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Design of an intercooler of a turbocharger unit to enhance the volumetric
1.
International Journal of
Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 3, May - June (2013) © IAEME 1 DESIGN OF AN INTERCOOLER OF A TURBOCHARGER UNIT TO ENHANCE THE VOLUMETRIC EFFICIENCY OF DIESEL ENGINE Mohd Muqeem1 , Dr. Manoj Kumar2 1 Student, M. Tech., Mechanical Engineering, IFTM University, Delhi Road, Moradabad, UP, India, 244102 2 Professor, Mechanical Engineering Department, IFTM University, Delhi Road, Moradabad, UP, India, 244102 ABSTRACT The commercially available automotive intercooler used to cool down the compressed hot air from turbo compressor fails when the summers are very hot and the speed of the vehicle is lowered. This is because, when speed of the vehicle gets reduced, the mass flow rate of atmospheric air in to the intercooler also get reduced and when the summers are hot, the temperature of atmospheric air becomes very high due to which the efficiency of intercooler get reduced. As a result of this, the density of air and consequently the mass flow rate delivered by the turbo compressor and entering into the engine get reduced. An intercooler is being designed here with proper heat transfer area to increase this mass flow rate by mixing some additional amount of conditioned air into the atmospheric air entering into the intercooler to cool the hot air delivered by the turbo compressor. KEYWORDS: Heat exchanger core, intercooler, mass flow rate and volumetric efficiency. 1. INTRODUCTION In turbo-charging, the volumetric efficiency of the engine is improved by pumping the air into the combustion chamber instead of sucking, as in normally aspirated engine. By doing this, volume of air sucked into the combustion chamber is more than its capacity under static conditions [1]. This is done by using a compressor driven by a turbine, both mounted on the same shaft. During this process, when the air is passed through the compressor, its temperature is increased due to compression [3]. For further reduce this temperature, the air is passed through the intercooler while this intercooler is not able to reduce the temperature of INTERNATIONAL JOURNAL OF MECHANICAL ENGINEERING AND TECHNOLOGY (IJMET) ISSN 0976 – 6340 (Print) ISSN 0976 – 6359 (Online) Volume 4, Issue 3, May - June (2013), pp. 01-10 © IAEME: www.iaeme.com/ijmet.asp Journal Impact Factor (2013): 5.7731 (Calculated by GISI) www.jifactor.com IJMET © I A E M E
2.
International Journal of
Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 3, May - June (2013) © IAEME 2 the air as initially it was. In summers when the speed of the vehicle is low, the performance of the intercooler becomes very low. If it is possible to down the temperature of the air nearer or below the ambient temperature after intercooler and the mass flow rate will increase to a good extent. The volumetric efficiency of the engine will also increase to high extent due to increase in the mass flow rate of air, as more quantity of air will be pushed into the combustion chamber [4][5][6]. Through the review of technologies used in turbocharging, it has been concluded that intercooler is never made refrigerated to cool the hot air [2]. To achieve this, the intercooler of the turbocharger unit is made refrigerated to some extent by passing the conditioned air into it as the cold fluid, coming from cooling coil of the automotive air conditioning system. By this method, the compressed hot air will be cooled by the mixture of two, the cooled air from air conditioning system and the atmospheric air coming from the front side of the vehicle. 2. MATERIALS AND METHOD 2.1 The Detailed specifications of the engine for which the design of intercooler is being proposed The model selected for the modification in intercooler of turbocharger is of Maruti Suzuki Swift VDi for which the technical specifications are as follows: Table 2.1: Technical Specifications of the Engine of Maruti Suzuki Swift VDi 1. Engine type, Valve and Fuel System 1.3L, In-line 4, 16 Valves, Dual Overhead Camshaft(DOHC), Common Rail Direct Injection (CRDi), Fixed Geometry Turbocharger with Intercooler, Diesel 2. Displacement 1248 cc 3. Maximum Power 76/4000 HP/rpm 4. Maximum Torque 190/2000 Nm/rpm 5. No. of Cylinders 4 6. Valves per Cylinder 4 7. Valve System DOHC 8. Fuel Type Diesel 9. Fuel System Common Rail Direct Injection (CRDi) 10. Drive System 2 Wheel Drive(Front) 11. Maximum Speed 160 km/h 12. No. of Gears 5 13. Bore 69.6 mm 14. Stroke 82 mm 15. Compression Ratio 17.6:1 16. Fuel Efficiency Highway 19.1 Km/L City 14.4Km/L
3.
