Safety Factor of Pump Vibrations on Ships Based on The

Journal of Mechanical Engineering Research and Developments

ISSN: 1024-1752

CODEN: JERDFO

Vol. 43, No. 7, pp. 180-192

Published Year 2020

180

Safety Factor of Pump Vibrations on Ships Based on The Natural

Frequency of Pump Vibrations According to ISO 10816-3

Damora Rhakasywi†*, Amir Marasabessy‡, Mohammad Rusdy Hatuwe†, Sjaiful

Kotahatuhaha‡†

†Faculty of Engineering, Mechanical Engineering, Universitas Pembangunan Nasional Veteran Jakarta, Jl. Limo

Raya No.80, Limo, Kec. Limo, Kota Depok, Jawa Barat 16514. ‡Faculty of Engineering, Naval Engineering, Universitas Pembangunan Nasional Veteran Jakarta, Jl. Limo Raya

No.80, Limo, Kec. Limo, Kota Depok, Jawa Barat 16514. ‡†PT. SKF Industrial Indonesia, Gedung Talavera Lt.09. Jl. TB Simatupang Jakarta.

* Corresponding Author E-mail: [email protected]

ABSTRACT: Maintenance of ships to support operational aspects on an ongoing basis is very important from

operational cycle management or life cycle management. In this case the engines on the ship, especially in the

engine room which is a machine with a safety factor is quite high, so that if there is a damage can be known

immediately. One type of machinery referred to here is the pump system as a single pump or groups pump. The

purpose of this research is to develop a vibration monitoring system for centrifugal pumps on the ship by

placing sensors on the pump. The research method was carried out experimentally by installing 6 units of

accelerometer sensor connected to DAQ (Data Acquisition) and computer. The results of the study explain

pump vibrations at frequencies of 24.7 Hz have been categorized as exceeding the threshold value of the natural

pump frequency of 20 Hz or 1200 rpm. The value of pump vibration frequency greater than the natural

frequency of the 20 Hz pump according to ISO 10816-3 standard can cause cracks in the pump system on the

pump structure or pump components.

KEYWORDS: Safety Factor, Pump Vibration, Abnormality, Natural Frequency, Data Acquisition, Ship

INTRODUCTION

It is generally understood that the machining maintenance methods are as follows: damage treatment where

repairs are carried out directly on the spot, periodic maintenance, predictable maintenance and proactive

maintenance. The engines that exist on the ship, especially in the engine room are engine systems that have a

critical level high enough if there is damage must be repaired immediately. One type of machinery referred to

here is the pumping system individually or pump group. Vibration is one of the main problems considered in the

design and manufacture of pumps in this case the radial force and impeller vibration induced by the fluid in the

centrifugal pump is investigated at different flow rates using numerical simulations and the vibrations in the

volute are tested by experimental means [1]. New axial dynamics models including the transient force of the

balance disc were studied to predict the vibrational characteristics of a multilevel pump rotor system, the

distribution of pressure in axial distances and the dynamic forces suitable for nonlinear reduction in which the

axial gap increases from 0.2 mm to 1 mm then space pressure the inside is more sensitive to the inlet pressure

than the rotating speed, especially when the axial gap is 0.2 mm [2]. Multistage pumps for improved design with

low vibration and noise features in industrial applications. In this research, it becomes very important to fully

understand the vibration patterns of complex types of machines.

The study was to examine the vibration and stability of cantilevered centrifugal pumps under different flow

rates. The results showed the effect of operational conditions on the vibration of multilevel cantilever centrifugal

pumps. The vibration velocity is caused by mass imbalance at the flow rate point, the main type of vibration

frequency for the inlet and outlet is high frequency [3]. Monitoring of machine condition is a primordial field of

study aimed at avoiding downtime in industrial plants which results in financial and time loss. The research uses

internet of things (IoT) technology to classify pump vibration signals, as identification of normal operation

stages, new cavitation stages and severe cavitation stages, using vibration signals, which are collected on the

Safety Factor Of Pump Vibrations On Ships Based On The Natural Frequency Of Pump Vibrations According To ISO 10816-3

181

MEMS sensor. The results of these studies show that the Hu moment combined with KNN has the best accuracy

(99.47%) with a score time of 17 ms. Thus, the approach is reliable and efficient for detecting cavitation in

pumps [4].

