JP4349297B2 - Cylinder injection internal combustion engine fuel injection device and cylinder injection internal combustion engine - Google Patents

Description

  The present invention relates to a direct injection internal combustion engine (hereinafter referred to as an engine) in which fuel is directly supplied to a combustion chamber by a fuel injection valve (hereinafter referred to as an injector).

  Japanese Patent Laid-Open No. 11-159382 discloses a fuel injection valve (hereinafter referred to as an injector) that injects fuel directly into a combustion chamber, and compresses the internal combustion engine (hereinafter referred to as an engine) when it is in a low-load low-rotation operating region. In a cylinder injection engine that stratifies and burns an air-fuel mixture by injecting fuel in a stroke, when at least one of the engine load and the rotational speed is in a relatively high operating region within a region where stratified combustion is performed In the compression stroke, the fuel is divided into a plurality of times and injected to expand the stratified operation region and improve the fuel efficiency.

  Japanese Patent Application Laid-Open No. 7-119507 discloses that fuel is divided and injected efficiently in a uniform combustion (agreement with homogeneous combustion) region at high load and low rotation to reduce the amount of fuel injected per time, and the fuel is effectively used. A technique for atomizing and diffusing to obtain good uniform combustion is described.

JP 11-159382 A JP-A-7-119507

  However, in each of the above conventional techniques, a fuel spray with a long penetration is used as an injector and the piston is used as a guide, or the plug is directly hit, so the injected fuel adheres to the piston in the stratified combustion region. Or, it passes through the spark plug and adheres to the wall surface of the combustion chamber. In addition, even if the fuel is divided and injected several times at the same fuel injection timing, there is a problem that a lot of fuel comes in contact with the piston and the combustion chamber wall surface due to the nature of the system. Cannot be improved.

  An object of the present invention is to widen the stable combustion region.

  To achieve the above object, the present invention injects fuel with a short-penetration spray in a specific stratified combustion region in a stratified combustion state, and in a stratified combustion state in a specific homogeneous combustion region in a homogeneous combustion state. It was configured to switch to a spray state having a longer penetration than the previous penetration.

  In the present invention configured as described above, the stable combustion region of the engine can be expanded in the in-cylinder injection engine, so that it is possible to improve fuel consumption and exhaust (emission).

  One system example of a direct injection engine to which the present invention is applied is shown in FIGS.

  The engine 30 is provided with two intake pipes A and B, a plate 20 that divides them up and down, and an air flow control valve 21 at the starting point of the plate 20.

  Thus, a forward tumble air flow 50 from the intake valve 10 side to the exhaust valve 11 side and the piston 31 is formed in the combustion chamber.

  The strength of the air flow 50 can be changed by controlling the opening degree of the air flow control valve 21 via a link 21B by an electronically controlled actuator 21A.

  In order to easily maintain the tumble air flow 50, a tumble storage groove 50A for guiding the tumble air flow is provided on the top surface of the piston 31.

  The spark plug 32 is disposed at the center of the combustion chamber, and the injector 1 for directly injecting fuel into the combustion chamber has a fuel injection hole between the two intake valves 10 provided in the combustion chamber, and is approximately 30 from the horizontal. It was tilted upwards.

  The injector 1 is composed of a solenoid valve having an electromagnetic coil, and is configured to be controlled to open and close by a control signal from an engine control unit (hereinafter referred to as ECU) 41.

  When a fuel injection control signal from the ECU 41 is input to the injector drive circuit 40, an electromagnetic coil 2 of the injector 1 described in detail later is energized by the battery VB, and the plunger 3 is pulled up and attached to the tip of the plunger 3. The valve body 3a is separated from the valve seat (not shown), and high-pressure fuel pressurized by a high-pressure pump (not shown) is injected into the combustion chamber.

  Since the fuel is injected with a swirling force given by a swirler 4 provided upstream of the valve 3a of the injector 1, it is a hollow conical spray in the intake stroke injection where the pressure in the combustion chamber is low.

  On the other hand, in the compression stroke injection with a high pressure in the combustion chamber, the spray is crushed and becomes a solid spray.

  In the present embodiment, in the stratified combustion region, as shown in the figure, the spray 60a previously injected diffuses in the direction of the plug 32 and stays in the vicinity of the plug 32, and then the injected spray 60b is burned as a fire type. Configured.

  In the figure, reference numeral 32a denotes an ignition coil that receives an ignition signal from the ECU 41 and causes the spark plug 32 to generate an ignition spark.

  An outline of the present embodiment will be described based on FIGS. 3 (a) and 3 (b).

  In the present embodiment, the fuel is divided into a plurality of times and injected at a time very close to each other in the compression stroke.

  When spraying with a swirler injector (injecting fuel necessary for combustion in a single valve opening during a single fuel injection timing), spraying is performed as shown in Fig. 3 (a). Have.

  When the same injection quantity is divided into two injections, as shown in FIG. 3B, the injection quantity per injection is reduced, so that the spray penetration force is reduced.

  When the longer one of the penetration L2 of the first injection and the penetration L3 of the second injection is compared with the penetration L1 of the batch injection, the former penetration L2 (L3) is shorter.

  And when compared with an injector that does not have a swirler upstream of the valve, the same injection amount is twice in the present embodiment with a swirler upstream of the valve when the same fuel supply amount and the same fuel pressure are used. The degree of shortening of the penetration when divided and injected was large.

  Further, when two continuous injections are performed in the same pressure atmosphere, the second injection 60b arrives at the place where the spray 60a of the first injection has lost its linear advance force and stays there, and the whole area is narrow. It was confirmed that the spray stayed at a high concentration.

  However, in the actual combustion chamber, the pressure in the combustion chamber at the timing when the first injection 60a and the second injection 60b are injected is different (the time of the first injection 60a is lower than the time of the second injection 60b).

