WO2014125570A1 - 内燃機関の制御装置 - Google Patents
内燃機関の制御装置 Download PDFInfo
- Publication number
- WO2014125570A1 WO2014125570A1 PCT/JP2013/053275 JP2013053275W WO2014125570A1 WO 2014125570 A1 WO2014125570 A1 WO 2014125570A1 JP 2013053275 W JP2013053275 W JP 2013053275W WO 2014125570 A1 WO2014125570 A1 WO 2014125570A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- temperature
- control device
- control
- heat exchanger
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
- F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/20—Cooling circuits not specific to a single part of engine or machine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/23—Layout, e.g. schematics
- F02M26/28—Layout, e.g. schematics with liquid-cooled heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/33—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage controlling the temperature of the recirculated gases
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/41—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories characterised by the arrangement of the recirculation passage in relation to the engine, e.g. to cylinder heads, liners, spark plugs or manifolds; characterised by the arrangement of the recirculation passage in relation to specially adapted combustion chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/16—Outlet manifold
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
Definitions
- the present invention relates to a control device for an internal combustion engine.
- EGR exhaust Gas Recirculation
- an EGR cooler is known as a device for cooling the exhaust gas recirculated to the cylinder.
- the EGR cooler is disposed in an EGR passage that recirculates a part of the exhaust discharged from the cylinder to the intake passage, and cools the exhaust that passes through the EGR passage (hereinafter sometimes referred to as EGR gas) with a refrigerant. Yes.
- EGR gas exhaust that passes through the EGR passage
- Patent Document 1 discloses a heat exchanger having a heat exchanger having a plurality of gas passages (referred to as a honeycomb structure in Patent Document 1).
- a honeycomb structure in Patent Document 1
- the heat exchanger according to Patent Document 1 When the heat exchanger according to Patent Document 1 is arranged in the EGR passage so that the EGR gas passes through the heat exchanger according to Patent Document 1, the heat exchanger according to Patent Document 1 exhibits a function as an EGR cooler. Can do.
- Patent Document 1 discloses using a material containing SiC as the material of the heat exchange element.
- SiC has higher thermal conductivity and better corrosion resistance to exhaust than metals such as stainless steel.
- a heat exchanger having a heat exchanger made of a material containing SiC according to Patent Document 1 is used as an EGR cooler, it is considered that the cooling performance and corrosion resistance of the EGR cooler can be improved.
- a refrigerant that passes through the engine body of the internal combustion engine may be used as a refrigerant for the EGR cooler.
- refrigerant stop control when the supply of refrigerant to the engine body is stopped in order to promote warm-up of the internal combustion engine, the flow of refrigerant into the EGR cooler is also stopped (hereinafter referred to as refrigerant stop control). Called).
- refrigerant stop control When the refrigerant stop control is executed and the heat exchanger is heated by the EGR gas and the temperature is increased, the temperature of the heat exchanger may be a predetermined value or more.
- the refrigerant stop control is finished in such a state, if a predetermined flow rate of refrigerant flows into the EGR cooler, there is a possibility that the temperature of the heat exchanger is rapidly lowered.
- FIG. 9 is a schematic diagram showing a temperature change of SiC strength.
- shaft of FIG. 9 has shown the intensity
- the horizontal axis indicates a value (temperature difference) obtained by subtracting the temperature of SiC from the reference temperature, and the lower the value, the higher the degree of decrease in the temperature of SiC.
- SiC has a property that when the temperature is suddenly lowered, the strength is also suddenly lowered.
- An object of the present invention is to provide a control device for an internal combustion engine that can suppress deterioration of a heat exchanger made of a material containing SiC.
- a control device for an internal combustion engine is a control applied to an internal combustion engine provided with an EGR cooler having a heat exchanger made of a material containing SiC, arranged in an EGR passage for introducing EGR gas into an intake passage of the internal combustion engine.
- a refrigerant stop control unit that executes a refrigerant stop control for stopping refrigerant from flowing into the EGR cooler, and the refrigerant stop control by the refrigerant stop control unit is terminated when the temperature of the refrigerant is equal to or higher than a predetermined value.
- the control apparatus for an internal combustion engine according to the present invention can weaken the degree of cooling of the heat exchanger by the refrigerant when the refrigerant stop control is finished. Thereby, the temperature decrease rate of the heat exchanger when the refrigerant stop control is completed can be reduced. As a result, since the rapid decrease in the temperature of the heat exchanger when the refrigerant stop control is completed can be suppressed, the deterioration of the heat exchanger can be suppressed.
- the internal combustion engine includes a pump that supplies a refrigerant to an engine main body of the internal combustion engine and the EGR cooler, and the control unit has a temperature of the refrigerant equal to or higher than the predetermined value and the refrigerant stop control unit
- the output of the pump when the refrigerant stop control is finished is reduced compared to the output of the pump when the refrigerant temperature is less than the predetermined value and the refrigerant stop control by the refrigerant stop control unit is finished. Also good.
- the refrigerant temperature is less than the predetermined value and the refrigerant stop control by the refrigerant stop control unit is finished.
- the flow rate of the refrigerant passing through the EGR cooler can be controlled to a small flow rate. Thereby, deterioration of a heat exchanger can be suppressed.
- control unit may gradually change the output of the pump to a target output in reducing the output of the pump. According to this configuration, a sudden change in the temperature of the heat exchanger can be effectively suppressed. Thereby, deterioration of a heat exchanger can be suppressed effectively.
- the present invention can provide a control device for an internal combustion engine that can suppress deterioration of a heat exchanger made of a material containing SiC.
- FIG. 1 is a schematic diagram of an internal combustion engine to which a control device according to a first embodiment is applied.
- FIG. 2A is a schematic cross-sectional view of an EGR cooler.
- FIG. 2B is a front view of the heat exchanger.
