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浙江大学学报(工学版)
Journal of ZheJiang University (Engineering Science)  2020, Vol. 54 Issue (6): 1240-1248    DOI: 10.3785/j.issn.1008-973X.2020.06.022
Mechanical Engineering     
Variable buoyancy system performance for profile buoy “Fuxing”
Yan-long ZHAO1,2,3(),Xing-fei LI1,2,3,Shao-bo YANG1,2,3,*(),Hong-yu LI3,4,Jia-yi XU1,2,3,Yue LIN5
1. State Key Laboratory of Precision Measurement Technology and Instruments, Tianjin University, Tianjin 300072, China
2. Pilot National Laboratory for Marine Science and Technology (Qingdao), Qingdao 266237, China
3. Qingdao Institute for Marine Technology of Tianjin University, Qingdao 266237, China
4. College of Ocean Science and Engineering, Shandong University of Science and Technology, Qingdao 266590, China
5. CCS Qingdao Branch, Qingdao 266071, China
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Abstract  

A mathematical model of piston pump inlet pressure was established to analyze the influence of the spring stiffness, pipeline diameter and ballast tank vacuum degree on the volume efficiency, based on the relationship between plunger pump inlet pressure and hydraulic oil saturation vapor pressure, in order to improve the pump volumetric efficiency under the special application condition of variable buoyancy system (VBS), of which the inner tank is in vacuum environment. Combined with AMESim software, the flow characteristics of oil discharge and oil return of VBS were analyzed emphatically. A test platform of VBS was built to verify the accuracy of simulation model and calculation results. Result show that it is prone to cavitation when the inlet pressure of the plunger pump is lower than the saturated vapor pressure of the hydraulic oil, which causes the volumetric efficiency of the plunger pump to decrease significantly. By adjusting the value range of spring stiffness, oil suction pipe diameter and ballast tank vacuum, etc., the inlet pressure can meet the design requirements, which helps to improve the volumetric efficiency of the plunger pump, to reduce the operating energy consumption of the profile buoy, thereby to improve the endurance of the profile buoy.

Key words： buoy      variable buoyancy system (VBS)      volumetric efficiency      inlet pressure      saturated vapor pressure      AMESim software     
Received: 13 May 2019      Published: 06 July 2020
CLC:  TH 137.7  
Corresponding Authors: Shao-bo YANG     E-mail: zhaoyanlong22@163.com;yangskyle@tju.edu.cn
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Yan-long ZHAO
Xing-fei LI
Shao-bo YANG
Hong-yu LI
Jia-yi XU
Yue LIN
Cite this article:

Yan-long ZHAO,Xing-fei LI,Shao-bo YANG,Hong-yu LI,Jia-yi XU,Yue LIN. Variable buoyancy system performance for profile buoy “Fuxing”. Journal of ZheJiang University (Engineering Science), 2020, 54(6): 1240-1248.

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http://www.zjujournals.com/eng/10.3785/j.issn.1008-973X.2020.06.022     OR     http://www.zjujournals.com/eng/Y2020/V54/I6/1240


剖面浮标“浮星”可变浮力系统性能研究

为了提高柱塞泵的容积效率，针对可变浮力系统（VBS）中内油箱处于真空环境下的特殊应用工况，基于柱塞泵进油口压力与液压油饱和蒸汽压的关系，建立柱塞泵进油口压力数学模型，分析弹簧刚度、吸油管路直径和压载舱真空度对柱塞泵容积效率的影响；结合AMESim软件，重点分析VBS排油和回油的流量特性；为了验证仿真模型和计算结果的准确性，搭建VBS性能测试平台. 结果表明：当柱塞泵进油口压力低于液压油饱和蒸汽压时，容易发生气穴现象，柱塞泵的容积效率会明显下降；通过调节弹簧刚度、吸油管路直径和压载舱真空度等参数的取值范围，使进油口压力满足设计要求，可以提高柱塞泵的容积效率，降低剖面浮标的运行能耗，从而提高剖面浮标的续航能力.


