# Research on Distribution of Flow Field and Simulation of Working Pulsation Based on Rotating-Sleeve Distributing-Flow System

Authors: Yanjun Zhang; Hongxin Zhang; Jingzhou Yang; Qinghai Zhao; Xiaotian Jiang; Qianchang Cheng; Qingsong Hua
Journal: Modelling and Simulation in Engineering
 (2017)

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## Abstract

To solve problems of leakage, vibration, and noise caused by disorders of flow field distribution and working pulsation in the rotating-sleeve distributing-flow system, governing equations of plunger and rotating sleeve and computational fluid dynamics (CFD) model are developed through sliding mesh and dynamic mesh technology to simulate flow field and working pulsation. Simulation results show that the following issues exist: obviously periodic fluctuation and sharp corner in flow pulsation, backward flow when fluid is transformed between discharge and suction, and serious turbulence and large loss in kinetic energy around the damping groove in transitional movements. Pressure in the pump chamber rapidly rises to 2.2 MPa involving over 10% more than nominal pressure when the plunger is at the Top Dead Center (TDC) considering changes about damping groove’s position and flow area in two transitional movements. Shortly pressure overshoot gradually decreases to a normal condition with increasing flow area. Similarly, pressure in the pump chamber instantaneously drops to a saturated vapor pressure −98.9 KPa when the plunger is at the Bottom Dead Center (BDC). With increasing flow area the overshoot gradually increases to the normal condition. This research provides foundations for investigating flow field characteristic and structure optimization of rotating-sleeve distributing-flow system.


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## Body

## 1. Introduction

A distributing-flow system, the most important component of hydraulic system, is widely used in the fluid power industry because of robustness, controllability, and wide operating range. However, the distributing-flow system controlled flow by valves has many disadvantages including bulk mass, large pressure loss, noise, and going against high frequency, which can easily cause noise and vibration on account of flow pulsation [1]. To solve these issues, the novel rotating-sleeve distributing-flow system is proposed which uses reciprocating motion of plunger and single-track rotation of rotating sleeve to achieve distribution functions. It has reliable seal, high efficiency, and little impact from working frequency. To further improve its performance, the flow characteristics of rotating-sleeve distributing-flow system could be theoretically investigated; then the system efficiently reduces damage to the pump, such as undesirable noise, vibration, and cavitation even reducing working reliability of the pump [2–4].Flow ripple, a significant characteristic of piston pump, is closely relevant with the pressure fluctuation, backward flow, and noise of inner fluid. Noises in pump can be effectively reduced by taking factors influencing the flow ripple into account and focusing on flow ripple in the process through structure optimization [5]. Dhananchezhiyan and Hiremath [6] reported that the flow ripple is associated with pressure pulsation in various drive frequencies of micro pumps. Hence, intensive studies of the flow ripple and the pressure pulsations are necessary for better understanding the flow process [7].Recently, various analytic and simulative methods have been extensively studied on distribution of flow field and working pulsation. Particularly, the CFD simulation is generally utilized in many fluid field and hydraulic researches. Luo et al. [8] developed an adiabatic dehumidifier model using CFD technology and the interior heat and mass transfer processes were then simulated. Ma et al. [9] utilized a new CFD model with user defined function to simulate pump’s fluid characteristic and predict the flow ripple. At the same time, the flow ripple was tested under different working parameters such as rotation speed and working pressure. Delele et al. [10] conducted research on CFD model based on an Eulerian-Eulerian multiphase which can predict the fluid flow profile and study the effects of drum rotational speed. In addition, they used experimental results of particle and fluid velocities and residence time to verify the model simulation.The slide mesh and dynamics grid technology have been continually employed in CFD model to improve its simulation functions and apply varied motions into the model flexibly. Wang [11] utilized the dynamics CFD model to simulate cavitation of axial piston pump, which uses compressible fluid pump model with nine pistons. Guo et al. [12] studied the sliding mesh method of Fluent® to simulate the dynamic behavior in the course of ball valve closure. In addition, Vitagliano et al. [13] ran a slide mesh generated in zones of the flow field and connected with sliding boundaries under different rotation speed conditions to simulate unsteady flows with surfaces in relative motion.Fortunately, some researchers have found effective ways to reduce working pulsation to decrease noise. Lee et al. [14, 15] investigated the computed time-accurate pressure field and the loss generation process to establish the causal link to the induced flow ripple in the turbine system. Alves et al. [16] found that combining CFD modeling and analytical techniques is a great way to predict the oil flow rate in the eccentric-tube centrifugal oil pumping system. The research group led by Palmberg set a precompression volume in valve plate between the discharged kidney slot and sucked kidney slot [17]. They found that small precompression volume can amazingly lessen enormous problems of noise, pulsation, and hydraulic impact [18, 19]. And an axial piston pump’s valve plate which adopts a prepressurization fluid path consisting of a damping hole, a buffer chamber, and an orifice can reduce flow ripple to some extent [20].This paper aims to reduce vibration and noise by developing a novel rotating-sleeve distributing-flow system and analyzing the relationship between turbulence energy, velocity, and working pulsation through CFD simulation. In addition, the influences with respect to backward flow, flow pulsation, and pressure fluctuation are investigated. A complete simulation model with relevant parameters have been established and flow characteristics can be explicitly described. Furthermore, this work provides theoretical foundation for structure optimization of distributing-flow system and performance improvement.


