JP6171957B2 - Control unit for direct injection gasoline engine - Google Patents

Description

  The technology disclosed herein relates to a control device for a direct injection gasoline engine.

  In an engine, it is preferable to improve thermal efficiency, and one of the methods is to reduce cooling loss. In the engine according to Patent Document 1, the cooling loss on the wall surface of the combustion chamber is reduced by configuring the wall surface defining the combustion chamber with a heat insulating material.

JP 2009-243355 A

  By the way, there are a case where the cooling loss is not sufficiently reduced only by configuring the wall surface of the combustion chamber with a heat insulating material, or a case where it is desired to reduce the cooling loss without changing the configuration of the engine. From such a viewpoint, it is desired to reduce the cooling loss by a method other than that in which the wall surface of the combustion chamber is made of a heat insulating material.

  The technology disclosed herein has been made in view of the above points, and the object is to reduce the cooling loss on the wall surface of the combustion chamber by a method other than configuring the wall surface of the combustion chamber with a heat insulating agent. There is.

  The technology disclosed herein is directed to a control device for a direct injection gasoline engine. This control device for a direct injection gasoline engine controls an engine body having a piston provided in a cylinder, an injector for injecting fuel containing at least gasoline into the cylinder through an injection port, and an injection mode of the injector. A control unit, wherein the control unit causes the injector to perform multi-stage injection in a period from the latter half of the compression stroke to the initial stage of the expansion stroke in an operation region where the engine load of the engine body is equal to or greater than a predetermined load. Includes a first injection for injecting fuel at a predetermined first interval from the immediately preceding fuel injection, and a second injection for injecting fuel at a second interval longer than the first interval from the immediately preceding fuel injection. Is included.

  Here, the “second half of the compression stroke” means the second half when the compression stroke is divided into two equal parts, the first half and the second half. “Initiation of the expansion stroke” means an initial time when the expansion stroke is divided into three equal parts, namely, initial stage, middle period, and final stage.

  When the fuel is injected, a region where a negative pressure is generated in the vicinity of the central axis of the fuel injection is generated due to the Coanda effect. The size of the negative pressure region changes according to the injection interval in the multistage injection. Specifically, when the injection interval is large, the pressure in the negative pressure region can be recovered before the next fuel is injected, so the negative pressure region becomes smaller. When the negative pressure region is small, the fuel spray is not attracted to the negative pressure so much and is easily diffused in a direction spreading radially outward with the central axis as the center. On the other hand, when the injection interval is small, the fuel is injected one after another, so that the negative pressure in the negative pressure region is maintained and the negative pressure region becomes larger. When the negative pressure region is large, the fuel spray is attracted to the negative pressure, and the spread outward in the radial direction is suppressed. That is, as the injection interval is larger, the fuel spray is more easily diffused, and as the injection interval is smaller, the spread of the fuel spray is suppressed.

  According to the above configuration, since the first injection is performed with a relatively short first interval from the immediately preceding fuel injection, the negative pressure region during the first injection is relatively large. Therefore, the fuel spray by the first injection is attracted to the negative pressure region, and the spread of the radially outer side is suppressed. On the other hand, since the second injection is performed with a relatively long second interval from the immediately preceding fuel injection, the negative pressure region during the second injection is relatively small. Therefore, the fuel spray by the second injection is not attracted so much to the negative pressure region, and spreads outward in the radial direction is relatively large.

  Here, since the fuel spray by the second injection spreads outward in the radial direction, the scattering distance of the fuel spray in the central axis direction becomes relatively short. On the other hand, since the fuel spray by the first injection has a small outward spread in the radial direction, the scattering distance of the fuel spray in the central axis direction becomes relatively long. That is, the fuel spray by the first injection and the fuel spray by the second injection are dispersed in the central axis direction. As a result, the fuel concentration distribution in the central axis direction can be homogenized.

  When fuel is injected while the injection interval is constant in multistage injection, the fuel spray moves away from the injector, and at the time of ignition, the fuel concentration in a portion away from the injector, for example, in the vicinity of the piston becomes high. When the fuel burns in this state, a large amount of heat is generated in the vicinity of the piston, and the amount of heat generated by the combustion is dissipated through the piston, resulting in a large cooling loss.

  On the other hand, in the above configuration, the concentration of fuel concentration can be dispersed in the direction of the central axis as compared with multistage injection with a constant injection interval. That is, the concentration of fuel concentration in the vicinity of the piston is alleviated. This reduces heat dissipation through the piston during combustion. As a result, cooling loss can be reduced.

  On the other hand, in order to reduce the fuel concentration in the vicinity of the piston, it is conceivable to locally increase the fuel concentration in a specific portion such as the center of the combustion chamber or the vicinity of the injector. However, in this method, when the amount of fuel is large, the fuel concentration in the portion becomes too thick, and the CO emission amount increases. On the other hand, according to the configuration in which the fuel concentration distribution is dispersed, it is possible to realize the above-described reduction in cooling loss while suppressing the CO emission amount.

  The first injection and the second injection are preferably performed continuously, but another fuel injection may be interposed between the first injection and the second injection. Even in such a case, the scattering distance in the central axis direction of the fuel spray by the first injection is relatively short, and the scattering distance in the central axis direction of the fuel spray by the second injection is relatively long. .

Further, the injector is configured to be able to adjust the effective sectional area of the nozzle hole, and the control unit controls the injector so that the effective sectional area of the nozzle hole becomes smaller as the interval from the immediately preceding fuel injection becomes longer. you adjustment.

  According to this configuration, when the effective sectional area of the nozzle hole is adjusted, the particle size of the fuel spray injected from the nozzle hole changes. When the particle size of the fuel spray changes, the momentum of the fuel spray changes. When the momentum of the fuel spray changes, the scattering distance of the fuel spray changes. Specifically, the larger the effective area of the nozzle hole, the larger the particle size of the fuel spray and the longer the spray distance of the fuel spray.

  Here, since the effective sectional area of the nozzle is made smaller as the interval from the immediately preceding fuel injection becomes longer, the effective sectional area of the nozzle of the first injection is relatively large, and the effective sectional area of the nozzle of the second injection is It is adjusted relatively small. That is, since the fuel spray by the first injection has a relatively large momentum, the scattering distance in the traveling direction becomes long, so the scattering distance in the central axis direction also becomes relatively long. In the first place, since the fuel spray by the first injection has a relatively slow momentum decay, the scattering distance in the central axis direction is further increased. On the other hand, since the fuel spray by the second injection has a relatively small momentum, the scattering distance in the traveling direction is shortened, so that the scattering distance in the central axis direction is also relatively short. In the first place, in the fuel spray by the second injection, the momentum decay is relatively fast, and therefore the scattering distance in the central axis direction is further shortened.

  Furthermore, the fuel spray by the second injection has a relatively short scattering distance in the radial direction as a result of a short scattering distance in the traveling direction. Since the outward spread in the radial direction is different between the first injection and the second injection, if the scattering distance in the traveling direction is the same, the fuel spray by the second injection has a longer scattering distance outward in the radial direction. . On the other hand, by reducing the scattering distance in the traveling direction of the fuel spray by the second injection, the difference between the fuel spray by the first injection and the fuel spray by the second injection is reduced with respect to the scattering distance to the radially outer side. be able to.

Further, the second injection, Ru performed later than the first injection.

  According to this configuration, the fuel spray of the second injection has a short scattering distance in the central axis direction and a small outward spread in the radial direction. That is, the fuel spray of the second injection stays relatively near the nozzle. On the other hand, the fuel spray of the first injection has a large momentum and scatters far compared. For this reason, when the first injection is performed after the second injection, the fuel spray by the second injection staying in the vicinity of the injection port may be scattered along with the fuel spray of the first injection. On the other hand, by performing the second injection after the first injection, it is possible to perform the fuel injection to the vicinity of the injection port after the fuel injection to the position away from the injection port first. Thereby, the fuel spray by 2nd injection can be kept in a desired position.

  Further, the multistage injection includes at least three fuel injections including the first injection and the second injection, and the injection interval of the multistage injection may be gradually increased.

  According to said structure, in multistage injection, the fuel injection to the position away from the nozzle hole in the center axis direction is performed first, and then the fuel injection to the position near the nozzle hole is sequentially performed thereafter. By doing so, it becomes easy to form an air-fuel mixture in which the fuel concentration is dispersed in the central axis direction.

  Furthermore, the injector is configured to be able to adjust the effective cross-sectional area of the nozzle hole, and the multi-stage injection has a relatively large effective cross-sectional area of the nozzle hole as compared with the first injection group. A second injection group having a small and / or relatively small injection interval, and the control unit adjusts the injector so that at least the first injection group includes the first injection and the second injection. It may be.

