CN1497160A - Piston of internal-combustion engine - Google Patents

Piston of internal-combustion engine Download PDF

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Publication number
CN1497160A
CN1497160A CNA2003101045853A CN200310104585A CN1497160A CN 1497160 A CN1497160 A CN 1497160A CN A2003101045853 A CNA2003101045853 A CN A2003101045853A CN 200310104585 A CN200310104585 A CN 200310104585A CN 1497160 A CN1497160 A CN 1497160A
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China
Prior art keywords
piston
section
skirt
cylinder
thrust
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CNA2003101045853A
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CN1228542C (en
Inventor
和秀
嶽和秀
子
平出玲子
明
河合范明
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Honda Motor Co Ltd
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Honda Motor Co Ltd
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29L—INDEXING SCHEME ASSOCIATED WITH SUBCLASS B29C, RELATING TO PARTICULAR ARTICLES
    • B29L2031/00—Other particular articles
    • B29L2031/748—Machines or parts thereof not otherwise provided for
    • B29L2031/7506—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/107—Manufacturing or mounting details

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  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

An object of the present invention is to effectively achieve the reduction in piston slap sound in both of an expansion stroke and a compression stroke in consideration of a difference between the behaviors of a piston in the expansion stroke and the compression stroke. For this purpose, in a piston P having a skirt 12 formed into an intermediately bulged barrel type, the axis L2 of a piston pin is offset with respect to the cylinder axis L1, and the decrement in radius of a lower skirt portion 20 is set to be large on a thrust side and small in an anti-thrust side. In the expansion stroke, the piston is positively swung, while the skirt 12 is put into abutment against a wall surface of a cylinder bore, thereby reducing the piston slap sound.

Description

Internal combustion engine
The application's denomination of invention that to be Honda Motor Co. propose January 28 calendar year 2001 is that internal combustion engine, application number are dividing an application of 00101184.7 application.
The present invention relates to have the internal combustion engine in skirt section, and relate in particular to the piston-shaped of minimizing piston slap.
In internal combustion engine, this piston comprises the wrist pin and the skirt section that forms the middle barrel-shaped of protruding that has with respect to the axis of cylinder offset.From the Japanese Utility Model patent publication No. is to recognize a kind of like this technology the No.53-40546: partial cut-out is positioned at the top in the skirt section on the side relative with the skew side of wrist pin, and the top that this cuts is easy to cause the wall of cylinder-bore and scratch and the spot between this part, therefore can prevent to produce Cylinder sticking.
The piston slap that piston slap cylinder-bore wall is produced is tended to reduce in barrel-shaped skirt section, but in above-mentioned known piston, on the lubricated viewpoint of piston, improves on barrel-shaped on the top in skirt section.This is helpless to reduce piston slap.
Therefore, the objective of the invention is to guarantee: utilize the difference of pistons work situation between expansion stroke and the compression stroke and thrust to reduce piston slap in expansion stroke and the compression stroke effectively.
To achieve these goals, according to a first aspect of the invention and feature, a kind of piston of internal-combustion engine is provided, this piston comprises barrel-shaped skirt section, and this skirt section is made up of upper skirt that is arranged in maximum diameter part top and the skirt end that is arranged in maximum diameter part below, upper skirt and skirt end have the little radius of radius than maximum diameter part, it is characterized in that: be provided with to such an extent that the radius reduction of the skirt end on the specific thrust side is little in the radius reduction of the skirt end on the thrust side.
With regard to above-mentioned layout, when piston when expansion stroke is swung, when simultaneously the skirt end of the piston on thrust sides, maximum diameter part and upper skirt engage with the wall generation of cylinder-bore with specified order successively, owing to guaranteed that on thrust sides the radius of skirt end fully reduces, therefore, permission piston swing, thus and alleviated skirt section collision cylinder-bore wall and reduced piston slap.
In compression stroke, the skirt end on the thrust side at first produces with the wall of cylinder-bore and engages, and in the swing afterwards of piston, thereby the wall of the collision of the upper skirt on thrust side cylinder-bore produces piston slap.But, because the radius reduction of the skirt end on the thrust side is provided with lessly, therefore, the tilting of the piston angle that skirt end on the thrust side is produced when engaging the wall of cylinder-bore can be suppressed to a smaller value, and alleviated at piston afterwards and swung the vibration that causes that upper skirt is produced when colliding the thrust side in opposite direction, thereby reduced piston slap.
