Aula 24 - Cavitation
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Transcript of Aula 24 - Cavitation
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Cavitation
Contents: Occurence of cavitation in turbomachinery with
liquids: movie Examples of Cavitation
Cavitation effects in turbomachinery performance Net Positive Suction Head (NPSH)
Suction specific velocity
Thoma’s Coefficient
Exercises
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Cavitation
Cavitation: evaporation, followed bycondensation (almost instantaneously)
How to detect cavitation:
Change in performance curves
Visual observation of bubble formation
Noise and vibrations
Cavitation effects: Noise, vibration
Material erosion
Performance reduction (efficiency, etc.)
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Occurrence of Cavitation in pumps
In the figure below p1
is less than the atmosferic
pressure. If p1 < pvap (T) Evaporation
However minimum pressure occurs inside the pump
pmin < pvap (T) Evaporation cavitation
Pumps
Pump
Head loses in suction
pipe
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Occurrence of Cavitation in pumps
vap p p p p 1min
to avoid cavitation
Minimum
Pressure
Compression face
Suction face
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Occurrence of Cavitation in pumps
To avoid cavition:
vap p p p 1 p p p vap 1
g
V
g
p
g
p
g
V
g
p vap
22
21
211
Piping System (H s ) Pump ( NPSH )
p o
asp s Z e g
V
g
p
g
p
2
2
101
g
p Z e
g p vapasp s
0
H s > H si
Pump
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Occurrence of Cavitation in pumps
Suction Head ():
it only depends on piping system g
p
g
V
g
p H vap
s
2
211
NPSH (also critical value of ):it only depends of the pump
g
V
g
p
H NPSH si 2
2
1
Curves of H si
are given by the pump supplier:
H si = F(Q,N,D, , , geometric parameters)
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Occurrence of Cavitation in pumps
NPSH - H si
(it only depends on the
pump) g
V
g
p H si
2
2
1
Plots of H , and H si for the pumporiginal diameter (260 mm) and
after turning (“torneamento”)
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Occurrence of Cavitation in turbines
Now, head loses in the diffuser (part of the supply) areincluded in the NPSH definition
No cavitation if
H s > H si
Hydraulic Turbines
Applying Bernoulli’s equation:
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Occurrence of Cavitation
NPSH:
it only depends of the machine g V
g
p H si
2
2
1
H si = F(Q,N,D, , , geometrical parameters)
Applying dimensional analysis:
2
3 , ND
ND
Q f
H
H sii
negligible Re
influence
Critical Thoma´s
Coefficient
No cavitation if: > i
Thoma´s Coefficient = H s /H only depends on piping system
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Occurrence of Cavitation
Suction specific velocity: 43 s gH
Q N S
Critical suction specific velocity
343 ND
Q F gH
Q N S si
i
No cavitation if S < S i
We can use S i or i
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Occurrence of Cavitation
Critical suction specific velocity:
3 ND
Q
f H
H sii
Turbomachines of same geometrical family have
equal (S i)max and ( i )max
Critical Thoma´s Coefficient:
343 ND
Q F
gH
Q N S
si
i
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Occurrence of Cavitation
Reference values: Pumps: 2,5 < (S i)max = F () < 3,5 (S i)max = 3
Turbines: 3,5 < (S i)max = F () < 5,2 (S i)max = 4
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Occurrence of
Cavitation
PumpTurbine
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Problems 5 and 8Problems 5 and 8 – The pump, with the attached performance curves and a
D=265 mm rotor, delivers a flow of 260 m3/h when installed in a given piping
system (reservoirs open to the atmosphere and with 12 m head difference).It is intended to decrease the flow rate to 180 m3/h; 4 possible solutions for this
are considered:
a) Partially close discharge pipe valve;
b) Adjustment of the rotation speed;
c) Turning the rotor diameter (use given performance curves for rotor diametersless than 265mm);
d) Installing a re-circulating circuit by connecting the pump outlet to its inlet in
such a way that some pump flow recirculates and the flow in the main duct is
the desired flow rate of 180 m3/h.
Assuming fully turbulent flow at the pipe, find the pump power consumption and
the maximum height above the upstream reservoir free-surface for each of the
four possible control processes used to deliver 180m3/h to the downstream
reservoir. Assume that atmospheric pressure applies at the free-surface of the two
reservoirs and Zasp=0,5 m (for 180 m3/h), pvap=2,45 kPa and patm=101,3 kPa)
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Problems 5 and 8 – piping system characteristic
017
pump
Piping system
characteristics = 12 +
= 7.4 × 10− ℎ
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Problems 5 and 8 a) – Valve adjustment
1
pump
Power: =
= 13646
Maximum height:
≤ 9.59 = 7.79 1.8
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Problems 5 and 8 b) – Rotational speed
adjustment
2
3Operation point (2):
= 180 ℎ
= 14,4
Efficiency of point 2? = 80%
= 4.44 × 10−
Power: =
= 8820
Maximum height: ≤ 9.59 = 8.12
= 1.47
Computed from same
Thoma’s Coefficients between
points 2 and 3
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Problems 5 and 8 c) – Rotor diameter adjustment
2
Operation point (2):
= 180 ℎ
= 14,4
Efficiency of point 2? = 75%
Power: =
= 9408
Maximum height: ≤ 9.59 = 8.12
= 1.8
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Problems 5 and 8 d) – Recirculation circuit
4
recirculation
Operation point (4)?
= 280 ℎ = 14,4
= 68%
Power: = = 16142
Maximum height:
≤ 9.59 = 8.12
= 3.5