JP4548183B2 - Control device for spark ignition engine - Google Patents

Description

  The present invention relates to a control device for a spark ignition engine, and more particularly, to a spark having an operation mode in which premixed compression auto-ignition combustion (HCCI) is performed, which is referred to as “compression auto-ignition” in this specification. The present invention relates to a control device for an ignition engine.

In a spark ignition type engine, an engine having intake air heating means for heating intake air in order to accelerate the compression self-ignition timing is known. For example, in the technique disclosed in Patent Document 1, when shifting from a high load operation in which forced ignition is performed by spark ignition to a low load operation in which compression self-ignition operation is performed, the temperature of the air-fuel ratio is increased by increasing the temperature of the mixture. On the other hand, when shifting from low load operation to high load operation, the pumping loss is reduced between the misfire region and the knocking region by lowering the temperature of the mixture and changing the air-fuel ratio to the rich side. Both reduction and knocking prevention are achieved.
JP 2003-269201 A

Incidentally, in order to execute the compression self-ignition operation on the low load side, it is necessary to considerably increase the in-cylinder temperature. However, if the in-cylinder temperature exceeds a predetermined temperature (for example, 250 ° C.), the maximum heat generation rate ((J / deg · m ³ ) MAX) is generated before the compression top dead center. There was a problem that reverse torque acts.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a control device for a spark ignition engine capable of performing a compression self-ignition operation with good fuel efficiency even in an operation region on a low load side.

In order to solve the above problems, the present invention provides a plurality of cylinders for burning an air-fuel mixture, in-cylinder heating means for increasing the in-cylinder temperature of each cylinder, operating state detecting means for detecting the operating state of the engine, and operating state In a control apparatus for a spark ignition gasoline engine, comprising: a control means for executing a compression self-ignition operation in a predetermined operating region by controlling the in-cylinder heating means based on detection by the detection means. Fuel injection means capable of controlling injection and ignition means for igniting a mixture of injected fuel and air are provided, and in a predetermined partial load operation region, the in-cylinder temperature of the operating cylinder is increased to perform compression self-ignition operation. In the partial load operation region, on the predetermined low load side, the reduced cylinder operation for operating only a part of the cylinders is executed, while in the partial load operation region exceeding the predetermined low load, the operation is performed. Said control means cylinder heating means such cylinders is increased, and controls the fuel injection means and the ignition means, the predetermined low-load side and the high load side of the switching point, knocking occurs by operating cylinders when the reduced-cylinder A control device for a spark ignition engine characterized by being set to a load that reaches a predetermined maximum heat generation rate with high frequency . In this aspect, the so-called compression self-ignition operation is executed in the partial load operation region, so that the fuel consumption and the exhaust performance can be improved. Further, in the operation region where the compression self-ignition operation is executed, the reduced cylinder operation is executed on the predetermined low load side, so the load per cylinder in operation is amplified, so that the in-cylinder temperature is relatively low. Even at low temperatures, combustion stability is improved. As a result, it becomes possible to realize compression self-ignition at a relatively low in-cylinder temperature in the engine low-load operation region where the compression self-ignition operation is most likely to become unstable. It is possible to avoid ignition and maintain fuel efficiency improvement in a low load operation region. On the other hand, when the operating state shifts to a high load side that is equal to or higher than a predetermined load, the operating rate of the cylinder is increased, so that knocking at a high load can be prevented. In addition, it is possible to use a driving range with good fuel efficiency. That is, as a result of intensive research by the present inventors, the knocking limit of the operating cylinder may occur at a certain maximum heat generation rate ((J / deg · m3) MAX) depending on a predetermined in-cylinder temperature and air-fuel ratio. all right. Therefore, by setting the switching point based on a predetermined maximum heat generation rate at which the frequency of occurrence of knocking by the operating cylinder increases, the operating range in which the compression self-ignition operation can be performed is extended to the high load side, and fuel efficiency is improved. This makes it possible to use a large number of operating areas.

  In a preferred embodiment, the predetermined low load side operation region is a warm idle operation. In this aspect, it is possible to improve the fuel consumption and the exhaust performance by the compression self-ignition from the idle operation region where the operation frequency is high.