- FIG. 3 is a diagram illustrating an example of a flowchart when the control device according to the first embodiment executes temperature control.
- FIG. 4 is a diagram illustrating an example of a flowchart when the control device according to the first modification of the first embodiment executes temperature control.
- FIG. 5 is a schematic diagram for explaining the configuration of the internal combustion engine according to the second embodiment.
- FIG. 6 is a diagram illustrating an example of a flowchart when the control device according to the second embodiment executes temperature control.
- FIG. 1 is a schematic diagram of an internal combustion engine to which a control device according to a first embodiment is applied.
- FIG. 2A is a schematic cross-sectional view of an EGR cooler.
- FIG. 2B is a
- FIG. 7 is a diagram illustrating an example of a flowchart when the control device according to the first modification of the second embodiment executes temperature control.
- FIG. 8A is a schematic diagram for explaining the temperature change of the heat exchanger when the temperature control according to the first and second embodiments is executed.
- FIG. 8B is a schematic diagram for explaining a change in the refrigerant flow rate in the cooler refrigerant passage when the temperature control according to the first and second embodiments is executed.
- FIG. 9 is a schematic diagram showing a temperature change of SiC strength.
- FIG. 1 is a schematic diagram of an internal combustion engine 5 to which a control device 10 is applied.
- the type of the internal combustion engine 5 is not particularly limited, and various internal combustion engines such as a diesel engine and a gasoline engine can be used.
- a gasoline engine is used as an example of the internal combustion engine 5.
- the internal combustion engine 5 includes a control device 10, an engine body 20 in which a cylinder 21 is formed, an intake passage 30 connected to the cylinder 21, an exhaust passage 31 connected to the cylinder 21, and a throttle 40 disposed in the intake passage 30.
- the intake passage 30 is a passage through which intake air passes. In this embodiment, fresh air flows into the upstream end of the intake passage 30 in the intake flow direction.
- the engine body 20 includes a cylinder block in which a cylinder 21 is formed, a cylinder head disposed at the upper portion of the cylinder block, and a piston disposed in the cylinder 21.
- the internal combustion engine 5 is provided with a pump 50 for supplying a refrigerant.
- the internal combustion engine 5 includes a first supply passage 60, a first discharge passage 61, a second supply passage 62, and a second discharge passage 63 as refrigerant passages through which the refrigerant passes.
- the internal combustion engine 5 includes an EGR (Exhaust Gas Recirculation) passage 70, an EGR valve 80 disposed in the EGR passage 70, and an EGR cooler 90 disposed in the EGR passage 70.
- the internal combustion engine 5 further includes a crank position sensor 100, a temperature sensor 101a, and a temperature sensor 101b.
- the control device 10 is a device that controls the engine body 20, the throttle 40, the pump 50, and the EGR valve 80.
- an electronic control unit Electronic Control Unit
- the CPU 11 controls the engine body 20, the throttle 40, the pump 50 and the EGR valve 80.
- CPU11 performs each step of each flowchart mentioned later.
- the ROM 12 and the RAM 13 have a function as a storage unit that stores information necessary for the operation of the CPU 11.
- the refrigerant discharged from the pump 50 passes through the first supply passage 60 and flows into a refrigerant passage formed inside the engine body 20 (hereinafter sometimes referred to as an engine body refrigerant passage).
- the refrigerant that has passed through the engine body refrigerant passage passes through the first discharge passage 61 and returns to the pump 50.
- a part of the refrigerant in the engine main body refrigerant passage passes through the second supply passage 62 and is guided to the EGR cooler 90.
- the refrigerant that has passed through the EGR cooler 90 passes through the second discharge passage 63 and returns to the engine body refrigerant passage.
- the pump 50 according to the present embodiment supplies the refrigerant to both the engine body 20 and the EGR cooler 90.
- an electric water pump is used as an example of the pump 50.
- the EGR passage 70 is a passage for recirculating a part of the exhaust discharged from the cylinder 21 to the intake passage 30.
- the exhaust gas that passes through the EGR passage 70 and recirculates to the intake passage 30 is referred to as EGR gas. That is, the EGR passage 70 is a passage for introducing EGR gas into the intake passage 30.
- the EGR passage 70 according to this embodiment connects the passageway of the intake passage 30 and the passageway of the exhaust passage 31.
- the upstream end of the EGR passage 70 in the EGR gas flow direction is connected to the exhaust manifold in the exhaust passage 31.
- a portion of the EGR passage 70 on the downstream side of the portion where the EGR cooler 90 is disposed passes through the inside of the engine body 20 (a cylinder block in this embodiment).
- the EGR valve 80 opens and closes the EGR passage 70 in response to an instruction from the control device 10.
- the flow rate (m 3 / s) of the EGR gas can be adjusted.
- the EGR valve 80 is opened (specifically, when the opening degree of the EGR valve 80 becomes a value larger than 0), the flow of EGR gas into the cylinder 21 is started, and the EGR valve 80 is closed. In this case, the flow of EGR gas into the cylinder 21 is stopped. Further, as the opening degree of the EGR valve 80 increases, the flow rate of EGR gas flowing into the cylinder 21 also increases.
- the EGR cooler 90 is a device that cools the EGR gas by exchanging heat between the refrigerant and the EGR gas. Details of the EGR cooler 90 will be described later.
- the crank position sensor 100 detects the position of the crankshaft of the internal combustion engine 5 and transmits the detection result to the control device 10.
- the temperature sensor 101a detects the temperature of the refrigerant in a cooler refrigerant passage 94 (illustrated in FIG. 2A described later) that is a refrigerant passage formed inside the EGR cooler 90, and the detection result is controlled by the control device.
- Tell 10 The temperature sensor 101b detects the temperature of the exhaust and transmits the detection result to the control device 10.
