CN102678218B

CN102678218B - structure of exhaust gas separation device of internal combustion engine

Info

Publication number: CN102678218B
Application number: CN201210154057.8A
Authority: CN
Inventors: 高桥元幸
Original assignee: Mitsui Engineering and Shipbuilding Co Ltd
Current assignee: Mitsui Yiaisi Co ltd; Mitsui Engineering and Shipbuilding Co Ltd
Priority date: 2009-01-19
Filing date: 2010-01-18
Publication date: 2014-10-29
Anticipated expiration: 2030-01-18
Also published as: KR101259332B1; CN101818700A; CN102661208A; CN102678218A; KR20100084989A; KR101338778B1; KR20130005252A; KR101202626B1; KR20130006402A; KR101279331B1; CN102661208B; CN102678365A; KR20110134367A; CN102661182A

Abstract

The invention provides a structure of an exhaust gas separation device of an internal combustion engine, aiming at improving the fuel efficiency and work efficiency of the internal combustion engine. A sectional area of a low temperature chamber (14) from a predetermined position as a starting point (SP) to a low temperature exhaust channel inlet is in the shape of a vortex expanding gradually in the rotary direction of combustion gas. The inner wall surface (12a) of a high temperature chamber (12) is provided with flow adjustment plates (17, 18) guiding high temperature combustion gas guided into the high temperature chamber to a high temperature channel smoothly. A hydraulic cylinder body (40) forming a plurality of hydraulic cylinders (43) is provided with a hydraulic zero position control device (52) used for limiting a lower limit position of an auxiliary valve air piston and controlling a zero limit position of an auxiliary valve (25). The hydraulic cylinder body (40) is formed by an outer side hydraulic cylinder body (41) and an inner side hydraulic cylinder body (42); the plurality of hydraulic cylinders (43) and a first hydraulic channel are formed in the inner side hydraulic cylinder body; a second hydraulic channel (69) is formed between the outer side hydraulic cylinder body and the inner side hydraulic cylinder body; and third hydraulic channels (61, 62, 63) are formed in the outer side hydraulic cylinder body.

Description

The structure of the exhaust gas separation device of internal-combustion engine

Patent application of the present invention is the divisional application of the application for a patent for invention that application number is 201010003754.4, the applying date is on January 18th, 2010, denomination of invention is " structure of the exhaust gas separation device of internal-combustion engine ".

Technical field

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

Background technique

At internal-combustion engine for example in two stroke uniflow scavenging diesel engine, as shown in figure 12, pack an outlet valve (hereinafter referred to as main valve) 121 at exhaust-manifold 111, open and close this main valve 121, combustion gas (exhaust gas) are discharged to exhaust receiver (exhaust set portion), also carry out scavenging simultaneously.Scavenging is undertaken by importing scavenging by the not shown scavenging port that is located at inboard wall of cylinder liner.In addition, exhaust-manifold 111 the secondary valve 125 separating with main valve 121 is set and be separated into via this pair valve 125 two above hot room 106 with below Constant Low Temperature Facilities 108.

In addition, opening the valve initial stage (initial stage of exhaust) of main valve 121, the combustion gas of high pressure and high-temperature import hot room 106 from cylinder, and from this hot room 106, through high-temperature exhaust air passage 112, the combustion gas of high temperature are discharged to exhaust receiver (outside).In addition, opening valve mid-term to during closing valve (from the mid-term of exhaust to the later stage) from main valve, remaining combustion gas in cylinder are directed into Constant Low Temperature Facilities 108, and from this Constant Low Temperature Facilities 108, through cryopumping passage 113, the combustion gas of low temperature are discharged (with reference to patent documentation 1) to outside.

Therefore, below Constant Low Temperature Facilities 108, the rotating flow with strong vortex causing at scavenging port is directed.At this, the combustion gas of the high temperature of the hot room 106 above importing are because be the exhaust initial stage, so without strong especially vortex.

As the suction means of internal-combustion engine, following invention (with reference to patent documentation 2) is disclosed,, in the individual induction tube of being located between commutator and hood, Auxiliary valves, Fuelinjection nozzle, the bypass Auxiliary valves of cutting out while being arranged on lean combustion or when idling or low temperature also links commutator and the straight passage of the jetburner both sides of Fuelinjection nozzle, thus, easily form air intake passage.

The structure example of the exhaust gas separation device of the internal-combustion engine of the prior art as shown in figure 13, Constant Low Temperature Facilities 108 forms with concentric manner with the relief opening 105a of exhaust-manifold 105, from main valve 121 open valve mid-term to the combustion gas of low temperature that import this Constant Low Temperature Facilities 108 during closing valve from cylinder body through the relief opening 105a of exhaust-manifold 105 as shown in the streamline of arrow A ~ H, with respect to the center of outlet 113a and the centre line L at Constant Low Temperature Facilities 108 center that link cryopumping passage 113, flow to cryopumping passage 113 with strong vortex (rotating flow).In Figure 13, the lengths table of streamline is shown in the flow velocity of the combustion gas of this position.

But the flow velocity of combustion gas accelerates to the streamline position of arrow H gradually from the streamline position of the arrow A of Figure 13, obtains Peak Flow Rate in the position of arrow H, in addition, in the streamline position of arrow A ~ G, most region becomes extremely slow around relief opening 105a.

; because the flow resistance of the combustion gas in Constant Low Temperature Facilities 108 is large; so mobile deterioration of the combustion gas of discharging to cryopumping passage 113 from Constant Low Temperature Facilities 108; can not form the exhaust of the flow matching with the section area of the outlet 113a of exhaust passage 113, the problem that exists scavenging efficiency extremely to worsen.

Its reason is considered to, because Constant Low Temperature Facilities 108 forms with concentric manner with the relief opening 105a of exhaust-manifold 105, so symmetrical with respect to the centre line L that links the center of outlet 113a of cryopumping passage 113 and the Constant Low Temperature Facilities 108Nei center of the relief opening 105a of exhaust-manifold 105, thus, flow to the mobile deterioration of the combustion gas of cryopumping passage 113 from Constant Low Temperature Facilities 108.

In addition, in patent documentation 1, disclosed suction means is to make the formation of air intake passage simply invent, instead of the present application makes during valve the scavenging with strong vortex that in cylinder, remaining combustion gas are discharged, caused by the scavenging port of cylinder to exhaust receiver through cryopumping passage from Constant Low Temperature Facilities be imported into the invention of Constant Low Temperature Facilities from the valve mid-term of opening of main valve to closing like that.

In addition, as the structure of the exhaust gas separation device of the internal-combustion engine of prior art, proposed to eliminate by combustion residue and be attached on current plate and the accumulation forming, prevent the scheme (with reference to patent documentation 3) of the exhaust gas purifier for internal combustion engine of current plate shutoff.In addition, also proposed to possess the scheme (with reference to patent documentation 4) of the internal-combustion engine of the exhaust receiver that can effectively suppress vibration in the internal-combustion engine with large-scale low pressure turbocharger.

But the structure example of the exhaust gas separation device of the internal-combustion engine of the prior art is as be formed as in the section configuration as shown in Figure 14.In this structure, import the combustion gas of hot room 106 through the relief opening 105a of exhaust-manifold 105 from cylinder, as mentioned above because be so that the exhaust initial stage is not especially with vortex (rotating flow), with respect to the center of outlet 112a and the centre line L at hot room 106 center that link high-temperature exhaust air passage 112, be as shown by arrows roughly symmetrical flow and discharge, flow to high-temperature exhaust air passage 112.In Figure 14, represent that the streamline length of combustion gas flow shows the flow velocity in its position.

At this, the combustion gas of discharging from hot room 106 are collided with the internal face 106a of hot room 106 the position of the opposition side of the outlet 112a of high-temperature exhaust air passage 112, and one portion becomes backflow and is detained and stagnates, and flow and are hindered smoothly.In addition, in the position of the outlet 112a side of the high-temperature exhaust air passage 112 of hot room 106, produce eddy current in a part for the combustion gas of discharging from hot room 106, flow and still hindered smoothly.

For this reason, flowing in hot room 106 and from hot room 106 to the interior mobile combustion gas of high-temperature exhaust air passage 112 extremely worsened.Its result, can not discharge the combustion gas of the flow matching with the minimum cross-sectional area of high-temperature exhaust air passage 112, the problem that exists exhaust efficiency extremely to worsen.

In addition, in above-mentioned each patent documentation 3 and 4, any publicity is not done in the invention of discharging combustion gas through high-temperature exhaust air passage to an exhaust receiver (exhaust set portion) from hot room about opening and closing outlet valve.

Then, the discharge valve apparatus 110 shown in Figure 12 is arranged on for example valve seat 102 of cylinder body 101.This discharge valve apparatus 110 is configured to be possessed: the outlet valve (hereinafter referred to as main valve) 121 that carries out exhaust, the cryopumping passage 113 that the high-temperature exhaust air passage 112 that the high-temperature gas of exhaust-manifold 111 is used and cryogenic gas are used, switch the secondary valve 125 that flow of combustion gas to this high-temperature exhaust air passage 112 and cryopumping passage 113, be located at housing 115, carry out the oil hydraulic cylinder of opening valve events 128 of main valve 121, be located at hydraulic cylinder 117, carry out multiple for example three oil hydraulic cylinders 130 of the switching action of secondary valve 125, be fixed on the top of the valve rod 122 of main valve 121, carry out the main valve air slide 123 of the restoring action of this main valve 121, be fixed on the top of the valve rod 126 of secondary valve 125, carry out the secondary valve air slide 127 of the restoring action of this pair valve 125, receive these air slides 123, 127, the housing 116 of the pneumatic spring chamber 129 of air pressure is paid in formation.

At this, above-mentioned discharge valve apparatus 110 has represented to be applicable to the situation of two stroke uniflow scavenging type internal-combustion engine.Two stroke uniflow scavenging type internal-combustion engine, for example, have intakeport (scavenging port) at cylinder sleeve sidewall, and 121 of main valves carry out exhaust.

The valve events of opening of main valve 121 carries out to diagram below promotion valve rod 122 by the oil hydraulic cylinder 128 being moved by the hydraulic pressure of high pressure.In addition, it closes valve events (restoring action) and carries out to diagram top pull-up valve rod 122 by being arranged on main valve air slide 123 on valve rod 122., be formed at air pressure in the pneumatic spring chamber 129 of main valve air slide 123 belows and become the action source of closing valve events of main valve 121.

