CN203702323U - Air inlet device of internal combustion engine - Google Patents

Abstract

The utility model provides an air inlet device of an internal combustion engine. By means of the air inlet device, even though a partition board in an air inlet passage forms a strip at an air inlet end, the rigidity can be guaranteed easily, and tumble with strong eddy flow can be generated. The air inlet passage (P) is locallydivided into an upper air inlet passage (Up) and a lower air inlet passage (Lp) by the partition board (60);according to the air inlet device of the internal combustion engine, an inlet air distributing valve (65) arranged in the downstream position of a throttle valve (22) and theupstream position of the partition board (60) is used for controlling inlet air flowing in the upper air inlet passage (Up) and the lower air inlet passage (Lp), the partition board (60) comprises an air inlet pipe side partition board (61) formed on an air inlet pipe (20) and an air inlet port partition board (62) formed in an air inlet port (44), and a downstream end part (61b) of the air inlet pipe side partition board (61) and an upstream end part (62a) of the air inlet port partition board (62) are connected in a vertical coinciding manner.

Description

The air inlet system of internal-combustion engine

Technical field

The utility model relates to a kind of air inlet system of the internal-combustion engine that is equipped on vehicle.

Background technique

Exist in the following structure that forms air inlet system, that is, and at the low load area of internal-combustion engine, in order to seek to reduce combustion efficiency, in firing chamber, make the air inlet that is inhaled into produce and roll stream, and fuel is transported to the surrounding of ignition spark plug on top, firing chamber and layering, thereby improve combustion efficiency.

Direction that the intake valve port of air inlet port and exhaust port end face from the firing chamber of cylinder head separates towards each other with exhaust valve port is bending and extend, this air inlet port in the air inlet of firing chamber guiding, flow into towards exhaust side the exhaust side that drops to cylinder thorax on one side on one side from approaching the air inlet that the central part of side direction firing chamber, inside edge of cylinder axis (central shaft of cylinder thorax) of intake valve port sucks, afterwards, make air-flow bending and rise to air inlet side along piston-top surface, thereby forming the so-called stream that rolls.

Therefore, there is an example (with reference to patent documentation 1) of following air inlet system, in order to increase the ratio of the air inlet that the inside edge side of cylinder axis from approaching intake valve port sucks, utilize next door that the interior separation of air inlet port is become to upper and lower path, the air intake control valve of the switching of below path is carried out in the upstream side setting of next door, path below closing after internal-combustion engine just starts, thereby make the mobile air inlet of path above air inlet port from as above the inside edge side of intake valve port of prolongation of path be inhaled into, produce eddy current strong roll stream.

Patent documentation 1: TOHKEMY 2008-151078 communique

In the air inlet system of patent documentation 1, insert or be integrally formed the tubular passage portion of ports having liner at the upstream side of air inlet port, and form next door in the passage portion of this port liner.

The downstream side of next door from passage portion to air inlet port is outstanding very greatly.

Because next door is outstanding very greatly from passage portion, so owing to being difficult to guarantee rigidity, there is restriction aspect overhang, as shown in accompanying drawing Fig. 1 of patent document 1, the downstream in next door is positioned at the position of quite leaning on front of the suction valve of air inlet port.

Therefore, stream and the mobile air inlet of the upside path in the next door of the air inlet port downstream through next door is rolled in generation, cause just entering before firing chamber diffusion downwards, make to reduce from the air inlet of the side direction firing chamber, inside edge of intake valve port, thus be difficult to produce eddy current strong roll stream.

Model utility content

The utility model is made in view of the above problems, object is to provide a kind of air inlet system of internal-combustion engine, even if being formed as the dividing plate in inlet air pathway strip in air inlet port, it also can easily guarantee rigidity, and approach the downstream of firing chamber due to dividing plate is extended to, thus can produce eddy current strong roll stream.

In order to achieve the above object, the air inlet system of the internal-combustion engine of first aspect model utility, between the upper end face (Japanese: Top face) 41 of the end face (Japanese: courtyard face) of its piston 25 in the cylinder thorax 16b that is entrenched in sliding freely cylinder block 16 and the cylinder head 17 relative with this end face, form combuster 40, direction that each air inlet port 44 and exhaust port 45 separate with exhaust valve port 43 towards each other from the intake valve port 42 of from end face opening to described cylinder head 17 described is bending and be formed extended at both sides, form to have with suction tude 20 at air inlet port 44 and be connected and continuous inlet air pathway P, be provided with throttle valve 22 in described suction tude 20, described inlet air pathway P is separated into the downside inlet air pathway Lp of the upside inlet air pathway Up of the central part by firing chamber 40 and the peripheral part by firing chamber 40 partly by dividing plate 60, in the downstream of described throttle valve 22, utilization is arranged on the air inlet distributing valve 65 of upstream of described dividing plate 60 to controlling at described upside inlet air pathway Up and the mobile air inlet of described downside inlet air pathway Lp, the air inlet system of described internal-combustion engine utilizes inlet control mechanism 71 to drive and controls described air inlet distributing valve 65, the air inlet system of described internal-combustion engine is characterised in that, described dividing plate 60 forms by being formed at the suction tude side dividing plate 61 of described suction tude 20 and the air inlet port side dividing plate 62 being formed in air inlet port 44, the downstream end 61b of described suction tude side dividing plate 61 self links with end, the upstream 62a of described air inlet port side dividing plate 62 with overlapping.

Second aspect model utility is characterised in that, in the described upside inlet air pathway Up side of described suction tude 20, mode with the downstream side burner oil towards described upside inlet air pathway Up arranges sparger 23, the link above of end, the upstream 62a of the downstream end 61b of described suction tude side dividing plate 61 and described air inlet port side dividing plate 62 with overlapping.

Third aspect model utility is characterised in that, described sparger 23 is configured to, the downstream side burner oil towards described air inlet port side dividing plate 62 with linking department 61b, the 62a of described suction tude side dividing plate 61.

Fourth aspect model utility is characterised in that, described suction tude side dividing plate 61 is formed by resin, and the downstream end 61b of described suction tude side dividing plate 61 has the extruding force crimping producing because of resiliently deformable and lays equal stress on and be combined on end, the upstream 62a of described air inlet port side dividing plate 62.

The 5th aspect model utility is characterised in that, the downstream end 61b of described suction tude side dividing plate 61 is more outstanding and enter in inlet end mouth 44 than the downstream open end of described suction tude 20.

