Россия
Калининградская область, Россия
Рыбный жир перерабатывают из пелагических жирных видов рыб, у человека они являются источниками жирных кислот, особенно омега-3. Рыбный жир различается по составу жирных кислот. Изучаются новые источники рыбы или рыбьего жира. Повышение эффективности технологических линий связано с совершенствованием межоперационного транспортирования рыбного жира. Производители технологических линий используют одновинтовые насосы для транспортирования рыбного жира. Одновинтовые насосы вы-годны для перекачивания высоковязких сред, обладают относительно невысокой стоимостью. Цель статьи – адаптация к рыбному жиру метода расчета системы непрерывной подачи рыбного жира с учетом характеристик технологического трубопровода, одновинтового насоса и реологических параметров рыбного жира. Использованы результаты анализа рабочих характеристик одновинтовых насосов, результаты экспериментальных работ. Использовано уравнение Букингэма – Рейнера при расчете потерь на трение в трубопроводе, а также модифицированное число Рейнольдса. Оценены расход, мощность, влияние на них вязкости жидкости для насоса Atlas W63-1B при разных частотах вращения ротора. При увеличении частоты увеличивается напор при постоянном расходе или расход при постоянном напоре. Приведены примеры определения гидравлических и энергетических параметров насосных систем при перекачивании рыбного жира. При увеличении вязкости производительность существенно уменьшается, а затраченная мощность увеличивается. С уменьшением диаметра гидравлическое сопротивление трубопровода возрастает. Представленный алгоритм расчета перемещения рыбного жира в трубопроводных системах позволяет рационализировать насосные системы, создавать энергоэффективные технологии работы с рыбным жиром, обеспечивать научно обоснованный выбор насоса.
рыбоперерабатывающий завод, жирные кислоты, рабочие характеристики, частота вращения ротора
Introduction
Increasing the productivity and energy efficiency of technological lines is impossible without improving the interoperative transportation of fish oil (FO) [1-7]. However, hydraulic calculations of the process pipeline are often performed without taking into account the performance characteristics of pumping units. Only a few publications analyze the operation of pumps when pumping FO. Thus, in [8], the effect of FO viscosity on the performance of cam pumps (CP) was studied. It was found that the performance of CP when pumping FO is noticeably higher than when pumping water; an increase in the temperature of FO leads to a decrease in CP performance. At the same time, the characteristics of the pipeline were not taken into account. Process line manufacturers prefer to use single screw pumps (SSP) for interoperable transportation of FO (see, for example, [9]). This is due to the well-known advantages of SSP when pumping high-viscosity media [10] and the relatively low cost [11-18].
In [16], the characteristics of the process pipeline were not taken into account, which makes it difficult to use the results for design calculations.
The purpose of this article is to develop a method for calculating a continuous FO supply system taking into account the characteristics of the process pipeline, SSP and rheological parameters of FO.
Materials and methods
The results of the analysis [16] can be used for the performance characteristics of the SSP. The supply (Q, m3/s) and the consumed power (N, kW) of the SSP pumping water at 20 °C can be calculated using the formulas:
Q0 = (a0 – a1 · Δp) (n – a2 · Δp); (1)
N0 = n (b1 + b2 · Δp) (2)
where a0, a1, a2, b1, b2 are empirical constants, the values of which are determined from experimental data; Δp is the pressure drop, Pa; n is the rotor speed (RS), s–1. For example: a0 = 0.0020225 m3; a1 = 3.50 · 10–7 m3/kPa; a2 = 1.88 · 10–6 s–1/kPa; b1 = 0.4755 kJ; b2 = 0.001492 kJ/kPa (Atlas W63-1B pump).
According to formula (2), the spent power of the SSP increases linearly both with an increase in both RS and pressure drop. According to formula (1), the dependence of the SSP supply on RS is linear, and on Δp is nonlinear. However, such non-linearity is manifested only at large pressure drops.
