KR101338778B1 - Structure of exhaust gas separation device of internal combustion engine - Google Patents

Abstract

To improve the fuel efficiency, reliability and working efficiency of the internal combustion engine.
Solution
The low temperature chamber 14 has a vortex shape in which the cross-sectional area up to the inlet of the low-temperature exhaust passage is gradually widened in the turning direction of the combustion gas with the predetermined position as the starting point SP. On the inner wall surface 12a of the high temperature chamber 12, the rectifying plates 17 and 18 which guide | induce the high temperature combustion gas introduce | transduced into a high temperature chamber to the high temperature exhaust passage are formed. In the hydraulic cylinder block 40 in which the several hydraulic cylinders 43 were formed, the hydraulic zero position control apparatus 52 which controls the zero limit position of the sub valve 25 by regulating the lower limit position of the sub valve air piston is provided. . The hydraulic cylinder block 40 is formed of the outer hydraulic cylinder block 41 and the inner hydraulic cylinder block 42, and a plurality of hydraulic cylinders 43 and the first hydraulic passage 65 are formed in the inner hydraulic cylinder block, A second hydraulic passage 69 is formed between the outer hydraulic cylinder block and the inner hydraulic cylinder block, and third hydraulic passages 61, 62, 63 are formed in the outer hydraulic cylinder block.

Description

Structure of Exhaust Gas Separation Unit of Internal Combustion Engine {STRUCTURE OF EXHAUST GAS SEPARATION DEVICE OF INTERNAL COMBUSTION ENGINE}

The present invention relates to the structure of an exhaust gas separation device of an internal combustion engine.

In an internal combustion engine, for example, a two cycle uniflow diesel engine, as shown in FIG. 12, one exhaust valve (hereinafter referred to as a main valve) 121 is inserted into the exhaust valve box 111. The main valve 121 is opened and closed to exhaust the combustion gas (exhaust gas) to the exhaust receiver (exhaust assembly), and scavenging is also performed. The scavenging is performed by introducing scavenging from an unillustrated scaffold formed on the inner wall of the cylinder liner. In addition, the exhaust valve box 111 includes a sub valve 125 which is different from the main valve 121, and an upper high temperature chamber 106 and a lower low temperature chamber 108 separated into two via the sub valve 125. Formed.

Then, at a valve opening initial stage (exhaust initial stage) of the main valve 121, combustion gas having a high pressure and a high temperature is introduced into the high temperature chamber 106 from the cylinder, and the high temperature exhaust passage 112 is opened from the high temperature chamber 106. The combustion gas of high temperature is discharged | emitted to the exhaust receiver (outside) via this. In addition, the remaining combustion gas in the cylinder is introduced into the low temperature chamber 108 from the valve opening middle stage of the main valve until the valve is closed (from the middle stage of exhaust) to the low temperature exhaust passage 113 from the low temperature chamber 108. The low temperature combustion gas is discharged to the outside (see Patent Document 1).

Therefore, the lower cold chamber 108 is led to a swirl flow having a strong swirl formed at the scavenging pot. However, since the high temperature combustion gas guide | induced to the upper high temperature chamber 106 is an exhaust initial stage, there was no especially strong swirl.

An intake device of an internal combustion engine, the intake pipe formed between the collector and the engine head bypasses the auxiliary valve, which is closed during lean combustion, idle, or low temperature, the fuel injection valve, and the auxiliary valve to inject the collector and the fuel injection valve. The invention which forms the straight path | route which connects both sides of and made easy the formation of an intake path | path by these is disclosed (refer patent document 2).

In the structure of the exhaust gas separation device of the conventional internal combustion engine, for example, as shown in FIG. 13, the low temperature chamber 108 is formed concentrically with the exhaust port 105a of the exhaust valve box 105, and the main valve 121 is provided. The low temperature combustion gas introduced into the low temperature chamber 108 from the cylinder through the exhaust port 105a of the exhaust valve box 105 from the valve opening middle stage to the closing of the valve is in the streamline of arrows AH. As shown, it flows into the low temperature exhaust passage 113 with strong swirl (orbital flow) with respect to the centerline L connecting the center of the outlet 113a of the low temperature exhaust passage 113 to the center of the low temperature chamber 108. . In FIG. 13, the length of the streamline indicates the flow velocity of the combustion gas at the position.

However, the flow velocity of the combustion gas is gradually increasing from the position of the streamline of arrow A in FIG. 13 to the position of the streamline of arrow H, while obtaining the maximum flow rate at the position of arrow line H, while the position of the streamline of arrows A-G. That is, in most areas around the exhaust port 105a, it is very slow.

That is, since the flow resistance of the combustion gas in the low temperature chamber 108 is large, the flow of the combustion gas discharged | emitted from the low temperature chamber 108 to the low temperature exhaust passage 113 worsens, and to the cross-sectional area of the outlet 113a of the exhaust passage 113 is reduced. There is a problem that the exhaust of the proper flow rate is not achieved and the scavenging efficiency is very poor.

Since the low temperature chamber 108 is formed concentrically with the exhaust port 105a of the exhaust valve box 105, the center of the outlet 113a of the low temperature exhaust passage 113 and the exhaust port of the exhaust valve box 105 ( It becomes symmetrical with respect to the center line L connecting the center in the low temperature chamber 108 of 105a, and this causes a bad flow of the combustion gas from the low temperature chamber 108 to the low temperature exhaust passage 113. I can think of it.

On the other hand, the intake apparatus disclosed in Patent Document 1 simplifies the configuration of the intake passage, and as in the present invention, residual combustion gas in the cylinder is discharged from the valve opening middle period of the main valve to the closing of the valve. The invention is not directed to the exhaust chamber, which is discharged from the low temperature chamber via the low temperature exhaust passage to the exhaust receiver, and the scavenging with strong swirl formed at the scavenging port of the cylinder is led to the low temperature chamber.

Next, as a structure of the exhaust gas separation apparatus of the conventional internal combustion engine, the exhaust purification apparatus of the internal combustion engine which eliminated the deposit by the adhesion of the combustion residue to the rectification plate, and prevents blockage of the rectification plate is proposed (patent document 3). Reference). Moreover, in the internal combustion engine equipped with the large-size low-pressure turbocharger, the internal combustion engine provided with the exhaust receiver which can suppress a vibration effectively is proposed (refer patent document 4).

However, the structure of the exhaust gas separation device of the conventional internal combustion engine is formed into a cross-sectional shape as shown in FIG. 14, for example. In this structure, since the combustion gas introduced from the cylinder into the high temperature chamber 106 through the exhaust port 105a of the exhaust valve box 105 is the exhaust initial stage as described above, in particular, swirl (orbital flow) is accompanied. As shown by the arrow, with respect to the center line L connecting the center of the outlet 112a of the high temperature exhaust passage 112 and the center of the high temperature chamber 106, it becomes a substantially symmetrical flow and is discharged | emitted, and is high temperature. It flows to the exhaust passage 112. In FIG. 14, the length of the streamline representing the flow of the combustion gas indicates the flow velocity at the position.

Here, the combustion gas discharged from the high temperature chamber 106 touches the inner wall surface 106a of the high temperature chamber 106 at a position opposite to the outlet 112a of the high temperature exhaust passage 112, and part of the combustion gas is refluxed. It does not stay and flow, and smooth flow is inhibited. In addition, in the position of the outlet 112a side of the high temperature exhaust passage 112 of the high temperature chamber 106, vortex is generated in a part of the combustion gas discharged from the high temperature chamber 106, and smooth flow is also hindered.

For this reason, the flow of the combustion gas which flows in the high temperature chamber 106 and from the high temperature chamber 106 into the hot exhaust path 112 becomes very bad. As a result, the combustion gas of the flow volume suitable for the minimum cross-sectional area of the hot exhaust path 112 cannot be discharged, and there exists a problem that exhaust efficiency is very bad.

Moreover, in each said patent document 3 and 4, the invention which opened and closes an exhaust valve and discharges combustion gas from one high temperature chamber to one exhaust receiver (exhaust assembly part) from a high temperature chamber is not disclosed at all.

Next, the exhaust valve apparatus 110 shown in FIG. 12 is attached to the valve seat 102 of the cylinder block 101, for example. The exhaust valve device 110 includes an exhaust valve (hereinafter referred to as a main valve) 121 that exhausts, a high temperature gas exhaust passage 112 for hot gas and a low temperature gas exhaust passage for cold gas of the exhaust valve box 111. 113, a sub valve 125 for switching the flow of combustion gas to the high temperature exhaust passage 112 and the low temperature exhaust passage 113, and a casing 115 to form a valve opening operation of the main valve 121. A plurality of, for example, three hydraulic cylinders 130 and a main valve 121, which are formed in the hydraulic cylinder block 117 and the hydraulic cylinder block 117 to perform the switching operation of the sub valve 125. The main valve air piston 123 fixed to the upper portion of the valve stem 122 of the main valve 121 to perform a recovery operation of the main valve 121, and fixed to the upper portion of the valve stem 126 of the secondary valve 125. A secondary valve air piston 127 for performing a recovery operation of the valve 125, There is the one configured by a casing 116 that forms the air piston (123, 127) for receiving the air spring chamber (129) to impart to the air pressure.

Here, the exhaust valve apparatus 110 mentioned above has shown the case where it applies to the 2 cycle uniflow type diesel engine. In the two-cycle uniflow type diesel engine, for example, the cylinder liner sidewall has an intake port (small device), and the main valve 121 performs exhaust only.

The valve opening operation of the main valve 121 is performed by the hydraulic cylinder 128 operating by high pressure hydraulic pressure being pushed downward of the valve stem 122. Moreover, the valve closing operation (recovery operation) is performed by the main valve air piston 123 attached to the valve stem 122 pulling the valve stem 122 upward. That is, the air pressure in the air spring chamber 129 formed below the main valve air piston 123 is an operating source of the valve closing operation of the main valve 121.

The switching operation of the secondary valve 125 is performed by a plurality of hydraulic cylinders 130 formed in the hydraulic cylinder block 117 by high pressure hydraulic pressure, and also concentrically with the valve stem 122 of the main valve 121. The sub-valve air piston 127 attached to the valve stem 126 extrapolated to be free to slide in the axial direction is carried out by pushing upwards.

Moreover, the restoration operation | movement is performed by sending out the oil_pressure | hydraulic of several hydraulic cylinder 130, and pushing the valve stem 126 downwardly by the secondary valve air piston 127 attached to the valve stem 126. That is, the air pressure in the air spring chamber 129 formed above the secondary valve air piston 127 is an operating source of the recovery operation of the secondary valve 125. The exhaust valve apparatus provided with such a sub valve is disclosed by Unexamined-Japanese-Patent No. 2008-248720, for example (patent document 5).

