CN111750257A - Control method and system for vehicle variable displacement engine oil pump - Google Patents
Control method and system for vehicle variable displacement engine oil pump Download PDFInfo
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- CN111750257A CN111750257A CN202010523747.0A CN202010523747A CN111750257A CN 111750257 A CN111750257 A CN 111750257A CN 202010523747 A CN202010523747 A CN 202010523747A CN 111750257 A CN111750257 A CN 111750257A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
- F16N7/38—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N21/00—Conduits; Junctions; Fittings for lubrication apertures
- F16N21/02—Lubricating nipples
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N25/00—Distributing equipment with or without proportioning devices
Abstract
The invention discloses a control method and a system of a variable displacement engine oil pump for a vehicle, wherein the method comprises the following steps: when the engine speed exceeds a preset threshold value, acquiring the engine speed n, the engine load r and a target air inlet VVT angle piAnd target exhaust VVT angle peAccording to n, r, piAnd peDetermining a target oil pressure Po1(ii) a Obtaining piston cooling nozzle state and engine oil temperature ToAnd actual oil pressure Po2According to n, Po1、ToAnd determining the feedforward control duty cycle Pct for the piston cooling nozzle stateF(ii) a According to Po1And Po2Difference PoEDetermining a deviation impact factor P1Overshoot the influence factor P2And steady state influence factor P3(ii) a According to PoEAnd P1Calculating P term control percentageRatio PctPAccording to PoEAnd P2Calculating the percentage control Pct of the D termD(ii) a According to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n‑1)Calculating the I term accumulation term adjustment term pcts(ii) a According to pcts、PoEAnd P3Calculating an I term accumulation term PctII(ii) a According to PctI(n‑1)And PctIICalculating the percent control of term I, PctI(ii) a At a rate of PctF、PctP、PctDAnd PctIThe sum is the duty ratio Pct of the oil pump. The invention sets target oil pressure for different working conditions, and improves the responsiveness and the precision of oil pressure closed-loop control by a feedforward plus PID control method.
Description
Technical Field
The invention relates to the field of engine control, in particular to a control method and a control system of a variable displacement engine oil pump for a vehicle.
Background
The variable-displacement oil pump control system can continuously change the pump oil amount of the oil pump according to the requirements of various parts of an engine on the oil pressure under the conditions of different rotating speeds, temperatures, loads and the like, so that the control is more precise, the complete distribution as required is realized, the pump oil loss of the traditional fixed-displacement oil pump in the full rotating speed range is avoided, and the friction and the oil consumption can be effectively reduced.
However, in order to further improve the performances of fuel economy, dynamic property, emission and the like of the engine, the requirement on the control complexity of the engine is increased, for example, a piston cooling nozzle is arranged on the engine to reduce the heat load of the piston and strengthen the lubrication of the piston pin and connecting rod bearing; and the requirement of the control precision of VVT (Variable Valve Timing), and the like, how to realize the control of the oil pump under different working conditions is an urgent problem to be solved.
Disclosure of Invention
The invention aims to overcome the defects of the background technology and provide a control method and a control system of a variable displacement oil pump for a vehicle, which respectively set target oil pressure for different working conditions and improve the responsiveness and the precision of closed-loop control of the oil pressure by a control method of feedforward plus PID.
In a first aspect, a method for controlling a variable displacement oil pump for a vehicle includes:
when the engine speed exceeds a preset threshold value, acquiring the engine speed n, the engine load r and a target intake VVT angle piAnd target exhaust VVT angle peAccording to n, r, piAnd peDetermining a target oil pressure Po1；
Obtaining piston cooling nozzle state and engine oil temperature ToAnd actual oil pressure Po2According to n, Po1、ToAnd determining the feedforward control duty cycle Pct for the piston cooling nozzle stateF；
Calculating Po1And Po2Difference value P ofoEAccording to PoEAnd the corresponding mapping table respectively determine the deviation influence factors P1Overshoot the influence factor P2And steady state influence factor P3(ii) a According to PoEAnd P1Calculating the percentage of P control PctPAccording to PoEAnd P2Calculating the percentage control Pct of the D termD(ii) a According to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation terms(ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI；
At a rate of PctF、PctP、PctDAnd PctIThe sum is the duty ratio Pct of the oil pump at the current moment.
In a first possible implementation manner of the first aspect according to the first aspect, the engine speed n, the engine load r, and the target intake VVT angle p are obtainediAnd target exhaust VVT angle peBefore, the method also comprises the following steps:
obtaining piston cooling nozzle control activation, piAnd peWhen the oil pressures are both 0, different first target oil pressures under n and r are obtained, and a mapping table corresponding to the first oil pressure is established;
obtaining piston cooling nozzle control activation, peWhen it is 0, it is differentN, r and p ofiTarget oil pressure of the same n and piTaking the maximum target oil pressure under each engine load as a second target oil pressure, and establishing a mapping table corresponding to the second oil pressure;
obtaining piston cooling nozzle control activation, piWhen 0, different n, r and peTarget oil pressure of the same n and peTaking the maximum target oil pressure under each engine load as a third target oil pressure, and establishing a mapping table corresponding to the third oil pressure;
according to n, r, piAnd peDetermining a target oil pressure Po1The method specifically comprises the following steps:
determining a first target oil pressure according to n, r and a corresponding mapping table; according to n, piDetermining a second target oil pressure according to the corresponding mapping table; according to n, peAnd determining a third target oil pressure according to the corresponding mapping table, and selecting the maximum value of the first target oil pressure, the second target oil pressure and the third target oil pressure as a target oil pressure Po1。
In a second possible implementation manner of the first aspect according to the first aspect, the engine speed n, the engine load r, and the target intake VVT angle p are obtainediAnd target exhaust VVT angle peBefore, the method also comprises the following steps:
acquiring different n and P at a preset reference temperatureo1The duty ratio of the oil pump is lower, and a corresponding mapping table is established;
obtaining different n and P at different engine oil temperatureso1Duty ratio of the oil pump, and calculating the oil temperature influence factor based on the mapping table at the preset reference temperature
Establishing a corresponding mapping table;
according to n, Po1、PctpAnd ToDetermining a feedforward control duty cycle PctFThe method specifically comprises the following steps:
according to n, Po1And corresponding mapping table to determine the feedforward basic duty ratio Pct0According toToDetermining an oil temperature influencing factor
When piston cooling nozzle control is not activated, according to Pct0And
calculating PctF，
When the piston cooling nozzle control is activated, the cooling nozzle influence factor Pct at the last moment is acquiredP(n-1)Calculating the influence factor Pct of the cooling nozzle at the current timeP(n)，PctP(n)＝PctP(n-1)+ C, n-1, 2, …, where C is a constant increment, n is an integer, PctP(0)Is 0; according to Pct0、PctP(n)And fToCalculating PctF，PctF＝(Pct0+PctP(n))×fTo。
According to the first aspect, in a third possible implementation manner of the first aspect, the method is according to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation terms(ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeIThe method specifically comprises the following steps:
obtaining minimum limit value Pct of oil pump duty ratiominAnd a maximum limit value PctmaxAccording to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation termsIs determined by the judgment factor Sum, Sum equals to PctF+PctP+PctD+PctI(n-1)；
When Sum is less than PctminAt time, pcts＝ks*(Sum-Pctmin) Wherein k issIs a smoothing coefficient;
when Sum is greater than or equal to PctminPct or lessmaxAt time, pcts＝0；
When Sum is greater than PctmaxAt time, pcts＝ks*(Sum-Pctmax)；
According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII，PctII＝PoE*P3-pcts；
According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI，PctI＝PctII+PctI(n-1)。
In a fourth possible implementation manner of the first aspect according to the first aspect, the engine speed n, the engine load r, and the target intake VVT angle p are obtainediAnd target exhaust VVT angle peBefore, the method also comprises the following steps:
when the engine speed is lower than a preset threshold value, the engine oil temperature T is obtainedoAnd a starting water temperature T;
according to ToDetermining a starting duty ratio according to the corresponding mapping table, and determining starting set time according to T and the corresponding mapping table;
controlling the oil pump according to the starting duty ratio, and defining the oil pump as starting control;
and when the rotating speed of the engine exceeds a preset threshold value, the starting control is quitted after the starting set time.
According to the first aspect, in a fifth possible implementation manner of the first aspect, PctF、PctP、PctDAnd PctIAfter the sum is the duty ratio Pct of the oil pump at the current moment, the method also comprises the following steps:
when the vehicle is in the process of flameout under power-off, the engine oil temperature T is acquiredo；
According to ToRespectively determining a target duty ratio and target set time by corresponding mapping tables;
and controlling the oil pump according to the target duty ratio, and resetting the duty ratio after the target set time.
In a second aspect, there is provided a control system for a variable displacement oil pump for a vehicle, comprising:
an oil pressure determination module to: when the engine speed exceeds a preset threshold value, acquiring the engine speed n, the engine load r and a target intake VVT angle piAnd target exhaust VVT angle peAccording to n, r, piAnd peDetermining a target oil pressure Po1；
A feed forward analysis module connected with the oil pressure determination module for: obtaining piston cooling nozzle state and engine oil temperature ToAnd actual oil pressure Po2According to n, Po1、ToAnd determining the feedforward control duty cycle Pct for the piston cooling nozzle stateF；
And the PID analysis module is connected with the oil pressure determination module and the feedforward analysis module and is used for: calculating Po1And Po2Difference value P ofoEAccording to PoEAnd the corresponding mapping table respectively determine the deviation influence factors P1Overshoot the influence factor P2And steady state influence factor P3(ii) a According to PoEAnd P1Calculating the percentage of P control PctPAccording to PoEAnd P2Calculating the percentage control Pct of the D termD(ii) a According to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation terms(ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI；
A duty cycle analysis module connected to the feedforward analysis module and the PID analysis module, and configured to: at a rate of PctF、PctP、PctDAnd PctIThe sum is the duty ratio Pct of the oil pump at the current moment.
According to the second aspect, in a first possible implementation manner of the second aspect, the method further includes:
a data acquisition module to: obtaining piston cooling nozzle control activation, piAnd peWhen the oil pressures are both 0, different first target oil pressures under n and r are obtained, and a mapping table corresponding to the first oil pressure is established; obtaining piston cooling nozzle control activation, peWhen 0, different n, r and piTarget oil pressure of the same n and piTaking the maximum target oil pressure under each engine load as a second target oil pressure, and establishing a mapping table corresponding to the second oil pressure; obtaining piston cooling nozzle control activation, piWhen 0, different n, r and peTarget oil pressure of the same n and peTaking the maximum target oil pressure under each engine load as a third target oil pressure, and establishing a mapping table corresponding to the third oil pressure;
the oil pressure determining module is connected with the data acquiring module and is further used for: determining a first target oil pressure according to n, r and a corresponding mapping table; according to n, piDetermining a second target oil pressure according to the corresponding mapping table; according to n, peAnd determining a third target oil pressure according to the corresponding mapping table, and selecting the maximum value of the first target oil pressure, the second target oil pressure and the third target oil pressure as a target oil pressure Po1；
The data acquisition module is further configured to: acquiring different n and P at a preset reference temperatureo1The duty ratio of the oil pump is lower, and a corresponding mapping table is established; obtaining different n and P at different engine oil temperatureso1Duty ratio of the oil pump, and calculating the oil temperature influence factor f based on the mapping table at the preset reference temperatureToAnd establishing a corresponding mapping table;
the feedforward analysis module is connected with the data acquisition module and is further configured to: according to n, Po1And corresponding mapping table to determine the feedforward basic duty ratio Pct0According to ToDetermining an oil temperature influencing factor
When piston cooling nozzle control is not activated, according to Pct0And
calculating PctF，
When the piston cooling nozzle control is activated, the cooling nozzle influence factor Pct at the last moment is acquiredP(n-1)Calculating the influence factor Pct of the cooling nozzle at the current timeP(n)，PctP(n)＝PctP(n-1)+ C, n-1, 2, …, where C is a constant increment, n is an integer, PctP(0)Is 0; according to Pct0、PctP(n)And
calculating PctF，
According to the first possible implementation manner of the second aspect, in a second possible implementation manner of the second aspect, the method further includes:
the PID analysis module is used for: obtaining minimum limit value Pct of oil pump duty ratiominAnd a maximum limit value according to PctmaxPctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation termsIs determined by the judgment factor Sum, Sum equals to PctF+PctP+PctD+PctI(n-1)(ii) a When Sum is less than PctminAt time, pcts＝ks*(Sum-Pctmin) Wherein k issIs a smoothing coefficient; when Sum is greater than or equal to PctminPct or lessmaxAt time, pcts0; when Sum is greater than PctmaxAt time, pcts＝ks*(Sum-Pctmax) (ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII，PctII＝PoE*P3-pcts(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI，PctI＝PctII+PctI(n-1)。
According to a second possible implementation manner of the second aspect, in a third possible implementation manner of the second aspect, the method further includes:
a starting control module for obtaining the engine oil temperature T when the engine speed is lower than a preset threshold valueoAnd a starting water temperature T; according to ToDetermining a starting duty ratio according to the corresponding mapping table, and determining starting set time according to T and the corresponding mapping table; controlling the oil pump according to the starting duty ratio, and defining the oil pump as starting control; when the rotating speed of the engine exceeds a preset threshold value, the starting control is quitted after the starting set time;
a shutdown control module for acquiring the engine oil temperature T when the vehicle is in the process of power-off and flameouto(ii) a According to ToRespectively determining a target duty ratio and target set time by corresponding mapping tables; and controlling the oil pump according to the target duty ratio, and resetting the duty ratio after the target set time.
