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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.
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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)

1.一种船用柴油机基于现象学过程的放热率快速预测方法，其特征是：包括以下步骤：1. a method for rapidly predicting the heat release rate of a marine diesel engine based on a phenomenological process, is characterized in that: comprise the following steps: 步骤1：根据柴油机几何参数与工况参数确定边界条件与初始条件，将整个柴油机工作过程从压缩开始到燃烧结束划分为许多小的计算步长，并采用能量守恒方程式计算从压缩到喷油开始每个曲轴转角步长的缸内温度变化
Figure FDA0003337961070000011
Step 1: Determine the boundary conditions and initial conditions according to the geometric parameters and working condition parameters of the diesel engine, divide the entire diesel engine working process from the start of compression to the end of combustion into many small calculation steps, and use the energy conservation equation to calculate the start from compression to fuel injection. In-cylinder temperature change per crank angle step
Figure FDA0003337961070000011
Figure FDA0003337961070000012
Figure FDA0003337961070000012
 式中
Figure FDA0003337961070000013
为一个步长内的缸内传热量，
Figure FDA0003337961070000014
为工质所作体积功，m为工质质量，cv1为工质比热容。in the formula
Figure FDA0003337961070000013
is the heat transfer in the cylinder in one step,
Figure FDA0003337961070000014
is the volume work done by the working medium, m is the mass of the working medium, and c v1 is the specific heat capacity of the working medium. 依照上式，根据初始条件的温度T1求解出第一个步长终点的温度T2，将T2作为下一步长的初始温度迭代计算，得到压缩至喷油开始时刻各步长的温度。已知各步长温度，由理想气体状态方程pV＝RT可以得到相应各步长的压力p。According to the above formula, the temperature T 2 at the end of the first step is solved according to the temperature T 1 of the initial condition, and T 2 is used as the initial temperature of the next step to iteratively calculate, and the temperature of each step at the time of compression to the start of fuel injection is obtained. Knowing the temperature of each step, the pressure p of each step can be obtained from the ideal gas state equation pV=RT. 步骤2：喷油开始后，采用下式计算各个时间步长内的喷雾贯穿距S、空气卷吸率ma：Step 2: After the fuel injection starts, use the following formula to calculate the spray penetration distance S and the air entrainment rate ma in each time step:
Figure FDA0003337961070000015
Figure FDA0003337961070000015
Figure FDA0003337961070000016
Figure FDA0003337961070000016
 式中，Δpinj为喷油压力与缸内压力之差，ρg为缸内工质密度，t为从喷油开始到该计算步长为止的时间，dnoz为喷孔直径，T为缸内温度，mf为喷油质量流量。In the formula, Δp inj is the difference between the injection pressure and the pressure in the cylinder, ρ g is the density of the working medium in the cylinder, t is the time from the start of fuel injection to the calculation step, d noz is the diameter of the injection hole, and T is the cylinder Internal temperature, m f is the mass flow of fuel injection. 步骤3：计算步骤2中喷雾的发展带来的缸内湍动能k的变化：Step 3: Calculate the change in in-cylinder turbulent kinetic energy k due to the development of the spray in Step 2:
Figure FDA0003337961070000017
Figure FDA0003337961070000017
 式中M代表喷雾区的总质量，uj为喷孔出口速度，∈为湍能耗散率，采用如下公式计算：where M represents the total mass of the spray area, u j is the nozzle outlet velocity, ∈ is the turbulent energy dissipation rate, which is calculated by the following formula:
Figure FDA0003337961070000018
Figure FDA0003337961070000018
 式中，Lj为缸内湍能尺度，用下式计算：In the formula, L j is the scale of turbulent energy in the cylinder, which is calculated by the following formula:
Figure FDA0003337961070000019
Figure FDA0003337961070000019
 式中，ρf为燃油密度。where ρ f is the fuel density. 步骤4：计算每一步长内喷雾的蒸发率，只有蒸发的喷雾才能参与最终燃烧：Step 4: Calculate the evaporation rate of the spray in each step length, only the evaporated spray can participate in the final combustion:
Figure FDA0003337961070000021
Figure FDA0003337961070000021
Figure FDA0003337961070000022
Figure FDA0003337961070000022
 式中，ra为单位质量燃油的吸热速率，p为缸内压力，rv为燃油蒸发速率，mliq为当前步长内液态燃油的质量，E为单位质量燃油蒸发所需的热量。where ra is the heat absorption rate per unit mass of fuel, p is the in-cylinder pressure, r v is the fuel evaporation rate, m liq is the mass of liquid fuel in the current step size, and E is the heat required for the evaporation of unit mass of fuel. 步骤5：采用如下公式计算滞燃期τi：Step 5: Calculate the ignition delay period τ i using the following formula:
Figure FDA0003337961070000023
Figure FDA0003337961070000023
 式中，Sp为当前工况的活塞平均速度，R为气体常数，Ea为燃油的活化能，可通过下式计算：In the formula, Sp is the average speed of the piston in the current working condition, R is the gas constant, E a is the activation energy of the fuel, which can be calculated by the following formula: Ea＝618840/(CN+25)E a =618840/(CN+25) 式中，CN为燃油的辛烷值。where CN is the octane number of the fuel. 步骤6：计算步骤4中蒸发燃油的燃烧速率，计算过程如下采用层流-湍流特征时间模型：Step 6: Calculate the burning rate of the evaporated fuel in Step 4. The calculation process is as follows using the laminar-turbulent characteristic time model:
Figure FDA0003337961070000024
Figure FDA0003337961070000024
 式中，x代表燃油的质量分数，τc是燃烧的特征时间。特征时间τc由层流特征时间τl与湍流特征时间τt以及延迟系数f组成：In the formula, x represents the mass fraction of fuel oil, and τ c is the characteristic time of combustion. The characteristic time τ c is composed of the laminar characteristic time τ l , the turbulent characteristic time τ t and the delay coefficient f: τc＝τl+fτt τ c =τ l +fτ t 式中层流特征时间τl采用下式计算：In the formula, the laminar flow characteristic time τ l is calculated by the following formula:
Figure FDA0003337961070000025
Figure FDA0003337961070000025
 其中A为标定系数，[Fuel]为燃油摩尔浓度分数，[O2]为氧气摩尔浓度分数。Where A is the calibration coefficient, [Fuel] is the fuel molar concentration fraction, and [O 2 ] is the oxygen molar concentration fraction. 湍流特征时间τt则是根据步骤3中所计算的湍动能k与湍能耗散率∈计算：The turbulent characteristic time τ t is calculated according to the turbulent kinetic energy k and the turbulent energy dissipation rate ∈ calculated in step 3: τt＝0.1k/∈τ t =0.1k/∈ 延迟系数f的计算公式为：The formula for calculating the delay coefficient f is:
Figure FDA0003337961070000026
Figure FDA0003337961070000026
 式中，r是所有燃烧产物的质量与所有反应物质量的比值，表示为：where r is the ratio of the mass of all combustion products to the mass of all reactants, expressed as:
Figure FDA0003337961070000027
Figure FDA0003337961070000027
 步骤7：根据步骤6中所计算的燃烧速率，可计算出缸内整体的放热率dQ/dt：Step 7: According to the combustion rate calculated in Step 6, the overall heat release rate dQ/dt in the cylinder can be calculated:
Figure FDA0003337961070000028
Figure FDA0003337961070000028
 式中，LHV是燃料的低热值，Nnoz是柴油机喷油器上喷孔的数目。where LHV is the low calorific value of the fuel, and N noz is the number of injection holes on the diesel injector.
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