JP2013147949A - Blow-by gas processing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a blow-by gas processing device capable of reducing oil mist in blow-by gas without increasing a pressure loss or a size of a filter element in an internal combustion engine.SOLUTION: Oil mist present around oil can be absorbed in the oil by intermolecular force while the oil sprayed to a blow-by gas passage 18 from an oil spraying part 22 falls, and the oil mist in blow-by gas can be thereby reduced. The diameter of the oil mist not fully removed is increased through the combination with the sprayed oil, so that the oil mist is then easily captured by a cyclone type oil separator 14. Accordingly, there is no need for reducing the mesh size of a filter element with an increase in pressure loss or for increasing the size of the filter element.

Description

  The present invention relates to a blow-by gas processing apparatus that guides blow-by gas generated from an internal combustion engine to an oil separator through a blow-by gas path.

  When a large amount of oil mist is mixed in the blow-by gas of the internal combustion engine, when it is introduced into the intake air, the oil mist placed in the combustion chamber at a high temperature and high pressure becomes an ignition source and ignites before the ignition plug is energized. The phenomenon, so-called pre-ignition is likely to occur. For this reason, an oil separator is disposed in the blow-by gas path to remove oil mist (see, for example, Patent Document 1).

  So-called cyclonic and labyrinth oil separators equipped with centrifugal separation and baffle plates both perform gas-liquid separation using the difference between the inertial force acting on the gas component in blow-by gas and the inertial force acting on the oil droplet component. Is. Therefore, it is suitable for capturing relatively large oil droplets and is not suitable for capturing small oil droplets.

  Therefore, a technique is known in which gas-liquid separation performance is improved by providing a capturing means suitable for each size of oil droplet. That is, in Patent Document 1, relatively large oil droplets in blow-by gas are captured by centrifugal separation, then medium-sized oil droplets are captured by a filter net, and oil mist is finally captured by a filter element.

JP 2001-336413 A (page 4, FIG. 3)

  An engine with a higher pressure and temperature in the combustion chamber than a naturally aspirated engine, such as a supercharged engine, is likely to be an ignition source even with relatively small oil droplets. There is a need for further improvement in capture performance.

  However, if it is intended to improve the performance of capturing small oil droplets using the filter element, it is necessary to make the filter finer and increase the pressure loss of the blow-by gas flow path or to enlarge the apparatus itself.

  The present invention is directed to a blow-by gas processing apparatus capable of reducing oil mist in blow-by gas without causing an increase in pressure loss or an increase in size of a filter element or the like.

In the following, means for achieving the above-mentioned purpose, and its operation and effect are described.
The blow-by gas processing apparatus according to claim 1 is a blow-by gas processing apparatus that guides the blow-by gas generated from the internal combustion engine to the oil separator through the blow-by gas path, and in the air in the blow-by gas path, the oil is granular, An oil spraying means for spraying in a linear or film form is provided.

  In this way, by spraying the oil in the granular, linear, or film form in the air in the blow-by gas path, the granular, linear, or film-like oil falls in the blow-by gas. In such a falling state of oil, oil mist existing around the granular, linear or film-like oil can be absorbed into the granular, linear or film-like oil by its intermolecular force. As a result, the oil mist in the blow-by gas is enlarged and dropped and removed as it is.

  Since the oil mist that could not be completely removed is increased in diameter by the combination with the sprayed oil, it is easily captured by a subsequent cyclone type oil separator. Therefore, it is possible to improve the capturing performance of small oil droplets without making the filter finer, so that the pressure loss does not increase.

In this way, oil mist in blow-by gas can be reduced without causing an increase in pressure loss or an increase in size of the filter element or the like.
In the blow-by gas processing apparatus according to claim 2, in the blow-by gas processing apparatus according to claim 1, the oil spraying means introduces oil into the blow-by gas path by an accumulator or a pump, and is granular, linear, or It is characterized by being dispersed in a film form.

  The oil may be dispersed in the air by introducing the oil into the blow-by gas path by an accumulator that accumulates the oil or a pump that sucks and sends out the oil, and forms the particles in the form of particles, lines, or films.

With such a configuration, oil can be sprayed regardless of the rotation of the internal combustion engine at the time of spraying and the hydraulic pressure associated with the rotation.
The blow-by gas processing apparatus according to claim 3, wherein in the blow-by gas processing apparatus according to claim 1 or 2, the oil spraying means is a flow direction of blow-by gas in the air in the blow-by gas path by spraying oil. Is characterized in that the granular, linear or film-like oil is moved in the opposite direction.

  In this way, the granular, linear, or film-like oil moves in a direction opposite to the flow direction of the blow-by gas, so that a larger amount of blow-by gas and By contacting, a larger amount of oil mist can be adsorbed. This increases the efficiency of oil mist removal.

  The blow-by gas processing apparatus according to claim 4, wherein in the blow-by gas processing apparatus according to claim 3, the oil spraying means is configured such that the blow-by gas rises from the lower side to the upper side in the vertical direction in the blow-by gas path. It is characterized by spraying oil in the area where

  Thus, in the region where the blow-by gas rises, only the oil is sprayed into the air in the blow-by gas path, and most of the sprayed granular, linear or film-like oil counters the flow direction of the blow-by gas by its own weight. Will fall in the direction of

  Thus, a large amount of oil mist can be adsorbed by coming into contact with a larger amount of blow-by gas while the granular, linear or film-like oil is falling. This increases the efficiency of oil mist removal.

  The blow-by gas processing apparatus according to claim 5 is the blow-by gas processing apparatus according to claim 4, wherein the region is a space covered by a front cover.

  As the region where the blow-by gas rises in this way, a space covered by the front cover of the internal combustion engine can be mentioned. Therefore, oil mist can be efficiently removed only by spraying oil into the air inside the front cover.

  In the blowby gas processing apparatus according to claim 6, in the blowby gas processing apparatus according to claim 4 or 5, the oil spraying means has a direction of the oil spraying port as a direction intersecting a flow direction of the blowby gas. It is characterized by being.

