- •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 II hydrostatics.
5. Hydrostatic pressure
It was mentioned before that the only stress possible in a fluid at rest is that of compression, or hydrostatic pressure. The following two properties of hydrostatic pressure in fluids are important.
1. The hydrostatic pressure at the boundary of any fluid volume is always directed inward and normal to that boundary.
This property arises from the fact that in a fluid at rest no tensile or shear stresses are possible. Hydrostatic pressure can act only normal to a boundary, as otherwise it would necessarily have a tensile
or shearing component.
By "boundary" is meant the real or imaginary surfaces of any elementary fluid body taken within a given volume.
2. The hydrostatic pressure at any point in a fluid is the same in all directions, i. e., pressure in a fluid does not depend on the inclination of the surface on which it is acting at a given point.
To prove this statement, imagine inside a fluid at rest an elementary body having the shape of a right-angled tetrahedron with three edges dx, dy and dz parallel to the respective axes of a coordinate system (Fig. 5).
Let there be acting near this elementary volume a unit body force whose components are X, Y and Z, let px, pu and pg be the respective hydrostatic pressures acting on the faces normal to the x, y and z axes, and let pn be the hydrostatic pressure on the inclined face of area dS. All the pressures are, of course, normal to the respective areas.
Now let us develop the equilibrium equation for the elementary volume parallel to the x axis. The sum of the projections of the pressure forces on axis ox is
The mass of a tetrahedron is equal to its volume times its density, i. e., у dxdydzq; hence the body force acting on the tetrahedron parallel to the x axis is
,
The equilibrium equation for the tetrahedron takes the form
Dividing through by [which is the projection of the area of the inclined face dS on plane yOz and is therefore equal to], we have
.
When the tetrahedron is made to shrink infinitely, the last member of the equation, which contains the term dx, will tend to zero, the pressures px and pn remaining finite.
Hence, in the limit
px — pn = 0,
or
px = pn
Developing similar equations for equilibrium parallel to the у and x axes, we obtain
py = pn and pz = pn
or
px = py = pz = pn . (2.1)
As the dimensions dx, dy and dz of the tetrahedron were chosen arbitrarily, the inclination of face dS is also arbitrary, and, consequently, when the tetrahedron shrinks to a point the pressure at that point is the same in all directions.
This can also be proved very easily by means of the formulas of strength of materials for compression stresses acting along two and three mutually perpendicular directions.* For this we only have to assume the shearing stress in these formulas equal to zero, and we obtain
These two properties of hydrostatic pressure, which were proved for a fluid at rest, also hold good for ideal fluids in motion. Fn a real moving fluid, however, shearing stresses are developed which were not taken into account in our reasoning. That is why, strictly speaking, hydrostatic pressure does not display these properties in a real fluid.