CN112576392B - Engine system and control method thereof - Google Patents
Engine system and control method thereof Download PDFInfo
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- CN112576392B CN112576392B CN202011289880.0A CN202011289880A CN112576392B CN 112576392 B CN112576392 B CN 112576392B CN 202011289880 A CN202011289880 A CN 202011289880A CN 112576392 B CN112576392 B CN 112576392B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D41/0027—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures the fuel being gaseous
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D19/02—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with gaseous fuels
- F02D19/021—Control of components of the fuel supply system
- F02D19/022—Control of components of the fuel supply system to adjust the fuel pressure, temperature or composition
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D19/02—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with gaseous fuels
- F02D19/026—Measuring or estimating parameters related to the fuel supply system
- F02D19/027—Determining the fuel pressure, temperature or volume flow, the fuel tank fill level or a valve position
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/04—Introducing corrections for particular operating conditions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
- F02M21/0221—Fuel storage reservoirs, e.g. cryogenic tanks
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
- F02M21/0221—Fuel storage reservoirs, e.g. cryogenic tanks
- F02M21/0224—Secondary gaseous fuel storages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
- F02M21/0245—High pressure fuel supply systems; Rails; Pumps; Arrangement of valves
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/40—Engine management systems
Abstract
The invention belongs to the technical field of engines, and particularly relates to an engine system and a control method thereof. The control method comprises the following steps: calibrating a maximum pressure value P1 of the gas buffer tank and an initial calculation pressure value P2 of the gas pressurization estimation model; acquiring a real-time pressure value P of a gas pressure buffer tank; comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1; according to the fact that the real-time pressure value P is not less than the initial calculation pressure value P2 and is less than the maximum pressure value P1, the cycle number N of the gas pump needed by the gas buffer tank is calculated through the real-time pressure value P and the gas pressurization prediction model * (ii) a According to N * Not less than 1, controlling the fuel gas pump to carry out the next working cycle; according to N * And if the pressure is less than 1, controlling the fuel gas pump to stop working. According to the invention, by setting the gas pressurization estimation model, the relation between the pressure in the gas buffer tank and the working cycle of the gas pump can be calculated, the piston is prevented from reversely running in the middle stroke, the abrasion of the piston is slowed down, and the power consumption of the part of accessories is reduced.
Description
Technical Field
The invention belongs to the technical field of vehicles, and particularly relates to an engine system and a control method thereof.
Background
Direct in-cylinder injection gas engines typically require higher fuel supply pressures in order to inject a sufficient amount of fuel within the engine's effective cycle window and to cause the fuel to mix with the in-cylinder air at a faster rate.
The existing gas pressurization technology generally utilizes a hydraulic system to pressurize gas to a target pressure through a gas pump. The gas pump utilizes the gas mixture in the piston compression gas jar, and when the piston moved certain intermediate position of effective stroke, the gas pressure in the gas buffer tank reached maximum pressure value P1, and the hydraulic oil on gas pump top pressure release suddenly this moment, piston change traffic direction fast under the effect of jar internal high pressure gas, and piston sealing ring atress direction sharply changes this moment, and the atress is strikeed great, and wearing and tearing aggravation. In addition, the piston runs in the opposite direction, the effective output of the next cycle of the fuel gas pump is reduced, and the power consumption of the hydraulic system is further increased.
Disclosure of Invention
The invention aims to at least solve the problem of accelerated wear of the gas pump caused by reverse movement of the existing gas pump when the pressure in the gas buffer tank reaches the limit. The purpose is realized by the following technical scheme:
a first aspect of the invention proposes a control method of an engine system, the control method including the steps of:
s1: the maximum pressure value P1 of the gas buffer tank and the initial calculation pressure value P2 of the gas pressurization estimation model;
s2: acquiring a real-time pressure value P of a gas pressure buffer tank;
s3: comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1;
s4: according to the fact that the real-time pressure value P is not less than the initial calculation pressure value P2 and is less than the maximum pressure value P1, the cycle number N of the gas pump needed by the gas buffer tank is calculated through the real-time pressure value P and a gas pressurization prediction model * ；
S5: according to N * Not less than 1, controlling the fuel gas pump to perform the next working cycle;
s6: according to N * And if the pressure is less than 1, controlling the fuel gas pump to stop working.
