CN101523018A - Internal combustion engine - Google Patents

Abstract

When viewed from the upper face of a cylinder head (52A) in which an intake port (10A) communicating with a combustion chamber (54) of an internal combustion engine (50A) is formed, a starting point (Pl) of the port (10A) is defined as a point of intersection of the streamline of the intake port (10A) and an inlet-side opening plane of the intake port (10A) as projected on a horizontal plane (S), and an end point (P2) is defined as a point of intersection of the streamline of the port (10A) and the center -axis of an intake valve (55) as projected on the horizontal plane (S). The starting point (Pl) is located closer to the center of the chamber (54) than a straight line (L2) that contains the end point (P2) and extends in a direction orthogonal to the axis of the crankshaft on the plane (S), and the streamline (F) of the port (10A) projected on the horizontal plane (S) is curved toward the center of the chamber (54), with respect to a straight line (L1) that contains the starting point (P1) and extends in a direction orthogonal to the axis of the crankshaft on the plane (S).

Description

Internal-combustion engine

Technical field

[0001] the present invention relates to a kind of internal-combustion engine, though relate in particular to a kind of valve stroke when suction valve be in little in scope in the time also can strengthen in the firing chamber, form wave the revolution air-flow internal-combustion engine.

Background technique

[0002] in order to improve the mode in the air inlet inflow firing chamber, multiple suction port design has been proposed.For example, in being the Japanese patent application (JP-A-10-169453) of 10-169453, publication number proposes, a kind of direct-injection internal combustion engine with following suction port is provided: suction port slopes inwardly promptly towards inclining towards each other, thereby along with suction port becomes near the firing chamber, the distance between two suction ports diminishes gradually.In the direct-injection internal combustion engine of constructing like this, two bursts of tumble flows from two suction ports merge together so that at the strong turbulent flow of formation on every side at spark plug when forming around the spark plug of the mixed gas with dense air fuel ratio, motor can come work with the lean mode with improved reliability thus.At publication number is also to propose in the Japanese patent application (JP-A-09-236043) of 09-236043, a kind of cylinder head with upright mouthful internal-combustion engine is provided, this upright mouthful camshaft axially on crooked so that guarantee the interval that is used for rocking arm between upright mouthful and the interior pivot.In interior establishing in the cylinder head of the motor of the rocking arm of pintle type and upright mouthful, the interval that can be used for forming upright mouthful is limited greatly.Even the other problem that also can make in this case, the deterioration of intake efficiency or cause owing to interval constraint minimizes.

[0003] simultaneously, be used for being known in the art in the technology of waving the revolution air-flow that the cylinder of motor produces such as tumble flows or eddy current.By the intensity that such motor produced have increase wave the revolution air-flow, can enlarge motor with the lean-burn zone of lean mode work and can improve output performance.In this, the mode of air inlet being introduced in the cylinder is to produce one of high-intensity key factor of waving the revolution air-flow.For this background, be to have proposed to be used for improving the technology of air inlet being introduced the mode of cylinder in the Japanese patent application (JP-A-07-279751) of 07-279751 and the Japanese utility model application (JP-U-59-135335) that publication number is 59-135335 at publication number.

[0004], need design to be convenient to realize to satisfy the intake port shape of the best of these needs or the suction port of layout in order in cylinder, to produce the high-intensity revolution air-flow that waves.Yet, when in the valve stroke of suction valve mainly is in, arriving in the high scope, typically strengthened and waved the revolution air-flow.Figure 39 A and Figure 39 B also schematically show the typical case with suction port 10X of firing chamber 54, suction valve 55 and outlet valve 56 (10Xa among Figure 39 A and 10Xb) and 10Y (10Ya among Figure 39 B and 10Yb).In Figure 39 A and Figure 39 B, when above cylinder head, observing, suction port 10X and 10Y are projected on the horizontal plane, and the intersection point of the inlet side opening surface of the streamline of each suction port and suction port is defined as starting point P1 on being projected in horizontal plane S the time, and the intersection point of the central shaft of the streamline of suction port and suction valve 55 is defined as terminal point P2 on being projected in horizontal plane S the time.Here, the central shaft of suction valve 55 is not meant the axle of the bar of suction valve, and is meant the axle at the center of the umbrella portion of passing suction valve.Equally in Figure 39 A and Figure 39 B, straight line L1 represent to comprise starting point P1 and with horizontal plane S on the upwardly extending straight line in side of axle quadrature of bent axle, and straight line L2 represent to comprise terminal point P2 and with horizontal plane S on the upwardly extending straight line in side of axle quadrature of bent axle.

[0005] in Figure 39 A, illustrate suction port 10X (10Xa and 10Xb), suction port 10X is shaped, thereby the straight line of connection source P1 and terminal point P2 is with to be projected in the streamline F (will abbreviate " the projection streamline of suction port " as) of the suction port on the horizontal plane S basic identical, and the distance two suction port 10Xa on the direction from starting point P1 to terminal point P2 and 10Xb increases gradually.In Figure 39 B, illustrate suction port 10Y (10Ya and 10Yb), suction port 10Y is shaped, thereby the projection streamline F of suction port is not positioned at the position than the center of the more close firing chamber 54 of straight line L1, that is, projection streamline F is not positioned on the inboard of straight line L1 (in other words, being positioned on the outside of straight line L1).Use the suction port 10X and the 10Y that are shaped like this, air inlet flows into the firing chamber 54 equably from the whole zone of the downstream side opening of suction port 10, therefore, when the valve stroke of suction valve be in little in scope in the time, advantageously strengthen and wave the revolution air-flow.

[0006] especially when the valve stroke of suction valve be in little in scope in the time because the main flow of air inlet does not have specific alignment features usually, promptly, main flow is not flowed on any specific direction, therefore, for example, the valve stem of suction valve becomes the major obstacle of inlet stream.Therefore, when valve stroke be in little in scope in the time, even exist in form in the firing chamber wave the revolution air-flow, also not always according to be enhanced desiredly.Therefore, reducing such as the effulent of HC and CO and alleviating the mixability of the required mixed gas of the deterioration of fuel economy, improve the required flame propagation feature of burning during in cold-starting or lean-burn work, and preventing remaining some improved space on the required velocity of combustion of detonation.Yet, also do not propose to be used to design the specific policy or the scheme of suction port, even so that valve stroke be in little in scope in, also can advantageously strengthen and wave the revolution air-flow.

Another problem that runs into when [0007] air inlet flows in the cylinder is that the bar of suction valve and therefore shunting have been disturbed in air inlet, can not form the inlet stream of expection thus in the firing chamber.In this, when suction valve was promoted greatly, a large amount of air inlets was introduced in the cylinder consumingly, therefore, even there is above problem, also relatively easily produced the high-intensity revolution air-flow that waves in cylinder.Yet, when suction valve is raised, be difficult to produce fully from the enough high-intensity revolution air-flow that waves of having of inlet stream.Therefore when the valve stroke of suction valve be in little in scope in the time, need to improve mode in the cylinder introduced in air inlet, so that generation has the enough high-intensity revolution air-flow that waves.

[0008] for aforesaid background, in the JP-A-07-279751 of as above checking, propose, the opening of suction port is displaced to the outside of firing chamber with suction valve, thereby forms the inlet stream that is directed in a large number to the middle part of firing chamber, and with the middle part of inlet stream suction to the firing chamber.Therefore, when the valve stroke of suction valve be in little in scope in the time, according to the technology of proposition in above checking open, can improve mode in the cylinder is introduced in air inlet.Yet, use this technology, air inlet is divided into the tributary by the bar of suction valve, has therefore still stayed the air inlet that does not flow to the middle part, firing chamber in a large number, and this makes to be difficult to provide to have the enough high-intensity revolution air-flow that waves.Equally, use the technology that is proposed, when air inlet valve position in in the high lift zone time, air inlet may be assembled ground too much around the middle part of firing chamber, and the air inlet in the inflow cylinder may be with too high speed bump cylinder wall, and this may cause the reduction of the intensity of waving the revolution air-flow that produces in cylinder.

Summary of the invention

[0009] considers the problems referred to above, produced the present invention.Therefore, the purpose of this invention is to provide a kind of internal-combustion engine, wherein, suction port is designed to: though when the valve stroke of suction valve be in little in scope in the time, also can strengthen in the firing chamber, produce wave the revolution air-flow, and wherein, from the valve stroke of suction valve be in little to scope in the time, can in an advantageous manner air inlet be introduced in the cylinder and wave the revolution air-flow so that in cylinder, produce.

[0010] according to a scheme of the present invention, a kind of internal-combustion engine is provided, this internal-combustion engine comprises the suction port that is connected with the firing chamber, and has a suction valve that umbrella portion and an end are connected to the bar in the umbrella portion, wherein, suction port has starting point and terminal point: when observing above the cylinder head that is formed with suction port, starting point is the subpoint of first intersection point on horizontal plane of the inlet side opening surface of the streamline of suction port and suction port; Terminal point is the subpoint of second intersection point on horizontal plane of the central shaft of the streamline of suction port and suction valve.In this internal-combustion engine, be projected in the center curvature of the streamline of the suction port on the horizontal plane towards the firing chamber, so that be positioned at position at least in part than the center of first straight line and the more close firing chamber of second straight line, first straight line comprise starting point and with horizontal plane on bent axle the axle quadrature direction on extend, second straight line comprise terminal point and with horizontal plane on bent axle the axle quadrature direction on extend.

[0011] though design during suction port the relation of the position between the Origin And Destination can change widely, suck that the design of suction port is depended in air inlet in the firing chamber and outside straight or inside mobile by suction port.In internal-combustion engine, flow into the air inlet in the firing chamber because the shape of bending is endowed the alignment features of enhancing, thereby air inlet may be flowed on specific direction more with the design of above-mentioned suction port.Therefore, though when the valve stroke of suction valve be in little in scope in the time, also can strengthen in the firing chamber, produce wave the revolution air-flow.

[0012] in aforesaid internal-combustion engine, starting point can be positioned at the position than the center of the more close firing chamber of second straight line.

[0013] shown in Figure 39 A, when suction port was designed to make that starting point and terminal point are placed as mentioned above, the air inlet of the suction port of flowing through was tended to outwards be guided by integral body in flowing into the firing chamber time usually.On the other hand, in the internal-combustion engine that has with the suction port of aforesaid mode bending, can be directed inboard when the main flow of the air inlet of control damper deflection etc. is in flowing into the firing chamber with the valve stem of the suction valve of flowing through.Thereby, prevented that the main flow of air inlet from disturbing valve stem.Therefore, though when the valve stroke of suction valve be in little in scope in the time, also can strengthen in the firing chamber, produce wave the revolution air-flow.

[0014] in aforesaid motor, starting point can be positioned on second straight line.

[0015] when suction port was designed to make that starting point and terminal point are located as mentioned above, the air inlet of the suction port of flowing through was tended to flow in the firing chamber as the crow flies usually.On the other hand, in the internal-combustion engine of suction port design, can guide the main flow of air inlet in aforesaid mode, therefore with aforesaid bending, even when the valve stroke of suction valve be in little in scope in the time, also can strengthen in the firing chamber, produce wave the revolution air-flow.

[0016] in aforesaid motor, starting point can not be positioned at the position than the center of the more close firing chamber of second straight line.