  According to the above configuration, the first injection group has a relatively large effective sectional area of the nozzle hole and / or a relatively large injection interval. On the other hand, in the second injection group, the effective sectional area of the injection hole is relatively small and / or the injection interval is relatively small. As described above, the effective cross-sectional area of the nozzle hole not only affects the scattering distance of the fuel spray, but also affects the susceptibility of the fuel spray from the negative pressure region. That is, when the effective area of the nozzle hole is large, the particle size of the fuel spray is large, so that the fuel spray is not easily affected by the negative pressure region. The fuel spray having a large particle size is not attracted so much to the negative pressure region, and is less likely to be decelerated by the negative pressure region. On the other hand, since the effective area of the nozzle hole is small in the particle size of the fuel spray, the fuel spray is easily affected by the negative pressure region. The fuel spray having a small particle size is easily attracted to the negative pressure region, and is easily decelerated by the negative pressure region. That is, the fuel spray by the first injection group has a relatively long scattering distance in the traveling direction and is likely to spread and spread. On the other hand, in the fuel spraying by the second injection group, the scattering distance in the traveling direction is relatively short and the spread is suppressed. Therefore, adjusting the fuel concentration distribution in the central axis direction in the first injection group, which is likely to scatter and diffuse further, is more effective than adjusting the fuel concentration distribution in the central axis direction in the second injection group. The influence on the concentration distribution of the air-fuel mixture formed in the entire multistage injection is great. Therefore, by including the first injection and the second injection in the first injection group, it is possible to effectively form an air-fuel mixture in which the fuel concentration is dispersed in the central axis direction.

  The injector includes a nozzle body in which the nozzle hole is formed and a valve body that opens and closes the nozzle hole, and is configured so that an effective sectional area of the nozzle port changes according to a lift amount of the valve body. You may be allowed to.

  According to the injector, by adjusting the lift amount of the valve body, it is possible to adjust the effective cross-sectional area of the injection hole, and thus, the particle size of the fuel spray can be changed.

  According to the said structure, the cooling loss in the wall surface of a combustion chamber can be reduced.

It is a schematic block diagram which shows a direct injection gasoline engine. It is sectional drawing which shows the internal structure of an injector. It is a figure which illustrates the driving | operation map of an engine. It is sectional drawing which shows notionally the shape of the air-fuel | gaseous mixture layer formed in a combustion chamber. It is a figure explaining the spread direction of the fuel spray injected from an injector. It is a figure which shows the injection interval of a fuel. It is a figure which shows the lift amount of an outside valve-opening type injector. (A) Conceptual diagram showing the spread of fuel spray when the fuel injection interval is long, (B) Conceptual diagram showing the spread of fuel spray when the fuel injection interval is short. (A) The conceptual diagram which shows the spread of fuel spray when the lift amount of an injector is small, (B) The conceptual diagram which shows the spread of fuel spray when the lift amount of an injector is large. It is a figure which shows the injection aspect in a medium load and a low rotation area | region. It is a figure which shows the fuel concentration distribution of the combustion chamber in a medium load and a low rotation area | region. It is a figure which shows the injection aspect in a medium load and a high rotation area | region. It is a figure which shows the fuel concentration distribution of the combustion chamber in a medium load and high rotation area | region. It is sectional drawing which shows the internal structure of the injector which concerns on other embodiment.

  Hereinafter, exemplary embodiments will be described in detail with reference to the drawings.

  FIG. 1 schematically shows a direct injection gasoline engine 1 (hereinafter simply referred to as an engine 1). The engine 1 includes various actuators associated with the engine body, various sensors, and an engine controller 100 that controls the actuators based on signals from the sensors.

  The engine 1 is mounted on a vehicle such as an automobile, and its output shaft is connected to drive wheels via a transmission, although not shown. The vehicle is propelled by the output of the engine 1 being transmitted to the drive wheels. The engine body of the engine 1 includes a cylinder block 12 and a cylinder head 13 mounted thereon, and a plurality of cylinders 11 are formed in the cylinder block 12 (in FIG. 1). , Only one cylinder 11 is shown). Although not shown, a water jacket through which cooling water flows is formed inside the cylinder block 12 and the cylinder head 13.

  Here, the fuel of the engine 1 is gasoline in the present embodiment, but it may be gasoline containing bioethanol or the like, and may be any fuel as long as it is a liquid fuel containing at least gasoline.

  A piston 15 is slidably inserted into each cylinder 11. The piston 15 divides the combustion chamber 17 together with the cylinder 11 and the cylinder head 13. In the illustrated example, the combustion chamber 17 is a so-called pent roof type, and its ceiling surface (that is, the lower surface of the cylinder head 13) has a triangular roof shape composed of two inclined surfaces on the intake side and the exhaust side. The crown surface of the piston 15 has a convex shape corresponding to the ceiling surface, and a concave cavity (concave portion) 15a is formed at the center of the crown surface. The shape of the ceiling surface and the crown surface of the piston 15 may be any shape as long as a high geometric compression ratio described later is realized. For example, both the ceiling surface and the crown surface of the piston 15 (that is, the portion excluding the cavity 15a) may be configured by surfaces perpendicular to the central axis of the cylinder 11, and the ceiling surface is triangular as described above. While forming a roof shape, the crown surface of the piston 15 (that is, the portion excluding the cavity 15 a) may be configured by a surface perpendicular to the central axis of the cylinder 11.

  Although only one is shown in FIG. 1, two intake ports 18 are formed in the cylinder head 13 for each cylinder 11, each of which is a lower surface of the cylinder head 13 (that is, an inclined surface on the intake side on the ceiling surface of the combustion chamber 17). Opening to communicate with the combustion chamber 17. Similarly, two exhaust ports 19 are formed in the cylinder head 13 for each cylinder 11, and each opens to the lower surface of the cylinder head 13 (that is, the inclined surface on the exhaust side of the ceiling surface of the combustion chamber 17). 17 communicates. The intake port 18 is connected to an intake passage (not shown) through which fresh air introduced into the cylinder 11 flows. A throttle valve 20 for adjusting the intake flow rate is interposed in the intake passage, and the opening degree of the throttle valve 20 is adjusted in response to a control signal from the engine controller 100. On the other hand, the exhaust port 19 is connected to an exhaust passage (not shown) through which burned gas (that is, exhaust gas) from each cylinder 11 flows. Although not shown, an exhaust gas purification system having one or more catalytic converters is disposed in the exhaust passage. The catalytic converter includes a three-way catalyst.

  The cylinder head 13 is provided with an intake valve 21 and an exhaust valve 22 so that the intake port 18 and the exhaust port 19 can be shut off (closed) from the combustion chamber 17, respectively. The intake valve 21 is driven by an intake valve drive mechanism, and the exhaust valve 22 is driven by an exhaust valve drive mechanism. The intake valve 21 and the exhaust valve 22 reciprocate at a predetermined timing to open and close the intake port 18 and the exhaust port 19, respectively, and perform gas exchange in the cylinder 11. Although not shown, the intake valve drive mechanism and the exhaust valve drive mechanism each have an intake camshaft and an exhaust camshaft that are drivingly connected to the crankshaft. These camshafts are synchronized with the rotation of the crankshaft. Rotate. In addition, at least the intake valve drive mechanism includes a hydraulic, electric, or mechanical variable phase mechanism (VVT) 23 that can continuously change the phase of the intake camshaft within a predetermined angle range. It consists of In addition, you may make it provide the variable lift mechanism (CVVL (Continuous Variable Valve Lift)) which can change a valve lift amount continuously with VVT23.

  A spark plug 31 is disposed on the cylinder head 13. The spark plug 31 is attached and fixed to the cylinder head 13 by a known structure such as a screw. In the illustrated example, the spark plug 31 is attached and fixed in a state inclined to the exhaust side with respect to the central axis of the cylinder 11, and the tip thereof faces the ceiling of the combustion chamber 17. The tip of the spark plug 31 is located in the vicinity of a nozzle port 41 of an injector 33 described later. The arrangement of the spark plug 31 is not limited to this. In the present embodiment, the ignition plug 31 is a plasma ignition type plug, and the ignition system 32 includes a plasma generation circuit. The spark plug 31 generates plasma by discharge by the ignition system 32 and injects the plasma into the cylinder from the tip of the spark plug 31 to ignite the fuel. The ignition system 32 receives a control signal from the engine controller 100 and energizes the ignition plug 31 to generate plasma at a desired ignition timing. The spark plug 31 is not limited to a plasma ignition type plug, but may be a spark ignition type plug that is commonly used.

