CN114790981B - Method for preventing hydraulic pump of HPDI engine air supply system from short stroke - Google Patents
Method for preventing hydraulic pump of HPDI engine air supply system from short stroke Download PDFInfo
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- CN114790981B CN114790981B CN202210419074.3A CN202210419074A CN114790981B CN 114790981 B CN114790981 B CN 114790981B CN 202210419074 A CN202210419074 A CN 202210419074A CN 114790981 B CN114790981 B CN 114790981B
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- 238000000034 method Methods 0.000 title claims abstract description 34
- 230000006835 compression Effects 0.000 claims abstract description 218
- 238000007906 compression Methods 0.000 claims abstract description 218
- 239000000446 fuel Substances 0.000 claims abstract description 115
- 238000005086 pumping Methods 0.000 claims abstract description 72
- 230000002035 prolonged effect Effects 0.000 abstract description 3
- 239000007789 gas Substances 0.000 description 20
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 4
- 239000010720 hydraulic oil Substances 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 239000003345 natural gas Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000002737 fuel gas Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000008707 rearrangement Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/10—Other safety measures
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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
- F02M21/0293—Safety devices; Fail-safe measures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2207/00—External parameters
- F04B2207/02—External pressure
-
- 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
- Y02T10/30—Use of alternative fuels, e.g. biofuels
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Combustion & Propulsion (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention discloses a method for preventing a hydraulic pump of an HPDI engine air supply system from generating a short stroke, which comprises the steps of calculating the pressure in a buffer tank after the current compression stroke according to the actual pressure of the buffer tank before the current compression stroke is opened, the pressure corresponding to the fuel which is driven into the buffer tank by the current compression stroke and the pressure corresponding to the fuel which is consumed by the engine in the current compression stroke and the current back suction stroke; judging whether the pressure in the buffer tank after the current compression stroke is greater than the set maximum bearing pressure of the buffer tank, and if the pressure in the buffer tank after the current compression stroke is greater than the set maximum bearing pressure of the buffer tank, not opening the current compression stroke; and if the pressure in the buffer tank after the current compression stroke is less than or equal to the set maximum bearing pressure of the buffer tank, opening the current compression stroke. The hydraulic pump can be prevented from stopping working in the compression stroke and the back-pumping stroke, and the service life of the hydraulic pump can be prolonged.
Description
Technical Field
The invention relates to the technical field of HPDI engines, in particular to a method for preventing a hydraulic pump of an air supply system of an HPDI engine from short stroke.
Background
The HPDI (High Pressure Direct Injection ) engine is a high power in-cylinder high pressure direct injection compression ignition natural gas engine that uses natural gas as the primary fuel while ensuring power, torque and efficiency of the primary diesel engine. In the working process of the HPDI engine, the buffer tank provides the gas fuel required by the engine, the gas fuel in the buffer tank needs to be kept in a high-pressure state, along with the running of the engine, the fuel in the buffer tank is continuously reduced, when the pressure is reduced to a certain degree, generally to 28MPa, the pressure requirement of the engine on the gas fuel cannot be met, at the moment, the gas fuel in the LNG gas tank needs to be continuously pumped into the buffer tank through the compression stroke and the back-pumping stroke of the hydraulic pump until the pressure of the buffer tank reaches the set maximum bearing pressure of the buffer tank, and the maximum bearing pressure of the buffer tank is generally set to be 32MPa. At present, the control method of the engine air supply system is that when the actual pressure of the buffer tank reaches 32Mpa, the hydraulic pump stops working. However, under normal conditions, when the actual pressure of the buffer tank reaches 32Mpa, the hydraulic pump is in the compression stroke and the back-pumping stroke process, the back-pumping stroke is not ended, a short stroke appears, the hydraulic oil of the hydraulic pump is suddenly released, the piston of the hydraulic pump rapidly ends the back-pumping stroke under the action of high-pressure fuel gas in the cylinder, the stress impact of the piston is larger, the wearing is aggravated, the service life of the hydraulic pump can be influenced, and if the actual pressure of the buffer tank reaches 32Mpa, the gas fuel is continuously pumped to the buffer tank until the back-pumping stroke is ended, the pressure in the buffer tank exceeds 32Mpa, and the pressure-bearing limit of the buffer tank is exceeded, so that a certain potential safety hazard exists.