In the exhaust valve device shown in FIG. 12, the secondary valve 125 is held at a position shown at the beginning of exhaust when the main valve 121 starts to open at the time of exhaust, so that the high-temperature exhaust gas 112 is discharged. Is discharged from the position shown after the middle stage of the exhaust to the low temperature exhaust passage 113, and discharged to the low temperature exhaust passage 113.

However, in this conventional exhaust valve apparatus 110, the sub valve 125 is cylindrical and the inner peripheral surface is fixed to the valve stem 126 by the some plate-shaped rib 125c. And the lower end part 125a of the sub valve 125 which comprises a cylindrical shape is formed in the shape which the front end (lower end surface) 125b opened in the trumpet shape, and this front end 125b is upper side of the valve seat 102. Has a slight gap with the rounding processing unit 102a.

The secondary valve 125 is pushed down by the secondary valve air piston 127 together with the degeneration of the hydraulic cylinder 130 to perform a valve closing, that is, a recovery operation. For example, an abnormality is caused in the drive system of the hydraulic cylinder 130. When it arises, there exists a problem that the sub valve air piston 127 may fall too much, and the front-end | tip 125b of the sub valve 125 may land (collide) with the rounding process part 102a above the valve seat 102. .

Since the sub-valve 125 is formed by the rib of a complicated shape, when the front-end 125b is seated on the rounding process part 102a above the valve seat 102, a big impact stress will act on a rib, and it will be broken. As a result, the entire sub-valve 125 may be damaged in some cases.

For this reason, since it is necessary to obtain the strength of the rib especially, the sub valve 125 is difficult to form into an inexpensive cast product, and forgings are formed by cutting. Therefore, the manufacturing cost of the secondary valve 125 becomes very high. For this reason, even when an abnormality occurs in the drive system of the hydraulic cylinder 130, the tip 125b of the subordinate valve 125 is seated (collides) to the rounding treatment part 102a above the valve seat 102. There is a strong call to prevent.

Moreover, in the structure of the exhaust gas separation apparatus of the conventional internal combustion engine mentioned above, the several (three) hydraulic cylinder 130 of the hydraulic cylinder block 117 is perpendicular from the upper end surface of the said hydraulic cylinder block 117. As shown in FIG. 15, it communicates with the hydraulic passages 131-134 formed in the bottom part by the horizontal perforation from the side surface 117a.

These hydraulic passages 131 to 134 are vertically formed in parallel with the hydraulic passage 135 formed on the side surface 117a of the hydraulic cylinder block 117 and the hydraulic cylinder 130 so that one end (upper side) of the hydraulic passage is hydraulic. While communicating with the passage 135, the other end communicates with the hydraulic passage 136 which communicates with the hydraulic passages 131, 134.

However, since the hydraulic passages 131 to 136 of the hydraulic cylinder block 117 are formed by machining (boring), the machining becomes complicated and the bending (curing) at the time of drilling is performed. ) And cutting powder (cutting powder) are difficult to remove and there is a problem that a great deal of effort and cost are required for the post-treatment. Moreover, when cutting powder (cutting powder) even a little remains in the hydraulic passage, there exists a problem that it may cause the sliding problem of a hydraulic cylinder.

(Patent Document 1) [Patent Document 1] Japanese Utility Model Model: Japanese Patent Utility Model Publication No. 02-145617

(Patent Document 2) [Patent Document 2] Japanese Laid-Open Patent Publication: Japanese Laid-Open Patent Publication 2002-364472

(Patent Document 3) [Patent Document 3] Japanese Laid-Open Patent Publication: Japanese Laid-Open Patent Publication No. 2007-182786

(Patent Document 4) [Patent Document 4] Japanese Laid-Open Patent Publication: Japanese Patent Laid-Open Publication No. 07-317558

(Patent Document 5) [Patent Document 5] Japanese Laid-Open Patent Publication: Japanese Laid-Open Patent Publication 2008-248720

This invention is made | formed in order to solve such a problem, Comprising: It aims at improving fuel efficiency, reliability, and work efficiency of an internal combustion engine.

Specifically, the internal combustion which reduces the flow resistance of the combustion gas in the low temperature chamber of the exhaust gas separation device and exhausts it without inhibiting the scavenging flow pattern accompanied by the strong swirl formed in the scavenging port can significantly increase the scavenging efficiency. It provides a structure of the engine exhaust gas separation device and facilitates the flow of the combustion gas in the hot chamber and the hot exhaust passage in the exhaust valve box for discharging the high temperature combustion gas to the exhaust receiver, thereby exhausting efficiency. An object of the present invention is to provide a structure of an exhaust gas separation device of an internal combustion engine, which is designed to significantly increase the pressure.

In addition, even when an abnormality occurs in the drive system of the hydraulic cylinder that opens and operates the secondary valve, the lower limit position of the secondary valve is regulated to prevent the lower end portion from seating on the valve seat, thereby preventing damage or deformation of the secondary valve. It provides a structure of the exhaust gas separation device of the internal combustion engine and facilitates machining (boring) of the hydraulic passage that communicates each hydraulic cylinder, and also causes bending (curing) and cutting powder generated during machining. It is possible to improve the workability of the (cutting) removal processing work, thereby facilitating the final inspection of the hydraulic cylinder block, reducing the cost, and as described above, bending of the hydraulic passage ( Since it is easy to remove curling and cutting powder (cutting powder), it is possible to prevent the sliding problem of the hydraulic cylinder caused by the cutting powder. To provide an exhaust structure of a gas separation apparatus for an internal combustion engine that can improve the reliability and to challenge.

MEANS TO SOLVE THE PROBLEM In order to solve the said subject, the means employ | adopted by this invention is a main valve which exhausts in-cylinder combustion gas, and the high temperature combustion gas formed in the exhaust valve box and discharged | emitted through the main valve from a cylinder to the outside. A high temperature exhaust passage, a low temperature chamber formed in the exhaust valve box to introduce low-temperature combustion gas discharged through the main valve from the cylinder, a low temperature exhaust passage formed in the exhaust valve box to discharge the combustion gas in the low temperature chamber to the outside, and exhaust In the structure of the exhaust gas separation device of an internal combustion engine provided in a valve box and having a secondary valve for switching the flow of combustion gas to the hot exhaust passage and the cold exhaust passage, the low temperature chamber has a low temperature exhaust passage starting from a predetermined position. The cross-sectional area up to the inlet of the vortex is gradually widened in the direction of combustion gas It is in doing.

The combustion gas discharged from the cylinder after the valve opening middle stage of the main valve is introduced into the low temperature chamber and discharged from the low temperature chamber to the outside through the low temperature exhaust passage. The shape of the low-temperature chamber is a vortex shape in which the cross-sectional area to the inlet of the low-temperature exhaust passage is gradually widened in the rotational direction of the combustion gas, starting from a predetermined position, so that the combustion gas formed by the scavenging from the air mechanism and accompanied by strong swirl It is possible to lead to the low temperature chamber without inhibiting the swirl, which can greatly reduce the flow resistance of the combustion gas. As a result, the combustion gas of the flow volume suitable for the cross-sectional area of the low temperature exhaust passage can be smoothly discharged, and the scavenging efficiency is remarkably improved.

In the structure of the exhaust gas separation device of the internal combustion engine, it is preferable that the inlet of the low temperature chamber and the low temperature exhaust passage smoothly be curved to the curved surface of the different radius of curvature. In this way, by smoothly extending the inlet of the low temperature chamber and the low temperature exhaust passage to the curved surface of the different radius of curvature, the flow resistance of the exhaust gas discharged from the low temperature chamber to the low temperature exhaust passage can be further reduced.

In the structure of the exhaust gas separation device of the internal combustion engine, the starting point is located at a position shifted by a predetermined angle in the rotational direction of the combustion gas from the center line connecting the center of the outlet of the cold exhaust passage and the center of the exhaust port of the cylinder. It is desirable to have. In this way, the vortex-shaped starting point of the low-temperature chamber is introduced into the low-temperature chamber by setting it at a position shifted by a predetermined angle in the rotational direction of the combustion gas from the center line connecting the center of the outlet of the low-temperature exhaust passage and the center in the low-temperature chamber of the exhaust port of the cylinder. It is possible to more smoothly flow the combustion gas thus induced into the low temperature exhaust passage.

In the structure of the exhaust gas separation device of the internal combustion engine, the low temperature chamber is preferably formed by curved surfaces having different curvature radii which gradually increase from the starting point to the inlet of the low temperature exhaust passage. Thus, by forming the low temperature chamber from the starting point to the inlet of the low temperature exhaust passage, the curved surface of the different curvature radius sequentially increases, so that a spiral exhaust passage whose sectional area gradually increases toward the inlet of the low temperature exhaust passage can be formed, and thus combustion It is possible to form an exhaust passage that does not further inhibit the swirl of the gas.

Moreover, in order to solve the said subject, the means employ | adopted by this invention is the main valve which exhausts in-cylinder combustion gas, and the high temperature combustion gas formed in the exhaust valve box and discharged | emitted through the main valve from a cylinder to the outside. A high temperature exhaust passage to discharge, a low temperature exhaust passage formed in the exhaust valve box to discharge the low temperature combustion gas discharged through the main valve from the cylinder to the outside, and a high temperature exhaust passage and the low temperature exhaust passage formed in the exhaust valve box to In the structure of the exhaust-gas separation apparatus of the internal combustion engine provided with the sub valve which switches the flow of a combustion gas, a sub valve has a staff cylinder shape and a skirt part is formed in the front-end | tip.

In this way, by forming a skirt at the tip of the sub-valve forming the cylindrical shape, the combustion gas discharged from the exhaust port of the cylinder head can be smoothly guided to the low temperature chamber without inhibiting swirl, and thus the combustion gas is discharged into the low temperature chamber. The efficiency is significantly improved.

In the structure of the exhaust gas separation device of the internal combustion engine, the skirt portion preferably has a truncated cone cylindrical shape having a larger diameter than the outer diameter of the front end. Thus, by making the outer diameter of the rear end of the skirt part of a sub valve into the shape of a truncated cone cylinder of a larger diameter than the outer diameter of a front end, the skirt part which has the inclined outer peripheral surface so that the diameter may expand from the front end to the rear end facing the exhaust port of an exhaust valve box is formed. The inclined outer circumferential surface of the skirt allows the combustion gas discharged from the exhaust port of the exhaust valve box to be smoothly guided into the low temperature chamber, whereby the scavenging efficiency can be further improved.

In the structure of the exhaust gas separation device of the internal combustion engine, the skirt portion has a smaller outer diameter than the exhaust port of the exhaust valve box, and the outer peripheral surface of the rear end can make sliding contact with the inner peripheral surface of the exhaust port of the exhaust valve box. It is preferable. In this way, the outer diameter of the skirt tip is made smaller than the exhaust port of the exhaust valve box, and the outer peripheral surface of the rear end can be slid in contact with the inner peripheral surface of the exhaust port of the cylinder head, thereby smoothly inserting the skirt portion into the exhaust port of the exhaust valve box. You can do it. In addition, by sliding the outer peripheral surface of the rear end of the skirt portion into the exhaust port, the gap between the exhaust port and the cylinder-shaped sub valve can be prevented. As a result, the combustion gas discharged from the exhaust port of the cylinder head can be led to the low temperature chamber without leakage.