[0017] when suction port is designed to make that starting point and terminal point are located as mentioned above, the air inlet of the suction port of flowing through is tended to inwardly be guided by integral body when flowing into the firing chamber usually.In the internal-combustion engine of suction port design with aforesaid bending, can strengthen the alignment features (that is, air inlet more may inwardly be guided) of air inlet, therefore, even when the valve stroke of suction valve be in little in scope in the time, also can strengthen in the firing chamber, produce wave the revolution air-flow.

[0018] therefore, in aforesaid internal-combustion engine, even when the valve stroke of suction valve be in little in scope in the time, also can strengthen in the firing chamber, produce wave the revolution air-flow.

[0019] in a preferred embodiment of the invention, suction valve is specific suction valve, be offset at this specific suction valve king-rod, thereby two air inlets on the both sides on the plane of the central shaft that comprises bar become bigger by the inboard at the center that is positioned at more close firing chamber in the zone by the zone, and the central shaft of bar does not comprise the center of the bottom surface of umbrella portion.

[0020] in motor according to aforesaid preferred embodiment, when the valve stroke of suction valve be in little in scope in the time, more may prevent from soon to flow into the bar of the air inlet interference intake valve in the firing chamber, thereby formation is towards the inlet stream of the increasing amount at the middle part of firing chamber towards the middle part of firing chamber.Therefore, from the valve stroke of suction valve be in little to scope in the time, can in an advantageous manner air inlet be introduced in the cylinder and wave the revolution air-flow so that in cylinder, form.

[0021] aforesaid preferred embodiment is with the difference of the technology that proposes in JP-A-07-279751 that is as above verified and JP-U-59-135335: consider the present invention improve from the valve stroke of suction valve be in little to scope in the time purpose of the type of flow of the air inlet that begins and the height of the necessity that achieves the goal, bar is offset in aforesaid mode.In this, consider the easiness of intensity and processing, the bar of suction valve forms usually, make the central shaft of bar comprise the center of the bottom surface of umbrella portion, and bar extends on the direction vertical with the bottom surface.For example, change with the position one of the opening of suction port so that improving the situation of the type of flow of air inlet under the situation of non-migration bar compares with the position of suction valve, offset arm is favourable or preferred with regard to the variation degrees of freedom that increases.Still in this, in aforesaid motor, can advantageously improve the mode in the air inlet inflow cylinder.

[0022] although comprising the plane of the central shaft of bar needn't be defined in and can air inlet be divided into the inboard of bar and the single plane in the outside by the zone with respect to the firing chamber, this plane as be divided into inboard by the zone air inlet with respect to the firing chamber and the outside so that flow in the cylinder so that in cylinder, produce the main flow of the air inlet of waving the revolution air-flow and mainly be included in the inboard and determine by the plane in the zone.In this, in being formed with the motor of being convenient in cylinder, produce as the suction port that waves the tumble flows of turning round air-flow, if further make described plane and cylinder spool parallel of the central shaft that comprises bar, then the main flow of air inlet mainly is included in inboard by in the zone, therefore, more may prevent from soon to disturb bar towards the air inlet that the middle part of firing chamber flows in the cylinder with higher reliability.

The meaning of [0023] above statement " inboard become bigger by the zone " is, the situation of the suction valve commonly used that is provided with not according to the preferred embodiment skew with bar is therein compared, and inboardly becomes bigger by the zone.In this, the suction valve commonly used of bar non-migration is arranged in the motor that is formed with the suction port of being convenient in cylinder to produce tumble flows therein, suppose usually air inlet by the zone by and the parallel plane of the axle of cylinder be divided into substantially inboard by zone and the outside by regional.Accordingly, in a preferred embodiment, more specifically, the skew of the bar of specific suction valve, thus inboard becoming than other zone by the zone is that the outside is bigger by the zone.

[0024] bar of as above illustrated specific suction valve can the off-centring with respect to specific suction valve arrive upstream side on the flow direction of air inlet.

[0025] is offset the bar of specific suction valve so that improve the ad hoc approach that air inlet flows into the mode of cylinder as being used for, when on horizontal plane, observing, bar can be offset on the direction vertical with the flow direction of air inlet, and can on the flow direction of air inlet, further be displaced to the downstream side in the center with respect to specific suction valve, perhaps can on the flow direction of air inlet, further be displaced to upstream side in the center with respect to specific suction valve.That is, the bar of specific suction valve can depart from central shaft and the plane parallel with inlet stream that comprises cylinder.If the bar of specific suction valve center with respect to specific suction valve on the flow direction of air inlet further is displaced to the downstream side, then inlet stream may not be formed on smoothly specific suction valve umbrella portion directly over and the downstream.Therefore, preferably bar is offset in aforesaid mode, and promptly the off-centring with respect to particular valve arrives upstream side on the flow direction of air inlet.

[0026] specific suction valve can form, make specific suction valve umbrella portion with the inboard by the corresponding part in zone have than umbrella portion with the outside by the littler volume of regional corresponding part.

[0027] in aforesaid motor, can make that the inboard of air inlet of position at the center that is positioned at more close firing chamber is bigger by the zone than the outside by the zone, therefore, when the valve stroke of suction valve be in little in scope in the time, can make the inlet stream of increasing amount to the middle part of firing chamber.Therefore, from the valve stroke of suction valve be in little to scope in the time, can in an advantageous manner air inlet be introduced in the cylinder and wave the revolution air-flow so that in cylinder, produce.Equally, even in the degrees of offset of bar, promptly the side-play amount of bar is reduced to than under the littler situation of the side-play amount of the bar of the suction valve that does not make the bigger and offset arm of inboard volume by the zone, and equal effect also can be provided, the intensity that therefore, can advantageously keep suction valve.

[0028] preferably, the umbrella portion of specific suction valve forms so that do not stop inlet stream on the whole periphery of this suction valve smoothly.In order to form the umbrella portion of specific suction valve smoothly, at least a portion of the umbrella portion of specific suction valve can form with arc on cross section.In this, the umbrella portion of specific suction valve can all form with arc on cross section by regional corresponding part by regional corresponding part and with the outside with the inboard, and can so that with the radius of curvature of inboard by regional corresponding part than littler by the radius of curvature of regional corresponding part with the outside so as can easily to make as mentioned above and the inboard littler by the volume ratio and the outside of regional corresponding part by the volume of regional corresponding part.

[0029] specific suction valve may further include anti-rotation device, and anti-rotation device prevents that specific suction valve from rotating around the central shaft of the bar of described specific suction valve.

[0030] when specific suction valve rotated around bar, suction port may fully not closed.This problem can be eliminated by the specific suction valve with above-mentioned anti-rotation device is provided.

[0031] in aforesaid motor, from the valve stroke of suction valve be in little to scope in the time, can in an advantageous manner air inlet be introduced in the cylinder and wave the revolution air-flow so that in cylinder, produce.

[0032] in another preferred embodiment of the present invention, suction valve is specific suction valve, in this specific suction valve, when air inlet valve position during in closed condition, bar tilts, thereby with the direction of the substantially parallel axes of bent axle on, the far-end of bar be positioned at than the more close central shaft that comprises cylinder in the center of the bottom surface of umbrella portion and with the position of the basic plane orthogonal of axle of bent axle.

[0033] in the motor that the bar of specific suction valve tilts in aforesaid mode, the inlet stream of increase is attracted to the middle part of firing chamber, so that can increase or strengthen the main flow that flows into the air inlet in the cylinder towards the middle part of firing chamber.Therefore, according to preferred embodiment, even when the valve stroke of suction valve be in little in scope in the time, also can strengthen the intensity of waving the revolution air-flow that in cylinder, produces, and from the valve stroke of suction valve be in little to scope in the time, air inlet can be introduced in an advantageous manner in the cylinder so that in cylinder, produce the described revolution air-flow that waves.

[0034] in above-mentioned motor, the bar of specific suction valve tilts, and the umbrella portion of suction valve also tilts, and being dispersed thereby specifically guide around the firing chamber along the air inlet that the part at the center of the more close firing chamber of ratio bar of the umbrella portion of specific suction valve flows.Usually, along with the lift of suction valve becomes higher, the main flow of air inlet more may concentrate on the firing chamber the middle part around, this has caused flowing to the increase of flow velocity of air inlet at the middle part of firing chamber.On the other hand, in motor according to aforesaid preferred embodiment, flow into air inlet in the cylinder when advantageously having prevented in the lift of suction valve is in high scope with too high speed bump cylinder wall, and the intensity of waving the revolution air-flow that produces can not reduce or unlikely reduce in cylinder.In the above description of preferred embodiment, as example, phrase " specific air inlet valve position is under the closed condition " is used for specific suction valve is defined as the specific suction valve of under certain state (that is closed condition).Identical phrase will be used for the description of the following example.

[0035] when specific air inlet valve position during in closed condition, the bar of specific suction valve can tilt, thereby on the flow direction of air inlet, the far-end of bar is positioned at the position than the more close relief opening in described center.

[0036] utilizes above the layout, can further disperse towards the lower dead center of cylinder along the air inlet that umbrella portion flows in the cylinder.Therefore, prevented that advantageously the air inlet in the inflow cylinder from clashing into cylinder wall with too high flow velocity, this intensity of waving the revolution air-flow that can cause producing in cylinder reduces.In addition, in aforesaid motor, the main flow that can prevent air inlet concentrate on too much the firing chamber the middle part around, and the bar that depends on specific suction valve has further improved the intensity of waving the revolution air-flow in the degree that the flow direction of air inlet tilts.

[0037] like this, in aforesaid motor, from the valve stroke of suction valve be in little to scope in the time begin, can in an advantageous manner air inlet be introduced in the cylinder and wave the revolution air-flow so that in cylinder, produce, and prevent air inlet simultaneously with too high speed bump cylinder wall, this intensity of waving the revolution air-flow that can cause producing in cylinder reduces.