  When oil is sprayed from the oil spray port set in such a direction, the oil is sprayed in a direction intersecting the flow direction of the blow-by gas. And most of the granular, linear or film-like oil descends in the blow-by gas by its own weight. As a result, most of the granular, linear or film-like oil moves in a direction opposite to the flow direction of the blow-by gas.

Therefore, oil mist can be efficiently removed simply by spraying oil from the oil spray port.
The blow-by gas processing apparatus according to claim 7 is the blow-by gas processing apparatus according to claim 3, wherein the oil spraying means sprays oil in a space covered with a cam cover.

  When oil is sprayed in the space covered with the cam cover in this way, the oil collides with the camshaft rotating inside the cam cover, and is spread widely in the air inside the cam cover, particularly as oil droplets that are granular oil.

For this reason, oil comes in contact with a large amount of blow-by gas, and a large amount of oil mist can be adsorbed. This increases the efficiency of oil mist removal.
The blow-by gas processing apparatus according to claim 8 is characterized in that, in the blow-by gas processing apparatus according to claim 3, the oil spraying means sprays oil in a space covered with a crankcase.

  Since the crankshaft and the components associated therewith are rotating in the crankcase, when oil is sprayed into the space covered by the crankcase, the oil collides with these components, especially as oil droplets that are granular oil Widely dispersed in the air inside the crankcase.

For this reason, a large amount of oil mist can be adsorbed by contacting the oil with a large amount of blow-by gas. This increases the efficiency of oil mist removal.
The blow-by gas processing apparatus according to claim 9, wherein the oil spraying means sprays oil when the internal combustion engine is at a low rotation speed or at a low hydraulic pressure. In addition, the spraying of oil is stopped when the internal combustion engine is at a high rotation speed or at a high hydraulic pressure.

  In an internal combustion engine, oil is supplied to each part by an oil jet or the like for lubrication and cooling. For this reason, at the time of high rotation of the internal combustion engine or the accompanying high hydraulic pressure, a certain amount of oil droplets are generated in the blow-by gas path during the supply of the lubricating oil or the oil as the refrigerant, resulting in an accompanying oil mist removing effect. .

  However, when the internal combustion engine is running at a low speed or at a low oil pressure, the accompanying oil mist removal effect by such lubricating oil or oil as a coolant is lost. For this reason, the oil spraying means provided for removing mist should spray oil sufficiently by discharging using, for example, an electric pump, especially at low rotation or low hydraulic pressure of the internal combustion engine. Do not spray oil during hydraulic pressure. This prevents the generation of granular, linear, or film-like oil in the blow-by gas path more than necessary particularly at high revolutions of the internal combustion engine. Therefore, the rotational resistance of the rotational component of the internal combustion engine can be suppressed, which can contribute to improving the fuel consumption of the internal combustion engine.

  The blow-by gas processing device according to claim 10, wherein the blow-by gas processing device according to any one of claims 1 to 9 is an oil surface that suppresses vibrations on an oil surface of an oil pan when the internal combustion engine rotates at a high speed. A vibration suppression means is provided.

  When the internal combustion engine rotates at a high speed, the rotational configuration of the internal combustion engine such as a crankshaft causes the oil level of the oil pan to ripple through the surrounding air. As a result, oil droplets jump out of the oil surface and become rotational resistance of the internal combustion engine.

  Accordingly, the oil level vibration suppressing means can suppress unnecessary oil droplets and reduce the rotational resistance of the internal combustion engine by suppressing vibrations on the oil level of the oil pan during high rotation of the internal combustion engine. For this reason, it can contribute to the fuel consumption improvement of an internal combustion engine.

FIG. 2 is a cross-sectional view showing the internal configuration of the internal combustion engine of the first embodiment. (A), (B) Structure and function explanatory drawing of the oil spraying part of Embodiment 1. FIG. (A), (B) Structure and function explanatory drawing of the oil spraying part of Embodiment 2. FIG. (A), (B) Structure and function explanatory drawing of the oil spraying means of Embodiment 3. FIG. (A), (B) Structure and function explanatory drawing of the oil spraying means of Embodiment 3. FIG. FIG. 6 is a cross-sectional view showing the internal configuration of the internal combustion engine of the fourth embodiment. FIG. 6 is a configuration explanatory diagram of an oil spraying unit according to a fifth embodiment. (A), (B) The partial structure and function explanatory drawing of the oil spraying part of Embodiment 5. FIG. (A), (B) Sectional drawing which shows the internal structure and function of the internal combustion engine of Embodiment 6. FIG. FIG. 10 is a perspective view of an oil level vibration suppressing mechanism of a sixth embodiment. Sectional drawing which shows the internal structure and function of the oil surface vibration suppression mechanism of Embodiment 7. Sectional drawing which shows the internal structure and function of the oil surface vibration suppression mechanism of Embodiment 7.

[Embodiment 1]
<Configuration of Embodiment 1> FIG. 1 shows an internal configuration of an internal combustion engine 2 to which the invention described above is applied. The internal combustion engine 2 is an inline 4-cylinder gasoline engine. Here, blow-by gas that escapes from between the piston 4 and the cylinder 6 into the crankcase 8 passes through the front cover 10 from the front side of the crankcase 8 and is introduced into the cam case 12 as indicated by the broken arrow line. Is done. In the rear portion of the cam case 12, the oil is removed by the oil separator 14, and passes through a pipe 16 through a PCV (Positive Crankcase Ventilation) valve and a filter element that finally captures oil mist. It flows into the intake path. Therefore, the space in the crankcase 8, the front cover 10, and the cam case 12 corresponds to the blow-by gas path 18.

  In this blow-by gas path 18, an oil spraying portion 22 (corresponding to oil spraying means) is provided in the cylinder head 20 at a position in the front cover 10. The oil spraying part 22 is particularly arranged at the upper part in the front cover 10 and is arranged at a position above the position of the cylinder 6.