Multiple oil hydraulic cylinders 130 of being located at hydraulic cylinder 117 are moved by high-pressure and hydraulic, promote secondary valve air slide 127 to diagram top, carry out thus the switching action of secondary valve 125, this pair valve air slide 127 is arranged on concentric and on the valve rod 126 that is axially free to slide extraterrestrial embedding with the valve rod 122 of main valve 121.

In addition, its restoring action is by discharging the hydraulic pressure of multiple oil hydraulic cylinders 130, being carried out to diagram below promotion valve rod 126 by the secondary valve air slide 127 being arranged on valve rod 126., be formed at air pressure in the pneumatic spring chamber 129 of secondary valve air slide 127 tops and become the action source of the restoring action of secondary valve 125.There is the discharge valve apparatus of so secondary valve, for example in TOHKEMY 2008-248720 communique open (with reference to patent documentation 5).

In the discharge valve apparatus shown in Figure 12, the secondary valve 125 exhaust initial stage that main valve 121 starts to open in the time of exhaust remains on illustrated position, the exhaust gas of high temperature is discharged to high-temperature exhaust air passage 112, after exhaust mid-term from illustrated position by pressure, be switched to cryopumping passage 113 sides, be discharged to cryopumping passage 113.

But, in the discharge valve apparatus 110 of the prior art, the cylindrical shape of secondary valve 125, inner peripheral surface is fixed on valve rod 126 Shangdis by multiple tabular rib 125c and forms.In addition, the underpart 125a of the secondary valve 125 of cylindrical shape is formed as its front end (lower end surface) 125b and is the horn-like shape of opening, and the fillet part 102a of this front end 125b and valve seat 102 tops retains micro-gap ground in opposite directions.

Secondary valve 125 is depressed by secondary valve air slide 127 and is closed valve when oil hydraulic cylinder 130 contractings are moved back, carry out restoring action, but for example in the case of the drive system of oil hydraulic cylinder 130 occur abnormal,, there is the front end 125b of secondary valve 125 (conflict) problem on the fillet part 102a above valve seat 102 of likely taking a seat in secondary valve air slide 127 excessive descent.

Because secondary valve 125 is formed by the rib of complicated shape, so in the case of the fillet part 102a above front end 125b is seated at valve seat 102, act on large impact stress and breakage occurs on rib, secondary valve 125 entirety can be damaged sometimes thus.

For this reason, secondary valve 125 need to obtain the intensity of rib especially, thus be difficult to utilize cheap casting piece to form, and formed by cutting smithing product.Therefore, the manufacture cost of secondary valve 125 is high.Due to such reason, though strong request in the case of the drive system of oil hydraulic cylinder 130 occur abnormal, the front end 125b that also can prevent secondary valve 125 (conflict) the fillet part 102a above valve seat 102 that takes a seat.

In addition, in the structure of the exhaust gas separation device of the internal-combustion engine of above-mentioned prior art, multiple (three) oil hydraulic cylinder 130 of hydraulic cylinder 117 vertically forms from the upper-end surface of this hydraulic cylinder 117, as shown in figure 15, the hydraulic channel 131 ~ 134 that runs through setting in its bottom by 117a level is from the side communicated with.

In addition, these hydraulic channels 131 ~ 134 are communicated with hydraulic channel 135 and hydraulic channel 136, this hydraulic channel 135 is formed at the top of the side 117a of hydraulic cylinder 117, this hydraulic channel 136 and oil hydraulic cylinder 130 vertical formation side by side, one end (upper end) is communicated with hydraulic channel 135, and the other end is communicated with hydraulic channel 131,134 simultaneously.

But, each hydraulic channel 131 ~ 136 of hydraulic cylinder 117 is because being to be formed by machining (Drilling operation), so processed complex, the overlap (crimping) in the time of Drilling operation or the eliminating difficulty of cutting swarf (smear metal) simultaneously, exists its reprocessing to need more labour and the problem of expense.In addition, at cutting swarf (smear metal), even if the in the situation that of remaining in hydraulic channel micro-ly, having may be to the bad problem of slip of bringing oil hydraulic cylinder.

[patent documentation 1] day disclosure model utility: Beneficial 02-145617 communique

[patent documentation 2] Japanese Laid-Open Patent: JP 2002-364472 communique

[patent documentation 3] Japanese Laid-Open Patent: JP 2007-182786 communique

[patent documentation 4] Japanese Laid-Open Patent: Unexamined Patent 07-317558 communique

[patent documentation 5] Japanese Laid-Open Patent: JP 2008-248720 communique

Summary of the invention

The present invention makes in order to solve such problem, and its problem is that the burnup that realizes internal-combustion engine is improved, reliability improves and operating efficiency improves.

Specifically, its problem is, the flow resistance of the combustion gas in the Constant Low Temperature Facilities that reduces exhaust gas separation device is provided, do not hinder the scavenging with strong vortex causing at scavenging port nowed forming carry out exhaust, can obviously improve the structure of the exhaust gas separation device of the internal-combustion engine of scavenging efficiency, the mobile smooth and easy of the hot room that makes in the exhaust-manifold for the combustion gas of high temperature are discharged to exhaust receiver and the combustion gas of high-temperature exhaust air passage is also provided in addition, obviously improve thus the structure of the exhaust gas separation device of the internal-combustion engine of exhaust efficiency.

And then, its problem is also, even if provide drive system in the case of making secondary valve open the oil hydraulic cylinder of valve events that the lower position that also can limit secondary valve abnormal occurs, prevent that its underpart is landed on valve seat, prevent the structure of the exhaust gas separation device of the internal-combustion engine of the damaged or distortion of secondary valve, the structure of the exhaust gas separation device of such internal-combustion engine is also provided in addition, , easily be communicated with the machining (Drilling operation) of the hydraulic channel of each oil hydraulic cylinder, can improve the overlap (crimping) that produces or the workability of removing processing operation of cutting swarf (smear metal) in the time of machining simultaneously, the fine finishing inspection of hydraulic cylinder is also easy thereupon, can realize the minimizing of expense, and then removing of the overlap of hydraulic channel (crimping) or cutting swarf (smear metal) becomes easily as described above, can prevent that thus the slip of the oil hydraulic cylinder causing because of cutting swarf is bad, realizes the raising of reliability.

In order to solve above-mentioned problem, the means that the present invention adopts are the structure of the exhaust gas separation device of internal-combustion engine, possess: the main valve that carries out the exhaust of the combustion gas in cylinder, be located in exhaust-manifold, the combustion gas of high temperature of discharging via main valve from cylinder discharged to outside high-temperature exhaust air passage, be located in exhaust-manifold, import the Constant Low Temperature Facilities of the combustion gas of the low temperature of discharging via main valve from cylinder, be located in exhaust-manifold, the combustion gas in Constant Low Temperature Facilities discharged to outside cryopumping passage, be located in exhaust-manifold, switch the secondary valve that flow of combustion gas to high-temperature exhaust air passage and cryopumping passage, wherein, Constant Low Temperature Facilities is taking assigned position as starting point the scrollwork shape expanding gradually in the sense of rotation of combustion gas to the section area of the entrance of cryopumping passage.

The combustion gas of discharging from cylinder after valve mid-term of opening at main valve are imported into Constant Low Temperature Facilities, from Constant Low Temperature Facilities through cryopumping passage discharged to outside.The scrollwork shape expanding gradually in the sense of rotation of combustion gas by the shape of Constant Low Temperature Facilities being formed as taking assigned position as starting point to the section area of entrance of cryopumping passage, thereby can, importing Constant Low Temperature Facilities with the combustion gas of strong vortex not hinder the mode of vortex by causing from the scavenging of scavenging port, can significantly reduce the flow resistance of combustion gas.Its result, can smooth and easy discharge and the combustion gas of the flow that matches of the section area of cryopumping passage, significantly improves scavenging efficiency.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, the entrance of Constant Low Temperature Facilities and cryopumping passage arranges sleekly continuously with the curved surface of different radius of curvature.Like this, by the entrance of Constant Low Temperature Facilities and cryopumping passage is arranged sleekly continuously with the curved surface of different radius of curvature, can further reduce from Constant Low Temperature Facilities the flow resistance discharged to the exhaust gas of cryopumping passage.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, starting point is positioned at the center line at Constant Low Temperature Facilities Nei center of the center of outlet from linking cryopumping passage and the relief opening of cylinder to the position of the sense of rotation skew predetermined angular of combustion gas.Like this, by the starting point of the scrollwork shape of Constant Low Temperature Facilities being set in to the position of sense of rotation skew predetermined angular of revenue centre alignment combustion gas of the Constant Low Temperature Facilities that is positioned at the center of outlet from linking cryopumping passage and the relief opening of cylinder, the flowing of combustion gas importing in Constant Low Temperature Facilities can be imported to cryopumping passage more swimmingly.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, Constant Low Temperature Facilities is become the Surface forming of large different radius of curvature gradually by the entrance from starting point to cryopumping passage.Like this, by the Surface forming Constant Low Temperature Facilities by the different radius of curvature increasing gradually from starting point to the entrance of cryopumping passage, thereby the exhaust passage that can form the scroll that its section area increases gradually to the entrance of cryopumping passage, can form the exhaust passage that does not further hinder combustion gas vortex.

In addition, in order to solve above-mentioned problem, the means that the present invention adopts are the structure of the exhaust gas separation device of internal-combustion engine, it possesses: the main valve that carries out the exhaust of the combustion gas in cylinder, be located in exhaust-manifold, the combustion gas of the high temperature of discharging via main valve from cylinder discharged to outside high-temperature exhaust air passage, be located in exhaust-manifold, the combustion gas of the low temperature of discharging via main valve from cylinder discharged to outside cryopumping passage, be located in exhaust-manifold, switch the mobile secondary valve of combustion gas to high-temperature exhaust air passage and cryopumping passage; Wherein, secondary valve is straight cylinder shape, forms skirt section at front end simultaneously.

Like this, form skirt section by the front end at the secondary valve that is straight cylinder shape, the combustion gas that the relief opening from cylinder cap can be discharged do not hinder vortex ground and import to smoothly Constant Low Temperature Facilities, significantly improve the scavenging efficiency of combustion gas to Constant Low Temperature Facilities.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, skirt section is the external diameter frustum of a cone cylindrical shell shape larger than the external diameter of front end of rear end.Like this, be formed as the external diameter frustum of a cone cylindrical shell shape larger than the external diameter of front end of rear end by the skirt section of secondary valve, have with the relief opening of exhaust-manifold in opposite directions and with the skirt section of the outer circumferential face that tilts to the mode of rear end hole enlargement from front end thereby form, the combustion gas that can the relief opening from exhaust-manifold be discharged by the outer circumferential face of the inclination in this skirt section import Constant Low Temperature Facilities more swimmingly, further improve scavenging efficiency.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, the external diameter of the front end in skirt section is less than the diameter of the relief opening of exhaust-manifold, simultaneously the outer circumferential face of rear end can with the inner peripheral surface sliding contact of the relief opening of exhaust-manifold.Like this, by the external diameter of the front end in skirt section is formed as to the diameter more young than the exhaust of exhaust-manifold, and make rear end outer circumferential face can with the inner peripheral surface sliding contact of the relief opening of cylinder cap, thereby skirt section can be inserted swimmingly to the relief opening of exhaust-manifold.In addition, by making rear end outer circumferential face and the relief opening sliding contact in skirt section, can shutoff relief opening and the secondary valve of straight cylinder shape between gap.Thus, the relief opening from cylinder cap can be discharged to combustion gas and import Constant Low Temperature Facilities without leaking.

