CN105020046B - For the body group of engine and the engine with the body group - Google Patents

Abstract

The invention discloses a kind of body group for engine and the engine with the body group.The body group includes：Cylinder head；Cylinder block, the internal face of the cylinder wall of cylinder is cylindrical wall, the cross section of cylinder wall is annular, annular is circumferentially divided into four sections of segmental arcs being sequentially connected, every section of segmental arc is further divided into first paragraph, second segment and the 3rd section, the corresponding central angle of first paragraph is α 1 and wall thickness is h1, the corresponding central angle of second segment is α 2 and wall thickness is h2, 3rd section of corresponding central angle is α 3 and wall thickness is h3, the longitudinal centre line of 3rd segment distance engine of wherein each segmental arc is farthest, the first paragraph of each segmental arc is nearest apart from longitudinal centre line, wherein α 1, α 2 and α 3 meet relational expression：α 1+ α 2+ α 3=90 °；H1, h2 and h3 meet one of following relationship：H1 ＜ h2≤h3, h1≤h2 ＜ h3.The body group of the present invention has light weight, small volume, and can be effectively improved the problem on deformation of cylinder.

Description

For the body group of engine and the engine with the body group

Technical field

The present invention relates to automotive field, more particularly, to a kind of body group for engine and the hair with the body group Motivation.

Background technology

The body group of engine includes cylinder head, cylinder head gasket, cylinder block and oil sump.It is formed with cylinder block multiple Cylinder, piston can do reciprocating linear motion in cylinder.In cycle of engine work done, especially for compression stroke and work Work(stroke, piston can be applied to cylinder wall very big power, and cylinder wall is chronically under power effect and easily deformed, so as to drop Fuel economy, dynamic property and the discharge performance of low engine, cause the degradation of engine.

It is existing to solve the problems, such as that cylinder deformation typically all increases the thickness of cylinder wall on the whole, make the thickness of cylinder wall more It is thick and uniform, or increase the thickness of body group side wall and side wall is made into plane treatment.But, it is this to improve the side of cylinder deformation Formula not only increases the quality and volume of body group, while the flow resistance of cooling water in water jacket may be increased, meeting when serious Cause cylinder cooling not enough, deteriorate the combustion efficiency of engine, increase discharge and fuel consumption.

The content of the invention

It is contemplated that at least solving one of above-mentioned technical problem of the prior art to a certain extent.Therefore, this hair A bright purpose is a kind of body group for engine of proposition, and the body group has light weight, small volume, and can be effective Improve the problem on deformation of cylinder.

It is another object of the present invention to propose a kind of engine with body group as described above.

Body group for engine according to embodiments of the present invention, including：Cylinder head；And cylinder block, the cylinder There is at least one cylinder in vivo, the internal face of the cylinder wall of the cylinder is cylindrical wall, the cross section of the cylinder wall For annular, the annular is circumferentially divided into four sections of segmental arcs being sequentially connected, every section of segmental arc be further divided into first paragraph, Second segment and the 3rd section, the corresponding central angle of the first paragraph is α 1 and wall thickness is h1, and the corresponding central angle of the second segment is α 2 and wall thickness is h2, the 3rd section of corresponding central angle is α 3 and wall thickness is h3, wherein the 3rd section of each segmental arc away from Longitudinal centre line from the engine is farthest, and the first paragraph of each segmental arc is nearest apart from the longitudinal centre line, its Middle α 1, α 2 and α 3 meet relational expression：α 1+ α 2+ α 3=90 °；H1, h2 and h3 meet one of following relationship：H1 ＜ h2≤h3, h1 ≤ h2 ＜ h3.

Body group according to embodiments of the present invention, by structure improvement so as to effectively increase cylinder intensity and just Degree, can effectively prevent the deformation of cylinder, it is ensured that engine can be stablized, Effec-tive Function, improve the fuel economy of engine And power output performance.Body group according to embodiments of the present invention is particularly suitable for dual fuel engine, and such as gasoline, diesel is double Engine fuel.

In addition, body group according to embodiments of the present invention, can also have following additional technical feature：

According to some embodiments of the present invention, h1, h2 and h3 meet following relationship respectively：6.5mm≤h1≤7mm, 7mm ≤ h2≤7.5mm, 7.5mm≤h3≤9.5mm.

According to some embodiments of the present invention, the wall thickness of each segmental arc is according to the first paragraph court from the segmental arc It is gradually thickening to the 3rd section of direction of the segmental arc.

According to some embodiments of the present invention, α 1, α 2 and α 3 meet relational expression respectively：1≤40 ° of 30 °≤α, 15 °≤α 2≤ 25 °, 3≤40 ° of 30 °≤α.

According to some embodiments of the present invention, α 1=35 °, α 2=20 °, α 3=35 °.

According to some embodiments of the present invention, the first side wall of the side of cylinder block first and the side of cylinder block second Second sidewall is respectively formed as on the symmetrical waveform of the longitudinal centre line, and the waveform has the first arc section and the Two arc sections, first arc section is relative with described 3rd section in the transverse direction of the body group, and second arc section connects It is connected between two neighboring first arc section.

According to some embodiments of the present invention, the radius of curvature of first arc section is R1, second arc section Radius of curvature is that R2, wherein R2 and R1 ratio meet relational expression：2.1≤R2/R1≤2.5.

According to some embodiments of the present invention, top plate is additionally provided with the top of the cylinder block, the thickness of the top plate is H4, a diameter of D of the cylinder, wherein h4 and D ratio meet relational expression：0.15≤h4/D≤0.19.

According to some embodiments of the present invention, block jacket is provided with the cylinder block, the block jacket Depth is h5, the row of the first piston ring of the piston of the engine during lower dead center is moved to from top dead centre on the piston Journey is that h6, wherein h5 and h6 ratio meet relational expression：0.75≤h5/h6≤0.85.

A kind of embodiment according to a further aspect of the invention, it is proposed that engine with body group as described above.

Brief description of the drawings

Fig. 1 is the top view of the cylinder block of body group according to embodiments of the present invention；

Fig. 2 is the front view of the cylinder block of body group according to embodiments of the present invention；

Fig. 3 is the rough schematic view of the cylinder block shown in Fig. 1；

Fig. 4 is the schematic diagram in cylinder section；

Fig. 5 is the distribution schematic diagram of threaded fastener；

Fig. 6 is water jacket depth one to go in ring the ratio of journey and the curve of cylinder wall pressure with piston in upper and lower stop Graph of a relation；

Fig. 7 is the schematic diagram of cylinder head according to embodiments of the present invention；

Fig. 8 is the schematic diagram of air intake duct and exhaust duct；

Fig. 9 is the schematic diagram of inlet valve and exhaust valve；

Figure 10 is the set location schematic diagram of spark plug；

The partial schematic diagram of Figure 11 pistons and cylinder head；

Figure 12 is the intention of the part of piston；

Figure 13 is that any one of pit passes through the schematic diagram of the vertical section of axis of rotation；

Figure 14 is the stereogram of piston；

Figure 15 is the stereogram of engine；

Figure 16-Figure 18 is the comparison diagram that engine according to embodiments of the present invention uses different compression ratios；

Figure 19-Figure 20 be engine according to embodiments of the present invention under two operating modes, using pair of different spray-cone angles Than figure；

Figure 21-Figure 22 be engine according to embodiments of the present invention piston and conventional piston HC, NOx comparison diagram；

Figure 23 is the swirl ratio schematic diagram of engine chamber according to embodiments of the present invention.

Embodiment

Embodiments of the invention are described below in detail, the example of the embodiment is shown in the drawings, wherein from beginning to end Same or similar label represents same or similar element or the element with same or like function.Below with reference to attached The embodiment of figure description is exemplary, it is intended to for explaining the present invention, and be not considered as limiting the invention.

In the description of the invention, it is to be understood that term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", " under ", "front", "rear", "left", "right", " vertical ", " level ", " top ", " bottom " " interior ", " outer ", " up time The orientation or position relationship of the instruction such as pin ", " counterclockwise " are, based on orientation shown in the drawings or position relationship, to be for only for ease of The description present invention and simplified description, rather than indicate or imply that the device or element of meaning must have specific orientation, Yi Te Fixed azimuth configuration and operation, therefore be not considered as limiting the invention.

In addition, term " first ", " second " are only used for describing purpose, and it is not intended that indicating or implying relative importance Or the implicit quantity for indicating indicated technical characteristic.Thus, define " first ", the feature of " second " can express or Implicitly include one or more this feature.In the description of the invention, " multiple " are meant that at least two, such as two It is individual, three etc., unless otherwise specifically defined.

In the present invention, unless otherwise clearly defined and limited, term " installation ", " connected ", " connection ", " fixation " etc. Term should be interpreted broadly, for example, it may be fixedly connected or be detachably connected, or integrally；Can be that machinery connects Connect or electrically connect；Can be joined directly together, can also be indirectly connected to by intermediary, can be in two elements The connection in portion or the interaction relationship of two elements.For the ordinary skill in the art, can be according to specific feelings Condition understands the concrete meaning of above-mentioned term in the present invention.