The increasing industrial productivity has resulted in major breakthroughs in the field of centrifugal pump

maintenance to ensure optimal operation under different conditions, one of the important mechanisms affecting

the stable and dynamic operation of the pump is the cavitation conditions, from the results of these studies

indicate that the characteristics of the impeller geometry affect the development and cavitation behavior [5].

Other research conducted sea water piston pumps using the main power components for underwater equipment,

pulsation and low-pressure vibration are the main requirements of high-quality sea water piston pumps to

improve stability, underwater reliability. The simulation results show that the pressure pulsation rate reaches

17% [6]. Diagnostic method using vibration analysis for pump error detection by means of Fast Fourier

Transform (FFT) in the form of a vibration signal received by the sensor [7].

Cavitation is an important problem that occurs in all pumps, in this study it detects and diagnoses the

phenomenon of cavitation in centrifugal pumps using vibration. The results obtained from time and frequency

vibration signals are analyzed to provide an understanding of cavitation detection at the pump. The method used

is Fast Fourier Transform (FFT) to perform frequency domain analysis (FDA) [8]. Other studies have conducted

a diagnostic process using vibration sensors to monitor the phenomenon of cavitation in gerotor pumps used for

automotive applications [9]. Another study reports a Vibration-based Electromagnetic Energy Harvester (VEH)

designed to power wireless sensors so that they can be used in industrial centrifugal pumps. The design consists

of two independent moving parts; the middle and the outside. The experimental results are in accordance with

the simulation results because the average error percentage is within the acceptable range of 6.15%. A case

study is also presented in which the Zig Bee transceiver was successfully powered from the output produced by

VEH [10].

The phenomenon of fluid-induced instability is one of the common problems as large amplitude sub-

synchronous vibrations from the pump shaft and pump structure due to vortex flow. When the pump is not

operated at its best efficiency point, some of the mechanical energy is transferred to the fluid that produces the

vortex. The vortex flow has a very low pressure at its center and forms steam bubbles at a very high speed, the

formation of vapor bubbles (cavitation) produces a hammer effect that can cause vibrations and sounds this must

be avoided because it can cause engine damage due to fatigue [11]. This research investigates the vibrations of

fluid flow from centrifugal pumps using computational fluid dynamics (CFD) and cyclostationarity signals,

pump vibration models are set as amplitude modulation (AM) models. The results of the comparison between

CFD and cyclostationarity signal show convergence results [12].

Two sources of vibration in the pump using three screws, studied to provide a basis for vibration control, an

experimental test model was carried out to obtain the vibration response of three pump threads, from the test

results explained that the screw contact force is more dominant than the fluid tensile force [13]. Another study

used a simulated vertical mount configuration in which an electric motor was bolted over a twin screw pump in

an unsupported manner, the natural frequency of the pump / motor structure could be very low, resulting in

destructive vibrations. Resonance can occur when a driving force is not balanced on the motor or pump. In this

study, a finite element analysis software simulation is used to calculate the natural frequency of the pump

structure and then create a potential modification model to determine its impact in eliminating harmful

resonances [14].

Other studies explain the results obtained on measuring centrifugal pump vibrations by measuring the pressure

pulses, which are generated in the pipe system. More than 9 different operating modes are used on 1,000

m3/hour centrifugal pumps during the process of measuring vibration and pulsation pressure. From the results of

this study obtained in the booster pipe and main pump, 1.31 bar to 0.68 bar, by only running a booster pump, the

pressure pulse is reduced significantly to the value of 0.63 bar [15]. Vibration analysis on a pump assembly with

four positions can be very dangerous for the operation of a total pump pool. Vibration can affect the pumping

aggregate segment, so it needs to be done vibration analysis. From these results it was found that in an electric

motor, it is possible to determine bearing damage and other mechanical damage such as incorrect clutch position


182

[16]. Other research conducted by [17], the value of the change in relative pressure and vibration is measured

using 14 pressure sensors and 2 vibration sensors mounted inside the axial pump, it is concluded that horizontal

and vertical vibrations with twice the frequency have little relationship with the pulsating pressure for the inlet

impeller.

