# Simulation and Experimental Study on Characteristics of Multiorifice Nozzle in Radial Jet Drilling

Authors: Tao Zhang; Yumei Li; Hui Lu; Jianing Jiang
Journal: Geofluids
 (2022)

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## Abstract

The radial jet drilling (RJD) is a key technology to improve the development efficiency of low-permeability oil and gas resources. In order to seek a reasonable hydraulic engineering parameter combination of hydraulic radial jet drilling, to obtain the optimal hydraulic energy distribution, a jet radial horizontal drilling simulation experiment system of the casing windowing is designed. A sequence of experimental investigations focused on engineering parameters of pump displacement, rotating speed, and frequency of high-pressure plunger pump is performed, and the operability and the feasibility of the experiment are verified. To evaluate the maximum drillable length and the self-propelled force of a jet nozzle, a 3D numerical model based on ANSYS-CFX is developed to evaluate the effects of the inlet flow displacement, the flow rates ratioK, and the angle ratio F:B of the forward orifice and backward orifice of the jet nozzle on its maximum drillable length and self-propelled force by sensitivity analysis. Finally, the comparison of numerical simulation results (Ln), mathematical results (Lm), and experiment results (Le) of the maximum drillable length are presented. It is observed that the simulation results are consistent with the experiment results with an average accuracy of 97.07%. Therefore, the proposed numerical model has a good performance in predicting the maximum drillable length of the multiorifice nozzle. The research results can provide theoretical guidance for improving the rock breaking and drilling capability of radial jet drilling technology.


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## Body

## 1. Introduction

Radial jet drilling (RJD) technology was imposed in the 1980s [1]. In the exploration of oil and gas wells, the application of radial jet drilling (RJD) technology can effectively reduce drilling costs for the unconventional oil and gas wells, abandoned renovation wells, and geothermal development wells, especially the exploration or development wells with poor fracturing effects [2–5]. Additionally, the RJD technology has been growing in applications aimed to increase the oil well drainage area and reduce the pore pressure of the reservoir for the low-permeability reservoirs and significantly increased reservoir production [6].The hydraulic radial jet drilling technology mainly includes two processes: casing windowing and radial jet drilling. One of the cores is the casing windowing technology. Whether the radial jet drilling can be successfully completed depends on the casing windowing. The success of casing windowing directly affects the subsequent channel construction of radial horizontal wells. In the process of the casing windowing, it is necessary to use the blade bit to drill a microwellbore about 25 mm on the inside of the casing and then to connect the high-pressure hose with a coiled tubing. The high-pressure fluid is sprayed through the jet nozzle to penetrate the rock layer to form a tiny horizontal wellbore with a length of about 100 m and a diameter of about 50 mm, whose radius of curvature is much smaller than that of conventional well [7, 8]. The radial oil and gas passages break through the near-well reservoir pollution zone and establish multiple diversion channels for the far-well zone, increasing well production. To obtain larger self-propelled force to pull the hose forward, the jet nozzle design is of great importance when selecting bottom-hole drilling tools. The casing window drilling tool assembly structure is shown in Figure 1.Figure 1
The casing window drilling tool assembly structure.In recent years, the application of the radial jet drilling (RJD) technology is increasingly investigated to stimulate low performing wells, such as geothermal wells and coalbed methane [9–11]. Chi et al. calculated the maximum drillable length of jet nozzle by theoretical analysis and experiments [12]. Li and Zhang developed a 3D numerical model based on ANSYS-CFX to investigate the self-propelled ability of a multiorifice nozzle, remarkably the effects of the physical parameters of the multiorifice nozzle on its self-propelled ability by sensitivity analysis [13]. Wang et al. conducted the experimental study of the NGH, and focusing on the effects of traverse jetting speed, jetting flow rate on rock breaking was studied [14]. Yang analyzed the effects of the jet velocity, distance, and saturation on the NGH sediment by experiment and simulation [15]. Wang et al. developed an engineering construction chart for solid fluidization well through jet experiments [16]. Liao et al. conducted the rock-breaking experiments of the self-propelled jetting efficiency and developed a numerical model of the self-propelled force of multiorifice nozzles [17]. For all the above studies, the optimization design of hydraulic parameters of radial horizontal wells and conventional drilling technologies are different in terms of optimization objectives and constraints. The existing hydraulic parameter design methods are not applicable to radial horizontal well technology.In this paper, a jet radial horizontal drilling simulation experiment system of the casing windowing is designed, and the reasons for not opening window in the experiment are analyzed. To evaluate the maximum drillable length and the self-propelled force of a multiorifice nozzle, a 3D numerical model of the nozzle is established based on ANSYS-CFX. A sequence of simulations are develop to investigate the effects of the inlet flow displacement, the flow rates ratioK, and the angle ratio F:B of the forward orifice and backward orifice of the jet nozzle on its maximum drillable length and self-propelled force by a series of sensitivity analysis. The design method of hydraulic parameters for radial horizontal drilling is proposed, which provides theoretical support for the application of radial horizontal well technology.


