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Assessment of heat transfer in a triangular duct with different configurations of ribs using computational fluid dynamics

  • Mohammed Hadi Hameed EMAIL logo and Hafidh Hassan Mohammed
Published/Copyright: February 5, 2024
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Open Engineering
From the journal Open Engineering Volume 14 Issue 1

Abstract

Numerical investigation was performed to improve heat transfer in triangular ducts using ribs of different sizes and shapes. Increased heat transfer may be achieved by the roughness in the duct surface, which is a prospective and successful method. It is shown that the sectional shape of the roughness given on the area exposed to heat has a major impact on the effective performance of heat transfer channels. This research will study the results of using different shapes and sizes of roughness components, such as triangular rib (e/W = 0.1, 0.2, and 0.3) as well as semi-circular rib (R/W = 0.1, 0.2, and 0.3). Likewise, the influence of rib width b (b/w = 0.2, 0.4, and 0.6) is examined using computational fluid dynamics for variable Reynolds number (1,000 < Re < 1,800) at fix rib height (e/W, R/W = 0.1). ANSYS FLUENT 2020 R1 is used to model the heat and the flow dynamics in roughened ducts. The best performance was for the semi-circular ribs. At a Reynolds number of 1,200, the optimum ratio of enhancement (ε) for the semi-circular rib sample e = 0.2 × W was 1.717. Additionally, sample 4 has the greatest Nusselt number across all Reynolds numbers and is the best-shaped sample. Furthermore, the pressure drop and the friction factor also increase when the rib width is increased, the sample (p = 0.2 × W) highest pressure drop and coefficient of friction values.

Keywords: ribs; triangular duct; laminar flow; performance factor

Nomenclature Subscripts

A

heated surface area (m2)

bm

bulk mean fluid temperature

Dh

channel hydraulic diameter (m)

pmT

mean plate temperature

h

convective heat transfer coefficient (W/K m2)

L

length of the rectangular duct (m)

f

fanning friction factor

T

temperature (K)

K

thermal conductivity (W/m K)

Re

Reynolds number

Nu

local Nusselt number

Pr

Prandtl number

P

local pressure (N/m2)

ν

kinematic viscosity of fluid

W

length of the side of the triangle (m)

P

wetted perimeter (m)

μ

dynamic viscosity (kg/m s)

ρ

density of fluid (kg/m3)

u,v,w

velocity component in x, y, and z direction, respectively (m/s)

x, y, z

Cartesian coordinates in horizontal, vertical, and depth direction (m)

C p

specific heat capacity (J/kg K)

a

thermal diffusivity (m2/s)

1 Introduction

Energy conversion and utilization via heat exchange is a universal phenomenon. When heat exchangers are optimized for various uses, they become more cost-effective without sacrificing performance [1]. Heat exchangers are used in a wide variety of industries, including the transportation industry, the aerospace industry, the chemical industry, the healthcare industry, the pharmaceutical industry, and the energy industry. Therefore, it is important to build the heat exchanger such that it operates as efficiently and dependably as feasible as [2].

There are a number of approaches to improve the efficiency of thermal devices, such as using active methods, passive techniques, or a hybrid of the two. However, active strategies of heat transfer augmentation need costly equipment due to their reliance on external sources of power to enhance thermal transfer [1].

Therefore, swirl inserts are used in passive technique, which are easy to make and installed in an exchanger of heat rapidly, which leads, by creating turbulence, to the main liquid, as well as causing the boundary layer that exists there to be periodically disturbed by the duct's oscillating cross-section, swirl flow introduced into a duct increase its convective heat transmission [1,2].

Besides that, there is a close relationship between the flow and heat transmission, and the geometric form of the channels. Therefore, pressure loss is the most crucial aspect of ribs’ effect on flow. Hence, it was discovered that among the most frequent duct designs, the triangular cross-sectional duct had the smallest pressure drop [3,4,5].

