CN102606338A - Piston for a stroke piston combustion engine - Google Patents
Piston for a stroke piston combustion engine Download PDFInfo
- Publication number
- CN102606338A CN102606338A CN2011104152067A CN201110415206A CN102606338A CN 102606338 A CN102606338 A CN 102606338A CN 2011104152067 A CN2011104152067 A CN 2011104152067A CN 201110415206 A CN201110415206 A CN 201110415206A CN 102606338 A CN102606338 A CN 102606338A
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- piston
- cylinder
- place
- ring
- centralising device
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 26
- 230000000694 effects Effects 0.000 claims description 15
- 239000013049 sediment Substances 0.000 description 12
- 229910000906 Bronze Inorganic materials 0.000 description 6
- 239000010974 bronze Substances 0.000 description 6
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 6
- 230000001050 lubricating effect Effects 0.000 description 5
- 239000008041 oiling agent Substances 0.000 description 5
- 238000005516 engineering process Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
- 238000013459 approach Methods 0.000 description 3
- 239000000446 fuel Substances 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 3
- 238000012423 maintenance Methods 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000007667 floating Methods 0.000 description 2
- 239000010763 heavy fuel oil Substances 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000002000 scavenging effect Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000001066 destructive effect Effects 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 238000010304 firing Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- JEIPFZHSYJVQDO-UHFFFAOYSA-N iron(III) oxide Inorganic materials O=[Fe]O[Fe]=O JEIPFZHSYJVQDO-UHFFFAOYSA-N 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000012797 qualification Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F5/00—Piston rings, e.g. associated with piston crown
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
The piston has a cylinder (2) arranged along a cylinder axis (A) between an upper dead center and a bottom dead center in an axial direction. A piston ring gasket (3) comprising two piston rings (31, 32) is arranged at a mantle surface (100). The gasket is arranged between a piston crown (4) with a top land (5) and a piston skirt (6). The piston skirt forms a lower portion that is turned away from a combustion chamber surface (7) of the piston. Centering units (8, 81) e.g. guide rings, are provided on the piston for radially centering the piston in the cylinder.
Description
Technical field
The present invention relates to the piston that is used for reciprocating internal combustion engine as described in the preamble according to independent claims 1, said reciprocating internal combustion engine is large two-stroke diesel engine especially.
Background technique
The piston that for example be used for large-sized diesel motor (but not only be used for these large-sized diesel motors) known from existing technology is equipped with one group of a plurality of piston ring usually, and said a plurality of piston rings are arranged in the corresponding piston annular groove up and down stackedly.Known piston ring group typically comprises at least two piston rings, yet, be generally three, four or even five piston rings, this depends on size and/or the power of motor or the specific operation condition that depends on needs and operate motor.In this respect, growing trend is to make the piston ring group have the least possible piston ring.For example, the piston ring group that only has two piston rings is advantageously used simultaneously, under very specific situation, and piston even can only have a single piston ring basically.
The piston ring that satisfies difference in functionality is vulnerable to significant strain under serviceability, said difference in functionality is such as being: in cylinder, guide piston; Oiling agent is distributed on the working surface of cylinder and/or and wipes oiling agent from the working surface of cylinder; Towards crankcase sealing combustion space or the like.Piston ring therefore with the cylinder bearing face rubbing contact, firing pressure has to absorbed by piston ring, and therefore piston ring is vulnerable to significant thermal strain, mechanical strain and chemical strain.
Aspect this, the piston ring group can not taken over the piston in the cylinder as often supposing by error centering.That is, this is impossible fully owing to constructing reason.Piston ring self all the time admittedly in cylinder with respect to radially with the form of centering by guiding automatically; This is because their external diameter is selected as the internal diameter that is slightly larger than cylinder all the time under non-installation situation; The diameter elastic variable of piston ring wherein makes piston ring along promoting towards cylinder wall all the time under the limited pressure of peripheral direction.By contrast, the internal diameter of piston ring is greater than the external diameter of the piston ring groove that is positioned at the piston place, and wherein piston ring is disposed in this piston place.Therefore piston ring group or single piston ring are arranged by " free floating ground " with respect to piston or with respect to piston ring groove.This also is indispensable; Because maybe the time piston ring can be not and piston ring groove rubbing contact for good and all; Because otherwise piston ring will no longer be guided at the cylinder wall place ideally; In cylinder wall place and/or piston ring groove, kill, and therefore possibly take place badly damaged, even heavy wear.
