WO2014112538A1 - 内燃機関 - Google Patents
内燃機関 Download PDFInfo
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- WO2014112538A1 WO2014112538A1 PCT/JP2014/050604 JP2014050604W WO2014112538A1 WO 2014112538 A1 WO2014112538 A1 WO 2014112538A1 JP 2014050604 W JP2014050604 W JP 2014050604W WO 2014112538 A1 WO2014112538 A1 WO 2014112538A1
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- WIPO (PCT)
- Prior art keywords
- nozzle
- temperature
- internal combustion
- combustion engine
- nozzle tip
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
- F02D35/02—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions
- F02D35/025—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions by determining temperatures inside the cylinder, e.g. combustion temperatures
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
- F02D35/0007—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for using electrical feedback
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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
- F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
- F02M53/04—Injectors with heating, cooling, or thermally-insulating means
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N25/00—Investigating or analyzing materials by the use of thermal means
- G01N25/56—Investigating or analyzing materials by the use of thermal means by investigating moisture content
- G01N25/66—Investigating or analyzing materials by the use of thermal means by investigating moisture content by investigating dew-point
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/04—Introducing corrections for particular operating conditions
- F02D41/042—Introducing corrections for particular operating conditions for stopping the engine
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/05—Fuel-injection apparatus having means for preventing corrosion
Definitions
- the present invention relates to an internal combustion engine.
- Patent Document 1 proposes a method for estimating the nozzle tip temperature, adjusting the EGR amount based on the estimated nozzle tip temperature, and reducing corrosion.
- the nozzle tip temperature is involved in the attachment of condensed water to the nozzle tip.
- the nozzle tip temperature continuously decreases after the engine is stopped. For this reason, even if the nozzle tip temperature at a certain time point is acquired, it is difficult to accurately predict how the nozzle tip temperature subsequently decreases and the occurrence of condensation occurs. For this reason, the said patent document 1 has room for improvement in determination of generation
- an object of the internal combustion engine disclosed in this specification is to accurately determine the occurrence of condensation at the nozzle tip in order to effectively suppress condensation at the nozzle tip.
- the internal combustion engine disclosed in the present specification determines whether or not condensation has occurred at the nozzle tip based on the amount of heat received by the nozzle of the injector and the temperature at the tip of the injector when the ignition is turned off.
- a control unit for determining is provided. This control unit may perform at least one of control for reducing the nozzle heat dissipation rate when it is determined that condensation occurs at the nozzle tip, and control for improving the rate of temperature decrease at the portion located around the nozzle. it can.
- the temperature at the nozzle tip is involved in the formation of condensation at the nozzle tip and adhesion of condensed water, but the change in the nozzle tip temperature after the engine has stopped is affected by the amount of heat received by the nozzle at the time the ignition is turned off. receive. Therefore, by taking into account the amount of heat received by the nozzle, it is possible to accurately grasp the change in the nozzle tip temperature and more accurately determine whether condensation has occurred at the nozzle tip.
- the control unit performs at least one of control for reducing the nozzle heat dissipation rate when it is determined that condensation occurs at the nozzle tip, and control for improving the rate of temperature decrease at a portion located around the nozzle.
- control is performed in a direction in which the nozzle tip temperature is maintained as much as possible, and in a direction in which the temperature of the portion located around the nozzle is reduced as much as possible.
- it is only necessary to take at least one of a measure for slowing down the nozzle tip temperature drop rate and a measure for improving the temperature drop rate of the portion located around the nozzle.
- the control unit calculates a nozzle tip temperature decrease rate based on the nozzle heat receiving amount, calculates a dew point arrival time based on the decrease rate, and whether or not condensation has occurred at the nozzle tip based on the dew point arrival time Can be judged.
- the control unit can perform racing execution control in the control for reducing the nozzle heat dissipation rate. Further, the control unit can perform idle extension control in the control for reducing the nozzle heat dissipation rate. Furthermore, the control unit may increase the idle speed in the idle extension control.
- the amount of heat received by the nozzle can be increased by performing racing execution control, idle extension control, and measures for increasing the idle speed.
- the amount of heat received by the nozzle increases, the subsequent heat release rate of the nozzle becomes slow, and the rate of decrease in the nozzle tip temperature decreases. That is, the nozzle tip temperature is unlikely to decrease.
- the dew point arrival time can be lengthened and dew condensation at the nozzle tip can be suppressed.
- the control unit can improve the piston temperature decreasing rate in the control to improve the temperature decreasing rate of the portion located around the nozzle.
- the piston is selected as a portion located around the nozzle, and the piston dew point temperature arrival time is made earlier than the nozzle dew point temperature arrival time by improving the piston temperature decreasing rate. Thereby, dew condensation at the nozzle tip is avoided.
- the control unit can introduce cooling water in the radiator into the engine body in the control to improve the temperature decrease rate of the portion located around the nozzle, and can improve the cylinder bore wall temperature decrease rate.
- a bore wall is selected as a portion positioned around the nozzle, and the dew point temperature arrival time of the bore wall is made earlier than the nozzle dew point temperature arrival time by improving the rate of decrease in the bore wall temperature. Thereby, dew condensation at the nozzle tip is avoided.
