阅读说明：本技术 发动机涡轮增压器的增压控制方法及装置 (Supercharging control method and device for engine turbocharger ) 是由 王盼盼 江楠 张红倩 张家林 张润东 于 2021-08-02 设计创作，主要内容包括：本发明实施例公开了一种发动机涡轮增压器的增压控制方法及装置。其中,发动机涡轮增压器的增压控制方法包括：基于涡轮增压器物理模型,根据目标增压压力值,获取前馈值；将所述目标增压压力值和所述发动机的节气门前的实际压力值的差值经预设闭环控制算法,获取修正值；根据所述前馈值和所述修正值,控制所述涡轮增压器的废气旁通阀的开度。本发明实施例提供的技术方案可以提高瞬态工况变化时增压器对进气压力控制的响应速度,能够消除稳态误差。(The embodiment of the invention discloses a method and a device for controlling the boost of an engine turbocharger. The supercharging control method of the engine turbocharger comprises the following steps: acquiring a feedforward value according to a target supercharging pressure value based on a physical model of the turbocharger; obtaining a correction value by a preset closed-loop control algorithm according to the difference value between the target supercharging pressure value and the actual pressure value of the engine before a throttle valve; and controlling the opening of a waste gas bypass valve of the turbocharger according to the feedforward value and the correction value. The technical scheme provided by the embodiment of the invention can improve the response speed of the supercharger on the control of the air inlet pressure when the transient working condition changes, and can eliminate the steady-state error.)

1. A supercharging control method of an engine turbocharger, characterized by comprising:

acquiring a feedforward value according to a target supercharging pressure value based on a physical model of the turbocharger;

obtaining a correction value by a preset closed-loop control algorithm according to the difference value between the target supercharging pressure value and the actual pressure value of the engine before a throttle valve;

and controlling the opening of a waste gas bypass valve of the turbocharger according to the feedforward value and the correction value.

2. The boost control method of an engine turbocharger according to claim 1, wherein the turbocharger includes: a compressor and a turbine; the physical model of the turbocharger comprises: a compressor physical model and a turbine physical model;

based on the physical model of the turbocharger, obtaining the feedforward value according to the target supercharging pressure value comprises:

acquiring target power of the gas compressor according to a target supercharging pressure value on the basis of the physical model of the gas compressor;

determining the target power of the turbine according to the target power of the compressor;

and acquiring a feed-forward value according to the target power of the turbine based on the physical model of the turbine.

3. The method of controlling boost pressure of an engine turbocharger according to claim 2,

based on the physical model of the gas compressor, obtaining the target power of the gas compressor according to the target supercharging pressure value comprises the following steps:

and determining the target power of the compressor according to a target supercharging pressure value, an upstream pressure detection value of the compressor, an air inlet temperature detection value of the compressor and an air inlet amount detection value of the compressor on the basis of the physical model of the compressor.

4. The method of controlling boost pressure of an engine turbocharger according to claim 2,

based on the physical model of the turbine, obtaining a feed forward value in accordance with the target power of the turbine comprises:

determining a target pressure ratio of an upstream pressure and a downstream pressure of the turbine based on the target power of the turbine;

determining a target upstream pressure value of the turbine according to a target pressure ratio of the upstream pressure and the downstream pressure of the turbine and a downstream pressure detection value of the turbine;

based on the turbine physical model, a feed-forward value is acquired in accordance with a target upstream pressure value of the turbine, a downstream pressure detection value of the turbine, a flow rate detection value of the gas flowing into the wastegate valve, and an upstream temperature detection value of the turbine.

5. The method of controlling boost pressure of an engine turbocharger according to claim 1, wherein controlling the opening degree of a wastegate valve of the turbocharger in accordance with the feed-forward value and the correction value includes:

and determining a driving signal of an electric control driver for controlling the opening of the waste gas bypass valve according to the feedforward value and the correction value.

6. A boost control apparatus of an engine turbocharger, characterized by comprising:

the feedforward control module is used for acquiring a feedforward value according to a target supercharging pressure value based on a physical model of the turbocharger;

the closed-loop control module is used for acquiring a correction value by a preset closed-loop control algorithm according to the difference value between the target supercharging pressure value and the actual pressure value of the engine before a throttle valve;

and the opening control module is used for controlling the opening of the waste gas bypass valve of the turbocharger according to the feedforward value and the correction value.