  As shown in FIG. 2A, the oil spraying portion 22 has an oil spraying port 24 that is flat in the horizontal direction. The oil spray port 24 is directed to the blow-by gas path 18 in the front cover 10. An oil introduction port 26 formed on the opposite side of the oil spray port 24 is connected to an oil hole 28 formed in the cylinder head 20 and receives supply of oil from the oil hole 28 side.

Oil is supplied to the oil hole 28 from an oil pump 32 driven by rotation of the crankshaft 30. The oil pump 32 sucks the oil 36 in the oil pan 34 through the strainer 38, pressurizes it, and sends it out to the oil hole 28.
<Operation of Embodiment 1> During operation of the internal combustion engine 2, the oil spraying portion 22 is supplied with oil from the oil hole 28, so that the oil spray portion 22 is in the upper position in the front cover 10 and is shown by the solid arrow in FIG. As shown, the oil spray port 24 is in a state of spraying oil in the horizontal direction so as to intersect the blow-by gas flow direction in the blow-by gas path 18.

  The oil spray port 24 is in a flat state spreading in the horizontal direction. Therefore, when the oil flowing in the oil hole 28 enters the oil spraying portion 22 from the oil introduction port 26, the flow spreads in a flat state in the horizontal direction as shown in FIG. Then, when sprayed from the oil spray port 24, it is sprayed in the air in the blow-by gas path 18 as a flat flow, that is, an oil film (corresponding to film-like oil) spreading in the horizontal direction.

  The direction of movement of the oil film sprayed from the oil spray port 24 into the air is the direction in which the direction of the oil spray port 24 intersects the flow direction of the blow-by gas (the direction from the lower side to the upper side in the vertical direction). The oil immediately after sprayed from the spray port 24 moves in a direction crossing the flow direction of the blow-by gas. However, after that, the moving direction is bent downward in the vertical direction by its own weight, and finally falls almost vertically in the air in the blow-by gas path 18. During this fall, the oil film gradually changes to oil droplets that are granular oil due to its surface tension, and falls not only as an oil film state but also as oil drops.

The falling direction of the oil droplet or oil film is finally downward in the vertical direction. In the blow-by gas path 18 in the front cover 10, the blow-by gas flows from the lower side to the upper side in the vertical direction as shown. For this reason, in the air in the blow-by gas path 18, the oil droplets or the oil film moves in a direction opposite to the flow direction of the blow-by gas.
<Effects of Embodiment 1> (1) During the fall of oil in the air in the blow-by gas path 18, oil mist existing around the granular or film-like oil is removed by the intermolecular force. Can be absorbed in oil. As a result, the oil mist in the blow-by gas is enlarged and dropped and removed as it is. Therefore, oil mist in blow-by gas can be reduced.

  Since the oil mist that could not be completely removed is increased in diameter by the combination with the sprayed oil, it is easily captured by the subsequent cyclonic oil separator 14. Accordingly, since the performance of capturing small oil droplets can be improved without making the filter element provided on the side of the pipe 16 fine, the pressure loss does not increase and the filter element does not need to be enlarged.

  Such blow-by gas treatment is based on the spraying of oil droplets or oil film in the air in the blow-by gas path 18, so that the spraying itself does not hinder the flow of blow-by gas. Therefore, the pressure loss does not increase even if the volume in the front cover 10 is not particularly increased.

In this way, oil mist in the blow-by gas can be reduced without using a configuration that causes an increase in pressure loss or an increase in size of the filter element or the like.
(2) Oil is sprayed in the air by the blow-by gas path 18 set in the space in the front cover 10. For this reason, it is possible to easily move the oil in a direction opposite to the flow direction of the blow-by gas in the region where the blow-by gas rises only by spraying oil in the air.

Further, granular or film-like oil is spread in the horizontal direction by the oil spraying port 24 and sprayed. As a result, oil can be sprayed over a wide range of the entire blow-by gas path 18.
Therefore, a large amount of blow-by gas can be contacted while the granular or film-like oil falls, and a large amount of oil mist can be adsorbed. This increases the efficiency of oil mist removal.

[Embodiment 2]
<Configuration of Embodiment 2> In this embodiment, an oil spraying section 122 shown in FIG. 3 is used instead of the oil spraying section 22 shown in FIG. The other structure is as described in FIG. Therefore, the same configuration will be described with reference to FIG.

As shown in FIG. 3A, in the oil spraying part 122 of the present embodiment, the oil spraying port 124 is divided into a plurality of holes (here, six holes). For this reason, the spraying of oil from the oil spraying port 124 is in a state of being discharged in a linear form from a plurality of holes. Thus, although it is initially linear oil, it falls into a granular shape due to surface tension in the lower part while falling.
<Operation of Embodiment 2> For this reason, during operation of the internal combustion engine 2, as shown by the solid line arrow in FIG. As in the case of 1), the oil is sprayed horizontally so as to cross the blow-by gas path 18 at the upper position in the front cover 10.

  In the cylinder head 20, the oil spray port 124 is arranged with a plurality of holes arranged in the horizontal direction, so that the oil that has flowed through the oil hole 28 enters the oil spray unit 122 from the oil introduction port 126. The flow spreads in a flat state in the horizontal direction and is sprayed from each hole of the oil spraying port 124. Therefore, at the time of this spraying, it is sprayed in the blow-by gas passage 18 as a plurality of linear oils arranged so as to spread in the horizontal direction.

  The direction of movement of the linear oil sprayed from the oil spray port 124 is a direction that intersects the flow direction of the blowby gas at first, since the direction of the oil spray port 124 intersects the flow direction of the blowby gas. is there. However, after that, it bends downward in the vertical direction due to its own weight, and finally falls in the blow-by gas path 18 almost vertically and enters the oil pan 34. During this fall, the linear oil gradually changes to oil droplets that are granular oil due to the surface tension, and falls not only as linear oil but also as oil droplets.

In this way, the falling direction of the oil droplets or linear oil is finally downward in the vertical direction. In the blow-by gas path 18 in the front cover 10, the blow-by gas flows upward from below in the vertical direction. Accordingly, in the air in the blow-by gas path 18, oil droplets or linear oil move in a direction opposite to the flow direction of the blow-by gas.
<Effects of Embodiment 2> (1) Even when oil is sprayed from the oil spray port 124 in which holes are arranged in the horizontal direction as in the present embodiment, oil can be sprayed over a wide range of the entire blow-by gas path 18, The same effect as in the first embodiment is produced.

