ML060940272

Enclosure 4, Ziada, S. & Shine, S., 1999 Strouhal Numbers of Flow-Excited Acoustic Resonance of Closed Side Branches, Journal of Fluids and Structures 13, 127-142

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Issue date:	09/02/1998
From:	Shine S, Ziada S McMaster Univ, Ontario, Canada, Univ of Nairobi, Kenya
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ENCLOSURE 4 Ziacla, S. & Shine, S., 1999 Strouhal numbers of flow-excited acoustic resonance of closed side branches. Journal of Fluids and Structures 13,127-142.

Journal of Fluids and Structures (1999) 13, 127-142 Article No.: jfls. 1998.0189 All articles available online at http://wwW.idealibrary.com.on 1DEa0L STROUHAL NUMBERS OF FLOW-EXCITED ACOUSTIC RESONANCE OF CLOSED SIDE BRANCHES S. ZIADA Department of Mechanical Engineering, McMaster University Hamilton, Ontario, Canada AND S. SHINE Department of Mechanical Engineering, University of Nairobi, Nairobi, Kenya (Received 14 February 1997 and in revised form 2 September 1998)

Flow-excited acoustic resonances of piping systems containing closed side-branches are often encountered in engineering applications. They are excited by the unstable shear layer which separates the mean flow in the main pipe from the stagnant fluid in the branch. The object of this paper is to develop a design chart that can be used to predict the critical flow velocities in the main pipe at which acoustic resonances are initiated. Model tests were carried out on three different configurations of side-branches (single, tandem, and coaxial branches). For each of these pipe configurations, the effects of the diameter ratio, the distance from an upstream elbow and the acoustic damping are investigated in some detail. The test results are implemented into a design chart to predict the flow velocity at the onset of resonance as a function of the system operational and geometric parameters.

© 1999 Academic Press

1. INTRODUCTION ACOUSTIC STANDING WAVES in closed side-branches are often excited by the flow in the main pipe. The excited modes are typically those consisting of an odd number of quarter wavelengths along the length of the branch. The pulsation amplitudes generated by this type of acoustic resonance can be several times higher than the dynamic head in the main pipe. This level is sufficiently high to cause severe noise and/or vibration problems.

Flow-excited acoustic resonances of closed side branches have been reported in the literature for a wide variety of practical applications, including natural gas, steam and water piping systems. In power plants for example, a turbine by-pass pipe forms two closed side-branches when the by-pass valve is closed; one branch upstream of the valve is connected to the fresh steam pipe, and a downstream branch connected to the cold reheat pipe. Chen & Stirchler (1977) and Gillessen & Roller (1989) reported vibration problems in such pipe arrangements. Acoustic resonances may also occur in pipe branches leading to safety valves, to boiler relief valves, or to any auxiliary unit when the isolation valve is closed, see e.g. Baldwin & Simmons (1986) and Bernstein & Bloomfield (1989). Closed side-branches can also be found in pumping and compressor stations, in which standby units are normally separated from the system by means of isolation or check valves. Chen

& Florjancic (1975) and Bruggeman (1987) reported serious pipe vibrations in pumping and compressor installations.

0889-9746/99/010127 + 16 530.00 e) 1999 Academic Press

128 S. ZIADA AND S. SHINE Acoustic resonances of side-branches are caused by a feedback excitation mechanism referred to in the literature as a "fluid-resonant mechanism" (Rockwell & Naudascher 1978; Stoneman et al. 1988; Ziada 1994). As shown in Figure 1, the feedback is provided by the acoustic particle velocity of the resonant standing wave in the side-branch. This particle velocity induces new perturbations in the unstable shear layer at the separation location. As the shear-layer perturbations are amplified and convected downstream, they interact with the acoustic field and produce acoustic energy which reinforces the resonance of the acoustic mode. Side-branchcs are particularly liable to resonance, because the particle velocity of the resonant modes has its maximum amplitude at the location of the shear layer.

This makes the excitation of the shear layer by the resonant acoustic mode as well as the interaction of the resulting shear-layer oscillations with the resonant acoustic mode very eflicient.

Most of the recent theoretical models of this excitation mechanism are based on the acoustic analogy developed by Howe (1975, 1980). He showed that the instantaneous acoustic power, A, generated by vorticity, oi, convecting within a sound field is given by

= -p O-(v X u) d (1) where p is the fluid density, v is the fluid velocity, u the particle velocity of the sound field, and 1'. is the volume containing the vorticity field. Thus, acoustic resonances will be self-sustained if the integral of the acoustic power over an acoustic cycle is positive, and this implies that a favourable timing of vorticity convection with respect to the sound cycle must be maintained.

By means of this acoustic analogy and flow visualization techniques, Bruggeman (1987),

Stoneman et al. (1988), Graf (1989), Peters (1993), Ziada (1994) and others have shown that Flow Acoustic particle velocity excites shear layer Standing acoustic wave+

• -.------d Figure 1. Feedback mechanism of flowv-excited acoustic resonances of closed side-branches (the fluid-resonant mechanism).

