CN203856595U - Cylinder cover for engine and engine with cylinder cover - Google Patents

Abstract

The utility model discloses a cylinder cover for an engine and the engine with the cylinder cover. An air inlet channel and an air outlet channel which correspond to a cylinder are formed in the cylinder cover, a sparking plug corresponding to the cylinder is arranged on the cylinder cover and is located on the exhaust side of the corresponding cylinder, and the sparking plug is arranged obliquely relative to the center line of the cylinder corresponding to the sparking plug. According to the cylinder cover for the engine and the engine with the cylinder cover, due to the fact that the sparking plug on the cylinder cover is arranged obliquely and is located on the exhaust side, interference between the sparking plug and other parts is avoided, and the manufacturing difficulty of the cylinder cover is lowered.

Description

For the cylinder head of motor and there is the motor of this cylinder head

Technical field

The utility model relates to automotive field, especially relates to a kind of cylinder head for motor and has the motor of this cylinder head.

Background technique

The body group of motor comprises cylinder head, cylinder head gasket, cylinder block and oil sump.In cylinder block, be formed with a plurality of cylinders, piston can do reciprocating linear motion in cylinder.Wherein, the spark plug on conventional engines adopts arrangement placed in the middle, and spark plug overlaps with cylinder centerline.But for duel fuel engine, may exist and other parts situation that for example diesel injector interferes, thereby cause air cylinder head structure too complicated.

Model utility content

The utility model is intended to solve at least to a certain extent one of above-mentioned technical problem of the prior art.For this reason, an object of the present utility model is to propose a kind of cylinder head for motor, and the spark plug in this cylinder head adopts biasing set-up mode and is positioned at exhaust side, avoids interfering with other parts, reduces the manufacture difficulty of cylinder head.

Another object of the present utility model is to propose a kind of motor with above-mentioned cylinder head.

According to the utility model embodiment's the cylinder head for motor, in described cylinder head, be formed with the intake duct corresponding with cylinder and air outlet flue, in described cylinder head, be provided with the spark plug corresponding with cylinder described in each, described spark plug is positioned at the exhaust side of corresponding cylinder, and described spark plug is obliquely installed with respect to the center line of the cylinder corresponding with this spark plug.

According to the spark plug in the utility model embodiment's cylinder head, adopt biasing set-up mode and be positioned at exhaust side, thereby avoiding interfering with other parts, reducing the manufacture difficulty of cylinder head.

In addition, according to the utility model embodiment's the cylinder head for motor, can also there is following additional technical feature:

According to embodiments more of the present utility model, the center line of described spark plug with the angle of the center line of corresponding cylinder between 6 °-14 °.

According to embodiments more of the present utility model, the center line of described spark plug with the angle of the center line of corresponding cylinder between 8 °-12 °.

According to embodiments more of the present utility model, the first end of described spark plug extend in corresponding cylinder and the second end passes the air outlet flue that this cylinder is corresponding and stretches out.

According to embodiments more of the present utility model, the air outlet flue that described in each, cylinder is corresponding is two, and the close to each other and next-door neighbour of the afterbody of described two air outlet flues to be to form common-use tunnel, and described second end of described spark plug is through described common-use tunnel and stretch out.

According to embodiments more of the present utility model, the angle of the vertical plane of the center line of intake valve and the vertical center line by described motor is between 0 °-5 °; And

The center line of described exhaust valve and the angle of described vertical plane are between 0 °-5 °.

According to embodiments more of the present utility model, the angle between the center line of intake valve and the center line of exhaust valve is in 10 °.

According to embodiments more of the present utility model, the intersection point of the center line of described spark plug and the bottom surface of described cylinder head is in the 0.2D of described cylinder bore to the distance of the center line of described cylinder, the diameter that described D is cylinder.

According to embodiments more of the present utility model, the intersection point of the center line of described spark plug and the bottom surface of described cylinder head is in the 0.15D of described cylinder bore to the distance of the center line of described cylinder.

According on the other hand of the present utility model, a kind of motor with above-mentioned cylinder head has also been proposed.

Accompanying drawing explanation

Fig. 1 is according to the stereogram of the utility model embodiment's motor;

Fig. 2 is the partial sectional view of the motor of having a try according to the utility model;

Fig. 3 is the partial schematic diagram in Fig. 2;

Fig. 4 is diesel injector, spark plug and the schematic diagram of corresponding cylinder centerline;

Fig. 8 is the schematic diagram of the pit of piston;

Fig. 9 is any vertical section figure that passes through rotational axis of pit;

Figure 10 is the stereogram of piston.

