KR810001659B1 - Internal combustion engine - Google Patents

Abstract

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Description

Internal combustion engine

1 is a cross-sectional view showing a first embodiment of the present invention.

2 is a view in the direction of the arrow A-A of FIG.

3 is a view in the direction of the arrow B of FIG.

4 is a view in the direction of the arrow C-C of FIG.

5 is an engine output diagram provided in the explanation of the operation of the first embodiment.

6 is a sectional view showing a second embodiment of the present invention.

7 is a sectional view showing the principal parts of a third embodiment of the present invention.

8 is a sectional view showing the principal parts of a fourth embodiment of the present invention.

9 is a sectional view showing the principal parts of a fifth embodiment of the present invention.

10 is a sectional view showing the principal parts of a sixth embodiment of the present invention;

11 is an operation explanatory diagram of a sixth embodiment.

The present invention relates to an improvement in an internal combustion substrate, in particular an internal combustion engine for automobiles. In the conventional internal combustion engine for automobiles, since the opening degree of the throttle valve is small and the intake amount is small during the idle operation and the neck operation, the speed of the mixed gas flowing into the cylinder from the intake manifold in the intake stroke is low. Therefore, the swirl of the mixed gas in the cylinder is also weak. As a result, the vortex of the mixed gas remaining in the cylinder is weakened and the ignition and combustibility are lowered during the ignition which is usually performed at the final stage of the compression stroke. Therefore, in order to ensure stable operation of the engine, the performance is better than that of medium and high loads. It is necessary to supply a mixture gas having a small ratio, which not only leads to an increase in fuel cost, but also has a drawback of increasing CO and HC in the exhaust gas due to incomplete combustion of the rich mixture. In recent years, it has been proposed to combust a mixed gas sufficiently thinner than a theoretical mixing ratio for the purpose of reducing CO and HC in the exhaust gas of the engine, and also to reduce the NOx in the exhaust gas. Although a part of the gas is extracted from the exhaust system of the engine and mixed with the weight of the mixer to combust, it is proposed that in any case, the ignition and combustibility of the mixed gas will be lowered. There was a drawback that the drivabirity was lowered and the fuel cost worsened.

It is a main object of the present invention to provide an internal combustion engine of a passenger car, which can improve fuel costs, particularly in idle and light load driving.

Another object of the present invention is to provide a engine of a passenger car which can stably burn lean mixed gas which is difficult to operate stably under idle conditions and light loads in a conventional engine, and as a result, there are few harmful components in exhaust gas.

It is still another object of the present invention to stably combust a mixed gas containing a large amount of reflux exhaust gas, which is difficult to operate stably under idle conditions and light loads with a conventional engine, and as a result, It is to provide an engine of a passenger car which can reduce NOx.

Another object of the present invention is to provide a passenger car engine capable of stably burning a lean mixer or a mixer containing a large amount of reflux exhaust gas without accompanying poor performance such as deterioration of a large output, low operability, and poor fuel cost. It is another object of the present invention to provide a passenger car engine which can reduce harmful gas components in the exhaust gas from the conventional engine in the light ring driving region of the eye ring and the low speed low load.

The above-mentioned title of the present invention includes a combustion chamber having an intake port and an exhaust port, a main intake passage leading to the air fuel mixture gas generated by the mixed gas generating apparatus, and the combustion chamber described above. A spark plug attached to the cylinder head so that a spark interval is arranged at a predetermined position of the cylinder head, and an injection hole formed in the cylinder head forming the combustion chamber, a sub-intake passage connected to the injection hole, and a main intake passage described above. A gas supply source for supplying gas to the sub suction passage at a sufficient gas supply pressure even at a light load operation with a small opening of the throttle valve, and a sub intake valve for opening and closing the sub suction passage installed in the cylinder head. It is effectively achieved by the internal combustion engine, characterized in that it has an operating mechanism for opening the above-described intake stroke in the intake stroke period.

The gas supplied to the intake air passage is preferably air, but may be a mixed gas of fuel and air, or may be an exhaust gas of the engine itself. When the gas is air, the gas supply source is air, and in the case of a mixed gas, an intake manifold is suitable for the gas supply engine with a vaporizer and an exhaust manifold for exhaust gas. It becomes a gas supply source.