[Embodiment 3]
<Configuration of Third Embodiment> In the first and second embodiments, the oil spraying portions 22 and 122 introduce oil from the oil pump 32 through the oil hole 28. In the present embodiment, FIG. As shown in FIG. 3, the oil spraying part 222 is not configured to introduce the oil supplied from the oil pump 32 as it is. Here, the oil accumulated in the accumulator 242 is introduced via the hydraulic control valve 240. Since the other configuration is as shown in FIG. 1, the same configuration will be described with reference to FIG. The arrangement of the oil spraying part 222 is the same as that of the oil spraying part 22 in FIG.

Here, the oil spraying means includes an oil spraying section 222, a hydraulic control valve 240, an accumulator 242, and a check valve 244.
Oil from the oil pump 32 is sent to the check valve 244 via the oil hole 28. The check valve 244 opens when the pressure difference between the inlet and the outlet is 200 kPa. The oil that has passed through the check valve 244 is sent to the accumulator 242 via the oil passage 244a as pressure accumulation oil.

The accumulator 242 is connected to the oil spraying part 222 via the hydraulic control valve 240. Oil is supplied to the hydraulic control valve 240 from the oil hole 28 side, and the hydraulic control valve 240 is opened when the hydraulic pressure reaches a low hydraulic pressure state (90 to 200 kPa in this case) within a specific range. When the hydraulic control valve 240 is opened, the oil accumulated in the accumulator 242 is supplied to the oil spraying unit 222 and sprayed from the oil spraying port 224 into the air in the blow-by gas path 18 as an oil film.
<Operation of Embodiment 3> When the internal combustion engine 2 is in a stopped state and no oil is supplied from the oil pump 32, the valve 240a is moved by the spring 240b as shown in FIG. The oil passage 222a between the accumulator 242 and the oil spraying part 222 is closed. For this reason, even if oil is accumulated in the accumulator 242, the oil is not sprayed from the oil spraying port 224.

  In the initial state in which the internal combustion engine 2 is started and is once in a low rotation state, the oil supplied from the oil pump 32 to the oil hole 28 is at a low pressure (90 to 200 kPa in this case), as shown in FIG. As shown, the valve 240a in the hydraulic control valve 240 moves slightly against the spring 240b.

  As a result, the through hole 240c formed in the valve 240a moves to open the oil passage 222a. Assuming that no oil is accumulated in the accumulator 242 at the first low pressure after the start-up, no oil is supplied from the accumulator 242 to the oil spraying section 222 through the oil passage 222a. If oil is present in the accumulator 242 when the internal combustion engine 2 rotates at a low speed, the oil is pushed out of the accumulator 242 by the pressure of the spring 242a in the accumulator 242 as shown in FIG. Then, the oil is supplied to the oil spraying part 222 through the oil passage 222a. As a result, oil is sprayed into the blow-by gas path 18 from the oil spray port 224.

  When the internal combustion engine 2 enters a high rotation state, the oil supplied from the oil pump 32 to the oil hole 28 is increased in pressure. When the oil pressure exceeds 200 kPa due to this increase in pressure, the valve 240a in the oil pressure control valve 240 moves to the maximum against the spring 240b as shown in FIG. As a result, the valve 240a closes the oil passage 222a.

  At this time, the check valve 244 is further opened. Accordingly, the oil is introduced into the oil passage 244a through the check valve 244. Since this oil has a high pressure, the plunger 242b is pushed up against the spring 242a in the accumulator 242, and is accumulated in the accumulator 242. Therefore, when the internal combustion engine 2 is rotating at high speed, only the oil is accumulated in the accumulator 242, and no oil is sprayed from the oil spray port 224 of the oil spray unit 222 into the blow-by gas path 18.

  Then, when the internal combustion engine 2 is in a low rotation state and the oil pressure is reduced and the hydraulic pressure is in the range of 90 to 200 kPa, the spring 240b pushes back the valve 240a against the hydraulic pressure in the hydraulic control valve 240. As a result, the through hole 240c coincides with the oil passage 222a, and the hydraulic control valve 240 is opened.

  For this reason, the oil accumulated in the accumulator 242 is introduced into the oil spraying section 222 via the hydraulic control valve 240 and the oil passage 222a. As a result, oil is sprayed from the oil spray port 224 into the blow-by gas path 18.

Thereafter, as long as the operation of the internal combustion engine 2 is continued, the oil accumulation in the accumulator 242 is performed without the oil spraying from the oil spraying part 222 into the blow-by gas path 18 in the high rotation state of the internal combustion engine 2. In the low rotation state of the internal combustion engine 2, high-pressure oil accumulated in the accumulator 242 during the high rotation state is sprayed from the oil spraying part 222 into the blow-by gas path 18. Such oil accumulation at high rotation (high hydraulic pressure:> 200 kPa) and oil spraying at low rotation (low hydraulic pressure: 90 to 200 kPa) are repeated.
<Effects of Embodiment 3> (1) The same effects as in Embodiment 1 are produced.

(2) The oil spraying from the oil spraying part 222 into the blow-by gas path 18 is performed when the internal combustion engine 2 is at a low speed (at low oil pressure) and not at a high speed (at high oil pressure).
In the internal combustion engine 2, oil is supplied to each part by an oil jet or the like to be lubricated and cooled. In particular, when the internal combustion engine 2 is rotating at a high speed or at a high hydraulic pressure associated therewith, a certain amount of oil droplets may be blown by the supply of oil as lubricating oil or refrigerant liquid without being sprayed from the oil spraying section 222. 18 occurs. This incidentally produces an oil mist removing effect. However, when the internal combustion engine 2 is at a low rotation speed or a low hydraulic pressure, the incidental oil droplet spraying effect by such lubricating oil or oil as a coolant is lost.