  By the way, in the injector provided with the swirler, when the atmospheric pressure is low, it becomes a hollow cone spray, and when the atmospheric pressure is high, it becomes a solid compact spray.

  For this reason, in the actual machine, as shown in FIG. 3 (c), the first injection spray 60a of the hollow cone spray injected into the low-pressure combustion chamber is light, so it is widely distributed along the air flow, and the combustion in a relatively high-pressure state The solid second injection spray 60b injected into the chamber does not diffuse as much as the preceding first injection 60a due to relatively heavy fuel particles and weak air flow, and collects around the plug.

  Due to this atmospheric pressure difference, an ideal air-fuel mixture was formed in which a rich air-fuel mixture layer around the plug and a thin air-fuel mixture layer around it.

  When the injection period T1 is longer than 2 milliseconds, the hollow cone spray injected from the injector with the swirler becomes a bell-shaped spray due to the pressure difference between the inside and outside of the spray, and the fuel spray spread angle (θ1, θ2) ) Is narrowed and spray dispersion is suppressed.

  On the other hand, if the injection is divided into a plurality of times, the injection period per time can be shortened, the narrowing of the spread angle of the spray can be prevented, and the fuel can be widely dispersed (θ1 <θ2).

  In the injector with swirler, the spread angle of the fuel can be controlled by performing batch injection or by dividing the injection into two.

  FIG. 4 shows the pattern of the injection method according to this embodiment, and FIG. 5 shows the operating region of the direct injection engine in which this embodiment is implemented.

  In FIG. 5, the horizontal axis represents the rotational speed and the vertical axis represents the load. Regions (1) and (2) are homogeneous operation, (3) is weak stratification operation, and (4) and (5) are regions in which stratification operation is performed. .

  In the high load and high speed homogeneous operation region of (1), it is necessary to inject a large amount of fuel in a short time. Therefore, as shown in FIG. 4 (1), batch injection in the intake stroke or from the exhaust stroke to the intake stroke Inject all at once. At high rotation and high load, the air flow in the combustion chamber is strong, and spray is concentrated on the intake valve side and the air utilization rate is bad, but batch injection with strong penetrating force is performed to reach the exhaust valve side and promote mixing This will improve output and improve fuel efficiency.

  In the region of high load and low rotation of (2), as shown in FIG. 4 (2), the fuel is injected in a plurality of times during the intake stroke, thereby reducing the penetration force (penetration) of the spray and exhausting. Reduces fuel adhesion to the side cylinder wall and piston crown.

  Moreover, by shortening the injection period per time, the spray angle of the first injection 60a can be expanded to promote mixing.

  (3) is a weak stratification operation region, and the injection is divided into an intake stroke and a compression stroke as shown in FIG. 4 (3).

  A lean air-fuel mixture is formed around by the intake stroke injection, and weak stratified combustion is achieved using the spray of the compression stroke injection as an ignition type.

  (4) is a stratified operation region, and is a relatively high rotation region, and stratified combustion is performed by batch injection in the compression stroke as shown in FIG. 4 (4).

  In the stratified operation region of low load and low rotation of (5), stable combustion by stratified combustion is difficult in any conventional engine by guiding the fuel spray of the multiple compression stroke injection shown in FIG. 4 (5) by air flow. In this area, stable combustion by stratified combustion was realized.

  As a result, the stratified charge combustion area has been expanded, and fuel consumption has been reduced and emissions have been improved.

  In the compression stroke multiple injections (twice) shown in FIG. 4 (5), as shown in FIG. 8, the first injection is performed before or during the compression stroke, and a lean air-fuel mixture layer 60a is formed in the vicinity of the plug. The injection is performed during or after the compression stroke, and is ignited and burned when the spray 60b reaches the spark plug.

  Because the spark plug has a combustible air-fuel mixture layer, a lean air-fuel mixture layer around it, and an air layer on the outside, the air-fuel mixture burns efficiently, and since there is no air-fuel mixture on the wall surface, the quench layer cannot propagate flame HC production is reduced, and HC emissions can be reduced.

  In this case, since the second injection is performed in a situation where the air flow in the latter stage of the compression stroke is very weak, in the conventional system, the spray does not have a penetrating force to reach the plug.

  However, in this embodiment, since the first injection generates a flow in the plug direction as shown in FIG. 9 as shown in FIG. 9, the second injection reaches both the spark plug and the action pulled by the flow. Can be reached. As a result, the stable combustion region is expanded and the fuel consumption is further improved.

  When the timings of the first injection and the second injection are made very close (about 1.5 ms) in the compression stroke injection shown in FIG. 4 (5), the time required for the air-fuel mixture to pass through the plug as shown in FIG. Can be extended.

  In a so-called tumble guide engine that transports fuel to the spark plug by tumble air flow, ignition can be performed only during the period when the air-fuel mixture passes through the spark plug. Therefore, when the timing of the first injection and the second injection is optimized, the spray continues. It is possible to ignite at both timings and the combustion stable region is expanded.

  As described above, in the multiple compression stroke injection, by controlling the interval between the first injection and the second injection, the fuel efficiency is improved by the weak stratification of the mixture (FIG. 11 mixture curve 60), and the mixture plug Two effects are obtained: expansion of the combustion stable region by extension of the passage time (FIG. 11 mixture curve 61).

  Further, in a situation where the catalyst is not sufficiently warmed up at the time of starting, fuel is injected in the compression stroke and the expansion stroke as shown in FIG.

  The lean combustion is performed in the compression stroke, the fuel is injected in the expansion stroke, the second spray is combusted by the surplus air in the first combustion and the heat from the combustion, the exhaust temperature is improved, and the catalyst warm-up time is reduced. Since exhaust gas purification can be achieved by early activation of the catalyst, there is an effect of reducing exhaust gas.

