A FUEL INJECTION TYPE INTERNAL COMBUSTION ENGINE

Abstract: An engine comprising a piston having a cavity formed on the top face thereof. A projection having an impingement face at the top thereof is formed at the center of the cavity. Fuel is injected from a fuel injector toward the impingement face to form a richer air-fuel mixture around the projection. A spark plug or a glow plug is arranged to ignite the richer air-fuel mixture at the end of the compression stroke.

Description: 1. Field of the invention The present invention relates to a fuel injection type internal combustion engine of the kind defined by the precharacterizing features of claim 1. 2. Description of the Related art An internal combustion engine of the kind defined above is known from the JP-A-59 211 716. Fuel is injected from the injection nozzle towards the adjacent impingement face of the projection formed on the bottom wall of the cavity at the top face of the piston so that the angle of fuel spray becomes equal about 15° through 20°. At this time a part of the fuel thus injected is divided into fine particles, and thus the first stage atomizing operation is carried out. Then the fuel impinges upon the impingement face and the flow direction of the fuel is deflected so that it spreads radially outwardly from the impingement face. This fuel flow is shaped in the form of a conical thin film of fuel when it leaves the outer periphery of the impingement face. Then this thin film is torn due to the shearing force of air and divided into fine particles, and thus the second stage atomizing operation is carried out. Although the thermal efficiency of this known internal combustion machine, due to the two stage atomizing operation thereof, is superior to the type of internal combustion machines, i.e. known from the WO-A-8 500 197, having the fuel injected from the injection nozzle in all radial directions, there remains the need for further improving the thermal efficiency of that internal combustion machine. SUMMARY OF THE INVENTION The object of the present invention is to provide an internal combustion engine of the kind defined at the preamble in which the thermal efficiency is further improved. This object is attained by the characterizing features of claim 1. Advantageous developments of the invention are given in the subclaims. The thermal efficiency of the internal combustion engine in question is further improved by means of a single stage atomization of substantially all the injected fuel at the impingement face, exclusively, thereby forming the air-fuel mixture layer only around the projection at the top face of the piston. The present invention may be more fully understood from the description of preferred embodiments of the invention set forth below, together with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS In the Drawings: Fig. 1 is a cross-sectional side view of an embodiment of an internal combustion engine according to the present invention; Fig. 2 is a cross-sectional plan view of the cylinder head illustrated in Fig. 1; Fig. 3 is a cross-sectional view of a projection, illustrating various possible shapes of the projection; Fig. 4 is a flow chart of the process for the control of fuel injection and ignition; Fig. 5 is a diagram illustrating a map for the start timing of the fuel injection; Fig. 6 is a diagram illustrating a map for the ignition timing; Fig. 7 is a diagram illustrating injection timing; Fig. 8 is a diagram illustrating ignition timing; Fig. 9 is a cross-sectional side view of the engine at the time of a start of a fuel injection; Fig. 10 is a cross-sectional side view of the engine at the time of ignition; Fig. ll is a diagram illustrating thermal efficiency; Fig. l2 is a cross-sectional side view of another embodiment of the engine according to the present invention; Fig. l3 is a cross-sectional side view of a further embodiment of the engine according to the present invention; Fig. l4 is a cross-sectional side view of a still further embodiment of the engine according to the present invention; Fig. l5 is a cross-sectional side view of yet another further embodiment of the engine according to the present invention; Fig. l6 is a flow chart of the process for the control of a glow plug; Fig. l7 is a diagram illustrating the relationship between the output current of the glow plug and the engine load; Fig. l8 is a diagram illustrating the relationship between a desired current and the engine load; Fig. l9 is a cross-sectional side view of a further embodiment of the engine according to the present invention; Fig. 20 is a cross-sectional side view of a still further embodiment of the engine according to the present invention; Fig. 2l is a cross-sectional side view of the piston, illustrating various possible modifications of the impingement member; Fig. 22 is a plan view of the piston, illustrating various possible shapes of the cavity; Fig. 23 is a plan view of the piston, illustrating a possible arrangement of the cavity; Fig. 24 is a cross-sectional side view of a still further embodiment of the engine according to the present invention; Fig. 25 is a cross-sectional side view of the piston, illustrating various possible cross-sectional shapes of the cavity; Fig. 26 is a cross-sectional plan view of yet another embodiment of the engine according to the present invention; Fig. 27 is a diagram illustrating the opening degree of the air control valves; Fig. 28 is a cross-sectional side view of a further embodiment of the engine according to the present invention; Fig. 29 is a cross-sectional side view of a still further embodiment of the engine according to the present invention; Fig. 30 is a cross-sectional side view of yet another embodiment of the engine according to the present invention; Fig. 31 is a cross-sectional