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온돌의 연탄개스유량에 관한 연구 (2) (유도연관내의 개스유동)
민만기,정재선,Min, Man-Gi,Jeong, Jae-Seon 대한설비공학회 1975 설비저널 Vol.4 No.4
By the experiment of a model Ondol heating system gas flow characteristics in a briquette flue tube was investigated. As a heat source electric heater was used, which renders steady flow condition of air. working fluid. It was observed that the flow augumentation may be obtained by increasing the vertial elevation of the flue tube, namely increase in the tube length or increase in the tube inclination, and the gas temperature at the tube entrance Among several factors which augument the flow rate slope of the flue tube has the most striking effect and then the temperature of gas entering the tube. Increase in length of the tube also auguments the flow but the rate of augumentation is so small that it gives little assistance to improvement of the flow The flow in a briguette flue gas does not essentially satisfy the one dimensional steady flow assumption. It is also observed that the flow begins to accompany irregular velocity fluctuation as inclination of the tube increases.
온돌의 연탄개스유량에 관한 연구(1) (함습저온열기류의 굴뚝통풍력)
민만기,Min Man-Ki 대한설비공학회 1975 설비저널 Vol.4 No.2
Natural draft and flow which low temperature moist gas produces in the chimney of an Ondol heating system were numerically analysed. Among several factors involved inlet gas temperature has the strongest influence on the chimney performance and then next specific humidity of the gas. Thermal conductivity of the chimney wall, however, has little influence on the performance of such a low temperature chimney. Under given flow conditions there exists an optimum chimney height which gives a maximum flow rate for a given chimney diameter. This optimum value of chimney height inereases with increase in chimney diameter, inlet gas temperature and specific humidity.
민만기,김주균,Min Man-Ki,Kim Joo-Kyoon 대한설비공학회 1978 설비저널 Vol.7 No.1
At Grashof numbers $10^{10},\;5{\times}10^{10}$, and $10^{11}$ nonlinear partial differential equations for two dimensional thermal circulation of air in a rectangular enclosure heated from below are solved numerically by finite difference explicit methood in time-dependent form. Two vertical walls and ceiling are held at low temperature and floor at high temperture. Results are compared with From's numerical solutions at $10^9{\lesssim}\;N_{Gr}\;<10^{13}$. The effective draft temperature fields are also obtained to examine cold draft problem, there included a line of constant effective draft temperature $-1.667^{\circ}C$ which is essentially Houghten's $80\%$ comfort data.
민만기,Min, Man-Ki 대한설비공학회 1983 설비저널 Vol.12 No.4
Cyclic heating performance of 3 ton air-to-air unitary heat pump installed in a residence in the Washington, D.C. area was determined by applying the bin method to field test result. Cyclic degradation coefficient Cn of heat pump may be expressed in terms of heating load factor HLF as the following : $$C_D=\frac{1-HLF^m}{1-HLF}$$ where $$C_D{\ge}m$$ The less is the value of exponent m, the better is, the performance of a heat pump, depending upon the heat pump design.
민만기,이승우,Man Man-Ki,Lee Seung Woo 대한설비공학회 1983 설비저널 Vol.12 No.4
Two-dimensional jet flows into a couple of confined rectangular enclosures such as an Ondol flue channel and their flow distributions were analyzed by numerical graphics : rectangular space in one enclosure is vacated and the other has 8 rectangular small posts. Both enclosures have a protruded inlet nozzle and on outlet on its center line. Steady state incompressible laminar viscous flow was assumed. The primitive forms of Navier-Stokes equations and continuity equation in a cartesian coordinate system were solved numerically by the Marker and Cell method for Reynolds numbers of 5, 10, 20, 30 and 40. From the numerical graphics it was found that the flow regions in both enclosures were devided into tow parts ; one part was the jet flow localized in a narrow center region of the enclosure and the other part was the very slow recirculating flow occupying the rest of the flow region in the enclosures. However there were a little differences in the shapes of jet flow in both enclosures for Reynolds numbers of 5 and 10 and also in the shapes of recirculating flows in both enclosures for all Reynolds number. Also it was found that waving flow appeared right before the outlet at Reynolds number of 20 and more.