Description of drawings

[0038] in conjunction with the accompanying drawings, by reading the following detailed description of the preferred embodiments of the present invention, feature of the present invention, advantage and technology and industrial significance will be understood better, wherein:

Fig. 1 is the figure that schematically shows with the suction port 10A of the major component of internal-combustion engine 50A;

Fig. 2 is the schematic representation of the suction port 10A of three-dimensional representation;

Fig. 3 is the figure that schematically shows the suction port 10A when observing on suction port 10A projection horizontal plane thereon;

Fig. 4 is the plotted curve that shows for valve stroke and the relation between the upset intensity of suction port 10A and suction port 10X commonly used;

Fig. 5 is the figure that schematically shows the suction port 10B when observing on suction port 10B projection horizontal plane thereon;

Fig. 6 is the figure that schematically shows the suction port 10C when observing on suction port 10C projection horizontal plane thereon;

Fig. 7 is the figure that schematically shows the major component of the internal-combustion engine 100A related with cylinder when observing on vertical cross section;

Fig. 8 is the figure that schematically shows the described major component of the internal-combustion engine 100A when observing on the major component projection horizontal plane thereon of the internal-combustion engine 100A related with cylinder;

Fig. 9 is the figure that schematically shows along the suction valve 155A in the cross section of line A-A intercepting shown in Figure 8;

Figure 10 is the plotted curve that shows the relation between upset intensity and the valve stroke;

Figure 11 is the plotted curve of relation that shows between the flow of side-play amount L, upset intensity, valve intensity and air;

Figure 12 be schematically show when with the vertical direction in the bottom surface of the ub of umbrella portion of suction valve 155Ab on the figure that is arranged in the suction valve 155Ab on the direction identical when observing with the direction of Fig. 8;

Figure 13 and Fig. 8 similarly scheme, and it illustrates the major component of motor 100A, and wherein side-play amount L is set to greater than D/4;

Figure 14 is the plotted curve that schematically shows in the firing chamber distribution of the flow velocity that 154 middle part measures;

Figure 15 shows for bar stm being displaced to the situation of upstream side flowing on the F of air inlet and bar stm being displaced to the side-play amount L of situation in downstream side and the plotted curve of the relation between the upset intensity;

Figure 16 is for to schematically show the figure of suction valve 155Bb with the similar mode of the mode of Figure 12;

Figure 17 is the plotted curve that schematically shows in the firing chamber distribution of the flow velocity that 154 middle part measures;

Figure 18 A, Figure 18 B and Figure 18 C show the fuel consumption feature of internal-combustion engine 100B when lean-burn is worked and the figure of the output performance when high capacity is worked;

Figure 19 be schematically show with the similar cross section of cross section, A-A shown in Figure 8 in the figure of suction valve 155C;

Figure 20 is for to schematically show the figure of suction valve 155C with the similar mode of the mode of Figure 12;

Figure 21 is the plotted curve that schematically shows in the firing chamber distribution of the flow velocity that 154 middle part measures;

Figure 22 is the figure that schematically shows the described major component of the internal-combustion engine 100D when observing on the major component projection horizontal plane thereon of the internal-combustion engine 100D related with cylinder;

Figure 23 is the figure that schematically shows the described major component of the internal-combustion engine 100E when observing on the major component projection horizontal plane thereon of the internal-combustion engine 100E related with cylinder;

Figure 24 is the plotted curve that shows the relation between upset intensity and the valve stroke;

Figure 25 is the figure that schematically shows the major component of the internal-combustion engine 200A related with cylinder when observing in vertical cross section;

Figure 26 is the figure that schematically shows the described major component of the internal-combustion engine 200A when observing on the major component projection horizontal plane thereon of the internal-combustion engine 200A related with cylinder;

Figure 27 is the figure that schematically shows along the suction valve 255A in the cross section of as shown in Figure 26 line B-B intercepting;

Figure 28 A and Figure 28 B are the figure that schematically shows the flow pattern that flows into the air inlet in the cylinder;

Figure 29 is the plotted curve that shows the relation between upset intensity and the valve stroke;

Figure 30 A and Figure 30 B are the figure that schematically shows the flow pattern that flows into the air inlet in the cylinder;

Figure 31 A and Figure 31 B are the plotted curve that schematically shows in the firing chamber distribution of the flow velocity that 254 middle part measures;

Figure 32 for with the similar mode of the mode of Figure 26 schematically show when with the major component projection horizontal plane thereon of the related internal-combustion engine 200B of cylinder on the figure of described major component of internal-combustion engine 200B during observation;

Figure 33 is for schematically showing the figure that is arranged in the suction valve 255Bb on the direction identical with the direction of Figure 32 separately;

Figure 34 A and Figure 34 B are the plotted curve that schematically shows in the firing chamber distribution of the flow velocity that 254 middle part measures;

Figure 35 A, Figure 35 B and Figure 35 C show the fuel consumption feature of internal-combustion engine 200B when lean-burn is worked and the figure of the output performance when high capacity is worked;

Figure 36 is the figure that schematically shows the described major component of the internal-combustion engine 200C when observing on the major component projection horizontal plane thereon of the internal-combustion engine 200C related with cylinder;

Figure 37 is the figure that schematically shows the described major component of the internal-combustion engine 200D when observing on the major component projection horizontal plane thereon of the internal-combustion engine 200D related with cylinder;

Figure 38 is the plotted curve that shows the relation between upset intensity and the valve stroke; And

Figure 39 A and Figure 39 B schematically show with the suction port 10X commonly used of firing chamber 54, suction valve 55 and outlet valve 56 and the figure of 10Y.

Embodiment

[0039] in following description and accompanying drawing, will the present invention be described in more detail in conjunction with one exemplary embodiment.

[0040] at first, the first embodiment of the present invention will be described.Fig. 1 schematically shows the suction port 10A (representing suction port 10Aa and suction port 10Ab) according to the suction port design of the internal-combustion engine of the first embodiment of the present invention of having with the major component of internal-combustion engine 50A.Motor 50A is the direct fuel jet type gasoline engine that injects fuel directly in the cylinder.It should be understood, however, that the present invention is not limited to be applied to such motor, but can be applied to the motor of other type except that direct fuel jet type gasoline engine.Though motor 50A is the in-line four cylinder engine with layout four cylinders point-blank, cylinder arrangement and cylinder number are not limited to cylinder arrangement and the cylinder number of motor 50A, but can suitably select.Though illustrate the major component of motor 50A in the present embodiment, more specifically, as the major component of the cylinder 51a of typical cylinder, remaining cylinder is constructed in a similar manner.

[0041] motor 50A comprises cylinder block 51, cylinder head 52A, piston 53 and other parts.Cylinder 51a with general cylindrical is formed in the cylinder block 51.Piston 53 is contained among the cylinder 51a.Be used for guiding the cavity 53a of tumble flows T to be formed on the end face of piston 53.Cylinder head 52A be fixed to cylinder block 51 above.Firing chamber 54 forms the space that is centered on by cylinder block 51, cylinder head 52A and piston 53.Cylinder head 52A is formed with suction port 10A (10Aa and 10Aa) and relief opening 20 (20a and 20b): air inlet is drawn onto firing chamber 54 by suction port 10A; Combustion gas are discharged from firing chamber 54 by relief opening 20.Equally, the suction valve 55 and being used to that is used for opening and closing the runner of each the suction port 10A outlet valve 56 that opens and closes the runner of each relief opening 20 is installed in cylinder head 52A.In addition, for example, spark plug and Fuelinjection nozzle (not shown) are installed among the cylinder head 52A.

[0042] air inlet flows in the firing chamber 54 by suction port 10A after by the deflection of control damper (not shown), so that produce high-intensity tumble flows T in firing chamber 54.Though the inlet side opening of suction port 10A is formed in the side of cylinder head 52A in the present embodiment, suction port 10A can be formed in cylinder head 52A top upright mouthful for the inlet side opening.Equally, the revolution air-flow that waves that produces in firing chamber 54 is not limited to tumble flows T, but can for, for example in the reverse tumble flows of going in ring in the opposite direction with the side of as shown in Figure 1 tumble flows T, or as the inclination flip stream of the combination of tumble flows T and eddy current.

[0043] Fig. 2 has shown the schematic representation of suction port 10A for three-dimensional map.The Vertical direction indication as shown in Figure 2 and the parallel direction of direction of cylinder 51a extension, and the direction of the direction quadrature that substantially horizontal indication and cylinder 51a extend.As shown in Figure 2, when observing above cylinder head 52A, suction port 10A (10Aa, 10Ab) is projected on the horizontal plane S.With bent axle the axle quadrature vertical surface G horizontal plane S is divided into the inboard and the outside.In Fig. 2, illustrate vertical surface G1 that comprises starting point P1 and the vertical surface G2 that comprises terminal point P2 respectively.In this, starting point P1 is the intersection point that is projected in the inlet side opening surface of the streamline of the suction port 10A on the horizontal plane S and suction port 10A, and terminal point P2 is the intersection point that is projected in the central shaft of the streamline of the suction port 10A on the horizontal plane S and suction valve 55.In this embodiment, the central shaft of suction valve 55 is included among the vertical surface G2.Recognize that from Fig. 2 starting point P1 is positioned on the inboard of vertical surface G2.Recognize that also the projection streamline F of suction port 10A is crooked in the vertical surface G1, the projection streamline F of suction port 10A is the streamline that is projected on the horizontal plane S.Horizontal plane S and vertical surface G1 intersect forming straight line L1 (referring to Fig. 3), and horizontal plane S intersects with formation straight line L2 (referring to Fig. 3) with vertical surface G2.In other words, starting point P1 is positioned at the position than the center of the more close firing chamber of straight line L2, straight line L2 comprise terminal point P2 and with horizontal plane on bent axle the axle quadrature direction on extend, and the streamline of the suction port in the time of on being projected in horizontal plane is bent into the center than the more close firing chamber of straight line L1, straight line L1 comprise starting point P1 and with horizontal plane on bent axle the axle quadrature direction on extend.

Suction port 10A when [0044] Fig. 3 schematically shows on being projected in horizontal plane (10Aa, 10Ab).In Fig. 3, illustrate firing chamber 54 and suction valve 55 and outlet valve 56 with suction port 10A.As shown in Figure 3, starting point P1 is positioned on the inboard of straight line L2.The projection streamline F of suction port 10A is crooked in the straight line L1.Use this layout, mainly in the front half part of curved section, be directed, so that between the inwall of the valve stem of suction valve 55 and suction port 10A, be introduced into the firing chamber 54 by the main flow of the air inlet of control damper deflection.That is, even the position of starting point P1 and terminal point P2 has relation as shown in Figure 3, the suction port 10A with suction port design of such bending also can guide main flow in aforesaid mode.Curved section can be designed, more specifically, position, length and the tortuosity of determining curved section such as the specification at the angle of inclination of suction port 10A can be depended on.

[0045] Fig. 4 shows for having according to the suction port 10A of the suction port of present embodiment design and the valve stroke and the relation of overturning between the intensity of the suction port 10X commonly used of example as a comparison.Suction port 10X is designed to shown in Figure 39 A.In the present embodiment, the main flow of air inlet concentrates on the inboard of suction port 10A, with convenient valve stroke be in little in scope in the time form the stream of the umbrella be suitable for suction valve 55, and air inlet is introduced in the firing chamber 54 the most smoothly.As a result, 10X compares with suction port, especially valve stroke little in scope in can strengthen upset intensity.Recognize from the above description, though suction port 10A provide valve stroke when suction valve 55 be in little in scope in the time, also can strengthen the suction port design of the motor that waves the revolution air-flow that in the firing chamber, produces.

[0046] next, the suction port 10B that description is had suction port design according to a second embodiment of the present invention.Suction port 10B is with the difference that has according to the suction port 10A of first embodiment's suction port design: starting point P1 is positioned as and is included on the straight line L3, straight line L3 comprise terminal point P2 and with horizontal plane S on the direction of axle quadrature of bent axle on extend, and the projection streamline F that is projected in the suction port 10B on the horizontal plane S is crooked in the straight line L3.Suction port 10B when Fig. 5 schematically shows on being projected in horizontal plane (10Ba, 10Bb).Fig. 5 also shows with the firing chamber 54 of suction port 10B and suction valve 55 and outlet valve 56.Recognize that from Fig. 5 starting point P1 is arranged on the straight line L3 of suction port 10B, and the projection streamline F of suction port 10B is crooked in the straight line L3.

