- •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
23. Entrance conditions in laminar flow. The α coefficient
In the case of a straight pipe of uniform diameter leading from a reservoir, when the flow is laminar the velocity distribution at the entrance is practically uniform, especially if the entrance is rounded (Fig. 46). Further on viscous forces cause the velocity to change across a section: the layers in the vicinity of the wall are slowed down, but as the rate of discharge is constant for successive sections the velocity in the centre must be accelerated. More and more layers are gradually retarded until finally the parabolic velocity profile characteristic of laminar flow develops.
The section of a pipe from the entrance to the point where the parabolic velocity profile develops is called the entrance, or transition, length (denoted leni). Beyond the entrance length steady laminar flow takes place and the velocity profile is parabolic as long as the pipe is straight and of same diameter. The laminar flow theory set forth here is valid only for steady laminar flow and cannot be applied to entrance conditions.
The entrance length can be determined from the following approximate formula in terms of the pipe diameter and Reynolds number:
(6.8)
Substituting Recr = 2,300 into Eq. (6.8), we obtain the maximum entrance length, which is 66.5 diameters.
As mentioned, resistance to flow in the entrance length is greater than in subsequent sections. The reason is that the value of the derivative dvldy at the pipe wall in the entrance length is larger than in the steady-flow portions of the pipe. As a result, the shear stress, as determined by Newton's law, is greater, the more so the closer the considered section is to the pipe entrance, i.e., the smaller the coordinate x.
Loss of head in a pipe section, when l < lent is determined by Eqs (6.5) or (6.6) and (6.7), with a correction factor К greater than unity. The value of К can be found from the graph in Fig. 47, where it is given as a function of the dimensionless parameter . The greater the parameter the smaller К until, at
i. e., at x = lent, К = 1.09. Thus, the resistance of the entrance length of a pipe is 9 per cent higher than the resistance of an equal length with steady laminar flow.
For short pipes the factor K, as is apparent from the diagram, is substantially greater than unity.
When the length I of a pipe is greater than the entrance length lenV the loss of head comprises the loss in the entrance length and the loss in the steady-flow portion, i. e.,
Taking into account Eqs (6.7) and (6.8) and after the necessary transformations and computations,
If the relative length of the pipeline -y is large enough, the number 0.165 inside the parentheses can be neglected.. However, when
accurate calculations are necessary for pipelines whose length is commensurable with lent it must be taken into account.
Knowing the velocity distribution law (6.1) and the relation between mean velocity and loss of head (6.4) it is simple to determine the value of the coefficient a, which takes into account nonuniform velocity distribution when Bernoulli's equation is applied to steady laminar flow in circular pipes.
Take Eq. (4.15) and substitute into it the expressions (6.1) and (6.4) for the velocity and mean velocity, respectively. Then, taking into account that
and
dS = 2nrdr,
and after the necessary cancellations, we obtain
Substituting the variable
we obtain
(6.10)
Thus, the actual kinetic energy of a stream with laminar flow with parabolic velocity distribution is twice the kinetic energy of an identical stream with uniform velocity distribution.
It can be demonstrated in like manner that the momentum of laminar flow with parabolic velocity distribution is P times greater than the momentum of a similar flow with uniform velocity distribution, the coefficient (5 being constant:
For the transition length of a pipe with a rounded entrance the coefficient a increases from 1 to 2 (see Fig. 47).