Disclosure of Invention
The invention aims to provide a method for preventing a hydraulic pump of an air supply system of an HPDI engine from generating a short stroke, so as to solve the problem that when the actual pressure of a buffer tank reaches the set maximum bearing pressure of the buffer tank, the hydraulic pump is in a compression stroke and a back-pumping stroke, the back-pumping stroke is not ended, and the service life of the hydraulic pump is influenced when the hydraulic pump stops working.
To achieve the purpose, the invention adopts the following technical scheme:
a method of preventing a short stroke of a hydraulic pump of an air supply system of an HPDI engine, comprising:
determining an actual pressure P of a surge tank before a current compression stroke is opened 0 ；
Estimating a pressure P corresponding to fuel injected into a buffer tank in a current compression stroke 1 ；
Estimating a pressure P corresponding to fuel consumed by the engine in a current compression stroke and a current return stroke 2 ；
Opening the front buffer tank according to the actual pressure P of the current compression stroke 0 The pressure P corresponding to the fuel which is injected into the buffer tank in the current compression stroke 1 And the pressure P corresponding to the fuel consumed by the engine in the current compression stroke and the current back-pumping stroke 2 Calculating the pressure P in the buffer tank after the current compression stroke 3 ；
Before the current compression stroke is started, judging the pressure P in the buffer tank after the current compression stroke 3 Whether the pressure is larger than the set maximum bearing pressure of the buffer tank, if so, the pressure P in the buffer tank after the current compression stroke 3 When the pressure is larger than the set maximum bearing pressure of the buffer tank, the current compression stroke is not started; if the pressure P in the buffer tank is after the current compression stroke 3 And if the pressure is smaller than or equal to the set maximum bearing pressure of the buffer tank, opening the current compression stroke.
As a preferable mode of the method for preventing the hydraulic pump of the air supply system of the HPDI engine from short-stroke, the method is characterized in that the actual pressure P of the front buffer tank is opened according to the current compression stroke 0 The pressure P corresponding to the fuel which is injected into the buffer tank in the current compression stroke 1 And the pressure P corresponding to the fuel consumed by the engine in the current compression stroke and the current back-pumping stroke 2 Calculating the pressure P in the buffer tank after the current compression stroke 3 Comprising the following steps: by the formula: p (P) 3 ＝P 0 +P 1 -P 2 Calculating the current compressionPressure P in surge tank after stroke 3 。
As a preferable scheme of the method for preventing the hydraulic pump of the air supply system of the HPDI engine from short stroke, the estimated pressure P corresponding to the fuel injected into the buffer tank in the current compression stroke 1 Comprising the following steps:
determining a pressure P corresponding to fuel injected into the buffer tank in a last compression stroke 1 ’；
The pressure P corresponding to the fuel which is injected into the buffer tank in the current compression stroke 1 Equal to the pressure P corresponding to the fuel injected into the buffer tank in the last compression stroke 1 ’。
As a preferable mode of the method for preventing the hydraulic pump of the air supply system of the HPDI engine from short-stroke, the method determines the pressure P corresponding to the fuel injected into the buffer tank in the last compression stroke 1 ' comprising:
determining the increased pressure delta P of the buffer tank in the last compression stroke and the last back-pumping stroke;
determining a pressure P corresponding to fuel consumed by the engine in a last compression stroke and a last return stroke 2 ’；
The pressure P corresponding to the fuel which is injected into the buffer tank in the last compression stroke 1 ' equal to the pressure delta P increased by the buffer tank in the last compression stroke and the last back-pumping stroke plus the pressure P corresponding to the fuel consumed by the engine in the last compression stroke and the last back-pumping stroke 2 ’。
As a preferred embodiment of the method for preventing the hydraulic pump of the air supply system of the HPDI engine from having a short stroke, the determining the pressure Δp increased in the surge tank in the last compression stroke and the last pumping back stroke includes:
the pressure delta P increased by the buffer tank in the last compression stroke and the last back-pumping stroke is equal to the actual pressure P of the buffer tank before the current compression stroke is opened 0 Subtracting the actual pressure P of the buffer tank before the last compression stroke is opened 0 ’。
As one of the above-mentioned methods for preventing the occurrence of short strokes of the hydraulic pump of the air supply system of the HPDI enginePreferably, the method determines the pressure P corresponding to the fuel consumed by the engine in the last compression stroke and the last back-pumping stroke 2 ' comprising:
determining a total fuel consumption of a previous compression stroke and a previous back-pumping stroke;
obtaining the corresponding pressure P of the fuel consumed by the engine in the last compression stroke and the last back-pumping stroke according to the total fuel consumption of the last compression stroke and the last back-pumping stroke and an ideal gas state equation 2 ’。
As a preferred embodiment of the method for preventing the hydraulic pump of the air supply system of the HPDI engine from having a short stroke, the determining the total fuel consumption of the last compression stroke and the last return stroke includes:
determining the total duration of the last compression stroke and the last back-pumping stroke and the fuel consumption rate of the last compression stroke and the last back-pumping stroke;
the total fuel consumption of the last compression stroke and the last withdrawal stroke is equal to the total duration of the last compression stroke and the last withdrawal stroke multiplied by the fuel consumption rate of the last compression stroke and the last withdrawal stroke.
