Combustion Chamber of an Internal Combustion Engine

The present invention relates to a construction of the combustion chamber of an internal combustion engine.

As a method of simultaneously reducing the amount of harmful HC, CO and NO.sub.x components in the exhaust gas, a method of using a lean air-fuel mixture has been used. In addition, as a method of reducing the amount of harmful NO.sub.x components in the exhaust gas, a method of using a mixture containing the recirculated exhaust gas therein has been used. However, in either when a lean air-fuel mixture is used or when a mixture containing the recirculated exhaust gas therein is used, a problem occurs in that, since the flame speed of either mixture is very low and the burning velocity is thus low, a stable combustion cannot be obtained. In order to obtain a stable combustion by using a lean air-fuel mixture or a mixture containing the recirculated exhaust gas therein, it is necessary to increase the burning velocity. As of increasing the burning velocity, a method creation of a strong turbulence in the combustion chamber can be used. As an engine which is capable of increasing the burning velocity by creating a turbulence in the combustion chamber, the inventor has proposed an engine which comprises a first downwardly projecting raised portion formed on the periphery of the inner wall of the cylinder head and having a flat bottom face so as to form a first squish area between the flat bottom face of the first raised portion and a flat peripheral portion of the top face of the piston when the piston approaches the top dead center. In addition, this engine further comprises a second upwardly projecting raised portion formed on the top face of the piston at a position opposite to the flat peripheral portion of the top face of the piston with respect to the axis of the cylinder so as to form a second squish area between the inner wall of the cylinder head and the rear face of the second raised portion when the piston approaches the top dead center. In addition, in this engine, the second raised portion has an inclined front face which is exposed to the combustion chamber and smoothly connected to the flat peripheral portion of the piston. At the end of the compression stroke, a swirl motion rotating about the horizontal axis is created in the combustion chamber by a pair of squish flows spouted from the first and the second squish areas, respectively, in the combustion chamber.

In the above-mentioned engine, since a swirl motion is created in the combustion chamber, it is true that the burning velocity is increased. However, there is a danger that knocking will occur. Nevertheless, in the above mentioned engine, the construction of the combustion chamber is not designed so as to positively prevent knocking from occurring.

An object of the present invention is to provide an internal combustion engine capable of further increasing the burning velocity and preventing knocking from occurring when an engine is operating under a heavy load by creating a considerably strong swirl motion in the combustion chamber.

According to the present invention, there is provided an internal combustion engine comprising: a cylinder block having a cylinder bore therein; a cylinder head mounted on the cylinder block and having an inner wall; a first raised portion having on its lower end a flat bottom face and being formed on the periphery of the inner wall of the cylinder head so as to project downwards; a piston reciprocally movable in the cylinder bore and having a top face which has a flat peripheral portion approachable to the flat bottom face so as to create a first squish area therebetween at the end of the compression stroke for spouting out a first squish flow along the top face of the piston, the inner wall of the cylinder head and the top face of the piston defining a combustion chamber therebetween; and intake valve movably mounted on the cylinder head for guiding a combustible mixture into the combustion chamber; an exhaust valve movably mounted on the cylinder head for discharging exhaust gas into the atmosphere; a second raised portion formed on the top face of the piston at a position opposite to the first raised portion with respect to an axis of the piston and having a rear face and a front face exposed to the combustion chamber, the rear face being approachable to the inner wall of the cylinder head so as to create a second squish area therebetween at the end of the compression stroke for spouting out a second squish flow which moves forwards in the upper interior of the combustion chamber in the direction opposite to the spouting direction of the first squish flow, the first and second squish flows cooperating with each other to create a strong swirl motion rotating about a horizontal axis in the combustion chamber, and; a spark plug having a spark gap located in the combustion chamber, wherein the front face of the second raised portion comprises a gently inclined front face portion located beneath the exhaust valve, and a steeply inclined front face portion located beneath the intake valve.

The present invention may be more fully understood from the description of a preferred embodiment of the invention set forth below, together with the accompanying drawings.

FIG. 1 is a cross-sectional side view of an internal combustion engine according to the present invention;

FIG. 2 is a bottom view taken along the line II--II in FIG. 1;

FIG. 3 is a cross-sectional side view taken along the line III--III in FIG. 1;

FIG. 4 is a perspective view of a piston;

FIG. 5 is a plan view of a piston;

FIG. 6 is a side view of a piston;

FIG. 7 is a cross-sectional side view taken along the line VII--VII in FIG. 2, and;

FIG. 8 is a cross-sectional side view taken along the line VIII--VIII in FIG. 2.

