본 소개 자료는 International Symposium on Hydraulic Structures에서 발행한 “Performance Assessment of FLOW-3D and XFlow in the Numerical Modelling of Fish-bone Type Fishway Hydraulics” 논문을 기반으로 합니다.
Figure 1. Three main regions in the fish-bone-type fishway.
연구 배경 및 목적
문제 정의
어도(Fishway)는 물고기의 이동을 돕기 위해 설계된 수리 구조물이며, 수력학적 특성이 어류 이동에 미치는 영향을 평가하는 것이 중요함.
기존 수리 모델링 방법은 주로 실험적 접근법을 사용하였으며, 최근 CFD(Computational Fluid Dynamics)를 이용한 수치 해석이 널리 적용되고 있음.
기존의 **격자 기반(mesh-based) CFD 방법(FLOW-3D)**과 비격자(meshless) CFD 방법(XFlow) 간의 성능 차이를 평가하는 연구가 필요함.
연구 목적
FLOW-3D(FVM 기반)와 XFlow(Lattice Boltzmann Method 기반)의 수리학적 모델링 성능을 비교 분석.
어류 이동과 관련된 유동 구조(유속, 난류 특성, 흐름 깊이)를 평가하고 두 모델의 정확성을 비교.
실험 데이터와 시뮬레이션 결과를 비교하여 두 모델의 신뢰성을 검증.
연구 방법
어도(Fishway) 모델 설정
실험 환경: 길이 10m, 너비 1m의 실험 수로(flume) 내 fish-bone 형태 어도 모델 구축.
높은 유량(0.075 m³/s)에서는 두 모델 모두 유사한 유속 분포를 보였으나, 낮은 유량(0.016 m³/s)에서는 XFlow의 정확도가 낮음.
난류 특성 분석
FLOW-3D가 블록 후류 영역에서의 와류(Swirling Flow)를 보다 정밀하게 포착.
XFlow는 격자 해상도를 높이지 않으면 난류 구조를 정확히 표현하지 못함.
계산 비용 및 효율 비교
FLOW-3D는 시뮬레이션 정확도가 더 높지만, 계산 시간이 평균 9시간 소요.
XFlow는 7시간 내에 시뮬레이션을 완료하지만 정확도가 다소 낮음.
XFlow는 해상도를 증가시키면 정확도가 향상되지만 계산 시간이 4일로 증가.
결론 및 향후 연구
결론
FLOW-3D는 유동 구조 및 난류 특성을 보다 정밀하게 예측하며, 실험 결과와의 일치도가 높음.
XFlow는 상대적으로 빠른 계산 속도를 제공하지만 정확도가 다소 떨어짐.
FLOW-3D는 고해상도 격자 설정이 가능하여 복잡한 흐름을 모델링하는 데 더 적합함.
향후 연구 방향
다양한 어도 설계(블록 배열, 경사 변화)에 대한 추가 연구 수행.
고해상도 XFlow 모델링을 통한 정확도 개선 연구.
실제 어류 이동 데이터를 활용한 모델 보정 및 최적화 연구 진행.
연구의 의의
본 연구는 FLOW-3D와 XFlow의 수리학적 성능을 비교하고, 어도(Fishway) 모델링에서의 적용 가능성을 평가하였다. 결과적으로 FLOW-3D가 보다 높은 정확성을 보이며, 수리 구조물 설계 최적화에 중요한 도구가 될 수 있음을 확인하였다.
Figure 1. Three main regions in the fish-bone-type fishway.Figure 3. Stream traces for (a) FLOW-3D and (b) XFlow at 0.075 m3
/s.
References
Bayon, A., Valero, D., García-Bartual, R., Vallés-Morán, F.J., and López-Jiménez, P.A. (2016). “Performance assessment of OpenFOAM and FLOW-3D in the numerical modeling of a low Reynolds number hydraulic jump.” Environ. Model. Software, 80, 322-335.
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Chen, S.C., Wang, S.C., and Tfwala, S.S. (2017). “Hydraulics driven upstream migration of taiwanese indigenous fishes in a fish-bone-type fishway.” Ecol. Eng., 108(Part A), 179-193.
Flow Science (2012). Flow-3D User Manual: v10.1, Flow Science, Inc.
Harlow, F.H. (1964). “The Particle-in-Cell Computing Method for Fluid Dynamics.” Methods in Computational Physics, 3, 319-343.
Hirt, C.W., and Nichols, B.D. (1981). “Volume of fluid (VOF) method for the dynamics of free boundaries.” Journal of Computational Physics, 39(1), 201-225.
Hirt, C.W., and Sicilian, J.M. “A porosity technique for the definition of obstacles in rectangular cell meshes.” Proc., Proceeding 4th International Conference on Numerical Ship Hydrodynamics.
Kueh, T.C., Beh, S.L., Rilling, D., and Ooi, Y. (2014). “Numerical Analysis of Water Vortex Formation for the Water Vortex Power Plant.” International Journal of Innovation, Management and Technology, 5(2), 111-115.
Liu, J., Koshizuka, S., and Oka, Y. (2005). “A hybrid particle-mesh method for viscous, incompressible, multiphase flows.” Journal of Computational Physics, 202(1), 65-93.
Luo, L.S., Krafczyk, M., and Shyy, W. (2010). “Lattice Boltzmann Method for Computational Fluid Dynamics.” Encyclopedia of Aerospace Engineering, John Wiley & Sons, Ltd.
Markauskas, D., Kruggel-Emden, H., Sivanesapillai, R., and Steeb, H. (2017). “Comparative study on mesh-based and mesh-less coupled CFD-DEM methods to model particle-laden flow.” Powder Technology, 305, 78-88.
Yi Wei ;Genyu Chen;Nengru Tao;Wei Zhou https://doi.org/10.1063/5.0191504
In order to comprehensively reveal the evolutionary dynamics of the molten pool and the state of motion of the fluid during the high-precision laser powder bed fusion (HP-LPBF) process, this study aims to deeply investigate the specific manifestations of the multiphase flow, solidification phenomena, and heat transfer during the process by means of numerical simulation methods. Numerical simulation models of SS316L single-layer HP-LPBF formation with single and double tracks were constructed using the discrete element method and the computational fluid dynamics method. The effects of various factors such as Marangoni convection, surface tension, vapor recoil, gravity, thermal convection, thermal radiation, and evaporative heat dissipation on the heat and mass transfer in the molten pool have been paid attention to during the model construction process. The results show that the molten pool exhibits a “comet” shape, in which the temperature gradient at the front end of the pool is significantly larger than that at the tail end, with the highest temperature gradient up to 1.69 × 108 K/s. It is also found that the depth of the second track is larger than that of the first one, and the process parameter window has been determined preliminarily. In addition, the application of HP-LPBF technology helps to reduce the surface roughness and minimize the forming size.
Laser powder bed fusion (LPBF) has become a research hotspot in the field of additive manufacturing of metals due to its advantages of high-dimensional accuracy, good surface quality, high density, and high material utilization.1,2 With the rapid development of electronics, medical, automotive, biotechnology, energy, communication, and optics, the demand for microfabrication technology is increasing day by day.3 High-precision laser powder bed fusion (HP-LPBF) is one of the key manufacturing technologies for tiny parts in the fields of electronics, medical, automotive, biotechnology, energy, communication, and optics because of its process characteristics such as small focal spot diameter, small powder particle size, and thin powder layup layer thickness.4–13 Compared with LPBF, HP-LPBF has the significant advantages of smaller focal spot diameter, smaller powder particle size, and thinner layer thickness. These advantages make HP-LPBF perform better in producing micro-fine parts, high surface quality, and parts with excellent mechanical properties.
HP-LPBF is in the exploratory stage, and researchers have already done some exploratory studies on the focal spot diameter, the amount of defocusing, and the powder particle size. In order to explore the influence of changing the laser focal spot diameter on the LPBF process characteristics of the law, Wildman et al.14 studied five groups of different focal spot diameter LPBF forming 316L stainless steel (SS316L) processing effect, the smallest focal spot diameter of 26 μm, and the results confirm that changing the focal spot diameter can be achieved to achieve the energy control, so as to control the quality of forming. Subsequently, Mclouth et al.15 proposed the laser out-of-focus amount (focal spot diameter) parameter, which characterizes the distance between the forming plane and the laser focal plane. The laser energy density was controlled by varying the defocusing amount while keeping the laser parameters constant. Sample preparation at different focal positions was investigated, and their microstructures were characterized. The results show that the samples at the focal plane have finer microstructure than those away from the focal plane, which is the effect of higher power density and smaller focal spot diameter. In order to explore the influence of changing the powder particle size on the characteristics of the LPBF process, Qian et al.16 carried out single-track scanning simulations on powder beds with average powder particle sizes of 70 and 40 μm, respectively, and the results showed that the melt tracks sizes were close to each other under the same process parameters for the two particle-size distributions and that the molten pool of powder beds with small particles was more elongated and the edges of the melt tracks were relatively flat. In order to explore the superiority of HP-LPBF technology, Xu et al.17 conducted a comparative analysis of HP-LPBF and conventional LPBF of SS316L. The results showed that the average surface roughness of the top surface after forming by HP-LPBF could reach 3.40 μm. Once again, it was verified that HP-LPBF had higher forming quality than conventional LPBF. On this basis, Wei et al.6 comparatively analyzed the effects of different laser focal spot diameters on different powder particle sizes formed by LPBF. The results showed that the smaller the laser focal spot diameter, the fewer the defects on the top and side surfaces. The above research results confirm that reducing the laser focal spot diameter can obtain higher energy density and thus better forming quality.
LPBF involves a variety of complex systems and mechanisms, and the final quality of the part is influenced by a large number of process parameters.18–24 Some research results have shown that there are more than 50 factors affecting the quality of the specimen. The influencing factors are mainly categorized into three main groups: (1) laser parameters, (2) powder parameters, and (3) equipment parameters, which interact with each other to determine the final specimen quality. With the continuous development of technologies such as computational materials science and computational fluid dynamics (CFD), the method of studying the influence of different factors on the forming quality of LPBF forming process has been shifted from time-consuming and laborious experimental characterization to the use of numerical simulation methods. As a result, more and more researchers are adopting this approach for their studies. Currently, numerical simulation studies on LPBF are mainly focused on the exploration of molten pool, temperature distribution, and residual stresses.
Finite element simulation based on continuum mechanics and free surface fluid flow modeling based on fluid dynamics are two common approaches to study the behavior of LPBF molten pool.25–28 Finite element simulation focuses on the temperature and thermal stress fields, treats the powder bed as a continuum, and determines the molten pool size by plotting the elemental temperature above the melting point. In contrast, fluid dynamics modeling can simulate the 2D or 3D morphology of the metal powder pile and obtain the powder size and distribution by certain algorithms.29 The flow in the molten pool is mainly affected by recoil pressure and the Marangoni effect. By simulating the molten pool formation, it is possible to predict defects, molten pool shape, and flow characteristics, as well as the effect of process parameters on the molten pool geometry.30–34 In addition, other researchers have been conducted to optimize the laser processing parameters through different simulation methods and experimental data.35–46 Crystal growth during solidification is studied to further understand the effect of laser parameters on dendritic morphology and solute segregation.47–54 A multi-scale system has been developed to describe the fused deposition process during 3D printing, which is combined with the conductive heat transfer model and the dendritic solidification model.55,56
Relevant scholars have adopted various different methods for simulation, such as sequential coupling theory,57 Lagrangian and Eulerian thermal models,58 birth–death element method,25 and finite element method,59 in order to reveal the physical phenomena of the laser melting process and optimize the process parameters. Luo et al.60 compared the LPBF temperature field and molten pool under double ellipsoidal and Gaussian heat sources by ANSYS APDL and found that the diffusion of the laser energy in the powder significantly affects the molten pool size and the temperature field.
The thermal stresses obtained from the simulation correlate with the actual cracks,61 and local preheating can effectively reduce the residual stresses.62 A three-dimensional thermodynamic finite element model investigated the temperature and stress variations during laser-assisted fabrication and found that powder-to-solid conversion increases the temperature gradient, stresses, and warpage.63 Other scholars have predicted residual stresses and part deflection for LPBF specimens and investigated the effects of deposition pattern, heat, laser power, and scanning strategy on residual stresses, noting that high-temperature gradients lead to higher residual stresses.64–67
In short, the process of LPBF forming SS316L is extremely complex and usually involves drastic multi-scale physicochemical changes that will only take place on a very small scale. Existing literature employs DEM-based mesoscopic-scale numerical simulations to investigate the effects of process parameters on the molten pool dynamics of LPBF-formed SS316L. However, a few studies have been reported on the key mechanisms of heating and solidification, spatter, and convective behavior of the molten pool of HP-LPBF-formed SS316L with small laser focal spot diameters. In this paper, the geometrical properties of coarse and fine powder particles under three-dimensional conditions were first calculated using DEM. Then, numerical simulation models for single-track and double-track cases in the single-layer HP-LPBF forming SS316L process were developed at mesoscopic scale using the CFD method. The flow genesis of the melt in the single-track and double-track molten pools is discussed, and their 3D morphology and dimensional characteristics are discussed. In addition, the effects of laser process parameters, powder particle size, and laser focal spot diameter on the temperature field, characterization information, and defects in the molten pool are discussed.
II. MODELING
A. 3D powder bed modeling
HP-LPBF is an advanced processing technique for preparing target parts layer by layer stacking, the process of which involves repetitive spreading and melting of powders. In this process, both the powder spreading and the morphology of the powder bed are closely related to the results of the subsequent melting process, while the melted surface also affects the uniform distribution of the next layer of powder. For this reason, this chapter focuses on the modeling of the physical action during the powder spreading process and the theory of DEM to establish the numerical model of the powder bed, so as to lay a solid foundation for the accuracy of volume of fluid (VOF) and CFD.
1. DEM
DEM is a numerical technique for calculating the interaction of a large number of particles, which calculates the forces and motions of the spheres by considering each powder sphere as an independent unit. The motion of the powder particles follows the laws of classical Newtonian mechanics, including translational and rotational,38,68–70 which are expressed as follows:����¨=���+∑��ij,
(1)����¨=∑�(�ij×�ij),
(2)
where �� is the mass of unit particle i in kg, ��¨ is the advective acceleration in m/s2, And g is the gravitational acceleration in m/s2. �ij is the force in contact with the neighboring particle � in N. �� is the rotational inertia of the unit particle � in kg · m2. ��¨ is the unit particle � angular acceleration in rad/s2. �ij is the vector pointing from unit particle � to the contact point of neighboring particle �.
Equations (1) and (2) can be used to calculate the velocity and angular velocity variations of powder particles to determine their positions and velocities. A three-dimensional powder bed model of SS316L was developed using DEM. The powder particles are assumed to be perfect spheres, and the substrate and walls are assumed to be rigid. To describe the contact between the powder particles and between the particles and the substrate, a non-slip Hertz–Mindlin nonlinear spring-damping model71 was used with the following expression:�hz=��������+��[(�����ij−�eff����)−(�����+�eff����)],
(3)
where �hz is the force calculated using the Hertzian in M. �� and �� are the radius of unit particles � and � in m, respectively. �� is the overlap size of the two powder particles in m. ��, �� are the elastic constants in the normal and tangential directions, respectively. �ij is the unit vector connecting the centerlines of the two powder particles. �eff is the effective mass of the two powder particles in kg. �� and �� are the viscoelastic damping constants in the normal and tangential directions, respectively. �� and �� are the components of the relative velocities of the two powder particles. ��� is the displacement vector between two spherical particles. The schematic diagram of overlapping powder particles is shown in Fig. 1.
Schematic diagram of overlapping powder particles.
Because the particle size of the powder used for HP-LPBF is much smaller than 100 μm, the effect of van der Waals forces must be considered. Therefore, the cohesive force �jkr of the Hertz–Mindlin model was used instead of van der Waals forces,72 with the following expression:�jkr=−4��0�*�1.5+4�*3�*�3,
(4)1�*=(1−��2)��+(1−��2)��,
(5)1�*=1��+1��,
(6)
where �* is the equivalent Young’s modulus in GPa; �* is the equivalent particle radius in m; �0 is the surface energy of the powder particles in J/m2; α is the contact radius in m; �� and �� are the Young’s modulus of the unit particles � and �, respectively, in GPa; and �� and �� are the Poisson’s ratio of the unit particles � and �, respectively.
2. Model building
Figure 2 shows a 3D powder bed model generated using DEM with a coarse powder geometry of 1000 × 400 × 30 μm3. The powder layer thickness is 30 μm, and the powder bed porosity is 40%. The average particle size of this spherical powder is 31.7 μm and is normally distributed in the range of 15–53 μm. The geometry of the fine powder was 1000 × 400 × 20 μm3, with a layer thickness of 20 μm, and the powder bed porosity of 40%. The average particle size of this spherical powder is 11.5 μm and is normally distributed in the range of 5–25 μm. After the 3D powder bed model is generated, it needs to be imported into the CFD simulation software for calculation, and the imported geometric model is shown in Fig. 3. This geometric model is mainly composed of three parts: protective gas, powder bed, and substrate. Under the premise of ensuring the accuracy of the calculation, the mesh size is set to 3 μm, and the total number of coarse powder meshes is 1 704 940. The total number of fine powder meshes is 3 982 250.
Geometric modeling of the powder bed computational domain: (a) coarse powder, (b) fine powder.
B. Modeling of fluid mechanics simulation
In order to solve the flow, melting, and solidification problems involved in HP-LPBF molten pool, the study must follow the three governing equations of conservation of mass, conservation of energy, and conservation of momentum.73 The VOF method, which is the most widely used in fluid dynamics, is used to solve the molten pool dynamics model.
1. VOF
VOF is a method for tracking the free interface between the gas and liquid phases on the molten pool surface. The core idea of the method is to define a volume fraction function F within each grid, indicating the proportion of the grid space occupied by the material, 0 ≤ F ≤ 1 in Fig. 4. Specifically, when F = 0, the grid is empty and belongs to the gas-phase region; when F = 1, the grid is completely filled with material and belongs to the liquid-phase region; and when 0 < F < 1, the grid contains free surfaces and belongs to the mixed region. The direction normal to the free surface is the direction of the fastest change in the volume fraction F (the direction of the gradient of the volume fraction), and the direction of the gradient of the volume fraction can be calculated from the values of the volume fractions in the neighboring grids.74 The equations controlling the VOF are expressed as follows:𝛻����+�⋅(��→)=0,
(7)
where t is the time in s and �→ is the liquid velocity in m/s.
The material parameters of the mixing zone are altered due to the inclusion of both the gas and liquid phases. Therefore, in order to represent the density of the mixing zone, the average density �¯ is used, which is expressed as follows:72�¯=(1−�1)�gas+�1�metal,
(8)
where �1 is the proportion of liquid phase, �gas is the density of protective gas in kg/m3, and �metal is the density of metal in kg/m3.
2. Control equations and boundary conditions
Figure 5 is a schematic diagram of the HP-LPBF melting process. First, the laser light strikes a localized area of the material and rapidly heats up the area. Next, the energy absorbed in the region is diffused through a variety of pathways (heat conduction, heat convection, and surface radiation), and this process triggers complex phase transition phenomena (melting, evaporation, and solidification). In metals undergoing melting, the driving forces include surface tension and the Marangoni effect, recoil due to evaporation, and buoyancy due to gravity and uneven density. The above physical phenomena interact with each other and do not occur independently.
Laser heat sourceThe Gaussian surface heat source model is used as the laser heat source model with the following expression:�=2�0����2exp(−2�12��2),(9)where � is the heat flow density in W/m2, �0 is the absorption rate of SS316L, �� is the radius of the laser focal spot in m, and �1 is the radial distance from the center of the laser focal spot in m. The laser focal spot can be used for a wide range of applications.
Energy absorptionThe formula for calculating the laser absorption �0 of SS316L is as follows:�0=0.365(�0[1+�0(�−20)]/�)0.5,(10)where �0 is the direct current resistivity of SS316L at 20 °C in Ω m, �0 is the resistance temperature coefficient in ppm/°C, � is the temperature in °C, and � is the laser wavelength in m.
Heat transferThe basic principle of heat transfer is conservation of energy, which is expressed as follows:𝛻𝛻𝛻�(��)��+�·(��→�)=�·(�0����)+��,(11)where � is the density of liquid phase SS316L in kg/m3, �� is the specific heat capacity of SS316L in J/(kg K), 𝛻� is the gradient operator, t is the time in s, T is the temperature in K, 𝛻�� is the temperature gradient, �→ is the velocity vector, �0 is the coefficient of thermal conduction of SS316L in W/(m K), and �� is the thermal energy dissipation term in the molten pool.
Molten pool flowThe following three conditions need to be satisfied for the molten pool to flow:
Conservation of mass with the following expression:𝛻�·(��→)=0.(12)
Conservation of momentum (Navier–Stokes equation) with the following expression:𝛻𝛻𝛻𝛻���→��+�(�→·�)�→=�·[−pI+�(��→+(��→)�)]+�,(13)where � is the pressure in Pa exerted on the liquid phase SS316L microelement, � is the unit matrix, � is the fluid viscosity in N s/m2, and � is the volumetric force (gravity, atmospheric pressure, surface tension, vapor recoil, and the Marangoni effect).
Surface tension and the Marangoni effectThe effect of temperature on the surface tension coefficient is considered and set as a linear relationship with the following expression:�=�0−��dT(�−��),(14)where � is the surface tension of the molten pool at temperature T in N/m, �� is the melting temperature of SS316L in K, �0 is the surface tension of the molten pool at temperature �� in Pa, and σdσ/ dT is the surface tension temperature coefficient in N/(m K).In general, surface tension decreases with increasing temperature. A temperature gradient causes a gradient in surface tension that drives the liquid to flow, known as the Marangoni effect.
Metal vapor recoilAt higher input energy densities, the maximum temperature of the molten pool surface reaches the evaporation temperature of the material, and a gasification recoil pressure occurs vertically downward toward the molten pool surface, which will be the dominant driving force for the molten pool flow.75 The expression is as follows:��=0.54�� exp ���−���0���,(15)where �� is the gasification recoil pressure in Pa, �� is the ambient pressure in kPa, �� is the latent heat of evaporation in J/kg, �0 is the gas constant in J/(mol K), T is the surface temperature of the molten pool in K, and Te is the evaporation temperature in K.