The dynamic model of axial piston pump is modeled as a dynamic system with four masses and 19 degrees of

freedom (DOF). Dynamic excitation force is calculated using piston chamber pressure which is simulated with a

three-dimensional computational fluid dynamics (CFD) model. The results show that the moment of excitation

force has a major contribution to most vibrations, vibration can be reduced significantly by optimizing the bolt

mounting position [18]. Experimental studies that focus on monitoring vibration based conditions and fault

diagnosis of centrifugal pumps, two types of interrelated errors, namely: blockage of flow in the inlet pipe and

the formation of impending bubbles in the pump are considered, centrifugal pumps are installed in the Machine

Fault Simulator (MFS) settings for experimental purposes [19]. The reversible pump turbine prototype at the

hydroelectric power station was investigated experimentally, the vibration performance and its physical origin,

the pump valve was opened (48 - 90) %. From the results of the analysis, it was found that valve vibrations were

mostly caused by fluid flow inside the pump turbine [20].

Analysis of experimental and numerical hydraulic vibrations in pipe systems under multi-excitations, from the

results of this study obtained by the FEM (finite element method) can predict the vibration characteristics of the

pipe with sufficient accuracy, and can see the dangerous phenomena caused by these vibrations [21]. Vibration

analysis and experimental studies on water piston pumps using liner-motor-driven on marine vessels to provide

an effective method of detecting vibration characteristics as well as a reference for the design and optimization

of linear motor-driven piston water pumps [22]. Experiments of pump vibration on ship propulsion using

damper bearings, the results show that in order to improve the safety and reliability of navigation, the hull

deformation, especially the horizontal hull deformation excitation, so that the rotation speed and resonance

frequency are required to be designed properly at the excitation frequency of the hull deformation [23]. Other

studies regarding vibrations that occur in pump impellers using numerical simulations and experiments, from the

results of these studies resulted in deviations in the value of the pressure that occurs in the hydraulic pump of

5% [24,25].

This research has only been carried out on ships to read the vibrations that occur in the cooling pumps of the

main engine of the ship in operation. The research objective is to apply a technological approach through the

development of a centrifugal pump monitoring system on ships continuously by placing sensors in the pump to

read the vibration value that occurs in the centrifugal pump in safe conditions, as well as providing an

explanation of the natural frequency vibration of a centrifugal pump if the vibration exceeds the natural

frequency vibration of the pump it can cause damage to the pump components. The problem that often arises in

centrifugal pumps is that they often experience cracks caused by pump vibrations, so it is necessary to monitor

the operating centrifugal pump. The purpose of this research in the future is to apply the industrialization

technology approach 4.0 where the operation of the centrifugal pump cooling for ship propulsion engines is

monitored online by placing sensors on the pump. The method used is FFT (Fast Fourier Transform), for online

reading of pump operation with a vibration analysis approach to understand the pump operating conditions, both

normal and abnormal conditions to prevent unscheduled or unpredictable operating failures.

METHODOLOGY

Set Up Sensor

This research was conducted experimentally pairing 3 sensors in the stuffing box and 3 sensors in the electrical

motor in the main engine centrifugal pump, the experimental setup that will be used in this research activity is as

follows. Figure 1 show accelerometer sensor 100 mV/g, sensors to be installed in the stuffing box and electrical

motor components are as many as 6 units with an accuracy level of up to 10,000 Hz (60 - 600,000 CPM)

frequency response.