## 2. The Mathematical Model

### 2.1. Calculation of Self-Propelled Force

The recoil force that pushes the nozzle forward is obtained by the kinetic energy theorem of the nozzle outlet section [18].
(1)FΔt=mν2−mν1,where F—the force on per unit volume, N;∆t—the time on per unit volume of fluid, s;m—the mass of the fluid per unit volume, kg;V1—the average flow velocity in the nozzle outlet section, m/s;V2—the average flow velocity outside the nozzle outlet section, m/s.According to the principle that the acting force is equal to the reaction force,F in the above formula is the jet recoil force Fz. It is known as m/Δt=ρd, assuming that the flow path of jet nozzle is circular, according to the continuity equation between the outlet sections of jet nozzle, i.e., A=πd2/4, it is obtained:
(2)Fz=ρqυ21‐d2d12,where d2/d14≤1Simplified expression of jet velocity at jet nozzle outlet:(3)ν=44.77p,where P—the jet pressure, MPa;V—the jet flow rate, m/s.Substituting (3) into Equation (2), and finally,
(4)Fz=0.745qp,where Fz—the recoil force of water flow, N;q—the jet flow, L/min.Substituting the formula into Equation (4) yields another expression:
(5)Fz=1.56d2p,where d—the outlet diameter of the nozzle, mm.The expression of recoil force is:(6)Ff=n11.56pd12cosθ1,where n1—the number of backward orifices;θ1—the angle of the backward orifices, °;d1—the diameter of the backward orifices, mm.The expression of rock breaking force is:(7)Fp=n21.56pd22cosθ2,where FP—the breaking rock force, N;n2—the number of forward orifices;θ2—the angle of the forward orifices, °;d2—the diameter of the forward orifices, mm.The self-propelled force of the multiorifice nozzle is expressed as:(8)Ft=Fz−Fp.


