阅读说明：本技术 一种发动机响应时间的计算方法及装置 (Method and device for calculating response time of engine ) 是由 崔亚彬 吴慎超 王阔 张冬冬 段景辉 于 2020-04-01 设计创作，主要内容包括：本发明提供了一种发动机响应时间的计算方法及装置,应用于发动机停缸控制领域,该方法可以包括获取扭矩切换过程中发动机的当前气门正时角度与目标气门正时角度的角度差,以及所述发动机的主油道机油压力；根据所述角度差与所述主油道机油压力计算所述发动机的第一响应时间；根据所述主油道机油压力计算所述发动机的第二响应时间；根据所述第一响应时间与所述第二响应时间,确定所述发动机的系统响应时间。通过本发明实施例提供的方案,能够准确计算随机停缸发动机在扭矩切换过程中实际所需要的系统响应时间。(The invention provides a method and a device for calculating the response time of an engine, which are applied to the field of cylinder deactivation control of the engine, wherein the method comprises the steps of obtaining the angle difference between the current valve timing angle and the target valve timing angle of the engine in the torque switching process and the oil pressure of a main oil gallery of the engine; calculating a first response time of the engine according to the angle difference and the main oil gallery oil pressure; calculating a second response time of the engine according to the oil pressure of the main oil gallery; determining a system response time of the engine based on the first response time and the second response time. By the scheme provided by the embodiment of the invention, the actually required system response time of the randomly deactivated engine in the torque switching process can be accurately calculated.)

1. A method of calculating an engine response time, the method comprising:

acquiring the angle difference between the current valve timing angle and the target valve timing angle of the engine in the torque switching process and the oil pressure of a main oil gallery of the engine;

calculating a first response time of the engine according to the angle difference and the main oil gallery oil pressure;

calculating a second response time of the engine according to the oil pressure of the main oil gallery;

determining a system response time of the engine based on the first response time and the second response time.

2. The method of claim 1, wherein after obtaining the angular difference between the current valve timing angle and the target valve timing angle of the engine during the torque transition, further comprising:

acquiring a gas quantity difference between a current gas quantity and a target gas quantity of the engine in the torque switching process;

the calculating a first response time of the engine according to the angle difference and the main gallery oil pressure comprises:

and calculating first response time of the engine according to the angle difference, the oil pressure of the main oil gallery and the air quantity difference.

3. The method of claim 2, wherein said calculating a first response time of the engine based on the angular difference, the main gallery oil pressure, and the air quantity difference comprises:

determining a first initial response time according to the angle difference and the oil pressure of the main oil gallery;

determining a gas circuit delay coefficient according to the gas quantity difference and the current rotating speed of the engine;

and calculating the first response time according to the first initial response time and the gas path delay coefficient.

4. The calculation method of claim 1, wherein the calculating a second response time of the engine from the main gallery oil pressure comprises:

determining a second initial response time according to the oil pressure of the main oil gallery;

determining an engine oil pressure drop coefficient according to the angle difference and the engine oil pressure of the main oil gallery;

and calculating a second response time of the engine according to the second initial response time and the oil pressure drop coefficient.

5. The method of claim 1, wherein after determining the system response time of the engine based on the first response time and the second response time, further comprising:

acquiring a torque difference in a torque switching process, and determining torque response time according to the torque difference;

and determining the cylinder deactivation rate and the cylinder deactivation sequence of the engine according to the torque response time and the system response time.

6. An apparatus for calculating engine response time, the apparatus comprising:

the data acquisition module is used for acquiring the angle difference between the current valve timing angle and the target valve timing angle of the engine in the torque switching process and the oil pressure of a main oil gallery of the engine;

the first response time calculation module is used for calculating first response time of the engine according to the angle difference and the oil pressure of the main oil gallery;

the second response time calculation module is used for calculating second response time of the engine according to the oil pressure of the main oil gallery;

a system response time determination module to determine a system response time of the engine based on the first response time and the second response time.

7. The device of claim 6, wherein the data obtaining module is further configured to obtain a gas amount difference between a current gas amount and a target gas amount of the engine during the torque switching process;

the first response time calculation module is specifically configured to calculate a first response time of the engine according to the angle difference, the main oil gallery oil pressure, and the air quantity difference.