Taking into account [16]:
φ1(νb) ≡ Q / Q0 = 1 – 0.000789 · (νb – 1);
νb = ν / ν0; (3)
φ2(νb) ≡ N / N0 = 1 + 0.001765 · (νb – 1) (4)
where φ1,2 – dimensionless coefficients; v0, Q0, N0 is the kinematic viscosity, supply and power for water; 1 ≤ vb ≤ 534 with determination index R2 = 0.97. Then for FO with a dimensionless viscosity coefficient,
vb can be written as follows
Q = (a0 – a1 · Δp) (n – a2 · Δp) (1 – 0.000789 · (νb – 1)). (5)
To evaluate the effect of the viscosity of FO on the characteristics of SSP, it is necessary to set its rheological parameters. The results of experimental work can be used for the rheological model of FO [17, 18]. The effective viscosity of catfish fat (Catfish oils) at a temperature of t = 25 °C and various processing methods was investigated. The shear rate varied from zero to 1,200 s–1. The use of the Bingham plastic model showed good results (see Table 1):
μ = μp + τ0 / ω (6)
where µ is the coefficient of effective dynamic viscosity, Pa·s; µp is the coefficient of plastic viscosity of Bingham, Pa·s; τ0 is the limiting shear stress, Pa; ω is the shear rate, s–1.
According to the Table 1 it can be seen that untreated Fish oil has the highest viscosity. FO has the lowest viscosity after deodorization. In all the conditions considered [19], the determination index is very high R2 > 0.99.
Table 1
Parameters of catfish fish oil using the Bingham model
|
Processing FO |
τ0, Pa |
μp, Pa·s |
R2 |
|
Without processing (FOW) |
4.79 |
0.042 |
0.991 |
|
Neutralization (FON) |
2.42 |
0.030 |
0.995 |
|
Deodorization (FOD) |
1.40 |
0.024 |
0.995 |
* Compiled according to [19].
To use formulas (3), (4), it is necessary to calculate the ratio of kinematic viscosities vb. Formula (6) is written in dimensionless form as follows:
vb = f1(ω) = µp / (ρ · v0) + τ0 / (ω · ρv0) (7)
where ρ is the density FO, kg/m3. The velocity shift in SSP is approximately estimated as follows: ω ≈ 2πnr / δ (r is the radius of the screw, δ is the average gap value). For example, for FON by (7) it turns out
νb ≈ 45.41 + 824.6 / n. (8)
During the flow of FO, hydraulic losses are present in the pipe. The coefficient of hydraulic friction losses along the length of a round pipe (CHFL) λ during the flow of a pseudoplastic liquid (Bingham model) obeys the well-known Buckingham-Reiner equation:
λ = (64 / Re) (1 + Bi / 6 – (64 / 3) Bi 4 / (λ · Re)3);
Bi = τ0 d / (v ηA); Re = v ρ d / ηA
where ηA – absolute viscosity coefficient; Bi is the Bingham number; Re is the Reynolds number; d is the inner diameter of the pipe, m; v is the velocity of the liquid, m/s; v = Q / S, S is the cross–sectional area of the pipe, m2, S = πd2 / 4.
In [19] it was shown that in the laminar flow regime of a non-Newtonian fluid, CHFL can be calculated using the approximate formula
λn = 64 / ReM, (9)
as for a Newtonian fluid, but using a modified Reynolds number ReM, where the modified Reynolds number of the Bingham liquid is determined by the formula
ReM = Re / ((3m + 1) / (4m) + Bi / 8); (10)
m = 1 / (1 + Bi / 8). (11)
Convert the expression in the denominator of formula (11) as follows:
1 / m = 1 + Bi / 8; (3m + 1) / (4m) = 0.25 (3 + 1 / m) = 0.25 (4 + Bi / 8) = 1 + Bi / 32. (12)
When substituting (12) into (10) and then into (9), it turns out
ReM = Re / (1 + 5 · Bi / 32); λn = (64 / Re) (1 + 5 · Bi / 32).