Embodiment

Describe embodiment of the present utility model below in detail, described embodiment's example is shown in the drawings, and wherein same or similar label represents same or similar element or has the element of identical or similar functions from start to finish.Below by the embodiment who is described with reference to the drawings, be exemplary, be intended to for explaining the utility model, and can not be interpreted as restriction of the present utility model.

In description of the present utility model, it will be appreciated that, term " " center ", " longitudinally ", " laterally ", " 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 indications such as " counterclockwise " are based on orientation shown in the drawings or position relationship, only the utility model and simplified characterization for convenience of description, rather than device or the element of indication or hint indication must have specific orientation, with specific orientation structure and operation, therefore can not be interpreted as restriction of the present utility model.

In addition, term " first ", " second " be only for describing object, and can not be interpreted as indication or hint relative importance or the implicit quantity that indicates indicated technical characteristics.Thus, one or more these features can be expressed or impliedly be comprised to the feature that is limited with " first ", " second ".In description of the present utility model, the implication of " a plurality of " is at least two, for example two, and three etc., unless otherwise expressly limited specifically.

In the utility model, unless otherwise clearly defined and limited, the terms such as term " installation ", " being connected ", " connection ", " fixing " should be interpreted broadly, and for example, can be to be fixedly connected with, and can be also to removably connect, or be integral; Can be mechanical connection, can be to be also electrically connected to; Can be to be directly connected, also can indirectly 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, can understand as the case may be the concrete meaning of above-mentioned term in the utility model.

In the utility model, unless otherwise clearly defined and limited, First Characteristic Second Characteristic it " on " or D score can comprise that the first and second features directly contact, also can comprise that the first and second features are not directly contacts but contact by the other feature between them.And, First Characteristic Second Characteristic " on ", " top " and " above " comprise First Characteristic directly over Second Characteristic and oblique upper, or only represent that First Characteristic level height is higher than Second Characteristic.First Characteristic Second Characteristic " under ", " below " and " below " comprise First Characteristic under Second Characteristic and tiltedly, or only represent that First Characteristic level height is less than Second Characteristic.

Below with reference to Fig. 1-Figure 10, describe in detail according to the utility model embodiment's motor 1000, the feature of motor 1000 is directly to input machine internal-combustion and produce power 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 that combustion gas is acted on to the torque that power on piston 109 changes bent axle into, with to work mechanism output mechanical energy.Usually, connecting rod mainly comprises piston rod group, crankshaft-flywheel group and body group.

Piston rod group changes the to-and-fro motion of piston 109 into bent axle rotatablely move, and changes the power acting on piston 109 into the bent axle externally torque of output simultaneously, thereby drives the vehicle wheel rotation of vehicle.Usually, piston rod group comprises piston 109, piston ring, wrist pin and connecting rod etc., and wrist pin is used for connecting piston and connecting rod.Crankshaft-flywheel group mainly consists of bent axle and flywheel.

Body group is the support of motor, is the assembling matrix of piston rod group, crankshaft-flywheel group, distribution device and motor 1000 each system major parts.Body group mainly comprises cylinder head 101, cylinder head gasket, cylinder block 201 and oil sump 301 (as shown in Figure 1), 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 3) and the end face of cylinder block 201 of cylinder head 101, 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 description of the present utility model, as shown in Figure 1, the length direction that longitudinally refers to motor 1000 of motor 1000 (or body group), the thickness that laterally refers to motor 1000 (width) direction of motor 1000 (or body group), the short transverse of motor 1000 (or body group) refers to the direction of the center line that is parallel to cylinder 203.

As Fig. 1 and in conjunction with as shown in Fig. 2, cylinder block 201 has at least one cylinder 203, cylinder 203 is the cylindrical cavities that move and lead therein for piston 109, cylinder 203 is generally formed on the first half of cylinder block 201, and the Lower Half of cylinder block 201 can be generally crankcase, but be not limited to this.For straight engine 1000, as shown in Figure 2, its a plurality of cylinders 203 are that a plurality of cylinders 203 are 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 2).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 to this.