In addition, in order to solve above-mentioned problem, the means that the present invention adopts are the structure of the exhaust gas separation device of internal-combustion engine, it possesses: the main valve that carries out the exhaust of the combustion gas in cylinder, be located in exhaust-manifold, import the hot room of the combustion gas of the high temperature of discharging via main valve from cylinder, be located in exhaust-manifold, the combustion gas in hot room discharged to outside high-temperature exhaust air passage, be located in exhaust-manifold, the combustion gas of low temperature of discharging via main valve from cylinder discharged to outside cryopumping passage, be located in exhaust-manifold, switch the secondary valve that flow of combustion gas to high-temperature exhaust air passage and cryopumping passage, wherein, arrange lead the swimmingly current plate of high-temperature exhaust air passage of the combustion gas that import to the high temperature in hot room at the internal face of hot room.

In this invention, be directed to hot room at the valve initial stage of opening of main valve from the combustion gas of the high temperature of cylinder discharge, pass through high-temperature exhaust air passage discharged to outside from hot room.At this, make the combustion gas of discharging and import to hot room from cylinder without being detained the smooth and easy high-temperature exhaust air passage that flows at the newly-installed current plate of internal face of hot room.Thus, flowing of the combustion gas in hot room and high-temperature exhaust air passage is same, and its result mean velocity is accelerated, and can successfully discharge the combustion gas of the flow matching with the minimum cross-sectional area of high-temperature exhaust air passage.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, current plate is made up of the first current plate that is positioned at a side contrary with the outlet side of high-temperature exhaust air passage centered by the relief opening by exhaust-manifold and arrange towards the center of outlet side.Like this, by the opposition side at outlet side hot room internal face, be positioned at high-temperature exhaust air passage centered by the relief opening of exhaust-manifold and towards the center of outlet side, the first current plate is set, thereby distribute the combustion gas that import to hot room from cylinder in the both sides of the first current plate approximate equality, and its internal face along hot room is flowed, can effectively prevent interference or the delay of the combustion gas at this position.Thus, make flowing of combustion gas extremely smooth and easy.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, current plate is made up of the second current plate that is positioned at the outlet side of high-temperature exhaust air passage centered by the relief opening by exhaust-manifold and arrange towards the center of outlet side.Like this, by the internal face at hot room, centered by the relief opening of exhaust-manifold, be positioned at the outlet side of high-temperature exhaust air passage and towards the center of outlet side, the second current plate be set, thereby distribute the combustion gas that import from cylinder in the both sides of second plate approximate equality, make it in high-temperature exhaust air channel flow, can effectively prevent interference or the delay of the combustion gas at this position.Thus, make flowing of combustion gas extremely smooth and easy.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, the bi-side of the first current plate are circular-arc concave curved surface from the front end at the outlet side center towards high-temperature exhaust air passage towards the internal face of hot room and expand.Like this, be located at the bi-side of the first current plate of hot room by handle, be circular-arc concave curved surface from the front end at the center of the outlet side towards high-temperature exhaust air passage towards the internal face of hot room and expand formation, the combustion gas that can make to import to hot room along concave curved surface both sides approximate equality towards smooth and easy the flowing of internal face of hot room, make flowing of combustion gas further smooth and easy.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, the bi-side of above-mentioned the second current plate are circular-arc concave curved surface from the front end at the outlet side center towards high-temperature exhaust air passage towards the internal face of hot room and expand.Like this, be located at the bi-side of the second current plate of hot room by handle, be circular-arc concave curved surface from the front end at the center of the outlet side towards high-temperature exhaust air passage towards the internal face of hot room and expand formation, can make the combustion gas of discharging from hot room flow in both sides approximate equality along concave curved surface, smooth and easy mobile at high-temperature exhaust air passage.Thus, flowing of combustion gas can be further smooth and easy.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, near the internal face entrance by making hot room is set in hot room and is convex curved surface and bloats the bellying forming.Near the entrance of hot room, easily forming eddy current along internal face the combustion gas in cylinder imports to hot room.But, be located in hot room by like this near the internal face entrance by making hot room being to convex curved surface and bloating the bellying forming, flow near the combustion gas of the cylinder internal face along the hot room entrance of hot room, the combustion gas that import from cylinder are in hot room, then flow smoothly to high-temperature exhaust air passage.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine preferably, be arranged on the support unit of valve rod of the secondary valve of supporting being the roughly rectification part of inverted cone shape, make the front end of this rectification part be the undergauge Cheng Bingxiang main valve side extension of circular-arc concave curved surface ground.Like this, be circular-arc concave curved surface and extend to form to main valve side by making to be arranged on the front end of the rectification part on the support unit of valve rod of the secondary valve of supporting, thereby can make to lead swimmingly in hot room from the combustion gas of cylinder, then the high-temperature exhaust air passage that leads swimmingly, can make flowing of combustion gas more smooth and easy.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine preferably, be arranged on the support unit of valve rod of the secondary valve of supporting being roughly obconic rectification part, make the front end of this rectification part be the circular-arc concave curved surface ground undergauge corresponding with the convex curved surface of above-mentioned bellying and extend to main valve side, make the bellying co-operation of front end and the hot room of rectification part.Like this, the front end that is arranged on the rectification part on the support unit of valve rod of the secondary valve of supporting by handle is formed as the concave curved surface corresponding with the convex curved surface of bellying that is located at high-temperature exhaust air passage, bellying co-operation with hot room, thereby make the shape of exhaust passage further smooth, make from the combustion gas of cylinder can further lead swimmingly hot room and high-temperature exhaust air passage.

In addition, in order to solve above-mentioned problem, the means that the present invention adopts are the structure of the exhaust gas separation device of internal-combustion engine, possess: the main valve that carries out air-breathing and/or exhaust, carry out the secondary valve of the switching switching of the multiple air-breathing and/or exhaust passage of extending via main valve branch from cylinder, carry out the oil hydraulic cylinder of opening valve events of main valve, carry out multiple oil hydraulic cylinders of the switching action of secondary valve, carry out the main valve air slide of the restoring action of main valve, carry out the secondary valve air slide of the restoring action of secondary valve, drive the air chamber of main valve air slide and secondary valve air slide; Wherein, form the lower position of the secondary valve air slide of restriction is set on the hydraulic cylinder of multiple oil hydraulic cylinders and controls secondary valve zero point restriction site the dead-center position control gear of hydraulic type.

Main valve utilizes oil hydraulic cylinder to drive valve, utilizes main valve air slide to close valve.Secondary valve utilizes multiple oil hydraulic cylinders to drive valve, utilizes secondary valve air slide to close valve.The dead-center position control gear of hydraulic type, in the time that secondary valve closes valve by the action of secondary valve air slide, while carrying out restoring action, limits its lower position, i.e. dead-center position.Thus, can between the upper-end surface of the valve seat of the lower end surface of secondary valve and main valve, ensure gap, can prevent that the lower end surface of secondary valve from taking a seat (conflict) in the upper-end surface of the valve seat of main valve, can prevent the damaged or distortion of secondary valve.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, dead-center position control gear arranges in opposite directions multiple oil hydraulic cylinders at hydraulic cylinder and secondary valve air slide and forms.Like this, form dead-center position control gear by multiple firmly oil hydraulic cylinders being set with respect to the secondary valve air slide of strong construction, can make the secondary valve air slide that is closed valve events (restoring action) by air pressure brute force stop reliably.Thus, make secondary valve stop at dead-center position (lower position) even the lower end surface of secondary valve stops at and the upper-end surface of the valve seat of main valve between deposit on gapped position.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, multiple oil hydraulic cylinders of dead-center position control gear are along circumferentially uniformly-spaced configuration on same circumference, and hydraulic channel forms together with ground.Like this, the multiple oil hydraulic cylinders that form dead-center position control gear by handle along circumferentially uniformly-spaced configuration, can bear equably the powerful pressing force of secondary valve air slide on same circumference, also can prevent in addition the unfavorable condition of the distortion etc. of secondary valve air slide.In addition, be communicated with by the hydraulic channel that makes multiple hydraulic pistons, can make these multiple hydraulic pistons move with the hydraulic pressure of homogeneous simultaneously, can make secondary valve air slide stop well.Thus, can carry out accurately the positioning control of the lower position (dead-center position) of secondary valve.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine preferably, the multiple oil hydraulic cylinders that carry out the switching action of secondary valve are circumferentially equally spaced being configured on same circumference, and multiple oil hydraulic cylinders of dead-center position control gear are alternately configured on same circumference with the multiple oil hydraulic cylinders that carry out secondary valve switching action.Like this, the multiple oil hydraulic cylinders of switching action that carry out secondary valve by handle are along circumferentially uniformly-spaced configuration on same circumference, and can making secondary valve air slide resist it, powerful air pressure ground is impartial promotes, and also can prevent in addition the unfavorable condition of the distortion etc. of secondary valve air slide.In addition, the multiple oil hydraulic cylinders that form dead-center position control gear by handle are configured on same circumference and with these oil hydraulic cylinders and alternately configure with the multiple oil hydraulic cylinders that carry out secondary valve switching action, move multiple oil hydraulic cylinders similarly with the switching of carrying out secondary valve, can bear equably the powerful pressing force of secondary valve air slide, also can prevent in addition the unfavorable condition of distortion of secondary valve air slide etc.Thus, can stop well secondary valve air slide, can highi degree of accuracy carry out the positioning control of the dead-center position (lower position) of secondary valve.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine preferably, control valve unit also possesses: the hydrostatic sensor detecting being supplied to the hydraulic pressure of dead-center position control gear, produces the secondary valve device for preventing breakage of reporting to the police and/or stopping internal-combustion engine at hydrostatic sensor when the hydraulic pressure detecting exceedes authorized pressure.This is to utilize hydrostatic sensor to detect the hydraulic pressure of the oil hydraulic cylinder that is supplied to dead-center position control gear, in the time that this hydraulic pressure exceedes authorized pressure, (conflict) taken a seat in the upper-end surface of the valve seat of main valve in the lower end surface that judges secondary valve, carries out the generation of warning or stopping of internal-combustion engine.Thus, can prevent more reliably damaged the or distortion of secondary valve.