  On the central axis of the cylinder 11 in the cylinder head 13, an injector 33 that directly injects fuel into the cylinder (that is, in the combustion chamber 17) is disposed. The injector 33 is fixedly attached to the cylinder head 13 with a known structure such as using a bracket. The tip of the injector 33 faces the center of the ceiling of the combustion chamber 17.

  As shown in FIG. 2, the injector 33 has an outer valve-opening type having a nozzle body 40 in which a nozzle port 41 for injecting fuel into the cylinder 11 is formed, and an outer valve 42 for opening and closing the nozzle port 41. It is an injector. The injector 33 injects fuel in a direction that is inclined with respect to a predetermined central axis S and spreads radially outward from the central axis S, and can adjust the effective sectional area of the nozzle port 41. It is configured. The nozzle port 41 is an example of a nozzle hole, and the outer opening valve 42 is an example of a valve body.

  The nozzle body 40 is a tubular member extending along the central axis S, and the fuel circulates therein. The opening edge of the nozzle port 41 is formed in a tapered shape whose diameter increases toward the tip side at the tip portion of the nozzle body 40. The proximal end of the nozzle body 40 is connected to a case 45 in which a piezo element 44 is disposed. The outer opening valve 42 includes a valve main body 42 a and a connecting portion 42 b that is connected from the valve main body 42 a through the nozzle main body 40 to the piezo element 44. The valve body 42 a is exposed to the outside from the nozzle body 40 at the tip of the nozzle body 40. When the portion of the valve body 42a on the side of the connecting portion 42b has substantially the same shape as the opening edge of the nozzle port 41, and the portion abuts (that is, sits) on the opening edge of the nozzle port 41, The nozzle port 41 is closed.

  The injector 33 is arranged such that the central axis S coincides with the central axis X of the cylinder 11 and the nozzle port 41 faces the ceiling portion of the combustion chamber 17.

  The piezo element 44 opens the nozzle port 41 by pressing the outer opening valve 42 in the direction of the central axis and lifting it from the opening edge of the nozzle port 41 of the nozzle body 40 by deformation due to application of voltage. At this time, the fuel is injected in a direction that is inclined with respect to the central axis S from the nozzle opening 41 and spreads in a radial direction centering on the central axis S. Specifically, the fuel is injected in a cone shape (specifically, a hollow cone shape) around the central axis S. The taper angle of the cone is 90 ° to 100 ° in the present embodiment (the taper angle of the inner hollow portion of the hollow cone is about 70 °). When the application of voltage to the piezo element 44 is stopped, the piezo element 44 returns to the original state, and the outer opening valve 42 closes the nozzle port 41 again. At this time, the compression coil spring 46 disposed around the connecting portion 42 b in the case 45 facilitates the return of the piezo element 44.

  As the voltage applied to the piezo element 44 increases, the lift amount (hereinafter simply referred to as lift amount) of the outer open valve 42 from the state in which the nozzle port 41 is closed increases (see also FIG. 7). The larger the lift amount, the larger the opening degree (that is, the effective sectional area) of the nozzle port 41 and the larger the particle size of the fuel spray injected from the nozzle port 41 into the cylinder. Conversely, the smaller the lift amount, the smaller the opening of the nozzle port 41 and the smaller the particle size of the fuel spray injected from the nozzle port 41 into the cylinder. The response of the piezo element 44 is fast, and, for example, about 20 multistage injections are possible in one cycle. However, the means for driving the outer valve 42 is not limited to the piezo element 44.

  The fuel supply system 34 includes an electric circuit for driving the outer opening valve 42 (piezo element 44) and a fuel supply system for supplying fuel to the injector 33. The engine controller 100 outputs an injection signal having a voltage corresponding to the lift amount to the electric circuit at a predetermined timing, thereby operating the piezo element 44 and the outer valve 42 via the electric circuit, A desired amount of fuel is injected into the cylinder. When the injection signal is not output (that is, when the voltage of the injection signal is 0), the nozzle opening 41 is closed by the outer opening valve. Thus, the operation of the piezo element 44 is controlled by the injection signal from the engine controller 100. Thus, the engine controller 100 controls the operation of the piezo element 44 to control the fuel injection from the nozzle port 41 of the injector 33 and the lift amount during the fuel injection.

  The fuel supply system is provided with a high-pressure fuel pump (not shown) and a common rail, and the high-pressure fuel pump pumps the fuel supplied from the fuel tank via the low-pressure fuel pump to the common rail. The pumped fuel is stored at a predetermined fuel pressure. The fuel stored in the common rail is injected from the nozzle port 41 by operating the injector 33 (that is, the outer opening valve 42 is lifted).

  The engine controller 100 is a controller based on a well-known microcomputer, and includes a central processing unit (CPU) that executes a program, a memory that is configured by, for example, RAM and ROM, and stores a program and data, And an input / output (I / O) bus for inputting and outputting signals. The engine controller 100 is an example of a control unit.

  The engine controller 100 includes at least a signal related to the intake air flow from the air flow sensor 71, a crank angle pulse signal from the crank angle sensor 72, an accelerator opening signal from the accelerator opening sensor 73 that detects the amount of depression of the accelerator pedal, And the vehicle speed signal from the vehicle speed sensor 74 is received, respectively. Based on these input signals, the engine controller 100 calculates control parameters of the engine 1, such as a desired throttle opening signal, fuel injection pulse, ignition signal, valve phase angle signal, and the like. Then, the engine controller 100 converts these signals into a throttle valve 20 (more precisely, a throttle actuator that moves the throttle valve 20), a fuel supply system 34 (more precisely, the above electric circuit), an ignition system 32, and Output to VVT23 or the like.

  The geometric compression ratio ε of the engine 1 is 15 or more and 40 or less. In the present embodiment, the engine 1 is also an engine 1 having a relatively high expansion ratio as well as a high compression ratio because of the configuration where the compression ratio = expansion ratio. The thermal efficiency is improved by increasing the geometric compression ratio.

  As shown in FIG. 1, the combustion chamber 17 includes a wall surface of the cylinder 11, a crown surface of the piston 15, a lower surface (that is, a ceiling surface) of the cylinder head 13, and valve heads of the intake valve 21 and the exhaust valve 22. And a surface. And in this engine 1, in order to reduce a cooling loss, the heat insulation layer 61, 62, 63, 64, 65 is provided in each of these surfaces, and the combustion chamber 17 is thermally insulated. In addition, below, when these heat insulation layers 61-65 are named generically, a code | symbol "6" may be attached | subjected to a heat insulation layer. The heat insulation layer 6 may be provided on all of these section screens, or may be provided on a part of these section screens. Further, in the illustrated example, the heat insulating layer 61 on the cylinder wall surface is provided at a position above the piston ring 14 in a state where the piston 15 is located at the top dead center. 14 is configured not to slide. However, the heat insulating layer 61 on the cylinder wall surface is not limited to this configuration, and the heat insulating layer 61 may be provided over the entire stroke or a part of the stroke of the piston 15 by extending the heat insulating layer 61 downward. Further, a heat insulating layer may be provided on the port wall surface near the opening on the ceiling surface side of the combustion chamber 17 in the intake port 18 and the exhaust port 19, although it is not the wall surface that directly partitions the combustion chamber 17. In addition, the thickness of each heat insulation layer 61-65 illustrated in FIG. 1 does not show actual thickness, but is only an illustration, and does not show the magnitude relationship of the thickness of the heat insulation layer in each surface.

  The heat insulation structure of the combustion chamber 17 will be described in more detail. As described above, the heat insulating structure of the combustion chamber 17 is constituted by the heat insulating layers 61 to 65 provided on the respective screens that define the combustion chamber 17, and these heat insulating layers 61 to 65 are the combustion gas in the combustion chamber 17. Therefore, the heat conductivity is set to be lower than that of the metal base material constituting the combustion chamber 17. Here, for the heat insulating layer 61 provided on the wall surface of the cylinder 11, the cylinder block 12 is the base material, and for the heat insulating layer 62 provided on the crown surface of the piston 15, the piston 15 is the base material. For the heat insulating layer 63 provided on the ceiling surface, the cylinder head 13 is a base material, and for the heat insulating layers 64 and 65 provided on the valve head surfaces of the intake valve 21 and the exhaust valve 22, respectively, the intake valve 21 and the exhaust valve 22 are provided. Are the base materials. Accordingly, the base material is aluminum alloy or cast iron for the cylinder block 12, cylinder head 13 and piston 15, and heat-resistant steel or cast iron for the intake valve 21 and exhaust valve 22.