8. The apparatus of claim 7, wherein the first response time calculation module comprises:

a first initial response time determination submodule for determining a first initial response time according to the angle difference and the oil pressure of the main oil gallery;

the gas circuit delay coefficient determining submodule is used for determining a gas circuit delay coefficient according to the gas quantity difference and the current rotating speed of the engine;

and the first response time determining submodule is used for calculating the first response time according to the first initial response time and the gas circuit delay coefficient.

9. The apparatus of claim 6, wherein the second response time calculation module comprises:

the second initial response time determining submodule is used for determining second initial response time according to the oil pressure of the main oil gallery;

the engine oil pressure drop coefficient determining submodule is used for determining an engine oil pressure drop coefficient according to the angle difference and the engine oil pressure of the main oil gallery;

and the second response time determining submodule is used for calculating the second response time of the engine according to the second initial response time and the oil pressure drop coefficient.

10. The apparatus of claim 6, further comprising:

the torque response time determining module is used for acquiring torque difference in the torque switching process and determining torque response time according to the torque difference change rate;

and the random cylinder deactivation module is used for determining the cylinder deactivation rate and the cylinder deactivation sequence of the engine according to the torque response time and the system response time.

Technical Field

The invention relates to the field of engine cylinder deactivation control, in particular to a method and a device for calculating engine response time.

Background

Automobile emission is an important aspect of current environmental and energy problems, how to ensure normal running of an automobile and better save energy and reduce emission are research hotspots in the internal combustion engine industry, and what is the most important is how to reduce oil consumption and emission.

At present, in order to avoid the problems of excessive energy supply, energy waste and the like in the engine working engineering, when the engine works under a small load, an engine cylinder stopping technology is adopted, namely, a part of cylinders of the engine are closed, so that the pumping loss and friction are reduced, the engine can be positioned in a region with lower oil consumption when the engine works under the small load, and the oil consumption and the emission are reduced. However, the cylinder deactivation technology of the current engine can only perform fixed cylinder deactivation, namely, the operation of the corresponding cylinder is stopped every time the cylinder is fixedly stopped. Although the fixed cylinder deactivation is simple to implement, the optimal fuel consumption region cannot be selected according to the state of the engine, and the effect of reducing fuel consumption is limited. If a random cylinder deactivation mode is adopted, and the optimal cylinder deactivation mode is correspondingly selected according to the current state of the engine, the engine can be always in the optimal oil consumption area, and the effects of energy conservation and emission reduction are obviously improved.

When the engine selects a stochastic cylinder deactivation scheme, the particular stochastic cylinder deactivation scheme may be selected with a torque response time between the target torque and the current torque. If the torque response time is larger than the system response time, the random cylinder deactivation scheme of the engine is switched, but the engine system response time is limited by the gas path response time and the response time of the valve mechanism, so that the actual engine system response time cannot be accurately calculated. Therefore, how to accurately calculate the system response time in the process of randomly switching the torque of the cylinder deactivation engine is an urgent problem to be solved in the field.

Disclosure of Invention

In view of the above, the present invention provides a method and a device for calculating engine response time, so as to solve the problem that in the prior art, the system response time cannot be accurately calculated in the process of torque switching of an automobile randomly deactivated engine.

In order to achieve the purpose, the technical scheme of the invention is realized as follows:

the first aspect of the embodiment of the invention discloses a method for calculating the response time of an engine, which comprises the following steps:

acquiring the angle difference between the current valve timing angle and the target valve timing angle of the engine in the torque switching process and the oil pressure of a main oil gallery of the engine;

calculating a first response time of the engine according to the angle difference and the main oil gallery oil pressure;

calculating a second response time of the engine according to the oil pressure of the main oil gallery;

determining a system response time of the engine based on the first response time and the second response time.

Optionally, after obtaining an angle difference between a current valve timing angle and a target valve timing angle of the engine during the torque switching, the method further includes:

acquiring a gas quantity difference between a current gas quantity and a target gas quantity of the engine in the torque switching process;

the calculating a first response time of the engine according to the angle difference and the main gallery oil pressure comprises:

and calculating first response time of the engine according to the angle difference, the oil pressure of the main oil gallery and the air quantity difference.

Optionally, the calculating a first response time of the engine according to the angle difference, the main gallery oil pressure, and the air quantity difference includes:

determining a first initial response time according to the angle difference and the oil pressure of the main oil gallery;

determining a gas circuit delay coefficient according to the gas quantity difference and the current rotating speed of the engine;

and calculating the first response time according to the first initial response time and the gas path delay coefficient.