side view of a further embodiment of the engine according to the present invention; Fig. 32 is a cross-sectional side view of a still further embodiment of the engine according to the present invention; Fig. 33 is a cross-sectional side view of a still further embodiment of the engine according to the present invention; and Fig. 34 is a cross-sectional plan view of the engine, taken along the line XXXIV-XXXIV in Fig. 33. DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to Figures 1 and 2, reference numeral 1 designates a cylinder block, 2 a piston reciprocally movable in the cylinder block 1, 3 a cylinder head fixed to the cylinder block 1, and 4 a combustion chamber formed between the piston 2 and the flat inner end wall 3a of the cylinder head 3; 5 designates a pair of intake valves, 6 a pair of intake passages, 7 a pair of exhaust valves, and 8 an exhaust passage. A cavity 9 having a circular cross-section is formed in the central portion of the flat top face of the piston 2. The cavity 9 has a cylindrical circumferential wall 9a and a substantially flat bottom wall 9b. A projection 10 projecting toward the cylinder head 3 is formed on the central portion of the bottom wall 9b. The projection 10 has an impingement face 10a having a circular shape and extending in parallel to the top face of the piston 2 and has a frustum-shaped circumferencial wall 10b having a cross-sectional area which increases downward. In the embodiment illustrated in Fig. 1, the impingement face 10a is located on the axis of the cylinder. The impingement face 10a may be formed so that it has a flat shape as illustrated in Fig. 3(a), a concave shape having a concaved central portion as illustrated in Fig. 3(b), or a convex shape convexing toward the cylinder head 3, as illustrated in Fig. 3(c). A fuel injector 11 is arranged at the center of the inner end wall 3a of the cylinder head 3. This fuel injector 11 comprises a single nozzle 12, a needle 13 controlling the opening operation of the nozzle 12, and a piezoelectric element 14 for actuating the needle 13. When a voltage is applied to the piezoelectric element 14, the piezoelectric element 14 expands in the longitudinal direction thereof, and the opening operation of the nozzle bore 12 is carried out by moving the needle 13 in the longitudinal direction. Note, instead of the fuel injector 11 operated by the piezoelectric element 14, a conventional fuel injector operated by a solenoid, or a conventional fuel injector having a needle actuated by a discharge pressure of a fuel injection pump may be used. The piezoelectric element 14 of the fuel injector 11 is connected to an electronic control unit 20, and thus the fuel injecting operation from the fuel injector 11 is effected by the output signal from the electronic control unit 20. A spark plug l5 is mounted on the cylinder head 3. The spark gap l5a of the spark plug l5 is arranged to be very close to the circumferential wall l0b of the projection l0 when the piston l5 reaches top dead center (TDC) as illustrated in Fig. l. The electronic control unit 20 is constructed as a computer and comprises a ROM (read only memory) 22, a RAM (random access memory) 23, a CPU (microprocessor, etc.) 24, an input port 25, and an output port 26. The ROM 22, the RAM 23, the CPU 24, the input port 25, and the output port 26 are interconnected by a bidirectional bus 2l. A crank angle sensor 27 and an engine speed sensor 28 are connected to the input port 25. The crank angle sensor 27 produces an output signal indicating that the piston 2 in, for example, No. l cylinder, is at TDC, and thus the cylinder at which the injecting operation of fuel should be carried out is determined from the output signal of the crank angle sensor 28. The engine speed sensor 28 produces an output pulse at each 30 degree rotation of the crankshaft (not shown) of the engine. Therefore, it is possible to calculate the present crank angle (CA) and the engine speed from the output signal of the engine speed sensor 28. A load sensor 30 is connected to an accelerator pedal 29 and connected the input port 25 via an AD converter 3l. The load sensor 30 produces an output voltage which is proportional to the depression of the accelerator pedal 29. The output port 26 is connected to the piezoelectric element l4 of the fuel injector ll via a drive circuit 32 and connected to the spark plug l5 via a drive circuit 33 and an ignitor 34. The fuel injection and ignition process will be hereinafter described with reference to Fig. 4. Referring to Fig. 4, in step 40, the engine speed NE calculated from the output pulses of the engine speed sensor 28 is input to the CPU 24, and the output signal of the load sensor 30, which represents the load of the engine P, is also input to the CPU 24. Then, in step 4l, the amount of fuel to be injected from the fuel injector ll is calculated from, for example, the engine load P. Then, in step 42, the start timing of the fuel injection is obtained from the engine speed N and the engine load P. The relationship between the start timing of the fuel injection I and N, P is stored in the ROM 22 in the form of a map as illustrated in Fig. 5, and thus, in step 42, the start timing of the fuel injection I is obtained from the relationship stored in the ROM 22. Then, in step 43, the stop timing of the fuel injection is calculated from the start timing of the fuel injection I and the amount of fuel to be injected calculated in step 4l. Then, in step 44, the ignition timing is obtained from the engine speed N and the engine load P. The relationship between the ignition timing ϑ and N, P is stored in the ROM 22 in the form of a map as illustrated in Fig. 6, and thus, in step 44, the ignition timing ϑ is obtained from the relationship stored in the ROM 22. Then, in step 45, data