CN105020019A - Engine - Google Patents

Abstract

The invention discloses an engine. The engine comprises a crank-link mechanism, a diesel oil injector, a gasoline injector and an air distribution mechanism, wherein the crank-link mechanism comprises an engine body unit, a piston connecting rod unit and a crankshaft flywheel unit; at least one air cylinder is arranged inside an air cylinder body of the engine body unit; an air charging passage and an air discharging passage corresponding to each air cylinder are formed in an air cylinder cover of the engine body unit; the bottom surface of the air cylinder cover is a plane; each air cylinder is correspondingly provided with at least one diesel oil injector; the gasoline injector is used for injecting gasoline fuel; the air distribution mechanism comprises an air charging valve and an exhausting valve corresponding to each air cylinder; each of the air charging valve and the exhausting valve is used for opening or closing a corresponding combustion chamber, wherein the swirl rate of the combustion chamber is ranged from 1 to 6, and the compression ratio is ranged from 13 to 17. By reasonably controlling the compression ratio and the swirl rate, the engine disclosed by the invention has the advantages of achieving a relatively good combustion effect and being beneficial for improving the combustion efficiency, the power output performance and the fuel economy of the engine.

Description

Motor

Technical field

The present invention relates to automotive field, especially relate to a kind of motor.

Background technique

The body group of motor comprises cylinder head, cylinder head gasket, cylinder block and oil sump.Be formed with multiple cylinder in cylinder block, piston can do reciprocating linear motion in cylinder.Conventional gasoline engin poor thermal efficiency, high not as diesel engine combusts efficiency, and diesel engine emissions is higher, time especially for cold-starting, noxious gas emission is multiplied, and there is the problem of cold-starting difficulty.

Summary of the invention

The present invention is intended to solve one of above-mentioned technical problem of the prior art at least to a certain extent.For this reason, one object of the present invention is to propose a kind of motor, particularly a kind of duel fuel engine, and this motor has suitable compression ratio and swirl rate, and combustion efficiency is high, power character is strong and fuel economy is good.

According to the motor of the embodiment of the present invention, comprise: connecting rod, described connecting rod comprises body group, piston connecting rod unit and crankshaft-flywheel group, in the cylinder block of described body group, there is at least one cylinder, be formed with the intake duct corresponding with each described cylinder and air outlet flue in the cylinder head of described body group, the bottom surface of described cylinder head is plane; Diesel injector, each described cylinder correspondence arranges diesel injector described at least one; For the gasoline ejector of injected petrol fuel; And distribution device, described distribution device comprises intake valve and the exhaust valve of corresponding each described cylinder, each in described intake valve and described exhaust valve is all used to open or close corresponding firing chamber, and the swirl rate of wherein said firing chamber is between 1-6, and compression ratio is between 13-17.

According to the motor of the embodiment of the present invention, by reasonably controlling compression ratio and swirl rate, thus preferably firing effect can be obtained, being beneficial to the combustion efficiency, Power output performance and the fuel economy that improve motor.

In addition, according to the motor of the embodiment of the present invention, following additional technical feature can also be had:

According to some embodiments of the present invention, the swirl rate in described firing chamber is between 1.5-5.

According to some embodiments of the present invention, described compression ratio is 14.8-15.5.

According to some embodiments of the present invention, the center line of described diesel injector overlaps with the center line of corresponding cylinder.

According to some embodiments of the present invention, the spray cone angle of described diesel injector is between 70 °-85 °.

According to some embodiments of the present invention, the spray cone angle of described diesel injector is between 75 °-80 °.

According to some embodiments of the present invention, the end face of described piston is formed with pit, described pit is revolution shape, described solid of rotation has throat structure, the rotational axis of described solid of rotation overlaps with the center line of corresponding cylinder, the relative aperture of wherein said piston remains between 0.7-0.8, and the reducing ratio of described piston remains between 0.8-0.9.

According to some embodiments of the present invention, the revolution bus of described solid of rotation comprises the diapire mixing line segment of the sidewall profiles section for the formation of the sidewall of described pit and the diapire for the formation of described pit, described sidewall profiles section comprises the side wall transition section, sidewall reducing section and the side wa ll circle arc section that are connected successively, described diapire mixing line segment comprises diapire first straightway, diapire first arc section, diapire second straightway, diapire second arc section and diapire the 3rd straightway that are connected successively, and wherein said diapire first straightway is connected with described side wa ll circle arc section.

According to some embodiments of the present invention, the radius of curvature of described side wall transition section is 18-22mm, the radius of curvature of described sidewall reducing section is at 1.5-2mm, the radius of curvature of described side wa ll circle arc section is between 3.5-4.5mm, the radius of curvature of described diapire first arc section is 11-15mm, and the radius of curvature of described diapire second arc section is 23-27mm; And described diapire first straightway is parallel with the bottom surface of described cylinder head respectively with described diapire the 3rd straightway, the inclined bottom surface of the relatively described cylinder head of described diapire second straightway is arranged, the length of wherein said diapire first straightway is 3.5-4.5mm, the angle of the bottom surface of described diapire second straightway and described cylinder head at 20 °-24 °, described diapire the 3rd straightway when described piston is in top dead center and the distance of the bottom surface of described cylinder head be 2.5-3.5mm.

According to some embodiments of the present invention, by chamfered transition between the end face of described piston and the sidewall of described piston, the length of described chamfering is 0.5-2mm, and the compression clearance of described piston is 1-2.5mm.

Accompanying drawing explanation

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

Fig. 2 is the plan view of the cylinder block of body group according to the embodiment 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 cross section;

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

Fig. 6 is that the water jacket degree of depth and piston one to go in ring the ratio of journey and the curve relation figure of cylinder wall pressure when upper and lower stop;

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

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

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

Figure 10 is the setting position schematic diagram of spark plug;

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

Figure 12 is the intention of the local of piston;

Figure 13 is any one schematic diagram by the vertical section of rotational axis of pit;

Figure 14 is the stereogram of piston;

Figure 15 is the stereogram of motor;

Figure 16-Figure 18 is the comparison diagram adopting different compression ratio according to the motor of the embodiment of the present invention;

Figure 19-Figure 20 be according to the motor of the embodiment of the present invention under two operating modes, adopt the comparison diagram of different spray-cone angle;

Figure 21-Figure 22 is piston according to the motor of the embodiment of the present invention and the HC of conventional piston, the comparison diagram of NOx emission;

Figure 23 is the swirl rate schematic diagram of the engine chamber according to the embodiment of the present invention.

Embodiment

Be described below in detail embodiments of the invention, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the present invention, and can not limitation of the present invention be interpreted as.

In describing the invention, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end " " interior ", " outward ", " clockwise ", orientation or the position relationship of the instruction such as " counterclockwise " are based on orientation shown in the drawings or position relationship, only the present invention for convenience of description and simplified characterization, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore limitation of the present invention can not be interpreted as.

In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristics.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise one or more these features.In describing the invention, the implication of " multiple " is at least two, such as two, three etc., unless otherwise expressly limited specifically.

In the present invention, unless otherwise clearly defined and limited, the term such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; Can be mechanical connection, also can be electrical connection; Can be directly be connected, also indirectly can be connected by intermediary, can be the connection of two element internals or the interaction relationship of two elements.For the ordinary skill in the art, above-mentioned term concrete meaning in the present invention can be understood as the case may be.

In the present invention, unless otherwise clearly defined and limited, fisrt feature second feature it " on " or D score can comprise the first and second features and directly contact, also can comprise the first and second features and not be directly contact but by the other characterisation contact between them.And, fisrt feature second feature " on ", " top " and " above " comprise fisrt feature directly over second feature and oblique upper, or only represent that fisrt feature level height is higher than second feature.Fisrt feature second feature " under ", " below " and " below " comprise fisrt feature immediately below second feature and tiltedly below, or only represent that fisrt feature level height is less than second feature.

Describe in detail according to the motor 1000 of the embodiment of the present invention below with reference to Fig. 1-Figure 23, the feature of motor 1000 is directly machine entered internal-combustion and produce powers after liquid or gaseous fuel and air mixing, and then is transformed into mechanical energy.For vehicle, its motor 1000 generally can adopt four-stroke form, and motor 1000 generally can comprise distribution device, connecting rod, supply system, ignition system, cooling system and lubrication system etc.