In addition, in the structure of the exhaust gas separation device of above-mentioned internal-combustion engine preferably, secondary valve is straight cylinder shape, can slide axially with the inner peripheral surface of the exhaust-manifold that is formed as straight interior cylindrical shape, its lower end surface retains with gap in opposite directions in the upper-end surface of the valve seat that closes valve position and main valve simultaneously.By such setting, can slide and switch swimmingly action on one side at the inner peripheral surface of exhaust-manifold on one side in the straight underpart of secondary valve.In addition, secondary valve is by preventing that with the gap of the upper-end surface of the valve seat of main valve its lower end surface from taking a seat (conflict) in the upper-end surface of the valve seat of main valve, prevents more reliably damaged the or distortion of secondary valve.

In addition, in order to solve above-mentioned problem, the means that the present invention adopts are the structure of the exhaust gas separation device of internal-combustion engine, and its side end face at hydraulic cylinder forms multiple oil hydraulic cylinders that have the end, and each oil hydraulic cylinder possesses the exhaust-manifold being communicated with by the hydraulic channel that is formed at hydraulic cylinder, wherein, hydraulic cylinder is by outside hydraulic cylinder, the inner side hydraulic cylinder being embedded in this outside hydraulic cylinder with liquid-tight formula forms, form multiple oil hydraulic cylinders at inner side hydraulic cylinder, with its one end each oil hydraulic cylinder opening simultaneously the other end at the first hydraulic channel of the outer circumferential face opening of this inner side oil hydraulic cylinder, between outside hydraulic cylinder and inner side hydraulic cylinder, form the second hydraulic channel being communicated with each the first hydraulic channel, outside hydraulic cylinder form its one end the second hydraulic channel opening simultaneously the other end at the 3rd hydraulic channel of the outer circumferential face opening of outside hydraulic cylinder.

According to the present invention, because serving as reasons, outside hydraulic cylinder forms hydraulic cylinder with the inner side hydraulic cylinder that is embedded in this outside hydraulic cylinder, inner side hydraulic cylinder form multiple oil hydraulic cylinders and its one end each oil hydraulic cylinder opening simultaneously the other end at the first hydraulic channel of the outer circumferential face opening of inner side hydraulic cylinder, so, can shorten the first hydraulic channel, the machining (Drilling operation) of this first hydraulic channel becomes easily, and the processing of removing of the overlap (crimping) producing in the time of Drilling operation or cutting swarf (smear metal) also becomes easy.

In addition, because form the second hydraulic channel of being communicated with each the first hydraulic channel between outside hydraulic cylinder and inner side hydraulic cylinder, so that the processing of the second hydraulic channel also becomes is easy.And then, because form one end and the second hydraulic channel open communication, the other end the 3rd hydraulic channel at the outer circumferential face opening of outside hydraulic cylinder at outside hydraulic cylinder, so, the machining (Drilling operation) of the 3rd hydraulic channel becomes easily, and the overlap (crimping) producing when Drilling operation or the processing of removing of cutting swarf also become easy.

; form by hydraulic cylinder being divided into outside hydraulic cylinder and inner side hydraulic cylinder; the machining (Drilling operation) of hydraulic channel becomes extremely easy, the raising of the overlap (crimping) producing can realize machining (Drilling operation) time or the workability of removing processing operation of cutting swarf (smear metal) simultaneously.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine preferably, outside hydraulic cylinder is round-ended cylinder shape, the cylindrical shape of inner side hydraulic cylinder, multiple oil hydraulic cylinders form along circumferentially retaining compartment of terrain at inner side hydraulic cylinder, each the first hydraulic channel is radial formation from each oil hydraulic cylinder, and the second hydraulic channel in the form of a ring.Like this, by be have the outside of round-ended cylinder shape hydraulic cylinder in the inner side hydraulic cylinder of embedded cylindrical shape, form multiple oil hydraulic cylinders at inner side hydraulic cylinder along circumferentially retaining compartment of terrain, be and form radially each the first hydraulic channel from each oil hydraulic cylinder, the second hydraulic channel is formed as to ring-type, thereby the processing of outside hydraulic cylinder and inner side hydraulic cylinder becomes extremely easy.In addition, by the first hydraulic channel forming at inner side hydraulic cylinder is to radial formation from oil hydraulic cylinder to the outer circumferential face of this inner side hydraulic cylinder, can shorten hydraulic channel, Drilling operation becomes easy simultaneously.And then the processing of removing of the overlap (crimping) producing when Drilling operation or cutting swarf also becomes easy.In addition, by making the second hydraulic channel be formed as ring-type, easily carry out and be formed as being communicated with of radial each the first hydraulic channel, its processing simultaneously also becomes easy.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine preferably, the second hydraulic channel makes the outer circumferential face of the bottom side of the inner side hydraulic cylinder of cylindrical shape be recessed into ring-type with concentric manner, and the inner peripheral surface of outside hydraulic cylinder between form the hydraulic channel of ring-type.Like this, the outer circumferential face of bottom side of the inner side hydraulic cylinder by making cylindrical shape is recessed into ring-type with concentric manner, and the inner peripheral surface of outside hydraulic cylinder between form the hydraulic channel of ring-type, using the hydraulic channel of this ring-type as the second hydraulic channel, it is easy that the machining of the second hydraulic channel becomes.

In the structure of the exhaust gas separation device of above-mentioned internal-combustion engine, preferably, one end of the first hydraulic channel is at the bottom side inner peripheral surface opening of oil hydraulic cylinder.Like this, by making to be communicated with the first hydraulic channel of each oil hydraulic cylinder and the second hydraulic channel at the bottom side inner peripheral surface opening of oil hydraulic cylinder, can shorten the first hydraulic channel, the Drilling operation of this first hydraulic channel becomes easily simultaneously, and then the overlap (crimping) producing when Drilling operation or the processing of removing of cutting swarf also become easy.

As mentioned above, the structure of the exhaust gas separation device of internal-combustion engine of the present invention possesses: the main valve that carries out the exhaust of the combustion gas in cylinder, be located in exhaust-manifold, from cylinder via main valve discharge high-temperature combustion gas discharged to outside high-temperature exhaust air passage, be located in exhaust-manifold, import the Constant Low Temperature Facilities of the combustion gas of the low temperature of discharging via main valve from cylinder, be located in exhaust-manifold, the combustion gas in Constant Low Temperature Facilities discharged to outside cryopumping passage, be located in exhaust-manifold, switch the secondary valve that flow of combustion gas to high-temperature exhaust air passage and cryopumping passage, wherein, Constant Low Temperature Facilities is the scrollwork shape that the section area to cryopumping feeder connection expands gradually in the sense of rotation of combustion gas taking assigned position as starting point.

In addition, the structure of the exhaust gas separation device of internal-combustion engine of the present invention possesses: the main valve that carries out the exhaust of the combustion gas in cylinder, be located in exhaust-manifold, the combustion gas of the high temperature of discharging via main valve from cylinder discharged to outside high-temperature exhaust air passage, be located in exhaust-manifold, the combustion gas of the low temperature of discharging via main valve from cylinder discharged to outside cryopumping passage, be located in exhaust-manifold, switch the mobile secondary valve of combustion gas to high-temperature exhaust air passage and cryopumping passage; Wherein, secondary valve is straight cylinder shape, and forms skirt section at front end.

Therefore, play such excellent effect: can reduce the flow resistance of combustion gas in Constant Low Temperature Facilities, can not hinder the scavenging with strong vortex causing at scavenging port nowed forming carry out exhaust, can show the aobvious scavenging efficiency that improves.

In addition, the structure of the exhaust gas separation device of internal-combustion engine of the present invention possesses: the main valve that carries out the exhaust of the combustion gas in cylinder, the hot room of the combustion gas of the high temperature of be located in exhaust-manifold, importing being discharged from cylinder via main valve, be located in exhaust-manifold, the combustion gas in hot room discharged to outside high-temperature exhaust air passage, be located in exhaust-manifold, the combustion gas of the low temperature of discharging via main valve from cylinder discharged to outside cryopumping passage, be located in exhaust-manifold, switch the mobile secondary valve of combustion gas to high-temperature exhaust air passage and cryopumping passage; Wherein, at the internal face of hot room, the current plate that the combustion gas that import to the high temperature in hot room is directed into swimmingly to high-temperature exhaust air passage is set.

Therefore, for being same the combustion gas of high temperature discharged to the mobile of combustion gas of outside hot room and high-temperature exhaust air passage, its result mean velocity is accelerated, and can discharge smoothly the combustion gas of the flow matching with the minimum cross-sectional area of high-temperature exhaust air passage.That is, play such excellent effect: the mobile of the combustion gas in hot room and high-temperature exhaust air passage becomes extremely smooth and easy, can significantly improve the exhaust efficiency of internal-combustion engine.

In addition, the structure of the exhaust gas separation device of internal-combustion engine of the present invention possesses: the main valve that carries out air-breathing and/or exhaust, carry out the secondary valve of the switching switching of the multiple air-breathing and/or exhaust passage of extending via main valve branch from cylinder, carry out the oil hydraulic cylinder of opening valve events of main valve, carry out multiple oil hydraulic cylinders of the switching action of secondary valve, carry out the main valve air slide of the restoring action of main valve, carry out the secondary valve air slide of the restoring action of secondary valve, drive the air chamber of main valve air slide and secondary valve air slide; Wherein, the lower position of the secondary valve air slide of restriction is set on the hydraulic cylinder that is formed with multiple oil hydraulic cylinders and control secondary valve zero point restriction site the dead-center position control gear of hydraulic type.

Like this, by make secondary valve switch on the hydraulic cylinder of oil hydraulic cylinder of action in formation, the lower position of the secondary valve air slide of restriction is set and control secondary valve zero point restriction site the dead-center position control gear of hydraulic type, can in the time that having carried out restoring action, limit by secondary valve its lower position, dead-center position, can critically adjust and ensure the gap between the lower end surface of secondary valve and the upper-end surface of the valve seat of main valve, can prevent that the lower end surface of secondary valve from taking a seat (conflict) in the upper-end surface of the valve seat of main valve.Thus, play such excellent effect: can reliably prevent the damaged or distortion of secondary valve, can form at an easy rate secondary valve by precision casting, can realize the significantly reduction of cost simultaneously.