As a preferable scheme of the method for preventing the hydraulic pump of the air supply system of the HPDI engine from short stroke, the pressure P corresponding to the fuel consumed by the engine in the current compression stroke and the current back-pumping stroke is estimated 2 Comprising the following steps:
determining a total fuel consumption of the current compression stroke and the current back-pumping stroke;
obtaining the corresponding pressure P of the fuel consumed by the engine in the current compression stroke and the back-pumping stroke according to the total fuel consumption of the current compression stroke and the current back-pumping stroke and an ideal gas state equation 2 。
As a preferred embodiment of the method for preventing the hydraulic pump of the air supply system of the HPDI engine from short-stroke, the determining the total fuel consumption of the current compression stroke and the current back-pumping stroke includes:
determining the total duration of the current compression stroke and the current back-pumping stroke and the fuel consumption rate of the current compression stroke and the current back-pumping stroke;
the total fuel consumption of the current compression stroke and the current draw-back stroke is equal to the total duration of the current compression stroke and the current draw-back stroke multiplied by the fuel consumption rate of the current compression stroke and the current draw-back stroke.
As a preferred embodiment of the method for preventing the hydraulic pump of the air supply system of the HPDI engine from short-stroke, the determining the total duration of the current compression stroke and the current back-pumping stroke and the fuel consumption rate of the current compression stroke and the current back-pumping stroke includes:
the total duration of the current compression stroke and the current back-pumping stroke is equal to the total duration of the last compression stroke and the last back-pumping stroke; the fuel consumption rate of the current compression stroke and the current draw back stroke is equal to the maximum fuel consumption rate of the engine calibration.
The invention has the beneficial effects that:
the invention aims to provide a method for preventing a hydraulic pump of an HPDI engine air supply system from generating a short stroke, which is used for calculating the pressure in a buffer tank after a current compression stroke according to the actual pressure of the buffer tank before the current compression stroke is opened, the pressure corresponding to the fuel which is driven into the buffer tank in the current compression stroke and the pressure corresponding to the fuel which is consumed by the engine in the current compression stroke and the current back-pumping stroke; before the current compression stroke is started, judging the pressure P in the buffer tank after the current compression stroke 3 Whether the pressure is larger than the set maximum bearing pressure of the buffer tank, if the pressure P in the buffer tank is after the current compression stroke 3 When the pressure is larger than the set maximum bearing pressure of the buffer tank, the current compression stroke is not started; if the pressure P in the buffer tank is after the current compression stroke 3 And if the pressure is less than or equal to the set maximum bearing pressure of the buffer tank, the current compression stroke is started. When the calculated pressure in the buffer tank after the current compression stroke is greater than the set maximum bearing pressure of the buffer tank, if the current compression stroke is carried out, the pressure in the buffer tank after the current compression stroke is extremely high in practiceThe pressure is more than the maximum bearing pressure of the buffer tank, and a certain potential safety hazard exists. And, if the current compression stroke is performed, when the pressure in the buffer tank is equal to the set maximum bearing pressure of the buffer tank, the current compression stroke and the current back-pumping stroke are not finished, the piston of the hydraulic pump may be stopped at the middle position, and a short stroke occurs, resulting in a reduction in the service life of the hydraulic pump. Therefore, if the pressure in the buffer tank after the current compression stroke is greater than the set buffer tank maximum bearing pressure, the current compression stroke is not opened, and if the pressure in the buffer tank after the current compression stroke is less than or equal to the set buffer tank maximum bearing pressure, the current compression stroke is opened. The short stroke of the hydraulic pump can be prevented from affecting the life of the hydraulic pump. On the basis of the existing engine configuration, whether the hydraulic pump has a short stroke or not can be judged by the ECU calculation without other equipment, and the service life of the hydraulic pump is prolonged.
