9ＯＴＥＣ
Vol. 28（2023），9 ～ 18

Experimental investigation on the influence ofheaving and yawing on the heat transfer coefficientand pressure drop of the plate evaporator
Yi Chena, Zeen Zhanglib, Dan Huac*
a.b.c. Jiangsu Key Laboratory of Micro and Nano Heat Fluid Flow Technology and Energy Application, School ofEnvironmental Science and Engineering, Suzhou University of Science and Technology,
Suzhou, Jiangsu 215009, China

Abstract
Plate heat exchangers are widely used in energy systems. The offshore floating platform's ocean
thermal energy conversion (OTEC) system will be affected by the sea surface's wind, waves, tides, andcurrents, resulting in various motion postures. The additional inertia force brought by different motion
postures will change the heat transfer characteristics of the heat exchanger, among which yawing andheaving are representative. Therefore, this paper carries out an experimental study on the influence ofyawing and heaving format on the heat transfer coefficient and pressure drop of a herringbone corrugatedplate evaporator using a heat exchanger thermal performance testing system and a six-degree-of-freedom
platform. The experimental results show that both yawing and heaving formats have enhanced effects on
the heat exchange coefficient of the herringbone corrugated plate evaporator, and it is more evident in
the heaving format. The total heat transfer coefficients of the heat exchangers under different swaying
motion conditions are significantly improved compared with the land-based state, and the enhanced heattransfer ranges from 7.03% to 20.61%. The plate evaporator has sound resistance effects on the pressure
drop of the evaporator in both yawing and heaving formats. The "herringbone" corrugated plateevaporator has good resistance to the pressure drop of the evaporator for both bow yawing and heaving
format, and the pressure drop has no noticeable change compared with the stable working conditions inthese two motions.
Key words :澳OTEC, plate heat exchanger, yawing and heaving format, pressure drop, heat transfer.澳
Nomenclature𝛷𝛷𝑘𝑘quantity of heat(W)Heat transfer coefficient of microcell area(W/(m2·℃))

𝛥𝛥𝛥𝛥

Temperature difference of heat transfer between fluids(℃)

K

Average heat transfer coefficient(W/(m2·℃)

𝛥𝛥𝛥𝛥mThe log-mean temperature difference between fluids(℃)

𝑀𝑀𝑅𝑅

Mass flow of refrigerant(kg/s)

𝑑𝑑A

Microunit heat transfer area

𝒬𝒬𝑅𝑅

The heat absorbed by the refrigerant(W)𝛥𝛥ℎ𝑅𝑅

Enthalpy difference between refrigerant import and export(J/kg)

𝐺𝐺𝐿𝐿 

volume flow of hot water(m3/s)

𝑄𝑄𝐿𝐿

Heat release on the hot water side(W)_____________________________________________________________________________________* Date of Manuscript Acceptance 2023.12.28
E-mail of corresponding author: huadan@usts.edu.cn

10

Yi CHENA, Zeen ZHANGLIB and Dan HUAC

𝜌𝜌𝐿𝐿 

𝑐𝑐𝑝𝑝𝑝𝑝 

The specific heat capacity of hot water at constant pressure(J/(kg·K))

𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑖𝑖𝑖𝑖 Inlet temperature of hot water(℃)

𝑚𝑚𝑤𝑤,𝑡𝑡𝑡𝑡 澳entity of hot water(kg/m3)

Hot water side mass flow rate

𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑜𝑜𝑜𝑜𝑜𝑜 

outlet temperature of hot water(℃)

𝛥𝛥𝛥𝛥

thermal balance error(%)

𝑇𝑇𝑒𝑒 

Evaporation temperature(℃)

htotal heat transfer coefficient(℃)ℎ𝑟𝑟𝑟𝑟𝑟𝑟 heart side heat transfer coefficientɑyawing amplitude(°)