It was shown in [20, 21] that the pressure loss coefficients (PLC) in local hydraulic resistances can also be calculated using formulas used for laminar flow of a Newtonian fluid, replacing the usual Reynolds number with a modified one. So in the tap (smooth turn), the PLC is calculated using the formula:
ζ = A / ReM
where the value is A ≈ 200 if the radius of rounding is 2d. The characteristics of the pipeline in this form:
Δp ≡ fT (Q) = ΔpS + 0.5ρ · (4Q / πd2)2 (zA + 64L / d) / ReM (13)
where z is the number of pipeline bends, ΔpS is the static pressure drop.
Formula (5) for a given supply value Q can be considered a quadratic equation with respect to the pressure drop Δp. Its solution is a form of SSP load characteristic:
ΔpL = fL(Q) (14)
where fL – load characteristic of the pump.
Then the SSP supply at the operating point (OP), equating (13) and (14):
fL(QOP) = fT(QOP).
Results and discussion
Dependences (1), (2) correspond to experimental data [22] obtained by supplying water using SSP (Fig. 1).
|
|
|
|
a |
b |
Fig. 1. The dependence of the supply (a) and the consumed power (b) Atlas W63-1B single screw pump from pressure drop
at different rotor speed: 1 – 200 rpm; 2 – 400 rpm; 3 – 600 rpm; 4 – 800 rpm.
The points are experimental data [22], the lines are calculated according to (1) and (2)
Substituting (6) into (3) and (4), one can estimate the effect of the viscosity of FO on the operation of SSP. According to Fig. 2 it can be seen that with a decrease in RS, the effect of the viscosity of FO on the characteristics of SSP increases.
|
|
|
|
a |
b |
Fig. 2. Assessment of the effect of fish oil viscosity on the operation of the Atlas W63-1B single-screw pump depending
on the rotor speed: a – reduction in feed; b – increase in power consumption; 1 – untreated fish oil; 2 – neutralized fish oil; 3 – deodorized fish oil
FOW has the highest coefficient of kinematic viscosity, therefore its influence is the greatest, and FOD has the least. If n = 3 s–1, then SSD performance decreases by 25% when pumping FOW, power consumption increases by 56%, and when pumping FOD, respectively, by 8 and 19%.
It is possible to select SSP parameters for transporting FO with the specified properties. Suppose it is necessary to supply FOW Q0 = 6 dm3/s using SSP Atlas W63-1B. The length of the pipeline is L = 30 m, z = 3.
In Fig. 3, according to the formula (13), the characteristics of the pipeline are constructed at three diameter values (lines 1-3).
Fig. 3. Determination of the operating point of the pumping unit during pumping, neutralized fish oil:
1 – characteristics of the pipeline at d = 50 mm; 2 – at d = 35 mm; 3 – at d = 30 mm;
4 – pressure characteristic of the turboprop pump at n = 4.32 s–1; 5 – at n = 4.68 s–1; 6 – at n = 5.10 s–1
As the diameter decreases, the hydraulic resistance of the pipeline increases.
It is possible to determine the RS at which the required SSP supply will be. Let d = 35 mm (line 2 in Fig. 3). OP should be at the intersection point of line 2 with the vertical Q0 = 6 dm3/s (point B in Fig. 3). According to Q0, formula (13) allows us to calculate the pressure drop in OP: ΔpOР = 428.3 kPa. If the obtained value of ΔpOР, Q0 and formula (8) are substituted into (5), we obtain a nonlinear equation with one unknown – n. Solving it numerically leads to the desired value RS n = 4.68 s–1. The parameters in the other two OP were calculated in a similar way in Fig. 3. The calculation results are presented in Table 2 (η – efficiency;
E – pecific energy of the liquid).
Table 2
The results of calculating the parameters of the pumping unit at the operating point for neutralized fish oil
|
d, mm |
ΔpOР, kPa |
n, s–1 |
NOР, kW |
ηOР, % |
EOР, kJ/dm3 |
|
50 |
264.6 |
4.32 |
5.32 |
29.9 |
0.89 |
|
35 |
428.3 |
4.68 |
7.25 |
35.4 |
1.21 |
|
30 |
608.0 |
5.10 |
9.62 |
37.9 |
1.60 |
The results of similar calculations for pumping FOD are shown in Fig. 4 and in Table 3.
