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Assessment of liquid and gas impingement cooling fluids with numerical solution for better steel austempering
Journal of Engineering and Applied Science volume 69, Article number: 88 (2022)
Abstract
Impingement jet heat transfer was studied using liquid and gas fluids to determine better cooling fluid. The materials used were rectangular steel plates of 230 mm by 120 mm by 12 mm, single jet diameters of 10–40 mm with impingement gaps of 115–155 mm. A computational fluid dynamics software application ANSYS 2020R1 was employed for simulation, and lumped thermal mass analysis was used for experimental modeling. The experimental results showed an increase in heat transfer coefficient with increased pipe diameters and with a corresponding increase in impingement gaps and flow rate. This revealed 265.4–383.9 W/m^{2} K and 85.3–109 W/m^{2} K at diameter 10 mm and 336.5–365 W/m^{2} K and 109.0–137.5 W/m^{2} K at diameter 40 mm for both water and air, respectively. Numerical simulation revealed heat flux of 22518–38.94 W/m^{2} and 7570.2–4.25 W/m^{2} and 6742.8–27.1 W/m^{2} and 4155.6–6.1 W/m at diameters 10 mm and 40 mm, respectively. This confirmed that water remains a better cooling fluid with a 6.2% difference at the diameter of 10 mm and a 0.1% difference at the diameter of 40 mm. An acceptable error margin of 4 to 18% upon the comparison of empirical analysis with numerical simulation is obtained. The above suggests a better cooling rate for the microstructure of the steel using water against air.
Introduction
The jet impingement cooling process is a heat removal process that enables the removal of heat from a hot surface faster. Over the years, with the continual enhancement of steel material functions, the growing demand for cost cutting by reducing the use of alloying elements, and streamlining processes: the thermomechanical control process (TMCP), has become increasingly important [1, 2]. At one point of the designer’s desired need, steel materials are subject to either of the following: bending and at the other to twisting, rotations, etc. Attending operations under these conditions requires certain specific properties to be able to successfully withstand the various conditions the designers subject them to [3]. Heat treatment, heating, and soaking at cooling temperature cycles steel are reduced, help before now to handle as much as possible, yet in recent times could not do more [4, 5]. Opined that by restructuring its microstructure and physical structure with proper monitoring and controlling of its temperature during heating and cooling processes. Its usage with the evolving engineering and technology advancement is due to the designer’s quest for newer applications, which causes the manipulation of steel’s mechanical and metallurgical properties to the designer’s desired design application. Therefore, there is a need for improving steel properties, which demand cost reduction in alloying elements, modeling, and streamlining processes, hence need for a better process [1]. In particular, the hotrolling process, which is a wellknown manufacturing method of steel strips, requires great management since it has a crucial influence on the properties of the final product [2].
Meanwhile, the modes of cooling by quenching process using different fluids opened it up for improvement. The era of controlled cooling opens up, an important part of thermomechanical controlled process (TMCP) technology, which significantly influences the microstructure and mechanical property of hotrolled steel plates [6, 7]. As one of the important elements of this technology, the technique that allows the precise control of the fluid quenching temperature can be cited along with the metallurgical and controlled rolling techniques [1]. Therefore, jet impingement cooling, a type of accelerated controlled cooling, is a process used to achieve high heat removal yield from a heated material using the desired coolant for easy cooling. Steel production having desired mechanical and metallurgical properties requires accurate temperature control during the cooling process as noted by [8]. This work looks for a solution to the Leidenfrost phenomenon in water from another fluid.
Steel as an engineering material
Agreeing to the Society of Automobile Engineers and the American Institute of Steel, iron and steel are alloys of iron and carbon that normally have less than 1.0wt% of carbon [9]. It may contain other alloying elements at different compositions and/or heat treatment [10,11,12]. In this present work, we recognized three main grades of steel: low, medium, and high carbon steel with carbon content ranges of 0.015–0.30%wt for low carbon steel, 0.031–0.58%wt for medium carbon steel, and 0.6–2%wt for high carbon steel [13].
Hydrodynamics of jet impingement
Jet from the ROT cooling stage first exits the circular nozzle and impinges over the dry heated plate surface (freesurface jet), followed next by arrays that collide with the leftover fluid on the surface (plunging jet). These two types are mostly treated as freesurface jets in comparison with the submerged jet. Accordingly, [14] showed some types of single jet impingement cooling. This work uses a freesurface jet impingement cooling profile as shown in Fig. 1 below.
