Design and Simulation of Two Stroke Engines

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Design and Simulation of Two-Stroke Engines 2.53 R.S. Benson, "Influence of Exhaust Belt Design on the Discharge Process in Two- Stroke Engines," Proc. I. Mech. E., Vol 174, No 24, 1960, p713. 2.54 W.A. Woods, "On the Formulation of a Blowdown Pulse in the Exhaust System of a Two-Stroke Cycle Engine," Int. J. Mech. ScL, Vol 4, 1962, p259. 2.55 W.L. Cahoon, "Unsteady Gas Flow Through a Naturally Aspirated Two-Stroke Internal Combustion Engine," Ph.D. Thesis, Dept. Mech. Eng., The Queen's University of Belfast, Nov. 1971. 2.56 F.J. Wallace, R.W. Stuart-Mitchell, "Wave Action following the Sudden Release of Air Through an Engine Port System," Proc. I. Mech. E., Vol IB, 1953, p343. 2.57 F.J. Wallace, M.H. Nassif, "Air Flow in a Naturally Aspirated Two-Stroke Engine," Proc.I.Mech.E., Vol 168, 1954, p515. 2.58 W.J.D. Annand, "Heat Transfer in the Cylinders of Reciprocating Internal Combustion Engines," Proc.I.Mech.E., Vol 177, 1963, p973. 2.59 G.P. Blair, W.L. Cahoon, C.T Yohpe, "Design of Exhaust Systems for V-twin Motorcycle Engines," SAE Paper No. 942514, Society of Automotive Engineers, Warrendale, PA, 1994. 2.60 G. Woschni, "A Universally Applicable Equation for Instantaneous Heat Transfer in the Internal Combustion Engine," SAE Paper No. 670931, Society of Automotive Engineers, Warrendale, PA, 1967. 2.61 D.D. Agnew, "What is Limiting Engine Air Flow. Using Normalised Steady Air Flow Bench Data," SAE Paper No. 942477, Society of Automotive Engineers, Warrendale, PA, 1994. 2.62 D.E. Winterbone, R.J. Pearson, "A Solution of the Wave Equation using Real Gases," Int.J.Mech.ScL, Vol 34, No 12, 1992, pp917-932. 2.63 R.J. Pearson, D.E. Winterbone, "Calculating the Effects of Variations in Composition on Wave Propagation in Gases," Int.J.Mech.ScL, Vol 35, No 6, 1993. 2.64 J.F. Bingham, "Unsteady Gas Flow in the Manifolds of Multicylinder Automotive Engines," Ph.D. Thesis, Dept. Mech. Eng., The Queen's University of Belfast, Oct. 1983. 2.65 G.P. Blair, S.J. Kirkpatrick, R. Fleck, "Experimental Evaluation of a ID Modelling Code for a Pipe Containing Gas of Varying Properties," SAE Paper No. 950275, Society of Automotive Engineers, Warrendale, PA, 1995. 2.66 G.P. Blair, S.J. Kirkpatrick, D.O. Mackey, R. Fleck, "Experimental Evaluation of a ID Modelling Code for a Pipe System Containing Area Discontinuities," SAE Paper No. 950276, Society of Automotive Engineers, Warrendale, PA, 1995. 196
s in Two- stem of a :>ke Inter- "niversity elease of 3. Engine," Chapter 2 - Gas Flow through Two-Stroke Engines Appendix A2.1 The derivation of the particle velocity for unsteady gas flow This section owes much to the text of Bannister [2.2], which I found to be a vital component of my education during the period 1959-1962. His lecture notes have remained a model of clarity and a model of the manner in which matters theoretical should be written by those who wish to elucidate others. The exact differential equations employed by Earnshaw [2.1] in his solution of the propagation of a wave of finite amplitude are those established using the notation of Lagrange. Fig. A2.1(a) shows a frictionless pipe of unit cross-section, containing gas at reference conditions of po and po- The element AB is of length, dx, and at distance, x, from an origin of time and distance. Fig. A2.1(b) shows the changes that have occurred in the same element AB by time, t, due to the influence of a pressure wave of finite amplitude. The element face, A, has now been displaced to a position, L, farther on from the initial position. Thus, at time t, the distances of A and B from the origin are no longer separated by dx but by a dimension which is a function of that very displacement; this is shown in Fig. A2.1(b). The length of the f element is now 1 + — dx. The density, p, in this element at this instant is related by the fact dx) that the mass in the element is unchanged from its initial existence at the reference conditions and that the pipe area, A, is unity; _c D5 o o \J < ^ > p0Adx = pA 1 + — dx (A2.1.0) •w W < ^ > ^. ^ A B gas properties y R f\ reference po To / | L+dx+ *P= dx dx pipe area=unity \J (a) initial conditions B P+^dx dX (b) after time t Fig. A2.1 Lagrangian notation for a pressure wave. 197
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Design and Simulation of Two-Stroke
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A Second Mulled Toast When as a stu
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Acknowledgments As explained in the
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Table of Contents Nomenclature xv C
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Table of Contents 2.10.1 Flow at pi
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Table of Contents 3.5.3.1 The use o
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Table of Contents 6.1.3 The effect
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Nomenclature NAME SYMBOL UNIT (SI)