International Journal of
Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 3, May - June (2013) © IAEME 3 2.2 Measurement of temperature and pressure of the air being supplied to the combustion chambers of the engine at specified RPMs Data recorded by Smart Diagnostic Tool (SDT) through various sensors located at different points in the engine is as follows: Table 2.2: Data recorded by SDT S. No. Parameters RMP of Engine Intake Air Temp. T1 (o C) Mass Flow Rate (g/s) Intake Absolute Pressure P1 (KPa) Boost Pressure P2 (KPa) 1 1047 62 7.68 97 99 2 1171 62 8.67 97 99 3 1325 62 9.53 97 99 4 1333 62 9.58 97 99 5 1347 63 9.63 97 99 6 1570 64 11.16 97 100 7 1578 64 11.23 97 100 8 1913 64 14.03 97 102 9 2122 64 15.41 97 102 10 2397 65 17.70 97 104 11 2706 65 23.45 97 112 12 2760 65 24.53 97 115 13 2834 65 24.88 97 116 14 2891 65 26.18 97 117 15 3487 67 43.43 97 137 16 3503 67 46.18 97 142 17 3574 67 46.33 97 143 18 4377 67 58.67 97 155 19 5091 67 64.00 97 165 20 6010 67 65.60 97 165 Here, at inlet the air temperature, air pressure and mass flow rate of air after air filter (i.e. at the inlet of the compressor) and at the outlet, only the one parameter is air pressure. So, to calculate the enthalpy of air at the compressor outlet, it is required to calculate the outlet temperature. The compression in the compressor is considered as poly-tropic and for this process; the relation between temperature and pressure is as follows [8]: Figure 2.1: Turbocharger compressor Compressor P1 T1 ṁ P2 T2 ṁ
4.
International Journal of
Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 3, May - June (2013) © IAEME 4 1 1 2 2 3 4 Let, P Intake air absolute pressure in T Intake air tempearaure in P Boost pressure in T Theoretical tempearaure after compressor in T Actual tempearaure after compressor in T Tempera o o o KPa C KPa C C = = = = = = ture of air after intercooler in Mass flow rate of air in / Polytropic Index (for air, n 1.3) o o C m g s n = = = For poly-tropic process, n-1 n 2 2 1 1 T P T P = Therefore, n-1 n 2 2 1 1 P T T P = Now calculating the values of T2 corresponding to T1, (assuming that the compressor is frictionless) the following data has been find out [9], Table 2.3: Temperature at the compressor outlet corresponding to intake temperature T1 S. No. Engine (rpm) T1 (o C) Theoretical temperature T2 (o C) Actual recorded temperature T3 (o C) 1 1047 62 63.58 92.44 2 1171 62 63.58 92.44 3 1325 62 63.58 92.44 4 1333 62 63.58 92.44 5 1347 63 64.58 93.86 6 1570 64 66.38 94.66 7 1578 64 66.38 94.66 8 1913 64 67.93 95.32 9 2122 64 67.93 95.32 10 2397 65 70.48 98.24 11 2706 65 76.40 104.42 12 2760 65 78.54 106.25 13 2834 65 79.24 106.90 14 2891 65 79.94 106.90 15 3487 67 93.03 121.20 16 3503 67 98.25 127.25 17 3574 67 98.85 127.44 18 4377 67 105.83 135.22 19 5091 67 111.34 141.56 20 6010 67 111.34 141.56
5.
International Journal of
Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 3, May - June (2013) © IAEME 5 2.3 Selection of material and design of intercooler to cool the compressed air The compact heat exchangers are best suited for automotive applications in gas to gas heat exchange Kays and London et al. [1964]. These exchangers generally have surface area of greater than 650 m2 per cubic meter of volume. According to the study, the suitable heat exchanger for the proposed problem should have about 800 m2 of surface area per cubic meter of volume of cross-flow type core with both fluids unmixed. In the proposed problem, on the basis of types of fluids on both sides of the heat exchanger with both fluids unmixed and the material of heat exchanger selected, the overall heat transfer will be as 50 W/ m2 o C [9]. The cold air entering in to the heat exchanger core is the mixture of air coming from automotive air conditioner cooling coil and the atmospheric air coming from the front. Figure 2.2: Compact heat exchanger core 3. RESULTS AND DISCUSSION 3.1 Amount of heat to be extracted from the air being supplied to the engine per second The difference of temperature at the compressor outlet in the theoretical value and the actual recorded value (T2 & T3) is due to the heat added to the air because of compressor friction [4][5]. Now our purpose is to extract this heat from the compressed air before going into the intake manifold. The commercial heat exchanger used in the engine specified in the table 2.1 to extract this heat, cool the air up to a limit as recorded by the Smart Diagnostic Tool (SDT) and the data is as follows:
6.