In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature it " on " or it " under " Can directly it be contacted including the first and second features, it is not direct contact but by it that can also include the first and second features Between other characterisation contact.Moreover, fisrt feature second feature " on ", " top " and " above " to include first special Levy directly over second feature and oblique upper, or be merely representative of fisrt feature level height higher than second feature.Fisrt feature exists Second feature " under ", " lower section " and " following " fisrt feature that includes are immediately below second feature and obliquely downward, or be merely representative of Fisrt feature level height is less than second feature.

The characteristics of engine 1000 according to embodiments of the present invention, engine 1000 are described in detail below with reference to Fig. 1-Figure 23 Be liquid or gaseous fuel and air mixing after directly input machine internal-combustion and produce energy, be then transformed into machinery again Energy.For vehicle, its engine 1000 can typically use four stroke forms, and engine 1000 can typically include gazogene Structure, toggle, feed system, ignition system, cooling system and lubricating system etc..

Wherein, the function of toggle is the torque that the power that combustion gas is acted on piston 109 is changed into bent axle, with To work mechanism output mechanical energy.Usually, toggle mainly includes piston connecting rod unit, crankshaft-flywheel group and body Group.

The reciprocating motion of piston 109 is changed into the rotary motion of bent axle by piston connecting rod unit, while will act on piston 109 On power be changed into the torque that bent axle is externally exported, so as to drive the vehicle wheel rotation of vehicle.Usually, piston connecting rod unit includes living Plug 109, piston ring (including first piston ring 114), piston pin and connecting rod etc., piston pin are used to connect piston and connecting rod.Bent axle Flywheel group is mainly made up of bent axle with flywheel.

Body group is the support of engine, is that piston connecting rod unit, crankshaft-flywheel group, valve actuating mechanism and engine 1000 are respectively The assembling matrix of system major part.Body group mainly includes cylinder head 101, cylinder head gasket, cylinder block 201 and oil sump 301 (as shown in figure 15), cylinder head 101 is located at the top surface of cylinder block 201, and cylinder head gasket is folded in the bottom surface M1 of cylinder head 101 (bottom surface M1 is as shown in Figure 9) between the top surface of cylinder block 201, for the seam between blanket gas cylinder cap 101 and cylinder block 201 Gap, oil sump 301 is arranged on the bottom of cylinder block 201.In the description of the invention, the longitudinal direction of engine 1000 (or body group) The length direction of engine 1000 is referred to, the transverse direction of engine 1000 (or body group) refers to the thickness of engine 1000 (width) direction, the short transverse of engine 1000 (or body group) refers to the direction of the center line parallel to cylinder 203.

Such as Fig. 1 and with reference to shown in Figure 11, cylinder block 201 has at least one cylinder 203, and cylinder 203 is existed for piston 109 Wherein move the cylindrical cavity that is oriented to, cylinder 203 is typically incorporated in the first half of cylinder block 201, and cylinder block 201 Lower half typically can be crankcase, but not limited to this.For straight engine 1000, as shown in figure 1, its multiple cylinder 203 be, i.e., multiple gas juxtaposed (longitudinal centre line 200 is as shown in Figure 3 and Figure 4) along the longitudinal centre line 200 of engine 1000 Longitudinal arrangement of the cylinder 203 along engine 1000 is in alignment.For V-type motor 1000, it is generally divided into two groups of gas Angle between cylinder 203, two groups of cylinders 203 is general between 30 ° -60 °, but not limited to this.

As shown in Figure 7 and Figure 8, corresponding with each cylinder 203 air intake duct 103 and exhaust duct are formed with cylinder head 101 104, air intake duct 103 is used to convey gas mixture (or air) to combustion chamber, and exhaust duct 104 is used to discharge waste gas.Typically Ground, can be two using Two In and Two Out air flue form, i.e. air intake duct 103 and exhaust duct 104, but not limited to this, for example also Scene 2 or one-in-and-one-out can be entered using three, for the ordinary skill in the art, can according to actual needs and The internal structure of cylinder head 101 and adaptive settings.

Valve actuating mechanism is arranged in cylinder head 101, and the effect of valve actuating mechanism is according in each cylinder 203 of engine 1000 The requirement of the working cycles and firing order of progress, time opening and closing inlet valve 108 and exhaust valve 110, make fresh punching Amount (such as gas mixture or air) is entered in cylinder 203 in time, and waste gas is discharged from cylinder 203 in time.

Valve actuating mechanism mainly includes valve group and valve transmission group part, and valve group generally comprises air inlet side valve (referred to as Inlet valve 108) and exhaust side valve (abbreviation exhaust valve 110), inlet valve 108 and exhaust valve 110 can be respectively by independent Camshaft actuated its timing open, close.Camshaft can link with the bent axle of engine 1000, camshaft and engine Can be using various ways such as gear drive, Chain conveyer or V belt translations between 1000.

Wherein, for four-stroke engine 1000, each cylinder 203 at least corresponds to an inlet valve 108 and one Exhaust valve 110, usually, the quantity of inlet valve 108 and the quantity of air intake duct 103 are identical, the quantity of exhaust valve 110 and row The quantity of air flue 104 is identical.It is for instance possible to use Two In and Two Out Four valve structure, or three enter the air valve structure of scene 2 five, The air valve structure of one-in-and-one-out two can certainly be used.Inlet valve 108 and exhaust valve 110 in each combustion chamber is convex by correspondence The driving of wheel shaft is so as to according to certain rule partially unrolling, so that it is (or fresh to fill into gas mixture into combustion chamber in time Air), and in time discharge waste gas after burning work done.

The function of spark plug 105 is that the high-tension electricity for producing ignition coil introduces combustion chamber, and is produced between two electrodes Raw electric spark, so as to light combustion mixture, spark plug 105 mainly can be by central electrode, lateral electrode, housing and insulator etc. Composition.In some embodiments of the invention, each cylinder 203 is correspondingly arranged at least one spark plug 105, the spark plug 105 can be fixed on the corresponding position of cylinder head 101 by the way of threaded connection.As optional embodiment, each Cylinder 203 is only correspondingly arranged a spark plug 105.

Gasoline ejector is used for injected petrol fuel, in an embodiment of the present invention, the specific setting to gasoline ejector Position is not particularly limited.For example, gasoline ejector can be one-to-one (that is, multi-point injection) with the quantity of cylinder 203, Gasoline ejector can be arranged in cylinder head 101 and can directly inject fuel into before the inlet valve 108 of correspondence cylinder 203 Side.Certainly, a gasoline ejector can also correspond to multiple cylinders 203 (that is, single point injection), and the fuel injector may be mounted at section In section before valve, fuel can enter in air intake branch after spraying into air stream, and be respectively allocated to each cylinder 203.

Diesel injector 107 is used to spray diesel fuel, and diesel injector 107 can be arranged in cylinder head 101, diesel oil The nozzle segment of fuel injector 107 can be located in corresponding combustion chamber.In some embodiments of the invention, each cylinder 203 It is correspondingly arranged at least one diesel injector 107.As optional embodiment, each cylinder 203 is only correspondingly arranged a bavin Oily fuel injector 107.

It should be appreciated that specific configuration, operation principle and phase on diesel injector 107 and gasoline ejector Oil supply system of pass etc. has been prior art and is well known for ordinary skill in the art, therefore here no longer one by one Repeat.

Wherein, as optional embodiment, each combustion chamber corresponds to a gasoline ejector and a diesel oil oil spout Device 107, and a gasoline ejector and a diesel injector 107 can be integrated into an entirety, a monoblock type Fuel injector can have a nozzle, and injected petrol is used for when needing injected petrol, and then be used for when needing injection diesel oil Spray diesel oil.Or a unit injector can also have two nozzles, one is used for injected petrol, and another is used for Diesel oil is sprayed, two nozzles are non-interference.In these embodiments, the Fuel Petroleum that gasoline ejector sprays is to be injected directly into In combustion chamber, and without air intake branch or air intake duct, multi-point injection and single point injection with above-mentioned gasoline ejector Set-up mode is different.

Because engine 1000 according to embodiments of the present invention has the diesel injector 107 for being used for spraying diesel oil and uses In the gasoline ejector of injected petrol, therefore engine 1000 according to embodiments of the present invention can also be referred to as gasoline, diesel pair Engine fuel 1000 (abbreviation dual fuel engine 1000).

Dual fuel engine 1000 according to embodiments of the present invention, when starting engine 1000, can pass through spark plug 105 modes of igniting carry out ignition start.And after the normal starting of dual fuel engine 1000, can be by spraying diesel oil with compression ignition Mode works, and now spark plug 105 can be stopped.So as to so that dual fuel engine according to embodiments of the present invention 1000, compared to Diesel engine, discharge can be effectively reduced when starting, difficult especially for Diesel engine cold-starting The problem of, can smoothly it be started by ignition way., can after dual fuel engine 1000 according to embodiments of the present invention is started To replace the ignition way of spark plug 105 by compression ignition mode, thus high compression ratio contributes to abundant burning, improves engine 1000 fuel economy and power output performance.