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

Piston connecting rod unit changes the to-and-fro motion of piston 109 rotary motion of bent axle into, the power acted on piston 109 is changed into the torque that bent axle externally exports simultaneously, thus drives the vehicle wheel rotation of vehicle.Usually, piston connecting rod unit comprises piston 109, piston ring (comprising first piston ring 114), wrist pin and connecting rod etc., and wrist pin is for connecting piston and connecting rod.Crankshaft-flywheel group is formed primarily of bent axle and flywheel.

Body group is the support of motor, is the assembling matrix of each system major part of piston connecting rod unit, crankshaft-flywheel group, distribution device and motor 1000.Body group mainly comprises 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 end face of cylinder block 201, cylinder head gasket is folded between the bottom surface M1 (bottom surface M1 as shown in Figure 9) of cylinder head 101 and the end face of cylinder block 201, for the gap between blanket gas cylinder cap 101 and cylinder block 201, oil sump 301 is arranged on the bottom of cylinder block 201.In describing the invention, the longitudinal direction of motor 1000 (or body group) refers to the length direction of motor 1000, the transverse direction of motor 1000 (or body group) refers to thickness (width) direction of motor 1000, and the short transverse of motor 1000 (or body group) refers to the direction of the center line being parallel to cylinder 203.

As Fig. 1 and in conjunction with shown in Figure 11, cylinder block 201 has at least one cylinder 203, cylinder 203 to move wherein the cylindrical cavity carrying out leading for piston 109, cylinder 203 is generally formed in the first half of cylinder block 201, and the Lower Half of cylinder block 201 can be generally crankcase, but be not limited thereto.For straight engine 1000, as shown in Figure 1, its multiple cylinder 203 is that namely multiple cylinder 203 is in alignment along the longitudinal arrangement of motor 1000 along the vertical center line 200 of motor 1000 juxtaposed (vertical center line 200 as shown in Figure 3 and Figure 4).For V-type motor 1000, it is generally divided into two groups of cylinders 203, and the angle between these two groups of cylinders 203 generally between 30 °-60 °, but is not limited thereto.

As shown in Figure 7 and Figure 8, be formed with the intake duct 103 corresponding with each cylinder 203 and air outlet flue 104 in cylinder head 101, intake duct 103 is for firing chamber transferring oil gas mixture (or air), and air outlet flue 104 is for combustion gas.Usually, two can be adopted to enter scene 2 air flue form, namely intake duct 103 and air outlet flue 104 are two, but be not limited thereto, three such as can also be adopted to enter scene 2 or one-in-and-one-out, for the ordinary skill in the art, can according to actual needs and the internal structure of cylinder head 101 and adaptive settings.

Distribution device is arranged in cylinder head 101, the effect of distribution device is the requirement according to the work cycle of carrying out in each cylinder 203 of motor 1000 and firing order, time opening and closedown intake valve 108 and exhaust valve 110, fresh momentum (such as gas mixture or air) is entered in cylinder 203 in time, and waste gas is discharged in time from cylinder 203.

Distribution device mainly comprises valve group and valve transmission group part, valve group generally comprises air inlet side valve (being called for short intake valve 108) and exhaust side valve (being called for short exhaust valve 110), and intake valve 108 and exhaust valve 110 can be opened, close respectively by its timing of independent camshaft actuated.Camshaft can link with the bent axle of motor 1000, can adopt the various ways such as gear transmission, Chain conveyer or V belt translation between camshaft and motor 1000.

Wherein, for four stroke engine 1000, at least corresponding intake valve 108 of each cylinder 203 and an exhaust valve 110, usually, the quantity of intake valve 108 is identical with the quantity of intake duct 103, and the quantity of exhaust valve 110 is identical with the quantity of air outlet flue 104.Such as, two can be adopted to enter scene 2 Four valve structure, or three enter scene 2 five air valve structure, one-in-and-one-out two air valve structure can certainly be adopted.Intake valve 108 in each firing chamber and exhaust valve 110 are by the driving of corresponding camshaft thus according to certain rule partially unrolling, thus in firing chamber, fill into gas mixture (or fresh air) in time, and in time waste gas is discharged after burning work done.

The function of spark plug 105 is that the high-tension electricity produced by spark coil introduces firing chamber, and produces electrical spark between two electrodes, thus lights inflammable mixture, and spark plug 105 mainly can be made up of centre electrode, lateral electrode, housing and insulator etc.In some embodiments of the invention, each cylinder 203 correspondence arranges at least one spark plug 105, and this spark plug 105 can adopt the mode be threaded to be fixed on the corresponding position of cylinder head 101.As optional mode of execution, each cylinder 203 correspondences arrange a spark plug 105.

Gasoline ejector is used for injected petrol fuel, in an embodiment of the present invention, does not make particular determination to the concrete setting position of gasoline ejector.Such as, gasoline ejector can be (that is, multi-point injection) one to one with the quantity of cylinder 203, and gasoline ejector can be arranged on the front that fuel also directly can be sprayed into by cylinder head 101 intake valve 108 of corresponding cylinder 203.Certainly, gasoline ejector also can corresponding multiple cylinder 203 (that is, single-point discharge), and this oil sprayer can be arranged in the section before closure, can flow in air intake branch after fuel sprays into air, and distributes to each cylinder 203 respectively.

Diesel injector 107 is for spraying diesel fuel, and diesel injector 107 can be arranged in cylinder head 101, and the nozzle segment of diesel injector 107 can be positioned at corresponding firing chamber.In some embodiments of the invention, each cylinder 203 correspondence arranges at least one diesel injector 107.As optional mode of execution, each cylinder 203 only correspondence arranges a diesel injector 107.

Should be understood that, about the concrete structure of diesel injector 107 and gasoline ejector, working principle and relevant oil supply system etc., be all well known for ordinary skill in the art for prior art, therefore repeat no longer one by one here.

Wherein, as optional mode of execution, the all corresponding gasoline ejector in each firing chamber and a diesel injector 107, and this gasoline ejector and this diesel injector 107 can be integrated as a whole, this unit injector can have a nozzle, when needs injected petrol for injected petrol, when needs spray diesel oil then for spraying diesel oil.Or this unit injector also can have two nozzles, one for injected petrol, another is for spraying diesel oil, two nozzle mutual noninterferences.In these embodiments, the Fuel Petroleum of gasoline ejector ejection is directly injected in firing chamber, and without air intake branch or intake duct, different from the multi-point injection of above-mentioned gasoline ejector and the set-up mode of single-point discharge.

Owing to having for spraying the diesel injector 107 of diesel oil and the gasoline ejector for injected petrol according to the motor 1000 of the embodiment of the present invention, therefore gasoline, diesel duel fuel engine 1000 (being called for short duel fuel engine 1000) also can be referred to as according to the motor 1000 of the embodiment of the present invention.

According to the duel fuel engine 1000 of the embodiment of the present invention, pilot engine 1000 time, ignition start can be carried out by spark plug 105 mode of igniting.And after duel fuel engine 1000 normal starting, can work in compression ignite mode by spraying diesel oil, now spark plug 105 can quit work.Thus, make, according to the duel fuel engine 1000 of the embodiment of the present invention compared to diesel engine, effectively to reduce discharge when starting, especially for the problem of diesel engine cold-starting difficulty, can be started smoothly by ignition way.After starting according to the duel fuel engine 1000 of the embodiment of the present invention, can be replaced the ignition way of spark plug 105 by compression ignite mode, high compression ratio contributes to Thorough combustion thus, improves fuel economy and the Power output performance of motor 1000.

In addition, according to the motor 1000 of the embodiment of the present invention because normal working stroke circulation time spark plug 105 can quit work, spark plug 105 can only be lighted a fire when starting, therefore the ignition times of spark plug 105 can be greatly reduced, improve the working life of spark plug 105, reduce user cost, also simplify control strategy simultaneously.

But, it should be noted that, the above-mentioned starting process about the duel fuel engine 1000 according to the embodiment of the present invention and normal stroke circulation are only schematically illustrate, can not be interpreted as it is to one restriction of the present invention, or imply that motor 1000 of the present invention only can start or more in the above described manner and state the work of mode normal circulation.

Inventor finds, for duel fuel engine 1000, the swirl rate of reasonable design compression ratio and firing chamber for motor 1000 fuel economy, reduce and discharge and improve Power output and have direct relation.