### 2.2. The Maximum Drillable Length

In the process of hydraulic jet rock breaking, the viscosity of the high-pressure hose wall is not considered. Assume that the friction force of the jet nozzle in the horizontal direction isFw, the friction force at the radial borehole wall is Ff. The resultant force in the horizontal direction of radial jet drilling system is calculated as
(9)Fpull=Fz−Fp−Fw−Ff,where
(10)Ff=μMg+μqhgl.In the above formula,μ is the sliding friction factor of the wellbore and wall; l is the penetration depth of the high-pressure hose, m; M is the mass of the jet nozzle, kg; qh is the mass of the high-pressure hose line, kg/m; g is the gravitational acceleration, N/kg.Assuming the jet nozzle is placed horizontally,(11)ddtM+lqnυ=Fz−Fp−Fw−Ff,where v is the drilling speed, m/s.For convenience, define a length coordinate:(12)x=l+Mqh=l+l0,where x is the extension length, m; l0 is the equivalent length of the jet nozzle, m.It is assumed that the frictional forceFw experienced by the high-pressure hose is a fixed value and can be determined experimentally. Since F=Ff+Fp, F can be written as:
(13)F=μMg+μqhgl+ηl+l0.According to formula (12),
(14)F=μqhgM/qh+ηl+l0=μqhg+ηx.In Equation (14), η is the coefficient of friction resistance, N/m.
(15)μqhg+η.Assume Equation (14) can be simplified to:
(16)F=kx,where k is the combined friction coefficient, N/m.In combination with Equations (11), (12), (14), and (15), we can obtain:
(17)ddtqhxυ=Fz−kx−20,(18)qh2ddtxυ2=Fz−kx−20x.Initial conditions of a given jet nozzle:xt=0=l0,υt=0=υx=l0=0.Integrate Equation (18) to obtain the motion equation:
(19)qh2xυ2=Fz−20x2−l02−k3x3−l03.Equation (19) can be written:
(20)qh2xυ2=nρQjνjcosθj−mρQiνicosθi−π4di2mpout−20x2−l02−k3x3−l03,where Qi is the flow of the ith forward orifice, L/s, Qj is the flow of the jth backward orifice, L/s; vi is the jet velocity of the ith forward orifice, m/s, vj is the jet velocity of the jth backward orifice, m/s; θi is the angle of forward orifice, °; and θj is the angle of backward orifice, °.Assuming that the value ofk=0.87N/m, we get:
(21)nρQjνjcosθj−mρQiνicosθi−π/4di2mpout−20x2−0.25−0.29x3−0.125qhx2.Whenv=0, the maximum drillable length can be expressed as follows:
(22)X=nρQjνjcosθj−mρQiνicosθi−π/4di2mpout−200.29.


## 2.1. Calculation of Self-Propelled Force

The recoil force that pushes the nozzle forward is obtained by the kinetic energy theorem of the nozzle outlet section [18].
(1)FΔt=mν2−mν1,where F—the force on per unit volume, N;∆t—the time on per unit volume of fluid, s;m—the mass of the fluid per unit volume, kg;V1—the average flow velocity in the nozzle outlet section, m/s;V2—the average flow velocity outside the nozzle outlet section, m/s.According to the principle that the acting force is equal to the reaction force,F in the above formula is the jet recoil force Fz. It is known as m/Δt=ρd, assuming that the flow path of jet nozzle is circular, according to the continuity equation between the outlet sections of jet nozzle, i.e., A=πd2/4, it is obtained:
(2)Fz=ρqυ21‐d2d12,where d2/d14≤1Simplified expression of jet velocity at jet nozzle outlet:(3)ν=44.77p,where P—the jet pressure, MPa;V—the jet flow rate, m/s.Substituting (3) into Equation (2), and finally,
(4)Fz=0.745qp,where Fz—the recoil force of water flow, N;q—the jet flow, L/min.Substituting the formula into Equation (4) yields another expression:
(5)Fz=1.56d2p,where d—the outlet diameter of the nozzle, mm.The expression of recoil force is:(6)Ff=n11.56pd12cosθ1,where n1—the number of backward orifices;θ1—the angle of the backward orifices, °;d1—the diameter of the backward orifices, mm.The expression of rock breaking force is:(7)Fp=n21.56pd22cosθ2,where FP—the breaking rock force, N;n2—the number of forward orifices;θ2—the angle of the forward orifices, °;d2—the diameter of the forward orifices, mm.The self-propelled force of the multiorifice nozzle is expressed as:(8)Ft=Fz−Fp.