  For this reason, oil is sprayed from the oil spray port 224 into the blow-by gas path 18 when the internal combustion engine 2 is rotating at low speed (low hydraulic pressure), and spraying is stopped at high speed (high hydraulic pressure). Thus, when the internal combustion engine 2 rotates at a high speed, the blow-by gas passage 18 does not generate more granular or membranous oil than necessary, so that the rotational resistance of the rotational component of the internal combustion engine 2 can be suppressed. Therefore, it is possible to contribute to improving the fuel consumption of the internal combustion engine 2.

[Embodiment 4]
<Configuration of Embodiment 4> The configuration of this embodiment is shown in FIG. In the present embodiment, unlike FIG. 1, the cylinder head 320 is not provided with an oil spreading portion, and instead, an oil spreading portion 322 is provided inside the cam case 312. Since the other configuration is the same as that shown in FIG. 1, the same configuration will be described with reference to FIG. 6 may have the flat oil spraying port 24 shown in FIG. 2 or the oil spraying port 124 having a plurality of holes shown in FIG. Also good. Furthermore, by adding the configuration of FIGS. 4 and 5 shown in the third embodiment, the oil may be sprayed only at a low oil pressure.

The oil spraying part 322 is disposed in front of the oil separator 314 in the blow-by gas path 318, and sprays oil in a film or a line in a direction opposite to the flow of the blow-by gas as indicated by the solid line arrow. Yes.
<Operation of Embodiment 4> Inside the cam case 312, a camshaft 313 is disposed on the cylinder head 320 and rotates in conjunction with the crankshaft 330 during operation of the internal combustion engine 302. For this reason, even if the oil sprayed from the oil spraying section 322 is initially in the form of a film or a line and is inadequate as oil droplets, it is provided on the rotating camshaft 313 or the camshaft 313. By colliding with the cam 313a, an oil droplet is surely formed. Further, the camshaft 313 and the cam 313a that are further rotated are widely dispersed in the air in the blow-by gas path 318 and dispersed.
<Effect of Embodiment 4> (1) The effect of Embodiment 1 is also obtained when the oil spraying portion 322 is provided in the cam case 312 as described above.

  (2) The oil sprayed from the oil spraying section 322 collides with the rotating camshaft 313 and the cam 313a, and is spread in the form of oil droplets in the blowby gas passage 318. Therefore, a large amount of blowby gas A large amount of oil mist can be adsorbed by contacting with. This increases the efficiency of oil mist removal.

Further, when the configurations of FIGS. 4 and 5 are added, the effects described in the third embodiment are produced.
[Embodiment 5]
<Configuration of Fifth Embodiment> In the internal combustion engine of the present embodiment, as shown in a partially broken view in FIG. 7, an oil spraying portion 434 is provided on the counterweight 432 of the crankshaft 430. An oil path 436 for oil jet is provided inside the crankshaft 430, and oil for oil jet is supplied to the connecting rod side.

  An oil path 438 branched from the oil jet oil path 436 is provided, and oil is supplied to the oil spraying portion 434 side. The other configuration is the same as that of the first embodiment shown in FIG. 1 except that the oil spraying portion is not formed on the cylinder head, so the same configuration will be described with reference to FIG. To do.

  As shown in FIG. 8A, the oil spraying portion 434 is disposed at the distal end of the counterweight 432 in the radial direction, that is, the farthest position from the rotation shaft of the crankshaft 430.

The oil spraying portion 434 has a check valve structure that closes the oil path 438. That is, a cylindrical seat portion 434 b is formed in the valve chamber 434 a from the tip opening 432 a of the counterweight 432. Further, in the valve chamber 434a, a steel ball 434d is disposed between the internal opening 434c of the seat portion 434b and the oil path 438, and a biasing force is applied to the steel ball 434d in a direction away from the internal opening 434c. A spring 434e is provided.
<Operation of Embodiment 5> The urging direction of the steel ball 434d by the spring 434e exists on the rotating shaft side of the crankshaft 430. When the crankshaft 430 has a low rotational speed, the steel ball 434d has no or little radial centrifugal force. In this way, when the internal combustion engine is in a low rotation state, as shown in FIG. 8A, the steel ball 434d is separated from the internal opening 434c by the biasing force of the spring 434e, and the seat 434b is opened. Has been. Therefore, the oil from the oil path 438 flows through the valve chamber 434a and the seat part 434b and is discharged from the tip opening 432a to the blow-by gas path 18 in the crankcase 8. That is, when the internal combustion engine is running at a low speed, the oil spraying unit 434 sprays oil from the tip opening 432a into the air in the blow-by gas path 18.

  At this time, the oil sprayed in the blow-by gas path 18 is made granular. Or even if it is linear at first, it is divided and dispersed by the surface tension. Furthermore, it collides with each part of the rotating crankshaft 430, it becomes granular reliably, and is widely disperse | distributed to the blowby gas path | route 18 in the crankcase 8.

When the crankshaft 430 has a high rotational speed, the centrifugal force on the steel ball 434d increases, and the internal opening 434c is closed by the steel ball 434d against the biasing force of the spring 434e as shown in FIG. 8B. . As a result, the oil in the oil path 438 cannot pass to the tip opening 432a side, and the discharge to the blow-by gas path 18 in the crankcase 8 stops. For this reason, when the internal combustion engine is in a high rotation state, the oil spraying portion 434 does not spray oil to the blow-by gas path 18 in the crankcase 8.
<Effects of Embodiment 5> (1) In this way, oil can be sprayed over a wide range of the entire blow-by gas path 18 by spraying oil from the oil spraying portion 434 provided on the counterweight 432 of the crankshaft 430. . For this reason, the same effect as the first embodiment is produced.

  (2) The oil spraying from the oil spraying portion 434 to the blow-by gas path 18 sprays oil when the internal combustion engine is running at a low speed (even at a low oil pressure). This produces the effect as described in the second embodiment (2).