  In a preferred embodiment, an external EGR device that recirculates a part of the burned gas to the intake passage is provided, and in the operation region in which the compression self-ignition operation is performed, the external EGR is introduced at least on the high load side, and the predetermined low In the operation region on the load side, the control means controls the external EGR device so as to stop the introduction of EGR gas. In this mode, during the compression self-ignition operation, the external EGR gas is introduced in the operation region on the high load side, so that an increase in the in-cylinder temperature due to the inert gas can be suppressed and knocking can be avoided. In addition, it is possible to expand the operating range in which compression self-ignition operation is possible to the high load side and maintain high fuel efficiency by stopping the EGR gas in the low load side operating region such as during idling operation. It becomes possible to do. Further, in this low load operation region, since the compression self-ignition operation is executed, it is possible to maintain high exhaust performance even if EGR gas is not introduced.

  In a preferred embodiment, the control means controls the external EGR device so that EGR gas is introduced during the compression self-ignition operation in which all cylinders are operating. In this aspect, the knocking limit at the time of the compression self-ignition operation can be expanded at a higher load.

  In a preferred embodiment, air-fuel ratio adjusting means for adjusting the air-fuel ratio by the control means is provided, and the forced ignition operation is executed on the higher load side than the partial load operation region, and the air-fuel ratio at the time of the compression self-ignition operation is the theoretical air-fuel ratio. The control means controls the air-fuel ratio adjusting means so that it becomes leaner than the fuel ratio. In this aspect, since the air-fuel ratio is set to be leaner than the stoichiometric air-fuel ratio in the operation region in which the compression self-ignition operation is executed, it is possible to achieve both avoidance of knocking and improvement of fuel consumption.

  As described above, according to the present invention, the reduced cylinder operation is executed on the predetermined low load side, and the combustion stability is improved even when the in-cylinder temperature is relatively low. There is a remarkable effect that it is possible to avoid premature ignition due to the increase and to maintain the improvement in fuel consumption in the low load operation region.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings.

  FIG. 1 is a configuration diagram illustrating a schematic configuration of a control device 10 according to an embodiment of the present invention, and FIG. 2 is a schematic cross-sectional view illustrating a structure of one cylinder of the four-cycle gasoline engine 20 according to FIG. .

  With reference to FIGS. 1 and 2, the illustrated control apparatus 10 includes a four-cycle gasoline engine 20 and a control unit 100 for controlling the engine 20.

  The engine 20 integrally includes a cylinder block 22 that rotatably supports the crankshaft 21 and a cylinder head 23 disposed on the upper portion of the cylinder block 22, and the cylinder block 22 and the cylinder head 23 include A plurality of cylinders 24 are provided.

  Each cylinder 24 is provided with a piston 26 connected to the crankshaft 21 via a connecting rod 25 and a combustion chamber 27 formed in the cylinder 24 by the piston 26. In the present embodiment, the geometric compression ratio of each cylinder 24 is set to 14.

  FIG. 3 is a schematic plan view showing the cylinder 24 in an enlarged manner.

  Referring to FIG. 3, a ceiling portion of combustion chamber 27 is formed for each cylinder 24 on the lower surface of cylinder head 23, and this ceiling portion has two inclined surfaces extending from the central portion to the lower end of cylinder head 23. It is a pent roof type.

  Two independent intake ports 28 and exhaust ports 29 are opened substantially symmetrically in the ceiling portion of the combustion chamber 27, and an intake valve 30 and an exhaust valve 31 are provided at the open ends of the ports 28 and 29. ing.

  A fuel injection valve 32 that receives a fuel injection pulse from the control unit 100 and injects fuel corresponding to the pulse width into the combustion chamber 27 is provided at the side of the combustion chamber 27.

  Referring also to FIG. 2, each cylinder 24 is provided with three spark plugs 34 that are fixed to the cylinder head 23 and emit a spark in the combustion chamber 27. The spark plugs 34 are arranged along the cylinder diameter parallel to the ridge line portion of the piston 26, the center one is arranged on the cylinder bore center Z, and the ones on both sides are arranged on the side edge of the combustion chamber 27. Each ignition plug 34 is connected to an ignition circuit 35 capable of controlling the ignition timing by electronic control. By controlling the ignition circuit 35 by the control unit 100, the ignition plug 34 is selectively ignited. To be controlled.