In addition, the structure of the exhaust gas separation device of internal-combustion engine of the present invention, its side end face at hydraulic cylinder forms multiple oil hydraulic cylinders that have the end, and each oil hydraulic cylinder is communicated with by the hydraulic channel that is formed at hydraulic cylinder; Wherein, the inner side hydraulic cylinder that hydraulic cylinder is embedded in outside hydraulic cylinder by outside hydraulic cylinder and liquid-tight formula forms, inner side hydraulic cylinder form multiple oil hydraulic cylinders and one end each oil hydraulic cylinder opening simultaneously the other end at the first hydraulic channel of the outer circumferential face opening of inner side oil hydraulic cylinder, between outside hydraulic cylinder and inner side hydraulic cylinder, form the second hydraulic channel of being communicated with each the first hydraulic channel, in outside hydraulic cylinder formation one end at the second hydraulic channel opening while the other end the 3rd hydraulic channel at the outer circumferential face opening of outside hydraulic cylinder.

Therefore, the hydraulic cylinder that forms multiple oil hydraulic cylinders by handle is divided into outside hydraulic cylinder and inner side hydraulic cylinder and forms, play such excellent effect: the machining (Drilling operation) of the hydraulic channel of each oil hydraulic cylinder connection is become easily, the raising of the overlap (crimping) producing machining can be realized time or the workability of removing processing operation of cutting swarf (smear metal) simultaneously.Thereupon, the fine finishing inspection of hydraulic cylinder also becomes easy, can realize the minimizing of expense, and then, by easily carrying out as mentioned above the overlap (crimping) of hydraulic channel or removing of cutting swarf (smear metal), the slip that can prevent the oil hydraulic cylinder causing because of cutting swarf is bad, can realize the raising of reliability, also plays above such excellent effect.

In addition, can realize burnup improvement and the raising of reliability and the raising of operating efficiency of internal-combustion engine by such scheme.

Brief description of the drawings

Fig. 1 is the major component sectional view that represents the diesel engine of the structure of the exhaust gas separation device of internal-combustion engine of the present invention.

Fig. 2 is the sectional view along the arrow line II-II of the diesel engine of Fig. 1.

Fig. 3 is the explanatory drawing of the combustion gas flow in the Constant Low Temperature Facilities shown in modal representation Fig. 2 and cryopumping passage.

Fig. 4 is the major component sectional view of watching the diesel engine of Fig. 1 from another angle.

Fig. 5 is the sectional view along the arrow line V-V of the diesel engine of Fig. 4.

Fig. 6 is the explanatory drawing of the combustion gas flow in the hot room shown in modal representation Fig. 5 and high-temperature exhaust air passage.

Fig. 7 is the major component sectional view that represents the diesel engine different from Fig. 1.

Fig. 8 is the sectional view along the arrow line VIII-VIII of the diesel engine of Fig. 7.

Fig. 9 is the sectional view of the operating position different from Fig. 8 of the diesel engine shown in Fig. 7.

Figure 10 is the sectional view along the arrow line X-X of the diesel engine of Fig. 7.

Figure 11 is the partial enlarged drawing of the oil hydraulic cylinder of the dead-center position control gear shown in Fig. 8.

Figure 12 is the major component sectional view that represents the diesel engine of prior art.

Figure 13 is the explanatory drawing of the combustion gas flow in Constant Low Temperature Facilities and the cryopumping passage of diesel engine of modal representation Figure 12.

Figure 14 is the explanatory drawing of the combustion gas flow in hot room and the high-temperature exhaust air passage of diesel engine of modal representation Figure 12.

Figure 15 is the sectional view along the arrow line XV-XV of the diesel engine of Figure 12.

Description of reference numerals

1 cylinder body; 2 valve seats; 2a relief opening; 3 cylinders; 5 exhaust-manifolds; 5a relief opening; 6 hot rooms; 6a internal face; 7 high-temperature exhaust air passages; 7a outlet; 8 Constant Low Temperature Facilitiess; 8a internal face; 9 cryopumping passages; 9a outlet; 10 discharge valve apparatus; 11 exhaust-manifolds; 11a relief opening; 11b underpart; 11c underpart inner peripheral surface; 12 hot rooms; 12a internal face; 12b bellying; 12c entrance; 13 high-temperature exhaust air passages; 13a outlet; The portion that is connected with of 13c, 13d hot room and high-temperature exhaust air feeder connection; 14 Constant Low Temperature Facilitiess (cryopumping passage); 14a internal face; 15 cryopumping passages; 15a cryopumping channel outlet; The portion that is connected with of 15b, 15c Constant Low Temperature Facilities and cryopumping passage; 17 current plates (the first current plate); 17a side; 18 current plates (the second current plate); 18a side; 16 housings; 17 hydraulic cylinders; 17a side; 21 main valves; 21a valve face; 22 valve rods; 23 main valve air slides; 24 secondary valves; 24a spoke (disc); 24b skirt section; 25 secondary valves; 25c rib; 25d underpart; 25e lower end surface; 26 valve rods; 27 rectification parts; 27a front end; 27b concave curved surface; 28 main valve oil hydraulic cylinders; 29 air slides; 30 hydraulic cylinders; 31 oil hydraulic cylinders; 35 housings; 36 pneumatic spring chambers; 37 secondary valve air slides; 40 hydraulic cylinders; 41 outside hydraulic cylinders; 41a hole; 41b outer circumferential face; 41c inner peripheral surface; 41d upper-end surface; 42 inner side hydraulic cylinders; 42a hole; 42b outer circumferential face; 43 secondary valve oil hydraulic cylinders; 44 pistons; The recess of 45 ring-types; 46 oil hydraulic cylinders; 47 pistons; 48 bolts; 51 secondary valve COMM communication; 52 dead-center position control gear; 55 hydrostatic sensors; 61,62,63,65 hydraulic channels; 66 annular slots; 67,68,70 hydraulic channels; The hydraulic channel of 69 ring-types; 75 bolts; 76 secondary valve device for preventing breakage; The diameter of Dv valve face; The outlet internal diameter of D01 cryopumping passage; The outlet internal diameter of D02 high-temperature exhaust air passage; The internal diameter of the secondary valve of D1; The external diameter of the rear end in D2 skirt section; The internal diameter of the front end in D3 skirt section; The external diameter of the front end in D4 skirt section; The center line of L1 cryopumping passage; The center line of L2 high-temperature exhaust air passage; O center; P hydraulic pressure; The radius of curvature of the portion that is connected with of R1, R5 Constant Low Temperature Facilities and cryopumping passage; R2 ~ R4 forms the radius of curvature of the scrollwork shape of Constant Low Temperature Facilities; The radius of curvature of the side of R11 the first current plate; The radius of curvature of the side of R21 the second current plate; The starting point of the scrollwork shape of SP Constant Low Temperature Facilities; θ ₁the angle of the center line of the starting point relative low temperature exhaust passage of the scrollwork of Constant Low Temperature Facilities; θ ₂the angle of the outer circumferential face relative diameter direction in the skirt section of secondary valve; δ gap (clearance).

Embodiment

Describe the working of an invention mode of the structure of the exhaust gas separation device for implementing internal-combustion engine of the present invention in detail referring to figs. 1 through Fig. 6.

Fig. 1 is major component sectional view diesel engine, centered by exhaust-manifold 11 that has been suitable for the structure of the exhaust gas separation device of internal-combustion engine of the present invention.As shown in Figure 1, exhaust-manifold 11 is arranged on the valve seat 2 of cylinder body 1, possesses main valve 21, is located at the hot room 12 in exhaust-manifold 11, the high-temperature exhaust air passage 13 being communicated with hot room 12, Constant Low Temperature Facilities 14, the cryopumping passage 15 that is communicated with Constant Low Temperature Facilities 14.In addition, have the mobile secondary valve 24 that is switched to a side of hot room 12 and high-temperature exhaust air passage 13 and a side of Constant Low Temperature Facilities 14 and cryopumping passage 15 of combustion gas.

In addition, be configured to and possess: the not shown oil hydraulic cylinder of opening valve events that carries out main valve 21, multiple for example three oil hydraulic cylinders 31 of being located at hydraulic cylinder 30, carrying out the switching action of secondary valve 24, be fixed on the valve rod 22 of main valve 21 top, carry out the not shown air slide of the restoring action of main valve 21, be fixed on the valve rod 26 of secondary valve 24 top, carry out the air slide 29 of the restoring action of secondary valve 24, the storage air slide of main valve 21 and the air slide 29 of secondary valve 24, be formed for the housing 35 of the pneumatic spring chamber 36 of paying air pressure.

This exhaust-manifold 11, has represented to be applicable to the situation of two stroke uniflow scavenging diesel engine as an example, in this two stroke uniflow scavenging diesel engine, on cylinder sleeve sidewall, have scavenging port, and main valve 21 carries out exhaust and scavenging.

Promote valve rod 22 by the not shown oil hydraulic cylinder being moved by high-pressure and hydraulic to diagram below, carry out the valve events of opening of main valve 21.In addition, by being arranged on not shown air slide on valve rod 22 to diagram top pull-up valve rod 22, that carries out main valve 21 closes valve events (restoring action)., be formed at air pressure in the pneumatic spring chamber 36 of below of above-mentioned air slide and become the action source of closing valve events of main valve 21.

Multiple oil hydraulic cylinders 31 of being located at hydraulic cylinder 30 are moved by high-pressure and hydraulic, and air slide 29 is promoted to diagram top, carry out thus the switching action of secondary valve 24.In addition, by discharging the hydraulic pressure of oil hydraulic cylinder 31, by air slide 29, valve rod 26 is promoted to diagram below, carry out the restoring action of secondary valve 24., be formed at air pressure in the pneumatic spring chamber 36 of top of air slide 29 and become the action source of the restoring action of secondary valve 24.

As shown in Figure 2, Constant Low Temperature Facilities 14 is formed as with respect to the centre line L that the center O in the Constant Low Temperature Facilities 14 of the center line of the outlet 15a center of cryopumping passage 15 and relief opening 11a is linked up, the scrollwork shape that is asymmetrical shape.On the assigned position of Constant Low Temperature Facilities 14, set the starting point SP of this scrollwork.

Starting point SP is positioned at the position of slightly leaning on Constant Low Temperature Facilities 14 sides than the continuous setting unit 15b of a side of the entrance of Constant Low Temperature Facilities 14 and cryopumping passage 15, centered by center O in the Constant Low Temperature Facilities 14 of the center line of relief opening 11a, be located at some in the skew of scrollwork direction from the centre line L of cryopumping passage 15, be offset predetermined angular θ from centre line L to diagram left-hand rotation direction ₁position.