representing the start timing of the fuel injection I, the stop timing of the fuel injection, and the ignition timing ϑ is output to the output port 26, and the fuel injecting and igniting operations are carried out on the basis of this data. Figure 7 illustrates an example of the fuel injection timing where methanol is used as the fuel, and Fig. 8 is illustrates an example of the ignition timing where methanol is used. In Fig. 7, line A₀ indicates the start timing of the fuel injection when the engine is operating under a heavy load, and line A₁ indicates the stop timing of the fuel injection where the engine is operating under a heavy load. Consequently, the arrow X in Fig. 7 indicates the length of time during which the injecting operation is carried out when the engine is operating under a heavy load. In addition, in Fig. 7, line B₀ indicates the start timing of the fuel injection where the engine is operating under a light load, and line B₁ indicates the stop timing of the fuel injection where the engine is operating under a light load. Consequently, the arrow Y in Fig. 7 indicates the length of time during which the injecting operation is carried out when the engine is operating under a light load. In Fig. 8, line C indicates the ignition timing where the engine is operating under a heavy load, and line D indicates the ignition timing where the engine is operating under a light load. As understood from Fig. 7, when the engine is operating under a heavy load, the start timing of the fuel injection occurs about l00 degree before TDC, that is, l00° BTDC. As mentioned above, Fig. 7 illustrates an example of the fuel injection timing. Consequently, the start timing of the fuel injection under a high load operating state may be slightly retarded relative to l00° BTDC or slightly advanced relative to l00° BTDC. In addition, where fuel other than methanol, that is, fuel such as gasoline, is used, the start timing of the fuel injection under a heavy load operating state may occur at about l80° BTDC. Accordingly, it is apparent that the start timing of the fuel injection is considerably advanced compared with the timing of the fuel injection adopted when methanol is used in a conventional engine. Figure 8 indicates another example of the ignition timing, showing that, even when methanol is used, the ignition timing in some engines is different from that shown in Fig. 7. In addition, if fuel other than methanol is used, the ignition timing is also different from that shown in Fig. 8, and is in accordance with the kind of fuel used. In the engine according to the present invention, the compression ratio can be made higher than l2:l, and the engine illustrated in Fig. l has a compression ratio of l6.2:l. According to the present invention, even if the engine has a high compression ratio, it is possible to obtain satisfactory combustion without knocking. A method of forming and igniting an air fuel mixture will be hereinafter described with reference to Figs. 9 and l0. Figure 9 illustrates the start of the injecting operation of fuel from the nozzle bore l2 of the fuel injector ll. The nozzle bore l2 is directed toward the impingement face l0a, and thus a large part of the fuel injected from the nozzle bore l2 impinges upon the impingement face l0a. That is, since the nozzle bore l2 is constructed as a single nozzle, a large part of the fuel injected from the nozzle bore l2 travels toward the impingement face l0a in the form of liquid fuel without becoming widely spread. As mentioned above, since a large part of the fuel injected from the nozzle bore l2 travels in the form of liquid fuel, the fuel thus injected has a strong penetrating force. Consequently, even if the distance between the nozzle bore l2 and the impingement face l0a is large, a large part of the fuel injected from the nozzle bore l2 reaches the impingement face l0a. The fuel impinging upon the impingement face l0a is broken up into fine particles and spread in the radial direction of the piston 2. However, since the fuel injected from the nozzle bore l2 has a downward inertia force, the fuel spreading in the radial direction travels toward the bottom wall 9b of the cavity 9 along the circumferential wall l0b of the projection l0, as illustrated by the arrow F in Fig. 9. Consequently, an area in which the density of the fuel is high is formed around the projection l0. Then, since the fuel around the projection l0 gradually spreads in the radial direction within the cavity 9, an air fuel mixture which gradually becomes lean toward the circumferential wall 9a of the cavity 9 from the circumferential wall l0a of the projection l0 is formed in the cavity 9. Since an air fuel mixture or an air in the cavity 9 is pushed downward while the piston 2 is moving upward, the air-fuel mixture and the air in the cavity 9 do not flow out upward from the cavity 9. Consequently, an air-fuel mixture layer is formed in the cavity 9, and only air exists in the combustion chamber 4 above the top face of the piston 2. Thus, the interior of the combustion chamber 4 is stratified. When the engine is operating under a heavy load, the start timing of the fuel injection is advanced, and thus the vaporizing and spreading of the fuel in the cavity 9 is sufficiently advanced when the piston 2 approaches TDC. Therefore, at this time, the interior of the cavity 9 is filled with an air-fuel mixture. Conversely, when the engine is operating under a light load, the start timing of fuel injection is retarded. Consequently, the spreading of the fuel in the cavity 9 is not sufficiently advanced when the piston 2 approaches TDC. Therefore, at this time, a rich fuel mixture layer is formed around the projection l0, and a doughnut shaped air layer is formed around the rich fuel mixture layer. Note, in either