- the temperature sensor 101b according to the present embodiment detects the temperature of the exhaust gas upstream of the EGR cooler 90.
- FIG. 2A is a schematic cross-sectional view of the EGR cooler 90.
- the EGR cooler 90 includes an outer pipe 91, an inner pipe 92 disposed inside the outer pipe 91, and a heat exchange body 93 disposed inside the inner pipe 92.
- the inner pipe 92 is connected to the EGR passage 70 so that EGR gas passes through the inner pipe 92.
- the flow direction of EGR gas is a direction from right to left.
- the portion illustrated by the region S in FIG. 2A is connected to the outer peripheral surface of the inner pipe 92.
- a space is provided between a region sandwiched by regions S present at both ends of the outer pipe 91 and the inner pipe 92.
- This space is a cooler refrigerant passage 94 that is a refrigerant passage through which the refrigerant passes.
- the region S has a function as a seal portion that suppresses leakage of the refrigerant from the cooler refrigerant passage 94.
- a refrigerant supply port 95 and a refrigerant discharge port 96 are provided in a portion of the outer pipe 91 constituting the cooler refrigerant passage 94.
- a second supply passage 62 is connected to the refrigerant supply port 95, and a second discharge passage 63 is connected to the refrigerant discharge port 96.
- the inner pipe 92 covers the entire outer peripheral wall surface of the heat exchanger 93. Further, the inner pipe 92 according to the present embodiment extends further upstream than the end face on the upstream side in the EGR gas flow direction of the heat exchanger 93, and more than the end face on the downstream side in the EGR gas flow direction of the heat exchanger 93. Furthermore, it extends downstream.
- the heat exchanger 93 is a medium that conducts the heat of the EGR gas to the cooler refrigerant passage 94.
- FIG. 2B is a front view of the heat exchanger 93. Specifically, FIG. 2B schematically illustrates the heat exchanger 93 viewed from the X direction in FIG. In FIG. 2B, the inner pipe 92 is also shown.
- the heat exchange body 93 according to the present embodiment is disposed inside the inner pipe 92 so as to contact the inner peripheral surface of the inner pipe 92.
- the outer diameter of the heat exchange element 93 is set to the same value as the inner diameter of the inner pipe 92 or a value slightly larger than the same value.
- the heat exchange body 93 according to the present embodiment is disposed inside the inner pipe 92 so as to be fitted to the inner peripheral surface of the inner pipe 92.
- the heat exchanger 93 has a gas passage 97 through which EGR gas passes.
- each gas passage 97 has a first partition wall 98 extending in the lateral direction in FIG. And a second partition wall 99 having an angle formed by a predetermined angle (in this embodiment, 90 degrees as an example).
- a predetermined angle in this embodiment, 90 degrees as an example.
- the material of the outer pipe 91 and the inner pipe 92 according to the present embodiment is stainless steel.
- the material of the outer pipe 91 and the inner pipe 92 is not limited to this, and for example, metals other than stainless steel or ceramics can be used.
- the material of the heat exchanging body 93 according to the present embodiment is a ceramic containing SiC (silicon carbide).
- the material of the first partition wall 98 and the second partition wall 99 of the heat exchange body 93 includes SiC.
- Specific examples of the material of the heat exchanger 93 include SiC (that is, a material in which no additive is added in addition to SiC), Si-impregnated SiC, (Si + Al) -impregnated SiC, metal composite SiC, etc.
- Si-impregnated SiC is used as an example of the material of the heat exchanger 93.
- the control device 10 executes a control process for stopping the operation of the pump 50 for a predetermined period (hereinafter, this control process is referred to as refrigerant stop control).
- this control process is referred to as refrigerant stop control.
- the refrigerant stop control is a control process for stopping the operation of the pump 50 and also a control process for stopping the refrigerant that has passed through the engine body 20 from flowing into the EGR cooler 90. Since the refrigerant flow in the engine body 20 is stopped by the execution of the refrigerant stop control, the engine body 20 can be warmed up early. Thereby, warm-up of the internal combustion engine 5 can be promoted.
- the timing when the control device 10 according to the present embodiment executes the refrigerant stop control is when the internal combustion engine 5 is started.
- a time necessary for warming up the internal combustion engine 5 can be used as the predetermined period during which the refrigerant stop control is executed. This predetermined period is obtained in advance by experiments, simulations, etc., and is stored in the storage unit of the control device 10.
- the control device 10 according to this embodiment starts the internal combustion engine 5 by stopping the operation of the pump 50 for a predetermined period from when the internal combustion engine 5 is started (specifically, from when cranking is started). Sometimes the refrigerant stop control is executed for a predetermined period.
- the timing when the control device 10 executes the refrigerant stop control is not limited to the time when the internal combustion engine 5 is started. Further, the predetermined period during which the refrigerant stop control is executed is not limited to the period as described above.
- the specific execution method of the refrigerant stop control is not limited to the method of stopping the operation of the pump 50 as described above.
- the internal combustion engine 5 includes a flow rate control valve in a refrigerant passage (specifically, the first supply passage 60 or the first discharge passage 61) between the pump 50 and the engine body 20.
- the control device 10 may control the flow control valve to be closed without stopping the operation of the pump 50.
- the flow of the refrigerant in the engine body 20 can be stopped by closing the flow control valve, and as a result, the flow of the refrigerant through the engine body 20 into the EGR cooler 90 can also be stopped. it can.
- control device 10 executes a control process (hereinafter referred to as temperature control) for suppressing the degree of temperature change of the heat exchanger 93 when the refrigerant stop control is finished.
- the temperature change of the heat exchanger 93 specifically means a change of the temperature of the heat exchanger 93 with respect to time. Details of the temperature control according to the present embodiment will be described with reference to a flowchart.
- FIG. 3 is a diagram illustrating an example of a flowchart when the control device 10 according to the present embodiment executes temperature control.