183

Figure 1. Accelerometer sensor 100 mV/g

Table 1. Sensor specifications

Specifications Standard Metric

Part Number AC 150 M/AC 150

Sensitivity (± 15 %) 100 mV/g

Frequency Response (±3dB) 60-600,000 CPM 1,0-10000 Hz

Dynamic Range ± 50 g, peak

Electrical

Settling Time < 2.5 seconds

Voltage Source (IEPE) 18-30 VDC

Constant Current Excitation 2-10 mA

Spectral Noise @ 10 Hz 14 μg/√Hz

Spectral Noise @ 100 Hz 2.3 μg/√Hz

Spectral Noise @ 1000 Hz 2 μg/√Hz

Output Impedance < 100 ohm

Bias Output Voltage 10-14 VDC

Case Isolation >108 ohm

Environmental

Temperature Range -58 to 250oF -50 to 121oC

Maximum Shock Protection 5,000 g, peak

Electromagnetic Sensitivity CE

Sealing Welded, Hermetic

Submersible Depth (AC150-

2C/3C) 200 ft 60 m

Physical

Sensing Element PZT Ceramic

Sensing Structure Shear Mode

Weight 3.2 oz 90 grams

Case Material 316L Stainless Steel

Mounting 1/4-28

Connector (non-integral) 2 Pin MIL-C-5015

Resonant Frequency 1,380,000 CPM 23000 Hz

Mounting Torque 2 to 5 ft. lbs 2,7 to 6,8 Nm

Mounting Hardware 1/4-28 Stud M6x1 Adapter Stud

Calibration Certificate CA10

Table 1 sensor specifications used in centrifugal pumps to read pump vibrations that occur during operation. The

test is carried out for 1 week to get the vibration data of the main engine centrifugal pump during operation with

variations of the valve open 0%, 4%, 11% and 46%.


184

Next figure 2 shows the connecting sensor cable with a length of ± 8 meters connected to the Data Acquisition

(DAQ) Unit can directly read the vibration chart of a centrifugal pump using a computer.

Figure 2. Cable connection DAQ

Then Figure 3 shows the Data Acquisition Unit (DAQ), in this study the instrument used is the vibration

measurements IOtech 672u engineering specification model and accuracy are described in table 2.

Figure 3. Vibration gauge DAQ

Table 2. Vibration gauge DAQ specifications

Features IOtech 672u

Channel Capacity 20

A/D Resolution (bits) 24

IEPE Current Source 4 mA

Programmable Input Ranges ± 40V

Accelerometer Inputs yes

Filter Type Linear Phase

Coupling AC, DC

Maximum Sample Rate 105 kHZ/ch

Simultaneous Sampling yes

Analog Trigger Source single channel

Digital I/O – Included 8

Other Supported I/O volts

PC Connectivity USB

Figure 4 shows the flowchart of the research conducted to obtain vibration data of the main engine centrifugal

pump on a 30 GT fiberglass fish ship. This research was conducted at PT. Proskuneo Kadarusman for collecting

centrifugal pump data.


185

Figure 4. Research flow chart

Experimental pump

Table 3 explains the specifications of the centrifugal pump used in the study. The pump used has a rotational

speed of 1200 RPM with water as a working fluid.

Table 3. Main engine coolant centrifugal pump specifications

Type Pump UC2110

Certification CE, ATEX

Maximum power hp (kW) 80.46 HP (60 kW)

Yes

No

Finish

Recommendation: Make recommendations to make decisions on the results of centrifugal pump vibrations

Data analysis: The results of the centrifugal pump vibration data are then analyzed based on the ISO 10816-3 standard

Collecting data: - Sensor installation in centrifugal pump system - Data Acquisition Unit (DAQ) settings on the pump - Data is collected when the ship is operating at a fishing ground for

one week

Field survey at the shipyard of PT. Proskuneo Kadarusman

Start

Data processing: Vibration data recorded on IOtech 672u vibration measurements are transferred to a computer for analysis


186

Maximum working pressure to 435 psi (30 Bar)

Maximum viscosity Over 200 cP

Type driving motor Tyrone

Output power 16.09 HP (12 kW)

Voltage 380V/50 Hz

Maximum speed 1200 RPM

Figure 5 shows the position of the sensors installed in the 2 main components of the centrifugal pump on the

stuffing box and the electrical motor, with horizontal (H) and vertical (V) positions. The installed sensor

position will store vibration data during the centrifugal pump operation, the test is carried out for 1 week with

the data stored 1 day for 9 hours. Description of the numbers 1H, 1V, 2H, 2V, 3H, 3V and 3AV (axial vertical)

indicate the number of vibration points to be measured as shown in Figure 5 and Figure 6. The installation

stages of the sensors are carried out by means of a soft drill based on the standard screw sensor then the sensor

is mounted using a screw.