  In addition, the heat insulating layer 6 preferably has a volumetric specific heat smaller than that of the base material in order to reduce cooling loss. That is, the gas temperature in the combustion chamber 17 varies with the progress of the combustion cycle, but in a conventional engine that does not have the heat insulation structure of the combustion chamber 17, the cooling water flows in a water jacket formed in the cylinder head or cylinder block. Thus, the temperature of the surface defining the combustion chamber 17 is maintained substantially constant regardless of the progress of the combustion cycle.

  On the other hand, since the cooling loss is determined by cooling loss = heat transfer coefficient × heat transfer area × (gas temperature−temperature of the section screen), the cooling temperature increases as the temperature difference between the gas temperature and the wall surface temperature increases. The loss will increase. In order to suppress the cooling loss, it is desirable to reduce the difference between the gas temperature and the temperature of the section screen. However, when the temperature of the section screen of the combustion chamber 17 is maintained substantially constant by cooling water, It is unavoidable that the temperature difference increases with fluctuation. Therefore, it is preferable to reduce the heat capacity of the heat insulating layer 6 so that the temperature of the section screen of the combustion chamber 17 changes following the fluctuation of the gas temperature in the combustion chamber 17.

The heat insulating layer 6 may be formed, for example, by coating a ceramic material such as ZrO ₂ on the base material by plasma spraying. The ceramic material may contain a number of pores. If it does in this way, the thermal conductivity and volume specific heat of the heat insulation layer 6 can be made lower.

  Further, in the present embodiment, as shown in FIG. 1, a port liner 181 made of aluminum titanate having an extremely low thermal conductivity, excellent heat insulation, and excellent heat resistance is integrated with the cylinder head 13. A heat insulating layer is provided in the intake port 18 by casting. With this configuration, when fresh air passes through the intake port 18, it is possible to suppress or avoid an increase in temperature due to heat received from the cylinder head 13. As a result, the temperature of the fresh air introduced into the cylinder 11 (initial gas temperature) is lowered, so that the gas temperature at the time of combustion is lowered and the temperature difference between the gas temperature and the section screen of the combustion chamber 17 is reduced. Become advantageous. Lowering the gas temperature at the time of combustion can lower the heat transfer rate, which is advantageous for reducing the cooling loss. In addition, the structure of the heat insulation layer provided in the intake port 18 is not limited to the casting of the port liner 181.

In the engine 1, the geometric compression ratio ε is set to 15 ≦ ε ≦ 40 as described above. The theoretical thermal efficiency η _th in the Otto cycle, which is the theoretical cycle, is η _th = 1−1 / (ε ^κ−1 ), and the theoretical thermal efficiency η _th increases as the compression ratio ε increases. However, the illustrated thermal efficiency of the engine (more precisely, the engine having no combustion chamber insulation structure) peaks at a predetermined geometric compression ratio ε (for example, about 15), and the geometric compression ratio ε is more than that. However, the illustrated thermal efficiency does not increase, and conversely, the illustrated thermal efficiency decreases. This is because, when the geometric compression ratio is increased while the fuel amount and the intake air amount are kept constant, the higher the compression ratio, the higher the combustion pressure and the combustion temperature. As described above, the combustion pressure and the combustion temperature are increased because the cooling loss is increased.

  On the other hand, in this engine 1, the heat insulating structure of the combustion chamber 17 is combined as described above so that the illustrated thermal efficiency is increased at a high geometric compression ratio ε. That is, the heat loss of the combustion chamber 17 is reduced to reduce the cooling loss, thereby increasing the indicated thermal efficiency.

  On the other hand, merely reducing the cooling loss by insulating the combustion chamber 17 converts the reduced cooling loss into the exhaust loss and does not contribute much to the improvement in the illustrated thermal efficiency. In addition, the high expansion ratio accompanying the high compression ratio efficiently converts the combustion gas energy corresponding to the reduction in cooling loss into mechanical work. That is, it can be said that the engine 1 greatly improves the illustrated thermal efficiency by adopting a configuration that reduces both the cooling loss and the exhaust loss.

  In this engine 1, in addition to the heat insulation structure of the combustion chamber 17 and the intake port 18, a heat insulation layer is formed by a gas layer in the cylinder (inside the combustion chamber 17), thereby further reducing the cooling loss. Yes. This will be described in detail below.

  FIG. 3 illustrates an operation map when the engine 1 is warm. The engine 1 is basically configured to burn the air-fuel mixture in the combustion chamber 17 by compression self-ignition over the entire operation region. In the operation map shown in FIG. 3, a heat insulating layer made of a gas layer is formed in the combustion chamber 17 in a low load region lower than a predetermined load and a medium load region where the load is higher than the low load region. In other words, in an operating state where the engine load is relatively low and the fuel injection amount is relatively small, a heat insulation layer is formed in the combustion chamber 17 by a gas layer, thereby reducing cooling loss and improving thermal efficiency. Plan. Here, the low load region and the medium load region respectively correspond to the low region and the medium region when the engine load region is divided into three regions of low, medium, and high (for example, divided into three equal parts). May be defined. In particular, the middle load region may be a region of a predetermined load or less (for example, 70% load or less) with respect to the fully open load, for example.

  FIG. 4 conceptually shows the shape of the air-fuel mixture layer formed in the combustion chamber 17 in the low load and medium load regions. The formation of a heat insulating layer by a gas layer in the combustion chamber 17 means that an air-fuel mixture layer is formed at the center of the combustion chamber 17 and a gas layer containing fresh air is formed around it as shown in FIG. That is. This gas layer may be only fresh air, and may contain burned gas (that is, EGR gas) in addition to fresh air. As will be described later, it is allowed that a small amount of fuel is mixed in the gas layer as long as the gas layer serves as a heat insulating layer.

  By reducing the ratio (S / V ratio) between the surface area (S) and the volume (V) of the gas mixture layer, the heat transfer area with the surrounding gas layer is reduced during combustion, and the gas mixture layer and the cylinder 11 Due to the gas layer between the cylinder 11 and the wall surface, the flame of the gas mixture layer does not come into contact with the wall surface of the cylinder 11, and the gas layer itself becomes a heat insulating layer to suppress the release of heat from the wall surface of the cylinder 11. Will be able to. As a result, the cooling loss can be greatly reduced.

  The engine controller 100 includes a nozzle port 41 of the injector 33 in a period from the latter half of the compression stroke to the initial stage of the expansion stroke so that an air-fuel mixture layer is formed in the central portion of the combustion chamber 17 and a gas layer is formed around it. In order to inject fuel into the cylinder 11, the injection signal is output to the electric circuit of the fuel supply system.

  In the low load region, since the fuel injection amount is relatively small, fuel is injected into the cylinder 11 from the injector 33 disposed on the central axis X of the cylinder 11 in the second half of the compression stroke to the initial stage of the expansion stroke. It is relatively easy to suppress the spread of the fuel spray by injecting and form the air-fuel mixture layer at the center in the combustion chamber 17 and the surrounding gas layer. However, since the fuel injection period becomes longer as the combustion injection amount increases, the fuel spray spreads particularly in the direction of the central axis X of the cylinder 11, and as a result, the air-fuel mixture layer forms, for example, the crown surface of the piston 15. Will come to touch. That is, the gas layer around the gas mixture layer is not reliably formed. As described above, the engine 1 has a high geometric compression ratio, and accordingly, the volume of the combustion chamber (that is, the space in the cylinder when the piston is located at the compression top dead center) is small. Therefore, in the engine 1, when the fuel spray spreads in the direction of the central axis X of the cylinder 11, the air-fuel mixture layer tends to touch the crown surface of the piston 15.

  Therefore, the engine 1 is formed in the combustion chamber 17 in order to reliably form the air-fuel mixture layer in the center of the combustion chamber 17 and the surrounding gas layer even in the middle load region where the fuel injection amount increases. Control the shape of the gas mixture. Specifically, as shown by the white arrow in FIG. 4, when the fuel injection amount increases, the fuel spray spreads outward in the radial direction intersecting the central axis X of the cylinder 11. As a result, the length of the air-fuel mixture layer in the direction of the central axis X is prevented from becoming longer, and the air-fuel mixture layer is prevented from touching the crown surface of the piston 15 while being spatially smaller than the direction of the central axis X. By expanding the air-fuel mixture layer to the outside in the radial direction with a sufficient margin, the air-fuel mixture layer is also prevented from touching the inner wall of the cylinder 11. Controlling the shape of the air-fuel mixture layer formed in the combustion chamber 17 means that when the length in the central axis direction of the air-fuel mixture layer formed in the combustion chamber 17 is L and the radial width is W, By adjusting the ratio (L / W) between the length L and the width W, the fuel injection amount increased while the L / W ratio was set to a predetermined value or more in order to reduce the S / V ratio. Sometimes, the L / W ratio is reduced.