According to the air inlet system of the internal-combustion engine of first aspect model utility, be formed at the suction tude side dividing plate 61 of suction tude 20 and be formed at the air inlet port side dividing plate 62 in air inlet port 44 because dividing plate 60 is split into, and the downstream end 61b of suction tude side dividing plate 61 self links with end, the upstream 62a of air inlet port side dividing plate 62 with overlapping, so suction tude side dividing plate 61 and air inlet port side dividing plate 62 be each other from suction tude 20 and air inlet port 44 is outstanding but overhang is very little, thereby can easily guarantee rigidity.

Therefore, can make air inlet port side dividing plate 62 extend to the downstream that approaches firing chamber, on the way can spread hardly and be directed near intake valve port in the mobile air inlet of upside inlet air pathway Up, entering firing chamber from the inside edge side of intake valve port, thus can produce eddy current strong roll stream.

According to the air inlet system of the internal-combustion engine of second aspect model utility, because the described upside inlet air pathway Up side in suction tude 20 arranges sparger 23 in the mode of the downstream side burner oil towards described upside inlet air pathway Up, and the link above of end, the upstream 62a of the downstream end 61b of suction tude side dividing plate 61 and air inlet port side dividing plate 62 with overlapping, so the fuel being sprayed by sparger 23 is difficult to immerse the coincidence face of linking department 61b, 61a, can prevent that fuel is to downside inlet air pathway Lp seepage.

According to the air inlet system of the internal-combustion engine of third aspect model utility, because sparger 23 is the downstream side burner oil with linking department 61b, the 62a of suction tude side dividing plate 61 towards air inlet port side dividing plate 62, so the burner oil of sparger 23 can be to downside inlet air pathway Lp seepage, in addition, because fuel is ejected into the air inlet port side dividing plate 62 that temperature is high, so can suppress the liquefaction of fuel.

According to the air inlet system of the internal-combustion engine of fourth aspect model utility, lay equal stress on and be combined in end, the upstream 61a of air inlet port side dividing plate 62 because there is the extruding force crimping producing because of resiliently deformable for the downstream end 61b of the suction tude side dividing plate 61 that become by resin-shaped, so do not use joint compound etc., can make the downstream end 61b of suction tude side dividing plate 61 and end, the upstream 62a of air inlet port side dividing plate 62 fluid-tight engagement link simply, make workability good.

According to the air inlet system of the internal-combustion engine of the 5th aspect model utility, because suction tude side dividing plate 61 is to make downstream end 61b more outstanding and enter the structure in inlet end mouth 44 than the downstream open end of suction tude 20, so in the time being assembled into tracheae 20, can be take the downstream end 61b of the suction tude side dividing plate 61 more outstanding than the downstream open end of suction tude 20 as benchmark the visual time relatively contraposition of end, upstream 62a with air inlet port side dividing plate 62, and be installed into tracheae 20, make workability good.

Accompanying drawing explanation

Fig. 1 is the right side view that carries the motor bike of the internal-combustion engine of the utility model one mode of execution.

Fig. 2 is the right side cross-sectional view of this internal-combustion engine.

Fig. 3 is the plan view of cylinder block.

Fig. 4 is the worm's eye view of cylinder head.

Fig. 5 is the explanatory drawing of the upper end face of firing chamber.

Fig. 6 is the sectional view of the major component of the internal-combustion engine under low load condition.

Fig. 7 is VII-VII line sectional view of Fig. 6.

Fig. 8 is VIII-VIII line sectional view of Fig. 6.

Fig. 9 is the stereogram of air inlet distributing valve.

Figure 10 is the X-X line sectional view of Figure 13.

Figure 11 be the aperture φ that represents air inlet distributing valve with respect to the control of throttle valve opening θ with roll stream than the plotted curve of the variation of Rt.

Figure 12 is the sectional view of the major component of the internal-combustion engine under middle load condition.

Figure 13 is the sectional view of the major component of the internal-combustion engine under high load condition.

Figure 14 is the exploded perspective view of the air inlet distributing valve of variation.

Figure 15 is the sectional view that is equivalent to Figure 10 of the example that uses this air inlet distributing valve.

Figure 16 be other mode of executions air inlet distributing valve aperture φ with respect to the control of throttle valve opening θ with roll stream than the plotted curve of the variation of Rt.

Description of reference numerals

1 motor bike; 2 vehicle frames; 10 internal-combustion engines; 11 crankcases; 12 bent axles; 13 main shafts; 14 countershafts; 16 cylinder block; 16b cylinder thorax; 17 cylinder head; 18 valve mechanism cover; 19 connecting pipes; 20 suction tude; 21 throttle valve bodys; 22 throttle valve; 23 spargers; 24 air-strainer; 25 pistons; 26 connecting rods; 30 active valve mechanisms; 31 camshafts; 32e, 32i pitman arm shaft; 33i intake rocker; 33e exhaust rocker arm; 34i, 34e valve guiding element; 40 firing chambers; End face on 41; 42 intake valve ports; 42a protuberance; 43 exhaust valve ports; 44 air inlet ports; 45 exhaust ports; 46 suction valves; 46p umbrella portion; 46pf end face; 46s air inlet valve lever; 47 outlet valves; 48 spark-plug holes; 51 arch recesses; 52 press sections; 53 guiding walls; 55 cut round surface; 56 pistons cut face; 60 dividing plates; 61 suction tude side dividing plates; End, 61a upstream; 61b downstream end; 62 air inlet port side dividing plates; End, 62a upstream; 62b downstream end; 65 air inlet distributing valves; Cv rotation centerline; 65d cuts recess; 66 running shafts; 67 tabular valve bodies; 67a cardinal extremity edge; 68 screws; 70 ECU; 71 inlet control mechanisms; 72 motor drive mechanisms; 80 air inlet distributing valves; 81 running shafts; 81a, 81b cut recess; 81s grooving; 82 tabular valve bodies; 82,83 pipe type rivets; P inlet air pathway; Cp path center line; Up upside inlet air pathway; Lp downside inlet air pathway; Mp via intermedia

Embodiment

Below, based on Fig. 1 to Figure 13, the utility model one mode of execution is described.

Fig. 1 is the unitary side view that carries the motor bike 1 of the internal-combustion engine 10 of present embodiment.

The vehicle frame 2 of this motor bike 1 is bent downwardly pairing left and right body frame 2b, 2b and forms steep rake 2ba, 2ba from head tube 2a rearward extends, and its underpart is the forwards bending of く shape until underpart.

