阅读说明：本技术 防止废气再循环冷却器的沸腾的控制设备和方法 (Control device and method for preventing boiling of exhaust gas recirculation cooler ) 是由 金汉相 于 2020-06-23 设计创作，主要内容包括：本公开涉及一种用于防止废气再循环冷却器的沸腾的控制设备和方法,该设备包括：冷却剂流入通道,被配置为允许冷却剂流入EGR冷却器；冷却剂排出通道,其一端连接至该EGR冷却器,以允许冷却剂冷却的EGR气体被排出；EGR阀,与EGR冷却器相邻而定位,以控制流入发动机的气体的流速；以及控制单元,被配置为根据发动机转数确定流入EGR冷却器的冷却剂的流速,确定EGR阀的开量,确定EGR冷却器是否处于微沸条件,并在EGR冷却器满足微沸条件时进行补偿以防止沸腾。(The present disclosure relates to a control apparatus and method for preventing boiling of an exhaust gas recirculation cooler, the apparatus comprising: a coolant inflow passage configured to allow coolant to flow into the EGR cooler; a coolant discharge passage, one end of which is connected to the EGR cooler to allow coolant-cooled EGR gas to be discharged; an EGR valve positioned adjacent the EGR cooler to control a flow rate of gas flowing into the engine; and a control unit configured to determine a flow rate of coolant flowing into the EGR cooler according to the number of engine revolutions, determine an opening amount of the EGR valve, determine whether the EGR cooler is in a micro-boiling condition, and compensate to prevent boiling when the EGR cooler satisfies the micro-boiling condition.)

1. A control device for preventing boiling of an exhaust gas recirculation cooler, the device comprising:

a coolant inflow passage configured to allow coolant to flow into the egr cooler;

a coolant discharge passage having one end connected to the egr cooler to allow a coolant that cools the egr gas to be discharged;

an exhaust gas recirculation valve positioned adjacent to the exhaust gas recirculation cooler to control a flow rate of gas flowing into the engine; and

a control unit configured to: the method includes determining a flow rate of coolant flowing into the EGR cooler according to a number of revolutions of an engine, determining an opening amount of the EGR valve, determining whether the EGR cooler is in a micro-boiling condition, and performing compensation to prevent boiling when the EGR cooler satisfies the micro-boiling condition.

2. The apparatus of claim 1, further comprising:

a coolant flow rate controller configured to control a flow rate of coolant flowing into the EGR cooler and located at the coolant inflow passage.

3. The apparatus according to claim 2, wherein the control unit is configured to control the coolant flow rate controller such that the flow rate of the coolant flowing into the egr cooler is increased under a micro-boiling condition of the egr cooler.

4. The apparatus of claim 3, wherein, when the flow rate of coolant flowing into the EGR cooler is not increased by the coolant flow rate controller, the control unit is configured to control the EGR valve such that the flow rate of EGR gas is decreased.

5. The apparatus of claim 1, wherein the control unit is configured to control the exhaust gas recirculation valve such that a flow rate of exhaust gas recirculation gas is reduced under a microboiling condition of the exhaust gas recirculation cooler.

6. A control method for preventing boiling of an exhaust gas recirculation cooler, the method comprising the steps of:

determining whether the coolant temperature measured by the control unit is greater than or equal to a predetermined value;

determining, by the control unit, a flow rate of exhaust recirculation gas according to a number of revolutions and a load of the engine when the coolant temperature is greater than or equal to the predetermined value;

determining, by the control unit, a flow rate of coolant flowing into an exhaust gas recirculation cooler in response to a number of revolutions of the engine;

determining whether coolant flowing into the EGR cooler is in a microboiling condition; and

when the control unit determines that the coolant is in the micro-boiling condition, compensation is performed by the control unit to prevent boiling.