Drawings
FIG. 1 is a flow chart of a method for preventing short travel of a hydraulic pump of an HPDI engine air supply system provided in an embodiment of the present invention.
Detailed Description
The invention is described in further detail below with reference to the drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting thereof. It should be further noted that, for convenience of description, only some, but not all of the structures related to the present invention are shown in the drawings.
In the description of the present invention, unless explicitly stated and limited otherwise, the terms "connected," "connected," and "fixed" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
In the present invention, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.
In the description of the present embodiment, the terms "upper", "lower", "right", and the like are based on the orientation or positional relationship shown in the drawings, and are merely for convenience of description and simplicity of operation, and do not indicate or imply that the apparatus or element in question must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the invention. Furthermore, the terms "first," "second," and the like, are used merely for distinguishing between descriptions and not for distinguishing between them.
The invention provides a method for preventing a hydraulic pump of an HPDI engine air supply system from short-stroke, as shown in FIG. 1, comprising the following steps:
determining an actual pressure P of a surge tank before a current compression stroke is opened 0 。
It will be appreciated that the surge tank is provided with a pressure sensor. Detecting the actual pressure P of the buffer tank before the current compression stroke is opened by a pressure sensor of the buffer tank 0 。
Estimating a pressure P corresponding to fuel injected into a buffer tank in a current compression stroke 1 。
Specifically, the current compression stroke is driven into the buffer tank at a pressure P corresponding to the fuel 1 Equal to the pressure P corresponding to the fuel injected into the buffer tank in the last compression stroke 1 '. It will be appreciated that the pressure corresponding to the fuel being injected into the surge tank during the compression stroke is dictated by the efficiency, back pressure, of the hydraulic pumpAnd the influence of the flow rate of the hydraulic oil, the pressure corresponding to the fuel actually injected into the surge tank in the compression stroke is not fixed. So that the last compression stroke is driven into the buffer tank at the corresponding pressure P 1 ' pressure P corresponding to fuel injected into the surge tank closest to the current compression stroke 1 。
It will be appreciated that the pressure to which the surge tank is added in the compression and the pumpback strokes is equal to the pressure corresponding to the fuel being driven into the surge tank for the compression stroke minus the pressure corresponding to the fuel being consumed by the engine in the compression and the pumpback strokes. Therefore, the pressure P corresponding to the fuel injected into the surge tank in the previous compression stroke 1 ' equal to the pressure ΔP increased by the surge tank in the last compression stroke and the last return stroke plus the pressure P corresponding to the fuel consumed by the engine in the last compression stroke and the last return stroke 2 ' P 1 ’＝ΔP+P 2 ’。
Specifically, the pressure Δp increased by the surge tank in the last compression stroke and the last return stroke is equal to the actual pressure P of the surge tank before the current compression stroke is opened 0 Subtracting the actual pressure P of the buffer tank before the last compression stroke is opened 0 ' i.e. Δp=p 0 -P 0 '. Actual pressure P of the buffer before opening the current compression stroke 0 And the actual pressure P of the buffer tank before the last compression stroke is opened 0 ' are all detected by the pressure sensor of the buffer vessel.