In addition, pairing left and right decline frame 2c, 2c from head tube 2a with the steep angle that tilts downwards, and extend substantially in parallel with the steep rake 2ba of body frame 2b under side-looking.

Vehicle seat track 2d, 2d rearward extend from the steep rake 2ba of body frame 2b, 2b, the top of 2ba, with back stay 2e, 2e supporting saddle guide rail 2d, the 2d of the central part of this vehicle seat track 2d, 2d and the bottom link of steep rake 2ba, 2ba.

On vehicle frame 2 as above, there is front fork 3 at head tube 2a pivot suspension, be supported with front-wheel 4 at its lower end axle, the back vent 5 that front end axle is bearing in the pivot plate 2f that is arranged at body frame 2b, 2b bottom rearward extends, axle is supported with trailing wheel 6 in its back-end, between the rear portion of back vent 5 and the central part of vehicle seat track 2d, 2d, rear portion buffer 7 is installed.

At the added fuel tank 8 that is provided with of body frame 2b, 2b, at the rear of fuel tank 8, vehicle seat 9 supports and is arranged on vehicle seat track 2d, 2d.

The internal-combustion engine 10 that is equipped on vehicle frame 2 is SOHC type bivalve monotubular quartastroke engines, and bent axle 12 points to width of the carbody direction with respect to car body, and under the attitude that erects leaning forward a little of inflator by suspension.

The crankcase 11 that rotates the bent axle 12 of ground axle suspension internal-combustion engine 10 freely forms change gear mechanism 15 being disposed between the main shaft 13 at rear of bent axle 12 and countershaft 14, countershaft 14 is output shafts, between countershaft 14 and the running shaft of trailing wheel 6, set up chain (not shown), this chain is to trailing wheel 6 transferring power.

With reference to Fig. 2, on crankcase 11, one casting cylinder liner 16L made of iron be cast in this cylinder block 16, cylinder head 17 via packing ring overlap cylinder block 16 above.Cylinder block 16 is coupled to one by stud bolt, the top of valve mechanism cover 18 coating gas cylinder caps 17 with cylinder head 17.

Overlap cylinder block 16 above of crankcase 11, cylinder head 17, valve mechanism cover 18 to extend upward (with reference to Fig. 1, Fig. 2) the attitude leaning forward a little from crankcase 11.

Suction tude 20 is rearward extended from the cylinder head 17 erecting that leans forward a little of the internal-combustion engine 10 that is mounted in as described above vehicle frame via connecting pipe 19, be provided with the butterfly type throttle valve body 21 of built-in throttle valve 22 in suction tude 20, and sparger 23 is installed, but also is provided with air inlet distributing valve 65 described later.

The air-strainer 24 linking with the rear end of this suction tude 20 is configured in the space being surrounded by body frame 2b, vehicle seat track 2d, back stay 2e (with reference to Fig. 1) under side-looking.

In addition, the outlet pipe that forwards extends from cylinder head 17 27 links with baffler 28, and this baffler 28 is bending downwards, and rearward bending, along the lower surface of crankcase 11 by rear and right side be configured in the right side of trailing wheel 6.

With reference to Fig. 2, crankcase 11 is cut apart by left and right, the underpart of cylinder liner 16L is embedded in the opening on the mating face that is formed on left and right crankcase and cylinder block 16 leans forward a little and outstanding upward, piston 25 reciprocatingly slides in the cylinder thorax 16b of the inside that is entrenched in freely this cylinder liner 16L, connecting rod 26 connects between the wrist pin 25p of piston 25 and the crankpin 12p of bent axle 12, thereby forms crank mechanism.

Between the upper end face 41 of the end face 25t of the piston 25 sliding and the cylinder head 17 relative with this end face 25t, form firing chamber 40 in the cylinder thorax 16b of cylinder block 16.

In cylinder head 17, on upper end face 41 with respect to being that cylinder axis C is positioned at each intake valve port 42 of opposite location and exhaust valve port 43 each other in the face of offering on 40 ground, firing chamber as the central shaft of cylinder thorax 16b, and the direction bending that separates towards each other with exhaust valve port 43 from intake valve port 42 respectively with exhaust port 45 of air inlet port 44 being formed extended at both sides.

Air inlet port 44 rearward extends from intake valve port 42, is communicated with suction tude 20 via connecting pipe 19, and exhaust port 45 links with outlet pipe 27.

Be mounted to one and be supported on sliding freely respectively the suction valve 46 of valve guiding element 34i, 34e and active valve mechanism 39 above that outlet valve 47 is arranged on cylinder head 17 drives with cylinder head 17 is chimeric, make the intake valve port 42 of air inlet port 44 and the exhaust valve port of exhaust port 45 43 and bent axle 12 rotary synchronous open and close.

With reference to Fig. 2, active valve mechanism 30 is on cylinder head 17, to make a camshaft 31 point to left and right directions and the active valve mechanism of the SOHC type internal-combustion engine that supported by axle, inclination fore-and-aft direction at camshaft 31 is supported with pitman arm shaft 32e, 32i, pitman arm shaft 32i in the wings swings the central authorities of ground axle suspension intake rocker 33i freely, and pitman arm shaft 32e forwardly swings the central authorities of ground axle suspension exhaust rocker arm 33e freely.

The intake cam protuberance of one end of intake rocker 33i and camshaft 31 joins, the other end is via adjusting screw and being joined by the upper end of the valve rod 46s of spring energized suction valve 46, the exhaust cam protuberance of one end of exhaust rocker arm 33e and bent axle 31 joins, the other end is via adjusting screw and being joined by the upper end of the valve rod 47s of spring energized outlet valve 47, by the rotation of camshaft 31, intake rocker 33i and exhaust rocker arm 33e are swung and driven for opening and closing suction valve 46 and outlet valve 47.

Fig. 3 is the plan view of cylinder block 16, runs through the rectangular opening of the chain chamber 16c that the chain that is provided with the circular hole of cylinder thorax 16b and feeds to active valve mechanism 30 transferring power passes on the mating face 16f engaging with cylinder head 17.

Fig. 4 is the worm's eye view of the cylinder head 17 that overlaps with cylinder block 16, on the mating face 17f relative with the mating face 16f of cylinder block 16, the upper end face 41 of firing chamber 40 forms on spill ground accordingly with cylinder thorax 16b, and runs through and be formed with the chain chamber 17c being communicated with accordingly with chain chamber 16c.