7. The method of claim 6, wherein determining, by the control unit, the flow rate of coolant flowing into the EGR cooler in response to a number of revolutions of the engine comprises:

the flow rate of the coolant flowing into the exhaust gas recirculation cooler is determined by the coolant flow rate controller and the number of revolutions of the engine.

8. The method of claim 6, wherein performing, by the control unit, compensation to prevent boiling when it is determined that the coolant is in the micro-boiling condition comprises:

control is performed by the control unit to increase the flow rate of the coolant flowing into the egr cooler.

9. The method of claim 8, wherein controlling, by the control unit, to increase the flow rate of coolant flowing into the EGR cooler comprises:

determining whether a flow rate of coolant flowing into the egr cooler is increased; and

when the flow rate of the coolant flowing into the EGR cooler is not increased, the flow rate of EGR gas is decreased.

10. The method of claim 9, wherein reducing the flow rate of the exhaust recirculation gas comprises:

controlling an opening of an EGR valve to reduce a flow rate of EGR gas flowing into the EGR cooler.

11. The method of claim 6, wherein performing compensation by the control unit to prevent boiling when it is determined that the coolant is in the micro-boiling condition comprises:

control is performed by the control unit to reduce the flow rate of the exhaust recirculation gas.

12. The method according to claim 6, wherein the micro-boiling condition is determined for a region in which the flow rate of the coolant flowing into the egr cooler increases linearly with an increase in the flow rate of the gas.

Technical Field

The present disclosure relates to a control apparatus and method for preventing boiling of an EGR cooler, and more preferably, to a control apparatus and method for preventing boiling of an EGR cooler, which controls a flow rate of gas flowing into an EGR or a flow rate of coolant entering the EGR cooler corresponding to a micro-boiling condition of the coolant located inside the EGR cooler, thereby preventing boiling of the coolant located inside the EGR cooler.

Background

Generally, Exhaust Gas Recirculation (EGR) functions to reduce the temperature of a combustion chamber by sucking a part of exhaust gas of a vehicle, thereby reducing the discharge of harmful substances such as nitrogen oxides and sulfur oxides.

Further, with the strictness of global air pollution regulations, EGR coolers are now used together to lower the temperature of EGR gas.

The exhaust gas flowing into the EGR cooler cools the EGR gas by the coolant discharged through the engine.

Further, when the temperature of the coolant is equal to or higher than a predetermined temperature and the temperature of the coolant flowing into the EGR cooler is equal to or higher than a boiling condition, the coolant is controlled to prevent driving of the EGR.

Further, since the coolant inside the EGR cooler is lost due to boiling, there is a problem that the engine is overheated due to lack of the coolant. In addition, since the coolant is lost due to boiling, the coolant should be replenished frequently, so that there is a problem in that the cost of replenishing the coolant increases.

In addition, in the conventional technology, the flow rate of the coolant flowing into the EGR cooler and the flow rate of the coolant circulating through the engine, the heater, the EGR cooler, and the radiator cannot be controlled, and there is a problem that the cooling efficiency of the EGR cooler is lowered, and the efficiency of the engine is finally lowered.

Disclosure of Invention

The present disclosure has been made in view of the above-mentioned problems occurring in the related art, and an object of the present disclosure is to provide a control apparatus and method for preventing boiling of an EGR cooler, which alleviate a boiling condition of coolant located inside the EGR cooler, thereby expanding an EGR operation condition.

An object of the present disclosure is to provide a control apparatus and method for preventing boiling of an EGR cooler, in which an opening amount of an EGR valve or a flow rate of coolant flowing into an EM cooler is controlled corresponding to a micro-condition (micro-condition) of a cooler located inside the EGR cooler.

The object of the present disclosure is not limited to the above object, and other objects of the present disclosure, which are not mentioned, may be understood by the following description and may be more clearly understood by the embodiments of the present disclosure. Further, the objects of the present disclosure can be achieved by the devices shown in the claims and combinations thereof.

To achieve the above object, a control apparatus and method for preventing boiling of an EGR cooler includes the following configurations.