As shown in Figure 3, be formed with the intake duct corresponding with each cylinder 203 103 and air outlet flue 104 in cylinder head 101, intake duct 103 is for to firing chamber transferring oil gas mixture (or air), and air outlet flue 104 is for combustion gas.Usually, can adopt two to enter scene 2 air flue form, be that intake duct 103 and air outlet flue 104 are two, but be not limited to this, for example can also adopt three to enter scene 2 or one-in-and-one-out, for the ordinary skill in the art, can be 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 according to the work cycle of carrying out in motor 1000 each cylinder 203 and the requirement of firing order, time opening and close intake valve 108 and exhaust valve 110, for example make, in fresh momentum (gas mixture or the air) cylinder 203 of entering in time, and waste gas is discharged from cylinder 203 in time.

Distribution device mainly comprises valve group and valve transmission group part, valve group generally comprises air inlet side valve and (is called for short intake valve 108, in conjunction with Fig. 6) and exhaust side valve (abbreviation exhaust valve 110, in conjunction with Fig. 6), intake valve 108 and exhaust valve 110 can by independent camshaft actuated, it be regularly opened, closes respectively.Camshaft can link with the bent axle of motor 1000, can adopt the various ways such as gear transmission, chain transmission or band transmission 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.For example, can adopt two to enter scene 2 four air valve structures, or three enter scene 2 five air valve structures, can certainly adopt one-in-and-one-out two air valve structures.Thereby the intake valve 108 in each firing chamber and exhaust valve 110 are opened according to certain rule circulation by the driving of corresponding camshaft, thereby 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 that spark coil is produced is introduced firing chamber, and produces electrical spark between two electrodes, thereby lights inflammable mixture, and spark plug 105 mainly can be comprised of centre electrode, lateral electrode, housing and insulator etc.In embodiments more of the present utility model, each cylinder 203 correspondence arranges a spark plug 105, and this spark plug 105 can adopt the mode being threaded to be fixed on the corresponding position of cylinder head 101.

Gasoline ejector, for injected petrol fuel, in embodiment of the present utility model, is not made particular determination to the concrete setting position of gasoline ejector.For example, gasoline ejector can be (that is, multi-point injection) one to one with the quantity of cylinder 203, and gasoline ejector can be arranged in cylinder head 101 and can directly fuel be sprayed into the place ahead of the intake valve 108 of corresponding cylinder 203.Certainly, gasoline ejector also can corresponding a plurality of cylinders 203 (that is, single-point discharge), and this oil sprayer can be arranged in the section before closure, can enter in air intake branch with air stream, and distribute to respectively each cylinder 203 after fuel sprays into.

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 embodiments more of the present utility model, each cylinder 203 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., all, for prior art and be well known for ordinary skill in the 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 for spraying diesel oil.Or this unit injector also can have two nozzles, one for injected petrol, and another is for spraying diesel oil, two nozzle mutual noninterferences.In these embodiments, the Fuel Petroleum of gasoline ejector ejection is to be 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 according to the utility model embodiment's motor 1000 for spraying the diesel injector 107 of diesel oil and for the gasoline ejector of injected petrol, therefore also can being referred to as gasoline, diesel duel fuel engine 1000 (being called for short duel fuel engine 1000) according to the utility model embodiment's motor 1000.

According to the utility model embodiment's duel fuel engine 1000, piloting engine 1000 o'clock, can carry out ignition start by spark plug 105 modes of igniting.And after duel fuel engine 1000 normal startings, can in compression ignite mode, work by spraying diesel oil, now spark plug 105 can quit work.Thereby, make according to the utility model embodiment's duel fuel engine 1000 than diesel engine, when starting, can effectively reduce discharge, for the problem of diesel engine cold-starting difficulty, by ignition way, can start smoothly especially.According to after the utility model embodiment's duel fuel engine 1000 startings, can by compression ignite mode, replace the ignition way of spark plug 105, high compression ratio contributes to abundant burning thus, improves fuel economy and the power output performance of motor 1000.

In addition, according to the utility model embodiment's motor 1000 because normal working stroke circulation time spark plug 105 can quit work, spark plug 105 can only be lighted a fire when starting, therefore can greatly reduce the igniting number of times of spark plug 105, improve the working life of spark plug 105, reduce user cost, also simplified control strategy simultaneously.

But, it should be noted that, above-mentioned about being only schematically to illustrate according to the starting process of the utility model embodiment's duel fuel engine 1000 and normal stroke cycle, can not be interpreted as it is to a kind of restriction of the present utility model, or imply that motor 1000 of the present utility model only can start or normal circulation work in the above described manner in the above described manner.