In the engine according to the present invention, the throttle opening degree is different, particularly during idling and at light load operation, so that the throttle valve has a large diaphragm action, the intake flow rate in the main intake passage is slow, the intake amount is low, and the intake air is low. In the stroke, the combustion chamber is at a high negative pressure, gas from the gas source is attracted to this powerful combustion chamber internal pressure, and is injected from the injection hole toward the set direction in the combustion chamber, and a strong vortex or turbulent flow is generated in the combustion chamber to increase the combustion speed. When the lean burn limit is extended and fuel economy is improved, and the above-mentioned jetting holes are applied around the spark interval of the spark plug disposed in the combustion chamber, the combustion gas is purged to improve the ignition performance. At the same time, the lean burn limit is extended by the isotope action.

Therefore, even if the mixing of the mixer is poor, the combustion chamber wall temperature is low, and the combustion property is poor, the lean mixed gas burning in the idling or light load operation range is reduced to the minimum and the increase in fuel cost is prevented. The maximum combustion temperature is lowered and the amount of NOx generated is extremely reduced.

When the exhaust gas reflux device is used in combination with the internal combustion engine of the present invention, it is possible to easily reduce the amount of NOx generated without setting the air-fuel ratio having poor controllability to a high value close to the combustion limit. Deterioration of the flammability and pre-flame wave velocity due to reflux is also improved by the above classification.

The above-mentioned title and other objects and advantages of the present invention will become apparent from the following description of embodiments of the present invention made with reference to the drawings. In addition, the same code | symbol is attached | subjected to the same or equal part in each drawing.

In the first embodiment of the present invention shown in FIG. 1 and FIG. 4, reference numeral 10 denotes a main body of an automobile gasoline internal combustion engine, 12 denotes a cylinder head, 14 denotes a cylinder block, and 16 denotes a Piston, 18 is combustion chamber, 20 is spark plug, 22 is intake port, 24 is exhaust port, 26 is main intake valve, 28 is intake manifold, 30 is a vaporizer and 32 is an air cleaner.

The injection hole 34 opened in the combustion chamber 18 is perforated in the cylinder head 12, and the equal injection hole is directed directly below the spark gap 36 of the spark plug 20, and at the same time the front of the piston 16. ) And is set in the piston 16 direction with a set angle of about 30 ° to 60 °, for example. In addition, the equal injection hole 34 is connected to the sub suction path 40 through the sub suction side 38.

The main intake side 26 and the side intake side 38 are mushroom sides driven together by the same talker arm 42, the rocker arms being fitted to the rocker shaft 44 and interlocked with a crankshaft of an engine not shown. And abutted by the cam 48 provided on the cam shaft 46 that is rotated. In addition, the arm part opposite to the contact surface of the rocker arm 42 to the cam 48 is bifurcated, and each of the branching parts is provided with adjustment screws 50 and 52, and the other adjustment screw ( 50) The end face abuts the top end face of the main intake side 26, and the other end of the adjusting screw 52 crosses the end end side of the sub intake side 38. As shown in FIG.

In addition, 54 and 56 are valve springs, 58 and 60 are spring seats, and 62 are valve guides of the intake side valves 38. The air cleaner 32 has a venturi 66 and a throttle valve in the vaporizer portion of the main air intake passage 64 which is connected to the intake port 22 via the vaporizer 30 and the intake manifold 28. 68) is arranged. An idle port 70 and a slawboard 72 are mainly installed on the inner wall of the intake passage near the fully closed position of the throttle valve 68, and the idle port 70, which supplies fuel during light load, and the idle port 70 is adjusted. The screw 74 is provided. On the other hand, the venturi 66 is provided with a main nozzle 76 which mainly supplies fuel to the heavy load.

An exhaust gas return passage 78, one end of which is connected to an exhaust manifold, for example, of an unillustrated engine, controls a flow rate of exhaust gas by detecting various operating states of the engine along the way. The other end is connected to the assembly part of the intake manifold 28 via 80. In addition, the sub intake passage 40 is connected to the main intake passage 64 upstream of the venturi 66 via the pipe 82.

According to the above configuration, most of the air sucked into the main intake passage 64 in the air cleaner 32 is mixed with fuel in the vaporizer 30 at a predetermined air-fuel ratio, and the combustion chamber 18 in the intake port 22. Is inhaled. On the other hand, a part of the intake air is guided to the injection hole 34 in the sub-intake passage 40 through the pipe 82, and is injected into the combustion chamber 18 from the copper injection hole (34).

