Page 246 - Fluid Mechanics and Thermodynamics of Turbomachinery
P. 246

Centrifugal Pumps, Fans and Compressors  227
                          Although the absolute Mach number at the impeller tip can be obtained almost
                          directly from eqn. (7.28) it may be instructive to find it from
                                          c 2      c 2
                                     M 2 D   D
                                          a 2  .
RT 2 / 1/2
                                            2
                                                 2
                          where       c 2 D .c C c / 1/2
                                             2   r2
                                     c r2 DPm/.  2 2 r t b 2 / D 2/.2 ð 2  ð 0.288 ð 0.011/ D 50.3 m/s
                                     c  2 D   s U 2 D 400 m/s.
                                          p
                                                       2
                                                2
                          Therefore   c 2 D  .400 C 50.3 / D 402.5 m/s.
                          Since      h 02 D h 01 C W
                                     h 2 D h 01 C W  1 2
                                                      c .
                                                     2 2
                                                                                  4
                                                        c //C p D 295 C .18.1
                          Therefore  T 2 D T 01 C .W  1 2                   8.1/10 /1005
                                                       2 2
                                        D 394.5K.
                          Hence,
                                               402.5
                                     M 2 D p             D 1.01.
                                            .402 ð 394.5/


                          The diffuser system
                            Centrifugal compressors and pumps are, in general, fitted with either a vaneless
                          or a vaned diffuser to transform the kinetic energy at impeller outlet into static
                          pressure.

                          Vaneless diffusers
                            The simplest concept of diffusion in a radial flow machine is one where the swirl
                          velocity is reduced by an increase in radius (conservation of angular momentum) and
                          the radial velocity component is controlled by the radial flow area. From continuity,
                          since Pm D  Ac r D 2 rb c r , where b is the width of passage, then
                                   r 2 b 2   2 c r2
                              c r D        .                                              (7.30)
                                     rb
                          Assuming the flow is frictionless in the diffuser, the angular momentum is constant
                          and c   D c  2 r 2 /r. Now the tangential velocity component c   is usually very much
                          larger than the radial velocity component c r ; therefore, the ratio of inlet to outlet
                          diffuser velocities c 2 /c 3 is approximately r 3 /r 2 . Clearly, to obtain useful reduc-
                          tions in velocity, vaneless diffusers must be large. This may not be a disadvantage
                          in industrial applications where weight and size may be of secondary importance
                          compared with the cost of a vaned diffuser. A factor in favour of vaneless diffusers
                          is the wide operating range obtainable, vaned diffusers being more sensitive to flow
                          variation because of incidence effects.
                            For a parallel-walled radial diffuser in incompressible flow, the continuity of mass
                          flow equation requires that rc r is constant. Assuming that rc   remains constant, then
   241   242   243   244   245   246   247   248   249   250   251