In order to find the optimal values for various rib design features, such as rib arrangement, rib elevation as well as angle of attack, several studies have been performed for non-circular ducts. For instance, Nidhul et al. [6] found that the Nusselt number in triangular channels with rectangular ribs rose by 245% at w/e = 11 and l/e = 11. Additionally, Hassan et al. [1] where a comparable investigation, values of for P/e = 10, e/w = 4, and e/D = 0.04 in the relative roughness dimension were found to provide the highest thermohydraulic performance parameter value of 1.89. Either, Kumer et al. [7] used square ribs in a triangle duct, which improves heat transmission by over 97% and results in the highest value of the thermal performance power (TPP) at Re = 17,900, with P/e = 10 and e/D = 0.05. in the work of Sheikholeslami et al. [8], using rectangular ribs, exergy losses to the environment are reduced by 43% and exergy losses due to heat transfer to the fluid are reduced by 62% when the dimension ratio e/w = 4. For e/w = 4, P/e = 10, and e/D = 0.04, the energetic efficiency (ex) and thermal efficiency (th) are maximized by 36 and 17%, respectively. Additionally, the ribbed triangular duct with adjustable rib angles (30° < a < 75°) was studied by Nidhul et al. [9] The results reveal that the efficacy of the ribbed (a = 45) triangular duct is 17% more than that of the rectangular ducts and 79% greater than that of the smooth duct. In addition, Kumar and Goel [10] learned ribs in various shapes and their effects (half-circle, circle, and triangle, square, and rectangle). At a Reynolds number of 18,700, the best value of the TPP associated with a forward-chamfered rectangular rib (with e/w = 2) was determined to be 2.75. Kumar et al. [4] studied the difference between semi-circular and square ribs. Semi-circular ribs have 26% more energy efficiency than square roughness at e/D as well as p/e measurements of 0.04 and 10, respectively. In addition, Goel et al. [11] investigated the impact of semi-spherical shaped ribs. The best result they obtained was an improvement of the Nusselt number by 5.33. At Reynolds number of 2,160 and longitude and transverse pitch ratio as well as 0.039 dimple depth, Kumar et al. [12] also proposed using ribs with a V form for reinforcement. When comparing smooth plates, it was revealed that thermal efficiency increases by an average of 4.93%, whereas performance enhances by an average of 4.41%. Nidhul et al. [13] used v-shaped ribs; when comparing smooth plates, it was revealed that thermal efficiency increases by an average of 4.93%, although performance increases by an average of 4.41%. There have also been several reports on the subject of increasing heat transmission using triangle channels.

In addition, research into non-circular channels, notably rectangular and square channels, has shown other interesting findings. Ameur [14] introduce by a numerical study of the rectangular duct with wavy ribs with angles from 0 to 45° and the height of the duct h/H = 0.4, 0.5, and 0.6. The overall performance factor increases from 1.27 until 1.53, and the corrugated angle reaches 0° up 45°, and h/H must set at 0.5. Debnath et al. [15] also looked at how a pentagonal rib in rectangular channels affected flow. At Re = 38,414, the ideal arrangement of e/D = 0.045 and P/e = 8 leads to increases in the Nusselt number as well as friction factor of 70 and 67.2%, respectively. In addition, Mahanand and Senapati [16] investigated the impact of rib on the inverted T-shape. A thermal enhancement rating of 1.87 is determined as a result of the enhanced heat transmission. Luan and Phu [17] also looked at the angled ribs at different angles between 0 and 180°. As a rule of thumb, the most efficient baffle angles were between 60 and 120°. And Choi and Choi [18] confirmed the triangular rib in the rectangular channel. Nusselt number enhancements varied between 1.19 and 3.37 depending on the investigated geometric conditions.

The influence of the longitudinal rib was shown in a numerical investigation of the square duct according to Kwankaomeng and Promvonge [19]. With 2,000, 0.3, and, 1.5, for Re, Br, and pr, respectively, the results obtained for the Nusselt number ratio and the maximum thermally enhancement factor of the angled baffles are close to 7.9 and 3.1, respectively. On the other hand, Singh et al. [20] investigated the 45° oblique ribs in the square duct. For both inline and staggered configurations, the Nusselt number normalized between 2.7 and 3.1, while thermal hydraulic performance varied from 1.2 to 1.5.

Reviewing the literature, the authors learned about the value of the rib and their possible use in the shape of a triangle duct to improve efficiency and output. Therefore, in this study, the flow and heat transfer characteristics of triangular ribbed air ducts were investigated. There have been very few investigations on the relationship between rib size and Nusselt number, friction coefficient, and pressure drop; especially when the flow is laminar, these studies are almost non-existent. Therefore, the aim of our current study was to show the effect of adding ribs to the triangular duct for the laminar flow and the Reynolds number ranging from 1,000 to 1,800. Thence, in order to demonstrate the impact on the aforementioned criteria, two varieties of ribs, triangular and semi-circular ribs, were examined. Each of them has three sizes, for triangle (b/W = 0.1, 0.15, and 0.2) and for semi-circle (R/W = 0.1, 0.15, and 0.2). In addition, the effect of increasing the rib width on heat transfer and pressure drop in triangular channels was studied, divided into three widths (b/W = 0.2, 0.4, and 0.6). In order to show the best type of ribs, it was necessary to study the effect of Reynolds number, rib size, and rib shape. Also, the comparison between the Nusselt number, the friction coefficient and the pressure drop result from the ribs exist must by used the performance coefficient. Thus, numerical simulations are carried out by utilizing the industrial ANSYS FLUENT 2020 R1 programmer to investigate the heat transfer and fluid behavior in a rib roughened triangle route using computational fluid dynamics (CFD) and to compare f and Nu in the duct.

2 CFD build process

In order to better understand the physical properties of the flow characteristics during laminar conditions and heat transfer from the rib side of the duct, a 3D model of the duct has been constructed using commercially ANSYS FLUENT by design modeler software.

