By Allan W. M. Bonnick
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Extra info for Automotive Computer Controlled Systems (Automobile Electronics Referex Engineering)
Chapter 8). At the low rotor speeds, the unbalance force remains small, and the journal locates nearly at the bearing center due to small weight of the rotor. In this case, the bearing has a small stiffness coefficient, as shown in Fig. 1; therefore, the rotor behaves as a rigid rotor. 36 Rotordynamics of Automotive Turbochargers UTW UCW compressor wheel oil film bearings φ 7 mm turbine shaft Fig. 2 An unbalanced rotor supported by oil-film bearings The vibration modes of the rotor are displayed in Fig.
It indicates that the journal of the turbochargers moves with the operating rotor speeds in the entire bearing clearance. Contrary to the turbochargers, the journal of the industrial turbomachines is initially near the bearing bottom at low rotor speeds due to their heavy rotor weight. Because the excited unbalance force is much smaller than the rotor weight (U2W < 1), the journal cannot move far away from the equilibrium position; hence, the journal orbit is smaller and more stable compared to the turbocharger rotors.
5 πT = 1 1 p3 p4 Fig. 3 Behavior of the pressure ratios πC versus πT 2 Thermodynamics of Turbochargers 23 The exhaust gas flow in the turbine can be considered as the flow in a nozzle where the inlet and outlet pressures are p3 and p4, respectively. Based on the flow equation for compressible fluids in the nozzle, the second turbocharger equation describes the mass flow rate through the turbine in a function of the pressure, temperature at the turbine inlet, and the turbine expansion ratio. 17) where µ is the flow coefficient due friction and flow contraction at the nozzle outlet; AT is the throttle cross-sectional area in the turbine wheel.
Automotive Computer Controlled Systems (Automobile Electronics Referex Engineering) by Allan W. M. Bonnick