关键词： 浮标,  可变浮力系统 (VBS),  容积效率,  进油口压力,  饱和蒸汽压,  AMESim软件 
Fig.1 Schematic diagram for variable buoyancy system（VBS）of profile buoy
Fig.2 Schematic diagram for profile movement process of buoy
Fig.3 Structure diagram of inner cylinder with piston
Fig.4 Structure diagram of inner cylinder with bladder
Fig.5 Force analysis diagram for inlet pressure of plunger pump
几何形状 k1 几何形状 k1
90°弯头 0.20 圆滑入口 0.05
45°弯头 0.15 锐边出口 1.00
三通接头 0.90 圆滑出口 1.00
锐边入口 0.50 ? ?
Tab.1 Loss coefficients for different geometric elements
Fig.6 AMESim simulation model for buoyancy drive system of profile buoy
参数 符号 数值 单位
液压油密度 $\rho $ ${\rm{850}}$ ${\rm{ kg}}/{{\rm{m}}^{\rm{3}}}$
运动黏度 $v$ 10 ${\rm{m}}{{\rm{m}}^{\rm{2}}}/{\rm{s}}$
吸油管路长度 $l$ ${\rm{0}}{\rm{.3}}$ ${\rm{m}}$
回油管路长度 $l'$ ${\rm{0}}{\rm{.8}}$ ${\rm{m}}$
内油缸直径 ${D_0}$ ${\rm{102}}$ ${\rm{mm}}$
管路直径 ${D_1}$ ${\rm{3}}{\rm{.05}}$ ${\rm{mm}}$
活塞质量 $m$ ${\rm{0}}{\rm{.7}}$ ${\rm{kg}}$
摩擦力 ${F_{\rm{f}}}$ ${\rm{10}}$ ${\rm{N}}$
柱塞泵排量 vg $0.1$ ${\rm{mL}}/{\rm{r}}$
饱和蒸汽压 ${p_3}$ $ - {\rm{40}}$ ${\rm{kPa}}$
电机电压 $U$ ${\rm{24}}$ ${\rm{V}}$
电枢绕组电感 $L$ ${\rm{0}}{\rm{.082}}$ ${\rm{mH}}$
电枢绕组电阻 $R$ $0.299$ ${\rm{\Omega }}$
单向阀开启压力 ${p_4}$ ${\rm{0}}{\rm{.1}}$ ${\rm{MPa}}$
Tab.2 Parameter setting for simulation model of VBS
Fig.7 Change of plunger pump displacement with time under different vacuum degrees
Fig.8 Change of plunger pump inlet pressure with time under different vacuum degrees
Fig.9 Gas volume fraction in hydraulic oil under different vacuum degrees
Fig.10 Reynolds number of oil inlet line during oil discharge
Fig.11 Total return oil volume and pressure difference with ballast tank vacuum degree of −12.7 kPa
Fig.12 Change curve of piston pump torque and displacement with pressure
Fig.13 Variation of plunger pump displacement with time under different oil suction pipe diameters
Fig.14 Variation of plunger pump inlet pressure with time under different oil suction pipe diameters
设备名称 设备参数
溢流阀 型号：HIP-10RV，额定压力：68.9 MPa
流量计 型号： ${\rm{CX}} - {\rm{M5}} - {\rm{SS}}$
测量范围：5~1 000 mL
二位二通球阀 额定压力： ${\rm{68}}{\rm{.9\;MPa}}$
压力表 量程：0~69 MPa
Tab.3 Related parameters of VBS performance test platform equipment
Fig.15 Schematic diagram of test platform for performance of VBS of float
Fig.16 Physical drawing of test platform for performance of VBS of float
Fig.17 Test results comparison of plunger pump displacement under different vacuum conditions of ballast tanks
Fig.18 Comparison of test and simulation results of total return oil changing with time under ballast tank vacuum degree of −12.7 kPa
Fig.19 Piston pump displacement under different seawater pressure values
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