Compared with the prior art, the invention respectively sets the target oil pressure for different working conditions, and improves the responsiveness and the precision of the closed-loop control of the oil pressure by a control method of feedforward plus PID.
Drawings
FIG. 1 is a schematic flow chart diagram of an embodiment of a method of controlling a variable displacement oil pump for a vehicle of the present invention;
FIG. 2 is a schematic flow chart diagram illustrating another embodiment of a method of controlling a variable displacement oil pump for a vehicle according to the present invention;
FIG. 3 is a schematic flow chart diagram illustrating another embodiment of a method of controlling a variable displacement oil pump for a vehicle according to the present invention;
FIG. 4 is a schematic flow chart diagram illustrating another embodiment of a method of controlling a variable displacement oil pump for a vehicle according to the present invention;
fig. 5 is a schematic configuration diagram of an embodiment of a control system of a variable displacement oil pump for a vehicle of the present invention.
Reference numerals:
100. a control system for a variable displacement engine oil pump for a vehicle; 110. an oil pressure determination module; 120. a feed-forward analysis module; 130. a PID analysis module; 140. a duty cycle analysis module; 150. a data acquisition module; 160. a start control module; 170. and a shutdown control module.
Detailed Description
In order that those skilled in the art will better understand the present invention, the following detailed description of the invention is provided in conjunction with the accompanying drawings and the detailed description of the invention.
Referring to fig. 1, an embodiment of the present invention provides a control method for a variable displacement oil pump for a vehicle, including the steps of:
when the engine speed exceeds a preset threshold value, acquiring the engine speed n, the engine load r and a target intake VVT angle piAnd target exhaust VVT angle peAccording to n, r, piAnd peDetermining a target oil pressure Po1；
Obtaining piston cooling nozzle state and engine oil temperature ToAnd actual oil pressure Po2According to n, Po1、ToAnd determining the feedforward control duty cycle Pct for the piston cooling nozzle stateF；
Calculating Po1And Po2Difference value P ofoEAccording to PoEAnd the corresponding mapping table respectively determine the deviation influence factors P1Overshoot the influence factor P2And steady state influence factor P3(ii) a According to PoEAnd P1Calculating the percentage of P control PctPAccording to PoEAnd P2Calculating the percentage control Pct of the D termD(ii) a According to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation terms(ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI；
At a rate of PctF、PctP、PctDAnd PctIThe sum is the duty ratio Pct of the oil pump at the current moment.
Specifically, in this embodiment, when the engine speed exceeds the preset threshold, the engine is controlled by the oil pump during operation, and the control of the oil pump during operation is divided into several parts.
The first part is the setting of a target oil pressure that depends on engine speed, engine load, piston cooling nozzle activation status, target VVT angle. The final target oil pressure is set by selecting the maximum value of the target oil pressure when the piston cooling nozzle is activated and the target oil pressure when the piston cooling nozzle is not activated, and limiting the rate of change of the target oil pressure to obtain the final target oil pressure for stability control. However, when the piston cooling nozzle is activated, the engine is less prone to knock and pre-ignition, increasing oil pressure and improving friction. When the piston cooling nozzle control is activated, the target oil pressure is higher than that when the piston cooling nozzle control is not activated under the same condition (the same engine speed, load or intake/exhaust VVT angle), and therefore the target oil pressure in the activated state of the piston cooling nozzle is directly set as the set target oil pressure. Obtaining the engine speed n, the engine load r and the target intake VVT angle piAnd target exhaust VVT angle peAccording to n, r, piAnd peDetermining a target oil pressure Po1。
The second part is the control of the oil pressure in the operation process, and the control of the oil pressure in the operation process adopts an improved feedforward plus PID control method.
First, therein the feedforward part PctFThe control of (2) is a control percentage when the actual oil pressure reaches the target oil pressure and becomes stable. Obtaining piston cooling nozzle state and engine oil temperature ToAnd actual oil pressure Po2According to n, Po1、ToAnd determining the feedforward control duty cycle Pct for the piston cooling nozzle stateF。
Secondly, the duty ratio Pct is controlled by PID to feedforwardFAnd closed-loop control is realized. Thus, according to PoEAnd the corresponding mapping table respectively determine the deviation influence factors P1Overshoot the influence factor P2And steady state influence factor P3Calculate Po1And Po2Difference value P ofoEAccording to PoEAnd P1Calculating the percentage of P control PctPAccording to PoEAnd P2Calculating the percentage control Pct of the D termD(ii) a According to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation terms(ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI。
The third part is PctF、PctP、PctDAnd PctIThe sum is the duty ratio Pct of the oil pump at the current moment, and the duty ratio is used for final control of the oil pump, so that the actual oil pressure follows the target oil pressure.
The method and the device set the target oil pressure respectively for different working conditions, and improve the responsiveness and the precision of the oil pressure closed-loop control through a feedforward + PID control method.