Therefore skirt end radius reduction has produced asymmetric in the above described manner on thrust sides and thrust side, on the two, can realize reducing piston slap in expansion stroke and compression stroke effectively.
According to a second aspect of the invention and feature, a kind of internal combustion engine with skirt section is provided, it is characterized in that: the curvature of the cross section in the skirt section on the thrust side be provided with cross section little in the skirt section on the specific thrust side, and the cross section at least a portion skirt section on the thrust side forms circular arc.
With regard to above-mentioned layout, the curvature of the cross section in the skirt section on the thrust side be provided with little on the specific thrust side, and the cross section at least a portion skirt section on the thrust side forms circular arc.Therefore, piston is reduced in compression stroke with the surface pressure that the wall of cylinder-bore contacts, thereby has reduced piston slap and improved the performance that prevents Cylinder sticking.
According to a third aspect of the invention we and feature, except second feature, a kind of internal combustion engine also is provided, has it is characterized in that: on each the axis opposite side that extends through piston middle spindle line arrival thrust sides and thrust side, circular arc is formed with 10 ° or bigger center angle.
With regard to above-mentioned layout, circular arc is formed with 10 ° or bigger center angle on each opposite side of axis.Therefore, in compression stroke, the pressure of contact surface of piston and cylinder-bore wall fully reduces.
In conjunction with the accompanying drawings, by describing below of preferred embodiment, above-mentioned purpose of the present invention, feature and advantage and other purpose, feature and advantage will become apparent.
Fig. 1 represents embodiments of the invention to 13B, wherein
Fig. 1 is the side view of internal combustion engine;
Fig. 2 is the cross-sectional view of piston;
Fig. 3 A and 3B are the schematic representation of explaining the definition of " thrust sides " and " thrust side ";
Fig. 4 A is the schematic representation of explaining the working procedure of expansion stroke to 4C;
Fig. 5 A is the schematic representation of explaining the working procedure of compression stroke to 5C;
Fig. 6 A and 6B are the schematic representation that is illustrated in the radius reduction and the relation between the Cylinder Vibration of skirt end in compression stroke and the expansion stroke;
Fig. 7 A is the schematic representation of the relation between the oval size of cross section in expression Cylinder Vibration and skirt section to 7C, and the relation between the gentle cylinder vibration of the center angle of the curved portion of the cross section in skirt section;
Thereby Fig. 8 is the schematic representation that the skirt section shape of expression skirt section shape of present embodiment and conventional example compares between them;
Thereby Fig. 9 A and 9B are the schematic representation that the result of expression result of present embodiment and conventional example compares between them;
Thereby Figure 10 is the schematic representation that the shape of cross section in the skirt section of the shape of cross section in skirt section of asymmetric bucket piston of expression present embodiment and conventional example compares between them;
Thereby Figure 11 A and 11B are the schematic representation that the result of the result of asymmetric bucket piston of expression present embodiment and conventional example compares between them;
Thereby Figure 12 A and 12B are the schematic representation that the result of the result of non-bucket piston of expression present embodiment and conventional example compares between them;
Thereby Figure 13 A and 13B are the schematic representation that the result of the result of asymmetric bucket piston of expression present embodiment and conventional example compares between them.
Now, by means of embodiment the present invention is described with reference to accompanying drawing.
The piston P of 4 stroke cycle internal-combustion engines shown in Figure 1 comprises the piston head 11 of facing the firing chamber and the skirt section 12 of facing crank box.Make two compression ring mounting grooves 13 and 14 and oil ring mounting grooves 15 in piston head 11 upper limits.Connecting rod 16 is its small end place is pivotably connected skirt section 12 by wrist pin 17 on.