In addition, spark plug 105 can be with when engine 1000 according to embodiments of the present invention is due to normal work stroke cycle It is stopped, spark plug 105 only can be lighted a fire when starting, therefore can greatly reduce the ignition times of spark plug 105, The service life of spark plug 105 is improved, use cost is reduced, while also simplify control strategy.

However, it is desirable to explanation, the above-mentioned starting on dual fuel engine 1000 according to embodiments of the present invention It is only schematically to illustrate that journey and normal stroke, which are circulated, it is impossible to is not understood as a kind of limitation to the present invention, or implies originally The engine 1000 of invention, which is only capable of starting in the above described manner or more, states the work of mode normal circulation.

Inventor has found, for dual fuel engine 1000, the swirl ratio of reasonable design compression ratio and combustion chamber Fuel economy, reduction discharge and improvement power output for engine 1000 have direct relation.

In view of this, with reference to shown in Figure 16-Figure 18, Figure 23, inventor is according to industry experience and many experiments for many years It was found that, by the way that by compression ratio control, between 13-17 particularly 14-16, swirl ratio is controlled between 1-6, can effectively be solved The problem of cold start of engine 1000 is difficult, while the knock problem for avoiding high compression ratio from bringing, makes engine 1000 start, transport Row is more steady, reliable, and power output is strong and has reached preferably fuel economy and relatively low noxious gas emission.

Further, with reference to shown in Figure 23, inventor has found, can be preferably by the way that swirl ratio is controlled between 1.5-5 Lift the performance of engine 1000, reduction discharge.Therefore as an alternative embodiment, the swirl ratio control of combustion chamber exists 1.5-5 between.

Wherein, in a preferred embodiment, the swirl ratio of combustion chamber is 1.7.In another preferred embodiment, The swirl ratio of combustion chamber is 1.8.In another preferred embodiment, the swirl ratio of combustion chamber is 2.

Thus, by the guiding function of cylinder wall, the gas mixture entered from air intake duct 103 in combustion chamber (or it is new Fresh air) vortex can be formed in cylinder 203, it is in by controlled vortex flow ratio between 1-6, is particularly between 1.5-5, matches somebody with somebody Higher compression ratio (such as 13-17) is closed, so as to substantially reduce burning and exhausting, while the power for increasing engine 1000 is defeated Go out.

Especially, for general vehicle, as shown in figure 23, particularly for family expenses vehicle, economic speed area exists Between 1000rpm-2000rpm, particularly in 1500rpm-2000rpm, and as can be seen from Figure 23, in engine 1000 During in below 2000rpm, swirl ratio is more excellent between 1-6 particularly 1.5-5.

Need explanation a bit, be prior art for the size for how controlling swirl ratio in cylinder 203, and be this Known to the those of ordinary skill in field.It is for instance possible to use the form of tangential and/or spiral inlet duct 103, while can also With reference to vortex valve technology, but in the present invention, for the specific setting position using the form of which kind of air intake duct 103 and swirl valve Put and be not particularly limited, for the ordinary skill in the art, the air inlet being adapted can be used as needed The form of road 103 and suitable swirl valve set location, if can realize by swirl ratio control 1-6 particularly 1.5-5 it Between.

Inventor has found that the control for compression ratio is same to the dynamic property of engine 1000, fuel economy and row Putting performance has vital effect.With reference to shown in Figure 16-Figure 18, inventor has found, by the way that compression ratio is controlled in 14.8- It is more excellent between 15.5.Therefore, according to one embodiment of present invention, compression ratio is between 14.8-15.5.

Especially, according to a preferred embodiment of the present invention, the compression ratio of engine 1000 is 15.1.According to the present invention Another embodiment, compression ratio is 15.3.

Thus, suitable swirl ratio is coordinated, such as, as preferred embodiment, compression ratio is in 14.8-15.5, swirl ratio Between 1.5-5, so as to preferably solve the problem of cold-starting of engine 1000 is difficult, it is to avoid because high compression ratio is led The phenomenon of detonation of cause, improves the fuel economy and dynamic property of engine 1000, and the discharge of pernicious gas is substantially reduced.

, wherein it is desired to which the abscissa in explanation, Figure 16-18 represents that engine 1000 is exported under rotating speed and the rotating speed Moment of torsion, ordinate represents fuel consumption, it is to be understood that under same rotational speed, fuel consumption is lower, it was demonstrated that start The fuel economy of machine is better.It can be clearly seen that when compression ratio (CR) is 14.8,15.1 and 15.5 from Figure 16-Figure 18 Significantly better than the situation that compression ratio is 13 and 17.

Piston 109 according to embodiments of the present invention is described in detail with reference to Fig. 7-Figure 15.

Because the type selecting of piston 109 is related to compression ratio, while being also related to the overall performance of engine 1000, therefore close Reason ground type selecting piston 109 is most important for engine 1000.

With reference to shown in Figure 11-Figure 14, according to some embodiments of the present invention, the top surface of piston 109 is formed with pit 111, The pit 111 collectively forms combustion chamber with the internal face of cylinder wall and the bottom surface M1 of cylinder head 101.Size, the type of pit 111 Line directly determines the construction of combustion chamber, and and then is associated with every combustion index of engine 1000.

In an embodiment of the present invention, pit 111 is preferably revolution shape, and the axis of rotation 117 of the revolving body is (as schemed Shown in 13) overlapped with the center line M2 (M2 is as shown in Figure 10) of corresponding cylinder 203, in other words, the pit 111 is formed in piston The center at 109 tops.Thus, pit 111 is centrally arranged can avoid the unbalance stress of piston 109 and cause cylinder wall local pressure Concentrate, so as to improve the problem on deformation of cylinder 203, while pit 111 can also reduce to a certain extent between two parties piston 109 with Friction between cylinder wall, the sealing between the life-span of raising piston 109 and piston 109 and cylinder wall, is reduced from piston Gap between 109 and cylinder wall and the combustion gas escaped into crankcase, it is to avoid the Some gases influence the property of crankcase inner engine oil Energy and life-span.

With reference to shown in Figure 11-Figure 13, pit 111 is cut for " ω " shape, i.e. pit 111 by the vertical of axis of rotation 117 Face is " ω " shape.Here, it is necessary to which explanation, pit 111 is that " ω " shape should broadly understood, you can be interpreted as pit 111 vertical section can be that the shape approximate with " ω " shape, the i.e. top of pit 111 should at least possess a necking spy Levy.Specific molded line on " ω " shape pit 111 will provide detailed description in conjunction with specific embodiments below.

As preferred embodiment, as shown in figure 11, the top of pit 111 has a throat structure 127, and piston 109 Relative aperture is maintained between 0.7-0.8, and the necking ratio of piston 109 is maintained between 0.8-0.9.Specifically, the bore of piston 109 The most narrow place of throat structure 127 and the ratio of the diameter of cylinder 203, i.e. relative aperture than referring to pit 111 are K4/D (wherein K4 As shown in figure 12, shown in cylinder bore D combinations Fig. 1).The necking of piston 109 is than referring to the throat structure 127 of pit 111 most Narrow place and the diameter ratio of the bottom the widest part of 111 throat structure of pit 127, i.e. necking ratio is K4/K5 (K4, K5 combination Figure 12 institutes Show).

Thus, the relative aperture and necking ratio of reasonable design piston 109 are passed through so that the relative aperture of piston 109 is maintained at Between 0.7-0.8, necking ratio is maintained between 0.8-0.9, so larger relative aperture and less necking Billy in diesel oil to Combustion chamber clearance and the diffusion in extinguishing area, advantageously reduce HC discharges.The heat transfer of combustion chamber in combustion process is also reduced simultaneously Loss, obtains fuel combustion more abundant, so as to improve the thermal efficiency of engine 1000.

The structure of pit 111 is elaborated below in conjunction with Figure 11-Figure 13.

As shown in figure 13, pit 111 is revolution shape, and revolving body has revolution bus 115 and axis of rotation 117, should Revolving body is rotated by 360 ° to be formed for revolution bus 115 around axis of rotation 117.In the example in figure 13, actually including revolution Any vertical section of axis 117, on the section, the medianly zygomorphic part of axis of rotation 117 can be used as revolution Bus 115, in the following description, is described using being located at turn around the part on the left of axis 117 as revolution bus 115.

Specifically, revolution bus 115 includes sidewall profiles section 119 and bottom wall mixing line segment 129, sidewall profiles section 119 Side wall for forming pit 111, the bottom wall mixing line segment 129 is used for the bottom wall for forming pit 111, wherein bottom wall mixing line segment 129 at least include bottom wall straightway and bottom wall curved section.

Because the line style of sidewall profiles section 119 and bottom wall mixing line segment 129 is directly connected to the shape of combustion chamber, and then It is related to thermal efficiency of engine 1000 etc..Therefore the tool of reasonable design sidewall profiles section 119 and bottom wall mixing line segment 129 The thermal efficiency and overall performance important role of the body line style to engine 1000.