- the control unit supplies the hot water in the heat storage tank to the cylinder head to which the injector is attached to thereby reduce the nozzle tip temperature decrease rate. It can be reduced, i.e. slowed down. As the amount of heat of the cylinder head to which the injector is mounted increases, the nozzle is difficult to dissipate heat. As a result, the nozzle tip temperature decreasing rate is slowed down. As a result, the dew point arrival time at the nozzle tip becomes longer, and condensation is less likely to occur at the nozzle tip.
- FIG. 1 is an explanatory diagram showing a schematic configuration of the internal combustion engine of the first embodiment.
- FIG. 2 is an explanatory view of an injector attached to the internal combustion engine.
- FIG. 3 is an explanatory diagram showing a state of a decrease in nozzle tip temperature after the internal combustion engine is stopped.
- FIG. 4 is a flowchart showing an example of control of the internal combustion engine of the first embodiment.
- FIG. 5 is an example of a map showing the condensation generation conditions.
- FIG. 6 is a flowchart showing an example of nozzle corrosion prevention control in the first embodiment.
- FIG. 7 is an explanatory diagram showing how the nozzle tip temperature changes due to racing.
- FIG. 8 is a flowchart illustrating an example of nozzle corrosion prevention control according to the second embodiment.
- FIG. 9A and 9B are graphs showing changes in the nozzle tip temperature due to idle extension.
- FIG. 10 is a block diagram showing the main part of the internal combustion engine of the third embodiment.
- FIG. 11 is a flowchart illustrating an example of nozzle corrosion prevention control according to the third embodiment.
- FIG. 12 is an explanatory view schematically showing a state of piston cooling in the third embodiment.
- 13A and 13B are graphs showing the effect of piston cooling.
- FIG. 14 is an explanatory view schematically showing the main part of the internal combustion engine of the fourth embodiment.
- FIG. 15 is a flowchart illustrating an example of nozzle corrosion prevention control according to the fourth embodiment.
- FIGS. 16A and 16B are graphs showing the effect of introducing the first radiator cooling water.
- FIG. 17 is an explanatory view schematically showing the main part of the internal combustion engine of the fifth embodiment.
- FIG. 18 is a flowchart illustrating an example of nozzle corrosion prevention control according to the fifth embodiment.
- FIG. 19 is an explanatory view schematically showing the main part of the internal combustion engine of the sixth embodiment.
- FIG. 20 is a flowchart illustrating an example of nozzle corrosion prevention control according to the sixth embodiment.
- FIG. 21 is an explanatory view showing a state in which hot water is supplied to a cylinder head provided in the internal combustion engine of the sixth embodiment.
- FIG. 1 is an explanatory diagram showing a schematic configuration of the internal combustion engine 100 of the first embodiment.
- a fuel injection device 1 is incorporated in the internal combustion engine 100.
- the internal combustion engine 100 is an internal combustion engine that performs in-cylinder injection, more specifically, a diesel internal combustion engine.
- the internal combustion engine 100 has four cylinders.
- the internal combustion engine 100 includes an engine body 101 including a cylinder head 101a and a cylinder block 101b, and the engine body 101 includes # 1 cylinder to # 4 cylinder.
- the fuel injection device 1 is incorporated in the internal combustion engine 100.
- the fuel injection device 1 includes # 1 injectors 107-1 to # 4 injectors 107-4 corresponding to # 1 cylinder to # 4 cylinders.
- the # 1 cylinder is equipped with a # 1 injector 107-1 and the # 2 cylinder is equipped with a # 2 injector 107-2.
- the # 3 cylinder is equipped with a # 3 injector 107-3, and the # 4 cylinder is equipped with a # 4 injector 107-4.
- # 1 injector 107-1 to # 4 injector 107-4 are connected to common rail 120, and high-pressure fuel is supplied from common rail 120.
- Each injector 107 is attached to a cylinder head 101a.
- Each injector 107 exchanges heat with the cylinder head 101a via the seat portion.
- the internal combustion engine 100 includes an intake manifold 102 and an exhaust manifold 103 attached to the engine body 101.
- An intake pipe 104 is connected to the intake manifold 102.
- An exhaust pipe 105 is connected to the exhaust manifold 103 and one end of an EGR passage 108 is connected. The other end of the EGR passage 108 is connected to the intake pipe 104.
- An EGR cooler 109 is provided in the EGR passage 108.
- the EGR passage 108 is provided with an EGR valve 110 that controls the flow state of the exhaust gas.
- An air flow meter 106 is connected to the intake pipe 104.
- the air flow meter 106 is electrically connected to the ECU 111.
- the ECU 111 is electrically connected to an injector 107-i (i represents a cylinder number), specifically, # 1 injector 107-1 to # 4 injector 107-4.
- the ECU 111 corresponds to a control unit and performs various controls that will be described in detail later.
- the ECU 111 is electrically connected to an NE sensor 112 that measures the rotational speed of the internal combustion engine, a water temperature sensor 113 that measures the coolant temperature, a fuel temperature sensor 114 that measures the temperature of the fuel, and a crank angle sensor 115. .
- the ECU 111 also stores an EGR rate map, a dew condensation determination map, and other maps. The ECU 111 performs various controls around the internal combustion engine.
- the injector 107 includes a nozzle 107a at the tip.