International Journal of
Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 3, May - June (2013) © IAEME 6 Table 3.1: Temperature recorded before and after intercooler S. No. Engine (rpm) Temperature before intercooler T3 (o C) Temperature after intercooler T4 (o C) 1 1047 92.44 70.25 2 1171 92.44 70.26 3 1325 92.44 70.28 4 1333 92.44 70.34 5 1347 93.86 71.42 6 1570 94.66 71.92 7 1578 94.66 72.01 8 1913 95.32 72.52 9 2122 95.32 72.61 10 2397 98.24 73.12 11 2706 104.42 74.59 12 2760 106.25 75.21 13 2834 106.90 75.32 14 2891 106.90 75.36 15 3487 121.20 77.27 16 3503 127.25 77.87 17 3574 127.44 77.91 18 4377 135.22 78.40 19 5091 141.56 79.20 20 6010 141.56 80.14 Here the purpose is to bring the temperature of air nearer to the ambient temperature by making the intercooler refrigerated. Here it is assumed to reduce the temperature (T4) up to 20 o C, so the calculations for the amount of heat to be extracted per second from the air have been find out by using the following relation of heat transfer o P 3 Heat to be extracted mass flow rate x specific heat x (initial temp final temp) m x C x (T 20) J/s = − = − The specific heat of air is directly proportional to the temperature and pressure. As the temperature and pressure increases, the value of CP for air also increases, but in the proposed problem the value of CP is taken constant (1000 J/Kg K) throughout as the changes in the value of CP are negligible. Therefore, the amount of heat to be extracted at different rpm calculated by the above formula is as follows:
7.
International Journal of
Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 3, May - June (2013) © IAEME 7 Table 3.2: Heat to be extracted at different RPM and mass flow rate of air S. No. Engine Speed (rpm) Mass flow rate of air mh (Kg/s) Heat to be extracted Q (J/s) 1 1047 0.00768 556.33 2 1171 0.00867 628.05 3 1325 0.00953 690.35 4 1333 0.00958 693.97 5 1347 0.00963 711.27 6 1570 0.01116 833.20 7 1578 0.01123 838.43 8 1913 0.01403 1056.73 9 2122 0.01541 1160.68 10 2397 0.01770 1384.84 11 2706 0.02345 1979.65 12 2760 0.02453 2115.71 13 2834 0.02488 2162.07 14 2891 0.02618 2275.04 15 3487 0.04343 4395.12 16 3503 0.04618 4952.80 17 3574 0.04633 4977.69 18 4377 0.05867 6759.96 19 5091 0.06400 7779.84 20 6010 0.06560 7974.34 3.2 Calculation for the volume of heat exchanger core on the basis of heat to be extracted at different speeds of the vehicle and RPM of engine. For designing or predicting the performance of a heat exchanger it is necessary that the total heat transfer may be related with its governing parameters: Let, o o Mass flow rate of air, Kg/s Specific heat of fluid at constant pressure, J/Kg C temperature of fluid, C temperature drop or rise of a fluid across the heat exchanger o p m c t t = = = = Subscripts h and c refer to the hot and cold fluids respectively; subscripts 1 and 2 correspond to the inlet and outlet conditions respectively.
8.