Shown in Fig. 3 and Fig. 4, according to the bottom surface M1 of the utility model embodiment's cylinder head 1, adopt non-integral type plane structure, particularly, the underside portion of the corresponding cylinder of cylinder head 1 is formed with fovea superior structure 401, in other words, take four-cylinder in upright arrangement as example, and the bottom surface of this cylinder head 1 can have four fovea superior structures 401, the corresponding cylinder 203 of each fovea superior structure 401.

Thus, owing to adopting non-integral type plane structure, be different from the flat-bottom structure of conventional diesel, therefore can be based on petrol engine according to the utility model embodiment's motor, the petrol engine of usining is transformed as prototype.

And owing to adopting fovea superior structure 401, piston 109 can be more near cylinder head when top dead center, effectively utilize cylinder cap space, the compression height of piston 109 is reduced, the weight saving of piston 109, thereby reduced the frictional loss of piston rod group, improved the thermal efficiency of motor.

Inventor's discovery, for duel fuel engine 1000, reasonable design compression ratio discharges and improves power output for fuel economy, the reduction of motor 1000 direct relation.

In view of this, inventor finds according to industry experience and great many of experiments for many years, by compression ratio being controlled to 13-17 particularly between 14-16, can effectively solve the problem of motor 1000 cold starting difficulties, the pinking problem of simultaneously avoiding high compression ratio to bring, make motor 1000 starting, operation more steadily, reliable, power output property is strong and reached preferably fuel economy and lower noxious gas emission.

Inventor further finds, more excellent by compression ratio is controlled between 14.8-15.5.Therefore,, according to an embodiment of the present utility model, compression ratio is between 14.8-15.5.Especially, according to a preferred embodiment of the present utility model, the compression ratio of motor 1000 is 15.1.According to another embodiment of the present utility model, compression ratio is 15.3.

Due to according to not only arranging diesel injector 107 in the utility model embodiment's cylinder head 101, also to arrange spark plug 105 simultaneously, therefore higher to the structural requirement of cylinder head 101, the while has also increased the layout difficulty of distribution device.

Shown in Fig. 6, because the suction ports 102 of intake valve 108 sealing intake duct 103 ends (place, firing chamber) and the center line of intake valve 108 and this suction port 102 are quadratures roughly, similarly, the relief openings 106 of exhaust valve 110 sealing air outlet flue 104 head ends (place, firing chamber) and the center line of exhaust valve 110 and this relief opening 106 are quadratures roughly, so the angle that arranges of intake valve 108 and exhaust valve 110 has reflected the angle between this suction port 102 and cylinder head 101 bottom surface M1 and relief opening 106 and cylinder head 101 bottom surface M1 indirectly.

For example, take intake valve 108 and the vertical plane M3 (M3 as shown in Figure 6) of vertical center line 200 by motor 1000 angle as 5 ° be example, this intake valve 108 is 85 ° of left and right with the angle of cylinder head 101 bottom surface M1, and because this suction port 102 and intake valve 108 are quadratures roughly, therefore this suction port 102 with the angle of cylinder head 101 bottom surfaces 5 ° of left and right, thereby can think intake duct 103 particularly the bottom surface angle of intake duct 103 rears and cylinder head 101 be 5 ° of left and right.

Similarly, take exhaust valve 110 and above-mentioned vertical plane M3 angle as 5 ° be example, this exhaust valve 110 is 85 ° of left and right with the angle of cylinder head 101 bottom surface M1, and because this relief opening 106 and exhaust valve 110 are quadratures roughly, therefore this relief opening 106 with the angle of cylinder head 101 bottom surfaces 5 ° of left and right, thereby can think air outlet flue 104 particularly the bottom surface angle of air outlet flue 104 initial segments and cylinder head 101 be 5 ° of left and right.

In brief, the angle that arranges of intake valve 108 and exhaust valve 110 has reflected the air outlet flue 104 (rear of air outlet flue 104 particularly indirectly, can think relief opening 104) and the angle of intake duct 103 (particularly the initial segment of intake duct 103, can think suction port 102) and cylinder head 101 bottom surfaces.That is, as shown in Figure 6, can think approx β 1=β 4, β 2=β 5.