operating state of the engine (heavy load or light load), an air-fuel mixture layer which is richer than the mixture in the other area of the cavity 9 is formed in the area around the projection l0. Figure l0 illustrates the start of the igniting operation. As mentioned above, a ring shaped rich air-fuel mixture layer is formed around the circumferential wall l0b of the projection l0 as illustrated by the broken line in Fig. l0, and the spark gap l5a of the spark plug l5 is arranged so that it is positioned within this rich air-fuel mixture layer when ignition is effected. As soon as the rich air-fuel mixture in the region G is ignited by the spark plug l5, a flame instantaneously spreads over the entire area of the rich air-fuel mixture layer. Then, the flame spreads in the cavity 9 in the radial direction and burns the air-fuel mixture in the cavity 9. Since the flame spreads from the central portion of the cavity 9 toward the peripheral portion thereof as mentioned above, the flame propagating distance becomes shorter, and the burning velocity is increased. As a result, the thermal efficiency is improved, and the amount of HC and CO produced is reduced. In addition, as mentioned above, since only air exists in the combustion chamber 4 above the top face of the piston 2, when the piston 2 approaches TDC as illustrated in Fig. l0, only air exists in the corner K of the combustion chamber 4 between the peripheral portion of the top face of the piston 2 and the flat inner wall of the cylinder head 3. Knocking occurs in such a way that, when the combustion is started and the pressure in the combustion chamber 4 increased, an air-fuel mixture existing in the corner K is compressed, causing the self-ignition of the air-fuel mixture. However, in the present invention, since only air exists in the corner K, the self-ignition can not occur in the corner K, and thus knocking does not occur. Therefore, in the present invention, it is possible to increase the compression ratio, and accordingly considerably increase the thermal efficiency. Figure ll illustrates the thermal efficiency where methanol is used as the fuel in the engine illustrated in Fig. l. From Fig. ll, it will be understood that the thermal efficiency is considerably increased compared with the case where methanol is used in a conventional engine. In the engine according to the present invention, as mentioned above, a rich air-fuel mixture layer is formed around the circumferential wall l0b of the projection l0 irrespective of the engine load, and the mixture in the rich air-fuel mixture layer is ignited by the spark plug l5. Consequently, it is possible to obtain a stable ignition of the air-fuel mixture and a successive stable combustion. Therefore, it is possible to obtain a stable idling operation of the engine without the generation of misfiring, and it is also possible to improve the thermal efficiency and reduce the amount of HC produced. In addition, in the engine according to the present invention, a throttle valve is not arranged in the intake passages 6, and the engine load is controlled by the amount of fuel injected from the fuel injector ll. Accordingly, since a throttle valve is not arranged in the intake passages 6, it is possible to improve the thermal efficiency when the engine is operating under a partial load. Furthermore, in the present invention, to prevent knocking, the engine is constructed so that only air exists in the combustion chamber 2 above the top face of the piston 2. To ensure than only air exists in the combustion chamber 2 above the top face of the piston 2, the entire amount of fuel injected from the fuel injector ll is introduced into the cavity 9. Consequently, it is possible to widen the spray angle α (Fig. 3) of the fuel so that the entire amount of fuel injected from the fuel injector ll travels toward the cavity 9 when the piston 2 is positioned at a crank angle (CA) corresponding to the most advanced starting time for the fuel injection. However, even if the spray angle α is widened as mentioned above, preferably a large part of fuel injected from the fuel injected from the fuel injector ll is impinged on the impingement face l0a. Although it is sufficient to ensure that the entire amount of fuel injected from the fuel injector ll is introduced into the cavity 9, if a large amount of fuel is injected from the fuel injector ll, the injected fuel must be fed into the cavity 9 at an early stage of the compression stroke. By starting the feed of the injected fuel into the cavity 9 at an early stage of the compression stroke, enough time is left before the ignition of the fuel by the spark plug l5. During this time, the spreading of the injected fuel is sufficient, and at the same time, the vaporization of the injected fuel is satisfactory promoted. Figure l2 through 34 illustrate various further embodiments of the present invention, as successively described hereinafter. Referring to Fig. l2, a cooling water passage l6 is formed in the cylinder head 3, and a hollow tube l7 made of copper and extending through the cooling water passage l6 is fitted into the cylinder head 3. The fuel injector ll is fitted into the hollow tube l7 so that the fuel injector ll is cooled by the cooling water flowing within the cooling water passage l6. In the present invention, it is important that a large part of the fuel injected from the fuel injector ll impinges on the impingement face l0a. To this end, the fuel injected from the fuel injector ll must have a strong penetrating force and thus will not be widely spread. However, if the temperature of the fuel injector ll is increased, fuel is atomized when flowing out from the nozzle bore l2. As a result, the fuel injected from the nozzle bore l2 is widely spread, and thus the penetrating force of the fuel is