CN113432881A - Method for simulating compression pressure and temperature in two-stroke cylinder by using four-stroke single cylinder - Google Patents
Method for simulating compression pressure and temperature in two-stroke cylinder by using four-stroke single cylinder Download PDFInfo
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Abstract
The invention provides a method for simulating compression pressure and temperature in a two-stroke cylinder by using a four-stroke single cylinder, which comprises the steps of estimating a plurality of compression ratios; solving the compression initial point pressure and temperature required by the intake air; and (3) solving the relation between target compression end point pressure and temperature and intake required pressure and temperature under different compression ratios: determining an initial compression ratio according to the boundary condition; determining initial stroke and connecting rod length: solving the instantaneous working volumes of the cylinders at different crank angles; and (3) solving a pressure curve and a temperature curve which change along with the rotation angle of the crankshaft: fitting a pressure curve and a temperature curve of the two-stroke engine without combustion compression and expansion by using an actually measured combustion curve of the two-stroke diesel engine; converting a crankshaft rotation angle domain and a time domain; an appropriate rotational speed is determined. The invention adopts a four-stroke quick compressor to simulate the pressure, the temperature and the motion state of a compression end point of a large-scale low-speed two-stroke long-stroke diesel engine and simulate the measurement of the spraying and the combustion of the large-scale low-speed two-stroke long-stroke diesel engine of a ship.
Description
Technical Field
The invention belongs to the technical field of optical engines, and particularly relates to a design method for simulating compression pressure and temperature in a two-stroke cylinder by using a four-stroke single cylinder.
Background
The marine low-speed two-stroke diesel engine is one of the most important power devices in the current shipping industry, and has great significance for the research on the combustion and atomization process of the marine low-speed two-stroke diesel engine.
The research on the combustion and atomization process of the marine low-speed two-stroke diesel engine needs to measure the combustion and atomization process. The measurement of the combustion and atomization process of the marine low-speed two-stroke diesel engine needs to adopt a device to simulate the pressure, the temperature and the motion state of the marine low-speed two-stroke long-stroke diesel engine. In the current device simulation, two problems exist. Firstly, in the simulation process, due to the limitation of various realistic factors such as experimental equipment and the like, the simulated compression pressure and temperature of the compression end point cannot reach the pressure and temperature of the target compression end point of the marine low-speed two-stroke long-stroke diesel engine; secondly, even if the simulated device can reach the pressure and temperature of the target compression end point of the marine low-speed two-stroke long-stroke diesel engine, the required whole instrument and equipment are too large and high in cost due to the fact that the stroke adopted by the simulated machine is too large, and meanwhile, when the piston reaches the top dead center due to the fact that the adopted stroke is too large, the distance between the top of the piston and the cylinder is relatively small, and therefore no space is provided for arranging a visual window on the cylinder to conduct optical measurement.
Therefore, in order to solve the problems, it is very important to design a cost-effective method for simulating the highest compression pressure, temperature and motion state of the marine low-speed two-stroke long-stroke diesel engine.