For example; Under the situation of longitudinally scavenged large two-stroke diesel engine; The use of piston ring group has become convention, and said piston ring group is made up of two to five piston rings, is used for respect to lower piston side sealing combustion space; Said lower piston side is pointed to and is received the space, and fresh air is from receiving spatial flow and cross the scavenging slit and getting into the combustion space of cylinder when scavenging period begins.Exerted pressure more or less tempestuously in the annular space of lower piston cyclic group between piston and cylinder wall.Aspect this, dissimilar unstability possibly appear between the lower piston ring, and this for example possibly cause pressure surge, this pressure surge and then cause piston fluctuation of service etc., this is because there is the too many piston ring with similar or identical function.
Large-scale diesel engine often is being used as the driver element of boats and ships or also is being used for Fixed Point Operation aspect this, for example be used to drive high-rating generator with the output electric energy.Aspect this, motor operation lastingly in cycle considerable time usually, this has just proposed high request to safety in operation and validity.In long especially maintenance period, therefore the economic treatment of low wearing and tearing and fuel and operative material is the central standard that is used for the operation of machine for the operator.Except that other factors, the piston operation action of this big cylinder diameter slow running diesel engine for the duration of maintenance period, validity and aspect the oiling agent consumption also directly to operating cost with for operational efficiency, be a kind of deciding factor therefore.Therefore this is not only complicated problems concerning the cylinder lubrication of motor; It is more and more important also to become; Wherein particularly in large-scale diesel engine, carry out cylinder lubrication, perhaps realize cylinder lubrication through the lubricant oil nozzle that is arranged in the cylinder wall through the lubricating fitting that is arranged in the piston that moves around.
Cause repeatedly that the in service of internal-combustion engine a point of problem is a residue of combustion, this residue of combustion can be deposited on the some place that the tool in the motor changes.At first, under the situation of the large two-stroke diesel engine of operating through heavy fuel oil commonly used, residue of combustion shows significant problem; Because employed fuel; Be heavy fuel oil, be filled with many materials that can cause various solid-state, liquid state and gaseous state residue of combustion, these residues can be deposited on piston place, piston ring groove place especially; Especially also be deposited on piston head place or cylinder place, preferably also be deposited near the upper dead center.
Particularly; Known for example under the situation of
two stroke engine (Wa Xilan); So-called wearing ring is set, to wipe the sediments of residue of combustion from piston head in the top of cylinder liner.This ring for example is formed into the thin-walled socket with rectangular cross-section, and this ring has self the littler interior cross section, cross section than cylinder usually.Wipe effect through the diameter restrictions generation, to wipe the sediments at piston head place.In engine operation, the internal diameter of wearing ring aspect this based on the diameter of piston head, and in fact particularly based on the maximum diameter of piston head.Therefore, the target of known wearing ring is to design internal diameter tightly to making the gap between piston head and the wearing ring become as far as possible little, but piston head is not mechanically skimmed over wearing ring with the mode of direct contact.
Be apparent that the design of wearing ring must be followed a large amount of trading off.Under low load and situation in colder piston head, the gap, promptly the interval between piston head and the wearing ring is only owing to thermal expansion effects and than big under the high capacity.Must consider aspect this in addition; The different parts such as cylinder bearing face, piston, particularly piston ring, piston ring groove and piston head in the cylinder circumferentially and vertically have different wearing and tearing according to the hours of operation that is carried out, and therefore these different parts do not have the diameter of any fixedly qualification.
Therefore be clear that in the motor known by existing technology, wearing ring and piston head can not interact under all operating conditionss and in the whole working life of participation parts ideally.
If in fact wearing ring and piston head interact with sealing means, then at first can not guarantee the desirable seal effect between wearing ring and the piston head in all cases near upper dead center.Except wiping residue of combustion; Another main purpose of wearing ring/piston head of pairing is the downside of abuts against plunger and therefore mainly seals huge gas pressure against the piston ring group that is arranged under the piston head, and the fuel-air mixture that this gas pressure forms in compression stroke perhaps through near the combustion space the upper dead center of lighting the piston that is arranged in cylinder forms.