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

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

But the utility model is not limited to this, in other embodiments of the present utility model, the angle β 3 between the center line of intake valve 108 and the center line of exhaust valve 110 can be less than 10 °.In other words, in this embodiment, the angle being not limited between intake valve 108 and vertical plane M3 must be in 5 °, exhaust valve 110 also must be within 5 ° with the angle of vertical section M3, for example the angle between intake valve 108 and vertical plane M3 can be 8 °, and angle between exhaust valve 110 and vertical plane M3 is less than 2 °, thereby guarantee that the angle β 3 between the two is not more than 10 °.

Thus, can guarantee that equally motor 1000 all has the preferably mixing rate in diffusive combustion stage under each rotating speed, and can increase turbulence intensity in reaching certain limit time, and then be beneficial to carrying out smoothly of combustion process, reduce smoke intensity simultaneously.Meanwhile, this narrower valve angle can make cylinder head 101 compact structures, reduces cooling loss and obtains best surface area/volume.It should be noted that, above-mentioned intake valve 108 refers to the intake valve transversely respect to one another 108 and exhaust valve 110 at motor 1000 with the angle of exhaust valve 110.

Inventor finds, by controlling the angle that arranges of above-mentioned intake valve 108, exhaust valve 110, coordinate suitable compression ratio (for example 13-17) simultaneously, thereby can solve better the problem of motor 1000 cold-starting difficulties, avoid the phenomenon of detonation causing due to high compression ratio, fuel economy and the power character of improving motor 1000, the discharge of harmful gas reduces greatly.

As some optional further embodiments, as shown in Figure 4, fovea superior structure 401 forms paulin shape, and in other words, fovea superior structure 401 has down " V " shape vertical section structure.Particularly, longitudinal vertical section of fovea superior structure 401 is for falling " V " shape, and this longitudinal vertical section refers to by the vertical section of the vertical center line 200 of motor 1000.The angle β 8 of " V " shape is between 171 ° 30 '-176 °.

Thus, the paulin shape cylinder head bottom surface structure in this angular range can mate the angle of high compression ratio and intake valve 108, exhaust valve 110 and vertical plane M3 better, thereby improves better combustion efficiency, reduces discharge.

Below in conjunction with Fig. 8-Figure 10, the piston 109 according to the utility model embodiment 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 simultaneously, therefore reasonably type selecting piston 109 is most important for motor 1000.

Shown in Fig. 8-Figure 10, according to embodiments more of the present utility model, 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 have directly determined the structure of firing chamber, and and then are associated with every combustion index of motor 1000.

In embodiment of the present utility model, pit 111 is revolution shape preferably, the rotational axis 117 (as shown in Figure 9) of this solid of rotation overlaps with the center line M2 (M2 as shown in Figure 7) of corresponding cylinder 203, and in other words, this pit 111 is formed on the center at piston 109 tops.Thus, pit 111 layout placed in the middle can be avoided piston 109 unbalance stress and cause cylinder wall local pressure to be concentrated, thereby can improve cylinder 203 problem on deformation, 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, minimizing escapes into the combustion gas in crankcase from gap between piston 109 and cylinder wall, avoids this part combustion gas to affect performance and the life-span of crankcase inner engine oil.

Shown in Fig. 8-Figure 10, pit 111 is " ω " shape, and the vertical section that passes through rotational axis 117 of pit 111 is " ω " shape.Here, it should be noted that, pit 111 should be made broad understanding for " ω " shape, and the vertical section that can be understood as pit 111 can be the shape approximate with " ω " shape, and 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, pit 111 tops have 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 throat structure 127 the narrowest places of pit 111 and the diameter of cylinder 203, and relative aperture is K4/D (wherein K4 as shown in Figure 8, cylinder bore D is in conjunction with shown in Fig. 3).The reducing of piston 109 is than referring to the throat structure 127 the narrowest places of pit 111 and the diameter ratio of pit 111 throat structure 127 bottom the widest position, i.e. reducing is than being K4/K5 (K4, K5 are in conjunction with shown in Fig. 8).

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

Below in conjunction with Fig. 8-Fig. 9, pit 111 structures are elaborated.

As shown in Figure 9, pit 111 is revolution shape, and solid of rotation has revolution bus 115 and rotational axis 117, and this solid of rotation is for revolution bus 115 is around rotational axis 117 rotating 360 degrees formation.In the example of Fig. 9, in fact any vertical section that comprises rotational axis 117, on this cross section, the medianly zygomorphic part of rotational axis 117 all can be used as revolution bus 115, in the following description, usining the part that is positioned at rotational axis 117 left sides is described as revolution bus 115.