  In order to realize such control of the shape of the air-fuel mixture layer, in the engine 1, the fuel injection interval (see FIG. 6) by the injector 33 and the lift amount (see FIG. 7) are adjusted. Thereby, as shown in FIG. 5, the spread of the fuel spray in the traveling direction and the spread of the fuel spray in the radial direction around the central axis S are controlled independently. The interval between fuel injections is defined as the interval from the end of fuel injection to the start of the next fuel injection, as conceptually shown in FIG. As described above, this injector 33 has a high response and can perform about 20 multistage injections within 1 to 2 msec. Further, as conceptually shown in FIG. 7, the lift amount of the injector 33 is proportional to the fuel injection opening area. As described above, the larger the lift amount, the more the injection opening area (that is, the effective disconnection of the nozzle port 41). Area) increases, and the smaller the lift amount, the smaller the injection opening area.

  FIG. 8 shows a fuel spray when the fuel injection interval is lengthened (FIG. (A)) and when the injection interval is shortened (FIG. (B)) while the lift amount of the injector 33 is made constant. Conceptually shows the difference in the spread of The fuel spray injected in a hollow cone shape from the injector 33 flows in the combustion chamber 17 at a high speed. Therefore, a negative pressure region is generated along the central axis S of the injector 33 inside the hollow cone due to the Coanda effect. When the fuel injection interval is long, the pressure in the negative pressure region recovers between the fuel injection and the next fuel injection, so the negative pressure region becomes smaller. On the other hand, when the fuel injection interval is short, the fuel injection is repeated without a gap, so that the recovery of the pressure in the negative pressure region is suppressed. As a result, the negative pressure region becomes large as shown in FIG.

  The fuel spray is attracted to this negative pressure. Since the negative pressure region is formed on the center side in the radial direction around the central axis S, when the negative pressure region is relatively large, as shown in FIG. 8B, the fuel spray expands in the radial direction. That is, the inclination angle of the fuel spray traveling direction with respect to the central axis S is suppressed. On the other hand, when the negative pressure region is relatively small, as shown in FIG. 8A, since the fuel spray is not attracted so much, it tends to spread in the radial direction, and the fuel spray with respect to the central axis S of the fuel spray The inclination angle in the traveling direction increases. That is, if the fuel injection interval of the injector 33 is shortened, the radial spread of the fuel spray can be suppressed. On the other hand, if the injection interval is increased, the radial spread of the fuel spray is promoted. Is possible.

  FIG. 9 shows a fuel spray when the lift amount of the injector 33 is reduced (FIG. (A)) and the lift amount is increased (FIG. (B)) while the fuel injection interval is made constant. Conceptually shows the difference in the spread of In this case, since the injection interval is the same, the negative pressure region in the combustion chamber 17 is the same, but the particle size of the fuel spray is different due to the difference in the lift amount. That is, when the lift amount of the injector 33 is reduced, the particle size of the fuel spray is also reduced, so that the momentum of the fuel spray is reduced. For this reason, the fuel spray is easily attracted to the center side in the radial direction due to the negative pressure, and as shown in FIG. 9A, spreading to the outside in the radial direction is suppressed. On the other hand, when the lift amount of the injector 33 is increased, the particle size of the fuel spray increases, so the momentum of the fuel spray increases. For this reason, the fuel spray is less likely to be attracted to the negative pressure, and as shown in FIG. 9B, the fuel spray tends to spread outward in the radial direction. That is, if the lift amount of the injector 33 is increased, the spread of the fuel spray in the radial direction can be promoted. On the other hand, if the lift amount is decreased, the spread of the fuel spray in the radial direction can be suppressed. become.

  Further, since the fuel spray having a large particle size has a large momentum, the scattering distance in the traveling direction becomes long. Furthermore, the fuel spray having a large particle size is not easily decelerated due to the influence of the negative pressure region, and this also increases the scattering distance. On the other hand, since the fuel spray with a small particle size has a small momentum, the scattering distance in the traveling direction becomes short. Further, the fuel spray having a small particle size is easily decelerated under the influence of the negative pressure region, and this also shortens the scattering distance.

  As described above, by changing the injection interval and the lift amount of the injector 33, it is possible to independently control the spread of the fuel spray in the two directions of the radial direction and the traveling direction. Therefore, in this engine 1, the lift amount is relatively small and the injection interval is relatively small, and the first injection group including a plurality of fuel injections having a relatively large lift amount and a relatively large injection interval. The shape of the air-fuel mixture layer is controlled in combination with the second injection group including a plurality of fuel injections. In any of the injection groups, multi-stage injection that performs fuel injection a plurality of times is executed. Here, the multistage injection means continuous fuel injection in which the fuel injection interval (interval from the end of fuel injection to the start of the next fuel injection) is 0.5 ms or less.

  Specifically, the first injection group includes a predetermined number of fuel injections in which the lift amount of the injector 33 is larger than that of the second injection group and the fuel injection interval is larger than that of the second injection group. By increasing the injection interval, the negative pressure region becomes smaller. In addition, the momentum of the fuel spray is increased by increasing the lift amount to increase the particle size of the fuel spray. As a result, a fuel spray is formed in which the scattering distance in the traveling direction is relatively long and spread in the radial direction.

  The second injection group includes a predetermined number of fuel injections in which the lift amount of the injector 33 is smaller than that of the first injection group and the fuel injection interval is smaller than that of the first injection group. By reducing the injection interval, the negative pressure region is expanded. In addition, the momentum of the fuel spray is reduced by reducing the lift amount and the particle size of the fuel spray. As a result, a fuel spray is formed in which the scattering distance in the traveling direction is relatively short and the spread in the radial direction is suppressed.

  The engine controller 100 controls the air-fuel mixture layer to have a shape corresponding to the operating state of the engine 1 by changing the ratio of the first injection group and the second injection group according to the operating state of the engine 1. . As a basic principle, by increasing the proportion of the first injection group, an air-fuel mixture layer spreading outward in the radial direction is formed, while by increasing the proportion of the second injection group, outward in the radial direction. An air-fuel mixture layer in which the spread of is suppressed is formed.

  Depending on the operating state of the engine 1, the first injection group is omitted and only the second injection group is executed, or only one fuel injection is included in the first injection group, and the second injection is performed thereafter. When the second injection group is omitted and only the first injection group is executed, or when the fuel injection included in the second injection group is only once and the first injection group is used. There is also. Further, the second injection group may be executed after the first injection group, or the first injection group may be executed after the second injection group.

  The engine controller 100 further controls the injection modes of the first injection group 8 and the second injection group 9 in accordance with the operating state of the engine 1 on the premise of the above-described multistage injection. FIG. 10 is a diagram illustrating an injection mode in a medium load and low rotation range. FIG. 11 is a diagram showing a fuel concentration distribution in the combustion chamber in a medium load and low rotation range. FIG. 12 is a diagram showing an injection mode in a medium load and high rotation range. FIG. 13 is a diagram showing a fuel concentration distribution in the combustion chamber in a medium load and high rotation range.

  Specifically, the engine controller 100 controls the injector 33 so that the fuel injection interval of the first injection group 8 gradually increases and the lift amount gradually decreases in the medium load region. At this time, the lift amount of the fuel injection included in the second injection group 9 is constant. The second injection group 9 is completed before the compression top dead center.

  Specifically, in the region on the low rotation side of the medium load, as shown in FIG. 10, the first injection group 8 includes four fuel injections. The lift amount of the first fuel injection 81 is the largest. The second fuel injection 82 is performed at a relatively small first interval a1 from the first fuel injection 81. The lift amount of the second fuel injection 82 is smaller than that of the first fuel injection 81. The third fuel injection 83 is performed with a second interval a2 larger than the first interval a1 from the second fuel injection 82. The lift amount of the third fuel injection 83 is smaller than that of the second fuel injection 82. The fourth fuel injection 84 is performed with a third interval a3 larger than the second interval a2 from the third fuel injection 83. The lift amount of the fourth fuel injection 84 is smaller than that of the third fuel injection 83. The second fuel injection 82 is an example of the first injection, and the third fuel injection 83 or the fourth fuel injection 84 is an example of the second injection. The third fuel injection 83 can also be an example of the first injection. In that case, the fourth fuel injection 84 is an example of the second injection.