  Next, referring to FIG. 2, each of the intake valve 30 and the exhaust valve 31 of each cylinder 24 is provided with a known tappet unit 36. The tappet unit 36 is periodically driven by cams 37 a and 38 a of camshafts 37 and 38 of a valve mechanism provided in the cylinder head 23. The valve operating mechanism for the intake valve 30 is provided with a variable valve timing mechanism 40 that can change the opening / closing timing of the intake valve 30. The variable valve timing mechanism 40 has a valve according to the operating state over a first timing in which the intake valve opening timing is near the intake top dead center and a second timing in which the intake valve opening timing is advanced. The timing is changed.

  Next, referring to FIGS. 1 and 2, a branch intake pipe 43 of the intake manifold 42 is connected to the intake port 28 of the engine 20. The branch intake pipe 43 is provided for each cylinder 24 and is connected to the intake manifold 42 in a state where an equal-length intake path is formed. In the illustrated embodiment, each cylinder 24 is formed with a pair of intake ports 28, and the downstream end of the branched intake pipe 43 is bifurcated corresponding to the intake port 28 of each cylinder 24. Has been. An open / close valve 44 is provided at the upstream side merge portion of the branch intake pipe 43. The on-off valve 44 is embodied by a three-way solenoid valve, and is configured such that the actuator 45 can individually open and close the aggregate portion of the branch intake pipe 43 by a desired amount. On the other hand, a known swirl on / off valve 43a is provided at one branch portion of the branch intake pipe 43 branched into two branches as shown in FIG. The swirl on / off valve 43a is driven by an actuator 43b to open and close. When one of the branch portions of the branch intake pipe 43 is closed by the swirl on / off valve 43a, the swirl on / off valve 43a passes through the other branch. The swirl is generated in the combustion chamber 27 by the intake air, and the swirl is weakened as the swirl generation opening / closing valve 43a is opened.

  An intake passage 46 for introducing fresh air into the intake manifold 42 is connected to the upstream side of the intake manifold 42. A throttle valve 47 is provided in the intake passage 46. A three-way solenoid valve 48 is provided on the upstream side of the throttle valve 47, and a heater 50 as a cylinder heating means is provided in a bypass passage 49 connected to the three-way solenoid valve 48. Therefore, by switching the three-way solenoid valve 48, fresh fresh air can be introduced as it is into the intake manifold 42, or air heated by the heater 50 can be introduced into the intake manifold 42. .

  Next, as shown in FIG. 1, the exhaust port 29 is connected to a bifurcated branch exhaust pipe 51 formed in pairs for each cylinder 24. The downstream end of each branch exhaust pipe 51 is connected to the exhaust manifold 52. An exhaust passage 53 for discharging burned gas is connected to the exhaust manifold 52.

  Between the intake manifold 42 and the exhaust manifold 52, an external EGR system 60 for returning the exhausted burned gas to the intake manifold 42 is provided.

  The external EGR system 60 is connected to a recirculation passage 61 formed between the intake manifold 42 and the exhaust manifold 52, and includes an EGR cooler 62, an EGR valve 63, and an actuator 64 that drives the EGR valve 63. Valve system.

  FIG. 4 is a configuration diagram showing the configuration of the in-cylinder heating system 70 as the in-cylinder heating means according to the embodiment of FIG.

  Referring to the drawing, a heating passage 71 is branchedly connected to the intake passage 46. In the middle of the heating passage 71, a cooling water heat exchanger 72 and an exhaust heat exchanger 73 are connected.

  The heating passage 71 is for returning the heat absorbed through the heat exchangers 72 and 73 to the intake side. A branch pipe 71 a branched for each cylinder 24 is provided on the downstream side of the heating passage 71, and each branch pipe 71 a is connected to the intake-side port of the corresponding on-off valve 44.

  The cooling water heat exchanger 72 is connected to the water cooling system 74 of the engine 20 to absorb the heat absorbed by the cooling water returning from the engine 20 to the radiator (not shown) into the intake air passing through the heating passage 71. Is.

  The exhaust heat exchanger 73 is connected to the exhaust passage 53 of the engine 20 to absorb the heat of burned gas into the intake air passing through the heating passage 71. The exhaust heat exchanger 73 is disposed on the downstream side of the cooling water heat exchanger 72 in the heating passage 71.

  In the present embodiment, the above-described heater 50 and these heat exchangers 72 and 73 constitute the main part of the in-cylinder heating system 70.