International Journal of
Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 3, May - June (2013) © IAEME 8 Assuming that there is no heat loss to the surroundings and the changes in potential energy and kinetic energy are negligible. From the energy balance in a heat exchanger Heat given up by the hot fluid, 1 2( )h ph h hQ m c t t= − Heat picked up by the cold fluid, 2 1( )c pc c cQ m c t t= − Total heat transfer rate in the heat exchanger, mQ UAθ= Where, U = Overall heat transfer coefficient between the two fluids, A = Effective heat transfer area, and mθ =Logarithmic mean temperature difference (LMTD) The expression for LMTD is essentially valid for single-pass heat exchangers. The analytical treatment of multiple pass shell and tube heat exchangers and cross-flow heat exchangers is much more difficult than single pas cases; such cases may be analyzed by using the following equation: mQ UAFθ= Where F is the correction factor 3.3 Calculation of mass flow rate and temperature of cold air into the heat exchanger Let, o o mass flow rate of air coming from the atmosphere, Kg/s mass flow rate of air automotive air conditioning system, kg/s specific heat of atmospheric air, J/Kg C specific heat of aut o atm aac patm paac m m c c = = = = o o o omotive ac system air, J/Kg C temperature of atmospheric air, C temperature of automotive ac system air, C atm aac t t = = According to energy balance: o ( ) ( ) o atm aacpatm atm c paac c aacm c t t m c t t− = − Here, the mass flow rate of cold air into the intercooler is calculated by accelerating the vehicle at constant rate in the same gear (3rd gear) so that the engine RPM and vehicle speed increases proportionally. The mass flow rate of conditioned air is considered constant. Let, the cross-sectional area of the intercooler facing front is 0.25 m2 , the density of air at normal temperature (20 o C), pressure is 1.2 kg/m3 and the required mass flow rate of air coming from automotive AC system is 0.6 Kg/s when the duct exit area is 0.1 m2 and the speed of air coming out of it is 5 m/s at a temperature of 15 o C, therefore the mass flow rate of mixed air (atmospheric air and the air coming from automotive AC system) entering into the intercooler can be calculated as follows: speed of vehicle x cross-sectional area of intercooler x density, kg/s o atmm =
9.
International Journal of
Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 3, May - June (2013) © IAEME 9 Table 3.3: Mass flow rate and temperature of cold air entering into intercooler S. No. Engine (rpm) Vehicle Speed (m/s) o atmm oo o c atm aacm m m= + ct 1 1047 0 0 0.6 15 2 1171 1.33 0.40 1.00 16.99 3 1325 4.17 1.25 1.85 18.39 4 1333 4.71 1.41 2.01 18.50 5 1347 5.32 1.60 2.20 18.61 6 1570 7.00 2.10 2.70 18.88 7 1578 7.28 2.18 2.78 18.93 8 1913 9.80 2.94 3.54 19.15 9 2122 11.2 3.36 3.96 19.24 10 2397 12.6 3.78 4.38 19.31 11 2706 14.00 4.20 4.80 19.38 12 2760 14.56 4.37 4.97 19.40 13 2834 15.40 4.62 5.22 19.42 14 2891 15.96 4.79 5.39 19.45 15 3487 18.20 5.46 6.06 19.50 16 3503 18.76 5.63 6.23 19.52 17 3574 19.60 5.88 6.48 19.54 18 4377 22.40 6.72 7.32 19.59 19 5091 24.64 7.40 8.00 19.63 20 6010 28.00 8.40 9.00 19.67 3.4 Calculation of intercooler core (heat exchanger) dimensions The required volume of cross-flow heat exchanger core (denoted as V) with both fluids unmixed for different amounts of heats to be extracted at different RPMs of the engine and at different speeds of the vehicle are as follows: Table 3.4: Required surface area of the intercooler core to reject heat S. No RPM 1ht 2ht 1ct 2ct mθ F Q A V 1 1047 92.44 20 15.00 15.92 26.22 0.976 556.33 0.4347 0.0005 2 1171 92.44 20 16.99 17.61 22.35 0.974 628.05 0.5770 0.0007 3 1325 92.44 20 18.39 18.76 18.85 0.973 690.35 0.7527 0.0009 4 1333 92.44 20 18.50 18.84 18.52 0.974 693.97 0.7694 0.0010 5 1347 93.86 20 18.61 18.93 18.44 0.974 711.27 0.7920 0.0010 6 1570 94.66 20 18.88 19.18 17.66 0.970 833.20 0.9727 0.0012 7 1578 94.66 20 18.93 19.23 17.47 0.969 838.43 0.9905 0.0012 8 1913 95.32 20 19.15 19.44 16.70 0.963 1056.73 1.3141 0.0016 9 2122 95.32 20 19.24 19.53 16.30 0.959 1160.68 1.4850 0.0019 10 2397 98.24 20 19.31 19.62 16.46 0.952 1384.84 1.7675 0.0022 11 2706 104.42 20 19.38 19.79 17.09 0.928 1979.65 2.4964 0.0031 12 2760 106.25 20 19.40 19.82 17.27 0.924 2115.71 2.6516 0.0033 13 2834 106.90 20 19.42 19.83 17.26 0.924 2162.07 2.7113 0.0034 14 2891 106.90 20 19.45 19.87 17.08 0.917 2275.04 2.9051 0.0036 15 3487 121.20 20 19.50 20.22 18.93 0.811 4395.12 5.7257 0.0072 16 3503 127.25 20 19.52 20.31 19.69 0.761 4952.80 6.6107 0.0083 17 3574 127.44 20 19.54 20.31 19.57 0.753 4977.69 6.7557 0.0084 18 4377 135.22 20 19.59 20.51 20.29 0.749 6759.96 8.8963 0.0111 19 5091 141.56 20 19.63 20.60 20.83 0.747 7779.84 9.9997 0.0125 20 6010 141.56 20 19.67 20.55 20.44 0.746 7974.34 10.459 0.0131
10.
