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
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.
Fig.1Schematic diagram for variable buoyancy system（VBS）of profile buoy
Fig.2Schematic diagram for profile movement process of buoy
Fig.3Structure diagram of inner cylinder with piston
Fig.4Structure diagram of inner cylinder with bladder
Fig.5Force 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.1Loss coefficients for different geometric elements
Fig.6AMESim 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.2Parameter setting for simulation model of VBS
Fig.7Change of plunger pump displacement with time under different vacuum degrees
Fig.8Change of plunger pump inlet pressure with time under different vacuum degrees
Fig.9Gas volume fraction in hydraulic oil under different vacuum degrees
Fig.10Reynolds number of oil inlet line during oil discharge
Fig.11Total return oil volume and pressure difference with ballast tank vacuum degree of −12.7 kPa
Fig.12Change curve of piston pump torque and displacement with pressure
Fig.13Variation of plunger pump displacement with time under different oil suction pipe diameters
Fig.14Variation 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.3Related parameters of VBS performance test platform equipment
Fig.15Schematic diagram of test platform for performance of VBS of float
Fig.16Physical drawing of test platform for performance of VBS of float
Fig.17Test results comparison of plunger pump displacement under different vacuum conditions of ballast tanks
Fig.18Comparison of test and simulation results of total return oil changing with time under ballast tank vacuum degree of −12.7 kPa
Fig.19Piston pump displacement under different seawater pressure values
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