According to the control method of the engine system, the real-time pressure value P in the gas buffer tank is compared with the initial calculation pressure value P2 of the gas pressurization estimation model, and if the real-time pressure value P is not less than the initial calculation pressure value P2 and is less than the maximum pressure value P1, the cycle number N of the gas pump required by the gas buffer tank is calculated * If N is present * Not less than 1, namely the pressure in the gas buffer tank is not less than the pressure generated in the gas buffer tank by the gas pump working for one cycle, the gas pump is controlled to carry out the next working cycle, and if N is less than N, the next working cycle is carried out * And if the pressure in the fuel gas buffer tank is less than 1, namely the pressure in the fuel gas buffer tank is less than the pressure generated in the fuel gas buffer tank by the fuel gas pump in one working cycle, controlling the fuel gas pump to stop working. According to the invention, through setting the gas pressurization estimation model, the relation between the pressure in the gas buffer tank and the working cycle of the gas pump can be calculated, so that the pressure in the gas buffer tank is prevented from reaching the maximum pressure value P1 when the piston of the gas pump moves to the middle stroke, the piston is prevented from reversely running under the action of the large impact force of high-pressure gas during the middle stroke, the abrasion of the piston is further reduced, meanwhile, the piston cannot reversely run during the middle stroke, and the next working cycle of the gas pump can be ensuredThe output of the loop, in turn, reduces the power consumption of the boost system.
In addition, the control method of the engine system according to the embodiment of the present invention may further have the following technical features:
in some embodiments of the present invention, after comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1, the method further comprises the following steps:
and controlling the fuel gas pump to stop working according to the real-time pressure value P not less than the maximum pressure value P1.
In some embodiments of the present invention, before comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1, the method further comprises the following steps:
calibrating a minimum pressure value P3 of the gas buffer tank according to the current running state of the engine;
comparing the real-time pressure value P with a minimum pressure value P3;
controlling the fuel gas pump to start working according to the condition that the real-time pressure value P is not greater than the minimum pressure value P3;
and comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1 after the real-time pressure value P is larger than the minimum pressure value P3.
In some embodiments of the present invention, after comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1, the method further comprises the following steps:
and controlling the fuel gas pump to be in a working state according to the fact that the real-time pressure value P is larger than the minimum pressure value P3 and smaller than the initial calculated pressure value P2.
In some embodiments of the invention, the number of cycles N of the gas pump required by the gas buffer tank is calculated through the real-time pressure value P and a gas pressurization prediction model * The method comprises the following steps:
N * ＝(P2-P)/ΔP (1)
in the formula (1), Δ P is a variation value of the pressure in the gas buffer tank within a time of one working cycle of the gas pump, wherein,
ΔP＝(M1-M2)*RT/V (2)
in formula (2), R is a gas constant of the fuel gas, T is a real-time temperature of the fuel gas buffer tank, V is a volume of the fuel gas buffer tank, M1 is a weight of the fuel gas pumped by the fuel gas pump in one working cycle period of the fuel gas pump, and M2 is a mass of the fuel gas consumed by the engine in one working cycle period of the fuel gas pump, wherein:
M1＝Vd*ρ*η (3)
in the formula (3), Vd is the geometric displacement of the gas pump, rho is the density of liquid gas, eta is the volumetric efficiency of the gas pump,
in the formula (4), Q is the weight of the fuel gas consumed by the engine in unit time, t is the time of one cycle of the working of the fuel gas pump,
η＝η 1 *η 2 *η 3 *η 4 *η 5 (5)
wherein eta is 1 Contribution factor, eta, to the volumetric efficiency of the gas pump for the angle of installation of the gas pump 2 Is a factor, eta, of the contribution of the gas pressure in the gas tank to the volumetric efficiency of the gas pump 3 Is a contribution factor, eta, of the gas temperature in the gas tank to the volumetric efficiency of the gas pump 4 Is a contribution factor, eta, of the gas liquid level in the gas tank to the volumetric efficiency of the gas pump 5 Is a factor contributing to the volumetric efficiency of the gas pump from the engine speed.
In some embodiments of the invention, η 1 、η 2 、η 3 、η 4 、η 5 The calibration is carried out according to the installation angle of the gas pump, the gas pressure in the gas tank, the natural gas temperature in the gas tank, the gas liquid level in the gas tank and the engine rotating speed respectively, and calibration data are stored in an engine system.