[Embodiment 6]
<Configuration of Sixth Embodiment> The longitudinal section of the main part of the internal combustion engine 502 of the present embodiment is as shown in FIG. 9 and suppresses vibrations at the oil surface 536a in the oil pan 534 when the internal combustion engine 502 rotates at a high speed. An oil level vibration suppression mechanism 538 (corresponding to oil level vibration suppression means) is provided. Other configurations are the same as those of the first to fifth embodiments. Therefore, the configuration of the present embodiment is a combination of the oil spraying means and the oil level vibration suppressing means.

The configuration of the oil level vibration suppression mechanism 538 is shown in FIG. The oil level vibration suppression mechanism 538 includes a baffle plate 540, a flap 542, and a rotation actuator 544.
The baffle plate 540 has four openings 540a. Four flaps 542 are provided corresponding to the openings 540a. Each of these flaps 542 has a shape slightly larger than the opening 540a. The entire oil level vibration suppression mechanism 538 is disposed so that the baffle plate 540 is positioned between the crankshaft 530 and the oil level 536a in a state where the oil level vibration suppression mechanism 538 is supported on the crankcase 508 side by the support column 540b attached to the baffle plate 540. Has been.

  The flap 542 is pivotally supported in the vicinity of the edge of each opening 540a on one side, and the opening 540a of the baffle plate 540 is opened as shown in FIG. 9A by the swing angle of the flap 542. The opening 540a can be closed as shown in FIG.

Links 542a are pivotally supported on both sides of the front end of the flap 542 so that the four flaps 542 can be driven to open and close at the same angle.
The rotation axis of the rotation actuator 544 is connected to the axis of one flap 542, and the rotation actuator 544, which is an electric motor, is driven by the control unit 546 so that the angles of the four flaps 542 are kept in the same state. Can be adjusted.

  Here, the control unit 546 adjusts the angle of the flap 542 by detecting the rotational speed of the internal combustion engine 502 or the hydraulic pressure from the oil pump driven by the internal combustion engine 502. Specifically, the control unit 546 is configured as an electronic control circuit, and detects the rotational speed of the internal combustion engine 502 with a sensor. When the rotational speed is less than 1500 rpm, the flap 542 is opened as shown in FIG. Separated from the portion 540a, the opening 540a is opened.

When the rotational speed of the internal combustion engine 502 is 1500 rpm or more, the control unit 546 closes the opening 540a by bringing the flap 542 as close as possible to the opening 540a as shown in FIG.
<Operation of Embodiment 6> When the internal combustion engine 502 is rotating at low speed, the oil mist can be removed from the blow-by gas by the oil being sprayed into the blow-by gas path by the oil spraying means of each embodiment as described above. At this time, since the baffle plate 540 of the oil level vibration suppression mechanism 538 has its opening 540a opened, the rotation of the crankshaft 530 causes the air between the crankshaft 530 and the oil level 536a to undergo pressure vibration and flow. This causes the oil level 536a to vibrate.

  As a result, the oil 536 is ejected in the form of oil droplets from the oil surface 536a. For this reason, even if the amount of oil sprayed by the above-described oil spraying means is small due to the low oil pressure, or even if the amount of oil in the accumulator 242 (FIGS. 4 and 5) is limited, the amount of oil spraying can be supplemented.

  When the internal combustion engine 502 is rotating at a high speed, as described above, the oil spraying means according to the first, second, and fourth embodiments sprays a larger amount of oil into the blowby gas path than when the engine is rotating at a low speed. Can be removed sufficiently.

  At this time, the baffle plate 540 of the oil level vibration suppression mechanism 538 closes the opening 540a, so that rotation of the crankshaft 530 may cause pressure vibration or flow between the crankshaft 530 and the baffle plate 540. This makes it difficult for the oil level 536a to vibrate. As a result, the amount of oil scattered from the oil surface 536a is suppressed.

  Even in the configuration in which the oil spraying from the oil spraying means is stopped at the time of high rotation as in the third and fifth embodiments, the opening 540a of the baffle plate 540 in the oil level vibration suppression mechanism 538 is provided at the time of low rotation of the internal combustion engine 502. By opening, the amount of oil spray can be supplemented as described above.

Even when the oil spraying means of the third and fifth embodiments stops the oil spraying at the time of high rotation of the internal combustion engine 502, the generation of oil droplets due to another oil supply configuration such as an oil jet increases. At this time, since the opening 540a of the baffle plate 540 is closed, the amount of oil scattered from the oil surface 536a is suppressed as described above, so that generation of oil droplets in the blow-by gas path can be suppressed as a whole.
<Effects of Embodiment 6> (1) While producing the effects of any of Embodiments 1 to 5 above, closing the opening 540a of the baffle plate 540 during high rotation causes more oil droplets to blow-by gas. It can be prevented from occurring in the route. For this reason, the rotational resistance of each part of the rotation of the internal combustion engine 502 can be reduced, and the fuel efficiency is improved.

[Embodiment 7]
<Configuration of Embodiment 7> FIG. 11 shows the internal configuration of an oil level vibration suppression mechanism 638 (corresponding to oil level vibration suppression means) of this embodiment. The oil level vibration suppression mechanism 638 suppresses vibrations on the oil level 636a in the oil pan when the internal combustion engine 602 rotates at a high speed. Other configurations are the same as those of the first to fifth embodiments. Therefore, the configuration of the present embodiment is a combination of the oil spraying means and the oil level vibration suppressing means.

The oil level vibration suppression mechanism 638 includes a hydraulic actuator 640 and a balance shaft cover 642.
The hydraulic actuator 640 includes a cylinder chamber 644 and a valve chamber 646. A hydraulic piston 648 is provided in the cylinder chamber 644, and a control slider 650 is provided in the valve chamber 646.

  The valve chamber 646 is connected to a hydraulic passage 646a, two drain passages 646b and 646c, a forward oil passage 646d, and a backward oil passage 646e. Oil from the oil pump of the internal combustion engine 602 is supplied from one end side of the valve chamber 646 by the hydraulic passage 646a. The drain passages 646b and 646c discharge oil in the valve chamber 646 from the respective positions.