The shape of cross section in the skirt section 12 of piston P is along cylinder-bore axis L 1Direction and change continuously.More particularly, skirt section 12 at its vertical intermediate portion (along cylinder-bore axis L 1Direction) have maximum diameter part 18, and upper skirt 19 and skirt end 20 are separated by maximum diameter part 18 each other.Maximum diameter part 18 is the parts with skirt section 12 of maximum outside diameter.Focus on expression like that as Fig. 1, along with making progress away from maximum diameter part 18, upper skirt 19 is along around cylinder-bore axis L 1Radius reduce gradually, and along with downwards away from maximum diameter part 18, skirt end 20 is along around cylinder-bore axis L 1Radius reduce gradually.Identical on the radius reduction of the upper skirt on the thrust sides of piston P 19 and thrust side at piston P, but the radius reduction of skirt end 20 is arranged to like this: bigger on the thrust sides of piston P, and less on the thrust side of piston P.The whole skirt section 12 of piston P is so a kind of barrel-shaped: vertical intermediate portion (maximum diameter part) is the thickest, and vertically opposite end (upper skirt 19 and skirt end 20) is thinner slightly.
The definition of " thrust sides " and " thrust side " will be described below.Fig. 3 A and 3B represent the expansion stroke of 4 stroke cycle internal-combustion engines.In expansion stroke, downward load Fg and the inertial force Fm that makes progress are applied on the piston P, and the load Fg that makes progress is produced by the caused cylinder interior pressure of the expansion of sky-combustion mixed gas, and inertial force Fm is produced by reciprocating mass.Therefore, along cylinder-bore axis L 1Power F on the direction (=Fg+Fm) be applied on the piston P, and resolve into along the component Fr on connecting rod 16 directions with perpendicular to cylinder-bore axis L 1Component Fs. on the direction
Component Fs is used for this thruster of piston P is leaned against power on the wall of cylinder-bore 22, and this component Fs is called the thrust of piston.The size of supposing thrust Fs is in maximum value when being subjected to breaking out the expansion stroke of load.Direction (right side of Fig. 3 A and 3B) at the thrust Fs that this time produced is called " thrust sides ", and its opposite direction (left side of Fig. 3 A and 3B) is called " thrust side ".
As shown in Figure 1, the axis L of wrist pin 2With respect to cylinder-bore axis L 1Distance alpha of skew thrust sides (right side of Fig. 1).Distance alpha is a very little amount, for example about 0.5mm.
The known technology that a kind of like this resistance of reducing friction is arranged: guarantee shape of cross section approaching real circle when piston P carries out thermal expansion in skirt section 12 by the skirt section 12 of piston P being formed the oval cross section shape, and this oval cross section shape has along piston pin axis L 2Minor axis that direction is extended and edge are perpendicular to piston pin axis L 2Axis L 3The major axis that direction is extended.On the contrary, in this embodiment, on thrust sides and thrust side, asymmetricly form the shape of cross section in skirt section 12.
By cut the skirt section 12 of piston P open at maximum diameter part 18 places, the solid line of Fig. 2 is represented along the section shape of Fig. 1 arrow a-a direction intercepting.As from seeing Fig. 2, be non-circular at maximum diameter part 18 places along section shape arrow a-a direction intercepting, whole skirt section 12, it is at piston pin axis L 2Have than minor diameter on the direction, and perpendicular to piston pin axis L 2Axis L 3Have than major diameter on the direction, and skirt section 12 asymmetricly is formed on thrust sides and the thrust side.More particularly, be to have at thrust sides upper edge arrow a-a direction section shape intercepting, skirt section 12 along piston pin axis L 2The ellipse of the minor axis that extends, each shape of cross section in these parts of thrust side upper skirt 12 is around cylinder-bore axis L simultaneously 1Be arc, and these parts in skirt section 12 are in perpendicular to piston pin axis L 2Axis L 3Opposite side on presumptive area in.By means of smoothed curve, the opposite end of curved portion is connected on the opposite end of the oval part on the thrust sides.