In this internal-combustion engine, opening valve mid-term to the combustion gas that import to the low temperature of Constant Low Temperature Facilities 14 during closing valve from cylinder via the relief opening 11a of exhaust-manifold 11 from main valve, with respect to the centre line L that the central link of the outlet 15a center of cryopumping passage 15 and Constant Low Temperature Facilities 14 is got up, watch from the diagram top of Fig. 2, be accompanied by anticlockwise strong vortex and flow into Constant Low Temperature Facilities 14 (rotating flow).

; Constant Low Temperature Facilities 14 is scrollwork shape; this scrollwork shape taking assigned position as starting point SP to the section area of the entrance of cryopumping passage 15, in more detail say from starting point SP to the section area of the continuous setting unit 15c of opposite side of cryopumping passage 15, expand gradually towards cryopumping passage 15 in the sense of rotation of combustion gas.In other words, Constant Low Temperature Facilities 14 is watched from the diagram top of Fig. 2, the scrollwork shape that its diameter of direction that is formed as turning right diminishes gradually.

Constant Low Temperature Facilities 14 from starting point SP to from the continuous setting unit 15c of cryopumping passage 15 Surface forming by different radius of curvature R 2, R3, R4, these radius of curvature are R4>R3>R2, from starting point SP to Constant Low Temperature Facilities 14 with the continuous setting unit 15c of the entrance of cryopumping passage 15, increase gradually and arrange continuously sleekly.

In addition, continuous setting unit 15b, the 15c of the entrance of Constant Low Temperature Facilities 14 and cryopumping passage 15 arrange respectively sleekly continuously with the curved surface of radius of curvature R 1, R5.For example, angle θ ₁be about 45 ° ~ 90 °, the radius of curvature R 2 ~ R4 that forms scrollwork shape is approximately 0.5 ~ 2.0 times of inner diameter D 01 of the outlet 15a of cryopumping passage 15.

Secondary valve 24 is straight cylinder shape, and its external diameter is slightly less than the relief opening 11a of exhaust-manifold 11, and the relief opening 2a of its internal diameter (secondary valve internal diameter) D1 and valve seat 2 is roughly the same.In addition, the diameter of the relief opening 11a of exhaust-manifold 11 is larger than the relief opening 2a of valve seat 2.The inner peripheral surface of secondary valve 24 is arranged on the outer circumferential face of valve rod 26 continuously by multiple tabular spokes (disc) 24a.The combustion gas of discharging via main valve 21 from cylinder 3 are through being discharged in hot room 12 between these spokes 24a.

At secondary valve 24, form the skirt section 24b of (diagram upper end) forward end (diagram lower end) undergauge from rear end at front end.External diameter (skirt section external diameter) the D2 frustum of a cone cylindrical shell shape (truncated cone shape) larger than the outer diameter D of front end 4 of 24bCheng rear end, skirt section, the diametric angle that outer circumferential face is the secondary valve 24 of straight cylinder shape is relatively θ ₂.In addition, the outer diameter D 2 of rear end is larger than the external diameter of secondary valve 24, and the outer diameter D 4 of front end is less than the inner diameter D of secondary valve 24 1.

The outer circumferential face of the rear end of skirt section 24b is formed as the face parallel with the outer circumferential face of secondary valve 24 that is straight cylinder shape, and the inner peripheral surface of the opening portion of front end is formed as the face parallel with the inner peripheral surface of secondary valve 24 that is straight cylinder shape.Therefore, the outer circumferential face of the front end of skirt section 24b is formed as being described angle θ with the inner peripheral surface of opening portion ₂rib (holding up), in this diesel engine, the outer diameter D of front end 4 is roughly the same with internal diameter (skirt section internal diameter) D3 of front end.

In addition, the external diameter of the front end of skirt section 24b forms slightly littlely than the relief opening 11a of exhaust-manifold 11, as shown in double dot dash line, the outer circumferential face of rear end can with the inner peripheral surface sliding contact of the relief opening 11a of exhaust-manifold 11.In addition, the front end that is the secondary valve 24 of straight cylinder shape arranges continuously in the substantial middle portion of the inner peripheral surface of skirt section 24b.

For example, diameter at the valve face 21a of main valve 21 is Dv, the secondary inner diameter D 1 of valve 24 and the ratio D1/Dv of Dv are about 0.9 ~ 1.2, and the outer diameter D 2 of 24b rear end, skirt section is about 1.0 ~ 1.3 with the ratio D2/Dv of Dv, and the inner diameter D 3 of the front end of skirt section 24b is about 0.7 ~ 1.0 with the ratio D3/Dv of Dv.

(or in Fig. 1 shown in double dot dash line) as shown in Figure 4, start out the initial stage (initial stage of exhaust) of valve at main valve 21, secondary valve 24 switches its position by air slide 29, skirt section 24b is inserted in the relief opening 11a of exhaust-manifold 11, and the inner peripheral surface sliding contact of the outer circumferential face of rear end and relief opening 11a, is communicated with cylinder 3 through the relief opening 2a of valve seat 2.

In addition, secondary valve 24 is communicated with cylinder 3 and hot room 12 through between tabular spoke 24a, meanwhile, and by the inaccessible Constant Low Temperature Facilities 14 of its cylindrical part.Thus, the combustion gas of the High Temperature High Pressure in cylinder 3 are discharged to hot room 12, from hot room 12 discharged to high-temperature exhaust air passage 13.The initial stage (initial stage of exhaust) that secondary valve 24 starts out valve at main valve 21 remains on the position shown in Fig. 4, the combustion gas of the High Temperature High Pressure in cylinder 3 discharged to hot room 12, from hot room 12 discharged to high-temperature exhaust air passage 13.

During the mid-term of driving valve to the later stage of main valve 21 (closing valve), air valve 29 boosts the position shown in Fig. 1 solid line by oil hydraulic cylinder 31, and secondary valve 24 is switched to Constant Low Temperature Facilities 14 sides.Thus, inaccessible hot room 12.In addition, Constant Low Temperature Facilities 14 is communicated with cylinder 3, and the interior remaining combustion gas of cylinder 3 (scavenging) are discharged to Constant Low Temperature Facilities 14 and cryopumping passage 15.These combustion gas are imported in Constant Low Temperature Facilities 14 swimmingly along the outer circumferential face of the inclination that is located at the skirt section 24b on valve 24 front ends.The combustion gas of discharging from cylinder 3 thus, are imported Constant Low Temperature Facilities 14 well.

As mentioned above, Constant Low Temperature Facilities 14 be from starting point SP to the continuous setting unit 15c of the entrance of cryopumping passage 15, the scrollwork shape expanding gradually at the sense of rotation section area of combustion gas, and be formed as round and smooth curved surface, so, the flow resistance that can significantly reduce the combustion gas in Constant Low Temperature Facilities 14, combustion gas flow to cryopumping passage 15 swimmingly.Thus, can not hinder the strong vortex being caused by the scavenging port of cylinder 3, can be being discharged to cryopumping passage 15 from cylinder 3 discharged to the combustion gas of Constant Low Temperature Facilities 14.Its result, can smooth and easy discharge and the combustion gas of the flow that matches of the section area of cryopumping passage 15, and scavenging efficiency significantly improves.

One example of the combustion gas flow in the Constant Low Temperature Facilities 14 shown in Fig. 3 presentation graphs 2 and cryopumping passage 15.Import to the combustion gas in Constant Low Temperature Facilities 14 from the cylinder 3 shown in Fig. 1 through the exhaust port 11a of exhaust-manifolds 11, mobile like that along the internal face 14a of scrollwork shape streamline A ~ H as shown by arrows, discharged to cryopumping passage 15.

The length of this streamline A ~ H represents the flow velocity of the combustion gas of this position.As shown in Figure 3, compared with the structure of the flow velocity of combustion gas and the exhaust gas separation device of the internal-combustion engine of the prior art shown in Figure 14, on the complete cycle of the exhaust port 11a of exhaust-manifold 11, be same, its result mean velocity is accelerated, and the discharge flow rate of combustion gas significantly increases.

In addition, as shown in Figure 5, above-mentioned hot room 12 is formed as being roughly symmetrical shape with respect to the centre line L 2 that the center O of the outlet 13a center of high-temperature exhaust air passage 13 and relief opening 11a and hot room 12 is linked up, and is provided for making two current plates 17,18 smoothly that flow of the combustion gas of discharging via main valve 21 from cylinder 3 at hot room 12.

As shown in Figure 4, current plate 17,18 is along axial (the diagram above-below direction) of hot room 12, along the discharge direction of the combustion gas of discharging from cylinder 3, and in the outlet 13a side of high-temperature exhaust air passage 13, is formed centrally in the centre line L 2 of high-temperature exhaust air passage 13.

Current plate 17 is the first current plate, as shown in Figure 5, be configured in the internal face 12a of hot room 12, and centered by the relief opening 11a of exhaust-manifold 11, be positioned at the opposition side of the outlet 13a of high-temperature exhaust air passage 13, as shown in Figure 4, roughly forming on whole height at hot room 12.

Current plate 18 is the second current plate, as shown in Figure 5, is formed on the internal face 12a of hot room 12, and centered by the relief opening 11a of exhaust-manifold 11 towards the outlet 13aCe center of high-temperature exhaust air passage 13.In addition, as shown in Figure 4, form to hanging down near the substantial middle height of hot room 12 from the upper wall surface of hot room 12.

As shown in Figure 5, the contrary side of the outlet 13a side internal face 12a of hot room 12 and high-temperature exhaust air passage 13, compared with outlet 13a side, the internal diameter of cylinder 3, more specifically say that the interval between the relief opening 11a of exhaust-manifold 11 is narrow, therefore, can not increase the height (length of centre line L 2 directions of high-temperature exhaust air passage 13) of (lengthening) current plate 17.

For this reason, current plate 17 forms than current plate 18 low (length of centre line L 2 directions of high-temperature exhaust air passage 13 is short), is formed as the degree of the roughly half of current plate 18.Current plate 18 forms than current plate 17 height (long in outlet 13a direction along centre line L 2) towards the outlet 13a side of high-temperature exhaust air passage 13.

The internal face 12a of the bi-side 17a of current plate 17 from front end towards hot room 12, expands formation to be for example mode of the circular-arc concave curved surface of radius of curvature R 11.Equally, the internal face 12a of the bi-side 18a of current plate 18 from front end towards hot room 12, expands formation to be for example mode of the circular-arc concave curved surface of radius of curvature R 21.