  In such a region, since the air flow itself is small, the fuel guide effect by the air flow is low, so that the fuel injection period is longer than the injection period of the other two-time injection regions, the penetration is made longer, and it is easy to reach the periphery of the plug.

  In the low-speed region where the engine is driven by the starter even during start-up, fuel is injected into the cylinder where the piston is stopped in the middle of the compression stroke to burn the first shot. By using multiple timing injections, it is possible to start from the first combustion by stratified combustion, and a direct fuel injection device with less HC generation and good fuel efficiency can be obtained.

  Usually, since the fuel pressure is low and the injection rate is low at the time of starting, it is necessary to make the injection period several times longer than that in normal operation. For this reason, in the conventional direct fuel injection device, the fuel spray penetration becomes too long and the fuel adheres to the opposite wall surface, or the fuel passes through the spark plug position at the ignition timing. Due to the problem that the fuel pressure was low and the atomization of the fuel was insufficient, stratified combustion could not be realized and it was started with homogeneous combustion.

  In this embodiment, by driving the injector twice at one fuel injection timing and dividing and injecting one injection fuel, penetration can be reduced, so that fuel adhesion to the opposing wall surface can be prevented, Further, since the amount of fuel is small, the fuel is sufficiently atomized even at a low pressure, so that it is possible to start from the first combustion by stratified combustion.

  As shown in FIG. 7, the ECU 41 detects engine coolant temperature, engine lubricating oil temperature, engine speed, load, throttle valve opening, crankshaft rotation angle, A / F (empty) from various sensors attached to the engine. The engine state is determined by receiving a signal such as a fuel ratio sensor output or an oxygen concentration detector output), and an injection method is selected in the flowchart of FIG. 6, and an injection timing, an injection period, an ignition timing, etc. And output to the ignition circuit 32a (32b in FIG. 2 indicates an ignition coil).

  In the homogeneous operation, the combustion chamber pressure hardly changes at the two injection timings, but in the stratified operation, the combustion chamber pressure changes as shown in FIG. Further, since the change ratio is a function of the injection timing, the rotation speed, and the intake air amount, an injection interval that matches the conditions is required.

  When the injection interval (time) is the same, if (b) is used as a reference condition, the combustion chamber pressure during the second injection is high under conditions such as (a) where there is a large amount of intake air, resulting in a compact spray. There may be a separation between the first and second sprays.

  In the case of the low rotation (c), since the pressure change is small, it is considered that a result close to a steady spray test can be obtained.

  In order to obtain an air-fuel mixture optimal for combustion, as shown in FIG. 13, the injection pause interval D1 between the first and second injections is shortened as the rotational speed and the intake air amount are increased or the injection timing is delayed.

  However, D1 must not be less than the time required for charging the capacitor of the booster circuit that supplies power to the injector (about 1.5 ms).

  As shown in FIG. 14, T2 / T3 is decreased as the rotational speed and the intake air amount are increased or the injection timing is delayed.

  That is, T3 is extended. However, T2 must not be less than the invalid injection pulse width shown in FIG.

  FIG. 15 shows the relationship between the injection period and the fuel flow rate, and it can be seen that there is a substantially proportional relationship. However, if the injection period is shortened, a region where linearity cannot be obtained appears due to delay in the opening of the plunger of the injector or unstable operation of the plunger.

  An injection period in a region where linearity cannot be obtained is called an invalid injection pulse width, and this region is not used.

  When the injection pulse width (injection period) enters this region, the fuel pressure is set low to reduce the flow rate, and the injection pulse width is increased accordingly.

  In the engine of the first embodiment, an injector with a swirler that is a wide-angle spray type injector is used to obtain a spray angle that can reach the plug. And in the region of low rotation and low load where a relatively long penetration is required, multiple compression stroke injections were applied.

  A second embodiment is shown in FIG.

  In this embodiment, a narrow-angle spray or solid spray type injector that can ensure a relatively long penetration is used, and one injection timing is one injection in a short condition of a low rotation and low load injection period, and the penetration is long at medium rotation. In the region where adhesion to the wall surface becomes a problem because it becomes too much, one injection timing is set to twice injection.

  By using a narrow-angle spray type injector, it was possible to form a fuel spray state that was easy to disperse without losing strong downflow from the intake valve even under homogeneous high load conditions.

  Since the injection pulse is short under low load conditions, if the injection is divided into two times, the injection pulse width of one injection may be less than the invalid injection pulse width. It is effective to increase the ejection pulse width.

  A third embodiment is shown in FIG. This is a structure in which the injector is arranged beside the ignition plug at the center of the combustion chamber, not on the side of the engine head. In the stratified operation, the penetration can be suppressed by the compression stroke injection twice, so that the adhesion to the piston crown surface can be reduced, the air-fuel mixture can be made into two layers, and an ideal mixed state can be obtained. In addition, since the fuel is injected from the center of the combustion chamber, the air-fuel mixture remains in the center without passing through the spray, so that stable combustion can be performed with wide injection and ignition timing. In the homogeneous operation, since the spray shape matches the shape of the combustion chamber, air can be used effectively. Even in homogeneous operation, it is possible to reduce wall adhesion by suppressing penetration and promote mixing by spray expansion by injecting twice in the compression stroke.

  In an injector that opens a valve by boosting the battery voltage with a booster and applying a high voltage to the coil, it is necessary to widen the injection interval in order to open the injector multiple times in a short time. This is because it takes time to charge the voltage from the battery voltage, and if the voltage is not sufficiently charged, the second valve opening may be delayed and the required injection amount may not be obtained. Therefore, an interval of about 1.5 ms or more is necessary.