Preferably, in another embodiment of the present invention, the engine speed n, the engine load r, and the target intake VVT angle p are obtainediAnd target exhaust VVT angle peBefore, the method also comprises the following steps:
obtaining piston cooling nozzle control activation, piAnd peWhen the oil pressures are both 0, different first target oil pressures under n and r are obtained, and a mapping table corresponding to the first oil pressure is established;
obtaining piston cooling nozzle control activation, peWhen 0, different n, r and piTarget oil pressure of the same n and piTaking the maximum target oil pressure under each engine load as a second target oil pressure, and establishing a mapping table corresponding to the second oil pressure;
obtaining piston cooling nozzle control activation, piWhen 0, different n, r and peTarget oil pressure of the same n and peTaking the maximum target oil pressure under each engine load as a third target oil pressure, and establishing a mapping table corresponding to the third oil pressure;
according to n, r, piAnd peDetermining a target oil pressure Po1The method specifically comprises the following steps:
determining a first target oil pressure according to n, r and a corresponding mapping table; according to n, piDetermining a second target oil pressure according to the corresponding mapping table; according to n, peAnd determining a third target oil pressure according to the corresponding mapping table, and selecting the maximum value of the first target oil pressure, the second target oil pressure and the third target oil pressure as a target oil pressure Po1。
Specifically, in this embodiment, the target oil pressure is determined based on the engine speed and the load, so as to establish a corresponding mapping table, and the optimal target oil pressure is selected according to the oil consumption and the dynamic performance under each working condition (the engine speed and the load determine the working condition, and at this time, the target intake VVT angle and the target exhaust VVT angle are both 0) on the rack. The engine oil pressure can be guaranteed to be conveyed to the surfaces of all friction parts of the engine when normal, and the normal work of the engine can be influenced even the damage to parts of the engine is caused by overhigh or overlow engine oil pressure.
And determining a target oil pressure based on the engine speed and the target intake VVT angle, thereby establishing a corresponding mapping table, and selecting the optimal target oil pressure according to oil consumption and dynamic property under each working condition (the engine speed and load and the current working condition determined under each target intake VVT angle, and the target exhaust VVT angle is 0 at the moment) on the rack. Different n, r and piThe lower points correspond to different target oil pressures, when n and piWhen the target oil pressure is determined to be different under different r, the maximum value is selected as corresponding n and piTarget oil pressure, so that the mapping table obtained by calibration is only matched with n and piCorrelated, not correlated with r. Similarly, a target oil pressure is determined based on the engine speed and the target exhaust VVT angle, and a corresponding map is created.
The engine speed or load is increased, the target oil pressure is increased, but the engine speed or load is too high, the oil pressure tends to be stable, and the oil consumption is reduced on the premise of improving the friction. The smaller the target intake VVT angle or the target exhaust VVT angle, particularly near the lock position, the larger the target oil pressure, the greater the stability of the VVT control, thereby improving fuel economy and emissions.
Determining a target oil pressure P based on the mapping table obtained by calibrationo1Then, a first target oil pressure is determined according to n, r and corresponding mapping tables, and n and p are usediAnd determining a second target oil pressure according to n and p according to the corresponding mapping tableeDetermining a third target oil pressure according to the corresponding mapping table, and selecting the maximum value of the first target oil pressure, the second target oil pressure and the third target oil pressure as a target oil pressure Po1。
Preferably, in another embodiment of the present invention, the engine speed n, the engine load r, and the target intake VVT angle p are obtainediAnd target exhaust VVT angle peBefore, the method also comprises the following steps:
acquiring different n and P at a preset reference temperatureo1The duty ratio of the oil pump is lower, and a corresponding mapping table is established;
obtaining different n and P at different engine oil temperatureso1Duty ratio of the oil pump, and calculating the oil temperature influence factor based on the mapping table at the preset reference temperature
Establishing a corresponding mapping table;
according to n, Po1、PctpAnd ToDetermining a feedforward control duty cycle PctFThe method specifically comprises the following steps:
according to n, Po1And corresponding mapping table to determine the feedforward basic duty ratio Pct0According to ToDetermining an oil temperature influencing factor
When piston cooling nozzle control is not activated, according to Pct0And
calculating PctF，
When the piston cooling nozzle control is activated, the cooling nozzle influence factor Pct at the last moment is acquiredP(n-1)Calculating the influence factor Pct of the cooling nozzle at the current timeP(n)，PctP(n)＝PctP(n-1)+ C, n-1, 2, …, where C is a constant increment, n is an integer, PctP(0)Is 0; according to Pct0、PctP(n)And
calculating PctF，
Specifically, in this embodiment, different n and P values are calibrated at a preset reference temperatureo1The duty ratio of the lower oil pump (under the steady-state working condition of the rack, in order to ensure that the target oil pressure is ensured at the current rotating speed, the duty ratio of a feed-forward part needs to be adjusted to ensure that the actual oil pressure is equal to the target oil pressure), and a corresponding mapping table is established, wherein the preset reference temperature can be freely set, but is generally set to 80 ℃, and is the normal working temperature of the oil pump. Obtaining different n and P at different engine oil temperatureso1Duty ratio of oil pump, and calculation of oil temperature influence factor based on mapping table at preset reference temperature
And establishes a corresponding mapping table. As shown in Table I, when the preset reference temperature is set to 80 ℃, the corresponding reference temperature is set to
1, the remaining oil temperature is passed based on the condition of the preset reference temperature
And (6) correcting. Table one is merely an illustration of when the preset reference temperature is set to 80 ℃, and the preset reference temperature can be freely set in practice.