In some embodiments of the present invention, the method for calibrating the volumetric efficiency η of the fuel-air pump comprises:
acquiring the rotating speed of an engine;
gas slow-obtaining deviceThe variation value delta P of the pressure in the flushing tank in the process of one cycle of the fuel pump 0 And the weight M2 of fuel gas consumed by the engine in one cycle on the fuel gas pump 0 ；
Calculating the volumetric efficiency eta of the fuel pump at the engine speed according to the equations (2) to (4) 0 ；
Comparative real-time volumetric efficiency eta 0 And the volumetric efficiency η stored in the system;
controlling the real-time volumetric efficiency eta according to the fact that the difference delta eta of the real-time volumetric efficiency and the volumetric efficiency is larger than the difference threshold value of the volumetric efficiency 0 And replacing the stored volumetric efficiency eta in the system and controlling the fault of the early warning system.
A second aspect of the invention provides an engine system configured to execute the control method of the engine system according to any one of the above embodiments, the engine system including:
an engine;
the engine is in driving connection with the hydraulic pump;
the hydraulic pump is in driving connection with the gas pump;
the engine is communicated with the gas tank through a gas pipeline, and a first temperature sensor, a first pressure sensor and a liquid level sensor are arranged in the gas tank;
the gas buffer tank is arranged on the gas pipeline, and a second temperature sensor and a second pressure sensor are arranged in the gas buffer tank;
and the controller is respectively electrically connected with the engine, the first temperature sensor, the first pressure sensor, the liquid level sensor, the second temperature sensor and the second pressure sensor.
An engine system according to an embodiment of the present invention.
In addition, the engine system according to the embodiment of the invention may further have the following technical features:
in some embodiments of the invention, the engine system further comprises an oil tank and a hydraulic pipeline, the hydraulic pipeline is communicated with the oil tank and the gas pump, and the hydraulic pipeline is provided with the hydraulic pump.
In some embodiments of the present invention, the engine system further comprises a hydraulic control valve disposed on the hydraulic line, and the hydraulic control valve is electrically connected to the controller.
Drawings
Various additional advantages and benefits will become apparent to those of ordinary skill in the art upon reading the following detailed description of the preferred embodiments. The drawings are only for purposes of illustrating the preferred embodiments and are not to be construed as limiting the invention. Also, like parts are designated by like reference numerals throughout the drawings. In the drawings:
FIG. 1 is a flow chart illustrating a method of controlling an engine system according to an embodiment of the present invention;
fig. 2 is a schematic structural diagram of an engine system according to an embodiment of the present invention.
The reference symbols in the drawings denote the following:
100: an engine system;
10: an engine;
20: a hydraulic pump;
30: a fuel-air pump;
40: gas tank, 41: first temperature sensor, 42: first pressure sensor, 43: a second temperature sensor;
50: a gas line;
60: gas buffer tank, 61: second temperature sensor, 62: a second pressure sensor;
70: a controller;
80: an oil tank;
90: hydraulic line, 91: an oil inlet pipe and 92: an oil return pipe;
110: and (4) a hydraulic control valve.
Detailed Description
Exemplary embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. While exemplary embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be embodied in various forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art.
It is to be understood that the terminology used herein is for the purpose of describing particular example embodiments only, and is not intended to be limiting. As used herein, the singular forms "a", "an" and "the" may be intended to include the plural forms as well, unless the context clearly indicates otherwise. The terms "comprises," "comprising," "including," and "having" are inclusive and therefore specify the presence of stated features, steps, operations, elements, and/or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and/or groups thereof.
Although the terms first, second, third, etc. may be used herein to describe various elements, components, regions, layers and/or sections, these elements, components, regions, layers and/or sections should not be limited by these terms. These terms may be only used to distinguish one element, component, region, layer or section from a second region, layer or section. Terms such as "first," "second," and other numerical terms when used herein do not imply a sequence or order unless clearly indicated by the context. Thus, a first element, component, region, layer or section discussed below could be termed a second element, component, region, layer or section without departing from the teachings of the example embodiments.