[0047] utilize above the layout, the main flow of air inlet mainly was directed before by curved section so that be introduced into the firing chamber 54 between the inwall of the valve stem of suction valve 55 and suction port 10B.That is, even the position of starting point P1 and terminal point P2 has relation as shown in Figure 5, the suction port 10B with suction port design of such bending also can guide main flow in aforesaid mode.Recognize from the above description, though suction port 10B provide valve stroke when suction valve 55 be in little in scope in the time, also can strengthen the suction port design of the motor that waves the revolution air-flow that in the firing chamber, produces.

[0048] next, the suction port 10C that description is had the suction port design of a third embodiment in accordance with the invention.Suction port 10C is with the difference that has according to the suction port 10A of first embodiment's suction port design: starting point P1 is not positioned on the inboard of straight line L2 (promptly, be positioned on the outside), and projection streamline F bending in the straight line L2 of suction port 10C when being projected in horizontal plane S and going up.Suction port 10C when Fig. 6 schematically shows on being projected in horizontal plane (10Ca, 10Cb).Fig. 6 also shows with the firing chamber 54 of suction port 10C and suction valve 55 and outlet valve 56.Recognize that from Fig. 6 starting point P1 is positioned on the outside of straight line L2, and the projection streamline F of suction port 10C is crooked in the straight line L2.

[0049] utilize above the layout, the main flow of air inlet mainly was directed before by curved section so that be introduced into the firing chamber 54 between the inwall of the valve stem of suction valve 55 and suction port 10C.That is, even the position of starting point P1 and terminal point P2 has relation as shown in Figure 6, the suction port 10C with suction port design of such bending also can guide main flow in aforesaid mode.When starting point P1 is positioned on the outside of straight line L2, can form suction port so that the essentially identical projection streamline of the straight line F with connection source P1 and terminal point P2 to be provided, so that air inlet inwardly is directed as a whole and therefore be introduced in the firing chamber 54.Yet, have the alignment features that can strengthen main flow according to the suction port 10C of the suction port of present embodiment design.Under starting point P1 was positioned at relatively situation near the position of straight line L2, for example, it is especially effective that the curve form of suction port 10C becomes.Recognize from the above description, though suction port 10C provide valve stroke when suction valve 55 be in little in scope in the time, also can strengthen the suction port design of the motor that waves the revolution air-flow that in the firing chamber, produces.

[0050] illustrated embodiment is the preferred embodiments of the present invention.Yet, it will be appreciated that the present invention is not limited to these embodiments, but the additional embodiments that can under the situation that does not deviate from principle of the present invention, utilize various improvement to be embodied as.For example, though suction port 10A, 10B and 10C are suction port independently in illustrated embodiment, but suction port is not limited to this type, but can reconnect (Siamese) mouth for gas-entered passageway is divided into two of two branched bottoms in the downstream side, two branched bottoms can be combined into single passage at upstream side.

[0051] next, the fourth embodiment of the present invention will be described.

[0052] Fig. 7 schematically shows the major component of the internal-combustion engine 100A of a fourth embodiment in accordance with the invention.More specifically, Fig. 7 shows the cylinder of the internal-combustion engine 100A when in vertical cross-sectional view.Motor 100A is direct fuel jet type petrol engine, and uses each cylinder to be provided with two suction valve structures of two suction valves.Yet, it will be appreciated that motor 100A is not limited to any specific type that can implement the present invention effectively and be provided with.For example, motor can be so-called lean-combustion engine, or for example has the motor of three suction valve structures as described later.Motor 100A can also have suitable cylinder number and suitable cylinder arrangement.

[0053] internal-combustion engine 100A has cylinder block 151, cylinder head 152, piston 153 and other parts.Cylinder 151a with general cylindrical is formed in the cylinder block 151, and piston 153 is contained among the cylinder 151a.Cylinder head 152 is fixed on the cylinder block 151.Firing chamber 154 forms the space that is centered on by cylinder block 151, cylinder head 152 and piston 153.Cylinder head 152 is formed with suction port 110Aa and 110Ab (will simply and usually be called " suction port 110A ", the mode of this name is applied to other parts) and relief opening 120 (120a and 120b): air inlet is introduced into (or introducing in the cylinder) in the firing chamber 154 by suction port 110Aa and 110Ab, and combustion gas are discharged from firing chamber 154 by relief opening 120.In addition, be used for opening and closing the outlet valve 156 that the suction valve 155A of each suction port 110A and being used to opens and closes each relief opening 120 and be installed in cylinder head 152 respectively.Motor 100A is provided with the anti-rotation device (not shown).The upwardly extending slot in side that anti-rotation device can for example extend by the bar stm that is formed on suction valve 155A in bar stm, and the bar holding part that engages with slot for cylinder head 152 settings realizes.In this embodiment, suction valve 155A (155Aa, 155Ab) is considered to specific suction valve.

[0054] spark plug 157 is installed in the cylinder head 152 so that its electrode stretches into the firing chamber 154 from the top.The Fuelinjection nozzle (not shown) is installed in the cylinder head 152 so that its spray-hole stretches among the suction port 110A.Fuelinjection nozzle is suitable for injecting fuel directly on intake stroke among the cylinder 151a.Fuelinjection nozzle is not limited to this type or position, but can be installed in the cylinder head 152 than the position of the more close cylinder block 151 of suction port 110A, or be installed in the position of 154 tops, firing chamber in the cylinder head 152 so that its spray-hole stretches in the firing chamber 154.Air inlet from suction port 110A inflow cylinder 151a produces in cylinder waves the revolution air-flow.In this embodiment, particularly, waving the revolution air-flow is the form of tumble flows T as shown in Figure 7.Be used for guiding the cavity of tumble flows T can be formed on the end face of piston 153.

[0055] Fig. 8 schematically shows the described major component of the internal-combustion engine 100A when observing on the major component projection horizontal plane thereon of the internal-combustion engine 100A related with cylinder.Fig. 9 schematically shows along the suction valve 155A (155Aa, 155Ab) in the cross section of the intercepting of the line A-A among Fig. 8.As shown in Figure 8, suction port 110A is long when extension is observed on horizontal plane with box lunch, makes the middle part of inlet stream to firing chamber 154.Utilize this layout, air inlet is formed on the main flow that produces the air inlet of tumble flows T in the cylinder simultaneously by the middle part that suction port 110A flows to firing chamber 154.Like this, as shown in Figure 8, air inlet flow to F and an axle L4 basic quadrature, the substantially parallel axes of axle L4 and bent axle.In this, the main flow that flows to F indication air inlet of air inlet flows so that produce the direction of tumble flows T in cylinder, and can depend on shape or the design of suction port 110A, is represented by the bearing of trend of the part of the placement bar stm of suction port 110A.

[0056] as Fig. 8 and shown in Figure 9, bar stm skew, thus the central shaft C1 of bar stm does not comprise the P2 of bottom center of the ub of umbrella portion of suction valve 155A.In the present embodiment, as shown in Figure 8, when observing on horizontal plane, in other words bar stm, is offset on the direction substantially parallel with axle L4 being offset with flowing on the vertical substantially direction of F of air inlet.Here, the planar S 1 of the central shaft C1 of the involved bar stm of air inlet runner of the suction port 110A of air inlet process is divided into two zones, that is, regional otr is passed through in the inboard regional inr of passing through and the outside.As shown in Figure 8, bar stm skew, thus the inboard of position that is positioned at the center of more close firing chamber 154 becomes bigger by regional inr than the situation of bar non-migration, more specifically, thereby inboardly becomes bigger by regional otr than the outside by regional inr.Therefore, as shown in Figure 8, more may prevent the caused air inlet interference bar stm that flows to the middle part of firing chamber 154.Therefore, when the valve stroke of suction valve be in little in scope in the time, more may form the inlet stream at the middle part that is drawn towards firing chamber 154.

[0057] in Fig. 8, suppose that further planar S 1 is the plane substantially parallel with the central shaft C3 of cylinder, and therefore, S1 is represented by straight line at Fig. 8 midplane.The cross section that is arranged in the position intercepting suction port 110A among the suction port 110A as the bar stm in can being contained in the rod guide plate (not shown) (is presented at the suitable cross section of shape of the suction port 110A of certain position on the bearing of trend of suction port 110A, for example, the cross section vertical with suction port 110A or with air inlet flow to the vertical cross section of F) time, the cross section of suction port 110A is divided into two-part by planar S 1, and these two-part correspond respectively to inboard by regional inr and the outside part by regional otr.

[0058] in this, preferably big by the corresponding part of regional otr by the corresponding part ratio of regional inr in all cross sections of suction port 110A with the outside with the inboard, but this is always not real, but depend on the design of suction port 110A.As mentioned above, the inboard air inlet that intercepts for the position that is arranged at bar stm among the suction port 110A by regional otr by the regional inr and the outside is passed through regional.Therefore, inboardly be not included in the air inlet position that bar stm is not arranged in suction port 110A cut apart by planar S 1 by the zone by regional otr by regional inr and the outside.

[0059] Figure 10 shows the relation between upset intensity and the valve stroke.Upset intensity is represented by the revolution of upset.Figure 10 shows the comparative result of the upset intensity between motor 100A and the internal-combustion engine 100X, and wherein internal-combustion engine 100X has the suction valve of bar stm non-migration, replaces suction valve 155A.The suction valve that has except that motor 100X is different from the suction valve of motor 100A, and motor 100X and motor 100A are basic identical.Recognize that from Figure 10 100X compares with motor, from the valve stroke of suction valve be in little to scope in the time, the upset intensity in motor 100A is enhanced.

[0060] next, the side-play amount L of bar stm will be described in detail.Figure 11 show side-play amount L, the upset intensity, valve intensity and air flow between relation.Figure 12 schematically shows when suction valve 115Ab is arranged on the direction identical with the direction of Fig. 8, is arranged in suction valve 155Ab on the right-hand side among Fig. 8 when observing on the direction vertical with the bottom surface of the ub of umbrella portion.As shown in figure 12, the side-play amount L of the distance of the some P5 of the intersection point of the central shaft C1 of the bottom surface of the ub of umbrella portion and bar stm (more specifically, as) of having set indication from center P2 to bar stm.In Figure 12, D represents the valve external diameter, i.e. the external diameter of the ub of umbrella portion of suction valve 155Ab.Equally, related with side-play amount L arrow " just " indication with the direction that flows to the basic quadrature of F of air inlet on away from the direction of the central shaft C3 displacement rod stm of cylinder.

[0061] as shown in figure 11, when side-play amount L was in 0 (zero) arrives the scope of D/12, upset intensity increased and increases along with side-play amount L.Even side-play amount L further is increased to greater than D/12, upset intensity also increases along with side-play amount L and increases with speed slowly.Therefore, if side-play amount L as in the indicated scope time, can improve upset intensity by following representation (1).

0<L ...(1)

[0062] on the other hand, if side-play amount L further is increased to about D/4, then the valve intensity of suction valve 155A begins to reduce greatly.If side-play amount L further is increased to greater than D/4, then valve intensity reduces greatly, and the flow of air begins to reduce greatly.The reduction of the flow of air is considered to cause by reducing by the extreme of the outside by the air inflow of regional otr.Therefore, side-play amount L is preferred in as the permissible range indicated by following representation (2).

0<L≤D/4 ...(2)

[0063] as shown in figure 11 and since when side-play amount L 0 in the scope of D/12 the time, during upset intensity is increasing greatly, so further preferably side-play amount L is in as by in the indicated recommended range of following representation (3).