The flow of the liquid in impingement process can be divided arbitrarily into two zones, the impingement zone characterized by a sharp increase in the streamwise velocity and a parallel flow zone with a more gradual change of streamwise. Figure 1 depicts the streamwise velocity (u_{i}). In hydrodynamics, the streamwise at the stagnation point increase to the jet streamwise velocity V_{ji}. The hydrodynamics of circular jets differ from others in the parallel flow region. This is because the water velocity in the parallel flow zone of circular jets decreases, whereas the water velocity for the planar jet does not decrease [16].
Computational fluid dynamics
Numerical solution based on computational fluid dynamics (CFD) is the analysis of systems involving fluid flow, heat transfer, and associated phenomena such as chemical reactions using computerbased simulation; this technique is very powerful and spans a wide range of industrial and nonindustrial application areas [17]. CFD is an effective and powerful tool to numerically simulate fluid flow and heat transfer. The conventional methods which are the most popular in CFD are the finite element method (FEM), finite volume method (FVM), finite difference method (FDM), and spectral methods. These methods solve nonlinear NavierStokes equations which are governing equations for CFD describing popular conservation of mass, momentum, and energy equations [18]. The baseline results from CFD analysis are compared with experimental analysis, using ANSYS FLUENT and many other fluid flow software as studied by [2, 9, 19].
Many numerical models have been studied like SST kw model while v^{2}f turbulence model for turbulence analysis because of its minimal error at the stagnation point and wall regions. Numerically, revealing that the ratio of the nozzle diameter to cylinder diameter affects Reynolds number value also showed that the RNG ke model is better in predicting heat transfer characteristics. We found also that inlet turbulent intensity and eddy viscosity ratio are vital for the accurate prediction of realistic results using various RANS turbulence models; all these models are for fluid flow characteristics onto the hot surface as studied by [20,21,22,23]. Nur et al. [24] studied hybrid nanofluid using single jet impingement cooling, and they showed that its heat transfer performance is highest and reduces the greatest amount of heat from the surface to the fluid. The models reviewed above are for the fluid and heated surface interaction. This work presents the knowledge in the behavior of the hot steel plate heat dissipation only. This has been uncertain in the literature for the single jet impingement cooling process. In the literature, it has been empirical analysis with minimal or no validation. Hence, this work assessed the behavior of controlled cooling of a hotrolled steel plate using liquid and gas single jet impingement cooling by the transient thermal model of ANSYS fluent 2020R1.
Methods
The schematic of the modified runout table system setup plant is used and hoses the combined liquid and gas lines in the same headers. The location of these parts is shown on the schematic diagram in Fig. 2.
Experimental procedure
Based on impingement diameters, D = 10 mm and 40 mm with corresponding varying impingement gaps H, of 115 and 155 mm at two different controlled cooling temperatures of 150 °C and 110 °C, respectively. The experiments carried out were with a modified test rig, in Fig. 2. The assessment and numerical simulations were done using lumped thermal mass analysis, used to generate various values of heat transfer coefficient (h), and ANSYS was employed for simulation and 3D modeling of the transient thermal model of the steel plate — 230 mm length by 120 mm width by 12 mm thickness, for temperature time and heat flux. The following test parameters based on Fig. 2 were used as experimental indicators: flow rate, nozzle velocity, constant impingement diameters, varying impingement gaps, surface temperatures, and controlled temperatures, cooling time, and rate.
The air jet impingement experiment was done using the same rig that has an air attachment nozzle at the flow valve close to the headers, with an air compressor machine producing and supplying the air. Table 1 shows the properties of the sampled impingement fluids — liquid and gas (water and air).
Medium carbon steel plates with known varying chemical compositions and mechanical properties were obtained from the Ajaokuta Nigerian Steel Company with a steel grade of 0.56%C, the ultimate tensile strength of 957.1 Mpa, and Brinell hardness of 252.98 having an impact strength of 34.11 J.
Data analysis
This model of the impingement process is centered on the demonstration of transientstate heat conductionconvection across the sampled workpiece thickness of 12 mm, length of 230 mm, and width of 120 mm dimensions (Fig. 3).
Integration from t = 0 to T = T_{s}:
where α becomes the following:
The gradient is Eq. 4 given as in Eq. 5, as follows:
where h is heat transfer coefficient W/m^{2} k
\(for\ steel, density\kern0.5em \rho =\frac{7900 hg}{m^3},\kern0.5em specific\ heat\ Cp=\frac{500J}{kgk}, sampled\ thickness\ w=0.012m\), and ∝ is a gradient from Eq. (5)
Thereafter, a spread Excel sheet was used to estimate h Eq. (6), where h =∝ρwc, for ∝ being the slope based on lumped numerical experimental temperaturetime plots. These values of convective heat transfer coefficient h were calculated.
Numerical simulation model