Solid–liquid–gas phase transitionWhen the laser hits the powder layer, the powder goes through three stages: heating, melting, and solidification. During the solidification phase, mutual transformations between solid, liquid, and gaseous states occur. At this point, the latent heat of phase transition absorbed or released during the phase transition needs to be considered.68 The phase transition is represented based on the relationship between energy and temperature with the following expression:�=�����,(�<��),�(��)+�−����−����,(��<�<��)�(��)+(�−��)����,(��<�),,(16)where �� and �� are solid and liquid phase density, respectively, of SS316L in kg/m3. �� and �� unit volume of solid and liquid phase-specific heat capacity, respectively, of SS316L in J/(kg K). �� and ��, respectively, are the solidification temperature and melting temperature of SS316L in K. �� is the latent heat of the phase transition of SS316L melting in J/kg.
3. Assumptions
The CFD model was computed using the commercial software package FLOW-3D.76 In order to simplify the calculation and solution process while ensuring the accuracy of the results, the model makes the following assumptions:
It is assumed that the effects of thermal stress and material solid-phase thermal expansion on the calculation results are negligible.
The molten pool flow is assumed to be a Newtonian incompressible laminar flow, while the effects of liquid thermal expansion and density on the results are neglected.
It is assumed that the surface tension can be simplified to an equivalent pressure acting on the free surface of the molten pool, and the effect of chemical composition on the results is negligible.
Neglecting the effect of the gas flow field on the molten pool.
The mass loss due to evaporation of the liquid metal is not considered.
The influence of the plasma effect of the molten metal on the calculation results is neglected.
It is worth noting that the formulation of assumptions requires a trade-off between accuracy and computational efficiency. In the above models, some physical phenomena that have a small effect or high difficulty on the calculation results are simplified or ignored. Such simplifications make numerical simulations more efficient and computationally tractable, while still yielding accurate results.
4. Initial conditions
The preheating temperature of the substrate was set to 393 K, at which time all materials were in the solid state and the flow rate was zero.
5. Material parameters
The material used is SS316L and the relevant parameters required for numerical simulations are shown in Table I.46,77,78
TABLE I.
SS316L-related parameters.
Property
Symbol
Value
Density of solid metal (kg/m3)
�metal
7980
Solid phase line temperature (K)
��
1658
Liquid phase line temperature (K)
��
1723
Vaporization temperature (K)
��
3090
Latent heat of melting ( J/kg)
��
2.60×105
Latent heat of evaporation ( J/kg)
��
7.45×106
Surface tension of liquid phase (N /m)
�
1.60
Liquid metal viscosity (kg/m s)
��
6×10−3
Gaseous metal viscosity (kg/m s)
�gas
1.85×10−5
Temperature coefficient of surface tension (N/m K)
��/�T
0.80×10−3
Molar mass ( kg/mol)
M
0.05 593
Emissivity
�
0.26
Laser absorption
�0
0.35
Ambient pressure (kPa)
��
101 325
Ambient temperature (K)
�0
300
Stefan–Boltzmann constant (W/m2 K4)
�
5.67×10−8
Thermal conductivity of metals ( W/m K)
�
24.55
Density of protective gas (kg/m3)
�gas
1.25
Coefficient of thermal expansion (/K)
��
16×10−6
Generalized gas constant ( J/mol K)
R
8.314
III. RESULTS AND DISCUSSION
With the objective of studying in depth the evolutionary patterns of single-track and double-track molten pool development, detailed observations were made for certain specific locations in the model, as shown in Fig. 6. In this figure, P1 and P2 represent the longitudinal tangents to the centers of the two melt tracks in the XZ plane, while L1 is the transverse profile in the YZ plane. The scanning direction is positive and negative along the X axis. Points A and B are the locations of the centers of the molten pool of the first and second melt tracks, respectively (x = 1.995 × 10−4, y = 5 × 10−7, and z = −4.85 × 10−5).
A series of single-track molten pool simulation experiments were carried out in order to investigate the influence law of laser power as well as scanning speed on the HP-LPBF process. Figure 7 demonstrates the evolution of the 3D morphology and temperature field of the single-track molten pool in the time period of 50–500 μs under a laser power of 100 W and a scanning speed of 800 mm/s. The powder bed is in the natural cooling state. When t = 50 μs, the powder is heated by the laser heat and rapidly melts and settles to form the initial molten pool. This process is accompanied by partial melting of the substrate and solidification together with the melted powder. The molten pool rapidly expands with increasing width, depth, length, and temperature, as shown in Fig. 7(a). When t = 150 μs, the molten pool expands more obviously, and the temperature starts to transfer to the surrounding area, forming a heat-affected zone. At this point, the width of the molten pool tends to stabilize, and the temperature in the center of the molten pool has reached its peak and remains largely stable. However, the phenomenon of molten pool spatter was also observed in this process, as shown in Fig. 7(b). As time advances, when t = 300 μs, solidification begins to occur at the tail of the molten pool, and tiny ripples are produced on the solidified surface. This is due to the fact that the melt flows toward the region with large temperature gradient under the influence of Marangoni convection and solidifies together with the melt at the end of the bath. At this point, the temperature gradient at the front of the bath is significantly larger than at the end. While the width of the molten pool was gradually reduced, the shape of the molten pool was gradually changed to a “comet” shape. In addition, a slight depression was observed at the top of the bath because the peak temperature at the surface of the bath reached the evaporation temperature, which resulted in a recoil pressure perpendicular to the surface of the bath downward, creating a depressed region. As the laser focal spot moves and is paired with the Marangoni convection of the melt, these recessed areas will be filled in as shown in Fig. 7(c). It has been shown that the depressed regions are the result of the coupled effect of Marangoni convection, recoil pressure, and surface tension.79 By t = 500 μs, the width and height of the molten pool stabilize and show a “comet” shape in Fig. 7(d).
Single-track molten pool process: (a) t = 50 ��, (b) t = 150 ��, (c) t = 300 ��, (d) t = 500 ��.
Figure 8 depicts the velocity vector diagram of the P1 profile in a single-track molten pool, the length of the arrows represents the magnitude of the velocity, and the maximum velocity is about 2.36 m/s. When t = 50 μs, the molten pool takes shape, and the velocities at the two ends of the pool are the largest. The variation of the velocities at the front end is especially more significant in Fig. 8(a). As the time advances to t = 150 μs, the molten pool expands rapidly, in which the velocity at the tail increases and changes more significantly, while the velocity at the front is relatively small. At this stage, the melt moves backward from the center of the molten pool, which in turn expands the molten pool area. The melt at the back end of the molten pool center flows backward along the edge of the molten pool surface and then converges along the edge of the molten pool to the bottom center, rising to form a closed loop. Similarly, a similar closed loop is formed at the front end of the center of the bath, but with a shorter path. However, a large portion of the melt in the center of the closed loop formed at the front end of the bath is in a nearly stationary state. The main cause of this melt flow phenomenon is the effect of temperature gradient and surface tension (the Marangoni effect), as shown in Figs. 8(b) and 8(e). This dynamic behavior of the melt tends to form an “elliptical” pool. At t = 300 μs, the tendency of the above two melt flows to close the loop is more prominent and faster in Fig. 8(c). When t = 500 μs, the velocity vector of the molten pool shows a stable trend, and the closed loop of melt flow also remains stable. With the gradual laser focal spot movement, the melt is gradually solidified at its tail, and finally, a continuous and stable single track is formed in Fig. 8(d).
Vector plot of single-track molten pool velocity in XZ longitudinal section: (a) t = 50 ��, (b) t = 150 ��, (c) t = 300 ��, (d) t = 500 ��, (e) molten pool flow.
In order to explore in depth the transient evolution of the molten pool, the evolution of the single-track temperature field and the melt flow was monitored in the YZ cross section. Figure 9(a) shows the state of the powder bed at the initial moment. When t = 250 μs, the laser focal spot acts on the powder bed and the powder starts to melt and gradually collects in the molten pool. At this time, the substrate will also start to melt, and the melt flow mainly moves in the downward and outward directions and the velocity is maximum at the edges in Fig. 9(b). When t = 300 μs, the width and depth of the molten pool increase due to the recoil pressure. At this time, the melt flows more slowly at the center, but the direction of motion is still downward in Fig. 9(c). When t = 350 μs, the width and depth of the molten pool further increase, at which time the intensity of the melt flow reaches its peak and the direction of motion remains the same in Fig. 9(d). When t = 400 μs, the melt starts to move upward, and the surrounding powder or molten material gradually fills up, causing the surface of the molten pool to begin to flatten. At this time, the maximum velocity of the melt is at the center of the bath, while the velocity at the edge is close to zero, and the edge of the melt starts to solidify in Fig. 9(e). When t = 450 μs, the melt continues to move upward, forming a convex surface of the melt track. However, the melt movement slows down, as shown in Fig. 9(f). When t = 500 μs, the melt further moves upward and its speed gradually becomes smaller. At the same time, the melt solidifies further, as shown in Fig. 9(g). When t = 550 μs, the melt track is basically formed into a single track with a similar “mountain” shape. At this stage, the velocity is close to zero only at the center of the molten pool, and the flow behavior of the melt is poor in Fig. 9(h). At t = 600 μs, the melt stops moving and solidification is rapidly completed. Up to this point, a single track is formed in Fig. 9(i). During the laser action on the powder bed, the substrate melts and combines with the molten state powder. The powder-to-powder fusion is like the convergence of water droplets, which are rapidly fused by surface tension. However, the fusion between the molten state powder and the substrate occurs driven by surface tension, and the molten powder around the molten pool is pulled toward the substrate (a wetting effect occurs), which ultimately results in the formation of a monolithic whole.38,80,81
Evolution of single-track molten pool temperature and melt flow in the YZ cross section: (a) t = 0 ��, (b) t = 250 ��, (c) t = 300 ��, (d) t = 350 ��, (e) t = 400 ��, (f) t = 450 ��, (g) t = 500 ��, (h) t = 550 ��, (i) t = 600 ��.
The wetting ability between the liquid metal and the solid substrate in the molten pool directly affects the degree of balling of the melt,82,83 and the wetting ability can be measured by the contact angle of a single track in Fig. 10. A smaller value of contact angle represents better wettability. The contact angle α can be calculated by�=�1−�22,
(17)
where �1 and �2 are the contact angles of the left and right regions, respectively.
Relevant studies have confirmed that the wettability is better at a contact angle α around or below 40°.84 After measurement, a single-track contact angle α of about 33° was obtained under this process parameter, which further confirms the good wettability.
B. Double-track simulation
In order to deeply investigate the influence of hatch spacing on the characteristics of the HP-LPBF process, a series of double-track molten pool simulation experiments were systematically carried out. Figure 11 shows in detail the dynamic changes of the 3D morphology and temperature field of the double-track molten pool in the time period of 2050–2500 μs under the conditions of laser power of 100 W, scanning speed of 800 mm/s, and hatch spacing of 0.06 mm. By comparing the study with Fig. 7, it is observed that the basic characteristics of the 3D morphology and temperature field of the second track are similar to those of the first track. However, there are subtle differences between them. The first track exhibits a basically symmetric shape, but the second track morphology shows a slight deviation influenced by the difference in thermal diffusion rate between the solidified metal and the powder. Otherwise, the other characteristic information is almost the same as that of the first track. Figure 12 shows the velocity vector plot of the P2 profile in the double-track molten pool, with a maximum velocity of about 2.63 m/s. The melt dynamics at both ends of the pool are more stable at t = 2050 μs, where the maximum rate of the second track is only 1/3 of that of the first one. Other than that, the rest of the information is almost no significant difference from the characteristic information of the first track. Figure 13 demonstrates a detailed observation of the double-track temperature field and melts flow in the YZ cross section, and a comparative study with Fig. 9 reveals that the width of the second track is slightly wider. In addition, after the melt direction shifts from bottom to top, the first track undergoes four time periods (50 μs) to reach full solidification, while the second track takes five time periods. This is due to the presence of significant heat buildup in the powder bed after the forming of the first track, resulting in a longer dynamic time of the melt and an increased molten pool lifetime. In conclusion, the level of specimen forming can be significantly optimized by adjusting the laser power and hatch spacing.
Evolution of double-track molten pool temperature and melt flow in the YZ cross section: (a) t = 2250 ��, (b) t = 2300 ��, (c) t = 2350 ��, (d) t = 2400 ��, (e) t = 2450 ��, (f) t = 2500 ��, (g) t = 2550 ��, (h) t = 2600 ��, (i) t = 2650 ��.
In order to quantitatively detect the molten pool dimensions as well as the remolten region dimensions, the molten pool characterization information in Fig. 14 is constructed by drawing the boundary on the YZ cross section based on the isothermal surface of the liquid phase line. It can be observed that the heights of the first track and second track are basically the same, but the depth of the second track increases relative to the first track. The molten pool width is mainly positively correlated with the laser power as well as the scanning speed (the laser line energy density �). However, the remelted zone width is negatively correlated with the hatch spacing (the overlapping ratio). Overall, the forming quality of the specimens can be directly influenced by adjusting the laser power, scanning speed, and hatch spacing.
Double-track molten pool characterization information on YZ cross section.
In order to study the variation rule of the temperature in the center of the molten pool with time, Fig. 15 demonstrates the temperature variation curves with time for two reference points, A and B. Among them, the red dotted line indicates the liquid phase line temperature of SS316L. From the figure, it can be seen that the maximum temperature at the center of the molten pool in the first track is lower than that in the second track, which is mainly due to the heat accumulation generated after passing through the first track. The maximum temperature gradient was calculated to be 1.69 × 108 K/s. When the laser scanned the first track, the temperature in the center of the molten pool of the second track increased slightly. Similarly, when the laser scanned the second track, a similar situation existed in the first track. Since the temperature gradient in the second track is larger than that in the first track, the residence time of the liquid phase in the molten pool of the first track is longer than that of the second track.
Temperature profiles as a function of time for two reference points A and B.
C. Simulation analysis of molten pool under different process parameters
In order to deeply investigate the effects of various process parameters on the mesoscopic-scale temperature field, molten pool characteristic information and defects of HP-LPBF, numerical simulation experiments on mesoscopic-scale laser power, scanning speed, and hatch spacing of double-track molten pools were carried out.
1. Laser power
Figure 16 shows the effects of different laser power on the morphology and temperature field of the double-track molten pool at a scanning speed of 800 mm/s and a hatch spacing of 0.06 mm. When P = 50 W, a smaller molten pool is formed due to the lower heat generated by the Gaussian light source per unit time. This leads to a smaller track width, which results in adjacent track not lapping properly and the presence of a large number of unmelted powder particles, resulting in an increase in the number of defects, such as pores in the specimen. The surface of the track is relatively flat, and the depth is small. In addition, the temperature gradient before and after the molten pool was large, and the depression location appeared at the biased front end in Fig. 16(a). When P = 100 W, the surface of the track is flat and smooth with excellent lap. Due to the Marangoni effect, the velocity field of the molten pool is in the form of “vortex,” and the melt has good fluidity, and the maximum velocity reaches 2.15 m/s in Fig. 16(b). When P = 200 W, the heat generated by the Gaussian light source per unit time is too large, resulting in the melt rapidly reaching the evaporation temperature, generating a huge recoil pressure, forming a large molten pool, and the surface of the track is obviously raised. The melt movement is intense, especially the closed loop at the center end of the molten pool. At this time, the depth and width of the molten pool are large, leading to the expansion of the remolten region and the increased chance of the appearance of porosity defects in Fig. 16(c). The results show that at low laser power, the surface tension in the molten pool is dominant. At high laser power, recoil pressure is its main role.
Simulation results of double-track molten pool under different laser powers: (a) P = 50 W, (b) P = 100 W, (c) P = 200 W.
Table II shows the effect of different laser powers on the characteristic information of the double-track molten pool at a scanning speed of 800 mm/s and a hatch spacing of 0.06 mm. The negative overlapping ratio in the table indicates that the melt tracks are not lapped, and 26/29 indicates the melt depth of the first track/second track. It can be seen that with the increase in laser power, the melt depth, melt width, melt height, and remelted zone show a gradual increase. At the same time, the overlapping ratio also increases. Especially in the process of laser power from 50 to 200 W, the melting depth and melting width increased the most, which increased nearly 2 and 1.5 times, respectively. Meanwhile, the overlapping ratio also increases with the increase in laser power, which indicates that the melting and fusion of materials are better at high laser power. On the other hand, the dimensions of the molten pool did not change uniformly with the change of laser power. Specifically, the depth-to-width ratio of the molten pool increased from about 0.30 to 0.39 during the increase from 50 to 120 W, which further indicates that the effective heat transfer in the vertical direction is greater than that in the horizontal direction with the increase in laser power. This dimensional response to laser power is mainly affected by the recoil pressure and also by the difference in the densification degree between the powder layer and the metal substrate. In addition, according to the experimental results, the contact angle shows a tendency to increase and then decrease during the process of laser power increase, and always stays within the range of less than 33°. Therefore, in practical applications, it is necessary to select the appropriate laser power according to the specific needs in order to achieve the best processing results.
TABLE II.
Double-track molten pool characterization information at different laser powers.
Laser power (W)
Depth (μm)
Width (μm)
Height (μm)
Remolten region (μm)
Overlapping ratio (%)
Contact angle (°)
50
16
54
11
/
−10
23
100
26/29
74
14
18
23.33
33
200
37/45
116
21
52
93.33
28
2. Scanning speed
Figure 17 demonstrates the effect of different scanning speeds on the morphology and temperature field of the double-track molten pool at a laser power of 100 W and a hatch spacing of 0.06 mm. With the gradual increase in scanning speed, the surface morphology of the molten pool evolves from circular to elliptical. When � = 200 mm/s, the slow scanning speed causes the material to absorb too much heat, which is very easy to trigger the overburning phenomenon. At this point, the molten pool is larger and the surface morphology is uneven. This situation is consistent with the previously discussed scenario with high laser power in Fig. 17(a). However, when � = 1600 mm/s, the scanning speed is too fast, resulting in the material not being able to absorb sufficient heat, which triggers the powder particles that fail to melt completely to have a direct effect on the bonding of the melt to the substrate. At this time, the molten pool volume is relatively small and the neighboring melt track cannot lap properly. This result is consistent with the previously discussed case of low laser power in Fig. 17(b). Overall, the ratio of the laser power to the scanning speed (the line energy density �) has a direct effect on the temperature field and surface morphology of the molten pool.
Simulation results of double-track molten pool under different scanning speed: (a) � = 200 mm/s, (b) � = 1600 mm/s.
Table III shows the effects of different scanning speed on the characteristic information of the double-track molten pool under the condition of laser power of 100 W and hatch spacing of 0.06 mm. It can be seen that the scanning speed has a significant effect on the melt depth, melt width, melt height, remolten region, and overlapping ratio. With the increase in scanning speed, the melt depth, melt width, melt height, remelted zone, and overlapping ratio show a gradual decreasing trend. Among them, the melt depth and melt width decreased faster, while the melt height and remolten region decreased relatively slowly. In addition, when the scanning speed was increased from 200 to 800 mm/s, the decreasing speeds of melt depth and melt width were significantly accelerated, while the decreasing speeds of overlapping ratio were relatively slow. When the scanning speed was further increased to 1600 mm/s, the decreasing speeds of melt depth and melt width were further accelerated, and the un-lapped condition of the melt channel also appeared. In addition, the contact angle increases and then decreases with the scanning speed, and both are lower than 33°. Therefore, when selecting the scanning speed, it is necessary to make reasonable trade-offs according to the specific situation, and take into account the factors of melt depth, melt width, melt height, remolten region, and overlapping ratio, in order to achieve the best processing results.
TABLE III.
Double-track molten pool characterization information at different scanning speeds.
Scanning speed (mm/s)
Depth (μm)
Width (μm)
Height (μm)
Remolten region (μm)
Overlapping ratio (%)
Contact angle (°)
200
55/68
182
19/32
124
203.33
22
1600
13
50
11
/
−16.67
31
3. Hatch spacing
Figure 18 shows the effect of different hatch spacing on the morphology and temperature field of the double-track molten pool under the condition of laser power of 100 W and scanning speed of 800 mm/s. The surface morphology and temperature field of the first track and second track are basically the same, but slightly different. The first track shows a basically symmetric morphology along the scanning direction, while the second track shows a slight offset due to the difference in the heat transfer rate between the solidified material and the powder particles. When the hatch spacing is too small, the overlapping ratio increases and the probability of defects caused by remelting phenomenon grows. When the hatch spacing is too large, the neighboring melt track cannot overlap properly, and the powder particles are not completely melted, leading to an increase in the number of holes. In conclusion, the ratio of the line energy density � to the hatch spacing (the volume energy density E) has a significant effect on the temperature field and surface morphology of the molten pool.
Simulation results of double-track molten pool under different hatch spacings: (a) H = 0.03 mm, (b) H = 0.12 mm.
Table IV shows the effects of different hatch spacing on the characteristic information of the double-track molten pool under the condition of laser power of 100 W and scanning speed of 800 mm/s. It can be seen that the hatch spacing has little effect on the melt depth, melt width, and melt height, but has some effect on the remolten region. With the gradual expansion of hatch spacing, the remolten region shows a gradual decrease. At the same time, the overlapping ratio also decreased with the increase in hatch spacing. In addition, it is observed that the contact angle shows a tendency to increase and then remain stable when the hatch spacing increases, which has a more limited effect on it. Therefore, trade-offs and decisions need to be made on a case-by-case basis when selecting the hatch spacing.
TABLE IV.
Double-track molten pool characterization information at different hatch spacings.
Hatch spacing (mm)
Depth (μm)
Width (μm)
Height (μm)
Remolten region (μm)
Overlapping ratio (%)
Contact angle (°)
0.03
25/27
82
14
59
173.33
30
0.12
26
78
14
/
−35
33
In summary, the laser power, scanning speed, and hatch spacing have a significant effect on the formation of the molten pool, and the correct selection of these three process parameters is crucial to ensure the forming quality. In addition, the melt depth of the second track is slightly larger than that of the first track at higher line energy density � and volume energy density E. This is mainly due to the fact that a large amount of heat accumulation is generated after the first track, forming a larger molten pool volume, which leads to an increase in the melt depth.