Pecked line on Fig. 2 (one-dot dashed line) has been represented along the section shape of arrow b-b direction upper skirt intercepting, piston P.As from seeing Fig. 2, whole piston P forms barrel-shaped, and therefore the section shape along the intercepting of arrow b-b direction is littler than being in section shape maximum diameter part 18, that intercept along arrow a-a direction in whole zone.Dotted line among Fig. 2 is represented along the shape of arrow c-c direction skirt end 20 intercepting, piston P.Because whole piston P forms barrel-shaped, therefore little along arrow c-c direction shape intercepting, skirt end 20 section shape than the maximum diameter part 18 that intercepts along arrow a-a direction in whole zone, but be provided with the radius reduction, therefore, as mentioned above, it is bigger on thrust sides, and less on the thrust side.Emphasis has represented the section shape of piston P and along the shape of the piston P that these direction of arrow intercepted, the size of the actual reduction of radius is approximately several 10 μ m.
As shown in fig. 8, the skirt section 12 of piston P in this embodiment highly is 35mm, the radius reduction is being 60 μ m on the thrust sides of skirt end 20, is being 0 μ m on the thrust side at skirt end 20, and is 90 μ m in the thrust sides of upper skirt 19 and thrust side on the two.
With reference to accompanying drawing 4A-4C, the work of expansion stroke is described below.
Fig. 4 A represents a kind of like this state: piston P is near the upper dead center, and is right after after combustion-empty mixture breaks out in the firing chamber.When the pressure of combustion gas promoted the top surface of piston P downwards, the pressure of combustion gas was around piston pin axis L 2Applied a moment M 1, because piston pin axis L 2With respect to cylinder-bore axis L 1Be displaced to thrust sides.This has caused that piston P swings along counterclockwise direction, and therefore, the lower end in the skirt section 12 on the thrust sides engages with the wall generation of cylinder-bore 22 at an A place.
In expansion stroke, the upper end of connecting rod 16 is with respect to cylinder-bore axis L 1Tilt to thrust sides, therefore produced thrust Fs, thereby piston P has been pushed against on the right wall of cylinder-bore 22.At this moment, the lower end in the skirt section 12 on the thrust sides of piston P engages with the wall of cylinder-bore 22, therefore around an A, thrust Fs has formed clockwise moment, therefore piston P swings along clockwise direction, and the lower end in skirt section 12 and the part between the upper end in turn produce with the wall of cylinder-bore 22 and contact (seeing Fig. 4 B and 4C) simultaneously.
As mentioned above, during the expansion stroke, when piston P descends, when swinging along clockwise direction simultaneously, on the thrust sides that the wall with cylinder-bore 22 engages, can guarantee the radius reduction (see figure 1) of the skirt end 20 of piston P basically.Therefore, guarantee that piston P pendulum angle along clockwise direction can enough reduce the slip sound of piston.Supposing that piston P swings along clockwise direction is prevented from, and under the situation that is not having swing under the effect of thrust Fs, piston P effectively collides on the wall of the cylinder-bore on the thrust sides 22 so, has therefore produced huge piston slap at that time.
In above-mentioned expansion stroke, piston slap (being the vibration of cylinder) can reduce (referring to Fig. 6 B) by the radius reduction that increases the skirt end 20 on the thrust sides.On the contrary, in compression stroke, if the radius reduction of the skirt end 20 on the thrust side increases, piston slap (being Cylinder Vibration) has correspondingly increased so, causes reaction (referring to Fig. 6 A).This is because piston P is mutually different in the working condition of expansion stroke and compression stroke.
To 5C, the work of compression stroke is described below with reference to accompanying drawing 5A.
Described equally as reference accompanying drawing 3A and 3B, formed load of the internal pressure of cylinder and the formed inertial force of reciprocating mass are applied on the piston P.When throttle valve was opened fully, when the internal pressure of cylinder was big, the thrust on the thrust direction was bigger, so the wall of the cylinder-bore 22 of piston P on the thrust side raises.But, during less load or at the less idle period of the internal pressure of cylinder, the wall of the cylinder-bore 22 on some B and the thrust side of bottom in skirt section 12 is produced contact: (1) negative pressure (power that makes progress), near starting stage of compression stroke (leave lower dead centre 40 °) this negative pressure of generation in cylinder; And (2) clockwise moment M 2, be displaced to thrust sides by wrist pin 17 and produce this moment.
