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Sylvain Quoilin Chapter 3 : Description of the Test Bench In expander mode, the working fluid is not air anymore and is at higher pressure than the atmospheric pressure. Any leakage to the outside of the scroll machine is a loss of working fluid for the cycle and must be avoided. In order to reduce this loss, an extra 0.8 mm layer (Reinzit 200 material) is inserted under the peripheral synthetic tube. The contact effort between the fixed and orbiting scroll bodies is increased (this effort can be adjusted by means of Allen screws), and a sealant adhesive is applied between the fixed scroll body and the mobile scroll. The drawback of this operation is the increase of the friction torque between the two parts. Another modification brought to the compressor is the obstruction of its aircooling circuit (air channel along the finned external envelope of the scroll). Indeed, the cooling of the gas is advantageous for a compression, but not for an expansion. 3.2.3 Justification of the choice of the scroll expander. A first distinction must be done between two main types of expanders : The turbomachines and the displacement type machines. The first type is the most used in traditional power plants. However, turbomachines have several drawbacks when used in lowtemperature heat recovery applications : ● The performances of most rotary machines are related to their peripheral speed (or tip speed) U [m/s], rather than directly to the shaft speed. They have an optimal tip speed, usually independent from the machine size. For scroll compressor this value ranges typically from 1 to 10 m/s, while for turbomachines, this value is close to 300 m/s. The tip speed is given by U=2⋅⋅N⋅R , R being the radius of the rotary machine. 60 When used in smaller units, the turbomachines have a lower radius R, and their optimal rotational speed is therefore increased. This very high shaft speed causes high mechanical stresses (e.g due to centrifugal loading), bearing friction losses, diminution of the bearing life, necessity for higher reduction gear, etc. A good example is the typical vehicle turbocharger : it usually runs at 100 000 rpm or higher. However, the turbocharger has no mechanical coupling to the engine or other mechanical unit, and the high speed in this case is not a problem. In contrast, the tip speed of a displacement type machine is inherently lower, and the drawbacks presented above disappear. [Platell, 1993] ● The pressure ratio of a singlestage turbomachine has a low value (typically 1.5), while the displacement machine can have as high pressure ratios as desired. This latter solution is hence preferred for the singlestage expansion usually used in the low temperature Rankine cycle. [Hung, 1996] 25PDF Image | Modeling of a Low Temperature Rankine Cycle for Small Scale Cogen
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