Table-engine oil temperature influence factor mapping table
According to n, Po1And corresponding mapping table to determine the feedforward basic duty ratio Pct0This Pct0Is the duty ratio at the preset reference temperature, therefore, the duty ratio according to T is also neededoAnd corresponding mapping table determining engine oil temperature influence factor
When piston cooling nozzle control is not activated, according to Pct0And
calculating PctF，
When the piston cooling nozzle control is active, Pct needs to be influenced by the cooling nozzle influencing factor0Firstly, correction is carried out to obtain the influence factor Pct of the cooling nozzle at the previous momentP(n-1)Calculating the influence factor Pct of the cooling nozzle at the current timeP(n)，PctP(n)＝PctP(n-1)+ C, n-1, 2, …, where C is a constant increment, n is an integer, PctP(0)Is 0. Then according to Pct0、PctP(n)And
calculating PctF，
Preferably, in further embodiments of the present invention, the method is based on PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation terms(ii) a According to pcts、PoEAnd P3Calculating the current timeThe I term of (c) is added to the term PctII(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeIThe method specifically comprises the following steps:
obtaining minimum limit value Pct of oil pump duty ratiominAnd a maximum limit value PctmaxAccording to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation termsIs determined by the judgment factor Sum, Sum equals to PctF+PctP+PctD+PctI(n-1)；
When Sum is less than PctminAt time, pcts＝ks*(Sum-Pctmin) Wherein k issIs a smoothing coefficient;
when Sum is greater than or equal to PctminPct or lessmaxAt time, pcts＝0；
When Sum is greater than PctmaxAt time, pcts＝ks*(Sum-Pctmax)；
According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII，PctII＝PoE*P3-pcts；
According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI，PctI＝PctII+PctI(n-1)。
Specifically, in this embodiment, the P term controls the percentage PctPThe purpose of the method is to control the deviation of the duty ratio within a preset range, so that the larger the oil pressure difference is, the larger the corresponding deviation influence factor is. The deviation influence factors are obtained by calibrating under different oil pressure differences, so that different oil pressure differences and corresponding deviation influence factors are obtained, and a corresponding mapping table is established, wherein the deviation influence factor mapping table is shown in table two, which is only an example for facilitating understanding, and the actual situation is not limited to this. Calculating Po1And Po2Difference value P ofoEObtaining the deviation influence factor P through the mapping table1Then according to PoEAnd P1Calculating the percentage of P control PctP，PctP＝PoE*P1。
Table two deviation impact factor mapping table
Percentage of control Pct of item DDThe control method aims to avoid the overshoot of the actual oil pressure in the process of responding to the target oil pressure, and the control percentage of the D item is determined according to the overshoot allowable precision range. Therefore, the greater the oil pressure differential, the greater the corresponding overshoot factor. The overshoot influence factor is obtained by calibrating under different oil pressure differences, so that different oil pressure differences and corresponding overshoot influence factors are obtained, and a corresponding mapping table is established, wherein the overshoot influence factor mapping table is shown in table three, which is only for convenience of understanding and is not limited to this. Calculating Po1And Po2Difference value P ofoEObtaining the overshoot influence factor P through the mapping table2Then according to PoEAnd P2Calculating the percentage control Pct of the D termD，
Wherein k is a constant, and k is a constant,
as the rate of change of the actual oil pressure,
the rate of change of the oil pressure difference.
Table three overshoot influence factor mapping table
Percent control of term I, PctIThe method aims to ensure that the differential pressure between the actual oil pressure and the target oil pressure is stable and the difference value is in a small range under the steady state after closed-loop PID adjustment during real vehicle calibration. Percent control of term I, PctIThe initial value is 0 and the integral percentage of the I term PctIIt is cleared when the starting process control is active. I term accumulation term PctIIAt the target oil pressure Po1Rate of change or actual oil pressure P2And clearing when the change rate is too large (exceeds a preset threshold). Wherein the I term adds up the term PctIIAdjustment term pctsThe method means that the duty ratio of the control process is saturated, and the I term accumulation term Pct is gradually adjusted when the duty ratio exceeds the limit valueIIOtherwise item I is not controlled.
Obtaining minimum limit value Pct of oil pump duty ratiominAnd a maximum limit value PctmaxGeneral PctminIs 0, PctmaxThe engine oil pump operating parameter is 100%, but is not particularly limited. According to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation termsIs determined by the judgment factor Sum, Sum equals to PctF+PctP+PctD+PctI(n-1)When Sum is less than PctminAt time, pcts＝ks*(Sum-Pctmin) Wherein k issFor smoothing coefficient, when Sum is greater than or equal to PctminPct or lessmaxAt time, pcts0, when Sum is greater than PctmaxAt time, pcts＝ks*(Sum-Pctmax)。
Then according to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII，PctII＝PoE*P3-pctsAccording to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI，PctI＝PctII+PctI(n-1)。
Referring to fig. 2, another embodiment of the present invention provides a control method for a variable displacement oil pump for a vehicle, which is an optimized embodiment of the above embodiment, and obtains an engine speed n, an engine load r, and a target intake VVT angle piAnd target exhaust VVT angle peBefore, the method also comprises the following steps:
when the engine speed is lower than the preset threshold value,obtaining the temperature T of the engine oiloAnd a starting water temperature T;
according to ToDetermining a starting duty ratio according to the corresponding mapping table, and determining starting set time according to T and the corresponding mapping table;
controlling the oil pump according to the starting duty ratio, and defining the oil pump as starting control;
and when the rotating speed of the engine exceeds a preset threshold value, the starting control is quitted after the starting set time.
Specifically, in the present embodiment, when the engine speed is lower than a certain value, the engine is considered to be in the starting process. Therefore, when the engine speed is lower than the preset threshold, the engine oil temperature T is acquiredoAnd a starting water temperature T according tooAnd determining the starting duty ratio according to the corresponding mapping table, and determining the starting set time according to the T and the corresponding mapping table. The mapping tables are obtained through calibration, the starting duty ratio is only related to the engine oil temperature, and the starting set time is only related to the starting water temperature, so that the corresponding mapping tables are established by obtaining the starting duty ratios at different engine oil temperatures, the mapping table of the engine oil temperature and the starting duty ratio is shown as table four, the corresponding mapping tables are established by obtaining the starting set time at different starting water temperatures, and the mapping table of the starting water temperature and the starting set time is shown as table five. Tables four and five are illustrated for ease of understanding and the practice is not limited thereto.
Mapping table for engine oil temperature and starting duty ratio
Mapping table for starting water temperature and starting set time
And controlling the oil pump according to the determined starting duty ratio, defining the oil pump as starting control, and when the rotating speed of the engine exceeds a preset threshold value, exiting the starting control after starting for a set time. Namely, the engine oil pump control of the starting process is carried out after the engine speed exceeds the preset threshold value to start the set time. The purpose of the engine oil pump control during starting is to improve the engine oil lubrication during starting and to accelerate the rise in engine oil temperature and reduce the friction of the crankshaft connecting rod mechanism.
Referring to fig. 3, another embodiment of the present invention provides a control method for a variable displacement oil pump for a vehicle, which is a preferred embodiment of the above embodiments, to PctF、PctP、PctDAnd PctIAfter the sum is the duty ratio Pct of the oil pump at the current moment, the method also comprises the following steps:
when the vehicle is in the process of flameout under power-off, the engine oil temperature T is acquiredo；
According to ToRespectively determining a target duty ratio and target set time by corresponding mapping tables;
and controlling the oil pump according to the target duty ratio, and resetting the duty ratio after the target set time.