Moreover, in order to solve the said subject, the means employ | adopted by this invention introduces the main valve which exhausts in-cylinder combustion gas, and the high temperature combustion gas formed in the exhaust valve box, and discharged | emitted through the main valve from a cylinder. And a high temperature exhaust passage formed in the exhaust valve box to discharge the combustion gas in the high temperature chamber to the outside, and a low temperature exhaust gas formed in the exhaust valve box to discharge the low temperature combustion gas discharged through the main valve from the cylinder to the outside. In the structure of the exhaust gas separation apparatus of an internal combustion engine having a passage and a sub-valve formed in the exhaust valve box to switch the flow of combustion gas to the hot exhaust passage and the low temperature exhaust passage, the high temperature chamber is provided on the inner wall surface of the high temperature chamber. The rectifier plate which guide | induces the high temperature combustion gas introduce | transduced into the high temperature exhaust passage smoothly is formed.

In this invention, the hot combustion gas discharged | emitted from the cylinder at the initial stage of valve opening of a main valve is introduce | transduced into a high temperature chamber, and is discharged | emitted from the high temperature chamber to the outside through a high temperature exhaust passage. Here, the rectifying plate newly formed on the inner wall surface of the high temperature chamber allows the combustion gas discharged from the cylinder to be introduced into the high temperature chamber to smoothly flow into the high temperature exhaust passage by eliminating its retention. As a result, the flow of the combustion gas in the high temperature chamber and the hot exhaust passage becomes constant, and as a result, the average flow rate is increased, so that the combustion gas at a flow rate suitable for the minimum cross-sectional area of the hot exhaust passage can be smoothly discharged.

In the structure of the exhaust gas separation device of the internal combustion engine, the rectifying plate preferably comprises a first rectifying plate formed on the side opposite to the outlet side of the hot exhaust passage and toward the outlet side centered around the exhaust port of the exhaust valve box. Do. Thus, the combustion introduced into the high temperature chamber from the cylinder by forming the first rectifying plate on the inner wall surface of the high temperature chamber, on the opposite side to the outlet side of the high temperature exhaust passage and toward the center of the outlet side centered on the exhaust port of the exhaust valve box. The gas can be divided almost equally on both sides of the first rectifying plate and can flow along the inner wall surface of the high temperature chamber, thereby effectively preventing interference and retention of the combustion gas in the site. As a result, the flow of the combustion gas becomes very smooth.

In the structure of the exhaust gas separation device of the internal combustion engine, the rectifying plate is preferably made of a second rectifying plate formed at the outlet side of the high temperature exhaust passage and toward the outlet center centered around the exhaust port of the exhaust valve box. Thus, by forming the second rectifying plate on the inner side of the inner wall of the high temperature chamber at the outlet side of the hot exhaust passage and toward the center of the outlet side centered on the exhaust port of the exhaust valve box, the combustion gas introduced from the cylinder is subjected to the second rectification. Almost equally divided on both sides of the plate can be allowed to flow in the high temperature exhaust passage, and interference and retention of the combustion gas at the site can be effectively prevented. As a result, the flow of the combustion gas becomes very smooth.

In the structure of the exhaust gas separation device of the internal combustion engine, the first rectifying plate is spread so that both sides thereof have an arc-shaped concave curved surface from the leading end toward the center of the outlet side of the high temperature exhaust passage toward the inner wall surface of the high temperature chamber. It is preferable. Thus, both sides of the first rectifying plate formed in the high temperature chamber are widened to form an arc-shaped concave curved surface from the tip toward the center of the outlet side of the high temperature exhaust passage toward the inner wall surface of the high temperature chamber, thereby introducing combustion into the high temperature chamber. The gas can be smoothly flowed toward the inner wall surface of the high-temperature chamber almost evenly on both sides along the concave curved surface, so that the flow of the combustion gas can be made smoother.

In the structure of the exhaust gas separation device of the internal combustion engine, the second rectifying plate is spread so that both sides thereof form an arc-shaped concave curved surface from the tip toward the center of the outlet side of the high temperature exhaust passage toward the inner wall surface of the high temperature chamber. It is desirable to have. Thus, both sides of the second rectifying plate formed in the high temperature chamber are formed so as to form an arc-shaped concave curved surface from the distal end toward the center of the outlet side of the high temperature exhaust passage toward the inner wall surface of the high temperature chamber, so that the combustion is discharged from the high temperature chamber. The gas flows almost evenly along the concave curved surface on both sides to smoothly flow in the hot exhaust passage. Thereby, the flow of combustion gas can be made smoother.

In the structure of the exhaust gas separation device of the internal combustion engine, it is preferable to form a bulge in the high temperature chamber by expanding the inner wall surface near the inlet of the high temperature chamber to form a convex curved surface. In the vicinity of the inlet of the high temperature chamber, vortices tend to form in the combustion gas introduced from the cylinder into the high temperature chamber along the inner wall surface. However, in this way, by forming a bulge formed in the high temperature chamber by expanding the inner wall surface near the inlet of the high temperature chamber to form a convex curved surface, the combustion gas from the cylinder flows along the inner wall surface of the high temperature chamber near the inlet of the high temperature chamber. Thus, the combustion gas introduced from the cylinder flows smoothly into the hot chamber and into the hot exhaust passage.

In the structure of the exhaust gas separation device of the internal combustion engine, a rectifying member having a substantially reverse conical shape is mounted on a supporting member for supporting the valve stem of the secondary valve, and the tip portion of the rectifying member has a diameter so as to form an arcuate concave curved surface. It is preferable to reduce and extend to the main valve side. In this way, the tip of the rectifying member mounted on the support member for supporting the valve stem of the secondary valve is formed to have an arc-shaped concave curved surface and extended to the main valve side, thereby smoothly burning the combustion gas from the cylinder into the hot chamber and into the hot exhaust passage. It is possible to guide the flow of the combustion gas more smoothly.

In the structure of the exhaust gas separation device of the internal combustion engine, a rectifying member having a substantially reverse cone shape is mounted on a supporting member for supporting the valve stem of the secondary valve, and the tip of the rectifying member corresponds to the convex curved surface of the bulging portion. It is preferable to reduce the diameter so as to form an arc-shaped concave curved surface, and to extend to the main valve side so that the tip of the rectifying member and the bulge of the high temperature chamber function together. In this way, the tip of the rectifying member attached to the support member for supporting the valve stem of the secondary valve is made to have the bulging portions of the high-temperature chamber cooperate with each other as a concave curved surface corresponding to the convex curved surface of the bulging portion formed in the hot exhaust passage. The shape of the exhaust passage is smoother, and the combustion gas from the cylinder can be guided more smoothly into the hot chamber and the hot exhaust passage.

Moreover, in order to solve the said subject, the means employ | adopted by this invention is a main valve which performs intake and / or exhaust, and switching of opening and closing of the several intake and / or exhaust passage which branched and extended through a main valve from a cylinder. A secondary valve to perform, a hydraulic cylinder for performing a valve opening operation of the main valve, a plurality of hydraulic cylinders for performing a switching operation of the secondary valve, a main valve air piston for performing a recovery operation of the main valve, and a recovery of the secondary valve In the structure of an exhaust gas separation device of an internal combustion engine having a secondary valve air piston for causing an operation and an air chamber for driving the primary valve air piston and the secondary valve air piston, the hydraulic cylinder block in which a plurality of hydraulic cylinders are formed is provided. It is a hydraulic zero position control device that controls the zero regulating position of the secondary valve by regulating the lower limit position of the valve air piston. There being one.

The main valve is opened by the hydraulic cylinder and closed by the main valve air piston. The secondary valve is valve-opened by a plurality of hydraulic cylinders, and the valve is closed by the secondary valve air piston. The hydraulic zero position control device regulates the lower limit position, that is, zero position, when the secondary valve is closed by the operation of the secondary valve air piston, that is, when the return operation is performed. As a result, a gap is secured between the lower end surface of the sub valve and the upper end surface of the valve seat of the main valve, and the lower end surface of the secondary valve can be prevented from seating (collision) on the upper surface of the main valve valve seat. Damage or deformation of the valve can be prevented.

In the structure of the exhaust gas separation device of the internal combustion engine, it is preferable that the zero point position control device is formed by providing a plurality of hydraulic cylinders to face the secondary valve air piston in the hydraulic cylinder block. In this way, by installing a plurality of solid hydraulic cylinders with respect to the sub-valve air piston of the structure where the zero position control device is solid, the sub-valve air piston which performs the valve closing operation (recovery operation) strongly by the air pressure is surely formed. It can be stopped. Thereby, the secondary valve can be stopped at the zero position (lower limit position), that is, the lower end surface of the secondary valve at a position having a gap between the upper end surface of the valve seat of the main valve.

In the structure of the exhaust gas separation device of the internal combustion engine, it is preferable that the plurality of hydraulic cylinders of the zero point position control device are arranged at equal intervals along the circumferential direction on the same circumference and communicate with the hydraulic passages. . In this way, by arranging a plurality of hydraulic cylinders forming the zero position control device at equal intervals on the same circumference along the circumferential direction, the strong pressing force of the secondary valve air piston can be equally accepted, and Problems such as deformation can also be prevented. In addition, by communicating the hydraulic passages of the plural hydraulic pistons, the plural hydraulic pistons can be operated with uniform hydraulic pressure and simultaneously, and the secondary valve air piston can be stopped well. Thereby, positioning control of the lower limit position (zero position) of the sub valve can be performed with good precision.

In the structure of the exhaust gas separation device of the internal combustion engine, the plurality of hydraulic cylinders for causing the switching operation of the sub valves are arranged at equal intervals in the circumferential direction on the same circumference, and the plurality of hydraulic cylinders of the zero point position control device. Is preferably arranged on the same circumference and alternately with a plurality of hydraulic cylinders for causing the switching operation of the sub valve. In this way, by arranging a plurality of hydraulic cylinders that allow the sub-valve switching operation to be performed at equal intervals along the circumferential direction on the same circumference, the sub-valve air piston can be evenly pushed against the strong air pressure. Problems such as deformation of the valve air piston can also be prevented. Then, the plurality of hydraulic cylinders forming the zero point position control device are arranged on the same circumference and alternately with these hydraulic cylinders and the plurality of hydraulic cylinders for performing the switching operation of the sub-valve, thereby enabling the switching operation of the sub-valve. Similarly to the hydraulic cylinder, the strong pressing force of the secondary valve air piston can be equally accepted, and problems such as deformation of the secondary valve air piston can be prevented. Thereby, the secondary valve air piston can be stopped well, and positioning control of the zero position (lower limit position) of the secondary valve can be performed with good accuracy.