ACOUSTIC RESONANCE OF SIDE BRANCHES 129 resonances will be initiated when the convection velocity of the shear layer vortices reaches a favourable value such that a net acoustic energy is produced over a complete cycle. When the acoustic pulsation is small, which is the case at the onset of resonance, the convection velocity of the shear-layer oscillation is dependent on the "local" characteristics of the velocity profile at the branch mouth and consequently on the pipe geometry upstream of, and at the mouth of, the branch. The onset and the velocity range of resonance may be influenced also by the acoustic damping due to radiation, viscous and heat conduction losses in the associated piping system. The object of the present work is to investigate experimentally the effect of the above-mentioned parameters on the critical flow velocity (V0) for the onset of resonance. The test results are then used to construct a simple design chart of critical Strouhal numbers (SO) which reflects the effects of flow and geometrical parameters. The critical flow velocity in the main pipe can be estimated from the design value of SO according to the formula V. =f 1d/S.,

(2) where d is the side-branch diameter, and fl is the acoustic resonance frequency.

Figure 2 shows the three arrangements of side-branches that are tested in this study, together with schematic presentations of their lowest resonance modes and the patterns of the acoustic flux associated with these modes. Note that the distance between the tandem branches, 1, and the main pipe diameter, D, are much smaller than the wavelength of the acoustic modes.

In the single branch case, Figure 2(a), the pulsation amplitude in the branch is strongly influenced by the acoustic radiation into the main pipe, and consequently by the friction and heat conduction losses in the main pipe as well as by the radiation losses at the main pipe terminations. For example, Jungowski et al. (1989) have shown that increasing the diameter of the branch, d, with respect to that of the main pipe, D, which increases the radiation losses into the main pipe, is associated with a rapid reduction in the pulsation amplitude at resonance.

In the case of two branches, Figure 2(b, c), which are well tuned (i.e. of equal length) and in close proximity, i.e., t1<<,

the acoustic flux at the mouth of one branch is equal but opposite to that at the mouth of the other branch. In the case of the coaxial branches for example, Graf & Ziada (1992) found that only 2% of the acoustic power in the branches is radiated into the main pipe. The two branches therefore strongly couple and form a subsys-tem with negligible radiation losses into the main pipe. Thus, the pulsation amplitude in the case of two (or multiple) branches can be drastically higher than that in the case of a single branch. Ziada & BUhlmann (1992) and Peters (1993) have shown that this is particularly the case for large values of d/D. Thus, the pipe geometries of Figure 2 were selected to allow the variation of radiation losses during the tests over a wide range: from a negligible value, as in the case of the coaxial branches, to a maximum value, as in the single branch case.

Viscous and heat conduction losses were varied during the tests by changing the diameter and the length of the side-branches, as well as by altering the static pressure during the tests.

The effect of the "local" mean velocity is investigated by adding an upstream elbow to distort the mean velocity profile at the mouth of the side-branches. The addition of the elbow also increases the flow turbulence at the branch mouth. However, earlier tests carried out by Ziada & Biihlmann (1992) have shown that increasing the turbulence level in the main pipe, by means of adding an orifice plate upstream of the tandem and coaxial branches, results in a substantial reduction in the pulsation amplitude, but a negligible effect on the critical flow velocity at the onset of resonance. In the present tests therefore, the alteration of the critical velocity resulting from the addition of the elbow is attributed to changes in the velocity profile rather than in the turbulence intensity.

130 S. ZIADA AND S. SHINE Li SE n

(a)

(b)

(c)

Figure 2. Tested arrangements of side-branches showing the acoustic pressure distribution of the first acoustic mode and the associated acoustic flux: (a) single branch; (b) tandem branches; (c) coaxial branches. The arrows in the bottom figures indicate the acoustic flux of the resonant acoustic modes.

2. EXPERIMENTAL FACILITY A pressurised-air test facility was used to carry out the tests. As shown in Figure 3, the facility is equipped with a filter, a low-noise pressure regulator and an orifice plate to measure the flow rate. All pipes were made of steel and the T-joints of the branches had sharp edges. Two absorption silencers were installed at both ends of the test-section to make the main pipe less reactive and, therefore, reduce the influence of the main pipe acoustics on the acoustical response of the side-branches. It was possible to vary the static pressure (P,)

during the tests by means of a throttle valve, which was installed at the downstream end of the system.

The inner diameter of the main pipe was D = 89 mm. Three sets of side-branches with diameter ratios of dID = 0 135, 025 and 0 57 were investigated. As shown in Figure 2, single tandem and coaxial side-branches were tested for each diameter ratio. The length of the branches (L) was also varied by means of pistons which could be moved inside the branches.

However, the two pipes forming the tandem or the coaxial geometries were always of equal length.

The initial set-up included a straight piece of pipe, 25D length, upstream of the branches.

Later on, a 900-elbow with a radius of 3D was installed upstream (Figure 4) to investigate

ACOUSTIC RESONANCE OF SIDE BRANCHES 131 1

3 11 4

8 6

7 9

5 Figure 3. Schematic presentation of the test facility. The numbers denote: 1, pressurized air supply; 2, filter; 3, low-noise pressure regulator 4, absorption silencer; 5, pipe (3 1 m); 6, metering orifice; 7, upstream pipe (5 05 m); 8, side branches; 9, downstream pipe (1 7 m); 10, throttle valve; II, high pressure hose; 12, exhaust chimney.