Disclosure of Invention
In view of the above, the present invention is directed to a method for simulating compression pressure and temperature in a two-stroke cylinder by using a four-stroke single cylinder, which simulates pressure, temperature and motion state at the compression end of a large low-speed two-stroke long-stroke diesel engine by using a relatively simple and small four-stroke fast compressor, and simulates measurement of spray and combustion of a large low-speed two-stroke long-stroke diesel engine by measuring the spray and combustion of the four-stroke fast compressor, so as to research the process and mechanism of spray and combustion of the large low-speed two-stroke long-stroke diesel engine.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
a method for simulating compression pressure and temperature in a two-stroke cylinder by using a four-stroke single cylinder specifically comprises the following steps:
step 1: selecting a plurality of proper compression ratios according to the target compression end point pressure and the target compression end point temperature of the simulated marine low-speed two-stroke long-stroke diesel engine;
step 2: solving the pressure and temperature required by air intake;
and step 3: according to the temperature, the pressure and the compression ratio obtained in the step (2), the relation between the target compression end point pressure and the intake required compression initial point pressure and the relation between the target compression end point temperature and the intake required compression initial point temperature under different compression ratios are obtained;
and 4, step 4: selecting a relatively proper initial compression ratio according to the three boundary conditions, the relation between the target compression end point pressure and the intake required compression start point pressure under different compression ratios and the relation between the target compression end point temperature and the intake required compression start point temperature;
and 5: determining the required initial stroke through the initial compression ratio obtained in the step 4, and modifying the size of the four-stroke prototype through the initial compression ratio to obtain the length of the connecting rod;
step 6: calculating instantaneous cylinder working volumes at different crank angles through an instantaneous cylinder working volume formula, wherein the instantaneous cylinder working volume formula is as follows:
wherein S is the piston stroke, epsilon is the compression ratio, D is the cylinder diameter, and lambda is the connecting rod-crank ratio,
the working volumes of the cylinders under different crank rotation angles can be obtained for the crank rotation angles;
and 7: calculating corresponding temperature and pressure by using the working volume of the instantaneous cylinder in the step 6 through an adiabatic state equation of ideal gas, and obtaining a pressure curve and a temperature curve which change along with the rotation angle of the crankshaft;
and 8: fitting a pressure curve and a temperature curve of the target marine large low-speed two-stroke long-stroke diesel engine without combustion compression expansion by using an actually measured combustion curve of the two-stroke diesel engine;
and step 9: conversion formula for converting from crank angle domain to time domain
Wherein n iseFor the rotation speed of the diesel engine, the curve obtained by calculation in the step 7 and the curve obtained by experimental fitting in the step 8 are converted from a crank angle domain to a time domain;
step 10: and determining a proper rotating speed, and enabling the pressure curve and the temperature curve obtained by calculation in the time domain to be consistent with the pressure curve and the temperature curve of the target marine large-scale low-speed two-stroke long-stroke diesel engine in the time domain in the step 9 near the top dead center.
Further, in step 1, several compression ratios between 6 and 12 are selected.
Further, the specific steps of step 2 are: adiabatic equation of state pV through ideal gasκConstant, where p is the cylinder pressure, V is the cylinder volume, and κ is the gas Constant, 1.4;
a relationship between the target compression end pressure and the required pressure of intake air is found,
wherein p is1Pressure required for admission, p2Is a target compression end pressure, v1Specific volume of cylinder before compression, v2The specific volume of the compressed cylinder; v. of1And v2The ratio of the pressure to the pressure is the compression ratio epsilon, and the pressure required by air intake is calculated;
and the relationship between the target compression end temperature and the required temperature of intake air,
wherein T is1Temperature, T, required for intake2Is the target compression end temperature; calculating the temperature required by air intake;
further, the three boundary conditions in step 4 are: first, the maximum pressure required for intake that can be achieved by the actual equipment; secondly, the maximum heating temperature required by the air intake which can be achieved by the actual equipment; thirdly, according to the requirement of the height of the visual window on the side surface of the cylinder, the size of the space required to be reserved when the piston moves to the top dead center.
Further, in step 4, under the limitation of the existing practical apparatus and method, the compression pressure can only reach 10bar at most, the heating temperature can only reach 120 ℃ at most, the required window height for optical measurement is 50mm, when the window height is 50mm, the volume inside the cylinder is calculated, the height which can be reached by the top dead center of the piston is calculated, and an initial compression ratio is determined to be 10 according to three boundary conditions.
Further, in the step 8, fitting a pressure curve and a temperature curve of the non-combustion compression expansion of the large low-speed two-stroke long-stroke diesel engine for the target ship by using an actually measured combustion curve of the CSSC340 two-stroke diesel engine; in the step 10, fitting a pressure curve and a temperature curve of the target marine large low-speed two-stroke long-stroke diesel engine without combustion compression expansion by using an actually measured combustion curve of the CSSC340 two-stroke diesel engine in a time domain, and comparing the pressure curve and the temperature curve with the calculated pressure curve and temperature curve; by adjusting the different speeds, the pressure curve and the temperature curve are consistent with those of the CSSC340 two-stroke diesel engine on the time axis, and the pressure curve and the temperature curve are consistent with those of the CSSC340 two-stroke diesel engine under the 100% working condition within plus or minus 20 milliseconds near the top dead center through calculation at 260 RPM.
