By Institution of Mechanical Engineers

ISBN-10: 085709209X

ISBN-13: 9780857092090

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Additional resources for 10th International Conference on Turbochargers and Turbocharging: 15-16 May 2012, Savoy Place, London

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11). ηT SeffT Eta-Turbocharging Seff-High Pressure turbine Seff-Low Pressure turbine 0 1 2 3 π C,LP/π C,HP 4 Fig. 11: Pressure repartition By reducing engine load the pressure distribution is changed. The above mentioned diagram is valid for full load operation but the choice of the pressure distribution at full load also has an influence on its evolution over the engine load profile. It has been observed, that the pressure ratio of the HP turbocharger remains fairly constant in the upper load range.

The valve to the high pressure manifold is opened before that to the low pressure manifold to allow the blowdown pulse to be recovered by the Turbo-Discharging turbine. The valve to the low pressure manifold is then opened to allow the displacement stroke of the piston to occur at a lower cylinder pressure. Such valving arrangements have been successfully demonstrated to reduce engine pumping work when applied to a turbocharging system (5). The full exhaust flow then passes through the turbocharging turbine.

3 for evaluating the induction process. 48 250 300 Tac [K] 350 400 Fig. 2 The exhaust process 12 According to different engine pex p cycle simulations for a highly 11 [bar] turbocharged engine with Miller 10 timing and an indicated mean 9 effective pressure pmi = 30 bar, 8 values of pex = 11 bar and Tex = 7 1000 K can be considered 6 representative. For the sake of a 1 5 simplicity no scavenging is pTI considered. The task is now to 4 establish the maximum power 3 4 2 that can be gained from the b 3 2 expansion of this exhaust gas.

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10th International Conference on Turbochargers and Turbocharging: 15-16 May 2012, Savoy Place, London by Institution of Mechanical Engineers

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