When performing a CFD simulation, the following assumptions are made [21]:

  1. The analysis is conducted under two conditions; the flow is in a steady state and incompressible.

  2. Flow is laminar.

  3. No variation in fluid properties occurs throughout the duct’s length.

  4. Table 1 shows the parameters of air under standard laboratory settings (300 K) where it was the medium of operation.

  5. A no-slip condition exists at the interface between fluid and solid.

Table 1

Characteristics of air used as a liquid medium [23]

No Symbol Operating parameters Value
1 T Temperature 300 K
2 ρ Density 1.165 kg/m3
3 µ Coefficient of viscosity 1.863 × 10−5 kg/m s
4 Pr Prandtl number 0.701
5 cp Specific heat 1,005 J/kg K
6 k Thermal conductivity 0.02675 W/m K

2.1 Description of simulation modeling

Thermal and hydraulic performance predictions were made using a triangular airflow duct with roughened bases by semi-circular and triangle-shaped ribs. In addition to comparing the ribs to the smooth channel, also compare them to three different-sized ribs (e/W = 0.1 sample 1, 0.15 sample 2, and 0.2 sample 3) for triangular rib and (R/W = 0.1 sample 4, 0.15 sample 5, and 0.2 sample 6) for semi-circular rib, and the rib height is equal to the width. Moreover, the effect of the width of the triangular ribs (b/w = 0.2, 0.4, and 0.6 for samples 7, 8, and 9 when e = 0.1 W) and semi-circular ribs (b/w = 0.2, 0.4, and 0.6 for samples 10, 11, and 12 when R = 0.1 W) is studied as the difference in the Nusselt number and the rest of the factors. Furthermore, the ribs are set up in the center of the duct’s base for all samples. Besides that, Figure 1 shows a cross-section of a semi-circular and a triangular rib, as well as a detailed design of a ribbed duct. Table 2 also provides information on the duct and rib sizes. Figure 2 shown the all used Ribs details as function for duct triangular dimensions. The entrance velocity is also calculated using a Reynolds number (Re) and the duct’s hydraulic diameter. The Reynolds number will be from 1,000 to 1,800. Furthermore, there is a consistent heat flux estimated to be 450 W/ m 2 at the duct’s base [21].

Figure 1 Ribs and ducts details used in the simulation.
Figure 1 Ribs and ducts details used in the simulation.
Figure 1

Ribs and ducts details used in the simulation.

Table 2

Dimensions of the channel and the ribs used in the simulation

No. Parameters Value/range No. Parameters Value/range
1 Equilateral triangular duct 9 Sample 6 (semi-circular rib) R = 0.1 × W
2 Side length for duct; W (m) W = 0.3 10 Sample 7 (triangular rib) Width b = 0.6 W
3 Total duct length; L (m) 1 11 Sample 8 (triangular rib) Width b = 0.4 W
4 Sample 1 (triangular rib) e = 0.2 × W 12 Sample 9 (triangular rib) Width b = 0.2 W
5 Sample 2 (triangular rib) e = 0.15 × W 13 Sample 10 (semi-circular rib) Width b = 0.6 W
6 Sample 3 (triangular rib) e = 0.1 × W 14 Sample 11 (semi-circular rib) Width b = 0.4 W
7 Sample 4 (semi-circular rib) R = 0.2 × W 15 Sample 12 (semi-circular rib) Width b = 0.2 W
8 Sample 5 (semi-circular rib) R = 0.15 × W 16 Reynolds number; Re 1,000–1,800
Figure 2 Ribs details.
Figure 2

Ribs details.

2.2 Governing equations

The governing equations for the steady laminar flow in a duct with a triangular cross-section may be written in the form of Cartesian coordinates as [22]:

Continuity

(1) ∂ u ∂ x + ∂ v ∂ y + ∂ w ∂ z = 0 .

X-momentum

(2) ρ d u d t = ρ g x − ∂ p ∂ x + μ ∂ 2 u ∂ x 2 + ∂ 2 u ∂ y 2 + ∂ 2 u ∂ z 2 .

Y-momentum

(3) ρ d v d t = ρ g y – ∂ p ∂ y + μ ∂ 2 v ∂ x 2 + ∂ 2 v ∂ y 2 + ∂ 2 v ∂ z 2 .

Z-momentum

(4) ρ d w d t = ρ g z − ∂ p ∂ z + μ ∂ 2 w ∂ x 2 + ∂ 2 w ∂ y 2 + ∂ 2 w ∂ z 2 .

In the aforementioned equations, the variables u, v, and w represent the x, y, and z components of velocity, whereas ρ , μ , and p stand for the density, dynamic viscosity, and static pressure, respectively.

Energy equation

(5) u ∂ T ∂ x + v ∂ T ∂ y + w ∂ T ∂ z = α ∂ 2 T ∂ x 2 + ∂ 2 T ∂ y 2 + ∂ 2 T ∂ z 2 .