In the structure of the exhaust gas separation device of the internal combustion engine, the valve device includes a hydraulic sensor for detecting the oil pressure supplied to the zero position control device, and a warning when the oil pressure detected by the oil pressure sensor exceeds a predetermined pressure. Or it is preferable to further provide the sub valve damage prevention apparatus which stops an internal combustion engine. This detects the oil pressure supplied to the oil pressure cylinder of the zero position control device by the oil pressure sensor, and when this oil pressure exceeds the predetermined pressure, the lower end surface of the secondary valve is seated (collided) to the upper end surface of the valve seat of the main valve. It judges that there exists and a warning is made and the internal combustion engine is stopped. As a result, damage or deformation of the secondary valve can be prevented more reliably.

Moreover, in the structure of the exhaust-gas separation apparatus of the said internal combustion engine, the sub valve can slide in the axial direction with the inner peripheral surface of the exhaust valve box formed in the cylinder shape, and formed in the inside cylinder shape, and the lower end surface is a valve | bulb. It is preferred to oppose the gap with the top surface of the valve seat of the main valve in the closed position. By doing in this way, a subordinate valve can perform a switching operation smoothly, with a straight lower end sliding the inner peripheral surface of an exhaust valve box. In addition, the secondary valve is prevented from being seated (collided) to the upper surface of the valve seat of the main valve by the gap with the upper surface of the valve seat of the main valve, thereby preventing the secondary valve from being broken or deformed. More reliably.

Moreover, in order to solve the said subject, in the means employ | adopted by this invention, two or more hydraulic cylinders with a bottom are formed in one side surface of a hydraulic cylinder block, and each hydraulic cylinder is connected by the hydraulic passage formed in the hydraulic cylinder block. In the structure of the exhaust gas separator of an internal combustion engine provided with an exhaust valve box, the hydraulic cylinder block is composed of an outer hydraulic cylinder block and an inner hydraulic cylinder block securely fitted in the outer hydraulic cylinder block, and the inner hydraulic cylinder block. A first hydraulic passage in which a plurality of hydraulic cylinders and one end thereof is opened in each hydraulic cylinder and the other end is opened in the outer circumferential surface of the inner hydraulic cylinder, and each first hydraulic pressure is formed between the outer hydraulic cylinder block and the inner hydraulic cylinder block. A second hydraulic passage is formed in communication with the passage, one end of which is connected to the outer hydraulic cylinder block. The third hydraulic passage is formed in the pressure passage while the other end is opened on the outer circumferential surface of the outer hydraulic cylinder block.

According to the present invention, the hydraulic cylinder block is formed of an outer hydraulic cylinder block and an inner hydraulic cylinder block fitted in the outer hydraulic cylinder block, and the plurality of hydraulic cylinders and one end thereof are opened in each hydraulic cylinder in the inner hydraulic cylinder block. In addition, since the other end forms the first hydraulic passage opening at the outer circumferential surface of the inner hydraulic cylinder block, the first hydraulic passage can be shortened, and the machining (boring) of the first hydraulic passage is facilitated. The removal processing of the warpage (curing) and the cutting powder (cutting powder) generated at the time of drilling are also easy.

Moreover, since the 2nd hydraulic passage which communicates with each 1st hydraulic passage between the outer hydraulic cylinder block and the inner hydraulic cylinder block was formed, the process of a 2nd hydraulic passage becomes easy. In addition, since the third hydraulic passage is formed so that one end of the outer hydraulic cylinder block is in open communication with the second hydraulic passage, and the other end is opened to the outer circumferential surface of the outer hydraulic cylinder block, machining of the third hydraulic passage (boring) is performed. In addition to facilitating, the process of removing warping (curing) and cutting powder generated at the time of drilling is also easy.

That is, by dividing the hydraulic cylinder block into the outer hydraulic cylinder block and the inner hydraulic cylinder block, the machining of the hydraulic passage (bore processing) becomes very easy, and the bending (curing) generated during the machining (boring) is performed. ) And the workability of the removal processing work of cutting powder (cutting powder) can be aimed at.

In the structure of the exhaust gas separation device of the internal combustion engine, the outer hydraulic cylinder block has a bottomed cylindrical shape, the inner hydraulic cylinder block has a circumferential shape, and the plurality of hydraulic cylinders have a circumferential direction to the inner hydraulic cylinder block. It is preferably formed at intervals, each first hydraulic passage is formed radially from each hydraulic cylinder, the second hydraulic passage is preferably formed in an annular shape. In this way, the inner hydraulic cylinder block having a cylindrical shape is inserted in the outer hydraulic cylinder block having a bottomed cylindrical shape, and a plurality of hydraulic cylinders are formed in the inner hydraulic cylinder block at intervals along the circumferential direction, and each first By forming the hydraulic passage radially from each hydraulic cylinder and forming the second hydraulic passage in an annular shape, processing of the outer hydraulic cylinder block and the inner hydraulic cylinder block becomes very easy. In addition, by forming the first hydraulic passage formed in the inner hydraulic cylinder block radially from the hydraulic cylinder toward the outer circumferential surface of the inner hydraulic cylinder block, the hydraulic passage can be shortened and the drilling can be facilitated. Moreover, the curvature (curing) and the removal process of the cutting powder which generate | occur | produced at the time of drilling are also easy. In addition, by forming the second hydraulic passage in an annular shape, communication between each of the first hydraulic passages formed in a radial shape becomes easy and the processing thereof becomes easy.

In the structure of the exhaust gas separation device of the internal combustion engine, the second hydraulic passage is concave annularly concave in the bottom side outer peripheral surface of the inner hydraulic cylinder block forming a circumferential shape between the inner hydraulic surface of the outer hydraulic cylinder block. It is desirable to form an annular hydraulic passage therein. In this way, the bottom outer peripheral surface of the inner hydraulic cylinder block forming the circumferential shape is concave annularly concave to form an annular hydraulic passage between the inner peripheral surface of the outer hydraulic cylinder block, and the annular hydraulic passage is removed. By setting it as 2 hydraulic passages, the machining of a 2nd hydraulic passage becomes easy.

In the structure of the exhaust gas separation device of the internal combustion engine, it is preferable that one end of the first hydraulic passage is open to the inner peripheral surface of the bottom side of the hydraulic cylinder. In this way, the first hydraulic passage can be shortened by opening the first hydraulic passage communicating with each of the hydraulic cylinders and the second hydraulic passage to the inner peripheral surface of the bottom side of the hydraulic cylinder, and the drilling of the first hydraulic passage is facilitated. Moreover, the curvature (curing up) and the removal process of the cutting powder which generate | occur | produced at the time of a pore process also become easy.

As described above, the structure of the exhaust gas separation device of the internal combustion engine of the present invention includes a main valve for exhausting combustion gas in the cylinder, and a high temperature combustion gas formed in the exhaust valve box and discharged from the cylinder through the main valve. A high temperature exhaust passage for discharging gas to the exhaust chamber, a low temperature chamber formed in the exhaust valve box to introduce low-temperature combustion gas discharged from the cylinder through the main valve, and a low temperature exhaust passage formed in the exhaust valve box to discharge the combustion gas in the low temperature chamber to the outside And a sub-valve formed in the exhaust valve box and having a sub-valve for switching the flow of combustion gas to the hot exhaust passage and the low temperature exhaust passage, the low temperature chamber has a predetermined position as a starting point. Slurry that gradually crosses the cross-sectional area to the inlet of the low-temperature exhaust passage in the direction of combustion gas It forms the shape.

Alternatively, the structure of the exhaust gas separation device of the internal combustion engine of the present invention includes a main valve for exhausting combustion gas in a cylinder, and a high temperature combustion gas formed in the exhaust valve box and discharged from the cylinder through the main valve to the outside. A high temperature exhaust passage, a low temperature exhaust passage formed in the exhaust valve box to discharge the low-temperature combustion gas discharged through the main valve from the cylinder to the outside, and a combustion in the high temperature exhaust passage and the low temperature exhaust passage formed in the exhaust valve box. In the structure of the exhaust-gas separation apparatus of the internal combustion engine provided with the sub valve which switches a gas flow, the sub valve has a staff cylinder shape, and the skirt part is formed in the front-end | tip.

Therefore, it is possible to reduce the flow resistance of the combustion gas in the low-temperature chamber and to exhaust the gas without causing a significant swirl formed at the scavenging port, without exhausting the scavenging flow, thereby significantly improving the scavenging efficiency.

Moreover, the structure of the exhaust gas separation apparatus of the internal combustion engine of the present invention is a main valve for exhausting combustion gas in a cylinder, and a high temperature for introducing hot combustion gas formed in the exhaust valve box and discharged from the cylinder through the main valve. A high temperature exhaust passage formed in the exhaust valve box to discharge the combustion gas in the high temperature chamber to the outside; a low temperature exhaust passage formed in the exhaust valve box to discharge the low temperature combustion gas discharged through the main valve from the cylinder to the outside; In a structure of an exhaust gas separation device of an internal combustion engine having a secondary valve formed in an exhaust valve box and switching a flow of combustion gas to a high temperature exhaust passage and a low temperature exhaust passage, the inside wall surface of the high temperature chamber is introduced into the high temperature chamber. A rectifying plate is formed to smoothly guide the high temperature combustion gas into the high temperature exhaust passage.

Therefore, the flow of the combustion gas in the high temperature chamber and the high temperature exhaust passage for discharging the high temperature combustion gas to the outside becomes constant, and as a result, the average flow rate is increased, so that the combustion gas having a flow rate suitable for the minimum cross-sectional area of the high temperature exhaust passage is smooth. Can be discharged. That is, the flow of the combustion gas in the high temperature chamber and the high temperature exhaust passage becomes very smooth, and exhibits an excellent effect of significantly increasing the exhaust efficiency of the internal combustion engine.

Moreover, the structure of the exhaust-gas separation apparatus of the internal combustion engine of this invention is the main valve which performs intake and / or exhaust, and switches the opening and closing of the several intake and / or exhaust passage which branch and extends through a main valve from a cylinder. A secondary valve, a hydraulic cylinder for performing a valve opening operation of the main valve, a plurality of hydraulic cylinders for performing a switching operation of the secondary valve, a main valve air piston for performing a recovery operation of the main valve, and a recovery operation of the secondary valve In the structure of the exhaust gas separation device of an internal combustion engine having a sub-valve air piston for performing the operation and an air chamber for driving the main valve air piston and the sub-valve air piston, the sub-valve is provided in a hydraulic cylinder block in which a plurality of hydraulic cylinders are formed. Forms a hydraulic zero position control device that controls the zero regulating position of the secondary valve by regulating the lower limit position of the air piston. The.

