Vol. 06, Issue 08,August 2021 IMPACT FACTOR: 7.98 (INTERNATIONAL JOURNAL) 120 MODELING OF IC ENGINE FIN USING VARIOUS MATERIALS
Gadak Sagar Sanjay
Department of Mechanical Engineering, BM College of Technology, RGPV, Bhopal Professor Purushottam Kumar Sahu
Department of Mechanical Engineering, BM College of Technology, RGPV, Bhopal Abstract -For the present work, we have considered the three different fin materials namely malleable cast iron, pure aluminum, and magnesium AZ31B alloy. These materials are taken because of their high machinability and good thermal properties. The geometry is made in CATIA V5R121 software and the analysis work is done using ANSYS 14.0 work bench.
The heat flux is calculated for all the three materials in consideration and with fin numbers varying from one to five. Finally, the theoretical and simulation results are compared and it has been observed that both results are in good agreement to give us the concluding remark that which material will be the best for IC engine fins.
Keywords: IC engine, Fins, Malleable cast iron, pure aluminum, Magnesium AZ31B, Heat flux, CATIA, and ANSYS.
1. INTRODUCTION 1.1 Introduction of Fin
A fin may be a surface that extends from associate object to extend the speed of warmth transfer to or from the setting by increasing convection. For the principle of conduction, convection, radiation of an pin configuration determines the amount of heat it transfers Increasing the temperature difference between the fin configuration and the depends on the environment, slightly increasing the convection heat transfer coefficient, or slightly increasing the surface area of the pin configuration of the object increases the heat transfer. Sometimes it is not economical or it is not feasible to change the first two options. Adding a fin configuration to the object, however, slightly increases the surface area and can sometimes be economical solution to heat transfer problems.
Circumferential fins around the cylinder, square and rectangular shape of a motor cycle engine and fins attached to condenser tubes of a refrigerator are a few familiar examples only occurs when there's a temperature distinction, Flows quicker once this distinction is higher, continually flows from high to temperature, larger is bigger with greater expanse.
1.2 Heat Exchangers
The general operate of a device is to transfer heat from one fluid to a different. The basic part of a device may be viewed as a tube with one fluid running through it and another fluid flowing by on the skin. There
are thus three heat transfer operations that need to be described:
1. Heat transfer from fluid to the inner wall of the tube,
2. Heat transfer through the tube wall, and
3. Heat transfer from the outer tube wall to the outside fluid.
Heat exchangers square measure generally classified in step with flow arrangement and sort of construction. The simplest device is one that the recent and cold fluids move within the same or opposite directions in a very concentrically tube (or double-pipe) construction. In the parallel-flow arrangement of Figure 2 the hot and cold fluids enter at the same end, flow in the same direction, and leave at the same end. In the counter flow arrangement of Figure 1.1, the fluids enter at opposite ends, flow in opposite directions, and leave at opposite ends.
Figure 1.1 Concentric tubes heat exchangers
Vol. 06, Issue 08,August 2021 IMPACT FACTOR: 7.98 (INTERNATIONAL JOURNAL) 121 Figure 1.2 Cross-flow heat exchangers
Alternatively, the fluids may be in cross flow (perpendicular to each other), as shown by the finned and UN finned tubular heat exchangers of Figure 3. The two configurations take issue in keeping with whether or not the fluid moving over the tubes is unmixed or mixed. In Figure 3, the fluid is said to be unmixed because the fins prevent motion in a direction that is transverse to the main flow direction. Under this case the fluid temperature varies with and. fluid motion, hence mixing, in the transverse direction is possible, and temperature variations are primarily in the main flow direction. Since the tube flow is unmixed, each fluid square measure unmixed within the finned money handler, whereas one fluid is mixed and therefore the different world organization mixed within the finned money handler.
To develop the methodology for warmth money dealer analysis and style, we glance at the matter of warmth transfer from a fluid within a tube to a different fluid outside.
Figure 1.3 Geometry for heat transfer between two fluids [6]
1.3 Rectangular Plain Fins
Plain fins square measure far and away the foremost common of all compact cores or surfaces utilized in compact heat exchangers. The plain fin surfaces are characterized by long uninterrupted flow passages, with performance similar to that obtained inside long circular tubes Kays &
London (1984). Although passages of triangular and rectangular cross section square measure additional common, any desired form will be given to the fins, considering solely producing constraints.