The injection amount and the intensity of the jetting in the injection hole 34 change depending on the opening degree of the throttle valve 68, that is, the load of the engine. In other words, during idling or light load with a small throttle opening, the amount of the mixer supplied from the main intake passage 64 is small according to the aperture action of the throttle valve 68, and the combustion chamber 18 generates a high negative pressure during the intake stroke. Since the main air intake passage 64 upstream of the venturi 66 is approximately atmospheric pressure, a large amount of air is strongly ejected from the injection hole 34 into the combustion chamber 18 due to the pressure difference. As a result, the intake mixer in the combustion chamber 18 generates strong vortex or turbulence due to the above-described jet flow of air, and the mixer sucked in the main intake passage 64 by the mixing of air is stratified. It is diluted or it is diluted in heterogeneous half state.

In addition, since the jet flows through the vicinity of the same interval just below the flame interval 36 of the spark plug 20, the residual combustion gas near the flame interval 36 also flows and is evacuated, and near the flame interval 36. Fresh suction gas is introduced. Therefore, even in the ignition performed in the second half of the extrusion stroke, strong vortices or turbulences exist in a state where air and the mixer are distributed in a layered or half phase, and a suction mixed gas always flows near the flame gap 36. According to the experiment, the flame propagation speed is improved compared to the conventional engine, the fire limit is greatly expanded, the fuel efficiency is improved, and the output decreases and the operability is improved even when the gas mixture is thinned. I could confirm that.

In addition, in this embodiment, the inner diameter of the injection hole 34 is set to about 3 mm and the inner diameter of the sub intake passage 40 is set to about 5 mm, and the intake air amount supplied from the sub intake passage 40 in the light load operation region is the main intake air. It is set at about 10 to 20% of the intake air amount supplied from the passage 64. Moreover, the vaporizer 30 is adjusted so that the air-fuel ratio of the sum total of the intake air supplied from the main air intake path 64 and the sub intake air path 40 may acquire the characteristic as shown in FIG.

5 is an engine output line diagram in which the engine output line is held on the vertical axis, and the engine speed is set on the horizontal axis. A solid line A is an open output line of the throttle valve 68, and a solid line B is output at an idle opening degree of the throttle valve. The line and solid line C are the flat road running curves, the one-dot chain line is the back pressure line of the intake manifold negative pressure generated at the intake manifold 28, the two-dot chain line is the back throttle opening curve, the dashed line is an iso-fueled non-airline Represents the air-fuel ratio. In addition, the hatched part D indicates the light load operation area.

In the light load driving region indicated by the hatched portion D, the air-fuel ratio is adjusted to about 15 to 17, which is larger than the air-fuel ratio in the same region of a normal engine. The amount of exhaust gas sucked into the intake manifold 28 via the exhaust gas reflux passage 78 is controlled by the control valve 80, but the amount of exhaust gas reflux is adjusted to suppress the amount of NOx discharged within the set value. .

On the other hand, in the high load operating region with a large throttle opening degree, the diaphragm action by the throttle valve 68 is small and a large amount of the mixer is sucked into the combustion chamber 18 because the main air inlet passage 64 is provided, so that the intake path ( Although the injection amount and power output at 40) are lowered, the vortex effect of the injection air is also reduced, but in this case, the intake efficiency is high and a strong vortex or turbulent flow when the mixer flows from the intake port 22 into the combustion chamber 18. In addition, since the temperature of the inner wall of the combustion chamber 18 also increases, the flame propagation speed is high and the combustibility is good, even if a strong vortex or turbulence is not generated due to the classification in the injection hole 34.

As is clear from the above, according to the present embodiment, the combustion chamber 18 has a relatively low internal wall temperature, a poor combustion efficiency such as poor suction efficiency, and the combustion chamber is re-composed to the mixer in which a part of the exhaust gas is mixed in the light load operating region. (18) It is stably not only a mixer having a total air fuel ratio of 11 to 14 obtained by mixing air flowing in the injection hole 34, but also a poor combustible mixer having a lean mixer having a total air fuel ratio of about 15-21. At this time, a strong vortex or turbulent flow is generated by the strong air injection in the injection hole 34, and the injected air is mixed in a suitable layer or half state in the mixer similar to the main intake passage 64. As a result, the combustion speed is improved without increasing the amount of NOx generated, the combustion completion time is shortened, the fuel efficiency is reduced, and the operability is improved. Furthermore, HC, CO The introduction of emissions of unburned's also achieves the effect that reduction.