The thermal diffusivity of a substance is denoted by the symbol α , and it is defined as follows:

(6) α = k ρ c p ,

where c p is the liquid’s specific heat and k is its thermal conductivity.

3 Build mesh independence

In order to solve the required energy, momentum, and mass differential equations, Ansys fluent 2020 R1 builds a non-uniform fine grid. The purpose of the grid independence test is to investigate the effect of grid size on the mean value of Nu. Nu average value predictions were created using a simulation with a grid size ranging from the coarse (18,826 elements) to the fine (678,113 elements). In this work, a grid independent test is performed at the Reynolds number equal to 1,500 on a triangular rib duct having a side dimension of 0.2 W (sample 1). In the duct, the mean Nusselt number went from 18,826 up 678,113 when the grid design was improved. Grid independence test results are shown in Figure 3. After 208,163 items, there is only a little dispersion from the mean Nu values. As a result, an analysis involving 208,163 components is carried out for each feasible combination of roughness parameters as presented in Figure 4.

Figure 3 Distribution of elements and Nusselt numbers.
Figure 3

Distribution of elements and Nusselt numbers.

Figure 4 Roughness kinds and their respective meshes.
Figure 4

Roughness kinds and their respective meshes.

3.1 Solution architecture

The equations governing the concepts of energy, continuity, and momentum are solved using the finite volume method implemented in Ansys Fluent 2020 R1. The SIMPLE technique and the upwind approach to the second-order discretization of the equations governing the system are used [24]. Convergence requirements of 10 − 3 as well as 10 − 6 for the velocity component of the equation and the energy components, respectively, are also speculative. Finally, a value of 1,000 iterations is chosen such that the surface’s heat transfer coefficient (h) and pressure difference remain steady throughout the simulation.

3.2 Boundary requirements

These boundary criteria determine the nature of the fluid flow inside the duct:

  1. As a function of the Reynolds amount and the hydraulic diameter, the inlet entrance speed is a constant.

  2. Table 1 displays the parameters of the air and confirms that its temperature is comparable to that of the atmosphere (300 K).

  3. Pressure at the outlet is the same as the surrounding air.

  4. The walls: the duct’s side wall must be insulated to prevent heat transmission.

  5. A constant heat flux of 450 W/ m 2 is applied to the base.

4 Data extraction

This CFD simulation sets out to learn more about how semi-circle and triangles influence flow in a triangular duct. Non-dimensional numbers Nu and f characterize the duct’s thermal and hydraulic performance, respectively.

The intake velocity may be determined using the Reynolds number as one of the input variables in the following way:

(7) Re = ρ v in D H μ .

Through the use of simulations, a numerical value is derived for the duct’s area-averaged temperature (Ta) and the bulk-averaged temperature (Tb).

To obtain the typical duct heat transfer coefficient, one uses the following formula [25]:

(8) h = q ( Tp − Tb ) .

The average Nusselt number (Nu) is calculated using the duct’s hydraulic diameter and can be expressed as:

(9) Nu = h D H K ,

where D H represents the hydraulic diameter, h the heat transfer factor, and k the thermal conductivity of the fluid.

The air flow rate and pressure drop across the testing duct were used to calculate the friction coefficient f, as shown in the following:

(10) f = ∆ P D H 2 ρ L v in 2 .

This is the testing duct’s length, L, and the pressure drop, ∆P:

(11) ∆ P = p in − p out = 9.81 × Δ h × ρ m × cos θ .

When the surface roughness is artificially to promote heat transfer, the pressure drop as well as pumping power also increases. The ribs in the duct may boost heat transfer, but they also cause a significant pressure drop; therefore, their usage must be justified. The efficiency parameter ( ε ) for duct ribs may be expressed as follows:

(12) ε = Nu Nu 0 f f o − 1 3 .

5 Validation

Convective heat transfer was explored in a duct with a triangular cross-section and laminar flow for case 3 with a constant heat flux from the base to air in the study by Rajneesh Kumar [6]. The base is maintained at a constant heat flow throughout the numerical simulations, while the walls insulated and the findings are checked against the published research. Table 3 and Figure 5 compare the Rajneesh Kumar [6] findings for case 3 with the bulk temperatures for Re values of 100–2,000. Bulk temperature values observed are in agreement with those anticipated by Rajneesh Kumar [6]. Bulk temperature predictions are 5.79% off from actual measurements. This validates the suggested numerical approach for assessing heat transfer by convection in a variety of uniform heat flux wall designs.

Table 3

Values of bulk temperature for [6] and present study

Re T ave (In present study) T ave [7]
100 375.5442 371.217
500 348.759 314.091
1,000 333.5218 307.046
1,500 326.8865 314.091
2,000 323.0695 303.567
Figure 5 Comparison of bulk temperature values for validation.
Figure 5

Comparison of bulk temperature values for validation.