C Average l

velocity I

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-I Y D I I

I I1. I I

I I

I I

I

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I branch I I

I I

I I

Flow i

in l

Figure 4. Schematic presentation of a nonuniform velocity profile (due to an upstream elbow) approaching two side-branches. Note that for the purposes of simplicity, a linear profile is shown.

the effect of the mean velocity profile on the onset of resonance. The side-branch(es) and the elbow were always in the same plane and the distance between them (Y) was varied. In most of the tests, the branches were positioned at the outer side of the elbow, i.e. similar to branch I in Figure 4.

132 S. ZIADA AND S. SHINE The mean velocity (V) in the main pipe was calculated from the flow rate that was measured by means of the orifice plate. The pressure fluctuations at the closed ends of the branches were measured with the aid of Kistler transducers. A dual channel spectrum analyser was used to analyse the pressure signals.

The maximum flow velocity in the main pipe was limited by the maximum capacity of the facility (2000 m 3 /hr) and the test pressure. A maximum Reynolds number of 0 5 x 106 was reached during tests, but that at the onset of resonance was less than 0&26 x 106. These values are comparable to those encountered in many practical applications.

The flow velocity at the onset of resonance is defined in this paper as the velocity at which the slope of the acoustic response curve changes abruptly.

3. EFFECT OF RADIATION AND VISCOUS LOSSES The objective of this section is to study the effect of acoustic damping on the onset of acoustic resonances of side-branches. To achieve this, the diameter ratio d/D was kept constant, whereas the radiation, viscous and heat conduction losses of the side-branches were varied. Radiation losses into the main pipe can be varied by altering the arrangement of the side-branches. As mentioned earlier, the coaxial branches have the lowest whereas the single branch has the highest radiation losses.

Acoustic damping in the side-branch due to viscous and heat conduction losses depends on the acoustic attenuation constant, a, which is given by

[e=

Elf/47rp] 1 2/dC (Nepers/m),

(3) where pS is the equivalent coefficient of viscosity which includes the effect of heat conduc-tion, C is the speed of sound, d is the branch diameter, and f is the oscillation frequency; for more details, see Kinsler & Frey (1950). The acoustic attenuation can therefore be decreased by increasing the static pressure P3 to increase the fluid density, or by reducing the length of the side-branch. It should be noted, however, that'a reduction in the side-branch length (L) increases the resonance frequency (f : C/4L) and therefore a becomes higher proportionally to 1/1./L, whereas the total attenuation loss (aL) decreases proportionally to L. Thus, the net effect of shortening the branch is a reduction in viscous and heat conduction losses.

Figure 5 shows a comparison between the acoustic responses of two tandem and two coaxial branches of similar diameter ratio (d/D = 0-57). The amplitude of the acoustic pulsation, P. was measured at the closed end of the branch and is normalized by the dynamic head in the main pipe, IpV2. The Strouhal number is defined by S =f 1d/V, (4) wheref, is the frequency of the first acoustic mode (i.e., the one-quarter wavelength mode). Tle Strouhal numnber becomes smaller as theflow velocity in the main pipe V is increased. As expected, because of the difference in radiation losses, the coaxial branches have a larger resonance amplitude and a wider resonance (or lock-in) range than those of the tandem branches.

However, the Strouhal number at the onset of resonance is virtually the same in both cases (SO - 0 55). Thus, the radiation losses seem to have a negligible effect on the onset of resonance.

The effect of viscous, losses on the acoustic response of the coaxial arrangement is depicted in Figures 6 and 7. Both figures show the effect of increasing viscous losses (aL) by an amount equivalent to 50% of its original value, first by altering the test pressure, Figure 6, and then by increasing the length of the branch, Figure 7. The pulsation amplitude and the lock-in range increase as viscous losses are reduced. When the pulsation amplitude becomes sufficiently large, it exhibits hysteresis with the flow velocity. This non-linear

ACOUSTIC RESONANCE OF SIDE BRANCHES 133 9

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o 0

I I II I

\\

I 0

j 0

UU I

i CA

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3 4 o 4-0.1 0.3 0.5 0.7 S

Figure 5. Amplitude of acoustic pulsation as a function of Strouhal number showing the effect of radiation damping. dID = 057, P, = 4 bar; o, coaxial branches, L = 1105 cm, f, = 725 Hz; *, tandem branches, L = 100 cm, f = 80 Hz.

15 10

-I ZZ 5

0 0.1 0.3 0.5 S

0.7 Figure 6. Acoustic response or coaxial branches showing the effect of static pressure. d/D = 0 57, L = 61 cm, ft = 132 Hz; e, P. = 15 bar; a, P, = 3-5 bar.

134 S. ZIADA AND S. SHINE 15 AS

'8 10 o5iJ Jl0

\\AA

'A

0.