𝛽𝛽heaving amplitude(mm)1. Introduction
In recent years, the development and utilization of marine resources has become an essential strategy
for national economic development (Zhang C B,2023), and ocean thermal energy conversion hasreceived widespread attention as a marine renewable energy source. Ocean thermal energy conversion is
the primary way to utilize ocean temperature difference energy (Weimin Liu,2020). The ocean thermalenergy conversion involves a variety of thermal cycles, including the organic Rankine cycle, the Kalina
cycle, the Uehara cycle, etc. ( Fan C C,2023) . In these thermal cycles, the heat exchanger is one of thecritical thermal energy conversion components, and the herringbone corrugated plate heat exchanger has
the advantages of a high heat transfer coefficient, compact structure, and slight temperature difference atthe end, which is a standard heat exchanger element in the OTEC system. (Ji Zhang,2019 and Hu Z,2022)
The ocean thermal energy conversion set up on the floating platform at sea will be affected by thewind, waves, tides, and currents on the sea surface and generate a variety of motion format (Zhen
Tian,2020). The additional inertia force brought by different motions will change the two-phase flowheat transfer characteristics inside the heat exchanger (Chen Chong,2015), which in turn affects the
dynamic state of the system and threatens its safe and stable operation. Among all the ocean motion
format, yawing and heaving are the two motion format that account for a large proportion. Among them,yawing refers to the rotational motion of the ship's front part (bow) relative to the horizontal plane, andheaving format refers to the periodic vibration motion of the ship in the vertical direction in the water.
These two format may impact the performance of plate heat exchangers in ocean thermal energy
conversion systems (Jinghua Wei,2011). The reason may be that the ocean motion causes the medium on
both sides of the plate to form a complex flow pattern on the corrugated plate, resulting in the irregularpassage of the fluid through the corrugated plate, which affects the heat transfer and heat exchange
efficiency. At present, the experimental studies on the thermal performance of heat exchangers under
ocean motion conditions have focused more on casing or shell and tube heat exchangers under tilting andswaying formats, without involving the herringbone-shaped corrugated plates, and also lacked the ruleof change of the influence of yawing and heaving motion on the thermal performance of heat exchangers.
Based on the current research situation, this research simulates two kinds of motion postures ofyawing and heaving by using a six-degree-of-freedom platform through the heat exchanger thermal
performance testing system with R410A as the working fluids and experimentally researches the heattransfer characteristics of the herringbone corrugated plate evaporator with different flow rates of theExperimental investigation on the influence of heaving and yawing on the heat transfer coefficientand pressure drop of the plate evaporator

working fluids, yawing and heaving postures under different motion frequencies; and probes the change
rules of the two postures on the influence of the heat transfer characteristics. The change rule of theinfluence of the two formation the heat transfer characteristics is investigated

2. Method and theoretical analysis
2.1 Test setup and six-degree-of-freedom platform
To realize the determination of the heat transfer coefficient and pressure drop of the herringbone
corrugated plate evaporator, a test system was designed and constructed, which consists of an R410A
process circuit, a cold water circuit, and a hot water circuit, as shown in Fig. 1.

Figure 1(a) Heat exchanger thermal performance testing system

11

12

Yi CHENA, Zeen ZHANGLIB and Dan HUAC

Fig. 1 (b) Six-degree-of-freedom platform
The working fluid circuit consists of a tank, a plate heat exchanger, two coil heat exchangers, acentrifugal pump, an electric heater, and a test section. Fluid from the tank through the centrifugal pumpinto the preheating area, through the electric heater to ensure that the liquid is no longer in a supercooled
state and saturated state, and then the watery form of the mass into the test section, and then the mass ofthe fluid in the test section of the evaporator is heated to the superheated state, and then flow into thecondenser and the supercooled by which the cold fluid condensation to the supercooled state, and finally
flow back to the storage tank. Finally, it flows back to the storage tank. The 6-DOF (Six Degrees ofFreedom) motion platform can generate periodic single-degree-of-freedom motions or multiple-degreeof-freedom coupled motions, and the test section is connected by a high-pressure oil pipe to avoid thepossibility of damage to the pipeline during the motion and to prevent leakage of the work material.
2.2 Test section
To reflect the actual heat transfer performance of the "herringbone" corrugated plate heat exchanger
under ocean movement conditions, the plate heat exchanger in this test uses the vacuum brazing method,
and the material is 304 stainless steel. The structural parameters are determined according to therequirements of the heat exchanger in the actual ocean temperature difference power generation system.
The test section can be divided into mass, thermal fluid, and measurement. Work part to ensure that
R410A saturated liquid state into the heat exchanger, saturated gas state or superheated gas state out of
the heat exchanger to avoid uneven distribution of the two phases of the measurement error will be causedby the same time to ensure that the temperature of R410A into the heat exchanger to reach the test preset
temperature. The thermal fluid part needs to ensure that the thermal fluid entering the heat exchanger
during the test remains at the preset temperature of the test.
In the measurement part, the inlet and outlet of the work material and the inlet and outlet of the plate
heat exchanger thermal fluid are selected as the measurement points. The temperature and pressure of
the inlet and outlet of the working fluid side and the hot water measurement are measured by PT100 RTD