According to an embodiment, a control apparatus for preventing boiling of an Exhaust Gas Recirculation (EGR) cooler comprises: a coolant inflow passage configured to allow coolant to flow into the EGR cooler; a coolant discharge passage having one end connected to the EGR cooler to allow coolant that cools EGR gas to be discharged; an EGR valve positioned adjacent to the EGR cooler to control a flow rate of gas flowing into the engine; and a control unit configured to: the method includes determining a flow rate of coolant flowing into the EGR cooler according to a number of revolutions of an engine, determining an opening amount of the EGR valve, determining whether the EGR cooler is in a micro-boiling condition, and performing compensation to prevent boiling when the EGR cooler satisfies the micro-boiling condition.

In addition, the control apparatus for preventing boiling of the EGR cooler may further include: a coolant flow rate controller configured to control a flow rate of coolant flowing into the EGR cooler and located at the coolant inflow passage.

In addition, the control unit may be configured to control the coolant flow rate controller so as to increase the flow rate of the coolant flowing into the EGR cooler under the micro-boiling condition of the EGR cooler.

In addition, when the flow rate of the coolant flowing into the EGR cooler is not increased by the coolant flow rate controller, the control unit may be configured to control the EGR valve such that the flow rate of the EGR gas is decreased.

In addition, the control unit may be configured to control the EGR valve under a micro-boiling condition (micro-boiling condition) of the EGR cooler such that the flow rate of EGR gas is reduced.

Further, according to another embodiment of the present disclosure, a control method for preventing boiling of an Exhaust Gas Recirculation (EGR) cooler includes: determining whether the coolant temperature measured by the control unit is greater than or equal to a predetermined value; determining, by the control unit, a flow rate of the EGR gas according to a number of revolutions and a load of the engine when the coolant temperature is greater than or equal to the predetermined value; determining, by the control unit, a flow rate of coolant flowing into an EGR cooler in response to the number of revolutions of the engine; determining whether coolant flowing into the EGR cooler is in a micro-boiling condition; and performing compensation by the control unit to prevent boiling when the control unit determines that the coolant is in the micro-boiling condition.

In addition, determining, by the control unit, a flow rate of coolant flowing into the EGR cooler in response to the number of revolutions of the engine may include: the flow rate of the coolant flowing into the EGR cooler is determined by the coolant flow rate controller and the number of revolutions of the engine.

In addition, when it is determined that the coolant is in the micro-boiling condition, the performing, by the control unit, compensation to prevent boiling may include: control is performed by the control unit to increase the flow rate of the coolant flowing into the EGR cooler.

In addition, the controlling by the control unit to increase the flow rate of the coolant flowing into the EGR cooler may include: determining whether a flow rate of coolant flowing into the EGR cooler is increased; and reducing the flow rate of the EGR gas when the flow rate of the coolant flowing into the EGR cooler is not increased.

In addition, reducing the flow rate of the EGR gas may include: the opening amount of the EGR valve is controlled to reduce the flow rate of EGR gas flowing into the EGR cooler.

In addition, when it is determined that the coolant is in the micro-boiling condition, performing compensation by the control unit to prevent boiling may include: control is performed to reduce the flow rate of the EGR gas by the control unit.

In addition, the micro-boiling condition may be determined for a region in which the flow rate of the coolant flowing into the EGR cooler linearly increases as the flow rate of the gas increases.

According to the above-described embodiments, the following effects can be obtained by the present disclosure in the configurations and combinations and use relationships described below.

The present disclosure has the effect of further enlarging the driving condition of the EGR by the condition of compensating the flow rate of the gas and the flow rate of the flowing coolant in response to the temperature condition of the coolant inside the EGR cooler.

Further, the present invention provides an effect of improving engine driving efficiency by enlarging EGR driving conditions.