  When an injector that can be driven by a battery voltage is used, voltage charging is not required, and therefore it is possible to perform injection several times in a very close time. In this case, it is possible to measure the expansion of the stable region by injecting twice in the compression stroke even in the high rotation region of the stratified operation.

  Further, in the engine equipped with a 42V battery, the fuel flow rate does not become unstable even with a smaller pulse width, so that it is possible to inject a plurality of times without dropping the fuel pressure even in a low load region.

  Although the above embodiment has been described with reference to an engine in which the air-fuel mixture is guided by air and stratified, it can also be used in the configuration shown in FIG.

  In the in-cylinder injection engine having a piston with a flat crown surface in FIG. 19, the fuel injected from the injector 1 is directly hit the spark plug 32 to form an air-fuel mixture.

  As the injector 1, for example, a solid spray-type injector is used in which the spray shape is hardly changed due to a change in the in-cylinder pressure.

  In particular, it is important that the spray angle in the direction of the spark plug does not change, so that the fuel can reach the spark plug without being affected by the injection timing and the rotational speed.

  Further, since the piston has a flat shape without a cavity, it is possible to reduce the cooling loss and intake loss of the piston crown surface and improve the fuel efficiency.

  In the engine with this configuration, the time for the spray to pass through the spark plug is short. However, by dividing the injection at one injection timing into a plurality of times and appropriately setting the first and second intervals, The time during which the air-fuel mixture exists can be extended and the combustion stable region can be expanded.

  Further, by dividing the injection at one injection timing into a plurality of times, the penetration can be shortened, so that fuel adhesion to the wall surface on the exhaust valve side can be reduced, and fuel consumption and exhaust can be improved.

  Although the embodiment has been described with respect to the injector with the swirler and the solid spray type injector, a hole nozzle type injector, a plate nozzle type injector, or the like can also be used.

  Although the example which divided | segmented injection into 2 times was described in the Example, you may divide | segment into the frequency | count beyond it.

  Next, detailed configurations of the injector with swirler and the injector driven by the battery voltage used in this embodiment are shown in FIGS. 20 (a), (b), 21 (a), (b), (c). explain.

  FIG. 21A is an enlarged view of the nozzle tip portion of the injector, and shows a swirler 117 according to the present embodiment. The swirler 117 is formed with an axial groove 212, a radial groove 221, and an annular chamber 251 at the outlet of the radial groove 221.

  The axial groove 212 is formed by a passage on a half-moon section surrounded by a plane obtained by cutting a cylindrical side surface of the swirler 117 by two parallel planes and a cylindrical inner peripheral surface of the nozzle.

  The axial groove 212 and the radial groove 221 are fuel passages introduced from above, but the fuel that has passed through the axial groove 212 is eccentric with respect to the valve shaft center by the radial groove 221 and is upstream of the valve seat. It is introduced into the swirl chamber 231. As a result, a so-called turning force is applied to the fuel. Here, the divergence angle of the fuel injection injected from the nozzle 208, that is, the injection angle, is indicated by the offset L of the radial groove 221 provided in the swirler 117 (the distance between the center of the valve shaft and the groove: FIG. 20B). ) And the width and depth of the groove can be adjusted.

  When the offset L of the radial groove 221 is small, or when the width and depth of the groove are increased, a swirl flow is likely to occur. However, the annular chamber 251 has an effect of alleviating the fluctuation of the swirl fuel. .

Since the annular chamber 251 has a larger diameter than the downstream fuel swirl chamber 231, even if the flow velocity of the fuel passing through the radial groove 221 is lowered, the swirl force can be increased by increasing the offset L of the radial groove 221. As a result, the swirl chamber can be used effectively.

  As a result, fluctuations can be avoided and fuel mixing can be actively promoted.

  When the valve 116 leaves the valve seat 210 twice at one injection timing, the fuel flows through the longitudinal passage 212, the radial groove 221, the annular chamber 251, the swirl chamber 231, and the injection port 190 each time and is injected into the combustion chamber. The

  In the valve-closing section between the first injection and the second injection, the fuel stays exclusively in the annular chamber 251 and stands by for sure injection from the initial stage of the second injection.

  Without this annular groove, when the valve is repeatedly opened and closed within a short period of time, fuel supply may not catch up with it and fuel may run out.

  Thus, in the fuel injection valve provided in this embodiment, fuel is supplied from the radially outer side to the inner side through the radial passage 221 a plurality of times during one injection timing. There was no change in the swirling action, and a stable atomization action was achieved at the fuel nozzle, enabling stable fuel injection into the high-pressure combustion chamber.

  The fuel atomization effect in the divided injection and the fuel supply response to the high-speed valve drive, which cannot be realized with an injector without swirler, were obtained.

  Next, an embodiment of an injector and a fuel injection device used in this embodiment will be described with reference to FIGS. 21 (a), (b), and (c).

  21A is a cross-sectional view showing the overall structure of the injector 1 (an enlarged view of the tip nozzle portion is shown in FIG. 20A), and FIG. 21B is a fuel injection device (injector 1 and injector drive circuit 40). It is a schematic diagram which shows the wiring structure of ().

  First, the structure of the injector 1 will be described with reference to FIG.

  The injector 1 is supplied with pressurized fuel from a fuel pump, and opens and closes a fuel passage between a ball valve 116 forming a valve body and a seat surface (valve seat surface) 210 formed on the yoke casing 114 side. The fuel injection amount from the fuel injection hole 190 is controlled.

  The ball valve 116 is attached to the tip of the plunger 115, and a swirler 117 for atomizing fuel is provided in the vicinity of the upstream of the seat surface 210.

  As a means for generating a driving force for the ball valve 116, the injector 1 is provided with a control coil 111 and a hold coil 112. When these coils are energized, a magnetic flux is generated, and a core 113, a yoke 114 and a plunger 115 are generated. As a result, an attractive force is generated between the opposing end surfaces of the core 113 and the plunger 115.

