• Journal of the Korean Society of Fisheries and Ocean Technology
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• v.32 no.3
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• pp.310-315
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• 1996

엔진 배기가스의 동력과 유량이 배기행정의 직전 단계에서 관찰되었다. 배기가스 양을 적당히 조정함으로써 터보 과급의 입구 압력을 증가시킬 수 있었으며 엔진의 흡기, 소기 및 배기과정에서 가스질량과 엔진의 동력, 그리고 터보과급 효과도 감소하였다. 터보 과급장치를 기하학적으로 적절화시킴으로써 싸이클의 동기화 및 동력의 효율이 고려된 열교환 과정의 효율 기준도 제기되었으며 디젤엔진의 연소싸이클을 재수정하는 과정과 터빈의 동역학적 특성도 제시되었다.

• Proceedings of the Korean Society for Noise and Vibration Engineering Conference
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• 2007.11a
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• pp.913-917
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• 2007

The turbocharger for a vehicle is consisting of a centrifugal compressor and turbine. These compressor and turbine are vibrating and emitting noises through the T/C body, exhaust system (Catalyst, Bellows, Pipe, etc) and Intake system (Hoses, Intercooler pipes, Intercooler) as rotating. A turbocharger cold test bench is constructed to reduce these noises, especially for the purpose of realizing transient operating environment and oil temperature control to simulate the vehicle operating characteristics with intake system and exhaust system. This research laid the groundwork to develop a lower noise level T/C through understanding the mechanism of the noise source of T/C.

• Journal of the korean Society of Automotive Engineers
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• v.5 no.2
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• pp.1-14
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• 1983

총차량 중량이 15ton이 넘는 대형 트럭의 경우 1970년도에 18%에 불과하던 터보 챠저엔진의 비율은 점차 증가하여 1977년에 42%에 달하였고 1990년도에는 75%까지 증가할 것으로 예상 된다. 또한 현재 터보 챠저엔진의 BMEP는 11.2kg/$cm^{2}$, after cooled엔진은 13.6kg/$cm^{2}$에 이르나 앞으로는 after cooled엔지의 BMEP는 13-17kg/$cm^{2}$로 증대할 것이다. 그러나 터보 챠저엔진의 최대의 단점은 저속에서의 낮은 boost압력과 고속에서의 over boost압력을 갖는다는 것이나, 현재까지는 뚜렷한 해결책을 찾지 못하고 있는 실정이다. 따라서 1980년대에는 현재 사용되고 있는 터보 챠저나 이를 개선한 고성능 터보챠저를 부 착한 엔진이나 after cooled엔진이 주로 사용될 것으로 보인다. 앞으로 터보 챠저가 대형트럭용 엔진에 더욱 확대 사용되고 또 소형 디이젤 엔진이나 가솔린 엔진에서도 이용되기 위해서는 (1) 저속에서의 boost압력 증대 (2) 압력비의 증대 (3) 압축기 사용 flow range의 확대 (4) 소형 터보 챠저의 개발 등이 수반되어야 하며 이외에도 배기가스의 효율적인 에너지전달, 콤푸레샤 효율의 증대, 굉음의 감소, 저렴한 터보 챠저 및 after cooler의 개발, 터보 챠저의 소형화 등이 이루어져야 할 것이다.

• Transactions of the Korean Society of Mechanical Engineers
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• v.19 no.2
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• pp.580-590
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• 1995

To design and develop a turbocharged engine, ti needs that many study must be preceded about the characteristics of engine performance. Especially, a basic data about deciding target power is urgently needed for which is practically useful for engine design. The power output of turbo-charged engine is dominated by engine speed, displacement, compression ratio, air fuel ratio and charge pressure ratio. Therefore, the independent effect of these factors on power output was clarified from experiment, and the experimental equation to predict the power was founded from there results. The predicted power output from the experimental equation was well coincided with power measured through experiment.

• Journal of the Korea Academia-Industrial cooperation Society
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• v.22 no.2
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• pp.386-391
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• 2021

Turbocharging is becoming a key technology for both diesel and gasoline engines. Regarding gasoline engines, turbocharging can help reduce carbon dioxide (CO2) emissions when used in conjunction with other technologies. This paper presents measurements of the turbine efficiency of pulsating flow in a twin-scroll turbocharger for gasoline engines. A cold gas test bench with a pulse generator was manufactured. The turbine efficiencies were calculated using the measured data of the instantaneous pressure and temperature of the inlet and exit of the turbine. The measurements were carried out at turbine speeds from 60,000 to 100,000 rpm under a pulsating flow of 25.0 Hz and 33.0 Hz. The turbine efficiencies ranged from 0.517 to 0.544. At the pulse frequency, 33.3 Hz, the variations in efficiency were 7.7% and 2.6% at turbine speeds of 60,000 rpm and 100,000 rpm, respectively. The turbine efficiency of the pulsating flow compared to those of steady flow was 7.0% and 3.0% lower at a turbine speed of 60,000 rpm and 100,000 rpm, respectively. The pulsating flow deteriorated the turbine efficiency, but the effects of pulsating flow decreased with increasing turbine speed.