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speed of rotation speed of rotation
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attenuation or transmission loss wa
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Page 168 and 169: Design and Simulation of Two-Stroke
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Design and Simulation ofTwo'Stroke
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Chapter 4 Combustion in Two-Stroke
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Chapter 4 - Combustion in Two-Strok
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a stratilpl o tions to ivior. If m
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CD 30 -, W 20 - LU CO iS _J LU OC 1
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181 also x3 = — = 0.905 x6 = 2.17
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to be cur .3.20) .3.21) .3.22) for
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3.23) com- :on is hhas has a /eng-
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stroke .3.29) mean me to 3land ssio
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a LU z: en 3 CO a LU z EC D m O ho
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CD 1.2 -i 1.0 - di „„ LU 0.8 cc
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CO —> 111" cc LU < LU _J LU CC £
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Combustion in compression-ignition
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stroke ari more often lseful lental
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lat the ssi ;tribu- ELEVATION VIEWS
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CYLINDER HEAD TYPE IS CENTRAL BORE,
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CO E 50 40 - O O _i Hi > I CO 30 Z)
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CURRENT INPUT DATA FOR 2-STROKE 'SP
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Cylin- PP £ Pa- tics of Paper Chap
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vfitro- ;titi >tants 1970. i(In- Ch
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£2 = Pi P2 I Pi J Chapter 4 - Comb
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CHAINSAW AT 9600 rpm. Chapter 4- Co
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LLI •z. O N -z. 0.21 -, 0.20 DC 0
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Chapter 7 Reduction of Fuel Consump
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Chapter 7 • Reduction of Fuel Con
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Chapter 7 - Reduction of Fuel Consu
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^ s C£ Q 2^ E Q. Q_ z' o ISSI HCEM
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o > z~ Q w CO UJ w g x O z o z o m
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0.35 • 0.34 LU ° 0.33 - c 03 DC
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§ 2000
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y, ,6 Chapter 7 - Reduction of Fuel
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Chapter 7- Reduction of Fuel Consum
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INLET FOR r AIR AND FUEL Chapter 7
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Chapter 8 Reduction of Noise Emissi
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Chapter 8 • Reduction of Noise Em
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Chapter 8 - Reduction of Noise Emis
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1 Chapter 8 - Reduction of Noise Em
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• • / . • Appendix Listing of
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Active radical (AR) combustion and
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initial conditions, assumptions reg
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in two-stroke engine (schematic dia
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exhaust timing control valve, effec
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I Exhaust emissions/exhaust gas ana
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Exhaust systems (continued) untuned
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gas constant/universal gas constant
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in crankcase heat transfer analysis
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Mercury Marine air-assisted fuel in
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I PISTON POSITION (computer program
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Pressure wave reflection (in pipes)
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local acoustic velocity, 60 local M
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Simulation, engine See Computer mod
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temperature vs. crankshaft angle (c
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work per thermodynamic (Otto) cycle
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