Referring to FIGS. 1 through 3, 1 designates a cylinder block, 2 a piston reciprocally movable in the cylinder block 1, 3 a cylinder head fixed onto the cylinder block 1 via a gasket 4 and 5 a combustion chamber formed between the top face of the piston 2 and the inner wall of the cylinder head 3. 6 designates an intake valve, 7 an intake port, 8 an exhaust valve, 9 an exhaust port, 10 a spark plug and 11 an electrode of the spark plug 10. As is illustrated in FIGS. 1 through 3, the inner wall of the cylinder head 3 has an annular flat surface 12 which extends circumferentially over the entire periphery of the inner wall of the cylinder head. The flat surface portion 12a of the annular flat surface 12, which is located on the left side in FIG. 2, has a uniform width illustrated by the arrow A in FIG. 2, while flat surface portions 12b and 12c of the annular flat surface 12, which are located on the right side in FIG. 2, have widths which are wider than the width A of the flat surface portion 12a as illustrated by the arrows B and C in FIG. 2, respectively. In addition, from FIG. 2, it will be understood that the flat surface portion 12b located near the exhaust valve 8 has width B which is wider than width C of the flat surface portion 12c located near the intake valve 6. As is illustrated in FIGS. 1, 3, 4 and 5, an annular flat surface 13 arranged to face the annular flat surface 12 of the cylinder head 3 and having a shape which is approximately equal to that of the annular flat surface 12 is formed on the top face of the piston 2. That is, the flat surface portion 13a of the annular flat surface 13, which is formed on the top face of the piston 2 so as to face the flat surface portion 12a of the cylinder head 3, has a uniform width which is approximately equal to the width A of the annular flat surface 12, and the flat surface portions 13b and 13c of the annular flat surface 13, which are formed on the top face of the piston 2 so as to face the flat surface portions 12b and 12c, respectively, have widths which are wider than the width of the flat surface portion 13a of the piston 2. Consequently, when the piston 2 is positioned at the top dead center as illustrated in FIG. 1, a flat and annular squish area S is formed between the annular flat surface 12 of the cylinder head 3 and the annular flat surface 13 of the piston 2. As illustrated in FIGS. 1 and 3, the top face 14 of the combustion chamber 5 has a spherical shape; in addition, the side wall 15 of the combustion chamber 5 extends approximately vertically from the flat surface portions 12b, 12c of the cylinder head 3 to the top face 14 of the combustion chamber 5. A downwardly projecting raised portion 16 is formed on the top face 14 at a position opposite to the spark plug 10 with respect to the axis of the piston 2, and the bottom wall 16a of the raised portion 16 has a spherical shape. The lower edge of the bottom wall 16a of the raised portion 16 is connected to the flat surface portion 12a of the cylinder head 3, and the upper edge of the bottom wall 16a is connected to the top face 14 of the combustion chamber 5 via a steeply inclined side wall 16b arranged to be exposed to the combustion chamber 5. A raised portion 17 is formed on the top face of the piston 2 at a position opposite to the flat surface portions 13b, 13c of the piston with respect to the axis of the piston 2, and the rear face 18 of the raised portion 17 has a spherical shape complementary to the shape of the bottom wall 16a of the raised portion 16. In addition, the lower edge of the rear face 18 of the raised portion 17 is connected to the flat surface portion 13a of the piston 2. Consequently, when the piston 2 is positioned at the top dead center as illustrated in FIG. 1, a spherical shell shape squish area T is formed between the bottom wall 16a of the raised portion 16 and the rear face 18 of the raised portion 17. In addition, a flat and shallow depression 19 is formed in the central portion of the top face of the piston 2 at a position located inside of the flat surface portions 13b, 13c of the piston 2, and the raised portion 17 has an inclined front face 20 extending from the flat depression 19 to a ridge 21 of the raised portion 17 and arranged to be exposed to the combustion chamber 5. As is illustrated in FIG. 1, the ridge 21 of the raised portion 17 is rounded. As is illustrated in FIGS. 3 through 8, the front face 20 of the raised portion 17 comprises a gently inclined front face portion 20a and a steeply inclined front face portion 20b, which are interconnected via a step portion 22 having a smoothly curved surface. As is illustrated in FIGS. 7 and 8, the gently inclined front face portion 20a is formed beneath the exhaust valve 8, and the steeply inclined front face portion 20b is formed beneath the intake valve 6. Consequently, from FIGS. 7 and 8, it will be understood that the vertical cross-section of the combustion chamber 5, which includes the axis of the exhaust valve 8 and is illustrated in FIG. 7, is much smaller than that of the combustion chamber 5, which includes the axis of the intake valve 6 and is illustrated in FIG. 8. As can be seen in FIGS. 5-8, the gently inclined portion 20a has a greater surface area than that of the steeply inclined portion 20b. Each inclined portion has a planar face. Furthermore, both inclined portions extend in and are inclined in substantially the same direction. Thus, a line drawn horizontally across the gently inclined portion would be substantially parallel to a line drawn horizontally across the steeply inclined portion. As is illustrated in FIGS. 1 through 3, a semi-cylindrical recess 23, which has a particular shape wherein the lower end of the semi-cylinder is obliquely cut, is formed on the top face 14 of the combustion chamber 5 at a position opposite to the squish area T with respect to the axis of the piston 2, and the electrode 11 of the spark plug 10 is arranged in the recess 23. Consequently, the electrode 11 of the spark plug 10 is partially enclosed by a vertically extending semi-cylindrical wall 24. As mentioned hereinafter, when the piston 2 approaches the top dead center, a pair of squish flows shown by the arrows F and G in FIG. 1 is spouted from the squish areas S and T, respectively, and the electrode 11 of the spark plug 10 is arranged on an extension of the squish are T so that the squish flow G impinges directly upon the electrode 11. However, it should be noted that, when the downward movement of the piston 2 is started, a pair of gas streams flowing towards the squish areas S and T in directions which are opposite to those of the squish flows G and F, respectively, is created in the combustion chamber 5.