For convenience of description, spatially relative terms, such as "inner", "outer", "lower", "below", "upper", "above", and the like, may be used herein to describe one element or feature's relationship to another element or feature as illustrated in the figures. Such spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "below" or "beneath" other elements or features would then be oriented "above" or "over" the other elements or features. Thus, the example term "below … …" can include both an orientation of above and below. The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
As shown in fig. 1, an embodiment of a first aspect of the invention proposes a control method of an engine system, the control method including the steps of:
s1: the maximum pressure value P1 of the gas buffer tank and the initial calculation pressure value P2 of the gas pressurization prediction model;
s2: acquiring a real-time pressure value P of a gas pressure buffer tank;
s3: comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1;
s4: according to the fact that the real-time pressure value P is not less than the initial calculation pressure value P2 and is less than the maximum pressure value P1, the cycle number N of the gas pump needed by the gas buffer tank is calculated through the real-time pressure value P and a gas pressurization prediction model * ；
S5: according to N * Not less than 1, controlling the fuel gas pump to perform the next working cycle;
s6: according to N * And if the air quantity is less than 1, controlling the fuel gas pump to stop working.
According to the control method of the engine system, the real-time pressure value P in the gas buffer tank is compared with the initial calculation pressure value P2 of the gas pressurization estimation model, and if the real-time pressure value P is not less than the initial calculation pressure value P2 and is less than the maximum pressure value P1, the cycle number N of the gas pump required by the gas buffer tank is calculated * If N is * Not less than 1, that is, the pressure in the gas buffer tank is not less than the pressure generated in the gas buffer tank by the gas pump working for one cycle, then the control is carried outThe gas-making pump carries out the next working cycle if N * And if the pressure in the fuel gas buffer tank is less than 1, namely the pressure in the fuel gas buffer tank is less than the pressure generated in the fuel gas buffer tank by the fuel gas pump in one working cycle, controlling the fuel gas pump to stop working. According to the invention, through setting the gas pressurization estimation model, the relation between the pressure in the gas buffer tank and the working cycle of the gas pump can be calculated, so that the pressure in the gas buffer tank is prevented from reaching the maximum pressure value P1 when the piston of the gas pump moves to the middle stroke, the piston is prevented from reversely running under the action of the large impact force of high-pressure gas during the middle stroke, the abrasion of the piston is further slowed down, meanwhile, the piston cannot reversely run during the middle stroke, the output quantity of the next working cycle of the gas pump can be ensured, and the power consumption of a pressurization system is further reduced.
In some embodiments of the present invention, after comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1, the method further comprises the following steps: and controlling the fuel gas pump to stop working according to the real-time pressure value P not less than the maximum pressure value P1. And if the real-time pressure value P in the gas buffer tank is equal to P2 after the gas pump performs the next working cycle, controlling the gas pump to stop working so as to avoid damaging the gas buffer tank.
In some embodiments of the present invention, before comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1, the method further comprises the following steps: calibrating a minimum pressure value P3 of the gas buffer tank according to the current running state of the engine; comparing the real-time pressure value P with a minimum pressure value P3; controlling the fuel gas pump to start working according to the condition that the real-time pressure value P is not greater than the minimum pressure value P3; and comparing the real-time pressure value P with an initial calculated pressure value P2 and a maximum pressure value P1 after the real-time pressure value P is greater than the minimum pressure value P3. When real-time pressure value P is less than or equal to minimum pressure value P3, the use that the engine provided is difficult to satisfy to gas in the gas buffer tank, at this moment, need control gas pump work to improve the gas pressure in the gas buffer tank, in order to guarantee the normal operating of engine. After the real-time pressure value P is greater than the minimum pressure value P3, it is necessary to further compare the real-time pressure value P with the initial calculated pressure value P2.
In some embodiments of the present invention, after comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1, the method further comprises the following steps: and controlling the fuel gas pump to be in a working state according to the fact that the real-time pressure value P is larger than the minimum pressure value P3 and smaller than the initial calculated pressure value P2. And when the real-time pressure value P is greater than the minimum pressure value P3 and less than the initial calculated pressure value P2, controlling the fuel gas pump to continue working so as to ensure the normal operation of the engine.