In view of this, shown in composition graphs 16-Figure 18, Figure 23, inventor finds according to industry experience for many years and great many of experiments, by compression ratio being controlled at 13-17 particularly between 14-16, swirl rate controls between 1-6, effectively can solve the problem of motor 1000 cold starting difficulty, avoid the pinking problem that high compression ratio is brought simultaneously, motor 1000 is started, runs more steadily, reliable, Power output is strong and reach preferably fuel economy and lower noxious gas emission.

Further, shown in Figure 23, inventor finds, by controlling between 1.5-5 by swirl rate, can promote the performance of motor 1000 better, reduces discharge.Therefore as a kind of optional mode of execution, the swirl rate of firing chamber controls between 1.5-5.

Wherein, in a preferred embodiment, the swirl rate of firing chamber is 1.7.In another preferred embodiment, the swirl rate of firing chamber is 1.8.In another preferred embodiment, the swirl rate of firing chamber is 2.

Thus, by the guiding function of cylinder wall, the gas mixture (or fresh air) entered in firing chamber from intake duct 103 can form eddy current in cylinder 203, be between 1-6 by controlled vortex flow ratio, particularly be between 1.5-5, coordinate higher compression ratio (such as 13-17), thus greatly can reduce burning and exhausting, increase the Power output of motor 1000 simultaneously.

Especially, for general vehicle, as shown in figure 23,, particularly family expenses vehicle, economic speed district is between 1000rpm-2000rpm, particularly at 1500rpm-2000rpm, and as can be seen from Figure 23, when motor 1000 is in below 2000rpm, swirl rate is particularly more excellent between 1.5-5 at 1-6.

Need to illustrate a bit, for how, in control cylinder 203, the size of swirl rate has been prior art, and is well known for ordinary skill in the art.Such as, form that is tangential and/or spiral inlet duct 103 can be adopted, simultaneously also can in conjunction with swirl valve technology, but in the present invention, particular determination is not made for adopting the concrete setting position of which kind of intake duct 103 form and swirl valve, for the ordinary skill in the art, suitable intake duct 103 form and suitable swirl valve setting position can be adopted as required, as long as can realize being controlled by swirl rate at 1-6 particularly between 1.5-5.

Inventor finds, the control for compression ratio has vital effect to the power character of motor 1000, fuel economy and emission performance equally.Shown in composition graphs 16-Figure 18, inventor finds, more excellent by being controlled between 14.8-15.5 by compression ratio.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 motor 1000 is 15.1.According to another embodiment of the invention, compression ratio is 15.3.

Thus, coordinate suitable swirl rate, such as preferred embodiment, compression ratio is at 14.8-15.5, swirl rate between 1.5-5, thus can solve the problem of motor 1000 cold-starting difficulty better, avoids the phenomenon of detonation because high compression ratio causes, improve fuel economy and the power character of motor 1000, the discharge of harmful gas reduces greatly.

Wherein, it should be noted that, the abscissa in Figure 16-18 represents the moment of torsion that motor 1000 exports under rotating speed and this rotating speed, y coordinate represents fuel consumption rate, is understandable that, under same rotational speed, fuel consumption rate is lower, proves that the fuel economy of motor is better.Can clearly be seen that from Figure 16-Figure 18, is the situation of 13 and 17 significantly better than compression ratio when compression ratio (CR) is 14.8,15.1 and 15.5.

Below in conjunction with Fig. 7-Figure 15, the piston 109 according to the embodiment of the present invention is described in detail.

Because the type selecting of piston 109 is related to compression ratio, be also related to the overall performance of motor 1000, therefore reasonably type selecting piston 109 is most important for motor 1000 simultaneously.

Shown in composition graphs 11-Figure 14, according to some embodiments of the present invention, the end face of piston 109 is formed with pit 111, and this pit 111 forms firing chamber jointly with the internal face of cylinder wall and the bottom surface M1 of cylinder head 101.The size of pit 111, molded line directly determine the structure of firing chamber, and and then are associated with every combustion index of motor 1000.

In an embodiment of the present invention, pit 111 is preferably revolution shape, the rotational axis 117 (as shown in figure 13) of this solid of rotation overlaps with the center line M2 (M2 as shown in Figure 10) of corresponding cylinder 203, and in other words, this pit 111 is formed in the center at piston 109 top.Thus, pit 111 is arranged between two parties and can be avoided piston 109 unbalance stress and cause cylinder wall local pressure to be concentrated, thus cylinder 203 problem on deformation can be improved, pit 111 can also reduce the friction between piston 109 and cylinder wall between two parties to a certain extent simultaneously, improve the life-span of piston 109 and the sealing between piston 109 and cylinder wall, reduce the combustion gas escaped in crankcase from gap between piston 109 and cylinder wall, avoid this Some gases to affect performance and the life-span of crankcase inner engine oil.

Shown in composition graphs 11-Figure 13, pit 111 is " ω " shape, and namely pit 111 is " ω " shape by the vertical section of rotational axis 117.Here, it should be noted that, pit 111 should make broad understanding for " ω " shape, and the vertical section that namely can be understood as pit 111 can be the shape approximate with " ω " shape, and namely the top of pit 111 at least should possess a reducing feature.Concrete molded line about " ω " shape pit 111 will provide detailed description below in conjunction with specific embodiments.

As preferred embodiment, as shown in figure 11, pit 111 top has throat structure 127, and the relative aperture of piston 109 remains between 0.7-0.8, and the reducing ratio of piston 109 remains between 0.8-0.9.Particularly, the relative aperture of piston 109 refers to the ratio of the narrowest place of throat structure 127 of pit 111 and the diameter of cylinder 203, and namely relative aperture is K4/D (wherein K4 as shown in figure 12, shown in cylinder bore D composition graphs 1).The reducing of piston 109 is than the diameter ratio at the narrowest place of throat structure 127 and pit 111 throat structure 127 bottom the widest position that refer to pit 111, and namely reducing is than being K4/K5 (K4, K5 are in conjunction with Figure 12 Suo Shi).

Thus, by relative aperture and the reducing ratio of reasonable design piston 109, the relative aperture of piston 109 is made to remain between 0.7-0.8, reducing ratio remains between 0.8-0.9, relative aperture larger like this and less reducing Billy, are conducive to reducing HC discharge in diesel oil to the diffusion in firing chamber clearance and extinguishing district.Also reduce the heat transfer loss of firing chamber in combustion process simultaneously, fuel combustion is obtained more abundant, thus improve the thermal efficiency of motor 1000.

Below in conjunction with Figure 11-Figure 13, pit 111 structure is elaborated.

As shown in figure 13, pit 111 is revolution shape, and solid of rotation has revolution bus 115 and rotational axis 117, and this solid of rotation is formed around rotational axis 117 rotating 360 degrees for turning round bus 115.In the example in figure 13, in fact any vertical section of rotational axis 117 is comprised, on this cross section, the medianly zygomorphic part of rotational axis 117 all can as revolution bus 115, in the following description, be described using the part be positioned on the left of rotational axis 117 as revolution bus 115.

Particularly, revolution bus 115 comprises sidewall profiles section 119 and diapire mixing line segment 129, this sidewall profiles section 119 is for the formation of the sidewall of pit 111, this diapire mixing line segment 129 is for the formation of the diapire of pit 111, and wherein diapire mixing line segment 129 at least comprises diapire straightway and diapire curved section.

Line style due to sidewall profiles section 119 and diapire mixing line segment 129 is directly connected to the shape of firing chamber, and then is related to the thermal efficiency etc. of motor 1000.Therefore the concrete line style of reasonable design sidewall profiles section 119 and diapire mixing line segment 129 is to the thermal efficiency of motor 1000 and overall performance important role.

Shown in Figure 13, specifically, sidewall profiles section 119 can comprise side wall transition section 121, sidewall reducing section 123 and side wa ll circle arc section 125, and side wall transition section 121, sidewall reducing section 123 are connected from top to bottom successively with side wa ll circle arc section 125.Side wall transition section 121 is for the formation of connecting the transition portion of throat structure 127 with piston 109 end face, and sidewall reducing section 123 is for the formation of above-mentioned throat structure 127, and side wa ll circle arc section 125 is for the formation of the lower sidewall portions of firing chamber.