  Referring to FIG. 1, in order to detect the operating state of engine 20, air flow sensor SW1 is provided in intake passage 46, and intake temperature sensor SW2 for predicting the in-cylinder temperature downstream of on-off valve 44. (See FIG. 2). The cylinder block 22 is provided with a crank angle sensor SW3 for detecting the rotation speed of the crankshaft 21 and an engine water temperature sensor SW4 for detecting the temperature of the cooling water (see FIG. 2). Further, the exhaust passage 53 is provided with an oxygen concentration sensor SW5 for controlling the air-fuel ratio. Further, the heater 50 and the exhaust heat exchanger 73 are provided with temperature sensors SW7 and SW8, respectively, and the temperature of the intake air in the bypass passage 49 heated by the heater 50 and the temperature of the intake air in the heating passage 71 are measured. It can be detected.

  The engine 20 is provided with a control unit 100 as control means. The control unit 100 includes an air flow sensor SW1, an intake air temperature sensor SW2, a crank angle sensor SW3, an engine water temperature sensor SW4, an oxygen concentration sensor SW5, an accelerator opening sensor SW6 for detecting engine load, and temperature sensors SW7 and SW8. Are connected as input elements. Each of these sensors SW1 to SW8 is a specific example of the driving state detection sensor in the present embodiment. On the other hand, the control unit 100 includes a variable valve timing mechanism 40, an actuator 43b of a swirl generating on-off valve 43a, an actuator 45 of an on-off valve 44, an actuator of a throttle valve 47, a three-way electromagnetic valve 48 in an intake passage 46, a heater 50, an external An actuator 64 of the EGR system 60 is connected as a control element.

  Referring to FIG. 1, a control unit 100 has a CPU 101, a memory 102, an interface 103, and a bus 104 for connecting these units 101 to 103. The control unit 100 operates according to programs and data stored in the memory 102. The operation state determination means for determining is functionally configured.

  FIG. 5 is a characteristic diagram illustrating an example of operation region setting for performing control according to the operation state according to the embodiment of FIG. 1.

  Referring to FIG. 5, in the illustrated embodiment, the engine speed N is set to execute the compression self-ignition operation in the partial load operation region D, and to execute the forced ignition operation by spark ignition in the remaining region. Has been.

In the operating region D to perform compression self-ignition operation, the operating region D ₁ of the predetermined low-load side, the reduced-cylinder operation in which only a part of the cylinders 24 is running is performed. By performing the reduced-cylinder operation in the operating region D ₁ of the the low load side, idling operation or the like, the combustion stability poor low load side, can be relatively increased load per cylinder running It is possible to improve the combustion stability without increasing the in-cylinder temperature T. In the illustrated example, since an in-line four-cylinder engine is employed, the second and third cylinders sandwiched between the cylinders 24 that are operated during the reduced-cylinder operation are selected. Thus, in the illustrated embodiment, it is possible to execute the compression self-ignition operation by effectively using the high-temperature side cylinder 24 that hardly dissipates heat.

On the other hand, in the operating region D ₂ of the high-load side than the predetermined load, all cylinders 24 compression-ignition operation and running is executed. Incidentally, it is taken up widely with higher load side of the operating region D, to more finely divide the operating range D _2, in multiple stages may be carried out reduced-cylinder operation. For example, in a V6, V8 type engine, a reduced cylinder operation in which only the second, third, and sixth cylinders are operated may be executed. Similarly, in the V12 type engine, a reduced cylinder operation in which only the sixth, ninth, and twelfth cylinders are operated may be executed.

  As a method of adjusting the in-cylinder temperature, the target in-cylinder temperature T based on the engine operating state and the intake air amount are stored in advance in the memory 102 as a control map, and the air flow sensor SW1, the intake air temperature sensor SW2, the accelerator opening sensor The values are read from the control map so that the in-cylinder temperature T and the target intake air amount are detected from the detected values of SW6 and temperature sensors SW7 and SW8, and the throttle valve 47, on-off valve 44, and three-way solenoid valve 48 are opened. This is achieved by adjusting the amount.

Next, a description will be given of a control factor for determining the scope of the operating region D _1.