Optionally, the calculating a second response time of the engine according to the main gallery oil pressure includes:

determining a second initial response time according to the oil pressure of the main oil gallery;

determining an engine oil pressure drop coefficient according to the angle difference and the engine oil pressure of the main oil gallery;

and calculating a second response time of the engine according to the second initial response time and the oil pressure drop coefficient.

Optionally, after determining the system response time of the engine according to the first response time and the second response time, further comprising:

acquiring a torque difference in a torque switching process, and determining torque response time according to the torque difference;

and determining the cylinder deactivation rate and the cylinder deactivation sequence of the engine according to the torque response time and the system response time.

A second aspect of an embodiment of the present invention discloses an apparatus for calculating a response time of an engine, which may include:

the data acquisition module is used for acquiring the angle difference between the current valve timing angle and the target valve timing angle of the engine in the torque switching process and the oil pressure of a main oil gallery of the engine;

the first response time calculation module is used for calculating first response time of the engine according to the angle difference and the oil pressure of the main oil gallery;

the second response time calculation module is used for calculating second response time of the engine according to the oil pressure of the main oil gallery;

a system response time determination module to determine a system response time of the engine based on the first response time and the second response time.

Optionally, the data obtaining module is further configured to obtain a gas quantity difference between a current gas quantity and a target gas quantity of the engine during the torque switching process;

the first response time calculation module is specifically configured to calculate a first response time of the engine according to the angle difference, the main oil gallery oil pressure, and the air quantity difference.

Optionally, the first response time calculation module includes:

a first initial response time determination submodule for determining a first initial response time according to the angle difference and the oil pressure of the main oil gallery;

the gas circuit delay coefficient determining submodule is used for determining a gas circuit delay coefficient according to the gas quantity difference and the current rotating speed of the engine;

and the first response time determining submodule is used for calculating the first response time according to the first initial response time and the gas circuit delay coefficient.

Optionally, the second response time calculation module includes:

the second initial response time determining submodule is used for determining second initial response time according to the oil pressure of the main oil gallery;

the engine oil pressure drop coefficient determining submodule is used for determining an engine oil pressure drop coefficient according to the angle difference and the engine oil pressure of the main oil gallery;

and the second response time determining submodule is used for calculating the second response time of the engine according to the second initial response time and the oil pressure drop coefficient.

Optionally, the apparatus further comprises:

the torque response time determining module is used for acquiring torque difference in the torque switching process and determining torque response time according to the accelerator pedal opening change rate;

and the random cylinder deactivation module is used for determining the cylinder deactivation rate and the cylinder deactivation sequence of the engine according to the torque response time and the system response time.

Compared with the prior art, the method and the device for calculating the response time of the engine have the following advantages:

according to the method and the device for calculating the response time of the engine, provided by the embodiment of the invention, the first response time and the second response time in the torque switching process are calculated respectively according to the angle difference and the oil pressure of the main oil gallery in the process of switching the current torque of the engine to the target torque, and the first response time and the second response time are compared, so that the accurate system response time is determined, and the system response time required by the random cylinder deactivation engine in the torque switching process is accurately calculated. In addition, the determined system response time can also be applied to subsequent switching of the cylinder deactivation rate of the engine and selection of a cylinder deactivation sequence scheme, and the selection of the cylinder deactivation rate and the cylinder deactivation scheme can be more consistent with the actual working state of the engine based on the determined system response time, so that the effect of reducing the oil consumption of the engine while the output of the engine is kept is achieved.

Drawings

The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:

FIG. 1 is a flow chart of steps of a method for calculating engine response time according to an embodiment of the present invention;

FIG. 2 is a flowchart illustrating steps in an alternate method for calculating engine response time according to an embodiment of the present invention;

FIG. 3 is a block diagram of the logic structure of a method of calculating engine response time in an embodiment of the present invention;

FIG. 4 is a flowchart illustrating steps in an alternate method for calculating engine response time in accordance with an embodiment of the present invention;

fig. 5 is a block diagram of an engine response time calculation apparatus 500 according to an embodiment of the present invention.

Detailed Description

It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.

The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.

Referring to fig. 1, which shows a flowchart of steps of a method for calculating an engine response time according to an embodiment of the present invention, as shown in fig. 1, the method may include:

step 101: the method comprises the steps of obtaining the angle difference between the current valve timing angle and the target valve timing angle of the engine in the torque switching process, and obtaining the oil pressure of a main oil gallery of the engine.