The second embodiment of the present invention shown in FIG. 6 is a switching valve 84 of air and exhaust gas in the middle of the pipe 82 communicating with the intake passage 40 in the first embodiment described above. ) Is a retrofit. The deformable body 86 of the switching valve 84 is connected to the central portion of the diagram 92 of the diaphragm device 90 via the rod 88. The two chambers encased by the diaphragm 92, while the chamber 94 is open to the atmosphere, the other chamber 96 communicates with the intake manifold 28 via the pipe 98, and the other chamber. Inside the 96, a spring 100 for pressing the diaphragm 92 upwards in FIG. 6 is incorporated. A portion communicating with the intake passage 64 of the pipe 82 communicates with the upper wall of the chamber 102 containing the deformed body 86. The side wall of the chamber 102 communicates with the sub-intake passage 40 of the pipe 82. The part which communicates with) is opened. The chamber 102 communicates with the chamber 108 via the through hole 106 of the partition 104 through which the rod 88 penetrates, and the branch pipe of the exhaust gas return passage 78 is connected to the side wall of the chamber 108. 110 communicates with the opening.

The deformed body 86 moves up and down by the operation of the diaphragm device 92, and when it rises, closes the opening of the pipe 82, and when it descends, it closes the hole 106.

Reference numeral 112 denotes a reverse valve that is installed in a pipe 82 and allows air to flow only in the direction of the chamber 102 in the main intake passage 64, and the diaphragm 90 is a seal. When a negative pressure of 300 mmHg or more, for example, a set negative pressure is conducted to 96, the diaphragm 92 is sucked downward and lowered in response to the pressure of the spring 100.

According to the above-described configuration, when the intake manifold negative pressure is equal to or higher than the set negative pressure in the idle ring or the light load operating region where the throttle valve 68 has a small opening degree, the diaphragm 92 is lowered to change the body. 86 closes the through hole 106, and the injection hole 34 is supplied with air upstream from the venturi 66 of the main air intake passage 64. As shown in FIG. In addition, when the intake manifold negative pressure is equal to or lower than the set negative pressure in the high load operating region in which the throttle valve 68 has a large opening degree, the diaphragm 92 rises so that the deformation 86 opens the opening of the pipe 82. In the injection hole 34, the exhaust gas in the exhaust gas reflux passage 78 includes the branch pipe 110, the chamber 108, the perforation 106, the chamber 102, the sub-aspirator, that is, the pipe 82, and the secondary gas. It is guided through the intake passage 40. Therefore, in the light load driving region, a strong jet of air is injected into the combustion chamber 18 in the injection hole 34, resulting in phantom thinning of the mixer and the generation of strong vortices or turbulences. The same effect is obtained. On the other hand, in the high load operating region where the jetting hole 34 is weakly classified, the exhaust gas is also discharged from the injection hole 34 together with the exhaust gas reflux from the exhaust gas return passage 78 passing through the main intake passage 64. By refluxing, the exhaust gas reflux amount is increased at high load, and in ordinary lean combustion, the effect of reducing the amount of generation of NOx that is limited to any limit can be further improved due to the limit of combustibility.

In the third embodiment of the present invention shown in FIG. 7, in the first embodiment described above, the pipe 82 connected to the main air inlet passage 64 upstream in the venturi 66 A secondary air passage 116 supplied from the air pump 114 to the exhaust system to an exhaust gas purification device (not shown) such as a thermal reactor or a catalytic converter installed in the exhaust system of the engine for the purpose of reburning unburned gas. In the first embodiment, the injection hole 34, which was a small diameter hole having a diameter of about 3 mm, was changed to a large diameter injection hole 34 'that is the same as the bore diameter of the bulb seat portion of the intake valve 38. In this case, since the pressure difference is large between the discharge pressure of the air pump 114 and the negative pressure of the combustion chamber 18 in the intake stroke, and the pore diameter of the injection hole 34 'is large, a large amount of air enters the combustion chamber 18. It is sprayed and is effective when a large amount of air jet is required.

The fourth embodiment of the present invention shown in FIG. 8 has made some modifications to the first embodiment described above, and in this embodiment is connected to the upstream main intake passage 64 in the venturi 66. The pipe 82 is configured to communicate with the main air intake passage 64 between the venturi 66 and the throttle valve 68. According to this embodiment, the opening degree of the throttle valve 68 is small, and fuel is mainly supplied from the slow system of the idle port 70 and the slow port 72, so that the fuel supply from the main nozzle 76 is small. In the light load operation region, an extremely thin mixed gas containing a small amount of fuel injected from the main nozzle 76 is injected into the combustion chamber 18 from the injection hole 34, and in the injection hole 34 also in the injection hole 34 in the high load operation region. Mixers of the same air-fuel ratio are sprayed with mixers sucked in passage 64.