Compared with the prior art, the design method for simulating the compression pressure and the temperature in the two-stroke cylinder by using the four-stroke single cylinder has the following advantages:
the pressure and temperature of combustion and spray of a large low-speed two-stroke long-stroke diesel engine are successfully simulated by adopting a relatively simple and small four-stroke rapid compressor; the simulation ensures the accuracy, reduces the investment cost, and can realize the research on the spraying and burning process and mechanism of the large-scale low-speed two-stroke long-stroke diesel engine for the ship
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a flowchart illustrating the overall steps of the present invention;
FIG. 2 is a graph of target compression end point and intake required pressure at different compression ratios;
FIG. 3 is a graph of the target compression end point and the required temperature of intake air at different compression ratios;
FIG. 4 is a graph of calculated and target pressure curves and actual measured combustion in the crank angle domain;
FIG. 5 is a graph of calculated temperature curves and target temperature curves in the crank angle domain;
FIG. 6 is a graph of calculated and target pressure curves and actual measured combustion in the time domain;
FIG. 7 is a graph of calculated temperature curves and target temperatures in the time domain;
FIG. 8 is a graph of a calculated pressure curve versus a target pressure curve and actual measured combustion over time after adjusting the speed;
FIG. 9 is a graph of a temperature curve calculated when the rotational speed is adjusted and a target temperature curve in a time domain;
FIG. 10 is a graph of the validation of the accuracy of a patent by one-dimensional model simulation verification with commercial software.
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.
The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
Fig. 1 is a flow chart illustrating an overall process of a design method for simulating compression pressure and temperature in a two-stroke cylinder by using a four-stroke single cylinder according to the present application.
In the embodiment, a four-stroke single-cylinder rapid compressor with the cylinder diameter of 320mm and the rated rotating speed of 260RPM is adopted to simulate the combustion and the spraying of a marine low-speed two-stroke long-stroke diesel engine with the cylinder diameter of 340mm, the stroke of 1600mm, the compression ratio of 20.5, the scavenging amount of 7.44L and the rated rotating speed of 157RPM, the simulated target compression pressure of the four-stroke single-cylinder is 160bar, and the target compression temperature is 627 ℃.
A design and verification method for simulating compression pressure and temperature in a two-stroke cylinder by using a four-stroke single cylinder specifically comprises the following steps:
step 1: determining several suitable compression ratios;
selecting a plurality of proper compression ratios according to the target compression end pressure and the target compression end temperature of the simulated marine low-speed two-stroke long-stroke diesel engine, wherein the selected compression ratio is between 6 and 12;
step 2: solving the pressure and temperature required by air intake;
establishing a zero-dimensional model, and utilizing an ideal gas adiabatic state equation: pVκConstant, where p is the cylinder pressure, V is the cylinder volume, and κ is the gas Constant, 1.4;
to obtain the eyesThe relationship between the target compression end pressure and the pressure required for intake air,
wherein p is1Pressure required for admission, p2Is a target compression end pressure, v1Specific volume of cylinder before compression, v2The specific volume of the compressed cylinder; v. of1And v2The ratio of the pressure to the pressure is the compression ratio epsilon, and the pressure required by air intake is calculated;
and the relationship between the target compression end temperature and the required temperature of intake air,
wherein T is1Temperature, T, required for intake2Is the target compression end temperature; calculating the temperature required by air intake;
and step 3: drawing a relation graph between target compression end point pressure and pressure required by air inlet under different compression ratios, and a relation graph between target compression end point temperature and temperature required by air inlet under different compression ratios;
