- •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
27. Turbulent flow in noncircular pipes
The foregoing discourse referred to turbulent flow in circular pipes. The engineer, however, may encounter cases of turbulent flow in noncircular pipes as, for example, in cooling systems. Let us investigate the effect of pipe shape on friction in turbulent flow.
The total friction acting on the boundary surface of a stream of length I can be expressed as follows:
where П = perimeter of a cross-section;
t0 = shear stress at the wall, which depends mainly on the dynamic pressure, i. e., on the mean velocity and viscosity (see Sees 17 and 25).
Thus, for a given cross-sectional area and given discharge (and, consequently, given mean velocity) the frictional force is proportional to the perimeter of the cross-section. Hence, to reduce friction and friction losses, the perimeter must be reduced. A circular cross-section has the smallest perimeter for a given area, and that is why it is the best from the point of view of reducing energy (head) losses in a pipe.
In evaluating the effects of section shape on head losses, the so-called hydraulic radius, or hydraulic mean depth, Rh is introduced, defined as the ratio of the area of a cross-section to its perimeter:
(7 6)
(Sometimes the concept of hydraulic diameter Dh = 4R4 is used.) The hydraulic radius can be computed for any cross-section. Thus, for a circular cross-section
whence
(7.7)
for an oblong cross-section with sides a X b
for a square with side a
For a clearance of height a we have from the foregoing (assuming a very small in comparison with b)
Expressing the hydraulic radius in terms of geometric diameter [Eq. (7.7)] and substituting into the basic equat.on for head losses due to friction (4.18), we obtain
(7.8)
As this equation presents a more general expression than the loss law given by Eq. (4.18), it should be valid for both circular and non-circular pipes.
Experience confirms the validity of Eq. (7.8) for pipes of any shape. The friction factor к is computed from the same equations (7.1) and (7.2), but the Reynolds number is expressed in terms of Rh:
(7.9)
Example. Determine the pressure loss due to friction in the cylindrical portion of the cooling conduit of the combustion chamber of a Reintochter liquid-propellant rocket. The coolant (nitric acid) is delivered through the space between coaxial tubes. The diameter of the inner tube D = 155 mm, the clearance between the tubes 6 = 2 mm and the length of the conduit / = 500 mm. The rate of discharge of the coolant G = 10 kg/sec, specific weight yk = 1,510 kg/ra1. Assume the temperature of the acid in the section under consideration to be constant tm = S0°C (v = 0.25 cst).
Solution, (i) Velocity of flow through clearance:
(ii) Hydraulic radius of conduit:
(iii) Reynolds number:
(iv) Pressure loss due to friction:
Pressure losses in conic sections of the cooling system are much greater» but their computation requires integration.