- the nozzle 107a is provided with a nozzle hole. If condensed water containing an acid component is condensed on the tip of the nozzle 107a and adheres, corrosion may occur. If the periphery of the nozzle hole corrodes, the nozzle hole diameter may change. If the nozzle hole diameter changes, it will affect proper fuel injection. Therefore, the ECU 111 determines whether or not condensation has occurred and performs nozzle corrosion prevention control.
- the injector 107 is attached to the cylinder head 101a.
- the state of the nozzle tip temperature decrease after engine stop will be described.
- the solid line and the alternate long and short dash line indicate the transition of the nozzle tip temperature before and after the engine is stopped.
- the solid line and the alternate long and short dash line match the nozzle tip temperature when the engine is stopped.
- the rate at which the nozzle tip temperature decreases after the engine stops is slower on the solid line than on the one-dot chain line.
- the time t2 at which the nozzle tip temperature reaches the dew point indicated by the solid line is longer than the time t1 at which the nozzle tip temperature reaches the dew point indicated by the alternate long and short dash line.
- a longer dew point arrival time increases the possibility of condensation at portions other than the nozzle tip, which is advantageous in terms of preventing nozzle corrosion.
- the nozzle tip temperature when the engine is stopped is the same, the nozzle tip temperature decrease rate is different because the amount of received nozzle heat before the engine is stopped is different.
- the amount of heat received around the nozzle can be included in the amount of heat received by the nozzle. That is, the amount of heat received by the nozzle can include the amount of heat received by the cylinder head 101a to which the injector 107 is attached. Referring to FIG.
- FIG. 4 is a flowchart showing an example of control of the internal combustion engine 100.
- FIG. 5 is an example of a map showing the condensation generation conditions.
- FIG. 6 is a flowchart showing an example of nozzle corrosion prevention control of the internal combustion engine 100.
- FIG. 7 is an explanatory diagram showing a state in which the nozzle tip temperature changes due to the racing performed as nozzle corrosion prevention control.
- the internal combustion engine 100 is controlled mainly by the ECU 111 functioning as a control unit.
- step S1 a calculation for estimating the nozzle tip temperature Tnzl is performed.
- the nozzle tip temperature Tnzl is a point in time, that is, an instantaneous nozzle tip temperature.
- the nozzle tip temperature Tnzl is calculated and estimated by the following Equation 1.
- Tnzl F (NE ⁇ IT ⁇ TQ) ⁇ f (Tw ⁇ Tf) Equation 1
- NE Engine speed IT: Injection timing
- TQ Injection amount
- Tf Water temperature
- step S2 a calculation for estimating the nozzle heat receiving amount Q is performed.
- the nozzle heat receiving amount Q can be obtained as a value obtained by integrating the instantaneous nozzle tip temperature Tnzl calculated in step S1 for a certain period ⁇ .
- the nozzle heat receiving amount Q is calculated and estimated by the following formula 2, for example.
- the fixed period ⁇ is a period that can be arbitrarily set based on the matching conditions.
- Q ⁇ Tnzl Equation 2
- step S3 performed subsequent to step S2, the nozzle heat receiving amount Q calculated in step S2 is stored in the ECU 111.
- step S4 which is performed subsequent to step S3, an ignition off command (IG OFF) is confirmed, and the process proceeds to step S5.
- step S5 the nozzle tip temperature Tnzl and the nozzle heat receiving amount Q are read out.
- the nozzle tip temperature Tnzl to be read is a value at the time when the ignition is turned off. It should be noted that the point in time when the ignition is turned off does not mean exactly one specific point in time but can be one point in the period before and after the timing when the ignition is turned off. For example, it may be a point in time when the internal combustion engine 100 is stopped by turning off the ignition.
- step S6 the nozzle tip temperature decrease rate v is calculated based on the nozzle tip temperature Tnzl and the nozzle heat receiving amount Q read in step S5.
- the decrease rate v is calculated by the following Equation 3.
- v f (Tnzl ⁇ Q) Equation 3
- step S7 the dew point arrival time t is calculated based on the nozzle tip temperature Tnzl read in step S5 and the decrease rate v calculated in step S6.
- step S8 which is performed subsequent to step S7, it is determined whether or not the dew point arrival time t is equal to or less than a predetermined threshold value a.
- the threshold value a is a value determined by adaptation for each actual machine as a value for determining whether or not condensation occurs at the nozzle tip. If the dew point arrival time t is longer than the threshold value a, it is determined that the occurrence of condensation at the nozzle tip is avoided.
- step S8 If it is determined No in step S8, the process ends. That is, when the dew point arrival time t is longer than the threshold value a, it is considered that condensation occurs at a location other than the nozzle tip and that condensation at the nozzle tip is avoided, so no special nozzle corrosion prevention measures are required. It is. On the other hand, when it is determined Yes in step S8, the process proceeds to step S9 and nozzle corrosion prevention control is performed.
- the nozzle corrosion prevention control is a subroutine, which will be described in detail later.
- FIG. 5 is an example of a map showing the dew condensation occurrence conditions.
- the nozzle heat receiving amount Q is taken into account, condensation may occur at the nozzle tip even if the nozzle tip temperature Tnzl at a temporary point, for example, when the ignition is off, is high.
- the nozzle tip temperature Tnzl at the time when the ignition is turned off is low, condensation may be avoided at the tip of the nozzle if the amount of heat Q received is large. Note that it may be determined whether the nozzle corrosion prevention control needs to be executed based on a map as shown in FIG.