Experimental investigation on the influence of heaving and yawing on the heat transfer coefficientand pressure drop of the plate evaporator

and diffusion silicon manometer. During installation, liquid raw tape ensures the test system is sealed toprevent leakage. At the same time, all PT100 RTDs in the system are calibrated by a high-precisionrhodium-iron resistance thermometer before use, and the uncertainty of the calibrated PT100 RTDs is
within ±0.1℃. The instrument can directly measure the working fluid's temperature, pressure, andvolume flow rate. The working fluid's mass flow rate can be calculated by utilizing the fluid properties
in the NIST REFPROP database. The heat exchange capacity on the hot liquid side can be calculated
from the corresponding inlet and outlet temperatures of the hot liquid side, and the calculation of the heatexchange capacity of the hot fluid and the inlet and outlet temperatures of the working fluid side canobtain the heat transfer coefficient of the plate heat exchanger. Plate heat exchanger pressure drop can beobtained from the difference between the corresponding pressures of the import and export of theworking fluid side.
2.3 Test conditions
To quantitatively analyze the heat transfer performance of the herringbone corrugated plate heatexchanger under ocean motion conditions, the test operating conditions of the plate heat exchanger were
set up to simulate the ocean motion conditions, including the temperature, pressure, and volume flowrate of the thermal fluid side. R410A is selected as the work material according to the operation process
and operation conditions in the ocean temperature difference power generation. With low ozone depletion
potential and high refrigeration performance, it is widely used in various industrial and commercial
refrigeration equipment. R410A's density is usually between 1.2~1.5 g/cm³ under standard temperatureand pressure conditions. Its specific heat capacity is about 0.59~0.65 kJ/(kg-K). Its latent heat ofevaporation is about 260~280 kJ/kg.
2.4 Theoretical calculation of evaporative heat transfer coefficient
The theoretical basis for heat exchanger thermal measurements is the principle of thermal
equilibrium: thermal equilibrium between hot and cold fluids, i.e., the amount of heat absorbed andemitted.
The general form of the heat transfer equation:𝐹𝐹𝛷𝛷 −heat,W;𝛷𝛷 = ∫0 𝑘𝑘 𝛥𝛥𝛥𝛥𝛥𝛥A

𝑘𝑘—ℎ𝑒𝑒𝑒𝑒𝑒𝑒 transfer coefficient of any microcell area of the heat exchanger， W/(m2·℃)
𝛥𝛥𝛥𝛥—Temperature difference between the two fluids in this microcell area,℃

𝑑𝑑A—Micro-unit heat transfer area；

The following simplified heat transfer equation is usually used in practical engineering:Φ—-heat exchange,W;𝛷𝛷 = 𝐾𝐾𝐾𝐾𝐾𝐾𝑡𝑡𝑚𝑚

K—Average heat transfer coefficient over the entire heat exchanger area,W/(m2·℃)
Δtm—logarithmic mean temperature difference between the two fluids,℃

The following describes the calculation formula corresponding to the measured thermal
performance of the plate heat exchanger.
Heat absorption on the refrigerant side:
𝒬𝒬𝑅𝑅 = 𝑀𝑀R 𝛥𝛥ℎR

𝒬𝒬𝑅𝑅 —Heat absorbed by the refrigerant,W；

𝑀𝑀R —Mass flow rate of refrigerant,kg/s;

13

14

Yi CHENA, Zeen ZHANGLIB and Dan HUAC

𝛥𝛥ℎR —Enthalpy difference between refrigerant inlet and outlet,J/kg；

Water-side heat release:

𝑄𝑄𝐿𝐿 = 𝐺𝐺𝐿𝐿 𝜌𝜌𝐿𝐿 𝑐𝑐𝑝𝑝𝑝𝑝 (𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑖𝑖𝑖𝑖 − 𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑜𝑜𝑜𝑜𝑜𝑜 )𝑄𝑄𝐿𝐿 —heat release on the hot water side,W;
𝐺𝐺𝐿𝐿 —Volume flow rate of hot water,m3/s;𝜌𝜌𝐿𝐿 —Density of hot water,kg/m3;

cpL —-Specific heat capacity of hot water at constant pressure,J/(kg·K);

𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑖𝑖𝑖𝑖 —Hot water inlet temperature,℃；

𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑜𝑜𝑜𝑜𝑜𝑜 —Hot water outlet temperature,℃；

Relative error of heat balance:

𝛥𝛥𝛥𝛥 =(𝑄𝑄𝑅𝑅 − 𝑄𝑄𝐿𝐿 )× 100%𝑄𝑄𝐿𝐿

ΔQ—-Thermal balance error,%；𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅𝑅 heat absorption,W;

QL —heat release on the hot water side,W;

Log mean temperature difference:(𝑇𝑇𝑒𝑒 − 𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑜𝑜𝑜𝑜𝑜𝑜 ) − (𝑇𝑇𝑒𝑒 − 𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑜𝑜𝑜𝑜𝑜𝑜 )𝛥𝛥𝑡𝑡𝑚𝑚 =𝑇𝑇 − 𝑇𝑇ln 𝑇𝑇𝑒𝑒 − 𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑜𝑜𝑜𝑜𝑜𝑜
𝑒𝑒𝑤𝑤,𝑡𝑡𝑡𝑡,𝑜𝑜𝑜𝑜𝑜𝑜
Δt m —log mean temperature difference,℃；
Te —Evaporating temperature,℃；

𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑖𝑖𝑖𝑖 —Hot water inlet temperature,℃；

𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑜𝑜𝑜𝑜𝑜𝑜 —Hot water outlet temperature,℃；

The temperature difference in the plate heat exchanger is calculated using the logarithmic heattransfer temperature difference𝛥𝛥𝛥𝛥𝑚𝑚. As in the above equation because the heat transfer curve on the waterside of the plate heat exchanger is not linear. So, the logarithmic heat transfer temperature difference isan integral mean
Total heat transfer coefficient:ℎ=

𝒬𝒬𝐿𝐿(𝐴𝐴𝐴𝐴𝑡𝑡𝑚𝑚 )h—Total heat transfer coefficient, W/(m2·℃)；
𝒬𝒬L —heat release on the hot water side, W;
A—Heat exchange area,m2；

Δt m —blogmeantemperature difference,℃；

3 Uncertainty analysis
The direct errors generated by all the instrumentation used in this test are listed in Table 1.
Table 1 The direct errors generated by all the instrumentation
Instrument
uncertainty

Typology

Measurement range

Uncertainties

Experimental investigation on the influence of heaving and yawing on the heat transfer coefficientand pressure drop of the plate evaporator

instrument
temperature sensor
Pressure sensors

PT100-50~150℃
2%
Diffusion Silicon
0~2500kPa
0.6%
Manometer
Electromagnetic flow
0~5m3/h
0.5%
meter
flowmeter
Vortex Flow Meter
0~5m3/h
1.3%
At the same time, in a complex test system, the indirect error is affected by the theory on which it
is based, the number of instruments used, the length of time experienced, etc., and each increment in theprocess will increase the chance of introducing error. This test system's analysis of indirect mistakes isbased on the error transfer theory. The main indirect error of this test occurs in the two parts of the test
section: water-side heat transfer error and heat transfer coefficient error. The following formula can becalculated; the results are listed in Table 2.
Water-side heat transfer error in the test section:𝜉𝜉(𝑄𝑄𝐿𝐿 ) = √𝜉𝜉𝑚𝑚𝑤𝑤,𝑡𝑡𝑡𝑡
22𝑚𝑚𝑤𝑤,𝑡𝑡𝑡𝑡+22𝜉𝜉𝑃𝑃𝑃𝑃(𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑖𝑖𝑖𝑖 − 𝑇𝑇𝑤𝑤,𝑡𝑡𝑡𝑡,𝑜𝑜𝑜𝑜𝑜𝑜 )2

Predicted uncertainty of the water-side heat transfer coefficient: For the expected fate of the waterside heat transfer coefficient, it can generally be considered to be within +10%. Let α = Te − Tw,s,in ，
β = Te − Tw,t,out ，εα = √2 × ξ2PT ，εβ = √2 × ξ2PT 。

εβ 2
εα 2
𝜉𝜉(Δt m ) = √ε2α + ε2β + ( ) + ( )αβTotal heat transfer coefficient error for the test section.

ξ(h) = √ξ2Δtm + 2ξ2PT

Refrigerant side heat transfer coefficient error.

