Optimization of the structure of water axial piston pump and cavitation of plunger cavity based on the Kriging model
Zegang Sun^{1} , Shide Xiao^{2} , Mingheng Xu^{3} , Wei Wei^{4}
^{1, 2, 3, 4}School of Mechanical Engineering, Southwest Jiaotong University, Chendu, 610031, P. R. China
^{1}School of Mechanical Engineering, Sichuan University of Science and Engineering, Zigong, 643000, P. R. China
^{2}Corresponding author
Journal of Vibroengineering, Vol. 18, Issue 4, 2016, p. 24602474.
https://doi.org/10.21595/jve.2016.16819
Received 14 January 2016; received in revised form 22 April 2016; accepted 20 May 2016; published 30 June 2016
JVE Conferences
The cavitation flow of axial piston pump was simulated by the FLUENT software. Simulation results show that 1) Plunger cavity cavitation degree increase nearly one time when the piston pump rotation rate increase from 1500 r/min to 3000 r/min; 2) The axial piston pump L shape throttling groove is more conductive to inhibiting cavitation of plunger cavity than the V shape; 3) The variation law which shows the influence of the thickness of cylinder kidney shape port on the cavitation of plunger cavity. This paper put forward the twoway inclined type cylinder barrel kidney shape port, which was beneficial to improve the selfsucking of the plunger cavity under high speed rotation and could inhibit the cavitation of plunger cavity. The Kriging agent model of has been established by taking the configuration parameters of oneway inclined cylinder kidney shape port as independent variables and the mean value of the gas volume fraction of plunger cavity as target function, based on the Kriging interpolation principle. The optimized structure of the oneway inclined type cylinder barrel kidney shape port is obtained through the Kriging agent model which is optimized by using improved genetic algorithm. The structure of the cylinder kidney shape port and the valve plate throttling grooves are obtained, which mostly inhibit the cavitation of plunger cavity with above analysis. The structure has a strong inhibitory on the plunger cavity cavitation through the simulation analysis and verification.
Keywords: water axial piston pump, cavitation, dynamic mesh, sliding mesh, twoway inclined type cylinder barrel kidney shape port, Kriging interpolation principle.
1. Introduction
Axial piston pump which has the advantages of high working pressure, high limit power and convenient variable adjustment, is widely used in the field of industrial hydraulic and walking hydraulic field. In recent years, with the increasing awareness of environmental protection, hydraulic transmission technology with water as the medium has been developed Huazhong University of Science and Technology, Zhejiang University and other institutes have been carried out the research work of the water hydraulic axial piston pump [1, 2].
Along with the development of industry, the working speed and pressure of the axial piston pump becomes higher than before. Compared with the hydraulic oil, water has the characteristics of high saturated vapor pressure and low solubility of air so the plunger cavity water axial piston pump prone to cavitation [3, 4].
At present, many scholars have carried out intensive study on the flow characteristics, pressure impact and cavitation of the axial piston pump, which has achieved some results. Kosodo [5] studied the pressureflow characteristics and cavitation of hydraulic pump and motor valve plate V groove of the hydraulic system through experiment, and putted forward that the direction of the flow, temperature, pressure and Reynolds coefficient exert greater impact on cavitation. Edge K. A. [6, 7] found that the pressure overshoot of the piston pump is much large than the calculation of the existing theoretical model, and pointed out the model of adding the inertia term of fluid acceleration in the decompression groove. He considered that the large slope triangle groove is conducive to reducing the pressure overshoot. W. Kollek [8] has simulated and studied the piston and cylinder of oblique axial piston pump, and then illustrated that the pump must occurred cavitation in the absorption area. They established the relationship between sound diagnosis signal and the cavitation, and putted forward conception of cavitation in hydraulic system of sound instrument detection. S. Gold [9] built the test platform with organic transparent pipe, and observed the cavitation of the entrance of piston pump by adjusting the inlet pressure and camera technology. The law of the internal pipeline bubble production and development can be clearly observed. Because the pipeline can’t withstand high pressure, the experiment only observed the low pressure zone of axial piston pump entrance. Zhou Hua [10] analyzed the mechanism of cavitation inception and outlet pressure ripple, and carried out the experimental study on cavitation inception characteristics of seawater hydraulic pump. Liu Xiaohong [11] put forward that the cavitation of the valve plate depends on not only the value of velocity and pressure, but also the direction of velocity. She also pointed out that the change of valve plate structure must change the velocity direction to reduce cavitation of the valve plate. ZHAI Jiang [12] have numerically