Design and Simulation of Two Stroke Engines

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Design and Simulation of Two-Stroke Engines LU GC a: LU CL LU (a) one supplier pipe to the branch .I1_ T 2._ Ta"^ T01 ^ T 02 ISENTROP CL INE ) r 1|2/ , ^3 . yPs1 yps3 - - T03 ENTROPY (a) two supplier pipes to the branch /% 2 74 The temperature-entropy characteristics. (b)for two supplier pipes, where the assumption is that the superposition pressure in the faces of pipes 1 and 2 are identical, the equations for pipes 2 and 3 become: vG52 Ps2 = P02( X i2 + X r2 " *) c s2 = G 52 a 02( X i2 " X r2) m 2 = Ps2 A 2 c s2 (2.14.10) ^G51 Ps3 = P0e3( X i3 + X r3 " ! ) c s3 = G 51 a 0e3( X i3 " X r3) m 3 = Ps3 A 3 c s3 (2.14.11) The First Law of Thermodynamics is, where the local work, heat transfer and system state changes are logically ignored, and the ho term is the stagnation specific enthalpy: m l h 01 + m 2 h 02 + m 3 h 03 = ° 120 (2.14.12)
Chapter 2 - Gas Flow through Two-Stroke Engines This single line expression is the one to be used if the approximation is made that T02 equals T03 for a single supplier pipe situation; it is also strictly correct for a two supplier pipes model. To solve without that assumption, the equation must be split into two and analyzed specifically for the separate flows from pipe 1 to 2 and from pipe 1 to 3. The reference densities in question emanate from this step, as shown below. The normal isentropic expression for the reference densities is expressed as: n - PO n - PO n - _P-0_ P01 " R~T~ P ° 2 " R~T~~ P ° 3 " i T (2.14.13) KJIQJ K 2H)2 K 3 X 03 but should gas be entering pipes 1 or 2 as a result of a non-isentropic process then these become for pipes 2 and 3, The stagnation enthalpies appear as: n - Po n - Po P0e2 - P0e3 " (2.14.14) K 1 e2 02 K 1 e3 03 (a) for one supplier pipe the stagnation enthalpies are, h _ G 51 a 01 X sl + c sl h _ G 5e2 a e2 X s2 + c s2 h _ G 5e3 a e3 X s3 + c s3 (2.14.15) Zd Z* Zt (b)for two supplier pipes, as with continuity, only the statement for stagnation enthalpy for pipe 2 is altered, hQ2 = G 52 a 02Xs 2 2 + CS 2 2 (21416) The pressure loss equations first presented in Eq. 2.14.2 devolve to: (a) for one supplier pipe for flow from pipe 1 to pipes 2 and 3, *s I.6810 „ ^ 1.6 8,c. CL12 = 1-6 - —f- CL13 = 1.6 - —ii (2.14.17) 167 167 Pofx^ 71 - Xs G 2 7e2 ) = CL12ps2cs 2 2 pofx^ 71 - Xs G 3 7e3 ) = CL13ps3c 2 3 (2.14.18) 121
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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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Design and Simulation ofTwo-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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• • / . • 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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Roots blower in turbocharged/superc
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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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Design and Simulation of Two Stroke Engines

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