according to the pressure required by the intake air obtained in the step 2 and the corresponding target compression end pressure and compression ratio, drawing a relation graph between the pressure required by the intake air under different compression ratios and the target compression end pressure, as shown in fig. 2; similarly, according to the temperature required by the intake air obtained in the step 2 and the corresponding target compression end temperature and compression ratio, drawing a relation graph between the temperature required by the intake air and the target compression end temperature under different compression ratios, as shown in fig. 3;
and 4, step 4: determining an initial compression ratio;
in the application, under the limitation of the existing practical instrument and method, the maximum inlet pressure can only reach 10bar, the maximum heating temperature can only reach 120 ℃, the required window height for carrying out optical measurement is 50mm, the three-dimensional graph is analyzed through the data, when the set window height is 50mm, the height which can be reached by the top dead center of the piston and the working volume of the cylinder can be calculated, and the height and the volume limit that the compression ratio cannot be overlarge. According to three boundary conditions of the highest air inlet pressure, the maximum heating temperature and the limitation of the window height, an initial compression ratio can be determined in a relation graph of the compression ratio, the temperature and the pressure, and the selected initial compression ratio is 10;
and 5: determining the required initial stroke through the initial compression ratio obtained in the step 4, and modifying the initial compression ratio by combining the geometric dimension of the four-stroke prototype machine to obtain the length of the connecting rod; the four-stroke prototype machine is an existing four-stroke rapid compression expansion machine;
step 6: calculating the instantaneous working volume of the cylinder;
by the formula of the working volume of the instantaneous cylinder,
wherein S is the initial stroke, epsilon is the compression ratio, D is the cylinder diameter, and lambda is the connecting rod-crank ratio,
for the crankshaft angle, different crankshaft angles can be obtained
The working volume of the lower cylinder; the connecting rod-crank ratio is the crank length/the connecting rod length, and the crank length is half of the initial stroke length;
and 7: solving a pressure curve and a temperature curve;
using the instantaneous cylinder displacement in step 6, passing the adiabatic equation of state pV of the ideal gaskObtaining pressures and temperatures at different crank angles, and obtaining a pressure curve which changes along with the crank angle, namely a four-stroke engine curve and a temperature curve in fig. 4, namely a four-stroke engine curve in fig. 5;
and 8: fitting a pressure curve of the target marine large low-speed two-stroke long-stroke diesel engine without combustion compression expansion, namely a two-stroke engine curve in fig. 4 and a temperature curve of the target marine large low-speed two-stroke long-stroke diesel engine without combustion compression expansion, namely a two-stroke engine curve in fig. 5 by using an actually measured combustion curve of the CSSC340 two-stroke diesel engine, namely a two-stroke engine measured value curve in fig. 4;
and step 9: conversion formula for converting from crank angle domain to time domain
Converting the curve calculated in the step 7 and the curve fitted by the experiment in the step 8 from the crank angle domain to the time domain, wherein neObtaining a pressure curve obtained by calculation and a target pressure curve and an actually measured combustion curve in a time domain for the rotating speed of the low-speed two-stroke long-stroke diesel engine and the rotating speed of the four-stroke engine, as shown in fig. 6; and obtaining a temperature curve and a target temperature curve under the time domain, as shown in fig. 7;
step 10: determining a suitable rotational speed;
comparing a pressure curve of the target marine large low-speed two-stroke long-stroke diesel engine, which is fitted by using an actually measured combustion curve of the CSSC340 two-stroke diesel engine, with the calculated pressure curve, and comparing a temperature curve of the target marine large low-speed two-stroke long-stroke diesel engine with the calculated temperature curve;
by adjusting different rotating speeds and calculating to obtain that the pressure curve and the temperature curve obtained by calculation at 260RPM are consistent with the pressure curve and the temperature curve of the CSSC340 two-stroke diesel engine under the 100% working condition within plus and minus 20 milliseconds near the top dead center as shown in figures 8 and 9, the four-stroke rapid compressor simulating the compression pressure and the temperature in the two-stroke cylinder is obtained.