Fig. 4. Determination of the operating point of the pumping unit when pumping deodorized fish oil:
1 – characteristics of the pipeline at d = 50 mm; 2 – at d = 35 mm; 3 – at d = 30 mm;
4 – pressure characteristic of a single-screw pump at n = 7.76 s–1; 5 – at n = 3.98 s–1; 6 – at n = 4.23 s–1
Table 3
The results of calculating the parameters of the pumping unit at the operating point for deodorized fish oil mm
|
d, mm |
ΔpOР, kPa |
n, s-1 |
NOР, kW |
ηOР, % |
EOР, kJ/dm3 |
|
50 |
232.9 |
3.76 |
3.58 |
39.0 |
0.597 |
|
35 |
324.6 |
3.98 |
4.40 |
44.3 |
0.733 |
|
30 |
426.7 |
4.23 |
5.38 |
47.6 |
0.896 |
Conclusion
Viscosity significantly affects the operation of the FO pumping system. FOW has the highest coefficient of kinematic viscosity, while FOD has the lowest.
When pumping FOW compared to pumping FOD, the performance is almost 3 times less, the power consumed is 3 times more for a constant SSP frequency.
The developed method for calculating the continuous FO supply system, taking into account the characteristics of the process pipeline, SSP and rheological parameters of FO, can be used in the development of technological processes for working with FO.
1. Liao J., Xiong Q., Yin Y., Ling Z., Chen S. The Ef-fects of Fish Oil on Cardiovascular Diseases: Systematical Evaluation and Recent Advance // Front Cardiovasc Med. 2021. V. 8. P. 802306. DOI:https://doi.org/10.3389/fcvm.2021.802306.
2. Yi M., You Y., Zhang Y., Wu G., Karrar E., Zhang L., Zhang H., Jin Q., Wang X. Highly Valuable Fish Oil: Formation Process, Enrichment, Subsequent Utilization, and Storage of Eicosapentaenoic Acid Ethyl Esters // Molecules. 2023. V. 28 (2). P. 672. DOI:https://doi.org/10.3390/molecules28020672.
3. Jayasinghe P., Adeoti I., Hawboldt K. A Study of Process Optimization of Extraction of Oil from Fish Waste for Use as A Low-Grade Fuel // J. Am. Oil. Chem. Soc. 2013. V. 90. P. 1903–1915. DOI:https://doi.org/10.1007/s11746-013-2321-1.
4. Balwan W. K., Saba N. Study of Role of Fish Oil in Human Health // Glob. Acad. J. Med. Sci. 2021. V. 3. Iss. 1. P. 14–18. DOI:https://doi.org/10.36348/gajms.2021.v03i01.002.
5. Fard S. G., Wang F., Sinclair A. J., Elliott G., Turchini G. M. How does high DHA fish oil affect health? A systematic review of evidence // Critical Reviews in Food Science and Nutrition. 2019. V. 59. P. 1684–1727. DOI: 1080/10408398.2018.1425978.
6. Артемова А. Г., Бредихина О. В., Артемов Р. В., Баскакова Ю. А. О возможности применения ультразвука для интенсификации процесса выделения жира из голов тихоокеанских лососевых рыб // Актуальная биотехнология. 2019. № 3 (30). С. 254–258.
7. Vaska S. C., Muralakar P., Arunkumar H. S., Shen-bagam R., Jeevitha D., Umesh Chimmalgi, Vinay T. V., Nagaraju M. Current trends in production and processing of fish oils & its chemical analytical techniques: an over-view. European Chemical Bulletin, 2023, vol. 12 (5), pp. 1705-1725. DOI:https://doi.org/10.48047/ecb/2023.12.si5a.049.