With reference to shown in Figure 13, specifically, sidewall profiles section 119 can include side wall transition section 121, side wall necking section 123 and side wa ll circle arc section 125, side wall transition section 121, side wall necking section 123 and side wa ll circle arc section 125 phase successively from top to bottom Even.Side wall transition section 121 is used for the transition portion for forming connection throat structure 127 and the top surface of piston 109, side wall necking section 123 The throat structure 127 above-mentioned for being formed, side wa ll circle arc section 125 is used for the lower sidewall portions for forming combustion chamber.

Bottom wall mixing line segment 129 includes bottom wall first straight line section 131, the first arc section of bottom wall 133, bottom wall second straight line section 135th, the second arc section of bottom wall 137 and the straightway 139 of bottom wall the 3rd, wherein bottom wall first straight line section 131, the arc section of bottom wall first 133rd, bottom wall second straight line section 135, the second arc section of bottom wall 137 and the straightway 139 of bottom wall the 3rd diametrically from outside to inside according to It is secondary to be connected, and the outer end of bottom wall first straight line section 131 is connected with the lower end of side wa ll circle arc section 125.

Inventor has found, by the way that sidewall profiles section 119 and bottom wall mixing line segment 129 are set according to above-mentioned line style Meter, is conducive to diesel oil to combustion chamber clearance and the diffusion in extinguishing area, advantageously reduces the discharge of the pernicious gases such as HC.

Further, because sidewall profiles section 119 is made up of a variety of curved sections, bottom wall mixing line segment 129 is by a variety of curved sections And straightway constitute, therefore each curved section and straightway relevant parameter be directly connected to the thermal efficiency of engine 1000 with And the performance of engine 1000.

In some embodiments of the present invention, as shown in figure 13, the radius of curvature r0 of side wall transition section 121 can be 18- Between 22mm, preferably 20mm, the radius of curvature r1 of side wall necking section 123 can be between 1.5-2mm, side wa ll circle arc section 125 Radius of curvature r2 between 3.5-4.5mm, preferably between 3.5-4mm, bottom wall first straight line section 131 is preferably parallel to gas The bottom surface M1's of cylinder cap 101, the length of bottom wall first straight line section 131 can be between 3.5-4.5mm, preferably 4mm, bottom wall first The radius of curvature r3 of arc section 133 can be preferably 13mm, bottom wall second straight line 135 opposite cylinder heads of section between 11-15mm 101 inclined bottom surface is set, and slanted angle β 7 can be between 20 ° -24 °, preferably 22 °, the song of the second arc section of bottom wall 137 Rate radius r4 can be 23-27mm, and preferably 25mm, the straightway 139 of bottom wall the 3rd is preferably parallel to the bottom surface of cylinder head 101, And the straightway 139 of bottom wall the 3rd is located at the top (oblique upper) of bottom wall first straight line section 131, the i.e. straightway 139 of bottom wall the 3rd Setting height be more than the setting height of bottom wall first straight line section 131.

Above-mentioned design method can cause the relative aperture of piston 109 to be maintained between 0.7-0.8, and necking ratio is maintained at 0.8- Between 0.9, and it is a kind of more preferably embodiment, is spread beneficial to diesel oil to combustion chamber clearance, so that effectively reduction HC row Put.

In combination with shown in Figure 22, Figure 22 shows that piston 108 according to embodiments of the present invention is set using above-mentioned line style After meter, the control experiment carried out with former conventional piston as can be seen from Figure 22, causes engine using above-mentioned Alignment Design 1000 HC discharge of poisonous waste is substantially reduced, and reduces NOx, beneficial to the progress of burning, improves the abundant degree of burning.

In some embodiments of the invention, bottom of the 3rd straightway when piston 109 is in top dead centre with cylinder head 101 Face M1 distance is between 2.5mm-3.5mm, i.e. K3=2.5mm-3.5mm (as shown in figure 11), preferably 3mm, i.e. K3= 3mm.By reasonably controlling the distance (when piston 109 is in top dead centre) of the 3rd straightway and the bottom surface M1 of cylinder head 101, so that The characteristics of enabling the pit 111 to form tray type gasoline combustion, efficiency of combustion is improved, makes burning more abundant, reduction discharge.

Flow into compression clearance in order that obtaining diesel oil and conductance being preferably mixed during piston 109 compresses and quench Region is put out, as preferred embodiment, by the transition of chamfering 118 between the top surface of piston 109 and the side wall of piston 109, such as Shown in Figure 11, the angle of chamfering 118 can be 45 °, and length can be 0.5-2mm, and the compression clearance K2 of piston 109 is 1- 2.5mm.Here, compression clearance refers to piston 109 top surface of piston 109 and distance of the bottom surface of cylinder head 101 in top dead centre.

Thus, by setting chamfering 118 in the top outer rim of piston 109 and controlling the length of chamfering 118 in 0.5-2mm, together When control piston 109 compression clearance between 1-2.5mm, coordinate radius of curvature 18-22mm side wall transition section 121, this The combination design of three can make diesel oil, and gas compressed water conservancy diversion enters to compress clearance and work well in the compression process of piston 109 The extinguishing region of plug 109 and cylinder wall, enabling the ignition mixture in this region has more preferable fire behaviour, can effectively reduce HC discharge, improves the utilization rate of fuel oil, reduces oil consumption.

As preferred embodiment, the length of chamfering 118 between the top surface of piston 109 and the side wall of piston 109 is in 1- 1.5mm, the compression clearance of piston 109 is 1.5-2mm, thus enables that ignition mixture has more excellent fire behaviour, lifting The fuel economy of engine 1000, greatly reduces the discharge of pernicious gas.

With reference to shown in Figure 21, Figure 21 shows piston 108 according to embodiments of the present invention using above-mentioned compression clearance, side wall Comparability test of the combination design compared to original conventional piston progress of changeover portion 121 and chamfering 118, it can be seen from figure 21 that After above-mentioned design, the HC discharge of poisonous waste of engine 1000 can be caused to substantially reduce, NOx is reduced, beneficial to combustion The progress of burning, improves the abundant degree of burning.

To sum up, the structure of piston 109 according to embodiments of the present invention fully combines traditional diesel oil " ω " type and tray type The characteristics of gasoline combustion, by the optimization and innovative design to combustion chamber line style, dual fuel engine 1000 is met in difference To the demand of chamber structure under mode of operation.

Meanwhile, the dimensional structure structure of the top surface of the piston 109 larger relative aperture of piston 109 and less necking Than the larger compression that the structure of chamfering 118 and the top surface of piston 109 at the edge of piston 109 are produced with the cooperation of the bottom surface of cylinder head 101 Clearance is conducive to the extinguishing area that diesel oil is directed in compression process between compression clearance and piston 109 and cylinder wall, can have The reduction HC discharges of effect, improve the utilization rate of fuel.

In addition, piston 109 according to embodiments of the present invention forms shallow " ω " type on the whole, surface to volume ratio is substantially reduced, from And the external heat transfer loss in the course of the work of engine 1000 is reduced, improve the thermal efficiency of engine 1000.

In addition, the bottom surface M1 of the cylinder head 101 of engine 1000 according to embodiments of the present invention is plane, coordinate this " ω " type piston 109 and suitable swirl ratio (such as 1.5-5) and compression ratio (such as 14.8-15.5), so that on the whole The properties of engine 1000 are improved, the discharge of pernicious gas is reduced.Also, engine according to embodiments of the present invention 1000 can be transformed using Diesel engine as prototype.

Inlet valve 108, exhaust valve 110 and spark plug 105 are carried out in conjunction with specific embodiments referring to Fig. 7-Figure 10 It is described in detail.

In embodiments of the invention, spark plug 105 is arranged in cylinder head 101, and for example spark plug 105 can pass through screw thread knot Structure is fastened in cylinder head 101.The set location of spark plug 105 is related to flame travel, area of flame spreading rate, combustion Speed etc. is burnt, discharge important during for starting.

Inventor has found that as shown in Figure 10, by the way that spark plug 105 is biased, that is, the center line M2 for deviateing cylinder 203 is set Put, at the same control spark plug 105 and the intersection point of cylinder head 101 apart from the center line of cylinder 203 apart from K1 for starting when burning fire The control of flame and burn rate has beneficial effect.

Thus, in certain embodiments, spark plug 105 deviates the center line M2 settings of correspondence cylinder 203, that is to say, that The center line of spark plug 105 is misaligned with the center line M2 of corresponding cylinder 203, and preferably, spark plug 105 is to be located at Exhaust side, as shown in Figure 7.

Further, in certain embodiments, the intersection point of the bottom surface of the center line of spark plug 105 and cylinder head 101 is apart from gas The center line M2 of cylinder 203 between K1 is the diameter D of cylinder 203 0.35-0.45, i.e. K1=0.35-0.45D.