- FIG. 6 is a flowchart showing an example of the nozzle corrosion prevention control (control for lowering the nozzle heat dissipation speed) of the internal combustion engine 100 as described above. Specifically, it is an example of racing execution control.
- step S9a1 the amount of heat Qr necessary for inhibiting corrosion is calculated.
- the amount of heat Qr is calculated by the following equation 5 as an example.
- Qr f (Tnzl) Formula 5
- Tnzl uses the value read in step S5 in the flowchart shown in FIG.
- the amount of heat Qr can be obtained as the amount of heat for entering the condensation avoidance region (OK region) by fitting the nozzle tip temperature Tnzl to the map shown in FIG.
- step S9a2 the heat shortage ⁇ Q is calculated.
- ⁇ Q is calculated by Equation 6 below.
- ⁇ Q f (Q ⁇ Qr) Equation 6
- Q uses the value read in step S5 in the flowchart shown in FIG.
- step S9a3 calculation is performed to determine the accelerator opening degree ⁇ and the number of times n of racing.
- step S9a4 racing is actually performed with no load. Changes in the nozzle tip temperature Tnzl due to racing will be described with reference to FIG. For example, when the nozzle tip temperature Tnzl is Tnzl1 and is in the state indicated by a1 in FIG. 7, the amount of heat is deficient by ⁇ Q1 in order to escape from the condensation generation region (NG region) and enter the condensation avoidance region (OK region). To do. Assuming that the amount of heat when racing once with the determined accelerator opening ⁇ is dQ, the number of times of racing is ⁇ Q ⁇ dQ.
- the first racing is performed at 100% of the opening ⁇ .
- the state indicated by a2 in FIG. 7 is obtained.
- the second racing is performed, for example, at 70% of the opening degree ⁇ so as to exceed 0.5.
- the nozzle tip temperature Tnzl is Tnzl2 and is in a state indicated by b1 in FIG. 7, the amount of heat to escape from the condensation generation region (NG region) and enter the condensation avoidance region (OK region) is ⁇ Q2 is insufficient.
- the amount of heat when racing once with the determined accelerator opening ⁇ is dQ
- the number of times of racing is ⁇ Q ⁇ dQ.
- the first racing is performed at 80% or more of the opening degree ⁇ . Thereby, it will be in the state shown by b2 in FIG. 7, and it can escape to an OK area
- the accelerator opening degree ⁇ is increased, the amount of increase in the nozzle heat receiving amount Q per one time can be increased, but an appropriate accelerator opening degree ⁇ considering noise and the like is set.
- the amount of heat Q received by the nozzle can be increased by performing the racing execution control.
- the nozzle heat dissipation rate of the injector is reduced.
- the rate of decrease v of the nozzle tip temperature Tnzl decreases, and the dew point arrival time t at the nozzle tip becomes longer. Thereby, dew condensation can be avoided at the nozzle tip.
- FIG. 8 is a flowchart showing an example of control of the internal combustion engine 100 of the second embodiment, specifically, idle extension control.
- 9A and 9B are graphs showing changes in the nozzle tip temperature due to idle extension.
- the second embodiment is different from the first embodiment in the content of nozzle corrosion prevention control (control that lowers the nozzle heat dissipation speed) performed by the ECU 111.
- idle extension control is performed instead of the racing execution control in the first embodiment. That is, the contents of steps S1 to S8 in the flowchart shown in FIG. 4 are the same as those in the first embodiment. Since the basic configuration of the internal combustion engine 100 is the same as that of the first embodiment, a detailed description thereof is omitted.
- step S9b1 the ECU 111 calculates a difference ⁇ t between the dew point arrival time t and the threshold value a.
- ⁇ t is calculated by Equation 7 below.
- ⁇ t f (t ⁇ a) Equation 7
- step S9b2 which is subsequently performed, the nozzle tip temperature increase amount ⁇ Tnzl is calculated.
- the nozzle tip temperature increase amount ⁇ is calculated based on the difference ⁇ t.
- step S9b3 the idle extension time ⁇ tille is calculated based on the nozzle tip temperature increase amount ⁇ .
- step S9b4 it is determined whether or not ⁇ tidle calculated in step S9b3 is equal to or less than a predetermined threshold value tmax.
- the threshold value tmax is a value defined as the longest time allowed as the idle extension time.
- the threshold value tmax can be determined in consideration of noise or the like, for example.
- step S9b4 the process proceeds to step S9b5, and idle extension of time ⁇ tidle is performed.
- the idle extension measure is performed after confirming that the vehicle gear is in the neutral (N) or parking (P) state and that the side brake is applied.
- step S9b4 the process proceeds to step S9b6.
- step S9b6 the idle speed is increased.
- step S9b7 idle extension is performed for time tref in consideration of the increased idle rotational speed.
- step S9b8 After performing the idle extension in steps S9b5 and S9b7, it is determined in step S9b8 whether the necessary temperature increase has been completed. If it is determined Yes in step S9b8, the process ends (end). On the other hand, when it is determined No, the process proceeds to step S9b9 to perform injection after engine stop. If condensation at the nozzle tip cannot be avoided despite increasing the idle speed, avoid excessive idol extension and attach fuel to the nozzle tip to prevent nozzle corrosion. . After step S9b9, the process ends (END).