7. The boost control device of an engine turbocharger according to claim 6, wherein the turbocharger includes: a compressor and a turbine; the physical model of the turbocharger comprises: a compressor physical model and a turbine physical model;

the feedforward control module includes:

the compressor power type obtaining unit is used for obtaining the target power of the compressor according to a target supercharging pressure value on the basis of the compressor physical model;

the turbine power determining unit is used for determining the target power of the turbine according to the target power of the compressor;

and the feed-forward value acquisition unit is used for acquiring a feed-forward value according to the target power of the turbine based on the physical model of the turbine.

8. The boost control device of an engine turbocharger according to claim 7,

the compressor model calculation unit is used for determining the target power of the compressor according to a target supercharging pressure value, an upstream pressure detection value of the compressor, an air inlet temperature detection value of the compressor and an air inlet amount detection value of the compressor based on the physical model of the compressor.

9. The boost control device of an engine turbocharger according to claim 7,

the feedforward value acquisition unit includes:

a pressure ratio determining subunit for determining a target pressure ratio of the upstream pressure and the downstream pressure of the turbine, based on the target power of the turbine;

an upstream pressure determining subunit for determining a target upstream pressure value of the turbine based on a target pressure ratio of an upstream pressure and a downstream pressure of the turbine, and a downstream pressure detection value of the turbine;

a feedforward value acquisition subunit configured to acquire a feedforward value from a target upstream pressure value of the turbine, a downstream pressure detection value of the turbine, a flow rate detection value of the gas flowing into the wastegate valve, and an upstream temperature detection value of the turbine, based on the turbine physical model.

10. The boost control device of an engine turbocharger according to claim 6, wherein the opening degree control module is configured to determine a drive signal of an electrically controlled actuator that controls the opening degree of the wastegate valve, based on the feed forward value and the correction value.

Technical Field

The invention relates to the technical field of engines, in particular to a method and a device for controlling the boost of an engine turbocharger.

Background

The control of the air intake amount of the engine generally adopts the joint control of a throttle valve and a supercharger. Generally, under low load, the air intake amount is mainly controlled by a throttle valve, and a supercharger is not involved; at medium and high loads, the supercharger intervenes, and the throttle valve and the supercharger jointly control the intake air amount.

Because the gas after being supercharged by the supercharger enters the cylinder of the engine and needs to flow through a section of pipeline, the air inlet control has certain hysteresis. In the prior art, the control on the supercharger is mainly realized through single closed-loop control, the control method can realize good pressure control in a steady state, but cannot well respond to the supercharging pressure in transient working condition change, and the problem of slow response of actual air inflow change exists.

Disclosure of Invention

The embodiment of the invention provides a supercharging control method and device of an engine turbocharger, which are used for improving the response speed of the turbocharger to intake pressure control during transient working condition change and eliminating steady-state errors.

In a first aspect, an embodiment of the present invention provides a method for controlling boost of an engine turbocharger, including:

acquiring a feedforward value according to a target supercharging pressure value based on a physical model of the turbocharger;

obtaining a correction value by a preset closed-loop control algorithm according to the difference value between the target supercharging pressure value and the actual pressure value of the engine before a throttle valve;

and controlling the opening degree of a waste gate valve of the turbocharger according to the feedforward value and the correction value.

Further, the turbocharger includes: a compressor and a turbine; the physical model of the turbocharger comprises: a compressor physical model and a turbine physical model;

based on the physical model of the turbocharger, obtaining the feedforward value according to the target supercharging pressure value comprises:

based on a physical model of the gas compressor, acquiring target power of the gas compressor according to a target supercharging pressure value;

determining the target power of the turbine according to the target power of the compressor;

based on the physical model of the turbine, a feed forward value is obtained according to the target power of the turbine.

Further, based on the physical model of the compressor, obtaining the target power of the compressor according to the target supercharging pressure value includes:

and determining the target power of the compressor according to the target supercharging pressure value, the upstream pressure detection value of the compressor, the air inlet temperature detection value of the compressor and the air inlet amount detection value of the compressor on the basis of the physical model of the compressor.

Further, obtaining a feed forward value from a target power of the turbine based on the physical model of the turbine comprises:

determining a target pressure ratio of an upstream pressure and a downstream pressure of the turbine according to the target power of the turbine;

determining a target upstream pressure value of the turbine according to a target pressure ratio of the upstream pressure and the downstream pressure of the turbine and a downstream pressure detection value of the turbine;

based on the turbine physical model, a feed forward value is acquired from a target upstream pressure value of the turbine, a downstream pressure detection value of the turbine, a flow rate detection value of an air flowing into the wastegate valve, and an upstream temperature detection value of the turbine.