• Proceedings of the Korean Society of Marine Engineers Conference
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• 2005.06a
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• pp.92-100
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• 2005

Since HiMSEN H21/32, a new medium speed diesel engine of Hyundai's own design, was introduced in 2001, Hyundai has added new models of H25/33 and H17/28 into HiMSEN engine family. These two new engines take after faithfully to the original HiMSEN concept of a PRACTICAL engine by Hi-Touch and Hi-Tech. The prototype of H25/33 was developed jointly with Rolls Royce Bergen originally and also introduced in 2001. But most of the engine design have been changed by Hyundai for the commercial versions to be a member of HiMSEN family, which has little interchangeability with the prototype. H17/28 is now under development as the smallest size of the family. This new engine also has the longest stroke of a class engine, which has been proven as the best basis for future environmental challenge. The higher compression ratio of 17 and optimized Miller Timing with Simplified pulse turbocharging system applied all HiMSEN engines as which showed the most practical solution against current heavy fuel combustion issues for the time being before introducing digital control system. This paper describes the design and development of these new HiMSEN engines and also reviews the service experiences of H21/32 and H25/33, which launched successfully.

• Tribology and Lubricants
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• v.32 no.6
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• pp.183-188
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• 2016

Engine oil plays an important role in the mechanical lubrication and cooling of a vehicle engine. Recently, engine development has focused on the adoption of gasoline direct injection (GDI) and turbocharging methodology to achieve high-power and high-speed performance. However, oil dilution is a problem for GDI engines. Oil dilution occurs owing to high-pressure fuel injection into the combustion chamber when the engine is cold. The chemical components of engine oil are currently developed to accommodate gasoline fuel; however, bio-alcohol mixtures have become a recent trend in fuel development. Bio-alcohol fuels are alternatives to fossil fuels that can reduce vehicle emissions levels and greenhouse gas pollution. Therefore, the chemical components of engine oil should be improved to accommodate bio-alcohol fuels. This study employs a 2.0 L turbo-gas direct injection (T-GDI) engine in an experiment that dilutes oil with fuel. The experiment utilizes a variety of fuels, including sub-octane gasoline fuel (E0) and a bio-alcohol fuel mixture (Ethanol E3~E7). The results show that the lowest amount of oil dilution occurs when using E3 fuel. Analyzing the diluted engine oil by measuring density and moisture with respect to kinematic viscosity shows that the lowest values of these parameters occur when testing E3 fuel. The reason is confirmed to influence the vapor pressure of the low concentration bio-alcohol-fuel mixture.

• Steel and Composite Structures
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• v.43 no.5
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• pp.523-532
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• 2022

Turbocharger technology is one of the ways to survive in a competitive market that is facing increasing demand for fuel and improving the efficiency of vehicle engines. Turbocharging allows the engine to operate at close to its maximum power, thereby reducing the relative friction losses. One way to optimally understand the behavior of a turbocharger is to better understand the heat flow. In this paper, a 1.7 liter, 4 cylinder and 16 air valve gasoline engine turbocharger with compressible, viscous and 3D flow was investigated. The purpose of this paper is numerical investigation of the number of heat transfer in gasoline engines turbochargers under 3D flow and to examine the effect of different types of coatings on its performance; To do this, modeling of snail chamber and turbine blades in CATIA and simulation in ANSYS-FLUENT software have been used to compare the results of turbine with experimental results in both adiabatic and non-adiabatic (heat transfer) conditions. It should be noted that the turbine blades are modeled using multiple rotational coordinate methods. In the experimental section, we simulated our model without coating in two states of adiabatic and non-adiabatic. Then we matched our results with the experimental results to prove the validation of the model. Comparison of numerical and experimental results showed a difference of 8-10%, which indicates the accuracy and precision of numerical results. Also, in our studies, we concluded that the highest effective power of the turbocharged engine is achieved in the adiabatic state. We also used three types of SiO₂, Sic and Si₃N₄ ceramic coatings to investigate the effect of insulating coatings on turbine shells to prevent heat transfer. The results showed that SiO₂ has better results than the other two coatings due to its lower heat transfer coefficient.

• Journal of the Korea Academia-Industrial cooperation Society
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• v.18 no.1
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• pp.585-591
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• 2017

Turbocharging is widely used in diesel and gasoline engines as an effective way to reduce fuel consumption. But turbochargers have turbo-lag due to mechanical friction losses. Bearing friction losses are a major cause of mechanical friction losses and are particularly intensified in the lower speed range of the engine. Current turbochargers mostly use oil bearings (two journal bearings and one thrust bearing). In this study, we focus on the bearing friction in the lower speed range. Experimental equipment was made using a drive motor, load cell, magnetic coupling, and oil control system. We measured the friction losses of the turbocharger while considering the influence of the rotation speed, oil temperature, and pressure. The friction power losses increased exponentially when the turbocharger speed increased.