simulated the internal cavitation flow of the water axial piston pump by CFD. Xu Bing [13] compared the flow ripple of axial piston pump with precompression volume with the flow ripple of axial piston pump without precompression volume by simulation and experimental means. Yuan Shihua [14] studied the dynamic in evolution and effects of gas phase in cavitation of axial piston pump. Shu Wang [15] putted forward that the valve plate design was a critical issue in addressing the cavitation or aeration phenomena in the axial piston pump. N. P. Mandal et al. [16] developed a methodology for designing a swashplate axial piston pump whose barrel kidney are wider than the bridges separating the kidney ports on the plate. Besides reducing pressure ripples and avoiding cavitation for minimizing the fluidborne noise, maximization of the pump discharge has also been considered in formulating an objective function to be minimized. S. Kumar et al. [17] put forward that to avoid cavitation, it is important to consider the inclusion of grooves at the piston stroke length and near to the piston pressure side.
Although domestic and foreign scholars have done some research on the axial piston pump cavitation, the literature that includes the impact of the cylinder barrel and valve plate structure of the axial piston pump on the plunger cavity cavitation is less. This paper takes a certain type of the water axial piston pump as research object and analyzes the impact of the cylinder barrel and valve plate structure on cavitation of plunger cavity. The model has taken account the compressibility of the fluid and gas. The content of this paper mainly includes several aspects: 1) Establishment of the finite element simulation model of axial piston pump. 2) Analysis of the impact of cylinder rotation speed on the plunger cavity cavitation. 3) Analysis of ‘V’ and ‘L’ shape throttling groove structure of valve plate influence on the plunger cavity cavitation. 4) Analysis and comparison of ordinary axial piston pump cylinder barrel kidney shape port, oneway incline kidney shape port and twoway incline kidney shape port influence on the plunger cavity cavitation. 5) The Kriging agent model of the structure parameters of oneway incline kidney shape port cylinder and value of gas volume fraction of plunger cavity is established, and the optimized structure is obtained by improved genetic algorithm. 6) The optimization structure of piston pump cylinder and valve plate which can inhibit the cavitation of the plunger cavity to the maximum are put forward according to the former analysis.
2. Establishment of simulation model
2.1. Research object
The research object of this paper is the water axial piston pump. Its structure is shown in Fig. 1. The angle of the swash plate is 15°. The cross angle $\alpha $ is 4°. The number of the piston $i$ is 9. The piston diameter is 21 mm. Piston distribution circle diameter is 81 mm. Rotation rate $n$ is 1500 r/min.
Fig. 1. Structural representation of axial piston pump
Fig. 2. Internal fluid in axial piston pump
2.2. Internal flow channel geometry model of axial piston pump
On the premise of no neglect of the leakage of the axial piston pump, the flow channel geometry model of axial piston pump is shown in Fig. 2. In this model, the position of valve plate, suction port and drainage port are fixed. The kidney shape port and plunger cavity rotate with the cylinder, and the volume of the plunger cavity changes with the piston movement. The structure of plunger cavity of axial piston pump, valve plate, and kidney shape port is shown in Fig. 3.
2.3. Mesh division
The axial piston pump is divided by the structure and unstructure grid due to its complex internal flow channel and its changeable size. The mesh is encrypted in small throttling groove, as shown in partial enlargement of Fig. 4. The grid consists of 168813 elements.
2.4. Boundary conditions
As it is shown in Fig. 4, nine plunger cavity of the cylinder barrel is rotated around with the $Z$ axis, and the movement speed of the piston is expressed as:
The pump inlet and outlet are set as pressure inlet and outlet respectively. The paper determined the values of inlet pressure and outlet pressure as 3.3E5 Pa and 5 MPa respectively. The saturated vapor pressure of water is 2367.8 Pa. The value of the gas volume fraction of pump inlet and outlet is zero. The compressibility of the liquid and gaseous fluid and the piston velocity are set through UDF by using the commercial fluent software and the mixture model, RNG $k$$\epsilon $ model, dynamic mesh and sliding mesh. The control equations were space dispersed by finite volume method and nonstaggered grid. The two order upwind scheme is adopted in turbulent kinetic energy term. The others adopt the first order upwind scheme. The time dispersion adopts two order full implicit schemes. The SIMPLE algorithm is used in velocity component in momentum equation and pressure coupling problem. Every iterative calculation accuracy is set as 10^{8}, and time step is set as 10^{4}.
Fig. 3. Valve plate and the plunger cavity structure
Fig. 4. Internal flow channel mesh division of axial piston pump
Fig. 5. Distribution contours of gas volume fraction of No. 1 plunger cavity
2.5. Cavitation process analysis of plunger cavity