- FIG. 9A shows a change in the nozzle tip temperature due to idle extension when the nozzle tip temperature Tnzl at the time when the ignition is off is Tnzl1.
- FIG. 9B shows the change in the nozzle tip temperature due to idle extension when the nozzle tip temperature Tnzl at the time of ignition off is Tnzl2.
- ⁇ tidle falls within the threshold value tmax even at the normal idling speed. For this reason, the nozzle tip temperature Tnzl can escape to the condensation avoidance region (OK region) by performing the idling extension of ⁇ tilde.
- ⁇ tidle exceeds the threshold value tmax at the normal idle speed. Therefore, the idle speed is increased. Then, by performing idle extension for time tref, the nozzle tip temperature Tnzl can escape to the condensation avoidance region (OK region).
- the nozzle heat receiving amount Q can be increased by performing idle extension control.
- the nozzle heat dissipation rate of the injector is reduced.
- the rate of decrease v of the nozzle tip temperature Tnzl decreases, and the dew point arrival time t at the nozzle tip becomes longer. Thereby, dew condensation can be avoided at the nozzle tip.
- FIG. 10 is a block diagram showing a main part of the internal combustion engine 100 of the third embodiment.
- FIG. 11 is a flowchart showing an example of control of the internal combustion engine 100 of the third embodiment.
- FIG. 12 is an explanatory view schematically showing a state of piston cooling in the third embodiment.
- 13A and 13B are graphs showing the effect of piston cooling.
- the internal combustion engine 100 of the third embodiment includes an electric oil pump 121 electrically connected to the ECU 111 as a main part thereof. As shown in FIG. 12, the electric oil pump supplies oil to an oil jet 122 that cools the piston 101c accommodated in the cylinder block 101b. The oil jet 122 is provided for each cylinder, and injects oil toward the cooling channel 101c1 included in the piston 101c to cool the piston 101c.
- the internal combustion engine 100 includes a crank position control device 123 that can stop the piston at an arbitrary position.
- the crank position control device 123 is electrically connected to the ECU 111, and can rotate the crank by a drive unit that operates according to a command from the ECU 111 to arbitrarily change the piston position.
- step S9c1 a command is issued to the crank position control device 123, and the piston stop position is controlled while referring to the crank angle detected by the crank angle sensor 115. Specifically, the four-cylinder pistons 101c are all stopped at the same position. Thereby, the oil injection by the oil jet 122 can be performed equally to all the pistons 101c, and the pistons 101c can be uniformly cooled.
- step S9c2 the electric oil pump 121 is turned on, the oil is actually injected from the oil jet 122, and the piston 101c is cooled.
- the reason why the electric oil pump 121 is employed is that the oil jet 122 can be operated even after the internal combustion engine 100 is stopped.
- step S9c3 it is determined whether the piston temperature has become lower than the dew point temperature.
- the piston temperature may be directly measured.
- the relationship between the drive time of the electric oil pump 121 and the piston temperature drop may be grasped in advance, and the drive time of the electric oil pump 121 may be managed.
- step S9c4 the electric oil pump 121 is turned off, and the process ends.
- step S9c3 is repeated.
- the piston temperature is set to be equal to or lower than the dew point temperature before the nozzle tip temperature Tnzl. This avoids condensation at the nozzle tip.
- oil is suitable for piston cooling because it has a lower specific heat than water and has a higher cooling effect than water.
- the piston temperature is reduced as shown in FIG. 13 (B) by cooling the piston. It can be set as the state which reaches
- the determination as to whether or not condensation occurs at the nozzle tip is the same as in the first embodiment. That is, steps S1 to S8 in the flowchart shown in FIG. 4 are the same as those in the first embodiment, but whether or not condensation occurs at the nozzle tip is determined by comparing the nozzle tip temperature Tnzl and the piston temperature. You can also. That is, it can be determined that condensation occurs at the nozzle tip when the nozzle tip temperature Tnzl is lower than the piston temperature.
- FIG. 14 is an explanatory view schematically showing a main part of the internal combustion engine 100 of the fourth embodiment.
- FIG. 15 is a flowchart showing an example of control of the internal combustion engine 100 of the fourth embodiment, specifically, cooling water introduction control.
- FIGS. 16A and 16B are graphs showing the effect of introducing the first radiator cooling water.
- the internal combustion engine 100 includes a first radiator 130 that cools cooling water flowing through the engine body 101.
- the first radiator 130 is connected to a water jacket provided in the engine body 101 by a first flow path 131.
- the first flow path 131 allows cooling water to flow from the engine body 101 side to the first radiator 130 side.
- a first temperature sensor 132 is attached to the first flow path 131 on the side close to the engine body 101.
- a second temperature sensor 133 is attached to the first flow path 131 on the side close to the first radiator 130.
- the first temperature sensor 132 acquires the temperature of the cooling water flowing through the engine body 101 (engine water temperature).
- the second temperature sensor 133 acquires the temperature of the cooling water in the first radiator (first radiator water temperature).
- Both the first temperature sensor 132 and the second temperature sensor 133 are electrically connected to the ECU 111.
- the first radiator 130 is connected to the engine body 101 by the second flow path 134.
- the second flow path 134 allows cooling water to flow from the first radiator 130 side to the engine body 101 side.