Specifically, the pressure P corresponding to the fuel consumed by the engine in the last compression stroke and the last pumping back stroke is obtained according to the total fuel consumption of the last compression stroke and the last pumping back stroke and an ideal gas state equation 2 '. The ideal gas state equation is: pv=mrt, where: p is the pressure corresponding to the fuel consumed by the engine in the compression stroke and the back-pumping stroke; v is the volume of the buffer tank; m is the total fuel consumption of the compression stroke and the back-pumping stroke; r is a gas constant, and is a constant related to the gas species; t is the temperature of the buffer tank. Wherein the total fuel consumption of the last compression stroke and the last back-pumping stroke is equal to the total fuel consumption of the last compression stroke and the last back-pumping strokeThe duration is multiplied by the fuel consumption rate of the last compression stroke and the last withdrawal stroke. It will be appreciated that the total duration of the last compression stroke and the last return stroke, and the fuel consumption rate of the last compression stroke and the last return stroke, are calculated by the ECU. The temperature of the buffer tank can be detected by a temperature sensor provided to the buffer tank. From this, in the ideal gas state equation, the volume V of the surge tank, the total fuel consumption m of the compression stroke and the return stroke, the gas constant R, and the temperature T of the surge tank can be known, and the pressure P corresponding to the fuel consumed by the engine in the last compression stroke and the last return stroke can be obtained from the ideal gas state equation 2 ’。
Estimating a pressure P corresponding to fuel consumed by the engine in a current compression stroke and a current return stroke 2 。
Specifically, according to the total fuel consumption and the ideal gas state equation of the current compression stroke and the current back-pumping stroke, the pressure P corresponding to the fuel consumed by the engine in the current compression stroke and the back-pumping stroke is obtained 2 . The ideal gas state equation is: pv=mrt, where: p is the pressure corresponding to the fuel consumed by the engine in the compression stroke and the back-pumping stroke; v is the volume of the buffer tank; m is the total fuel consumption of the compression stroke and the back-pumping stroke; r is a gas constant, and is a constant related to the gas species; t is the temperature of the buffer tank. Wherein the total fuel consumption of the current compression stroke and the current draw-back stroke is equal to the total duration of the current compression stroke and the current draw-back stroke multiplied by the fuel consumption rate of the current compression stroke and the current draw-back stroke. It will be appreciated that the total duration of the current compression stroke and the current draw back stroke, as well as the fuel consumption rate of the current compression stroke and the current draw back stroke, are both calculated by the ECU. The temperature of the buffer tank can be detected by a temperature sensor provided to the buffer tank. Thus, the pressure P corresponding to the fuel consumed by the engine in the current compression stroke and the current back-pumping stroke can be obtained through the ideal gas state equation 2 。
Due to the total duration of the current compression stroke and the current draw back stroke, and the current compression stroke and the current draw backThe fuel consumption rate of the stroke is unknown, so that the total duration of the last compression stroke and the last back-pumping stroke is adopted as the total duration of the current compression stroke and the current back-pumping stroke, and the total duration of the last compression stroke and the last back-pumping stroke can be estimated more accurately. The fuel consumption rates of the current compression stroke and the current draw back stroke employ the maximum fuel consumption rate of the engine calibration. The calculated pressure P corresponding to the fuel consumed by the engine in the current compression stroke and the back-pumping stroke 2 For its maximum predicted value.
Opening the actual pressure P of the front buffer tank according to the current compression stroke 0 Pressure P corresponding to fuel injected into buffer tank in current compression stroke 1 And the pressure P corresponding to the fuel consumed by the engine in the current compression stroke and the current back-pumping stroke 2 Calculating the pressure P in the buffer tank after the current compression stroke 3 。
Specifically, by the formula: p (P) 3 ＝P 0 +P 1 -P 2 Calculating the pressure P in the buffer tank after the current compression stroke 3 。
Before the current compression stroke is started, judging the pressure P in the buffer tank after the current compression stroke 3 Whether the pressure is larger than the set maximum bearing pressure of the buffer tank, if the pressure P in the buffer tank is after the current compression stroke 3 When the pressure is larger than the set maximum bearing pressure of the buffer tank, the current compression stroke is not started; if the pressure P in the buffer tank is after the current compression stroke 3 And if the pressure is less than or equal to the set maximum bearing pressure of the buffer tank, the current compression stroke is started.