6 Results and discussion

6.1 Changes in Reynolds number

Reynolds number and Nusselt number have consistently been proven to rise simultaneously. The link between the Reynolds number and the Nusselt number in the smooth duct and other models is shown in Figure 6. Additionally, when rising the Reynolds number, the input air velocity rises and more air enters the test zone. Therefore, duct temperature decreases as a result of improved heat transmission when rising the Reynolds number. However, as the plate length increases, the local measure of Nusselt always drops. As the boundary layer increases and the velocity along the surface decreases, the temperature rises and the heat’s coefficient of transfer decreases as it moves lower down the surface of the duct. As a general rule, ribbed surfaces are more apparent and allow more heat to pass through than smooth ones. In addition, it is noted that sample 4 has the highest Nusselt number compared to other samples, while has sample 3 the lowest Nusselt number.

Figure 6 Effect of the Nusselt number depending on the Reynolds number along the duct.
Figure 6

Effect of the Nusselt number depending on the Reynolds number along the duct.

In addition, Figure 7 shows the relationship between the Reynolds number and the average Nusselt number. It should be noted that all samples have a similar behavior and sample 4 has the highest average Nusselt number of all samples. Furthermore, Figure 8 illustrates the heat distribution and streamlines of samples 4 and 6. It is clear from the figure that the vortices generated in sample 4 are much higher than the other models, which explains the advantage of the Nusselt number.

Figure 7 Relationship between the Reynolds number and the average Nusselt number.
Figure 7

Relationship between the Reynolds number and the average Nusselt number.

Figure 8 Temperature distribution and streamlines of samples 4 and 6 at Reynolds number of 1,800: (a) temperature distribution for sample 4, (b) streamline for sample 4, (c) temperature distribution for sample 6, and (d) streamline for sample 6.
Figure 8

Temperature distribution and streamlines of samples 4 and 6 at Reynolds number of 1,800: (a) temperature distribution for sample 4, (b) streamline for sample 4, (c) temperature distribution for sample 6, and (d) streamline for sample 6.

6.2 Impact of a rib size and form

The shape and size of the ribs greatly effect on the rate of heat transfer in the ducts. Figure 9 demonstrates how the size of the ribs impacts in the heat transfer coefficient and the Nusselt number. Therefore, as the size of the rib increases, the rate of heat transfer increases as a result of the increase in turbulence in the flow, as is evident in Figure 9 for two type’s ribs. In addition, it is clear from Figure 9 that samples 1, 4, and 5 have the highest value of the Nusselt number due to the larger size. Likewise, the shape of the ribs has a very important effect on the rate of heat transfer. Therefore, as shown in the figure, it is clear from the comparison between the semi-circular ribs and the triangular ribs that the semi-circular rib has a much higher effect than its triangular counterpart. The semi-circular shape outperforms the triangle in all sizes, which improves heat transfer.

Figure 9 Effect of the size and shape of the ribs on the Nusselt number for samples 1–6.
Figure 9

Effect of the size and shape of the ribs on the Nusselt number for samples 1–6.

In addition to what has been mentioned, and when comparing the ribs in terms of width and their effect on heat transfer, as can be seen in Figure 10, sample 11 has the highest Nusselt number compared to the rest of the models. In addition, sample 8 has the lowest heat transfer rate, although the width is equal between them.

Figure 10 Effect of the shape of the ribs on the Nusselt number for samples 7–12.
Figure 10

Effect of the shape of the ribs on the Nusselt number for samples 7–12.

In addition, Figure 11 shows the temperature distribution as a result of the effect of the size and shape of the ribs. It turns out that the large size has a much higher impact than the smaller size. Also, it is clear from the aforementioned figure that the effect of the triangular shadow is concentrated in the middle more than the rest of the parts of the channel. However, the thermal distribution in the semi-circular ribs is distributed over the width of the channel, which explains its preference over the triangular ribs.

Figure 11 Temperature distribution depends on the shape and size of the ribs in the duct.
Figure 11

Temperature distribution depends on the shape and size of the ribs in the duct.

6.3 Impact of pressure decline

One of the most important problems caused by ribs is pressure loss. Therefore, channels with ribs require higher pumping forces compared to smooth ones. Pressure loss along the testing section of the ribbed surface is shown in Figure 12 compared to the smooth surface. It is shown that all models’ pressure drops rise when ribs are included. Therefore, as can be seen in same figure, the pressure loss depends on the rib shape and streamline. Therefore, as shown in the figure, sample 7 has the highest pressure drop value, while sample 3 has the lowest, and the values are mediated for the rest of the samples.

Figure 12 Pressure drop along the duct for all samples at the Reynolds number of 1,800.
Figure 12

Pressure drop along the duct for all samples at the Reynolds number of 1,800.