- the control device 10 (specifically, the CPU 11) according to the present embodiment executes the first START of FIG. 3 when the internal combustion engine 5 is started. Further, the control device 10 repeatedly executes the flowchart of FIG. 3 at a predetermined cycle. First, the control device 10 determines whether or not the EGR valve 80 is opened before the end of the refrigerant stop control (step S10). When it determines with No by step S10, the control apparatus 10 performs step S40 mentioned later.
- step S10 the control device 10 acquires the temperature (Ta) of the heat exchanger 93 (step S20).
- Step S20 is executed before the end of the refrigerant stop control. That is, in step S20, the control device 10 acquires the temperature of the heat exchange body 93 before the end of the refrigerant stop control.
- the control device 10 acquires the temperature of the heat exchange body 93 based on an index having a correlation with the temperature of the heat exchange body 93.
- the control device 10 as an example of an index having a correlation with the temperature of the heat exchanger 93, the temperature of the exhaust existing upstream of the heat exchanger 93 (hereinafter sometimes referred to as upstream exhaust temperature). Is used.
- the control device 10 acquires the upstream exhaust temperature based on the detection result of the temperature sensor 101b.
- the storage unit of the control device 10 stores a map that defines the temperature of the heat exchanger 93 in association with the upstream exhaust temperature.
- the control device 10 extracts the temperature of the heat exchanger 93 corresponding to the upstream exhaust temperature acquired based on the detection result of the temperature sensor 101b from the map of the storage unit, and sets the extracted temperature of the heat exchanger 93 in step S20. Obtained as the temperature (Ta) of the heat exchanger 93.
- the specific acquisition method of the temperature (Ta) of the heat exchanger 93 is not limited to the method of acquiring based on the index as described above.
- the control device 10 determines the temperature of the heat exchanger 93 based on the detection result of the temperature sensor. You can also get
- step S20 the control device 10 determines whether or not the temperature (Ta) of the heat exchanger 93 acquired in step S20 is equal to or higher than a predetermined value a (step S30).
- the control apparatus 10 performs normal control (step S40).
- the control device 10 controls the flow rate of the refrigerant that passes through the EGR cooler 90 after the refrigerant stop control is ended to a predetermined flow rate (hereinafter referred to as a normal flow rate).
- control device 10 controls the duty ratio of the pump 50 to control the flow rate of the refrigerant passing through the cooler refrigerant passage 94 of the EGR cooler 90 to the normal flow rate after completion of the refrigerant stop control. More specifically, the control device 10 controls the duty ratio of the pump 50 so that the output (specifically, the rotational speed) of the pump 50 becomes an output corresponding to the normal flow rate (this is referred to as a normal output). Yes. Next, the control device 10 ends the execution of the flowchart.
- step S50 the control device 10 controls the flow rate of the refrigerant passing through the EGR cooler 90 after the refrigerant stop control is finished to a smaller flow rate than the normal flow rate. That is, when the temperature of the heat exchange body 93 is equal to or higher than the predetermined value a and the refrigerant stop control by the control apparatus 10 is finished, the control device 10 performs the refrigerant stop control by the control device 10 when the temperature of the heat exchange body 93 is lower than the predetermined value a. Compared to the case where the operation is completed, the flow rate of the refrigerant passing through the EGR cooler 90 is controlled to a small flow rate.
- step S50 the control device 10 controls the duty ratio of the pump 50 so that the output (specifically, the rotation speed) of the pump 50 is the output of the pump 50 when step S40 is executed. Reduced compared to normal output. That is, the control device 10 outputs the output of the pump 50 when the temperature of the heat exchanger 93 is equal to or higher than the predetermined value a and the refrigerant stop control by the control device 10 is finished. 10 is reduced compared to the output of the pump 50 when the refrigerant stop control by 10 is completed.
- the control apparatus 10 performs the temperature control which concerns on step S50 for a predetermined period.
- control device 10 outputs the output of the pump 50 when the temperature of the heat exchanger 93 is equal to or higher than the predetermined value a and the refrigerant stop control by the control device 10 is finished.
- the output of the pump 50 is reduced to a predetermined target output (this is because the temperature of the heat exchanger 93 is less than the predetermined value a and the control device 10 Instead of changing all at once (that is, not suddenly changing) until the refrigerant stop control by is completed, the target output is lower than the normal output.
- the control apparatus 10 may change the output of the pump 50 continuously to the target output, or may change it stepwise to the target output.
- the predetermined value a used in step S30 for example, when the temperature of the heat exchanger 93 becomes equal to or higher than the predetermined value a, when the normal control according to step S40 is executed instead of executing step S50.
- the temperature at which the heat exchanger 93 may be deteriorated can be used.
- the predetermined value a is obtained in advance by experiments, simulations, etc. and stored in the storage unit.
- step S50 the control device 10 according to the present embodiment controls the refrigerant passing through the EGR cooler 90 so that the temperature of the heat exchanger 93 after the refrigerant stop control is finished does not fall below a predetermined value x lower than the predetermined value a.
- the flow rate is controlled. That is, in step S50, the control device 10 according to the present embodiment compares the flow rate of the refrigerant passing through the EGR cooler 90 with the normal flow rate so that the temperature of the heat exchanger 93 after the refrigerant stop control is finished does not fall below the predetermined value x. And decrease. After step S50, the control device 10 ends the execution of the flowchart.
- the control device 10 passes through the EGR cooler 90 when the temperature of the heat exchanger 93 is equal to or higher than the predetermined value a and the refrigerant stop control is finished.
- the refrigerant flow rate is controlled to be smaller than the refrigerant flow rate (normal flow rate) passing through the EGR cooler 90. .
- the degree of cooling of the heat exchanger 93 by the refrigerant can be weakened. Thereby, the temperature decrease rate of the heat exchanger 93 when the refrigerant stop control is completed can be reduced.