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

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

Shown in Fig. 9, particularly, sidewall curved section 119 can comprise sidewall changeover portion 121, sidewall reducing section 123 and sidewall arc section 125, and sidewall changeover portion 121, sidewall reducing section 123 are connected from top to bottom successively with sidewall arc section 125.Sidewall changeover portion 121 is used to form the transition portion that connects throat structure 127 and piston 109 end faces, and sidewall reducing section 123 is used to form above-mentioned throat structure 127, and sidewall arc section 125 is used to form the lower sides part of firing chamber.

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

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

Further, because sidewall curved section 119 consists of multiple curved section, diapire mixing line segment 129 consists of multiple curved section and straightway, so the relevant parameter of each curved section and straightway is directly connected to the performance of the thermal efficiency and the motor 1000 of motor 1000.

In embodiments more of the present utility model, as shown in Figure 9, the radius of curvature r0 of sidewall changeover portion 121 can be between 18-22mm, 20mm preferably, the radius of curvature r1 of sidewall reducing section 123 can be between 1.5-2mm, the radius of curvature r2 of sidewall arc section 125 is between 3.5-4.5mm, preferably between 3.5-4mm, diapire the first straightway 131 is preferably parallel to cylinder block end face, the length of diapire the first straightway 131 can be between 3.5-4.5mm, be preferably 4mm, the radius of curvature r3 of diapire the first arc section 133 can be between 11-15mm, be preferably 13mm, the top surface inclination setting of diapire the second straightway 135 relative cylinder block 201, slanted angle β 7 can be between 20 °-24 °, be preferably 22 °, the radius of curvature r4 of diapire the second arc section 137 can be 23-27mm, be preferably 25mm, diapire the 3rd straightway 139 is preferably parallel to cylinder block end face, and diapire the 3rd straightway 139 is positioned at the top (oblique upper) of diapire the first straightway 131, it is the height that arranges that arranging of diapire the 3rd straightway 139 is highly greater than diapire the first straightway 131.

Above-mentioned design can be so that the relative aperture of piston 109 remains between 0.7-0.8, reducing ratio remains between 0.8-0.9, and be a kind of more preferably mode of execution, being beneficial to diesel oil spreads to firing chamber clearance, thereby effectively reduce HC discharge, reduce NOx, be beneficial to the carrying out of burning, improved the abundant degree of burning.

To sum up, according to the utility model embodiment's piston 109 structures, fully combine the feature of traditional diesel oil " ω " type and tray type gasoline combustion, by to the optimization of firing chamber line style and innovative design, met duel fuel engine 1000 demand to chamber structure under different working modes.

Meanwhile, according to the utility model embodiment's piston 109, form on the whole shallow " ω " type, surface to volume ratio reduces greatly, thereby has reduced motor 1000 external heat transfer loss in the course of the work, has improved the thermal efficiency of motor 1000.

In addition, according to the bottom surface M1 of the cylinder head 101 of the utility model embodiment's motor 1000, there is fovea superior structure 401, coordinate this " ω " type piston 109 and suitable air valve angle and compression ratio (for example 14.8-15.5), thereby the properties that has promoted on the whole motor 1000, has reduced the discharge of harmful gas.And, according to the utility model embodiment's motor 1000, can using diesel engine and transform as prototype.

Below with reference to Fig. 7, in conjunction with specific embodiments spark plug 105 and diesel injector 107 are described in detail.

First the set-up mode of spark plug 105 is described.

In embodiment of the present utility model, spark plug 105 is arranged in cylinder head 101, and for example spark plug 105 can be 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., the discharge important during for starting.

Inventor finds, as shown in Figure 7, by by spark plug 105 biasing, the center line M2 that departs from cylinder 203 arranges, control simultaneously spark plug 105 and cylinder head 101 intersection points apart from the distance K1 of cylinder 203 center lines during for starting the control of combustion flame and rate of burning there is beneficial effect.

Thus, in certain embodiments, the center line M2 that spark plug 105 departs from corresponding cylinder 203 arranges, that is to say, 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 intersection point of the bottom surface of the center line of spark plug 105 and cylinder head 101 is apart from the distance K1 of the center line M2 of cylinder 203 in 0.2D, and wherein D is the diameter (internal diameter) of cylinder 203, and K1 is less than 0.2D.