Drawings

The above and other objects, features and other advantages of the present disclosure will be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings, in which:

fig. 1 is a block diagram showing a coupling relationship between components of a control apparatus for preventing boiling of an EGR cooler according to an embodiment of the present disclosure;

fig. 2 is a block diagram showing a coupling relationship between components of a control apparatus for preventing boiling of an EGR cooler according to another embodiment of the present disclosure;

FIG. 3 is a flowchart illustrating a control method for preventing boiling of an EGR cooler that does not include a coolant flow rate controller, according to an embodiment of the present disclosure;

FIG. 4 is a graph illustrating compensation performed over a boiling interval by controlling gas flow rate according to an embodiment of the present disclosure;

FIG. 5 is a flow chart illustrating a control method for preventing boiling of an EGR cooler including a coolant flow rate controller according to another embodiment of the present disclosure; and

fig. 6 is a graph illustrating compensation performed within a boiling interval by controlling the gas flow rate and the flow rate of coolant flowing into the EGR cooler according to another embodiment of the present disclosure.

Detailed Description

Hereinafter, embodiments of the present disclosure will be described in detail with reference to the accompanying drawings. The embodiments of the present disclosure may be modified in various forms, and the scope of the present disclosure should not be construed as being limited to the following embodiments. This embodiment is provided to more fully explain the present disclosure to those skilled in the art.

Also, the terms "means", "unit", "module", and the like described in the specification mean a unit for processing at least one function or operation, which may be implemented as hardware, software, or a combination of hardware and software.

Further, "slight boiling" described in the specification refers to a condition under which the coolant in the EGR cooler 110 starts to boil, depending on the coolant temperature, the gas flow rate, the flow rate of the coolant in the EGR cooler 110, wherein the slight boiling region and the boiling region can be basically understood as the same meaning.

The present disclosure relates to a control apparatus and method for preventing boiling of coolant flowing into an EGR cooler 110, and provides a technique for enlarging an operating condition of the EGR cooler 110 and improving driving efficiency of an engine 200.

Fig. 1 is a view showing a control apparatus for preventing boiling in an EGR cooler 110 included in an EGR system 100 according to an embodiment of the present disclosure.

The EGR system 100 is configured to control the opening amount of the EGR valve to flow in the exhaust gas of the engine 200. The EGR system 100 includes an EGR cooler 110 for cooling high temperature exhaust gas. Further, an EGR valve for controlling the flow rate of gas flowing into the EGR system 100 is provided at one end of the EGR cooler 110 or adjacent to the EGR cooler 110, and is controlled by the control unit 400 of the vehicle.

The coolant is supplied to flow into the EGR cooler 110 along an inflow passage 111 that branches from an inlet of a cooler line into the engine 200.

Alternatively, the coolant discharged after cooling the engine 200 may be introduced into the EGR cooler 110 through the inflow passage 111.

According to an embodiment of the present disclosure, referring to fig. 1, the control apparatus for preventing boiling of the EGR cooler is configured such that the EGR cooler 110 is always kept in an open state to allow the coolant to flow in the EGR cooler 110 in proportion to the number of revolutions of the engine 200.

The control apparatus is configured such that the coolant introduced into the EGR cooler 110 cools the gas passing through the EGR system 100, circulating through the exhaust passage 112. Then, the control apparatus is configured such that the discharged coolant is cooled by the radiator and then introduced into the engine 200, thereby being introduced into the EGR cooler 110 again.

The control unit 400 includes a Water Temperature Sensor (WTS) that measures the temperature of the coolant. The control unit 400 is provided to determine the boiling condition of the coolant inside the EGR cooler 110, taking into account the temperature of the coolant flowing into the EGR cooler 110.

More preferably, the at least one or more sensors may be located at a forward end of the EGR cooler 110 or at an end adjacent to an inlet of the engine 200.

Further, the control unit 400 determines the flow rate of the coolant flowing into the EGR cooler 110 according to the number of revolutions of the engine 200, wherein the flow rate of the coolant may be set based on a map value stored through an Engine Management System (EMS).