## 2. Operating Principle of Rotating-Sleeve Distributing-Flow System

In this section, a novel rotating-sleeve distributing-flow system is developed and analyzed. The plunger pulled by the crank-link mechanism achieves coupled reciprocating movement and then uses drive pin to transmit force into rotating sleeve along the cam groove pathway in unidirectional rotating movement. The drive pin moves while rolling with the cam groove molded line obtained by fitting linear equation through quadratic differential, rotating angle of rotating sleeve, and crank angle. Figure1 indicates the operating principle and components of rotating-sleeve distributing-flow system for mass flow with high frequency and efficiency.Figure 1
Structure principle of rotating-sleeve distributing-flow system.(1) Cam groove; (2) loading chamber; (3) inlet; (4) valve port; (5) pump chamber; (6) damping groove; (7) plunger; (8) blind flange; (9) pump body; (10) collecting chamber; (11) outlet; (12) drive pin; (13) compression spring; (14) rotating sleeve.In this system, there are two major movements: axial reciprocating movement of the plunger and unidirectional rotating movement of rotating sleeve. The plunger finishes reciprocating movements powered by the crankshaft and connecting rod mechanism via a connector cross slider. The displacement of plunger in reciprocating motion is formulated as follows:(1)x=r1-cos⁡φ+λ2sin2⁡φ,where r is the radius of bent axle, φ is crank angle about the crankshaft and connecting rod mechanism, λ=r/l is the ratio of crank and connecting link, and l is link length.Due toφ=ωt, the derivative of the displacement of plunger x with respect to the time t can be expressed as follows:(2)u=r·ω·sin⁡φ+λ2sin⁡2φ,where ω is angular velocity of bent axle.Angular velocity and acceleration of rotating sleeve have no obvious phase step and inflection point when sine molded line is selected for cam groove. Therefore, the relationship between the cam groove’s axial displacement and rotating-sleeve angle is given as follows:(3)zθ=S21-cos⁡θ0≤θ≤π,where S is plunger stroke and θ is the rotating-sleeve angle rotating around the central axis.Substituting (1) into (3), the rotating-sleeve angle θ with respect to crank angle φ is obtained as follows:(4)θ=arccos⁡cos⁡φ-λ2sin2⁡φ,0≤φ≤π2π-arccos⁡cos⁡φ-λ2sin2⁡φ,π≤φ≤2π.The angular velocity of rotating sleeve by taking the derivative oft in (3) can be expressed as follows: (5)ωt=±ω1-C02·sin⁡φ+λ2sin⁡2φ,where ωt is a positive number during 0≤φ<π and ωt is a negative number during π≤φ<2π and C0=cos⁡φ-0.5λsin2⁡φ.