Thus, piloting engine 1000 o'clock, can avoid occurring phenomenon of detonation, improve flame area spreading rate and rate of burning, balanced flame travel, effectively avoids pre-ignition, also facilitates motor 1000 cleaning waste gas simultaneously, improve better ignition difficulties problem, and greatly improved 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 utility model embodiment has diesel injector 107, by by spark plug 105 biasing, thereby for the arrangement of diesel injector 107 provides the useful space, avoid the two on mounting point, to interfere and affect the performance of motor 1000.

As preferred embodiment, the intersection point of the bottom surface of the center line of spark plug 105 and cylinder head 101 apart from the distance of the center line of cylinder 203 in 0.15D, i.e. K1 < 0.15D.

Wherein, in a preferred embodiment, K1=0.098D.In another preferred embodiment, K1=0.105D.In yet another preferred embodiment, K1=0.12D.

In embodiment of the present utility model, 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 these cylinder 203 correspondences and stretches out, and the direction referring to deviating from firing chamber that stretches out is here extended.By this layout, can be so that cylinder head 101 structures be compacter, avoid interfering with diesel injector 107 simultaneously, spark plug 105 can be saved arrangement space to the maximum limit through air outlet flue 104, while is less for exhaust performance impact, has greatly improved the space availability ratio of cylinder head 101 end faces.

Embodiment as further optimization, in conjunction with Fig. 5, 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 and stretch out through this common-use tunnel 112.Like this, spark plug 105 is positioned at the center of two air outlet flues 104, makes the overall structure of cylinder head 101 compacter, and space availability ratio is higher, is beneficial to and reduces the volume that body group takies, and the layout that is in particular distribution device and diesel injector 107 is provided convenience.

But spark plug 105 also can be set to not through air outlet flue 104 in the utility model, and be positioned at air outlet flue 104 towards a side place of intake duct 103, as shown in Figure 3.In brief, for the ordinary skill in the art, can design according to actual needs and flexibly the position relationship of spark plug 105 and air outlet flue 104, include, but are not limited to the above-mentioned form of passing air outlet flue form and not passing air outlet flue.

Inventor's discovery, for conventional engines 1000, 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 spark plug 105 biasing arranges in the application, so angle is set can 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 an embodiment of the present utility model, spark plug 105 is obliquely installed with respect to the center line of the cylinder 203 of these spark plug 105 correspondences, be that the center line of spark plug 105 and the center line of cylinder 203 are uneven, as shown in Figure 7.

Further, in certain embodiments, as shown in Figure 7, the center line of spark plug 105 with the angle β 6 of the center line of corresponding cylinder 203 between 6 °-14 °.Thus, can improve flame area spreading rate and rate of burning, balanced flame travel, effectively avoids pre-ignition, also facilitates motor 1000 cleaning waste gas simultaneously, improves better ignition difficulties problem.

As preferred embodiment, as shown in Figure 7, the center line of spark plug 105 with the angle β 6 of the center line of corresponding cylinder 203 between 8 °-12 °.

Thus, not only can effectively avoid liquid fuel collision spark plug 105 and supply the mixed gas of overrich and on spark plug 105, form carbon distribution to spark plug 105, also having weighed near the cooling effect of spark plug 105.Simultaneously by adopting the setting type of diesel injector 107 and spark plug 105 larger spacing, and spark plug 105 is in tilted layout in exhaust side, thereby be beneficial to, improve flame area spreading rate and rate of burning, balanced flame travel, thus avoid better pre-ignition.

Diesel injector 107 according to the utility model embodiment is described below.

In embodiments more of the present utility model, the diesel injector 4 relatively center line M2 biasing of corresponding cylinder 203 arranges.As preferred embodiment, the center line of diesel injector 4 is parallel with the center line of cylinder 203, i.e. cylinder setting corresponding to diesel injector 4 quadratures, and diesel injector 4 is positioned at air inlet side, thereby opposed with the spark plug 105 that is positioned at exhaust side, reasonably utilized the space of cylinder head 101.

Further, as shown in Figure 7, the intersection point of the bottom surface of the center line of diesel injector 4 and cylinder head 1 to the distance of the center line K2 of cylinder in 0.06D, i.e. K2 < 0.06D, as shown in Figure 7.

Thus, diesel injector 4 is arranged near center line, and diesel oil oil bundle can be distributed relatively equably in firing chamber, reduces each oily Shu Changdu and differs and cause mixed gas lack of homogeneity, thereby improve burning.