According to the simulation model, the inlet pressure of axial piston pump is 1.01×10^{5} Pa and the outlet pressure is 3.0×10^{6} Pa. The simulation results are shown in Fig. 5. and Fig. 6.
Fig. 5 and Fig. 6 shows that the plunger cavity of water axial piston pump appears the cavitation when the plunger cavity sucks water. Due to the high rotation speed of the plunger cavity, the bubbles in the plunger cavity operated by means of centrifugal force are concentrated in the inner side. When piston cavity drains water, its pressure is high with no cavitation now. When the drainage is over, the plunger cavity passes through the bottom dead centre (BDC) and enters suction port. The pressure of plunger cavity fluid is greater than outlet pressure when the plunger cavity just contacts V shape throttling groove. The fluid in plunger cavity flows backward to outlet in an instant. At this time, the cavitation is not obvious. With the rotation of pump cylinder barrel, the piston moves with variable velocity along the axial, and the plunger cavity pressure drops. The gas in the fluid will precipitate when the fluid pressure in the plunger cavity is lower than the saturated vapor pressure of fluid or air separation pressure of fluid. At this time, the plunger cavity cavitation has been occurrence. The degree of plunger cavity cavitation is little at the beginning and end of drainage period. The degree of plunger cavity cavitation is serious at 0.028 second to 0.03 second this time. The plunger cavity cavitation is most serious especial at 0.0295 second.
Fig. 6. Curve chart of mean value of volume fraction of No. 1 plunger cavity
Fig. 7. Comparison of the mean value of volume fraction of plunger cavity with different rotating rate
3. Effect of cylinder rotation speed on cavitation of plunger cavity
The inlet pressure of the axial piston pump is 3.03×10^{5} Pa, and the outlet pressure is 5.0×10^{6} Pa. The cylinder barrel rotation rate is 1500 r/min and 3000 r/min. The thickness of cylinder barrel kidneyshape port is 11 millimeters, that is $H=$11 millimeters.
Fig. 7. shows that the gas volume fraction of the fluid in the plunger cavity significantly increases when the pump speed increases. It is indicated that the cavitation degree of the fluid in the plunger cavity increases when the axial piston pump rotation rate increases.
4. Analysis on the influence of valve plate throttling groove structure on the plunger cavity cavitation
4.1. V shaped and L shaped throttling groove flow area and hydraulic radius
Fig. 8 shows geometric sketch map of V and L shape throttling groove.
Calculation formula of the flow area and hydraulic radius of V shape throttling groove is expressed as follows:
Fig. 8. Geometric sketch map of V and L shape throttling groove
Calculation formula of the flow area and hydraulic radius of L shape throttling groove is express as follows:
The flow area toneup of V shape throttling groove is very small when the $x$ is small, but the flow area toneup of L shape throttling groove is large when the $x$ is smaller. Therefore, high speed axial piston pump with shape throttling groove is more appropriate.
4.2. Effect of V shape and L shape throttling grooves on the plunger cavity cavitation
The simulation analysis of the plunger cavity cavitation is carried out on the axial piston pump with V and L shape throttling groove of valve plate under the rotating speed of 1500 r/min and 3000 r/min. The simulation result is shown in Fig. 9. The high flow toneup performance of L shape throttling groove is not obvious when the rotation rate of the axial piston pump is low but it is very obvious when the rotation rate of the axial piston pump is high. Because L shape throttling groove has high flow toneup and the fluid which flow into the plunger cavity is increased, cavitation degree of the plunger cavity decreases significantly.
5. The influence of kidney shape port of cylinder structure on cavitation of plunger cavity
5.1. Kidney shape port of cylinder barrel structure
Fig. 10 shows kidney shape port of cylinder barrel structure. The kidney shape port is divided into three types including straight kidney shape, oneway inclined type kidney shape and twoway inclined type kidney shape. Table 1 is the structural parameters of the kidney shape port of cylinder barrel.
5.2. Influence of the inclined type kidney shape port structure of cylinder barrel on selfsucking property
5.2.1. Analysis on the selfsucking property of plunger cavity with
Fig. 11 (AA view in Fig. 10) shows the oneway inclined kidneyshape port. Because the kidneyshape port inclines certain angle relative to the $XY$ plane, the fluid in the kidneyshape port is influenced by centrifugal force when the cylinder rotates at high speed.
Fig. 9. Comparison of the mean value of gas volume fraction of No. 1 plunger cavity under different rotation rate and different throttling groove
Fig. 10. Kidneyshape port structure of cylinder barrel
Fluid press along the path is expressed as:
where $\mu $ is dynamic viscosity, $l$ is pipe length, $v$ is average flow velocity, $d$ is pipe diameter, for noncircular pipe with hydraulic diameter ${d}_{h}$ instead of $d$.
Table 1. Structural parameters of the cylinder barrel kidney shape port
Kidney shape port of cylinder barrel structure