In some embodiments of the invention, if the real-time pressure value P is greater than the minimum pressure value P3 and the real-time pressure value P is less than the initial calculated pressure value P2, the gas pump is controlled to continue to work, and the cycle number N of the gas pump required by the gas buffer tank is calculated through the real-time pressure value P and a gas pressurization prediction model * The method comprises the following steps:
N * ＝(P2-P)/ΔP (1)
in the formula (1), Δ P is a variation value of the pressure in the gas buffer tank within a time of one operation cycle of the gas pump, wherein,
ΔP＝(M1-M2)*RT/V (2)
in formula (2), R is a gas constant of the fuel gas, T is a real-time temperature of the fuel gas buffer tank, V is a volume of the fuel gas buffer tank, M1 is a weight of the fuel gas pumped by the fuel gas pump in one working cycle period of the fuel gas pump, and M2 is a mass of the fuel gas consumed by the engine in one working cycle period of the fuel gas pump, wherein:
M1＝Vd*ρ*η (3)
in the formula (3), Vd is the geometric displacement of the gas pump, rho is the density of liquid gas, eta is the volumetric efficiency of the gas pump,
in the formula (4), Q is the weight of the fuel gas consumed by the engine in unit time, t is the time of one cycle of the working of the fuel gas pump,
η＝η 1 *η 2 *η 3 *η 4 *η 5 (5)
wherein eta 1 is a contribution factor of the installation angle of the gas pump to the volumetric efficiency of the gas pump, eta 2 is a contribution factor of the gas pressure in the gas tank to the volumetric efficiency of the gas pump, eta 3 is a contribution factor of the gas temperature in the gas tank to the volumetric efficiency of the gas pump, eta 4 is a contribution factor of the gas liquid level in the gas tank to the volumetric efficiency of the gas pump, and eta 5 is a contribution factor of the engine speed to the volumetric efficiency of the gas pump.
Specifically, η 1, η 2, η 3, η 4, η 5 are respectively calibrated according to the installation angle of the gas pump, the gas pressure in the gas tank, the natural gas temperature in the gas tank, the gas liquid level in the gas tank, and the engine speed, and the calibration data are stored in the engine system.
In further embodiments of the present invention, the volumetric efficiency η of the fuel pump may also be calibrated by a calibration method comprising the steps of:
acquiring the rotating speed of an engine;
obtaining the variation value delta P of the pressure in the gas buffer tank in the last circulation process of the gas pump 0 And the weight M2 of fuel gas consumed by the engine in one cycle on the fuel gas pump 0 ；
Calculating the volumetric efficiency eta of the fuel pump at the engine speed according to the equations (2) to (4) 0 ；
Comparative real-time volumetric efficiency eta 0 And the volumetric efficiency η stored in the system;
controlling the real-time volumetric efficiency eta according to the fact that the difference delta eta of the real-time volumetric efficiency and the volumetric efficiency is larger than the difference threshold value of the volumetric efficiency 0 And replacing the volumetric efficiency eta stored in the system, and controlling the fault of the early warning system.
The calibration method calculates the volumetric efficiency eta in real time at a certain speed of the engine 0 Comparing real time volumetric efficiency eta 0 The difference value delta eta between the stored volume efficiency eta in the system, if the delta eta is less than or equal to the difference threshold value of the volume efficiency check, the volume efficiency eta corresponding to the speed stored in the engine is reserved, and if the real-time volume efficiency eta is 0 If the volumetric efficiency eta is less than the same as the stored volumetric efficiency eta in the engine, the system explodes and firesGas inefficiency and use of real-time volumetric efficiency eta 0 replacement The volumetric efficiency eta, so that the stored volumetric efficiency in the engine system always conforms to the actual working state of the engine gas system.
The iterative method of the volumetric efficiency η takes the engine rotation speed as a variable, other parameters (the installation angle of the gas pump, the gas pressure in the gas tank, the natural gas temperature in the gas tank, and the gas liquid level in the gas tank) as quantitative values, and also takes the installation angle of the gas pump, the gas pressure in the gas tank, the natural gas temperature in the gas tank, or the gas liquid level in the gas tank as variable values, and other parameters are quantitative values, and updates the data of the volumetric efficiency in a real-time state into the system.
A second aspect of the present invention provides an engine system 100, the engine system 100 being configured to execute the control method of the engine system according to any one of the embodiments, the engine system 100 including: engine 10, hydraulic pump 20, gas pump 30, gas jar 40, gas buffer tank 60 and controller 70, concretely, engine 10 is connected with hydraulic pump 20 drive, hydraulic pump 20 is connected with gas pump 30 drive, gas pump 30 sets up in gas jar 40, gas pump 30 is used for driving the gas in the gas jar 40, engine 10 passes through gas pipeline 50 intercommunication with gas jar 40, be equipped with first temperature sensor 41 in the gas jar 40, first pressure sensor 42 and level sensor 43, gas buffer tank 60 sets up on gas pipeline 50, be equipped with second temperature sensor 61 and second pressure sensor 62 in the gas buffer tank 60, controller 70 respectively with engine 10, first temperature sensor 41, first pressure sensor 42, level sensor 43, second temperature sensor 61, second pressure sensor 62 electricity is connected.