International Journal of
Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print), ISSN 0976 – 6359(Online) Volume 4, Issue 3, May - June (2013) © IAEME 10 From the results shown in the table 3.4, it has been concluded that the maximum volume of the core of heat exchanger required is 0.0131 m3 , rejecting the heat at maximum speed of engine. As it has already been discussed in the previous section that the required cross-sectional area of the heat exchanger is 0.25 m2 , so the required dimensions of the intercooler core will be as length (l1) =0.5 m, breadth (l3) =0.5 m and thickness (l2) =0.0524 m. 4. CONCLUSION When the normal intercooler is used, the temperature of air in the intake manifold ranges from 70-80 o C in the pressure range of 99-165 KPa and in this range the density of air ranges between 1.0053 Kg/m3 to 1.6281 Kg/m3 . By adopting the above specified dimensions of the intercooler (heat exchanger) core, it will be possible to supply the air to the intake manifold at the temperature 20 o C. With the application of the designed dimensions of the intercooler core, the temperature in the intake manifold will remain 20 o C and the pressure ranges from 99-165 KPa and in this range of temperature and pressure, the density of air will range from 1.1769-1.9614 Kg/m3 . The result shows that there is high gain in the mass flow rate of air in to the engine on using the above designed intercooler. Due to this more oxygen will be available in the combustion chamber to burn the fuel. Increasing the oxygen content with the air leads to faster burn rates and the ability to control exhaust emissions. Added oxygen in the combustion air offers more potential for burning fuel. REFERENCES [1] Mohd Muqeem, Turbocharging with Air Conditioner Assisted Intercooler, IOSR Journal of Mechanical and Civil Engineering (IOSRJMCE) ISSN: 2278-1684 Vol. 2, Issue 3, PP 38-44, 2012. [2] Mohd Muqeem and Dr. Manoj Kumar, “Turbocharging of IC Engine: A Review”, International Journal of Mechanical Engineering and Technology (IJMET), Volume 4, Issue 1, 2012, pp. 142 - 149, ISSN Print: 0976 – 6340, ISSN Online: 0976 – 6359. [3] Flynn, P.F. Turbocharging Four-Cycle Diesel Engines: SAE paper 790314, SAE trans., vol. 88, 1979. [4] Watson, N. and Janota, M.S. Turbocharging the Internal Combustion Engine, Wiley- Interscience Publications, John Wiley, New York, 1982. [5] Gyssler, G. Problems Associated with Turbocharging Large Two-Stroke Diesel Engines Proc. CIMAC, paper B.16, 1965. [6] Bhinder, F.S. Supercharging Compressors-Problems and Potentials of the Various Alternatives, SAE paper 840243, 1984. [7] John B. Heywood. Internal Combustion Engine Fundamentals, McGraw-Hill series in mechanical engineering. [8] Holman J.P., Heat Transfer, 10th Edition, Tata McGraw Hill Education Private Limited, New Delhi. [9] Kays, W.M. and A.L. London. Compact Heat Exchangers, 2nd Edition, New York, McGraw Hill, 1964. [10] Pundlik R. Ghodke and Dr. J. G. Suryawanshi, “Advanced Turbocharger Technologies for High Performance Diesel Engine - Passanger Vehicle Application”, International Journal of Mechanical Engineering & Technology (IJMET), Volume 3, Issue 2, 2012, pp. 620 - 632, ISSN Print: 0976 – 6340, ISSN Online: 0976 – 6359.
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