D. Simulation analysis of molten pool with powder particle size and laser focal spot diameter
Figure 19 demonstrates the effect of different powder particle sizes and laser focal spot diameters on the morphology and temperature field of the double-track molten pool under a laser power of 100 W, a scanning speed of 800 mm/s, and a hatch spacing of 0.06 mm. In the process of melting coarse powder with small laser focal spot diameter, the laser energy cannot completely melt the larger powder particles, resulting in their partial melting and further generating excessive pore defects. The larger powder particles tend to generate zigzag molten pool edges, which cause an increase in the roughness of the melt track surface. In addition, the molten pool is also prone to generate the present spatter phenomenon, which can directly affect the quality of forming. The volume of the formed molten pool is relatively small, while the melt depth, melt width, and melt height are all smaller relative to the fine powder in Fig. 19(a). In the process of melting fine powders with a large laser focal spot diameter, the laser energy is able to melt the fine powder particles sufficiently, even to the point of overmelting. This results in a large number of fine spatters being generated at the edge of the molten pool, which causes porosity defects in the melt track in Fig. 19(b). In addition, the maximum velocity of the molten pool is larger for large powder particle sizes compared to small powder particle sizes, which indicates that the temperature gradient in the molten pool is larger for large powder particle sizes and the melt motion is more intense. However, the size of the laser focal spot diameter has a relatively small effect on the melt motion. However, a larger focal spot diameter induces a larger melt volume with greater depth, width, and height. In conclusion, a small powder size helps to reduce the surface roughness of the specimen, and a small laser spot diameter reduces the minimum forming size of a single track.
Simulation results of double-track molten pool with different powder particle size and laser focal spot diameter: (a) focal spot = 25 μm, coarse powder, (b) focal spot = 80 μm, fine powder.
Table V shows the maximum temperature gradient at the reference point for different powder sizes and laser focal spot diameters. As can be seen from the table, the maximum temperature gradient is lower than that of HP-LPBF for both coarse powders with a small laser spot diameter and fine powders with a large spot diameter, a phenomenon that leads to an increase in the heat transfer rate of HP-LPBF, which in turn leads to a corresponding increase in the cooling rate and, ultimately, to the formation of finer microstructures.
TABLE V.
Maximum temperature gradient at the reference point for different powder particle sizes and laser focal spot diameters.
Laser power (W)
Scanning speed (mm/s)
Hatch spacing (mm)
Average powder size (μm)
Laser focal spot diameter (μm)
Maximum temperature gradient (×107 K/s)
100
800
0.06
31.7
25
7.89
11.5
80
7.11
IV. CONCLUSIONS
In this study, the geometrical characteristics of 3D coarse and fine powder particles were first calculated using DEM and then numerical simulations of single track and double track in the process of forming SS316L from monolayer HP-LPBF at mesoscopic scale were developed using CFD method. The effects of Marangoni convection, surface tension, recoil pressure, gravity, thermal convection, thermal radiation, and evaporative heat dissipation on the heat and mass transfer in the molten pool were considered in this model. The effects of laser power, scanning speed, and hatch spacing on the dynamics of the single-track and double-track molten pools, as well as on other characteristic information, were investigated. The effects of the powder particle size on the molten pool were investigated comparatively with the laser focal spot diameter. The main conclusions are as follows:
The results show that the temperature gradient at the front of the molten pool is significantly larger than that at the tail, and the molten pool exhibits a “comet” morphology. At the top of the molten pool, there is a slightly concave region, which is the result of the coupling of Marangoni convection, recoil pressure, and surface tension. The melt flow forms two closed loops, which are mainly influenced by temperature gradients and surface tension. This special dynamic behavior of the melt tends to form an “elliptical” molten pool and an almost “mountain” shape in single-track forming.
The basic characteristics of the three-dimensional morphology and temperature field of the second track are similar to those of the first track, but there are subtle differences. The first track exhibits a basically symmetrical shape; however, due to the difference in thermal diffusion rates between the solidified metal and the powder, a slight asymmetry in the molten pool morphology of the second track occurs. After forming through the first track, there is a significant heat buildup in the powder bed, resulting in a longer dynamic time of the melt, which increases the life of the molten pool. The heights of the first track and second track remained essentially the same, but the depth of the second track was greater relative to the first track. In addition, the maximum temperature gradient was 1.69 × 108 K/s during HP-LPBF forming.
At low laser power, the surface tension in the molten pool plays a dominant role. At high laser power, recoil pressure becomes the main influencing factor. With the increase of laser power, the effective heat transfer in the vertical direction is superior to that in the horizontal direction. With the gradual increase of scanning speed, the surface morphology of the molten pool evolves from circular to elliptical. In addition, the scanning speed has a significant effect on the melt depth, melt width, melt height, remolten region, and overlapping ratio. Too large or too small hatch spacing will lead to remelting or non-lap phenomenon, which in turn causes the formation of defects.
When using a small laser focal spot diameter, it is difficult to completely melt large powder particle sizes, resulting in partial melting and excessive porosity generation. At the same time, large powder particles produce curved edges of the molten pool, resulting in increased surface roughness of the melt track. In addition, spatter occurs, which directly affects the forming quality. At small focal spot diameters, the molten pool volume is relatively small, and the melt depth, the melt width, and the melt height are correspondingly small. Taken together, the small powder particle size helps to reduce surface roughness, while the small spot diameter reduces the forming size.
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웨어의 두 가지 서로 다른 배열(즉, 직선형 웨어와 직사각형 미로 웨어)을 사용하여 웨어 모양, 웨어 간격, 웨어의 오리피스 존재, 흐름 영역에 대한 바닥 경사와 같은 기하학적 매개변수의 영향을 평가했습니다.
유량과 수심의 관계, 수심 평균 속도의 변화와 분포, 난류 특성, 어도에서의 에너지 소산. 흐름 조건에 미치는 영향을 조사하기 위해 FLOW-3D® 소프트웨어를 사용하여 전산 유체 역학 시뮬레이션을 수행했습니다.
수치 모델은 계산된 표면 프로파일과 속도를 문헌의 실험적으로 측정된 값과 비교하여 검증되었습니다. 수치 모델과 실험 데이터의 결과, 급락유동의 표면 프로파일과 표준화된 속도 프로파일에 대한 평균 제곱근 오차와 평균 절대 백분율 오차가 각각 0.014m와 3.11%로 나타나 수치 모델의 능력을 확인했습니다.
수영장과 둑의 흐름 특성을 예측합니다. 각 모델에 대해 L/B = 1.83(L: 웨어 거리, B: 수로 폭) 값에서 급락 흐름이 발생할 수 있고 L/B = 0.61에서 스트리밍 흐름이 발생할 수 있습니다. 직사각형 미로보 모델은 기존 모델보다 무차원 방류량(Q+)이 더 큽니다.
수중 흐름의 기존 보와 직사각형 미로 보의 경우 Q는 각각 1.56과 1.47h에 비례합니다(h: 보 위 수심). 기존 웨어의 풀 내 평균 깊이 속도는 직사각형 미로 웨어의 평균 깊이 속도보다 높습니다.
그러나 주어진 방류량, 바닥 경사 및 웨어 간격에 대해 난류 운동 에너지(TKE) 및 난류 강도(TI) 값은 기존 웨어에 비해 직사각형 미로 웨어에서 더 높습니다. 기존의 웨어는 직사각형 미로 웨어보다 에너지 소산이 더 낮습니다.
더 낮은 TKE 및 TI 값은 미로 웨어 상단, 웨어 하류 벽 모서리, 웨어 측벽과 채널 벽 사이에서 관찰되었습니다. 보와 바닥 경사면 사이의 거리가 증가함에 따라 평균 깊이 속도, 난류 운동 에너지의 평균값 및 난류 강도가 증가하고 수영장의 체적 에너지 소산이 감소했습니다.
둑에 개구부가 있으면 평균 깊이 속도와 TI 값이 증가하고 풀 내에서 가장 높은 TKE 범위가 감소하여 두 모델 모두에서 물고기를 위한 휴식 공간이 더 넓어지고(TKE가 낮아짐) 에너지 소산율이 감소했습니다.
Two different arrangements of the weir (i.e., straight weir and rectangular labyrinth weir) were used to evaluate the effects of geometric parameters such as weir shape, weir spacing, presence of an orifice at the weir, and bed slope on the flow regime and the relationship between discharge and depth, variation and distribution of depth-averaged velocity, turbulence characteristics, and energy dissipation at the fishway. Computational fluid dynamics simulations were performed using FLOW-3D® software to examine the effects on flow conditions. The numerical model was validated by comparing the calculated surface profiles and velocities with experimentally measured values from the literature. The results of the numerical model and experimental data showed that the root-mean-square error and mean absolute percentage error for the surface profiles and normalized velocity profiles of plunging flows were 0.014 m and 3.11%, respectively, confirming the ability of the numerical model to predict the flow characteristics of the pool and weir. A plunging flow can occur at values of L/B = 1.83 (L: distance of the weir, B: width of the channel) and streaming flow at L/B = 0.61 for each model. The rectangular labyrinth weir model has larger dimensionless discharge values (Q+) than the conventional model. For the conventional weir and the rectangular labyrinth weir at submerged flow, Q is proportional to 1.56 and 1.47h, respectively (h: the water depth above the weir). The average depth velocity in the pool of a conventional weir is higher than that of a rectangular labyrinth weir. However, for a given discharge, bed slope, and weir spacing, the turbulent kinetic energy (TKE) and turbulence intensity (TI) values are higher for a rectangular labyrinth weir compared to conventional weir. The conventional weir has lower energy dissipation than the rectangular labyrinth weir. Lower TKE and TI values were observed at the top of the labyrinth weir, at the corner of the wall downstream of the weir, and between the side walls of the weir and the channel wall. As the distance between the weirs and the bottom slope increased, the average depth velocity, the average value of turbulent kinetic energy and the turbulence intensity increased, and the volumetric energy dissipation in the pool decreased. The presence of an opening in the weir increased the average depth velocity and TI values and decreased the range of highest TKE within the pool, resulted in larger resting areas for fish (lower TKE), and decreased the energy dissipation rates in both models.
1 Introduction
Artificial barriers such as detour dams, weirs, and culverts in lakes and rivers prevent fish from migrating and completing the upstream and downstream movement cycle. This chain is related to the life stage of the fish, its location, and the type of migration. Several riverine fish species instinctively migrate upstream for spawning and other needs. Conversely, downstream migration is a characteristic of early life stages [1]. A fish ladder is a waterway that allows one or more fish species to cross a specific obstacle. These structures are constructed near detour dams and other transverse structures that have prevented such migration by allowing fish to overcome obstacles [2]. The flow pattern in fish ladders influences safe and comfortable passage for ascending fish. The flow’s strong turbulence can reduce the fish’s speed, injure them, and delay or prevent them from exiting the fish ladder. In adult fish, spawning migrations are usually complex, and delays are critical to reproductive success [3].
Various fish ladders/fishways include vertical slots, denil, rock ramps, and pool weirs [1]. The choice of fish ladder usually depends on many factors, including water elevation, space available for construction, and fish species. Pool and weir structures are among the most important fish ladders that help fish overcome obstacles in streams or rivers and swim upstream [1]. Because they are easy to construct and maintain, this type of fish ladder has received considerable attention from researchers and practitioners. Such a fish ladder consists of a sloping-floor channel with series of pools directly separated by a series of weirs [4]. These fish ladders, with or without underwater openings, are generally well-suited for slopes of 10% or less [1, 2]. Within these pools, flow velocities are low and provide resting areas for fish after they enter the fish ladder. After resting in the pools, fish overcome these weirs by blasting or jumping over them [2]. There may also be an opening in the flooded portion of the weir through which the fish can swim instead of jumping over the weir. Design parameters such as the length of the pool, the height of the weir, the slope of the bottom, and the water discharge are the most important factors in determining the hydraulic structure of this type of fish ladder [3]. The flow over the weir depends on the flow depth at a given slope S0 and the pool length, either “plunging” or “streaming.” In plunging flow, the water column h over each weir creates a water jet that releases energy through turbulent mixing and diffusion mechanisms [5]. The dimensionless discharges for plunging (Q+) and streaming (Q*) flows are shown in Fig. 1, where Q is the total discharge, B is the width of the channel, w is the weir height, S0 is the slope of the bottom, h is the water depth above the weir, d is the flow depth, and g is the acceleration due to gravity. The maximum velocity occurs near the top of the weir for plunging flow. At the water’s surface, it drops to about half [6].
Fig. 1
Extensive experimental studies have been conducted to investigate flow patterns for various physical geometries (i.e., bed slope, pool length, and weir height) [2]. Guiny et al. [7] modified the standard design by adding vertical slots, orifices, and weirs in fishways. The efficiency of the orifices and vertical slots was related to the velocities at their entrances. In the laboratory experiments of Yagci [8], the three-dimensional (3D) mean flow and turbulence structure of a pool weir fishway combined with an orifice and a slot is investigated. It is shown that the energy dissipation per unit volume and the discharge have a linear relationship.
Considering the beneficial characteristics reported in the limited studies of researchers on the labyrinth weir in the pool-weir-type fishway, and knowing that the characteristics of flow in pool-weir-type fishways are highly dependent on the geometry of the weir, an alternative design of the rectangular labyrinth weir instead of the straight weirs in the pool-weir-type fishway is investigated in this study [7, 9]. Kim [10] conducted experiments to compare the hydraulic characteristics of three different weir types in a pool-weir-type fishway. The results show that a straight, rectangular weir with a notch is preferable to a zigzag or trapezoidal weir. Studies on natural fish passes show that pass ability can be improved by lengthening the weir’s crest [7]. Zhong et al. [11] investigated the semi-rigid weir’s hydraulic performance in the fishway’s flow field with a pool weir. The results showed that this type of fishway performed better with a lower invert slope and a smaller radius ratio but with a larger pool spacing.
Considering that an alternative method to study the flow characteristics in a fishway with a pool weir is based on numerical methods and modeling from computational fluid dynamics (CFD), which can easily change the geometry of the fishway for different flow fields, this study uses the powerful package CFD and the software FLOW-3D to evaluate the proposed weir design and compare it with the conventional one to extend the application of the fishway. The main objective of this study was to evaluate the hydraulic performance of the rectangular labyrinth pool and the weir with submerged openings in different hydraulic configurations. The primary objective of creating a new weir configuration for suitable flow patterns is evaluated based on the swimming capabilities of different fish species. Specifically, the following questions will be answered: (a) How do the various hydraulic and geometric parameters relate to the effects of water velocity and turbulence, expressed as turbulent kinetic energy (TKE) and turbulence intensity (TI) within the fishway, i.e., are conventional weirs more affected by hydraulics than rectangular labyrinth weirs? (b) Which weir configurations have the greatest effect on fish performance in the fishway? (c) In the presence of an orifice plate, does the performance of each weir configuration differ with different weir spacing, bed gradients, and flow regimes from that without an orifice plate?
2 Materials and Methods
2.1 Physical Model Configuration
This paper focuses on Ead et al. [6]’s laboratory experiments as a reference, testing ten pool weirs (Fig. 2). The experimental flume was 6 m long, 0.56 m wide, and 0.6 m high, with a bottom slope of 10%. Field measurements were made at steady flow with a maximum flow rate of 0.165 m3/s. Discharge was measured with magnetic flow meters in the inlets and water level with point meters (see Ead et al. [6]. for more details). Table 1 summarizes the experimental conditions considered for model calibration in this study.
Fig. 2
Table 1 Experimental conditions considered for calibration
Computational fluid dynamics (CFD) simulations were performed using FLOW-3D® v11.2 to validate a series of experimental liner pool weirs by Ead et al. [6] and to investigate the effects of the rectangular labyrinth pool weir with an orifice. The dimensions of the channel and data collection areas in the numerical models are the same as those of the laboratory model. Two types of pool weirs were considered: conventional and labyrinth. The proposed rectangular labyrinth pool weirs have a symmetrical cross section and are sized to fit within the experimental channel. The conventional pool weir model had a pool length of l = 0.685 and 0.342 m, a weir height of w = 0.141 m, a weir width of B = 0.56 m, and a channel slope of S0 = 5 and 10%. The rectangular labyrinth weirs have the same front width as the offset, i.e., a = b = c = 0.186 m. A square underwater opening with a width of 0.05 m and a depth of 0.05 m was created in the middle of the weir. The weir configuration considered in the present study is shown in Fig. 3.
Fig. 3
2.3 Governing Equations
FLOW-3D® software solves the Navier–Stokes–Reynolds equations for three-dimensional analysis of incompressible flows using the fluid-volume method on a gridded domain. FLOW -3D® uses an advanced free surface flow tracking algorithm (TruVOF) developed by Hirt and Nichols [12], where fluid configurations are defined in terms of a VOF function F (x, y, z, t). In this case, F (fluid fraction) represents the volume fraction occupied by the fluid: F = 1 in cells filled with fluid and F = 0 in cells without fluid (empty areas) [4, 13]. The free surface area is at an intermediate value of F. (Typically, F = 0.5, but the user can specify a different intermediate value.) The equations in Cartesian coordinates (x, y, z) applicable to the model are as follows:
�f∂�∂�+∂(���x)∂�+∂(���y)∂�+∂(���z)∂�=�SOR
(1)
∂�∂�+1�f(��x∂�∂�+��y∂�∂�+��z∂�∂�)=−1�∂�∂�+�x+�x
(2)
∂�∂�+1�f(��x∂�∂�+��y∂�∂�+��z∂�∂�)=−1�∂�∂�+�y+�y
(3)
∂�∂�+1�f(��x∂�∂�+��y∂�∂�+��z∂�∂�)=−1�∂�∂�+�z+�z
(4)
where (u, v, w) are the velocity components, (Ax, Ay, Az) are the flow area components, (Gx, Gy, Gz) are the mass accelerations, and (fx, fy, fz) are the viscous accelerations in the directions (x, y, z), ρ is the fluid density, RSOR is the spring term, Vf is the volume fraction associated with the flow, and P is the pressure. The k–ε turbulence model (RNG) was used in this study to solve the turbulence of the flow field. This model is a modified version of the standard k–ε model that improves performance. The model is a two-equation model; the first equation (Eq. 5) expresses the turbulence’s energy, called turbulent kinetic energy (k) [14]. The second equation (Eq. 6) is the turbulent dissipation rate (ε), which determines the rate of dissipation of kinetic energy [15]. These equations are expressed as follows Dasineh et al. [4]:
In these equations, k is the turbulent kinetic energy, ε is the turbulent energy consumption rate, Gk is the generation of turbulent kinetic energy by the average velocity gradient, with empirical constants αε = αk = 1.39, C1ε = 1.42, and C2ε = 1.68, eff is the effective viscosity, μeff = μ + μt [15]. Here, μ is the hydrodynamic density coefficient, and μt is the turbulent density of the fluid.
2.4 Meshing and the Boundary Conditions in the Model Setup
The numerical area is divided into three mesh blocks in the X-direction. The meshes are divided into different sizes, a containing mesh block for the entire spatial domain and a nested block with refined cells for the domain of interest. Three different sizes were selected for each of the grid blocks. By comparing the accuracy of their results based on the experimental data, the reasonable mesh for the solution domain was finally selected. The convergence index method (GCI) evaluated the mesh sensitivity analysis. Based on this method, many researchers, such as Ahmadi et al. [16] and Ahmadi et al. [15], have studied the independence of numerical results from mesh size. Three different mesh sizes with a refinement ratio (r) of 1.33 were used to perform the convergence index method. The refinement ratio is the ratio between the larger and smaller mesh sizes (r = Gcoarse/Gfine). According to the recommendation of Celik et al. [17], the recommended number for the refinement ratio is 1.3, which gives acceptable results. Table 2 shows the characteristics of the three mesh sizes selected for mesh sensitivity analysis.Table 2 Characteristics of the meshes tested in the convergence analysis
The results of u1 = umax (u1 = velocity component along the x1 axis and umax = maximum velocity of u1 in a section perpendicular to the invert of the fishway) at Q = 0.035 m3/s, × 1/l = 0.66, and Y1/b = 0 in the pool of conventional weir No. 4, obtained from the output results of the software, were used to evaluate the accuracy of the calculation range. As shown in Fig. 4, x1 = the distance from a given weir in the x-direction, Y1 = the water depth measured in the y-direction, Y0 = the vertical distance in the Cartesian coordinate system, h = the water column at the crest, b = the distance between the two points of maximum velocity umax and zero velocity, and l = the pool length.
Fig. 4
The apparent index of convergence (p) in the GCI method is calculated as follows:
�=ln(�3−�2)(�2−�1)/ln(�)
(7)
f1, f2, and f3 are the hydraulic parameters obtained from the numerical simulation (f1 corresponds to the small mesh), and r is the refinement ratio. The following equation defines the convergence index of the fine mesh:
GCIfine=1.25|ε|��−1
(8)
Here, ε = (f2 − f1)/f1 is the relative error, and f2 and f3 are the values of hydraulic parameters considered for medium and small grids, respectively. GCI12 and GCI23 dimensionless indices can be calculated as:
GCI12=1.25|�2−�1�1|��−1
(9)
Then, the independence of the network is preserved. The convergence index of the network parameters obtained by Eqs. (7)–(9) for all three network variables is shown in Table 3. Since the GCI values for the smaller grid (GCI12) are lower compared to coarse grid (GCI23), it can be concluded that the independence of the grid is almost achieved. No further change in the grid size of the solution domain is required. The calculated values (GCI23/rpGCI12) are close to 1, which shows that the numerical results obtained are within the convergence range. As a result, the meshing of the solution domain consisting of a block mesh with a mesh size of 0.012 m and a block mesh within a larger block mesh with a mesh size of 0.009 m was selected as the optimal mesh (Fig. 5).Table 3 GCI calculation
The boundary conditions applied to the area are shown in Fig. 6. The boundary condition of specific flow rate (volume flow rate-Q) was used for the inlet of the flow. For the downstream boundary, the flow output (outflow-O) condition did not affect the flow in the solution area. For the Zmax boundary, the specified pressure boundary condition was used along with the fluid fraction = 0 (P). This type of boundary condition considers free surface or atmospheric pressure conditions (Ghaderi et al. [19]). The wall boundary condition is defined for the bottom of the channel, which acts like a virtual wall without friction (W). The boundary between mesh blocks and walls were considered a symmetrical condition (S).