Because the fuel consumption rate of the current compression stroke and the current back-pumping stroke adopts the maximum fuel consumption rate calibrated by the engine, the calculated pressure P corresponding to the fuel consumed by the engine in the current compression stroke and the back-pumping stroke 2 For its maximum predicted value, thereby calculating the pressure P in the buffer vessel after the current compression stroke 3 For its minimum predicted value, the pressure P in the buffer tank after the calculated current compression stroke 3 When the pressure is larger than the set maximum bearing pressure of the buffer tank, if the current compression stroke is carried out, the buffer is buffered after the current compression strokeThe pressure in the tank is more likely to be larger than the set maximum bearing pressure of the buffer tank, and certain potential safety hazards exist. And, if the current compression stroke is performed, when the pressure in the buffer tank is equal to the set maximum bearing pressure of the buffer tank, the current compression stroke and the current back-pumping stroke are not finished, the piston of the hydraulic pump may be stopped at the middle position, and a short stroke occurs, resulting in a reduction in the service life of the hydraulic pump. Therefore, if the pressure P in the surge tank after the current compression stroke 3 If the pressure P is larger than the set maximum bearing pressure of the buffer tank, the current compression stroke is not opened, and if the pressure P in the buffer tank is lower than the set maximum bearing pressure of the buffer tank after the current compression stroke 3 And if the pressure is less than or equal to the set maximum bearing pressure of the buffer tank, the current compression stroke is started. The short stroke of the hydraulic pump can be prevented from affecting the life of the hydraulic pump. On the basis of the existing engine configuration, whether the hydraulic pump has a short stroke or not can be judged only through ECU calculation without other equipment, and the service life of the hydraulic pump is prolonged.
It will be appreciated that the operation is performed by starting the hydraulic pump until the actual pressure of the hydraulic pump is reduced to 28Mpa or below.
It is to be understood that the above examples of the present invention are provided for clarity of illustration only and are not limiting of the embodiments of the present invention. Various obvious changes, rearrangements and substitutions can be made by those skilled in the art without departing from the scope of the invention. It is not necessary here nor is it exhaustive of all embodiments. Any modification, equivalent replacement, improvement, etc. which come within the spirit and principles of the invention are desired to be protected by the following claims.
Claims (10)
1. A method of preventing a short stroke of a hydraulic pump of an air supply system of an HPDI engine, comprising:
determining an actual pressure P of a surge tank before a current compression stroke is opened 0 ；
Estimating a pressure P corresponding to fuel injected into a buffer tank in a current compression stroke 1 ；
Estimating the current compression stroke and the current back-pumping strokePressure P corresponding to fuel consumed by engine 2 ；
Opening the front buffer tank according to the actual pressure P of the current compression stroke 0 The pressure P corresponding to the fuel which is injected into the buffer tank in the current compression stroke 1 And the pressure P corresponding to the fuel consumed by the engine in the current compression stroke and the current back-pumping stroke 2 Calculating the pressure P in the buffer tank after the current compression stroke 3 ；
Before the current compression stroke is started, judging the pressure P in the buffer tank after the current compression stroke 3 Whether the pressure is larger than the set maximum bearing pressure of the buffer tank, if so, the pressure P in the buffer tank after the current compression stroke 3 When the pressure is larger than the set maximum bearing pressure of the buffer tank, the current compression stroke is not started; if the pressure P in the buffer tank is after the current compression stroke 3 And if the pressure is smaller than or equal to the set maximum bearing pressure of the buffer tank, opening the current compression stroke.