The circular open edge 41s of the upper end face 41 of the firing chamber 40 of the mating face 17f of cylinder head 17 is consistent with the circular hole of cylinder thorax 16b.

Offer the intake valve port 42 in large footpath at the rear side of upper end face 41, offer the exhaust valve port 43 slightly less than the diameter of intake valve port 42 in the front side of upper end face 41.

In addition, run through at upper end face 41 the outstanding spark-plug hole 48 of front end being provided with for ignition spark plug (not shown).

Fig. 5 is the firing chamber 40 along the end on observation cylinder head 17 of cylinder axis C,, along cylinder axis to the figure shown in looking, with reference to this Fig. 5, intake valve port 42 along cylinder axis to and to apparent time, than circular upper end face edge of opening 41s corresponding to the circular hole with cylinder thorax 16b of the upper end face 41 of firing chamber 40 biasing highlightedly more laterally, intake valve port 42 has the part shown in the loose point of protuberance 42a(Fig. 5 of the crescent shape outstanding from upper end face edge of opening 41s).

If the opening girth of protuberance 42a is the ratio of covering (ス キ Application グ cuts and closes) Rm with respect to the ratio of the all-round length of opening of the edge of opening 42s of intake valve port 42, the ratio of the covering Rm that biasing of this intake valve port 42 produces is 20～50% left and right.

In addition, with reference to Fig. 5, have and surround the elliptoid shape of cross section of intake valve port 42 and exhaust valve port 43 in major semi axis direction both sides and form arch recess 51 at upper end face 41, in upper end face 41, the pairing left and right crescent shape part in the outside of arch recess 51 is formed with respectively press section 52,52.

In the outside of intake valve port, from the two end part of the protuberance 42a of the crescent shape of intake valve port 42 around along a pair of guiding wall 53,53 of the edge of opening 42s bending of intake valve port 42 toward each other, and open gradually and form towards described exhaust valve port 43 sides.

With respect to the upper end face 41 of the firing chamber 40 of the cylinder head 17 being formed as described above, as shown in Figure 3 and Figure 6, the cylinder thorax 16b of cylinder block 16 is formed with and cuts round surface 55, and this incision round surface 55 is that the rear section relative with the protuberance 42a of intake valve port 42 cylinder thorax 16b and edge of opening cylinder head 17 sides cut until maximum valve lift position along the 46p of the umbrella portion periphery of suction valve 46 to the movement direction of suction valve 46.

As shown in Figure 6, incision round surface 55 is cast into the end face part of the cylinder liner 16L without flanged lip of the cylinder block 16 of the aluminum alloy system of casting cylinder liner 16L made of iron in covering, tilt to cut ground formation.

Because the periphery of the 46p of umbrella portion of suction valve 46 approaches incision round surface 55 ground along this incision round surface 55 and moves, so open from suction valve 46 until move between maximum valve lift position, must be by gap extremely narrow between the periphery of the 46p of umbrella portion of suction valve 46 and incision round surface 55 from the air inlet of the outer ledge side (protuberance 42a side) of intake valve port 42, major part is blocked to firing chamber 40 and sucks, in crested state.

Therefore, the air inlet crested sucking from the outer ledge side of intake valve port 42, is only drawn in firing chamber on a small quantity, thereby take the suction of the inside edge side from intake valve port 42 as main, therefore, forms and easily produce the structure of rolling stream.

It should be noted that, the maximum valve lift position of suction valve 46 also can be positioned at crosses the position of cutting round surface 55 a little.

The part relative with the protuberance 42a of intake valve port 42 of the peripheral portion of the end face 25t of piston 25 cut abreast with the end face 46pf of the 46p of umbrella portion of suction valve 46 and formed incision face 56(with reference to Fig. 6), when opening suction valve 46 along with the decline of piston 25 carry out lift in intake stroke, due to the inlet stream Inbound from outer ledge side and piston, to cut face 56 vertical, so can not promote to suck air inlet from the outer ledge side direction firing chamber 40 of intake valve port 42, more suppress contrary generation of rolling stream.

In gas handling system, from suction tude 20 via connecting pipe 19 until the inlet air pathway P of air inlet port 44 from the downstream portion of suction tude 20 until the curved part of air inlet port 44 is divided into upside inlet air pathway Up and downside inlet air pathway Lp by dividing plate 60.

Cylinder head 17 comprises and forms the part of air inlet port 44 and formed by aluminum alloy, and with respect to this, suction tude 20 is formed by resin.

Therefore, dividing plate 60 is configured to by with suction tude 20 shape all-in-one-piece suction tude side dividing plates 61, form with cylinder head 17 shape all-in-one-piece air inlet port side dividing plates 62 in air inlet port 44, and end, the upstream 62a of the downstream end 61b of suction tude side dividing plate 61 and air inlet port side dividing plate 62 ground that self overlaps links.

With reference to Fig. 2 and Fig. 6, the downstream end 61b of suction tude side dividing plate 61 is more outstanding and enter in air inlet port 44 than the downstream open end of suction tude 20, and end, the upstream 62a of air inlet port side dividing plate 62 arrives the upstream open end to air inlet port 44.

Resinous suction tude side dividing plate 61 enter downstream end 61b in air inlet port 44 have the extruding force producing because of resiliently deformable be crimped on air inlet port side dividing plate 62 end, upstream 62a above and overlap and link.

The passage sections of inlet air pathway P is formed as circle, as shown in Figure 6, the dividing plate 60 that this inlet air pathway P is separated is up and down positioned at than the centrode of the upper and lower width of maximum of inlet air pathway P (this inlet air pathway P in the situation that suction tude side dividing plate 61 together with air inlet port side dividing plate 62, as the circular centrode of passage sections) be path center line Cp side's more on the upper side position, the passage sections of upside inlet air pathway Up is long-pending than the passage sections of downside inlet air pathway Lp long-pending little (with reference to Fig. 7).

As shown in Figure 7, the in the situation that of this inlet air pathway P, the long-pending ratio of passage sections of upside inlet air pathway Up and downside inlet air pathway Lp is, from upstream side opening till downstream side opening roughly 3 to 7.

Air inlet port side dividing plate 62 is along the shape bending of air inlet port 44, the downstream end 62b of air inlet port side dividing plate 62 arrives the air inlet valve lever 46s of the suction valve 46 of the curved part that is positioned at air inlet port 44, as shown in Figure 8, downstream end 62b form from front-end edge take the shape of the letter U depression recess 62u, thereby make this U-shaped recess 60u run through to the valve guiding element 34i of air inlet port 44 interior extensions.