Further, the controlling the opening degree of the wastegate valve of the turbocharger based on the feed-forward value and the correction value includes:

and determining a drive signal of an electrically controlled actuator for controlling the opening of the wastegate valve based on the feedforward value and the correction value.

In a second aspect, an embodiment of the present invention further provides a boost control device for a turbocharger of an engine, including:

the feedforward control module is used for acquiring a feedforward value according to a target supercharging pressure value based on a physical model of the turbocharger;

the closed-loop control module is used for acquiring a correction value from the difference value between the target supercharging pressure value and the actual pressure value of the engine before the throttle valve through a preset closed-loop control algorithm;

and the opening control module is used for controlling the opening of the waste gas bypass valve of the turbocharger according to the feedforward value and the correction value.

Further, the turbocharger includes: a compressor and a turbine; the physical model of the turbocharger comprises: a compressor physical model and a turbine physical model;

the feedforward control module includes:

the compressor power type obtaining unit is used for obtaining the target power of the compressor according to the target supercharging pressure value based on the physical model of the compressor;

the turbine power determining unit is used for determining the target power of the turbine according to the target power of the compressor;

and the feed-forward value acquisition unit is used for acquiring a feed-forward value according to the target power of the turbine based on the physical model of the turbine.

Further, the compressor model calculation unit is used for determining the target power of the compressor according to the target supercharging pressure value, the upstream pressure detection value of the compressor, the air inlet temperature detection value of the compressor and the air inlet amount detection value of the compressor based on the physical model of the compressor.

Further, the feedforward value acquisition unit includes:

a pressure ratio determining subunit for determining a target pressure ratio of the upstream pressure and the downstream pressure of the turbine, based on the target power of the turbine;

an upstream pressure determining subunit for determining a target upstream pressure value of the turbine based on a target pressure ratio of the upstream pressure and the downstream pressure of the turbine, and a downstream pressure detection value of the turbine;

and a feedforward value acquisition subunit configured to acquire a feedforward value from a target upstream pressure value of the turbine, a downstream pressure detection value of the turbine, a gas flow amount detection value flowing into the wastegate valve, and an upstream temperature detection value of the turbine, based on the turbine physical model.

And the opening control module is used for determining a driving signal of an electric control driver for controlling the opening of the waste gas bypass valve according to the feedforward value and the correction value.

In the technical scheme of the embodiment of the invention, based on a physical model of the turbocharger, a feedforward value is obtained according to a target supercharging pressure value; obtaining a correction value by a preset closed-loop control algorithm according to the difference value between the target supercharging pressure value and the actual pressure value of the engine before a throttle valve; and controlling the opening degree of a waste gate valve of the turbocharger according to the feedforward value and the correction value. Through feedforward control and feedback closed-loop control based on a physical model of the turbocharger, the response speed of the turbocharger to the intake pressure control during transient working condition change can be improved, and steady-state deviation is reduced.

Drawings

FIG. 1 is a flowchart of a method for controlling boost pressure of an engine turbocharger according to an embodiment of the present invention;

FIG. 2 is a schematic structural diagram of an engine according to an embodiment of the present invention;

FIG. 3 is a control schematic diagram provided by an embodiment of the present invention;

FIG. 4 is a flowchart of a method for controlling boost pressure of a turbocharger of an engine according to another embodiment of the present invention;

FIG. 5 is a flowchart of a method for controlling boost pressure of a turbocharger of an engine according to another embodiment of the present invention;

FIG. 6 is a graphical illustration of throttle fluid characteristics provided by an embodiment of the present invention;

FIG. 7 is a schematic structural diagram of a boost control device of an engine turbocharger according to an embodiment of the present invention;

FIG. 8 is a schematic structural diagram of a boost control device of a turbocharger of another engine according to an embodiment of the present invention;

fig. 9 is a schematic structural diagram of an electronic device according to an embodiment of the present invention.

Detailed Description

The present invention will be described in further detail with reference to the accompanying drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some of the structures related to the present invention are shown in the drawings, not all of the structures.

The embodiment of the invention provides a supercharging control method of an engine turbocharger. Fig. 1 is a flowchart of a method for controlling boost pressure of an engine turbocharger according to an embodiment of the present invention. Fig. 2 is a schematic structural diagram of an engine according to an embodiment of the present invention. Fig. 3 is a control schematic diagram according to an embodiment of the present invention. The method for controlling the boost pressure of the turbocharger of the engine can be executed by a boost pressure Control device of the turbocharger of the engine, which can be realized by software and/or hardware, and the device can be integrated in an Electronic Control Unit (ECU) of the engine. The supercharging control method of the engine turbocharger specifically comprises the following steps:

and step 110, acquiring a feedforward value according to the target supercharging pressure value based on the physical model of the turbocharger.