Figure 5. Sensor position placement

Figure 6. The actual position of the sensor installation

RESULTS AND DISCUSSION

Pump Vibration Analysis


187

The results of measurements using DAQ IOtech 672u obtained vibration data on the centrifugal pump of the

ship engine cooling in table 4, centrifugal pump experiments for ship engine coolers using variations of the

discharge valve opening to obtain vibration values based on safety factors is 11% according to ISO standards

[26], when opening the valve as described in figure 7.

Table 4. Centrifugal pump vibration measurement results

Part Sensors point Discharge valve opening

0 % 4 % 11 % 46 %

Electrical motor

1H, 1V - 5.785 4.949 5

1V, 1V - 6.682 3.193 3.118

2H, 2V - 4.881 2.166 2.210

2V, 2V - 4.661 1.312 1.335

Pump Stuffing Box

3V, 3V 15.315 12.679 9.515 5.193

3H, 3V 16.804 11.808 9.864 4.840

3A, 3V 11.456 5.91 5.252 3.147

Figure 7. Pump vibrations are based on Standard ISO 10816-3

Figure 7 displays the stuffing box is a component home of a centrifugal pump impeller, Mtr DE is the part of the

motor that is connected to the pump clutch and Mtr NDE is a part that is not connected to the pump clutch. The

position of the sensor is placed on these components. Information table 4, displays the value of each vibration

point on the electrical motor versus pump stuffing box when compared to the percentage of the discharge valve

opening, the horizontal or vertical position of the pump vibration value is higher at the point of pump stuffing

box.

Table 5. ISO Standard 10816-3 [27]


188

Complicated vibration chart reading takes time for technicians to understand, so a simple method for reading

charts using color display needs to be developed [27]. The display of the color indicates for certain conditions

such as, green with a safe meaning, yellow with the meaning that there is already an abnormality indication and

red with the meaning of danger, in accordance with ISO-10816-3 Standards, vibration standard values with

various categories are shown in table 5. This simplification method is by building certain algorithms that can be

processed from the vibration sensor output to produce graphical readings as desired. These sensors are attached

to the centrifugal pump so they can be read in real time. The natural frequency possessed by the pump casing

during vibration testing is explained in Figure 8 and Figure 9. Random frequencies in addition to the blade pass

frequency (BPF) line can produce turbulence flow disturbances thereby creating random frequencies in other

parts, this gives an indication that it can stimulate the natural frequency of the natural frequency of the pump

casing (24.7 Hz). Based on data from the pump specifications in table 3.1, the value of the natural frequency of

the pump is (1200rpm)/(60 minute) = 20 Hz, so that the resonance generated can create several impacts such as

the phenomenon of cracking in the pump casing.

Figure 8. The results of natural centrifugal pump frequency measurement

Figure 9. The natural frequency of the pump when collecting data


189

The results of the data obtained explain that the natural frequency is approaching the same value as the

maximum speed motor output, the natural frequency value of the centrifugal pump is obtained from the

measurement results shown in figure 9. By using the explanation in figure.3.5, lower boundary (1132.8 CPM-

1185.6 CPM) and Upper boundary (1699.2 CPM-1778.4 CPM) can be explained that the natural frequency is in

the lower limit and the upper limit of each area of resonance. Figure 9 explains that the operational speed is in

the area of resonance and the natural effect of this phenomenon is that the vibrational amplitude produced is

quite high. To reduce vibrations caused by the resonance effect, the pump operating speed must be ± 25% below

the natural frequency limit value of the pump. In this case, the increase in natural frequency or resonance area

must not occur due to the influence of the rotating speed of the pump engine.