## 3. Models and Methods

### 3.1. Fluid Model

In light of structure and operating principle of rotating-sleeve distributing-flow system, the fluid model is established as shown in Figure2, in which the model indicates the main components with loading chamber, inlet, pump chamber, collecting chamber, outlet, and rotating sleeve.Figure 2
Fluid model of rotating-sleeve distributing-flow system.(1) Loading chamber; (2) inlet; (3) pump chamber; (4) collecting chamber; (5) outlet; (6) valve port.In this paper, the fluid model is simulated and analyzed by fluid simulation software Fluent®. The motions of plunger and rotating sleeve are defined in fluid model using Users Defined Function. Standardk-ε turbulence model and SIMPLE arithmetic are applied into simulation settings. Technologies of sliding mesh and dynamic mesh are also utilized in the fluid model according to its specific motion characteristics. The model parameters and boundary conditions are defined in Table 1.Table 1
The parameters of distributing-flow system.
Parameters
Value
Symbol/unit
The radius of bent axle
0.03
m
The ratio of crank and connecting link
0.25
/
Crankshaft speed
150
n/(r/min)
Water density
998
kg/m3
Water viscosity
0.001003
Pa/s−1
Inlet pressure
0.1
MPa
Outlet pressure
2
MPa
Saturated vapor pressure
2339
Pa
Time step
0.001
S


### 3.2. Cavitation Model

The cavitation model is based on the flow equation Navier-Stokes with variable density and standard viscosity in hydromechanics. In this paper, taking the viscidity and turbulence into consideration and gas-liquid two-phase flow as the object of study, the transmission equation considering the content of gaseous mass is given as follows [21–24]: (6)∂∂tρf+∇·ρV→f=∇·Γ∇f+Re+Rc,where ρ is average density of gas-liquid mixture, f is gaseous mass content, Re and Rc denote velocity of bubble in generation and disappearance, respectively, V→ denotes average velocity of gaseous phase in two-dimensional flow, and Г denotes effective transmission efficiency.Based on the bubble dynamic equation of Rayleigh-Plesset, the bubble dynamics can be described by the variation of bubble radius under the surface tension term and the second derivative term in the equation neglected as follows:(7)dRBdt=2pv-p3ρlsgn⁡pv-p1ρ=fρv+1-fρlpv=psat+pturb,where RB is bubble radius, p is pressure, pv is the critical pressure of gas, psat is saturation pressure of gas, pturb is the pressure caused by turbulence, ρv is gaseous density, and ρl is average fluid density.Combining transmission equation of mass with the equation of continuity, the relationship of density in mixture and volume fraction is described as follows:(8)dρdt=ρv-ρldαdt,where α is the gas volume fraction.If the bubble numbers aren in unit volume, the gas volume fraction with respect to bubble radius can be expressed as follows:(9)α=4πnRB33.Substituting (9) into (8), the relationship of density in mixture and bubble dynamic is obtained as follows:(10)dρdt=ρv-ρl36πnα23dRBdt.According to the above equations, the velocity of bubble in generation and disappearance can be described, respectively, as follows:(11)Rc=3αρvρlRBρ2pv-p3ρlRe=31-αρvρlRBρ2pv-p3ρl.The gas volume fraction is proportional to average velocity and average velocity can be denoted by turbulence energy. When the surface tension coefficient of bubble is introduced, the velocity of bubble in generation and disappearance also can be described, respectively, as follows:(12)Rc=Ccfρvρlσ2Kpv-p3ρlRe=Ce1-fρvρlσ2Kpv-p3ρl,where Cc and Ce denote empirical constant, respectively, Cc=0.02, Ce=0.01, and σ is the surface tension coefficient of bubble.