Wherein, prior to step 110, a turbocharger physical model may be pre-established. As shown in fig. 2, the turbocharger 100 may include: a compressor 1, a turbine 2 and a wastegate valve 3. The outlet of the compressor 1 may communicate with the inlet of a cylinder 11 of the engine via a throttle 4. An exhaust port of a cylinder 11 of the engine may be communicated with an intake port of the turbine 2 and a first end of the wastegate valve 3 through a tee structure, and an exhaust port of the turbine 2 and a second end of the wastegate valve 3 may be communicated with an exhaust gas treatment device through a tee structure. Exhaust gas discharged from a cylinder 11 of the engine is introduced into the turbine 2, and the energy of the exhaust gas is used for driving the turbine 2 to rotate, thereby driving the compressor 1 coaxial with the turbine to realize supercharging.

The pressure at the outlet of the compressor 1 can be controlled by controlling the opening of the wastegate valve 3. The larger the opening degree of the wastegate valve 3 is, the larger the flow rate of the gas flowing into the wastegate valve 3 is, the smaller the flow rate of the gas flowing into the turbine 2 is, the smaller the energy for rotating the turbine 2 is, the worse the supercharging capacity of the compressor 1 is, and the smaller the pressure at the outlet of the compressor 1 is. The smaller the opening degree of the wastegate valve 3 is, the smaller the flow rate of the gas flowing into the wastegate valve 3 is, the larger the flow rate of the gas flowing into the turbine 2 is, the larger the energy for rotating the turbine 2 is, the stronger the supercharging capacity of the compressor 1 is, and the larger the pressure at the outlet of the compressor 1 is.

In order to enable the pressure of the air outlet of the air compressor 1 to reach the target supercharging pressure value, the opening degree of the waste gas bypass valve can be calculated based on a physical model of the turbocharger. The turbocharger physical model may include a formula and/or a data mapping table. The formula and/or data mapping table for the physical model of the turbocharger may be obtained from relationships between the turbocharger parameters provided by the turbocharger manufacturer. The formula and/or data mapping table of the physical model of the turbocharger may include a plurality of parameters such as the pressure of the outlet port, the opening degree of the wastegate valve, and the like. And setting the pressure of the air outlet in a formula and/or a data corresponding table of a physical model of the turbocharger as a target supercharging pressure value, taking the opening of the waste gas bypass valve as an unknown quantity, detecting other parameters through corresponding sensors, and substituting the parameters into the formula and/or the data corresponding table of the physical model of the turbocharger to obtain the opening K1 of the waste gas bypass valve as a feedforward value. Alternatively, the drive signal D1 of the electronically controlled actuator 13 for controlling the opening degree of the wastegate valve 3 is obtained as a feedforward value based on the opening degree K1 of the wastegate valve. The feed forward value corresponds to the base value. In order to make the physical model of the turbocharger more accurate, parameters in the physical model of the turbocharger can be converted and corrected according to standard environmental conditions.

The feedforward control is realized by acquiring a feedforward value based on a physical model of the turbocharger, and the response speed of the turbocharger to the control of the intake pressure during transient working condition change can be improved.

And step 120, obtaining a correction value by a preset closed-loop control algorithm according to the difference value between the target supercharging pressure value and the actual pressure value of the engine before the throttle valve.

The preset closed-loop control algorithm may include a Proportional Integral Derivative (PID) algorithm or a Proportional Integral (PI) algorithm, etc. The correction value may be a correction value of the opening degree of the wastegate valve, or the correction value may be a correction value of a drive signal of the electronically controlled actuator 13 that controls the opening degree of the wastegate valve 3.

Wherein steady state errors may be reduced by feedback closed loop control.

And step 130, controlling the opening of the waste gate valve of the turbocharger according to the feedforward value and the correction value.

If the feedforward value and the correction value correspond to the opening degree of the wastegate valve of the turbocharger, a target value of the opening degree of the wastegate valve is obtained based on the feedforward value and the correction value, and a target value of the drive signal of the electronically controlled actuator 13 that controls the opening degree of the wastegate valve 3 is obtained based on the target value of the opening degree of the wastegate valve. If the feedforward value and the correction value correspond to the drive signal of the electronically controlled actuator 13 that controls the opening degree of the wastegate valve 3, the target value of the drive signal of the electronically controlled actuator 13 that controls the opening degree of the wastegate valve 3 can be directly obtained from the feedforward value and the correction value.