lessened. However, this results in a problem whereby it is impossible to cause a large apart of the injected fuel to impinge on the impingement face l0a. To eliminate the problem, in the embodiment illustrated in Fig. l2, the fuel injector ll is cooled by the cooling water. Referring to Fig. l3, a coolant chamber l6a is formed around the hollow tube l7 in the cylinder head 3 and connected to a coolant supply pump l6d via a coolant passage l6b and a cooler l6c. In this embodiment, a coolant such as cooling water, lubricating oil or air is fed into the cooler l6c by a coolant supply pump l6d and cooled in the cooler l6c. The coolant is compulsorily fed into the coolant chamber l6a, and thus the fuel injector ll is compulsorily cooled by this coolant. The coolant then flows out from an outlet l6e. In this embodiment, since the fuel injector ll is compulsorily cooled by the coolant, it is possible to further prevent a high temperature at the fuel injector ll. In the embodiment illustrated in Fig. l4, instead of a spark plug, a glow plug l8 is used. This glow plug l8 is positioned within the rich air-fuel mixture layer G when ignition is carried out. That is, the glow plug l7 is arranged to be close to the circumferential wall l0b of the projection l0 when the piston 2 approaches TDC. In this embodiment, the ignition of the rich mixture in the rich air-fuel mixture layer G is carried out, when this piston 2 moves upward and the rich air-fuel mixture layer G comes into contact with the tip of the glow plug l7. As mentioned above, in the present invention, it is possible to ignite the rich mixture in the rich air-fuel mixture layer G by using the glow plug l8. However, the temperature of the glow plug l8 is changed in accordance with a change in the engine load. That is, when the engine is operating under a heavy load, since the temperature of burnt gas around the glow plug l8 becomes high, the temperature of the glow plug l8 also becomes high, and when the engine is operating under a light load, since the glow plug l8 is cooled by excess air in the combustion chamber 4, the temperature of the glow plug l8 also becomes low. Also, an air-fuel mixture in the rich air-fuel mixture layer G becomes slightly lean as the engine load becomes low, and therefore, the rich air-fuel mixture is less easily ignited as the engine load becomes low. Consequently, in order to easily ignite the rich air-fuel mixture, the temperature of the glow plug l5 must be increased as the engine load becomes low. Note, as mentioned above, when the engine is operating under a light load, the temperature of the glow plug l5 itself becomes low, but a high temperature is required for the glow plug l5 to easily ignite the rich air-fuel mixture. Therefore, where the temperature of the glow plug l5 is not controlled as in the embodiment illustrated in Fig. l4, it is necessary to continuously feed a large electrical power to the glow plug l5 so that the temperature of the glow plug l5 is sufficiently high when the engine is operating under a light load. However, if a large electrical power is continuously fed into the glow plug l5, when the engine is operating under a heavy load, the temperature of the glow plug l5 becomes extremely high, beyond a necessary temperature. Consequently, a problem occurs in that the consumption of electrical power is increased. Figure l5 illustrates an embodiment in which the temperature of the glow plug l8 is controlled and maintained at an optimum temperature which is changed in accordance with a change in the engine load. Referring to Fig. l5, a temperature detector l9 illustrated by a broken line is arranged in the glow plug l8 to detect the temperature of the glow plug l8. In the embodiment illustrated in Fig. l5, the temperature detector l9 is constructed by a thermocouple. However, any other temperature detector may be adopted. The temperature detector l9, i.e., the thermocouple, is connected to the input port 25 via an AD converter 35. Figure l6 illustrates a flow chart of the process for controlling the glow plug l8. Referring to Fig. l6, in step 50, the value of the output current of the temperature detector l9 is input to the CPU 24. As illustrated in Fig. l7, the output current I of the temperature detector l9 is increased as the temperature T of the glow plug l8 is increased. Then, in step 5l, a desired current I₀ is calculated on the basis of the output signal of the load sensor 30. Figure l8 illustrates the relationship between the desired current I₀ and the engine load P. As illustrated in Fig. l8, the desired current I₀ becomes low as the engine load P becomes high. The relationship illustrated in Fig. l8 is stored in the ROM 22. Then, at step 52, it is determined whether the output current I is larger than the desired current I₀. If I > I₀ , the routine goes to step 53, and the current X fed to the glow plug l8 is decreased by a fixed value α. Conversely, if I ≦ I₀ , the routine goes to step 54, and it is determined whether the output current I of the temperature detector l9 is smaller than the desired current I₀. If I < I₀ , the routine goes to step 55, and the current X fed to the glow plug l9 is increased by a fixed value α. Consequently, the current X fed into the glow plug l9 is controlled so that the output current I of the temperature detector l9 becomes equal to the desired current I₀ , that is, the temperature T of the glow plug l8 becomes high as the engine load L becomes low. Then, in step 56, data representing the current X fed to the glow plug l8 is output to the output port 26, and the current X fed to the glow plug l8 is controlled by this data. In the embodiment illustrated in Fig. l5, the temperature of the glow plug l8 is controlled in response to a change in the engine load L. However, the temperature of