CN114004179A - Heat release rate rapid prediction method of marine diesel engine based on phenomenological process - Google Patents

Heat release rate rapid prediction method of marine diesel engine based on phenomenological process Download PDF

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CN114004179A
CN114004179A CN202111299997.1A CN202111299997A CN114004179A CN 114004179 A CN114004179 A CN 114004179A CN 202111299997 A CN202111299997 A CN 202111299997A CN 114004179 A CN114004179 A CN 114004179A
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刘龙
唐元亨
刘栢慧
张琦
梅齐昊
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Abstract

The invention provides a method for quickly predicting the heat release rate of a marine diesel engine based on a phenomenological process, which is based on a phenomenological modeling mechanism, considers penetration of spraying, air entrainment, evaporation and combustion from the moment of oil injection, reduces the real combustion process of the diesel engine by a formula as simple as possible, and realizes quick prediction of the heat release rate. According to the adjustment of the oil injection condition and the geometric parameters of the diesel engine, the model prediction method is not limited to the diesel engine with a specific model and a specific operation condition. Besides the heat release rate, the method can also predict other combustion characteristic parameters such as a stagnation period, cylinder pressure, air entrainment rate and the like.

Description

Heat release rate rapid prediction method of marine diesel engine based on phenomenological process
Technical Field
The invention relates to the field of diesel engine combustion performance analysis, in particular to a method for quickly predicting heat release rate of a marine diesel engine based on a phenomenological process.
Background
The marine diesel engine is one of main power devices of various large ocean-going ships in the world, and the performance of the marine diesel engine has a great influence on the benefit of the shipping industry. The heat release rate of the diesel engine is one of core parameters representing combustion and working performance, a method capable of rapidly predicting the heat release rate is found, and the method plays an important role in improving the transient performance prediction capability and the operation reliability of the marine diesel engine.
At present, the method for predicting the heat release rate of the diesel engine mainly comprises zero-dimensional model prediction and CFD model prediction. The zero-dimensional model is simple to build, the prediction speed and the response are high, but the combustion part is replaced by a Weber or double Weber semi-empirical formula, so that the physicochemical process in the diesel engine cannot be reflected, and the predicted heat release rate is lack of authenticity. The CFD model has a detailed structure which is most similar to the working process of a real diesel engine, but because the factors considered in calculation are excessive, the calculation load is large, the operation efficiency is low, and the rapid prediction of the heat release rate is difficult to realize.
Disclosure of Invention
The invention aims to realize a rapid heat release rate prediction method of a marine diesel engine based on a phenomenological process, which is used for rapidly calculating the heat release rate and predicting the performance of a working condition based on a real spray development and combustion mechanism and providing a better numerical analysis method for transient performance prediction of the marine diesel engine.
A method for rapidly predicting the heat release rate of a marine diesel engine based on a phenomenological process comprises the following steps:
step 1, determining boundary conditions and initial conditions according to geometric parameters and working condition parameters of the diesel engine, dividing the whole working process of the diesel engine into a plurality of small calculation steps from the beginning of compression to the end of combustion, and calculating the temperature change in the cylinder of each crank angle step from the beginning of compression to the beginning of oil injection by adopting an energy conservation equation
Figure BDA0003337961080000011
Figure BDA0003337961080000012
In the formula
Figure BDA0003337961080000013
Is the in-cylinder heat transfer amount in one step,
Figure BDA0003337961080000014
volume work for the working medium, m mass of the working medium, cv1Is the specific heat capacity of the working medium.
According to the above formula, temperature T according to initial conditions1Solving for the temperature T of the end of the first step2Will T2And performing iterative calculation on the initial temperature serving as the next step to obtain the temperature of each step length from the compression to the oil injection starting moment. Knowing the temperature of each step, the pressure p can be obtained from the ideal gas state equation pV ═ RT for each step.
Step 2, after oil injection is started, calculating the spray penetration distance S and the air entrainment rate m in each time step by adopting the following formulaa：