  The cylinder chamber 644 is divided into a forward oil chamber 644a and a reverse oil chamber 644b by a hydraulic piston 648. The forward side oil passage 646d connects the forward side oil chamber 644a and the valve chamber 646, and the backward side oil passage 646e connects the backward side oil chamber 644b and the valve chamber 646.

  A control slider 650 serving as a valve element disposed in the valve chamber 646 includes a connection between the hydraulic passage 646a and the drain passages 646b and 646c, the forward-side oil passage 646d, and the backward-side oil passage 646e, and the hydraulic passage 646a. It is switched according to the hydraulic pressure supplied from. For this purpose, a spring 652 in a compressed state is disposed in the valve chamber 646 on the side opposite to the hydraulic passage 646a with respect to the control slider 650, and urges the control slider 650 toward the hydraulic passage 646a.

  The balance shaft cover 642 has a semi-cylindrical shape, and one end side thereof is connected to the hydraulic piston 648 via a rod 642a with the semi-cylindrical portion thereof facing down. Therefore, the balance shaft cover 642 moves integrally with the hydraulic piston 648 in the axial direction of the rod 642a. In the moving direction of the balance shaft cover 642, there is a vibration-absorbing balance shaft 602 b that is rotated in conjunction with the crankshaft 602 a of the internal combustion engine 602.

In the state where the rod 642a is drawn into the cylinder chamber 644 as shown in FIG. 11, the balance shaft cover 642 does not cover the balance shaft 602b. As shown in FIG. 12, when the hydraulic piston 648 moves and the rod 642a extends from the cylinder chamber 644, the balance shaft cover 642 covers the balance shaft 602b from the lower side and isolates the balance shaft 602b from the oil surface 636a. .
<Operation of Embodiment 7> When the internal combustion engine 602 has a low rotation speed and the oil from the oil pump has a low oil pressure (less than 200 kPa in this case), the control slider 650 in the valve chamber 646 moves from the hydraulic passage 646a. The applied pressure is relatively small. For this reason, the control slider 650 cannot compress the spring 652, and is in the state shown in FIG. That is, the oil in the hydraulic passage 646a is supplied to the backward oil chamber 644b by the internal passage 650a of the control slider 650 through the backward oil passage 646e. The oil in the forward oil chamber 644a enters the valve chamber 646 via the forward oil passage 646d and is discharged from the drain passage 646b.

  As a result, the hydraulic piston 648 moves to the right side in the figure, and the rod 642a is pulled into the cylinder chamber 644. Therefore, there is almost no balance shaft cover 642 between the balance shaft 602b rotated by the crankshaft 602a and the oil 636 in the oil pan. In this state, the balance shaft 602b rotates.

  For this reason, the rotation of the balance shaft 602b causes the air between the balance shaft 602b and the oil surface 636a to generate pressure vibration and flow, and vibrates the oil surface 636a. As a result, the oil 636 jumps out from the oil surface 636a in the form of oil droplets. For this reason, even if the amount of oil sprayed by the above-described oil spraying means is small due to the low oil pressure, or even if the amount of oil in the accumulator 242 (FIGS. 4 and 5) is limited, the amount of oil spraying can be supplemented.

  When the internal combustion engine 602 is rotating at a high speed, as described above, the oil spraying means of the first, second, and fourth embodiments sprays a larger amount of oil into the blowby gas path than at the time of the low rotation, thereby causing oil mist from the blowby gas. Can be removed sufficiently.

  At this time, the oil from the oil pump becomes a high pressure (200 kPa or more in this case), and the state shown in FIG. 12 is obtained. That is, the control slider 650 compresses the spring 652 by the hydraulic pressure on the hydraulic passage 646a side. Therefore, the oil in the hydraulic passage 646a is supplied to the advance side oil chamber 644a via the advance side oil passage 646d. The oil in the backward oil chamber 644b enters the valve chamber 646 through the backward oil passage 646e and is discharged from the drain passage 646c.

  As a result, the hydraulic piston 648 moves to the left in the figure, and the rod 642a extends from the cylinder chamber 644. Therefore, the balance shaft cover 642 is sufficiently inserted between the balance shaft 602b and the oil 636. Thus, the balance shaft 602b rotates in the state covered with the balance shaft cover 642.

  Therefore, even if the air between the balance shaft 602b and the balance shaft cover 642 causes pressure vibration and flow due to the rotation of the balance shaft 602b, the vibration of the oil surface 636a due to this is prevented. As a result, the amount of oil scattered from the oil surface 636a is suppressed.

  Even in the configuration in which the oil spraying from the oil spraying means is stopped at the time of high rotation as in the third and fifth embodiments, the balance shaft cover 642 of the oil level vibration suppression mechanism 638 is shown in FIG. By becoming a state, the amount of oil spraying can be supplemented as described above.

Even when the oil spraying means of the third and fifth embodiments stops the oil spraying at the time of high rotation of the internal combustion engine 602, the generation of oil droplets due to another oil supply configuration such as an oil jet increases. At this time, the oil level vibration suppression mechanism 638 is in the state shown in FIG. 12, and as a result, the amount of oil scattered from the oil level 636a is suppressed as described above, thereby suppressing the generation of oil droplets in the blow-by gas path as a whole. it can.
<Effects of Embodiment 7> (1) The effects of any one of Embodiments 1 to 5 are produced, and the balance shaft cover 642 covers the balance shaft 602b at the time of high rotation. It can be prevented from occurring in the gas path. For this reason, the rotational resistance of each part of the rotation of the internal combustion engine 602 can be reduced, and the fuel efficiency is improved.

[Other embodiments]
In each of the above embodiments, the oil spraying from the oil spraying part is due to the oil supply from the oil pump driven by the output of the internal combustion engine, but separately provided an electric pump for oil spraying, The oil from this electric pump may be the target to be sprayed.

  In this case, by controlling the drive of the electric pump by the control circuit regardless of the output level of the internal combustion engine, oil can be sprayed or stopped in the blow-by gas path with a high degree of freedom. For example, in the configuration of the first and second embodiments, the electric pump is driven to spray oil when the internal combustion engine is at low speed (low hydraulic pressure), and the oil is stopped at high speed (high hydraulic pressure) to stop the electric pump. It can be controlled to stop spraying.