  6 to 8 are graphs showing the relationship between the crank angle and the heat generation rate dQ / dθ, which are the basis of the control conditions set in the control unit 100. FIG. These graphs are obtained based on the research results of the present inventors, and a control map based on these graphs is stored in the memory 102 of the control unit 100. In each figure, the curve indicated by the broken line is a characteristic when the minimum fuel injection amount capable of compression self-ignition is set when the throttle is fully opened, and the curve indicated by the solid line is the air-fuel ratio up to the knocking limit at the same in-cylinder temperature T as the broken line The characteristic when the value is lowered is shown. Further, the reference numeral of the curve indicated by the solid line is obtained by adding a subscript to the reference numeral of the curve indicated by the broken line corresponding to the in-cylinder temperature T.

Referring to FIG. 6, when engine 20 is operated in a no-load state by compression self-ignition, in-cylinder temperature T needs to be set to T1 (= 270 ° C.). At this T1, the maximum heat generation rate (dQ / dθ) MAX is generated before the compression top dead center. Therefore, if the air-fuel ratio is lowered as it is, the reverse torque increases. Also, even at T2 (= 250 ° C), which is 20 ° C lower than T1, the maximum heat generation rate (dQ / dθ) MAX still occurs before the compression top dead center. Torque is generated. Next, referring to FIG. 7, when the load increases, the in-cylinder temperature T is T3 (= 225 ° C.), T4 (= 205 ° C.), T5 (= 190 ° C.), T6 (= 175 ° C.). , T7 (= 160 ° C.), the maximum heat release rate (dQ / dθ) MAX appears after compression top dead center. These characteristics, in the present embodiment, in the operating region D ₁ of the low-load side, by relatively increasing the engine load by executing a predetermined reduced-cylinder operation, compressed with a relatively low in-cylinder temperature T Self-ignition operation is possible.

Next, referring to FIG. 8, when the in-cylinder temperature characteristics T1 to T7 are overlapped, a peak is obtained when the heat generation rate dQ / dθ is approximately a predetermined value (about 80 J / deg · m ³ ). Yamagata knock limit curve will be drawn. In this embodiment, driving the boundary of the area D ₁ and the operation region D ₂ on the basis of the predetermined heat generation rate dQ / d [theta] (about 80J / deg · m ^3), in-cylinder air-fuel ratio of the operating cylinders is the stoichiometric air The air-fuel ratio to be set is set in a range that is less than λ = 2 in an operation state that is leaner than the fuel ratio and when the throttle is fully opened. In FIG. 8, the left straight line in the figure shows the combustion start timing at each in-cylinder temperature T1 to T7, and the right straight line shows the end of combustion with a combustion fluctuation rate of less than 5% (MFB = 95%). It represents the limit.

By the way, referring to FIG. 7 and FIG. 8, when the load state further increases and the in-cylinder temperature T continues to be lowered accordingly, the combustion of the air-fuel mixture delays the combustion start timing itself in proportion to the temperature drop, and the maximum The heat release rate (dQ / dθ) MAX gradually approaches the compression bottom dead center. Therefore, as shown in FIG. 8, at a predetermined low temperature T8 (= 150 ° C.), the air-fuel ratio capable of compression self-ignition becomes A / F = 30 (λ = 2), and the maximum heat generation rate (dQ / dθ) MAX However, the crank angle exceeds 15 °. Therefore, in this embodiment, in the case of naturally aspirated engines without external EGR, the air-fuel ratio in the boundary at the .lambda.2, determines the upper limit of the operating range D ₂ in FIG. 5, the upper limit of the operating region D ₂ In the high load operation region, the forced ignition operation by spark ignition is set to be executed.

  FIG. 9 is a graph showing the relationship between the net thermal efficiency (IMEP) and the indicated fuel consumption rate (ISFC) at 1500 rpm.

Referring to FIG. 9, in the operating region D _1, when operated by temporarily operate the all cylinders 24 in the absence of external EGR, illustrated fuel consumption rate, 200 become closer. In contrast, in the operating region D _1, if you perform a reduced-cylinder operation, the increase in the load per cylinder, the illustrated fuel consumption rate, is significantly reduced.

Further, as shown in the figure, when EGR gas is introduced in each of the operation regions D ₁ and D ₂ , the fuel consumption rate increases as the EGR gas ratio increases, and the fuel consumption increases as the load increases. The rate was found to be low. Therefore, in this embodiment, in the operating region D ₂ of the high-load side, at least in the high load side, by introducing external EGR, to improve the exhaust performance while preventing knocking in the slow combustion, homogeneous charge compression ignition The operation region D in which operation is possible is expanded to the high load side.