Fig. 6
The convergence of the steady-state solutions was controlled during the simulations by monitoring the changes in discharge at the inlet boundary conditions. Figure 7 shows the time series plots of the discharge obtained from the Model A for the three main discharges from the numerical results. The 8 s to reach the flow equilibrium is suitable for the case of the fish ladder with pool and weir. Almost all discharge fluctuations in the models are insignificant in time, and the flow has reached relative stability. The computation time for the simulations was between 6 and 8 h using a personal computer with eight cores of a CPU (Intel Core i7-7700K @ 4.20 GHz and 16 GB RAM).
Fig. 7
3 Results
3.1 Verification of Numerical Results
Quantitative outcomes, including free surface and normalized velocity profiles obtained using FLOW-3D software, were reviewed and compared with the results of Ead et al. [6]. The fourth pool was selected to present the results and compare the experiment and simulation. For each quantity, the percentage of mean absolute error (MAPE (%)) and root-mean-square error (RMSE) are calculated. Equations (10) and (11) show the method used to calculate the errors.
MAPE(%)100×1�∑1�|�exp−�num�exp|
(10)
RMSE(−)1�∑1�(�exp−�num)2
(11)
Here, Xexp is the value of the laboratory data, Xnum is the numerical data value, and n is the amount of data. As shown in Fig. 8, let x1 = distance from a given weir in the x-direction and Y1 = water depth in the y-direction from the bottom. The trend of the surface profiles for each of the numerical results is the same as that of the laboratory results. The surface profiles of the plunging flows drop after the flow enters and then rises to approach the next weir. The RMSE and MAPE error values for Model A are 0.014 m and 3.11%, respectively, indicating acceptable agreement between numerical and laboratory results. Figure 9 shows the velocity vectors and plunging flow from the numerical results, where x and y are horizontal and vertical to the flow direction, respectively. It can be seen that the jet in the fish ladder pool has a relatively high velocity. The two vortices, i.e., the enclosed vortex rotating clockwise behind the weir and the surface vortex rotating counterclockwise above the jet, are observed for the regime of incident flow. The point where the jet meets the fish passage bed is shown in the figure. The normalized velocity profiles upstream and downstream of the impact points are shown in Fig. 10. The figure shows that the numerical results agree well with the experimental data of Ead et al. [6].
Fig. 8Fig. 9Fig. 10
3.2 Flow Regime and Discharge-Depth Relationship
Depending on the geometric shape of the fishway, including the distance of the weir, the slope of the bottom, the height of the weir, and the flow conditions, the flow regime in the fishway is divided into three categories: dipping, transitional, and flow regimes [4]. In the plunging flow regime, the flow enters the pool through the weir, impacts the bottom of the fishway, and forms a hydraulic jump causing two eddies [2, 20]. In the streamwise flow regime, the surface of the flow passing over the weir is almost parallel to the bottom of the channel. The transitional regime has intermediate flow characteristics between the submerged and flow regimes. To predict the flow regime created in the fishway, Ead et al. [6] proposed two dimensionless parameters, Qt* and L/w, where Qt* is the dimensionless discharge, L is the distance between weirs, and w is the height of the weir:
��∗=���0���
(12)
Q is the total discharge, B is the width of the channel, S0 is the slope of the bed, and g is the gravity acceleration. Figure 11 shows different ranges for each flow regime based on the slope of the bed and the distance between the pools in this study. The results of Baki et al. [21], Ead et al. [6] and Dizabadi et al. [22] were used for this comparison. The distance between the pools affects the changes in the regime of the fish ladder. So, if you decrease the distance between weirs, the flow regime more likely becomes. This study determined all three flow regimes in a fish ladder. When the corresponding range of Qt* is less than 0.6, the flow regime can dip at values of L/B = 1.83. If the corresponding range of Qt* is greater than 0.5, transitional flow may occur at L/B = 1.22. On the other hand, when Qt* is greater than 1, streamwise flow can occur at values of L/B = 0.61. These observations agree well with the results of Baki et al. [21], Ead et al. [6] and Dizabadi et al. [22].
Fig. 11
For plunging flows, another dimensionless discharge (Q+) versus h/w given by Ead et al. [6] was used for further evaluation:
�+=��ℎ�ℎ=23�d�
(13)
where h is the water depth above the weir, and Cd is the discharge coefficient. Figure 12a compares the numerical and experimental results of Ead et al. [6]. In this figure, Rehbock’s empirical equation is used to estimate the discharge coefficient of Ead et al. [6].
�d=0.57+0.075ℎ�
(14)
Fig. 12
The numerical results for the conventional weir (Model A) and the rectangular labyrinth weir (Model B) of this study agree well with the laboratory results of Ead et al. [6]. When comparing models A and B, it is also found that a rectangular labyrinth weir has larger Q + values than the conventional weir as the length of the weir crest increases for a given channel width and fixed headwater elevation. In Fig. 12b, Models A and B’s flow depth plot shows the plunging flow regime. The power trend lines drawn through the data are the best-fit lines. The data shown in Fig. 12b are for different bed slopes and weir geometries. For the conventional weir and the rectangular labyrinth weir at submerged flow, Q can be assumed to be proportional to 1.56 and 1.47h, respectively. In the results of Ead et al. [6], Q is proportional to 1.5h. If we assume that the flow through the orifice is Qo and the total outflow is Q, the change in the ratio of Qo/Q to total outflow for models A and B can be shown in Fig. 13. For both models, the flow through the orifice decreases as the total flow increases. A logarithmic trend line was also found between the total outflow and the dimensionless ratio Qo/Q.
Fig. 13
3.3 Depth-Averaged Velocity Distributions
To ensure that the target fish species can pass the fish ladder with maximum efficiency, the average velocity in the fish ladder should be low enough [4]. Therefore, the average velocity in depth should be as much as possible below the critical swimming velocities of the target fishes at a constant flow depth in the pool [20]. The contour plot of depth-averaged velocity was used instead of another direction, such as longitudinal velocity because fish are more sensitive to depth-averaged flow velocity than to its direction under different hydraulic conditions. Figure 14 shows the distribution of depth-averaged velocity in the pool for Models A and B in two cases with and without orifice plates. Model A’s velocity within the pool differs slightly in the spanwise direction. However, no significant variation in velocity was observed. The flow is gradually directed to the sides as it passes through the rectangular labyrinth weir. This increases the velocity at the sides of the channel. Therefore, the high-velocity zone is located at the sides. The low velocity is in the downstream apex of the weir. This area may be suitable for swimming target fish. The presence of an opening in the weir increases the flow velocity at the opening and in the pool’s center, especially in Model A. The flow velocity increase caused by the models’ opening varied from 7.7 to 12.48%. Figure 15 illustrates the effect of the inverted slope on the averaged depth velocity distribution in the pool at low and high discharge. At constant discharge, flow velocity increases with increasing bed slope. In general, high flow velocity was found in the weir toe sidewall and the weir and channel sidewalls.
Fig. 14Fig. 15
On the other hand, for a constant bed slope, the high-velocity area of the pool increases due to the increase in runoff. For both bed slopes and different discharges, the most appropriate path for fish to travel from upstream to downstream is through the middle of the cross section and along the top of the rectangular labyrinth weirs. The maximum dominant velocities for Model B at S0 = 5% were 0.83 and 1.01 m/s; at S0 = 10%, they were 1.12 and 1.61 m/s at low and high flows, respectively. The low mean velocities for the same distance and S0 = 5 and 10% were 0.17 and 0.26 m/s, respectively.
Figure 16 shows the contour of the averaged depth velocity for various distances from the weir at low and high discharge. The contour plot shows a large variation in velocity within short distances from the weir. At L/B = 0.61, velocities are low upstream and downstream of the top of the weir. The high velocities occur in the side walls of the weir and the channel. At L/B = 1.22, the low-velocity zone displaces the higher velocity in most of the pool. Higher velocities were found only on the sides of the channel. As the discharge increases, the velocity zone in the pool becomes wider. At L/B = 1.83, there is an area of higher velocities only upstream of the crest and on the sides of the weir. At high discharge, the prevailing maximum velocities for L/B = 0.61, 1.22, and 1.83 were 1.46, 1.65, and 1.84 m/s, respectively. As the distance between weirs increases, the range of maximum velocity increases.
Fig. 16
On the other hand, the low mean velocity for these distances was 0.27, 0.44, and 0.72 m/s, respectively. Thus, the low-velocity zone decreases with increasing distance between weirs. Figure 17 shows the pattern distribution of streamlines along with the velocity contour at various distances from the weir for Q = 0.05 m3/s. A stream-like flow is generally formed in the pool at a small distance between weirs (L/B = 0.61). The rotation cell under the jet forms clockwise between the two weirs. At the distances between the spillways (L/B = 1.22), the transition regime of the flow is formed. The transition regime occurs when or shortly after the weir is flooded. The rotation cell under the jet is clockwise smaller than the flow regime and larger than the submergence regime. At a distance L/B = 1.83, a plunging flow is formed so that the plunging jet dips into the pool and extends downstream to the center of the pool. The clockwise rotation of the cell is bounded by the dipping jet of the weir and is located between the bottom and the side walls of the weir and the channel.
Fig. 17
Figure 18 shows the average depth velocity bar graph for each weir at different bed slopes and with and without orifice plates. As the distance between weirs increases, all models’ average depth velocity increases. As the slope of the bottom increases and an orifice plate is present, the average depth velocity in the pool increases. In addition, the average pool depth velocity increases as the discharge increases. Among the models, Model A’s average depth velocity is higher than Model B’s. The variation in velocity ranged from 8.11 to 12.24% for the models without an orifice plate and from 10.26 to 16.87% for the models with an orifice plate.
Fig. 18
3.4 Turbulence Characteristics
The turbulent kinetic energy is one of the important parameters reflecting the turbulent properties of the flow field [23]. When the k value is high, more energy and a longer transit time are required to migrate the target species. The turbulent kinetic energy is defined as follows:
�=12(�x′2+�y′2+�z′2)
(15)
where ux, uy, and uz are fluctuating velocities in the x, y, and z directions, respectively. An illustration of the TKE and the effects of the geometric arrangement of the weir and the presence of an opening in the weir is shown in Fig. 19. For a given bed slope, in Model A, the highest TKE values are uniformly distributed in the weir’s upstream portion in the channel’s cross section. In contrast, for the rectangular labyrinth weir (Model B), the highest TKE values are concentrated on the sides of the pool between the crest of the weir and the channel wall. The highest TKE value in Models A and B is 0.224 and 0.278 J/kg, respectively, at the highest bottom slope (S0 = 10%). In the downstream portion of the conventional weir and within the crest of the weir and the walls of the rectangular labyrinth, there was a much lower TKE value that provided the best conditions for fish to recover in the pool between the weirs. The average of the lowest TKE for bottom slopes of 5 and 10% in Model A is 0.041 and 0.056 J/kg, and for Model B, is 0.047 and 0.064 J/kg. The presence of an opening in the weirs reduces the area of the highest TKE within the pool. It also increases the resting areas for fish (lower TKE). The highest TKE at the highest bottom slope in Models A and B with an orifice is 0.208 and 0.191 J/kg, respectively.
Fig. 19
Figure 20 shows the effect of slope on the longitudinal distribution of TKE in the pools. TKE values significantly increase for a given discharge with an increasing bottom slope. Thus, for a low bed slope (S0 = 5%), a large pool area has expanded with average values of 0.131 and 0.168 J/kg for low and high discharge, respectively. For a bed slope of S0 = 10%, the average TKE values are 0.176 and 0.234 J/kg. Furthermore, as the discharge increases, the area with high TKE values within the pool increases. Lower TKE values are observed at the apex of the labyrinth weir, at the corner of the wall downstream of the weir, and between the side walls of the weir and the channel wall for both bottom slopes. The effect of distance between weirs on TKE is shown in Fig. 21. Low TKE values were observed at low discharge and short distances between weirs. Low TKE values are located at the top of the rectangular labyrinth weir and the downstream corner of the weir wall. There is a maximum value of TKE at the large distances between weirs, L/B = 1.83, along the center line of the pool, where the dip jet meets the bottom of the bed. At high discharge, the maximum TKE value for the distance L/B = 0.61, 1.22, and 1.83 was 0.246, 0.322, and 0.417 J/kg, respectively. In addition, the maximum TKE range increases with the distance between weirs.
Fig. 20Fig. 21
For TKE size, the average value (TKEave) is plotted against q in Fig. 22. For all models, the TKE values increase with increasing q. For example, in models A and B with L/B = 0.61 and a slope of 10%, the TKE value increases by 41.66 and 86.95%, respectively, as q increases from 0.1 to 0.27 m2/s. The TKE values in Model B are higher than Model A for a given discharge, bed slope, and weir distance. The TKEave in Model B is higher compared to Model A, ranging from 31.46 to 57.94%. The presence of an orifice in the weir reduces the TKE values in both weirs. The intensity of the reduction is greater in Model B. For example, in Models A and B with L/B = 0.61 and q = 0.1 m2/s, an orifice reduces TKEave values by 60.35 and 19.04%, respectively. For each model, increasing the bed slope increases the TKEave values in the pool. For example, for Model B with q = 0.18 m2/s, increasing the bed slope from 5 to 10% increases the TKEave value by 14.34%. Increasing the distance between weirs increases the TKEave values in the pool. For example, in Model B with S0 = 10% and q = 0.3 m2/s, the TKEave in the pool increases by 34.22% if you increase the distance between weirs from L/B = 0.61 to L/B = 0.183.
Fig. 22
Cotel et al. [24] suggested that turbulence intensity (TI) is a suitable parameter for studying fish swimming performance. Figure 23 shows the plot of TI and the effects of the geometric arrangement of the weir and the presence of an orifice. In Model A, the highest TI values are found upstream of the weirs and are evenly distributed across the cross section of the channel. The TI values increase as you move upstream to downstream in the pool. For the rectangular labyrinth weir, the highest TI values were concentrated on the sides of the pool, between the top of the weir and the side wall of the channel, and along the top of the weir. Downstream of the conventional weir, within the apex of the weir, and at the corners of the walls of the rectangular labyrinth weir, the percentage of TI was low. At the highest discharge, the average range of TI in Models A and B was 24–45% and 15–62%, respectively. The diversity of TI is greater in the rectangular labyrinth weir than the conventional weir. Fish swimming performance is reduced due to higher turbulence intensity. However, fish species may prefer different disturbance intensities depending on their swimming abilities; for example, Salmo trutta prefers a disturbance intensity of 18–53% [25]. Kupferschmidt and Zhu [26] found a higher range of TI for fishways, such as natural rock weirs, of 40–60%. The presence of an orifice in the weir increases TI values within the pool, especially along the middle portion of the cross section of the fishway. With an orifice in the weir, the average range of TI in Models A and B was 28–59% and 22–73%, respectively.
Fig. 23
The effect of bed slope on TI variation is shown in Fig. 24. TI increases in different pool areas as the bed slope increases for a given discharge. For a low bed slope (S0 = 5%), a large pool area has increased from 38 to 63% and from 56 to 71% for low and high discharge, respectively. For a bed slope of S0 = 10%, the average values of TI are 45–67% and 61–73% for low and high discharge, respectively. Therefore, as runoff increases, the area with high TI values within the pool increases. A lower TI is observed for both bottom slopes in the corner of the wall, downstream of the crest walls, and between the side walls in the weir and channel. Figure 25 compares weir spacing with the distribution of TI values within the pool. The TI values are low at low flows and short distances between weirs. A maximum value of TI occurs at long spacing and where the plunging stream impinges on the bed and the area around the bed. TI ranges from 36 to 57%, 58–72%, and 47–76% for the highest flow in a wide pool area for L/B = 0.61, 1.22, and 1.83, respectively.
Fig. 24Fig. 25
The average value of turbulence intensity (TIave) is plotted against q in Fig. 26. The increase in TI values with the increase in q values is seen in all models. For example, the average values of TI for Models A and B at L/B = 0.61 and slope of 10% increased from 23.9 to 33.5% and from 42 to 51.8%, respectively, with the increase in q from 0.1 to 0.27 m2/s. For a given discharge, a given gradient, and a given spacing of weirs, the TIave is higher in Model B than Model A. The presence of an orifice in the weirs increases the TI values in both types. For example, in Models A and B with L/B = 0.61 and q = 0.1 m2/s, the presence of an orifice increases TIave from 23.9 to 37.1% and from 42 to 48.8%, respectively. For each model, TIave in the pool increases with increasing bed slope. For Model B with q = 0.18 m2/s, TIave increases from 37.5 to 45.8% when you increase the invert slope from 5 to 10%. Increasing the distance between weirs increases the TIave in the pool. In Model B with S0 = 10% and q = 0.3 m2/s, the TIave in the pool increases from 51.8 to 63.7% as the distance between weirs increases from L/B = 0.61 to L/B = 0.183.
Fig. 26
3.5 Energy Dissipation
To facilitate the passage of various target species through the pool of fishways, it is necessary to pay attention to the energy dissipation of the flow and to keep the flow velocity in the pool slow. The average volumetric energy dissipation (k) in the pool is calculated using the following basic formula:
�=����0��
(16)
where ρ is the water density, and H is the average water depth of the pool. The change in k versus Q for all models at two bottom slopes, S0 = 5%, and S0 = 10%, is shown in Fig. 27. Like the results of Yagci [8] and Kupferschmidt and Zhu [26], at a constant bottom slope, the energy dissipation in the pool increases with increasing discharge. The trend of change in k as a function of Q from the present study at a bottom gradient of S0 = 5% is also consistent with the results of Kupferschmidt and Zhu [26] for the fishway with rock weir. The only difference between the results is the geometry of the fishway and the combination of boulders instead of a solid wall. Comparison of the models shows that the conventional model has lower energy dissipation than the rectangular labyrinth for a given discharge. Also, increasing the distance between weirs decreases the volumetric energy dissipation for each model with the same bed slope. Increasing the slope of the bottom leads to an increase in volumetric energy dissipation, and an opening in the weir leads to a decrease in volumetric energy dissipation for both models. Therefore, as a guideline for volumetric energy dissipation, if the value within the pool is too high, the increased distance of the weir, the decreased slope of the bed, or the creation of an opening in the weir would decrease the volumetric dissipation rate.
Fig. 27
To evaluate the energy dissipation inside the pool, the general method of energy difference in two sections can use:
ε=�1−�2�1
(17)
where ε is the energy dissipation rate, and E1 and E2 are the specific energies in Sects. 1 and 2, respectively. The distance between Sects. 1 and 2 is the same. (L is the distance between two upstream and downstream weirs.) Figure 28 shows the changes in ε relative to q (flow per unit width). The rectangular labyrinth weir (Model B) has a higher energy dissipation rate than the conventional weir (Model A) at a constant bottom gradient. For example, at S0 = 5%, L/B = 0.61, and q = 0.08 m3/s.m, the energy dissipation rate in Model A (conventional weir) was 0.261. In Model B (rectangular labyrinth weir), however, it was 0.338 (22.75% increase). For each model, the energy dissipation rate within the pool increases as the slope of the bottom increases. For Model B with L/B = 1.83 and q = 0.178 m3/s.m, the energy dissipation rate at S0 = 5% and 10% is 0.305 and 0.358, respectively (14.8% increase). Figure 29 shows an orifice’s effect on the pools’ energy dissipation rate. With an orifice in the weir, both models’ energy dissipation rates decreased. Thus, the reduction in energy dissipation rate varied from 7.32 to 9.48% for Model A and from 8.46 to 10.57 for Model B.
Fig. 28Fig. 29
4 Discussion
This study consisted of entirely of numerical analysis. Although this study was limited to two weirs, the hydraulic performance and flow characteristics in a pooled fishway are highlighted by the rectangular labyrinth weir and its comparison with the conventional straight weir. The study compared the numerical simulations with laboratory experiments in terms of surface profiles, velocity vectors, and flow characteristics in a fish ladder pool. The results indicate agreement between the numerical and laboratory data, supporting the reliability of the numerical model in capturing the observed phenomena.
When the configuration of the weir changes to a rectangular labyrinth weir, the flow characteristics, the maximum and minimum area, and even the location of each hydraulic parameter change compared to a conventional weir. In the rectangular labyrinth weir, the flow is gradually directed to the sides as it passes the weir. This increases the velocity at the sides of the channel [21]. Therefore, the high-velocity area is located on the sides. In the downstream apex of the weir, the flow velocity is low, and this area may be suitable for swimming target fish. However, no significant change in velocity was observed at the conventional weir within the fish ladder. This resulted in an average increase in TKE of 32% and an average increase in TI of about 17% compared to conventional weirs.
In addition, there is a slight difference in the flow regime for both weir configurations. In addition, the rectangular labyrinth weir has a higher energy dissipation rate for a given discharge and constant bottom slope than the conventional weir. By reducing the distance between the weirs, this becomes even more intense. Finally, the presence of an orifice in both configurations of the weir increased the flow velocity at the orifice and in the middle of the pool, reducing the highest TKE value and increasing the values of TI within the pool of the fish ladder. This resulted in a reduction in volumetric energy dissipation for both weir configurations.
The results of this study will help the reader understand the direct effects of the governing geometric parameters on the hydraulic characteristics of a fishway with a pool and weir. However, due to the limited configurations of the study, further investigation is needed to evaluate the position of the weir’s crest on the flow direction and the difference in flow characteristics when combining boulders instead of a solid wall for this type of labyrinth weir [26]. In addition, hydraulic engineers and biologists must work together to design an effective fishway with rectangular labyrinth configurations. The migration habits of the target species should be considered when designing the most appropriate design [27]. Parametric studies and field observations are recommended to determine the perfect design criteria.
The current study focused on comparing a rectangular labyrinth weir with a conventional straight weir. Further research can explore other weir configurations, such as variations in crest position, different shapes of labyrinth weirs, or the use of boulders instead of solid walls. This would help understand the influence of different geometric parameters on hydraulic characteristics.
5 Conclusions
A new layout of the weir was evaluated, namely a rectangular labyrinth weir compared to a straight weir in a pool and weir system. The differences between the weirs were highlighted, particularly how variations in the geometry of the structures, such as the shape of the weir, the spacing of the weir, the presence of an opening at the weir, and the slope of the bottom, affect the hydraulics within the structures. The main findings of this study are as follows:
The calculated dimensionless discharge (Qt*) confirmed three different flow regimes: when the corresponding range of Qt* is smaller than 0.6, the regime of plunging flow occurs for values of L/B = 1.83. (L: distance of the weir; B: channel width). When the corresponding range of Qt* is greater than 0.5, transitional flow occurs at L/B = 1.22. On the other hand, if Qt* is greater than 1, the streaming flow is at values of L/B = 0.61.