Specifically, the controller 70 acquires the pressure, temperature and liquid level in the gas tank 40 through the first temperature sensor 41, the first pressure sensor 42 and the liquid level sensor 43, acquires the temperature and pressure in the gas buffer tank 60 through the second temperature sensor 61 and the second pressure sensor 62, and the controller 70 acquires the pressure, temperature and liquid level in the gas tank 40, pressure and temperature of the gas buffer tank 60, volume (constant) of the gas buffer tank 60, and gas level (constant) of the gas buffer tank 60 through the pressure of the gas tank 40, the temperature of the gas tank 40, the liquid level of the gas tank 40, and the pressure and temperature of the gas buffer tank 60Calculating N by parameters such as the weight Vd of the gas pumped by the pump 30 in unit time, the volume rho of the gas liquid, the volumetric efficiency eta of the gas pump 30, and the time t of one cycle of the gas pump * 。
According to the engine system 100 of the embodiment of the invention, the engine 10 drives the hydraulic pump 20 to act through the rear force taking mechanism so as to convey hydraulic oil into the fuel gas pump 30, so that the fuel gas pump 30 acts, the fuel gas pump 30 acts in the fuel gas tank 40 so as to enable fuel gas to enter the fuel gas buffer tank 60 from the fuel gas tank 40, the controller 70 obtains the real-time pressure value P of the fuel gas buffer tank 60 through the second pressure sensor 53 in the fuel gas buffer tank 60, compares the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1, and starts to calculate the cycle number N of the fuel gas pump 30 required by the fuel gas buffer tank 60 if the real-time pressure value P is not less than the initial calculated pressure value P2 and is less than the maximum pressure value P1 * If N is present * Not less than 1, i.e., the pressure in the gas buffer tank 60 is not less than the pressure generated in the gas buffer tank 60 by the operation of the gas pump 30 for one cycle, the gas pump 30 is controlled to perform the next operation cycle, if N is * And if the pressure in the gas buffer tank 60 is less than 1, namely the pressure in the gas buffer tank 60 is less than the pressure generated in the gas buffer tank 60 by the gas pump 30 in one working cycle, the gas pump 30 is controlled to stop working. The controller is used for calculating the relation between the pressure in the gas buffer tank and the working cycle of the gas pump, so that the pressure in the gas buffer tank is prevented from reaching the maximum pressure value P1 when the piston of the gas pump moves to the middle stroke, the piston is prevented from reversely running under the action of the large impact force of high-pressure gas during the middle stroke, the abrasion of the piston is further reduced, meanwhile, the piston cannot reversely run during the middle stroke, the output quantity of the next working cycle of the gas pump can be ensured, and the power consumption of a pressurization system is further reduced.
In some embodiments of the present invention, the engine system 100 further includes an oil tank 80 and a hydraulic line 90, the hydraulic line 90 connects the oil tank 80 and the gas pump 30, and the hydraulic line 90 is provided with the hydraulic pump 20. In this embodiment, the hydraulic pipeline 90 includes an oil inlet pipe 91 and an oil return pipe 92, two ends of the oil inlet pipe 91 are connected to the oil tank 80 and the gas pump 30, the hydraulic pump 20 is disposed on the oil inlet pipe 91, the oil inlet pipe 91 is used for conveying hydraulic oil to the gas pump 30, two ends of the oil return pipe 92 are connected to the gas pump 30 and the oil tank 80, and the oil return pipe 92 is used for conveying hydraulic oil from the gas pump 30 to the oil tank 80. The controller 70 controls the engine 10 to drive the hydraulic pump 20 to suck hydraulic oil from the oil tank 80 through the rear pressure taking mechanism and to deliver the hydraulic oil to the gas pump 30 through the oil inlet pipe 91, thereby controlling the gas to be output from the gas tank 40. The hydraulic oil in the fuel pump 30 is supplied to the oil tank 80 through the oil return pipe 92.