According to the embodiment of the present disclosure, the control unit 400 determines whether the temperature of the coolant is greater than or equal to a predetermined temperature, and determines the flow rate of the gas flowing into the EGR system 100 and the flow rate of the coolant flowing into the EGR cooler 110 when it is determined that the temperature of the coolant is greater than or equal to the predetermined temperature.

More preferably, the control unit 400 is provided such that the flow rate of gas is set according to the number of revolutions and the load of the engine 200 based on the map value stored in the control unit 400, and the flow rate of coolant flowing into the EGR cooler 110 is also determined.

The boiling condition of the coolant inside the EGR cooler 110 is determined based on the gas flow rate and the flow rate of the coolant determined as described above.

When the micro-boiling condition of the coolant located inside the EGR cooler 110 is satisfied, the control unit 400 may reduce the flow rate of the gas flowing inside the EGR system 100 by controlling the opening amount of the EGR valve.

The EGR system 100 having the reduced gas flow rate is driven under the non-boiling condition, and therefore, the driving environmental condition of the EGR system 100 is set to be alleviated.

Referring to fig. 1, according to an embodiment of the present disclosure, anti-boiling compensation is performed for an engine 200 and an EGR cooler 110 configured to allow coolant to always pass therethrough. More preferably, the EGR valve is provided to be controlled according to the micro-boiling condition based on the gas flow rate in the EGR cooler 110 and the flow rate of the coolant.

Fig. 2 is a block diagram showing a control apparatus for preventing boiling of the EGR cooler 110 using a coolant flow rate controller 300, the coolant flow rate controller 300 controlling the flow rate of coolant flowing into the EGR cooler 110, as compared with fig. 1.

In fig. 2, the coupling relationship in the control apparatus including the coolant flow rate controller 300 that controls the flow rate of the coolant flowing into the EGR cooler 110 is shown.

As shown, coolant located in the reservoir is pressurized by a water pump, and the pressurized coolant may be controlled by a coolant flow rate controller 300 to dispense the coolant.

More preferably, the flow rate of coolant flowing into the EGR cooler 110 located adjacent to the engine 200 may be controlled by the coolant flow rate controller 300.

The control unit 400 is configured to control the opening amount of the EGR valve in response to the coolant temperature and the micro-boiling condition of the coolant inside the EGR cooler 110. Further, the flow rate of coolant flowing into the EGR cooler 110 is controlled so that the EGR system 100 can be controlled under non-boiling conditions.

That is, the control unit 400 determines whether the coolant temperature is greater than or equal to a predetermined temperature, sets the flow rate of gas according to the number of revolutions and load of the engine 200, and determines the flow rate of coolant flowing into the EGR cooler 110. Furthermore, the control unit determines a micro-boiling condition inside the EGR cooler 110.

More preferably, the flow rate of gas flowing into the EGR cooler 110 and the flow rate of coolant may be selected through a map value stored in the control unit 400 according to the number of revolutions and load of the engine.

When the micro-boiling condition is satisfied in the EGR cooler 110, the control unit 400 controls to increase the flow rate of the coolant flowing into the EGR cooler 110 through the coolant flow rate controller 300. When it is determined that the flow rate of the coolant flowing into the EGR cooler 110 is not increased, the flow rate of the gas flowing into the EGR system 100 is further controlled to be decreased by controlling the opening amount of the EGR valve.

When the coolant is inclined to one side according to the climbing condition of the vehicle, the compensation control operation of increasing the flow rate of the coolant may not be performed. Therefore, in the above-described running state, the coolant flowing into the EGR cooler 110 cannot be increased. Therefore, the control unit 400 performs control to increase the flow rate of the coolant flowing into the EGR cooler 110, and then determines whether the flow rate of the coolant inside the EGR cooler 110 is increased.

