CN102691565A - Cylinder assembly and piston for a longitudinally flushed stroke piston combustion engine - Google Patents
Cylinder assembly and piston for a longitudinally flushed stroke piston combustion engine Download PDFInfo
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- CN102691565A CN102691565A CN2012100277335A CN201210027733A CN102691565A CN 102691565 A CN102691565 A CN 102691565A CN 2012100277335 A CN2012100277335 A CN 2012100277335A CN 201210027733 A CN201210027733 A CN 201210027733A CN 102691565 A CN102691565 A CN 102691565A
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- setting device
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 45
- 230000002000 scavenging effect Effects 0.000 claims description 84
- 239000000314 lubricant Substances 0.000 claims description 30
- 238000011010 flushing procedure Methods 0.000 abstract 3
- 239000003921 oil Substances 0.000 description 26
- 238000012856 packing Methods 0.000 description 18
- 239000000446 fuel Substances 0.000 description 11
- 230000000694 effects Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 6
- 230000000875 corresponding effect Effects 0.000 description 5
- 238000005461 lubrication Methods 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 4
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000013016 damping Methods 0.000 description 4
- 239000003595 mist Substances 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000008859 change Effects 0.000 description 3
- 239000003034 coal gas Substances 0.000 description 3
- 239000000295 fuel oil Substances 0.000 description 3
- 125000006850 spacer group Chemical group 0.000 description 3
- 239000000571 coke Substances 0.000 description 2
- 239000002283 diesel fuel Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000010304 firing Methods 0.000 description 2
- 238000007373 indentation Methods 0.000 description 2
- 238000007790 scraping Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 235000009470 Theobroma cacao Nutrition 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 244000240602 cacao Species 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 239000003610 charcoal Substances 0.000 description 1
- 238000004939 coking Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 230000002596 correlated effect Effects 0.000 description 1
- 239000010727 cylinder oil Substances 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 239000008041 oiling agent Substances 0.000 description 1
- 238000005498 polishing Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/02—Engines characterised by using fresh charge for scavenging cylinders using unidirectional scavenging
- F02B25/04—Engines having ports both in cylinder head and in cylinder wall near bottom of piston stroke
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L11/00—Valve arrangements in working piston or piston-rod
- F01L11/02—Valve arrangements in working piston or piston-rod in piston
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L11/00—Valve arrangements in working piston or piston-rod
- F01L11/02—Valve arrangements in working piston or piston-rod in piston
- F01L11/04—Valve arrangements in working piston or piston-rod in piston operated by movement of connecting-rod
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
- F02B25/26—Multi-cylinder engines other than those provided for in, or of interest apart from, groups F02B25/02 - F02B25/24
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
- F02B33/04—Engines with reciprocating-piston pumps; Engines with crankcase pumps with simple crankcase pumps, i.e. with the rear face of a non-stepped working piston acting as sole pumping member in co-operation with the crankcase
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
Abstract
The invention relates to a cylinder assembly 1 for a longitudinally flushed stroke piston combustion engine and especially to a large-size two-stroke diesel generator moving slowing and flushing longitudinally. The cylinder assembly 1 includes an air cylinder provided with a combustion room 200 and an entrance area 22. A piston 3 moving back and forward long a cylinder axis Z is installed between an upper dead point and a lower dead point in the cylinder 2. And a flushing air entrance 4 is arranged in the cylinder 2 to facilitate to lead the flushing air 4 into the combustion room 200. The cylinder arrangement comprises a piston (3) which is provided as two piece piston. A mantle piston (32) is provided with a piston ring (33), where a main piston (31) is positioned in the mantle piston. A retaining device is provided at a cylinder for the mantle piston. The rinsing air (41) is introduced from an inlet area (22) to a combustion chamber (200) by the rinsing air opening (320) of the mantle piston.
Description
Technical field
The present invention relates to a kind of cylinder unit and piston that is used for longitudinally scavenged stroke piston combustion engine, in particular for cylinder unit and piston according to the longitudinally scavenged large-scale two-stroke diesel engine of the slow operation of independent claims preamble.
Background technique
Large-sized diesel motor often is used as ship or also has the drive unit in the Fixed Point Operation, for example, is used for the high-rating generator of driving and generating electric energy.Usually with continuous operation modes running considerable time section, this Security and usability to operation has proposed very high requirement to motor in this regard.For this reason, for the operator, especially long service cycle, little wearing and tearing and the economic utilization of fuel and operative material are the central tenets of operating machines.In other item; This heavy caliber slowly piston run action of the DENG of operation is a deciding factor for long service cycle, usability, and via the consumption of lubricant oil directly for running cost and all be deciding factor for economic benefit therefore.Therefore the challenge of piston run action has higher significance forever for large-sized diesel motor.