- An electric valve 135 and an electric water pump 136 are disposed in the second flow path 134.
- the electric valve 135 and the electric water pump 136 are electrically connected to the ECU 111.
- a bypass flow path 137 branched from the first flow path 131 is connected to the electric valve 135.
- step S9d1 it is determined whether or not the engine water temperature acquired by the first temperature sensor 132 is higher than the first radiator water temperature acquired by the second temperature sensor 133.
- the process proceeds to step S9d2, where the electric water pump 136 is operated and the electric valve 135 is opened. That is, the cooling water in the first radiator 130 having a low temperature is introduced into the engine body 101. As a result, the rate of temperature decrease of the cylinder bore wall 101b1 is improved.
- step S9d2 the process returns to step S9d1 again and the process is repeated.
- step S9d3 the process proceeds to step S9d3, the electric water pump 136 is stopped, and the electric valve 135 is closed.
- step S9d1 there are cases where the process of step S9d2 is performed and whether the process is not performed.
- the process of step S9d2 is performed, the nozzle corrosion prevention control is performed.
- step S9d3 the process ends (END).
- the cylinder bore wall temperature is set to be equal to or lower than the dew point temperature before the nozzle tip temperature Tnzl. This avoids condensation at the nozzle tip.
- the cylinder bore wall is cooled, as shown in FIG. 16 (B).
- the cylinder bore wall temperature can reach the dew point first.
- the determination as to whether or not condensation occurs at the nozzle tip is the same as in the first embodiment. That is, steps S1 to S8 in the flowchart shown in FIG. 4 are the same as those in the first embodiment, but the determination of whether or not dew condensation occurs at the nozzle tip is based on the nozzle tip temperature Tnzl and the cylinder bore wall temperature when the engine is stopped. It can also be done by comparison. For example, it can be determined that condensation occurs at the nozzle tip when the nozzle tip temperature Tnzl is lower than the cylinder bore wall temperature + ⁇ ° C.
- FIG. 17 is an explanatory view schematically showing the main part of the internal combustion engine 100 of the fifth embodiment.
- FIG. 18 is a flowchart showing an example of control of the internal combustion engine 100 of the fifth embodiment, specifically, cooling water introduction control.
- the internal combustion engine 100 includes the first radiator 130 and the first flow path 131 described in the fourth embodiment.
- a second flow path 134 is also provided.
- a temperature-sensitive thermostat 138 is provided instead of the electric valve 135 provided in the fourth embodiment.
- a mechanical water pump 139 is provided instead of the electric water pump 136.
- the internal combustion engine 100 further includes a second radiator 141 that cools the cooling water introduced into the water-cooled intercooler (I / C) 140.
- the second radiator 141 is connected to a water jacket provided in the engine main body 101 by a third flow path 142.
- the third flow path 142 flows cooling water from the second radiator 141 side to the engine body 101 side.
- an electric water pump 143 and a first electric valve 144 are arranged in the second radiator 141.
- the second radiator 141 is connected to the water-cooled intercooler 140 through the fourth flow path 145.
- the fourth flow path 145 allows the cooling water to flow from the water cooling intercooler 140 side to the second radiator side.
- the fourth flow path 145 is connected to the engine body 101 by the fifth flow path 147.
- the fifth flow path 147 allows cooling water to flow from the engine body 101 side to the fourth flow path 145 side.
- a second electric valve 146 is disposed in the fifth flow path 147.
- a first temperature sensor 148 is mounted between the second radiator 141 and the electric water pump 143 in the third flow path 142.
- a second temperature sensor 149 is mounted between the engine body 101 and the second electric valve 146 in the fifth flow path 147.
- the first electric valve 144 is connected to the water-cooled intercooler 140 through the sixth flow path 150.
- the electric water pump 143, the first electric valve 144, the second electric valve 146, the first temperature sensor 148, and the second temperature sensor 149 are each electrically connected to the ECU 111.
- the first temperature sensor 148 obtains the temperature of the cooling water in the second radiator (second radiator water temperature).
- the second temperature sensor 149 acquires the temperature of the cooling water flowing through the engine body 101 (engine water temperature).
- step S9e1 it is determined whether the engine water temperature acquired by the second temperature sensor 149 is higher than the second radiator water temperature acquired by the first temperature sensor 148.
- step S9e2 the electric water pump 143 is operated, the first electric valve 135 is opened, and the second electric valve 146 is closed. That is, the cooling water in the second radiator 141 having a low temperature is introduced into the engine body 101. As a result, the rate of temperature decrease of the cylinder bore wall 101b1 is improved.
- step S9e2 the process returns to step S9e1 again, and the process is repeated.
- step S9e3 the electric water pump 143 is stopped, the first electric valve 135 is closed, and the second electric valve 146 is opened.
- step S9e2 there are cases where the process in step S9e2 is performed and cases where the process is not performed.
- the nozzle corrosion prevention control is performed.
- step S9d3 the process ends (END).
- the cylinder bore wall temperature is set to be equal to or lower than the dew point temperature before the nozzle tip temperature Tnzl. This avoids condensation at the nozzle tip.
- cooling water in the second radiator 141 through which cooling water having a temperature lower than that of the first radiator 130 circulates is introduced into the engine body 101. For this reason, compared with 4th Embodiment, it is easy to reduce cylinder bore wall temperature.