In practical application, when a driver drives a car, the current torque of the engine can be changed by stepping on the accelerator pedal to change the opening degree of the accelerator pedal. When the engine demand torque changes, it is considered that the engine needs to enter the random cylinder deactivation mode and the cylinder deactivation rate needs to be adjusted according to the target torque, at which time, in order to reach the target torque from the current torque, the amount of intake air in the engine needs to be changed. Alternatively, the intake air amount of the engine may be changed by changing the valve timing angle. The air inlet of the engine is influenced by the air inlet pipeline, so that air path delay is generated, the valve timing angle change needs to stop the work of an engine cylinder electromagnetic valve according to a cylinder deactivation signal, engine oil enters the hydraulic rocker arm mechanism until the angle switching is completed, and valve mechanism delay is generated.

To solve the above problem, the embodiments of the present invention can be used to calculate the system response time during the engine torque switching process, i.e., the response time required for the engine from the start of the torque switching to the completion of the actual torque switching. Specifically, during the torque switching, the current valve timing angle may be obtained directly from the current state of the engine, such as directly from an engine ECU (Electronic Control Unit). Since the engine should have a corresponding valve timing angle in order to achieve a corresponding torque, there is a preset correspondence between the valve timing angle and the torque. At this time, the target valve timing angle may be obtained according to the target torque in the torque switching process and the corresponding relationship between the torque and the valve timing angle, and after the target valve timing angle and the current valve timing angle are obtained, the current valve timing angle and the target valve timing angle may be subtracted to obtain the angle difference in the torque switching process. The target torque and the opening degree of the accelerator pedal have a preset corresponding relationship, and optionally, the target torque and the opening degree of the accelerator pedal have a preset corresponding relationship and are stored in the ECU.

In the embodiment of the invention, when the engine changes the valve timing angle from the current valve timing angle to the target valve timing angle, the electromagnetic valve of the engine cylinder needs to be stopped according to the cylinder deactivation signal, and then the engine oil enters the hydraulic rocker mechanism until the angle switching is completed, wherein the influence of the pressure of the engine oil in the main oil gallery is larger in the process of the engine oil entering the hydraulic rocker mechanism. Therefore, the main oil gallery oil pressure during the torque switching process may be obtained, and optionally, the main oil gallery oil pressure may be obtained by an oil pressure sensor installed on the engine main oil gallery.

Step 102: and calculating a first response time of the engine according to the angle difference and the oil pressure of the main oil gallery.

In the embodiment of the invention, after the angle difference in the torque switching process is obtained, the first response time of the engine reaching the target valve timing angle from the current valve timing angle can be calculated according to the angle difference and the oil pressure of the main oil gallery, wherein the first response time comprises the air passage delay time and is mainly determined by the time required by the adjustment of the valve timing angle, and the first response time is mainly related to the time required by the valve timing angle to change the angle difference because the air inlet pipeline has the effect of blocking air inlet on the basis of the adjustment of the valve timing angle. Because the oil pressure of the main oil gallery also has certain influence on the changing process of the valve timing angle, the time required for changing the valve timing angle by the angle difference can be actually determined according to the angle difference and the oil pressure of the main oil gallery, and therefore the response time of an air inlet pipeline of the engine is determined to obtain first response time.

Step 103: and calculating a second response time of the engine according to the oil pressure of the main oil gallery.

In the embodiment of the invention, the second response time can comprise valve mechanism delay time, and mainly comprises the time required by the ECU of the automobile to start working of the electromagnetic valve after the ECU sends out a cylinder deactivation signal according to the cylinder deactivation rate and the cylinder deactivation sequence, and the engine oil enters the hydraulic rocker arm mechanism until the engine is switched to the cylinder deactivation state, and the process is greatly influenced by the pressure of the engine oil in the main oil gallery, so that the second response time of the engine can be calculated according to the pressure of the engine oil in the main oil gallery.

Step 104: determining a system response time of the engine based on the first response time and the second response time.

In the embodiment of the present invention, after the first response time and the second response time are obtained, the system response time may be determined according to the first response time and the second response time, and optionally, a larger value of the first response time and the second response time may be used as the system response time, that is, a target valve timing angle is reached from a current valve timing angle in an engine intake process and a process of adjusting a valve timing angle with an engine, or a process of allowing engine oil to enter a hydraulic rocker arm mechanism until engine switching is completed according to a cylinder deactivation signal solenoid valve operation is completed, and which required time is the actual system response time.