Specifically, in the present embodiment, during the vehicle is electrically turned off, the engine is considered to be in the shutdown process. Thus, the engine oil temperature T is obtainedoAccording to ToAnd respectively determining the target duty ratio and the target setting time by the corresponding mapping table. The mapping tables are obtained through calibration, the target duty ratio and the target set time are only related to the engine oil temperature, therefore, the corresponding mapping tables are respectively established by obtaining the target duty ratio and the target set time under different engine oil temperatures, the mapping table of the engine oil temperature and the target duty ratio is shown in a table six, the corresponding mapping table is established by obtaining the target set time under different engine oil temperatures, and the mapping table of the engine oil temperature and the target set time is shown in a table seven. Tables six and seven are illustrated for ease of understanding and the practice is not limited thereto. And controlling the oil pump according to the determined target duty ratio, and clearing the duty ratio after the target setting time. The purpose is to improve the restarting of the vehicle in a short time after the vehicle is stopped and reduce the friction work in the starting process of the engine. But the oil pump is stopped after a period of time, so that the overlarge electricity load is avoided.
Mapping table for indicating six engine oil temperatures and target duty ratios
| Temperature of engine oil (. degree.C.) | -20 | 0 | 20 | 30 | 50 |
| Target duty ratio (%) | 25 | 20 | 18 | 5 | 0 |
Seven-table mapping table for engine oil temperature and target set time
| Temperature of engine oil (. degree.C.) | 20 | 0 | 20 | 30 | 50 |
| Target setting time(s) | 0 | 8 | 5 | 2 | 0 |
As shown in fig. 4, another embodiment of the present invention provides a control method for a variable displacement engine oil pump for a vehicle, which is an optimized embodiment of the foregoing embodiment, each period determines a current working condition of an engine according to an engine speed, when the engine is in a shutdown working condition, that is, when the vehicle is turned off electrically, the engine oil pump is controlled by the engine oil pump in the shutdown working condition of the foregoing embodiment until the engine oil pump control is finished in the shutdown process, and then, whether the engine is in a start working condition is continuously monitored; when the engine is in a starting working condition, namely the rotating speed is lower than a preset threshold value, the engine oil pump control is controlled through the starting working condition of the embodiment until the engine oil pump control is finished in the starting process, and then whether the engine is in a stopping working condition or not is continuously monitored; when the engine is in the operating condition, that is, the rotating speed is higher than the preset threshold value, the engine oil pump control is controlled through the operating condition of the above embodiment, firstly, the target oil pressure is set, then, the duty ratio of the oil pump is set, and finally, the engine oil pump is controlled to execute according to the duty ratio of the oil pump.
The present application improves oil pump control for engine starting, controls target oil pressure based on whether piston cooling nozzles are activated or not, improves stability and responsiveness during closed-loop control, and improves friction for restart by oil pump control during engine shutdown. The lubricating and fuel economy of the engine is improved in consideration of all operation working conditions of the engine.
Referring to fig. 5, an embodiment of the present invention provides a control system 100 for a variable displacement oil pump for a vehicle, including:
an oil pressure determination module 110 to: when the engine speed exceeds a preset threshold value, acquiring the engine speed n, the engine load r and a target intake VVT angle piAnd target exhaust VVT angle peAccording to n, r, piAnd peDetermining a target oil pressure Po1；
A feed forward analysis module 120 coupled to the oil pressure determination module 110 for: obtaining piston cooling nozzle state and engine oil temperature ToAnd actual oil pressure Po2According to n, Po1、ToAnd determining the feedforward control duty cycle Pct for the piston cooling nozzle stateF；
A PID analysis module 130 coupled to the oil pressure determination module 110 and the feed forward analysis module 120 for: calculating Po1And Po2Difference value P ofoEAccording to PoEAnd the corresponding mapping table respectively determine the deviation influence factors P1Overshoot the influence factor P2And steady state influence factor P3(ii) a According to PoEAnd P1Calculating the percentage of P control PctPAccording to PoEAnd P2Calculating the percentage control Pct of the D termD(ii) a According to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation terms(ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI；
A duty cycle analysis module 140 connected to the feedforward analysis module 120 and the PID analysis module 130, and configured to: at a rate of PctF、PctP、PctDAnd PctIThe sum is the duty ratio Pct of the oil pump at the current moment.
A data acquisition module 150 configured to: obtaining piston cooling nozzle control activation, piAnd peWhen the oil pressures are both 0, different first target oil pressures under n and r are obtained, and a mapping table corresponding to the first oil pressure is established; obtaining piston cooling nozzle control activation, peWhen it is 0, it is differentN, r and p ofiTarget oil pressure of the same n and piTaking the maximum target oil pressure under each engine load as a second target oil pressure, and establishing a mapping table corresponding to the second oil pressure; obtaining piston cooling nozzle control activation, piWhen 0, different n, r and peTarget oil pressure of the same n and peTaking the maximum target oil pressure under each engine load as a third target oil pressure, and establishing a mapping table corresponding to the third oil pressure;
the oil pressure determination module 110, connected to the data acquisition module 150, is further configured to: determining a first target oil pressure according to n, r and a corresponding mapping table; according to n, piDetermining a second target oil pressure according to the corresponding mapping table; according to n, peAnd determining a third target oil pressure according to the corresponding mapping table, and selecting the maximum value of the first target oil pressure, the second target oil pressure and the third target oil pressure as a target oil pressure Po1；
The data obtaining module 150 is further configured to: acquiring different n and P at a preset reference temperatureo1The duty ratio of the oil pump is lower, and a corresponding mapping table is established; obtaining different n and P at different engine oil temperatureso1Duty ratio of the oil pump, and calculating the oil temperature influence factor f based on the mapping table at the preset reference temperatureToAnd establishing a corresponding mapping table;
the feedforward analysis module 120 is connected to the data acquisition module 150, and is further configured to: according to n, Po1And corresponding mapping table to determine the feedforward basic duty ratio Pct0According to ToDetermining an oil temperature influencing factor
When piston cooling nozzle control is not activated, according to Pct0And
calculating PctF，
When piston cools nozzle controlWhen activated, the influence factor Pct of the cooling nozzle at the last moment is obtainedP(n-1)Calculating the influence factor Pct of the cooling nozzle at the current timeP(n)，PctP(n)＝PctP(n-1)+ C, n-1, 2, …, where C is a constant increment, n is an integer, PctP(0)Is 0; according to Pct0、PctP(n)And
calculating PctF，
The PID analysis module 130 is configured to: obtaining minimum limit value Pct of oil pump duty ratiominAnd a maximum limit value according to PctmaxPctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation termsIs determined by the judgment factor Sum, Sum equals to PctF+PctP+PctD+PctI(n-1)(ii) a When Sum is less than PctminAt time, pcts＝ks*(Sum-Pctmin) Wherein k issIs a smoothing coefficient; when Sum is greater than or equal to PctminPct or lessmaxAt time, pcts0; when Sum is greater than PctmaxAt time, pcts＝ks*(Sum-Pctmax) (ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII，PctII＝PoE*P3-pcts(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI，PctI＝PctII+PctI(n-1)。
The starting control module 160 obtains the engine oil temperature T when the engine speed is lower than a preset thresholdoAnd a starting water temperature T; according to ToDetermining a starting duty ratio according to the corresponding mapping table, and determining starting set time according to T and the corresponding mapping table; controlling the oil pump according to the starting duty ratio, and defining the oil pump as starting control; when the engine speed exceeds a predetermined thresholdWhen the value is later, the starting control is quitted after the starting set time;
the shutdown control module 170 acquires the oil temperature T when the vehicle is in the process of power-off shutdowno(ii) a According to ToRespectively determining a target duty ratio and target set time by corresponding mapping tables; and controlling the oil pump according to the target duty ratio, and resetting the duty ratio after the target set time.