D/12≤L≤D/4 ...(3)

[0064] Figure 14 schematically shows in the firing chamber distribution of the flow velocity of the air that 154 middle part measures.Figure 14 shows the comparative result about the flow velocity between motor 100A and the motor 100X.When side-play amount L was in as the scope indicated by following representation (4), the flow velocity that obtains in motor 100A was greater than the flow velocity that obtains in motor 100X, still less than predetermined value.

0<L<D/12 ...(4)

[0065] on the other hand, if side-play amount L as by above representation (3) in the indicated recommended range, then flow velocity becomes and is equal to or greater than predetermined value.Recognize that from this result further preferably side-play amount L is in as by in the indicated recommended range of representation (3).As by above representation (3) or (4) even indicated scope is considered to also can provide rational effect when the change in location of the bar stm when flowing to of air inlet observed on the F time.In Figure 12, zone AR1 represent with as corresponding and be considered to provide the zone of rational effect by the indicated scope of representation (4), and regional AR2 represent with as corresponding and be considered to provide the zone of rational effect by the indicated scope of representation (3).In the motor 100A of structure as mentioned above, from the valve stroke of suction valve be in little to scope in the time, can in an advantageous manner air inlet be introduced in the cylinder so that in cylinder, produce tumble flows T.

[0066] next, the fifth embodiment of the present invention will be described.Except that the suction valve 155B (it represents suction valve 155Ba and 155Bb) of motor 100B has replaced the suction valve 155A of motor 100A, basic identical according to the 5th embodiment's internal-combustion engine 100B and the 4th embodiment's motor 100A.The difference of suction valve 155B and suction valve 155A is: when when flowing to of air inlet observed on the F, the bar stm of suction valve 155B further is displaced to the upstream side of center P 2.In this embodiment, suction valve 155B is considered to specific suction valve.

[0067] Figure 15 shows for bar stm at flowing to of air inlet is displaced to upstream side on the F situation and bar stm in the side-play amount L of the situation that is displaced to the downstream side on the identical direction and the relation between the upset intensity.Similar with Figure 12, Figure 16 schematically show with Fig. 8 in be arranged in suction valve 155Ab on the right-hand side and be arranged in suction valve 155Bb on the right-hand side similarly.As shown in figure 16, set the established angle θ of the acute angle that expression forms by straight line L6 and straight line L7: the flowing to the basic quadrature of F and comprise center P 2 of straight line L6 and air inlet, straight line L7 comprises center P 2 and is positioned at some P5 on the central shaft C1 of bar stm.The arrow " just " related indication with the established angle θ among Figure 16 as shown in figure 16, when bar stm when flowing to of air inlet is displaced to upstream side on the F, suppose established angle θ on the occasion of.In Figure 16, side-play amount L sets in the mode identical with mode among Figure 12.

[0068] as above about as described in the 4th embodiment, side-play amount L as be preferred by above representation (3) in the indicated recommended range.If established angle θ further is set to greater than about 70 degree or less than about-70 degree, then bar stm will be comprised in the regional AR1.Therefore, established angle θ is preferred in as the permissible range indicated by following representation (5).

-70°≤θ≤70° ...(5)

Yet, with what notice be, if bar stm is positioned at regional AR1, improved upset intensity more or less, and therefore, if established angle θ is equal to or greater than-90 ° and be equal to or less than 90 °, then can provide rational effect.

[0069] as shown in figure 16, if bar stm is displaced to upstream side, and established angle θ is set at 90 °, and then along with side-play amount L increases, upset intensity increases with low speed, increases greatly then.If bar stm is displaced to the downstream side, and established angle θ is set at-90 °, then along with side-play amount L increases, upset intensity reduces with low speed, reduces greatly then.This may be because when bar stm is displaced to the downstream side, is difficult to be formed into smoothly the inlet stream in downstream side directly over the ub of umbrella portion.Therefore, further preferably established angle θ is in as by in the indicated recommended range of following representation (6).

0°≤θ≤70° ...(6)

[0070] if side-play amount L greater than D/4, even then under established angle θ is set to situation in above-mentioned scope, valve intensity also reduces as shown in figure 15.Therefore, under the situation of determining established angle θ, preferably bar stm is formed and makes side-play amount L and established angle θ respectively in the scope of representation (3) and representation (6).In Figure 16, regional AR3 represent with side-play amount L be set to as by representation (3) the corresponding zone of situation in the indicated scope, and established angle θ is set in as the scope indicated by representation (6).Therefore, in the present embodiment, as shown in figure 16, thereby bar stm skew is comprised in the regional AR3.

[0071] Figure 17 schematically shows in the firing chamber distribution of the flow velocity of the air that 154 middle part measures.Figure 17 shows the comparative result about the flow velocity between motor 100B and the motor 100X.When the bar stm of suction valve 155B was positioned at regional AR3, motor 100B provided the flow velocity bigger than predetermined value beta.Predetermined value beta is greater than above mentioned predetermined value.Next, motor 100B provides such as the last high flow velocity of flow velocity at the motor 100A described in the fourth embodiment of the present invention.

[0072] Figure 18 A, Figure 18 B and Figure 18 C show fuel consumption feature and the output performance when high capacity work of motor 100B when lean-burn is worked.By the specific fuel consumption of motor 100B and the relation between the air fuel ratio, in Figure 18 A, specifically shown the fuel consumption feature when lean-burn is worked, and, in Figure 18 B, specifically shown the output performance when high capacity is worked by the Engine torque of motor 100B and the relation between the engine speed.In Figure 18 B, output performance is indicated by fully loaded performance.Figure 18 A and Figure 18 B show the comparative result between motor 100X and the motor 100B.Figure 18 C has shown fuel consumption reduced rate and the output performance raising rate that expectation obtains when side-play amount L is in the scope of representation (2) and representation (3) quantitatively, and has shown expectation obtains when established angle θ is in the scope of representation (5) and representation (6) fuel consumption reduced rate and output performance raising rate.

[0073] when the suitable degree of bar stm skew, from the valve stroke of suction valve be in little to scope in the time, can in cylinder, form high-intensity tumble flows T and can produce strong turbulent flow.Therefore, improved combustion characteristic when lean-burn is worked, this has caused the reduction of specific fuel consumption, and has improved output performance when high capacity is worked.Shown in Figure 18 A, 100X compares with motor, reduced specific fuel consumption in motor 100B, and has enlarged the lean-burn zone that motor can rare air fuel ratio work.Equally, shown in Figure 18 B, 100X compares with motor, in motor 100B, is enhanced at the gamut intrinsic motivation moment of torsion of engine speed.To recognize from Figure 18 B that along with engine speed reduces, the raising degree of Engine torque increases, and along with engine speed reduces, the more remarkable effect of bringing by offset arm stm.

[0074] if side-play amount L is set in the scope of representation (2) and representation (3), then expectation obtains quantitative fuel consumption reduced rate and the output performance raising rate that shows in Figure 18 C.If established angle θ is set in the scope of representation (5) and representation (6), then expectation obtains the fuel consumption reduced rate and the output performance raising rate of quantitative indication in Figure 18 C.In the motor 100B of structure as mentioned above, from the valve stroke of suction valve be in little to scope in the time, air inlet can be introduced in an advantageous manner in the cylinder so that in cylinder, produce tumble flows T.

[0075] next, the sixth embodiment of the present invention will be described.Except the suction valve 155C (representing suction valve 155Ca and suction valve 155Cb) of motor 100C has replaced the suction valve 155B of motor 100B, according to the 6th embodiment's internal-combustion engine 100C with basic identical according to the 5th embodiment's motor 100B.The difference of suction valve 155C and suction valve 155B is: make the ub of umbrella portion with the volume of inboard by the corresponding part of regional inr less than the ub of umbrella portion with the volume of the outside by the corresponding part of regional otr.More specifically, when centering on the central shaft C1 rotation of bar stm by the corresponding part of regional otr with the outside, in order to be stacked in inboard by on the corresponding part of regional inr, these parts are inconsistent each other, but with the inboard by the corresponding part of regional inr be at least partially contained within the outside by in the corresponding part of regional otr.In this embodiment, suction valve 155C is considered to specific suction valve.

[0076] Figure 19 schematically show with the similar cross section of the section A-A of Fig. 8 in suction valve 155C (155Ca and 155Cb).Suction valve 155C specifically forms, make when in the cross section that provides by the plane that comprises central shaft C1, observing, the ub of umbrella portion all forms with arc by the corresponding part of regional otr by the corresponding part of regional inr with the outside with the inboard, and make with the inboard by the corresponding part of regional inr have than with the outside by the littler radius of curvature of the corresponding part of regional otr.Form respectively have a radius of curvature R 2 with the inboard by the corresponding part of regional inr and have a radius of curvature R 1 with the outside by the corresponding part of regional otr, so that be connected with bar stm smoothly, and radius of curvature R 2 is set to less than radius of curvature R 1.

[0077] in the 6th embodiment that the ub of umbrella portion forms in aforesaid mode, the ub of umbrella portion with the inboard by the corresponding part of regional inr have than with the outside by the littler volume of the corresponding part of regional otr.Therefore, can make inboard bigger by regional inr, and therefore, can be in the valve stroke of suction valve little in scope in the time form towards the firing chamber inlet stream of the further increase at 154 middle part.The ub of umbrella portion of suction valve 155C is formed on the whole girth smoothly in order to avoid stop inlet stream.In this, the ub of umbrella portion of suction valve 155A and 155B forms in a similar fashion.

[0078] Figure 20 with Figure 12 or the similar mode of Figure 16 schematically show with Fig. 8 in be arranged in the suction valve 155C (155Cb) of suction valve 155A similar arrangements on right-hand side on the right-hand side.In Figure 20, side-play amount L sets in the mode identical with mode among Figure 12, and established angle θ sets in the mode identical with mode among Figure 16.In having the motor 100C of suction valve 155C, can form towards the firing chamber inlet stream of the further increase at 154 middle part as mentioned above.Therefore, even make little than in motor 100A or 100B of side-play amount L among the motor 100C, motor 100C also can provide and the equal effect of effect that is provided by motor 100A or 100B.Therefore, under the situation of motor 100C, and compared by the indicated recommended range of above representation (3), the recommended range of side-play amount L is can following row representation (7) indicated and enlarge.

D/24≤L≤D/4 ...(7)

In Figure 20, regional AR4 represents and by the indicated corresponding zone of recommended range of above representation (7), in this zone, supposing provides rational effect.

[0079] under the situation of determining established angle θ, when side-play amount L is D/4, if established angle θ spends greater than about 80 or less than about-80 degree, then bar stm is comprised in the above-mentioned zone AR4.Therefore, under the situation of motor 100C, and compared by the indicated permissible range of above representation (5), the permissible range of established angle θ is can following row representation (8) indicated and enlarge.

-80°≤θ≤80° ...(8)

[0080] as under the situation of motor 100B, in motor 100C, preferably bar stm is at the upstream side that is displaced on the F with respect to center P 2 that flows to of air inlet.Therefore, under the situation of motor 100C, and compared by the indicated recommended range of above representation (6), the recommended range of established angle θ can be indicated and enlarge according to following row representation (9).