Straight fins in triangular arrangement can be manufactured at high speeds and hence are less expensive than rectangular fins.
But generally they are structurally weaker than rectangular fins for the same passage size and fin thickness. They even have lower heat transfer performance compared to rectangular fins, significantly in streamline flow. Plain fins square measure employed in those applications wherever core pressure drop is vital. The application range from aerospace air-conditioning to oil refining a heat exchanger with rectangular plain fin as shown in Figure 1.5 requires a smaller flow frontal area than that with interrupted fins for specified pressure drop, heat transfer and mass flow rate. The heat transfer sweetening achieved with plain fins results in the main from magnified space density, instead of any substantial rise within the heat transfer constant.
Figure 1.4 Plate fin heat exchanger with rectangular plain fins[10]
1.4 Rectangular Perforated Fins
This surface geometry is made by punching a pattern of spaced holes in the fin material before it is formed into flow channels as shown in Figure 1.4. The channels is also triangular or rectangular in form with either spherical or rectangular perforations. The thermal performance of the perforated fin is less than that of a good offset strip fin. The
Vol. 06, Issue 08,August 2021 IMPACT FACTOR: 7.98 (INTERNATIONAL JOURNAL) 122 statement concluded from open literature
under references Maiti (2002) and Shah (1981), however, it depends on various geometrical parameters and it is only relative comparison. Perforated fins are now used only in limited number of applications such as tabulators in oil coolers Furthermore, the perforated fin represents a wasteful way of making an enhanced surface, since the fabric removed in creating the perforated hole is wasted. Even though a negligible quantity of material removed for making holes or perforations, there is an improvement in performance of the heat exchanger. As the aim is to increase the heat transfer coefficient, it cannot be called as material waste. The effect of perforated fin surface on heat transfer coefficient in detail as given in section 2.5.2.
1.5 Direct a Objective The objective of this work is
1. To model a rectangular fin geometry using some modelling software
2. To model the same geometry using different number of fins.
3. To analyse heat transfer through the fins using some analysis software.
4. To calculate the heat flux numerically to predict whether it resembles the software based analysis or not.
5. To repeat the same steps using different number of fins.
6. To change the fin material and reanalyse the same using the given boundary conditions as taken in previous geometry.
2 MODELING AND SIMULATION
Figure 2.1 Heat flux for single fin geometry using magnesium (AZ31B) as
fin material
The figure 4.1 represents the heat flux for single fin geometry using magnesium (AZ31B) as fin material. It is been observed that the maximum heat flux is 3669.72 w/m2 as obtained from simulation result.
Figure 2.2: Heat flux for two fin geometry using magnesium (AZ31B) as fin material The figure 2.2 represents the heat flux for two fin geometry using magnesium (AZ31B) as fin material. It is been observed that the maximum heat flux is 3992.71 w/m2 as obtained from simulation result.
Figure 2.3 Heat flux for three fin geometry using magnesium (AZ31B) as
fin material
The figure 2.3 represents the heat flux for three fin geometry using magnesium (AZ31B) as fin material. It is been observed that the maximum heat flux is 4250.91 w/m2 as obtained from simulation result.
Vol. 06, Issue 08,August 2021 IMPACT FACTOR: 7.98 (INTERNATIONAL JOURNAL) 123 Figure 2.4 Heat flux for four fin geometry
using magnesium (AZ31B) as fin material The figure 2.4 represents the heat flux for four fin geometry using magnesium (AZ31B) as fin material. It is been observed that the maximum heat flux is 4592.51 w/m2 as obtained from simulation result.
Figure 2.5 Heat flux for five fin geometry using magnesium (AZ31B) as fin material The figure 2.5 represents the heat flux for five fin geometry using magnesium (AZ31B) as fin material. It is been observed that the maximum heat flux is 4785.67 w/m2 as obtained from simulation result.
Figure 2.6 Heat flux for one fin geometry using malleable cast iron as fin material
The figure 2.6 represents the heat flux for one fin geometry using malleable cast iron as fin material. It is been observed that the maximum heat flux is 4379.1 w/m2 as obtained from simulation result.
Figure 2.7 Heat flux for two fin geometry using malleable cast iron as fin material The figure 2.7 represents the heat flux for two fin geometry using malleable cast iron as fin material. It is been observed that the maximum heat flux is 4712.82 w/m2 as obtained from simulation result.