A II A

0 1 A Q

A 0.1 0.3 0.5 0.7 S

Figure 7. Acoustic response of the coaxial branches showing the effect of the branch length (i.e., the effect of acoustic attenuation). A, L = 61 cm, ft = 132 5 Hz, P. = 3 5 bar; o, L = 110 5 cm, f1 = 72-5 Hz, P. = 4 bar; A, L= 158-5 cm,f1 = 50 Hz, P, = 4 bar.

feature has been investigated in some detail for the case of closed side-branches by Graf

& Ziada (1993) and Ziada (1994).

Despite the large differences in the pulsation amplitude and the resonance range, the resonance starts in all the cases shown Figures 6 and 7 at the same value of Strouhal number (SO ; 0 55). These results are in agreement with those published by Peters (1993) for coaxial side-branches with a diameter ratio of d/D = 1. Altering viscous losses in this pipe config-uration by a factor of 8, by varying the length of the branches from 0-1 m to 0-397 m and the test pressure from I bar to 15 bar, influenced the pulsation amplitude and the lock-in range substantially, but had a negligible effect on the Stroudhal number at the onset of resonance.

Thus, it can be concluded that the effect of viscous and radiation losses on the Strouhal number at the onset of resonance is very small and can be neglected.

4. EFFECT OF THE DIAMETER RATIO Figure 8 shows test results of single, tandem and coaxial branches for three different diameter ratios (dID = 0 135, 0-25 and 0-57). The maximum amplitude at resonance in-creases with the diameter ratio, especially for the coaxial case which produces the strongest resonance. In each case of diameter ratio, the resonances of the tandem and the coaxial branches start at similar Strouhal numbers. For the single-branch case, it is more difficult to determine the onset of resonance because the pulsation amplitude is rather small in general.

In these cases, the response curves were blown up and the criterion of abrupt change in the slope was used to determine the onset of resonance. It is clear from Figure 8 that the resonance range, and in particular the onset of resonance, shifts to lowver Strouhal numbers (i.e. to higher velocities) as the diameter ratio is decreased. This feature is delineated in

dlD=0.135 0.25 0.57 1.0 10.0 A

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0.2 5.0 -

0.0 _

0.2 r)0 C:

0 z

z

_m 0

n m

m 0.6 m

cW 0.4 0.6 0.2 0.4 fdl V fdl V 0.4 fdl V Figure 8. Comparison between the acoustic responses of single, tandem and coaxial side-branches for several values of diameter ratios: *, single; *,

tandem; and 0, coaxial branches. (a) dID = 0135; (b) dID = 0-25; (c) dID = 0 57.

136 S. ZIADA AND S. SHINE 3

00 ii I'.O L

I

• 1

-vw 0.1 0.2 0.3 0.4 0.5 0.6 0.7 fadl V Figure 9. Effect of the diameter ratio of tandem branches on the critical Strouhal number of the onset of resonance. W, d/D = 0135; *, 025; o, 075.

Figure 9 which shows typical resonance curves of tandem branches with different diameter ratios. The critical Strouhal number So is reduced, i.e., the onset of resonance is delayed, when d/D is decreased. The effect of dID on SO is seen to be quite strong and should be taken into account when evaluating the liability of a system to resonance.

The relation between S. and d/D stems from the alternation of the convection velocity of the vortices forming at the branch mouth when d/D is varied. This is because the size of the formed vortices scales with the diameter of the side-branch (Ziada 1994). Since the bound-ary-layer thickness in the main pipe is independent of the side-branch diameter, a larger size vortex will experience a higher mean velocity and will be swept faster along the branch mouth. The phase condition for the onset of oscillation, i.e., the favourable phasing between the vortex convection velocity and the acoustic oscillation, will therefore be achieved at a lower reduced velocity when the diameter of the side-branch (and consequently the vortex size) is larger.

5. EFFECT OF UPSTREAM ELBOWS Resonances are initiated when the convection velocity of the shear-layer vortices is in-creased to an appropriate value such that a net positive acoustic energy is generated over a complete cycle. Thus, when the mean velocity profile in the main pipe is not uniform, one would expect the onset of oscillation to be related to the "local" flow velocity at the mouth of the branch, see Figure 4. in order to investigate this aspect, an elbow with a radius of 3D was installed upstream of the branch. The distance Y between the elbow and the branch was varied from 1 -8D to I OD. The effect of the upstream elbow was investigated for the cases

ACOUSTIC RESONANCE OF SIDE BRANCHES 137 of single, tandem and coaxial branches. However, neither the velocity profile nor the turbulence level at the outlet of the elbow were measured.

The acoustic response of a single side-branch (d/D = 0135) excited by a uniform flow (YID = oo) is compared in Figure 10 with that excited by the (nonuniform) flow at the outlet of the elbow. The figure shows the results when the side-branch was installed first at the inner and then at the outer side of the elbow. The relative amplitude (P/I-pV2 ) and the Strouhal number are based on the average velocity calculated from the measured flow rate.

The elbow is seen to affect the lock-in range and the amplitude of pulsation.