As a result, the plunger 115 and the ball valve 116 are displaced away from the seat surface 210 (to the right in the drawing), and fuel is injected.

  When there is no suction force by the control coil 111 and the hold coil 112 (non-energized state), the ball valve 116 is pressed against the seat surface 210 via the plunger 115 by the spring force of the return spring 118, and the injector 1 is closed. It becomes a state.

  One end of the control coil 111 and the hold coil 112 is electrically connected to form a B terminal. The other end of the control coil 111 is a C terminal, and the other end of the hold coil 112 is an H terminal.

  Two coils so that when the positive terminal of the battery is connected to the B terminal and the C terminal and the H terminal are connected to the negative terminal of the battery, a magnetic flux is generated in the same direction as the control coil 111 and the hold coil 112 (intensifying each other). The winding method and wiring are determined.

  In the drawing, wiring routing is schematically described.

  Next, the wiring configuration of the injector drive circuit 100 will be described with reference to FIG.

For the injector 1, a core 113, a control coil 111, and a hold coil 112 are described.

  The injector control circuit 100 is supplied with a battery voltage from the battery VB, and performs energization control to the control coil 111 and the hold coil 112 based on an injection signal from the engine controller 41.

  The injector control circuit 100 includes a hold coil transistor ON / OFF circuit 104 that controls energization of the hold coil 112 and a control coil transistor ON / OFF circuit 114 that controls energization of the control coil 111.

  Each transistor ON / OFF circuit shares current information to each coil detected by the hold coil current detection resistor 103R and the control coil current detection resistor 113R, and these information and the injection signal from the engine controller 1 Is applied to the hold coil power transistor 102t and the control coil power transistor 112t in accordance with the output of the signal processing circuit 120 with reference to.

  When the hold coil power transistor 102 t and the control coil power transistor 112 t are turned on, the voltage of the battery VB is applied to the hold coil 112 and the control coil 111.

  101R and 111R are the internal resistance of the hold coil 112 and the control coil 111 and the equivalent resistance of the drive circuit, respectively.

  The control coil 111 and the hold coil 112 have different electrical characteristics. This is because the control coil 111 and the hold coil 112 have different roles in the respective stages of closing, opening, holding and closing.

  In this embodiment, the control coil 111 is a coil exclusively used in the initial valve opening state, and the hold coil 112 is a coil used in the valve opening holding state.

  Each difference is described below.

  First, characteristics required for the coil when the valve is opened are shown below.

  When the valve is opened, the set load by the return spring 118 described above and the fuel pressure by the pressurized fuel act on the ball valve, so that a large blocking force acts on the valve opening operation.

  When the electromagnetic force reaches a magnitude that overcomes these forces, the plunger 115 starts to be displaced for the first time.

  Therefore, the time required to generate the force affects the valve opening delay, and therefore needs to be as short as possible.

  The magnetomotive force is a value U (= NI) obtained by multiplying the number of turns N (T) of the coil by the inflow current I (A), and can be applied to the evaluation of the magnetic force that can reach the minute time Δt.

  When the internal resistance of the drive circuit is zero, the smaller the number of turns, the smaller the inductance component and the resistance component, and a larger amount of current flows. As a result, the magnetomotive force that can be reached during the minute time Δt increases.

  The magnetomotive force decreases as the number of turns of the coil decreases. However, since the inductance of the coil is proportional to the square of the number of turns N, it can be seen that the increase in current due to the decrease in inductance is larger than the decrease in magnetomotive force due to the decrease in the number of turns. It was.

  In other words, in order to obtain a large magnetic force when the valve is opened by driving at a low voltage such as a battery voltage, it is considered desirable to improve the responsiveness by increasing the magnetomotive force with current rather than increasing the magnetomotive force with the number of turns.

  However, in reality, there is an internal resistance inside the drive circuit, and at the same time as limiting the maximum value of the ultimate magnetomotive force, the optimum number of turns varies depending on the internal resistance value of the drive circuit.

  Furthermore, the ease of current flow is influenced not only by the coil in the injector, but also by the internal resistance on the control circuit side, the resistance of the switching device, and the voltage drop.

  For this reason, it is necessary to minimize the internal resistance on the control circuit side, the resistance of the switching device, and the voltage drop.

  The coil at the time of valve opening, that is, the control coil 111 of this embodiment and the power transistor 112t of this coil 111 are configured as follows.

  First, the winding diameter of the control coil 111 is a thick winding with a small resistivity.

  Further, the power transistor 112t is bipolar, CMOS or bi-CMOS to reduce the ON resistance when energized and to reduce the equivalent internal resistance 111R of the control coil circuit.

  Furthermore, the number of turns in the vicinity where the ultimate magnetomotive force is the largest is determined according to the resistance value of the internal resistance 111R determined based on such a configuration.

  Normally, in the valve opening holding operation, the valve body can be held in an open state with a smaller magnetomotive force than when the valve is opened.

  This is because the fuel is injected by opening the valve, the pressure is balanced before and after the ball valve 16, the force due to the fuel pressure is reduced, and at the same time, the air gap between the core 113, the yoke 114 and the plunger 115 is reduced. This is because the magnetomotive force can be effectively used.

  Further, when the valve is closed after the valve is opened, the magnetomotive force at the time of holding the valve is lowered by stopping the application of the voltage, and the magnetic force is lowered. When the load is below the set load of the spring 118, the valve closing operation is started. However, if the magnetomotive force at the time of holding the valve is too large, the valve closing delay will be caused.

  Therefore, when the valve is held open, it is necessary to hold it with a low magnetomotive force close to the holding limit.