The pressure energy that should guarantee especially to produce near the combustion space upper dead center is utilized as far as possible fully, and the bottom that untapped pressure energy is partly flowed away through piston get into cylinder with the form of gas with receive in the centre.In addition; Under the situation of the deficiency of the sealing between wearing ring and the piston head, there is such risk all the time, promptly; The air-flow that individual particle is downward through piston is pulled out the sediments of residue of combustion with uncontrolled mode; Make them can be deposited over the for example bottom that is arranged in the cylinder bearing face place of cylinder, thus their contamination gas cylinder lubricating oils especially, and under the worst situation, can cause damage such as heavy wear.
Aspect this, aforesaid destructive sediments not only causes the problem at piston head place.And the pollutant of any kind of and sediments all can cause the execution near near all the other outer circumferential face places of the piston piston ring group and the piston skirt.
The reason of avoiding these sedimentss at the outer circumferential face place of piston to become becoming more and more important be due to the fact that especially reduce at the same time burning consume need be increasingly high under the situation about consuming with oiling agent performance level; In addition; At first, the emission standard increasingly stringent that also becomes.
Yet; The sediments of dirt or iron rust or other sediments not only cause more fuel consumption and oiling agent consumption at the outer circumferential face place of piston; Naturally also cause the wear phenomenon that causes by pollution at piston, piston ring and cylinder wall place, and cause discharge value to worsen.
Aspect this; Great problem causes basically by the piston of the guiding of the piston skirt in cylinder centering in cylinder definitely all the time not; But in fact piston can move with slight inclination or eccentric slightly mode; Make that under this serviceability the circumferential outer circumferential face in the edge of piston evenly and is not fully cleaned by wiper ring all the time.This is due to the fact that; Promptly as last illustrated; The piston of piston ring in can not the centering cylinder; It also can not be by near the jacket surface centering of the piston piston head, piston set or the piston skirt because the external diameter of piston all the internal diameter than cylinder is little in all points, near the piston diameter the piston skirt especially.
Usually the guidance tape of processing and be arranged on the piston skirt place by the soft relatively material such as bronze also is used for the piston of guide cylinder admittedly, but it does not have the centering function fully.The external diameter of guidance tape is slightly larger than the diameter of piston skirt self admittedly.Yet, between the working surface of guidance tape and cylinder, still have the sizable gap in the millimeter scope.In the ideal case, guidance tape does not also contact with cylinder bearing face fully.The bronze guidance tape only is the safety measure that can prevent for example tilting of the piston, thereby the hard relatively material of piston skirt directly contacts with cylinder bearing face, and damages this working surface.If therefore unwanted inclination takes place piston, the soft relatively guidance tape of then only being processed by bronze contacts with cylinder bearing face, makes to avoid the damage to cylinder bearing face to a great extent.
In fact, in large-scale diesel engine, between piston and cylinder, there is the annular space that on average is approximately 1mm to 5mm, can avoids piston not to be stuck in the cylinder thus.
In the ideal case, the sediments that under serviceability, is formed on the piston head place is removed clean by wearing ring.Yet, if for example motor from low load accelerated service to higher load, the diameter of piston head is for example because thermal effect and increase manyly than the internal diameter of cylinder.This result who causes is, the sediments at piston place can contact the working surface of cylinder, and this can cause damaging working surface and under the worst situation, cause taking place heavy wear.In addition; Because piston can not collide with wearing ring; Therefore, must guarantee the gap between wearing ring and the piston head, this gap is all enough for any serviceability; If for example when the load of motor reduces, become internal diameter than wearing ring of the diameter of piston head is little and reduce manyly than the internal diameter of cylinder, then this causes the effect of wearing ring obviously to reduce.
Therefore hope to reduce between piston and the cylinder wall as much as possible basically or piston and wearing ring between the size in gap, to guarantee the better effects of wearing ring.Yet; This causes following risk; For example at the serviceability of motor when higher load or bigger rotational speed change; If piston external diameter increases manyly than the internal diameter of cylinder or wearing ring, then piston is stuck in the cylinder or piston head contacts with wearing ring, in any case this also must be avoided.