8. Akhmedova N. R., Levicheva O. I., Naumov V. A. Influence of liquid food products viscosity on lobe pump performance (case of pumping fish oil) // Vestnik of As-trakhan State Technical University. Series: Fishing indus-try. 2022. N. 3. P. 74–81. DOI:https://doi.org/10.24143/2073-5529-2022-3-74-81.
9. Насосы для рыбьего жира. URL: https://vpumpen.ru/po-produktam/ryibij-zhir?ysclid=m0ob0j01li481390044(дата обращения: 05.03.2024).
10. Балденко Д. Ф., Балденко Ф. Д., Гноевых А. Н. Одновинтовые гидравлические машины: моногр. в 2 т. М.: ИРЦ Газпром, 2005. Т. 1. Одновинтовые насосы. 488 с.
11. Bi H., Wu M., Zhang X. Design of parameters opti-mization system for crew pump well // Int. Journal of Simulation: Systems, Science and Technology. 2016. V. 17. N. 25. P. 11–16. DOI:https://doi.org/10.5013/IJSSST.a.17.25.01.
12. Yan D., Kovacevic A., Tang Q., Rane S., Zhang W. Numerical modelling of twin-screw pumps based on computational fluid dynamics // Proceedings of the Insti-tution of Mechanical Engineers, Part C: Journal of Mechanical Engineering Science. 2017. V. 231. N. 24. P. 4617–4634. DOI:https://doi.org/10.1177/0954406216670684.
13. Yin Y., Zhou C., Zhao F., Wang L., Ye Z., Jin J. Design and investigation on a novel piezoelectric screw pump // Smart Materials and Structures. 2020. V. 29. N. 8. DOI:https://doi.org/10.1088/1361-665X/ab98ec.
14. Wang Z., Shi H., Wang S., Wang Z., Hao M., Wang J. Study on the operating characteristic of disc seal single screw pump used in energy recovery systems // Int. Journal of Refrigeration. 2020. V. 118. P. 336–344. DOI:https://doi.org/10.1016/j.ijrefrig.2020.05.029.
15. Andrenko P., Rogovyi A., Hrechka I., Khovanskyi S., Svynarenko M. Characteristics improvement of laby-rinth screw pump using design modification in screw // Journal of Physics: Conference Series. 2021. V. 1741. DOI:https://doi.org/10.1088/1742-6596/1741/1/012024.
16. Наумов В. А. Оценка влияния вязкости жидких пищевых продуктов на нагрузочные характеристики одновинтовых насосов // Техника и технология пище-вых производств. 2021. Т. 51. № 2. С. 290–300. DOI:https://doi.org/10.21603/2074-9414-2021-2-290-300.
17. Sathivel S., Yin H., Prinyawiwatkul W., King J. M. Comparisons of chemical and physical properties of Catfish oils prepared from different extracting processes // Journal of Food Science. 2009. V. 74. Iss. 2. P. E70–E76.
18. Madlener K., Frey B., Ciezki H. K. Generalized Reynolds number for non-Newtonian fluids // Progress in Propulsion Physics. 2009. V. 1. P. 237 – 250.
19. Sathivel S., Prinyawiwatkul W., Negulescu I. I., King J. M., Basnayake B. F. A. Effects of purification process on rheological properties of Catfish oil // Journal of the American Oil Chemists' Society. 2003. V. 80. N. 8. P. 829–832.
20. Csizmadia P., Hos C. CFD-based estimation and experiments on the loss coefficient for Bingham and pow-er-law fluids through diffusers and elbows // Journal of Computers & Fluids. 2014. V. 99. P. 116–123.
21. Csizmadia P., Till S. The effect of rheology model of an activated sludge on to the predicted losses by an elbow // Periodica Polytechnica Mechanical Engineering. 2018. V. 62 (4). P. 305–311.
22. Atlas – Progressive cavity pump. URL: https://www.alphadynamic.eu/products/atlas-progressive-cavity-pump (дата обращения: 20.12.2023).