The coil at the time of opening and holding, that is, the hold coil 112 of the present embodiment and the power transistor 102 of the hold coil 112 are configured as follows. First, the hold coil 112 generally does not need to have a particularly small internal resistance, and the wire diameter may be selected giving priority to the space factor.

  In this embodiment, the control coil 111 has the characteristics required for the coil when the valve is opened, and the hold coil 112 has the characteristics required for the coil when the valve is held open. Ideal operation is possible at each stage.

  Furthermore, it is desirable that the control coil 111 and the hold coil 112 are disposed on the core 113 and the yoke 114 as described above.

  This is because in the magnetic circuit composed of the core 113, the yoke 114, and the plunger 115, the magnetic flux concentrates in the vicinity of the coil, and a large magnetomotive force is applied at an early stage particularly when the valve is opened, which requires a large magnetic force. This is because it is advantageous to arrange the control coil 111 close to the plunger 115.

  In this embodiment, a wide dynamic range as a performance standard can be achieved.

  In order to expand the dynamic range, it is necessary to keep the minimum injection flow rate low. The injection amount is controlled by the ON time of the injection signal, and the injection signal that gives the minimum injection flow rate is shortened to the limit. Although it is necessary to reduce valve opening and closing delays with respect to this short injection signal, this embodiment is configured as follows.

  The energization of the control coil 111 is stopped at Tp, but the energization of the hold coil 112 is continued until the valve closing command after the injection signal falls, that is, after Tp.

  At the start of valve closing, the smaller the current value of each of the coils 111 and 112, the faster the magnetic flux falls, which is advantageous for shortening the valve closing delay.

  In particular, since the hold coil 112 has a slower magnetomotive force falling compared to the control coil 111, it is desirable that the current of the hold coil 112 be minimized.

  The electrical characteristics of the hold coil 112 are determined so that the magnetomotive force that reaches a minute time after the voltage application of the control coil 111 is sufficient to generate the magnetic force necessary for the valve opening operation.

  The start of energization of the hold coil 112 may not be simultaneous with the injection signal input, and is sufficient even after a delay. The current reached when the injection signal falls of the hold coil 112 can be made lower than when energization is started simultaneously with the injection signal.

  As described above, by delaying the energization to the hold coil 12, the current at the falling edge of the injection signal, that is, the valve closing command can be reduced, and the valve closing delay can be shortened.

  In the present embodiment, the control coil 111 and the hold coil 112 whose characteristics are determined in this way cause two current flow interruptions at one injection timing.

  The fuel injection device configured as described above operates as follows (see FIG. 21C).

  The ECU 41 outputs a command Tsg for multiple injections to the drive circuit 40 in accordance with the operating state of the engine.

  The drive circuit 40 turns on the control coil transistor 112t and the hold coil transistor 102t from the signal processing circuit 120 through the circuit 114 for the first injection T2. The total current when viewed from the battery is indicated by a thick line in the lower diagram of FIG. The transistor 112t is turned off after the time t2 has elapsed since energization. The transistor 102t is controlled to be ON during the first injection period T2. As a result, the valve opened by the sum of the magnetomotive forces of both coils is maintained in the open state by the holding force of the coil 111. During this time, the fuel is injected from the injection port into the combustion chamber through the swirler.

  When the time T2 elapses, the energization of the transistor 102t is also cut off, so that the coil is demagnetized, the plunger 115 is pushed back by the return spring 118, the valve 116 is seated on the valve seat 120, and the fuel injection hole is closed.

  However, after a slight valve closing period t4, the drive circuit 40 turns on the control coil transistor 112t and the hold coil transistor 102t from the signal processing circuit 120 through the circuit 114 again for the second injection T3.

  The total current when viewed from the battery is indicated by a thick line in the lower diagram (left) of FIG.

  The transistor 112t is turned off after the time t3 has elapsed since energization.

  The transistor 102t is controlled to be ON during the second injection period T3. As a result, the valve opened by the sum of the magnetomotive forces of both coils is maintained in the open state by the holding force of the coil 111. During this time, the fuel is injected from the injection port into the combustion chamber through the swirler.

  When the time T3 elapses, the current to the transistor 112t is also cut off, so that the coil is demagnetized, the plunger 115 is pushed back by the return spring 118, the valve 116 is seated on the valve seat 120, the fuel injection port is closed, and the second injection is performed. finish.

  In this embodiment, the injector can be driven by the power supply voltage despite being driven at high speed.

  Moreover, since the valve is held with a small holding current after the valve is opened, power consumption can be reduced even if the injector is opened or closed twice or more during one injection timing.

  If the battery VB is a 42 volt battery, the drive current is reduced by the increase in voltage, or if the current is kept the same, the number of turns of the coil can be reduced and the injector can be made smaller.

  The plurality of types of injectors described above can be configured as injectors having both characteristics. That is, the swirler-equipped injector can be configured with a two-coil battery-powered injector. The solid spray or narrow angle spray type injector can be constituted by a two-coil type battery driven injector.

  When any injector is used, as shown in FIG. 22, a deflecting spray type injector having a change element 199 for changing the fuel injection direction to the plug side at the tip can be obtained. In this embodiment, the changing element 199 is configured as a protrusion having a fuel outlet passage 198 whose central axis is inclined by an angle δ in the plug mounting direction with respect to the central axis h1 of the injector.

  According to this injector, at least two deflected sprays are supplied toward the plug during one injection timing.

  According to this configuration, a guide mechanism such as air or a piston cavity is not necessary.

  Therefore, it can be used in combination with a piston having a flat crown surface.

  Further, it is not necessary to provide a tumble air flow generating device at the intake port.

  The problems of the prior art to be solved in the present embodiment are as follows.

