- •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
41. Unsteady flow through pipes
The general case of unsteady flow is fairly complicated, so we shall restrict ourselves to the main special cases which are found in aeronautical engineering: unsteady flow in a pipe of uniform cross-section and in compound pipes in series.
Take a pipe of length / and diameter d arbitrarily located in space (Fig. 106) and denote by zx and z2 the respective elevation heads of the initial (1-1) and terminal (2-2) cross-sections. Let a liquid be flowing through the pipe with an acceleration
which, in the general case, may vary with time.
The velocityv and the acceleration /, evidently, are the same at all cross-sections of the pipe at a given instant.
We neglect friction losses at first and assume the velocity distribution across the sections to be uniform.
Take a differential cylindrical control volume of length dl and cross-section dS (Fig. 106) and develop its equation of motion.
Projection of the pressure force and the gravity force on the tangent to the centre line of the pipe yields
or
As
then
(remembering also that p is a function not only of I but of t as well). Integrating along the pipe for a specific moment of time, we have
or
where
The equation resembles Bernoulli's equation for relative motion. The term hin is also called the inertia head, not to be confused with ΔHn, however, as their physical meanings are quite different. The quantity hin, as is evident from Eq. ( 10.4), represents the difference between the specific energies of the liquid at sections 1-1 and 2-2 at a given time due to the acceleration (or retardation) of the flow in the pipe. The difference is positive when there is acceleration, i.e., the specific energy decreases along the stream; in the case of retardation it is negative, which means that the specific energy is increasing from the first section to the second.
By analogy with the Bernoulli equation, any energy losses (minor or friction) must be written down in the right-hand side of Eq. (10.4):
Remember that this equation is valid only for pipes of uniform cross-section. If a pipeline consists of a series of pipes of different cross-sectional areas, Sv S2, etc., then, obviously, the inertia head along the whole of the pipeline must be found as the sum of the inertia heads of each portion. The respective accelerations in this case are found from the following equations, which are obtained by differentiating the continuity equations with respect to time:
Furthermore, it follows from the energy considerations cited before that in this case the velocity heads must be considered at the initial and end sections of the pipe.
The equation of unsteady flow between sections 1-1 and n-n takes the form
This equation is used in computing the starting and transient regimes of aircraft hydraulic systems, notably fuel supply systems for liquid-propellant rocket motors.
The following exampleixvill illustrate this equation. Let the piston in Fig. 107 be moving to the left with a positive acceleration j'. Applying Eq. (10.6) between sections 0-0 and 2-7, and then between sections 2-2 and 3-3, and constructing the hydraulic gradient for the moment of time under consideration, we have
and
Thus, in the first case the inertia head, which is added to the head loss, causes a still greater pressure drop at the piston than in the case of uniform motion. A vacuum forms at section 1-1 and the liquid may even separate from the piston. In the second case, addition of the heads hf and htn causes a pressure increase at the piston.
When the acceleration / is negative, i. e., the flow is retarded, the inertia head is negative in both cases and, consequently, it compensates, to a greater or lesser extent, for the loss of head, reducing the vacuum on the one side and increasing the pressure on the other.
Example. Determine the absolute pressure at the intake of the pump of the aircraft lubricating system in the example to Chapter VI (see Fig. 51), if the aircraft dives with a negative £-load of ng= - 1 (inertia force is directed upwards).
Solution. Tho unit inertia force is (see Sec. 11)
and the inertia head
From Bernoulli's equation for relative motion,
or
The pressure at the pump intake is too low, which means that steps must be taken to improve the performance of the lubricating system at high altitudes.