Specifically, the functions of each apparatus in this embodiment are elaborated in the corresponding method embodiment, and are not described here one by one.
It will be apparent to those skilled in the art that various changes and modifications may be made in the present invention without departing from the spirit and scope of the invention. Thus, if such modifications and variations of the present invention fall within the scope of the claims of the present invention and their equivalents, the present invention is also intended to include such modifications and variations.
Claims (10)
1. A control method for a variable displacement oil pump for a vehicle, characterized by comprising the steps of:
when the engine speed exceeds a preset threshold value, acquiring the engine speed n, the engine load r and a target intake VVT angle piAnd target exhaust VVT angle peAccording to n, r, piAnd peDetermining a target oil pressure Po1；
Obtaining piston cooling nozzle state and engine oil temperature ToAnd actual oil pressure Po2According to n, Po1、ToAnd determining the feedforward control duty cycle Pct for the piston cooling nozzle stateF；
Calculating Po1And Po2Difference value P ofoEAccording to PoEAnd the corresponding mapping table respectively determine the deviation influence factors P1Overshoot the influence factor P2And steady state influence factor P3(ii) a According to PoEAnd P1Calculating the percentage of P control PctPAccording to PoEAnd P2Calculating the percentage control Pct of the D termD(ii) a According to PctF、PctP、PctDAnd last time I item control percentagePctI(n-1)Calculating an adjustment term pct for the I term accumulation terms(ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI；
At a rate of PctF、PctP、PctDAnd PctIThe sum is the duty ratio Pct of the oil pump at the current moment.
2. The method according to claim 1, wherein the engine speed n, the engine load r, the target intake VVT angle p, and the like are obtainediAnd target exhaust VVT angle peBefore, the method also comprises the following steps:
obtaining piston cooling nozzle control activation, piAnd peWhen the oil pressures are both 0, different first target oil pressures under n and r are obtained, and a mapping table corresponding to the first oil pressure is established;
obtaining piston cooling nozzle control activation, peWhen 0, different n, r and piTarget oil pressure of the same n and piTaking the maximum target oil pressure under each engine load as a second target oil pressure, and establishing a mapping table corresponding to the second oil pressure;
obtaining piston cooling nozzle control activation, piWhen 0, different n, r and peTarget oil pressure of the same n and peTaking the maximum target oil pressure under each engine load as a third target oil pressure, and establishing a mapping table corresponding to the third oil pressure;
according to n, r, piAnd peDetermining a target oil pressure Po1The method specifically comprises the following steps:
determining a first target oil pressure according to n, r and a corresponding mapping table; according to n, piDetermining a second target oil pressure according to the corresponding mapping table; according to n, peAnd determining a third target oil pressure according to the corresponding mapping table, and selecting the maximum value of the first target oil pressure, the second target oil pressure and the third target oil pressure as a target oil pressure Po1。
3. The method according to claim 1, wherein the engine speed n, the engine load r, the target intake VVT angle p, and the like are obtainediAnd target exhaust VVT angle peBefore, the method also comprises the following steps:
acquiring different n and P at a preset reference temperatureo1The duty ratio of the oil pump is lower, and a corresponding mapping table is established;
obtaining different n and P at different engine oil temperatureso1Duty ratio of the oil pump, and calculating the oil temperature influence factor based on the mapping table at the preset reference temperature
Establishing a corresponding mapping table;
according to n, Po1、PctpAnd ToDetermining a feedforward control duty cycle PctFThe method specifically comprises the following steps:
according to n, Po1And corresponding mapping table to determine the feedforward basic duty ratio Pct0According to ToDetermining an oil temperature influencing factor
When piston cooling nozzle control is not activated, according to Pct0And
calculating PctF，
When the piston cooling nozzle control is activated, the cooling nozzle influence factor Pct at the last moment is acquiredP(n-1)Calculating the influence factor Pct of the cooling nozzle at the current timeP(n)，PctP(n)＝PctP(n-1)+ C, n-1, 2, …, where C is a constant increment, n is an integer, PctP(0)Is 0; according to Pct0、PctP(n)And
calculating PctF，
4. The method of claim 1, wherein the Pct is based onF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation terms(ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeIThe method specifically comprises the following steps:
obtaining minimum limit value Pct of oil pump duty ratiominAnd a maximum limit value PctmaxAccording to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation termsIs determined by the judgment factor Sum, Sum equals to PctF+PctP+PctD+PctI(n-1)；
When Sum is less than PctminAt time, pcts＝ks*(Sum-Pctmin) Wherein k issIs a smoothing coefficient;
when Sum is greater than or equal to PctminPct or lessmaxAt time, pcts＝0；
When Sum is greater than PctmaxAt time, pcts＝ks*(Sum-Pctmax)；
According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII，PctII＝PoE*P3-pcts；
According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI，PctI＝PctII+PctI(n-1)。
5. The method according to claim 1, wherein the engine speed n, the engine load r, the target intake VVT angle p, and the like are obtainediAnd target exhaust VVT angle peBefore, the method also comprises the following steps:
when the engine speed is lower than a preset threshold value, the engine oil temperature T is obtainedoAnd a starting water temperature T;
according to ToDetermining a starting duty ratio according to the corresponding mapping table, and determining starting set time according to T and the corresponding mapping table;
controlling the oil pump according to the starting duty ratio, and defining the oil pump as starting control;
and when the rotating speed of the engine exceeds a preset threshold value, the starting control is quitted after the starting set time.
