Online Detection of Cavitation Phenomenon in a Centrifugal Pump using Audible Sound 1 Shrikumar Gupta, 2Vimal Kumar Chouksey & 3Manish Srivastava 1 C.M.J. University-India, 2CSVTU Bhilai-India, 3 Chonbuk National University-South Korea. E-mail : shrisscet@gmail.com, vimalkumarchouksey@gmail.com, 84.srivastava@gmail.com occurs due to low vapour pressure and bubble formation. These bubbles collapse together and also impact on the impeller blades which generate noise, vibration, also decrease the pump performance and damage the pump if cavitation is present in the pump for long time. Abstract - Experimental study has been performed on a centrifugal pump to analyze the level of sound due to cavitation and the change in the level of sound with the change in discharge level. The experimental study has been carried out in the centrifugal pumps of different capacities .When cavitation occurs then due to low vapour pressure the bubbles collapse. These bubbles impact on the blades, as a result, the level of sound changes. This level of sound has been used to detect the cavitation in the centrifugal pump. With the change in NPSH (Net positive suction head) the sound level varies and at a critical point, when cavitation gets fully developed, the level of sound goes at peak. The noise generated by a centrifugal pump depends on its geometry (size and form) and on the operating conditions (speed and load). Another factor that increases noise is pump instability. Pump instability may be caused by stall, surge and cavitation in the pump. Stall and surge can occur when the pump operates below the design flow rate or BEP (Q<Qdes), whereas cavitation can occur within the entire operating regime. Cavitation can occur without stall and surge, and vice versa [1, 2]. Cavitation occurs more easily at higher flow rates (Q >Qdes), due to the increased velocity of flow and the pressure drop; therefore this type of instability can be avoided by pushing the operating point toward lower flow rates. But at lower flow rates, the stall and surge can cause pump operation instability, especially with pumps with unstable characteristics, when the surge point appears at the flow rate, which is higher than zero (Q > 0). The cavitation as a type of noise generation mechanism is the scope of this paper. Cavitation occurs when the absolute static pressure at some point within a pump falls below the saturated vapour pressure of the fluid. At the prevailing temperature conditions, the fluid starts to flash and vaporization occurs. Vaporisation of the flowing fluid is connected with the onset of bubbles. The bubbles are caught up by the flowing liquid and collapse within the impeller when they reach a region of higher pressure, where they condense. This process is accompanied by a violent collapse or implosion of the The level of sound has been measured for a centrifugal pump at different flow rates. Different parameters related to sound has also been measured. This shows the group of results with specific patterns. From these results it has been obtained that when the discharge level decreases, the NPSH critical value (where cavitation gets fully developed) also decreases. When this experiment is repeated, each time similar results are obtained. The different calculations based on sound have been performed to analyze the result. These results help to develop an online detection technique for centrifugal pump using audible sound. Keywords-Pump, Cavitation, Technique, Audible Sound. I. Cavitation Detection INTRODUCTION Cavitation is the formation of vapour bubbles of a flowing liquid in a region where the pressure of the liquid falls below its vapour pressure. At this vapour pressure, growth of bubbles takes place which collapse together causes vibration, noise generation and finally known as cavitation. At the suction side cavitation ISSN (PRINT) : 2320 – 8945, Volume -1, Issue -5, 2013 103 ITSI Transactions on Electrical and Electronics Engineering (ITSI-TEEE) bubbles and a tremendous increase in pressure, which has the character of water hammer, blows [3]. This process of cavitation and bombardment of the pump surface by the bursting bubbles causes three different, undesirable, effects:(a) Deterioration of the hydraulic performance of the pump (total delivery head, capacity and efficiency), (b) possible pitting and material erosion of the impeller blades and shrouds(and volute casing) in the vicinity of the collapsing bubbles and (c) vibration of the pump walls excited by the pressure and flow pulsations, and resultant noise. Therefore, cavitation in the pump, as an unacceptable phenomenon, should by all means be avoided. a distance of 0.5m .software based on Real time analyzer, was used for the spectral analysis. Since the NPSH values vary with flow rates, the procedure was repeated for different flow rates. Microphone is required so that sound can be sensed and analyzed with the help of software and computer. The microphone should be sensible enough that minimum level sound pressure can also be measured. The sound pressure due to noise is sensed by the sensible microphone .When the microphone is placed at some distance from the setup; connect this microphone through the computer or laptop. Then, due to the change in pressure level of air, the variation in the level of sound pressure takes place which is used as a parameter to analyze through the software. To do this, we have to know the moment of cavitation inception within the pump and when it gets fully developed, especially for pumps working in industrial environments. Cavitation within the water pumps (and water turbines) has been the subject of much