Based on the feedforward of a turbocharger model, the input of the feedforward is mostly the value measured by an actual sensor, and the feedforward is more suitable for the actual working condition; and the feedforward control can make the boost pressure go on according to the demand boost pressure, corresponding transient state change in real time, and closed-loop control can eliminate the steady state error for the better tracking of boost pressure is expected value.

Alternatively, the opening degree of the wastegate valve 3 of the turbocharger is controlled based on the sum of the feed forward value and the correction value. The drive signal of the electronically controlled actuator 13 that controls the opening degree of the wastegate valve 3 is determined based on the sum of the feed forward value and the correction value.

In the technical scheme of the embodiment, a feedforward value is obtained according to a target supercharging pressure value based on a physical model of a turbocharger; obtaining a correction value by a preset closed-loop control algorithm according to the difference value between the target supercharging pressure value and the actual pressure value of the engine before a throttle valve; and controlling the opening degree of a waste gate valve of the turbocharger according to the feedforward value and the correction value. Through feedforward control and feedback closed-loop control based on a physical model of the turbocharger, the response speed of the turbocharger to the intake pressure control during transient working condition change can be improved, and steady-state deviation is reduced.

The embodiment of the invention provides a supercharging control method of an engine turbocharger. Fig. 4 is a flowchart of a supercharging control method for a turbocharger of an engine according to another embodiment of the present invention. The turbocharger may include: a compressor and a turbine. The turbocharger physical model may include: a compressor physical model and a turbine physical model. On the basis of the above embodiment, the supercharging control method includes:

and step 210, acquiring the target power of the compressor according to the target supercharging pressure value based on the physical model of the compressor.

Wherein, before step 210, a compressor physical model can be established in advance. In order to make the pressure at the air outlet of the compressor 1 reach the target supercharging pressure value, the power required to be supplied to the compressor is the target power. The larger the target supercharging pressure value is, the larger the target power of the required compressor is.

The compressor physical model may include equations and/or data mapping tables. The formula and/or data mapping table of the compressor physical model may include a plurality of parameters such as pressure of the air outlet, power of the compressor, and the like. Setting the pressure of an air outlet in a formula and/or a data corresponding table of a physical model of the air compressor as a target supercharging pressure value, taking the power of the air compressor as an unknown quantity, detecting other parameters through corresponding sensors, and substituting the parameters into the formula and/or the data corresponding table of the physical model of the air compressor to obtain the power of the air compressor as the target power of the air compressor.

And step 220, determining the target power of the turbine according to the target power of the compressor.

Optionally, the target power P2 of the turbine is P1/η, where the reduced power correction coefficient η is the efficiency of the turbine 2 driving the compressor 1 to achieve supercharging, and P1 is the target power of the compressor.

Step 230, acquiring a feed forward value according to the target power of the turbine based on the physical model of the turbine.

Wherein, prior to step 230, a turbine physics model may be pre-established. The greater the target power of the turbine 2, the smaller the opening degree of the required wastegate valve 3. The turbine physics model may include equations and/or data mapping tables. The turbine physical model formula (also known as a throttle equation) and/or the data map may include a plurality of parameters such as turbine power, wastegate valve opening, and the like. The turbine power in the turbine physical model formula and/or data correspondence table is set as the turbine target power P2, the waste gate valve 3 opening is used as unknown quantity, the rest parameters can be detected by corresponding sensors, and the residual parameters are substituted into the turbine physical model formula and/or data correspondence table to obtain the waste gate valve opening K1 as feed-forward value. Alternatively, the drive signal D1 of the electronically controlled actuator 13 for controlling the opening degree of the wastegate valve 3 is obtained as a feedforward value based on the opening degree K1 of the wastegate valve.

And 240, obtaining a correction value by the difference value between the target supercharging pressure value and the actual pressure value of the engine before the throttle valve through a preset closed-loop control algorithm.

And step 250, controlling the opening of the waste gas bypass valve of the turbocharger according to the feedforward value and the correction value.

The embodiment of the invention provides a supercharging control method of an engine turbocharger. Fig. 5 is a flowchart of a supercharging control method for a turbocharger of an engine according to another embodiment of the present invention. On the basis of the above embodiment, the supercharging control method includes:

and step 310, determining the target power of the compressor according to the target supercharging pressure value, the upstream pressure detection value of the compressor, the air inlet temperature detection value of the compressor and the air inlet amount detection value of the compressor based on the physical model of the compressor.