- the degree of temperature change of the heat exchanger 93 when the refrigerant stop control is completed can be suppressed.
- the control device 10 since the output of the pump 50 is gradually changed to the target output in step S50, the control device 10 causes a sudden change in the temperature of the heat exchanger 93 as compared with a case where the output of the pump 50 is suddenly changed. It can be effectively suppressed. Thereby, deterioration of the heat exchange body 93 can be suppressed effectively.
- FIG. 4 is a diagram illustrating an example of a flowchart when the control device 10 according to the present modification executes temperature control.
- the flowchart of FIG. 4 differs from the flowchart of FIG. 3 according to the first embodiment in that step S20a is provided instead of step S20, and step S30a is provided instead of step S30.
- Step S20a and step S30a are different from step S20 and step S30, respectively, in that an index having a correlation with the temperature of the heat exchanger 93 is used instead of using the temperature of the heat exchanger 93.
- step S20a the control device 10 according to the present modification obtains an index having a correlation with the temperature of the heat exchanger 93.
- the control device 10 according to this modification uses the temperature of the refrigerant as an example of an index having a correlation with the temperature of the heat exchanger 93. More specifically, the control device 10 uses the temperature of the refrigerant in the cooler refrigerant passage 94 as the temperature of the refrigerant.
- the control device 10 according to the present modification acquires the refrigerant temperature (Tb) in the cooler refrigerant passage 94 based on the detection result of the temperature sensor 101a.
- step S30a the control device 10 determines whether or not the refrigerant temperature (Tb) in the cooler refrigerant passage 94 acquired in step S20a is equal to or higher than a predetermined value b.
- the predetermined value b is the refrigerant temperature in the cooler refrigerant passage 94 corresponding to the predetermined value a.
- the predetermined value b for example, when the temperature of the refrigerant in the cooler refrigerant passage 94 is equal to or higher than the predetermined value b, when the normal control according to step S40 is executed instead of executing step S50, It is possible to use a temperature at which the exchanger 93 may be deteriorated.
- the predetermined value b is obtained in advance by experiments, simulations, etc. and stored in the storage unit.
- step S40 when it determines with No by step S30a, the control apparatus 10 performs step S40.
- Step S40 in FIG. 4 is the same as step S40 in FIG.
- the control apparatus 10 performs step S50.
- Step S50 in FIG. 4 is the same as step S50 in FIG.
- the control device 10 according to the present modification uses the normal flow rate (the refrigerant flow rate when step S40 is executed) as the flow rate of the refrigerant passing through the EGR cooler 90 after the end of the refrigerant stop control. Compared to the above, the flow rate is controlled to be small.
- control device 10 (specifically, the CPU 11) according to the present modification has a refrigerant temperature that is less than the predetermined value b when the refrigerant temperature is equal to or higher than the predetermined value b and the refrigerant stop control by the control device 10 ends.
- the flow rate of the refrigerant passing through the EGR cooler 90 is controlled to a smaller flow rate than when the refrigerant stop control by the control device 10 is completed.
- control device 10 compares the output of the pump 50 after the refrigerant stop control is completed in Step S50 with the normal output (this is the output of the pump 50 when Step S40 is executed). It is decreasing. That is, the control device 10 according to the present modified example outputs the output of the pump 50 when the refrigerant temperature is equal to or higher than the predetermined value b and the refrigerant stop control by the control device 10 is finished. The refrigerant output is reduced as compared with the output of the pump 50 when the refrigerant stop control is completed.
- step S50 the control device 10 outputs the output of the pump 50 when the refrigerant temperature is equal to or higher than the predetermined value b and the refrigerant stop control by the control device 10 is finished.
- the output of the pump 50 is set to a predetermined target output (this is because the control of the refrigerant stop control by the control device 10 when the temperature of the refrigerant is less than the predetermined value b)
- the output is gradually changed to a value lower than the normal output that is the target output in the case of termination.
- the control apparatus 10 may change the output of the pump 50 continuously to the target output, or may change it stepwise to the target output.
- step S50 the degree of cooling of the heat exchanger 93 by the refrigerant when the refrigerant stop control is completed can be weakened. Thereby, the temperature decrease rate of the heat exchanger 93 when the refrigerant stop control is completed can be reduced. As a result, since the rapid decrease in the temperature of the heat exchanger 93 when the refrigerant stop control is finished can be suppressed, the deterioration of the heat exchanger 93 can be suppressed.
- the heat exchanger 93 is compared with the case where the output of the pump 50 is suddenly changed. Can be effectively suppressed. Thereby, deterioration of the heat exchange body 93 can be suppressed effectively.
- the control device 10 controls the pump 50 when performing the temperature control, but is not limited thereto.
- the control device 10 performs temperature control by controlling this. May be.
- the control device 10 uses this flow rate. You may perform temperature control by controlling the opening degree of a control valve.
- the CPU 11 that executes the refrigerant stop control corresponds to a member that functions as a refrigerant stop control unit that executes the refrigerant stop control.
- the CPU 11 that executes Step S50 corresponds to a member that functions as a control unit that controls the flow rate of the refrigerant that passes through the EGR cooler 90 and a control unit that controls the output of the pump 50.
- FIG. 5 is a schematic diagram for explaining the configuration of the internal combustion engine 5a. Specifically, FIG. 5 shows a configuration in the vicinity of the EGR cooler 90 of the internal combustion engine 5a and the control device 10a.
- the internal combustion engine 5a includes a control device 10a instead of the control device 10, and further includes a second pump 51, a third supply passage 64, a third discharge passage 65, and a check valve 110. 1 and different from the internal combustion engine 5 of FIG.
- the internal combustion engine 5 a also includes components other than the control device 10 shown in FIG. 1.