the glow plug l8 also may be controlled in response to changes in other parameters such as the atmospheric pressure, the temperature of the outside air, the temperature of the cooling water of the engine, and the like. In the embodiment illustrated in Fig. l9, the spark plug l5 is provided in addition to the glow plug l8 equipped with the temperature detector l9. In this embodiment, the rich air-fuel mixture is ignited by both the spark plug l5 and the glow plug l8. However, the igniting operation by the spark plug l5 and the glow plug l8 may be controlled so that the ignition is carried out by only the glow plug l8 when the engine is operating under a light load, and that the ignition is carried out by only the spark plug l5 when the engine is operating under a heavy load. In an embodiment illustrated in Fig. 20, the projection l0 comprises a small projection l0c projecting slightly upward from the bottom wall 9b of the cavity 9, and an impingement member 60 fixed to the small projection l0c. The impingement member 60 is made of a wear-proof material which is different from the material of the piston 2, and in addition, the impingement member 60 has a heat insulating construction so that the temperature of the impingement face l0a becomes high. That is, methanol has a large latent heat, and thus the impingement element l8 has a heat insulating construction so that the temperature of the impingement face l0d is not decreased too much due to the latent heat of methanol when methanol is used as the fuel. By maintaining a high temperature of the impingement face l0a, it is possible to promote the vaporization of the fuel which impinges upon the impingement face l0a. Figure 2l illustrated various modifications of the impingement members 60. Figure 22 illustrates various modifications of the contour shape of the cavity 9. In the embodiment illustrated in Fig. 22(A), the contour of the cavity 9 has an approximately square shape, and in the embodiment illustrated in Fig. 22(C), the contour of the cavity 9 has an approximately triangular shape. In addition, in the embodiment illustrated in Fig. 22(b), the cavity 9 has a cross shape. In an embodiment illustrated in Fig. 23, the impingement face l0a is eccentrically arranged relative to the axis of the cylinder, and fuel is injected toward the impingement face l0a. In the embodiments illustrated in Figs. 22 and 23, the distance between the impingement face l0a and the circumferential wall 9a, 9c of the cavity 9 is changed in accordance with the flame propagating direction, so that the combustion time can be controlled. In an embodiment illustrated in Fig. 24, the circumferential wall 9a of the cavity 9 has an annular rib 9d formed thereon and radially inwardly projecting from the upper end portion of the circumferential wall 9a. Figure 25 illustrates other various modifications of the cross-sectional shape of the cavity 9. In the embodiments illustrated in Fig. 25(A) and (B), the circumferential wall 9e, 9f of the cavity 9 has a conical shape having a cross-section which diverges towards the bottom wall 9b of the cavity 9 and, in the embodiment illustrated in Fig. 25(C), the circumferential wall 9g of the cavity 9 has a conical shape having a cross-section which converges toward the bottom wall 9b of the cavity 9. In an embodiment illustrated in Fig. 26, air control valves 6l are arranged in the intake passages 6. Figure 27 illustrates the relationship between the engine load P and the opening degree ϑ of the air control valves 4l. As illustrated in Fig. 27, the air control valves 6l are half open when the engine load P is low or zero, and the air control valves 6l are abruptly fully open when the engine load P is increased. As mentioned previously, in the present invention, it is necessary to form the rich air-fuel mixture layer G around the projection l0 (Fig. l0). However, if an extremely strong swirl motion or turbulence is created in the combustion chamber 4, it is difficult to form the rich air-fuel mixture layer G around the projection l0 in some engines, particularly when the amount of fuel injected from the fuel injector ll is small, that is, when the engine is operating under a light load. In such engines, preferably the air control valves 6l are closed to a half open position and the amount of air fed into the combustion chamber 4 reduced, so that an extremely strong swirl motion or turbulence is not created when the engine is operating under a light load. Figures 28 through 30 illustrate various modifications capable of creating a further rich air-fuel mixture around the spark gap l5a of the spark plug l5. That is, referring to Fig. 28, the impingement face l0a of the projection l0 is formed by an inclined face which is inclined downward toward the spark gap l5a of the spark plug l5. By inclining the impingement face l0a of the projection l0 toward the spark gap l5a of the spark plug l5, more fuel injected from the fuel injection ll can be introduced around the spark gap l5a of the spark plug l5, and thus it is possible to create a further rich air-fuel mixture around the spark gap l5a of the spark plug l5. In addition, as illustrated by the broken line in Fig. 28, only one half of the impingement face l0a which is positioned near the spark gap l5a of the spark plug l5, may be formed by an inclined face. In the embodiment illustrated in Fig. 29, the nozzle bore l2 of the fuel injector ll is directed to the peripheral portion of the impingement face l0a, which is positioned near the spark gap l5a of the spark plug l5. In this embodiment, since more fuel injected from the fuel injector ll is introduced around the spark gap l5a of the spark plug l5, it is possible to create a further rich air-fuel mixture around the spark gap l5a of the spark plug l5. In the embodiment illustrated