6.4 Results of friction

As can be seen in Figure 13, the coefficient for friction is influenced both by the value of the Reynolds number and by the rib size. As a result, the friction coefficient reduces with a rise in Reynolds number but obviously rises as rib size grows. Increasing the size of the ribs causes an increase in the coefficient of friction due to the increase in the area of contact with the liquid, so the samples 1 and 7 have the highest friction coefficient. In addition, as can be seen in the figure, the tiny size of the ribs in samples 3 and 6 keeps the resultant coefficient friction almost constant.

Figure 13 Effect of friction coefficient on along duct length at Reynolds number of 1,800.
Figure 13

Effect of friction coefficient on along duct length at Reynolds number of 1,800.

6.5 Proportional increase

One of the primary aims of heat transfer enhancement is to increase the Nusselt number and decrease the pressure loss. Therefore, the overall enhancement ratio represents the amount of heat transfer accomplished by the pump’s power (or pressure drop). Equation (12) also allows one to determine the thermal performance of a factor or the overall enhanced ratio.

Therefore, determining the efficiency of the rib components is crucial. The thermal performance of a factor is used to measure the efficiency of the ribs. The thermal performance depends on both Nu and f, and a larger value is preferable when planning a duct’s layout. Therefore, it is possible that the performance factor increases with the increase of the Reynolds number. Various combinations of roughness factors result in varied (ε) values, as shown in Figure 14.

Figure 14 Overall enhancement ratio.
Figure 14

Overall enhancement ratio.

Therefore, it is important to evaluate thermohydraulic performance, which considers not only improvement in heat transfer but also improvement in friction factor, in order to determine the best type of rib shape and size that results in a maximum rise in heat transfer via the least possible for friction factor. The thermohydraulic performance parameter (ε) is defined as the ratio of the increase in heat transfer through a roughened duct to that via a smooth duct at the same pumping power input.

Figure 13 shows that sample 4 at Re of 1,200 yields the greatest increase in enhancement ratio by virtue of the addition of rib.

7 Conclusions

Under the impact of constant roughness parameters, the effects of different shape rough elements on the improvement of heat transfer and the coefficient of friction for a triangle cross-sectional flow pass are explored numerically. Roughness pieces of varied forms are placed centrally in the foundation, with their rough sides facing the flow of air. Three different sized triangles (e/W = 0.2, 0.15, and 0.1) and three sized semi-circles (R/W = 0.2, 0.15, and 0.1) were studied, for a total of six distinct roughness geometries, in addition to studying the effect of the width of the ribs of the models 3 and 6 for e/W = 0.1 and R/W = 0.1, respectively. Therefore, the total number of samples was 12, and four Reynolds numbers were 1,000, 1,200, 1,500, and 1,800. Thermal performance may be predicted using the Nusselt number (Nu), flow characteristics using the frictional factor (f), and overall performance in comparison with a smooth duct using the overall enhancement ratio (ε). The most notable findings of this study are as follows:

  1. Increases in the heat transfer coefficients and the Nusselt number are the results of the addition of ribs to the triangular channel, which increases the rate of heat transmission.

  2. The values of Nu and f are profoundly impacted by the flow parameter. Nu is greatest for high Re values. However, the converse is true in that f is maximized with low Re values.

  3. Sample 4 semi-circular rib has the maximum heat transfer rates and Nusselt number as compared with another shape because it mixes the fluid that flows layers within the channel better than the others.

  4. The rate of pressure drop increases with the increase in the width of the rib; therefore, it will be noted that the highest pressure drop is for sample 7.

  5. Sample 7 has the highest coefficient of friction among all models based on the rate of pressure drop.

  6. The semi-circular rib sample 4 with the greatest rate of 1.717 for Reynolds number of 1,200 had the best factors for the performance of all the ribs evaluated.

  7. The percentage increase in the Nusselt number was 71.7% for sample 4.

  1. Conflict of interest: The authors state no conflict of interest.

  2. Data availability statement: Most datasets generated and analyzed in this study are comprised in this submitted manuscript. The other datasets are available on reasonable request from the corresponding author with the attached information.

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Received: 2023-06-30
Revised: 2023-08-09
Accepted: 2023-09-02
Published Online: 2024-02-05

© 2024 the author(s), published by De Gruyter

This work is licensed under the Creative Commons Attribution 4.0 International License.

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https://doi.org/10.1515/eng-2022-0523
Keywords for this article
ribs; triangular duct; laminar flow; performance factor
Creative Commons
BY 4.0