### 3.3. Turbulence Model

Turbulence energy represents turbulent fluctuation and directly reflects dissipation and stability of fluid flow. If turbulence energy is larger in some areas, these areas will have more loss of kinetic energy and become more unstable [16]. The standard k-ε turbulence modelbased on Reynolds Average Navier-Stokes equation is applied in our simulation and dissipation rate of turbulence energy defined as follows [22, 23]:(13)ε=μρ∂μt′∂xk∂μi′∂xk¯,where turbulence viscosity μt is the function of fundamental unknown quantity Turbulent Kinetic Energy k and dissipation rate ε and is expressed as follows:(14)μt=ρCμk2ε,where k and ε are fundamental unknown quantities in standard k-ε model, respectively. For incompressible fluid, the corresponding transport equations are given as(15)∂ρk∂t+∂ρkμi∂xi=∂∂xjμ+μtσk∂k∂xj+Gk-ρε∂ρε∂t+∂ρεμi∂xi=∂∂xjμ+μtσk∂ε∂xj+C1εkGk-C2ερε2k,where Gk is the generation of turbulence energy occurred by average velocity gradient and is defined as(16)Gk=μt∂μi∂xj+∂μj∂xi∂μi∂xj,where C1ε, C2ε, and Cμ are empirical constants, respectively, C1ε=1.44, C2ε=1.92, Cμ=0.09, σk and σε are Prandtl values, respectively, corresponding to turbulence energy and dissipation rate, σk=1.0, and σε=1.3.


## 3.1. Fluid Model

In light of structure and operating principle of rotating-sleeve distributing-flow system, the fluid model is established as shown in Figure2, in which the model indicates the main components with loading chamber, inlet, pump chamber, collecting chamber, outlet, and rotating sleeve.Figure 2
Fluid model of rotating-sleeve distributing-flow system.(1) Loading chamber; (2) inlet; (3) pump chamber; (4) collecting chamber; (5) outlet; (6) valve port.In this paper, the fluid model is simulated and analyzed by fluid simulation software Fluent®. The motions of plunger and rotating sleeve are defined in fluid model using Users Defined Function. Standardk-ε turbulence model and SIMPLE arithmetic are applied into simulation settings. Technologies of sliding mesh and dynamic mesh are also utilized in the fluid model according to its specific motion characteristics. The model parameters and boundary conditions are defined in Table 1.Table 1
The parameters of distributing-flow system.
Parameters
Value
Symbol/unit
The radius of bent axle
0.03
m
The ratio of crank and connecting link
0.25
/
Crankshaft speed
150
n/(r/min)
Water density
998
kg/m3
Water viscosity
0.001003
Pa/s−1
Inlet pressure
0.1
MPa
Outlet pressure
2
MPa
Saturated vapor pressure
2339
Pa
Time step
0.001
S


## 3.2. Cavitation Model

The cavitation model is based on the flow equation Navier-Stokes with variable density and standard viscosity in hydromechanics. In this paper, taking the viscidity and turbulence into consideration and gas-liquid two-phase flow as the object of study, the transmission equation considering the content of gaseous mass is given as follows [21–24]: (6)∂∂tρf+∇·ρV→f=∇·Γ∇f+Re+Rc,where ρ is average density of gas-liquid mixture, f is gaseous mass content, Re and Rc denote velocity of bubble in generation and disappearance, respectively, V→ denotes average velocity of gaseous phase in two-dimensional flow, and Г denotes effective transmission efficiency.Based on the bubble dynamic equation of Rayleigh-Plesset, the bubble dynamics can be described by the variation of bubble radius under the surface tension term and the second derivative term in the equation neglected as follows:(7)dRBdt=2pv-p3ρlsgn⁡pv-p1ρ=fρv+1-fρlpv=psat+pturb,where RB is bubble radius, p is pressure, pv is the critical pressure of gas, psat is saturation pressure of gas, pturb is the pressure caused by turbulence, ρv is gaseous density, and ρl is average fluid density.Combining transmission equation of mass with the equation of continuity, the relationship of density in mixture and volume fraction is described as follows:(8)dρdt=ρv-ρldαdt,where α is the gas volume fraction.If the bubble numbers aren in unit volume, the gas volume fraction with respect to bubble radius can be expressed as follows:(9)α=4πnRB33.Substituting (9) into (8), the relationship of density in mixture and bubble dynamic is obtained as follows:(10)dρdt=ρv-ρl36πnα23dRBdt.According to the above equations, the velocity of bubble in generation and disappearance can be described, respectively, as follows:(11)Rc=3αρvρlRBρ2pv-p3ρlRe=31-αρvρlRBρ2pv-p3ρl.The gas volume fraction is proportional to average velocity and average velocity can be denoted by turbulence energy. When the surface tension coefficient of bubble is introduced, the velocity of bubble in generation and disappearance also can be described, respectively, as follows:(12)Rc=Ccfρvρlσ2Kpv-p3ρlRe=Ce1-fρvρlσ2Kpv-p3ρl,where Cc and Ce denote empirical constant, respectively, Cc=0.02, Ce=0.01, and σ is the surface tension coefficient of bubble.