In this way, the sub-valve is returned by forming a hydraulic zero position control device for regulating the zero limit position of the sub-valve by regulating the lower limit position of the sub-valve air piston in the hydraulic cylinder block in which the hydraulic cylinder for switching the sub-valve is formed. The lower limit position, that is, the zero point position, can be regulated, and the gap between the lower end surface of the sub valve and the upper end surface of the valve seat of the main valve can be precisely adjusted and ensured. Seating (collision) on the upper surface of the valve seat of the main valve can be prevented. This makes it possible to reliably prevent breakage and deformation of the secondary valve, and enables the secondary valve to be inexpensively formed by precision casting, thereby exhibiting an excellent effect of significantly reducing the cost.

Moreover, in the structure of the exhaust gas separation device of the internal combustion engine of the present invention, a plurality of hydraulic cylinders having a bottom are formed on one side end surface of the hydraulic cylinder block, and each hydraulic cylinder is an internal combustion in communication with the hydraulic passage formed in the hydraulic cylinder block. In the structure of the exhaust gas separation device of the engine, the hydraulic cylinder block is composed of an outer hydraulic cylinder block and an inner hydraulic cylinder block securely fitted in the outer hydraulic cylinder block, and the inner hydraulic cylinder block includes a plurality of hydraulic cylinders. A second hydraulic passage having one end opened to each hydraulic cylinder and the other end opened to the outer circumferential surface of the inner hydraulic cylinder and communicating with each first hydraulic passage between the outer hydraulic cylinder block and the inner hydraulic cylinder block; The hydraulic passage is formed, and one end is opened to the second hydraulic passage in the outer hydraulic cylinder block and the other end is A third hydraulic passage opening on the outer circumferential surface of the outer hydraulic cylinder block is formed.

Therefore, by dividing the hydraulic cylinder block in which the plurality of hydraulic cylinders are formed into the outer hydraulic cylinder block and the inner hydraulic cylinder block, the machining (boring) of the hydraulic passage that communicates each hydraulic cylinder becomes easy, and the machine It shows the excellent effect that the workability of the removal processing of the curvature (curing) and cutting powder (cutting powder) which generate | occur | produce at the time of processing can be aimed at. As a result, the finishing inspection of the hydraulic cylinder block can be facilitated, and the cost can be reduced, and as described above, the bending powder (curing) and the removal of the cutting powder (cutting powder) of the hydraulic passage can be facilitated. It is possible to prevent the sliding problem of the hydraulic cylinder resulting from the above, and also shows an excellent effect of improving the reliability.

As a result, the fuel consumption of the internal combustion engine can be improved, the reliability can be improved, and the work efficiency can be improved.

BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing of the principal part which shows the diesel engine which concerns on the structure of the waste gas separation apparatus of the internal combustion engine of this invention.
FIG. 2 is a cross-sectional view taken along arrow line II-II of the diesel engine of FIG. 1.
FIG. 3 is an explanatory diagram schematically showing the flow of combustion gas in the low temperature chamber and the low temperature exhaust passage shown in FIG. 2. FIG.
4 is a sectional view of an essential part of the diesel engine of FIG. 1 as seen from another angle.
5 is a cross-sectional view along the arrow line VV of the diesel engine of FIG.
FIG. 6: is explanatory drawing which showed typically the flow of the combustion gas in the high temperature chamber and high temperature exhaust channel shown in FIG.
7 is a cross-sectional view of an essential part showing a diesel engine different from that in FIG. 1.
FIG. 8 is a cross-sectional view taken along the arrow line VIII-VIII of the diesel engine of FIG. 7.
FIG. 9 is a cross-sectional view at an operating position different from that of FIG. 8 of the diesel engine shown in FIG. 7. FIG.
10 is a cross-sectional view along the arrow line XX of the diesel engine of FIG. 7.
FIG. 11 is a partially enlarged view of a hydraulic cylinder of the zero point position control device shown in FIG. 8.
It is sectional drawing of the principal part which shows the conventional diesel engine.
FIG. 13: is explanatory drawing which showed typically the flow of combustion gas in the low temperature chamber and the low temperature exhaust passage of the diesel engine of FIG.
It is explanatory drawing which shows typically the flow of the combustion gas in the high temperature chamber and the high temperature exhaust passage of the diesel engine of FIG.
FIG. 15 is a cross-sectional view taken along arrow line XV-XV of the diesel engine of FIG. 12.

EMBODIMENT OF THE INVENTION The form for implementing the invention of the structure of the exhaust gas separation apparatus of the internal combustion engine of this invention is demonstrated in detail with reference to FIGS.

BRIEF DESCRIPTION OF THE DRAWINGS It is sectional drawing of the principal part centering on the exhaust valve box 11 of the diesel engine which applied the structure of the exhaust gas separation apparatus of the internal combustion engine which concerns on this invention. As shown in FIG. 1, the exhaust valve box 11 is attached to the valve seat 2 of the cylinder block 1, and the main valve 21 and the high temperature chamber 12 formed in the exhaust valve box 11 are shown. ), A high temperature exhaust passage 13 communicating with the high temperature chamber 12, a low temperature chamber 14, and a low temperature exhaust passage 15 communicating with the low temperature chamber 14. Moreover, the sub valve 24 which switches the flow of a combustion gas is provided in the high temperature chamber 12, the high temperature exhaust passage 13 side, the low temperature chamber 14, and the low temperature exhaust passage 15 side.

Moreover, the hydraulic cylinder which is not shown in which the valve opening operation | movement of the main valve 21 is performed, and the several hydraulic cylinders which are provided in the hydraulic cylinder block 30 and which perform the switching operation of the sub valve 24 are performed, for example. 31, an air piston (not shown) fixed to the upper portion of the valve stem 22 of the main valve 21 to perform the recovery operation of the main valve 21, and the valve stem 26 of the sub valve 24. The air piston 29 is fixed to the upper portion of the sub-valve 24 to perform the recovery operation, the air piston of the main valve 21 and the air piston 29 of the sub-valve 24 to receive the air pressure It becomes the structure provided with the casing 35 which forms the air spring chamber 36 for.

This exhaust valve box 11 shows a case where the exhaust valve box 11 is applied to a two-cycle uniflow diesel engine as an example. In this two-cycle uniflow diesel engine, an exhaust mechanism is provided on the side wall of the cylinder liner, and the main valve ( 21) exhausts and purges.

The valve opening operation of the main valve 21 is performed by the hydraulic cylinder (not shown) which is operated by the high pressure hydraulic pressure by pushing the valve stem 22 downward. Moreover, the valve closing operation | movement (recovery operation | movement) is performed by pulling up the valve stem 22 to the upper direction which shows the air piston not shown in figure which was attached to the valve stem 22. FIG. That is, the air pressure in the air spring chamber 36 formed below the air piston is an operating source of the valve closing operation of the main valve 21.

The switching operation of the sub valve 24 is performed by the plurality of hydraulic cylinders 31 formed on the hydraulic cylinder block 30 being operated by high pressure hydraulic pressure, and pressing the air piston 29 upwardly. Moreover, the restoration operation | movement is performed by sending out the oil_pressure | hydraulic of the hydraulic cylinder 31, and pushing the valve stem 26 downwardly by the air piston 29 shown. That is, the air pressure in the air spring chamber 36 formed above the air piston 29 serves as an operation source of the recovery operation of the sub valve 24.

As shown in FIG. 2, the low temperature chamber 14 connects the center line L that connects the center of the outlet 15a of the low temperature exhaust passage 15 and the center O in the low temperature chamber 14 of the center line of the exhaust port 11a. ) Is formed in an asymmetrical swirl shape. The starting point SP of this vortex is set at the predetermined position of the low temperature chamber 14.

The starting point SP is located slightly on the low temperature chamber 14 side than the speaker 15b on one side of the low temperature chamber 14 and the low temperature exhaust passage 15 inlet, and is located within the low temperature chamber 14 of the center line of the exhaust port 11a. The center O is formed at a position deviated by a predetermined angle θ1 from the center line L of the low-temperature exhaust passage 15 slightly in the vortex direction, that is, from the center line L toward the left side of the illustration.

In this internal combustion engine, the low temperature combustion gas introduced into the low temperature chamber 14 from the cylinder through the exhaust port 11a of the exhaust valve box 11 during the period from the valve opening middle stage of the main valve to the valve closing is the low temperature exhaust passage 15. With respect to the center line L connecting the center of the outlet 15a of the center and the center of the low temperature chamber 14, as seen from the upper side shown in FIG. 2, the low temperature chamber (with a strong swirl in the counterclockwise direction) 14) flows into.

That is, the low temperature chamber 14 has a predetermined cross-sectional area from the starting point SP to the inlet section of the low temperature exhaust passage 15 from the starting point SP, more specifically, the predetermined position as the starting point SP. The cross-sectional area to 15c has a vortex shape which gradually widens toward the low temperature exhaust passage 15 in the direction of rotation of the combustion gas. In other words, the low temperature chamber 14 is formed in a vortex shape whose diameter gradually narrows in the clockwise rotation direction as seen from above in FIG. 2.

The low temperature chamber 14 is formed of curved surfaces of different radii of curvature R2, R3, and R4 from the starting point SP to the extending portion 15c with the low temperature exhaust passage 15, and these radii of curvature R4> It becomes R3> R2, and it grows to the smooth part 15c of the inlet part of the low temperature chamber 14 and the low temperature exhaust passage 15 inlet from the starting point SP sequentially and smoothly.

Moreover, the extending parts 15b and 15c of the inlet of the low temperature chamber 14 and the low temperature exhaust passage 15 are each smoothly spoken by the curved surface of curvature radius R1, R5. For example, the angle θ1 is about 45 ° to 90 °, and the curvature radii R2 to R4 forming the vortex are about 0.5 to 2.0 times the inner diameter D01 of the outlet 15a of the low temperature exhaust passage 15. do.

The secondary valve 24 has a cylindrical shape, the outer diameter of which is slightly smaller than the exhaust port 11a of the exhaust valve box 11, and the inner diameter (sub valve inner diameter D1) of the exhaust port of the valve seat 2 is reduced. It becomes almost the same diameter as (2a). In addition, the exhaust port 11a of the exhaust valve box 11 has a larger diameter than the exhaust port 2a of the valve seat 2. The secondary valve 24 has its inner peripheral surface protruded by a plurality of plate-shaped wheel spokes (spokes) 24a on the outer peripheral surface of the valve stem 26. The combustion gas discharged from the cylinder 3 via the main valve 21 is discharged into the high temperature chamber 12 through these width | varieties 24a.

The sub valve 24 is formed with a skirt portion 24b that is reduced in diameter from the rear end (upper end) to the front end (lower end). The skirt portion 24b has a truncated cone cylindrical shape (conical trapezoidal state) in which the outer diameter (skirt portion outer diameter) D2 of the rear end has a larger diameter than the outer diameter D4 of the front end, and the sub-valve forming a cylindrical shape ( 24) the angle of the outer peripheral surface with respect to the radial direction of . And the outer diameter D2 of a rear end becomes larger diameter than the outer diameter of the sub valve 24, and the outer diameter D4 of a front end becomes smaller diameter than the inner diameter D1 of the sub valve 24. As shown in FIG.