Figure BDA0003337961080000021
Figure BDA0003337961080000022
In the formula,. DELTA.pinjIs the difference between the injection pressure and the in-cylinder pressure, rhogIs the density of the working medium in the cylinder, t is the time from the beginning of the injection to the calculation step length, dnozIs the diameter of the orifice, T is the temperature in the cylinder, mfIs the mass flow of the injected fuel.
Step 3, calculating the change of the turbulence energy k in the cylinder brought by the development of the spray in the step 2:
Figure BDA0003337961080000023
wherein M represents the total mass of the spray zone, ujThe nozzle outlet speed belongs to turbulence energy dissipation rate, and the following formula is adopted for calculation:
Figure BDA0003337961080000024
in the formula, LjFor the in-cylinder turbulence energy scale, the following equation is used to calculate:
Figure BDA0003337961080000025
in the formula, ρfIs the fuel density.
And 4, calculating the evaporation rate of the spray in each step, wherein only the evaporated spray can participate in final combustion:
Figure BDA0003337961080000026
Figure BDA0003337961080000027
in the formula, raIs the rate of heat absorption per unit mass of fuel, p is the in-cylinder pressure, rvM is the evaporation rate of fuel oilliqAnd E is the mass of the liquid fuel in the current step length, and the heat required by the evaporation of the unit mass of the fuel.
Step 5, calculating the stagnation period tau by adopting the following formulai：
Figure BDA0003337961080000028
In the formula, SpThe average speed of the piston under the current working condition, R is a gas constant, EaThe activation energy of the fuel can be calculated by the following formula:
Ea＝618840/(CN+25)
in the formula, CN is the octane number of the fuel oil.
And 6, calculating the combustion rate of the evaporated fuel in the step 4, wherein a laminar-turbulent characteristic time model is adopted in the calculation process as follows:
Figure BDA0003337961080000029
wherein x represents the mass fraction of fuel, τcIs the characteristic time of combustion. Characteristic time taucFrom laminar characteristic time τlWith characteristic time τ of turbulencetAnd a delay factor f consisting of:
τc＝τl+fτt
characteristic time tau of laminar flowlCalculated using the formula:
Figure BDA0003337961080000031
wherein A is a calibration coefficient, [ Fuel]Is the molar fraction of fuel oil, [ O ]2]Is the oxygen molar fraction.
Characteristic time of turbulence τtThen it is calculated from the turbulence energy k calculated in step 3 and the turbulence dissipation factor ∈:
τt＝0.1k/∈
the delay coefficient f is calculated by the formula:
Figure BDA0003337961080000032
where r is the ratio of the mass of all combustion products to the mass of all reactants, expressed as:
Figure BDA0003337961080000033
and 7, calculating the heat release rate dQ/dt of the whole cylinder according to the combustion rate calculated in the step 6:
Figure BDA0003337961080000034
where LHV is the lower heating value of the fuel, NnozThe number of the spray holes on the diesel injector.
Compared with the prior art, the invention has the beneficial effects that:
the method is based on a phenomenological modeling mechanism, considers the penetration of spray, air entrainment, evaporation and combustion from the moment of oil injection, reduces the real combustion process of the diesel engine by a formula as simple as possible, and realizes the rapid prediction of the heat release rate. According to the adjustment of the oil injection condition and the geometric parameters of the diesel engine, the model prediction method is not limited to the diesel engine with a specific model and a specific operation condition. Besides the heat release rate, the method can also predict other combustion characteristic parameters such as a stagnation period, cylinder pressure, air entrainment rate and the like.
Drawings
FIG. 1 is a flow chart of a prediction method of the present invention;
FIG. 2 is a graph comparing the calculated results and experimental results for the cylinder pressure and heat release rate of a diesel engine of a certain model;
FIG. 3 shows parameters for a model of diesel engine of the present invention.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
Aiming at the problems that the existing heat release rate prediction method of the diesel engine is difficult to reflect a real process, the calculation speed is too slow, the transient prediction performance is poor and the like, the method is based on a phenomenological modeling theory, considers the processes of penetration of spray, air entrainment, evaporation and combustion from the moment of oil injection, and provides the heat release rate rapid prediction method based on the phenomenological process. The method has the advantages of high calculation speed, high precision and wide application range, and is convenient for predicting and evaluating the transient working performance of the marine diesel engine.
The purpose of the invention is realized by the following technical scheme:
step 1: according to geometric parameters and working conditions of the diesel engineThe parameters determine boundary conditions and initial conditions, the whole diesel engine working process is divided into a plurality of small calculation steps from the beginning of compression to the end of combustion, and the following energy conservation equation is adopted to calculate the temperature change in the cylinder of each crank angle step from the beginning of compression to the beginning of oil injection
Figure BDA0003337961080000041
Figure BDA0003337961080000042
In the formula
Figure BDA0003337961080000043
Is the in-cylinder heat transfer amount in one step,
Figure BDA0003337961080000044
volume work for the working medium, m mass of the working medium, cv1Is the specific heat capacity of the working medium. According to the above formula, temperature T according to initial conditions1Solving for the temperature T of the end of the first step2Will T2And performing iterative calculation on the initial temperature serving as the next step to obtain the temperature of each step length from the compression to the oil injection starting moment. Knowing the temperature of each step, the pressure p can be obtained from the ideal gas state equation pV ═ RT for each step.
Step 2: after the oil injection is started, the spray penetration distance S and the air entrainment rate m in each time step are calculated by adopting the following formulaa：
Figure BDA0003337961080000045
Figure BDA0003337961080000046
In the above formula,. DELTA.pinjIs the difference between the injection pressure and the in-cylinder pressure, rhogThe density of the working medium in the cylinder, and t is the time from the beginning of oil injection to the calculation step lengthM, dnozIs the diameter of the orifice, T is the temperature in the cylinder, mfIs the mass flow of the injected fuel.
And step 3: calculating the change of the turbulence energy k in the cylinder brought by the development of the spray in the step 2:
Figure BDA0003337961080000047
wherein M represents the total mass of the spray zone, ujThe nozzle outlet speed belongs to turbulence energy dissipation rate, and the following formula is adopted for calculation:
Figure BDA0003337961080000048
in the formula, LjFor the in-cylinder turbulence energy scale, the following equation is used to calculate:
Figure BDA0003337961080000049
in the formula, ρfIs the fuel density.
And 4, step 4: the evaporation rate of the spray in each step is calculated, and only the evaporated spray can participate in the final combustion:
Figure BDA00033379610800000410
Figure BDA00033379610800000411
in the formula, raIs the rate of heat absorption per unit mass of fuel, p is the in-cylinder pressure, rvM is the evaporation rate of fuel oilliqAnd E is the mass of the liquid fuel in the current step length, and the heat required by the evaporation of the unit mass of the fuel.
And 5: the combustion lag period tau is calculated by the following formulai：
Figure BDA00033379610800000412
In the formula, SpThe average speed of the piston under the current working condition, R is a gas constant, EaThe activation energy of the fuel can be calculated by the following formula:
Ea＝618840/(CN+25)
in the formula, CN is the octane number of the fuel oil. When the in-cylinder crank angle exceeds the calculated value of the stagnation period formula, the fuel evaporated in step 4 starts to burn.
Step 6: and (4) calculating the combustion rate of the evaporated fuel in the step (4), wherein a laminar-turbulent characteristic time model is adopted in the calculation process as follows:
Figure BDA0003337961080000051
wherein x represents the mass fraction of fuel, τcIs the characteristic time of combustion. Characteristic time taucFrom laminar characteristic time τlWith characteristic time τ of turbulencetAnd a delay factor f consisting of:
τc＝τl+fτt
characteristic time tau of laminar flowlCalculated using the formula:
Figure BDA0003337961080000052
wherein A is a calibration coefficient, [ Fuel]Is the molar fraction of fuel oil, [ O ]2]Is the oxygen molar fraction.
Characteristic time of turbulence τtThen it is calculated from the turbulence energy k calculated in step 3 and the turbulence dissipation factor ∈:
τt＝0.1k/∈
the delay coefficient f is calculated by the formula:
Figure BDA0003337961080000053
where r is the ratio of the mass of all combustion products to the mass of all reactants, expressed as:
Figure BDA0003337961080000054
step 7, calculating the heat release rate dQ/dt of the entire cylinder from the combustion rate calculated in step 6:
Figure BDA0003337961080000055
where LHV is the lower heating value of the fuel, NnozThe number of the spray holes on the diesel injector.
The foregoing is merely a description of preferred embodiments of the present invention and does not limit the spirit and scope of the invention. Any modification, variation, improvement, etc. made by those skilled in the art based on the technical solution of the present invention should fall into the protection scope of the present invention without departing from the innovative concept of the present invention and the protection scope of the claims. The technical content of the invention is fully described in the claims.