During operation, at the time of the intake stroke, when the downward movement of the piston 2 is started, the pair of gas streams flowing towards the squish areas S and T at high speed in directions which are opposite to those of the squish flows G and F, respectively, is created in the combustion chamber 5 due to the temporary pressure drop within the squish areas S and T, and a strong turbulence is thus created in the combustion chamber 5. As a result of this, the air-fuel ratio of a lean mixture or a mixture containing the recirculated exhaust gas therein in the combustion chamber 5 becomes uniform over the entire region of the combustion chamber 5. When the mixture contains the recirculated exhaust gas therein, the air-fuel mixture is completely mixed with the recirculated exhaust gas due to the above-mentioned strong turbulence. After this, at the time of the compression stroke, when the piston 2 approaches the top dead center, the squish flows F and G are spouted from the squish areas S and T, respectively. The squish flow F spouted from the squish area S flows towards the front face 20 of the raised portion 71, and the squish flow G spouted from the squish area T moves forward towards the recess 23. Then, the squish flow G impinges upon the semi-cylindrical wall 24, and a microturbulence is thus created in the recess 23. On the other hand, the squish flow F flowing towards the front face 20 of the raised portion 17 from the squish area 5 moves forward along the front face 20 of the raised portion 17 and then comes into violent contact with the squish flow G spouted from the squish area T. As a result of this violent contact, the flow direction of the squish flow G is changed so that the squish flow G flows along the top face 14 of the combustion chamber 5 as illustrated by the arrow H in FIG. 1. At this time, since the flow direction of the squish flow F is changed by the steeply inclined side wall 16b of the raised portion 16, the squish flow F also flows along the top face 14 of the combustion chamber 5 as illustrated by the arrow H in FIG. 1. By forming the steeply inclined side wall 16b which extends upwards from the ridge 21 of the raised portion 17, the squish flow G is not considerably decelerated by the squish flow F, and the squish flow F itself is also not considerably decelerated. Then, the squish flow H flowing along the top face 14 of the combustion chamber 5 passes in front of the recess 23 and moves downwards along the vertical side wall 15. At this time, since the electrode 11 of the spark plug 10 is arranged within the recess 23, the squish flow H does not impinge directly upon the electrode 11 of the spark plug 10. Then, the squish flow H flowing downwardly along the vertical side wall 15 comes into violent contact with the squish flow F spouted from the squish area S. As a result, the flow direction of the squish flow F is changed as illustrated by the arrow I in FIG. 1. At this time, the squish flow G also flows along the flat bottom of the depression 19 as illustrated by the arrow I in FIG. 1. By forming the depression 19 in the top face of the piston 2, the squish flow F is not considerably decelerated by the squish flow H, and the squish flow F is also not considerably decelerated. Thus, a strong swirl motion, shown by the arrow K, which is rotating about the horizontal axis is created in the combustion chamber 5.