research, numerous studies and almost all books describing centrifugal pumps [3–9]. According to the available literature, there are two different ways to detect the onset of cavitation in a liquid: numerical or analytical modeling and engineering methods. The microphone is placed at a distance of 0.5 meter from the experimental setup and the experiment is performed. The level of sound is measured by connecting the microphone with the computer. The variation in the level of sound is measured by the software. The software is based on the frequency scale from 20Hz to 20 kHz in the X- axis and decibel sound pressure level (SPL) in the Y- axis. During observation, the range of decibel scale varies up to 100 dB. Numerical and analytical modeling is often used to predict the onset of cavitation of a single bubble [4, 7– 10] and rarely within a pump. There are some wellknown models, which can be used in describing the phenomena and behaviour of cavitation cores [4, 7–9, 11, 12]. However, there is no exact algorithm to calculate the noise due to cavitation at the different operating conditions of a centrifugal pump. It is well known that the noise due to cavitation increases approximately linearly with the flow rate, the number of bubbles, the maximum equivalent volume of the cavitation bubbles and their concentration per unit volume [3], but due to the chaotic rise of the bubbles in number and size (volume), however, there is no possibility of predicting an exact value of the emitted noise. The software is a real time analyzer, so graph through the software can be directly plotted. For using the software, computer (in which software is running) is connected with the microphone and the exact value of the noise level is obtained at real time. The experiment set up diagram has been shown in figure 1. Pump, in which experiment has been performed, is connected with the suction pipe and discharge pipe. Manometer and Control valve are connected towards suction side. Pressure guage, Control valve, and Flow meter are connected towards discharge side. Cavitation causes, Reduction in pump capacity, Reduction in the head of the pump, formation of bubbles in a low pressure area of the pump volute, a noise that can be heard when the pump is running, and Damage which can be seen on the pump impeller and volute. II. EXPERIMENTAL SETUP A 550 kW pumping set is used for the experiment. The performance and the cavitation characteristics, as well as the noise characteristics were measured on a special test stand in a closed loop, according to the valid ISO 3555 standard (quality level B) [18].To detect the onset of the cavitation of the pump, NPSH available is measured at a constant speed 2900 rpm and constant flow rate. At the same time, the spectra and total emitted level of noise were measured by a microphone placed at Figure -1 Experiment Set Up ISSN (PRINT) : 2320 – 8945, Volume -1, Issue -5, 2013 104 ITSI Transactions on Electrical and Electronics Engineering (ITSI-TEEE) According to the need of this experiment, the available NPSH is varied and checked for the incipient cavitation point of cavitation and for the time at which cavitation gets fully developed. because of flow separation. The variation in the level of sound has been shown in the Fig 3. III. EXPERIMENTAL RESULTS AND OBSERVATIONS Table -1 Specification of Pump Flow Rates Head n Power 0.150 m3 /s 80 meter 2535 min-1 550kw Discrete Frequency Method According to this method, the noise spectra before the cavitation incipient and after cavitation gets fully developed are observed. By using the software and microphone, the sound pressure level has been observed corresponding to NPSH. The lower graph (Fig-2) indicates the noise level before cavitation inception and the upper graph (Fig-2) indicates the noise level when cavitation gets fully developed. The curve has been plotted between noise level dB (Sound pressure level SPL) in the Y- axis and frequency (Hz) in X-axis. Figure-3 Difference in the noise level at the discrete frequency 175 Hz with respect to NPSH for pump Again the same experiment has been done for different flow rates then the following results for same discrete frequency at 175 Hz have been obtained. This clearly shows the similar pattern result for different flow rates. It has also been observed, as the NPSH critical value and sound pressure level decreases, flow rates also get decreased. The maximum difference of sound pressure level between before the cavitation incipient and after cavitation gets fully developed is at the discrete frequency 175 Hz of 18 dB. This initial result clearly shows that the maximum sound difference is at 175 Hz. Again the observation is taken for 175 Hz with respect to NPSH. Observations have been taken for different flow rates 0.120 m3/s to 0.075m3/s. The observation clearly indicates that for the change in discharge rates 0.120m3/s to 0.075m3/s at NPSH critical point, when cavitation gets fully developed, Noise level (Sound pressure level) changes from 86 [dB] to 72 [dB] . At NPSH critical point the level of sound is maximum. At 175 Hz, before cavitation incipient the sound level for 175 Hz frequency was 68[dB] and at fully developed cavitation (NPSH critical) the sound level is 86 [dB] for the discharge rates of 0.120m3/s. NPSH critical point decreases with the decrease in discharge rates. In the fig.