After the rotation speed is determined in step 10, step 11: the compression ratio and the stroke can be further accurately determined according to other performance parameters of the comprehensive rapid compressor: according to the initial compression ratio and the initial stroke, in the detailed design of the three-dimensional graph of the rapid compressor, after the design of the shape parameters of the window, the arrangement of the air inlet and outlet valves and the piston head is finished according to the initial compression ratio and the initial stroke, the final compression ratio and the final stroke are obtained through the volume calculation of the top dead center and the bottom dead center calculated by three-dimensional drawing software; the final compression ratio was 9.25 and the stroke was 460 mm.
Verification, step 12: verifying that the four-stroke rapid compressor simulates the whole process of combustion and atomization of a two-stroke diesel engine;
the final compression ratio and stroke obtained in the step 11 and the simulation of the one-dimensional combustion model according to the relevant geometric parameters of the fast compressor, the intake and exhaust parameters, the oil injection parameters and the like are simulated by using relevant commercial software, so that a comparison graph of a temperature curve and a pressure curve of the four-stroke fast compressor simulating the marine low-speed two-stroke diesel engine along with the change of the crank angle is obtained, as shown in fig. 10, obviously, the peak value comparison of the pressures at different crank angles, the pressures of the four-stroke machine and the two-stroke machine, and the temperature at different crank angles, the temperature peak values of the four-stroke machine and the two-stroke machine, it can be seen that, at the stage of compression and ignition combustion, the four-stroke quick compressor can well simulate the highest pressure and the highest temperature of a marine low-speed two-stroke diesel engine at the highest pressure and the highest temperature, and the accuracy of the four-stroke quick compressor can be well verified.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (6)
1. A method for simulating compression pressure and temperature in a two-stroke cylinder by using a four-stroke single cylinder is characterized by comprising the following steps of: the method specifically comprises the following steps:
step 1: selecting a plurality of proper compression ratios according to the target compression end point pressure and the target compression end point temperature of the simulated marine low-speed two-stroke long-stroke diesel engine;
step 2: solving the pressure and temperature required by air intake;
and step 3: according to the temperature, the pressure and the compression ratio obtained in the step (2), the relation between the target compression end point pressure and the intake required compression initial point pressure and the relation between the target compression end point temperature and the intake required compression initial point temperature under different compression ratios are obtained;
and 4, step 4: selecting a relatively proper initial compression ratio according to the three boundary conditions, the relation between the target compression end point pressure and the intake required compression start point pressure under different compression ratios and the relation between the target compression end point temperature and the intake required compression start point temperature;
and 5: determining the required initial stroke through the initial compression ratio obtained in the step 4, and modifying the size of the four-stroke prototype through the initial compression ratio to obtain the length of the connecting rod;
step 6: calculating instantaneous cylinder working volumes at different crank angles through an instantaneous cylinder working volume formula, wherein the instantaneous cylinder working volume formula is as follows:
wherein S is the piston stroke, epsilon is the compression ratio, D is the cylinder diameter, and lambda is the connecting rod-crank ratio,
the working volumes of the cylinders under different crank rotation angles can be obtained for the crank rotation angles;
and 7: calculating corresponding temperature and pressure by using the working volume of the instantaneous cylinder in the step 6 through an adiabatic state equation of ideal gas, and obtaining a pressure curve and a temperature curve which change along with the rotation angle of the crankshaft;
and 8: fitting a pressure curve and a temperature curve of the target marine large low-speed two-stroke long-stroke diesel engine without combustion compression expansion by using an actually measured combustion curve of the two-stroke diesel engine;
and step 9: conversion formula for converting from crank angle domain to time domain
Wherein n iseFor the rotating speed of the low-speed two-stroke long-stroke diesel engine, the curve obtained by calculation in the step 7 and the curve obtained by experimental fitting in the step 8 are converted from a crank angle domain to a time domain;
step 10: and determining a proper rotating speed, and enabling the pressure curve and the temperature curve obtained by calculation in the time domain to be consistent with the pressure curve and the temperature curve of the target marine large-scale low-speed two-stroke long-stroke diesel engine in the time domain in the step 9 near the top dead center.
2. The method of simulating compression pressure and temperature in a two-stroke cylinder using a four-stroke, single-cylinder engine as claimed in claim 1, wherein: in said step 1, several compression ratios between 6 and 12 are selected.