Natural frequency, damping and isolator

Excessive resonance can cause cracks in the pump so it needs to be done dampers. The purpose of the damper is

to reduce excessive cracking due to high resonance, to reduce the resonance that occurs by reducing the value of

transmissibility (T) so that excessive resonance after muted will decrease in value. The mathematical equation

that can be used to reduce the value of transmissibility is as follows (1) [28]

( )

( ) ( )222

2

21

21

rr

rT

+−

+= (1)

n

r

= (2)

m

kn = (3)

ratiodampingcriticalm

cwhere

n

==

2

: , m= mass of system (kg), k=stiffnes (N/m), c= viscous

damping (kg/s), ω = angular frequency (Hz) , ωn = natural frequency (Hz). Typical values for damping

ratio, are 0.005 – 0.01 for steel, and 0.05 – 0.1 for rubber. The inclusion of damping has the greatest effect in

the vicinity of resonance, decreasing the vibration amplitude. A curious effect of damping is that it results in

increased amplitude at frequencies > 1.4Fn. The selection of pump bearings by taking into account the damping

factor can change the actual natural frequency of the rotor using mathematical equations 1, the actual natural

frequency can be reduced to (≤fn) from the critical natural frequency described in Table 6.

Table 6. Natural frequency value to cycle per minute (CPM) and the area that receives resonance

Natural frequency Frequency (Hz) CPM = RPM Resonance Area

Speed 19.75 1185

Natural frequency of

the casing

24.7 1482 20 %

23.6 1416 16.3 %

Natural frequency

rotating components 24 1440 17.7 %

Based on the measurement results in table 6, natural frequency value to cycle per minute (CPM) and the area

that receives resonance with a critical speed of 1185 RPM based on figure 3.5 of the natural frequency value of

a 24.7 Hz centrifugal pump so that in making good designs advising the centrifugal pump engine must be

designed not to operate beyond the 120% value of the pump critical speed or equal to 1.2 x 1185 RPM = 1422

RPM [28].


190

CONCLUSIONS

High amplitude vibrations can cause the casing frequency value of 24.7 Hz to be above the normal natural

frequency value of centrifugal pumps around +/- 20%. The large amplitude value is caused by the resonance of

vibrations received from the centrifugal pump due to the turbulence flow of water fluid in the pump. The effect

of the resonant vibration value caused a cracking effect on the pump system for the pump structure and

components. In this research, using a centrifugal pump with a maximum speed of 1200 RPM impeller rotation

with a maximum value of normal pump vibration is 20 Hz. So that if the pump vibrates beyond the value of 20

Hz, it will have a bad impact on the structure of the pump which can cause cracks and damage to the pump. In

this study, trying to characterize the pump vibrations that arise when the pump is working, by attaching the

sensor to the vibrating pump area, after it is known that the vibration of the centrifugal pump caused by the

impeller rotation and the flowing fluid flow can provide a solution to prevent pump damage. From the research

conducted, it can be concluded that the ideal pump when operating must be below the natural frequency value of

the pump vibration, which is 20 Hz, if the pump vibration value is obtained above the natural frequency value,

this will be done to reduce the vibration by installing a vibration damper in the form of a flexible spring

installation based on ISO Standard 10816-3 so as to reduce the vibration effect that causes pump damage.

ACKNOWLEDGMENTS

This work was supported within the LPPM (Lembaga Penelitian dan Pengabdian Kepada Masyarakat) –

Universitas Pembangunan Nasional Veteran Jakarta (Project number: 345/UN61.0/HK.02/2020). The author

would like to thank the Galangan Kapal PT. Proskuneo Kadarusman.

REFERENCES

[1] B. Cui, J. Li, C. Zhang, and Y. Zhang, “Analysis of Radial Force and Vibration Energy in a Centrifugal

Pump,” Math. Probl. Eng., vol. 2020, pp. 1–12, 2020. doi: 10.1155/2020/6080942.

[2] W. Zhou, Y. Cao, N. Zhang, B. Gao, N. Qiu, and W. Zhang, “A Novel Axial Vibration Model of

Multistage Pump Rotor System with Dynamic Force of Balance Disc,” J. Vib. Eng. Technol., No.

0123456789, 2019, doi: 10.1007/s42417-019-00164-7.