When the branch is at the outer side of the elbow, curve I in Figure 10, the local velocity is higher than the average velocity. The resonance therefore starts at a lower flow rate, i.e., at a higher SO. Moreover, the relative amplitude becomes higher than the case of uniform flow (curve 3 in Figure 10). This increase, however, is rather superficial because the relative amplitude is based on the average velocity which is lower than the local velocity at the mouth of the branch, which excites the resonance. Conversely, when the branch is at the inner side of the elbow, curve 2 in Figure 10, the onset of resonance is delayed, i.e., it occurs at a higher flow rate, and the relative amplitude becomes (superficially) smaller. The three curves shown in Figure 10 may well become very close to each other if the local flow velocity is used to calculate the Strouhal number and the relative amplitude. This idea, however, has not been followed further, because its usefulness to practicing engineers is rather limited.

l The effect of the elbow on the critical Strouhal number is weakened when the distance 2/D between the elbow and the branch is increased. This feature is depicted in Figure 11, which shows measurements of a single branch with dID = 0 25 located at different distances from the upstream elbow. It is noteworthy that the effect of the elbow is still discernible, also when it is located at lOD upstream of the side-branch.

In the case of tandem branches also, the elbow promotes the onset of resonance and increases the relative amplitude of pulsation, Figure 12, whereas in the coaxial case, it has 1.5 1.0 33 1.0 2

2 0.0 0.2 0.3 0.4 0.5 f,dIV Figure 10. Effect of the upstream elbow on the acoustic response of a single branch; 0, branch at the outer side of the elbow; *, at the inner side; *, no elbow. dID = = 0135,f, = 490 Hz,.?/D = 185, P. = 3 bar.

138 S. ZIADA AND S. SHINE 1.0 0.

0.5 F 0.0 L 0.2I 0.4 0.5 fdI V 0.6 Figure 11. Pulsation amplitude versus Strouhal number for a single branch located at the outer side of, but at different distances (Y), from an upstream elbow; d/D = 0-25,f 1 = 326 Hz, P. = 3 bar. 0,.2/D = 1.8; *, YI/D = 6.2;

• , YI/D = 10; *,

I/D = mc.

4 c,2 I-0.2 0.4 fid/ V 0.6 Figure 12. Effect of the upstream elbow on the resonance of two tandem branches installed at its outer side; dID = 0 25; *, single branch without elbow; *, tandem branches without elbow; o, tandem branches with elbow at YID = 3 75.

ACOUSTIC RESONANCE OF SIDE BRANCHES 139 4

10 2

5 4.4 0

0 0.2 0.4 0.6 0.3 0.5 0.7 (a) fd /V (b) fedIV Figure 13. Effect of the upstream elbow on the resonance of two coaxial branches: o, without elbow; *, with elbow at SID = 3 8; (a) d/D = 0 25; (b) d/D = 0 57.

only a negligible effect, Figure 13. This difference seems to be due to the fact that the local flow velocities at the mouths of the two branches are similar, and higher than the mean velocity, in the tandem case, but different in the coaxial case. While the local velocity for one of the coaxial branches is higher than the average velocity, it is lower for the other branch, see Figure 4. The effect of this difference in local velocities seems to cancel itself out, resulting in only a slight difference from the case of uniform flow, Figure 13.

6. STROUHAL NUMBERS AT ONSET OF RESONANCE It has been shown that the main parameters that influence the Strouhal number at the onset of resonance (S0) are the diameter ratio d/D and the distance from an upstream elbow (Y/D), if there is any. Although the radiation and viscous losses strongly influence the maximum amplitude at resonance and the width of the lock-in range, they have been found to have a negligible effect on SO. The Strouhal number data are therefore plotted as a function of the distance LP/D in Figure 14, where the ratio d/D is taken as a parameter. It is seen that the value of S0 varies over a wide range (0-35 < S0 < 0-62). Thus, there is not a single value of SO which is applicable for all diameter ratios, for example. In fact, the authors observed lower values of SO in industrial applications with very small diameter ratios (d/D < 01).

The increase in S. as the diamneter ratio is increased, which is depicted in Figure 14, agrees qualitatively with the findings of Jungowski et al. (1989). Although they did not report on the critical Strouhal numbers, they observed an increase in the Strouhal number at the maximum amplitude of resonance as the diameter ratio is increased.

The critical flow velocity (V.) for the onset of resonance can be calculated from equation (1), where S. is the value obtained from Figure 14. If the maximum flow velocity of the installation V,, is lower than V., resonance will not occur. Whenever V, is found to be lower than V,,,, design modifications should be adopted to make V n,. < V.. This can be achieved by enlarging the branch diameter at the junction or by shortening the branch

140 S. ZIADA AND S. SHINE D

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135

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length to increase fl. If these modifications arc not possible, or they do not result in a sufficient increase in V., the pulsation amplitude at resonance should be estimated as outlined by Bruggeman (1987), Graf & Ziada (1992) or Peters (1993). The estimation of the pulsation amplitude indicates whether it is necessary, or not, to implement additional counter-measures such as those described by Ziada & Buhlmann (1992) and Ziada (1993).