-4 the noise level variation for each flow rates has been shown. For each flow rate, the sound pressure variation has been observed which can be used as a detection parameter for different pumps. Figure-2 Noise spectra before cavitation inception and after it was fully developed for PUMP In this Fig-3, noise level (sound pressure level) corresponding to NPSH has been observed. At 5.2 m of NPSH the noise level obtained is 68 dB before cavitation and at 2.8 m of NPSH the noise level obtained is 86 dB after fully developed cavitation. After this NPSH value the sound level decreases, this decrease is Figure- 4 Change in NPSH and level of sound with different flow rates for pump ISSN (PRINT) : 2320 – 8945, Volume -1, Issue -5, 2013 105 ITSI Transactions on Electrical and Electronics Engineering (ITSI-TEEE) The Fig.-4 clearly shows the change in level of sound and NPSH critical value for different flow rates. The similar pattern curve has been obtained for each flow rate .This figure clearly indicates that the sound pressure level at fully developed cavitation decreases as the flow rates decreases. V. REFERENCES The sound pressure level at discrete frequency tone has been used as a detection parameter and this technique is fully automated technique to determine cavitation in the pump. [1] L.Seungbae and Kh.Jung, ―Cavitation mode analysis of pump inducer, KSME International Journal,‖ Vol. 16No. 11, pp. 1497—1510, 2002. [2] M.Cudina, ―Noise as an indicator of cavitation and instability in centrifugal pump,‖ International Journal of Mechanical Engineering 45, pp.134– 146, 1999. [3] L.Nelik, ―Centrifugal and Rotary Pumps: Fundamentals with Applications,‖ LLC, FL: CRC Press, Journal of Mechanical Engineering, 1999. [4] E.Grist, , PA Taylor & Francis ―Cavitation and the Centrifugal Pump,‖Journal of Mechanical Engineering, 1999. [5] T.Uchiyama, ―Numerical simulation of Cavitation flow using the upstream finite element method,‖ Journal of Applied Mathematical Modeling 22, pp.235–250, 1998. [6] D.Japikse, D.W.Marscher and R.Furst , ―Design and Performance,‖ Journal of Mechanical Engineering Centrifugal Pump Vermont, U.S.A., Concepts ETI, Inc B, 1997. [7] M. Fanelli, ―Some Present Trends in Hydraulic Machinery Research, Hydraulic Machinery and Cavitation,‖ London: Kluwer Academic Publishers, Journal of Mechanical Engineering , 1996. [8] N. Bidin, R. A. Hassan and M. M. Sanagi, ―The behaviour of cavitation bubble on low impedance material,‖ Journal of Mechanical engineering Proceedings of the Second International Conference on Pumps and Fans, Beijing, 1995. [9] L.Mongeau, ―Sound generation by rotating stall in centrifugal turbo machines,‖ Journal of Mechanical Engineering, Journal of Sound and Vibration 163, pp.1–30, 1993. [10] D.G.Newland, ―Spectral and Wavelet Analysis,‖ Harlow: Addison- Wesley Longman Ltd., Journal of Random Vibrations, 1993. [11] F.R.Young, ―Cavitation‖ London: McGraw- Hill Company, 1989. [12] R.Palgrave and Cooper.P, TX. ―Visual studies of cavitation in pumping machinery,‖ Proceedings of the Third International Pump Symposium, Turbo machinery Laboratory, Texas A&M University, 1986. Table-2 Method Analysis Method used Discrete frequency lies between 100 to 200 Hz Difference in noise level [dB] 10-25[dB] PUMP 18[dB] IV. CONCLUSION AND FUTRE SCOPE The decreases in noise levels of the discrete frequency tone at 100-200 Hz before the incipient of cavitation and after cavitation fully developed is between 10 and 25 dB .This is enough to use the signal of the noise, to detect the onset of the cavitation process and to prevent further development of the cavitation process even in an industrial environment, where a background noise is present. The cavitation phenomenon causes the onset of bubble formation and their implosion with bombardment of the pumps inner surfaces with consequences of pressure fluctuation in liquid, vibrations in structure and noise in the surrounding air. In spectra of the emitted noise, there are discrete frequency tones, which are in close correlation with the development of the cavitation process. The discrete frequency remains unchanged, whereas its magnitude changes according to the development of the cavitation so that it can even be used to determine the NPSH available or critical value. The emitted noise of a pumping set depends on the speed and load of the pump and on the instability in the pump. Instability in the pump can also appear due to cavitation in the pump. Cavitation as a source of instability causes vibration, cavitation noise, pitting and Material erosion and deterioration of pump performance. Average sound pressure over a specific central frequency of octave band analysis can be used as cavitation detection parameters in centrifugal pumps. ISSN (PRINT) : 2320 – 8945, Volume -1, Issue -5, 2013 106 ITSI Transactions on Electrical and Electronics Engineering (ITSI-TEEE) [13] Nakayama.Y, Aoki.K and Ohta.H, ―Visualization of pressure distribution due to impact accompanying collapse of cavity on the vanes of mixed flow pump-turbine,‖ International Symposium on Physical and Numerical Flow Visualization ASME, Vol. 22, pp. 101–108, 1985. [14] H.Ohki, Y.Yoshinaga and Y.Tsutsumi, ―Visualization of relative flow patterns in centrifugal impellers,‖ The 3rd International Symposium on Flow Visualization,‖ Ann Arbor, Michigan, U.S.A., September 1983. [15] P.J.McNulty and I.S.Pearsall, ―Cavitation inception in pumps. Journal of Fluids Engineering,‖ 104, pp.99–104, 1982. [16] P.J.McNulty, National Engineering Laboratory Glasgow (NTIS: N82-22504), Measurement techniques and analysis of fluid-borne noise in pumps. 1981. [17] The stability of pumping systems Freeman scholar lecture. Texas A&M University, College Station, Modern cavitation criteria for centrifugal Pumps, pp. 3–11, 1980. [18] ISO 3555 1977(E) Centrifugal, mixed flow and axial pumps} code for acceptance tests} Class B. ISSN (PRINT) : 2320 – 8945, Volume -1, Issue -5, 2013 107