Fig. 2 is a flowchart of steps of another method for calculating an engine response time according to an embodiment of the present invention, as shown in fig. 2, and on the basis of fig. 1, after step 101, the method further includes:

step 1011: and acquiring a gas quantity difference between the current gas quantity and the target gas quantity of the engine in the torque switching process.

In the embodiment of the invention, the current air intake quantity can be directly obtained according to the current state of the engine. Since the engine should have a corresponding intake air amount in order to obtain a corresponding torque, there is a preset correspondence relationship between the intake air amount and the torque. The target air inflow can be obtained according to the target torque in the torque switching process and the corresponding relation between the torque and the air inflow, and after the target air inflow and the current air inflow are obtained, the current air inflow and the target air inflow can be subjected to subtraction, so that the air amount difference in the torque switching process is obtained.

Optionally, step 102 comprises:

step 1021: and calculating first response time of the engine according to the angle difference, the oil pressure of the main oil gallery and the air quantity difference.

In the embodiment of the invention, the time required for changing the angle difference of the valve timing angle under the condition of not being influenced by the air intake process can be obtained according to the angle difference and the oil pressure of the main oil gallery, but different air intake amounts have certain influence on the time in the actual process, so that in order to ensure that the calculated first response time is more consistent with the actual condition, the time required for changing the angle difference of the valve timing angle can be corrected through the obtained air difference in the torque switching process, and the first response time which is more consistent with the actual condition can be obtained.

Optionally, the step 1021 comprises:

substep S11: and determining first initial response time according to the angle difference and the oil pressure of the main oil gallery.

Optionally, in the embodiment of the present invention, a corresponding relationship between an angle difference of the valve timing angle, oil pressure of the main oil gallery and a first initial response time is measured according to an experiment on the engine, and a corresponding first initial response time table is drawn, so that a corresponding first initial response time is determined in the first initial response time table according to the angle difference in the current torque switching process and the oil pressure of the main oil gallery, where the first initial response time is a time required by the engine to reach a target valve timing angle from a current valve timing angle when an intake pipe does not block intake air.

Substep S12: and determining a gas path delay coefficient according to the gas amount difference and the current rotating speed of the engine.

In the embodiment of the invention, when the first response time is calculated, due to the blocking effect of the air inlet pipeline on the air inlet process, the time required for changing the angle difference of the valve timing angle is corrected according to the air quantity difference, and the air path delay coefficient of the air inlet pipeline of the current engine can be confirmed according to the air quantity difference, wherein the air quantity difference, the engine rotating speed and the air path delay coefficient of the air inlet pipeline have corresponding relations. Alternatively, the engine speed may be obtained from the ECU of the vehicle.

Step S13: and calculating the first response time according to the first initial response time and the gas path delay coefficient.

In the embodiment of the invention, because the first response time is hindered by the air inlet pipeline in practical application, the time required by the actual engine to reach the target valve timing angle from the current valve timing angle can be obtained by multiplying the first initial response time by the corresponding air circuit delay coefficient, namely the accurate first response time which is in line with the actual situation is obtained.

As shown in fig. 2, on the basis of fig. 1, step 103 includes:

step 1031: and determining a second initial response time according to the oil pressure of the main oil gallery.

In the embodiment of the invention, the process that the engine oil enters the hydraulic rocker mechanism is greatly influenced by the pressure of the engine oil in the main oil gallery, when the pressure of the engine oil in the main oil gallery is larger, the adjusting speed is high, the response time of the mechanism is shorter, when the pressure of the engine oil in the main oil gallery is smaller, the adjusting speed is slower, and the response time of the mechanism is longer, namely, the pressure of the engine oil in the main oil gallery and the response time of the mechanism have a corresponding relation, so that the initial response time of the mechanism, namely the second initial response time can be determined according to the pressure of the engine oil in the main oil gallery, and the second initial response time is the time required by adjusting the valve timing angle under.

Step 1032: and determining an engine oil pressure drop coefficient according to the angle difference and the engine oil pressure of the main oil gallery.

In the embodiment of the invention, part of oil pressure is consumed in the process of adjusting the valve timing angle, so that the fluctuation of the local oil pressure is caused, the adjustment of the valve timing angle is influenced, and the response time of a mechanism is influenced. In the embodiment of the invention, an engine oil pressure drop coefficient table is obtained through test verification, and the engine oil pressure drop coefficient in the adjustment from the current valve timing angle to the target valve timing angle can be uniquely determined according to the angle difference and the engine oil pressure of the main oil gallery, so that the influence of the valve timing angle adjustment on the mechanism response time is quantized.

