- •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
17. Mead losses (general considerations)
Losses of energy; or head losses fis they are commonly called; depend on the shape, size and roughness of a channel, the velocity and viscosity of a fluid; they do not depend on the absolute pressure of the fluid. Viscosity alone, though basically the primary cause of all head losses, hardly pver accounts for any substantial loss of energy. This, will be examined in detail further on.
Experiments show that in many cases head losses are approximately proportional to the square of the velocity. Very long ago this prompted the following genera) expression for head losses;
(4.17)
and for pressure losses:
The convenience of this expression is that it contains a dimen-sionless coefficient of proportionality ξ, called the loss coefficient, and the velocity head from Bernoulli's equation. The loss coefficient represents the ratio of head losses to velocity head.
Head losses are commonly divided into local losses (also form or minor losses) and friction (or major) losses.
Local losses are caused by local features, or so-called hydraulic resistances, such as change of shape or size of a channel. When a Quid flows through such local features its velocity changes and eddies may appear. Examples of local loss features are shown in Pig. 30: (a) gate, (b) orifice, (c) elbow, (d) valve. Local losses are determined from Eq. (4.17):
(4.17`)
or
which is known as Weisbacb's formula.
Here v is the mean velocity across the pipe section for which the local loss was determined.* If the diameter, and hence the velocity of flow, changes along the length of a pipe, it is more convenient to take the highest velocity (i.e., the velocity through the narrowest portion) as the basis for calculation. Every local feature is characterised by a certain loss coefficient ξ which can, in many cases, be regarded as approximately constant for a given type of feature. Local losses will be further considered in Chapter VIII.
Friction, or major, losses are energy losses which develop in straight pipes of uniform cross-section, i. e., with uniform flow, and they increase as the length of the pipe (Fig. 31). These losses are due to the internal friction in a fluid and therefore they appear not only in rough pipes but in smooth pipes as well.
Loss of head due to friction can be expressed according to the general equation of head losses (4.17), i. e.,
(4.18)
A more convenient form, however, is one in which the loss coefficient ξ is correlated with the relative length of a pipe.
Consider a portion of circular pipe equal in length to its diameter, denoting the loss coefficient in Eq. (4.18) by the symbol λ. Then for the whole pipe of length l and diameter d (see Fig. 31) the loss coefficient will be times greater, i. e.,
and instead of Eq. (4.18) we have
(4.18`)
or
(4.19)
Equation (4.18') is commonly known as Darcy's formula.
The diqaenaionless coefficient X is called the friction factor. It represents a coefficient of proportionality between the friction losses, on the one hand, and the product of relative pipe length and velocity head, on the other.
The physical meaning of A, is easily found from a consideration of the condition for uniform flow in a cylindrical pipe of length l and diameter d (see Fig. 31), namely that the sum of the two forces acting on the volume—pressure and friction—be zero. This equation has the form
where т, is the shear stress at the pipe wall.
From this, and taking into account Eq. (4.19), we readily obtain
(4.20)
i. e., the friction factor % is proportional to the ratio of the shear stress at the pipe wall and the dynamic pressure computed according to the mean velocity.
Head losses in closed conduits (pipes) in which a liquid is completely enclosed by solid boundaries (i.e., has no free surface) are due to the specific potential energy decreasing along the flow. In this case, if the specific kinetic energy does change at the given rate of discharge, this is due not to energy losses but to a change in the cross-section of the channel, as kinetic energy is a function of velocity only, which in turn depends on the rate of discharge and. cross-sectional area:
Consequently, in a pipe of uniform cross-section the velocity and specific kinetic energy of a liquid are constant, irrespective of local disturbances and head losses. Loss of head in this case is determined as the difference between the level of the liquid in two open piezometer tubes (see Figs 30 and 31).
Computation of head losses for various specific cases is one of the fundamental problems of hydraulics, and the two following chapters will be devoted to this.
* Henceforth the subscript m will be used for v only when confusion is possible between mean velocity and local velocity.