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Research Papers: Energy Systems Analysis

Performance Optimization of Mechanical Vapor Compression Desalination System Using a Water-Injected Twin-Screw Compressor

[+] Author and Article Information
Yousif Alkhulaifi

Mechanical Engineering Department,
College of Engineering,
King Fahd University of Petroleum and Minerals
(KFUPM),
P.O. Box 279,
Dhahran 31261, Saudi Arabia
e-mail: s201156090@kfupm.edu.sa

Esmail M. A. Mokheimer

Mem. ASME
Mechanical Engineering Department,
College of Engineering,
King Fahd University of Petroleum and Minerals
(KFUPM),
P.O. Box 279,
Dhahran 31261, Saudi Arabia;
Center of Research Excellence in Energy
Efficiency (CEEE),
King Fahd University of Petroleum and Minerals
(KFUPM),
P.O. Box 279,
Dhahran 31261, Saudi Arabia;
Center of Research Excellence in Renewable
Energy (CoRe-RE),
King Fahd University of Petroleum
and Minerals (KFUPM),
P.O. Box 279,
Dhahran 31261, Saudi Arabia
e-mail: esmailm@kfupm.edu.sa

Jihad H. AlSadah

Physics Department, College of Science,
King Fahd University of Petroleum
and Minerals (KFUPM),
Dhahran 31261, Saudi Arabia
e-mail: jhalsadah@kfupm.edu.sa

1Corresponding author.

Contributed by the Advanced Energy Systems Division of ASME for publication in the JOURNAL OF ENERGY RESOURCES TECHNOLOGY. Manuscript received October 7, 2018; final manuscript received November 20, 2018; published online December 24, 2018. Editor: Hameed Metghalchi.

J. Energy Resour. Technol 141(4), 042008 (Dec 24, 2018) (13 pages) Paper No: JERT-18-1765; doi: 10.1115/1.4042087 History: Received October 07, 2018; Revised November 20, 2018

In this study, the thermal and operational characteristics of a 400 m3/day mechanical vapor compression desalination (MVCD) system that uses a water-injected twin-screw compressor have been studied and presented. A mathematical model of the MVCD system has been developed including mass and energy conservation equations, heat transfer equations, as well as thermophysical correlations. The effects of the MVCD system design and operation parameters on the system performance are analyzed and discussed. The effect of different boiling-point elevation correlations on the specific area is investigated. The brine and distillate preheaters' areas are studied as a function of inlet seawater temperature. The effect of the injection pressure on system performance is studied. Results show that the optimal injection point is close to the beginning of the compression process. Using this optimum injection pressure, the reduction in power consumption was found to be about 7.3% for high compression ratios. The effects of the brine and feed salinity on system performance are also analyzed. It is found that the specific heat transfer area strongly depends on the brine salinity, especially at temperature differences less than 6 °C. It increases by 44% and 32% at a temperature difference of 4 and 6 °C, respectively. The compressor inlet volume flowrate increases by 9% when the brine salinity increases from 50,000 to 150,000 ppm at all brine boiling temperatures considered. The feed-to-distillate ratio increases rapidly with rising feed salinity, while it decreases with rising brine salinity.

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References

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Figures

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Fig. 1

Schematic diagram of a single-effect MVC with water-injected twin-screw compressor

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Fig. 2

A TS diagram of the water-injected two-stage compression process

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Fig. 3

Validation of (a) mass fraction of injected water, (b) compressor power, and (c) specific power consumption

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Fig. 4

A plot of the specific heat transfer area as a function of the brine boiling temperature at different temperature differences using Sharqawy et al. [31] best-fit BPE correlation (Eq. 26)

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Fig. 5

The effect of the injection pressure on (a) the specific power consumption and (b) mass fraction of injected water for a brine boiling temperature of 75 °C and various temperature differences

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Fig. 6

The effect of the injection pressure on (a) the specific power consumption and (b) mass fraction of injected water for a temperature difference of 10 °C and various brine boiling temperatures

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Fig. 7

The effect of the brine salinity on the specific heat transfer area at a brine boiling temperature of 75 °C, feed salinity of 42,000 ppm, and various temperature differences

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Fig. 8

The effect of the brine salinity on the specific heat transfer area at a temperature difference of 10 °C, feed salinity of 42,000 ppm, and various brine boiling temperatures

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Fig. 9

Heat exchangers area breakdown to study the effect of the brine salinity under a brine boiling temperature of 75 °C, feed salinity of 42,000 ppm, and a temperature difference of 4 °C

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Fig. 10

The effect of the feed salinity on the specific heat transfer area at a brine boiling temperature of 75 °C, brine salinity of 70,000 ppm, and various temperature differences

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Fig. 11

The effect of the feed salinity on the specific heat transfer area at a temperature difference of 10 °C, brine salinity of 70,000 ppm, and various brine boiling temperatures

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Fig. 12

Heat exchangers area breakdown to study the effect of the feed salinity under a brine boiling temperature of 75 °C, brine salinity of 70,000 ppm, and a temperature difference of 4 °C

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Fig. 13

The effect of the brine salinity on the inlet volume flow rate of the compressor at a temperature difference of 10 °C, 400 m3/day of fresh water, feed salinity of 42,000 ppm, and various brine boiling temperatures

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Fig. 14

The effect of the feed salinity on the inlet volume flow rate of the compressor at a temperature difference of 10 °C, brine salinity of 70,000 ppm, and various brine boiling temperatures

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Fig. 15

The effect of (a) brine and (b) feed salinity on the feed-to-distillate ratio for a 400 m3/day of fresh water

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Fig. 16

The effect of seawater inlet temperature on (a) brine and (b) distillate preheater area for various temperature differences

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Fig. 17

The effect of seawater inlet temperature on (a) brine and (b) distillate preheater area for various brine boiling temperatures

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