Diapire mixing line segment 129 comprises diapire first straightway 131, diapire first arc section 133, diapire second straightway 135, diapire second arc section 137 and diapire the 3rd straightway 139, wherein diapire first straightway 131, diapire first arc section 133, diapire second straightway 135, diapire second arc section 137 are connected diametrically from outside to inside successively with diapire the 3rd straightway 139, and the outer end of diapire first straightway 131 is connected with the lower end of side wa ll circle arc section 125.

Inventor finds, by sidewall profiles section 119 and diapire mixing line segment 129 being designed according to above-mentioned line style, being conducive to the diffusion of diesel oil to firing chamber clearance and extinguishing district, being conducive to the discharge of the harmful gases such as reduction HC.

Further, because sidewall profiles section 119 is made up of multiple curved section, diapire mixing line segment 129 is made up of multiple curved section and straightway, and therefore the relevant parameter of each curved section and straightway is directly connected to the thermal efficiency of motor 1000 and the performance of motor 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 between 18-22mm, preferably 20mm, the radius of curvature r1 of sidewall reducing section 123 can between 1.5-2mm, the radius of curvature r2 of side wa ll circle arc section 125 is between 3.5-4.5mm, preferably between 3.5-4mm, diapire first straightway 131 is preferably parallel to cylinder head 101 bottom surface M1's, the length of diapire first straightway 131 can between 3.5-4.5mm, be preferably 4mm, the radius of curvature r3 of diapire first arc section 133 can be between 11-15mm, be preferably 13mm, the inclined bottom surface of diapire second straightway 135 opposite cylinder heads 101 is arranged, slanted angle β 7 can between 20 °-24 °, be preferably 22 °, the radius of curvature r4 of diapire second arc section 137 can be 23-27mm, be preferably 25mm, diapire the 3rd straightway 139 is preferably parallel to cylinder head 101 bottom surface, and diapire the 3rd straightway 139 is positioned at the top (oblique upper) of diapire first straightway 131, namely the rational height of diapire the 3rd straightway 139 is greater than the rational height of diapire first straightway 131.

Above-mentioned design can make the relative aperture of piston 109 remain between 0.7-0.8, and reducing ratio remains between 0.8-0.9, and is one more preferably mode of execution, is beneficial to diesel oil to firing chamber clearance diffusion, thus effectively reduces HC discharge.

Simultaneously in conjunction with shown in Figure 22, Figure 22 shows according to the piston 108 of the embodiment of the present invention after the above-mentioned Alignment Design of employing, the control experiment carried out with former conventional piston, as can be seen from Figure 22, adopt above-mentioned Alignment Design that the HC discharge of poisonous waste of motor 1000 is reduced greatly, reduce NOx, be beneficial to the carrying out of burning, improve the abundant degree of burning.

In some embodiments of the invention, the 3rd straightway when piston 109 is in top dead center and the distance of the bottom surface M1 of cylinder head 101 between 2.5mm-3.5mm, i.e. K3=2.5mm-3.5mm (as shown in figure 11), be preferably 3mm, i.e. K3=3mm.By reasonably controlling the distance (when piston 109 is in top dead center) of the 3rd straightway and cylinder head 101 bottom surface M1, thus making pit 111 can form the feature of tray type gasoline combustion, improving combustion efficiency, make burning more abundant, reduce discharge.

In the process can compressed at piston 109 to make diesel oil, mixed conductance flows into compression clearance and extinguishing region better, as preferred embodiment, by chamfering 118 transition between the end face of piston 109 and the sidewall of piston 109, as shown in figure 11, this chamfering 118 angle can be 45 °, length can be 0.5-2mm, and the compression clearance K2 of piston 109 is 1-2.5mm.Here, compress clearance and refer to the end face of piston 109 piston 109 when top dead center and the distance of cylinder head 101 bottom surface.

Thus, by arranging chamfering 118 in piston 109 top outer rim and controlling the length of chamfering 118 at 0.5-2mm, the compression clearance of control piston 109 is between 1-2.5mm simultaneously, coordinate radius of curvature in the side wall transition section 121 of 18-22mm, the combination design of this three can make diesel oil in piston 109 compression process, be entered to compress the extinguishing region of clearance and piston 109 and cylinder wall well by the gas flow guiding compressed, make the ignition mixture in this region can have better fire behaviour, the discharge of HC can be effectively reduced, improve the utilization ratio of fuel oil, reduce oil consumption.

As preferred embodiment, chamfering 118 length between the end face of piston 109 and the sidewall of piston 109 is at 1-1.5mm, the compression clearance of piston 109 is 1.5-2mm, ignition mixture can be made thus to have more excellent fire behaviour, promote the fuel economy of motor 1000, greatly reduce the discharge of harmful gas.

Shown in Figure 21, Figure 21 shows and adopts above-mentioned compression clearance according to the piston 108 of the embodiment of the present invention, the Comparability test that former conventional piston is carried out is compared in the combination design of side wall transition section 121 and chamfering 118, as can be seen from Figure 21, after adopting above-mentioned design, the HC discharge of poisonous waste of motor 1000 can be made greatly to reduce, reduce NOx, be beneficial to the carrying out of burning, improve the abundant degree of burning.

To sum up, traditional diesel oil " ω " type and the feature of tray type gasoline combustion is fully combined according to piston 109 structure of the embodiment of the present invention, by to the optimization of firing chamber line style and innovative design, meet duel fuel engine 1000 demand to chamber structure under different working modes.

Simultaneously, the relative aperture that the dimensional structure structure of piston 109 end face piston 109 is larger and less reducing ratio, chamfering 118 structure at piston 109 edge and piston 109 end face and cylinder head 101 bottom surface coordinate the larger compression clearance produced to be conducive to diesel oil to be directed in compression process and to compress clearance and the extinguishing district between piston 109 and cylinder wall, HC discharge can be effectively reduced, improve the utilization ratio of fuel.

In addition, form shallow " ω " type on the whole according to the piston 109 of the embodiment of the present invention, surface to volume ratio reduces greatly, thus reduces motor 1000 heat transfer loss external in the course of the work, improves the thermal efficiency of motor 1000.

In addition, be plane according to the bottom surface M1 of the cylinder head 101 of the motor 1000 of the embodiment of the present invention, coordinate this " ω " type piston 109 and suitable swirl rate (such as 1.5-5) and compression ratio (such as 14.8-15.5), thus improve the properties of motor 1000 on the whole, reduce the discharge of harmful gas.Further, can transform using diesel engine as prototype according to the motor 1000 of the embodiment of the present invention.

In conjunction with specific embodiments intake valve 108, exhaust valve 110 and spark plug 105 are described in detail referring to Fig. 7-Figure 10.

At embodiments of the invention, spark plug 105 is arranged in cylinder head 101, and such as spark plug 105 is fastened in cylinder head 101 by worm structure.The setting position of spark plug 105 is related to flame travel, flame area spreading rate, velocity of combustion etc., for discharge important when starting.

Inventor finds, as shown in Figure 10, by being biased by spark plug 105, the center line M2 namely departing from cylinder 203 is arranged, and controls spark plug 105 simultaneously and has beneficial effect with the distance K1 of cylinder head 101 intersection point distance cylinder 203 center line for the control of combustion flame and rate of burning when starting.

Thus, in certain embodiments, the center line M2 that spark plug 105 departs from corresponding cylinder 203 is arranged, that is, the center line of spark plug 105 does not overlap with the center line M2 of corresponding cylinder 203, and preferably, spark plug 105 is positioned at exhaust side, as shown in Figure 7.

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

Thus, pilot engine 1000 time, can avoid phenomenon of detonation occurs, improve flame area spreading rate and rate of burning, balanced flame travel, effectively avoids pre-ignition, also facilitates motor 1000 to clean waste gas simultaneously, improve ignition difficulties problem better, and substantially increase the working stability of starting and low speed and load operating mode (now spark plug 105 also can participate in ignition operation).In addition, because the motor 1000 according to the embodiment of the present invention has diesel injector 107, by being biased by spark plug 105, thus providing the useful space for the center arrangement mode of diesel injector 107, avoiding the two to interfere on mounting point and affecting the performance of motor 1000.