As described above, in the present embodiment, in the partial load operation region D, so-called compression self-ignition operation is executed, so that fuel efficiency and exhaust performance can be improved. Further, in the operation region D in which the compression self-ignition operation is performed, in the predetermined operation region D ₁ on the low load side, the reduced cylinder operation in which only some of the cylinders 24 are operated is performed. Since the load per one is amplified, the combustion stability is improved even if the in-cylinder temperature T is relatively low. As a result, the compression self-ignition operation can be realized at a relatively low in-cylinder temperature T in the low load operation region D ₁ in which the compression self-ignition operation is most likely to be unstable, so that the in-cylinder temperature T is increased. to avoid pre-ignition by, made to improve the fuel efficiency can be maintained at a low-load operation region D _1. On the other hand, when the operating state shifts to a high load side with a predetermined load or higher, the operating rate of the cylinder 24 is increased, so that knocking at a high load can be prevented.

Further, in the present embodiment, the operating region D ₁ of the said predetermined low load side is an idle operation of the warm. For this reason, in this embodiment, it becomes possible to improve the fuel consumption and the exhaust performance by the compression self-ignition from the idle operation region where the operation frequency is high.

In the present embodiment, an external EGR system 60 that recirculates a part of burned gas to the intake passage 46 is provided, and in the operation region in which the compression self-ignition operation is performed, the external EGR is introduced at least on the high load side. in the operating region D ₁ of the said predetermined low-load side, the control unit 100 to stop the introduction of the EGR gas is used to control the external EGR system 60. Therefore, in this embodiment, during the compression-ignition operation, the operating region D ₂ of the high-load side, by an external EGR gas is introduced to suppress the increase in the cylinder temperature T with an inert gas, knocking Therefore, it is possible to expand the operation region D in which the compression self-ignition operation is possible to the high load side, and the EGR gas is stopped in the operation region D ₁ on the low load side such as during idling operation. By doing so, it becomes possible to maintain high fuel efficiency. Also, in the operating region D ₁ of the the low load side, the compression-ignition operation is being performed, EGR gas even if it is not introduced, it is possible to maintain high exhaust performance.

  In the present embodiment, the control unit 100 controls the external EGR system 60 so that EGR gas is introduced during the compression self-ignition operation in which all the cylinders 24 are operating. For this reason, in this embodiment, it becomes possible to expand the knocking limit at the time of compression self-ignition operation at higher load.

In the present embodiment, the switching point between the operation region D ₁ and the operation region D ₂ reaches a predetermined maximum heat generation rate (dQ / dθ) MAX at which the frequency of occurrence of knocking by the operating cylinder increases in the case of reduced cylinders. It is set based on the load. For this reason, in this embodiment, it becomes possible to use many driving regions with good fuel efficiency.

  In the present embodiment, a throttle valve 47 is provided as an air-fuel ratio adjusting means for adjusting the air-fuel ratio by the control unit 100. On the higher load side than the partial load operation region D, forced ignition operation is performed and compression is performed. The control unit 100 controls the throttle valve 47 so that the air-fuel ratio during the self-ignition operation becomes leaner than the stoichiometric air-fuel ratio. For this reason, in the present embodiment, in the operation region D in which the compression self-ignition operation is executed, the air-fuel ratio is set to be leaner than the stoichiometric air-fuel ratio, so it is possible to achieve both avoidance of knocking and improvement of fuel consumption. .

As described above, according to the present embodiment, the reduced cylinder operation is executed on the predetermined low load side, and the relatively low in-cylinder temperature in the engine low load operation region D ₁ in which the compression self-ignition operation is most likely to become unstable. Since it becomes possible to realize compression self-ignition at T, it is possible to avoid premature ignition by increasing the in-cylinder temperature T and to maintain fuel efficiency improvement in the low load operation region D _1. Has an effect.

  The above-described embodiments are merely preferred specific examples of the present invention, and the present invention is not limited to the above-described embodiments. For example, as a method of introducing the external EGR, in addition to the method of operating the external EGR system 60 described above, the setting of the variable valve timing mechanism 40 is changed, and the valve opening timing of the intake valve 30 is changed to the valve opening timing of the exhaust valve 31. It may be a method of performing so-called negative overlap to overlap.