When the control unit 400 does not perform the control of increasing the flow rate of the coolant flowing into the EGR cooler 110, the control unit 400 performs the control to further reduce the flow rate of the gas flowing into the EGR system 100, so that the coolant inside the EGR cooler 110 may not boil.

According to another embodiment of the present disclosure, when the micro-boiling condition of the EGR cooler 110 is satisfied, the coolant flow rate controller 300 is provided such that the flow rate of the coolant flowing into the EGR cooler 110 is increased in advance and the gas flowing in the EGR system 100 is reduced without increasing the flow rate of the coolant.

As described above, fig. 1 shows a constant passage structure in which coolant always passes through the EGR cooler 110 according to an embodiment of the present disclosure. Fig. 2 illustrates a structure in which the flow rate of coolant flowing into the EGR cooler 110 is controlled by a coolant flow rate controller 300 according to another embodiment of the present disclosure. Therefore, it will be appreciated that compensation is performed differently depending on the micro-boiling conditions.

Fig. 3 and 4 show a control method for preventing boiling of the EGR cooler 110 according to a constant passage structure and a driving point diagram of the EGR system 100 compensated under a non-boiling condition. Meanwhile, fig. 5 and 6 show a control method for preventing the boiling of the EGR cooler 110 in a system including the coolant flow rate controller 300 and a driving point diagram of the EGR cooler 110 compensated under the anti-boiling condition.

Fig. 3 is a flowchart showing a control method for preventing boiling of the EGR cooler 110 in the EGR system 100, in which the coolant always passes through the EGR cooler 110.

As shown, the control unit 400 includes the following steps: the temperature of coolant flowing into a cooling system of a vehicle is measured by a temperature sensor located in the cooling system of the vehicle, and it is determined whether the temperature is greater than or equal to a predetermined temperature (S110).

When the coolant temperature is below the predetermined temperature, the logic terminates. When the coolant temperature exceeds a predetermined temperature, the flow rate of gas flowing into the EGR system 100 is determined according to the number of revolutions of the engine 200 and the load of the engine 200 (S120).

The gas flowing into the EGR system 100 may be selected using a map value stored in an Engine Management System (EMS).

Further, the flow rate of the coolant flowing through the inflow passage 111 of the EGR cooler 110 is set, wherein the flow rate of the coolant may be determined by a map value stored in an Engine Management System (EMS) of the control unit 400 (S130).

Thereafter, it is determined whether the coolant inside the EGR cooler 110 satisfies the condition of the micro-boiling region (S140).

When the coolant flowing inside the EGR cooler 110 corresponds to the boiling region, the control unit 400 controls the opening amount of the EGR valve so that the flow rate of the gas flowing inside the EGR system 100 is reduced by 2Kg/h (S150), and then the process returns to the initial step (S160).

However, when the coolant in the EGR cooler 110 is not in the micro-boiling region (S140), the flow rate of the coolant of the EGR cooler 110 and the opening amount of the EGR valve are maintained at the original settings (S170), and then the process returns to the initial step (S150).

Referring to fig. 4, when the compensation control that reduces the opening amount of the EGR valve of fig. 3 is executed, the EGR cooler 110 is compensated by changing the EGR driving point from the slight-boiling region to the non-boiling region.

As shown, the flow rate of gas flowing into the EGR system 100 is shown on the X-axis and the flow rate of EGR coolant is shown on the Y-axis, where boiling regions and non-boiling regions are graphically shown by the relationship between the two factors.

Further, having a slight boiling point at different positions according to the temperature of the coolant, it can be seen that the higher the temperature of the coolant is measured, the lower the flow rate of the coolant is in the slight boiling region under the same gas flow rate.

The control unit 400 of the present disclosure is configured to perform anti-boiling control in a region where the flow rate of the coolant is linearly increased in response to an increase value of the gas flow rate.

That is, the control unit is configured to perform compensation control to prevent boiling in a region where the flow rate of the coolant linearly increases with an increase in the gas flow rate.