Then, by means of the thrust that produces on the pushing direction, piston P moves apart the wall (referring to Fig. 5 B) of the cylinder-bore 22 on the thrust side, and this piston P starts near the middle part between upper dead center and the lower dead centre step by step, and the direction of inertial force is changed near this middle part.Afterwards, be displaced to counterclockwise moment M that thrust sides produces by means of the rising of the internal pressure in (1) cylinder and (2) wrist pin 17 3, the some C on 12 top from the skirt section, piston P moves the wall of the cylinder-bore 22 of clashing on the thrust side, has therefore produced piston slap (referring to Fig. 5 C).
In order to reduce piston slap, to be suppressed to less degree be effective being in clockwise pendulum angle θ state shown in Fig. 5 A, piston P.This is because if the clockwise pendulum angle θ of piston P is less, produced the state procedure of colliding by the wall of the upper end in the skirt section 12 of the state of pendulum angle θ in a clockwise direction on the thrust side from piston P so with cylinder-bore 22, the counter-clockwise pendulum angle θ (referring to Fig. 5 C) of piston P will become less, therefore can prevent the increase of striking speed.
With regard to situation about being seen, in this embodiment, the radius reduction of the skirt end 20 of the piston P on the thrust side is arranged to a smaller value (referring to accompanying drawing 1).Therefore, produce when engaging with the wall of cylinder-bore 22 when the lower end that is in skirt section 12 state shown in Fig. 5 A, on the thrust side, the clockwise pendulum angle θ of piston P can be suppressed to less degree, consequently, has reduced piston slap.
As mentioned above, on the one hand, in expansion stroke, the barrel-shaped of the skirt section 12 of piston P guaranteed that piston P just swings, and therefore reduced piston slap, on the other hand, in compression stroke, do not expect that piston slap reduces the barrel-shaped effect that produces.Therefore, in compression stroke, the shape of cross section in skirt section 12 is asymmetric on thrust sides and thrust side, therefore, makes piston slap reduce.More particularly, big on the wall contact area specific thrust side of the cylinder-bore 22 on the cross section part of having guaranteed skirt section 12 at the arcuate surface that the skirt section cross section is set on the thrust side and the thrust side, therefore, in compression stroke, piston P has reduced with the surface pressure that the wall of cylinder-bore 22 contacts, thereby piston slap is reduced.In this case, the pressure of contact surface of the wall by reducing piston P and cylinder-bore 22 also can be realized the raising of anti-bite cylinder performance.
To describe in detail this below.In order to reduce piston slap, the skirt section 12 of therefore guaranteeing piston P produces with the wall of cylinder-bore 22 on its width regions that contact be effectively, thereby causes the surface pressure minimizing that contacts.But the desired value of the curvature (curvature) of skirt section 12 cross sections on thrust sides and thrust side is very different each other.This is to influence thrust on the less thrust side and have bigger different each other because be subjected to the internal pressure of cylinder to influence thrust and the internal pressure that is subjected to cylinder on the bigger thrust sides.
Fig. 7 A represents the oval size of cross section in the skirt section 12 on the thrust sides and the relation between the Cylinder Vibration.Oval size is limited by the deviation D-d between long axis of ellipse D and the minor axis d.If oval size is bigger, the curvature of cross section is bigger so, and if oval big or small less, the curvature of cross section is less so.As from seeing Fig. 7 A, if the oval size of the cross section in the skirt section on thrust sides 12 reduces, the shape of cross section in skirt section 12 is near arc so, and the vibration of cylinder begins to reduce gradually.But, if oval size further reduces, so along with threshold value (threshdd) Y as the limit, it is big that the vibration of cylinder becomes.This be because, if the cross section in skirt section 12 forms the shape near arc, the surface pressure on the sidewall direction is local so raises, and this side wall support skirt surface and have higher rigidity, consequently, Cylinder Vibration increases.
Fig. 7 B has represented the oval size of cross section in the skirt section 12 on the thrust side and the relation between the Cylinder Vibration.As seeing from Fig. 7 B, even the oval size of the cross section in the skirt section 12 on the thrust side reduces, so the shape of cross section in skirt section 12 is near arc, but almost do not reduce when the vibration of cylinder begins.But, if thereby oval size further reduces and surpasses extreme value Y, so the shape of cross section in skirt section 12 is near arc, so the vibration of cylinder sharply reduces.From this fact, can see that in order to reduce the piston slap of compression stroke, the oval size that therefore reduces the cross section in the skirt section 12 on the thrust side fully is effectively, so the cross section shape in skirt section 12 is near arc.