The simulation model is as shown in Fig. 4a which represents the hot steel plate 230 × 120 × 12 mm dimensions. The inlet nozzle diameters are 10 and 40 mm, while the impingement gaps are 115 and 155 mm. The mesh structure used in the study is in Fig. 4b. This study demonstrated a simple threedimensional geometry simulation. The type of fluids used in the simulation is liquid and gas coolant with ANSYS transient thermal model for simulation.
Grid independence
To determine the ideal number of grids used and the impact of the number of elements on heat transfer and the final temperature of the target surface, the mesh was analyzed. A coarse mesh with 552 number of elements and 0.02 m cell size employed in this study. Figure 5 shows the result of the grid independence test; additionally, patch conforming method and inflation method are applied to the geometry to ensure the flow of fluid near the target surface is well defined.
Boundary conditions
The boundary condition for the inlet velocity is determined based on the calculated Reynolds number. The inlet temperature and the surface temperature of the plate are set at 323 and in the range of 683 to 723 k for diameters of 10 mm and 40 mm, respectively. The temperature is set according to the working temperature of a microchip cooling system, which utilizes the fluid jet impingement cooling method of Nur et al. [24].
The final subcooled temperature was predetermined by the design in the range of 150 to 110 °C, and the heat transfer coefficient was calculated using LTMA and was inputted to ANSYS; thus, the wall heat flux was determined by the postprocessing stage.
The Reynolds number used as the input parameter is in the range of 5000 to 250,000. The pressure treatment adopted the firstorder upwind scheme for the turbulence numeric and the adventive scheme. While for the viscous model, a standard kepsilon model was selected. The simulation was defined as converged at an RMS value lower than 1.0E−4. The results of the simulation are calculated throughout the computational domain during the simulation process.
Results and discussion
Experimental temperaturetime evaluation
For controlled cooled temperature of 150 °C, diameter D = 10 mm. Results are presented in Tables 2 and 3, used for generating Fig. 6 and Tables 4 and 5 for Fig. 7 at D = 40 mm and controlled cooling temperature of 110 °C that corresponds to WJIC and AJIC, respectively.
From all the graphs above, irrespective of the controlled cooled temperatures, the initial surface temperatures of hotrolled steel plates showed the highest cooling time at a gap of 115 mm and lowest at a gap of 155 mm in each of the constant impingement diameters. This agrees with Onah, and Farial [25, 26] showing the same linear decrease.
Evaluated heat transfer coefficients (h) from LTMA
The results of the experiment for temperature time were then further analyzed by lumped thermal mass analysis which showed a linear decrease from various surface temperatures to various cooling times of the form y = − ∝ x + a for R^{2} = b, where ∝ is the slope used for estimation of various convective heat transfer coefficient h from Eq. (5).
Ln (theta) for diameter D = 10 mm controlled at temperature of 150 °C is presented in Tables 6, for WJIC and AJIC used to generate Fig. 8, while Table 7 for WJIC and AJIC at diameter 40 mm is for Fig. 9 at different impingement gaps of 115 and 155 mm, respectively.
However, in all the controlled temperatures, the values of the slope of lumped thermal mass analysis∝, in ln(theta) temperature against time for determining convective heat transfer coefficient (h), indicated a linear increase in impingement diameter D and a corresponding increase in impingement gap H. This is suggestive that the various values of convective heat transfer coefficient (h) as obtained would be more at higher diameter D and higher impingement gap H, for proficient steel cooling, as studied by [27,28,29].
Heat transfer coefficient h from LTMA
Results of heat transfer coefficient (h) for D = 10 mm are presented in Table 8.
At constant diameter D = 10 mm, the convective heat transfer coefficient “h” showed an increase with increasing impingement gaps. Water has the highest values at both diameters and gaps. Flow rate decreased with increasing impingement gaps. The water decreased from 1.625 × 10^{−3} m^{3}/s to 4.9 × 10^{−4} m^{3}/s, and air decreased from 3.67 × 10^{−3} m^{3}/s to 4.43 × 10^{−4} m^{3}/s. This inferred that the lower the impingement gap H, the higher the flow rate Q.
For constant diameter D = 40 mm, convective heat transfer coefficient “h” maintained the same pattern, with water still having the highest.
This infers that at any given constant pipe diameter (D), flow rate (Q) decreases with a corresponding increase in impingement gap (H), resulting in increased convective heat transfer coefficient (h). This will give a proficient higher heat extraction rate on hotrolled steel plates cooling in the steel mill industry and achieve designer desired microstructures of steel, as also studied by [27,28,29].
Study of numerical simulation results
Figures 10 and 11 describe the CFD temperaturetime controlled cooling model — region 1, is blue and totally cooled layer; region 2, is yellow, the middle layer, and partially cooled; and region 3, is red bottomed layer, gradually cooled, but still hotter than the two layers, Also, it indicates the temperaturetime plot of the model, at each of the regions. The steeper curve region 1 showed where the convective heat transfer coefficient h was applied and slowly goes down to region 2 and to region 3, where heat flow was perfectly insulated that retained some hotness in the steel plate. Figures 12 and 13 represent the CFDcontrolled heat flux model, where the top region showed the highest heat flux down to the bottom the lowest. Again, it also showed a plot of the heat flux against time. The rate of heat flux dissipation was 2.2 × 10^{−6} W/m^{2}/s and 1.74 × 10^{−7} W/m^{2}/s maximum for WJIC and AJIC, respectively.