Summary of the invention
Therefore; The objective of the invention is to propose a kind of improved piston; Through this piston; Can avoid the aforesaid shortcoming of existing technology, make particularly the problem got rid of about the sediments at the piston place no longer takes place, and therefore guarantee the more economical operation of large two-stroke diesel engine, longer maintenance period and the longer working life of final corresponding part and large-scale diesel engine.
The theme that satisfies these purposes of the present invention is a characteristic with the characteristic of independent claims 1.
Dependent claims relates to particularly advantageous mode of execution of the present invention.
Therefore the present invention relates to a kind of piston that is used to have the reciprocating internal combustion engine of at least one cylinder; Said reciprocating internal combustion engine is large two-stroke diesel engine especially; Said piston is arranged under installment state, can between upper dead center and lower dead centre, move to and fro vertically along cylinder-bore axis in said cylinder; And said piston comprises the piston ring group that is positioned at the jacket surface place; Said piston ring group comprises at least one piston ring, and said piston ring group is disposed in piston skirt and has between the piston head of top bank, and said piston skirt forms the bottom away from surface, the combustion space of this piston of said piston.According to the present invention, the place is provided with centralising device at said piston, so that said piston radial is centered in the said cylinder.
The centralising device according to the present invention that is positioned at said piston place through utilization guarantees that first the said piston through the said piston skirt guiding in the said cylinder also is centered in this cylinder through said centralising device now all the time exactly basically.That is, said piston with respect to axially in fact no longer including any inclination, and moves with almost ideal centering mode under serviceability.Therefore can select the annular space between said piston and the said cylinder littler first.For example through the present invention under the situation of large two-stroke diesel engine, can select less than 1.5mm, especially in addition less than 1mm or even less than the annular space of 0.5mm, and confirm that no longer having said piston is stuck in the risk in the said cylinder.
Therefore under the sediments that is formed on said piston head place under the said serviceability each serviceability, remove clean by wearing ring in said reciprocating internal combustion engine.Even when said motor increases greatlyyer than the internal diameter of said cylinder from the diameter of low load accelerated service to higher load and institute's piston head owing to for example thermal effect, also be like this for example.Because the present invention and opposite with existing technology; This no longer has following result; Promptly; The said sediments that is positioned at said piston place can contact with the said working surface of said cylinder, and this can cause damaging said working surface and under worst case, cause heavy wear, and this is because in fact no longer tilt and almost be directed with the mode of centering ideally according to piston of the present invention.
Although the diameter of said piston increases a lot; Said piston does not collide with said wearing ring yet; This cause between said piston and the said cylinder for example less than the much little annular space of 1mm, and in enough gaps of all guaranteeing under each serviceability between said wearing ring and the said piston head.Because compared with prior art when using according to piston of the present invention; Said annular space between said wearing ring and the said piston head can be selected little a lot; Even so the diameter of said piston head reduces to such an extent that Duo or reduce manyly than the internal diameter of said cylinder than the internal diameter of said wearing ring when the load of said motor or rotational speed reduce, the cleaning effect of said wearing ring also is able to greatly improve.
In for practice especially preferred embodiment; Said centralising device is set at said piston skirt place; Naturally, can also said centralising device be arranged in the zones of different of said piston, for example be arranged on said piston head place and perhaps also can be arranged near the piston set.
Aspect this; Said centralising device of the present invention for example can be a guide block; This guide block is direct radially outward at said piston place; And especially preferably but be not imperative ground, said guide block can be loaded by the spring element of radially effect, make the spaced radial of the variation between said piston and the said cylinder can in the border that can limit, be able to compensation.The stroke that can radially carry out at radially movable guide block aspect this be selected and and be restricted to, make said guide block can on cylinder wall, not apply too high power, thereby do not have danger for said cylinder wall and oil film.Should be understood that to replace to load said guide block that said guide block can also be supported with hydraulic pressure or pneumatic mode simultaneously or alternately with said spring element.