- FIG. 19 is an explanatory view schematically showing main parts of the internal combustion engine 100 of the sixth embodiment.
- FIG. 20 is a flowchart showing an example of control of the internal combustion engine 100 of the sixth embodiment, specifically, hot water flow control.
- FIG. 21 is an explanatory diagram showing a state in which hot water is supplied to a cylinder head 101a included in the internal combustion engine 100 of the sixth embodiment.
- the internal combustion engine 100 includes a flow path 151 through which cooling water that circulates through a water jacket provided therein.
- the cooling water circulation channel 151 includes an in-head channel 151a that flows in the cylinder head 101a and an in-block 101b that flows in the cylinder block 101b.
- a radiator 150, a thermostat valve 152, and a water pump 139 are disposed in the cooling water circulation passage 151.
- a bypass flow path 153 that bypasses the radiator 150 is connected to the thermostat valve 152.
- the internal combustion engine 100 includes a hot water circulation channel 154.
- the hot water circulation channel 154 shares the in-head channel 151a.
- An electric water pump 155 and a heat storage tank 156 are disposed in the hot water circulation channel 154.
- a first temperature sensor 157 is attached to the heat storage tank 156.
- the first temperature sensor 157 acquires the temperature of the hot water in the heat storage tank 156.
- a second temperature sensor 158 is attached to the cylinder head 101a.
- the second temperature sensor 158 is electrically connected to the ECU 111, and the second temperature sensor 158 is electrically connected to the ECU 111.
- the electric water pump 155 is electrically connected to the ECU 111.
- step S9f1 the engine water temperature and the temperature of the hot water in the heat storage tank 156 are acquired.
- the in-cylinder state of the engine main body 101 is grasped from the engine water temperature acquired by the second temperature sensor 158.
- step S9f2 the amount of heat to be applied to the injector 107 is calculated from the state in the cylinder of the engine body in order to avoid condensation at the nozzle tip. Then, a hot water supply amount commensurate with the amount of heat is calculated. In step S9f3, the electric water pump 155 is operated for a time corresponding to the calculated hot water supply amount.
- This increases the amount of heat of the cylinder head 101a and increases the nozzle tip temperature.
- the rate at which the nozzle tip temperature Tnzl decreases can be reduced.
- the temperature of locations other than the nozzle tip, for example, the cylinder bore wall and the piston is relatively lowered, and the cylinder bore wall temperature and the piston temperature become equal to or lower than the dew point temperature before the nozzle tip temperature Tnzl.
- dew condensation at the nozzle tip is avoided.
- Fuel Injection Device 100 Internal Combustion Engine 101 Engine Body 102 Intake Manifold 103 Exhaust Manifold 104 Intake Pipe 105 Exhaust Pipe 107 Injector 111 ECU 122 Oil Jet 130 First Radiator 141 Second Radiator 156 Heat Storage Tank
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- General Physics & Mathematics (AREA)
- Immunology (AREA)
- Pathology (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
- Fuel-Injection Apparatus (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Abstract
Description