Figures 14 and 15 describe the CFD temperaturetime controlled cooling model, showing the same pattern as D = 10 mm, and CFD temperaturetime plot, at each of the regions, having the same shape as the plot of D = 10 mm. Figures 16 and 17 represent the controlled heat flux model. It showed the same pattern of cooling as above, as well as showing a plot of the heat flux against time. The rate of heat flux dissipation was 1.10 × 10^{−7}W/m^{2}/s and 1.33 × 10^{−7}W/m^{2}/s maximum for WJIC and AJIC, respectively, which suggested water as a better impingement fluid as opined by [8, 26]. This dissipation of heat flux showed that water removes heat per unit area per second better than air in both diameters.
Table 9 showed the heat fluxes at D = 10 mm and 40 mm, highest at the top where the convective heat transfer coefficient value is more. Heat flux showed a 66.4% difference for D = 10 mm and 75.2 for D = 40 mm for WJIC and AJIC, respectively. Furthermore, heat fluxes decreased linearly from top to bottom, showing an increase in convective heat transfer coefficient with corresponding increasing impingement gap H.
Experimental and CFD numerical simulation temperaturetime profile validation
Experimental and simulated data of both diameters are presented in Table 10 at convective heat transfer coefficient of h for water and h for air.
Table 10 showed the controlled temperature of 150 °C and 110 °C and initial temperature T = 450 °C and 410 °C for varied time t(s) for both experimental data and the ANSYS CFD simulation data plotted in Fig. 18 for both diameters. An acceptable error margin is of 4.5–6.6%. Confirming the affirmation, that water is a better fluid as specified by Md Lokman and Onah [25, 30].
Experimental uncertainties concomitant
The concomitant uncertainties in this work are the vital influences or limitations that are very expedient in the attainment of the set goal in this work, which is very grim to regulate. Thus, the plus or minus estimation uncertainties are ways of checkmating the errors in the measurement of these influences. These influences are underscored in Table 11.
Uncertainties for random measurement
Random uncertainties with absolute temperature values are as follows: for D = 10 mm, H = 115 mm at 150 °C, and for water T = (450 + 440 + 430 + 420 + 410)/5 = 430 °C. Meanwhile, the spread of temperature measurement ΔT is 0.9 °C; thus, T = 430 ± 0.9 °C. Conversely, pressure random uncertainties were determined as follows: for D = 10 mm, H = 115 mm at 150 °C is (2.5 × 105 + 2.5 × 105 +2.5 × 105 + 2.5 × 105 + 2.5 × 105)/5 = 2.5 × 105 N/m^{2}, and equally the spread of pressure measurement ΔP is 0.1 × 105 N/m^{2}; thus, P = 2.5 × 105 ± 0.1 × 105 N/m^{2}.
Uncertainties for random measurement
The water flow meter used has a specification of an accuracy: ± 1% of reading uncertainty tolerance; in addition, the water pump used has a current of 2.5 amp and a capacity of 0.5 hp. The pressure gauge calibrated was in the range of 0 to 10 bars with a measurement uncertainty tolerance of ± 0.1. In the testing and installation of the thermocouple, it recorded 97 °C with an error of ± 0.26 °C. The volumetric measuring cylinder calibrated was in the range of 50 to 500 mm^{3} with ± 0.1 mm^{3} uncertainty error. Similarly, the stopwatch calibrated was in the range of 0 to 60 s and at the top end with an accuracy uncertainty of ± 0.1.
Uncertainties for reduction measurement
For temperature, the uncertainty is for D = 10 mm, H = 115 mm at150 °C for water, and T = 430 °C, since the uncertainty in measure ΔT is 0.9 °C; thus, T = 430 ± 0.9 °C, and then, reduction temperature uncertainty is (0.9/430) × 100 = 21%. In the pressure reduction uncertainty, D = 10 mm, H = 115 mm at150 °C, and P = (2.5 × 105 N/m^{2}). The associated uncertainty measurement ΔP is 0.1 × 105 N/m^{2}; thus, P = (2.5 × 105 ± 0.1 × 105 N/m^{2}), and then, reduction pressure uncertainty is (0.1 × 105/2.5 × 105) × 100 = 40%.
Conclusions
This study involved a comparative study of jet impingement fluids. Empirical results using lumped thermal mass analysis revealed convective heat transfer of 265–365 W/m^{2} K and 85–138 W/m^{2} K for WJIC and AJIC, respectively at diameters of 10 mm and 40 mm. CFD numerical simulation revealed maximum heat fluxes of 22518 W/m^{2} and 6742.8 W/m^{2} for water and 7570.2 W/m^{2} and 4155.6 W/m^{2} for air at 10 mm and 40 mm, respectively. This confirmed water as the best impingement cooling fluid with a 6.2% difference at a diameter of 10 mm and a 0.1% difference at a diameter of 40 mm. validation of empirical results with numerical simulation results showed an acceptable error margin of 4 to 18% for diameters 10 mm and 40 mm, respectively. Certainly, with Kandilkar [31] study, this further confirms results in the literature that water will give a proficient higher heat extraction rate on hotrolled steel plates in the steel mill industry.
Availability of data and materials
The datasets supporting the conclusions of this article are included in the article.
Abbreviations
 AJIC:

Air jet impingement cooling
 ANSYS:

Analytical system
 A:

Area (m^{2})
 CFD:

Computational fluid dynamics
 Cp:

Specific heat capacity (J/kg k)
 D:

Diameter (mm)
 ESUT:

Enugu State University of Science and Technology
 h:

Heat transfer coefficient (w/m^{2} k)
 H:

Impingement gap (mm)
 FEM:

Finite element method
 FVM:

Finite volume method
 FDM:

Finite difference method
 LTMA:

Lumped thermal mass analysis
 M:

Mass (kg)
 MME:

Metallurgical and material engineering
 PVC:

Polyvinyl chloride
 P:

Pressure (N/m^{2})
 Q:

Flow rate (m^{3}/s)
 ROT:

Runout table
 RMS:

Root mean square
 T:

Initial temperature (°C)
 T_{sub} :

Subcooled temperature (°C)
 T∞:

Infinite temperature (°C)
 TMCP:

Thermomechanical cooling process
 t:

Time (s)
 u_{i} :

Streamwise velocity (m/s)
 v_{ij} :

Streamwise jet velocity (m/s)
 WJIC:

Water jet impingement cooling
 w:

Thickness (m)
 ΔT:

Change in temperature (°C)
 ΔP:

Change in pressure (N/m^{2})
 Ρ:

Density (kg/m^{3})
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AN wrote up the manuscript. TO and AN conducted the laboratory experiments. BN supervised the laboratory experiment and structured, edited, read, and approved the final manuscript. The authors read and approved the final manuscript.
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AN is currently a lecturer, at the Department of Mechanical Engineering Caritas, Enugu. TO is a lecturer, Department of Mechanical and Production Engineering, Enugu State University of Science and Technology, Enugu state. BN is currently a Professor of Mechanical Engineering, at Michael Okpara University of Agriculture Umudike, Abia state.
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Nwankwo, A.M., Onah, T.O. & Nwankwojike, B.N. Assessment of liquid and gas impingement cooling fluids with numerical solution for better steel austempering. J. Eng. Appl. Sci. 69, 88 (2022). https://doi.org/10.1186/s44147022001398
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DOI: https://doi.org/10.1186/s44147022001398
Keywords
 Single jet impingement
 Lumped thermal mass
 Liquid and gas
 Numerical simulation
 Impingement cooling fluid