Then, the mixture is ignited by the spark plug 10. At this time, since a microturbulence is created in the recess 23 as mentioned previously, the mixture is easily ignited and then the flame rapidly spreads within the recess 23. After this, the flame swirls in the combustion chamber 5 together with the strong swirl motion K and the burning velocity is thus considerably increased. In addition, since the flame swirls in the combustion chamber 5, unburnt HC and CO located in the quench layers formed on the inner wall of the cylinder head 3 and on the top face of the piston 2 are burned. After this, when the downward movement of the piston 2 is started, the unburnt gas in the combustion chamber 5 is sucked into the squish areas S and T together with the flame. As a result, the unburnt HC and CO located in the quench layers formed on the inner wall of the cylinder head 3 and on the top face of the piston 2 within the squish areas S and T are burned.

As mentioned above, since the flat surface portion 12b of the cylinder head 3 has the width B which is wider than the width C of the flat surface portion 12c of the cylinder head 3, the squish flow spouted from the flat surface portion 12b as illustrated by the arrow Fb in F FIGS. 2 and 7 is stronger than that spouted from the flat surface portion 12c as illustrated by the arrow Fc in FIGS. 2 and 8. In addition, as is illustrated by the broken lines Tb, Tc in FIG. 2, the squish area T is so formed that the surface area of the squish area portion Tb located near the exhaust valve 8 is considerably greater than that of the squish area portion Tc located near the intake valve 6; as a result, the squish flow Gb spouted from the squish area portion Tb is stronger than the squish flow Gc spouted from the squish area portion Tc. Consequently, a swirl motion Kb (FIG. 7) which rotates about the horizontal axis and which is created in the combustion chamber 5 beneath the exhaust valve 8 by the pair of squish flows Fb, Gb becomes stronger than a swirl motion Kc (FIG. 8) which rotates about the horizontal axis and which is created in the combustion chamber 5 beneath the intake valve 6 by the pair of squish flows Fc, Gc. In addition, as is illustrated in FIGS. 7 and 8, since the gently inclined front face portion 20a of the raised portion 17 is arranged beneath the exhaust valve 8 and, in addition, the steeply inclined front face portion 20b of the raised portion 17 is arranged beneath the intake valve 6, the vertical cross-section of the combustion chamber 5, which includes the axis of the exhaust valve 8 and is illustrated in FIG. 7, is much smaller than that of the combustion chamber 5, which includes the axis of the intake valve 6 and is illustrated in FIG. 8. As a result of this, the speed of the swirl motion Kb created beneath the exhaust valve 8 becomes higher than that of the swirl motion Kc created beneath the intake valve 6. As is known to those skilled in the art, knocking occurs due to the fact that the self-ignition of the mixture located near the exhaust valve 8 is caused. However, by positively increasing the velocity of a swirl motion in the combustion chamber 5 beneath the exhaust valve 8 and causing the flame of the mixture ignited by the spark plug 10 to propagate immediately towards the space around the exhaust valve 8, it is possible to prevent knocking from occurring.

In an internal combustion engine having such a construction that a swirl motion is created in the combustion chamber by the squish flow, the strength of the squish flow has a great influence on the strength of the swirl motion. In addition, the surface area of the squish area has a great influence on the strength of the squish flow. However, it is impossible to increase the surface area of the squish flow to a great extent in view of the construction of an engine. In addition, in the case wherein an excessively strong swirl motion is created in the combustion chamber, there is a danger in that a misfire will occur. As a result of experiments conducted by the inventor, in the engine illustrated in FIGS. 1 through 8, it has been proven that, in order to obtain an ease of ignition and a good combustion, it is preferable that a surface area ratio of the sum of the squish area formed on the inner wall of the cylinder head 3 and the squish area formed on the top face of the piston 2 to the sum of the cross-sectional area of the cylinder bore and the surface area of the inner wall of the cylinder head 3, except for the surface area of the vertical side wall 15, be in the range of 30 percent to 50 percent. In addition, it has also been proven that the best ignition and combustion can be obtained when the above-mentioned surface area ratio is in the range of 35 percent to 40 percent. In the present invention, in order to form squish areas S and T having a large surface area while forming the combustion chamber 5 as compact as possible, the squish area S must be so formed that it has an annular shape.

According to the present invention, since it is possible to create a strong swirl motion in the combustion chamber while positively preventing knocking from occurring, the burning velocity can be considerably increased. As a result of this, a stable combustion can be obtained and, at the same time, the specific fuel comsumption can be improved.

While the invention has been described with reference to a specific embodiment chosen for purposes of illustration, it should be apparent that numerous modifications can be made thereto by those skilled in the art without departing from the spirit and scope of the invention.