By the internal face 12a from front end towards hot room 12 forms in the mode that is circular-arc concave curved surface and expands bi-side 17a, the 18a of current plate 17,18 like this, thereby can make from cylinder 3 mobile smooth and easy discharged to the combustion gas of hot room 12.In addition, the internal diameter of hot room 12 is larger than the internal diameter of high-temperature exhaust air passage 13, and continuous setting unit 13c, the 13d of the entrance of hot room 12 and high-temperature exhaust air passage 13 become round and smooth curved surface.

For example, in the case of the internal diameter of the outlet 13a of high-temperature exhaust air passage 13 being made as to D02, the diameter of the valve face of the main valve 21 shown in Fig. 4 (valve surface of contact) 21a being made as to Dv, the passage internal diameter of secondary valve 24 is made as D1, the radius of curvature R 11 of the side 17a of current plate 17 is approximately 0.2 ~ 0.5 times of channel outlet diameter D02, and the radius of curvature R 21 of the side 18a of current plate 18 is the degree of approximately 0.3～1.0 times of channel outlet diameter D02.In addition, the ratio D1/Dv of the diameter Dv of the passage inner diameter D 1 of secondary valve 24 and the valve face of main valve 21 (valve surface of contact) 21a is about 0.9～1.2 degree.

As shown in Figure 4, make near the internal face 12a of the diagram downside entrance 12c of hot room 12 be convex curved surface to diagram top and bloat, at the interior formation bellying of hot room 12 12b.It is desirable that bellying 12b is formed as ring-type in the mode of the entrance 12c around hot room 12.But bellying 12b not necessarily must, to be formed as ring-type around the mode of entrance 12c entirety, also can only be formed on the internal face 12a of diagram downside of high-temperature exhaust air passage 13 sides.

In addition, the valve rod 26 that makes secondary valve 24 connect the underpart of the hydraulic cylinder 30 to its supporting arrange and be roughly obconic rectification part 27.The front end 27a of this rectification part 27 and the bellying 12b of hot room 12 outside in opposite directions, be formed as the concave curved surface 27b that be circular-arc concave curved surface corresponding with the convex curved surface of bellying 12b, extends towards secondary valve 24 undergauges towards a side of main valve 21 simultaneously.

Internal face 12a by near the diagram downside entrance 12c at hot room 12 arranges the bellying 12b being made up of convex curved surface, at the front end 27a of rectification part 27 in opposite directions with it, the concave curved surface 27b corresponding with the convex curved surface of this bellying 12b is set, thereby the front end 27a of the bellying 12b of hot room 12 and rectification part 27 moves jointly, by their interaction combustion gas from cylinder 3 discharged in hot room 12, then discharge swimmingly to high-temperature exhaust air passage 13.

Fig. 6 is the figure of the example flowing of the combustion gas in the hot room 12 shown in presentation graphs 5 and high-temperature exhaust air passage 13.The exhaust port 11a that passes through exhaust-manifolds 11 from cylinder 3 is discharged to the combustion gas in hot room 12, by 17a left and right, the bi-side approximate equality that is concave curved surface along current plate 17 separately flow, thereby can prevent mutual interference, flow to the direction of high-temperature exhaust air passage 13 along the internal face 12a of hot room 12.

Flow towards high-temperature exhaust air passage 13 along the internal face 12a of hot room 12 from the combustion gas of discharging between current plate 17 and current plate 18.In addition, flow to high-temperature exhaust air passage 13 in the mode of the bi-side 18a that is concavity curved surface along current plate 18 near the combustion gas of discharging the current plate 18 of hot room 12.But, because the length of centre line L 2 directions of bi-side 18a long (height), so separate to approximate equality in long distance by the both sides in centre line L 2, thus can prevent mutual interference, can flow swimmingly.

In Fig. 6, the length of streamline represents the flow velocity of the combustion gas of this position.From Fig. 6 also, can significantly improve the channel resistance of hot room 12 and high-temperature exhaust air passage 13, can eliminate near the delay of the combustion gas entrance of delay that the combustion gas in hot room 12 cause because circle refluxes or high-temperature exhaust air passage 13, the combustion gas that can discharge the flow matching with the minimum cross-sectional area of high-temperature exhaust air passage 13, exhaust efficiency significantly improves.

In addition, by the shape of hot room 12 is formed as with respect to the shape of the outlet 13a symmetry of high-temperature exhaust air passage 13, with respect to the shape of centre line L 2 symmetries of high-temperature exhaust air passage 13, can the combustion gas that import from cylinder 3 with respect to centre line L 2 both sides approximate equality be separately discharged to high-temperature exhaust air passage 13, act on mutually with above-mentioned current plate 17,18, can reduce the delay of the combustion gas in hot room 12.

Then, describe the another way of the invention of the structure of the exhaust gas separation device for implementing internal-combustion engine of the present invention in detail with reference to Fig. 7 to Figure 11.In addition, in Fig. 7 to Figure 11, for at the additional identical reference character of the identical parts of the parts shown in Fig. 1 to Fig. 6 and omit part explanation.

Internal-combustion engine shown in Fig. 7 is the two stroke uniflow scavenging diesel engine as an example, this diesel engine has: the main valve 21 that be arranged on the valve seat 2 of cylinder body 1, carries out exhaust, cryopumping passage 15 these two (multiple) exhaust passages that the high-temperature exhaust air passage 13 used of high-temperature gas extending in the Hou You of main valve 21 side branch via main valve 21 from cylinder 3 and cryogenic gas are used, are disposed in exhaust-manifold 11, switch the secondary valve 25 that flow of combustion gas to this high-temperature exhaust air passage 13 and cryopumping passage 15.In addition, with respect to the oil hydraulic cylinder 43 that secondary valve 25 is moved, arrange the hydraulic channel for driving them.In this diesel engine, carry out exhaust from 21 of main valves.

As shown in Figure 7, the cylindrical shape of hydraulic cylinder 40 moving for carrying out the switching of secondary valve 25, is formed by outside hydraulic cylinder 41 and inner side hydraulic cylinder 42.Outside hydraulic cylinder 41 is has round-ended cylinder shape, the cylindrical shape of inner side hydraulic cylinder 42.At bottom center and the hydraulic cylinder 42 center, inner side of outside hydraulic cylinder 41, run through hole 41a, the 42a of the valve rod 26 that is provided with valve rod 22, the secondary valve 25 of inserting main valve 21.

Outside hydraulic cylinder 41 vertically runs through vertically and is provided with hydraulic channel 61 from upper-end surface 41d, the top of (outer circumferential face) 41b and run through hydraulic channel 62 is set at radial direction in side.One end (front end) of hydraulic channel 62 is communicated with the top of hydraulic channel 61, and the other end becomes supply and the exhaust port of hydraulic pressure at outer circumferential face 41b opening.In addition, the opening end of hydraulic channel 61 (diagram upper end) is by shutoff.

Near the bottom of outer circumferential face 41b, run through hydraulic channel 63 is set at radial direction, the lower ending opening of the hydraulic channel 61 of way Vertical direction is communicated with therein, and one end (front end) is at the inner peripheral surface 41c of this outside hydraulic cylinder 41 opening.These hydraulic channels 61,62,63 form by Drilling operation (machining).In addition, the opening end of the outer circumferential face 41b of hydraulic channel 63 is by shutoff.

Form the 3rd hydraulic channel by these hydraulic channels 61,62,63.Hydraulic channel 61,62,63 is short and simple in structure, the overlap (crimping) or the cutting swarf (smear metal) that can easily remove machining (Drilling operation) time, produce, and reprocessing is easy.

In addition, also the hydraulic channel 62 on above-mentioned vertical hydraulic channel 61 and top can be set and near the hydraulic channel 63 in bottom is only set, make the outer circumferential face 41b side opening of this hydraulic channel 63 and form supply and the exhaust port of hydraulic pressure, using this hydraulic channel as the 3rd hydraulic channel.By such setting, can make hydraulic channel 63, the 3rd hydraulic channel is extremely short and structure is also extremely simple, thereupon, the overlap (crimping) or the cutting swarf (smear metal) that can more easily and well remove machining (Drilling operation) time, produce, reprocessing is easier.

As shown in Fig. 8 and Figure 10, inner side hydraulic cylinder 42 the outer concentric of the hole at upper-end surface and center 42a and on same circumference for example, along circumferentially equally spaced forming multiple, three secondary valve oil hydraulic cylinders 43.

These secondary valve oil hydraulic cylinders 43 have been formed as the end, form in hydraulic channel 65(Fig. 8 and only illustrate one near bottom).Near the inner peripheral surface opening of one end of this hydraulic channel 65 bottom of secondary valve oil hydraulic cylinder 43, the other end at the outer circumferential face 42b(of this inner side hydraulic cylinder 42 with reference to Fig. 7) opening, be radially and form along radial direction.

This hydraulic channel 65 is also formed by Drilling operation (machining).This hydraulic channel 65 is extremely short and structure is also simple, the overlap (crimping) producing can easily remove Drilling operation time or cutting swarf (smear metal), and reprocessing is easy.In addition, this hydraulic channel 65 becomes the first hydraulic channel.

In the lower end of the outer circumferential face 42b of inner side hydraulic cylinder 42, on complete cycle, form the recess 45 of ring-type.In addition, the other end of above-mentioned hydraulic channel 65 is at the bottom surface opening of the recess 45 of this ring-type.Thus, the bottom of each secondary valve oil hydraulic cylinder 43 is communicated with recess 45.

Inner side hydraulic cylinder 42 as shown in Fig. 8 and Figure 10, at upper-end surface and secondary valve oil hydraulic cylinder 43 on same circumference and edge circumferentially equally spaced form multiple, for example three oil hydraulic cylinders 46.These three oil hydraulic cylinders 46 are alternately configuration between three secondary valve oil hydraulic cylinders 43, forms for example, than secondary valve oil hydraulic cylinder 43 shallow (degree of depth of 1/3 degree) (with reference to Fig. 8).As shown in figure 11, the cylinder sleeve of oil hydraulic cylinder 46 utilizes bolt 48 to be fixed on the upper-end surface of inner side hydraulic cylinder 42.

As shown in Figure 8, at the outer circumferential face 42b of inner side hydraulic cylinder 42, in the position corresponding with the bottom of oil hydraulic cylinder 46, on complete cycle, form annular slot 66.In addition, near the bottom of these oil hydraulic cylinders 46, form hydraulic channel 67(Fig. 8 and only illustrate one).This hydraulic channel 67 is radially and forms at radial direction, near the inner peripheral surface opening of one end bottom of oil hydraulic cylinder 46, and the other end is at the bottom surface of annular slot 66 opening.Thus, the bottom of each oil hydraulic cylinder 46 is communicated with annular slot 66.