- the second pump 51 is a pump different from the pump 50. That is, the internal combustion engine 5a according to the present embodiment includes two pumps (a pump 50 and a second pump 51).
- the second pump 51 supplies the refrigerant to the EGR cooler 90 in response to an instruction from the control device 10a. That is, the second pump 51 is a pump that is provided separately from the pump 50 and supplies the refrigerant to the EGR cooler 90.
- an electric water pump is used as an example of the second pump 51.
- the specific configuration of the second pump 51 is not limited to the electric water pump as long as the refrigerant can be supplied in response to an instruction from the control device 10a.
- the third supply passage 64 communicates the second pump 51 and the second supply passage 62.
- the third supply passage 64 is a refrigerant passage that guides the refrigerant discharged from the second pump 51 to the second supply passage 62.
- the third discharge passage 65 communicates the second pump 51 and the second discharge passage 63.
- the third discharge passage 65 is a refrigerant passage that returns the refrigerant that has flowed into the second discharge passage 63 via the EGR cooler 90 to the second pump 51.
- the check valve 110 is disposed on the upstream side in the refrigerant flow direction from the portion of the second supply passage 62 to which the third supply passage 64 is connected.
- the check valve 110 allows the refrigerant to pass from the engine main body 20 side of the second supply passage 62 to the EGR cooler 90 side, and suppresses the refrigerant from passing from the EGR cooler 90 side to the engine main body 20 side.
- the internal combustion engine 5a includes the check valve 110, the refrigerant flowing into the second supply passage 62 via the third supply passage 64 when the second pump 51 is operated with the pump 50 stopped is the engine body. Inflow to 20 is suppressed.
- control device 10a Details of the control device 10a will be described.
- the hardware configuration of the control device 10a is the same as that of the control device 10 of FIG. Specifically, the control device 10 a according to the present embodiment is also an electronic control device including the CPU 11, the ROM 12, and the RAM 13, similarly to the control device 10.
- the control device 10a is different from the control device 10 according to the first embodiment in that the control device 10a executes a flowchart of FIG. 6 described below instead of the flowchart of FIG.
- FIG. 6 is a diagram illustrating an example of a flowchart when the control device 10a according to the present embodiment executes temperature control.
- the flowchart of FIG. 6 differs from the flowchart of FIG. 3 in that step S30b is provided instead of step S30, and step S50a is provided instead of step S50.
- step S30b the control device 10a (specifically, the CPU 11) determines whether or not the temperature (Ta) of the heat exchanger 93 acquired in step S20 is equal to or higher than a predetermined value c.
- Step S30b is executed before the end of the refrigerant stop control.
- the control apparatus 10a performs the normal control which concerns on step S40.
- step S40 the control device 10a controls the flow rate of the refrigerant passing through the EGR cooler 90 to the normal flow rate after completion of the refrigerant stop control.
- Step S40 when controlling the flow rate of the refrigerant to the normal flow rate in Step S40, the control device 10a controls the flow rate of the refrigerant to the normal flow rate by controlling the pump 50 without operating the second pump 51.
- step S40 since the specific content of step S40 which concerns on a present Example is the same as that of step S40 of Example 1, detailed description beyond this is abbreviate
- step S50a the control device 10a starts the operation of the second pump 51. That is, the control device 10a according to the present embodiment executes the temperature control according to step S50a when the temperature of the heat exchanger 93 becomes equal to or higher than the predetermined value c before the refrigerant stop control is finished, and the control device 10a in step S50a 10 a starts the operation of the second pump 51.
- the second pump 51 according to the present embodiment starts the operation before the refrigerant stop control ends (specifically, before the operation of the pump 50 starts).
- the control device 10a ends the execution of the flowchart.
- the temperature control according to Step S50a is performed, so that the temperature of the heat exchanger 93 at the time when the refrigerant stop control is finished is changed to the heat before the refrigerant stop control is finished.
- the temperature can be lowered.
- the temperature decrease amount of the heat exchanger 93 when the refrigerant stop control is finished can be reduced.
- the control device 10a performs the second operation so that the temperature of the heat exchanger 93 when the refrigerant stop control ends does not exceed the second predetermined value y.
- the pump 51 may be controlled.
- the second predetermined value y the refrigerant stop control in the case where the operation of the second pump 51 is not started even though the temperature of the heat exchanger 93 becomes equal to or higher than the predetermined value c before the refrigerant stop control ends.
- a predetermined temperature lower than the temperature of the heat exchanger 93 at the end (hereinafter referred to as temperature z) can be used.
- the output (specifically, the rotational speed) of the second pump 51 so that the temperature of the heat exchanger 93 at the time when the refrigerant stop control is finished does not exceed the second predetermined value y.
- the control device 10a causes the second pump 51 to output the second pump 51 stored in the storage unit. 51 is controlled.
- the temperature of the heat exchange body 93 at the time when the refrigerant stop control is finished can be suppressed to be lower than the second predetermined value y.
- the temperature of the heat exchanging body 93 at the time when the refrigerant stop control is completed can be reliably reduced below the temperature z. Thereby, deterioration of the heat exchanger 93 can be suppressed more effectively.
- the predetermined value c used in step S30b is preferably a temperature at which deterioration of the heat exchanger 93 can be suppressed when it is determined No in step S30b and normal control according to step S40 is executed. In this case, it is because degradation of the heat exchange body 93 can be suppressed even if step S40 which concerns on a present Example is performed.
- the predetermined value c may be obtained in advance by experiments, simulations, etc. and stored in the storage unit.
- FIG. 7 is a diagram illustrating an example of a flowchart when the control device 10a according to the present modification executes temperature control.
- the flowchart of FIG. 7 differs from the flowchart of FIG. 6 in that step S20a is provided instead of step S20, and step S30c is provided instead of step S30b.
