Supercharger for double axle two stage turbine of supercharged diesel engine

Abstract

The invention discloses a second-level turbine boosting system and the double-shaft second-level turbine booster in the middle and large power high boosting diesel engine applied to ship, naval vessels and vehicle and the electricity generation. The low and high pressure level are made up of a normal structure single shaft turbine booster and a single shaft radial fan turbine booster, which are connected together in series with a boosting pipe between the outlet of the high pressure turbine and the inlet of the low pressure level turbine. Compared with current device, the invention can be applied to the second turbine boosting system in high boosting diesel machine with middle and large power applied to the quality.

Description

Technical field: [0001] The invention relates to a turbocharger in the technical field of middle and high-power high-pressure diesel engines used for ships, warships, locomotives and power generation. Background technique: [0002] In recent decades, with the continuous improvement and development of diesel engine structural design, material technology, supercharging system and fuel system, the single-cylinder power (or mean effective pressure) and strong load (the ratio of mean effective pressure and piston mean speed) of diesel engines product) has also been increasing. Among them, the acquisition of high average effective pressure value is mainly achieved by continuously increasing the boost ratio of the turbocharger. Recently developed four-stroke medium and high-speed diesel engines with advanced performance indicators have an average effective pressure as high as 2.5-2.7 MPa, which has reached the application limit of single-stage turbocharging. If the mean effective...

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Problems solved by technology

Due to the highest isentropic efficiency value (η tmax ≈0.9) is much higher than the highest isentropic efficiency value (η tmax ≈0.75) should be higher, and considering that the axial-flow turbine can only achieve its highest isentropic efficiency value under the condition of a relatively large gas flow (the blades of the flow part are long enough), but in the case of small flow (the blades are very short) Due to the sharp increase of the blade end loss (secondary flow loss), the isentropic efficiency is greatly reduced, which is far lower than the highest isentropic efficiency value that the radial turbine can achieve at a small flow rate.

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