  An injector conventionally used in a direct injection internal combustion engine is driven by a high voltage generator including a capacitor. Therefore, when the injector is driven to open and close several times during one injection timing, it is necessary to When it is necessary to charge the capacitor during the valve closing section, the injection interval cannot be reduced, and the combustion stroke time is short in the high engine speed region, a plurality of injection timings are required during one injection timing. There is a problem that it is not possible to inject twice.

  Furthermore, the above-mentioned prior art does not discuss stratified combustion in the operating region of an internal combustion engine in which a starter is driven. This is because when stratified combustion is performed in this state and combustion fails, many times as many HCs as usual are discharged, and it becomes impossible to satisfy strict European exhaust gas regulations, so the aim is to start with a rich air-fuel ratio so that combustion does not fail Is due to.

  However, when starting at a rich air-fuel ratio, more HC is discharged.

  Further, the conventional technology does not take into consideration that the power consumption is high when the injector is driven a plurality of times at one fuel injection timing.

  The purpose of this embodiment is as follows.

  The purpose is to expand the stratified charge combustion area to improve fuel efficiency and emissions.

  Another object is to increase the fuel consumption and the emission by expanding the operating range in which injection is performed a plurality of times during one injection timing.

  Yet another object is to reduce power consumption even if the injector is driven to open and close multiple times at one fuel injection timing.

  According to the embodiment, the above object is achieved as follows.

First,
The fuel injection valve is configured such that the state of the current flowing through the electromagnetic coil changes between the valve opening activation state and the subsequent valve opening holding state, and the valve opening activation state and valve opening are performed during one fuel injection timing. The holding state cycle was configured to be repeated at least twice.

Second,
The fuel injection valve is provided with two electromagnetic coils, and the state of the current flowing through the two electromagnetic coils is switched between the opening start state of the injection valve and the subsequent valve opening holding state, and one fuel injection During the timing, the cycle of the valve opening activation state and the valve opening holding state is repeated at least twice, and the current flowing state is switched each time.

Preferably,
In the first and second configurations, the cycle of the valve opening activation state and the valve opening holding state is configured to be repeated at least twice with a predetermined valve closing section between one injection timing.

Third,
The fuel injection valve has a valve body that opens and closes a fuel passage and a valve seat, and has a radial fuel passage from the radially outer side to the inside that imparts a turning force to the fuel upstream of the valve seat, and the fuel passage In this configuration, at least two fuel flows from the radially outer side to the inner side are formed during one fuel injection timing.

Fourth,
During the starter drive, the fuel injection valve is configured to open and close the fuel passage at least twice during one fuel injection timing.

Fifth,
The fuel injection valve is configured to be switched to a spray state with a long penetration and a spray state with a short penetration. In a short state, the fuel is injected at least twice during one injection timing.

Sixth,
The fuel injection valve includes a changing element that changes fuel spray in the direction of the plug in the fuel injection hole, and injects fuel from the changing element toward the spark plug at least twice during one injection timing. Configured to do.

Seventh,
Air flow is generated in the combustion chamber by the air flow generator provided at the intake port, and the fuel required for combustion is divided into multiple injections from the fuel injection valve. Configured to guide.
Is.

  In the present embodiment, the stratified operation range could be further expanded in the cylinder injection engine. In another embodiment, the formation of the air-fuel mixture can be controlled in various ways according to the operating conditions to improve the combustion stability, fuel consumption, and exhaust of the engine. In another embodiment, a system with low power consumption can be realized.

  The embodiment of this example is as follows.

Embodiment 1
In a fuel injection device for a direct injection internal combustion engine provided with a fuel injection valve for directly injecting fuel into a combustion chamber,
The fuel injection valve has an electromagnetic coil, and the electromagnetic coil is configured such that a state in which a current flows is changed between a valve opening activation state of the injection valve and a valve opening holding state thereafter,
A fuel injection device for a direct injection internal combustion engine in which the cycle of the valve opening activation state and the valve opening holding state is repeated at least twice during one fuel injection timing.

(Embodiment 2)
In a fuel injection device for a direct injection internal combustion engine provided with a fuel injection valve for directly injecting fuel into a combustion chamber,
The fuel injection valve has two electromagnetic coils, and the two electromagnetic coils are configured to switch a current flow state between a valve opening activation state of the injection valve and a subsequent valve opening holding state; and A fuel injection device for a direct injection internal combustion engine in which a state in which a current flows is switched so that a cycle of a valve opening activation state and a valve opening holding state is repeated at least twice during a single fuel injection timing.

(Embodiment 3)
In Embodiments 1 and 2, in a cylinder injection type internal combustion engine, a cycle of the valve opening activation state and the valve opening holding state is repeated at least twice with a predetermined valve closing section between one injection timing. Fuel injection device.

Embodiment 4
In a fuel injection device for a direct injection internal combustion engine provided with a fuel injection valve for directly injecting fuel into a combustion chamber,
The fuel injection valve has a valve body that opens and closes a fuel passage and a valve seat, and has a radial fuel passage from the radially outer side to the inside that imparts a turning force to the fuel upstream of the valve seat. A fuel injection device for a direct injection internal combustion engine, wherein a flow of fuel from the radially outer side to the inner side is formed at least twice in a passage during one fuel injection timing.

(Embodiment 5)
In a fuel control method for a direct injection internal combustion engine provided with a fuel injection valve that is started by a starter and directly injects fuel into a combustion chamber,
A fuel control method for a direct injection internal combustion engine, wherein the fuel injection valve opens and closes the fuel passage at least twice during one start of fuel injection during the starter drive.