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

In an embodiment of the present invention, as shown in Figure 7, the first end of spark plug 105 extend in corresponding cylinder 203, and the second end of spark plug 105 passes the air outlet flue 104 of this cylinder 203 correspondence and stretches out, and the direction referred to deviating from firing chamber that stretches out here extends.By this layout, cylinder head 101 structure can be made compacter, avoid interfering with diesel injector 107 simultaneously, spark plug 105 can save arrangement space to the maximum limit through air outlet flue 104, simultaneously less for exhaust performance impact, substantially increase the space availability ratio of cylinder head 101 end face.

As the embodiment optimized further, as shown in Figure 8, the air outlet flue 104 of each cylinder 203 correspondence is two, and the close to each other and next-door neighbour of the afterbody of two air outlet flues 104 is to form common-use tunnel 112, and the second end of spark plug 105 can pass this common-use tunnel 112 and stretch out.Like this, spark plug 105 is positioned at the center of two air outlet flues 104, and make the overall structure of cylinder head 101 compacter, space availability ratio is higher, and be beneficial to the volume reducing body group and take, the layout being in particular distribution device and diesel injector 107 is provided convenience.

Inventor finds, for conventional engines 1000, and the general layout placed in the middle of its spark plug 105, and the center line of spark plug 105 overlaps with the center line of cylinder 203.And in the application, spark plug 105 is biased arranges, therefore angle is set produces certain impact to flame area spreading rate and rate of burning of spark plug 105.

Inventor finds, spark plug 105 is obliquely installed and can improves this situation, therefore in one embodiment of the invention, spark plug 105 is obliquely installed relative to the cylinder 203 of this spark plug 105 correspondence, namely the center line of spark plug 105 and the center line of cylinder 203 are uneven, as shown in Figure 10.

Further, in certain embodiments, as shown in Figure 10, the center line of spark plug 105 and the angle β 6 of the center line of corresponding cylinder 203 are between 20 °-30 °.Thus, can improve flame area spreading rate and rate of burning, balanced flame travel, effectively avoids pre-ignition, also facilitates motor 1000 to clean waste gas simultaneously, improves ignition difficulties problem better.

In addition, spark plug 105 is obliquely installed and also helps spark plug 105 through air outlet flue 104, avoid interfering with the structure such as distribution device.

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

Thus, liquid fuel not only effectively can be avoided to collide spark plug 105 and supply the mixed gas of overrich to spark plug 105 and on spark plug 105, form carbon distribution, also weighed the cooling effect near spark plug 105.Simultaneously by adopting diesel injector 107 and the setting type of spark plug 105 compared with Large space, and spark plug 105 is in tilted layout in exhaust side, thus be beneficial to raising flame area spreading rate and rate of burning, balanced flame travel, thus avoid pre-ignition better.In addition, this angle design is also conducive to most through air outlet flue 104, avoids interfering with other structure.

Below in conjunction with Fig. 9, intake valve 108 and exhaust valve 110 are described.

Due to not only diesel injector 107 will be arranged according in the cylinder head 101 of the embodiment of the present invention, also to arrange spark plug 105 simultaneously, therefore higher to the structural requirement of cylinder head 101, too increase the layout difficulty of distribution device simultaneously.

Shown in composition graphs 7 and Fig. 9, because intake valve 108 closes the suction port 102 of intake duct 103 end (firing chamber place) and the center line of intake valve 108 is roughly orthogonal with this suction port 102, similarly, the relief opening 106 of air outlet flue 104 head end (firing chamber place) closed by exhaust valve 110 and the center line of exhaust valve 110 is roughly orthogonal with this relief opening 106, and therefore the angle that arranges of intake valve 108 and exhaust valve 110 reflects this suction port 102 and cylinder head 101 bottom surface M1 and the angle between relief opening 106 and cylinder head 101 bottom surface M1 indirectly.

Such as, for intake valve 108 be 5 ° by the angle of the vertical plane M3 (M3 as shown in Figure 9) of the vertical center line 200 of motor 1000, then this intake valve 108 is about 85 ° with the angle of cylinder head 101 bottom surface M1, and due to this suction port 102 and intake valve 108 be roughly orthogonal, therefore this suction port 102 and the angle of cylinder head 101 bottom surface are at about 5 °, thus can think that the bottom surface angle of intake duct 103 particularly intake duct 103 rear and cylinder head 101 is about 5 °.

Similarly, it is 5 ° for exhaust valve 110 and the angle of above-mentioned vertical plane M3, then this exhaust valve 110 is about 85 ° with the angle of cylinder head 101 bottom surface M1, and due to this relief opening 106 and exhaust valve 110 be roughly orthogonal, therefore this relief opening 106 and the angle of cylinder head 101 bottom surface are at about 5 °, thus can think that the bottom surface angle of air outlet flue 104 particularly air outlet flue 104 initial segment and cylinder head 101 is about 5 °.

In brief, the angle that arranges of intake valve 108 and exhaust valve 110 reflects air outlet flue 104 (the particularly rear of air outlet flue 104 indirectly, relief opening 104 can be thought) and the angle of intake duct 103 (the particularly initial segment of intake duct 103, can think suction port 102) and cylinder head 101 bottom surface.That is, as shown in Figure 9, β 1=β 4, β 2=β 5 can be thought approx.

And based on this, inventor finds, by appropriate design intake duct 103 (indirectly reflection suction port 102), the angle of air outlet flue 104 (indirectly reflection relief opening 106) and cylinder head 101 bottom surface M1, thus can not only conveniently design cylinder head 101, the internal structure reducing cylinder head 101 (is such as diesel injector 107, spark plug 105, various air flue, water jacket) design difficulty, especially simultaneously, by this angle of appropriate design, thus ensure that motor 1000 all has the mixing rate in preferably diffusive combustion stage under each rotating speed, and can turbulence intensity be increased when reaching in certain limit, and then be beneficial to carrying out smoothly of combustion process, reduce smoke intensity simultaneously.

Inventor finds, by suction port 102 and relief opening 106 are designed to and angle β 4, the β 5 of cylinder head 101 bottom surface M1 respectively between 0 °-6 °, to combustion process carry out smoothly and the reduction of smoke intensity has remarkable result.Therefore, in some embodiments of the invention, the center line of intake valve 108 and be between 0 °-6 ° by the angle β 2 of the vertical plane M3 of the vertical center line of motor 1000, similarly, the center line of exhaust valve 110 and the angle β 1 of this vertical plane M3 are also between 0 °-6 °.

Thus, the angle between intake valve 108 and exhaust valve 110 is less than 12 °, i.e. valve angle relative narrower, and this narrower valve angle can make cylinder head 101 compact structure, reduces cooling loss and obtains best surface area/volume.

As preferred embodiment, the angle β 3 between the center line of intake valve 108 and the center line of exhaust valve 110 is in 10 °.Wherein, it should be noted that, intake valve 108 here and the angle of exhaust valve 110 refer to the intake valve 108 and exhaust valve 110 that transversely correspond to each other at motor 1000.Thus, make cylinder head 101 structure compacter, cooling loss can be reduced better simultaneously and obtain best surface area/volume.

The diesel injector 107 according to the embodiment of the present invention is described in detail below in conjunction with Fig. 7, Figure 19-Figure 20.

With reference to shown in Fig. 7, the center line of diesel injector 107 overlaps with the center line of corresponding cylinder 203, and namely diesel injector 107 is arranged between two parties.Thus, diesel injector 107 can spray diesel fuel equably in firing chamber, coordinates " ω " type pit 111 arranged placed in the middle simultaneously, diesel fuel can be made more uniformly to be distributed in firing chamber, form average mixed gas, be beneficial to Thorough combustion.

Inventor finds, the spray cone angle of diesel injector 107 is remarkable to soot, NOx emission (emission index of oxynitrides) and fuel consumption rate three motor 1000 Index Influences.Shown in composition graphs 19-Figure 20, inventor is found by great many of experiments, during by being controlled between 70 °-85 ° by the cone angle of diesel injector 107, soot emission levels is lower, reduce NOx, namely oxynitride discharge reduces simultaneously, and fuel consumption rate also decreases simultaneously.

