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Chapter 3 to derive a novel methodological framework which may be of support to the designer. It is in fact shown how, in the general case, the relation between the design assumptions and the resulting machine features differs from the axial arrangement case. This, in turn, makes the development of design procedures specific for the radial-outflow turbine architecture necessary, in particular as the machine power output is reduced. Most of the available works on the subject of radial-outflow centrifugal turbines (ROTs) deal with the design of large power output machines and, usually, simplified procedures are borrowed from the vast literature available in the field of axial turbines, lacking specific treatments. A typical assumption is therefore that all the rows feature the same geometrical blade discharge angles (BDA) [11, 27, 28, 32]. Referring to Fig. 3.2, this implies that, for all the N stages of the machine, the Figure 3.2: Schematic of the two-dimensional flow through a turbine stage of the repeating type. All the rows feature the same geometrical angles (BDA). The peripheral velocity is assumed to N be constant along the machine, i.e., U2 = U3. The stage reaction degree is 0.5, and the velocity triangles are thus symmetrical. The sign convention for the flow angles is also reported, adapted from [22] following holds α1 =N −β2, and α2 =N −β3. Usually also the blade chords are kept equal, i.e. N bst = brot. (3.3) (3.4) Other simplifying assumptions are commonly introduced regarding the distribution of the total ex- pansion among the stages, and among stator and rotor in each stage (i.e. the stage degree of reaction R). For instance, these quantities can be kept constant among the stages, i.e., pout N pout 1/N = , pin stg pin total R=a, with(0PDF Image | New Concepts FOR Organic Rankine Cycle Power Systems
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