The external diameter of valve guiding element 34i equates with the width of U-shaped recess 60u, the chimeric depths to U-shaped recess 60u of valve guiding element 34i and do not produce gap, therefore, air inlet port side dividing plate 62 is separated inlet air pathway P as much as possible up and down until near the intake valve port 42 of air inlet port 44.

Therefore, with reference to Fig. 6, upside inlet air pathway Up is from the inside edge side (cylinder axis C side) of intake valve port 42 by the central part of firing chamber 40, and downside inlet air pathway Lp passes through the peripheral part of firing chamber 40 from the outer ledge side (protuberance 42a side) of intake valve port 42.

As shown in Figure 6, the sparger 23 that is arranged on suction tude 20 is installed to be, in the face of upside inlet air pathway Up, and towards the position burner oil in 62aGeng downstream side, end, upstream that is compared to linking department 61b, 62a that air inlet port side dividing plate 62 and suction tude side dividing plate 61 link.

In suction tude 20, in the downstream of throttle valve 22 and the provided upstream of suction tude side dividing plate 61 be equipped with air inlet distributing valve 65.

Air inlet distributing valve 65 is that running shaft 66 one that make tabular valve body 67 be supported on suction tude 20 from axle are extended the clack valve forming, and utilizes motor drive mechanism 72 that tabular valve body 67 is swung.

As shown in Figure 9 and Figure 10, be formed with the half-terete incision recess 65d cutting with parallel face along the rotation centerline Cv of running shaft 66 in the inlet air pathway P between the bearing of left and right, tabular valve body 67 extends along the incision bottom surface of cutting recess 65d.

It should be noted that, the back side of the incision recess 65d of running shaft 66 is also formed with the recess cutting a little.

Tabular valve body 67 is formed as cutting the axial width of recess 65d as the half elliptic of semi-minor axis, make to have the base end part and the incision bottom surface butt that cuts recess 65d of straight line, screw 68 is screwed into the recess at the back side via pad 68w from the back side, thereby tabular valve body 67 is bound up on running shaft 66 integratedly.

Also can utilize rivet to connect.

On the incision recess 65d that the base end part of tabular valve body 67 is arranged on to rotatingshaft 66 time, the cardinal extremity edge 67a of the base end part of tabular valve body 67 is positioned on the prolongation side face of the outer circumferential face of running shaft 66 roughly, cut recess 65d on the surface of the base end part of tabular valve body 67 as recess and residual.

Such air inlet distributing valve 65 extends with the upstream ora terminalis 61aa of the left and right horizontal direction of end, the upstream 61a of sensing suction tude side dividing plate 61 abreast at the rotation centerline Cv that makes running shaft 66, and be positioned at upstream extremity edge 61aa below near state under, running shaft 66 is rotated to the earth's axis freely and be bearing in suction tude 20, under the attitude that tabular valve body 67 is extended towards air inlet upstream side from this running shaft 66, be mounted.

If tabular valve body 67 utilizes the rotation of running shaft 66 and swings up and down integratedly, and the outer periphery that are semiellipse shape join with the path inner peripheral surface of the attitude that tilts and the rounded inlet air pathway P in cross section, can seal the half of inlet air pathway P completely.

Running shaft 66 axles of air inlet distributing valve 65 are bearing in the orthogonal position of path center line Cp of rotation centerline Cv and inlet air pathway P.

It should be noted that, the throttle valve 22 that is bearing in the upstream side of air inlet distributing valve 65 at the interior axle of suction tude 20 is to point to the butterfly valve rotating centered by the rotation centerline of the left and right horizontal direction orthogonal with the path center line Cp of inlet air pathway P.

Air inlet distributing valve 65 makes front end swing towards upstream throttle valve 22, the air inlet in throttle valve 22 downstreams is distributed up and down and mobile air inlet ratio in upside inlet air pathway Up and downside inlet air pathway Lp thereby can change.

The ECU(electronic control unit of controlling combustion engine 10) 70 there is inlet control mechanism 71, analyze the operating condition of internal-combustion engine 10 and utilize inlet control mechanism 71 to drive throttle valve 22 and the sparger 23 of controlling gas handling system, but, utilize inlet control mechanism 71 also can drive and control air inlet distributing valve 65.

With reference to Fig. 6, the throttle valve opening θ of throttle valve 22 is that while making from full cut-off, to start to turn to when parallel with inlet air pathway be full-gear, represents the load condition of internal-combustion engine 10.

Air inlet distributing valve 65 swings according to the load condition control of internal-combustion engine 10, the low load situation that is the air inlet distributing valves 65 during using low load condition shown in Fig. 6 as the air inlet distributing valve aperture φ of the pendulum angle of air inlet distributing valve 65 is spent as benchmark 0, increases clockwise pendulum angle in Fig. 6.

Roll stream mode can with bent axle 12 revolve turn around roll circulation speed roll stream represent than Rt.

Roll stream and roll stream angular velocity of rotation/angular velocity of crankshaft than Rt=

If it is larger than Rt to roll stream, produce eddy current strong roll stream.

Figure 11 represents the variation of the air inlet distributing valve aperture φ swinging according to throttle valve opening θ control air inlet distributing valve 65 and rolls stream than the variation of Rt.

Below, with reference to Figure 11, investigate the swing control of the air inlet distributing valve 65 under the load condition of internal-combustion engine 10 and roll stream and compare Rt.

As shown in Figure 6, at internal-combustion engine 10 during in low load operation state, throttle valve 22 leaves very littlely (throttle valve opening θ: little), and air inlet distributing valve 65 is positioned at the front-end edge of tabular valve body 67 the low load situation (air inlet distributing valve aperture φ=0) joining with the lower lateral circle surface of inlet air pathway P.

In the time that the front-end edge of tabular valve body 67 of this air inlet distributing valve 65 and the lower lateral circle surface of inlet air pathway P join, the lower surface of the cardinal extremity edge 67a that is positioned at rotation centerline Cv top of tabular valve body 67 and end, the upstream 61a of suction tude side dividing plate 61 joins, therefore, the upstream side opening of downside inlet air pathway Lp is sealed completely by air inlet distributing valve 65.

Therefore, air inlet distributing valve 65 can make air inlet be roughly all assigned to top and flow in upside inlet air pathway Up.