## 3.3. Turbulence Model

Turbulence energy represents turbulent fluctuation and directly reflects dissipation and stability of fluid flow. If turbulence energy is larger in some areas, these areas will have more loss of kinetic energy and become more unstable [16]. The standard k-ε turbulence modelbased on Reynolds Average Navier-Stokes equation is applied in our simulation and dissipation rate of turbulence energy defined as follows [22, 23]:(13)ε=μρ∂μt′∂xk∂μi′∂xk¯,where turbulence viscosity μt is the function of fundamental unknown quantity Turbulent Kinetic Energy k and dissipation rate ε and is expressed as follows:(14)μt=ρCμk2ε,where k and ε are fundamental unknown quantities in standard k-ε model, respectively. For incompressible fluid, the corresponding transport equations are given as(15)∂ρk∂t+∂ρkμi∂xi=∂∂xjμ+μtσk∂k∂xj+Gk-ρε∂ρε∂t+∂ρεμi∂xi=∂∂xjμ+μtσk∂ε∂xj+C1εkGk-C2ερε2k,where Gk is the generation of turbulence energy occurred by average velocity gradient and is defined as(16)Gk=μt∂μi∂xj+∂μj∂xi∂μi∂xj,where C1ε, C2ε, and Cμ are empirical constants, respectively, C1ε=1.44, C2ε=1.92, Cμ=0.09, σk and σε are Prandtl values, respectively, corresponding to turbulence energy and dissipation rate, σk=1.0, and σε=1.3.


## 4. Results and Discussion

### 4.1. Distribution of Turbulence Energy

The distribution of turbulence energy for one working cycle is shown in Figure3. It can be shown at rotating-sleeve angles of 180° and 360°, respectively. There are marks as evident highlight regions in specific area, and this phenomenon indicates that turbulence energy increases in the specific area. As shown in Figure 3, the angles of 180° and 360° are exactly when the interconversion between discharge and suction happens. Therefore, the flow field around highlight regions is seriously unstable to cause much loss of kinetic energy.Figure 3
Distribution of turbulence energy for one working cycle.


### 4.2. Velocity Distribution

The velocity distribution inX direction for the distributing-flow system within one working cycle is shown in Figure 4. It is shown from Figure 4 that, at rotating-sleeve angle of 10°, velocity gradient and velocity magnitude increase, at the same time, the turbulence energy increases as shown in Figure 3. Additionally, at rotating-sleeve angles of 180° and 360°, respectively, the flow velocity magnitude is a negative value around the damping groove, in which the turbulence energy increases. It is demonstrated that the flow condition around the damping groove is unstable.Figure 4
Velocity distribution inX direction for one working cycle.Figure5 shows velocity vector distribution around the damping groove when the rotating sleeve rotates from discharge to suction. At this moment, the plunger descends from the TDC; the loading chamber separates from the valve port in a critical state; and there exists subtle streaming of fluid caused by inertia effect in the loading chamber as shown in Figure 5(a). Besides, the damping groove instantaneously connects with the collecting chamber and valve port as shown in Figure 5(b). The simulation results from Figure 5(b) illustrate that transitory backward flow flows from the collecting chamber into the valve port and causes dramatic turbulence around the damping groove on account of high pressure in the pump chamber as well as low pressure in the collecting chamber (differential pressure is about 1.9 MPa), in which differential pressure resulting in backward flow flowing from the collecting chamber into the pump chamber reduces volume efficiency.Figure 5
Local velocity vector distribution with rotating-sleeve angle of 180°.Figure6 shows local velocity vector distribution when the rotating sleeve rotates from suction to discharge. At this moment, the plunger ascends from the Bottom Dead Center (BDC); the damping groove flashily connects with the loading chamber and valve port as shown in Figure 6(a). Figure 6(b) shows that the transient backward flow flows from the valve port into the loading chamber causing dramatic turbulence around the damping groove on account of high pressure in the valve port as well as low pressure in the loading chamber. At the same time, differential pressure causes backward flow to flow from the pump chamber into the loading chamber, which can seriously reduce volume efficiency; the loading chamber is separating from the valve port in a critical state; and there exists subtle streaming that is caused by inertia effect in the loading chamber.Figure 6
Local velocity vector distribution with rotating-sleeve angle of 360°.