(Embodiment 6)
In a fuel injection device for a direct injection internal combustion engine comprising a fuel injection valve for directly injecting fuel into a combustion chamber and configured to be able to switch the combustion state between a stratified combustion state and a homogeneous combustion state,
The fuel injection valve is configured to be switched between a spray state having a long penetration and a spray state having a short penetration, and in a specific stratified combustion region of the stratified combustion state, the spray valve is switched to a spray state having a short penetration. Fuel injection of a cylinder injection type internal combustion engine configured to switch to a spray state with a long penetration in a specific stratified combustion region and to inject fuel at least twice during one injection timing in a state where the penetration is short apparatus.

(Embodiment 7)
In a fuel injection device for a direct injection internal combustion engine comprising a fuel injection valve for directly injecting fuel into a combustion chamber and an ignition plug for igniting fuel spray injected from the fuel injection valve,
The fuel injection valve includes a changing element that changes fuel spray in the direction of the plug in the fuel injection hole of the fuel injection valve, and from the changing element, at least twice during one injection timing. A fuel injection device for a direct injection type internal combustion engine that injects fuel toward the spark plug.

(Embodiment 8)
A flow generating device provided in an intake port, having a combustion chamber into which air is sucked, a fuel injection valve that directly supplies fuel to the combustion chamber, an ignition plug that ignites the fuel, and a piston that changes the volume of the combustion chamber An injection control means configured to generate air flow in the combustion chamber and thereby guide the spray in the direction of the spark plug, and to control the fuel injection valve so as to divide and inject the fuel necessary for combustion into a plurality of times A cylinder injection type internal combustion engine provided with

(Embodiment 9)
9. The direct injection internal combustion engine according to the eighth embodiment, wherein the injection control means performs control so that fuel is divided and injected into a plurality of compression strokes in a low rotation and low load stratified operation region.

(Embodiment 10)
The direct injection internal combustion engine according to embodiment 8 or 9, wherein the injection control means controls the injection timing of each time so that the spray divided into a plurality of times passes continuously through the spark plug without being interrupted.

(Embodiment 11)
The injection control means generates a fuel spray flow from the fuel injection valve toward the spark plug in the preceding injection, and controls the fuel injection timing so as to guide the fuel spray by the subsequent injection to the spark plug by the fuel flow. The direct injection internal combustion engine according to any one of Embodiments 8 to 10.

(Embodiment 12)
The injection control means controls the fuel injection valve to inject fuel by one opening during a single fuel injection timing from the fuel injection valve at low engine speed and low load. The direct injection internal combustion engine according to any one of Embodiments 8 to 11, which uses a narrow-angle fuel injection valve having a penetration that only reaches the spark plug.

(Embodiment 13)
The direct injection internal combustion engine according to any one of embodiments 8 to 12, wherein the fuel injection valve is provided in the center of the combustion chamber and injects fuel from the upper portion of the combustion chamber into the combustion chamber.

(Embodiment 14)
The direct injection internal combustion engine according to any one of Embodiments 8 to 13, wherein the fuel injection valve is an upstream swirler type fuel injection valve.

(Embodiment 15)
The direct injection internal combustion engine according to any one of embodiments 8 to 14, wherein the fuel injection valve is a fuel injection valve that is driven at a voltage equal to or lower than a voltage generated by a battery mounted on the internal combustion engine.

The tumble guide cylinder injection engine perspective view. A tumble guide cylinder injection engine sectional view. (A), (b), (c) is a figure for demonstrating the difference in the spray characteristic of collective injection and two injections. Drawing for demonstrating the injection method in each driving | operation area | region. The injection method map by rotation speed-load. The flowchart of the injection method selection. Drawing for explaining composition of an engine control unit. The figure for demonstrating weakly stratified air-fuel | gaseous mixture distribution (large interval of 1st and 2nd injection) by 2 times of injection. The figure for demonstrating the air flow to the plug direction produced | generated by 1st injection. The figure for demonstrating the weak stratified gas mixture distribution (the space | interval of the 1st and 2nd injection is small) by 2 injections. The drawing for explaining the relationship between the crank angle and the air-fuel mixture concentration near the plug. The figure for demonstrating the influence which the cylinder pressure at the time of injection has on spraying. The figure for demonstrating the optimal value of the injection space | interval D1. The figure for demonstrating the optimal value of injection ratio T1 / T2. Drawing for demonstrating the relationship between an injection period and a fuel flow volume. The figure for demonstrating the case where the injector of a narrow angle spray is applied to the tumble guide cylinder injection engine. The figure for demonstrating the case where twice injection is applied to a direct injection cylinder direct injection engine. The figure for demonstrating the case where twice injection is applied to a wall guide cylinder injection engine. The figure for demonstrating the case where twice injection is applied to a flat piston type cylinder injection engine. (A), (b) is drawing for demonstrating the principal part of an injector. (A) is a drawing for explaining the configuration of the injector, (b) is a drawing for explaining the configuration of the control circuit of the injector, and (c) is a drawing for explaining the operation of the injector. The figure for demonstrating the principal part of a deflection | deviation spray type injector.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Injector, 2 ... Coil, 3 ... Plunger, 4 ... Swirler, 10 ... Intake valve, 21 ... Air flow control valve, 30 ... Engine, 31 ... Piston, 32 ... Spark plug, 50 ... Air flow, 60 ... Spraying, 111: Exhaust valve.

Claims (2)

It has an injection valve that is arranged obliquely to the cylinder head and injects fuel directly into the combustion chamber, and the spray shape is configured so that a part of the spray injected from the fuel injection valve is directed to the electrode direction of the spark plug In a control device for an internal combustion engine that performs stratified combustion by injecting fuel during the compression stroke,
During stratified combustion, when the engine speed is higher than a predetermined value, one injection is performed during the compression stroke, and when the engine speed is lower than the predetermined value, two or more injections are performed during the compression stroke. Control device.   The control apparatus according to claim 1, wherein the internal combustion engine includes a gas flow generation unit that generates a vertical vortex in the combustion chamber.

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