ξ(href ) = √ξ2Δtm + ξ2hTable 2 The main indirect error of this test
Uncertainty
Test Uncertainty Indirect Measurement
Parameters
Water-side heat transfer in the test section.𝑄𝑄𝐿𝐿±3.6%
Log-mean temperature difference.Δt m±4%
Total heat transfer coefficient of the test
±4.8%
section,hRefrigerant side heat transfer coefficient.ℎ𝑟𝑟𝑟𝑟𝑟𝑟±6.2%

4 Results and discussion

4.1 Influence of yawing format on heat transfer coefficientComparison of heat transfer coefficients under the conditions of constant mass flux of thermal fluidof 175 kg/(m2∙s), constant temperature of 25℃, mass flux of R410A on the mass side of the vessel of

15

16

Yi CHENA, Zeen ZHANGLIB and Dan HUAC

125-225 kg/(m2∙s), temperature of 10℃, yawing amplitude of 2.5°-7.5°, and yawing frequency of 0-1Hz
is shown in Fig. 2. Under different yawing conditions, the total heat transfer coefficient of the heatexchanger shows an overall trend of enhancement compared with the land-based state, and theenhancement is up to 10.24%. Under different yawing amplitudes, the change rule of frequency on theheat transfer coefficient tends to be the same; the enhanced heat transfer effect is significant at lower
frequencies and weakens at higher frequencies. Meanwhile, the influence of different yawing amplitude
on the heat transfer coefficient also shows a regular change; the peak value of the heat transfer coefficient
occurs at 0.4Hz when the yawing amplitude is 2.5°, and the peak value of the heat transfer coefficient
occurs at 0.2 Hz when the yawing amplitude is 5° and 7.5°. Thus, it can be judged that the heatexchanger's total heat transfer coefficient has an overall enhancement trend compared with the landbased condition. The enhancement is the largest at 10.24%. The peak value of the heat transfer coefficient
occurs at 0.2 Hz for 5° and 7.5° of the yawing amplitude. Thus, it can be judged that the optimal frequency
of enhanced heat transfer under yawing motion becomes lower with the increase in amplitude and isgenerally distributed in the low-frequency band. Compared with the land-based condition where the massflows and boils in a stable film between the plates, the yawing format adds the effect of rotating
centrifugal force to the flow of the group between the leaves, which disturbs the original stable flow of
the mass between the plates, speeds up the process of breaking up the liquid film, and then strengthens
the effect of heat transfer with the hot fluid; meanwhile, under the condition, the impact of the movement
frequency and amplitude of movement on the enhancement of heat transfer coefficient is similar, andthere is no noticeable difference. There is no significant change under the same volume flow rate for thepressure drop of the "herringbone" corrugated plate heat exchanger under yawing motion as shown in
Fig.3.

Fig. 2 Total heat transfer coefficients of heat exchangers with different frequencies in yawing format

Fig.3 Pressure drop of work material with different frequencies in yawing format
4.2 Effect of heaving format on heat transfer coefficient
The comparison of heat transfer coefficients under the conditions of constant thermal fluid mass flux ofExperimental investigation on the influence of heaving and yawing on the heat transfer coefficientand pressure drop of the plate evaporator

175 kg/(m2∙s), constant temperature of 25°C, mass flux of R410A of the vessel of 125-225 kg/(m2∙s),temperature of 10°C, heaving amplitude of 50 mm to 100 mm, and heaving frequency of 0.2-1 Hz are
shown in Fig.4. The total heat transfer coefficients of the heat exchangers under different heaving motion
conditions are significantly improved compared with the land-based state, and the enhanced heat transfer
ranges from 7.03% to 20.61%. Compared with the heat transfer coefficient in the heaving motion format,
the heat transfer coefficient under the same mass flow rate can be increased up to 13.66% as shown in
Fig.4. In the heaving format, the heat transfer coefficient increases with the increase of heaving amplitude,
and the effect of frequency on the heat transfer coefficient is similar to that of the yawing motion
condition, with significant enhancement of heat transfer effect at a lower frequency and weakening ofenhancement of heat transfer effect at a higher frequency. Compared with the land-based state in which
the work material is boiling in a stable membrane flow between the plates, the heaving format adds abias force to the flow of the work material between the leaves, which disturbs the original steady flow of
the work material between the plates, accelerates the process of liquid film breakup, and then strengthens
the effect of heat transfer with the hot fluid; the pressure drop of the herringbone plate heat exchanger inthis format is the same as that in the yawing motion format as shown in Fig.5.