Step 1033: and calculating a second response time of the engine from the current valve timing angle to the target valve timing angle according to the second initial response time and the oil pressure drop coefficient.

In the embodiment of the invention, in practical application, the mechanism response time, namely the second response time, is related to the oil pressure of the main oil gallery, and the oil pressure of the main oil gallery is influenced by the valve timing angle adjusting process, so that the time required by the actual engine to reach the target valve timing angle from the current valve timing angle can be obtained by multiplying the second initial response time by the corresponding oil pressure drop coefficient, namely the accurate second response time which is in line with the actual condition is obtained.

Fig. 3 is a logic structure block diagram of a method for calculating engine response time according to an embodiment of the present invention, and as shown in fig. 3, in the embodiment of the present invention, system response time is calculated according to the following logic, an angle difference between a target valve timing angle and a current valve timing angle and a main oil gallery oil pressure are obtained, the angle difference and the main oil gallery oil pressure are input into a first initial response time table to obtain a first initial response time, and the angle difference and the main oil gallery oil pressure are input into an oil pressure drop coefficient table to obtain an oil pressure drop coefficient; inputting the oil pressure of the main oil gallery into a second initial response time table to obtain second initial response time; acquiring a gas quantity difference between target gas inflow and current gas inflow, and inputting the gas quantity difference and the engine rotating speed into a gas circuit delay coefficient table to determine a gas circuit delay coefficient; obtaining first response time according to the first initial response time and the gas path delay coefficient, and obtaining second response time according to the second initial response time and the engine oil pressure drop coefficient; and taking a larger value in comparison between the first response time and the second response time as the system response time.

Fig. 4 is a flowchart illustrating steps of another method for calculating an engine response time according to an embodiment of the present invention, as shown in fig. 4, after step 104 on the basis of fig. 1, the method may further include:

step 105: and acquiring a torque difference in the torque switching process, and determining torque response time according to the torque difference.

In the embodiment of the invention, the torque difference can be a torque difference generated by the change of the opening degree of an accelerator pedal caused by the stepping of the accelerator pedal by a driver, and optionally, a target torque can be determined according to the position of the accelerator pedal, then the current torque of the engine can be obtained from an ECU of the engine, and the torque difference generated by the change of the opening degree of the accelerator pedal can be determined according to the target torque and the current torque. Since the torque response time is directly related to the torque difference, the torque response time can be obtained by the torque difference. Alternatively, a torque response time table, which is a correspondence table between the torque difference and the torque response time, may be established, and then the torque response time may be obtained by querying the torque difference generated due to the change in the opening degree of the accelerator pedal and the correspondence table between the torque difference generated due to the change in the opening degree of the accelerator pedal and the torque response time, which is established in advance. In an embodiment of the present invention, the predetermined torque response schedule may be obtained through multiple tests of the engine.

As will be appreciated by those skilled in the art, in the embodiment of the present invention, since the torque and the accelerator pedal opening have a corresponding relationship, the torque difference may also correspond to an accelerator pedal opening change rate generated when the engine is driven from the current torque to the target torque, and the accelerator pedal opening change rate refers to an opening change rate when the accelerator pedal is stepped from the current opening to the opening of the target torque by the driver. Alternatively, a corresponding relation table of the accelerator pedal opening change rate and the torque response time, that is, a torque response time table, may be established first, and then the torque response time may be obtained through query of the current accelerator pedal opening change rate and the pre-established corresponding relation table of the accelerator pedal opening change rate and the torque response time. In the embodiment of the present invention, the preset torque response time table may be obtained through a plurality of tests on the engine, and the embodiment of the present invention does not limit the preset torque response time table.

Step 106: and determining the cylinder deactivation rate and the cylinder deactivation sequence of the engine according to the torque response time and the system response time.