### 4.3. Analyses on Working Pulsation

#### 4.3.1. Flow Pulsation of Different Valve Port Structures

Figure7 demonstrates the mesh of distributing-flow system by dealing with structured mesh generation. The sliding grid option provides the grid interface for the sliding surfaces between the static inlet/outlet part of grid and the outside part of valve port, the inside part of valve port, and the static part of pump chamber. The piston movement is modeled by a dynamic grid with a moving and deforming mesh for the pump chamber part. In the grid, maximum parameter in overall mesh is 1; different parts have different local mesh parameter; total numbers of grid are 397602.Figure 7
Fluid model grid of distributing-flow system.Flow pulsation is the source of noise, pressure pulsation, and vibration of plunger pump. It can have adverse impacts towards working parts, especially some precise hydraulic system. Hence it should be emphasized that the characteristic of fluid is most meaningful with respect to the flow pulsation of the distributing-flow system. Figure8 shows that outlet flow shows periodic fluctuations with maximum flow about 5 × 10−4m3/s and backward flow appears at the end of processes, that is, suction and discharge. It can be illustrated that these analyses are consistent with findings in Figures 5 and 6. Moreover, it appears as instantaneous backward flow about 2.2 × 10−4m3/s according to the left zoom in plot corresponding to the TDC in Figure 9, which includes two working cycles. Similarly, it appears as instantaneous backward flow about 2.6 × 10−4m3/s according to the right zoom in plot corresponding to the BDC in Figure 9.Figure 8
The characteristic of outlet flow pulsation.Figure 9
The characteristic of local outlet flow pulsation.


#### 4.3.2. Pressure Pulsation of Different Valve Port Structures

The phenomena incorporating backward flow, local cavitation, and erosion can easily cause pressure pulsation with regard to inner flow. And once pressure pulsation happens, it can lead to intensive vibration of pump and cavitation and even resonance. Figure10 shows periodic fluctuation and distinct sharp corner in dead center of pressure pulsations. As partial zoom in plots including two working cycles in Figure 10, left zoom in plot in Figure 11 depicts that pressure in the pump chamber quickly rises until it reaches 2.2 × 106 Pa involving over 10% more than nominal pressure when the plunger is at the TDC on account of throttling action in the damping groove. However, pressure overshoot gradually reduces to normal condition followed by increasing flow area. Because of throttling action in the damping groove, pressure in the pump chamber abruptly drops to the saturated vapor pressure about −98.9 KPa of fluid when the plunger is at the BDC; however, the overshoot gradually increases to the normal condition with increasing flow area.Figure 10
The characteristic of pressure in the pump chamber.Figure 11
The characteristic of local pressure in the pump chamber.


## 4.1. Distribution of Turbulence Energy

The distribution of turbulence energy for one working cycle is shown in Figure3. It can be shown at rotating-sleeve angles of 180° and 360°, respectively. There are marks as evident highlight regions in specific area, and this phenomenon indicates that turbulence energy increases in the specific area. As shown in Figure 3, the angles of 180° and 360° are exactly when the interconversion between discharge and suction happens. Therefore, the flow field around highlight regions is seriously unstable to cause much loss of kinetic energy.Figure 3
Distribution of turbulence energy for one working cycle.