  In the third embodiment, instead of discharging the accumulated oil from the accumulator 242, oil is discharged from the separately provided oil pump to the hydraulic control valve 240 side instead of the accumulator 242 at low rotation (low hydraulic pressure). Also good.

  Instead of the hydraulic control valve 240 of the third embodiment, an electromagnetic valve is used to open the valve at a hydraulic pressure of 90 to 200 kPa by electronic control, and the oil from the accumulator 242 or the oil pump separately provided as described above is used. You may make it spread.

Further, an electromagnetic valve may be used in place of the check valve 244 of the third embodiment, and the valve may be controlled to open at 200 kPa or more.
-Although the rotary actuator 544 of the said Embodiment 6 was comprised with the electric motor, it comprises as a hydraulic actuator in addition to this, the flap 542 is opened by the control part 546 when hydraulic pressure is less than 200 kPa, and it closes above 200 kPa. The hydraulic pressure switching control may be executed.

  The control unit 546 of the sixth embodiment is not an electronic control circuit, and as a hydraulic switch, when the hydraulic pressure is less than 200 kPa, the drive of the rotary actuator 544 is stopped (switched off), the flap 542 is opened, and the rotary actuator 544 is operated at 200 kPa or more. The flap 542 may be closed by driving (switch-on).

  DESCRIPTION OF SYMBOLS 2 ... Internal combustion engine, 4 ... Piston, 6 ... Cylinder, 8 ... Crank case, 10 ... Front cover, 12 ... Cam case, 14 ... Oil separator, 16 ... Piping, 18 ... Blow-by gas path, 20 ... Cylinder head, 22 ... Oil Spreading part, 24 ... Oil spraying port, 26 ... Oil introduction port, 28 ... Oil hole, 30 ... Crankshaft, 32 ... Oil pump, 34 ... Oil pan, 36 ... Oil, 38 ... Strainer, 122 ... Oil spraying part, 124 DESCRIPTION OF SYMBOLS ... Oil spray port, 126 ... Oil introduction port, 222 ... Oil spray part, 222a ... Oil passage, 224 ... Oil spray port, 240 ... Hydraulic control valve, 240a ... Valve, 240b ... Spring, 240c ... Through-hole, 242 ... Accumulator 242a ... Spring, 242b ... Plunger, 244 ... Check valve, 244a ... Oil passage, 3 DESCRIPTION OF SYMBOLS 2 ... Internal combustion engine, 312 ... Cam case, 313 ... Cam shaft, 313a ... Cam, 314 ... Oil separator, 318 ... Blow-by gas path, 320 ... Cylinder head, 322 ... Oil dispersion part, 330, 430 ... Crankshaft, 432 ... Counter Weight, 432a ... tip opening, 434 ... oil spreading part, 434a ... valve chamber, 434b ... seat part, 434c ... internal opening, 434d ... steel ball, 434e ... spring, 436, 438 ... oil path, 502 ... internal combustion engine 508 ... Crank case 530 ... Crankshaft 534 ... Oil pan 536 ... Oil 536a ... Oil level 538 ... Oil level vibration suppression mechanism 540 ... Baffle plate 540a ... Opening portion 540b ... Post, 542 ... Flap , 542a ... link, 544 ... rotary actuator 546 ... control unit, 602 ... internal combustion engine, 602a ... crankshaft, 602b ... balance shaft, 636 ... oil, 636a ... oil level, 638 ... oil level vibration suppression mechanism, 640 ... hydraulic actuator, 642 ... balance shaft cover, 642a ... Rod, 644 ... Cylinder chamber, 644a ... Advance side oil chamber, 644b ... Backward side oil chamber, 646 ... Valve chamber, 646a ... Hydraulic passage, 646b, 646c ... Drain passage, 646d ... Advance side oil passage, 646e ... Backward Side oil passage, 648 ... hydraulic piston, 650 ... control slider, 650a ... internal passage, 652 ... spring.

Claims (10)

A blow-by gas processing device for flowing a blow-by gas generated from an internal combustion engine through a blow-by gas path and guiding it to an oil separator,
A blow-by gas processing apparatus comprising an oil spraying means for spraying oil in a granular, linear or film form in the air in the blow-by gas path. The blow-by gas processing apparatus according to claim 1, wherein the oil spraying means introduces oil into the blow-by gas path by an accumulator or a pump and sprays the oil in a granular, linear, or film form. Blow-by gas processing equipment. 3. The blow-by gas processing apparatus according to claim 1, wherein the oil spraying means has the granular and linear shapes in a direction opposite to a flow direction of the blow-by gas in the air in the blow-by gas path by spraying oil. Or the blow-by gas processing apparatus characterized by moving the film-form oil. 4. The blow-by gas processing apparatus according to claim 3, wherein the oil spraying means sprays oil in a region where the blow-by gas rises from the lower side to the upper side in the vertical direction in the blow-by gas path. Blow-by gas processing equipment. The blowby gas processing apparatus according to claim 4, wherein the region is a space covered with a front cover. 6. The blow-by gas processing apparatus according to claim 4, wherein the oil spraying means has a direction of the oil spraying port as a direction intersecting a flow direction of the blow-by gas. 4. The blow-by gas processing apparatus according to claim 3, wherein the oil spraying means sprays oil in a space covered with a cam cover. 4. The blow-by gas processing apparatus according to claim 3, wherein the oil spraying means sprays oil in a space covered with a crankcase. The blow-by gas processing apparatus according to any one of claims 1 to 8, wherein the oil spraying means sprays oil when the internal combustion engine is at a low rotation speed or low hydraulic pressure, and when the internal combustion engine is at a high rotation speed or high hydraulic pressure. A blow-by gas processing apparatus characterized in that the spraying of oil is stopped. The blow-by gas processing apparatus according to any one of claims 1 to 9, further comprising an oil level vibration suppressing unit that suppresses vibration on an oil level of an oil pan when the internal combustion engine rotates at high speed. Gas processing device.