  Thus, in the first injection group 8, the later the injection timing, the longer the injection interval and the smaller the negative pressure region. Therefore, the fuel spray by the fuel injection at the beginning of the first injection group 8 has a relatively large negative pressure region, so that the fuel spray is directed radially outward with respect to the central axis S, that is, radially outward of the combustion chamber 17. Spreading is suppressed. On the other hand, the fuel spray by the fuel injection toward the end of the first injection group 8 spreads radially outward of the combustion chamber 17 because the negative pressure region is relatively small (that is, the progress of the fuel spray with respect to the central axis S). The angle of inclination of the direction increases).

  Here, the greater the outward spread of the fuel spray in the radial direction, the shorter the scattering distance in the central axis direction. That is, the fuel spray by the fuel injection at the beginning of the first injection group 8 has a small spread in the radial direction, so that the scattering distance in the central axis direction becomes long. On the other hand, since the fuel spray by the fuel injection toward the end of the first injection group 8 has a large spread in the radial direction, the scattering distance in the central axis direction becomes short. That is, the arrival positions of the fuel sprays can be made different from each other in the central axis direction. As a result, fuel can be dispersed and injected in the central axis direction, and fuel spray can be dispersed in the central axis direction.

  In addition, in the first injection group 8, the lift amount becomes smaller as the injection interval becomes longer. When the lift amount is small, the particle size of the fuel spray is small and the momentum is small, so that the scattering distance in the traveling direction of the fuel spray is short. That is, the longer the injection interval, that is, the greater the spread in the radial direction, the shorter the scattering distance in the traveling direction. For example, if the scattering distance in the traveling direction of each fuel spray in the first injection group 8 is constant, the fuel spray can be dispersed in the central axis direction by adjusting the spread of the fuel spray in the radial direction. However, the scattering distance in the radial direction of the fuel spray is not uniform in the central axis direction. That is, the greater the spread of the fuel spray in the radial direction, the longer the scattering distance in the radial direction of the fuel spray. On the other hand, by shortening the scattering distance in the traveling direction of the fuel spray having a large spread in the radial direction, the difference in the scattering distance in the radial direction of each fuel spray can be reduced. That is, the spread in the radial direction as the entire air-fuel mixture layer can be made as uniform as possible in the central axis direction.

  Further, when the scattering distance in the traveling direction of the fuel spray is shortened, the scattering distance in the central axis direction of the fuel spray is also shortened. The fuel spray having a large spread in the radial direction is a fuel spray that is desired to be disposed in the vicinity of the nozzle opening 41 by suppressing the scattering distance in the central axis direction. Therefore, reducing the particle size of the fuel spray, which has a large spread in the radial direction, and shortening the scattering distance in the traveling direction can not only equalize the scattering distance in the radial direction of the fuel spray, but also reduce the fuel spray. It is also effective from the viewpoint of disposing near the nozzle. That is, by adjusting the particle size of the fuel spray, the fuel spray can be easily arranged at a desired position in the central axis direction.

  On the other hand, the fuel injections 90, 90,... Of the second injection group 9 have a relatively short injection interval and a large negative pressure region. Further, the fuel injections 90, 90,... Of the second injection group 9 have a relatively small momentum because the lift amount is relatively small and the fuel spray particle size is small. For this reason, the fuel spray by the second injection group 9 has a relatively short scattering distance and is likely to gather at the center in the radial direction due to the influence of negative pressure. More specifically, the injection interval of the fuel injections 90, 90,... Is shorter than the first interval a1 between the first fuel injection 81 and the second fuel injection 82 of the first injection group 8. Therefore, the fuel spray by the second injection group 9 is scattered more radially inward than the fuel spray by the first injection group 8.

  Further, the total injection amount by the first injection group 8 and the total injection amount by the second injection group 9 are substantially the same amount.

  As a result of such fuel injection by the first injection group 8 and the second injection group 9, at the time of ignition (predetermined timing after compression top dead center), the fuel spray is distributed in the central axis direction, The fuel concentration distribution is substantially uniform in the central axis direction. Note that the ignition of fuel can be determined, for example, when the combustion mass ratio of the fuel becomes 1% or more.

  Specifically, the fuel spray from the first fuel injection 81 (hereinafter referred to as “first fuel spray”) is scattered relatively freely, but the fuel spray from the second fuel injection 82 (hereinafter referred to as “fuel spray”). (Referred to as “second fuel spray”) is attracted to a large negative pressure region, and the spread in the radial direction is suppressed. Therefore, the fuel spray is scattered almost along the central axis S to the vicinity of the piston 15.

  In the third fuel injection 83, the negative pressure region is smaller than that in the second fuel injection 82. Therefore, although fuel spray by the third fuel injection 83 (hereinafter referred to as “third fuel spray”) is attracted to the negative pressure region, the inclination angle with respect to the central axis S is larger than that of the second fuel spray. And spread in the radial direction. Further, since the third fuel spray has a smaller particle size than the second fuel spray, the scattering distance in the traveling direction is short. Combined with the large spread in the radial direction and the short scattering distance in the traveling direction, the scattering distance in the central axis direction of the third fuel spray becomes shorter than that in the second fuel spray. That is, the third fuel spray is scattered only to a position closer to the nozzle opening 41 than the second fuel spray in the central axis direction. Further, since the third fuel spray has a short scattering distance in the traveling direction, the radial scattering distance is also short. Therefore, although the third fuel spray has a larger spread in the radial direction than the second fuel spray, the scattering distance in the radial direction is substantially the same as the second fuel spray.

  In the case of the fourth fuel injection 84, the negative pressure region is smaller than in the case of the third fuel injection 83. Therefore, although the fuel spray by the fourth fuel injection 84 (hereinafter referred to as “fourth fuel spray”) is attracted to the negative pressure region, the inclination angle with respect to the central axis S is larger than that of the third fuel spray. And spread in the radial direction. Further, since the fourth fuel spray has a smaller particle size than the third fuel spray, the scattering distance in the traveling direction is short. Combined with the large spread in the radial direction and the short scattering distance in the traveling direction, the scattering distance in the central axis direction of the fourth fuel spray becomes shorter than that in the third fuel spray. That is, the fourth fuel spray scatters only to a position closer to the nozzle opening 41 than the third fuel spray in the central axis direction. In addition, since the fourth fuel spray has a short scattering distance in the traveling direction, the radial scattering distance is also short. Therefore, although the fourth fuel spray has a larger spread in the radial direction than the third fuel spray, the scattering distance in the radial direction is substantially the same as the third fuel spray.

  As a result of such fuel injection by the first injection group 8, for example, at the time of ignition, the second fuel spray is located in the vicinity of the piston 15 in the central axis direction, and the third fuel spray is the piston 15 and the nozzle opening. The fuel spray for the fourth time is located in the vicinity of the nozzle port 41. Thus, the fuel spray by the first injection group 8 is dispersed in the central axis direction. Moreover, the scattering distance in the radial direction of any of the second to fourth fuel sprays is about the same.

  Thereafter, the fuel spray from the second injection group 9 is injected closer to the center in the radial direction than the fuel spray from the first injection group 8.

  As a result, at the time of ignition, the fuel spray is in a state of being approximately evenly distributed in the central axis direction. That is, as shown in FIG. 11, the fuel concentration distribution in the central axis direction is substantially uniform.

  When the fuel is combusted in this state, the concentration of the fuel in the vicinity of the piston 15 is eliminated, so that a large amount of heat is not generated locally in the vicinity of the piston 15. As a result, heat dissipation through the piston 15 is suppressed, and cooling loss is reduced.

  In order to reduce the fuel concentration in the vicinity of the piston 15, it is conceivable to locally increase the fuel concentration in a portion other than the vicinity of the piston 15, for example, the center of the combustion chamber 17. However, in this method, when the amount of fuel is large as in the middle load region, the fuel concentration becomes too high locally and the CO emission amount increases. On the other hand, when the fuel concentration distribution is homogenized as described above, the cooling loss can be reduced while suppressing the CO emission amount.

  Since the total injection amount by the first injection group 8 and the total injection amount by the second injection group 9 are substantially the same amount, the fuel by the second injection group 9 distributed in the center in the radial direction of the combustion chamber 17. The ratio of the spray and the fuel spray by the first injection group 8 distributed around the fuel spray by the second injection group 9 is approximately the same, and the fuel concentration distribution in the radial direction of the combustion chamber 17 is also shown in FIG. As shown, they are almost even.