Fig.4. Total heat transfer coefficient of the heat exchanger at different frequencies in heaving format

Fig.5. Pressure drop of working fluid at different frequencies in heaving format
Yawing and heaving format in this test have enhanced heat transfer effects on the "herringbone"corrugated plate heat exchanger. There is no significant difference between the effect of motion frequency
and motion amplitude on the heat transfer coefficient in yawing motion. In contrast, the effect of motion
amplitude on the heat exchanger's enhanced heat transfer is significantly higher than that of motion
frequency on the heat exchanger in heaving format. The reason may be as follows. The reason may lie
in compared with the land-based condition where the working fluid is boiling in a stable membrane flow
between the plates, the addition of a specific motion format disrupts the stable flow of the work material
between the plates, and then the process of boiling into a film is destroyed, the liquid film is broken under
the action of the additional inertial force brought about by the motion, which strengthens the effect of

17

18

Yi CHENA, Zeen ZHANGLIB and Dan HUAC

heat transfer with the hot fluid; and the different motion format play a different role in the influence ofthe process, and therefore, bring different strengthening effects. The different motion postures havedifferent effects on this process, bringing different intensification effects. In this experiment, the twodegrees of freedom motions have no significant effect on the pressure drop of the herringbone corrugatedplate heat exchanger

5 Conclusion
In this paper, a thermal performance test platform for heat and mass exchange equipment under
oceanic motion conditions is designed and constructed, and the thermal performance of the herringbone
corrugated plate evaporator is tested under the yawing and heaving with R410A as the working fluid andherringbone corrugated plate evaporator as the research object, and the following conclusions are drawn:(1) Both yawing and heaving motions reinforce the heat transfer coefficient of the herringbone corrugatedplate evaporator, which is more evident in the heaving motion.
(2) The herringbone corrugated plate evaporator has excellent resistance to the pressure drop of theevaporator for both yawing and heaving formats, and there is no significant change in the pressure dropin these two format compared with the stable condition.
(3) In this paper, only the thermal performance of the herringbone corrugated plate evaporator under thetwo format of yawing and heaving has been experimentally investigated. The thermal performance
characteristics of herringbone corrugated plate evaporator under other motion conditions will be exploredin the future.

Acknowledgment

The authors thank the FY2023 Joint Research Task of Ocean Energy of Institute of Ocean Energy

Reference
Zhang C B, Wu Z, Wang J D, Ding C, Gao T Y., Chen Y P.Thermodynamic performance of a radialinflow turbine for ocean thermal energy conversion using ammonia[J].Renewable Energy, 2023, 202:
907-920.
Weimin Liu, Xiaojian Xu , Fengyun Chen , Yanjun Liu , Shizhen Li , Lei Liu.A review of research on
the closed thermodynamic cycles of ocean thermal energy conversion [J]. Renewable and Sustainable
Energy Reviews, 2020, 119: 109581.
Fan C C, Wu Z, Wang J D, Chen Y P, Zhang C B. Thermodynamic process control of ocean thermalenergy conversion[J].Renewable Energy, 2023, 210: 810-821.
Ji Zhang, Xiaowei Zhu, Maria E. Mondejar, Fredrik Haglind.A review of heat transfer enhancement
techniques in plate heat exchangers[J]. Renewable and Sustainable Energy Reviews, 2019, 101: 305-328.
Hu Z, Wan Y R, Zhang C B, Chen Y P. Compression-assisted absorption refrigeration using ocean
thermal energy[J].Renewable Energy, 2022, 186: 755-768.
Zhen Tian, Bo Gu, Yuan Zhang , Wenzhong Gao . Flow boiling heat transfer under marine motions: A
comprehensive review[J]. Annals of Nuclear Energy, 2020, 143: 107455.
Chen Chong, Gao Pu-zhen, Tan Si-chao, Huang Dong .Effects of rolling motion on thermal–hydrauliccharacteristics of boiling flow in rectangular narrow channel[J]. Annals of Nuclear Energy, 2015, 76:
504-513.
Jinghua Wei, Liang-ming Pana, De-qi Chena, Hui Zhang, Jian-jun Xu, Yan-ping Huang .Numericalsimulation of bubble behaviors in subcooled flow boiling under swing motion[J]. Nuclear Engineeringand Design, 2011, 241(8): 2898-2908.
澳