The formula and/or the data mapping table of the compressor physical model may include: parameters such as the downstream pressure of the compressor, the upstream pressure of the compressor, the air inlet temperature of the compressor, the air inlet quantity of the compressor and the like. The downstream pressure of the compressor is the pressure at the outlet of the compressor 1. The upstream pressure of the compressor is the pressure at the inlet of the compressor 1.

As shown in fig. 3, the upstream pressure detection value of the compressor can be detected by a first pressure sensor 6 arranged at the air inlet of the compressor 1; the air inlet temperature detection value of the air compressor can be obtained by detecting a first temperature sensor 7 arranged at an air inlet of the air compressor 1; the air inflow detection value of the compressor can be obtained by detecting a first gas flow meter 5 arranged at the air inlet of the compressor 1.

And step 320, determining the target power of the turbine according to the target power of the compressor.

Step 330, determining a target pressure ratio of the upstream pressure and the downstream pressure of the turbine based on the target power of the turbine.

Wherein the larger the target power of the turbine 2, the larger the required target pressure ratio of the upstream pressure and the downstream pressure of the turbine. Prior to step 330, the power of the turbine may be pre-established to correspond to the pressure ratio of the upstream pressure and the downstream pressure of the turbine, such that the target pressure ratio of the upstream pressure and the downstream pressure of the turbine may be subsequently determined based on the target power of the turbine and the corresponding relationship of the power of the turbine to the pressure ratio of the upstream pressure and the downstream pressure of the turbine.

Step 340, determining a target upstream pressure value of the turbine according to the target pressure ratio of the upstream pressure and the downstream pressure of the turbine and the downstream pressure detection value of the turbine.

Wherein the downstream pressure of the turbine is the pressure at the outlet of the turbine 2. As shown in fig. 3, the downstream pressure detection value of the turbine may be detected by a second pressure sensor 8 provided at the outlet of the turbine 2.

And step 350, acquiring a feed-forward value according to the target upstream pressure value of the turbine, the downstream pressure detection value of the turbine, the air flow detection value flowing into the waste gate valve and the upstream temperature detection value of the turbine based on the physical model of the turbine.

Wherein the formula and/or data mapping table of the physical model of the turbomachine may include: downstream pressure of the turbine, upstream pressure of the turbine, amount of airflow into the wastegate valve, and upstream temperature of the turbine. The pressure upstream of the turbine may be the pressure at the inlet of the turbine. The temperature upstream of the turbine may be the temperature of the inlet of the turbine.

As shown in fig. 3, the upstream temperature detection value of the turbine may be detected by a second temperature sensor 10 provided at the intake port of the turbine 2; the detected value of the amount of flow of the gas flowing into the wastegate valve can be detected by the second gas flow meter 9 provided in the passage where the wastegate valve 3 is located.

And step 360, obtaining a correction value by the difference value between the target supercharging pressure value and the actual pressure value of the engine before the throttle valve through a preset closed-loop control algorithm.

The actual pressure value in front of the throttle valve 4 of the engine can be detected by a third pressure sensor 12 arranged on a passage where the throttle valve 4 is communicated with the air outlet of the compressor 1.

And step 370, determining a driving signal of an electric control driver for controlling the opening of the waste gate valve according to the feedforward value and the correction value.

Wherein, the opening degree of the wastegate valve 3 can be controlled by controlling the duty ratio of the drive signal of the electrically controlled driver 13. The electrically controlled actuator 13 may comprise an electrically controlled bleed valve or the like. The opening degree of the waste gas bypass valve is determined by the opening degree of the electronic control air release valve, and the required duty ratio at the electronic control air release valve can be obtained according to the mechanical relationship at the waste gas bypass valve. The opening of the wastegate valve can be controlled by controlling the drive signal of the electronically controlled actuator 13, thereby adjusting the energy of the exhaust gas flowing through the turbine.