Yet; For large-sized diesel motor; Be not limited only to these; Also carry out piston lubrication through the lubrication unit that is arranged as in piston or in cylinder wall, move around, lubricant oil is applied to through this unit on the operation surface of cylinder wall, to reduce the friction between piston and the operation surface and therefore to reduce to move surface and wear of piston-rings.For example; For example for the two-cycle engine of
, the wearing and tearing on the operation surface of 1000 hour operation period are less than 0.05mm for current modern engine.The oiling agent delivery volume of this motor and is not only for the purpose of cost and should be reduced delivery volume as much as possible significantly below 1.3g/kWh, and wherein wearing and tearing should be minimized simultaneously.
Aspect this, with regard to the concrete design of lubrication unit self and lubricated method, many different solutions are considered to be used for the lubrication system of cylinder operation surface lubrication.In various modification, corresponding solution is known for the person of ordinary skill of the art.
Yet, be used to improve lubricated all measures and all leave one because an open question still that structure causes, and therefore be not always the case for all known so far longitudinally scavenged internal-combustion engines with the piston run action.Like what those of ordinary skill in the art knew; Near piston is arranged in its lower dead centre and when discharging the path of the combustion space make fresh air enter into cylinder; Fresh air (also often being called scavenging air) usually at the lower end of cylinder via the scavenging air opening that is the scavenging form of slits usually, be introduced in the combustion space of the cylinder that is used for the longitudinally scavenged two-stroke motor.
Fresh air is through the scavenging slit; For example; Utilize turbosupercharger and be injected in the cylinder with predetermined pressure; Because the scavenging slit be arranged in cylinder cylinder wall opening and therefore disturb lubricant film, be formed uniformly lubricant film so can not be at the internal surface of cylinder usually in the zone of scavenging slit.In this; Even be starkly lower than and far above scavenging slit place (this means even in the outside of the cylinder part that is formed with the scavenging slit), all produced the negative effect that the scavenging slit causes for the formation of lubricant film significantly in the operation surface of cylinder.This means that the interference that lubricant film is flowed that is brought by the scavenging slit in cylinder operation surface continues in the zone away from the scavenging slit; Therefore and influence the run action of piston, and lubricated away between the respective pistons ring of the piston of scavenging slit and the cylinder wall in negative effect significantly.
Another negative effect of scavenging slit is to be caused with cooperating of piston ring by near scavenging slit when piston ring passes through the scavenging slit at the volley lower dead centre.Because piston ring must have certain mechanical radius preparatory tensioning so that they can more or less cooperate with cylinder wall hermetically; Therefore piston ring is not formed complete closed ring, but forms the trip ring with breach so that produce the tension force that piston ring packing ground is pointed to by the radially outward that is pressed in the cylinder wall place.Under disadvantageous condition; Because the tension force of the radially outward effect of piston ring; Piston ring can partly be pressed in the scavenging slit at the edge of indentation, there; Thereby these piston rings can be caught in the lower edge of scavenging slit, and this causes near cylinder wall is in the scavenging slit, forming dangerous scraping or groove mark.Under the worst situation, this can cause stuck piston and cause cylinder and/or the damage of piston, for the ship that is in the off-lying sea, can cause dangerous situation especially.
The lubricants capacity of can not ignore in addition, is owing to the process of piston-ring packing is lost via the scavenging slit.A certain amount of lubricant oil promptly is stored in the lubricant oil in the piston-ring packing; These lubricant oil are collected in the piston-ring packing at piston in cylinder between moving period; And bear air pressure, and be stored in this in the increase that in piston-ring packing, basically forms during the combustion process.When piston-ring packing passes through the scavenging slit then; The over pressure that is stored in the piston-ring packing suddenly receives the space and/or is discharged in the piston subspace self being discharged into via the scavenging slit, thereby the largest portion that side by side will be stored in the lubricant oil in the piston-ring packing equally is sent to via the scavenging slit and receives in the space.On the one hand, this causes the loss of relatively costly lubricant oil, and in yet another aspect, causes receiving the unnecessary pollution in space.In addition, lubricant oil is no longer available for the further motion of piston.
Another shortcoming is the fixed geometry of scavenging slit.This is for as can be especially unfavorable possible the purposes of " double fuel " motor, that is, and and for as can be with different fuel for example selectively with the perhaps motor operated of other different fuels of heavy oil or coal gas.And particularly the geometrical shape that can not change of scavenging slit and/or size are still keeping the mode of above-mentioned use up to now.