Fig. 7 C has represented the relation between the gentle cylinder vibration of the center angle of curved portion of cross section in the skirt section 12 on the thrust side.As seeing from Fig. 7 C, if the center angle of the curved portion on the thrust side increases, the vibration of cylinder reduces gradually so.In the center of curved portion angle surpassed ± 10 ° zone, the minimizing speed of Cylinder Vibration had increased, and therefore, can produce remarkable result.From this fact, the center angle of curved portion be arranged on a third aspect of the present invention ± 10 ° value or bigger value on.
Fig. 8 represents skirt section 12 shapes of the piston P among this embodiment and the skirt section shape of conventional piston, thereby to comparing between them.Conventional piston shown in Figure 8 belongs to barrel-shaped (on thrust sides and these both sides of thrust side, the radius reduction of skirt end is set to 40 μ m) of non-barrel-shaped (the radius reduction of skirt end is set to 0 (zero) in this shape) and symmetry.
Fig. 9 A and Fig. 9 B represent with this embodiment's the corresponding Cylinder Vibration of piston P and with the corresponding Cylinder Vibration of conventional piston, thereby to comparing between them.As from seeing Fig. 9 A, in expansion stroke, Cylinder Vibration reduces according to the order of symmetrical barrel-shaped and asymmetric barrel-shaped (in this embodiment) in non-barrel-shaped, the cylinder.Therefore, further confirmed by the radius reduction of the skirt end on the thrust sides 20 being increased to the effect that 60 μ m are produced in this embodiment.As from seeing Fig. 9 B, in compression stroke, the Cylinder Vibration maximum of symmetrical bucket piston, and the Cylinder Vibration of asymmetric barrel-shaped (being this embodiment) is identical with non-barrel-shaped Cylinder Vibration.Therefore, can further be confirmed by making radius reduction on the thrust side equal the effect that the radius reduction (promptly by the radius reduction on the thrust side is reduced to 0 μ m) on the non-bucket piston produced.
Figure 10 represents the shape of cross section in the skirt section 12 of the shape of cross section in skirt section 12 of piston P (belonging to asymmetric barrel-shaped) of this embodiment (shape of cross section of maximum diameter part 18) and conventional piston, thereby to comparing between them.Conventional piston shown in Figure 10 (belonging to asymmetric barrel-shaped) has two ellipses.In the ellipse therein, oval size (D-d 1) be 0.3 μ m, and in another elliptical shape, oval size (D-d 2) be 0.1mm.In this embodiment's piston, the oval size on the thrust sides equals the oval size on the conventional piston of 0.3mm, but this embodiment's piston skirt 12 is non-circular, and this is non-circular to have with respect to axis L on the thrust side 3Curved portion in+25 ° of scopes.
Figure 11 A and 11B represent to have this embodiment's shown in Figure 10 Cylinder Vibration (piston slap) of piston P and the Cylinder Vibration of conventional piston, thereby compare between them.As seeing from Figure 11 B, in compression stroke, Cylinder Vibration reduces according to the order of the conventional piston of the oval size with 0.3mm, the oval big or small conventional piston with 0.1mm and this embodiment's piston P, therefore, by be provided in this embodiment+effect that curved portions branch in 25 ° of scopes produces further confirmed.In expansion stroke, have the Cylinder Vibration maximum of the conventional piston of the oval size of 0.1mm, and the Cylinder Vibration with piston P of this embodiment is suppressed to the Cylinder Vibration size of the conventional piston that equals to have the oval size of 0.3mm.Therefore, further confirmed by the effect that shape of cross section produced that shape of cross section on the thrust sides is equaled have the conventional piston of the oval size of 0.3mm.