The outer circumferential surface of the rear end of the skirt portion 24b forms a surface parallel to the outer circumferential surface of the sub valve 24 forming the barrel shape, and the inner circumferential surface of the opening of the tip portion is parallel to the inner circumferential surface of the secondary valve 24 forming the barrel shape. It is one side. Therefore, the outer circumferential surface of the tip of the skirt portion 24b is the inner circumferential surface of the opening portion and the angle θ2. In this diesel engine, the outer diameter (D4) of the tip is almost the same diameter as the inner diameter (inner portion diameter of the skirt) D3 of the tip.

The outer diameter of the front end of the skirt portion 24b is slightly smaller than the exhaust port 11a of the exhaust valve box 11, and the outer circumferential surface of the rear end of the exhaust valve box 11 is represented by a two-dot chain line. It is possible to make sliding contact with the inner circumferential surface of the exhaust port 11a. And the front-end | tip of the sub valve 24 which forms a cylindrical shape is speaking to the substantially center part of the inner peripheral surface of the skirt part 24b.

For example, when the diameter of the valve face 21a of the main valve 21 is set to Dv, the ratio D1 / Dv of the inner diameters D1 and Dv of the subordinate valve 24 is about 0.9 to 1.2 and the skirt portion. (24b) The ratio (D2 / Dv) of the outer diameters D2 and Dv of the rear end is about 1.0 to 1.3, and the ratio (D3 / Dv) of the inner diameters (D3 and Dv) of the tip of the skirt portion 24b is about 0.7 to 1.0. do.

As shown in FIG. 4 (or as shown by the dashed-dotted line in FIG. 1), the sub valve 24 has the air piston 29 in the initial stage (the exhaust initial stage) when the main valve 21 starts to open the valve. ), The position is switched, the skirt portion 24b is inserted into the exhaust port 11a of the exhaust valve box 11, and the outer peripheral surface of the rear end is brought into sliding contact with the inner peripheral surface of the exhaust port 11a, so that the valve seat 2 Is communicated with the cylinder (3) via the exhaust port (2a).

And the sub valve 24 communicates the cylinder 3 and the high temperature chamber 12 between the plate | board wheel 24a, and closes the low temperature chamber 14 by the cylindrical part. Thereby, the high temperature and high pressure combustion gas in the cylinder 3 is discharged | emitted to the high temperature chamber 12, and is discharged | emitted from the high temperature chamber 12 to the high temperature exhaust passage 13. The secondary valve 24 is maintained at the position shown in FIG. 4 at the initial stage (the exhaust stage initial stage) when the main valve 21 starts to open the valve, and discharges the combustion gas of the high temperature and high pressure in the cylinder 3 to the high temperature chamber 12. And discharged from the high temperature chamber 12 to the high temperature exhaust passage 13.

The secondary valve 24 is pushed up to the position indicated by the solid line of FIG. 1 by the hydraulic cylinder 3 during the mid to late periods (valve closing) of the valve opening of the main valve 21. Is switched to the low temperature chamber 14 side. As a result, the high temperature chamber 12 is closed. The low temperature chamber 14 communicates with the cylinder 3, and the residual combustion gas (scavenged gas) in the cylinder 3 is discharged into the low temperature chamber 14 and the low temperature exhaust passage 15. This combustion gas is guide | induced smoothly in the low temperature chamber 14 along the inclined outer peripheral surface of the skirt part 24b formed in the front-end | tip of the sub valve 24. As shown in FIG. As a result, the combustion gas discharged from the cylinder 3 is satisfactorily introduced into the low temperature chamber 14.

As described above, the low temperature chamber 14 forms a vortex shape in which the cross-sectional area gradually widens in the turning direction of the combustion gas from the starting point SP to the opening portion 15c of the inlet of the low temperature exhaust passage 15, and furthermore, a smooth curved surface. Since the flow resistance of the combustion gas in the low temperature chamber 14 is greatly reduced, the combustion gas smoothly flows into the low temperature exhaust passage 15. Thereby, the combustion gas discharged from the cylinder 3 to the low temperature chamber 14 can be discharged to the low temperature exhaust passage 15 without inhibiting the strong swirl formed at the scavenging port of the cylinder 3. As a result, the combustion gas of the flow volume suited to the cross-sectional area of the low-temperature exhaust passage 15 can be smoothly discharged, and the scavenging efficiency is remarkably improved.

FIG. 3 shows an example of the flow of combustion gas in the low temperature chamber 14 and the low temperature exhaust passage 15 shown in FIG. 2. The combustion gas introduced into the low temperature chamber 14 from the cylinder 3 shown in FIG. 1 via the outlet 11a of the exhaust valve box 11 is a streamline A to H indicated by an arrow along the vortex inner wall surface 14a. And flows out into the low temperature exhaust passage 15.

The length of this streamline A-H has shown the flow velocity of the combustion gas in the position. As is apparent from FIG. 3, the flow rate of the combustion gas is constant over the entire circumference of the outlet 11a of the exhaust valve box 11 as compared with the structure of the exhaust gas separation device of the conventional internal combustion engine shown in FIG. 4, As a result, the average flow rate is increased, which greatly increases the discharge flow rate of the combustion gas.

On the other hand, the high temperature chamber 12 mentioned above has the center of the exit 13a of the high temperature exhaust passage 13, the exhaust port 11a, and the center O of the high temperature chamber 12, as shown in FIG. It is formed in a substantially symmetrical shape with respect to the connecting center line L2, and the high temperature chamber 12 has two rectifying plates (2) for smoothly flowing the combustion gas discharged from the cylinder 3 through the main valve 21. 17, 18) are formed.

As shown in FIG. 4, the rectifying plates 17 and 18 are arranged along the axial direction (up and down direction) of the high temperature chamber 12, that is, along the discharge direction of the combustion gas discharged from the cylinder 3, and at a high temperature. It is formed toward the center of the exit 13a side of the high temperature exhaust passage 13 on the center line L2 of the exhaust passage 13.

The rectifying plate 17 becomes a first rectifying plate, and as shown in FIG. 5, the high temperature exhaust gas is formed on the inner wall surface 12a of the high temperature chamber 12 and around the exhaust port 11a of the exhaust valve box 11. It is arrange | positioned on the opposite side to the outlet 13a of the channel | path 13, and is formed over the almost full height of the high temperature chamber 12, as shown in FIG.

The rectifying plate 18 becomes a second rectifying plate, and as shown in FIG. 5, the high temperature exhaust gas is formed on the inner wall surface 12a of the high temperature chamber 12 and around the exhaust port 11a of the exhaust valve box 11. It is formed toward the center of the outlet 13a side of the passage 13. Moreover, as shown in FIG. 4, it is dripped from the upper wall surface of the high temperature chamber 12 to the vicinity of the center height of the high temperature chamber 12, and is formed.

As shown in FIG. 5, the side opposite to the outlet 13a side of the high temperature exhaust passage 13 of the inner wall surface 12a of the high temperature chamber 12 has an inner diameter of the cylinder 3 as compared with the outlet 13a side, More specifically, the space | interval between the exhaust port 11a of the exhaust valve box 11 is narrow, and therefore, the height of the rectifying plate 17 (length in the centerline L2 direction of the high temperature exhaust passage 13) is high ( Long)

For this reason, the rectifying plate 17 is formed lower than the rectifying plate 18 (shorter the length in the direction of the center line L2 of the high temperature exhaust passage 13) and is approximately half of the rectifying plate 18. The rectifying plate 18 is formed higher than the rectifying plate 17 (longer in the direction of the outlet 13a along the center line L2) toward the outlet 13a side of the high temperature exhaust passage 13.

The rectifying plate 17 is formed so as to form, for example, an arc-shaped concave curved surface having a radius of curvature R11 toward the inner wall surface 12a of the high temperature chamber 12 from the front end 17a. Similarly, the rectifying plate 18 is formed so as to form an arcuate concave curved surface having, for example, a radius of curvature R21 toward the inner wall surface 12a of the high temperature chamber 12 from both ends. .

Thus, both side surfaces 17a and 18a of the rectifying plates 17 and 18 are formed so as to form an arc-shaped concave curved surface from the tip toward the inner wall surface 12a of the high temperature chamber 12 from the cylinder 3. The flow of the combustion gas discharged | emitted to the high temperature chamber 12 can be made smooth. In addition, the inner diameter of the high temperature chamber 12 is larger than the inner diameter of the high temperature exhaust passage 13, and the extension portions 13c and 13d of the inlet of the high temperature chamber 12 and the high temperature exhaust passage 13 are smooth curved surfaces. have.

For example, the diameter of the valve face (valve contact surface) 21a of the main valve 21 shown in FIG. 4 as D02 and the internal diameter of the outlet 13a of the high temperature exhaust passage 13 are Dv and the sub valve 24. When the inner diameter of the passage is D1, the radius of curvature R11 of the side surface 17a of the rectifying plate 17 is about 0.2 to 0.5 times the passage outlet diameter D02 and the side surface 18a of the rectifying plate 18. The radius of curvature R21 is about 0.3 to 1.0 times the passage exit diameter D02. The ratio D1 / Dv of the diameter Dv of the passage inner diameter D1 of the secondary valve 24 to the valve face (valve contact surface) 21a of the main valve 21 is about 0.9 to 1.2. do.

As shown in FIG. 4, the inner wall surface 12a of the lower side of the figure near the inlet 12c of the high temperature chamber 12 is made to expand and expand convex-shaped curved surface toward the upper part of the city, and the bulging part inside the high temperature chamber 12 ( 12b). The bulging portion 12b is preferably formed in an annular shape so as to surround the inlet 12c of the high temperature chamber 12. However, the bulging part 12b does not necessarily need to be ring-shaped so that the whole inlet 12c may be enclosed, and you may form only in the inner wall surface 12a of the illustration side by the side of the high temperature exhaust passage 13 side.

Moreover, the rectifying member 27 which becomes substantially reverse conical is formed in the lower end part of the hydraulic cylinder block 30 which penetrates and supports the valve stem 26 of the sub valve 24. As shown in FIG. The distal end portion 27a of the rectifying member 27 has a concave surface whose outer surface opposing the bulging portion 12b of the high temperature chamber 12 forms an arc-shaped concave curved surface corresponding to the convex curved surface of the bulging portion 12b. A curved portion 27b extends toward the main valve 21 while reducing the diameter toward the sub valve 24.

A bulging portion 12b made of a convex curved surface is formed on the inner wall surface 12a near the inlet 12c near the inlet 12c of the high temperature chamber 12, and on the tip portion 27a of the rectifying member 27 facing the same. By forming the concave curved portion 27b corresponding to the convex curved surface of the bulging portion 12b, the bulging portion 12b of the high temperature chamber 12 and the tip portion 27a of the rectifying member 27 function together with each other. By these interactions, the combustion gas can be smoothly discharged from the cylinder 3 into the high temperature chamber 12 and into the high temperature exhaust passage 13.