Shown in Figure 19 and Figure 20, Figure 19 and Figure 20 gives the comparison diagram that motor 1000 is in many groups spray cone angle of diesel injector 107 under different rotating speeds (two kinds of operating modes), namely spray cone angle is respectively 65 °, 70 °, 75 °, 78 °, 78.5 °, 85 ° and 90 °, and all corresponding three measurement indexs of each spray cone angle, be followed successively by soot (pollutant from left to right, soot), Nox (oxynitride discharge rate) and ISFC (fuel consumption rate), can clearly find out from Figure 19-Figure 20, spray cone angle is being greater than 70 °, when being less than 85 °, three indexs are all less than normal, namely being less than spray cone angle is 65 ° and 90 °.

Further, as shown in Figure 19-Figure 20, as preferred embodiment, the spray cone angle of diesel injector 107 is better between 75 °-80 °.Wherein, as one preferred embodiment, the spray cone angle of diesel injector 107 is 75 °.Another preferred embodiment in, the spray cone angle of diesel injector 107 is 78 °.Another preferred embodiment in, the spray cone angle of diesel injector 107 is 78.5 °.

Thus, in conjunction with diesel injector 107 arrangement placed in the middle, diesel oil oil bundle is evenly distributed in firing chamber, each oily Shu Changdu is avoided to differ and cause mixed gas lack of homogeneity, impact burning, simultaneously suitable spray cone angle can effectively reduce soot, NOx emission and fuel consumption rate, increases motor 1000 Power output, fuel economy on the whole, improve the thermal efficiency of motor 1000, reduce the discharge of harmful gas.

To sum up, in conjunction with the arrangement of spark plug 105, pit 111 line style of piston 109, swirl rate, the spray cone angle etc. of compression ratio and diesel injector 107, make the petrol gas of the motor 1000 according to the embodiment of the present invention, diesel oil oil gas and air can form homogeneous charge better, realize homogeneous combustion, flame combustion is abundant, relative to the diffusive combustion of diesel oil, improve the combustion efficiency in motor 1000 starting process, reduce emission effect when motor 1000 starts, and compared to petrol engine, high compression ratio can improve combustion efficiency further, increase power performance and the fuel economy of motor 1000.

The body group part according to the embodiment of the present invention is described in detail below with reference to Fig. 1-Fig. 6, because the motor 1000 according to the embodiment of the present invention is duel fuel engine, be different from traditional petrol engine and diesel engine, the problems such as such as have that inner pressure of air cylinder outburst is large, cylinder wall mutability, body group life-span are short, therefore need to redesign body group, to adapt to double fuel combustion mode.

Cylinder block 201 part 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 (being orthogonal to the cross section in cylinder centerline direction) of cylinder wall is annular, and wherein Fig. 4 shows the schematic diagram of the cross section of cylinder wall according to an embodiment of the invention.The outside of cylinder wall can be block jacket, cooling water can flow in block jacket and with cylinder wall contact heat-exchanging, thus reduce the operating temperature of cylinder 203 and cylinder 203 inner carrier.

Shown in Fig. 1 and composition graphs 4, the circular crosssection of cylinder wall is circumferentially divided into the four sections of arcuate segments 205,207,209,211 be connected successively, i.e. the first arcuate segment 205, second arcuate segment 207, the 3rd arcuate segment 209 and the 4th arcuate segment 211.And every section of arcuate segment is further divided into first paragraph 213, second segment 215 and the 3rd section 217, wherein the vertical center line 200 of the 3rd section of 217 distance motor of each arcuate segment farthest, the first paragraph 213 of each arcuate segment is nearest apart from this vertical center line 200, as shown in Figure 4.

In other words, shown in composition graphs 4, the first paragraph 213 of the first arcuate segment 205 is connected with the first paragraph 213 of the 4th arcuate segment 211, and joint is on vertical center line 200, the 3rd section 217 of first arcuate segment 205 is connected with the 3rd section 217 of the second arcuate segment 207, and joint is this distance vertical center line 200 farthest, circular crosssection.Similarly, the first paragraph 213 of the second arcuate segment 207 is connected with the first paragraph 213 of the 3rd arcuate segment 209, and joint is on vertical center line 200, the 3rd section 217 of 3rd arcuate segment 209 is connected with the 3rd section 217 of the 4th arcuate segment 211, and joint is this distance vertical center line 200 farthest, circular crosssection.

Wherein, as shown in Figure 4, the central angle of first paragraph 213 correspondence is α 1 and wall thickness is h1, and the central angle of second segment 215 correspondence is α 2 and wall thickness is h2, and the central angle of the 3rd section of 217 correspondences is α 3 and wall thickness is h3.Need to illustrate a bit, in the example of fig. 4, only for the 3rd arcuate segment 209, its first paragraph, second segment and the 3rd section are marked, and the first arcuate segment 205, second arcuate segment 207 and the 4th arcuate segment 211 have the structure the same with the 3rd arcuate segment 209, therefore do not mark one by one in the diagram.

Wherein α 1, α 2 and α 3 meet relation: α 1+ α 2+ α 3=90 °.Thus, the arc length of these four sections of arcuate segments is equal, and the central angle that namely every section of arcuate segment is corresponding is 90 °, thus the cross section of each cylinder 203 has the symmetry properties of height, as shown in Figure 4.

Further, h1, h2 and h3 meet one of following relationship: h1 < h2≤h3, h1≤h2 < h3.In other words, the thickness that distance vertical center line 200 thickness of the 3rd section 217 farthest compares the nearest first paragraph 213 of distance vertical center line 200 is thick, namely according to from first paragraph 213 towards the direction of the 3rd section 217, the thickness of each arcuate segment presents roughly variation tendency thickening gradually.

Like this, the radial force of piston suffered by cylinder 203, the power that piston suffered by the cylinder wall of each cylinder 203 applies increases along with the distance with vertical center line 200 and increases gradually, namely the closer to vertical center line 200, cylinder wall stressed relatively less, and more away from vertical center line 200, cylinder wall stressed relatively larger.

Thus, relatively the thickest by the 3rd section 217 being designed to thickness, it is relatively the thinnest that first paragraph 213 is designed to thickness, the Thickness Design of second segment 215 becomes between first paragraph 213 and the 3rd section 217 (or alternatively, second segment 215 is designed to equal with one of first paragraph 213 and the 3rd section 217), thus the stressed the best part intensity of cylinder wall is significantly improved, the distortion of this place's cylinder wall can be prevented better, for stressed relatively little part, then wall thickness is relatively thin, reduce quality and the volume of body group, and also avoid blindly thickening cylinder wall and causing the cooling of cylinder 203 not enough.

In brief, be cylindrical according to the internal face of the cylinder wall of the cylinder 203 of the embodiment of the present invention and outer wall is the Irregular Boundary Surface (as shown in Figure 4) of near cylindrical, this Irregular Boundary Surface makes cylinder wall thickening in stressed larger part, and at the stressed less parts thinner of cylinder wall, thus improve cylinder 203 and be out of shape and the cooling effect of cylinder 203, also reduce quality and the size of body group simultaneously.

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, can certainly be wall thickness grading structure, or also can be the combination of the two.But demand fulfillment second segment 215 is not less than the thickness of first paragraph 213, be not less than the thickness of second segment 215 for 3rd section 217, and get rid of all equal situation of three sections of thickness, namely the thickness of first paragraph 213, second segment 215 and the 3rd section 217 is in increasing trend substantially, so to gradual change increase progressively or jumping characteristic increase progressively then can adaptive settings as the case may be, this should be all easy understand for the ordinary skill in the art.

Inventor finds, reasonable design h1, h2 and h3, not only effectively can lower quality and the volume of body group, the body group quality avoiding the wall thickness blindly increasing cylinder wall to cause is excessive, cylinder 203 cools the problems such as not enough, the distortion of cylinder 203 can also be improved simultaneously, and gain in strength targetedly for yielding region.

In view of this, inventor finds, when h1, h2 and h3 meet following relationship respectively, not only can play the object increasing cylinder wall intensity, improve cylinder 203 problem on deformation, quality and the blocked up caused cylinder 203 of wall thickness that can also take into account body group cool deficiency, wherein 6.5mm≤h1≤7mm simultaneously, 7mm≤h2≤7.5mm, 7.5mm≤h3≤9.5mm.