## 4.2. Velocity Distribution

The velocity distribution inX direction for the distributing-flow system within one working cycle is shown in Figure 4. It is shown from Figure 4 that, at rotating-sleeve angle of 10°, velocity gradient and velocity magnitude increase, at the same time, the turbulence energy increases as shown in Figure 3. Additionally, at rotating-sleeve angles of 180° and 360°, respectively, the flow velocity magnitude is a negative value around the damping groove, in which the turbulence energy increases. It is demonstrated that the flow condition around the damping groove is unstable.Figure 4
Velocity distribution inX direction for one working cycle.Figure5 shows velocity vector distribution around the damping groove when the rotating sleeve rotates from discharge to suction. At this moment, the plunger descends from the TDC; the loading chamber separates from the valve port in a critical state; and there exists subtle streaming of fluid caused by inertia effect in the loading chamber as shown in Figure 5(a). Besides, the damping groove instantaneously connects with the collecting chamber and valve port as shown in Figure 5(b). The simulation results from Figure 5(b) illustrate that transitory backward flow flows from the collecting chamber into the valve port and causes dramatic turbulence around the damping groove on account of high pressure in the pump chamber as well as low pressure in the collecting chamber (differential pressure is about 1.9 MPa), in which differential pressure resulting in backward flow flowing from the collecting chamber into the pump chamber reduces volume efficiency.Figure 5
Local velocity vector distribution with rotating-sleeve angle of 180°.Figure6 shows local velocity vector distribution when the rotating sleeve rotates from suction to discharge. At this moment, the plunger ascends from the Bottom Dead Center (BDC); the damping groove flashily connects with the loading chamber and valve port as shown in Figure 6(a). Figure 6(b) shows that the transient backward flow flows from the valve port into the loading chamber causing dramatic turbulence around the damping groove on account of high pressure in the valve port as well as low pressure in the loading chamber. At the same time, differential pressure causes backward flow to flow from the pump chamber into the loading chamber, which can seriously reduce volume efficiency; the loading chamber is separating from the valve port in a critical state; and there exists subtle streaming that is caused by inertia effect in the loading chamber.Figure 6
Local velocity vector distribution with rotating-sleeve angle of 360°.


## 4.3. Analyses on Working Pulsation

### 4.3.1. Flow Pulsation of Different Valve Port Structures

Figure7 demonstrates the mesh of distributing-flow system by dealing with structured mesh generation. The sliding grid option provides the grid interface for the sliding surfaces between the static inlet/outlet part of grid and the outside part of valve port, the inside part of valve port, and the static part of pump chamber. The piston movement is modeled by a dynamic grid with a moving and deforming mesh for the pump chamber part. In the grid, maximum parameter in overall mesh is 1; different parts have different local mesh parameter; total numbers of grid are 397602.Figure 7
Fluid model grid of distributing-flow system.Flow pulsation is the source of noise, pressure pulsation, and vibration of plunger pump. It can have adverse impacts towards working parts, especially some precise hydraulic system. Hence it should be emphasized that the characteristic of fluid is most meaningful with respect to the flow pulsation of the distributing-flow system. Figure8 shows that outlet flow shows periodic fluctuations with maximum flow about 5 × 10−4m3/s and backward flow appears at the end of processes, that is, suction and discharge. It can be illustrated that these analyses are consistent with findings in Figures 5 and 6. Moreover, it appears as instantaneous backward flow about 2.2 × 10−4m3/s according to the left zoom in plot corresponding to the TDC in Figure 9, which includes two working cycles. Similarly, it appears as instantaneous backward flow about 2.6 × 10−4m3/s according to the right zoom in plot corresponding to the BDC in Figure 9.Figure 8
The characteristic of outlet flow pulsation.Figure 9
The characteristic of local outlet flow pulsation.


### 4.3.2. Pressure Pulsation of Different Valve Port Structures

The phenomena incorporating backward flow, local cavitation, and erosion can easily cause pressure pulsation with regard to inner flow. And once pressure pulsation happens, it can lead to intensive vibration of pump and cavitation and even resonance. Figure10 shows periodic fluctuation and distinct sharp corner in dead center of pressure pulsations. As partial zoom in plots including two working cycles in Figure 10, left zoom in plot in Figure 11 depicts that pressure in the pump chamber quickly rises until it reaches 2.2 × 106 Pa involving over 10% more than nominal pressure when the plunger is at the TDC on account of throttling action in the damping groove. However, pressure overshoot gradually reduces to normal condition followed by increasing flow area. Because of throttling action in the damping groove, pressure in the pump chamber abruptly drops to the saturated vapor pressure about −98.9 KPa of fluid when the plunger is at the BDC; however, the overshoot gradually increases to the normal condition with increasing flow area.Figure 10
The characteristic of pressure in the pump chamber.Figure 11
The characteristic of local pressure in the pump chamber.