Articles in the same Issue

  1. Regular Articles
  2. Methodology of automated quality management
  3. Influence of vibratory conveyor design parameters on the trough motion and the self-synchronization of inertial vibrators
  4. Application of finite element method in industrial design, example of an electric motorcycle design project
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  97. Effect of GFRP bar length on the flexural behavior of hybrid concrete beams strengthened with NSM bars
  98. Exploring the impact of parameters on flow boiling heat transfer in microchannels and coated microtubes: A comprehensive review
  99. Crumb rubber modification for enhanced rutting resistance in asphalt mixtures
  100. Special Issue: AESMT-6
  101. Design of a new sorting colors system based on PLC, TIA portal, and factory I/O programs
  102. Forecasting empirical formula for suspended sediment load prediction at upstream of Al-Kufa barrage, Kufa City, Iraq
  103. Optimization and characterization of sustainable geopolymer mortars based on palygorskite clay, water glass, and sodium hydroxide
  104. Sediment transport modelling upstream of Al Kufa Barrage
  105. Study of energy loss, range, and stopping time for proton in germanium and copper materials
  106. Effect of internal and external recycle ratios on the nutrient removal efficiency of anaerobic/anoxic/oxic (VIP) wastewater treatment plant
  107. Enhancing structural behaviour of polypropylene fibre concrete columns longitudinally reinforced with fibreglass bars
  108. Sustainable road paving: Enhancing concrete paver blocks with zeolite-enhanced cement
  109. Evaluation of the operational performance of Karbala waste water treatment plant under variable flow using GPS-X model
  110. Design and simulation of photonic crystal fiber for highly sensitive chemical sensing applications
  111. Optimization and design of a new column sequencing for crude oil distillation at Basrah refinery
  112. Inductive 3D numerical modelling of the tibia bone using MRI to examine von Mises stress and overall deformation
  113. An image encryption method based on modified elliptic curve Diffie-Hellman key exchange protocol and Hill Cipher
  114. Experimental investigation of generating superheated steam using a parabolic dish with a cylindrical cavity receiver: A case study
  115. Effect of surface roughness on the interface behavior of clayey soils
  116. Investigated of the optical properties for SiO2 by using Lorentz model
  117. Measurements of induced vibrations due to steel pipe pile driving in Al-Fao soil: Effect of partial end closure
  118. Experimental and numerical studies of ballistic resistance of hybrid sandwich composite body armor
  119. Evaluation of clay layer presence on shallow foundation settlement in dry sand under an earthquake
  120. Optimal design of mechanical performances of asphalt mixtures comprising nano-clay additives
  121. Advancing seismic performance: Isolators, TMDs, and multi-level strategies in reinforced concrete buildings
  122. Predicted evaporation in Basrah using artificial neural networks
  123. Energy management system for a small town to enhance quality of life
  124. Numerical study on entropy minimization in pipes with helical airfoil and CuO nanoparticle integration
  125. Equations and methodologies of inlet drainage system discharge coefficients: A review
  126. Thermal buckling analysis for hybrid and composite laminated plate by using new displacement function
  127. Investigation into the mechanical and thermal properties of lightweight mortar using commercial beads or recycled expanded polystyrene
  128. Experimental and theoretical analysis of single-jet column and concrete column using double-jet grouting technique applied at Al-Rashdia site
  129. The impact of incorporating waste materials on the mechanical and physical characteristics of tile adhesive materials
  130. Seismic resilience: Innovations in structural engineering for earthquake-prone areas
  131. Automatic human identification using fingerprint images based on Gabor filter and SIFT features fusion
  132. Performance of GRKM-method for solving classes of ordinary and partial differential equations of sixth-orders
  133. Visible light-boosted photodegradation activity of Ag–AgVO3/Zn0.5Mn0.5Fe2O4 supported heterojunctions for effective degradation of organic contaminates
  134. Production of sustainable concrete with treated cement kiln dust and iron slag waste aggregate
  135. Key effects on the structural behavior of fiber-reinforced lightweight concrete-ribbed slabs: A review
  136. A comparative analysis of the energy dissipation efficiency of various piano key weir types
  137. Special Issue: Transport 2022 - Part II
  138. Variability in road surface temperature in urban road network – A case study making use of mobile measurements
  139. Special Issue: BCEE5-2023
  140. Evaluation of reclaimed asphalt mixtures rejuvenated with waste engine oil to resist rutting deformation
  141. Assessment of potential resistance to moisture damage and fatigue cracks of asphalt mixture modified with ground granulated blast furnace slag
  142. Investigating seismic response in adjacent structures: A study on the impact of buildings’ orientation and distance considering soil–structure interaction
  143. Improvement of porosity of mortar using polyethylene glycol pre-polymer-impregnated mortar
  144. Three-dimensional analysis of steel beam-column bolted connections
  145. Assessment of agricultural drought in Iraq employing Landsat and MODIS imagery
  146. Performance evaluation of grouted porous asphalt concrete
  147. Optimization of local modified metakaolin-based geopolymer concrete by Taguchi method
  148. Effect of waste tire products on some characteristics of roller-compacted concrete
  149. Studying the lateral displacement of retaining wall supporting sandy soil under dynamic loads
  150. Seismic performance evaluation of concrete buttress dram (Dynamic linear analysis)