${\delta}_{xy}$
_{}(°)

${\delta}_{xz}$ (°)

$H$ (mm)

Straight kidney shape

90

0

715

Oneway inclined kidney shape

6585

0

715

Twoway inclined kidney shape

6585

1014

715

$s=\left(\pi {r}_{2}^{2}\pi {r}_{1}^{2}\right)\frac{\phi}{360}+\pi {r}_{3}^{2},{r}_{m}=\left(\frac{{r}_{1}+{r}_{2}}{2}\right)+\frac{z}{\mathrm{t}\mathrm{a}\mathrm{n}{\delta}_{xy}},$
$d{F}_{c}=\rho s{r}_{m}{\omega}^{2}dz,d{F}^{\mathrm{\text{'}}}=d{F}_{c}\mathrm{c}\mathrm{o}\mathrm{s}{\delta}_{xy},$
where $dm$ is the quality of $dz$ segment fluid of cylinder kidneyshape port, $d{F}_{c}$ is centrifugal force of $dm$, $d{F}^{\text{'}}$ is the component force of $d{F}_{c}$ along axis of the cylinder kidneyshape port.
When the cylinder rotates at high speed, the component of centrifugal force of fluid along the axis of cylinder kidneyshape port is expressed as:
where $s$ is sectional area of cylinder barrel kidneyshape port.
When ${\delta}_{xy}$ is smaller, the centrifugal force of cylinder kidneyshape port fluid and the component force $F$ along the axis of cylinder kidneyshape port is higher. Therefore, selfsucking capacity of the plunger cavity is improved. When the height $H$ of cylinder kidneyshape port is higher and the ${\delta}_{xy}$ is smaller, the length $L$ of cylinder kidneyshape port is increased. Meanwhile, loss pressure of fluid along the way is increased and pressure of fluid in the plunger cavity is reduced, which promote the generation of cavitation. So the cavitation degree of plunger cavity is related to the parameter ${\delta}_{xy}$ and $H$ of cylinder barrel kidneyshape port.
Fig. 11. Centrifual force of oneway inclined kidneyshape port of cylinder
Fig. 12. Analysis on the influence of the fluid drainage of the cylinder kidneyshape port on the ${\delta}_{xz}$
5.2.2. Analysis on the selfsucking property of plunger cavity from
The oneway inclined cylinder kidneyshape port rotate ${\delta}_{xz}$ around $X$ axis, then the twoway inclined cylinder kidneyshape port is formed. Fig. 12 (BB view in Fig. 10) shows the influence of ${\delta}_{xz}$ on the selfsucking capacity of the plunger cavity.
In Fig. 12 $V$ is linear speed, ${V}_{2}$ is the tangential velocity of cylinder kidneyshape port fluid, ${V}_{2}=V$, ${V}_{1}$ is the velocity of fluid enter cylinder kidneyshape port, then:
From the seventh formula, the value of the ${\theta}_{1}$ is related to the ${V}_{1}$ and the $\omega $. The value of the ${V}_{1}$ is determined by $P$ and ${V}_{Z}$. ${V}_{Z}$ is piston movement velocity, and $P$ is inlet pressure of axial piston pump. When ${\theta}_{1}$ and 90° – ${\delta}_{xz}$ are similar or equal, the fluid in the cylinder kidneyshape port can avoid tangential strong vortex phenomenon, and reduce the flow resistance. Therefore, ${V}_{Z}$ is changeable when the axial piston pump is working, so ${V}_{1}$ also changeable. It is very difficult to makeθ_{1} and 90° – ${\delta}_{xz}$ completely equal.
5.3. Simulation analysis on the influence of the structure of cylinder kidneyshape port on the cavitation of the plunger cavity
Comprehensive the previous analysis, the structure parameters (such as $H$, ${\delta}_{xy}$, ${\delta}_{xz}$) of cylinder barrel have an effect on the self suction of the plunger cavity. The simulation analysis on the cavitation of the plunger cavity is carried out by using FLUENT software.
5.3.1. Influence of
The simulation analysis on the structure parameters of the cylinder kidneyshape port is described as follows
1) The values of $H$ range from 7 to 15 mm.
2) The value of ${\delta}_{xy}$ is 85°.
3) The value of ${\delta}_{xz}$ is 0°.
4) The value of rotation rate is 3000 r/min.
Fig. 13 shows that the maximum value of the gas volume fraction of the plunger cavity is larger as the value of $H$ increases, when the value of $H$ ranges from 7 to 15 mm. However, the maximum value of the gas volume fraction of the plunger cavity decreases as the value of $H$ increases when the value of $H$ exceeds 11 mm. It is because only the value of $H$ increases to a certain value as the value of ${\delta}_{xy}$ is large that the component of centrifugal force of fluid along the axis of cylinder barrel kidneyshape port can overcome the pressure loss along the side of cylinder barrel kidneyshape port.