When the compensation is performed to reduce the gas flowing in the EGR system 100, the compensation is performed such that the driving point of the EGR cooler 110 is changed from the slight-boiling region to the non-boiling region.

More preferably, as an embodiment of the present disclosure, the control apparatus for preventing boiling of the EGR cooler 110 having a constant passage structure for coolant circulation has a micro-boiling condition in which the measured coolant temperature is 110 ℃, the gas flow rate is 16kg/h, and the flow rate of the coolant is 8 LPM.

Under the same conditions, when the gas flow rate flowing into the EGR system 100 is reduced by 2kg/h according to the anti-boiling compensation, the driving point (driving point) of the EGR cooler 110 may be moved from the boiling region to the non-boiling region (the gas flow rate at the driving point is 14kg/h, and the flow rate of the coolant is 8 LPM). That is, the control unit 400 is provided to perform the anti-boiling compensation by reducing the flow rate of the gas flowing into the EGR system 100.

Fig. 5 is a flowchart showing a control method of compensating for boiling by the control apparatus for preventing boiling of the EGR cooler 110 including the coolant flow rate controller 300.

As shown, the control unit 400 includes the following steps: the temperature of coolant flowing into a cooling system of a vehicle is measured by a temperature sensor located in the cooling system, and it is determined whether the temperature is greater than or equal to a predetermined temperature (S210).

When the coolant temperature exceeds a predetermined temperature, the flow rate of gas flowing into the EGR system 100 is determined according to the number of revolutions of the engine 200 and the load of the engine 200 (S220).

Preferably, the flow rate of gas flowing into the EGR system 100 may be determined according to a map value stored in the control unit 400. In another embodiment of the present disclosure, the flow rate of gas flowing into the EGR system 100 may be determined by an Engine Management System (EMS) using stored map values.

Further, the flow rate of the coolant flowing through the coolant inflow passage 111 of the EGR cooler 110 may be determined, and more particularly, the flow rate of the coolant may be determined by a map value stored in the control unit 400 (S230).

More preferably, the flow rate of coolant flowing into the EGR cooler 110 may be set using a mapped value of an Engine Management System (EMS), and more particularly, the flow rate of coolant may be set by the number of revolutions of the engine 200 of the vehicle and the opening amount of the coolant flow rate controller 300.

Thereafter, it is determined whether the coolant inside the EGR cooler 110 is in the micro-boiling region (S240).

When the coolant flowing in the EGR cooler 110 is in the boiling region, the flow rate of the coolant flowing into the EGR cooler 110 is increased by increasing the opening amount of the coolant flow rate controller 300 (S250), and it is determined whether the flow rate of the coolant is increased (S260).

More preferably, when compensation is performed to increase the flow rate of the coolant flowing into the EGR cooler 110, the flow rate of the coolant may be controlled to be increased by 2LPM (250) compared to the flow rate of the coolant driven before the compensation.

When it is determined that the flow rate of the coolant flowing into the EGR cooler 110 is increased by a predetermined increase amount by the compensation of increasing the opening amount of the coolant flow rate controller 300, the process returns to the initial step (S270). However, when it is determined that the flow rate of the coolant is not increased by the predetermined increase amount, control is performed to decrease the flow rate of the gas flowing into the EGR system 100 (S280).

More preferably, in the step of performing compensation for reducing the flow rate of gas, the opening amount of the EGR valve is controlled to reduce the flow rate of gas flowing in the EGR system 100 by 2Kg/h (S280), and then the process returns to the initial step (S270).

However, when the coolant in the EGR cooler 110 is not in the micro-boiling region (S240), the flow rate of the coolant of the EGR cooler 110 and the opening amount of the EGR valve are maintained as originally set (290), and then the process returns to the initial step (S270).

Fig. 6 is a graph showing the results of executing the control method for preventing boiling of the EGR cooler 110 including the coolant flow rate controller.