  151. Behavior of soil reinforced with micropiles
  152. Possibility of production high strength lightweight concrete containing organic waste aggregate and recycled steel fibers
  153. An investigation of self-sensing and mechanical properties of smart engineered cementitious composites reinforced with functional materials
  154. Forecasting changes in precipitation and temperatures of a regional watershed in Northern Iraq using LARS-WG model
  155. Experimental investigation of dynamic soil properties for modeling energy-absorbing layers
  156. Numerical investigation of the effect of longitudinal steel reinforcement ratio on the ductility of concrete beams
  157. An experimental study on the tensile properties of reinforced asphalt pavement
  158. Self-sensing behavior of hot asphalt mixture with steel fiber-based additive
  159. Behavior of ultra-high-performance concrete deep beams reinforced by basalt fibers
  160. Optimizing asphalt binder performance with various PET types
  161. Investigation of the hydraulic characteristics and homogeneity of the microstructure of the air voids in the sustainable rigid pavement
  162. Enhanced biogas production from municipal solid waste via digestion with cow manure: A case study
  163. Special Issue: AESMT-7 - Part I
  164. Preparation and investigation of cobalt nanoparticles by laser ablation: Structure, linear, and nonlinear optical properties
  165. Seismic analysis of RC building with plan irregularity in Baghdad/Iraq to obtain the optimal behavior
  166. The effect of urban environment on large-scale path loss model’s main parameters for mmWave 5G mobile network in Iraq
  167. Formatting a questionnaire for the quality control of river bank roads
  168. Vibration suppression of smart composite beam using model predictive controller
  169. Machine learning-based compressive strength estimation in nanomaterial-modified lightweight concrete
  170. In-depth analysis of critical factors affecting Iraqi construction projects performance
  171. Behavior of container berth structure under the influence of environmental and operational loads
  172. Energy absorption and impact response of ballistic resistance laminate
  173. Effect of water-absorbent polymer balls in internal curing on punching shear behavior of bubble slabs
  174. Effect of surface roughness on interface shear strength parameters of sandy soils
  175. Evaluating the interaction for embedded H-steel section in normal concrete under monotonic and repeated loads
  176. Estimation of the settlement of pile head using ANN and multivariate linear regression based on the results of load transfer method
  177. Enhancing communication: Deep learning for Arabic sign language translation
  178. A review of recent studies of both heat pipe and evaporative cooling in passive heat recovery
  179. Effect of nano-silica on the mechanical properties of LWC
  180. An experimental study of some mechanical properties and absorption for polymer-modified cement mortar modified with superplasticizer
  181. Digital beamforming enhancement with LSTM-based deep learning for millimeter wave transmission
  182. Developing an efficient planning process for heritage buildings maintenance in Iraq
  183. Design and optimization of two-stage controller for three-phase multi-converter/multi-machine electric vehicle
  184. Evaluation of microstructure and mechanical properties of Al1050/Al2O3/Gr composite processed by forming operation ECAP
  185. Calculations of mass stopping power and range of protons in organic compounds (CH3OH, CH2O, and CO2) at energy range of 0.01–1,000 MeV
  186. Investigation of in vitro behavior of composite coating hydroxyapatite-nano silver on 316L stainless steel substrate by electrophoretic technic for biomedical tools
  187. A review: Enhancing tribological properties of journal bearings composite materials
  188. Improvements in the randomness and security of digital currency using the photon sponge hash function through Maiorana–McFarland S-box replacement
  189. Design a new scheme for image security using a deep learning technique of hierarchical parameters
  190. Special Issue: ICES 2023
  191. Comparative geotechnical analysis for ultimate bearing capacity of precast concrete piles using cone resistance measurements
  192. Visualizing sustainable rainwater harvesting: A case study of Karbala Province
  193. Geogrid reinforcement for improving bearing capacity and stability of square foundations
  194. Evaluation of the effluent concentrations of Karbala wastewater treatment plant using reliability analysis
  195. Adsorbent made with inexpensive, local resources
  196. Effect of drain pipes on seepage and slope stability through a zoned earth dam
  197. Sediment accumulation in an 8 inch sewer pipe for a sample of various particles obtained from the streets of Karbala city, Iraq
  198. Special Issue: IETAS 2024 - Part I
  199. Analyzing the impact of transfer learning on explanation accuracy in deep learning-based ECG recognition systems
  200. Effect of scale factor on the dynamic response of frame foundations
  201. Improving multi-object detection and tracking with deep learning, DeepSORT, and frame cancellation techniques
  202. The impact of using prestressed CFRP bars on the development of flexural strength
  203. Assessment of surface hardness and impact strength of denture base resins reinforced with silver–titanium dioxide and silver–zirconium dioxide nanoparticles: In vitro study
  204. A data augmentation approach to enhance breast cancer detection using generative adversarial and artificial neural networks
  205. Modification of the 5D Lorenz chaotic map with fuzzy numbers for video encryption in cloud computing
  206. Special Issue: 51st KKBN - Part I
  207. Evaluation of static bending caused damage of glass-fiber composite structure using terahertz inspection
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