0°≤θ≤80° ...(9)

[0081], therefore can more advantageously keep the intensity of suction valve 155C because the scope of side-play amount L and established angle θ is aforesaid extended.Equally, under the situation of motor 100C, bar stm preferably forms, and is convenient to all satisfy by above representation (7) and (9) indicated scope.In Figure 20, regional AR5 represents to be set in the scope indicated by representation (7) with side-play amount L and established angle θ is set to the corresponding zone of situation in representation (9).

[0082] Figure 21 schematically shows in the firing chamber distribution of the flow velocity of the air that 154 middle part measures.Figure 21 shows the comparative result about the flow velocity between motor 100C, motor 100B and the motor 100X.Among the motor 100B and motor 100C that in Figure 21, compares mutually, side-play amount L is set to and identical value in the recommended range indicated by above representation (3), and established angle θ is set to and identical value in the recommended range indicated by above representation (6).Equally, in Figure 21, the ub of umbrella portion of the suction valve 155B of motor 100B forms, and what make the ub of umbrella portion has identical radius of curvature by the corresponding part of regional inr with the outside by the corresponding part of regional otr with the inboard, and is connected smoothly with bar stm.As shown in figure 21, motor 100C provides ratio engine 100C bigger flow velocity.In the motor 100C of structure as mentioned above, from the valve stroke of suction valve be in little to scope in the time, can in an advantageous manner air inlet be introduced in the cylinder so that in cylinder, form tumble flows T.

[0083] next, the seventh embodiment of the present invention will be described.Be according to the 7th embodiment's internal-combustion engine 100D and aforesaid the 4th to the 6th embodiment's motor 100A, 100B and the difference of 100C: motor 100D has three suction valve structures, that is, each cylinder is provided with three suction valves.Similar with Fig. 8, Figure 22 schematically shows the described major component of the motor 100D when observing on the major component projection horizontal plane thereon of the motor 100D related with cylinder.In motor 100D, the bar stm that is positioned at the suction valve 155D (155Da, 155Db) at two ends is offset in the similar mode of mode with the bar stm of suction valve 155A.In addition, the established angle θ of suction valve 155Da, 155Db can set with the similar mode of mode of the established angle θ of suction valve 155B, and with similar among the suction valve 155C, among suction valve 155Da, the 155Db each can form, make the ub of umbrella portion with the inboard by the corresponding part of regional inr have than with the outside by the littler volume of the corresponding part of regional otr.

[0084] in internal-combustion engine 100D as shown in figure 22, the suction valve 155Da, the 155Db that are positioned at two ends with respect to a cylinder are considered to specific suction valve.Specific suction valve is set like this, even have at motor 100D under the situation of three suction valve structures, when the valve stroke of suction valve be in little in scope in the time, also can form towards the firing chamber inlet stream of the increase at 154 middle part.In the motor 100D of structure as mentioned above, from the valve stroke of suction valve be in little to scope in the time, can in an advantageous manner air inlet be introduced in the cylinder so that in cylinder, produce tumble flows T.

[0085] next, the eighth embodiment of the present invention will be described.Except that suction port 110E (representing suction port 110Ea and suction port 110Eb) further is provided with control damper 160, with basic identical according to the 4th embodiment's motor 100A, wherein said control damper 160 makes the air inlet deflection among the suction port 110E so that produce high-intensity tumble flows T in cylinder according to the 8th embodiment's internal-combustion engine 100E.That is, motor 100E is equal to the motor 100A that further is equipped with control damper 160.Also can be provided with the essentially identical mode work of the mode of control damper 160 and control damper with the essentially identical effect of effect of control damper 160 is provided according to the 5th to the 7th embodiment's motor 100B, 100C and 100D.

[0086] similar with Fig. 8, Figure 23 schematically shows the described major component of the motor 100E when observation on the major component projection horizontal plane thereon of the motor 100E related with cylinder.Wherein supporting pivotally on one side of the both sides of control damper 160 by valve rod 161, and the another side of control damper 160 be formed with reentrant part K with when valve 160 cuts out with the middle part of inlet guide to firing chamber 154.In order to make reentrant part K with the middle part of inlet guide to firing chamber 154, the another side of control damper 160 is recessed, thereby the degree of depth of recess part is along with increasing near the corresponding part in the middle part with firing chamber 154 of valve 160, thereby and reentrant part K the heart is extended therein.When control damper 160 was closed fully or be semi-open, reentrant part K was passed through in the air inlet of the suction port 110E that flows through, thereby was directed the middle part to firing chamber 154.By before air inlet flows in the cylinder with the middle part of inlet guide to firing chamber 154, can increase the air inflow at the middle part that flows to firing chamber 154.As a result, can further reduce the air inflow of the bar stm of interference intake valve 155E, therefore can in an advantageous manner air inlet be introduced in the cylinder.

[0087] Figure 24 shows the relation between upset intensity and the valve stroke.Figure 24 shows the comparative result about the upset intensity between motor 100E and the internal-combustion engine 100Y, and internal-combustion engine 100Y has the suction valve of the bar non-migration that replaces suction valve 155E.Except that the suction valve of motor 100Y was different with the suction valve of motor 100E, motor 100Y and motor 100E were basic identical.Recognize that from Figure 24 when control damper 160 is closed fully, rather than when valve 160 was opened fully, upset intensity was enhanced.Recognize also that from Figure 24 100Y compares with motor, in motor 100E, from the valve stroke of suction valve be in little to scope in the time, when control damper 160 was closed fully, upset intensity was enhanced.In the motor 100E of structure as mentioned above, from the valve stroke of suction valve be in little to scope in the time, can in an advantageous manner air inlet be introduced in the cylinder so that in cylinder, produce tumble flows T.

[0088] next, the ninth embodiment of the present invention will be described.Figure 25 schematically shows the major component according to the internal-combustion engine 200A of the ninth embodiment of the present invention.More particularly, Fig. 7 shows the cylinder of the motor 200A when observing on vertical cross section.Motor 200A is direct fuel jet type petrol engine, and uses two suction valve structures (that is, each cylinder is provided with two suction valves).Yet, will be appreciated that motor 200A is not limited to and can implements any specific type of the present invention effectively.For example, motor can be so-called lean-combustion engine, or for example has the motor of three suction valve structures as described later.Motor 200A can also have suitable cylinder number and suitable cylinder arrangement.

[0089] internal-combustion engine 200A has cylinder block 251, cylinder head 252, piston 253 and other parts.Cylinder 251a with general cylindrical is formed in the cylinder block 251, and piston 253 is contained among the cylinder 251a.Cylinder head 252 is fixed on the cylinder block 251.Firing chamber 254 forms the space that is centered on by cylinder block 251, cylinder head 252 and piston 253.Cylinder head 252 is formed with suction port 210Aa and 210Ab (will simply and usually be called " suction port 210A ", the mode of this name is applied to other parts) and relief opening 220 (220a and 220b): air inlet is introduced in the firing chamber 254 (or introducing cylinder) by suction port 210Aa and 210Ab, and combustion gas are discharged from firing chamber 254 by relief opening 220.In addition, be used for opening and closing the outlet valve 256 that the suction valve 255A of each suction port 210A and being used to opens and closes each relief opening 220 and be installed in cylinder head 252 respectively.In this embodiment, suction valve 255A (255Aa, 255Ab) is considered to specific suction valve.

[0090] spark plug 257 is installed in the cylinder head 252 so that its electrode stretches out from the top enters the firing chamber 254.The Fuelinjection nozzle (not shown) is installed in the cylinder head 252 so that its spray-hole stretches among the suction port 210A.Fuelinjection nozzle is suitable for injecting fuel directly among the cylinder 251a at intake stroke.Fuelinjection nozzle is not limited to this type or position, but can be installed in position in the cylinder head 252 than the more close cylinder block 251 of suction port 210A, so that its spray-hole stretches in the firing chamber 254, or be installed in the position of 254 tops, firing chamber in the cylinder head 252.Air inlet from suction port 210A inflow cylinder 251a produces in cylinder waves the revolution air-flow.In this embodiment, particularly, waving the revolution air-flow is the form of tumble flows T as shown in figure 25.Be used for guiding the cavity of tumble flows T can be formed on the end face of piston 253.

[0091] Figure 26 schematically shows the major component of the described motor 200A when observing on the major component projection horizontal plane thereon of the motor 200A related with cylinder.Figure 27 schematically shows the suction valve 255A (255Aa, 255Ab) in the cross section that is intercepted along the line B-B among Figure 26.As shown in figure 26, suction port 210A is long when extension is observed on horizontal plane with box lunch, makes the middle part of inlet stream to firing chamber 254.Utilize this layout, inlet stream is formed on the main flow that produces the air inlet of tumble flows T in the cylinder simultaneously to the middle part of firing chamber 254.In this embodiment, as shown in figure 26, the main flow of air inlet is formed by the inlet stream that flows on the F that flows in air inlet.In this, the main flow that flows to F indication air inlet of air inlet flows so that produce the direction of tumble flows T in cylinder, and can depend on shape or the design of suction port 210A, is represented by the bearing of trend of placing the part of bar stm among the suction port 210A.

[0092] in Figure 26, the substantially parallel axes of straight line L4 and bent axle, and planar S 2 comprise cylinder central shaft C3 and with the basic quadrature of straight line L4, promptly with the basic quadrature of axle of bent axle.As Figure 26 and shown in Figure 27, when suction valve 255A is in closed condition, the bar stm of suction valve 255A tilts, thus when with the direction of the substantially parallel axes of bent axle on when observing, the far-end P11 of bar stm than the P2 of bottom center of the ub of umbrella portion more close more than indicated planar S 2.The P2 of bottom center of the far-end P11 of bar stm and the ub of umbrella portion all is positioned on the central shaft C1 of bar stm.In the motor 200A that suction valve 255A tilts as mentioned above, the air inflow of increase is attracted to a side at the middle part of more close firing chamber 254, so that can increase or strengthen the main flow that flows into the air inlet in the cylinder towards the middle part of firing chamber 254.Therefore, 200A is arranged as with motor, though when the valve stroke of suction valve be in little in scope in the time, also can improve the intensity of tumble flows T.

[0093] as shown in figure 27, in the motor 200A that the bar stm of suction valve 255A tilts, the ub of umbrella portion of suction valve 255A also tilts.As shown in figure 26, in the motor 200A of such structure, guided in mode to the peripheral expansion of firing chamber 254 in the air inlet of flowing along the ub of umbrella portion than the side at the center of the more close firing chamber 254 of bar stm.Therefore, in motor 200A, flow into air inlet in the cylinder when advantageously having prevented in the valve stroke of suction valve is in high scope with the inwall of too high speed bump cylinder 251a, this can cause the intensity of the tumble flows T that produces to reduce.Angle θ 2 is the acute angle between the central shaft C1 of the bar stm that is formed on suction valve 255A (255Aa and 255Ab) between bar shown in Figure 27.The inclined degree of suction valve 255A can angle θ 2 changes between this bar by setting.