FIG. 6 shows an example of the flow of combustion gas in the high temperature chamber 12 and the high temperature exhaust passage 13 shown in FIG. 5. Combustion gas discharged from the cylinder 3 through the outlet 11a of the exhaust valve box 11 into the high temperature chamber 12 is substantially left and right along both sides 17a forming a concave curved surface of the rectifying plate 17. The equally divided flow prevents mutual interference and flows along the inner wall surface 12a of the high temperature chamber 12 in the direction of the high temperature exhaust passage 13.

The combustion gas discharged from between the rectifying plate 17 and the rectifying plate 18 flows toward the high temperature exhaust passage 13 along the inner wall surface 12a of the high temperature chamber 12. Moreover, the combustion gas discharged from the vicinity of the rectifying plate 18 of the high temperature chamber 12 flows toward the high temperature exhaust passage 13 along the side surfaces 18a that form the concave curved surface of the rectifying plate 18. . In addition, since the length in the direction of the center line L2 of both side surfaces 18a is long (high), it is substantially equally divided over a long distance on both sides of the center line L2, thereby preventing interference with each other and flowing smoothly.

In FIG. 6, the length of the streamline indicates the flow velocity of the combustion gas at the position. As is also apparent from FIG. 6, the passage resistance of the high temperature chamber 12 and the high temperature exhaust passage 13 can be greatly improved, and the residence due to the circular reflux of the combustion gas in the high temperature chamber 12 or the high temperature can be improved. Retention of combustion gas in the inlet vicinity of the exhaust passage 13 is eliminated, and it is possible to exhaust the combustion gas at a flow rate suitable for the minimum cross-sectional area of the high temperature exhaust passage 13, so that the exhaust efficiency is significantly improved.

The cylinder 3 is formed by symmetrical with respect to the outlet 13a of the high temperature exhaust passage 13, that is, with respect to the center line L2 of the high temperature exhaust passage 13. ), The combustion gas introduced from the gas can be discharged to the high temperature exhaust passage 13 by dividing it almost evenly on both sides with respect to the center line L2, and together with the above-mentioned rectifying plates 17 and 18 in the high temperature chamber 12. It is possible to reduce the retention of combustion gas at

Next, another form for carrying out the invention of the exhaust gas separation device structure of the internal combustion engine of the present invention will be described in detail with reference to FIGS. 7 to 11. 7-11, the same code | symbol is attached | subjected to the member same as the member shown in FIGS. 1-6, and description is simplified briefly.

The internal combustion engine shown in FIG. 7 is a two-cycle uniflow type diesel engine as an example. The diesel engine is mounted on the valve seat 2 of the cylinder block 1 to exhaust the main valve 21 and the cylinder. Two (plural) of the hot exhaust gas passage 13 for the hot gas and the cold exhaust passage 15 for the cold gas, which branch and extend from the downstream side of the main valve 21 through the main valve 21 from (3). And an auxiliary valve 25 arranged in the exhaust valve box 11 to switch the flow of the combustion gas to the hot exhaust passage 13 and the cold exhaust passage 15. Moreover, with respect to the hydraulic cylinder 43 which operates the sub valve 25, the hydraulic passage for driving these is arrange | positioned. In this diesel engine, only the exhaust from the main valve 21 is performed.

As shown in FIG. 7, the hydraulic cylinder block 40 for performing the switching operation of the sub valve 25 has a circumferential shape and is formed by the outer hydraulic cylinder block 41 and the inner hydraulic cylinder block 42. have. The outer hydraulic cylinder block 41 has a cylindrical shape with a bottom, and the inner hydraulic cylinder block 42 has a cylindrical shape. The valve stem 22 of the main valve 21 and the valve stem 26 of the sub valve 25 are inserted through the bottom center of the outer hydraulic cylinder block 41 and the center of the inner hydraulic cylinder block 42. The holes 41a and 42a are formed through.

The outer hydraulic cylinder block 41 has the hydraulic passage 61 perforated vertically along the axial direction from the top surface 41d, and the hydraulic passage 62 on the upper side of the side surface (outer peripheral surface) 41b and in the radial direction. ) Is perforated. The hydraulic passage 62 has one end (front end) communicating with the upper portion of the hydraulic passage 61, and the other end is opened to the outer circumferential surface 41b to serve as a hydraulic supply and discharge port. In addition, the open end (upper end) of the hydraulic passage 61 is closed.

The hydraulic passage 63 is perforated in the radial direction near the bottom of the outer circumferential surface 41b, and in the middle thereof, the lower end of the hydraulic passage 61 in the vertical direction is opened and communicated with one end (the front end) of the outer hydraulic passage. The opening is opened in the inner circumferential surface 41c of the cylinder block 41. These hydraulic passages 61, 62, 63 are formed by drilling (machining). The open end of the outer circumferential surface 41b of the hydraulic passage 63 is closed.

These hydraulic passages 61, 62, and 63 form a third hydraulic passage. The hydraulic passages 61, 62, and 63 are short and simple in structure, and can easily remove warpage (curing) or cutting powder (cutting) generated during machining (perforation) and facilitate post-treatment. .

In addition, the above-mentioned vertical hydraulic passage 61 and the upper hydraulic passage 62 are removed, and only the hydraulic passage 63 in the vicinity of the bottom portion is formed, and the outer peripheral surface 41b side of the hydraulic passage 63 is opened to open the hydraulic pressure. The hydraulic passage may be a third hydraulic passage as the supply and the discharge port of. In this way, the hydraulic passage 63, i.e., the third hydraulic passage, can be made very short and the structure can be made very simple, and accordingly, warping (curing) or cutting powder ( Chips can be removed more easily and satisfactorily, and post-treatment is easier.

As shown in FIG. 8 and FIG. 10, the inner hydraulic cylinder block 42 is a sub-valve hydraulic cylinder concentrically on the outer side of the center hole 42a on the upper end face and at equal intervals along the circumferential direction on the same circumference. Plural, for example, three (43) is provided.

These secondary valve hydraulic cylinders 43 have a bottom, and a hydraulic passage 65 (only one is shown in FIG. 8) is formed near the bottom. One end of the hydraulic passage 65 is opened to the inner circumferential surface near the bottom of the sub valve hydraulic cylinder 43, and the other end is opened to the outer circumferential surface 42b of the inner hydraulic cylinder block 42 (see FIG. 7). It is formed radially along the radial direction.

This hydraulic passage 65 is also formed by drilling (machining). This hydraulic passage 65 is very short and has a simple structure, and can easily remove warpage (curing) and cutting powder (cutting powder) generated at the time of drilling, and it is easy to post-process. And this hydraulic passage 65 becomes a 1st hydraulic passage.

An annular recess 45 is formed at the lower end of the outer circumferential surface 42b of the inner hydraulic cylinder block 42 over its entire circumference. The other end of the hydraulic passage 65 is opened to the bottom surface of the annular recess 45. Thereby, the lower part of each sub valve hydraulic cylinder 43 communicates with the recessed part 45.

As shown in FIGS. 8 and 10, the inner hydraulic cylinder block 42 has a plurality of hydraulic cylinders 46 on the same circumference as the sub valve hydraulic cylinder 43 at equal intervals along the circumferential direction, For example, three are formed. These three hydraulic cylinders 46 are alternately arranged between the three sub valve hydraulic cylinders 43, and are formed to be shallower (for example, about 1/3 depth) than the sub valve hydraulic cylinders 43. (See FIG. 8). As shown in FIG. 11, the cylinder cylinder is fixed to the upper end surface of the inner side hydraulic cylinder block 42 by the bolt 48, as shown in FIG.

As shown in FIG. 8, in the outer peripheral surface 42b of the inner side hydraulic cylinder block 42, the annular groove 66 is formed in the position corresponding to the bottom part of the hydraulic cylinder 46 over the perimeter. And the hydraulic passage 67 (only one is shown in FIG. 8) is formed in the vicinity of the bottom part of these hydraulic cylinders 46. As shown in FIG. The hydraulic passage 67 is formed radially in the radial direction, one end of which is opened to the inner circumferential surface near the bottom of the hydraulic cylinder 46, and the other end of which is opened to the bottom surface of the annular groove 66. . As a result, the lower portion of each hydraulic cylinder 46 communicates with the annular groove 66.

This hydraulic passage 67 is also formed by drilling (machining). Similar to the hydraulic passage 65, the hydraulic passage 67 is very short and simple in structure, and can easily remove warpage (curing) and cutting powder (cutting powder) generated at the time of drilling. It is easy.

As shown in FIG. 8, in the outer hydraulic cylinder block 41, a hydraulic passage 68 is formed in the position corresponding to the annular groove 66 of the inner hydraulic cylinder block 42, and the annular groove ( 66).

And the inner side hydraulic cylinder block 42 is liquid-tightly fitted in the outer side hydraulic cylinder block 41 via the sealing member, and it is a hollow body (3) to the exhaust valve box 11 by the bolt 75 as shown in FIG. Iii) fixed. The annular hydraulic passage 69 is formed between the annular recess 45 of the lower end of the inner hydraulic cylinder block 42 and the inner circumferential surface of the outer hydraulic cylinder block 41 facing each other. This annular hydraulic passage 69 becomes a second hydraulic passage. In this way, the hydraulic cylinder block 40 is formed.

As shown in FIG. 8, each front end surface (upper surface shown) of the piston 44 of each sub valve hydraulic cylinder 43 abuts on the lower surface of the sub valve air piston 37. As shown in FIG. By these three sub valve hydraulic cylinders 43, a sub valve switching device 51 for switching the sub valve 25 is formed. The secondary valve switching device 51 is a solid secondary valve air piston by arranging a plurality of secondary valve hydraulic cylinders 43 for causing the switching operation of the secondary valve 25 at equal intervals along the circumferential direction on the same circumference. (37) can be pressed evenly against strong air pressure. Moreover, since it is arrange | positioned at equal intervals along a circumferential direction, problems, such as deformation of the sub valve air piston 37, can also be prevented.

As shown in FIG. 8, each front end surface (upper surface) of the piston 47 of each hydraulic cylinder 46 is in contact with the lower surface of the sub valve air piston 37. As shown in FIG. By these three hydraulic cylinders 46, the zero position control device 52 which regulates the lower limit position (zero position) when the sub-valve 25 recovers and descends is formed. Since the zero position control device 52 is provided with a plurality of solid hydraulic cylinders 46 provided with respect to the sub-valve air piston 37 having a solid structure, the valve closing operation is strongly performed by the air pressure (recovery operation). It is possible to reliably stop the sub-valve air piston 37.