6. The method of claim 1, wherein PctF、PctP、PctDAnd PctIAfter the sum is the duty ratio Pct of the oil pump at the current moment, the method also comprises the following steps:
when the vehicle is in the process of flameout under power-off, the engine oil temperature T is acquiredo；
According to ToRespectively determining a target duty ratio and target set time by corresponding mapping tables;
and controlling the oil pump according to the target duty ratio, and resetting the duty ratio after the target set time.
7. A control system for a variable displacement oil pump for a vehicle, comprising:
an oil pressure determination module to: when the engine speed exceeds a preset threshold value, acquiring the engine speed n, the engine load r and a target intake VVT angle piAnd target exhaust VVT angle peAccording to n, r, piAnd peDetermining a target oil pressure Po1；
A feed forward analysis module connected with the oil pressure determination module for: obtaining piston cooling nozzle state and engine oil temperature ToAnd actual oil pressure Po2According to n, Po1、ToAnd determining the feedforward control duty cycle Pct for the piston cooling nozzle stateF；
And the PID analysis module is connected with the oil pressure determination module and the feedforward analysis module and is used for: calculating Po1And Po2Difference value P ofoEAccording to PoEAnd the corresponding mapping table respectively determine the deviation influence factors P1Overshoot the influence factor P2And steady state influence factor P3(ii) a According to PoEAnd P1Calculating the percentage of P control PctPAccording to PoEAnd P2Calculating the percentage control Pct of the D termD(ii) a According to PctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation terms(ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI；
A duty cycle analysis module connected to the feedforward analysis module and the PID analysis module, and configured to: at a rate of PctF、PctP、PctDAnd PctIThe sum is the duty ratio Pct of the oil pump at the current moment.
8. The system of claim 7, further comprising:
a data acquisition module to: obtaining piston cooling nozzle control activation, piAnd peWhen the oil pressures are both 0, different first target oil pressures under n and r are obtained, and a mapping table corresponding to the first oil pressure is established; obtaining piston cooling nozzle control activation, peWhen 0, different n, r and piTarget oil pressure of the same n and piTaking the maximum target oil pressure under each engine load as a second target oil pressure, and establishing a mapping table corresponding to the second oil pressure; obtaining piston cooling nozzle control activation, piWhen 0, different n, r and peTarget oil pressure of the same n and peTaking the maximum target oil pressure under each engine load as a third target oil pressure, and establishing a mapping table corresponding to the third oil pressure;
the oil pressure determining module is connected with the data acquiring module and is further used for: determining a first target oil pressure according to n, r and a corresponding mapping table; according to n, piDetermining a second target oil pressure according to the corresponding mapping table; according to n, peAnd determining a third target oil pressure according to the corresponding mapping table, and selecting the maximum value of the first target oil pressure, the second target oil pressure and the third target oil pressure as a target oil pressure Po1；
The data acquisition module is further configured to: acquiring different n and P at a preset reference temperatureo1The duty ratio of the oil pump is lower, and a corresponding mapping table is established; obtaining different n and P at different engine oil temperatureso1Duty ratio of the oil pump, and calculating the oil temperature influence factor based on the mapping table at the preset reference temperature
Establishing a corresponding mapping table;
the feedforward analysis module is connected with the data acquisition module and is further configured to: according to n, Po1And corresponding mapping table to determine the feedforward basic duty ratio Pct0According to ToDetermining an oil temperature influencing factor
When piston cooling nozzle control is not activated, according to Pct0And
calculating PctF，
When the piston cooling nozzle control is activated, the cooling nozzle influence factor Pct at the last moment is acquiredP(n-1)Calculating the influence factor Pct of the cooling nozzle at the current timeP(n)，PctP(n)＝PctP(n-1)+ C, n-1, 2, …, where C is a constant increment, n is an integer, PctP(0)Is 0; according to Pct0、PctP(n)And
calculating PctF，
9. The system of claim 7, wherein:
the PID analysis module is used for: obtaining minimum limit value Pct of oil pump duty ratiominAnd a maximum limit value according to PctmaxPctF、PctP、PctDAnd the control percentage Pct of the I item at the previous momentI(n-1)Calculating an adjustment term pct for the I term accumulation termsIs determined by the judgment factor Sum, Sum equals to PctF+PctP+PctD+PctI(n-1)(ii) a When Sum is less than PctminAt time, pcts＝ks*(Sum-Pctmin) Wherein k issIs a smoothing coefficient; when Sum is greater than or equal to PctminPct or lessmaxAt time, pcts0; when Sum is greater than PctmaxAt time, pcts＝ks*(Sum-Pctmax) (ii) a According to pcts、PoEAnd P3Calculating the I-term accumulation term Pct of the current momentII，PctII＝PoE*P3-pcts(ii) a According to PctI(n-1)And PctIICalculating the I control percentage Pct of the current timeI，PctI＝PctII+PctI(n-1)。
10. The system of claim 7, further comprising:
a starting control module for obtaining the engine oil temperature T when the engine speed is lower than a preset threshold valueoAnd a starting water temperature T; according to ToAnd determining the starting duty ratio according to the corresponding mapping table and the TStarting the set time; controlling the oil pump according to the starting duty ratio, and defining the oil pump as starting control; when the rotating speed of the engine exceeds a preset threshold value, the starting control is quitted after the starting set time;
a shutdown control module for acquiring the engine oil temperature T when the vehicle is in the process of power-off and flameouto(ii) a According to ToRespectively determining a target duty ratio and target set time by corresponding mapping tables; and controlling the oil pump according to the target duty ratio, and resetting the duty ratio after the target set time.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114320521A (en) * | 2021-12-29 | 2022-04-12 | 浙江吉利控股集团有限公司 | Oil pump control method and device and engine system |
| CN114483246A (en) * | 2022-01-28 | 2022-05-13 | 重庆长安汽车股份有限公司 | Engine oil pressure control method and system for fully-variable engine oil pump |
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