- •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
42. Water hammer in pipes
Water hammer is the name given to a sudden change of pressure that develops inside pipes when a valve is closed rapidly.
The theoretical and experimental investigation of water-hammer phenomena were first carried out by N. E. Joukowski. The explanations set forth here are based on the basic conclusions of his fundamental work, Water Hammer^ published in 1899.
Water hammer is a very rapid process in which elastic deformations of both liquid and pipe take place.
Consider a liquid flowing through a pipe with a velocity uOi and let a valve be closed instantaneously (Fig. 108a). The velocity of the liquid particles next to the valve becomes zero and their kinetic energy turns into work done in deforming the pipe walls and the fluid. As a result, the pipe walls suffer an expansion and the fluid a compression corresponding to the pressure increase ApWh-* Other particles collide with the halted particles and also lose their velocity. The result is that the section n-n travels to the right with a velocity a; the transient region in which the pressure changes by kpwh is called the shock, or pressure, wave.
When the shock wave reaches the reservoir, the liquid in the pipe is at rest and in compression and the pipe walls are in tension; the pressure increase Apwh extends throughout the whole pipe (Fig. 1086).
This state, however, is unstable. Due to the pressure difference kpwhi the liquid particles start to flow towards the reservoir, the motion beginning at the cross-section adjoining the reservoir. The section n-n travels back to the valve with the velocity a, leaving in its wake the unloaded pressure p0 (Fig. 108 c).
The liquid and the walls are assumed to be absolutely elastic, therefore they revert to their initial state corresponding to the pressure p0. The work done in the deformation all turns back into kinetic energy and the liquid obtains its initial velocity v0, but in the opposite direction.
Now the liquid tends to move away from the valve (Fig. 108c?) and a negative shock wave — Apwh develops which travels from the valve to the reservoir with the velocity a, leaving in its wake the pipe walls contracted and the liquid expanded, due to the reduced pressure —kpwh (Fig. 108e). The kinetic energy of the liquid once again turns into the work done in deformation, but with the opposite sign.
*Iα this case liquid compressibility cannot be neglected, as is customary, in solving hydraulics problems, because the low compressibility of liquids isthe very cause for the development of the high water-hammer pressure &pwfl.
The state of the pipe when the negative shock wave reaches the reservoir is shown in Fig. 108/. As in Fig. 1086, the state is unstable, and Fig. 108g shows the levelling out of the pressure in the pipe and in the reservoir and the accompanying development of the velocity u0.
It is evident that as soon as the shock wave —Apwh is reflected from the reservoir and reaches the valve the same conditions thai were produced by the closure of the valve reappear and the cycle is repeated.
Joukowski in his experiments registered 12 complete cycles, with Apwh gradually degrading due to friction and dissipation of energy in the reservoir.
The history of a water hammer is illustrated diagrammatically in Fig. 109.
The upper diagram shows the change in the pressure Apwh that would be recorded by an indicator installed at the valve at A (the closure is assumed to be instantaneous).
The shock wave reaches B, in the middle of the pipe, after a time interval , and the pressure remains during the timeit takesthe shock wave to run from B to the reservoir and back; the pressure at B then reverts to p0 (i. e., Apwh = 0) and remains such till the negative shock wave comes from the valve after a time interval .
The value of the water-hammer pressure Apwh is found from a force equation in which the kinetic energy of the liquid turns into the work done in the deformation of the pipe walls and the liquid. Tho kinetic energy of a liquid in a pipe of radius R is
The work done in the deformation constitutes half the product of the force by the extension. Expressing the work done in expanding the pipe walls as the work done by the pressure forces in a displacement Ai? (Fig. 110), we obtain
From Hooke's law,
where o = normal stress in the pipe wall, which is related to the pressure Apwh and the wall thickness 6 by the well-known equation
Taking the expression for ΔR from Eq. (10.7) and the expression for a from (10.8) we obtain the following expression for the work done in the deformation of the pipe walls:
The work done in compressing a volume W of liquid can be represented as the work done by the pressure forces in the displacement Δl (Fig. 110):
By analogy with Hooke's law for linear extension, the relative reduction of the liquid volume is connected with the pressureby the relationship
where K volume modulus of the liquid (see Sec. 4.)
If W is the volume of liquid in a pipe, the expression for the work done in the compression of the liquid is
The equation of the acting forces takes the form
Solving with respect to Apwh gives Joukowski's formula:
The quantity
has the dimension of velocity. Its physical meaning can be interpreted by assuming the pipe to have absolutely rigid walls, i.e.,. Then the last expression turns into, which is the velocity with which sound propagates ("sonic"or "acoustic" velocity) in a homogeneous elastic medium of density ρ and volume modulus K.
Acoustic velocity in water is 1,435 m/sec, in gasoline, 1,116 m/sec, and in oil, 1,400 m/sec.
If, as is the case here,E =£ go, the quantity
represents acoustic velocity in a liquid filling a pipe with elastic walls.
It follows from the very nature of acoustic vibrations that the velocity of sound is the speed with which rarefactions or compressions of infinitely small amplitude propagate through a medium. When the density change is relatively small Hooke's law is valid, and it was used in developing Eq. (10.9). We come, thus, to the conclusion that the quantity a is the velocity of the shock wave examined in Fig. 108. Consequently, Joukowski's formula can be written in the form
This formula is valid for "instantaneous" closure of a valve, i. q., when the time of closure
At Tc > To water hammer is "incomplete" as the shock wave makes its round trip from the reservoir before the valve is completely closed. The pressure rise Ap'Wh is smaller, and it is commonly assumed that
Equation (10.10) and the expression for To yield instead of the foregoing
Thus, unlike Δpwh, the quantity Δpwh depends on the length of the pipe and does not depend on the velocity a.
It is evident from all that has been said that water-hammer effects can be reduced by increasing the closure time Tc. If this is not feasible for some reason or other, air chambers or surge tanks are installed in pipelines. They absorb the water-hammer shock, which is equivalent to increasing the time of valve closure.
Example. A receiver in an aircraft hydraulic system is cut out by means of an electromagnetic valve. The time of complete closure is rc = 0.02 sec.
Determine the pressure increase at the valve at the moment of cut-out under the following conditions (Fig. Ill):
Length of pipe from valve to accumulator which absorbs shock wave / =» = 4 m; pipe diameter d = 12 mm; thickness of pipe wall 6 = 1 mm; material, steel (E = 2.2 X 10e kg/cm2); volume modulus of AMIMO fluid # = 13,300 kg/cm2, density q = 90 kg sec2/m4; pipe flow velocity v% = 4.5 m/sec.
Solution, Determine the speed of propagation of a shock wave through pipe filled with AMIMO fluid:
or
Total water-hammer pressure if the closure were instantaneous would be
In this case, however, water hammer is less pronounced because the return trip of the shock wave takes
i. e., less than the time of the complete closure Tc. The pressure increase at the valve is only