- •Chapter I introduction
- •1. The subject of hydraulics
- •2. Historical background
- •3. Forces acting on a fluid. Pressure
- •4. Properties of liquids
- •Chapter II hydrostatics.
- •5. Hydrostatic pressure
- •6. The basic hydrostatic equation
- •7. Pressure head. Vacuum. Pressure measurement
- •8. Fluid pressure on a plane surface
- •Fig. 12. Pressure distribution on a rectangular wall
- •9. Fluid pressure on cylindrical and spherical surfaces. Buoyancy and floatation
- •Fig. 18. Automatic relief valve.
- •Relative rest of a liquid
- •10. Basic concepts
- •11. Liquid in a vessel moving with uniform acceleration in a straight line
- •12. Liquid in a uniformly rotating vessel
- •The basic equations of hydraulics
- •13. Fundamental concepts
- •14. Rate of discharge. Equation of continuity
- •15. Bernoulli's equation for a stream tube of an ideal liquid
- •16. Bernoulli's equation for real flow
- •17. Mead losses (general considerations)
- •18. Examples of application of bernoulli's equation to engineering problems
- •Chapter V flow through pipes. Hydrodynamic similarity
- •19. Flow through pipes
- •20. Hydrodynamic similarity
- •21. Cavitati0n
- •Chapter VI laminar flow
- •22.Laminar flow in circular pipes
- •23. Entrance conditions in laminar flow. The α coefficient
- •24. Laminar flow between parallel boundaries
- •Chapter VII turbulent flow
- •25. Turbulent flow in smooth pipes
- •26. Turbulent flow in rough pipes
- •27. Turbulent flow in noncircular pipes
- •Chapter VIII local features and minor losses
- •28. General considerations concerning local features in pipes
- •29. Abrupt expansion
- •30. Gradual expansion
- •31. Pipe contraction
- •32. Pipe bends
- •33. Local disturbances in laminar flow
- •34. Local features in aircraft hydraulic systems
- •Chapter IX flow through orifices, tubes and nozzles
- •35. Sharp-edged orifice in thin wall
- •36. Suppressed contraction. Submerged jet
- •37. Flow through tubes and nozzles
- •38. Discharge with varying head (emptying of vessels)
- •39. Injectors
- •Relative motion and unsteady pipe flow
- •40. Bernoulli's equation for relative motion
- •41. Unsteady flow through pipes
- •42. Water hammer in pipes
- •Chapter XI calculation of pipelines
- •43. Plain pipeline
- •44. Siphon
- •45. Compound pipes in series and in parallel
- •46. Calculation of branching and composite pipelines
- •47. Pipeline with pump
- •Chapter XII centrifugal pumps
- •48. General concepts
- •49. The basic equation for centrifugal pumps
- •50. Characteristics of ideal pump. Degree of reaction
- •51. Impeller with finite number of vanes
- •52. Hydraulic losses in pump. Plotting rated characteristic curve
- •53. Pump efficiency
- •54. Similarity formulas
- •55. Specific speed and its relation to impeller geometry
- •56. Relation between specific speed and efficiency
- •57. Cavitation conditions for centrifugal pumps (according to s.S. Rudnev)
- •58. Calculation of volute casing
- •59. Selection of pump type. Special features of centrifugal pumps used in aeronautical and rocket engineering
55. Specific speed and its relation to impeller geometry
The similarity formulas obtained in the foregoing section can be used to develop a useful practical factor for calculating and designing centrifugal pumps which is commonly known as specific speed.
From Eq. (12.31)
Substitution into Eq. (12.32) yields
Rearranging and raising to the power of 3/4, we obtain
This expression is valid not only for two homologous pumps I and II but for аяу number of homologous pumps operating under similar conditions.
Suppose that among these homologous pumps we have a standard pump with a head delivery Hs = 1 m, and a water horsepower Ns = 1 h.p. at γ = 1,000 kg/m3.
Using the power equation (12.2) it is easy to determine the capacity of the standard pump:
Now let us relate the parameters Qs, Hs, ns of the standard pump to the corresponding parameters Q, H, n of any other homologous pump under similar operating conditions using Eq. (12.37):
Substituting the values of Qs and Hs, we can determine the rotational speed of the standard pump:
The expression
is the specific speed.
The physical meaning of the quantity n5 is apparent from the foregoing reasoning: it is the rpm of a standard pump homologous with a given pump and generating, under similar operating conditions, a head Hs = 1 m at a rate of discharge of Qs = 0.075 m3/sec. The hydraulic and volumetric efficiencies of the two pumps are, naturally, the same.
The water horsepower of the standard pump is 1 h.p., provided that γ = 1,000 kg/m3. Pump capacity is less when the liquid is lighter and more when it is heavier. Therefore for general considerations capacity should not be introduced in defining ns.
It is not difficult now to determine the impeller diameter of a standard pump. From Eq. (12.32)
whence
In using Eqs (12.38) and (12.39) the metric units of measure are metres for H, m3/sec for Q and revolutions per minute for n.
Under certain conditions the specific speed ns characterises the ability of a pump to develop head and ensure a certain delivery. The higher the specific speed the less the head (for a given Q and n) and the greater the capacity (for a given H and n).
Specific speed depends on impeller design. Pumps with low specific speed have impellers with small relative width () but ahigh value of , i. e., long vanes, which is necessary to obtain a higher head. Flow through such an impeller is in a plane perpendicular to the axis of rotation.
With ns increasing the ratio (as well as ) decreases, I. e., the vanes are shorter and the relative width of the impeller is greater. Furthermore, the flow through the impeller departs from the plane of rotation and becomes increasingly three-dimensional. In the limit, at maximum values of ns, the flow is along the axis of rotation and the impeller is of the axial-flow type.
The vane angle p2 decreases from about 35° to 15° with ns increasing from 40 to 200.
Centrifugal and other rotodynamic pumps may be classified according to the specific speed as follows:
low-speed radial-flow: ;
normal-speed radial-flow: ;
high-speed radial-flow: ;
mixed-flow: ;
axial-flow, or propeller: .
The impeller shapes corresponding to these five types are presented schematically in Fig. 146.
The first three belong to the true centrifugal pump, the mixed-and axial-flow designs actually representing other pump types. Obviously, no sharp boundaries can be drawn between the different types of pumps, and the centrifugal impeller turns gradually, through a mixed-flow impeller, into a true propeller as ns increases.