Thus, in first paragraph 213 region, because wall thickness is relatively thin, the flow resistance of the cooling water in water jacket corresponding to this part-structure can be reduced, reduce the pressure loss.Meanwhile, by by the wall thickness control in second segment 215 region between 7-7.5mm, the sudden change of water jacket inner cooling water flow velocity can be avoided, cylinder 203 can be reduced again and be out of shape.Further, by being processed into maximum by the thickness of the 3rd section 217, thus add the intensity of the stressed biggest place part of cylinder wall well, and then resistance to deformation better.Be understandable that, preferably adopt between any two sections in first paragraph 213, second segment 215 and the 3rd section 217 and seamlessly transit mode and carry out transition, be convenient to casting processing like this.

In embodiment more of the present invention, the wall thickness of each arcuate segment is thickening gradually towards the direction of the 3rd section 217 of this arcuate segment according to the first paragraph 213 from this arcuate segment, in other words, one end that the distance second segment 215 of first paragraph 213 is far away is the thinnest, the distance second segment 215 of the 3rd section 217 one end far away is the thickest, and namely the thickness of cylinder wall cross section appears at the both lateral sides place of cylinder 203.Thus, can play the object increasing cylinder 203 intensity equally, improve cylinder 203 problem on deformation, quality and the blocked up caused cylinder 203 of wall thickness that can also take into account body group cool deficiency simultaneously.

Inventor finds, reasonable design α 1, α 2 and α 3 can lower quality and the volume of body group equally, but also can improve the distortion of cylinder 203, increases the life-span of motor.In view of this, inventor finds, α 1, α 2 and α 3 meet following relationship respectively, can play the object increasing cylinder wall intensity, improve cylinder 203 problem on deformation, wherein 30 °≤α 1≤40 °, 15 °≤α 2≤25 °, 30 °≤α 3≤40 °.

As preferred embodiment: α 1=35 °, α 2=20 °, α 3=35 °.Thus, coordinate the wall thickness design of first paragraph 213, second segment 215 and the 3rd section 217, i.e. 6.5mm≤h1≤7mm, 7mm≤h2≤7.5mm, 7.5mm≤h3≤9.5mm, thus the intensity of cylinder wall can be increased better, improve cylinder 203 problem on deformation, quality and the blocked up caused cylinder 203 of wall thickness that can also take into account body group cool deficiency simultaneously.

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

For conventional engines, the sidewall of its body group generally all adopts straight design (namely sidewall is plane).The quality of body group can be caused so large, take up room many, for the engine compartment that space arrangement requirement is increasingly severe, the volume how reducing motor under the prerequisite not affecting motor properties has become a kind of trend, and simultaneously this sidewall is the problem that the body group of plane also exists cylinder mutability.

In some embodiments of the invention, shown in composition graphs 1 and Fig. 3 (wherein Fig. 3 is the simplification view of Fig. 1), the first side wall 219 of cylinder block 201 first side and the second sidewall 221 of cylinder block 201 second side are formed as waveform respectively.Here, it should be noted that, this first side wall 219 and the second sidewall 221 are side wall surfaces of the first half of cylinder block 201, the wall portion namely above crankcase.By the first side wall 219 and the second sidewall 221 are set to waveform, thus the intensity of body group can be improved, improve the problem on deformation of cylinder 203.

Wherein, the first side wall 219 and the second sidewall 221, about vertical center line 200 symmetry of motor, are convenient to casting processing thus, and make the mass distribution of motor more even, avoid the defect occurring that local quality is concentrated, and make motor operation more steady.

About wavy sidewalls, shown in composition graphs 1 and Fig. 3, this waveform is made up of two kinds of arc sections, i.e. the first arc section 223 and the second arc section 225, first arc section 223 and the second arc section 225 are alternately arranged and are connected successively, in other words, connect second arc section 225 between two the first arc sections 223, and be connected with first arc section 223 between two the second arc sections 225.

Wherein the first arc section 223 is formed as outer convex type circular shape, and the second arc section 225 is formed as concave circular shape, and the first arc section 223 and the second arc section 225 tangent in joint.Thus, the first arc section 223 and the second arc section 225 transitions smooth, easy to process.

Each first arc section 223 is relative at the cylinder 203 transversely with corresponding of motor, particularly, as Fig. 3 and shown in composition graphs 1, the first arc section 223 is relative with the 3rd section 217 in the horizontal.Thus, can ensure that block jacket is unlikely to narrow on the one hand, reduce the flow resistance of cooling water, the effect of assistant reinforcement can also be played on the other hand to cylinder 203, prevent cylinder 203 from deforming.

Inventor finds, the reinforcement of the radius of curvature R 1 of reasonable design first arc section 223 and radius of curvature R 2 pairs of cylinders 203 of the second arc section 225 is so that vital effect is played in the reinforcement of whole body group.In view of this, inventor finds, when the ratio of the radius of curvature R 2 of the second arc section 225 and the radius of curvature R 1 of the first arc section 223 meets 2≤R2/R1≤3, effectively can improve the distortion of cylinder 203, improves the life-span of motor.

Further, as preferred embodiment, the ratio of R2 and R1 meets relation further: 2.1≤R2/R1≤2.5.Thus, the problem on deformation of cylinder 203 can be improved further, compare conventional planar sidewall structure, both alleviated the weight of body group and taken volume, in turn ensure that simultaneously body group particularly wall portion there are sufficient strength and stiffness, effectively can avoid cylinder 203 discontinuity that lateral wall pressure skewness causes and the problem on deformation caused.

In certain embodiments, as shown in Figure 2, the top of cylinder block 201 is also provided with top board 227, and the thickness of top board 227 is h4, and the diameter of cylinder 203 is D, and wherein the ratio of h4 and D meets relation: 0.15≤h4/D≤0.19.Thus, by coordinating wavy sidewalls structure, the stressed nonuniformity of cylinder 203 can be reduced further, thus greatly reduce the distortion of cylinder 203.

Based on sectional dimension, the reinforing function to cylinder 203 such as wavy sidewalls and top board 227 thickness of cylinder 203 above, inventor finds that cylinder 203 distortion is a composite factor, and from the viewpoint of combustion mode, a large amount of average mixed gass is there is in cylinder 203, the wet wall problem that high-eddy intensity causes should be reduced, improve the fogging degree of combustion gas in cylinder 203 again simultaneously, realize efficient burning.

Simultaneously, inventor also finds, in traditional arrangement, by piston in top dead center and lower dead center movement process, the region of one ring covering of piston is as the water jacket degree of depth, so most of heat can be scattered and disappeared by water jacket, thus cylinder 203 upper and lower can be caused while water jacket band too much heat away to form certain temperature gradient, thus exacerbates the thermal distortion of cylinder 203.

In view of this, inventor is found by industry experience for many years and a large amount of experiments, and the degree of depth of block jacket is that the pass by 75%-85% of stroke of piston its first piston ring when top dead center and lower dead center is optimum, as shown in Figure 6.In other words, the degree of depth of block jacket is h5, the stroke of the piston of the motor first piston ring during moving to lower dead center from top dead center (or from lower dead center moves to top dead center during) piston (the multiple piston ring middle distance piston-top surfaces on piston side perisporium nearest) is h6, and wherein the ratio of h5 and h6 meets relation: 0.75≤h5/h6≤0.85.

Thus, by the degree of depth of control cylinder body water jacket, serve minimizing cooling loss, reduce the object that cylinder 203 is out of shape, improves combustion efficiency.And especially, shown in composition graphs 6, meet relation by the ratio of control h5 and h6: 0.75≤h5/h6≤0.85, obvious for the pressure result reducing cylinder wall, thus substantially improve cylinder 203 and be out of shape.

For the motor of or high compression ratio higher for explosive force, such as duel fuel engine, pressure in firing chamber is high, therefore strict requirement is had for the bolt for fastening cylinder block 201 and cylinder head, if fastening not firm, may cause leaking gas between cylinder block 201 and cylinder head, have a strong impact on the performance of motor.

Particularly, shown in composition graphs 5, according to the body group of the embodiment of the present invention, its cylinder block 201 and cylinder head by threaded fastener 229 such as bolton, and alternatively, corresponding four threaded fasteners 229 of each cylinder 203.

These four threaded fasteners 229 are looped around the periphery of corresponding cylinder 203 and can be distributed in four point of intersection (as shown in Figure 5) of rectangle.Like this, can fixed effect be improved, and then increase the sealing between cylinder block 201 and cylinder head.

