 6061 T-6 from which the compressor is made. 75PDF Image | Operation and Analysis of a Supercritical CO2 Brayton Cycle
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