In order to make reliable guiding and the centering of said piston in said cylinder, in fact (with respect to circumferentially) is furnished with a plurality of guide blocks with the space that can limit at said piston place, preferably two, three, four or five guide blocks.Aspect this, can also be at said piston place with respect to two guide blocks axially are set to skew each other, thus even can prevent said tilting of the piston better.
In another embodiment, said centralising device of the present invention is a lead ring, and said lead ring advantageous particularly ground can load or also can be supported with hydraulic pressure or pneumatic mode by enough ring-type guide springs.Particularly, can axially be furnished with a plurality of lead rings with the space that can limit along said at said piston place, preferably two or three lead rings can especially easily prevent said tilting of the piston thus.
In another embodiment; Said centralising device can also be a guidance tape; This guidance tape has the thin bar of guiding along said extending circumferentially, naturally, can also axially be furnished with a plurality of guidance tapes with the space that can limit along said at said piston place; Preferably two or three guidance tapes, this can guarantee to resist the stability of the further improvement of said tilting of the piston equally.Aspect this, known and bronze band that be present in said piston place usually by any way own for example can also be made thicker simply, and can be designed to have thin bar, and said thin bar is formed by the peripheral groove in the said bronze band.Along the said thin bar in the said axially very narrow said guidance tape then along said cylinder wall slide and therefore in said cylinder the mode with centering guide said piston.Because the whole surface but the only very narrow thin bar of said guiding that are not said bronze band slide, therefore can not cause the lubricating film on this working surface that damages and can not damage this cylinder to the said working surface of said cylinder on the surface of said cylinder.
In another specific implementations of the present invention, said centralising device is a guide surface, and this guide surface radially has an elastic effect along said, and said guide surface is arranged in said piston skirt place and axially extends away from this piston skirt along said.In order to make said piston reliable guiding and centering in said cylinder, aspect this usually in practice, at said piston place with respect to circumferentially being furnished with a plurality of guide surfaces, preferably two, three, four or five guide surfaces with the space that can limit.
Obviously, the instance of describing in this application according to the mode of execution of piston of the present invention should be understood with exemplary approach, and all suitable combinations of the mode of execution that illustrates are particularly contained by the present invention.
Description of drawings
To explain the present invention in further detail with reference to accompanying drawing below.Have shown in the indicative icon:
Fig. 1 a is first mode of execution according to piston of the present invention that has by spring-loaded guide block;
Fig. 1 b is the section of edge according to the line I-I of Fig. 1 a;
Fig. 2 is second mode of execution with the lead ring that is loaded by guide spring;
Fig. 3 is the 3rd mode of execution with fixed position guide block;
Fig. 4 is the 4th mode of execution with guidance tape of the thin bar of tape guide; And
Fig. 5 is the 5th mode of execution with guide surface of radial elastic effect.
Embodiment
Mode with signal in Fig. 1 a illustrates first mode of execution according to the mode of execution of piston 1 of the present invention that has by spring-loaded guide block 8,81.In order to understand better, Fig. 1 b shows the piston 1 of Fig. 1 a with the section of I-I along the line.
According to Fig. 1 a or Fig. 1 b, piston 1 according to the present invention is a kind of piston 1 that is used for having usually the large two-stroke diesel engine of a plurality of cylinders 2.Piston 1 is shown as and is in installment state, and is arranged to and can moves to and fro in the axial direction by known mode axis A along cylinder between upper dead center and lower dead centre own.In this specific embodiment, comprise that the piston ring group 3 of two piston rings 31,32 is set at jacket surface 100 places, and be disposed in piston skirt 6 and have between the piston head 4 of top bank 5.The bottom away from the combustion space face 7 of this piston 1 of piston skirt 6 as known formation piston 1 itself.According to the present invention, aspect this, be provided with four centralising devices 8,81 altogether of the form that is the guide block 81 that loads by spring element 801 at piston 1 place, be used for piston skirt 6 places at piston 1 with piston 1 radial alignment at cylinder 2.Four guide blocks 81 are guaranteed all to guarantee to be directed and fitly be centered in the cylinder 2 at all operations state lower piston 1 of large-scale diesel engine; Although indispensable gap was much little when the annular space between feasible for example piston 1 and the cylinder wall was selected to than the use known piston; Wearing ring (for clearly former thereby not shown) also can be removed all sedimentss from piston head 4 best, and piston 1 is not contacted with wearing ring or cylinder wall when it moves.Obvious aspect this, the guide block or even the guide block more than four that (possibly be merely three) below four for example can be provided also.