  On the other hand, as shown in FIG. 12, the engine controller 100 sets the ratio of the second injection group 9 to the total fuel injection amount in one cycle in the high rotation side region of the medium load region. It is increased compared to the area. In the example of FIG. 12, the number of fuel injections included in the first injection group 8 is decreased by one and the number of fuel injections included in the second injection group 9 is increased by two compared to the example of FIG. Yes. Specifically, in the first injection group 8, the fourth fuel injection 84 is deleted, and only the first to third fuel injections 81 to 83 are provided.

  Further, the injection timing of the multistage injection is advanced compared to the low rotation region. This is because, assuming that the fuel is ignited at a predetermined crank angle, the time from the start of fuel injection to the predetermined crank angle becomes shorter as the engine speed increases. That is, it is for securing sufficient time corresponding to the ignition delay between the start of fuel injection and the predetermined crank angle.

  However, when the fuel is injected into the combustion chamber 17, the specific heat ratio in the combustion chamber 17 is lowered. Therefore, as the fuel injection timing is advanced, the temperature of the compression end temperature is less likely to increase and ignition is difficult. On the other hand, by increasing the ratio of the second injection group 9 with respect to the total injection amount as compared with the region on the low rotation side, a portion where the fuel concentration is locally high is formed, and the ignitability is improved. In the second injection group 9, the fuel spray has a small particle size and a large negative pressure region, so that the fuel spray is likely to gather near the radial center of the combustion chamber 17. That is, by increasing the ratio of the second injection group 9, as shown in FIG. 13, a portion having a locally high fuel concentration can be formed at the center in the radial direction of the combustion chamber 17. As a result, fuel can be ignited at a desired crank angle even when the rotational speed is high.

  Even in the high rotation range, in the first injection group 8, the fuel injection interval gradually increases and the lift amount gradually decreases. Thereby, the fuel concentration distribution in the central axis direction is substantially uniform. Therefore, even in the high rotation region, the amount of heat generated by combustion in the vicinity of the piston 15 can be reduced, and the cooling loss can be reduced.

  When the load on the engine 1 increases, the amount of fuel increases as compared with the case where the load is small. At this time, the engine controller 100 increases the ratio of the first injection group 8 to the total injection amount of fuel. . For example, the number of fuel injections included in the first injection group 8 increases. The fuel spray by the first injection group 8 is more likely to spread in the radial direction of the combustion chamber 17 than the second injection group 9. Since the combustion chamber 17 at the time of ignition has a flat shape extending in the radial direction, when the load increases and the amount of fuel increases, the radial space of the combustion chamber 17 is effectively used. The fuel concentration distribution in the combustion chamber 17 can be made substantially uniform in the central axis direction.

  Thus, the engine 1 includes an engine main body having the piston 15 provided in the cylinder 11, an injector 33 that injects fuel including at least gasoline into the cylinder 11 through the nozzle port 41, and the injector 33. And an engine controller 100 for controlling the injection mode. The engine controller 100 controls the injector 33 within the period from the latter half of the compression stroke to the initial stage of the expansion stroke in an operation region where the engine load of the engine 1 is equal to or greater than a predetermined load. The multi-stage injection is performed. In the multi-stage injection, the second fuel injection 82 that injects fuel at a predetermined first interval a1 from the first fuel injection 81 and the first fuel injection 82 from the first fuel injection 82 are performed. And a third fuel injection 83 for injecting fuel at a second interval a2 longer than the interval a1.

  According to said structure, the spreading of the fuel spray to the radial direction centering on the central axis of fuel injection can be suppressed by adjusting the injection space | interval in multistage injection. In the multistage injection, the fuel spray can be dispersed in the central axis direction by adjusting the spread of the fuel spray in the radial direction for each fuel injection.

  Specifically, since the second fuel injection 82 has a relatively short injection interval from the first fuel injection 81, a large negative pressure region is formed, and the second fuel spray is a negative pressure region. And the spread in the radial direction is suppressed. Therefore, the scattering distance in the central axis direction of the second fuel spray becomes relatively long. On the other hand, since the third fuel injection 83 has a relatively long injection interval from the second fuel injection 82, the negative pressure region is small, and the third fuel spray is attracted too much to the negative pressure region. However, the spread in the radial direction increases. Therefore, the scattering distance in the central axis direction of the third fuel spray becomes relatively short. As a result, the second fuel spray and the third fuel spray are dispersed in the central axis direction.

  In this way, fuel concentration in the vicinity of the piston 15 can be eliminated by dispersing the fuel spray in the central axis direction. As a result, the amount of heat generated in the vicinity of the piston 15 during combustion can be reduced, and the amount of heat released from the piston 15 can be reduced. As a result, cooling loss can be reduced.

  The injector 33 is configured to be able to adjust the effective cross-sectional area of the nozzle port 41, and the engine controller 100 is configured such that the effective cross-sectional area of the nozzle port 41 increases as the interval from the previous fuel injection increases. The injector 33 is adjusted to be small.

  According to this configuration, the fuel spray having a larger spread in the radial direction has a smaller particle size and a smaller momentum. That is, the scattering distance in the traveling direction of the fuel spray is shortened. When the scattering distance in the traveling direction of the fuel spray is shortened, naturally, the scattering distance in the radial direction is also shortened. That is, the fuel spray having a large spread in the radial direction has a shorter scattering distance in the central axis direction than the fuel spray having a small spread in the radial direction, but has a longer scattering distance in the radial direction. However, by shortening the scattering distance itself in the traveling direction of the fuel spray having a large radial spread, the scattering distance in the radial direction of the fuel spray can be shortened. Therefore, the scattering distance in the radial direction of the fuel spray having a large spread in the radial direction can be made closer to the fuel spray having a small spread in the radial direction.

  Further, the third fuel injection 83 with a relatively long injection interval and a relatively small effective sectional area of the nozzle port 41 has a relatively short injection interval and a relatively large effective sectional area of the nozzle port 41. This is performed after the second fuel injection 82.

  According to this configuration, the third fuel spray has a relatively small radial spread and a relatively short scattering distance in the traveling direction. That is, the third fuel spray tends to stay in the vicinity of the nozzle port 41. Therefore, after the third fuel injection 83, when fuel injection with a longer scattering distance is performed, the fuel spray staying in the vicinity of the nozzle port 41 is attracted by the later fuel spray and scattered far away. There is a possibility of going. As a result, it is difficult to keep the third fuel spray at a desired position. On the other hand, the second fuel spray that scatters far is injected first, and then the third fuel spray that has a short scatter distance is injected, so that each fuel spray can be easily placed at a desired position.

  Further, the multistage injection includes at least three fuel injections including the first injection and the second injection, and the injection interval of the multistage injection is gradually increased.

  According to this configuration, the fuel spray having a longer scattering distance in the central axis direction is injected earlier. Since the time until ignition becomes shorter as the fuel injection timing comes, the fuel spray having a long scattering distance in the direction of the central axis is injected first, so that the fuel spray can surely reach a desired position.

  The multi-stage injection includes the first injection group 8 and the second injection group 9 in which the effective sectional area of the nozzle port 41 is relatively small and the injection interval is relatively small compared to the first injection group 8. The engine controller 100 adjusts the injector 33 so that at least the first injection group 8 includes the second fuel injection 82 and the third fuel injection 83.

  Since the first injection group 8 has a larger fuel particle size and a smaller negative pressure region than the second injection group 9, the fuel spray from the first injection group 8 is easy to diffuse and to be scattered far away. That is, the fuel spray from the first injection group 8 easily reaches the piston 15. Therefore, by including the second fuel injection 82 and the third fuel injection 83 in at least the first injection group 8, the fuel spray scattered to the vicinity of the piston 15 can be effectively reduced as a whole of the multistage injection. can do.

<< Other Embodiments >>
As described above, the embodiment has been described as an example of the technique disclosed in the present application. However, the technology in the present disclosure is not limited to this, and can also be applied to an embodiment in which changes, replacements, additions, omissions, and the like are appropriately performed. Moreover, it is also possible to combine each component demonstrated by the said embodiment and it can also be set as new embodiment. In addition, among the components described in the accompanying drawings and detailed description, not only the components essential for solving the problem, but also the components not essential for solving the problem in order to exemplify the above technique. May also be included. Therefore, it should not be immediately recognized that these non-essential components are essential as those non-essential components are described in the accompanying drawings and detailed description.

  About the said embodiment, it is good also as the following structures.

  For example, in the first injection group 8, the later the injection timing, the longer the injection interval and the smaller the lift amount, but the present invention is not limited to this. In the second injection group 9, the injection interval may be longer and the lift amount may be smaller as the injection timing is later. In that case, in the first injection group 8, the injection interval and the lift amount may be constant. That is, in any of the first injection group 8 and the second injection group 9, the later the injection timing, the longer the injection interval and the smaller the lift amount.