Claims (1)

1. A method for quickly predicting the heat release rate of a marine diesel engine based on a phenomenological process is characterized by comprising the following steps of: the method comprises the following steps:
step 1: determining boundary conditions and initial conditions according to geometric parameters and working condition parameters of the diesel engine, dividing the whole working process of the diesel engine from the beginning of compression to the end of combustion into a plurality of small calculation steps, and calculating the temperature change in the cylinder of each crank angle step from the beginning of compression to the beginning of oil injection by adopting an energy conservation equation
Figure FDA0003337961070000011
Figure FDA0003337961070000012
In the formula
Figure FDA0003337961070000013
Is the in-cylinder heat transfer amount in one step,
Figure FDA0003337961070000014
volume work for the working medium, m mass of the working medium, cv1Is the specific heat capacity of the working medium.
According to the above formula, temperature T according to initial conditions1Solving for the temperature T of the end of the first step2Will T2And performing iterative calculation on the initial temperature serving as the next step to obtain the temperature of each step length from the compression to the oil injection starting moment. Knowing the temperature of each step, the pressure p can be obtained from the ideal gas state equation pV ═ RT for each step.
Step 2: after the oil injection is started, the spray penetration distance S and the air entrainment rate m in each time step are calculated by adopting the following formulaa：
Figure FDA0003337961070000015
Figure FDA0003337961070000016
In the formula,. DELTA.pinjIs the difference between the injection pressure and the in-cylinder pressure, rhogIs the density of the working medium in the cylinder, t is the time from the beginning of the injection to the calculation step length, dnozIs the diameter of the orifice, T is the temperature in the cylinder, mfIs the mass flow of the injected fuel.
And step 3: calculating the change of the turbulence energy k in the cylinder brought by the development of the spray in the step 2:
Figure FDA0003337961070000017
wherein M represents the total mass of the spray zone, ujThe nozzle outlet speed belongs to turbulence energy dissipation rate, and the following formula is adopted for calculation:
Figure FDA0003337961070000018
in the formula, LjFor the in-cylinder turbulence energy scale, the following equation is used to calculate:
Figure FDA0003337961070000019
in the formula, ρfIs the fuel density.
And 4, step 4: the evaporation rate of the spray in each step is calculated, and only the evaporated spray can participate in the final combustion:
Figure FDA0003337961070000021
Figure FDA0003337961070000022
in the formula, raIs the rate of heat absorption per unit mass of fuel, p is the in-cylinder pressure, rvM is the evaporation rate of fuel oilliqAnd E is the mass of the liquid fuel in the current step length, and the heat required by the evaporation of the unit mass of the fuel.
And 5: the combustion lag period tau is calculated by the following formulai：
Figure FDA0003337961070000023
In the formula, SpThe average speed of the piston under the current working condition, R is a gas constant, EaThe activation energy of the fuel oil can be calculated by the following formulaCalculating:
Ea＝618840/(CN+25)
in the formula, CN is the octane number of the fuel oil.
Step 6: and (4) calculating the combustion rate of the evaporated fuel in the step (4), wherein a laminar-turbulent characteristic time model is adopted in the calculation process as follows:
Figure FDA0003337961070000024
wherein x represents the mass fraction of fuel, τcIs the characteristic time of combustion. Characteristic time taucFrom laminar characteristic time τlWith characteristic time τ of turbulencetAnd a delay factor f consisting of:
τc＝τl+fτt
characteristic time tau of laminar flowlCalculated using the formula:
Figure FDA0003337961070000025
wherein A is a calibration coefficient, [ Fuel]Is the molar fraction of fuel oil, [ O ]2]Is the oxygen molar fraction.
Characteristic time of turbulence τtThen it is calculated from the turbulence energy k calculated in step 3 and the turbulence dissipation factor ∈:
τt＝0.1k/∈
the delay coefficient f is calculated by the formula:
Figure FDA0003337961070000026
where r is the ratio of the mass of all combustion products to the mass of all reactants, expressed as:
Figure FDA0003337961070000027
and 7: from the combustion rate calculated in step 6, the heat release rate dQ/dt of the entire cylinder can be calculated:
Figure FDA0003337961070000028
where LHV is the lower heating value of the fuel, NnozThe number of the spray holes on the diesel injector.
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