## 4.3.1. Flow Pulsation of Different Valve Port Structures

Figure7 demonstrates the mesh of distributing-flow system by dealing with structured mesh generation. The sliding grid option provides the grid interface for the sliding surfaces between the static inlet/outlet part of grid and the outside part of valve port, the inside part of valve port, and the static part of pump chamber. The piston movement is modeled by a dynamic grid with a moving and deforming mesh for the pump chamber part. In the grid, maximum parameter in overall mesh is 1; different parts have different local mesh parameter; total numbers of grid are 397602.Figure 7
Fluid model grid of distributing-flow system.Flow pulsation is the source of noise, pressure pulsation, and vibration of plunger pump. It can have adverse impacts towards working parts, especially some precise hydraulic system. Hence it should be emphasized that the characteristic of fluid is most meaningful with respect to the flow pulsation of the distributing-flow system. Figure8 shows that outlet flow shows periodic fluctuations with maximum flow about 5 × 10−4m3/s and backward flow appears at the end of processes, that is, suction and discharge. It can be illustrated that these analyses are consistent with findings in Figures 5 and 6. Moreover, it appears as instantaneous backward flow about 2.2 × 10−4m3/s according to the left zoom in plot corresponding to the TDC in Figure 9, which includes two working cycles. Similarly, it appears as instantaneous backward flow about 2.6 × 10−4m3/s according to the right zoom in plot corresponding to the BDC in Figure 9.Figure 8
The characteristic of outlet flow pulsation.Figure 9
The characteristic of local outlet flow pulsation.


## 4.3.2. Pressure Pulsation of Different Valve Port Structures

The phenomena incorporating backward flow, local cavitation, and erosion can easily cause pressure pulsation with regard to inner flow. And once pressure pulsation happens, it can lead to intensive vibration of pump and cavitation and even resonance. Figure10 shows periodic fluctuation and distinct sharp corner in dead center of pressure pulsations. As partial zoom in plots including two working cycles in Figure 10, left zoom in plot in Figure 11 depicts that pressure in the pump chamber quickly rises until it reaches 2.2 × 106 Pa involving over 10% more than nominal pressure when the plunger is at the TDC on account of throttling action in the damping groove. However, pressure overshoot gradually reduces to normal condition followed by increasing flow area. Because of throttling action in the damping groove, pressure in the pump chamber abruptly drops to the saturated vapor pressure about −98.9 KPa of fluid when the plunger is at the BDC; however, the overshoot gradually increases to the normal condition with increasing flow area.Figure 10
The characteristic of pressure in the pump chamber.Figure 11
The characteristic of local pressure in the pump chamber.


## 5. Conclusions

(1)
According to characteristic of the novel rotating-sleeve distributing-flow system, the governing equations between the plunger and rotating sleeve are established to obtain the dynamic model of distributing-sleeve system. By utilizing sliding mesh and dynamic mesh technology, the improved CFD model taking the cavitation and turbulence into consideration is employed to simulate flow field and working pulsation.
(2)
Simulations of rotating-sleeve distributing-flow system have been conducted based on the governing equations and the improved CFD model. Primary performance parameters such as turbulence energy distribution, velocity distribution, and working pulsation have been investigated. In addition, the relationship between performance parameters is studied for the distributing-flow system.
(3)
Periodic fluctuation and sharp corner exist in flow pulsation in addition to the backward flow issue between discharge and suction. Serious turbulence and large loss in kinetic energy around the damping groove exist. Moreover the noticeable periodic fluctuation and sharp corner appear in the pressure pulsation, and pressure in the pump chamber rapidly rises to 2.2 MPa involving over 10% more than nominal pressure when the plunger is at the TDC. On the other hand, pressure in the pump chamber instantaneously reduces to the saturated vapor pressure −98.9 KPa when the plunger is at the BDC. For the rest time period, the pressure overshoot gradually reaches stability until it closes to the normal condition with increasing flow area. Fluid field and working pulsation simulation could provide foundations for structure optimization.



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*Source: 1015494-2017-11-01.xml*