Several remarks should be made here regarding the use of the Strouhal number chart given in Figure 14. First, when single or tandem branches are installed at the inner side of an upstream elbow, the critical Strouhal number is lower than that for I/D = oo, see curve 2 in Figure 10. In such cases, the use of a value corresponding to.t'/D = oo is recommended because it results in conservative designs. Secondly, since the effect of upstream elbowvs on the critical Strouhal number of coaxial branches is negligible, a value corresponding to Y/D = oo should be used for coaxial branches, regardless of their position with respect to upstream elbows. Thirdly, it should be noted that Figure 14 is

ACOUSTIC RESONANCE OF SIDE BRANCHES 141 developed from the test results of one elbow radius. However, since this radius is relatively small (3D), the present results would be conservative for many practical applications which involve elbows with radius larger than 3D. If the radius is smaller than 3D, the designer should consider an additional margin of safety.

The developed chart can be used also for side-branches with square or rectangular cross-sections. However, the diameter d in the Strouhal number formula must be replaced by the equivalent diameter proposed by Bruggeman (1987),

de = (4/7t)H, (5) where H is the width of the branch mouth in the flow direction.

When the corners of the branch mouth are rounded with a radius of curvature r, the critical flow velocity scales with (d + r) instead of d (Bruggeman 1987). Figure 14, however, can still be used to estimate V0 by means of the formula V. =f,(d + r)/S..

(6)

Finally, the value corresponding to d/D = 0 57 can be used for larger diameter ratios.

This suggestion is based on the fact that the Strouhal numbers reported by Peters (1993) for d/D = I are similar to the present results for d/D = 057.

7.

SUMMARY

Single, tandem and coaxial arrangements of closed side-branches have been tested to investigate the effects of the flow and design parameters on the critical Strouhal number at which acoustic resonances are initiated. The critical Strouhal number is found to be strongly influenced by the diameter ratio of the side-branch, relative to the main pipe diameter, and by the distance between the branch(es) and the nearest upstream elbow; i.e., by the shape of the velocity profile at the mouth of the branch. Although radiation and viscous losses strongly influence the maximum amplitude during resonance and the width of the lock-in range, they are found to have negligible effect on the Strouhal number at the onset of resonance. The test results are used to construct a design chart that can be used to predict the flow velocity in the main pipe at which side-branch resonances may be initiated.

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CHEN, Y. N. & STORCHLER, R. 1977 Flow-induced vibrations and noise in a pipe system with blind branches due to coupling of vortex shedding. In Internoise 77, pp. B189-B203. Ziirich.

GILLESSEN, R. & ROLLER, R. 1989 Verminderung und Besietigung von Schwingungen an Rohrleitun-gssystemen (Reduction and elimination of vibration of piping systems). In Mindering von Rohrleitinigsschwvinguigigen, VDI Berichte Vol. 748, pp. 195-222. D1isseldorf: VDI Verlag.

GRAF, H. R. 1989 Experimental and computational investigation of the flow excited resonance in a deep cavity. Doctoral Dissertation, Department of Mechanical Engineering, Worcester Poly-technic Institute, U.S.A.

142 S. ZIADA AND S. SHINE GRAF, H. R. & ZIADA, S. 1992 Flow-induced acoustic resonance in closed side branches: An experi-mental determination of the excitation source. In Proceedings of ASME International Symposilul on Flow-Induced Vibration and Noise, Vol. 7: Fundanmental Aspects of Fluid-Structure Interactions (eds M. P. Paidoussis, T. Akylas & P. B. Abraham), AMD-Vol. 51, pp. 63-80. New York: ASME.

HOWE, M. S. 1975 Contribution to the theory of aerodynamic sound, with application to excess jet noise and the theory of the flute. Journal of Fluid Mechanics 71, 625-673.

HOWE, M. S. 1980 The dissipation of sound at an edge. Journal of Sound and Vibration 70, 407-411.

JUNGOWSKI, W. M., BORTRos, K. K. & STUDZINSKI, W. 1989. Cylindrical side-branch as tone generator.

Journal of Sound and Vibration 131, 265-285.

KINSLER, L. E. & FREY, A. R. 1950 Fundamentals of Acoustics. New York: Wiley.

PETERS, M. C. A. M. 1993. Aeroacoustic sources in internal flows. Doctoral Dissertation, Technische Universitit Eindhoven, Eindhoven, The Netherlands.

ROCKWELL, D. & NAUDASCIIER, E. 1978 Review-self sustaining oscillations of flow past cavities. ASME Journal of Fluids Engineering 100, 152-165.

STONEMAN, S. A. T., HOURGAN, K., STOKES, A. N. & WELSH, M. C. 1988 Resonant sound caused by flow past two plates in tandem in a duct. Journal of Fluid Mechanics 192, 455-484.

ZIADA, S. 1993. Flow-excited resonances of piping systems containing side-branches: Excitation mechanism, counter-measures and design guidelines. International Seminar on Acoustic Pulsa-tions in Rotating Machinery, pp. 1-34, AECL CANDU, Mississauga, Ontario, Canada.

ZIADA, S. 1994 A flow visualization study of flow-acoustic coupling at the mouth of a resonant side-branch, Journal of Fluids and Structures 8, 391-416.

ZIADA, S. & BOHLNANN, E. T. 1992 Self-excited resonances of two side-branches in close proximity.

Journal of Fluids and Structures 6, 583-601.