Schematically show the cross section of the piston 1 through second embodiment of the invention with reference to Fig. 2, centralising device 8 here is the lead ring 82 that is loaded by guide spring 802.Lead ring 802 is being designed to make external diameter only be slightly less than the internal diameter of cylinder 2 aspect this.Therefore piston 1 is kept with respect to lead ring 82 by the mode with centering by guide spring 802.This and piston ring 31,32 are completely different.Piston ring 31,32 is supported in the piston ring groove by the mode with free floating, and the result makes piston ring 31,32 can not make piston 1 centering in cylinder usually, but this can be realized by guide spring 802 when using lead ring 82.
Fig. 3 shows the 3rd specific implementations of the centralising device 8,83 with the form that is fixed position guide block 83; Fixed position guide block 83 is not perhaps to be loaded with the mode of pneumatic or hydraulic pressure by spring-loaded, and it is arranged in piston head 4 places as embodiment here.Can be selected as at the radially extended length that is designed such that them aspect this with the fixed position guide block of uniformly-spaced arranging (for example three) around the periphery of piston 1 and make all guide blocks 83 slide simultaneously, and therefore keep piston 1 with the mode of centering at the cylinder wall place.The surface that contacts with cylinder wall of guide block 83 be selected so for a short time aspect this and be designed so that cylinder wall or cylinder wall on lubricating film can not damaged unfriendly by guide block 83.
Fig. 4 shows the 4th mode of execution of the guidance tape 84 with the thin bar 804 of tape guide; Guidance tape 84 is designed such that only very narrow guiding approaches bar 804 (they are arranged in the guidance tape 84 with spiral form in the present embodiment) and contacts with cylinder wall, and therefore guarantees that the mode with centering guides piston 1 in cylinder 2.The surface that the cylinder wall with cylinder 2 of the thin bar 804 of guiding contact be selected so for a short time aspect this and be designed such that cylinder wall or cylinder wall on lubricating film can not be directed to and approach bar 804 and damage unfriendly.
At last; Schematically show the 5th mode of execution of the present invention with reference to Fig. 5; In this embodiment; Be provided with radially the flexibly guide surface 85 of guiding at piston skirt 6 places, these guide surfaces extend away from piston skirt 6 vertically, and a plurality of guide surfaces 85 (being preferably two, three, four or five guide surfaces 85) can be with respect to circumferentially arranging with the space that can limit at piston 1 place.Near external diameter guide surface 85 of piston 1 is selected as the internal diameter that only is slightly larger than cylinder 2 aspect this.Because guide surface 85 is designed to the footpath, edge for having elasticity, therefore, piston 1 is guided via the centering position of guide surface 85 in cylinder 2 all the time reliably.Surface that the cylinder wall with cylinder 2 of guide surface 85 contacts and the size that acts on the radial effect power on the cylinder wall through this guide surface 85 are being selected aspect this and are being designed such that lubricating film on cylinder wall or the cylinder wall can not be directed to face 85 and damage unfriendly.
Generally, through the present invention can greatly reduce first between piston and the cylinder wall or piston and wearing ring between the gap, make and guarantee that the effect of wearing ring is significantly increased.And in fact there is not following risk; Promptly; For example at the serviceability of motor when higher load or higher rotational speed change; If piston external diameter increases greatlyyer than the internal diameter of the internal diameter of cylinder or wearing ring, then piston is stuck in the cylinder or piston head contacts with wearing ring, and this is avoided through utilization piston according to the present invention reliably.
Claims (15)
1. piston that is used to have the reciprocating internal combustion engine of at least one cylinder (2), said reciprocating internal combustion engine is large two-stroke diesel engine especially, and this piston is arranged in said cylinder (2) can be along cylinder-bore axis (A) motion to and fro vertically between upper dead center and lower dead centre under the installment state; And said piston comprises and is positioned at the piston ring group (3) that jacket surface (100) is located that said piston ring group comprises at least one piston ring (31,32); Said piston ring group is disposed in piston skirt (6) and has between the piston head (4) of top bank (5), and said piston skirt (6) forms the bottom away from the surface, combustion space (7) of this piston of said piston, and said piston is characterised in that; Be provided with centralising device (8,81,82 at said piston place; 83; 84,85), so that said piston radial is centered in the said cylinder (2).