3. The method for simulating compression pressure and temperature in a two-stroke cylinder using a four-stroke, single-cylinder engine as claimed in claim 1, wherein: the specific steps of the step 2 are as follows: adiabatic equation of state pV through ideal gasκConstant, where p is the cylinder pressure, V is the cylinder volume, and κ is the gas Constant, 1.4;
a relationship between the target compression end pressure and the required pressure of intake air is found,
wherein p is1Pressure required for admission, p2Is a target compression end pressure, v1Specific volume of cylinder before compression, v2The specific volume of the compressed cylinder; v. of1And v2The ratio of the pressure to the pressure is the compression ratio epsilon, and the pressure required by air intake is calculated;
and the relationship between the target compression end temperature and the required temperature of intake air,
wherein T is1Temperature, T, required for intake2To the target compression end temperature(ii) a The required temperature of the intake air is calculated.
4. The method for simulating compression pressure and temperature in a two-stroke cylinder using a four-stroke, single-cylinder engine as claimed in claim 1, wherein: the three boundary conditions in step 4 are respectively: first, the maximum pressure required for intake that can be achieved by the actual equipment; secondly, the maximum heating temperature required by the air intake which can be achieved by the actual equipment; thirdly, according to the requirement of the height of the visual window on the side surface of the cylinder, the size of the space required to be reserved when the piston moves to the top dead center.
5. The method for simulating compression pressure and temperature in a two-stroke cylinder using a four-stroke, single-cylinder engine as claimed in claim 4, wherein: in the step 4, under the limitation of the existing practical instrument and method, the highest compression pressure can only reach 10bar, the maximum heating temperature can only reach 120 ℃, the required height of the window for optical measurement is 50mm, when the height of the window is 50mm, the volume inside the cylinder is calculated, the height which can be reached by the top dead center of the piston is calculated, and an initial compression ratio is determined to be 10 according to three boundary conditions.
6. The method for simulating compression pressure and temperature in a two-stroke cylinder using a four-stroke, single-cylinder engine as claimed in claim 1, wherein: in the step 8, fitting a pressure curve and a temperature curve of the non-combustion compression expansion of the large low-speed two-stroke long-stroke diesel engine for the target ship by using an actually measured combustion curve of the CSSC340 two-stroke diesel engine; in the step 10, fitting a pressure curve and a temperature curve of the target marine large low-speed two-stroke long-stroke diesel engine without combustion compression expansion by using an actually measured combustion curve of the CSSC340 two-stroke diesel engine in a time domain, and comparing the pressure curve and the temperature curve with the calculated pressure curve and temperature curve; by adjusting the different speeds, and by calculation, the pressure and temperature profiles calculated at 260RPM are consistent with those of a CSSC340 two-stroke diesel engine at 100% operating conditions within plus or minus 20 milliseconds around top dead center.
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| CN104484552A (en) * | 2014-11-20 | 2015-04-01 | 哈尔滨工程大学 | Method for calculating blown gas displacement of two-stroke low-speed diesel engine for boat |
| CN105863841A (en) * | 2016-05-23 | 2016-08-17 | 上海海事大学 | Method for conducting angle encoding on instantaneous pressure in engine cylinder |
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| CN111625960A (en) * | 2020-05-27 | 2020-09-04 | 海南热带汽车试验有限公司 | CFD-based E10 ethanol gasoline engine combustion three-dimensional simulation method |
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| CN104484552A (en) * | 2014-11-20 | 2015-04-01 | 哈尔滨工程大学 | Method for calculating blown gas displacement of two-stroke low-speed diesel engine for boat |
| CN105863841A (en) * | 2016-05-23 | 2016-08-17 | 上海海事大学 | Method for conducting angle encoding on instantaneous pressure in engine cylinder |
| CN106762176A (en) * | 2016-12-13 | 2017-05-31 | 安徽航瑞航空动力装备有限公司 | A kind of stroke admission calculation of pressure method of two cylinder machine four |
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