## 2.2. The Maximum Drillable Length

In the process of hydraulic jet rock breaking, the viscosity of the high-pressure hose wall is not considered. Assume that the friction force of the jet nozzle in the horizontal direction isFw, the friction force at the radial borehole wall is Ff. The resultant force in the horizontal direction of radial jet drilling system is calculated as
(9)Fpull=Fz−Fp−Fw−Ff,where
(10)Ff=μMg+μqhgl.In the above formula,μ is the sliding friction factor of the wellbore and wall; l is the penetration depth of the high-pressure hose, m; M is the mass of the jet nozzle, kg; qh is the mass of the high-pressure hose line, kg/m; g is the gravitational acceleration, N/kg.Assuming the jet nozzle is placed horizontally,(11)ddtM+lqnυ=Fz−Fp−Fw−Ff,where v is the drilling speed, m/s.For convenience, define a length coordinate:(12)x=l+Mqh=l+l0,where x is the extension length, m; l0 is the equivalent length of the jet nozzle, m.It is assumed that the frictional forceFw experienced by the high-pressure hose is a fixed value and can be determined experimentally. Since F=Ff+Fp, F can be written as:
(13)F=μMg+μqhgl+ηl+l0.According to formula (12),
(14)F=μqhgM/qh+ηl+l0=μqhg+ηx.In Equation (14), η is the coefficient of friction resistance, N/m.
(15)μqhg+η.Assume Equation (14) can be simplified to:
(16)F=kx,where k is the combined friction coefficient, N/m.In combination with Equations (11), (12), (14), and (15), we can obtain:
(17)ddtqhxυ=Fz−kx−20,(18)qh2ddtxυ2=Fz−kx−20x.Initial conditions of a given jet nozzle:xt=0=l0,υt=0=υx=l0=0.Integrate Equation (18) to obtain the motion equation:
(19)qh2xυ2=Fz−20x2−l02−k3x3−l03.Equation (19) can be written:
(20)qh2xυ2=nρQjνjcosθj−mρQiνicosθi−π4di2mpout−20x2−l02−k3x3−l03,where Qi is the flow of the ith forward orifice, L/s, Qj is the flow of the jth backward orifice, L/s; vi is the jet velocity of the ith forward orifice, m/s, vj is the jet velocity of the jth backward orifice, m/s; θi is the angle of forward orifice, °; and θj is the angle of backward orifice, °.Assuming that the value ofk=0.87N/m, we get:
(21)nρQjνjcosθj−mρQiνicosθi−π/4di2mpout−20x2−0.25−0.29x3−0.125qhx2.Whenv=0, the maximum drillable length can be expressed as follows:
(22)X=nρQjνjcosθj−mρQiνicosθi−π/4di2mpout−200.29.


## 3. Numerical Simulation

### 3.1. Geometry and Boundary

The multiorifice nozzle is the “core” of radial jet drilling (RJD) technology, especially the geometric design of the nozzle will have a greater impact on hydraulic parameters. The measuring instrument (CROMA, Hexagon, Sweden) is used to carry out the mapping design of the multiorifice nozzle. The 3D physical geometry model of the nozzle is shown in Figure2 [9]. The diameter of the jet nozzle is 25 mm, the total length is 17.5 mm, the inner diameter is 8.6 mm, the outer diameter is 12.5 mm, the diameter of front orifice is 0.5 mm, the diameter of backward orifice is 0.7 mm; and the inlet ambient pressure P=30MPa, inlet flow rate Q0. The flow field model of the jet nozzle is segmented by 3D modeling software, and then, the meshing model of multiorifice nozzles was established by ICEM (as shown in Figure 3). The boundary conditions of the inlet, outlet, and wall of the jet nozzle are set in the simulation of flow field characteristics. After setting the boundary conditions, the discrete format and relaxation factor are adjusted.Figure 2
The 3D physical geometry model of the nozzle through three-coordinate measuring instrument.Figure 3
The meshing model of multiorifice nozzle.