Then, the plurality of hydraulic cylinders 46 of the zero position control device 52 are arranged on the same circumference as the plurality of secondary valve hydraulic cylinders 43 for causing the switching operation of the secondary valve 25 to be performed on these secondary valve hydraulic cylinders. By alternately arranging with 43, similarly to the plurality of sub-valve hydraulic cylinders 43 for performing the switching operation of the sub-valve 25, the strong pressing force of the sub-valve air piston 37 can be equally accepted. In addition, problems such as deformation of the secondary valve air piston 37 can be prevented.

Thereby, the sub valve air piston 37 can be stopped well, and positioning control of the zero position (lower limit position) of the sub valve 25 can be performed with good precision. Therefore, the secondary valve 25 is positioned at the zero position (lower limit position), that is, the lower end surface 25e of the lower end portion 25d of the secondary valve 25 is between the upper end surface 2a of the valve seat 2 of the main valve 21. It is possible to reliably stop at a position having a gap (clearance)?

The lower valve portion 25d has a cylindrical shape, and the secondary valve 25 can slide in the axial direction with the inner circumferential surface 11c of the lower end portion 11b of the exhaust valve box 11 formed in a straight cylinder shape. Therefore, the sub valve 25 performs the switching operation smoothly while the straight lower end portion 25d slides the inner circumferential surface 11c of the exhaust valve box 11. Thereby, the sub valve 25 is prevented from seating (colliding) the lower end surface 25e of the lower end part 25d with the upper end surface 2a of the valve seat 2 of the main valve 21, It is prevented that the 25 is broken or deformed.

The opening opening in the outer circumferential surface 41b of the hydraulic passage 62 of the outer hydraulic cylinder block 41 shown in FIG. 7 serves as a supply and discharge port for hydraulic pressure, is connected to a hydraulic source (not shown), Supplied to drive the sub-valve switching device 51. In addition, in the hydraulic passage 68 of the outer hydraulic cylinder block 41 shown in FIG. 8, an opening opening in the outer circumferential surface 41b serves as a hydraulic supply and discharge port, and the hydraulic passage not shown through the hydraulic passage 70 is shown. Connected to the circle.

This zero position control device 52 detects the hydraulic pressure P of the hydraulic cylinder 46 by the hydraulic sensor 55 disposed in the hydraulic passage 68, and damages the secondary valve connected to the hydraulic sensor 55. When the prevention device 76 exceeds the predetermined pressure when the oil pressure detected by the hydraulic sensor exceeds the predetermined pressure, the lower end surface 25e of the secondary valve 25 is the upper end surface 2a of the valve seat 2 of the main valve 21. It is judged that the vehicle is seated (crashed), and the warning lamp is turned on (the occurrence of a warning) or the internal combustion engine is stopped according to the level of the detected value at that time. Thereby, damage or deformation of the sub valve 25 can be prevented more reliably.

As shown in FIG. 7 and FIG. 8, when the main valve 21 is closed, the sub valve hydraulic cylinder 43 of the sub valve switching device 51 is retracted, and the sub valve hydraulic cylinder 43 is closed. And the subordinate valve 25 are maintained at the zero position (lower limit position) by the zero position control device 52. And in the exhaust initial stage in which the main valve 21 was slightly valve-opened, the sub valve 25 is still maintained in the zero position (lower limit position), and high-temperature exhaust gas is discharged from between the ribs 25c. As indicated by the arrow in the drawing, the exhaust gas is discharged to the high temperature exhaust passage 13.

As shown in FIG. 9, when the valve opening of the main valve 21 advances and passes the initial stage of exhaust, the sub valve hydraulic cylinder 43 of the sub valve switching device 51 is extended to show the sub valve air piston 37. It pushes up one direction and switches the sub valve 25 to the low temperature exhaust passage 15 side, and discharges residual gas to the said low temperature exhaust passage 15 side as shown by an arrow.

When the exhaust is completed, the secondary valve hydraulic cylinder 43 of the secondary valve switching device 51 is retracted, and the secondary valve 25 is pushed downward by the secondary valve air piston 37. As shown in FIG. 7 and FIG. 8, the secondary valve air piston 37 abuts against the piston 47 of the hydraulic cylinder 46 of the zero point position control device 52, and the lowering thereof is regulated. 25) is firmly maintained at the zero position (lower limit position).

In addition, although the exhaust valve apparatus 10 mentioned above showed the case where it applied to the 2 cycle uniflow diesel engine which has a sub valve as an example, the structure of the exhaust gas separation apparatus of the internal combustion engine of this invention is The present invention is also applicable to other internal combustion engines having secondary valves, for example four-cycle diesel engines. In this four-cycle diesel engine, for example, the main valve is used for both the intake and exhaust, and the sub valve is used for switching the opening and closing of the intake passage and the exhaust passage which branch and extend from the cylinder through the main valve.

The structure of the exhaust gas separation device of the internal combustion engine of the present invention is not limited to the structure of the exhaust gas separation device of the diesel engine according to the embodiment described above, and the structure and the general hydraulic pressure of the exhaust gas separation device of the various internal combustion engines. This can be done for the equipment.

1: cylinder block
2: valve seat
2a: exhaust port
3: Cylinder
5: exhaust valve box
5a: exhaust vent
6: high temperature room
6a: inner wall
7: high temperature exhaust passage
7a: exit
8: low temperature room
8a: inner wall
9: low temperature exhaust passage
9a: exit
10: exhaust valve device
11: exhaust valve box
11a: exhaust vent
11b: lower part
11c: lower inner surface
12: high temperature room
12a: inner wall
12b: bulge
12c: entrance
13: high temperature exhaust passage
13a: exit
13c, 13d: speech section of high temperature chamber and hot exhaust passage inlet
14: low temperature room (low temperature exhaust passage)
14a: inner wall
15: low temperature exhaust passage
15a: low temperature exhaust passage exit
15b, 15c: speech section of cold chamber and cold exhaust passage
17: rectifying plate (first rectifying plate)
17a: side
18: rectification plate (second rectification plate)
18a: side
16: casing
17: hydraulic cylinder block
17a: side
21: main valve
21a: valve face
22: valve stem
23: main valve air piston
24: secondary valve
24a: spokes (spokes)
24b: skirt section
25: secondary valve
25c: rib
25d: lower part
25e: bottom surface
26: valve stem
27: commutation member
27a: tip
27b: concave curved portion
28: main valve hydraulic cylinder
29: air piston
30: hydraulic cylinder block
31: hydraulic cylinder
35 casing
36: air spring chamber
37: Vice Valve Air Piston
40: hydraulic cylinder block
41: outside hydraulic cylinder block
41a: hole
41b: outer circumference
41c: inner circumference
41d: top side
42: inner hydraulic cylinder block
42a: hole
42b: outer circumference
43: Vice Valve Hydraulic Cylinder
44: piston
45: annular recess
46: hydraulic cylinder
47: piston
48: Bolt
51: secondary valve switching device
52: zero position control device
55: hydraulic sensor
61, 62, 63, 65: hydraulic passage
66: annular groove
67, 68, 70: hydraulic passage
69: annular hydraulic passage
75: bolt
76: secondary valve damage prevention device
Dv: diameter of valve face
D01: Outlet diameter of the cold exhaust passage
D02: Outlet diameter of high temperature exhaust passage
D1: inner diameter of secondary valve
D2: Outer diameter of skirt rear end
D3: inner diameter of skirt
D4: Outer diameter of the skirt tip
L1: center line of the cold exhaust passage
L2: centerline of the hot exhaust passage
O: center
P: hydraulic
R1, R5: radius of curvature of the opening of the cold compartment and the cold exhaust passage
R2 to R4: radius of curvature forming the vortex of the low temperature chamber
R11: radius of curvature of the side of the first rectifying plate
R21: radius of curvature of the side of the second rectifying plate
SP: Vortex origin of low temperature room
θ ₁ : Angle with respect to the centerline of the cold exhaust passage at the vortex origin of the cold chamber
θ ₂ : Angle with respect to the radial direction of the outer peripheral surface of the skirt portion of the sub valve
δ: clearance (clearance)

Claims (8)

A main valve 21 for exhausting combustion gas in the cylinder 3, a high temperature chamber 12 formed in the exhaust valve box 11 and introducing a high temperature combustion gas discharged from the cylinder through the main valve; And a high temperature exhaust passage 13 formed in the exhaust valve box to discharge the combustion gas in the high temperature chamber to the outside, and a low temperature combustion gas formed in the exhaust valve box and discharged from the cylinder through the main valve. The internal combustion engine having low temperature exhaust passages 14 and 15 discharged to the exhaust valve box and secondary valves 25 formed in the exhaust valve box to switch the flow of the combustion gas to the high temperature exhaust passage and the low temperature exhaust passage. In the exhaust passage structure, the combustion gas having a high temperature introduced into the high temperature chamber to the inner wall surface 14a of the high temperature chamber is smoothly guided to the high temperature exhaust passage. Flow plates 17 and 18 are formed, and the rectifying plate includes a first rectifying plate 17 formed on the side opposite to the outlet 13a side of the hot exhaust passage and toward the center of the outlet side, and the hot exhaust passage. A second rectifying plate 18 formed on the outlet side and toward the center of the outlet side, wherein the first rectifying plate has both sides 17a from the leading end toward the outlet side center of the hot exhaust passage; Spread so that an arcuate concave curved surface may be formed toward the inner wall surface 12a of the greenhouse, and the second rectifying plate 18 may be formed of the high temperature chamber from a tip of which both side surfaces 18a face the center of the outlet side of the high temperature exhaust passage. Spread so as to form an arcuate concave curved surface toward the inner wall surface of the, and the high temperature chamber has a center line L connecting the outlet center of the high temperature exhaust passage and the high temperature chamber center O to each other. An exhaust passage structure of an internal combustion engine, characterized by being formed in a symmetrical shape. The method of claim 1,
A bulging portion 12b formed by expanding the inner wall surface 12a near the high temperature chamber inlet 12c to form a convex curved surface is formed in the high temperature chamber, and the bulging portion surrounds the inlet of the high temperature chamber. The exhaust passage structure of the internal combustion engine characterized by the above-mentioned. 3. The method according to claim 1 or 2,
A rectifying member 27 constituting an inverted cone shape is mounted on a supporting member 30 for supporting the valve stem 26 of the secondary valve 25, and the tip portion 27a of the rectifying member 27 has an arc shape. An exhaust passage structure of an internal combustion engine, characterized by a diameter reduction so as to form a concave curved surface and extending toward the main valve (21). 3. The method of claim 2,
A rectifying member 27 having an inverted cone shape is mounted to a supporting member 30 that supports the valve stem 26 of the secondary valve 25, and the tip portion 27a of the rectifying member 27 is attached to the high temperature chamber. The diameter is reduced so as to form an arc-shaped concave curved surface 27b corresponding to the convex curved surface of the bulging portion 12b of the 12, and is extended to the main valve 21 side, so that the tip and the high of the rectifying member An exhaust passage structure of an internal combustion engine, characterized in that the bulges in the greenhouse function together with each other. delete delete delete delete

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