In the embodiment of the invention, the working state of the engine can be divided into the working state of all cylinders and the working state of random cylinder deactivation. The all-cylinder working state is a state that all cylinders of the engine work; the random cylinder deactivation working state means that in the running process of the vehicle, the engine is controlled to work at different cylinder deactivation rates and cylinder deactivation sequences according to torque requirements under different loads, namely the vehicle can randomly control part of cylinders to stop working according to different torque requirements, so that the purpose that the engine can work with the least number of cylinders on the premise of meeting the torque requirements is achieved, and the optimal working condition oil consumption of the engine can be achieved as far as possible. In the working process, the piston is pushed to rotate by consuming fuel oil, but the energy generated by the consumed fuel oil is used for pushing the piston to rotate the crankshaft, and besides, a part of energy is taken away by high-temperature tail gas and cooling water, and a part of energy is used for overcoming friction resistance to do work, and in addition, a part of energy is used for overcoming pumping loss. Further, the larger the engine displacement, the greater the capacity loss due to friction and pumping loss, and therefore, the same torque is output and the smaller the energy loss of the small displacement engine to overcome friction and pumping loss is than that of the large displacement engine. Therefore, if the engine is controlled to work under a small load, that is, when the target torque is small, the torque output by the working cylinders which are partially closed and are ensured to work continuously can meet the target torque requirement of the engine, because the partial working cylinders are closed, which is equivalent to the reduction of the displacement of the engine, the pumping loss and the friction loss can be reduced, and therefore, the energy consumption of the engine can be saved by randomly stopping the cylinders.

It can be seen that the working principle of the random cylinder deactivation working state is equivalent to dynamically adjusting the displacement of the engine according to different working conditions, thereby reducing the energy consumption of the engine. In order to realize the random cylinder deactivation of the engine, each cylinder of the engine should be provided with an intake valve, an exhaust valve, an oil nozzle and an ignition device which can be independently opened and closed, so that the intake and exhaust of any cylinder can be stopped by closing the intake valve and the exhaust valve at any time, and the ignition and the oil injection are simultaneously stopped, thereby realizing the random cylinder deactivation effect.

In the embodiment of the invention, the cylinder deactivation rate represents the proportion of cylinders in the cylinder deactivation state in the process of the operation of the engine in all cylinders, taking a four-cylinder engine as an example, the four-cylinder engine comprises four cylinders including a first cylinder, a second cylinder, a third cylinder and a fourth cylinder, wherein the four cylinders sequentially enter the operating state once according to the first cylinder, the third cylinder, the fourth cylinder and the second cylinder in the full-cylinder operating state of the engine as a cycle, for convenience of description, the four-cylinder engine is described as 25 cycles, and when the cylinder deactivation rate is 20%, namely the four-cylinder engine is 25 cycles, the cylinders of the engine have 20 times of cylinder deactivation states and 80 times of cylinder deactivation states; when the cylinder deactivation rate is 25%, namely 25 cycles of the four-cylinder engine, 25 times of cylinders of the engine are in a cylinder deactivation state, and 75 times of cylinders of the engine are in an operating state.

In the embodiment of the present invention, the cylinder deactivation sequence indicates a cylinder in a cylinder deactivation state during the operation of the engine, and the position of the cylinder in the engine operation cycle is, for example, a four-cylinder engine, in a full-cylinder operation state, four cylinders sequentially enter an operating state according to the sequence of a first cylinder, a third cylinder, a fourth cylinder, a second cylinder, and a first cylinder, and when the cylinder deactivation rate is 33%, the cylinder deactivation sequence may be:

cylinder deactivation sequence scheme one:

first cylinder operation, third cylinder operation, fourth cylinder deactivation, second cylinder operation, first cylinder operation, third cylinder deactivation, fourth cylinder operation, second cylinder operation, first cylinder deactivation, · · · · · · ·;

cylinder deactivation sequence scheme two:

deactivating a first cylinder, activating a third cylinder, activating a fourth cylinder, deactivating a second cylinder, activating a first cylinder, activating a third cylinder, deactivating a fourth cylinder, activating a second cylinder, activating a first cylinder;

cylinder deactivation sequence scheme three:

first cylinder operation, third cylinder deactivation, fourth cylinder operation, second cylinder operation, first cylinder deactivation, third cylinder operation, fourth cylinder operation, second cylinder deactivation, first cylinder operation, ·.

The three cylinder deactivation sequences can be verified through experiments, and the cylinder deactivation sequence with the minimum engine vibration and the best transition when the states among the cylinders are switched is selected.

In the implementation of the invention, when the torque response time is shorter than the system response time, namely the time for explaining the torque change is shorter than the time required by the current engine cylinder deactivation switching, namely the time required by the engine to execute the cylinder deactivation command issuing is shorter than the time required by the process of the engine cylinder deactivation switching, at the moment, the system response time cannot meet the requirement of a driver on the torque switching, and the cylinder deactivation rate of the engine and the cylinder deactivation sequence can be controlled not to change. On the contrary, if the torque response time is greater than or equal to the system response time, the response time of the cylinder deactivation mechanism can meet the requirement of a driver for torque switching, and in order to achieve a more ideal energy-saving and emission-reduction effect, the engine of the engine mechanism can be controlled to determine a new cylinder deactivation rate and a new cylinder deactivation sequence according to the target torque.