- Step S20a and step S30c mainly use an index having a correlation with the temperature of the heat exchanger 93, specifically, the temperature of the refrigerant in the cooler refrigerant passage 94, instead of using the temperature of the heat exchanger 93.
- Step S20 and Step S30b are different from Step S20 and Step S30b, respectively.
- Step S20a in FIG. 6 is the same as step S20a in FIG. Specifically, in step S20a, the control device 10a according to the present modification obtains the refrigerant temperature (Tb) in the cooler refrigerant passage 94 based on the detection result of the temperature sensor 101a. After step S20a, the control device 10a executes step S30c.
- step S30c the control device 10a determines whether or not the refrigerant temperature (Tb) acquired in step S20a is equal to or higher than a predetermined value d.
- the predetermined value d is the temperature of the refrigerant in the cooler refrigerant passage 94 corresponding to the predetermined value c according to step S30b of FIG. Specifically, as the predetermined value d, it is preferable to use a temperature at which deterioration of the heat exchanger 93 can be suppressed when it is determined No in Step S30c and the normal control according to Step S40 is executed.
- step S40 is the same as step S40 in FIG.
- step S50a is the same as step S50a in FIG.
- the control device 10a performs a step when the temperature of the refrigerant (specifically, the temperature of the refrigerant in the cooler refrigerant passage 94) becomes equal to or higher than the predetermined value d before the refrigerant stop control ends.
- the temperature control according to S50b is executed, and the control device 10a starts the operation of the second pump 51 in the temperature control.
- the rapid decrease in the temperature of the heat exchanger 93 when the refrigerant stop control is terminated is suppressed. be able to. Thereby, since the rapid fall of the intensity
- the CPU 11 that performs the refrigerant stop control corresponds to a member that functions as a refrigerant stop control unit that executes the refrigerant stop control.
- the CPU 11 that executes step S50a corresponds to a member having a function as a control unit that controls the second pump 51.
- FIG. 8A is a schematic diagram for explaining a temperature change of the heat exchanger 93 when the temperature control according to the first embodiment and the second embodiment is executed.
- FIG. 8B is a schematic diagram for explaining a change in the refrigerant flow rate in the cooler refrigerant passage 94 when the temperature control according to the first and second embodiments is executed.
- the vertical axis represents temperature and the horizontal axis represents time.
- a curve 200 shows a change over time of the refrigerant temperature in the cooler refrigerant passage 94
- a curve 201 shows a change over time in the refrigerant temperature of the engine body refrigerant passage of the engine body 20.
- a curve 202 is obtained when step S40 is executed instead of executing step S50 when it is determined Yes in step S30 of the first embodiment (hereinafter, this is referred to as a case where the control according to the comparative example is executed). ) Shows the time change of the temperature of the heat exchanger 93.
- the comparative example shown by the curve 202 shows the time change of the temperature of the heat exchanger 93 when the normal flow rate refrigerant flows into the EGR cooler 90 after the refrigerant stop control is completed when it is determined Yes in step S30.
- a curve 203 indicates a change over time of the temperature of the heat exchanger 93 when the temperature control according to the first embodiment is executed.
- a curve 204 shows a time change of the temperature of the heat exchanger 93 when the temperature control according to the second embodiment is executed. Specifically, the curve 204 indicates that, in the temperature control according to step S50a, the second pump 51 is controlled such that the temperature of the heat exchanger 93 when the refrigerant stop control is finished does not exceed the second predetermined value y.
- a curve 205 shows a change over time of the refrigerant flow rate in the cooler refrigerant passage 94 when the normal control according to the comparative example is executed.
- a curve 206 indicates a change over time in the refrigerant flow rate of the cooler refrigerant passage 94 according to the first embodiment. The curve 206 merges with the curve 205 from the middle.
- a curve 207 indicates a change over time in the refrigerant flow rate of the cooler refrigerant passage 94 according to the second embodiment. The curve 207 merges with the curve 205 from the middle. Note that, when the temperature control according to the first modification of the first embodiment and the temperature control according to the first modification of the second embodiment are executed, the same diagram as FIG. 8B is obtained.
- time A is the time when the temperature of the heat exchanger 93 becomes equal to or higher than the predetermined value c in step S30b of FIG. 6 according to the second embodiment.
- Time B is the time when the refrigerant stop control is finished in the first and second embodiments. Referring to curve 207, in Example 2, the second pump 51 starts operation at time A, so the refrigerant flow rate in cooler refrigerant passage 94 starts increasing at time A.
- the control according to the comparative example curve 202
- the time D is a time when the temperature of the heat exchanger 93 becomes the lowest after the refrigerant stop control ends when the temperature control (curve 203) according to the first embodiment is executed.
- the temperature control according to the first embodiment is executed.
- the refrigerant flow rate in the cooler refrigerant passage 94 after the refrigerant stop control is controlled to be lower than the normal flow rate (therefore, the curve 206 is positioned below the curve 205).
- the temperature of the heat exchanger 93 according to the first embodiment is set to the lowest temperature, as can be seen from a comparison between the curve 203 (temperature control of the first embodiment) and the curve 202 (comparative example) in FIG.
- the time D becomes longer than the time C when the temperature of the heat exchange body 93 according to the comparative example becomes the minimum temperature. From this, it can be seen that the temperature decrease rate of the heat exchanger 93 after the end of the refrigerant stop control is reduced in the temperature control according to the first embodiment than in the case where the control according to the comparative example is executed. . Therefore, it can be seen that by executing the temperature control according to the first embodiment, it is possible to suppress a rapid decrease in the temperature of the heat exchanger 93 after the refrigerant stop control is completed.
- the heat exchanger 93 at the end of the refrigerant stop control in the second embodiment is shown.