### 3.2. Sensitivity Analysis

In this simulation, the inlet flow rateQ0 is set to 25 L/min, 35 L/min, 45 L/min, and 55 L/min, and multiple simulation models are established. Figure 4 shows the streamline diagram of velocity vector of jet nozzle. The jet velocity distribution diagram of forward orifice under different inlet displacement is shown in Figure 5. The jet velocity distribution diagram of backward orifice under different inlet flow displacement is shown in Figure 6. In the entire simulation, the maximum jet velocity is distributed near the forward orifices and backward orifices where there is a larger pressure difference.Figure 4
The streamline diagram of velocity vector of jet nozzle (F+B): 3+5.Figure 5
The jet velocity distributions of forward orifice under different inlet displacement.Figure 6
The jet velocity distributions of backward orifice under different inlet displacement.A series of simulations of the inlet flow displacement on the maximum flow rate of forward orifices and backward orifices of jet nozzle were investigated (as shown in Figure7). When the inlet displacement Q=25L/min, the velocity of backward orifice is 162.4 m/s, the velocity of forward orifice is 81.2 m/s, and the maximum flow rate is 199.8 m/s. It is observed that both the maximum flow rate of forward orifices and backward orifices increase as the inlet displacement increases. The flow rate of the backward orifices is greater than that of the forward orifices when the larger backward driving force can be obtained.Figure 7
Comparison of the maximum speed of the injector under different inlet displacements.The ratio of the flow rates of the forward orifice to that of the backward orifice of the jet nozzle is defined as [8]:
(23)K=n2Q2n1Q1=n2d22n1d12.The key parameter will reflect the performance of the jet nozzle. Given the variation of the inlet displacement, the curves of the maximum drillable length versus the ratioK are plotted in Figure 8. As indicated from the comprehensive analysis, the maximum drillable length increases with the ratio K until K=0.2, but a decreasing trend of the maximum drillable length is shown when K>0.2. As demonstrated from the results, the larger inlet displacement value, the larger the maximum drillable length when K<0.45; the larger inlet displacement value, the smaller the maximum drillable length when K>0.45. This shows that the ratio K changes within a certain ratio range, and the inlet displacement has a greater impact on the maximum drillable length. The ratio of the flow rates of the forward orifice to that of the backward orifice of the jet nozzle might have an optimal value according to the curve trend when the effect of drilling hole is the best.Figure 8
Effect of the ratioK on the maximum drillable length for representative values of Q.The calculated values of the self-propelled force with the inlet displacement are investigated from the simulation results for representative values of the angle ratio of the forward orifice and the backward orifice (as shown in Figure9). It is obvious that the self-propelled force increases by a larger magnitude when the flow rate Q<40L/min, and the magnitude tends to decrease as the inlet flow rate when Q>40L/min. The simulations show that the self-propelled force is constantly increasing as the ratio F:B decreasing under the same inlet displacement condition. This indicates that the recoil force increases with the increase of the inlet flow displacement, and the increasing trend is greater than that of the rock breaking force. Therefore, it is better to choose the larger inlet flow displacement to increase the recoil force, rock breaking force, and self-propelled force without considering other factors.Figure 9
Effects of the inlet flow rate on the self-propelled force for representative values ofF:B.


## 3.1. Geometry and Boundary

The multiorifice nozzle is the “core” of radial jet drilling (RJD) technology, especially the geometric design of the nozzle will have a greater impact on hydraulic parameters. The measuring instrument (CROMA, Hexagon, Sweden) is used to carry out the mapping design of the multiorifice nozzle. The 3D physical geometry model of the nozzle is shown in Figure2 [9]. The diameter of the jet nozzle is 25 mm, the total length is 17.5 mm, the inner diameter is 8.6 mm, the outer diameter is 12.5 mm, the diameter of front orifice is 0.5 mm, the diameter of backward orifice is 0.7 mm; and the inlet ambient pressure P=30MPa, inlet flow rate Q0. The flow field model of the jet nozzle is segmented by 3D modeling software, and then, the meshing model of multiorifice nozzles was established by ICEM (as shown in Figure 3). The boundary conditions of the inlet, outlet, and wall of the jet nozzle are set in the simulation of flow field characteristics. After setting the boundary conditions, the discrete format and relaxation factor are adjusted.Figure 2
The 3D physical geometry model of the nozzle through three-coordinate measuring instrument.Figure 3
The meshing model of multiorifice nozzle.