Further, the engine system 100 further includes a hydraulic control valve 110, the hydraulic control valve 110 is disposed on the oil inlet pipe 91 and the oil return pipe 92 of the hydraulic line 90, and the hydraulic control valve 110 is electrically connected to the controller 70, and the controller 70 is configured according to N * When the real-time pressure value P is less than 1 or the real-time pressure value P is greater than or equal to the maximum pressure value P1, the hydraulic control valve 110 is controlled to close to prevent the hydraulic oil from flowing in the oil inlet pipe 91 or the oil return pipe 92, so as to control the gas pump 30 to stop operating.
The above description is only for the preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are also included in the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.
Claims (9)
1. A control method of an engine system, characterized by comprising the steps of:
calibrating a maximum pressure value P1 of the gas buffer tank and an initial calculation pressure value P2 of the gas pressurization estimation model;
acquiring a real-time pressure value P of a gas pressure buffer tank;
comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1;
according to the fact that the real-time pressure value P is not less than the initial calculation pressure value P2 and is less than the maximum pressure value P1, the cycle number N of the gas pump needed by the gas buffer tank is calculated through the real-time pressure value P and a gas pressurization prediction model * ；
According to N * Not less than 1, and controlling the fuel gas pump to operateA working cycle;
according to N * If the pressure is less than 1, controlling the fuel gas pump to stop working;
calculating the cycle number N of the gas pump required by the gas buffer tank through the real-time pressure value P and the gas pressurization pre-estimation model * The method comprises the following steps:
N * ＝(P2-P)/ΔP (1)
in the formula (1), Δ P is a variation value of the pressure in the gas buffer tank within a time of one working cycle of the gas pump, wherein,
ΔP＝(M1-M2)*RT/V (2)
in formula (2), R is a gas constant of the fuel gas, T is a real-time temperature of the fuel gas buffer tank, V is a volume of the fuel gas buffer tank, M1 is a weight of the fuel gas pumped by the fuel gas pump in one working cycle period of the fuel gas pump, M2 is a mass of the fuel gas consumed by the engine in one working cycle period of the fuel gas pump, wherein:
M1＝Vd*ρ*η (3)
in the formula (3), Vd is the geometric displacement of the gas pump, rho is the density of liquid gas, eta is the volumetric efficiency of the gas pump,
in the formula (4), Q is the weight of the fuel gas consumed by the engine in unit time, t is the time of one cycle of the working of the fuel gas pump,
η＝η 1 *η 2 *η 3 *η 4 *η 5 (5)
wherein eta 1 Contribution factor of gas pump installation angle to gas pump volumetric efficiency, η 2 Is a factor, eta, of the contribution of the gas pressure in the gas tank to the volumetric efficiency of the gas pump 3 Is a contribution factor, eta, of the gas temperature in the gas tank to the volumetric efficiency of the gas pump 4 Is a contribution factor, eta, of the gas liquid level in the gas tank to the volumetric efficiency of the gas pump 5 For engine speed toThe contribution factor of the volumetric efficiency of the air pump.
2. The method of controlling an engine system according to claim 1, wherein said comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1 further comprises the steps of:
and controlling the fuel gas pump to stop working according to the real-time pressure value P not less than the maximum pressure value P1.
3. The method of controlling an engine system according to claim 1, wherein said comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1, further comprises the steps of:
calibrating a minimum pressure value P3 of the gas buffer tank according to the current running state of the engine;
comparing the real-time pressure value P with a minimum pressure value P3;
controlling the fuel gas pump to start working according to the condition that the real-time pressure value P is not greater than the minimum pressure value P3;
and comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1 after the real-time pressure value P is larger than the minimum pressure value P3.
4. The method of controlling an engine system according to claim 3, wherein said comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1 further comprises the steps of:
and controlling the fuel gas pump to be in a working state according to the fact that the real-time pressure value P is larger than the minimum pressure value P3 and smaller than the initial calculated pressure value P2.
5. The control method of an engine system according to claim 1, wherein η 1 、η 2 、η 3 、η 4 、η 5 And calibrating according to the installation angle of the gas pump, the gas pressure in the gas tank, the gas temperature in the gas tank, the gas liquid level in the gas tank and the engine rotating speed respectively, and storing calibration data in an engine system.