[3] L. Bai, L. Zhou, X. Jiang, Q. Pang, and D. Ye, “Vibration in a Multistage Centrifugal Pump under Varied

Conditions,” Shock Vib., vol. 2019, 2019, doi: 10.1155/2019/2057031.

[4] Q. Hu, E.F. Ohata, F.H.S. Silva, G.L.B. Ramalho, T. Han, and P.P. Rebouças Filho, “A new online

approach for classification of pumps vibration patterns based on intelligent IoT system,” Meas. J. Int.

Meas. Confed., Vol. 151, No. xxxx, Pp. 107138, 2020, doi: 10.1016/j.measurement.2019.107138.

[5] G. Mousmoulis, N. Karlsen-Davies, G. Aggidis, I. Anagnostopoulos, and D. Papantonis, “Experimental

analysis of cavitation in a centrifugal pump using acoustic emission, vibration measurements and flow

visualization,” Eur. J. Mech. B/Fluids, Vol. 75, Pp. 300–311, 2019. doi:

10.1016/j.euromechflu.2018.10.015.

[6] Z. Zuti, C. Shuping, W. Huawei, L. Xiaohui, D. Jia, and Z. Yuquan, “The approach on reducing the

pressure pulsation and vibration of seawater piston pump through integrating a group of accumulators,”

Ocean Eng., Vol. 173, No. 7, Pp. 319–330, 2019. doi: 10.1016/j.oceaneng.2018.12.078.

[7] D. Siano and M.A. Panza, “Diagnostic method by using vibration analysis for pump fault detection,”

Energy Procedia, Vol. 148, Pp. 10–17, 2018. doi: 10.1016/j.egypro.2018.08.013.

[8] A.R. Al-Obaidi, “Investigation of effect of pump rotational speed on performance and detection of

cavitation within a centrifugal pump using vibration analysis,” Heliyon, Vol. 5, No. 6, Pp. e01910, 2019.

doi: 10.1016/j.heliyon. 2019.e01910.

[9] D. Siano, E. Frosina, and A. Senatore, “Diagnostic Process by Using Vibrational Sensors for Monitoring

Cavitation Phenomena in a Getoror Pump Used for Automotive Applications,” Energy Procedia, Vol. 126,

Pp. 1115–1122, 2017. doi: 10.1016/j.egypro.2017.08.269.


191

[10] S.F.H. Gilani, M.H. Khir, R. Ibrahim, and E.H. Kirmani, “Modelling and development of a vibration-based

electromagnetic energy harvester for industrial centrifugal pump application,” Microelectronics J., Vol. 66,

Pp. 103–111, 2017. doi: 10.1016/j.mejo.2017.06.005.

[11] T.N. Kushwaha, “CW Pump Fluid Induced Vibration Troubleshooting Methodology,” Procedia Eng., Vol.

144, Pp. 274–282, 2016, doi: 10.1016/j.proeng.2016.05.133.

[12] S. Li, N. Chu, P. Yan, D. Wu, and J. Antoni, “Cyclostationary approach to detect flow-induced effects on

vibration signals from centrifugal pumps,” Mech. Syst. Signal Process., Vol. 114, Pp. 275–289, 2019. doi:

10.1016/j.ymssp.2018.05.027.

[13] W. Li, H. Lu, Y. Zhang, C. Zhu, X. Lu, and Z. Shuai, “Vibration analysis of three-screw pumps under

pressure loads and rotor contact forces,” J. Sound Vib., Vol. 360, Pp. 74–96, 2016. doi:

10.1016/j.jsv.2015.09.013.

[14] M. Tompkins, R. Stakenborghs, and G. Kramer, “Use of FEA software in evaluating pump vibration and

potential remedial actions to abate resonance in industrial vertical pump/motor combinations,” Int. Conf.

Nucl. Eng. Proceedings, ICONE, Vol. 1, Pp. 1–5, 2016. doi: 10.1115/ICONE24-60890.

[15] V. Barzdaitis, P. Mažeika, M. Vasylius, V. Kartašovas, and A. Tadžijevas, “Investigation of pressure

pulsations in centrifugal pump system,” J. Vibroengineering, Vol. 18, No. 3, Pp. 1849–1860, 2016. doi:

10.21595/jve.2016.15883.