## 3.2. Sensitivity Analysis

In this simulation, the inlet flow rateQ0 is set to 25 L/min, 35 L/min, 45 L/min, and 55 L/min, and multiple simulation models are established. Figure 4 shows the streamline diagram of velocity vector of jet nozzle. The jet velocity distribution diagram of forward orifice under different inlet displacement is shown in Figure 5. The jet velocity distribution diagram of backward orifice under different inlet flow displacement is shown in Figure 6. In the entire simulation, the maximum jet velocity is distributed near the forward orifices and backward orifices where there is a larger pressure difference.Figure 4
The streamline diagram of velocity vector of jet nozzle (F+B): 3+5.Figure 5
The jet velocity distributions of forward orifice under different inlet displacement.Figure 6
The jet velocity distributions of backward orifice under different inlet displacement.A series of simulations of the inlet flow displacement on the maximum flow rate of forward orifices and backward orifices of jet nozzle were investigated (as shown in Figure7). When the inlet displacement Q=25L/min, the velocity of backward orifice is 162.4 m/s, the velocity of forward orifice is 81.2 m/s, and the maximum flow rate is 199.8 m/s. It is observed that both the maximum flow rate of forward orifices and backward orifices increase as the inlet displacement increases. The flow rate of the backward orifices is greater than that of the forward orifices when the larger backward driving force can be obtained.Figure 7
Comparison of the maximum speed of the injector under different inlet displacements.The ratio of the flow rates of the forward orifice to that of the backward orifice of the jet nozzle is defined as [8]:
(23)K=n2Q2n1Q1=n2d22n1d12.The key parameter will reflect the performance of the jet nozzle. Given the variation of the inlet displacement, the curves of the maximum drillable length versus the ratioK are plotted in Figure 8. As indicated from the comprehensive analysis, the maximum drillable length increases with the ratio K until K=0.2, but a decreasing trend of the maximum drillable length is shown when K>0.2. As demonstrated from the results, the larger inlet displacement value, the larger the maximum drillable length when K<0.45; the larger inlet displacement value, the smaller the maximum drillable length when K>0.45. This shows that the ratio K changes within a certain ratio range, and the inlet displacement has a greater impact on the maximum drillable length. The ratio of the flow rates of the forward orifice to that of the backward orifice of the jet nozzle might have an optimal value according to the curve trend when the effect of drilling hole is the best.Figure 8
Effect of the ratioK on the maximum drillable length for representative values of Q.The calculated values of the self-propelled force with the inlet displacement are investigated from the simulation results for representative values of the angle ratio of the forward orifice and the backward orifice (as shown in Figure9). It is obvious that the self-propelled force increases by a larger magnitude when the flow rate Q<40L/min, and the magnitude tends to decrease as the inlet flow rate when Q>40L/min. The simulations show that the self-propelled force is constantly increasing as the ratio F:B decreasing under the same inlet displacement condition. This indicates that the recoil force increases with the increase of the inlet flow displacement, and the increasing trend is greater than that of the rock breaking force. Therefore, it is better to choose the larger inlet flow displacement to increase the recoil force, rock breaking force, and self-propelled force without considering other factors.Figure 9
Effects of the inlet flow rate on the self-propelled force for representative values ofF:B.