Again using FIG. 1, as the above-mentioned mixer is ejected from the injection hole 34 in the combustion chamber 18, the vortices or turbulent flow generated in the combustion chamber 18 are generated to increase the combustion rate. Directing the pore 34 toward the flame gap 36 of the spark plug 30, combined with the scavenging action of the combustion gas around the flame gap 36 improves the combustibility.

The fifth embodiment of the present invention shown in FIG. 9, in the above-described first embodiment, closes the intake side 38 and its side mechanism and only occurs in the combustion chamber 18 in the intake side passage 40. FIG. The reverse side 118 opened by the negative pressure to be formed as a negative intake side, the dynamic side 118 is installed in the mounting screw hole 12 of the pipe 82, the deformed body 122 and the degenerated body 122 ) Is pressed in the closing direction. The cylinder head 12 around the reverse side 118 is provided with a cooling water passage 126 for reverse side cooling. In this embodiment, the injection hole 34 is directed around the flame gap of the spark plug 20.

According to this embodiment, when negative pressure is generated in the combustion chamber 18 in the intake stroke, the reverse valve 122 is opened so that the air passes through the pipe 82 and the sub-intake passage 40 in the injection hole 34. 18 is injected into the chamber, and scavenging around the flame gap 36 of the spark plug 20 is generated, and a strong vortex or turbulence is generated in the mixer in the combustion chamber 18.

In the sixth embodiment of the present invention shown in FIG. 10, the cylindrical spray chamber 128 is formed on the combustion chamber 18 upper portion of the cylinder head 12, and the spray chamber 128 has an opening at the bottom. It communicates with the combustion chamber 18 via the injection hole 34 which was made. The volume stone 130 is installed in the spray chamber 128, and the volume stone 130 moves up and down in the spray chamber 128 by a valve mechanism driven by the rotation of the cam shaft 46. . The intake air passage 40 is opened to the atmosphere via a dedicated air cleaner 132 at one end thereof, and the other end is opened to the inner circumferential surface in the injection chamber 128, and the contact of the volume stone 13 is made. The opening and closing of the opening of the above-described intake passage 40 as the copper surface moves up and down.

In addition, 134 is a rocker arm for driving the volume stone 130, 136 is a spring seat, 138 is a return spring, 140 is a cam installed in the cam shaft 46, the cam 140 ) Cam profile is set so that the volume stone 130 is displaced as shown in FIG.

11 shows the timing of the volume stone 130 sliding in the injection chamber 128 in relation to the combustion stroke of the piston 16. The vertical axis represents the stroke position of the volume stone 130 and the horizontal axis represents time. . The combustion cycle of four cycles by the piston 16 is shown on the horizontal axis, and the minimum of the vertical axis | shaft has shown the highest position of the piston 130 in FIG.

In addition, X period in FIG. 11 is a period during which the intake air passage 40 is in communication with the injection chamber 128, and Y period is a period during which the volume stone 130 compresses air in the injection chamber 128. In FIG. The intake passage 40 and the injection hole 34 communicate with each other during the intake stroke of the engine (and may include a compression stroke initial stage if necessary).

According to this embodiment, air is injected into the combustion chamber 18 from the injection hole 34 by the negative pressure generated in the combustion chamber 18 within the X period, and within the Y period, the air is compressed to the compression of the volume stone 130. As a result, the jetting continues and the jetting from the injection hole 34 becomes stronger than in the respective embodiments described above, and the action of generating vortices and turbulence increases.

In addition, in this embodiment, when the injection direction of the injection hole 34 is directed to the periphery of the flame interval 36 of the ignition plug 20, the combustion limit of the lean fuel is particularly scavenged by the classification immediately before the ignition. Is effectively enlarged. In each of the above embodiments, the optimum intake air amount supplied from the sub intake passage 40 is different depending on the type of engine, but in the light load operation region, the intake air amount supplied from the main air intake passage 64 is described. It is set within the range of 5 to 30%.

Claims (1)

A combustion chamber having an intake port and an exhaust port, a main intake passage for guiding the air-fuel mixture gas generated by the mixed gas generating device to the intake port, and a spacing interval at a predetermined position in the combustion chamber; An ignition plug attached to the cylinder head, an opening in the wall surface of the cylinder head forming the combustion chamber, injection holes directed to the set direction in the combustion chamber and installed in the cylinder head, and a sub-intake path connected to the injection hole, A gas supply source for supplying gas to the sub-aspirator passage at a sufficient gas supply pressure even in a low-load operation of the throttle valve installed in the main intake passage, and a sub-intake valve for opening and closing the sub-intake passage installed in the cylinder head; And an operating mechanism for opening the intake valve to the intake stroke period.

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