Fig. 13. Comparison of the mean value of gas volume fraction of No. 1 plunger cavity under different $H$
Fig. 14. Comparison of the mean value of gas volume fraction of No. 1 plunger cavity under different ${\delta}_{xy}$
5.3.2. Influence of
The simulation analysis on the structure parameters of the cylinder kidneyshape port is described as follows:
1) The value of $H$ is 11 mm.
2) The value of ${\delta}_{xy}$ range from 65° to 85°.
3) The value of ${\delta}_{xz}$ is 0°.
4) The value of rotation rate is 3000 r/min.
Fig. 14 shows that when the gas volume fraction of the plunger cavity becomes smaller, the smaller the ${\delta}_{xy}$ is. It is shown that the selfsuction of the plunger cavity is enhanced by the centrifugal force of the cylinder barrel kidneyshape port fluid with high rotation and the cavitation of the plunger cavity is inhibited.
5.3.3. Influence of
The simulation analysis on the structure parameters of the cylinder kidneyshape port is described as follows:
1) The value of $H$ is 13 mm.
2) The value of ${\delta}_{xy}$ is 65°.
3) The values of ${\delta}_{xz}$ is 0°, 10°, 12°, 14°.
4) The value of rotation rate is 3000 r/min.
From the curve variation law of Fig. 15, it is found that the value of ${\delta}_{xz}$ has obvious effect on cavitation of plunger cavity. The time quantum that ranges from 0.01 second to 0.014 second is the period when the plunger cavity passes through the suction throttling groove. In this period when the value of ${\delta}_{xz}$ becomes greater, the gas volume fraction of plunger cavity is greater. Due to the increase of value of ${\delta}_{xz}$, the self suction of the plunger cavity becomes larger. At present the fluid pressure of the valve plate throttle groove drop sharply, and the cavitation is serious which is mainly caused by the small gain of valve plate throttling groove. In order to decrease the cavitation degree at this time, according to the results of the analysis in Section 4.2, the V shape throttling groove can be transformed into L shape throttling groove at high rotation rate.
Fig. 15. Comparison of the mean value of gas volume fraction of No. 1 plunger cavity under different ${\delta}_{xz}$
Fig. 16. Kriging agent model approximate surface
The time quantum that ranges from 0.01 second to 0.014 second is the period when the plunger cavity has passed through the suction throttling groove. The gas volume fraction of the plunger cavity at this time first decreases rapidly and then increases, which is caused by the rotation rate from being slow to fast. In this period, when ${\delta}_{xz}$ is not equal to 0, cavitation of the plunger cavity is more likely to be inhibited than when ${\delta}_{xz}$ is equals 0. When the value of ${\delta}_{xz}$ is equal to 10°, the increased gradient of the value of gas volume fraction is the smallest after 0.018 second. It is mainly because when the value of ${\delta}_{xz}$ is equal to 10°, the ${\theta}_{1}$ and 90° – ${\delta}_{xz}$ are best matched. Strong vortex phenomenon is reduced by the fluid in the cylinder kidney hole and the flow resistance is reduced as well.
6. Optimization study on the structure of the oneway inclined cylinder kidneyshape port
6.1. Basic principle of Kriging model
Kriging approximation model is a statistical foresting method which is widely used in mathematical geology based on stochastic processes. It can be used to optimization of regional variable, estimate of linear and unbiased interpolation. It has the statistical characteristics of smoothing effect and estimate of minimum variance. It has played an important role in linear geological statistics [1820].
The Kriging model assumes that the true relationship between the system response values and the independent variables can be expressed as follows:
where $y\left(x\right)$ is Kriging unknown model, $f\left(x\right)$ is Known function (return part) of $x\text{,}$$\beta $ is Corresponding undetermined parameter, $f{\left(x\right)}^{T}\beta $ is a deterministic part and called the deterministic drift, $z\left(x\right)$ is the error of random distribution and is a statistical process. Its mean value is 0 and the variance is not 0.
Take the Gauss function as correlation function ($R$), and that is:
The estimate of Kriging model in the experimental sample point estimate is:
where $m$ is sampling points, ${\theta}_{k}$ is the orthogonal correlation function of No. 13, $\beta $ is the Regression constant, $\widehat{\beta}$ is the estimated value of $\beta $, ${r}^{T}$ is the Correlation vector.
The likelihood function $L$ of the correlation function $R$ is defined as follows:
The least squares estimation of $\beta $ and $\sigma $ in the No. 15 formula is:
Thus, $\widehat{\beta}$ and $R$ can be determined for a certain sample space. The maximum likelihood method ${\theta}_{K}$ is:
The accuracy of predicted value $\widehat{y}\left(x\right)$ is determined by the distance between sample points and forecast point $X$. When the sample point is closer to the forecast point $X$, the error of the predicated value is smaller.
6.2. Establishment of Kriging agent model
Through simulation analysis above, it is found that the ${\theta}_{1}$ and 90° – ${\delta}_{xz}$ match best when the ${\delta}_{xz}$ equals 10°. At this moment, the cavitation degree of the plunger cavity is the smallest. At the same time, $H$ and ${\delta}_{xy}$ also affect the cavitation of the plunger cavity, but the $H$ and ${\delta}_{xy}$ have a certain correlation. Therefore, in this paper, the Kriging agent model is established using constant regression model by taking the parameters $H$ and ${\delta}_{xy}$ as independent variables and the gas volume fraction of plunger cavity as function value when the t equals 0.019 second. In this paper, the five level full factorial experimental design is used. Value of $H$ is 7, 9, 11, 13 and 15 mm. Value of ${\delta}_{xy}$ is 65°, 70°, 75°, 80° and 85°. The twentyfive structure models have been simulated and analyzed. The Kriging agent model is established by taking Gauss function as correlation function, and is shown in Fig. 16.
6.3. Optimization results of genetic algorithm (GA) and its simulation analysis
6.3.1. Genetic algorithm
GA is global, parallel, stochastic search methods, founded on Darwinian evolutionary principles. During the last decade GA has been applied in a variety of areas, with varying degrees of success within each. A significant contribution has been made in machine engineering. Commonly GA has been used to optimize both structure and parameter values for both controllers and plant models. It has also been applied to fault diagnosis, stability analysis, robot pathplanning and combinatorial problems. The proposed genetic algorithm can be performed by the following major steps:
Step 1. Generate the initial population.
Step 2. Calculate the fitness score and select two having the best scores.
Step 3. Perform crossover with rate of ${p}_{c}$ and mutation with the rate of ${p}_{m}$, and for reproduction of the new generation using the elitist selection method.
Step 4. Stop when the number of predefined iteration/computational time is reached.
6.3.2. Genetic algorithm operators
Now the genetic algorithm is applied to optimize the agent model. First, genetic operators and other parameters must be defined in the genetic algorithm, namely: population number, crossover with rate, mutation with rate, maximum number of generations (MUG), generation gap and variable interval. The paper determined the values of ${p}_{c}$ and ${p}_{m}$ as 0.9 and 0.7 respectively. The values of other parameters are shown in Table 2. The optimal solution of the Kriging agent model is shown in Fig. 17.
Table 2. The values of other parameters
Parameter