図1は第1実施形態の内燃機関100の概略構成を示す説明図である。内燃機関100には、燃料噴射装置1が組み込まれている。内燃機関100は、筒内噴射を行う内燃機関、より具体的にはディーゼル内燃機関である。内燃機関100は4気筒である。内燃機関100は、シリンダヘッド101aとシリンダブロック101bを備えたエンジン本体101を備え、そのエンジン本体101に♯1気筒~♯4気筒を備える。燃料噴射装置1は、この内燃機関100に組み込まれている。燃料噴射装置1は、♯1気筒~♯4気筒に対応して、♯1インジェクタ107-1~♯4インジェクタ107-4を備える。具体的に、♯1気筒には、♯1インジェクタ107-1が装着され、♯2気筒には♯2インジェクタ107-2が装着されている。♯3気筒には♯3インジェクタ107-3が装着され、♯4気筒には♯4インジェクタ107-4が装着されている。♯1インジェクタ107-1~♯4インジェクタ107-4はそれぞれコモンレール120に接続され、コモンレール120から高圧の燃料が供給される。各インジェクタ107は、シリンダヘッド101aに装着されている。各インジェクタ107は、シート部を介してシリンダヘッド101aとの間で熱の授受を行う。
Tnzl
=f(NE・IT・TQ)-f(Tw・Tf) 式1
NE:エンジン回転数 IT:噴射時期 TQ:噴射量
Tw:水温 Tf:燃温
Q=ΣTnzl 式2
v=f(Tnzl・Q) 式3
t=f(Tnzl・v) 式4
Qr=f(Tnzl) 式5
ΔQ=f(Q・Qr) 式6
つぎに、第2実施形態につき、図8、図9を参照しつつ説明する。図8は第2実施形態の内燃機関100の制御、具体的に、アイドル延長制御の一例を示すフロー図である。図9(A)(B)はアイドル延長によるノズル先端温度の変化を示すグラフである。
Δt=f(t・a) 式7
ΔTnzl=f(Δt) 式8
Δtidle=f(ΔTnzl) 式9
つぎに、第3実施形態につき、図10乃至図13を参照しつつ説明する。図10は第3実施形態の内燃機関100の主要部を示すブロック図である。図11は第3実施形態の内燃機関100の制御の一例を示すフロー図である。図12は第3実施形態におけるピストン冷却の様子を模式的に示す説明図である。図13(A)、(B)はピストン冷却の効果を示すグラフである。
つぎに、第4実施形態につき、図14乃至図16(A)、(B)を参照しつつ説明する。図14は第4実施形態の内燃機関100の主要部を模式的に示す説明図である。図15は第4実施形態の内燃機関100の制御、具体的に冷却水導入制御の一例を示すフロー図である。図16(A)、(B)は第1ラジエータ冷却水導入の効果を示すグラフである。
つぎに、第5実施形態につき、図17及び図18を参照しつつ説明する。図17は第5実施形態の内燃機関100の主要部を模式的に示す説明図である。図18は第5実施形態の内燃機関100の制御、具体的に冷却水導入制御の一例を示すフロー図である。
つぎに、第6実施形態につき、図19乃至図21を参照しつつ説明する。図19は第6実施形態の内燃機関100の主要部を模式的に示す説明図である。図20は第6実施形態の内燃機関100の制御、具体的に温水流通制御の一例を示すフロー図である。図21は第6実施形態の内燃機関100が備えるシリンダヘッド101aに温水を供給する様子を示す説明図である。
101 エンジン本体 102 インテークマニホールド
103 エキゾーストマニホールド 104 吸気管
105 排気管 107 インジェクタ
111 ECU 122 オイルジェット
130 第1ラジエータ 141 第2ラジエータ
156 蓄熱タンク
Claims (9)
- イグニションがオフとされた時点におけるインジェクタのノズル受熱量と前記インジェクタのノズル先端温度に基づいてノズル先端部における結露発生の有無を判定する制御部を備えた内燃機関。
- 前記制御部は、ノズル先端部に結露が発生すると判断したときにノズル放熱速度を低下させる制御、ノズルの周囲に位置する部分の温度の低下速度を向上させる制御の少なくとも一方の制御を行う請求項1に記載の内燃機関。
- 前記制御部は、
前記ノズル受熱量に基づいてノズル先端温度の低下速度を算出するとともに前記ノズル先端温度の低下速度に基づいて露点到達時間を算出し、前記露点到達時間に基づいてノズル先端部における結露発生の有無を判断する請求項1又は2に記載の内燃機関。 - 前記制御部は、
前記ノズル放熱速度を低下させる制御において、レーシング実施制御を行う請求項2に記載の内燃機関。 - 前記制御部は、
前記ノズル放熱速度を低下させる制御において、アイドル延長制御を行う請求項2又は4に記載の内燃機関。 - 前記制御部は、
前記アイドル延長制御において、アイドル回転数を上昇させる請求項5に記載の内燃機関。 - 前記制御部は、
前記ノズルの周囲に位置する部分の温度の低下速度を向上させる制御において、ピストン温度の低下速度を向上させる請求項2、4乃至6のいずれか一項に記載の内燃機関。 - 前記制御部は、
前記ノズルの周囲に位置する部分の温度の低下速度を向上させる制御において、ラジエータ内の冷却水をエンジン本体に導入し、シリンダボア壁温度の低下速度を向上させる請求項2、4乃至7のいずれか一項に記載の内燃機関。 - 前記制御部は、
前記ノズル放熱速度を低下させる制御において、蓄熱タンク内の温水を前記インジェクタが装着されたシリンダヘッドへ供給して前記ノズル先端温度の低下速度を低下させる請求項2、4乃至8のいずれか一項に記載の内燃機関。
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BR112015017160-5A BR112015017160B1 (pt) | 2013-01-21 | 2014-01-15 | Motor de combustão interna |
US14/761,706 US9810165B2 (en) | 2013-01-21 | 2014-01-15 | Internal combustion engine |
EP14740300.0A EP2947302A4 (en) | 2013-01-21 | 2014-01-15 | COMBUSTION ENGINE |
RU2015129543A RU2606965C1 (ru) | 2013-01-21 | 2014-01-15 | Двигатель внутреннего сгорания |
CN201480005310.0A CN104937246B (zh) | 2013-01-21 | 2014-01-15 | 内燃机 |
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EP (1) | EP2947302A4 (ja) |
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WO2018203361A1 (ja) * | 2017-05-01 | 2018-11-08 | 日産自動車株式会社 | 内燃機関の制御方法及び内燃機関の制御装置 |
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JP6463139B2 (ja) * | 2015-01-09 | 2019-01-30 | 株式会社Subaru | エンジンの冷却制御装置 |
JP2017096181A (ja) * | 2015-11-25 | 2017-06-01 | トヨタ自動車株式会社 | 内燃機関の制御装置 |
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BR112015017160B1 (pt) | 2022-02-08 |
JP5895859B2 (ja) | 2016-03-30 |
BR112015017160A2 (ja) | 2020-01-28 |
JP2014139416A (ja) | 2014-07-31 |
CN104937246B (zh) | 2018-07-27 |
RU2606965C1 (ru) | 2017-01-10 |
US20150354475A1 (en) | 2015-12-10 |
CN104937246A (zh) | 2015-09-23 |
EP2947302A1 (en) | 2015-11-25 |
US9810165B2 (en) | 2017-11-07 |
EP2947302A4 (en) | 2016-03-02 |
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