Therefore, the air inlet of the opening of opening a little by throttle valve 22 by air inlet distributing valve 65 by roughly all the very wise move inlet air pathway Up compared with narrow of guiding top flow, thereby become at a high speed, and by extending to the dividing plate 60 of air inlet valve lever 46s of the curved part that is positioned at air inlet port 44, be directed near intake valve port 42, therefore, most of air inlet is sucked at a high speed towards exhaust side to the central part of firing chamber 40 from the inner side edge side (cylinder axis C side) of intake valve port 42, what as shown in Figure 6, generation eddy current was strong rolls stream (rolling stream rises than Rt).

Intake valve port 42 is being setovered along the mode of cylinder outstanding crescent shape protuberance 42a outside axially to from apparent time to the circular hole of cylinder thorax 16b to have, thereby the outer ledge side of intake valve port 42 (protuberance 42a side) crested, and the air inlet by downside inlet air pathway Lp does not almost have, therefore, do not suck the air inlet of firing chamber 40 from the external side brim side of intake valve port 42, can not produce and hinder the contrary stream that rolls that rolls stream, make to roll miscarriage raw byer force, roll stream and uprise than Rt, the combustion efficiency can improve low load time.

As shown in figure 12, at internal-combustion engine 10 during in middle load operation state, throttle valve 22 is opened to intermediate degree (throttle valve opening θ: in), air inlet distributing valve 65 is positioned at front-end edge to approach the middle load situation (air inlet distributing valve aperture φ=β degree) of the upper lateral circle surface of inlet air pathway P, therefore, air inlet distributing valve 65 so that the ratio top mode less than below of air inlet distribute.

Therefore, as shown in the arrow of Figure 12, the air inlet although downside inlet air pathway Lp flows fully, also suppressed in the air inlet that upside inlet air pathway Up is mobile.

In addition, if the front-end edge of the tabular valve body 67 of air inlet distributing valve 65 leaves the lower lateral circle surface of inlet air pathway P, the cardinal extremity edge 67a of tabular valve body 67 leaves the lower surface of end, the upstream 61a of suction tude side dividing plate 61, between the incision recess 65d of air inlet distributing valve 65 and end, the upstream 61a of suction tude side dividing plate 61, forms via intermedia Mp.

Because via intermedia Mp is by downside inlet air pathway Lp, so be assigned to the most of upside inlet air pathway Up that flows into of the air inlet of upside in the air inlet being distributed up and down by air inlet distributing valve 65, but, the a part of air inlet that does not flow into upside inlet air pathway Up also can not be detained and can successfully flow into downside inlet air pathway Lp by via intermedia Mp, can suppress the disorder of inlet stream, and further suppress to flow into the air inlet of upside inlet air pathway Up.

Therefore, enter firing chamber 40 even if be suppressed in the mobile air inlet of upside inlet air pathway Up from the inside edge side of intake valve port 42, also only produce eddy current weak roll stream, and exist a little and produce from the air inlet that the outer ledge side of intake valve port 42 sucks the peripheral part of firing chamber 40 and contraryly roll stream and suppress to roll stream, therefore, do one's utmost to suppress to roll stream, roll stream and decline than Rt.

As shown in figure 13, at internal-combustion engine 10 during in high capacity operating condition, throttle valve 22 becomes standard-sized sheet (throttle valve opening θ: standard-sized sheet), end, the upstream 61a of air inlet distributing valve 65 and suction tude side dividing plate 61 is parallel and be positioned in the high capacity position (air inlet distributing valve aperture φ=α degree) of the plane that is positioned at the path center line Cp that comprises inlet air pathway P, therefore, air inlet distributing valve 65 distributes air inlet up and down with 1 to 1 ratio.

But, if the X-X line sectional view of Figure 13 and Figure 13 is as shown in Figure 10, between the incision recess 65d of air inlet distributing valve 65 and end, the upstream 61a of suction valve side dividing plate 61, be formed with via intermedia Mp, therefore, because a part for the air inlet that is dispensed to upside by air inlet distributing valve 65 is not detained by via intermedia Mp point-blank, and successfully flow into downside inlet air pathway Lp, so consequently, air inlet flows into upside inlet air pathway Up and downside inlet air pathway Lp in the mode that is divided into roughly 3 to 7 ratio by suction tude side dividing plate 61.

Therefore, as shown in the arrow of Figure 13, in upside inlet air pathway Up and the mobile enough air inlets of downside inlet air pathway Lp, be inhaled into firing chamber 40 and produce and roll stream from the inside edge side of intake valve port 42 in the mobile air inlet of upside inlet air pathway Up, enter firing chamber 40 and produce a little the contrary stream that rolls in the mobile air inlet crested of downside inlet air pathway Lp and from the outer ledge side of intake valve port 42, but, owing to sucking enough air inflows from upside inlet air pathway Up, so can produce roll the stream eddy current higher than Rt suitable roll stream, and can utilize enough air inlets that intake efficiency is maintained well.

As mentioned above, the air inlet system of this internal-combustion engine 10 makes the rotation centerline Cv of the running shaft 66 of air inlet distributing valve 65 point to abreast the upstream ora terminalis 61aa of dividing plate 60, and be positioned near the below of this upstream ora terminalis 61aa and rotate the earth's axis freely and be bearing in suction tude 20, the tabular valve body 67 extending towards air inlet upstream side from running shaft 66 swings up and down, the air inlet in throttle valve 22 downstreams is distributed up and down and can change the ratio in upside inlet air pathway Up and the mobile air inlet of downside inlet air pathway Lp, therefore, can roll according to the load condition adjustment of internal-combustion engine the strength of vortex of stream, and seek the optimization of combustion efficiency.

The air inlet system of this internal-combustion engine 10 is split into dividing plate 60 to be formed at the suction tude side dividing plate 61 of suction tude 20 and is formed at the air inlet port side dividing plate 62 in air inlet port 44, the down stream port 61b of suction tude side dividing plate 61 self links with end, the upstream 62a of air inlet port side dividing plate 62 with overlapping, therefore, from suction tude 20 and air inlet port 44 is outstanding, overhang is little respectively for suction tude side dividing plate 61 and air inlet port side dividing plate 62, thereby can easily guarantee rigidity.