2. piston according to claim 1, wherein, said centralising device (8,81,82,83,84,85) is set at said piston skirt (6) and locates.
3. according to claim 1 or the described piston of claim 2, wherein, said centralising device (8,81,82,83,84,85) is set at said piston head (4) and locates.
4. according to each described piston in the aforementioned claim, wherein, said centralising device (8,81,82,83,84,85) is set near the said piston ring group (3).
5. according to each described piston in the aforementioned claim, wherein, said centralising device (8,81,82,83,84,85) is radially outer guide block (8,81,83) at said piston place.
6. piston according to claim 5, wherein, said guide block (81,83) is loaded by the spring element (801) of radially effect and/or is supported with hydraulic pressure or pneumatic mode.
7. according to claim 5 or 6 described pistons, wherein, with respect to circumferentially being furnished with a plurality of guide blocks (8,81,83), be preferably two, three, four or five guide blocks (8,81,83) with the space that can limit at said piston place.
8. according to each described piston in the claim 5 to 7, wherein, at said piston place with respect to said two guide blocks (8,81,82) that axially are provided with to skew each other.
9. according to each described piston in the aforementioned claim, wherein, said centralising device (8,81,82,83,84,85) is lead ring (8,82).
10. piston according to claim 9, wherein, said lead ring (8,82) is directed to spring (802) loading and/or is supported with hydraulic pressure or pneumatic mode.
11. according to a described piston in claim 9 or 10, wherein, axially be furnished with a plurality of lead rings (8,82) along said, be preferably two or three lead rings (8,82) with the space that can limit at said piston place.
12. according to each described piston in the aforementioned claim, wherein, said centralising device (8,81,82,83,84,85) is the guidance tape (8,84) that has along the thin bar (804) of guiding of said extending circumferentially.
13. piston according to claim 12 wherein, axially is furnished with a plurality of guidance tapes (8,84) with the space that can limit at said piston place along said, is preferably two or three guidance tapes (8,84).
14. according to each described piston in the aforementioned claim, wherein, said centralising device (8; 81,82,83; 84; 85) be along said radially with the guide surface (8,85) of elastic type effect, said guide surface is arranged in that said piston skirt (6) is located and axially extends away from this piston skirt (6) along said.
15. piston according to claim 14 wherein, with respect to circumferentially being furnished with a plurality of guide surfaces (8,85) with the space that can limit, is preferably two, three, four or five guide surfaces (8,85) at said piston place.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP11151883.3 | 2011-01-24 | ||
| EP11151883 | 2011-01-24 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102606338A true CN102606338A (en) | 2012-07-25 |
| CN102606338B CN102606338B (en) | 2015-12-09 |
Family
ID=44146795
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110415206.7A Active CN102606338B (en) | 2011-01-24 | 2011-12-13 | For the piston of reciprocating internal combustion engine |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2479413A1 (en) |
| JP (1) | JP6130100B2 (en) |
| KR (1) | KR101941285B1 (en) |
| CN (1) | CN102606338B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107542593A (en) * | 2016-06-23 | 2018-01-05 | 曼卡车和巴士股份公司 | Internal combustion engine, especially stroke piston combustion engine |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1654595A (en) * | 1926-07-22 | 1928-01-03 | John A Cornell | Means for centralizing pistons |