In the graph of fig. 6, the same factors as those of fig. 4 are included. That is, the flow rate of gas flowing into the EGR system 100 is shown on the X-axis, and the flow rate of EGR coolant is shown on the Y-axis, where the relationship between the two factors is illustrated.

The control unit 400 of the present disclosure is configured to perform the anti-boiling control in a region where the flow rate of the coolant linearly increases in response to an increase value of the gas flow rate. Further, the anti-boiling compensation is performed in advance by the coolant flow rate controller 300, and thus it is possible to control to increase the flow rate of the coolant flowing into the EGR cooler 110.

When the flow rate of the coolant flowing into the EGR cooler 110 increases, compensation is made such that the driving point of the EGR cooler 110, which is located in a micro-boiling line, is moved to a non-boiling region.

Further, when the coolant is concentrated to one end of the vehicle due to the running condition of the vehicle, since it is difficult to increase the flow rate of the coolant flowing into the EGR cooler 110, the control unit 400 performs the coolant flow rate increase control and then determines whether the flow rate of the coolant actually flowing inside the EGR cooler 110 is increased by a predetermined increase amount.

However, when control for increasing the flow rate of the coolant inside the EGR cooler 110 by the control unit 400 is not performed according to the above-described conditions, the flow rate of the gas flowing inside the EGR system 100 is decreased by decreasing the opening amount of the EGR valve.

More preferably, as another embodiment of the present disclosure, there is provided a coolant circulation structure including the coolant flow rate controller 300, and the control device for preventing the boiling of the EGR cooler 110 has a micro-boiling condition in which a gas flow rate is 16kg/h, a coolant temperature is 110 ℃, and a coolant flow rate is 8 LPM.

When the flow rate of the coolant flowing into the EGR cooler 110 is controlled according to the anti-boiling compensation under the same conditions as previously described, the flow rate of the coolant is controlled to be changed from the initial 8LPM to 10 LPM.

Then, the control unit 400 determines whether the flow rate of the coolant is increased to 10LPM, and when the flow rate of the coolant is not compensated to 10LPM, the control unit 400 performs control to reduce the gas flowing into the EGR system 100 by 2 Kg/h.

In the case where the above-described control is performed, the drive point of the EGR cooler 110 may be shifted from the boiling region to the non-boiling region on the graph shown. Further, when the coolant flow control is performed, the drive point of the EGR cooler 110 is controlled to move upward with respect to the Y axis, and when the coolant flow control is not performed, the gas flow control flowing into the EGR system 100 is performed to control the drive point to move left with respect to the X axis.

Therefore, according to the above control, the drive point of the EGR cooler 110 is all shifted to the non-boiling region.

That is, the control unit 400 controls the flow rate of the coolant flowing into the EGR cooler 110 in advance through another embodiment of the present disclosure, and then additionally performs the reduction compensation of the gas flowing into the EGR system 100 under the condition that the coolant control is not performed, thereby performing the anti-boiling compensation of the EGR cooler 110.

As described above, the present disclosure provides a control apparatus and method for preventing boiling of the EGR cooler 110, which can drive the EGR system 100 in a slight-boiling region of the coolant.

The foregoing detailed description illustrates the present disclosure. Furthermore, the foregoing is intended to illustrate and explain preferred embodiments of the disclosure, and the disclosure may be used in various other combinations, modifications, and environments. That is, variations or modifications may be made within the scope of the concept of the present disclosure disclosed in the present specification, within the scope equivalent to the present disclosure and/or within the knowledge of the art or knowledge of the present disclosure. The described embodiments are intended to illustrate the best mode for carrying out the technical idea of the present disclosure, and various changes may be made in specific applications and uses of the present disclosure. Therefore, the detailed description of the present disclosure is not intended to limit the present disclosure to the disclosed embodiments. It is also to be understood that the appended claims are intended to cover other embodiments.