- the temperature is a case where the operation of the second pump 51 is not started even though the temperature of the heat exchanging body 93 becomes equal to or higher than a predetermined value c before the refrigerant stop control ends (for example, Lower than the temperature z of the heat exchanger 93 at the end of the refrigerant stop control when the control according to the comparative example of the curve 202 is executed or when the control according to the first embodiment of the curve 203 is executed).
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Exhaust-Gas Circulating Devices (AREA)
Abstract
Description
続いて実施例1の変形例1に係る内燃機関の制御装置10について説明する。本変形例に係る制御装置10は、実施例1に係る図3に代えて以下に説明する図4のフローチャートを実行する点において、実施例1に係る制御装置10と異なっている。図4は、本変形例に係る制御装置10が温度制御を実行する際のフローチャートの一例を示す図である。図4のフローチャートは、ステップS20に代えてステップS20aを備えている点と、ステップS30に代えてステップS30aを備えている点とにおいて、実施例1に係る図3のフローチャートと異なっている。なおステップS20aおよびステップS30aは、主として、熱交換体93の温度を用いる代わりに熱交換体93の温度と相関を有する指標を用いている点において、それぞれステップS20およびステップS30と異なっている。
続いて実施例2の変形例1に係る内燃機関の制御装置10aについて説明する。本変形例に係る制御装置10aは、実施例2に係る図6に代えて以下に説明する図7のフローチャートを実行する点において、実施例2に係る制御装置10aと異なっている。図7は、本変形例に係る制御装置10aが温度制御を実行する際のフローチャートの一例を示す図である。図7のフローチャートは、ステップS20に代えてステップS20aを備えている点と、ステップS30bに代えてステップS30cを備えている点とにおいて、図6のフローチャートと異なっている。なおステップS20aおよびステップS30cは、主として、熱交換体93の温度を用いる代わりに熱交換体93の温度と相関を有する指標、具体的にはクーラ冷媒通路94における冷媒の温度を用いている点において、それぞれステップS20およびステップS30bと異なっている。
10 制御装置
20 機関本体
21 気筒
30 吸気通路
31 排気通路
50 ポンプ
51 第2ポンプ
70 EGR通路
80 EGRバルブ
90 EGRクーラ
93 熱交換体
94 クーラ冷媒通路
Claims (3)
- 内燃機関の吸気通路にEGRガスを導入させるEGR通路に配置され、SiCを含む材質からなる熱交換体を有するEGRクーラを備える内燃機関に適用される制御装置であって、
冷媒が前記EGRクーラに流入することを停止させる冷媒停止制御を実行する冷媒停止制御部と、
前記冷媒の温度が所定値以上で前記冷媒停止制御部による前記冷媒停止制御が終了した場合に、前記冷媒の温度が前記所定値未満で前記冷媒停止制御部による前記冷媒停止制御が終了した場合に比較して、前記EGRクーラを通過する前記冷媒の流量を少ない流量に制御する制御部と、を備える内燃機関の制御装置。 - 前記内燃機関は、前記内燃機関の機関本体および前記EGRクーラに冷媒を供給するポンプを備え、
前記制御部は、前記冷媒の温度が前記所定値以上で前記冷媒停止制御部による前記冷媒停止制御が終了した場合における前記ポンプの出力を、前記冷媒の温度が前記所定値未満で前記冷媒停止制御部による前記冷媒停止制御が終了した場合における前記ポンプの出力に比較して低下させる請求項1記載の内燃機関の制御装置。 - 前記制御部は、前記ポンプの出力を低下させるにあたり、前記ポンプの出力を目標出力まで徐々に変化させる請求項2記載の内燃機関の制御装置。
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DE112013006652.1T DE112013006652B4 (de) | 2013-02-12 | 2013-02-12 | Steuerungsvorrichtung für die Kühlmittel-Strömungsrate in einem AGR-Kühler einer Verbrennungskraftmaschine |
PCT/JP2013/053275 WO2014125570A1 (ja) | 2013-02-12 | 2013-02-12 | 内燃機関の制御装置 |
JP2015500021A JP5943137B2 (ja) | 2013-02-12 | 2013-02-12 | 内燃機関の制御装置 |
US14/774,332 US9551270B2 (en) | 2013-02-12 | 2013-02-12 | Control device for coolant flow in an internal combustion engine |
CN201380072730.6A CN104981602B (zh) | 2013-02-12 | 2013-02-12 | 内燃机的控制装置 |
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PCT/JP2013/053275 WO2014125570A1 (ja) | 2013-02-12 | 2013-02-12 | 内燃機関の制御装置 |
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JP (1) | JP5943137B2 (ja) |
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EP3109428B1 (en) | 2015-06-24 | 2018-02-07 | Toyota Jidosha Kabushiki Kaisha | Exhaust heat recovery structure |
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CN106837618B (zh) * | 2016-12-26 | 2019-03-29 | 潍柴动力股份有限公司 | 判断egr冷却器的冷却效率劣化的方法及egr系统 |
CN114607534B (zh) * | 2022-03-24 | 2023-06-23 | 潍柴动力股份有限公司 | 一种行车被动再生egr冷却器的策略、装置及车辆 |
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- 2013-02-12 CN CN201380072730.6A patent/CN104981602B/zh not_active Expired - Fee Related
- 2013-02-12 DE DE112013006652.1T patent/DE112013006652B4/de not_active Expired - Fee Related
- 2013-02-12 US US14/774,332 patent/US9551270B2/en active Active
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CN104981602A (zh) | 2015-10-14 |
US20160010597A1 (en) | 2016-01-14 |
DE112013006652B4 (de) | 2017-10-26 |
CN104981602B (zh) | 2017-05-17 |
DE112013006652T5 (de) | 2015-11-19 |
US9551270B2 (en) | 2017-01-24 |
JP5943137B2 (ja) | 2016-06-29 |
JPWO2014125570A1 (ja) | 2017-02-02 |
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