[0094] as shown in figure 27, be attracted among the motor 200A at middle part of firing chamber 254, can make suction valve 255Aa, 255Ab shelve distance L v between thereon the valve seat than big in the distance that angle θ 2 is set under 0 ° the situation in the main flow of air inlet.That is, in motor 200A, can be under the situation that does not reduce the distance L v between the valve seat main flow of air inlet be inhaled middle part to firing chamber 254.Therefore, in motor 200A, the motor that equals 0 ° with angle θ 2 between bar is compared, and can be in the sufficient intensity of guaranteeing firing chamber 254 main flow of air inlet be inhaled the middle part to firing chamber 254.

[0095] Figure 28 A and Figure 28 B schematically show the pattern that flows into the inlet stream in the cylinder.More specifically, Figure 28 A schematically show when with Figure 25 in the pattern of inlet stream in the cylinder of identical internal-combustion engine 200X when in vertical cross section, observing, and Figure 28 B schematically show when with Figure 25 in the pattern of inlet stream in the cylinder of motor 200A during identical observation in vertical cross section.Except that angle θ 2 between motor 200X king-rod is set to 0 °, motor 200X and motor 200A are basic identical.In the motor 200X shown in Figure 28 A, when in the valve stroke of suction valve is in, arriving in the high scope, air inlet may cause the stream Fs of remarkable generation along the wall of cylinder 251a with the wall of too high speed bump cylinder 251a, and this has caused the intensity of the tumble flows T that produces in cylinder to reduce.On the other hand, in the motor 200A shown in Figure 28 B, when arriving in the high scope in the valve stroke of suction valve is in, air inlet flows in the cylinder when being dispersed suitable degree.Therefore, the stream Fs of above-mentioned wall along cylinder 251a unlikely takes place, otherwise can reduce or may the reducing of the intensity of the tumble flows T that prevents to produce.

[0096] Figure 29 shows the relation between upset intensity and the valve stroke.Upset intensity is represented by the revolution of upset.Figure 29 shows the comparative result about the upset intensity between motor 200X and the motor 200A.From Figure 29, recognize, compare with the upset intensity among the motor 200X, from the valve stroke of suction valve be in little to scope in the time, the upset intensity in motor 200A is enhanced.

[0097] next, incite somebody to action angle θ 2 between rising stem (RS.) in detail.In internal-combustion engine commonly used, angle θ 2 is set to 0 ° between bar.On the other hand, if angle θ 2 then can improve upset intensity in as the scope indicated by following representation (10).

0°<θ2 ...(10)

[0098] yet, along with angle θ between bar 2 increases, will be difficult to suitably place the cam (not shown) that is used to open and close suction valve 255A physically.Therefore, consider the placement of cam, angle θ 2 is preferred in as the permissible range indicated by following representation (11).

0°<θ2≤10° ...(11)

[0099] when angle θ 2 is set to greater than 0 °, flows into air inlet in the cylinder and 254 periphery disperse towards the firing chamber.Yet, take place if disperse excessively, may reduce rather than improve upset intensity.Figure 30 A and Figure 30 B schematically show the pattern of the inlet stream in the cylinder among the inflow engine 200A, and in motor 200A, angle θ 2 is set to greater than 6 ° and is equal to or less than 10 ° between bar.More specifically, Figure 30 A schematically shows the pattern of the inlet stream in the cylinder of the motor 200A when observing in the vertical cross section in Figure 25 (situation), and Figure 30 B schematically show when with as shown in figure 26 the similar cross section in (described) B-B (horizontal stroke) cross section in the form (mobile mode) of inlet stream among the motor 200A (a cylinder) during observation.

[0100] if angle θ 2 is set to greater than 6 ° and is equal to or less than 10 ° between bar, then depends on the shape of firing chamber 254, shown in Figure 30 A and Figure 30 B, the situation that the air inlet in the cylinder is exceedingly dispersed may occur flowing into.On the other hand, if angle θ 2 is set to greater than 0 ° and less than 1 °, then can not expect significant effect.Therefore, further preferably between bar angle θ 2 be in as by in the indicated recommended range of following representation (12).

1°<θ2≤6° ...(12)

[0101] Figure 31 A and Figure 31 B schematically show in the firing chamber distribution of the flow velocity of the air that 254 middle part measures.Figure 31 A and Figure 31 B show the comparative result about the flow velocity between motor 200A and the motor 200X, and in motor 200A, angle θ 2 is in the scope of above representation (12) between bar.More specifically, Figure 31 A show valve stroke when suction valve be in little in scope in the time the distribution of flow velocity, and the distribution of the flow velocity of Figure 31 B when showing in the valve stroke of suction valve is in the high scope.When angle θ 2 between bar as by representation (12) in the indicated scope time, shown in Figure 31 A, when the valve stroke of suction valve be in little in scope in the time, motor 200A provides the flow velocity greater than predetermined value 2.The Peak Flow Rate that predetermined value 2 can realize greater than motor 200X.On the other hand, when arriving in the high scope in the valve stroke of suction valve is in, shown in Figure 31 B, motor 200A provides the flow velocity that is equal to or greater than predetermined value beta 2.Predetermined value beta 2 is greater than predetermined value 2, and less than predetermined value gamma 2.Be higher than predetermined value gamma 2 if flow velocity becomes, then may take place, and reduce upset intensity along the stream Fs of the wall of cylinder 251a.

[0102] Figure 31 B also shows the flow velocity of the air among the motor 200A of example (hereinafter referred to as " motor 200A-1 ") as a comparison, and in this example, angle θ 2 is set to greater than 6 ° and is equal to or less than 10 ° between bar.Recognize that from Figure 31 B in motor 200A-1, the main flow of air inlet is drawn onto the middle part of firing chamber 254 too much, and flow velocity excessively is increased to greater than predetermined value gamma 2.On the other hand, between bar among the motor 200A of angle θ 2 in the scope of above representation (12), can will flow into the periphery that air inlet in the cylinder expands to firing chamber 254 with suitable degree.Therefore, in motor 200A, when in the valve stroke of suction valve is in, arriving in the high scope, can make flow velocity bigger than predetermined width W2 at the width of the distribution of the flow velocity that is equal to or greater than predetermined value beta 2, and prevent that the main flow of air inlet from concentrating on the middle part of firing chamber 254 too much, so that flow velocity becomes and is equal to or greater than β 2 and less than predetermined value gamma 2.In the motor 200A that constructs as mentioned above, from the valve stroke of suction valve be in little to scope in the time begin, can in an advantageous manner air inlet be introduced in the cylinder so that in cylinder, form tumble flows T, and prevent to flow into air inlet in the cylinder with the wall of too high speed bump cylinder 251a, this can cause the intensity of the tumble flows T that forms in cylinder to reduce.

[0103] next, the tenth embodiment of the present invention will be described.Remove when suction valve 255A is in closed condition, the bar stm of suction valve 255A tilts, thereby when when flowing to of air inlet observed on the F, the far point P11 of bar stm is positioned at beyond the position than center P 2 more close relief openings 220, and is basic identical according to the tenth embodiment's internal-combustion engine and the 9th embodiment's motor 200A.Below, will be called suction valve 255B (it represents suction valve 255Ba and suction valve 255Bb) with the suction valve 255A that this mode tilts.In this embodiment, suction valve 255B is considered to specific suction valve.Similar with Figure 26, Figure 32 schematically shows the major component of the described motor 200B when observing on the major component projection horizontal plane thereon of the motor 200B related with cylinder.Figure 33 schematically shows suction valve 255Bb separately, and suction valve 255Bb is arranged on the right-hand side among Figure 32, and is arranged on the direction identical with the direction of Figure 32.

[0104] in Figure 32 and Figure 33, when observing on horizontal plane, established angle θ 3 is defined as the acute angle between the central shaft C1 that is formed on straight line L6 and bar stm, straight line L6 comprise center P 2 and with air inlet flow to the basic quadrature of F.By suitably setting established angle θ 3, bar stm can also tilt at the F that flows to of air inlet.Arrow " just " indication related with established angle θ 3 among Figure 33 is when when flowing to of air inlet observed on the F, when the far-end P11 of bar stm is positioned at position than center P 2 more close relief openings 220, suppose established angle θ 3 be on the occasion of.

[0105] tilts and established angle θ 3 when being set to 90 ° as the bar stm of suction valve 255B, be difficult to middle part to firing chamber 254 is inhaled in air inlet.Equally, under 90 ° of situations about reducing,, then can not expect significant effect at established angle θ 3 if the degree that reduces is little.On the other hand, if established angle θ 3 less than 0 °, then may be difficult to be formed into smoothly the inlet stream in downstream side directly over the ub of umbrella portion.Therefore, further preferably established angle θ 3 as by following representation (13) in the indicated permissible range.

0°≤θ3≤70° ...(13)

[0106] if established angle θ is set in the scope of above representation (13), then the ub of umbrella portion further tilts, and also disperses towards the lower dead center of cylinder 251a along the air inlet that the ub of umbrella portion flows in a side at the center of the more close firing chamber 254 of bar stm.As a result, more advantageously prevented to flow into the wall of the air inlet bump cylinder 251a in the cylinder, this can cause significantly taking place along the stream Fs of the wall of cylinder 251a.Depend on the established angle θ 3 in the scope of representation (13), air inlet disperse the generation that can help tumble flows T, the mode that maybe can be suitable for producing tumble flows T is introduced air inlet in the cylinder.In this, further improving under the situation of upset intensity, further preferably established angle θ 3 is in as the recommended range indicated by following formula (14).

10°≤θ3≤60° ...(14)

[0107] Figure 34 A and Figure 34 B schematically show in the firing chamber distribution of the flow velocity of the air that 254 middle part measures.Figure 34 A and Figure 34 B show the comparative result about the flow velocity between motor 200B and the motor 200X, and in motor 200B, established angle θ 3 is in the scope of above representation (14).More specifically, Figure 34 A show valve stroke when suction valve be in little in scope in the time the distribution of flow velocity, and Figure 34 B show valve stroke be in the distribution of flow velocity in the high scope time.Angle θ 2 suitably sets in the scope of above representation (10) according to the setting value of established angle θ 3 between bar.When established angle θ 3 is in the scope of above representation (14), when the valve stroke of suction valve be in little in scope in the time, shown in Figure 34 A, motor 200B provides the flow velocity greater than predetermined value 2.Predetermined value 2 ratios can be big by the Peak Flow Rate that motor 200X obtains.On the other hand, when arriving in the high scope in the valve stroke of suction valve is in, shown in Figure 34 B, motor 200B provides the flow velocity greater than predetermined value beta 2 '.Predetermined value beta 2 ' is greater than predetermined value beta 2, and less than predetermined value gamma 2.

[0108] Figure 34 B also shows the flow velocity with respect to the air of motor 200B (hereinafter referred to as " motor 200B-1 ") of example as a comparison, wherein, the main flow of air inlet is drawn onto the middle part of firing chamber 254 too much, and flow velocity excessively is increased to greater than predetermined value gamma 2.On the other hand, in motor 200B, can will flow into air inlet in the cylinder with suitable degree and 254 periphery and bottom disperse towards the firing chamber, so as can to make flow velocity in the width of the distribution of the flow velocity that is equal to or greater than predetermined value beta 2 or scope greater than predetermined width W2.Therefore, when in the valve stroke of suction valve is in, arriving in the high scope, prevent that the main flow of air inlet from concentrating on the middle part of firing chamber 254 too much, so that flow velocity becomes greater than predetermined value beta 2 ' and less than predetermined value gamma 2.In Figure 33, zone AR11 represents to become with flow velocity in motor 200B and is equal to or greater than predetermined value 2 and less than zone or the scope of the corresponding established angle θ 3 of the situation of predetermined value beta 2, and regional AR12 represents and flow velocity become zone or the scope of the corresponding established angle θ 3 of situation that is equal to or greater than predetermined value beta 2.In the present embodiment, the established angle θ 3 of suction valve 255B is set to the value that is included among the regional AR12.