Thus, start engine 1000 when, can avoid occur phenomenon of detonation, improve area of flame spreading rate and Burn rate, balanced flame travel is prevented effectively from early combustion, while being also convenient for engine 1000 cleans waste gas, preferably changes Kind ignition difficulties problem, and substantially increase starting and low speed and load operating mode (now spark plug 105 can also participate in igniting Work) job stability.Further, since engine 1000 according to embodiments of the present invention has diesel injector 107, pass through Spark plug 105 is biased, so as to provide the useful space for the center arrangement mode of diesel injector 107, it is to avoid the two is being installed Interfered on position and influence the performance of engine 1000.

As preferred embodiment, the intersection point of the center line of spark plug 105 and the bottom surface of cylinder head 101 is apart from cylinder The distance of 203 center line is i.e. K1=0.375-0.425D between the 0.375-0.425 of the diameter of cylinder 203.

In an embodiment of the present invention, as shown in fig. 7, the first end of spark plug 105 is extend into corresponding cylinder 203, Second end of spark plug 105 is through the corresponding exhaust duct 104 of the cylinder 203 and stretches out, and stretching out here is referred to To the direction extension away from combustion chamber.By this arrangement, can make it that the structure of cylinder head 101 is compacter, at the same avoid with Diesel injector 107 is interfered, and spark plug 105 can save arrangement space to the maximum limit through exhaust duct 104, while right Influence smaller in exhaust performance, substantially increase the space availability ratio of the top surface of cylinder head 101.

As the embodiment further optimized, as shown in figure 8, the corresponding exhaust duct 104 of each cylinder 203 is two, two The afterbody of individual exhaust duct 104 is close to each other and close to form common-use tunnel 112, and the second end of spark plug 105 can be passed through should Common-use tunnel 112 simultaneously stretches out.So, spark plug 105 is located at the center of two exhaust ducts 104 so that cylinder head 101 it is whole Body structure is compacter, and space availability ratio is higher, beneficial to the volume that body group takes is reduced, specifically for valve actuating mechanism and diesel oil The arrangement of fuel injector 107 is provided convenience.

Inventor has found, for conventional engines 1000, and its spark plug 105 is general centrally arranged, and spark plug 105 Center line overlapped with the center line of cylinder 203.And the biasing of spark plug 105 is set in the application, therefore the setting of spark plug 105 Angle can produce certain influence to area of flame spreading rate and burn rate.

Inventor has found that this case can be improved by being obliquely installed spark plug 105, therefore in the implementation of the present invention In example, the cylinder 203 corresponding relative to the spark plug 105 of spark plug 105 is obliquely installed, i.e. the center line and gas of spark plug 105 The center line of cylinder 203 be it is not parallel, as shown in Figure 10.

Further, in certain embodiments, as shown in Figure 10, the center of the center line of spark plug 105 and corresponding cylinder 203 The angle β 6 of line is between 20 ° -30 °.Thus, it is possible to improve area of flame spreading rate and burn rate, balanced flame is passed Distance is broadcast, early combustion is prevented effectively from, while being also convenient for engine 1000 cleans waste gas, preferably improves ignition difficulties problem.

Spark plug 105 is also helped through exhaust duct 104 in addition, spark plug 105 is obliquely installed, it is to avoid with valve actuating mechanism Interfered etc. structure.

As preferred embodiment, as shown in Figure 10, the center line of the center line of spark plug 105 and corresponding cylinder 203 Angle β 6 between 23 ° -26 °.

Thus, not only it is possible to prevente effectively from liquid fuel collision spark plug 105 and mixing to the supply overrich of spark plug 105 Close gas and carbon distribution is formed on spark plug 105, the cooling effect also weighed near spark plug 105.Simultaneously by using diesel oil The arrangement form of fuel injector 107 and the larger spacing of spark plug 105, and spark plug 105 is in tilted layout in exhaust side, so that beneficial to carrying High area of flame spreading rate and burn rate, balanced flame travel, so as to preferably avoid early combustion.In addition, this Angle design is also most beneficial for through exhaust duct 104, it is to avoid interfered with other structures.

Inlet valve 108 and exhaust valve 110 are described with reference to Fig. 9.

Due to not only to arrange diesel injector 107 in cylinder head 101 according to embodiments of the present invention, while also to arrange Spark plug 105, thus it is higher to the structural requirement of cylinder head 101, while also increasing the arrangement difficulty of valve actuating mechanism.

With reference to shown in Fig. 7 and Fig. 9, because inlet valve 108 closes the air inlet 102 of the end of air intake duct 103 (at combustion chamber) And the center line of inlet valve 108 is substantially orthogonal with the air inlet 102, similarly, the closing exhaust duct 104 of exhaust valve 110 Exhaust outlet 106 and the center line of exhaust valve 110 of the end (at combustion chamber) are substantially orthogonal with the exhaust outlet 106, therefore air inlet The setting angle of door 108 and exhaust valve 110 reflects the air inlet 102 and the bottom surface M1 of cylinder head 101 and exhaust outlet indirectly Angle between 106 and the bottom surface M1 of cylinder head 101.

For example, with perpendicular M3 (M3 such as Fig. 9 institutes of inlet valve 108 and the longitudinal centre line 200 by engine 1000 Show) angle be that exemplified by 5 °, then the angle of the inlet valve 108 and the bottom surface M1 of cylinder head 101 is 85 ° or so, and due to the air inlet Mouth 102 is substantially orthogonal with inlet valve 108, therefore the air inlet 102 and the angle of the bottom surface of cylinder head 101 are at 5 ° or so, from And can consider that air intake duct 103 is particularly the endpiece of air intake duct 103 and the bottom surface angle of cylinder head 101 is 5 ° or so.

Similarly, so that exhaust valve 110 and above-mentioned perpendicular M3 angle are 5 ° as an example, then the exhaust valve 110 and cylinder The bottom surface M1 of lid 101 angle is 85 ° or so, and because the exhaust outlet 106 and exhaust valve 110 are substantially orthogonal, therefore the row Gas port 106 and the angle of the bottom surface of cylinder head 101 are at 5 ° or so, so as to think that it is initial that exhaust duct 104 is particularly exhaust duct 104 The bottom surface angle of section and cylinder head 101 is 5 ° or so.

In short, the setting angle of inlet valve 108 and exhaust valve 110 reflects exhaust duct 104 indirectly (is particularly exhaust duct 104 endpiece, it is believed that be exhaust outlet 104) and air intake duct 103 (it is particularly the initial segment of air intake duct 103, it is believed that Air inlet 102) with the angle of the bottom surface of cylinder head 101.That is, as shown in figure 9, can approx think β 1=β 4, β 2=β 5.

And based on this, inventor has found, by rationally designing air intake duct 103 (reflection air inlet 102 indirectly), exhaust duct Angle of 104 (the reflection exhaust outlets 106 indirectly) with the bottom surface M1 of cylinder head 101, so that cylinder head 101 can not only be conveniently designed, The design for reducing the internal structure (being, for example, diesel injector 107, spark plug 105, various air flues, water jacket) of cylinder head 101 is difficult Degree, while especially, by rationally designing the angle, preferably being spread so as to ensure that engine 1000 is respectively provided with each rotating speed The mixing rate of combustion phases, and turbulence intensity can be increased when reaching in certain limit, and then beneficial to the suitable of combustion process Profit is carried out, while reducing smoke intensity.

Inventor has found, by by air inlet 102 and exhaust outlet 106 be designed to the bottom surface M1 of cylinder head 101 angle β 4, β 5 respectively between 0 ° -6 °, to combustion process be smoothed out and the reduction of smoke intensity has remarkable result.Therefore, in this hair In some bright embodiments, the center line of inlet valve 108 is with the perpendicular M3's of the longitudinal centre line by engine 1000 Angle β 2 is between 0 ° -6 °, similarly, the center line of exhaust valve 110 and perpendicular M3 angle β 1 also 0 ° -6 ° it Between.

Thus, the angle between inlet valve 108 and exhaust valve 110 be less than 12 °, i.e. valve angle relative narrower, it is this compared with Narrow valve angle can make the compact conformation of cylinder head 101, reduce cooling loss and obtain optimal surface area/volume.

As preferred embodiment, the angle β 3 between the center line of inlet valve 108 and the center line of exhaust valve 110 exists In 10 °., wherein it is desired to which explanation, inlet valve 108 and the angle of exhaust valve 110 here are referred in the horizontal stroke of engine 1000 The inlet valve 108 and exhaust valve 110 corresponded to each other upwards.As a result, the structure of cylinder head 101 is compacter, while energy It is enough preferably to reduce cooling loss and obtain optimal surface area/volume.

Diesel injector 107 according to embodiments of the present invention is described in detail with reference to Fig. 7, Figure 19-Figure 20.

Shown in reference picture 7, the center line of diesel injector 107 is overlapped with the center line of corresponding cylinder 203, i.e., diesel oil sprays Oily device 107 is centrally arranged.Thus, diesel injector 107 can equably spray diesel fuel into combustion chamber, be occupied while coordinating " ω " the type pit 111 of middle arrangement, can cause diesel fuel to be more equally distributed in combustion chamber, form average gaseous mixture, Beneficial to abundant burning.