For the conventional weir and the rectangular labyrinth weir with the plunging flow, it can be assumed that the discharge (Q) is proportional to 1.56 and 1.47h, respectively (h: water depth above the weir). This information is useful for estimating the discharge based on water depth in practical applications.
In the rectangular labyrinth weir, the high-velocity zone is located on the side walls between the top of the weir and the channel wall. A high-velocity variation within short distances of the weir. Low velocity occurs within the downstream apex of the weir. This area may be suitable for swimming target fish.
As the distance between weirs increased, the zone of maximum velocity increased. However, the zone of low speed decreased. The prevailing maximum velocity for a rectangular labyrinth weir at L/B = 0.61, 1.22, and 1.83 was 1.46, 1.65, and 1.84 m/s, respectively. The low mean velocities for these distances were 0.27, 0.44, and 0.72 m/s, respectively. This finding highlights the importance of weir spacing in determining the flow characteristics within the fishway.
The presence of an orifice in the weir increased the flow velocity at the orifice and in the middle of the pool, especially in a conventional weir. The increase ranged from 7.7 to 12.48%.
For a given bottom slope, in a conventional weir, the highest values of turbulent kinetic energy (TKE) are uniformly distributed in the upstream part of the weir in the cross section of the channel. In contrast, for the rectangular labyrinth weir, the highest TKE values were concentrated on the sides of the pool between the crest of the weir and the channel wall. The highest TKE value for the conventional and the rectangular labyrinth weir was 0.224 and 0.278 J/kg, respectively, at the highest bottom slope (S0 = 10%).
For a given discharge, bottom slope, and weir spacing, the average values of TI are higher for the rectangular labyrinth weir than for the conventional weir. At the highest discharge, the average range of turbulence intensity (TI) for the conventional and rectangular labyrinth weirs was between 24 and 45% and 15% and 62%, respectively. This reveals that the rectangular labyrinth weir may generate more turbulent flow conditions within the fishway.
For a given discharge and constant bottom slope, the rectangular labyrinth weir has a higher energy dissipation rate than the conventional weir (22.75 and 34.86%).
Increasing the distance between weirs decreased volumetric energy dissipation. However, increasing the gradient increased volumetric energy dissipation. The presence of an opening in the weir resulted in a decrease in volumetric energy dissipation for both model types.
Availability of data and materials
Data is contained within the article.
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Sous la direction de : Marc Jolin, directeur de recherche Benoit Bissonnette, codirecteur de recherche
Modélisation de l’écoulement du béton frais
Abstract
현재의 기후 비상 사태와 기후 변화에 관한 다양한 과학적 보고서를 고려할 때 인간이 만든 오염을 대폭 줄이는 것은 필수적이며 심지어 중요합니다. 최신 IPCC(기후변화에 관한 정부 간 패널) 보고서(2022)는 2030년까지 배출량을 절반으로 줄여야 함을 나타내며, 지구 보존을 위해 즉각적인 조치를 취해야 한다고 강력히 강조합니다.
이러한 의미에서 콘크리트 생산 산업은 전체 인간 이산화탄소 배출량의 4~8%를 담당하고 있으므로 환경에 미치는 영향을 줄이기 위한 진화가 시급히 필요합니다.
본 연구의 주요 목적은 이미 사용 가능한 기술적 품질 관리 도구를 사용하여 생산을 최적화하고 혼합 시간을 단축하며 콘크리트 폐기물을 줄이기 위한 신뢰할 수 있고 활용 가능한 수치 모델을 개발함으로써 이러한 산업 전환에 참여하는 것입니다.
실제로, 혼합 트럭 내부의 신선한 콘크리트의 거동과 흐름 프로파일을 더 잘 이해할 수 있는 수치 시뮬레이션을 개발하면 혼합 시간과 비용을 더욱 최적화할 수 있으므로 매우 유망합니다. 이러한 복잡한 수치 도구를 활용할 수 있으려면 수치 시뮬레이션을 검증, 특성화 및 보정하기 위해 기본 신 콘크리트 흐름 모델의 구현이 필수적입니다.
이 논문에서는 세 가지 단순 유동 모델의 개발이 논의되고 얻은 결과는 신선한 콘크리트 유동의 수치적 거동을 검증하는 데 사용됩니다. 이러한 각 모델은 강점과 약점을 갖고 있으며, 신선한 콘크리트의 유변학과 유동 거동을 훨씬 더 잘 이해할 수 있는 수치 작업 환경을 만드는 데 기여합니다.
따라서 이 연구 프로젝트는 새로운 콘크리트 생산의 완전한 모델링을 위한 진정한 관문입니다.
In view of the current climate emergency and the various scientific reports on climate change, it is essential and even vital to drastically reduce man-made pollution. The latest IPCC (Intergovernmental Panel on Climate Change) report (2022) indicates that emissions must be halved by 2030 and strongly emphasizes the need to act immediately to preserve the planet. In this sense, the concrete production industry is responsible for 4-8% of total human carbon dioxide emissions and therefore urgently needs to evolve to reduce its environmental impact. The main objective of this study is to participate in this industrial transition by developing a reliable and exploitable numerical model to optimize the production, reduce mixing time and also reduce concrete waste by using technological quality control tools already available. Indeed, developing a numerical simulation allowing to better understand the behavior and flow profiles of fresh concrete inside a mixing-truck is extremely promising as it allows for further optimization of mixing times and costs. In order to be able to exploit such a complex numerical tool, the implementation of elementary fresh concrete flow models is essential to validate, characterize and calibrate the numerical simulations. In this thesis, the development of three simple flow models is discussed and the results obtained are used to validate the numerical behavior of fresh concrete flow. Each of these models has strengths and weaknesses and contributes to the creation of a numerical working environment that provides a much better understanding of the rheology and flow behavior of fresh concrete. This research project is therefore a real gateway to a full modelling of fresh concrete production.
Figure 2-15: Système expérimental du plan inclinéFigure 2-19: Essai d’affaissement au cône d’Abrams
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Spillways are constructed to evacuate flood discharge safely so that a flood wave does not overtop the dam body. There are different types of spillways, with the ogee type being the conventional one. A stepped spillway is an example of a nonconventional spillway. The turbulent flow over a stepped spillway was studied numerically by using the Flow-3D package. Different fluid flow characteristics such as longitudinal flow velocity, temperature distribution, density and chemical concentration can be well simulated by Flow-3D. In this study, the influence of slope changes on flow characteristics such as air entrainment, velocity distribution and dynamic pressures distribution over a stepped spillway was modelled by Flow-3D. The results from the numerical model were compared with an experimental study done by others in the literature. Two models of a stepped spillway with different discharge for each model were simulated. The turbulent flow in the experimental model was simulated by the Renormalized Group (RNG) turbulence scheme in the numerical model. A good agreement was achieved between the numerical results and the observed ones, which are exhibited in terms of graphics and statistical tables.
배수로는 홍수가 댐 몸체 위로 넘치지 않도록 안전하게 홍수를 피할 수 있도록 건설되었습니다. 다른 유형의 배수로가 있으며, ogee 유형이 기존 유형입니다. 계단식 배수로는 비 전통적인 배수로의 예입니다. 계단식 배수로 위의 난류는 Flow-3D 패키지를 사용하여 수치적으로 연구되었습니다.
세로 유속, 온도 분포, 밀도 및 화학 농도와 같은 다양한 유체 흐름 특성은 Flow-3D로 잘 시뮬레이션 할 수 있습니다. 이 연구에서는 계단식 배수로에 대한 공기 혼입, 속도 분포 및 동적 압력 분포와 같은 유동 특성에 대한 경사 변화의 영향을 Flow-3D로 모델링 했습니다.
수치 모델의 결과는 문헌에서 다른 사람들이 수행한 실험 연구와 비교되었습니다. 각 모델에 대해 서로 다른 배출이 있는 계단식 배수로의 두 모델이 시뮬레이션되었습니다. 실험 모델의 난류 흐름은 수치 모델의 Renormalized Group (RNG) 난류 계획에 의해 시뮬레이션되었습니다. 수치 결과와 관찰 된 결과 사이에 좋은 일치가 이루어졌으며, 이는 그래픽 및 통계 테이블로 표시됩니다.
댐 구조는 물 보호가 생활의 핵심이기 때문에 물을 저장하거나 물을 운반하는 전 세계에서 가장 중요한 프로젝트입니다. 그리고 여수로는 댐의 가장 중요한 부분 중 하나로 분류됩니다. 홍수로 인한 파괴 나 피해로부터 댐을 보호하기 위해 여수로가 건설됩니다.
수력 발전, 항해, 레크리에이션 및 어업의 중요성을 감안할 때 댐 건설 및 홍수 통제는 전 세계적으로 매우 중요한 문제로 간주 될 수 있습니다. 많은 유형의 배수로가 있지만 가장 일반적인 유형은 다음과 같습니다 : ogee 배수로, 자유 낙하 배수로, 사이펀 배수로, 슈트 배수로, 측면 채널 배수로, 터널 배수로, 샤프트 배수로 및 계단식 배수로.
그리고 모든 여수로는 입구 채널, 제어 구조, 배출 캐리어 및 출구 채널의 네 가지 필수 구성 요소로 구성됩니다. 특히 롤러 압축 콘크리트 (RCC) 댐 건설 기술과 더 쉽고 빠르며 저렴한 건설 기술로 분류 된 계단식 배수로 건설과 관련하여 최근 수십 년 동안 많은 계단식 배수로가 건설되었습니다 (Chanson 2002; Felder & Chanson 2011).
계단식 배수로 구조는 캐비테이션 위험을 감소시키는 에너지 소산 속도를 증가시킵니다 (Boes & Hager 2003b). 계단식 배수로는 다양한 조건에서 더 매력적으로 만드는 장점이 있습니다.
계단식 배수로의 흐름 거동은 일반적으로 낮잠, 천이 및 스키밍 흐름 체제의 세 가지 다른 영역으로 분류됩니다 (Chanson 2002). 유속이 낮을 때 nappe 흐름 체제가 발생하고 자유 낙하하는 낮잠의 시퀀스로 특징 지워지는 반면, 스키밍 흐름 체제에서는 물이 외부 계단 가장자리 위의 유사 바닥에서 일관된 흐름으로 계단 위로 흐릅니다.
또한 주요 흐름에서 3 차원 재순환 소용돌이가 발생한다는 것도 분명합니다 (예 : Chanson 2002; Gonzalez & Chanson 2008). 계단 가장자리 근처의 의사 바닥에서 흐름의 방향은 가상 바닥과 가상으로 정렬됩니다. Takahashi & Ohtsu (2012)에 따르면, 스키밍 흐름 체제에서 주어진 유속에 대해 흐름은 계단 가장자리 근처의 수평 계단면에 영향을 미치고 슈트 경사가 감소하면 충돌 영역의 면적이 증가합니다. 전이 흐름 체제는 나페 흐름과 스키밍 흐름 체제 사이에서 발생합니다. 계단식 배수로를 설계 할 때 스키밍 흐름 체계를 고려해야합니다 (예 : Chanson 1994, Matos 2000, Chanson 2002, Boes & Hager 2003a).
CFD (Computational Fluid Dynamics), 즉 수력 공학의 수치 모델은 일반적으로 물리적 모델에 소요되는 총 비용과 시간을 줄여줍니다. 따라서 수치 모델은 실험 모델보다 빠르고 저렴한 것으로 분류되며 동시에 하나 이상의 목적으로 사용될 수도 있습니다. 사용 가능한 많은 CFD 소프트웨어 패키지가 있지만 가장 널리 사용되는 것은 FLOW-3D입니다. 이 연구에서는 Flow 3D 소프트웨어를 사용하여 유량이 서로 다른 두 모델에 대해 계단식 배수로에서 공기 농도, 속도 분포 및 동적 압력 분포를 시뮬레이션합니다.
Roshan et al. (2010)은 서로 다른 수의 계단 및 배출을 가진 계단식 배수로의 두 가지 물리적 모델에 대한 흐름 체제 및 에너지 소산 조사를 연구했습니다. 실험 모델의 기울기는 각각 19.2 %, 12 단계와 23 단계의 수입니다. 결과는 23 단계 물리적 모델에서 관찰 된 흐름 영역이 12 단계 모델보다 더 수용 가능한 것으로 간주되었음을 보여줍니다. 그러나 12 단계 모델의 에너지 손실은 23 단계 모델보다 더 많았습니다. 그리고 실험은 스키밍 흐름 체제에서 23 단계 모델의 에너지 소산이 12 단계 모델보다 약 12 % 더 적다는 것을 관찰했습니다.
Ghaderi et al. (2020a)는 계단 크기와 유속이 다른 정련 매개 변수의 영향을 조사하기 위해 계단식 배수로에 대한 실험 연구를 수행했습니다. 그 결과, 흐름 체계가 냅페 흐름 체계에서 발생하는 최소 scouring 깊이와 같은 scouring 구멍 치수에 영향을 미친다는 것을 보여주었습니다. 또한 테일 워터 깊이와 계단 크기는 최대 scouring깊이에 대한 실제 매개 변수입니다. 테일 워터의 깊이를 6.31cm에서 8.54 및 11.82cm로 늘림으로써 수세 깊이가 각각 18.56 % 및 11.42 % 증가했습니다. 또한 이 증가하는 테일 워터 깊이는 scouring 길이를 각각 31.43 % 및 16.55 % 감소 시킵니다. 또한 유속을 높이면 Froude 수가 증가하고 흐름의 운동량이 증가하면 scouring이 촉진됩니다. 또한 결과는 중간의 scouring이 횡단면의 측벽보다 적다는 것을 나타냅니다. 계단식 배수로 하류의 최대 scouring 깊이를 예측 한 후 실험 결과와 비교하기 위한 실험식이 제안 되었습니다. 그리고 비교 결과 제안 된 공식은 각각 3.86 %와 9.31 %의 상대 오차와 최대 오차 내에서 scouring 깊이를 예측할 수 있음을 보여주었습니다.
Ghaderi et al. (2020b)는 사다리꼴 미로 모양 (TLS) 단계의 수치 조사를 했습니다. 결과는 이러한 유형의 배수로가 확대 비율 LT / Wt (LT는 총 가장자리 길이, Wt는 배수로의 폭)를 증가시키기 때문에 더 나은 성능을 갖는 것으로 관찰되었습니다. 또한 사다리꼴 미로 모양의 계단식 배수로는 더 큰 마찰 계수와 더 낮은 잔류 수두를 가지고 있습니다. 마찰 계수는 다양한 배율에 대해 0.79에서 1.33까지 다르며 평평한 계단식 배수로의 경우 대략 0.66과 같습니다. 또한 TLS 계단식 배수로에서 잔류 수두의 비율 (Hres / dc)은 약 2.89이고 평평한 계단식 배수로의 경우 약 4.32와 같습니다.
Shahheydari et al. (2015)는 Flow-3D 소프트웨어, RNG k-ε 모델 및 VOF (Volume of Fluid) 방법을 사용하여 배출 계수 및 에너지 소산과 같은 자유 표면 흐름의 프로파일을 연구하여 스키밍 흐름 체제에서 계단식 배수로에 대한 흐름을 조사했습니다. 실험 결과와 비교했습니다. 결과는 에너지 소산 율과 방전 계수율의 관계가 역으로 실험 모델의 결과와 잘 일치 함을 보여 주었다.
Mohammad Rezapour Tabari & Tavakoli (2016)는 계단 높이 (h), 계단 길이 (L), 계단 수 (Ns) 및 단위 폭의 방전 (q)과 같은 다양한 매개 변수가 계단식 에너지 소산에 미치는 영향을 조사했습니다. 방수로. 그들은 해석에 FLOW-3D 소프트웨어를 사용하여 계단식 배수로에서 에너지 손실과 임계 흐름 깊이 사이의 관계를 평가했습니다. 또한 유동 난류에 사용되는 방정식과 표준 k-ɛ 모델을 풀기 위해 유한 체적 방법을 적용했습니다. 결과에 따르면 스텝 수가 증가하고 유량 배출량이 증가하면 에너지 손실이 감소합니다. 얻은 결과를 다른 연구와 비교하고 경험적, 수학적 조사를 수행하여 결국 합격 가능한 결과를 얻었습니다.
METHODOLOGY
ListenReadSpeaker webReader: ListenFor all numerical models the basic principle is very similar: a set of partial differential equations (PDE) present the physical problems. The flow of fluids (gas and liquid) are governed by the conservation laws of mass, momentum and energy. For Computational Fluid Dynamics (CFD), the PDE system is substituted by a set of algebraic equations which can be worked out by using numerical methods (Versteeg & Malalasekera 2007). Flow-3D uses the finite volume approach to solve the Reynolds Averaged Navier-Stokes (RANS) equation, by applying the technique of Fractional Area/Volume Obstacle Representation (FAVOR) to define an obstacle (Flow Science Inc. 2012). Equations (1) and (2) are RANS and continuity equations with FAVOR variables that are applied for incompressible flows.
(1)
(2)where is the velocity in xi direction, t is the time, is the fractional area open to flow in the subscript directions, is the volume fraction of fluid in each cell, p is the hydrostatic pressure, is the density, is the gravitational force in subscript directions and is the Reynolds stresses.
Turbulence modelling is one of three key elements in CFD (Gunal 1996). There are many types of turbulence models, but the most common are Zero-equation models, One-equation models, Two-equation models, Reynolds Stress/Flux models and Algebraic Stress/Flux models. In FLOW-3D software, five turbulence models are available. The formulation used in the FLOW-3D software differs slightly from other formulations that includes the influence of the fractional areas/volumes of the FAVORTM method and generalizes the turbulence production (or decay) associated with buoyancy forces. The latter generalization, for example, includes buoyancy effects associated with non-inertial accelerations.
The available turbulence models in Flow-3D software are the Prandtl Mixing Length Model, the One-Equation Turbulent Energy Model, the Two-Equation Standard Model, the Two-Equation Renormalization-Group (RNG) Model and large Eddy Simulation Model (Flow Science Inc. 2012).In this research the RNG model was selected because this model is more commonly used than other models in dealing with particles; moreover, it is more accurate to work with air entrainment and other particles. In general, the RNG model is classified as a more widely-used application than the standard k-ɛ model. And in particular, the RNG model is more accurate in flows that have strong shear regions than the standard k-ɛ model and it is defined to describe low intensity turbulent flows. For the turbulent dissipation it solves an additional transport equation:
(3)where CDIS1, CDIS2, and CDIS3 are dimensionless parameters and the user can modify them. The diffusion of dissipation, Diff ɛ, is
(4)where u, v and w are the x, y and z coordinates of the fluid velocity; , , and , are FLOW-3D’s FAVORTM defined terms; and are turbulence due to shearing and buoyancy effects, respectively. R and are related to the cylindrical coordinate system. The default values of RMTKE, CDIS1 and CNU differ, being 1.39, 1.42 and 0.085 respectively. And CDIS2 is calculated from turbulent production () and turbulent kinetic energy ().The kinematic turbulent viscosity is the same in all turbulence transport models and is calculated from
(5)where : is the turbulent kinematic viscosity. is defined as the numerical challenge between the RNG and the two-equation k-ɛ models, found in the equation below. To avoid an unphysically large result for in Equation (3), since this equation could produce a value for very close to zero and also because the physical value of may approach to zero in such cases, the value of is calculated from the following equation:
(6)where : the turbulent length scale.
VOF and FAVOR are classifications of volume-fraction methods. In these two methods, firstly the area should be subdivided into a control volume grid or a small element. Each flow parameter like velocity, temperature and pressure values within the element are computed for each element containing liquids. Generally, these values represent the volumetric average of values in the elements.Numerous methods have been used recently to solve free infinite boundaries in the various numerical simulations. VOF is an easy and powerful method created based on the concept of a fractional intensity of fluid. A significant number of studies have confirmed that this method is more flexible and efficient than others dealing with the configurations of a complex free boundary. By using VOF technology the Flow-3D free surface was modelled and first declared in Hirt & Nichols (1981). In the VOF method there are three ingredients: a planner to define the surface, an algorithm for tracking the surface as a net mediator moving over a computational grid, and application of the boundary conditions to the surface. Configurations of the fluids are defined in terms of VOF function, F (x, y, z, t) (Hirt & Nichols 1981). And this VOF function shows the volume of flow per unit volume
(7)
(8)
(9)where is the density of the fluid, is a turbulent diffusion term, is a mass source, is the fractional volume open to flow. The components of velocity (u, v, w) are in the direction of coordinates (x, y, z) or (r, ). in the x-direction is the fractional area open to flow, and are identical area fractions for flow in the y and z directions. The R coefficient is based on the selection of the coordinate system.
The FAVOR method is a different method and uses another volume fraction technique, which is only used to define the geometry, such as the volume of liquid in each cell used to determine the position of fluid surfaces. Another fractional volume can be used to define the solid surface. Then, this information is used to determine the boundary conditions of the wall that the flow should be adapted for.
In this study, the experimental results of Ostad Mirza (2016) was simulated. In a channel composed of two 4 m long modules, with a transparent sidewall of height 0.6 m and 0.5 m width. The upstream chute slope (i.e. pseudo-bottom angle) Ɵ1 = 50°, the downstream chute slope Ɵ2 = 30° or 18.6°, the step heights h = 0.06 m, the total number of steps along the 50° chute 41 steps, the total number of steps along the 30° chute 34 steps and the total number of steps along the 18.6° chute 20 steps.
The flume inflow tool contained a jetbox with a maximum opening set to 0.12 meters, designed for passing the maximum unit discharge of 0.48 m2/s. The measurements of the flow properties (i.e. air concentration and velocity) were computed perpendicular to the pseudo-bottom as shown in Figure 1 at the centre of twenty stream-wise cross-sections, along the stepped chute, (i.e. in five steps up on the slope change and fifteen steps down on the slope change, namely from step number −09 to +23 on 50°–30° slope change, or from −09 to +15 on 50°–18.6° slope change, respectively).
Sketch of the air concentration C and velocity V measured perpendicular to the pseudo-bottom used by Mirza (Ostad Mirza 2016).