FIG. 6 is a graphical illustration of throttle fluid characteristics provided by an embodiment of the present invention. The horizontal axis represents the post-throttle pressure P_bWith the pressure P in front of the throttle_fPressure ratio P of_b/P_fAnd the vertical axis represents throttle airflow. According to the fluid characteristics of the throttle valve, the throttle valve is divided into a supersonic speed area, a throttling area and a non-throttling area according to the influence of the pressure ratio between the front and the rear of the throttle valve on the flow passing through the throttle valve. In the supersonic region, the pressure P behind the throttle_bWith the pressure P in front of the throttle_fPressure ratio P of_b/P_fLess than 0.5283, the amount of fresh intake air flowing through the throttle valve is constant regardless of the pressure ratio. In the throttle zone, 0.95<P_b/P_f<0.5283, the fresh air intake flowing through the throttle valve is substantially linear with the pressure ratio, and the flow rate is changed as the pressure ratio is changed. In the non-restricted zone, P_b/P_f>0.95, small changes in the pressure ratio across the throttle can cause large flow variations, which can be detrimental to system stability. This can be avoided to some extent if the supercharger is capable of rapid response: the control of the throttle valve has a throttling area and a non-throttling area, when the supercharger is inserted, if the throttle valve is in the non-throttling area, after the supercharger is inserted, the pressure ratio P between the back of the throttle valve and the front of the throttle valve is increased due to the pressure increase in front of the throttle valve_b/P_fAnd reducing the throttle control, switching the throttle control from the non-throttle zone control to the throttle zone, and if the control switching process is frequent, causing the throttle to shake, thereby causing the system to be unstable.

The embodiment of the invention provides a supercharging control device of an engine turbocharger. Fig. 7 is a schematic structural diagram of a boost control device of an engine turbocharger according to an embodiment of the present invention. The supercharging control device of the engine turbocharger can execute the supercharging control method of the engine turbocharger provided by any embodiment of the invention. The boost control device of the engine turbocharger comprises: a feed forward control module 410, a closed loop control module 420, and an opening control module 430.

The feedforward control module 410 is configured to obtain a feedforward value according to a target boost pressure value based on a turbocharger physical model; the closed-loop control module 420 is used for acquiring a correction value by a preset closed-loop control algorithm according to the difference value between the target supercharging pressure value and the actual pressure value of the engine before the throttle valve; the opening control module 430 is configured to control an opening of a wastegate valve of the turbocharger based on the feed forward value and the correction value.

The boost control device of the engine turbocharger provided by the embodiment of the invention can execute the boost control method of the engine turbocharger provided by any embodiment of the invention, so that the boost control device of the engine turbocharger provided by the embodiment of the invention also has the beneficial effects described in the embodiments, and the details are not repeated herein.

Alternatively, the turbocharger 100 includes: a compressor 1 and a turbine 2. Optionally, the physical model of the turbocharger comprises: a compressor physical model and a turbine physical model;

alternatively, on the basis of the foregoing embodiment, fig. 8 is a schematic structural diagram of a supercharging control apparatus of a turbocharger of an engine according to another embodiment of the present invention, and the feedforward control module 410 includes: a compressor power type obtaining unit 411, a turbine power determination unit 412, and a feed forward value obtaining unit 413.

The compressor power type obtaining unit 411 is configured to obtain a target power of the compressor according to a target supercharging pressure value based on a compressor physical model; the turbine power determining unit 412 is used for determining the target power of the turbine according to the target power of the compressor; the feedforward value obtaining unit 413 is configured to obtain a feedforward value according to a target power of the turbine based on the turbine physical model.

Optionally, on the basis of the foregoing embodiment, the compressor model calculating unit 411 is configured to determine the target power of the compressor according to the target supercharging pressure value, the upstream pressure detection value of the compressor, the air inlet temperature detection value of the compressor, and the air inlet amount detection value of the compressor, based on the compressor physical model.

Alternatively, on the basis of the above-described embodiment, with continued reference to fig. 8, the feedforward value acquisition unit 413 includes: a pressure ratio determining subunit 4131, an upstream pressure determining subunit 4132, and a feedforward value acquiring subunit 4133.

Wherein the pressure ratio determining subunit 4131 is configured to determine a target pressure ratio value of the upstream pressure and the downstream pressure of the turbine, based on the target power of the turbine; the upstream pressure determining subunit 4132 is configured to determine a target upstream pressure value of the turbine based on a target pressure ratio of the upstream pressure and the downstream pressure of the turbine, and a downstream pressure detection value of the turbine; the feedforward value acquisition subunit 4133 is configured to acquire a feedforward value from a target upstream pressure value of the turbine, a downstream pressure detection value of the turbine, a gas flow amount detection value flowing into the wastegate valve, and an upstream temperature detection value of the turbine, based on the turbine physical model.

Optionally, the opening control module 430 is configured to determine a driving signal of an electronically controlled actuator controlling the opening of the wastegate valve according to the feed forward value and the correction value.