Inventor has found, the spray cone angle of diesel injector 107 to soot, NOx (emission index of oxynitrides) and Three Index Influences of engine 1000 of fuel consumption are notable.With reference to shown in Figure 19-Figure 20, inventor is sent out by many experiments Existing, by the way that the cone angle of diesel injector 107 is controlled when between 70 ° -85 °, soot emission levels are relatively low, while NOx reduction, I.e. oxynitride discharge is reduced, while fuel consumption also decreases.

With reference to shown in Figure 19 and Figure 20, Figure 19 and Figure 20 give engine 1000 and are under different rotating speeds (two kinds of operating modes) The comparison diagram of multigroup spray cone angle of diesel injector 107, i.e. spray cone angle are respectively 65 °, 70 °, 75 °, 78 °, 78.5 °, 85 ° With 90 °, and each spray cone angle corresponds to three measurement indexs, and soot (pollutant, soot), Nox are followed successively by from left to right (, oxynitride discharge rate) and ISFC (fuel consumption), it should be apparent that spray cone angle from Figure 19-Figure 20 Three indexs are less than normal when more than 70 °, less than 85 °, i.e., be 65 ° and 90 ° less than spray cone angle.

Further, as shown in Figure 19-Figure 20, as preferred embodiment, the spray cone angle of diesel injector 107 exists Between 75 ° -80 ° preferably.Wherein, as one preferred embodiment, the spray cone angle of diesel injector 107 is 75 °.Another One preferred embodiment in, the spray cone angle of diesel injector 107 is 78 °.Another preferred embodiment in, bavin The spray cone angle of oily fuel injector 107 is 78.5 °.

Thus, with reference to the centrally arranged mode of diesel injector 107 so that diesel oil oil beam is evenly distributed in combustion chamber, keeps away Exempt from each oily Shu Changdu to differ and cause gaseous mixture lack of homogeneity, influence burning, while suitable spray cone angle can be reduced effectively Soot, NOx and fuel consumption, increase the power output of engine 1000, fuel economy on the whole, improve engine 1000 thermal efficiency, reduces the discharge of pernicious gas.

To sum up, with reference to spark plug 105 arrangement, the line style of pit 111, swirl ratio, compression ratio and the bavin of piston 109 Spray cone angle of oily fuel injector 107 etc. so that the petrol gas of engine 1000 according to embodiments of the present invention, diesel oil oil gas and Air can preferably form homogeneous charge, realize homogeneous combustion, and flame combustion is abundant, relative to the diffusion combustion of diesel oil, Improve the efficiency of combustion in the starting process of engine 1000, emission effect when reduction engine 1000 is started, and compared to For gasoline engine, high compression ratio can further improve efficiency of combustion, increase the power performance and fuel-economy of engine 1000 Property.

Body group part according to embodiments of the present invention is described in detail below with reference to Fig. 1-Fig. 6, due to according to of the invention real The engine 1000 for applying example is dual fuel engine, different from traditional gasoline engine and diesel engine, for example, there is inner pressure of air cylinder The problems such as outburst is big, cylinder wall mutability, body group short life, it is therefore desirable to redesigned to body group, with suitable Answer double fuel combustion mode.

The part of cylinder block 201 is described in detail below in conjunction with specific embodiment.

Cylinder 203 has cylinder wall, and the internal face of cylinder wall is cylindrical wall.The cross section of cylinder wall (is orthogonal to gas The section of cylinder centerline direction) it is annular, wherein Fig. 4 shows the cross section of cylinder wall according to an embodiment of the invention Schematic diagram.The outside of cylinder wall can be block jacket, and cooling water can flow and be connect with cylinder wall in block jacket Heat exchange is touched, so as to reduce the operating temperature of cylinder 203 and the inner carrier of cylinder 203.

Reference picture 1 and with reference to shown in Fig. 4, the ring section of cylinder wall is circumferentially divided into four sections of segmental arcs being sequentially connected 205th, 207,209,211, i.e. the first segmental arc 205, the second segmental arc 207, the 3rd segmental arc 209 and the 4th segmental arc 211.And And every section of segmental arc is further divided into first paragraph 213, second segment 215 and the 3rd section 217, wherein the 3rd section of each segmental arc 217 apart from engine longitudinal centre line 200 it is farthest, the first paragraph 213 of each segmental arc apart from the longitudinal centre line 200 most Closely, as shown in Figure 4.

In other words, with reference to shown in Fig. 4, the first paragraph 213 of the segmental arc 211 of first paragraph 213 and the 4th of the first segmental arc 205 It is connected, and junction is on longitudinal centre line 200, the 3rd section 217 of the first segmental arc 205 and the second segmental arc 207 It is connected for 3rd section 217, and junction is the ring section apart from the farthest of longitudinal centre line 200.Similarly, the second segmental arc 207 first paragraph 213 is connected with the first paragraph 213 of the 3rd segmental arc 209, and junction is on longitudinal centre line 200, the The 3rd section 217 of three segmental arcs 209 is connected with the 3rd section 217 of the 4th segmental arc 211, and junction be the ring section away from From the farthest of longitudinal centre line 200.

Wherein, as shown in figure 4, the corresponding central angle of first paragraph 213 is α 1 and wall thickness is h1, the corresponding circle of second segment 215 Heart angle is α 2 and wall thickness is h2, and the 3rd section of 217 corresponding central angle is α 3 and wall thickness is h3.Explanation is needed a bit, in showing for Fig. 4 In example, its first paragraph, second segment and the 3rd section are marked only by taking the 3rd segmental arc 209 as an example, and the first segmental arc 205th, the second segmental arc 207 and the 4th segmental arc 211 have the structure as the 3rd segmental arc 209, therefore in Fig. 4 simultaneously Do not mark one by one.

Wherein α 1, α 2 and α 3 meet relational expression：α 1+ α 2+ α 3=90 °.Thus, the arc length of four sections of segmental arcs is equal , i.e., the corresponding central angle of every section segmental arc is 90 °, so that the cross section of each cylinder 203 has the symmetry of height, such as Shown in Fig. 4.

Further, h1, h2 and h3 meet one of following relationship：H1 ＜ h2≤h3, h1≤h2 ＜ h3.In other words, distance The 3rd section 217 farthest of thickness of longitudinal centre line 200 compares the thickness of the first paragraph 213 nearest apart from longitudinal centre line 200 Will thickness, i.e., according to from first paragraph 213 towards the 3rd section 217 of direction, the thickness presentation of each segmental arc gradually it is thickening substantially Variation tendency.

So, it can be seen from the radial load of piston suffered by cylinder 203, piston suffered by the cylinder wall of each cylinder 203 applies Power be with the increase of the distance of longitudinal centre line 200 and it is gradually increased, i.e., closer to longitudinal centre line 200, cylinder wall Stress it is relatively smaller, and further away from longitudinal centre line 200, the stress of cylinder wall is relatively bigger.

So as to, by being designed to that thickness is relatively most thick by the 3rd section 217, first paragraph 213 be designed to thickness it is relatively most thin, the Two section 215 of thickness be designed between first paragraph 213 and the 3rd section 217 (or alternatively, second segment 215 be designed to First paragraph 213 and the 3rd section one of 217 it is equal), so that cylinder wall stress the best part intensity is significantly improved, Ke Yigeng The deformation of cylinder wall at this is prevented well, and for the relatively small part of stress, then wall thickness is relatively thin, reduces body group Quality and volume, and also avoid blindly cylinder wall is thickeied and cause cylinder 203 cooling deficiency.

In short, the internal face of the cylinder wall of cylinder 203 according to embodiments of the present invention is cylinder, outside wall surface is near Like the Irregular Boundary Surface (as shown in Figure 4) of cylinder, the Irregular Boundary Surface causes cylinder wall thickening in the larger part of stress, and In the less parts thinner of cylinder wall stress, thus improve cylinder 203 deform and cylinder 203 cooling effect, while Reduce the quality and size of body group.

It should be noted that each in above-mentioned first paragraph 213, second segment 215 and the 3rd section 217 such as can be at the wall thickness Structure, naturally it is also possible to be wall thickness grading structure, or can also be the combination of the two.But need to meet second segment 215 not Less than the thickness of first paragraph 213, the thickness for being not less than second segment 215 for the 3rd section 217, and exclude three sections of thickness equal feelings It is in increasing trend that condition, i.e. first paragraph 213, second segment 215 and the 3rd section 217 of thickness, which are generally, is incremented by then gradual change Or jumping characteristic incrementally then can adaptive settings as the case may be, this for the ordinary skill in the art, Should all it will be appreciated that.

Inventor has found that reasonable design h1, h2 and h3 not only can effectively lower the quality and volume of body group, keep away Exempt from body group quality blindly caused by the wall thickness of increase cylinder wall it is excessive, the problems such as cylinder 203 cools down deficiency, while can also change The deformation of kind cylinder 203, and targetedly increase intensity for yielding region.