APPENDIX: NOMENCLATURE d

side-branch diameter D

main pipe diameter frequency of the first (,.) acoustic mode L

length of side-branch LP distance between the side-branch and the upstream elbow P

amplitude of acoustic pulsation P.

static pressure S

Strouhal number (S =fd/V)

SO Strouhal number at onset of resonance (SO =f 1d/V)

V mean velocity in main pipe wavelength of the first acoustic mode

PROPRIETARY ENCLOSURE 5 Westinghouse Electric Company Calculation CN-PS-03-32, RCS Part Loop Flow Rates and Pressure Losses for PVNGS Units 1, 2, and 3 to Support SGR/PU, Revision 0 (MN-725-A00656)

ATTACHMENT 1 TO ENCLOSURE 5 WESTINGHOUSE LETTER DATED MARCH 30, 2006, "APPLICATION FOR WITHHOLDING PROPRIETARY INFORMATION FROM PUBLIC DISCLOSURE," WITH ACCOMPANYING AFFIDAVIT CAW-06-2123

W estinghouse Westinghouse Electric Company NuclearServices P. O. Box 355 Pittsburgh, Pennsylvania 15230-0355 USA U.S. Nuclear Regulatory Commission Direct tel: 412-374-4419 Document Control Desk Direct fax: 412-3744211 Washington, DC 20555-0001 e-mail: maurerbf(westinghouse.orom Our ref: CAW-06-2123 March 30,2006 APPLICATION FOR WITHHOLDING PROPRIETARY INFORMATION FROM PUBLIC DISCLOSURE

Reference:

Westinghouse Proprietary Calculation CN-PS-03-32, Rev. 0, "RCS Part-Loop Flow Rates and Pressure Losses for Palo Verde Units 1, 2 and 3 to Support Replacement Steam Generator/Uprate Program," December 9, 2003 The proprietary information for which withholding is being requested is contained in the above-referenced document, as identified in Affidavit CAW-06-2123 signed by the owner of the proprietary information, Westinghouse Electric Company LLC (Westinghouse). The affidavit, which accompanies this letter, sets forth the basis on which the information may be withheld from public disclosure by the Commission and addresses with specificity the considerations listed in paragraph (b)(4) of 10 CFR Section 2.390 of the Commission's regulations. This document is considered by Westinghouse to be proprietary in its entirety and a non-proprietary version is not available as it would be essentially all blank pages.

Accordingly, this letter authorizes the utilization of the accompanying affidavit by Arizona Public Service Company.

CDrrespondence with respect to the proprietary aspects of the application for withholding or the Westinghouse affidavit should reference this letter, CAW-06-2123, and should be addressed to B. F. Maurer, Acting Manager, Regulatory Compliance and Plant Licensing, Westinghouse Electric Company LLC, P.O. Box 355, Pittsburgh, Pennsylvania 15230-0355.

Very truly yours, B. F. Maurer, Acting Manager Regulatory Compliance and Plant Licensing Enclosure cc: B. Benney L. Feizollahi A BNFL Group Company

CAWV-06-2 123 bc:: B.F. Maurer (ECE 4-7A) IL R. Bastien, IL (Nivelles, Belgium)

C. Brinkman, IL (Westinghouse Electric Co., 12300 Twinbrook Parkway, Suite 330, Rockville, MD 208'2)

J. J. Compas (Westinghouse/Palo Verde site)

F. P. Ferraraccio (Westinghouse/Windsor)

RCPL Administrative Aide (ECE 4-7A) IL, IA (letter and affidavit only)

CAW-0)6-2 123 Page I CAW-06-2 123 Page 1 AFFIDAVIT STATE OF CONNECTICUT

)

) ss: WINDSOR, CT COUNTY OF HARTFORD

)

Before me, the undersigned authority, personally appeared Ian C. Rickard, who, being by me duly sworn according to law, deposes and says that he is authorized to execute this Affidavit on behalf of Westinghouse Electric Company LLC ("Westinghouse"), and that the averments of fact set forth in this Affidavit are true and correct to the best of his knowledge, information, and belief:

Ian C

ickard, Licensing Project Manager Regulatory Compliance and Plant Licensing Sworn t:o and subscribed before me this 30 "' day of March 2006.

My commission expires

CAW-06-2123 Pa -ye 2 CAW-(16-2 123 Pale 2 (1) 1, Ian C. Rickard, depose and say that I am the Licensing Project Manager, Regulatory Compliance and Plant Licensing, in Nuclear Services, Westinghouse Electric Company LLC

("Westinghouse"), and as such I have been specifically delegated the function of reviewing the proprietary information sought to be withheld from public disclosure in connection with nuclear power plant licensing and rule making proceedings, and am authorized to apply for its withholding on behalf of the Westinghouse Electric Company LLC.

(2)

I am making this Affidavit in conformance with the provisions of 10 CFR Section 2.390 of the Commission's regulations and in conjunction with the Westinghouse application for withholding accompanying this Affidavit.

(3)

I have personal knowledge of the criteria and procedures utilized by the Westinghouse Electric Company LLC in designating information as a trade secret, privileged or as confidential commercial or financial information.