[0109] Figure 35 A, Figure 35 B and Figure 35 C show fuel consumption feature and the output performance when high capacity is worked of motor 200B when lean-burn is worked.By the specific fuel consumption of motor 200B and the relation between the air fuel ratio, in Figure 35 A, specifically illustrated the fuel consumption feature when lean-burn is worked; And, in Figure 35 B, specifically illustrated the output performance when high capacity is worked by the Engine torque of motor 200B and the relation between the engine speed.In Figure 35 B, output performance is represented by fully loaded performance.Figure 35 A and Figure 35 B show the comparative result between motor 200X and the motor 200B.Figure 35 C shows fuel consumption reduced rate and the output performance raising rate that expectation obtains when angle θ 2 between bar is in the scope of representation (11) and representation (12) quantitatively, and shows expectation obtains when established angle θ 3 is in the scope of representation (13) and representation (14) fuel consumption reduced rate and output performance raising rate.

[0110] when the degree that it is suitable that bar stm tilts, from the valve stroke of suction valve be in little to scope in the time, by setting angle θ 2 and established angle θ 3 between bar, can in cylinder, form high-intensity tumble flows T and can produce strong turbulent flow.Therefore, improved combustion characteristic when lean-burn is worked, this has caused the reduction of specific fuel consumption, and can improve output performance when high capacity is worked.Shown in Figure 35 A, 200X compares with motor, has reduced specific fuel consumption in motor 200B, and enlarged motor can be with the lean-burn zone of rare air fuel ratio work.Equally, shown in Figure 35 B, 200X compares with motor, in motor 200B, has improved Engine torque on the gamut of engine speed.To recognize that from Figure 35 B along with engine speed reduces, the raising degree of Engine torque increases, and along with engine speed reduces, angle θ 2 and established angle θ 3 tilt bar stm between bar by suitably setting, and more significant effect is provided.

[0111] if angle θ 2 is set in the scope of representation (11) and representation (12) between bar, then expectation obtains the fuel consumption reduced rate and the output performance raising rate of quantificational expression in Figure 35 C.If established angle θ 3 is set in the scope of representation (13) and representation (14), then expectation obtains the fuel consumption reduced rate and the output performance raising rate of quantificational expression in Figure 35 C.In the motor 200B that constructs as mentioned above, from the valve stroke of suction valve be in little to scope in the time begin, air inlet can be introduced in an advantageous manner in the cylinder so that in cylinder, produce tumble flows T, and prevented to flow into air inlet in the cylinder with the wall of too high speed bump cylinder 251a, this can cause the intensity of the tumble flows T that forms in cylinder to reduce.

[0112] next, the 11st embodiment of the present invention will be described.According to the 11 embodiment's internal-combustion engine 200C be according to the 9th and the tenth embodiment's motor 200A and the difference of 200B: motor 200C has three suction valve structures, that is, each cylinder is provided with three suction valves.Similar with Figure 26, Figure 36 schematically shows the described major component of the motor 200C when observing on the major component projection horizontal plane thereon of the motor 200C related with cylinder.In motor 200C, angle θ is to set with the similar mode of the mode of suction valve 255A between the bar that forms between the bar stm at suction valve 255Ca, the 255Cb at two ends.In addition, the established angle θ 3 of suction valve 255Ca, 255Cb can set with the similar mode of the mode of suction valve 255B.

[0113] in motor 200C, the suction valve 255Ca, the 255Cb that are positioned at two ends with respect to a cylinder are considered to specific suction valve.Use the specific suction valve that is provided with like this, even have at motor 200C under the situation of three suction valve structures, when the valve stroke of suction valve be in little in scope in the time, can increase or enhanced flow to the main flow of the air inlet at the middle part of firing chamber 254, and in the valve stroke of suction valve is in the high scope time, can suppress along the generation of the stream Fs of the wall of cylinder 251a.In the motor 200C that constructs as mentioned above, from the valve stroke of suction valve be in little to scope in the time begin, air inlet can be introduced in an advantageous manner in the cylinder so that in cylinder, form tumble flows T, and prevented to flow into air inlet in the cylinder with the wall of too high speed bump cylinder 251a, this can cause the intensity of the tumble flows T that forms in cylinder to reduce.

[0114] next, the 12nd embodiment of the present invention will be described.Except that suction port 210D (representing suction port 210Da and suction port 210Db) further is provided with control damper 260, with basic identical according to the 9th embodiment's motor 200A, control damper 260 makes the air inlet deflection among the suction port 210D so that produce high-intensity tumble flows T in cylinder according to the 12 embodiment's internal-combustion engine 200D.That is, motor 200D is equal to the motor 200A that further is equipped with control damper 260. Motor 200B and 200C according to the tenth and the 11 embodiment can also be provided with control damper, and this control damper is with the essentially identical mode work of the mode of control damper 260 and provide and the essentially identical effect of the effect of control damper 160.

[0115] similar with Figure 26, Figure 37 schematically shows the described major component of the motor 200D when observation on the major component projection horizontal plane thereon of the motor 200D related with cylinder.Wherein supporting pivotally on one side of the both sides of control damper 260 by valve rod 261, and the another side of control damper 260 be formed with reentrant part K with when valve 260 cuts out with the middle part of inlet guide to firing chamber 254.In order to make reentrant part K with the middle part of inlet guide to firing chamber 254, the another side of control damper 260 is recessed, thereby the degree of depth of recess part is along with recess part increases near the corresponding part in the middle part with firing chamber 254 of valve 260, and reentrant part K the heart is extended therein.When control damper 260 was closed fully or be semi-open, the air inlet of the suction port 210A that flows through was directed the middle part to firing chamber 254 thus by reentrant part K.By flowing in air inlet before the cylinder with the middle part of inlet guide to firing chamber 254, can increase or enhanced flow to the main flow of the air inlet at the middle part of firing chamber 254.

[0116] Figure 38 shows the relation between upset intensity and the valve stroke.Figure 38 shows according to the internal-combustion engine 200Y of present embodiment and the comparative result of the upset intensity between the motor 200D.Except that in motor 200Y with bar between angle θ 2 be set at 0 °, motor 200Y and motor 200D are basic identical.From Figure 38, recognize, when control damper 260 is closed fully, rather than when valve 260 is opened fully, improved upset intensity.Recognize also that from Figure 38 200Y compares with motor, in motor 200D, from the valve stroke of suction valve be in little to scope in the time, when control damper 260 is closed fully, improved upset intensity.In the motor 200D that constructs as mentioned above, from the valve stroke of suction valve be in little to scope in the time begin, can in an advantageous manner air inlet be introduced in the cylinder so that in cylinder, form tumble flows T, and prevented to flow into air inlet in the cylinder with the wall of too high speed bump cylinder 251a, this can cause the intensity of the tumble flows T that forms in cylinder to reduce.

[0117] illustrated embodiment is the preferred embodiments of the present invention.Yet, will be appreciated that the present invention is not limited to these embodiments, and can under the situation that does not deviate from principle of the present invention, utilize various modifications or improvement to realize.

Claims (10)

1, a kind of internal-combustion engine (50A), it comprises the suction port (10A) that is connected with firing chamber (54), and has a suction valve (55) that umbrella portion (ub) and an end are connected to the bar (stm) in the described umbrella portion (ub), described suction port (10A) has starting point (P1) and terminal point (P2): when observing above the cylinder head (52A) that is formed with described suction port (10A), described starting point (P1) is the streamline (F) of described suction port (10A) and the subpoint of first intersection point on horizontal plane of the inlet side opening surface of described suction port (10A); Described terminal point (P2) is the described streamline (F) of described suction port (10A) and the subpoint of second intersection point on horizontal plane of the central shaft of described suction valve (55), it is characterized in that:

Be projected in the center curvature of the described streamline (F) of the described suction port (10A) on the described horizontal plane towards described firing chamber (54), so that be positioned at position at least in part than the described center of first straight line (L1) and the more close described firing chamber of second straight line (L2) (54), described first straight line (L1) comprise described starting point (P1) and with described horizontal plane on the direction of axle quadrature of bent axle on extend, described second straight line (L2) comprise described terminal point (P2) and with described horizontal plane on the direction of described axle quadrature of described bent axle on extend.

2, internal-combustion engine according to claim 1 is characterized in that, described starting point (P1) is positioned at the position than the described center of the more close described firing chamber of described second straight line (L2) (54).

3, internal-combustion engine according to claim 1 is characterized in that, described starting point (P1) is positioned on second straight line (L2).

4, internal-combustion engine according to claim 1 is characterized in that, described starting point (P1) is not positioned at the position than the described center of the more close described firing chamber of described second straight line (L2) (54).

5, according to each described internal-combustion engine in the claim 1 to 4, it is characterized in that, described suction valve (155A-155D) comprises specific suction valve (155A-155D), in described specific suction valve (155A-155D), described bar (stm) skew, thereby two air inlets on the both sides on the plane of the central shaft that comprises described bar (stm) are positioned at the inboard of position at the described center of more close described firing chamber (154) in by the zone becomes bigger by zone (inr), and the described central shaft (C1) of described bar (stm) does not comprise the center (P2) of the bottom surface of described umbrella portion (ub).

6, internal-combustion engine according to claim 5 is characterized in that, the described bar (stm) of described specific suction valve (155B) described center (P2) with respect to described specific suction valve (155B) on the flow direction of air inlet is displaced to upstream side.

7, according to claim 5 or 6 described internal-combustion engines, it is characterized in that, the described umbrella portion (ub) of described specific suction valve (155C) with described inboard by zone (inr) corresponding part have than described umbrella portion (ub) with the outside by zone (otr) corresponding part littler volume.

8, according to each described internal-combustion engine in the claim 5 to 7, it is characterized in that, described specific suction valve (155E) further comprises anti-rotation device, and described anti-rotation device prevents that described specific suction valve (155E) from rotating around the described central shaft (C1) of the described bar (stm) of described specific suction valve (155E).

9, according to each described internal-combustion engine in the claim 1 to 8, it is characterized in that, described suction valve (255A-255D) comprises specific suction valve (255A-255D), in described specific suction valve (255A-255D), when described air inlet valve position during in closed condition, described bar (stm) tilts, thereby with the direction of the described substantially parallel axes of described bent axle on, the far-end (P11) of described bar (stm) be positioned at than the more close central shaft (C3) that comprises cylinder in the center (P2) of the bottom surface of described umbrella portion and with the position of the basic plane orthogonal of described axle of described bent axle.

10, internal-combustion engine according to claim 9, it is characterized in that, when described specific suction valve (255A-255D) when being in closed condition, the described bar (stm) of described specific suction valve (255A-255D) tilts, thereby on the flow direction of air inlet, the described far-end (P11) of described bar (stm) is positioned at the position than the more close relief opening in described center (P2) (256).

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