Even for air inlet port side dividing plate 62 strips also can be guaranteed rigidity, make the downstream end 62b of air inlet port side dividing plate 62 arrive the air inlet valve lever 46s of the suction valve 46 of the curved part that is positioned at air inlet port 44, and the recess 62u that makes downstream end 62b strides across air inlet valve gap 46s, make air inlet port side dividing plate 62 extend to the downstream that approaches firing chamber, therefore, on the way can spread hardly and be directed near intake valve port in the mobile air inlet of upside inlet air pathway Up, and flow into towards exhaust side from the central part of the side direction firing chamber, inside edge of intake valve port, thereby can produce eddy current strong roll stream (with reference to Fig. 6).

In the mode of the downstream side burner oil towards upside inlet air pathway Up, sparger 23 is set in the upside inlet air pathway Up of suction tude 20 side, the downstream end 61b of suction tude side dividing plate 61 is to link with the mode overlapping on end, the upstream 62a of air inlet port side dividing plate 62, therefore, the fuel that injected device 23 sprays is difficult to immerse the coincidence face of linking department 61b, 62a, prevent that fuel is to downside inlet air pathway Lp seepage, and can efficiency carry out well fuel supply, thereby suppress combustion efficiency.

Because sparger 23 is configured to the downstream side burner oil with linking department 61b, the 62a of suction tude side dividing plate 61 towards air inlet port side dividing plate 62, so the burner oil of sparger 23 is difficult to be penetrated into downside inlet air pathway Lp more, in addition, because fuel is injected in the air inlet port side dividing plate 62 that temperature is high, so can suppress the liquefaction of fuel.

Because having the extruding force producing because of resiliently deformable, the downstream end 61b of the suction tude side dividing plate 61 for being become by resin-shaped also overlaps with end, the upstream 61a crimping of air inlet port side dividing plate 62, so do not use joint compound, also can easily make the downstream end 61b of suction tude side dividing plate 61 and end, the upstream 62a of air inlet port side dividing plate 62 fluid-tight engagement and linking simply, make functionality good.

Because suction tude side dividing plate 61 is to make downstream end 61b outstanding and enter the structure in air inlet port 44 from the downstream open end of suction tude 20, so in the time being assembled into tracheae 20, can be take the downstream end 61b of the suction tude side dividing plate 61 more outstanding than the downstream open end of suction tude 20 as benchmark the visual time relatively contraposition of end, upstream 62a with air inlet port side dividing plate 62, and suction tude 20 is arranged in cylinder head 17, makes workability good.

Figure 14 and Figure 15 represent the variation as the air inlet distributing valve of clack valve, and describe.

The part of this air inlet distributing valve 80 in the inlet air pathway P that is equivalent to running shaft 81 is formed with a pair of incision recess 81a, 81b, this incision recess 81a, 81b to be to cut in interior parallel plane plane with the central shaft that comprises rotary middle spindle Cv, cut plat part 81c between recess 81a, 81b run through be provided with two plane parallel of plat part 81c the grooving 81s that runs through.

The left and right width of grooving 81s is identical with incision recess 81a, 81b, equates with the internal diameter of inlet air pathway P.

Run through and be provided with mounting hole 81ch, 81ch at the position, two of left and right of plat part 81c.

Grooving 81s at the plat part 81c of this running shaft 81 embeds the base end part that has tabular valve body 82.

Tabular valve body 82 is formed as the semiellipse shape take the left and right width of grooving 81s as semi-minor axis, in the left and right of base end part with straight line, runs through accordingly and is provided with mounting hole 82h, 82h with mounting hole 81ch, the 81ch of the plat part 81c of running shaft 81.

As shown in figure 14, grooving 81s at the plat part 81c of running shaft 81 embeds the base end part that has tabular valve body 82, mounting hole 81ch, the 81ch of running shaft 81 and mounting hole 82h, the 82h of tabular valve body 82 are coordinated, make pipe type rivet 83,83 run through this mounting hole 81ch, 81ch and mounting hole 82ch, 82ch from cutting recess 81b side, and rivet the front end from cutting the outstanding pipe type rivet 83,83 of recess 81a, thereby tabular valve body 82 is arranged on running shaft 81 as air inlet distributing valve 80.

This air inlet distributing valve 80 so that near the mode that the rotation centerline Cv of running shaft 81 is positioned at the below of end, upstream 61a of suction tude side dividing plate 61 be arranged in the suction tude 20 of described mode of execution.

Tabular valve body 82 utilizes the rotation of running shaft 81 and swings up and down integratedly, at internal-combustion engine 10 during in low load operation state, if the outer periphery that are semiellipse shape are joined with the path inner peripheral surface of the attitude that tilts and the rounded inlet air pathway P in cross section, the lower surface of end, the upstream 61a of the ora terminalis of the plat part 81c of running shaft 81 and suction tude side dividing plate 61 joins, the upstream side opening of downside inlet air pathway Lp is sealed completely by air inlet distributing valve 65, air inlet is only by upside inlet air pathway Up, can make to roll miscarriage raw very by force.

At internal-combustion engine 10 during in middle high capacity operating condition, the upstream side opening of downside inlet air pathway Lp is opened, and form via intermedia Mp between the incision recess 81a of air inlet distributing valve 80 and end, the upstream 61a of suction tude side dividing plate 61, the a part of air inlet that does not enter upside inlet air pathway Up is not detained and can successfully flows into downside inlet air pathway Lp by via intermedia Mp, and can suppress the disorder of inlet stream.

Figure 15 is equivalent to the sectional view of the X-X line sectional view of Figure 13 while being high capacity operating condition, between the incision recess 81a of air inlet distributing valve 80 and end, the upstream 61a of suction tude side dividing plate 61, form via intermedia Mp.

In above mode of execution, intake valve port 42 is being setovered highlightedly along the outside of the cylinder circular upper end face peristome 41s that axially circular hole with cylinder thorax 16b of the upper end face 41 to apparent time to firing chamber 40 is corresponding, thereby cover the protuberance of firing chamber peripheral part, but, for the internal-combustion engine of the common cylinder head that uses intake valve port 42 not give prominence to from upper end face peristome 41s, also can be suitable for the utility model.

; in the time that the peripheral part of firing chamber 40 does not have crested and internal-combustion engine 10 in low load operation state; because air inlet distributing valve 65 seals the upstream side opening (air inlet distributing valve aperture φ: 0 degree) of downside inlet air pathway Lp; and air inlet is roughly all assigned to top and flows at upside inlet air pathway Up; so lead, narrower upside inlet air pathway Up and swiftly flowing air inlet are sucked towards exhaust side to the central part of firing chamber 40 at high speed from the inside edge side (cylinder axis C side) of intake valve port 42, can produce eddy current strong roll stream.