According to the method for calculating the response time of the engine, provided by the embodiment of the invention, the first response time, namely the gas path response time, and the second response time, namely the valve mechanism response time, in the torque switching process are calculated respectively according to the angle difference of the engine in the process of switching from the current torque to the target torque and the oil pressure of the main oil gallery, and the system response time is determined by comparing the gas path response time with the valve mechanism response time, so that the system response time required by the random cylinder deactivation engine in the torque switching process can be accurately calculated. In addition, the determined system response time can be applied to subsequent switching of the cylinder deactivation rate and selection of the cylinder deactivation sequence scheme of the engine, and the cylinder deactivation rate and the selection of the cylinder deactivation sequence scheme can be more consistent with the actual working state of the engine based on the determined system response time, so that the effect of reducing the oil consumption of the engine while the output of the engine is kept is achieved.

Fig. 5 is a block diagram of an apparatus 500 for calculating engine response time according to an embodiment of the present invention, as shown in fig. 5, the apparatus may include:

the data acquisition module 501 is configured to acquire an angle difference between a current valve timing angle and a target valve timing angle of an engine in a torque switching process, and an oil pressure of a main oil gallery of the engine;

a first response time calculation module 502 for calculating a first response time of the engine according to the angle difference and the main gallery oil pressure;

a second response time calculation module 503, configured to calculate a second response time of the engine according to the main gallery oil pressure;

a system response time determination module 504 that determines a system response time of the engine based on the first response time and the second response time.

Optionally, the data obtaining module 501 is further configured to obtain a gas quantity difference between a current gas quantity and a target gas quantity of the engine during the torque switching process;

the first response time calculation module 502 is specifically configured to calculate a first response time of the engine according to the angle difference, the main oil gallery oil pressure, and the air quantity difference.

Optionally, the first response time calculation module 502 includes:

a first initial response time determination submodule for determining a first initial response time according to the angle difference and the oil pressure of the main oil gallery;

the gas circuit delay coefficient determining submodule is used for determining a gas circuit delay coefficient according to the gas quantity difference and the current rotating speed of the engine;

and the first response time determining submodule is used for calculating the first response time according to the first initial response time and the gas circuit delay coefficient.

Optionally, the second response time calculation module 503 includes:

the second initial response time determining submodule is used for determining second initial response time according to the oil pressure of the main oil gallery;

the engine oil pressure drop coefficient determining submodule is used for determining an engine oil pressure drop coefficient according to the angle difference and the engine oil pressure of the main oil gallery;

and the second response time determining submodule is used for calculating the second response time of the engine according to the second initial response time and the oil pressure drop coefficient.

Optionally, the apparatus further comprises:

the torque response time determining module is used for acquiring torque difference in the torque switching process and determining torque response time according to the torque difference;

and the random cylinder deactivation module is used for determining the cylinder deactivation rate and the cylinder deactivation sequence of the engine according to the torque response time and the system response time.

The embodiment of the invention also provides an automobile which comprises the device for calculating the response time of the engine.

In summary, the device for calculating the response time of the engine provided in the embodiment of the present invention calculates the first response time, i.e., the gas path response time, and the second response time, i.e., the valve mechanism response time, in the torque switching process according to the angle difference and the oil pressure of the main oil gallery during the switching process of the engine from the current torque to the target torque, and determines the system response time by comparing the gas path response time and the valve mechanism response time, so as to accurately calculate the actually required system response time of the randomly deactivated engine in the torque switching process. In addition, the determined system response time can also be applied to subsequent switching of the cylinder deactivation rate of the engine and selection of the cylinder deactivation scheme, and the selection of the cylinder deactivation rate and the cylinder deactivation scheme can be more consistent with the actual working state of the engine based on the determined system response time, so that the effect of reducing the oil consumption of the engine while the output of the engine is kept is achieved.

It is clear to those skilled in the art that, for convenience and brevity of description, the specific working processes of the above-described systems, apparatuses and units may refer to the corresponding processes in the foregoing method embodiments, and are not described herein again.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention.

The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and all the changes or substitutions should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.