Abstract
In this chapter, we present the Newton’s second law and the first principle of thermodynamics as a set or ordinary differential equations for the pressure and the temperature inside the combustion chamber. The solution of these equations with the appropriate initial conditions in each stroke allows to follow the evolution of the thermodynamic properties of the gas mixture performing the engine cycle. The solution of such equations requires the formulation of some additional submodels for the engine: heat transfer through cylinder walls, frictions, working fluid properties, combustion and chemical reactions, and several others. We present those basic models and how are they engaged in the structure of a computer simulation scheme. Special attention is paid to the use of alternative fuels. Detailed chemical reactions for the combustion of such fuels are presented in Appendix F. We include an up-to-date bibliographic survey on advanced submodels that could help the reader to build a particular advanced simulation scheme.
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Notes
- 1.
A single dot denotes the first derivative with respect to time and two dots the second derivative.
- 2.
The pressure exerted by the oil in the crankcase over the bottom part of the piston in taken as negligible.
- 3.
In this and the following equations, the subscript \(u\) refers to the gas mixture before combustion. It is composed of fresh air and fuel, but also of reaction products from the previous cycle. The subscript \(b\) refers to the gas mixture after combustion, i.e., composed of reaction products. As it will be explained later, both mixtures coexist during combustion in the cylinder. This is one of the main identifying characteristics of two-zone simulations.
- 4.
It is considered that the gas mixture leaving the control volume is essentially formed by burned gases: all the fuel was burned out and the fresh mixture leaving out during the overlap period (see below) is negligible. There are no appreciable temperature changes from inside the cylinder to the exhaust duct, so \(\dot{m}_b(h_\mathrm{ex }-h_b)\simeq 0\).
- 5.
Swirl, as defined by Ferguson [13], is the rotational flow within the cylinder about its axis. It is associated to the existence of a nonzero angular momentum of the incoming flow. It is used in the design of some gasoline engines with the aim to boost a fast burn and in diesel engines to provoke a rapid mixing between fuel and air. Squish is the radial gas motion that takes place at the end of the compression stroke when the piston and the cylinder heads approach each other closely. It is especially associated to direct injection engines.
- 6.
The flame front is considered as the forward boundary of the reacting zone.
- 7.
- 8.
In a turbulent flow, Kolmogorov microscale is the eddy size at which molecular viscosity becomes important.
- 9.
Typical values for the quantities which characterize engine flames can be found in [32].
- 10.
The laminar flame speed, \(S_L\), is defined as the velocity relative to and normal to the flame front, with which unburned gas (locally) moves into the front and is transformed into products under laminar flow conditions [34].
- 11.
To have an approximate idea, for \(t\simeq 3\tau _b\), the term in the brackets in Eq. (2.36) is around \(95\,\%\) of \(u_t+S_L\). Typical characteristic speeds, \(u_t\), are in the interval \(2-6\) m/s (except for hydrogen, which are much faster) [25, 46, 47] and laminar flame speeds, \(S_L\), are around one order of magnitude smaller [34] depending on the fuel type, fuel–air ratio, and several other factors.
- 12.
For practical purposes, in simulations it is usually considered that combustion finishes at the moment the exhaust valve opens, so there could be a small fraction of unburned fuel in the combustion chamber among the residuals.
- 13.
For brevity we shall use the term fue ratio to refer to the ratio between the masses of fuel and air and their stoichiometric counterparts (see Eq. (A.3) in Appendix A) that is usually known as fuel–air equivalence ratio [48].
- 14.
The volumetric efficiency, \(e_v\), is a parameter used to quantify the effectiveness of the intake process. It is the mass that enters the cylinder during intake over the displaced volume \(e_v=m_\mathrm{in }/(\rho _i V_{dt})\). \(\rho _i\) is the density of the mixture evaluated at a reference state; for instance the average conditions on the intake manifold.
- 15.
These particular numerical values are arbitrary but useful for practical reasons.
- 16.
Although abnormal combustion comprises several phenomena, probably the most important are knock and surface ignition [54, 55]. Knock occurs when the mixture appears to ignite and burn ahead of the flame without any external ignition source. There is a rapid release of chemical energy of the gas which provokes pressure waves of considerable amplitude and a particular noise transmitted through the engine structure. Surface ignition is caused by the mixture igniting as consequence of a contact with a hot surface (overheated valve or spark plug) or hot-spot combustion chamber deposits. It may happen before the spark ignites the charge (pre-ignition) or after normal ignition (post-ignition).
- 17.
- 18.
As discussed by Heywood [90], friction work for compression ignition engines and spark ignition engines is different. Pumping work for SI engines is larger than that for similar CI engines. Piston-crank assembly friction losses are also different. So the use of the correlation for Chen and Flynn [75, 91] for SI engines in order to get accurate performance results should be carefully examined.
- 19.
Some engines incorporate recycled exhaust as a way to control NO\(_x\) emissions. They are usually called EGR (exhaust gas recirculation) engines.
- 20.
Unless explicitly mentioned, we shall take, \(T_\mathrm ref =298.15\) K.
- 21.
Pressure differences are also substantial, from approximately atmospheric pressure at intake to \(35\) atm at its highest value.
- 22.
In some modern engines, a fraction of recycled exhaust gases are injected into the fresh mixture with the objective of a greater dilution and thus control NO\(_x\) emissions. To quantify the percent of exhaust gas recycled an additional parameter is introduced: EGR\((\%)=(m_\text {EGR}/m_i)\times 100\) where \(m_\text {EGR}\) is the mass of exhaust gas recycled. In this case, the residual gas mass fraction in the fresh mixture is: \(x_r=(m_\text {EGR}+m_r)/m\).
- 23.
This key difference between combustion in both types of engines is more fundamental than the fact that for theoretical purposes a spark ignition engine is associated to an Otto cycle and a compression ignition engine to a Diesel cycle. In reality, combustion never occurs at constant volume in a spark ignition engine, nor does it occur under isobaric conditions in a compression ignition engine.
- 24.
The octane number of a fuel is a measure of its anti-knock properties. It is defined a 0–100 scale assigning \(0\) to n-heptane (a fuel predisposed to knock) and \(100\) to isooctane because of its anti-knock resistance. For instance, a \(95\) octane fuel has anti-knock performance equivalent to a mixture composed of \(95\,\%\) isooctane and \(5\,\%\) n-heptane by volume.
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Medina, A., Curto-Risso, P.L., Hernández, A.C., Guzmán-Vargas, L., Angulo-Brown, F., Sen, A.K. (2014). Physical Laws and Model Structure of Simulations. In: Quasi-Dimensional Simulation of Spark Ignition Engines. Springer, London. https://doi.org/10.1007/978-1-4471-5289-7_2
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