## 4. Field Experiment Description

In order to verify the simulation results of multiorifice nozzle, the field application experiment is conducted in well Nan XX-14, China. The field application apparatuses combination schematic of schematic of an RJD simulation experiment system with high-pressure water is shown in Figure10.Figure 10
Schematic of an RJD system with high-pressure water.The vertical depth of radial horizontal well is 2540 m; the inner diameter of the wellbore is 139.7 mm. The inner diameter of the multiorifice nozzle was 20.0 mm, and the outer diameter of the multiorifice nozzle was 12.2 mm. The number of the forward orifice is 3, and the number of the backward orifice was 6. The diameter of the forward orifice wasd2=0.50mm, and the diameter of the backward orifice was d1=0.70mm. The angle of the forward orifice was θ2=20°, and the angle of the backward orifice was θ1=30°; the jetting azimuth is 90°. The working pipe string was the tubing with an outer diameter of 0.06 mm, and the steering gear was put into the predetermined position. The roughness of wellbore wall is 1 mm, and the friction coefficient is 0.3. The jetting fluid is clean water, the density is 988 kg/m3, and the viscosity is 0.549 mPa·s. The treating pressure is 25~71 MPa, and the slurry proppant concentration is 35~115 kg/m3.In the experiment, it is found that the maximum drillable length of the jet nozzle has an increasing tendency and then decreasing with the increase of inlet flow displacement (as shown in Figure11). This is because the backward jet flow rate increases as the inlet displacement increases, and the self-propelled force also increases. It is obvious that the self-propelled force is larger when the number of the backward orifices is larger, and then, the maximum drillable length can be obtained. Excessive flow will lead to increased circulating pressure loss of the system and lower pressure drop of jet nozzle, which is not conducive to rock breaking. The inlet flow displacement is controlled around 30 L/min, the maximum drillable length 43.8 m of the jet nozzle can be obtained for representative values of F+B: 3+5. Therefore, it is more reasonable to choose the number of the backward orifices is B=5.Figure 11
Effects of inlet flow on the maximum drillable length atF+B: 3+6, 4+6, and 5+6.Figure12 shows the comparison of numerical simulation results (Ln), mathematical results (Lm), and experiment results (Le) of the maximum drillable length. It is obvious that the difference between the three results of Ln, Lm, and Le is very small, which proves that the simulation results are consistent with the experiment results with an average accuracy of 97.07%. Therefore, the proposed numerical model has a good performance in predicting the maximum drillable length of the microhole nozzle.Figure 12
Comparison of simulation, calculation, and experiment results of the maximum drillable length.


## 5. Conclusions

The research presented in this paper focused on the numerical simulation and experiment of a multiorifice nozzle in radial jet drilling. To evaluate the maximum drillable length and the self-propelled force, a 3D numerical model of multiorifice nozzles based on ANSYS-CFX is developed; the conclusions are summarized as follows:(1)
Multiple simulation models are established to investigate the effects of inlet flow displacement on the flow velocity of the forward orifices and backward orifices of the multiorifice nozzle. The numerical simulation results show that the maximum jet velocity are distributed near the forward orifices and backward orifices where there is a larger pressure difference. Both the maximum flow rate of forward orifices and backward orifices increase as the inlet displacement increases. The flow rate of the backward orifices is greater than that of the forward orifices when the larger backward driving force in rock breaking process can be obtained(2)
As indicated from the comprehensive analysis, the maximum drillable length increases untilK=0.2, but a decreasing trend of the maximum drillable length is shown when K>0.2. When K<0.45, the larger inlet displacement value, the larger the maximum drillable length; when K>0.45, the result is the opposite. This shows that the ratio of K changes within a certain ratio range, and the inlet displacement has a greater impact on the maximum drillable length(3)
The simulations show that the self-propelled force is constantly increasing as the ratioF:B decreasing under the same inlet displacement condition. The self-propelled force increases by a larger magnitude when the flow rate Q<40L/min, and the magnitude tends to decrease as the inlet flow rate when Q>40L/min(4)
The comparison of numerical simulation results (Ln), mathematical results (Lm), and experiment results (Le) of the maximum drillable length are presented. The difference between Ln, Lm, and Le is very small, which proves that the simulation results are consistent with the experiment results with an average accuracy of 97.07%. Therefore, the proposed numerical model has a good performance in predicting the maximum drillable length of the multiorifice nozzles



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*Source: 2531181-2022-01-11.xml*