2. The method for preventing a short stroke of a hydraulic pump of an air supply system of an HPDI engine according to claim 1, wherein said actual pressure P of the open front surge tank is based on said current compression stroke 0 The pressure P corresponding to the fuel which is injected into the buffer tank in the current compression stroke 1 And the pressure P corresponding to the fuel consumed by the engine in the current compression stroke and the current back-pumping stroke 2 Calculating the pressure P in the buffer tank after the current compression stroke 3 Comprising the following steps: by the formula: p (P) 3 ＝P 0 +P 1 -P 2 Calculating the pressure P in the buffer tank after the current compression stroke 3 。
3. The method of claim 1, wherein the predicted pressure P corresponding to fuel injected into the surge tank for the current compression stroke 1 Comprising the following steps:
determining a pressure P corresponding to fuel injected into the buffer tank in a last compression stroke 1 ’；
The currentPressure P corresponding to fuel injected into buffer tank in compression stroke 1 Equal to the pressure P corresponding to the fuel injected into the buffer tank in the last compression stroke 1 ’。
4. A method for preventing a short stroke of a hydraulic pump of an air supply system of an HPDI engine according to claim 3, wherein said determining the pressure P corresponding to the fuel injected into the buffer tank for the last compression stroke 1 ' comprising:
determining the increased pressure delta P of the buffer tank in the last compression stroke and the last back-pumping stroke;
determining a pressure P corresponding to fuel consumed by the engine in a last compression stroke and a last return stroke 2 ’；
The pressure P corresponding to the fuel which is injected into the buffer tank in the last compression stroke 1 ' equal to the pressure delta P increased by the buffer tank in the last compression stroke and the last back-pumping stroke plus the pressure P corresponding to the fuel consumed by the engine in the last compression stroke and the last back-pumping stroke 2 ’。
5. The method of preventing a short stroke of a hydraulic pump of an air supply system of an HPDI engine according to claim 4, wherein said determining the increased pressure Δp of the surge tank during the last compression stroke and the last return stroke comprises:
the pressure delta P increased by the buffer tank in the last compression stroke and the last back-pumping stroke is equal to the actual pressure P of the buffer tank before the current compression stroke is opened 0 Subtracting the actual pressure P of the buffer tank before the last compression stroke is opened 0 ’。
6. The method of preventing a short stroke of a hydraulic pump of an air supply system of an HPDI engine according to claim 4, wherein said determining the pressure P corresponding to the fuel consumed by the engine in the last compression stroke and the last return stroke 2 ' comprising:
determining a total fuel consumption of a previous compression stroke and a previous back-pumping stroke;
obtaining the corresponding pressure P of the fuel consumed by the engine in the last compression stroke and the last back-pumping stroke according to the total fuel consumption of the last compression stroke and the last back-pumping stroke and an ideal gas state equation 2 ’。
7. The method of preventing a short stroke of a hydraulic pump of an air supply system of an HPDI engine according to claim 6, wherein said determining a total fuel consumption of a last compression stroke and a last return stroke comprises:
determining the total duration of the last compression stroke and the last back-pumping stroke and the fuel consumption rate of the last compression stroke and the last back-pumping stroke;
the total fuel consumption of the last compression stroke and the last withdrawal stroke is equal to the total duration of the last compression stroke and the last withdrawal stroke multiplied by the fuel consumption rate of the last compression stroke and the last withdrawal stroke.
8. The method of claim 1, wherein the estimated pressure P corresponds to the fuel consumed by the engine during the current compression stroke and the current return stroke 2 Comprising the following steps:
determining a total fuel consumption of the current compression stroke and the current back-pumping stroke;
obtaining the corresponding pressure P of the fuel consumed by the engine in the current compression stroke and the back-pumping stroke according to the total fuel consumption of the current compression stroke and the current back-pumping stroke and an ideal gas state equation 2 。
9. The method of preventing a short stroke of a hydraulic pump of an air supply system of an HPDI engine according to claim 8, wherein said determining a total fuel consumption of the current compression stroke and current draw back stroke comprises:
determining the total duration of the current compression stroke and the current back-pumping stroke and the fuel consumption rate of the current compression stroke and the current back-pumping stroke;
the total fuel consumption of the current compression stroke and the current draw-back stroke is equal to the total duration of the current compression stroke and the current draw-back stroke multiplied by the fuel consumption rate of the current compression stroke and the current draw-back stroke.
10. The method of preventing a short stroke of a hydraulic pump of an air supply system of an HPDI engine according to claim 9, wherein said determining a total duration of a current compression stroke and a current draw back stroke and a fuel consumption rate of the current compression stroke and the current draw back stroke comprises:
the total duration of the current compression stroke and the current back-pumping stroke is equal to the total duration of the last compression stroke and the last back-pumping stroke; the fuel consumption rate of the current compression stroke and the current draw back stroke is equal to the maximum fuel consumption rate of the engine calibration.
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