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45injection-fuel ratio increases gradually. However, if a lot mass of water is injected, abulk of water in a cylinder will be a large amount and low temperature may absorbthe energy from the gas burned and decrease its temperature. The energy conversationto work in a cylinder will be less or almost equal value.4.5.2 Performance of water injection model at different equivalence ratio ( φ )This simulation test was run at 2,000 rpm, compression ratio of 0.8, waterinjection-fuel ratio ( XW) of 5 through 40 and the water injection duration angle of 10CA while using the difference compression ratios ( r) , varied from 0.8, 0.9, 1.0, 1.1and 1.2, respectively.1.1501.100IMEP (MPa)1.0501.0000.9500.900Eqivalence ratio 0.8Eqivalence ratio 0.9Eqivalence ratio 1.0Eqivalence ratio 1.1Eqivalence ratio 1.25 10 15 20 25 30 35 40Molar water injection -fuel ratio (Nw/Nf)FIGURE 4-23 IMEP- Molar water injection-fuel ratio with Equivalence ratioThermal efficiency (%)444240383634323028262422Eqivalence ratio 0.8 Eqivalence ratio 0.9Eqivalence ratio 1.0 Eqivalence ratio 1.1Eqivalence ratio 1.25 10 15 20 25 30 35 40Molar water injection -fuel ratio (Nw/Nf)FIGURE 4-24 Thermal efficiency- Molar water injection-fuel ratio withEquivalence ratio
46According to Figure 4-23 and Figure 4-24, there results help to predict thelimitation of maximum performances to simulate a spark ignition engine which variedequivalence ratio while molar water injection-fuel ratio is increased. The indicatedmean effective pressure (IMEP) and thermal efficiency curves are almost the same foreach equivalence ratio. However, it is not much difference in both curves at the 20 ofmolar water injection-fuel ratio, mass of water injection see Table 4-2. The both casesare approximately value of 50,000 Pa and 3% of IMEP and thermal efficiencyrespectively which is only fluctuate slightly around this value.Theoretically, In this case, a 0.8 value of equivalence ratio was chosen forgasoline that may be optimized value for this simulation which gives IMEP and thethermal efficiency and maximum efficiency occurs at stoichiometric. But, ifequivalence ratio is increased, which give the mass of fuel decreased as followingfuel-air ratio. However, if the molar water injection-fuel ratio increases gradually, alot mass of water is injected, the water in a cylinder will be a large amount, a bulk ofwater at low temperature may absorb the energy from the burned gas and decrease itstemperature. The energy conversation to work will be less or almost the same with theprevious results.4.5.3 Performance of water injected at different engine speed (RPM)This simulation test was run at compression ratio 10, equivalence ratio of 0.8,water injection-fuel ratio ( XW) of 5 through 40 and the water injection duration angleof 10 CA while using different engine speed (RPM), varied from 1000, 1500, 2000,2500 and 3000 respectively.1.100IMEP (MPa)1.0501.0000.9500.900RPM 1000 RPM 1500RPM 2000 RPM 2500RPM 30005 10 15 20 25 30 35 40Molar water injection -fuel ratio (Nw/Nf)FIGURE 4-25 IMEP- Molar water injection-fuel ratio with Engine speed
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ANALYSIS OF WATER INJECTION INTO HI
Page 3 and 4:
Thesis CertificateThe Graduate Coll
Page 5 and 6:
ชื่อ : นายปรม
Page 7 and 8: TABLE OF CONTENTSPageAbstract (in E
Page 9 and 10: LIST OF TABLESTablePage3-1 Solution
Page 11 and 12: LIST OF FIGURES (CONTINUED)FigurePa
Page 13 and 14: LIST OF ABBREVIATIONS, SYMBOLS AND
Page 15 and 16: CHAPTER 1INTRODUCTION1.1 Background
Page 17 and 18: 31.6.6 Water injected is assumed to
Page 19 and 20: 6for these working fluid models can
Page 22 and 23: CHAPTER 3METHODOLOGY FOR ANALYSIS O
Page 24 and 25: 11perform the necessary calculation
Page 26 and 27: 13h b P T w−0.2 0.8 −0.55 0.8=
Page 28 and 29: 15the procedure required Nitrogen(
Page 30 and 31: 171N22 NEq.3-461 1O+2N2 NOEq.3-472
Page 32 and 33: 19∂y1 cy ∂y1 cy ∂y 1 c ∂y 1
Page 34 and 35: 211/2( cy )∂y ∂∂c ∂y∂T
Page 36 and 37: 23[ A][ ∂y/ ∂ P] + [ ∂f / ∂
Page 38 and 39: 25⎛ • • •ln ln ⎞⎛⎞( )
Page 40 and 41: 27( θ= −π)θ>θ bθ>θ W( θ=π
Page 42 and 43: CHAPTER 4RESULTS AND DISCUSSIONThis
Page 44 and 45: 31FIGURE 4-1 Comparison of an actua
Page 46 and 47: 33FIGURE 4-4 Schematic of the port
Page 48 and 49: 35Temperature (K)250023002100190017
Page 50 and 51: 37cylinder temperature. So, a more
Page 52 and 53: 39Thermal efficiency (%)43424140393
Page 54 and 55: 41Theoretically, the high useful co
Page 62 and 63: 49When considering relative tempera
Page 66 and 67: 53When considering relative tempera
Page 70 and 71: CHAPTER 5CONCLUSIONS AND SUGGESTION
Page 72 and 73: REFERENCES1. Ricardo, H.R. The High
Page 74: APPENDIX ADerivative equations of i
Page 78 and 79: 64TABLE A-3 Curve fit coefficients
Page 80 and 81: 66TABLE A-5 Curve fit coefficients
Page 82 and 83: 68The following is the derivative v
Page 84 and 85: 70From the definition of entropyh =
Page 86 and 87: 72• ⎛ ⎞ • ⎛Tb∂u •b∂
Page 88 and 89: 74• ⎛1 ⎞ •∂u ⎛∂ ∂
Page 90 and 91: 76⎛ • • •ln ln ⎞⎛⎞( )
Page 92 and 93: 78The following is the derivative v
Page 94 and 95: 80From the definition of entropy h
Page 96 and 97: 82• ⎛ Tb u ⎞ • • ⎛bmTb
Page 98 and 99: 84• ⎛1 ⎞ • •∂u ⎛ ⎞
Page 100 and 101: 86• • • ⎛ u ⎞bmb( hW ub)
Page 102 and 103: 88Appendix D MATLAB program scripts
Page 104 and 105: 90[thetawater,pTbWQlHl2]=ode45('Rat
Page 106 and 107: 92-0.69353550E-14 -0.14245228E+05 0
Page 108 and 109:
940.21*(1-phi) 0 0]';dcdT=0;else %
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96dfdp=zeros(4,1);dYdT=zeros(11,1);
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98dcdT(1)=-dKdT(1)*sqrt(patm)/K(1)^
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100Iter=Iter+1;[hb,u,v,s,Y,cp,dlvlT
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102yprime(2)=-Const1/cpb/x*Qconvb+v
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104masswaterin=massfuel*mwpmf;% Tot
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106savefile = 'Volume.mat';RTWV=RTW
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108p=pTarray(:,1);T=pTarray(:,2);hc
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110gamma_der_tautau = 0;for i = 1 :
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