Inventor's discovery, the spray cone angle of diesel injector 107 is remarkable to soot, NOx discharge (emission index of oxynitrides) and three motor 1000 Index Influences of fuel consumption rate.Inventor finds by great many of experiments, and when the cone angle of diesel injector 107 being controlled between 70 °-85 °, soot emission levels is lower, and NOx reduces simultaneously, and oxynitride discharge reduces, and fuel consumption rate also decreases simultaneously.

Further, 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 the set-up mode of diesel injector 107 quadrature cylinders 203 and with the suitable distance of cylinder 203 center lines, diesel oil oil bundle is evenly distributed in firing chamber, avoid each oily Shu Changdu differ and cause mixed gas lack of homogeneity, impact burning, suitable spray cone angle can effectively reduce soot, NOx discharge and fuel consumption rate simultaneously, increases on the whole motor 1000 power output property, fuel economy, improve the thermal efficiency of motor 1000, reduce the discharge of harmful gas.

To sum up, arrangement in conjunction with spark plug 105, valve arranges angle, pit 111 line styles of piston 109, the spray cone angle of compression ratio and diesel injector 107 etc., make according to the petrol gas of the utility model embodiment's motor 1000, diesel oil oil gas and air can form homogeneous charge better, realize homogeneous combustion, flame combustion is abundant, diffusive combustion with respect to diesel oil, improved the combustion efficiency in motor 1000 starting process, emission effect while reducing motor 1000 starting, and than petrol engine, high compression ratio can further improve combustion efficiency, increase power performance and the fuel economy of motor 1000.

In the description of this specification, the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to be contained at least one embodiment of the present utility model or example in conjunction with specific features, structure, material or the feature of this embodiment or example description.In this manual, to the schematic statement of above-mentioned term not must for be identical embodiment or example.And the specific features of description, structure, material or feature can be with suitable mode combinations in any one or more embodiments or example.In addition, those skilled in the art can engage the different embodiments that describe in this specification or example and combine.

Although illustrated and described embodiment of the present utility model above, be understandable that, above-described embodiment is exemplary, can not be interpreted as restriction of the present utility model, those of ordinary skill in the art can change above-described embodiment in scope of the present utility model, modification, replacement and modification.

Claims (10)

1. the cylinder head for motor, it is characterized in that, in described cylinder head, be formed with the intake duct corresponding with cylinder and air outlet flue, in described cylinder head, be provided with the spark plug corresponding with cylinder described in each, described spark plug is positioned at the exhaust side of corresponding cylinder, and described spark plug is obliquely installed with respect to the center line of the cylinder corresponding with this spark plug.

2. the cylinder head for motor according to claim 1, is characterized in that, the center line of described spark plug with the angle of the center line of corresponding cylinder between 6 °-14 °.

3. the cylinder head for motor according to claim 2, is characterized in that, the center line of described spark plug with the angle of the center line of corresponding cylinder between 8 °-12 °.

4. the cylinder head for motor according to claim 3, is characterized in that, the first end of described spark plug extend in corresponding cylinder and the second end passes the air outlet flue that this cylinder is corresponding and stretches out.

5. the cylinder head for motor according to claim 4, it is characterized in that, the air outlet flue that described in each, cylinder is corresponding is two, close to each other and the next-door neighbour of the afterbody of described two air outlet flues to be to form common-use tunnel, and described second end of described spark plug is through described common-use tunnel and stretch out.

6. the cylinder head for motor according to claim 1, is characterized in that,

The angle of the vertical plane of the center line of intake valve and the vertical center line by described motor is between 0 °-5 °; And

The center line of described exhaust valve and the angle of described vertical plane are between 0 °-5 °.

7. the cylinder head for motor according to claim 1, is characterized in that, the angle between the center line of intake valve and the center line of exhaust valve is in 10 °.

8. the cylinder head for motor according to claim 1, it is characterized in that, the intersection point of the center line of described spark plug and the bottom surface of described cylinder head is in the 0.2D of described cylinder bore to the distance of the center line of described cylinder, the diameter that described D is cylinder.

9. the cylinder head for motor according to claim 8, is characterized in that, the intersection point of the center line of described spark plug and the bottom surface of described cylinder head is in the 0.15D of described cylinder bore to the distance of the center line of described cylinder.

10. a motor, is characterized in that, comprises according to the cylinder head for motor described in any one in claim 1-9.