At internal-combustion engine 10 during in middle high capacity operating condition, the upstream side opening of downside inlet air pathway Lp is opened, between the incision recess 81a of air inlet distributing valve 80 and end, the upstream 61a of suction tude side dividing plate 61, form via intermedia Mp, the a part of air inlet that does not enter upside inlet air pathway Up is not detained and can successfully flows into downside inlet air pathway Lp by via intermedia Mp, and can suppress the disorder of inlet stream.

In addition, in the present embodiment, at air inlet distributing valve 65 during in middle load operation state, the front-end edge of air inlet distributing valve 65 is rocked to the middle load situation (air inlet distributing valve aperture φ: β degree) of the upper lateral circle surface that approaches inlet air pathway P, but, do not carry out such control, can, from the paramount load operation state of low load operation state, proportionally increase air inlet distributing valve aperture φ with respect to the increase of throttle valve opening θ yet.

Figure 16 has represented following situation,, do not cover the peripheral part of firing chamber 40, and from the paramount load operation state of low load operation state, in the situation that proportionally increases air inlet distributing valve aperture φ and control with respect to the increase of throttle valve opening θ, control the variation of the air inlet distributing valve aperture φ that air inlet distributing valve 65 swings and roll stream than the variation of Rt according to throttle valve opening θ.

At internal-combustion engine 10 during in low load operation state, throttle valve 22 leaves very littlely (throttle valve opening θ: little), air inlet distributing valve 65 is positioned at the low load situation (air inlet distributing valve aperture φ=0 degree) that the front-end edge of tabular valve body 67 and the lower lateral circle surface of inlet air pathway P join, and the upstream side opening of downside inlet air pathway Lp is sealed completely by air inlet distributing valve 65.

Therefore, lead narrower upside inlet air pathway Up and mobile air inlet sucked towards exhaust side to the central part of firing chamber 40 at high speed from the inside edge side (cylinder axis C side) of intake valve port 42, what generation eddy current was strong rolls stream, rolls stream and rises than Rt, the combustion efficiency can improve low load time.

Be accompanied by throttle opening θ and become large, and the load operation state of internal-combustion engine 10 improves, if proportionally increase air inlet distributing valve aperture φ with throttle valve opening θ, air inlet distributing valve 65 is opened the upstream side opening of downside inlet air pathway Lp and air inlet is flowed at downside inlet air pathway Lp, being assigned to the via intermedia Mp that the air inlet of upside inlet air pathway Up also forms by part flows at downside inlet air pathway Lp, therefore, owing to reducing in the mobile air inlet of upside inlet air pathway Up, even so enter firing chamber 40 from the inside edge side of intake valve port 42, also only can produce eddy current weak roll stream, making to roll stream declines than Rt.

If more than throttle valve opening θ becomes greatly extremely to a certain degree, at air inlet distributing valve aperture φ parallel with end, the upstream 61a of suction tude side dividing plate 61 from becoming (air inlet distributing valve aperture φ=α) before, the air inlet ratio that is dispensed to upside inlet air pathway Up can not change, therefore, maintain stable eddy current weak roll stream, roll stream roughly more certain than Rt.

The strength of vortex of thus, rolling stream by adjustment can be sought the optimization of combustion efficiency.

Claims (6)

1. an air inlet system for internal-combustion engine, forms combuster (40) between the end face of its piston (25) in the cylinder thorax (16b) that is entrenched in sliding freely cylinder block (16) and the upper end face (41) with the relative cylinder head of this end face (17),

Direction that each air inlet port (44) and exhaust port (45) separate with exhaust valve port (43) towards each other from the intake valve port (42) of from end face opening to described cylinder head (17) described is bending and be formed extended at both sides,

Have with suction tude (20) and be connected and continuous inlet air pathway (P) in air inlet port (44) formation,

Be provided with throttle valve (22) in described suction tude (20),

Described inlet air pathway (P) is separated into the downside inlet air pathway (Lp) of the upside inlet air pathway (Up) of the central part by firing chamber (40) and the peripheral part by firing chamber (40) partly by dividing plate (60),

In the downstream of described throttle valve (22), utilize the air inlet distributing valve (65) of the upstream that is arranged on described dividing plate (60) to controlling at described upside inlet air pathway (Up) and the mobile air inlet of described downside inlet air pathway (Lp),

The air inlet system of described internal-combustion engine utilizes inlet control mechanism (71) to drive and controls described air inlet distributing valve (65), and the air inlet system of described internal-combustion engine is characterised in that,

Described dividing plate (60) is made up of the air inlet port side dividing plate (62) that is formed at the suction tude side dividing plate (61) of described suction tude (20) and be formed in air inlet port (44),

The downstream end (61b) of described suction tude side dividing plate (61) self links with the end, upstream (62a) of described air inlet port side dividing plate (62) with overlapping.

2. the air inlet system of internal-combustion engine as claimed in claim 1, is characterized in that,

In described upside inlet air pathway (Up) side of described suction tude (20), in the mode of the downstream side burner oil towards described upside inlet air pathway (Up), sparger (23) is set,

The downstream end (61b) of described suction tude side dividing plate (61) links above with the end, upstream (62a) of described air inlet port side dividing plate (62) with overlapping.

3. the air inlet system of internal-combustion engine as claimed in claim 2, is characterized in that,

Described sparger (23) is configured to, the downstream side burner oil towards described air inlet port side dividing plate (62) with the linking department (61b, 62a) of described suction tude side dividing plate (61).

4. the air inlet system of internal-combustion engine as claimed any one in claims 1 to 3, is characterized in that,

Described suction tude side dividing plate (61) is formed by resin,

The downstream end (61b) of described suction tude side dividing plate (61) has the extruding force crimping producing because of resiliently deformable and lays equal stress on and be combined on the end, upstream (62a) of described air inlet port side dividing plate (62).

5. the air inlet system of internal-combustion engine as claimed any one in claims 1 to 3, is characterized in that,

The downstream end (61b) of described suction tude side dividing plate (61) is more outstanding and enter in inlet end mouth (44) than the downstream open end of described suction tude (20).

6. the air inlet system of internal-combustion engine as claimed in claim 4, is characterized in that,

The downstream end (61b) of described suction tude side dividing plate (61) is more outstanding and enter in inlet end mouth (44) than the downstream open end of described suction tude (20).