In view of this, inventor has found, when h1, h2 and h3 meet following relationship respectively, can not only play increase gas The purpose of intensity of casing wall, improves the problem on deformation of cylinder 203, while the quality and wall thickness that can also take into account body group are blocked up caused Cylinder 203 cool down deficiency, wherein 6.5mm≤h1≤7mm, 7mm≤h2≤7.5mm, 7.5mm≤h3≤9.5mm.

Thus, in the region of first paragraph 213, because wall thickness is relatively thin, it is possible to reduce in the corresponding water jacket of the part-structure Cooling water flow resistance, reduce the pressure loss.Meanwhile, by by the wall thickness control in the region of second segment 215 7-7.5mm it Between, the mutation of cooling water flow velocity in water jacket can be avoided, cylinder 203 can be reduced again and deformed.Further, by by the 3rd section 217 thickness is processed into maximum, so that the intensity of cylinder wall stress maximum part is added well, and then better against Deformation.It is understood that being preferred to use in first paragraph 213, second segment 215 and the 3rd section 217 between any two sections smoothed The mode of crossing carries out transition, is so easy to casting to process.

In some alternative embodiments of the present invention, the wall thickness of each segmental arc is according to the first paragraph 213 from the segmental arc The 3rd section 217 of the direction towards the segmental arc is gradually thickening, in other words, first paragraph 213 apart from second segment 215 farther out one End is most thin, and the 3rd section 217 one end apart from second segment 215 farther out is most thick, i.e. the thickness of cylinder wall cross section appears in gas At the both lateral sides of cylinder 203.Thus, the purpose of the increase intensity of cylinder 203 can be equally played, improves the problem on deformation of cylinder 203, The blocked up caused cylinder 203 of quality and wall thickness that body group can also be taken into account simultaneously cools down deficiency.

Inventor has found that reasonable design α 1, α 2 and α 3 can equally lower the quality and volume of body group, but also can To improve the deformation of cylinder 203, increase the life-span of engine.In view of this, inventor has found, under α 1, α 2 and α 3 are met respectively Row relational expression, can play the purpose of increase cylinder wall intensity, improve the problem on deformation of cylinder 203, wherein 1≤40 ° of 30 °≤α, 3≤40 ° of 2≤25 ° of 15 °≤α, 30 °≤α.

As preferred embodiment：α 1=35 °, α 2=20 °, α 3=35 °.Thus, first paragraph 213, second segment are coordinated 215 and the 3rd section 217 wall thickness design, i.e. 6.5mm≤h1≤7mm, 7mm≤h2≤7.5mm, 7.5mm≤h3≤9.5mm, from And can preferably increase the intensity of cylinder wall, improve the problem on deformation of cylinder 203, while can also take into account body group quality and The blocked up caused cylinder 203 of wall thickness cools down deficiency.

The sidewall shape of body group is described in detail with reference to the specific embodiment shown in Fig. 1-Fig. 5.

For conventional engines, the side wall of its body group typically all uses straight design method, and (i.e. side wall is flat Face).It can so cause that the quality of body group is big, space-consuming is more, for space arrangement requirement severe enging cabin increasingly Speech, the volume of engine how is reduced on the premise of engine properties are not influenceed turns into a kind of trend, while this The problem of also there is cylinder mutability for the body group of plane in side wall.

In some embodiments of the invention, (wherein Fig. 3 is Fig. 1 simplification view), cylinder with reference to shown in Fig. 1 and Fig. 3 The first side wall 219 of the side of body 201 first and the second sidewall 221 of the side of cylinder block 201 second are respectively formed as waveform.Here, It should be noted that the first side wall 219 and second sidewall 221 are the side walls of the first half of cylinder block 201, i.e., on crankcase The sidewall sections of side.By the way that the first side wall 219 and second sidewall 221 are set into waveform, so as to improve body group Intensity, improves the problem on deformation of cylinder 203.

Wherein, the first side wall 219 is symmetrical on the longitudinal centre line 200 of engine with second sidewall 221, is thus easy to casting Processing is made, and makes the Mass Distribution of engine more uniform, it is to avoid the defect of local quality concentration occurs so that engine is run It is more steady.

On wavy sidewalls, with reference to shown in Fig. 1 and Fig. 3, the waveform is made up of two kinds of arc sections, i.e. the first arc section 223 and second arc section 225, the first arc section 223 and the second arc section 225 are alternately arranged and are sequentially connected, in other words, two Connected between first arc section 223 between second arc section 225, and two the second arc sections 225 and be connected with one first Arc section 223.

Wherein the first arc section 223 is formed as raised type circular shape, and the second arc section 225 is formed as concave circular arc Shape, and the first arc section 223 and the second arc section 225 are tangent in junction.Thus, the first arc section 223 and the second circular arc 225 transitions smooths of section, it is easy to process.

Each first arc section 223 is relative with corresponding cylinder 203 in the transverse direction of engine, specifically, such as Fig. 3 and knot Close shown in Fig. 1, the first arc section 223 is relative with the 3rd section 217 in the horizontal.Thus, block jacket can on the one hand be ensured It is unlikely to narrow, reduces the flow resistance of cooling water, on the other hand can also play a part of assistant reinforcement to cylinder 203, prevent Cylinder 203 deforms.

Inventor's discovery, the curvature of the arc section 225 of radius of curvature R 1 and second of the first arc section of reasonable design 223 Radius R2 plays vital effect to the reinforcement of cylinder 203 down to the reinforcement of whole body group.In view of this, invention human hair Existing, the ratio of the radius of curvature R 1 of the arc section 223 of radius of curvature R 2 and first of the second arc section 225 meets 2≤R2/R1≤3 When, the deformation of cylinder 203 can be effectively improved, the life-span of engine is improved.

Further, as preferred embodiment, R2 and R1 ratio further meet relational expression：2.1≤R2/R1≤ 2.5.Thus, it is possible to further improve the problem on deformation of cylinder 203, compared to conventional planar side wall construction, body is both alleviated The weight and occupancy volume of group, while in turn ensure that body group particularly sidewall sections have sufficient strength and stiffness, can To be effectively prevented from problem on deformation caused by the discontinuity of cylinder 203 that lateral wall pressure skewness is caused.

In certain embodiments, as shown in Fig. 2 the top of cylinder block 201 is additionally provided with top plate 227, the thickness of top plate 227 Ratio for h4, a diameter of D of cylinder 203, wherein h4 and D meets relational expression：0.15≤h4/D≤0.19.Thus, by with Multiplex shape wave side wall construction, can further reduce the inhomogeneities of the stress of cylinder 203, so as to substantially reduce the change of cylinder 203 Shape.

Reinforcement based on the sectional dimension of cylinder 203 above, wavy sidewalls and the thickness of top plate 227 etc. to cylinder 203 Effect, inventor has found that the deformation of cylinder 203 is a composite factor, and exists from the aspect of combustion mode, in cylinder 203 big The average gaseous mixture of amount, should reduce the wet wall problem that high-eddy intensity is caused, while improving combustion gas again in cylinder 203 Fogging degree, realizes efficient burning.

Meanwhile, inventor also found, in traditional arrangement, by piston in top dead centre and lower dead center motion process, piston A ring cover region as water jacket depth, so most of heat can be scattered and disappeared by water jacket, so that water jacket is taken away excessively The upper and lower part of cylinder 203 can be caused to form certain thermograde while heat, so as to exacerbate the thermal change of cylinder 203 Shape.

In view of this, inventor has found that the depth of block jacket is by industry experience for many years and substantial amounts of experiment The piston 75%-85% that its first piston ring walks overtravel in top dead centre and lower dead center is optimal, as shown in Figure 6.In other words, gas The depth of cylinder body water jacket is h5, and the piston of engine (or is moved to during lower dead center is moved to from top dead centre from lower dead center During stop) first piston ring on piston (apart from nearest one of piston-top surface in multiple piston rings on piston side perisporium) Stroke meet relational expression for h6, wherein h5 and h6 ratio：0.75≤h5/h6≤0.85.

Thus, by controlling the depth of block jacket, reduction cooling loss, reduction cylinder 203 is served and deforms, improve The purpose of efficiency of combustion.And especially, with reference to shown in Fig. 6, by controlling h5 and h6 ratio to meet relational expression：0.75≤ H5/h6≤0.85, the pressure result for reducing cylinder wall is substantially deformed so as to substantially improve cylinder 203.

For explosive force is higher or engine of high compression ratio for, such as dual fuel engine, combustion chamber Interior pressure is high, therefore has strict requirements for the bolt for fastening cylinder block 201 and cylinder head, if fastening is not It is firm, gas leakage between cylinder block 201 and cylinder head may be caused, the performance of engine is had a strong impact on.

Specifically, with reference to shown in Fig. 5, body group according to embodiments of the present invention, its cylinder block 201 and cylinder head are to pass through Such as bolt fastening of threaded fastener 229, and alternatively, four threaded fasteners 229 of each correspondence of cylinder 203.