Sketch of the air concentration C and velocity V measured perpendicular to the pseudo-bottom used by Mirza (Ostad Mirza 2016).
Pressure sensors were arranged with the x/l values for different slope change as shown in Table 1, where x is the distance from the step edge, along the horizontal step face, and l is the length of the horizontal step face. The location of pressure sensors is shown in Table 1.Table 1
Location of pressure sensors on horizontal step faces
Θ(°)
L(m)
x/l (–)
50.0
0.050
0.35
0.64
–
–
–
30.0
0.104
0.17
0.50
0.84
–
–
18.6
0.178
0.10
0.30
0.50
0.7
0.88
Location of pressure sensors on horizontal step faces
Inlet boundary condition for Q = 0.235 m3/s and fluid elevation 4.21834 m.
Inlet boundary condition for Q = 0.235 m3/s and fluid elevation 4.21834 m.
A 3D numerical model of hydraulic phenomena was simulated based on an experimental study by Ostad Mirza (2016). The water surcharge and flow pressure over the stepped spillway was computed for two models of a stepped spillway with different discharge for each model. In this study, the package was used to simulate the flow parameters such as air entrainment, velocity distribution and dynamic pressures. The solver uses the finite volume technique to discretize the computational domain. In every test run, one incompressible fluid flow with a free surface flow selected at 20̊ was used for this simulation model. Table 2 shows the variables used in test runs.Table 2
Variables used in test runs
Test no.
Θ1 (°)
Θ2 (°)
h(m)
d0
q (m3s−1)
dc/h (–)
1
50
18.6
0.06
0.045
0.1
2.6
2
50
18.6
0.06
0.082
0.235
4.6
3
50
30.0
0.06
0.045
0.1
2.6
4
50
30.0
0.06
0.082
0.235
4.6
Table 2 Variables used in test runs
For stepped spillway simulation, several parameters should be specified to get accurate simulations, which is the scope of this research. Viscosity and turbulent, gravity and non-inertial reference frame, air entrainment, density evaluation and drift-flux should be activated for these simulations. There are five different choices in the ‘viscosity and turbulent’ option, in the viscosity flow and Renormalized Group (RNG) model. Then a dynamical model is selected as the second option, the ‘gravity and non-inertial reference frame’. Only the z-component was inputted as a negative 9.81 m/s2 and this value represents gravitational acceleration but in the same option the x and y components will be zero. Air entrainment is selected. Finally, in the drift-flux model, the density of phase one is input as (water) 1,000 kg/m3 and the density of phase two (air) as 1.225 kg/m3. Minimum volume fraction of phase one is input equal to 0.1 and maximum volume fraction of phase two to 1 to allow air concentration to reach 90%, then the option allowing gas to escape at free surface is selected, to obtain closer simulation.
The flow domain is divided into small regions relatively by the mesh in Flow-3D numerical model. Cells are the smallest part of the mesh, in which flow characteristics such as air concentration, velocity and dynamic pressure are calculated. The accuracy of the results and simulation time depends directly on the mesh block size so the cell size is very important. Orthogonal mesh was used in cartesian coordinate systems. A smaller cell size provides more accuracy for results, so we reduced the number of cells whilst including enough accuracy. In this study, the size of cells in x, y and z directions was selected as 0.015 m after several trials.
Figure 3 shows the 3D computational domain model 50–18.6 slope change, that is 6.0 m length, 0.50 m width and 4.23 m height. The 3D model of the computational domain model 50–30 slope changes this to 6.0 m length, 0.50 m width and 5.068 m height and the size of meshes in x, y, and z directions are 0.015 m. For the 50–18.6 slope change model: both total number of active and passive cells = 4,009,952, total number of active cells = 3,352,307, include real cells (used for solving the flow equations) = 3,316,269, open real cells = 3,316,269, fully blocked real cells equal to zero, external boundary cells were 36,038, inter-block boundary cells = 0 (Flow-3D report). For 50–30 slope change model: both total number of active and passive cells = 4,760,002, total number of active cells equal to 4,272,109, including real cells (used for solving the flow equations) were 3,990,878, open real cells = 3,990,878 fully blocked real cells = zero, external boundary cells were 281,231, inter-block boundary cells = 0 (Flow-3D report).
Figure3 The 3D computational domain model (50–18.6) slope change, and boundary condition for (50–30 slope change) model.
The 3D computational domain model (50–18.6) slope change, and boundary condition for (50–30 slope change) model.
When solving the Navier-Stokes equation and continuous equations, boundary conditions should be applied. The most important work of boundary conditions is to create flow conditions similar to physical status. The Flow-3D software has many types of boundary condition; each type can be used for the specific condition of the models. The boundary conditions in Flow-3D are symmetry, continuative, specific pressure, grid overlay, wave, wall, periodic, specific velocity, outflow, and volume flow rate.
There are two options to input finite flow rate in the Flow-3D software either for inlet discharge of the system or for the outlet discharge of the domain: specified velocity and volume flow rate. In this research, the X-minimum boundary condition, volume flow rate, has been chosen. For X-maximum boundary condition, outflow was selected because there is nothing to be calculated at the end of the flume. The volume flow rate and the elevation of surface water was set for Q = 0.1 and 0.235 m3/s respectively (Figure 2).
The bottom (Z-min) is prepared as a wall boundary condition and the top (Z-max) is computed as a pressure boundary condition, and for both (Y-min) and (Y-max) as symmetry.
The air concentration distribution profiles in two models of stepped spillway were obtained at an acquisition time equal to 25 seconds in skimming flow for both upstream and downstream of a slope change 50°–18.6° and 50°–30° for different discharge as in Table 2, and as shown in Figure 4 for 50°–18.6° slope change and Figure 5 for 50°–30° slope change configuration for dc/h = 4.6. The simulation results of the air concentration are very close to the experimental results in all curves and fairly close to that predicted by the advection-diffusion model for the air bubbles suggested by Chanson (1997) on a constant sloping chute.
Figure 4
Experimental and simulated air concentration distribution for steps number −5, +1, +5, +8, +11 and +15 along the 50°–18.6° slope change for dc/h = 4.6.
VIEW LARGEDOWNLOAD SLIDE
Experimental and simulated air concentration distribution for steps number −5, +1, +5, +8, +11 and +15 along the 50°–18.6° slope change for dc/h = 4.6.
Experimental and simulated air concentration distribution for steps number −5, +1, +5, +8, +11 and +15 along the 50°–18.6° slope change for dc/h = 4.6.
Figure5 Experimental and simulated air concentration distribution for steps number −5, +1, +5, +11, +19 and +22 along the 50°–30° slope change, for dc/h = 4.6.
Experimental and simulated air concentration distribution for steps number −5, +1, +5, +11, +19 and +22 along the 50°–30° slope change, for dc/h = 4.6.
Figure 6 Experimental and simulated dimensionless velocity distribution for steps number −5, −1, +1, +5, +8, +11 and +15 along the 50°–18.6° slope change for dc/h = 2.6.
Experimental and simulated dimensionless velocity distribution for steps number −5, −1, +1, +5, +8, +11 and +15 along the 50°–18.6° slope change for dc/h = 2.6.
Figure 7 Experimental and simulated dimensionless velocity distribution for steps number −5, −1, +1, +5. +11, +15 and +22 along the 50°–30° slope change for dc/h = 2.6.
Experimental and simulated dimensionless velocity distribution for steps number −5, −1, +1, +5. +11, +15 and +22 along the 50°–30° slope change for dc/h = 2.6.
But as is shown in all above mentioned figures it is clear that at the pseudo-bottom the CFD results of air concentration are less than experimental ones until the depth of water reaches a quarter of the total depth of water. Also the direction of the curves are parallel to each other when going up towards the surface water and are incorporated approximately near the surface water. For all curves, the cross-section is separate between upstream and downstream steps. Therefore the (-) sign for steps represents a step upstream of the slope change cross-section and the (+) sign represents a step downstream of the slope change cross-section.
The dimensionless velocity distribution (V/V90) profile was acquired at an acquisition time equal to 25 seconds in skimming flow of the upstream and downstream slope change for both 50°–18.6° and 50°–30° slope change. The simulation results are compared with the experimental ones showing that for all curves there is close similarity for each point between the observed and experimental results. The curves increase parallel to each other and they merge near at the surface water as shown in Figure 6 for slope change 50°–18.6° configuration and Figure 7 for slope change 50°–30° configuration. However, at step numbers +1 and +5 in Figure 7 there are few differences between the simulated and observed results, namely the simulation curves ascend regularly meaning the velocity increases regularly from the pseudo-bottom up to the surface water.
Figure 8 (50°–18.6° slope change) and Figure 9 (50°–30° slope change) compare the simulation results and the experimental results for the presented dimensionless dynamic pressure distribution for different points on the stepped spillway. The results show a good agreement with the experimental and numerical simulations in all curves. For some points, few discrepancies can be noted in pressure magnitudes between the simulated and the observed ones, but they are in the acceptable range. Although the experimental data do not completely agree with the simulated results, there is an overall agreement.
Figure 8 Comparison between simulated and experimental results for the dimensionless pressure for steps number −1, −2, −3 and +1, +2 +3 and +20 on the horizontal step faces of 50°–18.6° slope change configuration, for dc/h = 4.6, x is the distance from the step edge.
Comparison between simulated and experimental results for the dimensionless pressure for steps number −1, −2, −3 and +1, +2 +3 and +20 on the horizontal step faces of 50°–18.6° slope change configuration, for dc/h = 4.6, x is the distance from the step edge.
Figure 9 Comparison between simulated and experimental results for the dimensionless pressure for steps number −1, −2, −3 and +1, +2 and +30, +31 on the horizontal step face of 50°–30° slope change configuration, for dc/h = 4.6, x is the distance from the step edge.
Comparison between simulated and experimental results for the dimensionless pressure for steps number −1, −2, −3 and +1, +2 and +30, +31 on the horizontal step face of 50°–30° slope change configuration, for dc/h = 4.6, x is the distance from the step edge.
The pressure profiles were acquired at an acquisition time equal to 70 seconds in skimming flow on 50°–18.6°, where p is the measured dynamic pressure, h is step height and ϒ is water specific weight. A negative sign for steps represents a step upstream of the slope change cross-section and a positive sign represents a step downstream of the slope change cross-section.
Figure 10 shows the experimental streamwise development of dimensionless pressure on the 50°–18.6° slope change for dc/h = 4.6, x/l = 0.35 on 50° sloping chute and x/l = 0.3 on 18.6° sloping chute compared with the numerical simulation. It is obvious from Figure 10 that the streamwise development of dimensionless pressure before slope change (steps number −1, −2 and −3) both of the experimental and simulated results are close to each other. However, it is clear that there is a little difference between the results of the streamwise development of dimensionless pressure at step numbers +1, +2 and +3. Moreover, from step number +3 to the end, the curves get close to each other.
Figure 10 Comparison between experimental and simulated results for the streamwise development of the dimensionless pressure on the 50°–18.6° slope change, for dc/h = 4.6, and x/l = 0.35 on 50° sloping chute and x/l = 0.3 on 18.6° sloping chute.
Comparison between experimental and simulated results for the streamwise development of the dimensionless pressure on the 50°–18.6° slope change, for dc/h = 4.6, and x/l = 0.35 on 50° sloping chute and x/l = 0.3 on 18.6° sloping chute.
Figure 11 compares the experimental and the numerical results for the streamwise development of the dimensionless pressure on the 50°–30° slope change, for dc/h = 4.6, and x/l = 0.35 on 50° sloping chute and x/l = 0.17 on 30° sloping chute. It is apparent that the outcomes of the experimental work are close to the numerical results, however, the results of the simulation are above the experimental ones before the slope change, but the results of the simulation descend below the experimental ones after the slope change till the end.
Figure 11 Comparison between experimental and simulated results for the streamwise development of the dimensionless pressure on the 50°–30° slope change, for dc/h = 4.6, and x/l = 0.35 on 50° sloping chute and x/l = 0.17 on 30° sloping chute.
Comparison between experimental and simulated results for the streamwise development of the dimensionless pressure on the 50°–30° slope change, for dc/h = 4.6, and x/l = 0.35 on 50° sloping chute and x/l = 0.17 on 30° sloping chute.
In this research, numerical modelling was attempted to investigate the effect of abrupt slope change on the flow properties (air entrainment, velocity distribution and dynamic pressure) over a stepped spillway with two different models and various flow rates in a skimming flow regime by using the CFD technique. The numerical model was verified and compared with the experimental results of Ostad Mirza (2016). The same domain of the numerical model was inputted as in experimental models to reduce errors as much as possible.
Flow-3D is a well modelled tool that deals with particles. In this research, the model deals well with air entrainment particles by observing their results with experimental results. And the reason for the small difference between the numerical and the experimental results is that the program deals with particles more accurately than the laboratory. In general, both numerical and experimental results showed that near to the slope change the flow bulking, air entrainment, velocity distribution and dynamic pressure are greatly affected by abrupt slope change on the steps. Although the extent of the slope change was relatively small, the influence of the slope change was major on flow characteristics.
The Renormalized Group (RNG) model was selected as a turbulence solver. For 3D modelling, orthogonal mesh was used as a computational domain and the mesh grid size used for X, Y, and Z direction was equal to 0.015 m. In CFD modelling, air concentration and velocity distribution were recorded for a period of 25 seconds, but dynamic pressure was recorded for a period of 70 seconds. The results showed that there is a good agreement between the numerical and the physical models. So, it can be concluded that the proposed CFD model is very suitable for use in simulating and analysing the design of hydraulic structures.
이 연구에서 수치 모델링은 두 가지 다른 모델과 다양한 유속을 사용하여 스키밍 흐름 영역에서 계단식 배수로에 대한 유동 특성 (공기 혼입, 속도 분포 및 동적 압력)에 대한 급격한 경사 변화의 영향을 조사하기 위해 시도되었습니다. CFD 기술. 수치 모델을 검증하여 Ostad Mirza (2016)의 실험 결과와 비교 하였다. 오차를 최대한 줄이기 위해 실험 모형과 동일한 수치 모형을 입력 하였다.
Flow-3D는 파티클을 다루는 잘 모델링 된 도구입니다. 이 연구에서 모델은 실험 결과를 통해 결과를 관찰하여 공기 혼입 입자를 잘 처리합니다. 그리고 수치와 실험 결과의 차이가 작은 이유는 프로그램이 실험실보다 입자를 더 정확하게 다루기 때문입니다. 일반적으로 수치 및 실험 결과는 경사에 가까워지면 유동 벌킹, 공기 혼입, 속도 분포 및 동적 압력이 계단의 급격한 경사 변화에 크게 영향을받는 것으로 나타났습니다. 사면 변화의 정도는 상대적으로 작았지만 사면 변화의 영향은 유동 특성에 큰 영향을 미쳤다.
Renormalized Group (RNG) 모델이 난류 솔버로 선택되었습니다. 3D 모델링의 경우 계산 영역으로 직교 메쉬가 사용되었으며 X, Y, Z 방향에 사용 된 메쉬 그리드 크기는 0.015m입니다. CFD 모델링에서 공기 농도와 속도 분포는 25 초 동안 기록되었지만 동적 압력은 70 초 동안 기록되었습니다. 결과는 수치 모델과 물리적 모델간에 좋은 일치가 있음을 보여줍니다. 따라서 제안 된 CFD 모델은 수력 구조물의 설계 시뮬레이션 및 해석에 매우 적합하다는 결론을 내릴 수 있습니다.
Flow Science의 CFD 엔지니어 인 개발자 및 Adwaith Gupta 인 Zongxian Liang이 블로그에 참여했습니다.
힘과 에너지 손실을 정확하게 예측하는 것은 오리피스 판에서 배출, 장애물을 지나는 흐름이나 갑작스런 수축이 있는 파이프에서의 흐름과 같이 많은 엔지니어링 문제를 모델링하는 데 중요합니다. 곧 출시 될 FLOW–3D v12.0 릴리스에는 새로운 수치 옵션 인 가상 경계 방법 (Immersed Boundary Method)이 있어 이러한 문제의 흐름을 정확하게 예측합니다.
가상 경계 방법(정확한 고스트 셀 기반)은 고체 유체 인터페이스에서 수치 자속 계산의 정확성을 향상시킵니다. Flow Science의 개발자 인 Zongxian Liang은 갑작스런 수축 파이프와 선박 선체에 대한 검증 예제를 제공합니다. 가상 경계 방법 및 고스트 셀 접근법에 대한 간단한 수학적 세부 사항은 블로그 끝에서 설명합니다.
갑작스럽게 수축되는 관
가상 경계 솔버의 정확도를 나타내는 유체 문제 중 하나는 그림 1과 같이 수축 파이프에서의 물의 손실을 추정하는 것입니다. 파이프는 직경 3m의 큰 섹션에서 1m의 작은 섹션으로 갑자기 수축됩니다. 대형 파이프 입구의 유량은 4m3/sec입니다. 속도 헤드는 수축 위치와 관련하여 업스트림 및 다운 스트림에서 3.5m로 측정됩니다. 문헌 [1,2]에서 사용 된 다른 가정에 기초하여, 머리 손실의 이론적 가치는 0.494m에서 0.711m의 범위에 있어야합니다. 이 시뮬레이션에서 하나의 직교 메쉬 블록이 전체 형상에 사용되고 압력 경계는 출구에서 정체 압력이 0으로 지정됩니다. 2 방정식 k-ω 모델은 최대 난류 혼합 길이가 0.07m로 설정되어 있습니다. 음의 x 방향으로 중력이 활성화됩니다. 완료 시간은 흐름이 일정하고 완전히 발달 된 것으로 간주되는 15 초로 설정됩니다.
그림 1. 수축 파이프의 모양, 속도 헤드 측정을위한 플럭스 표면의 위치 및 흐름 방향을 설명하는 회로도
갑작스런 수축 위치에서 세포 크기 및 메쉬 정렬의 효과를 조사하기 위해 2 변수 파라 메트릭 연구가 수행되었습니다. 메쉬의 셀 크기는 0.1m 및 0.05m입니다. 표 1에 나열된 4 가지 메쉬 정렬을 테스트했습니다. “정렬 됨”은 메시 평면이 갑작스러운 수축 위치와 정렬되는 기준 사례를 나타내고, “Z- 시프트 : X %”는 메시 평면이 z- 방향으로 수축 위치로부터 셀 크기의 X %만큼 시프트되었음을 나타냅니다.
가상 경계 솔버가 제공하는 예측은 모두 이론적으로 0.494에서 0.711 사이입니다. 특히 작은 셀 크기가 0.05m 인 경우 헤드 손실은 이론적 값의 중앙값의 4.6 % 인 0.603 이내입니다.
그리드 정렬
Aligned
Z-shifted: 25%
Z-shifted: 50%
Z-shifted: 75%
Cell size (m)
0.1
0.706
0.710
0.647
0.666
0.05
0.607
0.620
0.575
0.589
표1 : 가상 경계 솔버에 의해 예측되는 헤드 손실 (m)
선체 모델에 대한 저항력
외부 유동 역학 문제에서 힘의 정확한 예측은 일반적으로 설계 단계에서 중요합니다. 자유 표면의 외부 유동 문제의 예는 NAVY 선박 모델 선체에 대한 전체 저항력의 계산입니다. 이 경우 선체 길이는 5.72m이고 구배는 0.248m입니다. 선체 길이와 평균 유속 2.10 m/s 를 기준으로 시뮬레이션에서 레이놀즈 수는 약 12 × 106입니다. 이 경우는 대칭이므로 선체의 절반 만 모델링됩니다. 계산 영역은 길이 30m x 폭 8m, 깊이 5.5m이며 가장 작은 셀 크기가 0.02m 인 3 개의 중첩 된 메쉬 블록을 갖습니다. 입구 및 출구 경계에는 각각 속도 및 유출 조건이 사용됩니다. 역동적인 난류 길이 스케일 계산을 사용한 RNG 난류 모델은 난류 흐름과 운동량 이류에 대한 2 차 단 조성 보존 체계를 모델링하는 데 사용됩니다.
자유 표면 근처의 압력 윤곽 및 저항력 이력을 보여주는 애니메이션.
실험에서 총 항력 계수 0.0423을 기준으로 선체 모델의 절반에 대해 총 저항력은 22.62N입니다. 시뮬레이션의 힘은 x 방향의 전단력과 압력 력의 합으로 평균 35에서 50 초입니다. 가상 경계 솔버는 22.43N으로 실험 결과보다 0.8 % 낮습니다.
결론
우리는 이 두 가지 검증에서 가상 경계 방법이 문헌에 제공된 이론적 범위 내에서 머리 손실과 힘을 정확하게 추정한다는 것을 알 수 있습니다. 가상 경계 방법은 매우 기본적인 수준에서 플럭스 추정의 정확도를 향상 시키며 대부분은 아니지만 대부분의 어플리케이션에 대한 시뮬레이션 결과를 향상시킬 것으로 예상됩니다. 고스트 셀 기반 가상 경계 방법 개발에 대한 자세한 내용은 계속 읽으십시오. 그렇지 않으면 다음 블로그 게시물을 계속 지켜봐 주시기 바랍니다!
고스트 셀 기반 가상 경계 방법
FLOW-3D(볼드 기울기)에서, 자유 슬립 경계 조건은 속도의 대류에 적용되어 분수 셀 영역과 고체 경계 근처의 체적에 의해 야기되는 수치 경계층을 제거합니다. 제어 체적에 대한 합리적인 플럭스를 추정하기 위해, 가상 경계 솔버는 그림 2와 같이 경계 조건을 암시적으로 만족시키는 고체 속의 유체 속도를 계산합니다. 고체의 유체 셀을 고스트 셀이라고하며 이 방법을 일반적으로 고스트 셀 방식이라고 합니다.
그림 2. 제어 체적 왼쪽면의 플럭스 (파란색 점선으로 묶음)는 솔리드 안의 고스트 셀 u_ (i-1)의 속도를 사용하여 계산됩니다.
경계 조건을 시행하기 위해 고스트 셀의 이미지 포인트 (IP로 표시되는 열린 다이아몬드)가 고스트 셀 (GC로 표시되는 빨간색 다이아몬드)에서 법선의 벽까지 선분을 연장하여 유체 영역에 생성됩니다. GC와 IP 사이의 중간 점 (경계-절편 점으로 BI로 표시되는 열린 원)에서 벽과 교차합니다. BI의 비 침투 경계 조건과 GC 및 IP의 접선 속도가 벽 표면 속도와 같다고 가정하면 고스트 셀의 속도는 다음 방정식으로 계산됩니다.