Figure 2.8 Heat flux for three fin geometry using malleable cast iron as fin
material
The figure 2.8 represents the heat flux for three fin geometry using malleable cast iron as fin material. It is been observed that the maximum heat flux is 4819.02 w/m2 as obtained from simulation result.
Vol. 06, Issue 08,August 2021 IMPACT FACTOR: 7.98 (INTERNATIONAL JOURNAL) 124 Figure 2.9 Heat flux for four fin geometry
using malleable cast iron as fin material The figure 2.9 represents the heat flux for four fin geometry using malleable cast iron as fin material. It is been observed that the maximum heat flux is 4972.81 w/m2 as obtained from simulation result.
Figure 2.10 Heat flux for five geometry using malleable cast iron as fin material The figure 2.10 represents the heat flux for five fin geometry using malleable cast iron as fin material. It is been observed that the maximum heat flux is 4999.62 w/m2 as obtained from simulation result.
Figure 2.11 Heat flux for one fin geometry using pure aluminium as fin
material
The figure 2.11 represents the heat flux for one fin geometry using pure aluminium as fin material. It is been observed that the maximum heat flux is 5771.38 w/m2 as obtained from simulation result.
Figure 2.12 Heat flux for two fin geometry using pure aluminium as fin
material
The figure 2.12 represents the heat flux for two fin geometry using pure aluminium as fin material. It is been observed that the maximum heat flux is 6104.14 w/m2 as obtained from simulation result.
Figure 2.13: Heat flux for three fin geometry using pure aluminium as fin
material
The figure 2.13 represents the heat flux for three fin geometry using pure aluminium as fin material. It is been observed that the maximum heat flux is 6299.71 w/m2 as obtained from simulation result.
Vol. 06, Issue 08,August 2021 IMPACT FACTOR: 7.98 (INTERNATIONAL JOURNAL) 125 Figure 2.14: Heat flux for four fin
geometry using pure aluminium as fin material
The figure 2.14 represents the heat flux for four fin geometry using pure aluminium as fin material. It is been observed that the maximum heat flux is 6373.21 w/m2 as obtained from simulation result.
Figure 2.15 Heat flux for five fin geometry using pure aluminium as fin
material
The figure 2.15 represents the heat flux for five fin geometry using pure aluminium as fin material. It is been observed that the maximum heat flux is 6389.37 w/m2 as obtained from simulation result.
Table 2.1 Simulation results showing heat flux values for different materials of
fin considering three different fin materials
Number of fins
Fin Material Magnesium
(AZ31B) Malleabl e cast
iron
Pure aluminu
m 1 3669.72 4379.10 5771.38 2 3992.71 4712.82 6104.14 3 4250.91 4819.02 6299.71 4 4592.51 4971.81 6373.21 5 4785.67 4999.62 6389.37
Figure 2.16 Comparative figure between simulation and numerical data showing heat flux values for Magnesium (AZ31B)
fin material
Table 2.2 Comparative table between simulation and numerical data showing heat flux values for malleable cast iron fin material
Table 2.2 Comparative table between simulation and numerical data showing
heat flux values for pure aluminium as fin material
Following conclusions can be drawn on the basis of numerical analysis and ANSYS simulation the following conclusions can be
Vol. 06, Issue 08,August 2021 IMPACT FACTOR: 7.98 (INTERNATIONAL JOURNAL) 126 drawn in order to select suitable fin for
optimum heat transfer rates:
1. In all the cases represented here the pure aluminium have the highest amount of heat transfer rate among the three material namely pure aluminium, Malleable cast iron and magnesium (AZ31B).
2. The heat transfer using magnesium (AZ31B) as fin material is the second best material for fin material selection.
3. The Malleable cast iron is transferring the same heat with a very slow rate and should not be considered if pure aluminium and magnesium (AZ31B) are available as a option to use as fin material.
4. From the above charts it can be conclude that as the number of fins increases the numerical and simulation results are getting closer values of heat flux and so the software results can be taken directly as reference to select the fin material for actual applications.
5. In most of the cases the simulation results are providing the low values of heat transfer this may be due to the fact that we have taken a static atmospheric temperature and air velocity which may affect the heat transfer rates in actual practices.
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