Four threaded fasteners 229 are looped around the periphery of corresponding cylinder 203 and can be distributed in four friendships of rectangle At point (as shown in Figure 5).So, fixed effect can be improved, and then increases the sealing between cylinder block 201 and cylinder head.

Further, inventor has found, fore-and-aft distance (L1) and the corresponding cylinder 203 of two threaded fasteners 229 of homonymy Centre-to-centre spacing be consistent, thereby may be ensured that the thrust between two longitudinal screw fasteners 229 is evenly distributed on front and rear two On individual cylinder 203.And then can need to be adjusted within the specific limits according to specific arrangement for horizontal spacing arrangement (L2), If horizontal spacing (L2) selection is excessive, sealed thin weakness will be turned at the closest local place of adjacent two cylinder 203, it is difficult to close High-pressure gas at the ridge area of two cylinder 203 is sealed, and horizontal spacing (L2) chooses too small, will cause cylinder 203 apart from longitudinal center The sealing of the farthest of line 200 is difficult, while also resulting in the closest region unbalance stress of adjacent two cylinder 203, causes gas Cylinder 203 is deformed seriously.

In view of this, inventor has found, by reasonable design longitudinal pitch and the ratio of horizontal spacing, can obtain good Good fastening and sealing effectiveness.As a kind of embodiment, the control of the ratio between lateral separation and fore-and-aft distance 0.95-1.15 it Between it is more excellent.In other words, longitudinal length of the rectangle that four threaded fasteners 229 are distributed along engine is L1, rectangle edge hair The horizontal width of motivation is L2, so that 0.95≤L2/L1≤1.15.

Thus, by reasonable Arrangement threaded fastener 229, so that under the conditions of assembling operating mode, thermal stress operating mode etc. So that the pretightning force of threaded fastener 229 is evenly distributed in into the top surface of cylinder 203, reach pretightning force rationally cover cylinder block 201, The purpose in gap between cylinder head, greatly improves the sealing between cylinder block 201 and cylinder head, prevents the high temperature in combustion chamber Gas leak, it is ensured that engine can normally, stable operation.

Particularly as one of them preferred embodiment, L2/L1=0.95.It is used as another preferred embodiment party Formula, L2/L1=1.As another preferred embodiment, L2/L1=1.15.

On the distribution situation of threaded fastener 229, in other optional embodiments, each correspondence of cylinder 203 Four threaded fasteners 229 can also be equal with the distance of the center line of corresponding cylinder 203, so each threaded fastener 229 uniform forces, it is to avoid the single or stress of partial threads fastener 229 is concentrated and causes the threaded fastener 229 to occur running Phenomenon, the sealing and engine reliability of operation of influence cylinder block 201 and cylinder head.

For body group and the booster action of cylinder 203, it can also be realized by setting reinforcement structure.Especially for Sidewall sections at cylinder head jacket, due to permission spatially, can be entered by setting up reinforcement structure such as deep floor One step improves block jacket down to the intensity and rigidity of whole body group.

For deep floor can be set respectively on the first side wall 219 and second sidewall 221 of body group, the deep floor It can be one and longitudinally arranged, naturally it is also possible to be a plurality of and be spaced apart from each other along the short transverse of engine.Every adds Strong floor can be continuous in the vertical, naturally it is also possible to disconnect as needed.Two can be set below every floor The inclined floor of bar, so as to constitute stool formula rib structure, reduces the unbalance stress of cylinder 203 that block jacket intensity deficiency is caused It is even, and then preferably increase the intensity of cylinder 203, prevent cylinder 203 from deforming.

In addition, producing additional moment, Ke Yi for the interphase interaction for reducing threaded fastener 229 and bolt of main bearing cap Increase the floor of one or more above-below direction between threaded fastener 229 and bolt of main bearing cap, reduce because of addition bend power The cylinder 203 that square is caused is deformed.

In addition, deformed to reduce the cylinder 203 caused by crankcase mode difference, can on the outside of crankcase domes cloth Put one or more horizontal ribbed, and increase horizontal ribbed auxiliary rib structure, to form cross one another network structure, drop The low cylinder 203 caused by mode difference.

As preferred embodiment, the height that above-mentioned floor protrudes corresponding wall should control the 2- in the floor thickness 3 times or so, preferably 2.5 times or so, thus stiffening effect is obvious.For example, by taking the deep floor on the first side wall 219 as an example, The height that the deep floor protrudes the surface of the first side wall 219 is 2.5 times of the deep floor thickness more excellent.

To sum up, body group according to embodiments of the present invention, by the improvement of structure so as to effectively increase the strong of cylinder 203 Degree and rigidity, can effectively prevent the deformation of cylinder 203, it is ensured that engine can be stablized, Effec-tive Function, improve the combustion of engine Oily economy and power output performance.Body group according to embodiments of the present invention is particularly suitable for dual fuel engine, such as vapour Oily Diesel Dual-Fuel Engine.

In addition, embodiments in accordance with the present invention, which are further provided, includes the vehicle of engine 1000 as described above.Should When understanding, other compositions of vehicle according to embodiments of the present invention are equal such as driving system, steering, brakes Prior art and to be well known for ordinary skill in the art, therefore province is entered herein to the detailed description of conventional construction Slightly.

In the description of this specification, reference term " one embodiment ", " some embodiments ", " example ", " specifically show The description of example " or " some examples " etc. means to combine specific features, structure, material or the spy that the embodiment or example are described Point is contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not Identical embodiment or example must be directed to.Moreover, specific features, structure, material or the feature of description can be with office What combined in an appropriate manner in one or more embodiments or example.In addition, those skilled in the art can say this Not be the same as Example or example described in bright book are engaged and combined.

Although embodiments of the invention have been shown and described above, it is to be understood that above-described embodiment is example Property, it is impossible to limitation of the present invention is interpreted as, one of ordinary skill in the art within the scope of the invention can be to above-mentioned Embodiment is changed, changed, replacing and modification.

Claims (9)

1. a kind of body group for engine, it is characterised in that including：

Cylinder head；And

There is at least one cylinder, the internal face of the cylinder wall of the cylinder is cylindrical wall in cylinder block, the cylinder block, The cross section of the cylinder wall is annular, and the annular is circumferentially divided into four sections of segmental arcs being sequentially connected, every section of arc Section is further divided into first paragraph, second segment and the 3rd section, and the corresponding central angle of the first paragraph is α 1 and wall thickness is h1, and described the Two sections of corresponding central angles are α 2 and wall thickness is h2, and the 3rd section of corresponding central angle is α 3 and wall thickness is h3, wherein each The longitudinal centre line of engine described in 3rd segment distance of the segmental arc is farthest, and the first paragraph of each segmental arc is apart from institute State longitudinal centre line recently, wherein

α 1, α 2 and α 3 meet relational expression：

α 1+ α 2+ α 3=90 °；

H1, h2 and h3 meet one of following relationship：H1 ＜ h2≤h3, h1≤h2 ＜ h3；

Meanwhile, h1, h2 and h3 meet following relationship respectively：

6.5mm≤h1≤7mm,

7mm≤h2≤7.5mm,

7.5mm≤h3≤9.5mm。

2. the body group according to claim 1 for engine, it is characterised in that the wall thickness of each segmental arc is pressed It is gradually thickening according to the 3rd section of direction of the first paragraph from the segmental arc towards the segmental arc.

3. the body group according to claim 1 for engine, it is characterised in that α 1, α 2 and α 3 meet relation respectively Formula：

1≤40 ° of 30 °≤α,

2≤25 ° of 15 °≤α,

30°≤α3≤40°。

4. the body group according to claim 1 for engine, it is characterised in that α 1=35 °, α 2=20 °, α 3= 35°。

5. the body group according to claim 1 for engine, it is characterised in that the first of the side of cylinder block first Side wall and the second sidewall of the side of cylinder block second are respectively formed as on the symmetrical waveform of the longitudinal centre line, described Waveform has the first arc section and the second arc section, and first arc section is in the transverse direction of the body group with the described 3rd Section is relative, and second arc section is connected between two neighboring first arc section.

6. the body group according to claim 5 for engine, it is characterised in that the curvature of first arc section half Footpath is R1, and the radius of curvature of second arc section meets relational expression for R2, wherein R2 and R1 ratio：

2.1≤R2/R1≤2.5。

7. the body group according to claim 1 for engine, it is characterised in that also set up at the top of the cylinder block There is top plate, the thickness of the top plate meets relational expression for h4, a diameter of D of the cylinder, wherein h4 and D ratio：

0.15≤h4/D≤0.19。

8. the body group according to claim 1 for engine, it is characterised in that be provided with cylinder in the cylinder block Body water jacket, the depth of the block jacket is h5, the piston of the engine institute during lower dead center is moved to from top dead centre State the stroke of the first piston ring on piston and meet relational expression for h6, wherein h5 and h6 ratio：

0.75≤h5/h6≤0.85。

9. a kind of engine, it is characterised in that including the body for engine according to any one of claim 1-8 Group.