여기서,는 고스트 셀에서의 유체 속도, 이미지-포인트 및 경계-절편 포인트이고, 경계에서의 단위 법선 벡터입니다. 우리는 3 차 보간법을 사용하여 주변 셀에서 유체 속도를 사용하여 속도 값을 근사합니다.
여기서 u1, v1 그리고 w1 는 이미지 포인트를 둘러싼 보간 노드의 속도이고 α1, β1 및 γ1은 보간 계수입니다. 보간 계수 계산에 대한 자세한 내용은 Ref. 4. 찾을 수 있습니다.
보간은 다른 고스트 셀의 속도 값을 불러 와서 고스트 셀의 결합 시스템이 생성됩니다. 우리는 결과 시스템의 빠른 솔루션을 얻기 위해 수렴 가속 기술과 함께 Jacobi 기반 반복 방법을 사용합니다.
참고 문헌
1. White, F. M., Fluid Mechanics (McGraw-Hill Book Company, 2003). 2. Saleh, J., Fluid Flow Handbook (McGraw-Hill Professional, 2002). 3. Larsson, L., Stern, F. & Bertram, V., Benchmarking of computational fluid dynamics for ship flows: the Gothenburg 2000 workshop. Journal of Ship Research 47 (1), 63–81 (2003). 4. Mittal, R. et al., A versatile sharp interface immersed boundary method for incompressible flows with complex boundaries. Journal of computational physics 227 (10), 4825-4852 (2008).
이 기사에서 개발자인 Zongxian Liane박사는 곧 출시될 FLOW-3D v11.3에서 사용할 수 있는 새로운 Immersed Boundary Method에 대해 설명합니다.
힘과 에너지 손실에 대한 정확한 예측은 오리피스 판에서의 배출, 장애물을 지나가는 흐름 및 갑작스런 수축 관에서의 흐름과 같은 많은 엔지니어링 문제를 분석하는데 중요합니다. 셀 면적 및 부피 Method인 FAVORTM은 30년 전에 도입된 이래로 FLOW-3D의 표준 솔버로 적용되었으며 벽 근처의 운동량 fluxes를 근사화하는 간단한 방법을 사용했습니다 (Hirt and Sicilian 1985). 벽이나 자유 표면 근처에서 운동 이류항을 계산할 때 솔리드 또는 보이드 영역 내에 위치한 속도 값은 경계층의 모양을 제거하기 위해 0으로 설정됩니다. 물리적 관점에서 이 방법은 벽의 돌출부에 자유 미끄러짐(비침투)경계 조건을 적용하여 인공 경계층(Hirt1993)을 억제한다.
운동량 방정식에서 플럭스의 손실은 압력에 의해 보상됩니다. 특정 상황에서는 플럭스손실을 보상하는 압력의 비율이 시간에 따라 증가하며, 단일 유전물질로 표현되는 “세속적 불안정성”이라고 하는 수치적 불안정성을 야기할 수 있습니다. 속도의 증가 이러한 불안정성의 전개를 방지하기 위해, 경험적 기법을 사용하여 불안정성이 발생할 수 있는 위치에서 플럭스를 “보정” 했습니다. 그러나 이 방법은 선원으로부터의 플럭스 손실을 해결하지 못하며, 때때로 압력 변동과 같은 용액의 비정치적인 동작을 초래할 수 있습니다.
ghost – 내접 경계법 (Mittal et al., 2008)에 기초한 이류 항을 근사화하는 기법은 FLOW-3D v11.3을 위해 개발되었다. 이 내접 경계 방법 기술은 근본적으로이 문제를 해결하고보다 정확한 압력과 힘 예측을 제공합니다. ghost – 내접 경계법은 복잡한 형상을 포함하는 문제에서 전통적인 데카르트 그리드 근사법에서 강화 된 경계 처리로서 최근에 출현했다. 이 방법은 경계를 처리하는 수단 일 뿐이므로 기존의 해석기 구조가 비교적 적게 변경되어 기존의 FLOW-3D 해석기에 모델로 쉽게 추가 될 수 있으며 FLOW-3D의 다른 물리적 모델과 호환됩니다. 다양한 보간 방법과 함께 가중치 평균 프로브 기술을 사용하여 다른 지오메트리 구성을 처리합니다. 새 모델은 3D 메쉬 블록 또는 하이브리드 3D / 얕은 워터 메쉬 블록이있는 플로우에는 작동하지만 얕은 워터 메쉬에는 적합하지 않습니다.
Immersed Boundary Method Results
새로 도입된 경계 방법 모델의 간단한 예는 직경 1m의 원형 오리피스에서 물이 방출되는 것입니다. 물 용기의 길이는 10m, 폭은 10m, 오리피스 중앙부까지의 수위는 6m이다. 애니메이션에 표시된 것처럼 오리피스 Q에서 표고, h및 볼륨 유량의 강하는 각각 2차 곡선과 선형 곡선을 따릅니다.
시뮬레이션에서 배출 Cd의 평균 계수는 0.660으로, 비대칭 값 0.611보다 약 8% 큽니다(SwameeandSwamee, 2010). immersed boundary solver 을 사용한 시뮬레이션은 이중 인터페이스(Xeon E5-2623 v3)에서 약 19시간이 소요된다. 반면에 the standard solver의 방전 계수와 벽-블록은 각각 0.800과 39시간이 소요된다.
또 다른 예는 NAVY 선박 모델 선체에 대한 총 저항력의 계산입니다. 이 경우, 선체 길이는 5.72m이고, 드래프트는 0.248m이다. 평균유속은 2.10m/s이고, 레이놀즈 수는 약 12 × 106입니다. 이 해석은 대칭이므로 선체의 절반만 모델링됩니다. 계산 영역은 길이 30m, 너비 8m, 깊이 5.5m입니다. 선체 절반에 대해 실험적으로 얻어진 총 저항력의 평균은 22.62N이다 (Larsson et al., 2003). the standard solver의 총 저항력의 평균은 24.41N이었으며 실험 결과보다 7.9 % 차이가 있으며 immersed boundary solver 경우 총 저항력의 평균은 22.43N이었고 0.8 % 더 낮았습니다 (오류가 8 개 줄었습니다. 또한 immersed 경계 솔버는 약 40 시간 만에 완성되었으며 표준 솔버보다 8 시간 빠릅니다).
References
Hirt, C., & Sicilian, J. (1985). A porosity technique for the definition of obstacles in rectangular cell meshes. International Conference on Numerical Ship Hydrodynamics, 4th. Washington, D.C.
Hirt, C. (1993). Volume-fraction techniques: powerful tools for wind engineering. Journal of Wind Engineering and Industrial Aerodynamics, 46 & 47, 327-338.
Mittal, R., Dong, H., Bozkurttas, M., Najjar, F., Vargas, A., & von Loebbecke, A. (2008). A versatile sharp interface immersed boundary method for incompressible flows with complex boundaries. Journal of computational physics, 227(10), 4825-4852.
Swamee, P., & Swamee , N., (2010). Discharge equation of a circular sharp-crested orifice. Journal of Hydraulic Research, 48(1), 106-107.
This note describes the modeling used in FLOW-3D® for thermal expansion processes in onefluid, incompressible flows. Volume changes are modeled in unconfined flows while the limited compressibility model may be used to compute the change is pressure in flows that are confined and density cannot change.
FLOW-3D 는 고도의 정확성이 필요한 항공, 자동차, 수자원 및 환경, 금속 산업분야의 세계적인 선진 기업에서 사용됩니다.
FLOW-3D의 광범위한 다중 물리 기능(multiphysics )은 자유 표면 흐름, 표면 장력, 열전달, 난류, 움직이는 물체, 단순 변형 고체, 전기 기계, 캐비테이션, 탄/소성, 점성, 가소성, 입자, 고체 연료, 연소 및 위상 변화를 포함합니다. 이러한 모델은 FLOW-3D를 사용하는 사용자들이 기술 및 과학의 광범위한 문제를 해결하도록 설계를 최적화하고 복잡한 프로세스 흐름에 대한 통찰력을 얻을 수 있도록 합니다.
본 자료는 국내 사용자들의 편의를 위해 원문 번역을 해서 제공하기 때문에 일부 오역이 있을 수 있어서 원문과 함께 수록합니다. 자료를 이용하실 때 참고하시기 바랍니다.
What are Artificial and Numerical Viscosities?
The earliest, successful application of computational fluid dynamics was in connection with the Manhattan Project during World War II. Researchers used computations to study the propagation and interaction of shock waves, a subject crucial to the success of the atomic bomb.
전산 유체 역학 (CFD)의 적용으로 성과를 거둔 가장 오래된 예는 제 2 차 세계 대전 동안 진행된 맨해튼 계획에 관한 것이 있습니다. 연구진은 원자 폭탄의 개발에 필수 주제인 충격파의 전파와 상호 작용을 이해하기 위해 계산에 의한 분석을 실시했습니다.
Shock Wave Discontinuities/충격파의 불연속성
Shock waves are mathematically treated as discontinuities, but it was quickly recognized this would cause problems for any numerical solution. Of course, a shock wave is not a true physical discontinuity, but a very narrow transition zone whose thickness is on the order of a few molecular mean-free paths. Application of the conservation of mass, momentum, and energy conditions across a shock wave requires that there be a transformation of kinetic energy into heat energy. Physically, this transformation can be represented as a viscous dissipation, which was the idea latched onto by early investigators.
충격파는 수학적으로는 불연속적인 현상으로 간주되지만 어떤 수치 솔루션을 채용하고도 문제를 일으킬 수 있다는 것은 일찍부터 인식되어 있었습니다. 물론 충격파는 물리적으로 불연속적인 현상이 아니라, 분자의 평균 자유 공정과 같은 정도의 두께를 가진 매우 좁은 전이층입니다. 충격파에 질량, 운동량, 에너지의 저장 조건을 적용하려면 운동 에너지에서 열에너지로 변환 할 필요가 있습니다. 연구자들은 일찍부터 이 변환을 물리학적으로는 점성 소산으로 표현해야 한다는 것을 이해하고 있었습니다.
By introducing an unphysically large value of viscosity, investigators were able to thicken shock transition zones to where they could be resolved computationally. This artificial increase in the value of viscosity became known as an artificial viscosity.
연구자들은 비 물리적으로 큰 값의 점성을 통합하여 계산을 해결할 수 있을 때까지 충격파 전이 층을 두껍게하는 데 성공했습니다. 이렇게 인공적으로 점성의 값을 증가시킨 것을 “인공 점성”라고 부르게되었습니다.
Viscosity Dissipation/점성 소산
If the viscosity isn’t large enough, velocity oscillations about the correct mean velocity are observed to develop behind a shock. These oscillations can be interpreted as a macroscopic version of heat energy, i.e., fluctuating kinetic energy in place of fluctuating molecular energy. In hydraulic jumps, the hydraulic analogy of a shock wave, this fluctuating energy appears as a sequence of large eddies behind the jump.
점성이 충분히 높지 않은 경우 충격파 뒤에서 올바른 평균 속도 주위에서 속도가 진동하는 것이 확인되고 있습니다. 이러한 진동은 열에너지를 거시적으로 나타낸 것, 즉 변화하는 분자 에너지 대신에 변화하는 운동 에너지로 해석 할 수 있습니다. 수중에서 발생하는 충격파라고도 할 수 다이빙이 발생하면이 변동하는 에너지는다이빙 뒤에서 연속적인 큰 소용돌이로 나타납니다.
Artificial Viscosity/인공 점성
The proper formulation and magnitude needed for an artificial viscosity has undergone many refinements over the years and includes tests to apply this viscosity only in regions undergoing strong compression and with magnitudes that are various functions of the first and/or second power of the compression rate. The culmination of these refinements is best exhibited in the method pioneered by Godunov (S.K. Godunov, Mat. Sbornik 47, 271 (1959); translated as JPRS 7225, U.S. Dept. Com., 1960), in which a local “shock tube” or elementary wave solution is used to capture the existence and propagation characteristics of shock and rarefaction waves.
인공 점성의 엄격한 수식화와 필요한 값의 크기는 수년 동안 다양한 개량이 이루어지고 왔습니다. 강한 압축을 받는, 압축률의 1 제곱 및/또는 제곱의 함수로 표현하는 크기를 갖는 영역에서 이 점성을 적용하기위한 테스트도 개발되고 있습니다. 이렇게 쌓인 개선의 성과는 Godunov 의해 개발 된 기법에 잘 나타나 있습니다 (S.K. Godunov, Mat. Sbornik Volume 47, p.271 (1959), JPRS 7225로 U.S. Dept. Commerce 의해 번역, 1960). 이 방법은 국소적인 “충격파 관”라는 단순한 파동 실험 장치를 이용하여 충격파 및 희석파의 존재 및 전파 특성을 포착합니다.
Numerical Viscosity/수치 점성
Although artificial viscosity was introduced for numerical reasons, it is an elective addition used to modify a physical process so that it can be more easily computed. Artificial viscosity should not be confused with numerical viscosity, which is an unwanted consequence of certain types of numerical approximations.
인공 점성은 수치적인 이유로 고안되었습니다 만, 물리적 프로세스를 보다 쉽게 계산할 수 있도록 수정하기 위해 선택되어 도입된 개념입니다. 인공 점성은 수치 점성과 혼동해서는 안됩니다. 수치 근사 유형에 따라 수치 점성은 바람직하지 않습니다.
Numerical viscosity arises from discrete approximations to the momentum advection terms in Eulerian equations, or from re-zoning operations used in Lagrangian formulations. The origin of the effect is the use of a homogenizing assumption in the elements or control volumes underlying the approximation scheme. For instance, when momentum is exchanged between neighboring elements through a convective flux the resulting contributions in a given element are combined with the momentum already there to arrive at a new value of average momentum for that element. This combining or homogenizing process introduces a smoothing effect. When another step to advance time is taken, this new value is passed on to the next element in the direction of flow. Repetition of this smoothing operation over the many steps needed to carry a solution forward in time contributes to a “diffusion” of momentum in the direction of flow.
수치 점성은 오일러 방정식의 운동량 이류(advection) 항에 이산 근사와 라그랑주 공식화에서 사용되는 리-조닝(re-zoning) 처리에서 발생합니다. 그 영향의 근원은 근사 체계의 기반에있는 요소와 컨트롤 볼륨에서 균질화를 위해 사용하는 가정입니다. 예를 들어, 대류 플럭스를 통해 인접 셀 간의 운동량이 교환되면, 교환에서 발생한 모든 요소의 기여도가 이미 존재하고 있던 운동량에 추가하여 해당 요소의 평균 운동량의 새로운 값이 됩니다. 이 합산, 즉 균질화 과정을 통해 스무딩 효과를 얻을 수 있습니다. 시간이 진행하고 다음 시간 단계로 이동하면 이 새로운 값은 흐름의 방향에서 다음에 요소에 전달됩니다. 분석 시간으로 전진시키기 위해 필요한 여러 단계에 걸쳐 이 평활화 처리가 반복 됨으로써 흐름의 방향으로 운동량의 ‘확산’이 생깁니다.
Strictly speaking, the numerical diffusion does not behave like a true viscous diffusion because it is associated with fluid convection and does not possess the correct stress-versus-strain-rate dependency associated with a real viscosity. For example, numerical diffusion does not satisfy Newtonian relativity because it depends on the choice of computational grid, which is an absolute reference frame for the numerical approximations. Also, because the amount of numerical diffusion is proportional to the velocity of flow through a grid, it does not have the rotational symmetry possessed by a real viscosity.
엄밀하게 말하면, 수치 확산은 유체 대류와 관련된 것으로, 실제의 점성과 관련된 정확한 응력 변형 속도 의존성을 갖지 않기 때문에 진정한 점성 확산 거동과는 다릅니다. 예를 들어, 수치 확산 숫자 근사치의 절대 기준 좌표인 계산 격자의 선택 때문에 뉴턴 역학에서 상대성 원리에 부합하지 않습니다. 또한 수치 확산량은 격자 내를 통과하는 흐름의 속도에 비례하기 때문에 실제 점성이 갖는 회전 대칭이 없습니다.
Numerical Approximations/수치 근사
Research into numerical approximation schemes that minimize numerical viscosity effects is a continuing activity of a large part of the CFD community. The difficulty in developing such schemes is that some smoothing must always be incorporated into a numerical solution to keep it computationally stable and to smooth out dispersion errors. Dispersion errors are those errors that arise because components of a solution having different grid resolution requirements may propagate through the grid with slightly different speeds. Whenever this occurs, unphysical oscillations develop in the solution where these components reinforce or cancel one another.
수치 점성의 영향을 최소한으로 억제하는 수치 근사 체계의 연구는 CFD 분야에서 큰 부분을 차지하고있는 지속적인 활동입니다. 이러한 체계를 개발하는 어려움은 계산 안정성을 유지하고 분산 오차를 부드럽게하기 위해 수치 해법에 항상 어떤 평활화 처리를 통합해야 하는 것입니다. 분산 오차는 다른 격자 해상도 요구 사항이 솔루션의 성분이 약간 다른 속도로 격자 내를 전파 할 수있는 것이 원인으로 생기는 오차입니다. 이것이 발생한 경우 그러한 성분이 강화된 또는 상쇄되는 등 해 비 물리적인 진동이 발생합니다.
The trick is to develop approximation schemes that remain accurate (i.e., have a minimum of numerical smoothing) and at the same time are robust (i.e., have sufficient numerical smoothing to compensate for dispersion errors and to remain computationally stable for a wide range of applications).
이에 대처하는 요령은 정확성을 유지하는 (즉, 최소한의 수치 적 평활화를 포함) 동시에 강력한 (즉, 분산 오차를 보정 할 수있는 충분한 수치 적 평활화를 내장 각종 문제에 적용 할 수있을만큼 계산 안정성이있다) 근사 체계를 개발하는 것입니다.
What FLOW-3D Does
In FLOW-3D the default method is a first-order, upstream, advection technique that is extremely robust, but which introduces some numerical viscosity. If it is determined that this numerical viscosity is excessive, because sharp velocity profiles must be computed without the luxury of high grid resolution, then a second-order accurate, monotonicity preserving option can be employed with the flip of a switch.
For compressible flows, an implicitly coupled pressure-velocity solution option can be used in FLOW-3D to capture shock waves and minimize the appearance of post-shock oscillations.
FLOW-3D의 기본 기술은 매우 견고한 first-order, upstream, advection 이지만, 약간의 수치 점성을 포함합니다. 고해상도 격자를 사용할 수 없는 환경에서 뚜렷한 속도 프로파일을 계산할 수 없기 때문에 이 수치 점성이 너무 크다고 판단 된 경우, 간단한 조작으로 2 차 정확도의 단순성 유지 옵션을 선택 할 수 있습니다.
압축 흐름은 FLOW-3D의 implicitly 연성에 의한 압력 – 속도 해법 옵션을 사용하여 충격파를 포착하고 충격파 뒤에 출현하는 진동을 최소한으로 억제 할 수 있습니다.
In many simulations, fluid must flow out one or more boundaries of the computational region. But what constitutes a good boundary condition at such “outflow” boundaries?
경계 조건 – 유출
많은 시뮬레이션에서 유체는 계산 영역의 하나 이상의 경계에서 유출해야 합니다. 그러나 그러한 ‘유출’ 경계에서 좋은 경계 조건은 어떤 것이 있을까요?
In compressible flows, when the flow speed at the outflow boundary is supersonic, it makes little difference how the boundary conditions are specified since flow disturbances can’t propagate upstream. However, in low speed and incompressible flows disturbances introduced at an outflow boundary can affect the entire computational region.
압축성 흐름은 유출 경계에서 유속이 초음속일때 흐름의 교란이 상류로 전파 될 수 없기 때문에 경계 조건의 지정 방법에 따라 차이가 생기는 경우는 거의 없습니다. 그러나 느린 비압축성 흐름의 경우는 유출 경계에서 발생하는 동요는 계산 영역 전체에 영향을 미칠 수 있습니다.
Continuative Approximation
The simplest and most commonly used outflow condition is that of a “continuative” boundary. Continuative boundary conditions consist of zero normal derivatives at the boundary for all quantities. The zero-derivative condition is intended to represent a smooth continuation of the flow through the boundary.
연속 근사
가장 간단하고 가장 일반적으로 사용되는 유출 조건은 “연속”경계 조건입니다. 연속 경계 조건은 모든 유량의 경계에서 제로 법선 미분으로 구성되어 있습니다. 제로 미분 조건은 경계를 통과하고 매끄럽게 연속 흐름을 표현하는 것을 목적으로 하고 있습니다.
It must be stressed that the continuative boundary condition has no physical basis; it is a mathematical statement that may or may not provide the desired flow behavior. In particular, if flow enters the computational region across such a boundary, then the computations may be wrong because nothing has been specified about flow conditions existing outside the boundary.
여기에서 연속 경계 조건은 물리적 근거가 없는 것을 강조해야합니다. 이것은 수학적 이론이며 실제로 바람직한 흐름을 얻을 수 있을지 여부는 확실하지 않습니다. 특히 흐름이 이러한 경계를 통과하여 계산 영역에 들어갔을 경우 경계의 외부에 존재하는 흐름 조건에 관해서는 아무것도 지정되어 있지 않기 때문에 잘못된 계산이 될 수 있습니다.
Improved Continuative Approximation
FLOW-3D uses a special enhancement to continuative boundaries to improve their behavior. If flow attempts to enter the computational region across this type of boundary it must do so by starting from a condition of rest. This practice helps to reduce inflow and often results in a reasonable approximation of a smooth outflow condition. Nevertheless, a continuative boundary condition must always be viewed with suspicion.
연속 근사 개선
FLOW-3D는 특수 강화 방법을 사용하여 연속 경계의 거동을 개선하고 있습니다. 이 유형의 경계를 통과하여 계산 영역에 들어 가려고하는 흐름은 먼저 정지 조건에서 시작해야합니다. 이에 따라 유입이 감소하고 부드러운 유출의 조건을 합리적으로 근사 할 수있는 경우가 많습니다. 그럼에도 불구하고, 연속 경계 조건은 항상 의심의 눈으로 볼 필요가 있습니다.
