- •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
Chapter VIII local features and minor losses
28. General considerations concerning local features in pipes
It was mentioned in Sec. 17 that head losses may be of a dual nature: losses due to friction and local, or minor, losses. Friction losses in straight pipes of uniform cross-section were 'examined for laminar (Chapter VI) and turbulent (Chapter VII) flow. Now we shall examine the so-called minor losses due to local features or disturbances, i. e., to disturbances caused by changes in the size or shape of a conduit which affect the velocity and usually result in eddy formation.
In Sec. 17 there were given several examples of local features and a general formula for expressing minor losses through them (Eq. 4.17') based on experimental data, viz.,
Our task now is to learn to determine the loss coefficients for different types of local features.
The basic local features can be classified as follows:
(i) channel expansion, abrupt and gradual;
(ii) channel contraction, abrupt and gradual;
(iii) channel bend, sharp (elbows) and smooth.
More complicated local disturbances occur as combinations of some or all of the above-mentioned features. Thus, in flowing through a valve (Fig. 30c?) a liquid passes a bend, a contraction and an expansion to its initial size and eddy currents are set up.
We shall consider the basic local features in the order given in conditions of turbulent flow. It should be noted that the loss coefficient ξ in turbulent flow is determined almost exclusively by the geometry of the local features and changes very little with changes in absolute dimensions, velocity and kinematic viscosity v, i. e., with changes in the Reynolds number. Therefore, it is commonly considered to be independent of Re, which means the quadratic resistance law (rough-law flow). Laminar flow through local features will be considered at the end of this chapter.
29. Abrupt expansion
The values of the local loss coefficient are usually obtained experimentally, and experimental formulas or charts are used.
However, in turbulent flow through an abrupt expansion the loss of head can be determined with sufficient accuracy by purely analytical methods.
An abrupt expansion and the flow pattern therein is shown in Fig. 61. The flow breaks away from the edge of the narrow section and diverges not suddenly, like the pipe, but gradually, with eddies forming in the space between the stream and the pipe. It is this turbulence that causes the dissipation of energy. Experiments show that a continuous exchange of fluid particles between the main stream and the turbulence region takes place.
Consider two cross-sections of the stream: 1-1 through the plane of the expansion and 2-2, which marks the end of the region of extensive turbulence caused by the expansion. Since the stream between the two cross-sections is gradually diverging, its velocity must be decreasing and its pressure increasing. Therefore the liquid in the second piezometer stands at a level Д# higher than in the first piezometer. If there were no loss of head the level in the second piezometer would be still higher. The distance by which the second piezometer level falls short of what it might have been is the local loss due to the expansion.
Denoting the pressure, velocity and cross-sectional area at 1-1 by Px, vx and Sx, respectively, and at 2-2 by p2, v2 and S2, write Bernoulli's equation between the sections, assuming the velocity distribution across them to be uniform, i. e., ctj = a2 = 1. We Have:
Now let us apply the theorem of mechanics on the change in momentum to the cylindrical volume between sections 1-1 and 2-2. For this we must express the impulse of the external forces acting on the volume in the direction of the motion, assuming the tangential stress at the surface of the cylinder to be zero. Taking into account that the areas of the cylinder bases are the same and equal to S2 and assuming that the pressure px at section 1-1 is acting over the whole area 52, the impulse can be expressed in the form
The change in momentum corresponding to this impulse is found as the difference between the rate of flow of momenta past the two end sections. With uniform velocity distribution across the sections, this difference is equal to
Equating the two quantities,
Dividing through by S2y and taking into account that and transforming the right-hand side of the equation:
After rearranging the terms, we obtain:
Comparing this equation with Bernoulli's equation obtained before, we find that the two are completely analogous, whence we draw the conclusion that
(8.1)
i.e., the loss of head (specific energy) due to an abrupt expansion is equal to the velocity head computed for the velocity difference. This formula is commonly known as the Borda-Carnot theorem, in honour of the two French scientists, the former a hydraulicist, the latter a mathematician, who developed it.
Taking into account that, according to the continuity equation, the result obtained can also be
written down in the following form, corresponding to the general expression for local losses:
(8.1`)
Consequently, for the case of an abrupt expansion, the loss coefficient is
(8.1``)
This theorem is nicely confirmed by experiments in turbulent flow and it is used in calculations.
In the special case when the area S2 is very large as compared with Sx and, consequently, the velocity v2 can be assumed to be zero, the loss due to expansion is
i.e., the loss of velocity head and kinetic energy is complete; the loss coefficient is ξ = 1. This is the case of a pipe outlet into a large reservoir.
It should be noted that the. loss of head (energy) due to an abrupt enlargement is expended almost exclusively on. eddy formation due to separation of the stream from the wall, i. e., on sustaining a continuous rotational motion of the fluid masses and their constant exchange. That is why these losses, which vary as the square of the velocity (discharge), are called eddy losses. Another term occasionally employed is shock losses, as there takes place sudden slowing down and a shock effect as of a fast-flowing liquid suddenly striking a slowly flowing or stationary liquid.