  It goes without saying that various modifications can be made within the scope of the claims of the present invention.

It is a block diagram which shows schematic structure of the control apparatus which concerns on one Embodiment of this invention. 2 is a schematic cross-sectional view showing the structure of one cylinder of the four-cycle gasoline engine according to FIG. 1. It is a plane schematic diagram expanding and showing a cylinder. It is a block diagram which shows the structure of the cylinder heating system which concerns on embodiment of FIG. It is a characteristic view which shows an example of the driving | operation area | region setting for performing control according to the driving | running state which concerns on embodiment of FIG. It is a graph which shows the relationship between the crank angle used as the basis of the control conditions set to a control unit, and a heat release rate. It is a graph which shows the relationship between the crank angle used as the basis of the control conditions set to a control unit, and a heat release rate. It is a graph which shows the relationship between the crank angle used as the basis of the control conditions set to a control unit, and a heat release rate. It is a graph which shows the relationship between net thermal efficiency (IMEP) at the time of 1500 rpm, and illustration fuel consumption rate (ISFC).

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Controller 20 4-cycle gasoline engine 24 Cylinder 32 Fuel injection valve 34 Spark plug 40 Variable valve timing mechanism 50 Heater 70 In-cylinder heating system 71 Heating passage 72 Cooling water heat exchanger 73 Exhaust heat exchanger 100 Control unit D Partial load operation Region D ₁ (low load side) operation region D ₂ (high load side) operation region
dQ / dθ Heat generation rate (dQ / dθ) MAX Heat generation rate N Engine speed N1 Predetermined speed SW1 Air flow sensor (an example of operating state detection means)
SW2 intake air temperature sensor (an example of operation state detection means)
SW3 Crank angle sensor (an example of operation state detection means)
SW4 engine water temperature sensor (an example of operation state detection means)
SW5 Oxygen concentration sensor (an example of operation state detection means)
SW6 Accelerator opening sensor (an example of operation state detection means)
SW7, SW8 Temperature sensor (an example of operation state detection means)
T In-cylinder temperature

Claims (5)

A plurality of cylinders for burning the air-fuel mixture;
In-cylinder heating means for increasing the in-cylinder temperature of each cylinder;
Driving state detecting means for detecting the driving state of the engine;
In a control device for a spark ignition gasoline engine, comprising: a control means for performing a compression self-ignition operation in a predetermined operation region by controlling the in-cylinder heating means based on the detection of the operating state detection means;
Fuel injection means capable of controlling fuel injection for each cylinder;
An ignition means for igniting a mixture of injected fuel and air,
In the predetermined partial load operation region, the in-cylinder temperature of the operating cylinder is increased and the compression self-ignition operation is executed, and on the predetermined low load side in the partial load operation region, only a part of the cylinders are operated. while performing the operation, wherein in the predetermined partial load operation region exceeding the low load, the control means as cylinder running is increased to control the heating means, fuel injection means and the ignition means cylinder,
The switching point between the predetermined low load side and the high load side is set to a load that reaches a predetermined maximum heat generation rate at which the frequency of knocking by the operating cylinder increases in the case of reduced cylinders. Type engine control device. The control device for the spark ignition engine according to claim 1,
The control device for a spark ignition engine, wherein the predetermined low load side operation region is a warm idle operation. The control device for a spark ignition engine according to claim 1 or 2,
An external EGR device that recirculates a portion of the burned gas to the intake passage;
In the operation region in which the compression self-ignition operation is performed, the external EGR is introduced at least on the high load side, and the control means is configured to stop the introduction of EGR gas in the predetermined low load side operation region. A control device for a spark ignition engine characterized by controlling the engine. The control device for a spark ignition engine according to claim 3,
A control device for a spark ignition engine, wherein the control means controls an external EGR device so that EGR gas is introduced during compression self-ignition operation in which all cylinders are operating. In the control device for the spark ignition engine according to any one of claims 1 to 4,
Air-fuel ratio adjusting means for adjusting the air-fuel ratio by the control means is provided,
On the higher load side than the partial load operation region, the forced ignition operation is executed, and the control means controls the air-fuel ratio adjusting means so that the air-fuel ratio at the time of the compression self-ignition operation becomes leaner than the stoichiometric air-fuel ratio. control apparatus for a spark ignition engine, characterized in that it.

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