Figure 12 A and 12B represent to have the Cylinder Vibration (piston slap) of non-barrel-shaped (straight line type) piston with the wrist pin offset that equals 0.5mm and have the Cylinder Vibration of the non-bucket piston with three shape of cross sections shown in Figure 10, thereby compare between them.Can see from Figure 12 A and 12B, be that the Cylinder Vibration of non-bucket piston has reduced even have in compression stroke, the same with the asymmetric barrel-shaped situation shown in the 11B as Figure 11 A.
Figure 13 A and Figure 13 B represent to have the Cylinder Vibration of piston, and this piston has the wrist pin offset that is increased to 1.0mm from the 0.5mm shown in Figure 12 A and the 12B.As by Figure 13 A and 13B and Figure 12 A and 12B are compared see, on the one hand, along with the increase of wrist pin offset, the Cylinder Vibration of expansion stroke significantly reduces, on the other hand, the Cylinder Vibration of compression stroke increases slightly.Reason is: on the one hand, in expansion stroke, counter-clockwise moment M shown in Fig. 4 A 1Increase cause and originate in the joint lower end, skirt section 12 with less rigidity, thereby reduced Cylinder Vibration, and on the other hand, in compression stroke, clockwise moment M shown in Fig. 5 B 3Increase cause and originate in the joint upper end, skirt section 12 with big rigidity, thereby increased Cylinder Vibration.
Although described embodiments of the invention in detail, be understood that: the present invention is not limited to the foregoing description, can carry out various improvement in spirit of the present invention that does not break away from claims and limited and scope.
For example, the piston P of the internal-combustion engine of four stroke cycle illustrates in an embodiment, but the present invention can be applied on the piston of the motor that is not Otto (cycle) engine.Also can on non-barrel-shaped piston P, obtain by the effect that shape of cross section produced that is formed on the asymmetrical piston P on thrust sides and the thrust side, but, can further improve the effect that reduces piston slap effectively by non-bucket piston P and asymmetric bucket piston are combined.

Claims (2)

1. internal combustion engine with skirt section is characterized in that: the curvature of the cross section in the skirt section on the thrust side be provided with cross section little in the skirt section on the specific thrust side, and the cross section at least a portion skirt section on the thrust side forms circular arc.
2. internal combustion engine as claimed in claim 1 is characterized in that: on each the axis opposite side that extends through piston middle spindle line arrival thrust sides and thrust side, described circular arc is formed with 10 ° or bigger center angle.
CN 200310104585 1999-01-29 2000-01-28 Piston of internal-combustion engine Expired - Fee Related CN1228542C (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP02296299A JP4198810B2 (en) 1999-01-29 1999-01-29 Throttle body and manufacturing method thereof
JP22961/1999 1999-01-29
JP326721/1999 1999-11-17

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Application Number Title Priority Date Filing Date
CNB001011847A Division CN1153898C (en) 1999-01-29 2000-01-28 Piston for IC engine

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CN1497160A true CN1497160A (en) 2004-05-19
CN1228542C CN1228542C (en) 2005-11-23

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102094723A (en) * 2011-03-18 2011-06-15 湖南江滨机器（集团）有限责任公司 Piston and method for optimizing skirt profile section of piston
CN101668938B (en) * 2007-04-27 2012-04-18 马勒国际公司 Piston for an internal combustion engine
CN101784780B (en) * 2007-08-24 2013-03-27 本田技研工业株式会社 Piston of internal combustion engine
CN104131909A (en) * 2013-04-30 2014-11-05 铃木株式会社 Piston of internal combustion engine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101668938B (en) * 2007-04-27 2012-04-18 马勒国际公司 Piston for an internal combustion engine
CN101784780B (en) * 2007-08-24 2013-03-27 本田技研工业株式会社 Piston of internal combustion engine
CN102094723A (en) * 2011-03-18 2011-06-15 湖南江滨机器（集团）有限责任公司 Piston and method for optimizing skirt profile section of piston
CN104131909A (en) * 2013-04-30 2014-11-05 铃木株式会社 Piston of internal combustion engine
CN104131909B (en) * 2013-04-30 2017-06-30 铃木株式会社 The piston of internal combustion engine

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CN1228542C (en) 2005-11-23
JP4198810B2 (en) 2008-12-17
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