This hydraulic channel 67 is also formed by Drilling operation (machining).This hydraulic channel 67 is same with hydraulic channel 65 extremely short and structure is also simple, the overlap (crimping) producing can easily remove Drilling operation time or cutting swarf (smear metal), and reprocessing is easy.

As shown in Figure 8, at outside hydraulic cylinder 41, run through hydraulic channel 68 is set in the position corresponding with the annular slot 66 of inner side hydraulic cylinder 42, be communicated with this annular slot 66.

In addition, inner side hydraulic cylinder 42 is embedded in outside hydraulic cylinder 41 via the liquid-tight formula of sealed member, as shown in Figure 9, and by the fastening exhaust-manifold 11 that is fixed on of bolt 75.In addition, between the recess 45 of ring-type and the inner peripheral surface in opposite directions of outside hydraulic cylinder 41 of the underpart of inner side hydraulic cylinder 42, form the hydraulic channel 69 of ring-type.The hydraulic channel 69 of this ring-type becomes the second hydraulic channel.Like this, formed hydraulic cylinder 40.

As shown in Figure 8, butt below each front-end face of the piston 44 of each secondary valve oil hydraulic cylinder 43 (diagram upper-end surface) and secondary valve air slide 37.Form and make secondary valve 25 switch the secondary valve COMM communication 51 of action by these three secondary valve oil hydraulic cylinders 43.Secondary valve COMM communication 51 is carried out multiple secondary valve oil hydraulic cylinder 43 circumferentially uniformly-spaced configuration of edge on same circumference of the switching action of secondary valve 25 by handle, thereby can resist the impartial firmly secondary valve air slide 37 that promotes in powerful air pressure ground.In addition, because be along circumferentially uniformly-spaced configuration, so can prevent the undesirable condition such as distortion of secondary valve air slide 37.

As shown in Figure 8, butt below each front-end face (above diagram) of the piston 47 of each oil hydraulic cylinder 46 and secondary valve air slide 37.Form the secondary valve 25 of restriction by these three oil hydraulic cylinders 46 and carry out the dead-center position control gear 52 of lower position (dead-center position) of restoring action while declining.Dead-center position control gear 52 arranges multiple firmly oil hydraulic cylinders 46 by the secondary valve air slide 37 of relative strong construction and forms, and can make the secondary valve air slide 37 that is closed valve events (restoring action) by air pressure brute force stop reliably.

In addition, by multiple oil hydraulic cylinders 46 of dead-center position control gear 52 and the multiple secondary valve oil hydraulic cylinder 43 of the switching action of carrying out secondary valve 25 are configured on same circumference, and alternately configure with these secondary valve oil hydraulic cylinders 43, thereby can be same with the multiple secondary valve oil hydraulic cylinder 43 that the switching of carrying out secondary valve 25 is moved, bear equably the strong pressing force of secondary valve air slide 37, in addition, also can prevent the unfavorable condition such as distortion of secondary valve air slide 37.

Thus, can make secondary valve air slide 37 stop well, can carry out high-precision positioning control to the dead-center position of secondary valve 25 (lower position).Therefore, can make secondary valve 25 stop at reliably dead-center position (lower position) even the lower end surface 25e of the underpart 25d of secondary valve 25 stops at reliably and the upper-end surface 2a of the valve seat 2 of main valve 21 between retain the position of gapped (clearance) δ.

Secondary valve 25 its underpart 25d are straight cylinder shape, can be formed as straight in the inner peripheral surface 11c of underpart 11b of exhaust-manifold 11 of cylindrical shape slide axially.Therefore, the straight underpart 25d of secondary valve 25 slides and switches swimmingly action on one side at the inner peripheral surface 11c of exhaust-manifold 11 on one side.Thus, the lower end surface 25e that can prevent the underpart 25d of secondary valve 25 takes a seat (conflict) at the upper-end surface 2a of the valve seat 2 of main valve 21, can prevent that secondary valve 25 from damaged or distortion occurring.

The supply and the exhaust port that become hydraulic pressure at the opening portion of the outer circumferential face 41b opening of the hydraulic channel 62 of the outside hydraulic cylinder 41 shown in Fig. 7, be connected with not shown hydraulic power, and the hydraulic pressure of supplying with high pressure drives secondary valve COMM communication 51.In addition, the hydraulic channel 68 of the outside hydraulic cylinder 41 shown in Fig. 8 becomes supply and the exhaust port of hydraulic pressure at the opening portion of outer circumferential face 41b opening, be connected with not shown hydraulic power via hydraulic channel 70.

This dead-center position control gear 52 is by the hydraulic pressure P that is disposed in hydrostatic sensor 55 in hydraulic channel 68 and detects oil hydraulic cylinder 46, when the hydraulic pressure detecting at hydrostatic sensor exceedes authorized pressure, the lower end surface 25e that the secondary valve device for preventing breakage 76 being connected with hydrostatic sensor 55 is judged as secondary valve 25 (conflict) the upper-end surface 2a at the valve seat 2 of main valve 21 that takes a seat, according to the level of checkout value now, that carries out warning light lights stopping of (generation of warning) or internal-combustion engine.Thus, can prevent more reliably damaged the or distortion of secondary valve 25.

Shown in Fig. 7 and Fig. 8, in the time that main valve 21 closes valve, the secondary valve oil hydraulic cylinder 43 of secondary valve COMM communication 51 is shunk back, and by this pair valve oil hydraulic cylinder 43 and dead-center position control gear 52, secondary valve 25 is remained on to dead-center position (lower position).In addition, open slightly the exhaust initial stage of valve at main valve 21, secondary valve 25 still remains on dead-center position (lower position), the exhaust gas of high temperature between each rib 25c as shown by the arrows in Figure 7 like that discharged to high-temperature exhaust air passage 13.

As shown in Figure 9, in the time of the driving valve and continue to carry out through the exhaust initial stage of main valve 21, the secondary valve oil hydraulic cylinder 43 of secondary valve COMM communication 51 extends, secondary valve air slide 37 is boosted to diagram top, secondary valve 25 to cryopumping passage 15 sides switch, remaining exhaust gas as shown by arrows like that discharged to these cryopumping passage 15 sides.

In the time that exhaust finishes, the secondary valve oil hydraulic cylinder 43 of secondary valve COMM communication 51 is shunk back, and promotes to continue secondary valve 25 by secondary valve air slide 37 to diagram below simultaneously.In addition, as shown in Figures 7 and 8, piston 47 butts of the oil hydraulic cylinder 46 of secondary valve air slide 37 and dead-center position control gear 52, its decline is restricted, and can reliably secondary valve 25 be remained on to dead-center position (lower position).

In addition, above-mentioned discharge valve apparatus 10, represented to be applicable to the situation of the two stroke uniflow scavenging diesel engine with secondary valve as an example, but the structure of the exhaust gas separation device of internal-combustion engine of the present invention is also applicable to have other internal-combustion engines of secondary valve, such as four-stroke diesel engine etc.In this four-cycle diesel, for example main valve is used in air-breathing and exhaust both sides, and secondary valve is used in from cylinder and switches via the air intake passage of main valve branch extension and the switching of exhaust passage.

Industrial applicibility

The structure of the exhaust gas separation device of internal-combustion engine of the present invention, be not limited to the structure of the diesel exhaust gas gas fractionation unit of an above-mentioned mode of execution, can implement for the structure of the exhaust gas separation device of various internal-combustion engines or general hydraulic equipment.

Claims

1. the structure of the exhaust gas separation device of an internal-combustion engine, possess: the main valve (21) that carries out air-breathing and/or exhaust, carry out the multiple air-breathing and/or exhaust passage (13 of extending via described main valve branch from cylinder (3), 15) the secondary valve (25) that switching is switched, carry out the main valve oil hydraulic cylinder (28) of opening valve events of described main valve, carry out the multiple secondary valve oil hydraulic cylinder (43) of the switching action of described secondary valve, carry out the main valve air slide (23) of the restoring action of described main valve, carry out the secondary valve air slide (37) of the restoring action of described secondary valve, drive the air chamber (29) of described main valve air slide and described secondary valve air slide, it is characterized in that also possessing: be disposed in be formed with the hydraulic cylinder (40) of described multiple secondary valve oil hydraulic cylinders and limit the lower position of described secondary valve air slide and control described secondary valve zero point restriction site hydraulic type dead-center position control gear (52), when the hydrostatic sensor (55) that the hydraulic pressure of described dead-center position control gear detects and the described hydraulic pressure detecting at described hydrostatic sensor exceed authorized pressure, produce the secondary valve device for preventing breakage (76) of reporting to the police and/or stopping described internal-combustion engine to being supplied to.

2. the structure of the exhaust gas separation device of internal-combustion engine as claimed in claim 1, it is characterized in that, described dead-center position control gear (52) forms by multiple oil hydraulic cylinders (46) being set opposite to each other at described hydraulic cylinder (40) and described secondary valve air slide (37).

3. the structure of the exhaust gas separation device of internal-combustion engine as claimed in claim 2, it is characterized in that, described multiple oil hydraulic cylinders (46) of described dead-center position control gear (52) are circumferentially uniformly-spaced configuration of edge on same circumference, and connection is formed with hydraulic channel (66,67,68).

4. the structure of the exhaust gas separation device of internal-combustion engine as claimed in claim 2, it is characterized in that, carry out described multiple secondary valve oil hydraulic cylinder (43) circumferentially uniformly-spaced configuration of edge on same circumference of the switching action of described secondary valve (25), described multiple oil hydraulic cylinders (46) of described dead-center position control gear (52) configure on same circumference and alternately with described multiple secondary valve oil hydraulic cylinders.

5. the structure of the exhaust gas separation device of internal-combustion engine as claimed in claim 3, it is characterized in that, carry out described multiple secondary valve oil hydraulic cylinder (43) circumferentially uniformly-spaced configuration of edge on same circumference of the switching action of described secondary valve (25), described multiple oil hydraulic cylinders (46) of described dead-center position control gear (52) configure on same circumference and alternately with described multiple secondary valve oil hydraulic cylinders.

6. the structure of the exhaust gas separation device of the internal-combustion engine as described in any one in claim 1 to 5, it is characterized in that, described secondary valve (25) is straight cylinder shape, can slide axially with the inner peripheral surface of the exhaust-manifold (11) that is formed as straight interior cylindrical shape, and lower end surface (25e) retains gap (δ) in opposite directions in the upper-end surface (2a) of the valve seat (2) that closes valve position and described main valve (21).