[16] M. Milovančević, “Vibration analyzing in horizontal pumping aggregate by soft computing,” Meas. J. Int.

Meas. Confed., Vol. 125, Pp. 454–462, 2018. doi: 10.1016/j.measurement.2018.04.100.

[17] X. Duan, F. Tang, W. Duan, W. Zhou, and L. Shi, “Experimental investigation on the correlation of

pressure pulsation and vibration of axial flow pump,” Adv. Mech. Eng., Vol. 11, No. 11, Pp. 1–11, 2019.

doi: 10.1177/1687814019889473.

[18] S. Ye, J. Zhang, B. Xu, S. Zhu, J. Xiang, and H. Tang, “Theoretical investigation of the contributions of

the excitation forces to the vibration of an axial piston pump,” Mech. Syst. Signal Process., Vol. 129, Pp.

201–217, 2019. doi: 10.1016/j.ymssp.2019.04.032.

[19] A.K. Panda, J.S. Rapur, and R. Tiwari, “Prediction of flow blockages and impending cavitation in

centrifugal pumps using Support Vector Machine (SVM) algorithms based on vibration measurements,”

Meas. J. Int. Meas. Confed., Vol. 130, Pp. 44–56, 2018. doi: 10.1016/j.measurement.2018.07.092.

[20] Y. Zhang, X. Zheng, J. Li, and X. Du, “Experimental study on the vibrational performance and its physical

origins of a prototype reversible pump turbine in the pumped hydro energy storage power station,” Renew.

Energy, Vol. 130, Pp. 667–676, 2019. doi: 10.1016/j.renene.2018.06.057.

[21] P. Gao, H. Qu, Y. Zhang, T. Yu, and J. Zhai, “Experimental and Numerical Vibration Analysis of

Hydraulic Pipeline System under Multiexcitations,” Shock Vib., Vol. 2020, doi: 10.1155/2020/3598374.

[22] Y.Q. Huang, S.L. Nie, H. Ji, and S. Nie, “Vibration Analysis and Experimental Research of the Linear-

Motor-Driven Water Piston Pump Used in the Naval Ship,” Shock Vib., Vol. 2016, doi:

10.1155/2016/4608328.

[23] C. Zhang, D. Xie, Q. Huang, and Z. Wang, “Experimental research on the vibration of ship propulsion

shaft under hull deformation excitations on bearings,” Shock Vib., 2019. doi: 10.1155/2019/4367061.

[24] R. Birajdar and A. Keste, “Prediction of Flow-Induced Vibrations due to Impeller Hydraulic Unbalance in

Vertical Turbine Pumps Using One-Way Fluid−Structure Interaction,” J. Vib. Eng. Technol., Vol. 8, No. 3,

Pp. 417–430, 2020. doi: 10.1007/s42417-019-00174-5.

[25] P.K. Pradhan, S.K. Roy, and A.R. Mohanty, “Detection of Broken Impeller in Submersible Pump by

Estimation of Rotational Frequency from Motor Current Signal,” J. Vib. Eng. Technol., No. 0123456789,

2019, doi: 10.1007/s42417-019-00165-6.


192

[26] International Standard Organization, “ISO 10816-3: Mechanical vibration — Evaluation of machine

vibration by measurements on non-rotating parts — Part 3: Industrial machines with nominal power above

15 kW and nominal speeds between 120 r/min and 15 000 r/min when measured in situ,” Int. Stand.

Organ., Pp. 20, 1998.

[27] I. O. for Standardization, “ISO 10816-3:2009,” 2009. [Online]. Available:

https://www.iso.org/obp/ui/#iso:std:iso:10816:-3:ed-2:v1:en. [Accessed: 08-Jul-2020].

[28] M. F. Heertjes and J.-G. C. Van Der Toorn, “Vibration Isolation System,” J. Acoust. Soc. Am., vol. 129,

no. 4, p. 2353, 2011, doi: 10.1121/1.3582194.

Documents

Safety Factor of Pump Vibrations on Ships Based on The