6. The control method of an engine system according to claim 5, wherein the calibration of the volumetric efficiency η of the fuel pump comprises the steps of:
acquiring the rotating speed of an engine;
obtaining the variation value delta P of the pressure in the gas buffer tank in the last circulation process of the gas pump 0 And the weight M2 of fuel gas consumed by the engine in one cycle on the fuel gas pump 0 ；
Calculating the volumetric efficiency eta of the fuel pump at the engine speed according to the equations (2) to (4) 0 ；
Comparative real-time volumetric efficiency eta 0 And the volumetric efficiency η stored in the system;
controlling the real-time volumetric efficiency eta according to the fact that the difference delta eta of the real-time volumetric efficiency and the volumetric efficiency is larger than the difference threshold value of the volumetric efficiency 0 And replacing the stored volumetric efficiency eta in the system and controlling the fault of the early warning system.
7. An engine system configured to execute a control method of an engine system according to any one of claims 1 to 6, characterized by comprising:
an engine;
the engine is in driving connection with the hydraulic pump;
the hydraulic pump is in driving connection with the gas pump;
the engine is communicated with the gas tank through a gas pipeline, and a first temperature sensor, a first pressure sensor and a liquid level sensor are arranged in the gas tank;
the gas buffer tank is arranged on the gas pipeline, and a second temperature sensor and a second pressure sensor are arranged in the gas buffer tank;
a controller respectively connected with the hairThe engine, the first temperature sensor, the first pressure sensor, the liquid level sensor, the second temperature sensor and the second pressure sensor are electrically connected, and the controller is used for calibrating a maximum pressure value P1 of the gas buffer tank and an initial calculation pressure value P2 of a gas pressurization prediction model; the real-time pressure value P of the gas pressure buffer tank is obtained; for comparing the real-time pressure value P with the initial calculated pressure value P2 and the maximum pressure value P1; the system is used for calculating the cycle number N of the gas pump required by the gas buffer tank through the real-time pressure value P and a gas pressurization estimation model according to the fact that the real-time pressure value P is not less than the initial calculation pressure value P2 and is less than the maximum pressure value P1 * (ii) a For according to N * Not less than 1, controlling the fuel gas pump to carry out the next working cycle; for according to N * If the air quantity is less than 1, controlling the fuel gas pump to stop working;
calculating the cycle number N of the gas pump required by the gas buffer tank through the real-time pressure value P and the gas pressurization pre-estimation model * The method comprises the following steps:
N * ＝(P2-P)/ΔP (1)
in the formula (1), Δ P is a variation value of the pressure in the gas buffer tank within a time of one working cycle of the gas pump, wherein,
ΔP＝(M1-M2)*RT/V (2)
in formula (2), R is a gas constant of the fuel gas, T is a real-time temperature of the fuel gas buffer tank, V is a volume of the fuel gas buffer tank, M1 is a weight of the fuel gas pumped by the fuel gas pump in one working cycle period of the fuel gas pump, M2 is a mass of the fuel gas consumed by the engine in one working cycle period of the fuel gas pump, wherein:
M1＝Vd*ρ*η (3)
in the formula (3), Vd is the geometric displacement of the gas pump, rho is the density of liquid gas, eta is the volumetric efficiency of the gas pump,
in the formula (4), Q is the weight of the fuel gas consumed by the engine in unit time, t is the time of one cycle of the working of the fuel gas pump,
η＝η 1 *η 2 *η 3 *η 4 *η 5 (5)
wherein eta is 1 Contribution factor, eta, to the volumetric efficiency of the gas pump for the angle of installation of the gas pump 2 Is a factor, eta, of the contribution of the gas pressure in the gas tank to the volumetric efficiency of the gas pump 3 Is a factor, eta, of the contribution of the gas temperature in the gas tank to the volumetric efficiency of the gas pump 4 Is a contribution factor, eta, of the gas liquid level in the gas tank to the volumetric efficiency of the gas pump 5 Is a factor contributing to the volumetric efficiency of the gas pump from the engine speed.
8. The engine system of claim 7, further comprising an oil tank and a hydraulic line, the hydraulic line communicating the oil tank with the gas pump, the hydraulic line having the hydraulic pump disposed thereon.
9. The engine system of claim 8, further comprising a hydraulic control valve disposed on the hydraulic line and electrically connected to the controller.
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| CN114312288B (en) * | 2021-12-28 | 2023-04-11 | 三一汽车制造有限公司 | Gas storage system, exhaust control method and device thereof, storage medium and gas vehicle |
| CN114790981B (en) * | 2022-04-20 | 2024-02-20 | 潍柴动力股份有限公司 | Method for preventing hydraulic pump of HPDI engine air supply system from short stroke |
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