| GB377374A (en) * | 1931-06-10 | 1932-07-28 | C M I Engineering Company Ltd | An improved aluminium alloy piston for internal combustion engines |
| US2712483A (en) * | 1953-05-15 | 1955-07-05 | Patrick J Ciaccia | Friction-reducing piston construction for internal combustion engines |
| US4268042A (en) * | 1980-05-08 | 1981-05-19 | Borlan Albert G | Flexible bellows piston seal |
| GB2283555A (en) * | 1993-11-04 | 1995-05-10 | Ford Motor Co | Piston ring seal |
| DE19723047A1 (en) * | 1997-06-02 | 1998-12-03 | Georg Weber | Piston for e.g. Otto engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR528814A (en) * | 1920-03-24 | 1921-11-19 | Harry Ralph Ricardo | Improvements made to pistons |
| US2300647A (en) * | 1940-01-15 | 1942-11-03 | Vacuum Air Pressure Company Lt | Piston |
| US2438243A (en) * | 1944-10-20 | 1948-03-23 | Stanley M Zoromskis | Internal-combustion engine piston |
| JPS5633573B2 (en) * | 1973-06-04 | 1981-08-04 | ||
| JPS576751Y2 (en) * | 1977-01-18 | 1982-02-08 | ||
| JPS5832149U (en) * | 1981-08-26 | 1983-03-02 | 本田技研工業株式会社 | Piston steady rest device |
| JPS5892438U (en) * | 1981-12-17 | 1983-06-22 | トヨタ自動車株式会社 | Friction reduction device for internal combustion engine pistons |
| JPS61120062U (en) * | 1985-01-17 | 1986-07-29 | ||
| JPS636268A (en) * | 1986-06-26 | 1988-01-12 | Toyota Autom Loom Works Ltd | Piston for engine |
| JPH09317553A (en) * | 1996-05-27 | 1997-12-09 | Nippon Soken Inc | Piston for internal combustion engine |
| US6871577B2 (en) * | 2003-01-31 | 2005-03-29 | Tetra Laval Holdings & Finance, Sa | Fill pump piston centering support |
| JP4661831B2 (en) * | 2007-06-15 | 2011-03-30 | トヨタ自動車株式会社 | Piston and internal combustion engine |
| JP2009264143A (en) * | 2008-04-22 | 2009-11-12 | Mitsubishi Heavy Ind Ltd | Diesel engine and piston |
| EP2175107A1 (en) * | 2008-10-08 | 2010-04-14 | Wärtsilä Schweiz AG | Method for lubricating a large diesel engine and large diesel engine |
| EP2243940A1 (en) * | 2009-04-06 | 2010-10-27 | Wärtsilä Schweiz AG | Reduction device for reducing gas pressure in the piston ring package of a hydraulic piston combustion engine |
-
2011
- 2011-11-16 EP EP11189399A patent/EP2479413A1/en not_active Withdrawn
- 2011-12-06 KR KR1020110129656A patent/KR101941285B1/en active IP Right Grant
- 2011-12-13 CN CN201110415206.7A patent/CN102606338B/en active Active
-
2012
- 2012-01-23 JP JP2012011303A patent/JP6130100B2/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1654595A (en) * | 1926-07-22 | 1928-01-03 | John A Cornell | Means for centralizing pistons |
| GB377374A (en) * | 1931-06-10 | 1932-07-28 | C M I Engineering Company Ltd | An improved aluminium alloy piston for internal combustion engines |
| US2712483A (en) * | 1953-05-15 | 1955-07-05 | Patrick J Ciaccia | Friction-reducing piston construction for internal combustion engines |
| US4268042A (en) * | 1980-05-08 | 1981-05-19 | Borlan Albert G | Flexible bellows piston seal |
| GB2283555A (en) * | 1993-11-04 | 1995-05-10 | Ford Motor Co | Piston ring seal |
| DE19723047A1 (en) * | 1997-06-02 | 1998-12-03 | Georg Weber | Piston for e.g. Otto engine |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107542593A (en) * | 2016-06-23 | 2018-01-05 | 曼卡车和巴士股份公司 | Internal combustion engine, especially stroke piston combustion engine |
| CN107542593B (en) * | 2016-06-23 | 2021-12-03 | 曼卡车和巴士股份公司 | Internal combustion engine, in particular reciprocating piston internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6130100B2 (en) | 2017-05-17 |
| KR101941285B1 (en) | 2019-01-22 |
| EP2479413A1 (en) | 2012-07-25 |
| JP2012154331A (en) | 2012-08-16 |
| KR20120085642A (en) | 2012-08-01 |
| CN102606338B (en) | 2015-12-09 |
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