(4)

Pursuant to the provisions of paragraph (b)(4) of 10 CFR Section 2.390 of the Commission's regulations, the following is furnished for consideration by the Commission in determining whether the information sought to be withheld from public disclosure should be withheld.

(i)

The information sought to be withheld from public disclosure is owned and has been held in confidence by Westinghouse.

(ii) The information is of a type customarily held in confidence by Westinghouse and not customarily disclosed to the public. Westinghouse has a rational basis for determining ihe types of information customarily held in confidence by it and, in that connection, utilizes a system to determine when and whether to hold certain types of information in confidence.

The application of that system and the substance of that system constitute Westinghouse policy and provide the rational basis required.

Under that system, information is held in confidence if it falls in one or more of several types, the release of which might result in the loss of an existing or potential competitive advantage, as follows:

(a)

The information reveals the distinguishing aspects of a process (or component, structure, tool, method, etc.) where prevention of its use by any of Westinghouse'"

competitors without license from Westinghouse constitutes a competitive economic advantage over other companies.

(b)

It consists of supporting data, including test-data, relative to a process (or component, structure, tool, method, etc.), the application of which data secures a competitive economic advantage, e.g., by optimization or improved marketability.

(c)

Its use by a competitor would reduce his expenditure of resources or improve his competitive position in the design, manufacture, shipment, installation, assurance of quality, or licensing a similar product.

(d)

It reveals cost or price information, production capacities, budget levels, or commercial strategies of Westinghouse, its customers or suppliers.

(e)

It reveals aspects of past, present, or future Westinghouse or customer funded development plans and programs of potential commercial value to Westinghouse.

CAW-06-2 123 Pagre 3 CAW-06-2 123 Page 3 (f)

It contains patentable ideas, for which patent protection may be desirable.

(iii) There are sound policy reasons behind the Westinghouse system for classification of proprietary information, which include the following:

(a)

The use of such information by Westinghouse gives Westinghouse a competitive advantage over its competitors. It is, therefore, withheld from disclosure to protect the Westinghouse competitive position.

(b)

It is information that is marketable in many ways. The extent to which such information is available to competitors diminishes the Westinghouse ability to sell products and services involving the use of the information.

(c)

Use of this information by our competitors would put Westinghouse at a competitive disadvantage by reducing their expenditure of resources at our expense.

(d)

Each component of proprietary information pertinent to a particular competitive advantage is potentially as valuable as the total competitive advantage. If competitors acquire components of proprietary information, any one component may be the key to the entire puzzle, thereby depriving Westinghouse of a competitive advantage.

(e)

Unrestricted disclosure of this information would jeopardize the position of prominence of Westinghouse in the world market, and thereby give a market advantage to the competition of those countries.

(f)

The Westinghouse capacity to invest corporate assets in research and development depends upon the success in obtaining and maintaining a competitive advantage.

(iv) The information is being transmitted to the Commission in confidence and, under the provisions of 10 CFR Section 2.390; it is to be received in confidence by the Commission.

(v) The information sought to be protected is not available in public sources or available information has not been previously employed in the same original manner or method to the best of our knowledge and belief.

(vi) The proprietary information sought to be withheld by this submittal is that which is appropriately marked in "Westinghouse Proprietary Calculation CN-PS-03-32, Rev. 0, "RCS Part-Loop Flow Rates and Pressure Losses for Palo Verde Units 1, 2 and 3 to Support Replacement Steam Generator/Uprate Program," dated December 9, 2003 (Proprietary), being transmitted by the Arizona Public Service Company letter and Application for Withholding Proprietary Information from Public Disclosure, to the Document Control Desk. The proprietary information as submitted for use by Westinghouse was performed for Arizona Public Service Company and calculates the reactor coolant system flow rates and pressure losses for the Palo Verde units for various combinations of reactor coolant pumps in operation. Using Westinghouse proprietary methods this document considers replacement steam generator installation at power uprate conditions.

CAW-06-2 123 Pa a 4 CAW-06-2 123 Pale 4 This information is part of that which will enable Westinghouse to:

(a) Support the licensee in determining RCS Part-loop Flow Rates and Pressure Losses with consideration of RSG and Power Uprate.

Further this information has substantial commercial value as follows:

(a) Westinghouse plans to sell the use of similar information to its customers for purposes of meeting NRC requirements for licensing documentation.

(b) Westinghouse can sell support and defense of its methodology from which the Palo Verde flow rate and pressure loss calculation is based.

(c) The information requested to be withheld reveals the distinguishing aspects of a methodology which was developed by Westinghouse Public disclosure of this proprietary information is likely to cause substantial harm to the competitive position of Westinghouse because it would enhance the ability of competitors to provide similar advanced nuclear power plant designs and to provide licensing defense services for commercial power reactors without commensurate expenses. Also, public disclosure of the information would enable others to use the information to meet NRC requirements for licensing documentation without purchasing the right to use the information.

The development of the technology described in part by the information is the result of applying the results of many years of experience in an intensive Westinghouse effort and the expenditure of a considerable sum of money.

In order for competitors of Westinghouse to duplicate this information, similar technical programs would have to be performed and a significant manpower effort, having the requisite talent and experience, would have to be expended.

Further the deponent sayeth not.