Population number

MUG

Generation gap

$H$ (mm)

${\delta}_{xy}$
_{}(°)

Value

60

400

0.9

715

6585

When $H$ is 14.87 mm, and ${\delta}_{xy}$ is 70.61°, the minimum target value of the gas volume fraction of the plunger cavity is 26.24 %.
Fig. 17. The change lines chart of the genetic iterative optimization and calculation
Fig. 18. Curve charts of gas volume fraction in piston cavity of optimized structure of axial piston pump
6.4. Establishment of optimization structure of cylinder kidneyshape port of piston pump and its simulation analysis
According to the result of genetic optimization calculation, the main structural parameters of the oneway inclined cylinder kidneyshape port are determined. The value of $H$ is 14.87 mm and the value of ${\delta}_{xy}$ is 70.61°. Simulation analysis of gas fraction of plunger cavity is shown by curve 1 in Fig. 18.
To further reduce the cavitation degree of plunger cavity, the optimized structure of oneway inclined cylinder kidneyshape port can be transformed into the twoway inclined cylinder kidneyshape port. According to the result of the analysis in section 4.3.3, the value of ${\delta}_{xz}$ is 10°, which is determined. Simulation analysis of gas fraction of plunger cavity is shown by curve 2 in Fig. 18.
Comparing curve 2 with curve 1, the cavitation of the plunger cavity has some improvement from 0.016 second to 0.02 second. But in the range of 0.01 second to 0.014 second, the cavitation degree of the plunger cavity increases. The selfsuction of the plunger cavity increases, which is mainly because of adopting twoway inclined cylinder kidneyshape port. However, a certain degree of air suction has occurred because the flow gain of the V shape throttling groove is small when the plunger cavity passes through the V shape throttling groove of valve plate. In order to improve the situation, with the analysis of section 4.2, the V shape throttling groove can be replaced by L shape throttling groove. Simulation analysis of gas fraction of plunger cavity is shown by curve 3 in Fig. 18. According to the change regulation of the three curves in Fig. 18, it is obvious that the axial piston pump structure corresponding to the third curve in Fig. 18 has obviously inhibition to the cavitation of the plunger cavity.
7. Conclusions
Through the simulation analysis and research of axial piston pump, the following conclusions have been reached as follows:
1) The cavitation degree in plunger cavity of water axial piston pump increases doubly with the increase of the rotation rate of cylinder.
2) The L shape throttling groove of valve plate has better flow gain the V shape throttling groove and has a certain inhibition for the cavitation of the plunger cavity.
3) The twoway inclined cylinder kidneyshape port can improve the selfsuction of plunger cavity and reduce the cavitation of plunger cavity.
4) The approximate function relationship between the gas volume fraction of the plunger cavity and the structural parameters of the oneway inclined cylinder kidneyshape port is established by the Kriging interpolation principle. The strong coupling relationship between the gas volume fraction of the plunger cavity and the structure parameters of axial piston pump is solved. The optimal structure of the twoway inclined cylinder kidneyshape port is obtained through the analysis. The value of main structural parameters of it is shown in Table 3. This structure is best for the cavitation inhibition of the plunger cavity.
Table 3. The optimal structural parameters of twoway inclined cylinder kidney shape port
${\delta}_{xy}$ (°)

${\delta}_{xz}$ (°)

$h$ (mm)

70.67

10

14.87

Acknowledgements
Project supported by the Major National Science and Technology Projects of China (No. 2010ZX04015011) and by the Science and Technology Project of Sichuan Province of China (No. 2010GZ0093).
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