Further, inventor finds, the fore-and-aft distance (L1) of two threaded fasteners 229 of homonymy is consistent with the centre distance of corresponding cylinder 203, thus can ensure that the impacting force between two longitudinal screw fastening pieces 229 is evenly distributed on former and later two cylinders 203.Horizontal spacing is arranged that (L2) then can need to adjust within the specific limits according to concrete layout, if horizontal spacing (L2) is selected excessive, the place place nearest at adjacent two cylinders 203 will become sealed thin weakness, be difficult to sealing two cylinder 203 ridge area place high-pressure gas, and horizontal spacing (L2) is chosen too small, by the sealing difficulty causing cylinder 203 apart from vertical center line 200 farthest, also can cause the region unbalance stress that adjacent two cylinders 203 are nearest simultaneously, cause cylinder 203 to be out of shape seriously.

In view of this, inventor finds, by the ratio of reasonable design longitudinal pitch and horizontal spacing, can obtain good fastening and sealing effect.As a kind of mode of execution, the ratio of lateral separation and fore-and-aft distance controls between 0.95-1.15 more excellent.In other words, the rectangle that four threaded fasteners 229 distribute is L1 along the length of the longitudinal direction of motor, and this rectangle is L2 along the width of the transverse direction of motor, thus 0.95≤L2/L1≤1.15.

Thus, by reasonable Arrangement threaded fastener 229, thus all the pretightening force of threaded fastener 229 can be evenly distributed in cylinder 203 end face under condition such as assembling operating mode, thermal stress operating mode etc., reach the object in gap between the reasonable coating gas cylinder body 201 of pretightening force, cylinder head, greatly improve the sealing between cylinder block 201 and cylinder head, prevent the high-temperature gas in firing chamber from leaking, ensure motor can normally, stable operation.

Especially, as one of them preferred embodiment, L2/L1=0.95.As another preferred embodiment, L2/L1=1.As another preferred embodiment, L2/L1=1.15.

About the distribution situation of threaded fastener 229, in other optional mode of executions, four threaded fasteners 229 of each cylinder 203 correspondence also can be equal with the distance of the center line of corresponding cylinder 203, each like this threaded fastener 229 uniform force, avoid stressed the concentrating of single or partial threads fastening piece 229 and cause this threaded fastener 229 that running phenomenon occurs, affect sealing and the motor reliability of operation of cylinder block 201 and cylinder head.

For the reinforing function of body group and cylinder 203, structure can also be strengthened realize by arranging.Especially for the wall portion at cylinder head jacket place, due to permission spatially, block jacket can be improved further so that the strength and stiffness of whole body group by setting up reinforcement structure example such as deep floor.

Can arrange deep floor respectively on the first side wall 219 of body group and the second sidewall 221, this deep floor can be one and longitudinally arrange, can certainly be many and short transverse along motor is spaced apart from each other.Every bar deep floor can be continuous print in the vertical, can certainly disconnect as required.Two floors tilted can be set below every bar floor, thus form stool formula rib structure, reduce cylinder 203 discontinuity that block jacket strength deficiency causes, and then increase the intensity of cylinder 203 better, prevent cylinder 203 to be out of shape.

In addition, additional moment is produced with the interphase interaction of bolt of main bearing cap for reducing threaded fastener 229, the floor of one or more above-below direction can be increased between threaded fastener 229 and bolt of main bearing cap, reduce the cylinder 203 caused because of addition bend moment and be out of shape.

In addition, for the cylinder 203 reduced because crankcase mode difference causes is out of shape, can arranges that outside crankcase arch structure one or more is horizontal ribbed, and increase horizontal ribbed additional ribs plate structure, to form cross one another reticular structure, reduce the cylinder 203 because mode difference causes.

As preferred embodiment, the height that above-mentioned floor gives prominence to corresponding wall should control the 2-3 doubly left and right at this floor thickness, and be preferably about 2.5 times, stiffening effect is obvious thus.Such as, for the deep floor on the first side wall 219, the height that this deep floor gives prominence to the first side wall 219 surface is that 2.5 times of this deep floor thickness are more excellent.

To sum up, according to the body group of the embodiment of the present invention, effectively increase the strength and stiffness of cylinder 203 by the improvement of structure, effectively can prevent the distortion of cylinder 203, ensure that motor can be stablized, Effec-tive Function, improve fuel economy and the Power output performance of motor.Body group according to the embodiment of the present invention is particularly suitable for duel fuel engine, such as gasoline, diesel duel fuel engine.

In addition, the vehicle comprising motor 1000 as above is further provided according to embodiments of the invention.Should be understood that, all be well known for ordinary skill in the art for prior art as driving system, steering system, braking system etc. according to other configuration example of the vehicle of the embodiment of the present invention, therefore the detailed description of conventional construction omitted herein.

In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present invention or example.In this manual, to the schematic representation of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.In addition, the different embodiment described in this specification or example can carry out engaging and combining by those skilled in the art.

Although illustrate and describe embodiments of the invention above, be understandable that, above-described embodiment is exemplary, can not be interpreted as limitation of the present invention, and those of ordinary skill in the art can change above-described embodiment within the scope of the invention, revises, replace and modification.

Claims (10)

1. a motor, is characterized in that, comprising:

Connecting rod, described connecting rod comprises body group, piston connecting rod unit and crankshaft-flywheel group, in the cylinder block of described body group, there is at least one cylinder, be formed with the intake duct corresponding with each described cylinder and air outlet flue in the cylinder head of described body group, the bottom surface of described cylinder head is plane;

Diesel injector, each described cylinder correspondence arranges diesel injector described at least one;

For the gasoline ejector of injected petrol fuel; And

Distribution device, described distribution device comprises intake valve and the exhaust valve of corresponding each described cylinder, and each in described intake valve and described exhaust valve is all used to open or close corresponding firing chamber, wherein

The swirl rate of described firing chamber is between 1-6, and compression ratio is between 13-17.

2. motor according to claim 1, is characterized in that, the swirl rate in described firing chamber is between 1.5-5.

3. motor according to claim 1, is characterized in that, described compression ratio is 14.8-15.5.

4. motor according to claim 1, is characterized in that, the center line of described diesel injector overlaps with the center line of corresponding cylinder.

5. motor according to claim 4, is characterized in that, the spray cone angle of described diesel injector is between 70 °-85 °.

6. motor according to claim 5, is characterized in that, the spray cone angle of described diesel injector is between 75 °-80 °.

7. motor according to claim 1, it is characterized in that, the end face of described piston is formed with pit, described pit is revolution shape, described solid of rotation has throat structure, the rotational axis of described solid of rotation overlaps with the center line of corresponding cylinder, and the relative aperture of wherein said piston remains between 0.7-0.8, and the reducing ratio of described piston remains between 0.8-0.9.

8. motor according to claim 7, it is characterized in that, the revolution bus of described solid of rotation comprises the diapire mixing line segment of the sidewall profiles section for the formation of the sidewall of described pit and the diapire for the formation of described pit, described sidewall profiles section comprises the side wall transition section be connected successively, sidewall reducing section and side wa ll circle arc section, described diapire mixing line segment comprises diapire first straightway be connected successively, diapire first arc section, diapire second straightway, diapire second arc section and diapire the 3rd straightway, wherein said diapire first straightway is connected with described side wa ll circle arc section.

9. motor according to claim 8, it is characterized in that, the radius of curvature of described side wall transition section is 18-22mm, the radius of curvature of described sidewall reducing section is at 1.5-2mm, the radius of curvature of described side wa ll circle arc section is between 3.5-4.5mm, the radius of curvature of described diapire first arc section is 11-15mm, and the radius of curvature of described diapire second arc section is 23-27mm; And

Described diapire first straightway is parallel with the bottom surface of described cylinder head respectively with described diapire the 3rd straightway, and the inclined bottom surface of the relatively described cylinder head of described diapire second straightway is arranged,

The length of wherein said diapire first straightway is 3.5-4.5mm, the angle of the bottom surface of described diapire second straightway and described cylinder head at 20 °-24 °, described diapire the 3rd straightway when described piston is in top dead center and the distance of the bottom surface of described cylinder head be 2.5-3.5mm.

10. motor according to claim 9, is characterized in that, by chamfered transition between the end face of described piston and the sidewall of described piston, the length of described chamfering is 0.5-2mm, and the compression clearance of described piston is 1-2.5mm.