The supercharging control device of the engine turbocharger can execute the supercharging control method of the engine turbocharger provided by any embodiment of the invention, and has corresponding functional modules and beneficial effects of the execution method.

The engine may include a gas engine or a fuel engine, among others. The gas engine, especially for equivalent combustion, has a very high requirement for controlling the air intake amount compared with a diesel engine, and the control of the dynamic property and the responsiveness is strongly related to the control of the air intake amount, so that the gas engine needs to control the air intake amount more accurately to realize more accurate air-fuel ratio control, and realize better combustion control.

Fig. 9 is a schematic structural diagram of an electronic apparatus according to an embodiment of the present invention, as shown in fig. 9, the electronic apparatus includes a processor 70, a memory 71, an input device 72, and an output device 73; the number of the processors 70 in the electronic device may be one or more, and one processor 70 is taken as an example in fig. 8; the processor 70, the memory 71, the input device 72 and the output device 73 in the electronic apparatus may be connected by a bus or other means, and the bus connection is exemplified in fig. 9.

The memory 71, as a computer-readable storage medium, may be used to store software programs, computer-executable programs, and modules, such as program instructions/modules corresponding to the boost control method of an engine turbocharger in embodiments of the present invention (e.g., the feed-forward control module 410, the closed-loop control module 420, and the opening control module 430). The processor 70 executes various functional applications of the device/terminal/server and data processing by running software programs, instructions and modules stored in the memory 71, so as to realize the supercharging control method of the engine turbocharger.

The memory 71 may mainly include a storage program area and a storage data area, wherein the storage program area may store an operating system, an application program required for at least one function; the storage data area may store data created according to the use of the terminal, and the like. Further, the memory 71 may include high speed random access memory, and may also include non-volatile memory, such as at least one magnetic disk storage device, flash memory device, or other non-volatile solid state storage device. In some examples, the memory 71 may further include memory located remotely from the processor 70, which may be connected to the device/terminal/server via a network. Examples of such networks include, but are not limited to, the internet, intranets, local area networks, mobile communication networks, and combinations thereof.

The input device 72 may be used to receive input numeric or character information and generate key signal inputs related to user settings and function controls of the electronic apparatus. The output device 73 may include a display device such as a display screen.

Embodiments of the present invention provide a storage medium containing computer-executable instructions which, when executed by a computer processor, perform a method of boost control for an engine turbocharger, the method comprising:

acquiring a feedforward value according to a target supercharging pressure value based on a physical model of the turbocharger;

obtaining a correction value by a preset closed-loop control algorithm according to the difference value between the target supercharging pressure value and the actual pressure value of the engine before a throttle valve;

and controlling the opening degree of a waste gate valve of the turbocharger according to the feedforward value and the correction value.

Of course, the embodiment of the present invention provides a storage medium containing computer-executable instructions, and the computer-executable instructions are not limited to the operations of the method described above, and can also execute the relevant operations in the supercharging control method of the engine turbocharger provided in any embodiment of the present invention.

From the above description of the embodiments, it is obvious for those skilled in the art that the present invention can be implemented by software and necessary general hardware, and certainly, can also be implemented by hardware, but the former is a better embodiment in many cases. Based on such understanding, the technical solutions of the present invention may be embodied in the form of a software product, which can be stored in a computer-readable storage medium, such as a floppy disk, a Read-Only Memory (ROM), a Random Access Memory (RAM), a FLASH Memory (FLASH), a hard disk or an optical disk of a computer, and includes several instructions for enabling a computer device (which may be a personal computer, a server, or a network device) to execute the methods according to the embodiments of the present invention.

It should be noted that, in the embodiment of the above search apparatus, each included unit and module are merely divided according to functional logic, but are not limited to the above division as long as the corresponding functions can be implemented; in addition, specific names of the functional units are only for convenience of distinguishing from each other, and are not used for limiting the protection scope of the present invention.

It is to be noted that the foregoing is only illustrative of the preferred embodiments of the present invention and the technical principles employed. It will be understood by those skilled in the art that the present invention is not limited to the particular embodiments described herein, but is capable of various obvious modifications, rearrangements, combinations and substitutions as will now become apparent to those skilled in the art without departing from the scope of the invention. Therefore, although the present invention has been described in greater detail by the above embodiments, the present invention is not limited to the above embodiments, and may include other equivalent embodiments without departing from the spirit of the present invention, and the scope of the present invention is determined by the scope of the appended claims.