Other Approximations
For limited classes of problems, better outflow boundary conditions do exist. For example, special boundary treatments have been devised for wave propagation problems that try to determine the speed and direction of waves approaching the boundary and then set boundary conditions so that they continue through the boundary with a minimum of reflection. A useful example of this type of treatment, sometimes called a radiation boundary condition, is described by I. Orlanski, Jour. Comp. Phys. 21, 251 (1976).
기타 근사
문제의 종류는 한정되지만 좀 더 나은 유출 경계 조건도 존재합니다. 예를 들어, 파동 전파 문제에 대해 특별한 경계 처리가 고안되어 있습니다. 이것은 경계에 접근하는 파도의 속도와 방향을 확인하고 최소한의 반사 경계를 통과하여 연속적이도록 경계 조건을 설정하려고하는 것입니다. 이 유형의 처리가 유익한 예는 방사 경계 조건이라는 것도 있지만, I. Orlanski 씨의 Jour. Comp. Phys. 21,251 (1976)에 설명되어 있습니다.
As a general rule, a physically meaningful boundary condition, such as a specified pressure condition, should be used at outflow boundaries whenever possible. When a continuative condition must be used it should be placed as far from the main flow region as is practical so that any adverse influence on the main flow will be minimal.
원칙적으로 유출 경계는 가능한 한 지정된 압력 조건과 같은 물리적으로 유의 한 경계 조건을 사용하십시오. 연속 조건을 사용할 필요가 있는 경우, 실용성이 손상되지 않을 정도로 흐름의 주요 영역에서 최대한 멀리 배치하고, 주류에 대한 악영향을 최소화 할 수 있도록 해야합니다.
Can you imagine a computational fluid dynamics program that simulates the behavior of different materials separated by well-defined interfaces that are subject to arbitrarily large deformations? Can you also imagine this program capturing shock waves and tracking rarefactions, slip surfaces, and other non-linear hydrodynamic phenomena?
라그랑주 입자
잘 정의된 인터페이스로 구분하여 수시로 큰 변형이 발생하는 다양한 물질의 거동을 시뮬레이션 하는 전산 유체 역학 프로그램을 상상할 수 있습니까? 또한 이 프로그램이 충격파 및 저밀도 추적, 미끄럼 표면 등의 비선형 유체 역학 현상을 추적하는 것을 상상할 수 있습니까?
Developing such a program would be a daunting task. You may be surprised to learn that such a program was operating in 1955, long before computer graphics or mechanical pen plotters were available, and even before high-level programming languages like Fortran were popular. Fortran, or Formula Translation System, was proposed by IBM in 1954. The program having these amazing capabilities was a Particle-In-Cell (PIC) method originated by Francis H. Harlow of the Los Alamos National Laboratory (Harlow, F.H., “A Machine Calculation Method for Hydrodynamic Problems,” Los Alamos Scientific Laboratory report LAMS-1956, Nov. 1955).
그런 프로그램의 개발은 벅찬 작업입니다. 이러한 프로그램이 1955 년에 가동하고 있었다고 하니 놀랄지도 모릅니다. 컴퓨터 그래픽이나 기계식 펜 플로터가 실용화되기 훨씬 이전의 일이며, Fortran과 같은 고수준 프로그래밍 언어조차도 아직 일반화되어 있지 않았던 무렵입니다. Fortran, 즉 Formula Translation System은 1954 년 IBM에 의해 제안되었습니다. 이러한 놀라운 기능을 가진 프로그램은 PIC (Particle-In-Cell) 법으로 로스 알 라모스 국립 연구소 (Los Alamos National Laboratory)의 Francis H. Harlow 씨에 의해 고안되었다 (FH Harlow “A Machine Calculation Method for Hydrodynamic Problems “Los Alamos Scientific Laboratory report LAMS-1956, Nov 1955).
Figure 1: PIC calculation of a 2 cm diameter iron sphere hitting an aluminum plate at a supersonic speed
Central to the PIC method is the concept of a Lagrangian particle defined by a location (x,y,z). A particle is said to be Lagrangian when it moves as though it is an element of fluid. The particle may be thought of as the location of the center of mass of the fluid element. In addition to a location, Lagrangian particles are sometimes assigned one or more property values. In the PIC method, for instance, particles have specified masses and a label indicating what material they belong to.
PIC는 메소드 중심부는, 위치 (x, y, z)에 의해 정의된 라그랑 입자의 개념입니다. 파티클은 유체의 요소인 것처럼 움직일 때 “라그랑” 이라고 합니다. 이 입자는 유체 요소의 질량 중심의 위치로 간주 할 수습니다. 위치 외에, 라그랑 입자는 종종 하나 이상의 속성 값을 할당합니다. PIC는 방법에서, 예를 들면, 입자는 특정 질량과 그들이 속한 어떤 소재를 나타내는 라벨을 지정하고 있습니다.
While the underlying computational scheme used in the PIC method employs a fixed Eulerian grid, Lagrangian particles are used to move mass, momentum, and energy through this grid in a way that preserves the identities of the different materials. There are no connections between particles so they are free to move and follow the dynamics of a flow regardless of its complexity, Figure 1. Lagrangian particles are, in fact, the key feature in the PIC method that allows it to track large fluid deformations.
PIC 법에서 사용되는 기본 계산 방식은 고정 오일러 격자를 채용하고 있습니다 만,이 격자를 통과하는 질량, 운동량, 에너지의 이동은 라그랑주 입자가 사용 된 다양한 물질의 독자성이 유지되고 있습니다. 입자 사이의 연결은 없기 때문에 입자는 자유롭게 움직이고 복잡한 여부에 관계없이 흐름의 역학을 따르십시오 (그림 1). 실제로 라그랑주 입자는 유체의 대폭적인 변형을 추적 할 수있는 PIC 법의 중요한 기능입니다.
Why, then, isn’t the PIC method more widely used for continuum fluid mechanics? For example, there are no commercial CFD programs based on this method. It could be argued that the PIC method is best for compressible flows, while most commercial applications deal with incompressible-fluid situations.
그런데도 왜 PIC 법은 연속 유체 역학에 더 널리 사용되지 않는 이유는 무엇입니까? 예를 들어,이 기술을 기반으로 하는 상용 CFD 프로그램은 없습니다. PIC 법은 압축성 흐름에 최적인 반면 대부분의 상용 응용 프로그램에서는 비압축성 유체의 상황을 취급하고 있다는 것을 말할 수 있을지도 모릅니다.
Two additional reasons why the PIC method is not more wisely used are associated with the discreteness of Lagrangian particles. It is these discrete properties and their consequences that are the subject of this note. One obvious property is that finite changes in numerical values may occur because of changes in the number of particles. The other property is less obvious and is associated with a fundamental characteristic of fluids that generally makes it difficult to track a fluid element simply by tracking its center of mass (a discrete) location.
PIC 법이 더 현명하게 사용되지 않은 이유가 그 밖에도 2 개가 더 있지만, 그들은 라그랑주 입자의 이산과 관련되어 있습니다. 이러한 이산화 특성 및 그 결과야말로 이 책의 주제입니다. 분명한 특성 중 하나는 입자의 수의 변화에 따라 숫자의 유한 변화가 발생할 수있는 것입니다. 또 하나의 특성은 그다지 명확하지 않고, 유체의 기본적인 특성과 관련되어 있습니다. 이 특성에 따라 질량 중심 (이산화) 위치를 추적하는 것만으로는 유체 요소를 추적하기가 어려워지는 것입니다.
The Discrete Problem
Figure 2: (a) Flow in jet hitting a wall, (b) initial particle distribution, (c) subsequent particle distribution showing vertical packing and horizontal spreading.
In the PIC method particles have finite masses. This means that when a particle moves from one control volume of the fixed Eulerian grid into another it causes discrete changes to be recorded in the mass, momentum, and energy of the cells losing and gaining the particle. Such changes introduce fluctuations in the computed values of all fluid dynamic quantities. The magnitude of the fluctuations is inversely proportional to the square root of the average number of particles in a grid cell.
이산화 문제
PIC 법에서 입자는 유한의 질량을 가지고 있습니다. 즉, 고정 오일러 격자 컨트롤 볼륨 사이를 입자가 이동할 때 입자가 감소하는 셀과 증가하는 셀의 질량, 운동량, 에너지 이산 변화가 기록된다는 것입니다. 이러한 변화로 인해 유체 역학의 모든 양의 계산 값에 변동이 발생합니다. 변화의 크기는 격자 셀의 평균 입자 수의 제곱근에 반비례합니다.
Experience has shown that the PIC method works best with at least 16 particles per cell (i.e., a 4 by 4 array in two dimensions or 64 particles per cell in three dimensions). A smaller number of particles could be used when larger fluctuations could be tolerated (or when computing resources did not allow for a larger number, a frequent situation in the early days of CFD).
경험에서 PIC 법은 셀 당 입자 수를 16 개 이상 (2 차원의 경우는 4 × 4 배열, 3 차원의 경우 셀 당 64 개의 입자) 인 경우에 최적으로 작동하는 것으로 알려져 있습니다. 더 큰 변동을 허용 할 경우 (또는 CFD의 초기에 많았던 상황으로 컴퓨팅 자원의 문제로 인해 큰 수치를 사용할 수 없는 경우)는 사용하는 입자 수는 더 적게해도 괜찮습니다.
Experience also showed that better results were obtained when the initial placement of particles was not regular, but staggered. It is easy to see why this is so. Suppose the particles are arranged in a regular 4 x 4 array in x-y space. If the flow is only in the x direction then a column of four particles will pass from one cell to another at the same time, which would result in a very large change in the cell values. If the particles are staggered in space, however, it is more likely that only one particle at a time will cross a cell boundary, causing the minimum discrete change in cell values.
입자의 초기 위치가 일정하지 않고 불규칙하면 좋은 결과를 얻을 수도 있으며, 경험을 통해 알고 있습니다. 그 이유는 쉽게 확인할 수 있습니다. 입자가 일정한 4 × 4 배열에서 xy 공간에 나란히 있다고가정합니다. 흐름이 x 방향 만의 경우 4 개의 입자로 이루어진 열이 셀에서 셀에 동시에 이동하는 셀의 값이 크게 변화하는 결과가 됩니다. 그러나 공간에 입자가 불규칙하게 배치되어 있는 경우는 셀의 경계를 통과하는 입자는 1 회에 1 개만이 될 가능성이 높기 때문에 셀의 값의 이산 변화는 최소화됩니다 .
In more recent times another approach has been used to reduce the effect of discrete changes as particles move from cell to cell. This is the “smooth particle hydrodynamics” method in which particles have finite volumes that can overlap more than one grid cell at a time. As a particle approaches a cell boundary its volume continuously sweeps from one cell to the next.
최근 들어 입자가 셀에서 셀로 이동할 때 이산 변화의 영향을 완화하기 위해 다른 방법이 사용되어 왔습니다. 이것은 “부드러운 입자 유체 역학”법이며, 입자는 동시에 여러 개의 격자 셀과 겹칠 수 있는 유한 체적을가집니다. 입자가 셀 경계에 접근하면 그 부피는 원래의 셀에서 옆의 셀에 연속 스윕합니다.
The Element Distortion Problem
Figure 3: Same plots as in Fig.2 B-C except the initial particle distribution is staggered.
A more difficult problem associated with Lagrangian particles is that fluid elements rarely retain simple, convex shapes. Most often a fluid element will find itself subjected to shearing, expanding, or contracting flow processes that quickly draw it out into a long ribbon-like shape. To visualize this, you might try introducing small volumes of smoke into a strong light (e.g., from a slide projector) and see how rapidly they deform into thin curtains of smoke.
요소의 왜곡 문제
라그랑주 입자에 관련된 더 어려운 문제는 유체 요소가 간단한 볼록 형상을 유지하는 경우가 거의 없다는 것입니다. 종종 유체 요소는 전단, 팽창, 수축 등 유동 과정을 받고, 긴 리본 모양의 형상으로 늘어납니다. 이를 시각화하려면 소량의 연기에 강한 빛 (슬라이드 프로젝터 등)을 조사하여 연기가 얇은 커튼 모양으로 변형되는 속도를 확인하는 등의 방법이 있습니다.
This type of deformation means that material in a fluid element will not remain localized, and a Lagrangian particle following its center of mass will no longer be a good representation of the element. In a computational method element distortion can lead to a variety of problems. One of the most common problems is that particles will not retain a uniform distribution, but will tend to bunch up in some places and move apart in others.
이 유형의 변형은 유체 요소의 물질이 국소화된 상태로는되지 않고, 질량의 중심에 따라 라그랑주 입자는 요소를 충분히 표현할 수 없게 되는 것을 의미합니다. 계산법은 요소의 왜곡이 다양한 문제를 초래할 수 있습니다. 가장 일반적인 문제 중 하나는 입자가 균일 한 분포를 유지하는 것이 아니라 위치에 따라 1 개소에 정리하거나 흩어 지거나하는 경향이 있다는 것입니다.
A simple example of these processes occurs at stagnation point. Figure 2 shows what happens to a regular array of particles in a liquid jet when it strikes a wall and flows to either side of a stagnation point that is at the center of impact. The particles bunch together in a direction normal to the wall while at the same time move further apart along the wall.
이러한 과정의 간단한 예는 정체 지점에서 발생합니다. 그림 2는 액체 제트가 벽에 충돌, 충격의 중심에 있는 정체 점의 양쪽에 흐를 때, 규칙적인 입자 배열에 무슨 일이 일어나는지를 보여줍니다. 입자가 벽에 수직 방향으로 정렬하여 동시에 벽을 따라 바깥쪽으로 멀리 갈 수 있도록 이동합니다.
If the particles in the initial distribution are staggered these deformation processes are greatly reduced. See Figure 3. Unfortunately, staggering cannot completely eliminate this problem. In other circumstances, at a separation point or in regions of strong shear, particle staggering is not sufficient to keep particles evenly distributed.
초기 분포의 입자가 불규칙한 경우, 이러한 변형 과정은 크게 감소합니다. 그림 3을 참조하십시오. 공교롭게도 불규칙한 분포에서는이 문제를 완전히 배제 할 수 없습니다. 박리 점과 전단력이 강한 영역과 같은 다른 상황에서 입자를 불규칙해도 입자의 균일 한 분포를 유지하기에 충분하지 않습니다.
Numerical techniques can be used to add particles in expanding regions or eliminate them in regions of convergence. Or continuous repartitioning methods can be used to relocate particles for more even coverage. However, these operations introduce local smoothing that is effectively equivalent to an Eulerian computational method and throws away one of the best features of particles, namely that of their identity.
팽창 영역에 입자를 추가하거나 컨버전스 영역에서 입자를 제거하는 데에 많은 기술을 사용할 수 있습니다. 또한 continuous repartitioning methods을 사용하여보다 균일하게 입자를 재배치 할 수 있습니다. 그러나 이러한 작업은 오일러 계산법과 사실상 동등하게 국소적으로 부드럽게 해 입자의 가장 뛰어난 특징 중 하나 인 독자성이 없어집니다.
Other Considerations
Flow separation regions cause difficulties not only because of the difficulty of maintaining a uniform particle distribution but also because of the curvature of the flow near a separation point.
기타주의 사항
흐름의 분리 영역이 문제의 원인이 되는 이유는 입자의 균일 한 분포를 유지하기 어려울뿐만 아니라 박리 점 근처의 흐름 곡선이 있는 것입니다.
To understand why flow curvature can be a problem, consider the rigid-body rotation of a fluid. Lagrangian particles placed in such a flow should move in circles about the axis of rotation. In practice this rarely happens because most particle implementations advance the location of a particle using a linear expression of velocity. For instance, the x-location of a particle at time-step n+1 would be computed as xn+1=xn+dtU, where dt is the time-step size and U is the x-component of the flow velocity at the location of the particle.
흐름의 곡선이 왜 문제가 되는지를 이해하기 위해 유체의 강체 회전에 대해 생각합니다. 이러한 흐름 속에 배치된 라그랑주 입자는 회전축을 중심으로 원형을 그리며 움직입니다. 사실, 이런 일은 거의 일어나지 않습니다. 입자를 도입 할 때 종종 속도의 1 차식을 사용하여 입자의 위치를 전진시키기 때문입니다. 예를 들어, 시간 단계 n + 1의 입자의 x 위치는 xn + 1 = xn + dtU 계산됩니다. 여기서 dt는 시간 단계 크기, U는 입자의 위치에서의 흐름 속도의 x 성분입니다.
This expression, which is linear in the velocity, moves the particle in a direction tangent to the circle. Consequently, when the particle is moved along the tangent it moves to a slightly larger radius. After a sufficient number of time steps, particles will appear as though they are being thrown outward, a kind of numerical centrifugal effect.
이 수식은 속도의 1 차식이며, 원형의 접선 방향으로 입자를 이동합니다. 그 결과, 입자는 접선을 따라 이동 된 때 약간 큰 반경으로 이동합니다. 충분한 시간 단계 후, 입자는 외부에 던져진 것처럼 보입니다. 이것은 수치적 원심 효과의 일종입니다.
The only way to correct for this type of behavior is to sense when the flow has curvature and to use a second-order, quadratic expression to compute new particle positions.
이 유형의 행동의 유일한 해결 방법은 흐름 곡선이 있을 때 감지하여 2 차 식을 사용하여 입자의 새로운 위치를 계산하는 것입니다.
Diffusion processes are easy to include in particle methods using a type of random walk, or Monte Carlo model. One technique is to imagine a particle to be a point source for material that is diffusing outward. For a short time, dt, the diffusion can be represented as having a Gaussian distribution (i.e., having the solution to the diffusion equation for a point source). Since the particle cannot be subdivided, the distribution is instead treated as a probability distribution. The particle is then moved in the time interval dt to its most probable location. A random number generator is used to select a location in this probability distribution. The idea is that if enough trials are made the number of times the particle reaches a given position is proportional to the Gaussian distribution.
확산 과정은 랜덤 워크의 일종인 몬테카를로 모델을 사용하여 입자법에 쉽게 포함 할 수 있습니다. 하나의 방법은 입자가 바깥쪽으로 확산하는 물질의 점 원인이라고 가정하는 것입니다. 짧은 시간 (dt) 확산 가우스 분포를 가지고있음 (포인트 소스의 확산 방정식의 해를 가지고)으로 표시 할 수 있습니다. 입자를 세분화 할 수 없기 때문에 이 분포 대신에 확률 분포로 처리됩니다. 그 후, 입자는 dt는 시간 간격으로 가장 확률이 높은 위치로 이동됩니다. 이 확률 분포는 난수 생성기를 사용하여 위치가 선택됩니다. 이것은 충분한 시도를 실시하면, 입자가 주어진 위치 도달 횟수는 가우스 분포에 비례한다는 생각입니다.
Figure 4: Calculation of collapsing cylindrical column of water (a) splashing over a circular dyke (b). Particle finger looks especially realistic, but particles were not used in computation.
When particles are used as flow markers they make particularly nice graphic displays. A good example can be found in the Marker-and-Cell (MAC) method for free surface hydrodynamics (Harlow, F.H., Shannon, J.P., and Welch, J.E., “Liquid Waves by Computer,” Science 149, 1092 (1965)). In this method Lagrangian particles do not carry mass but are simply used as markers to define grid regions occupied by fluid. Results produced by the MAC method have appeared in many publications to illustrate the impressive things that can be done with computational fluid dynamics.
입자 흐름 마커로서 사용하면 특히 뛰어난 그래픽으로 표시됩니다. 자유 표면 유체 역학의 MAC (Marker-and-Cell) 법은, 좋은 예입니다 (FH Harlow, JP Shannon 및 JE Welch “Liquid Waves by Computer”Science 149,1092 (1965)). 이 방법은 라그랑주 입자는 질량 없이 단순히 유체로 채워져 있는 격자 영역을 정의하는 마커로 사용됩니다. MAC 법에서 얻어진 결과는 많은 출판물에 등장하고 전산 유체 역학에서 실현할 수있는 좋은 것을 설명하기 위해 사용되어 왔습니다.
Figure 4 shows a MAC-like computation of the flow of liquid originating from the collapse of a circular column (shown in outline to the left) and splashing over a cylindrical dyke. The small finger of marker particles at the top of the splash appears especially realistic. As it happens, this computation was performed using a Volume-of-Fluid (VOF) method in which Lagrangian particles had no computational role. The particles in the picture were only included in the computation to make the graphical display.
그림 4는 실린더 (왼쪽 가장자리 부분)이 무너지는 것으로부터 시작하여 원통형의 볼록한 부분에 있어서는 물보라를 올리는 액체의 흐름을 MAC과 같이 계산 한 경우를 보여줍니다. 비말 상단의 마커 입자의 작은 손가락 모양의 부분이 특히 리얼하게 보입니다. 우연히 이 계산은 VOF (Volume-of-Fluid) 법을 사용하여 수행됩니다. 라그랑주 입자는 계산상 역할은하지 않았습니다. 그림 속의 입자는 그래픽 표시 목적으로만 계산에 포함되었습니다.
This example shows that what seems to be a strong argument for the accuracy of discrete particles, that is, their ability to capture local details, is mostly a visual effect in this case since the dynamics was computed from purely cell-averaged quantities.
이 예는 이산화 된 입자가 정확한지 강력한 근거라고 생각되는 것, 즉 국소적인 내용을 파악하는 능력이 사건은 주로 시각 효과임을 보여줍니다. 이것은 순수한 셀 평균 금액에서 역학 계산 된 것입니다.
Lagrangian particles are an extremely useful computational tool, especially when they are used to track small amounts of material whose dispersion is to be minimized. When particles are used as a discrete model for a continuous medium, however, it must be remembered that they have some limitations. In this sense, particles are no different than any other discrete computational method. Some of the issues that should be considered when using Lagrangian particles have been, we hope, discreetly presented in this note.
라그랑주 입자는 특히 분산을 최소화해야 합니다. 소량의 물질을 추적 할 때 매우 유용한 계산 도구입니다. 그러나 연속 매체의 이산 모델로 입자를 사용하는 경우 몇 가지 제한 사항이 있음을 기억해야합니다. 이러한 의미에서, 입자는 다른 이산 계산법과 아무런 차이가 없습니다. 라그랑주 입자를 사용할 때 주의가 필요한 문제의 일부를이 책에서 조금이라도 보여줄 수 있으면 다행입니다.