  The first injection group 8 is not limited to the injection mode shown in FIGS. The number of fuel injections in the first injection group 8 is not limited to four times or three times. It may be 4 times or more.

  In the first injection group 8, the lift amount decreases as the injection interval from the immediately preceding fuel injection increases, but the present invention is not limited to this. For example, the lift amount may be constant.

  In the first injection group 8, the injection interval becomes larger as the injection timing comes later, but the present invention is not limited to this. For example, in the first injection group 8, the injection interval may be reduced as the injection timing comes later. Further, the injection interval need not be monotonously increased or decreased, and the injection interval may be increased or decreased during multi-stage injection.

  The first injection group 8 has a larger lift amount and a larger injection interval than the second injection group 9, but only one of the lift amount and the fuel interval may be larger.

  In the multistage injection, the second injection group 9 is executed after the first injection group 8, but the first injection group 8 may be executed after the second injection group 9 by reversing this.

  Further, the second injection group 9 is not limited to the injection mode shown in FIGS. For example, the fuel injection of the second injection group 9 may not be equally spaced, and the lift amount may not be constant.

  Furthermore, in the said embodiment, although the 1st injection group 8 and the 2nd injection group 9 are included in the multistage injection in a medium load area | region, only any one may be sufficient. For example, the multistage injection may be configured only by the second injection group 9. In this case, the first injection for injecting fuel into the second injection group 9 with a predetermined first interval from the immediately preceding fuel injection, and the fuel with a second interval longer than the first interval from the immediately preceding fuel injection. And second injection for injecting.

  That is, multistage injection is performed at least in the middle load region, and during the multistage injection, the first injection that injects fuel at a predetermined first interval from the immediately preceding fuel injection, and the first fuel injection from the immediately preceding fuel injection. As long as the second injection that injects the fuel at a second interval longer than the interval is included, an arbitrary injection form can be adopted.

  Further, the multi-stage injection including the first injection and the second injection is not limited to the middle load region. Similar control may be performed in the low load region and the high load region.

  Moreover, the structure of an injector is not restricted to the said embodiment. As long as the effective cross-sectional area of the nozzle can be changed, any injector can be employed. For example, a VCO (Valve Covered Orifice) nozzle type injector 233 as shown in FIG. 14 may be used. FIG. 14 is a cross-sectional view showing the internal configuration of the injector 233.

  Specifically, the injector 233 includes a nozzle body 240 in which a nozzle port 241 that injects fuel into the cylinder 11 is formed, and a needle valve 242 that opens and closes the nozzle port 241. The nozzle body 240 is a tubular member extending along a predetermined injection axis S, and the fuel circulates therein. The tip of the nozzle body 240 is formed in a conical shape. A mortar-shaped sheet portion 243 is formed on the inner peripheral surface of the tip portion of the nozzle body 240. A plurality of nozzle openings 241 are formed through the tip of the nozzle body 240. One end of the nozzle port 241 opens into the sheet portion 243. A plurality of nozzle ports 241 are arranged around the ejection axis S at equal intervals. The tip end portion of the needle valve 242 is formed in a conical shape and is seated on the seat portion 243 of the nozzle body 240. The nozzle port 241 is closed when the needle valve 242 is seated on the seat portion 243. The nozzle port 241 is an example of an injection port, and the needle valve 242 is an example of a valve body.

  The needle valve 242 is driven by a piezo element similarly to the injector 33. When the needle valve 242 is driven and lifted from the seat portion 243, a gap through which fuel can flow is formed between the seat portion 243 and the needle valve 242, and the fuel flowing through this gap passes through the nozzle port 241. Injected outside the nozzle body 240.

  At this time, cavitation occurs on the inner peripheral surface of the nozzle port 241 when fuel flows. The degree of cavitation (for example, the size of a region where cavitation occurs) varies according to the gap between the needle valve 242 and the seat portion 243, that is, the lift amount of the needle valve 242. Specifically, when the lift amount of the needle valve 242 is small and the gap between the needle valve 242 and the seat portion 243 is small, the region where cavitation occurs also becomes large. On the other hand, when the lift amount of the needle valve 242 is large and the gap between the needle valve 242 and the seat portion 243 is large, the region where cavitation occurs is also small. When the area where cavitation occurs is large, the effective sectional area of the nozzle port 241 is small. When the area where cavitation occurs is small, the effective cross-sectional area of the nozzle port 241 increases. That is, the smaller the lift amount of the needle valve 242, the smaller the effective sectional area of the nozzle port 241. The larger the lift amount of the needle valve 242, the larger the effective sectional area of the nozzle port 241.

  Furthermore, in the above embodiment, it is possible to change the shape of the air-fuel mixture layer in the combustion chamber 17 by changing the lift amount of the injector 33 and the fuel injection interval, but in addition to this, the fuel pressure To increase the range of change in the shape of the air-fuel mixture layer accompanying the change in the lift amount of the injector 33 and the fuel injection interval. That is, when the lift amount of the injector 33 is increased by increasing the fuel pressure, the kinetic energy of the fuel spray becomes larger, and when the fuel injection interval is reduced, the degree of negative pressure increases and the negative pressure region becomes larger. Expand more. As a result, the change width of the shape of the air-fuel mixture layer is further expanded.

  In the above example, the heat insulating structure of the combustion chamber 17 and the intake port 18 is adopted, and a heat insulating layer is formed by a gas layer in the cylinder (inside the combustion chamber 17). The invention can also be applied to an engine that does not employ the heat insulating structure of the combustion chamber 17 and the intake port 18.

  In addition, the fuel injection technique disclosed herein forms an air-fuel mixture layer and a surrounding gas layer in the combustion chamber 17, but is not limited thereto. Even when the gas layer does not exist and the air-fuel mixture layer contacts the wall surface of the combustion chamber 17, the fuel injection technique can be employed. For example, when the fuel injection amount increases with respect to the volume of the combustion chamber 17, the air-fuel mixture layer may come into contact with the wall surface of the combustion chamber 17. Even in such a case, the heat generation near the center of the combustion chamber 17 is increased, and the heat generation near the wall surface is suppressed, thereby suppressing the heat radiation from the wall surface of the combustion chamber 17 and cooling. Loss can be reduced.

  As described above, the technology disclosed herein is useful for a control device for a direct injection gasoline engine.

1 Engine 11 Cylinder
15 Piston 17 Combustion chamber 33 Injector 40 Nozzle body 41 Nozzle port (jet port)
42 Outside valve (valve)
8 First injection group 82 Second fuel injection (first injection)
83 3rd fuel injection (second injection)
9 Second injection group 100 Engine controller (control unit)
233 Injector 241 Nozzle port
242 Needle valve
a1 First interval a2 Second interval S Center axis X Center axis

Claims (4)

An engine body having a piston provided in the cylinder;
An injector that injects fuel including at least gasoline into the cylinder through a nozzle;
A control unit for controlling the injection mode of the injector,
The control unit causes the injector to perform multi-stage injection within a period from the latter half of the compression stroke to the initial stage of the expansion stroke in an operation region where the engine load of the engine body is equal to or greater than a predetermined load.
In the multistage injection, the first injection that injects fuel at a predetermined first interval from the immediately preceding fuel injection and the fuel that is injected from the immediately preceding fuel injection at a second interval longer than the first interval are injected. A second injection ,
The injector is configured to be able to adjust the effective cross-sectional area of the nozzle hole,
The control unit adjusts the injector so that the effective cross-sectional area of the nozzle becomes smaller as the interval from the immediately preceding fuel injection becomes longer,
The control device for a direct injection gasoline engine, wherein the second injection is performed after the first injection . In the direct injection gasoline engine control device according to claim 1 ,
The multi-stage injection includes at least three fuel injections including the first injection and the second injection,
A control device for a direct-injection gasoline engine in which the injection interval of the multistage injection is gradually increased. In the direct injection gasoline engine control device according to claim 1 or 2 ,
The injector is configured to be able to adjust the effective cross-sectional area of the nozzle hole,
The multi-stage injection includes a first injection group and a second injection group in which the effective sectional area of the nozzle is relatively small and / or the injection interval is relatively small compared to the first injection group,
The control unit is a control unit for a direct injection gasoline engine that adjusts the injector so that at least the first injection group includes the first injection and the second injection. In the control device for a direct injection gasoline engine according to claim 2 or 3 ,
The injector has a nozzle body in which the nozzle hole is formed, and a valve body that opens and closes the nozzle hole, and is configured such that an effective sectional area of the nozzle hole changes according to a lift amount of the valve body. Control unit for direct injection gasoline engine.

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