in Fig. 30, the fuel injector ll is arranged at an opposite angle to the spark plug l5 with respect to the axis of the cylinder X, and fuel injected from the fuel injector ll is caused to obliquely impinge upon the impingement face l0a. In this embodiment, since more fuel injected from the fuel injector ll is introduced into a space around the circumferential wall l0a of the projection l0, which space is located on a spark gap side, it is possible to create a further rich air-fuel mixture around the spark gap l5a of the spark plug l5. As mentioned above, in the embodiments illustrated in Figs. 28 through 30, since a further rich air-fuel mixture can be formed around the spark gap l5a of the spark plug l5, it is possible to further improve the ignitability. Figure 3l illustrates an embodiment which can prevent carbon from adhering to the impingement face l0a. Where fuel having a large latent heat such as methanol is used, since the impingement face l0a is cooled due to the latent heat of the fuel, carbon is less easily adhered to the impingement face l0a. Conversely, where fuel having a small latent heat such as gasoline is used, since the impingement face l0a is not sufficiently cooled, carbon has a tendency to easily adhere to the impingement face l0a. If carbon adheres to the impingement face l0a, when fuel impinges upon the impingement face l0a, the fuel is less easily spread in the radial direction, and thus only the air-fuel mixture formed around the impingement face l0a becomes excessively rich. Consequently, it is necessary to prevent carbon from adhering to the impingement face l0a as much as possible. In the embodiment illustrated in Fig. 3l, the fuel injector ll is arranged so that the clearance S between the impingement face l0a and the top face of the fuel injector ll becomes extremely small, for example, less than 2 mm, when the piston 2 reaches TDC. If the clearance S becomes less than about 2 mm when the piston 2 reaches TDC, the clearance S becomes smaller than the quench distance. As a result, since flame can not propagate into the clearance S, it is possible to prevent carbon from adhering to the impingement face l0a. In addition, in the embodiment illustrated in Fig. 3l, a space 62 is formed in the projection l0. By spraying a lubricating oil into the space 62 and cooling the impingement face l0a, it is possible to further present carbon from adhering to the impingement face l0a. Figure 32 illustrates the case where the present invention is applied to a 2 stroke engine. In Fig. 32, similar components are indicated by the same reference numerals used in Fig. l. Referring to Fig. 32, reference numeral 63 designates a pair of exhaust valves, 64 a pair of exhaust ports, and 65 a plurality of scavenge ports formed on the wall of the cylinder bore of the cylinder block l. When the scavenge ports 65 are uncovered by the piston 2, fresh air is fed into the combustion chamber 4 from the scavenge ports 65. At this time, burnt gas in the combustion chamber 4 is pushed out into the exhaust ports 64 via the exhaust valves 63, which are open. Subsequently, when the scavenge ports 65 are covered by the piston 2, and the exhaust valves 63 are closed, the compression stroke is started. When the piston 2 approaches TDC, as illustrated by the dashed-dotted line in Fig. 32, a rich air-fuel mixture formed around the projection l0 is ignited by the spark plug l5. Figures 33 and 34 illustrate the case where the present invention is applied to a Schnürle type 2 stroke engine. In Figs. 33 and 34, reference numeral 66 designates scavenge ports, and 67 an exhaust port. When the scavenge ports 66 are uncovered by the piston 2, fresh air is fed into the combustion chamber 4 from the scavenge ports 66. At this time, burnt gas in the combustion chamber 4 is pushed out into the exhaust port 67. Subsequently, when the scavenge ports 66 and the exhaust port 67 are covered by the piston 2, the compression stroke is started. When the piston 2 approaches TDC, as illustrated by the dashed-dotted line in Fig. 33, a rich air-fuel mixture formed around the projection l0 is ignited by the spark plug l5. In the engine according to the present invention, various fuels such as methanol, other alcohols, gasoline, liquefied petroleum gas, natural gas, and a mixture thereof can be used. Particularly in the present invention, since substantially all of the fuel injected from the fuel injector ll is introduced into the cavity 9, the lubricating oil adhering to the wall of the cylinder bore is not diluted by the fuel thus injected. Consequently, no matter which of the above-mentioned fuels is used, it is possible to prevent corrosion of the wall of the cylinder bore. In addition, since the fuel injector ll having only the single nozzle bore l2 can be used, the nozzle bore l2 will not be clogged, and in addition, it is not necessary to excessively increase the injection pressure. Consequently, it is possible to improve the reliability and durability of the engine, and lower the manufacturing cost of the engine. In addition, it has been proven that, where methanol is used, no particulates exist in the exhaust gas, and that the amount of HC, CO and NOx produced is extremely small. Furthermore, in the present invention, a gaseous fuel may be used. At this time, a large part of gaseous fuel must impinge upon the impingement face l0a so that only air exists in the corner K (Fig. l0) between the flat inner wall of the cylinder head 3 and the peripheral portion of the top face of the piston 2. According to the present invention, since knocking does not occur, it is possible to considerably increase the compression ratio of the engine, and as a result, since the thermal efficiency is considerably improved, it is possible to considerably improve the fuel consumption.

Claims: An internal combustion engine comprising: an engine body having at least one cylinder bore formed therein and having an inner end wall (3a) which closes one end of said at least one cylinder bore; a piston (2) reciprocally movable in said at least one cylinder bore and having a top face which faces said inner end wall (3a), said top face and said inner end wall (3a) defining a combustion chamber (4) therebetween, said top face having a cavity (9) formed thereon, said cavity (9) having a bottom wall (9b); a fuel injector (11); ignition means (15) arranged on said inner end wall (3a) to ignite a richer air-fuel mixture layer at the end of the compression stroke; and a projection (10) formed on the bottom wall (9b) of said cavity (9) within said cavity (9) and having an impingement face (10a) which faces said inner end wall (3a), said fuel injector (11) being arranged on said inner end wall (3a) and having a nozzle (12) directed toward said impingement face (10a) to cause at least part of fuel injected from said nozzle (12) to impinge upon said impingement face (10a) in the form of liquid fuel characterized in that substantially all of the fuel injected from said nozzle (12) is caused to impinge upon said impingement face (10a) in the form of liquid fuel so that the fuel is not substantially vaporized before it reaches the impingement face (10a), to thereby form said air-fuel mixture layer only around the projection (10). An internal combustion engine according to claim 1, wherein said inner end wall (3a) is formed by a flat wall. An internal combustion engine according to claim 1, wherein the top face of said piston is formed by a flat face, and said cavity (9) is formed on a central portion of the top face of said piston (2). An internal combustion engine according to claim 1, wherein the bottom wall (9b) of said cavity (9) is formed by a substantially flat wall. An internal combustion engine according to claim 1, wherein said cavity (9) has a circumferential wall (9a) surrounding said projection (10) and extending between the bottom wall (9b) of said cavity and the top face of said piston (2). An internal combustion engine according to claim 5, wherein the circumferential wall (9a) of said cavity (9) has a circular contour shape, and said impingement face (10a) is arranged at a center of said circular contour. An internal combustion engine according to claim 5, wherein the circumferential wall (9a) of said cavity (9) has a circular contour shape, and said impingement face (10a) is eccentrically arranged relative to a center of said circular contour. An internal combustion engine according to claim 5, wherein the circumferential wall (9a) of said cavity (9) has a polygonal contour shape, and said impingement face (10a) is arranged at a center of said polygonal shape. An internal combustion engine according to claim 5, wherein the circumferential wall (9a) of said cavity (9) has a substantially cylindrical shape. An internal combustion engine according to claim 9, wherein the circumferential wall (9a) of said cavity (9) has an annular rib (9d) radially inwardly projecting from an upper end of the circumferential wall (9a). An internal combustion engine according to claim 5, wherein the circumferential wall (9a) of said cavity (9) has a conical shape. An internal combustion engine according to claim 1, wherein said projection (10) is integrally formed on the bottom wall (9b) of said cavity (9). An internal combustion engine according to claim 12, wherein said projection (10) has a space therein for receiving a coolant. An internal combustion engine according to claim 1, wherein said projection (10) is formed by an impingement member (60) fixed to the bottom wall (9b) of said cavity (9). An internal combustion engine according to claim 14, wherein said impingement member (60) is made of a wear--proof material which is different from a material of said piston (2). An internal combustion engine according to claim 1, wherein said impingement face (10a) is formed by a flat face. An internal combustion engine according to claim 1, wherein said impingement face (10a) is formed by a concaved face. An internal combustion engine according to claim 1, wherein said impingement face (10a) is formed by a convexed face. An internal combustion engine according to claim 1, wherein said projection (10) has a circumferential wall (10b) and said ignition means (15) is arranged so as to be close to the circumferential wall (10b) of said projection (10) at the end of the compression stroke. An internal combustion engine according to claim 19, wherein the circumferential wall (10b) of said projection (10) has a frustum shape which diverges toward the bottom wall (9b) of said cavity (9). An internal combustion engine according to claim 19, wherein said impingemenet face (10a) has a portion which is inclined downward toward said ignition means (15). An internal combustion engine according to claim 19, wherein the nozzle (12) of said fuel injector (11) is directed to a portion of said impingement face (10a), which is positioned near said ignition means (15). An internal combustion engine according to claim 19, wherein said fuel injector (11) is arranged at an opposite angle to said ignition means (15) with respect to an axis of said cylinder bore. An internal combustion engine according to claim 1, wherein said fuel injector (15) is arranged to form a clearance less than 2 mm between said impingement face (10a) and the nozzle (12) of said fuel injector (11). An internal combustion engine according to claim 1, further comprising cooling means (16) for cooling said fuel injector. An internal combustion engine according to claim 25, wherein said cooling means (16) comprises a coolant passage (10b) surrounding said fuel injector (11). An internal combustion engine according to claim 26, wherein said cooling means (16) comprises a metallic hollow tube (17) extending through said coolant passage (16b), said fuel injector (11) being fitted into said hollow tube (17). An internal combustion engine according to claim 26, wherein said cooling means (16) comprises a cooler (16c) for cooling a coolant, and a pump (16d) for feeding the coolant into said coolant passage (16b) via said cooler (16c). An internal combustion engine according to claim 1, wherein said fuel injector (11) has a single nozzle (12). An internal combustion engine according to claim 1, wherein substantially all of the fuel injected from said fuel injector (11) is directed toward said cavity (9). An internal combustion engine according to claim 1, wherein the fuel injecting operation of said fuel injector (11) is started at about 60 degrees B.T.D.C. when the engine is operating under a heavy load. An internal combustion engine according to claim 31, wherein the fuel injecting operation of said fuel injecotr (11) is started at about 100 degrees B.T.D.C. when the engine is operating under a heavy load at a high speed.

Inventors: ONISHI, SIGERU
Applicants: NIPPON CLEAN ENGINE RESEARCH INSTITUTE CO., LTD.
Application year: 1987
Main classification: F02B23
IPC codes: F02B75, F02B23, F02B17