Summary of the invention
Thus; The purpose of this invention is to provide a kind of novel cylinder unit and piston that is used for longitudinally scavenged stroke piston combustion engine; Be used for the slowly large-scale two-stroke diesel engine of operation especially; This has been avoided problem well known in the prior art, and this is to be determined by the scavenging slit in the lower area of known cylinder unit especially to a great extent.
The theme of the present invention that satisfies this purpose is characterised in that the characteristic of independent claims 1 and independent claims 9.
Dependent claims relates to concrete favourable mode of execution of the present invention.
Therefore; The present invention relates to a kind of cylinder unit that is used for longitudinally scavenged stroke piston combustion engine; Cylinder unit in particular for a kind of longitudinally scavenged large-scale two-stroke diesel engine of slow operation comprises the cylinder with combustion space and entrance region, in this cylinder, piston is installed; Can along cylinder axis between upper dead center and lower dead centre, move around and, wherein be provided with scavenging air inlet so that scavenging air is incorporated in the combustion space at the cylinder place.According to the present invention, piston is two-part formula piston, and this two-part formula piston comprises cylinder sleeve piston with piston ring and the main piston that is arranged in the cylinder sleeve piston.Aspect this; The keeping unit that is used for the cylinder sleeve piston is set at the cylinder place; Promote from said main piston with respect to cylinder axis so that said cylinder sleeve piston can be held the unit at the lower dead centre annex, make scavenging air to be introduced in the combustion space from the scavenging air opening of entrance region through the cylinder sleeve piston.
Because piston according to the present invention is two-part formula piston; This two-part formula piston comprises outside cylinder sleeve piston and is positioned at main piston wherein; And be provided with the keeping unit that is used for said cylinder sleeve piston so that said cylinder sleeve piston can be raised through keeping unit with respect to cylinder axis from main piston in the zone of lower dead centre at the lower end of cylinder; Thereby scavenging air can be introduced in the combustion space from the scavenging air opening of entrance region through the cylinder sleeve piston; Cylinder sleeve piston and/or be arranged in the piston ring at piston-cylinder place; Therefore and piston no longer in its motion, near lower dead centre, directly contact as a whole with the scavenging air opening, particularly no longer directly contact, so that people also can ignore the scavenging air slit fully with the scavenging slit.
This means that in technological scheme according to the present invention the effect of releasing of scavenging slit is replaced by the motion of two-part formula piston in the lower zone of lower dead centre.But why this be the cylinder sleeve piston in cylinder after combustion process is accomplished along in the direction of lower dead centre is moved preferably damping ground be arranged on the keeping unit with supporting, this keeping unit is arranged in cylinder and moves the lining place and/or be integrated in wherein in the lower zone of cylinder.Because main piston is fixedly attached to bent axle effectively via piston rod; Keep through keeping unit and when the cylinder sleeve piston remains on this position at the cylinder sleeve piston; Main piston is moved further up to main piston along the direction to its lower dead centre and returns along the direction to upper dead center from its lower dead point position again, and is being with the cylinder sleeve piston again for this reason.
By this way; The piston ring that is arranged in the piston-ring packing at cylinder sleeve piston place always remains in the closing section of cylinder operation lining of cylinder, so that can not be included in lubricant oil in the piston-ring packing more for example through scavenging slit release or the release downside of piston.
In cylinder unit according to the present invention; Since piston-cylinder and therefore piston-ring packing directly with the lower zone of cylinder in suction port cooperate; Therefore produced different advantages, wherein fresh air for example can be injected into the cylinder with predetermined pressure from turbosupercharger through said suction port.
Can know in the prior art, mean that in the scavenging closing course piston top suffers mist of oil when piston top closure scavenging slit.This mist of oil is produced by the cylinder oil that for example is blown in advance the piston underside along the pressure that when being directed downwards of lower dead centre moved, discharges through the ring member from piston ring at piston.Aforementioned mist of oil is stable with sedimental form then, burning and coking and form the oil coke charcoal on piston top, and this causes known " linear planarization (liner polishing) " to destroy and under the worst situation, also can cause blocking.For two-part formula piston according to the present invention, because the periphery surface of cylinder sleeve piston no longer directly contacts scavenging air, piston top can not suffer the aforementioned mist of oil in the scavenging air.Therefore, when using, can avoid reducing at least in large quantities damage oil coke carbon deposit thing reliably at place, piston top according to two-part formula piston of the present invention.
Further advantage is; For cylinder unit according to the present invention; The cylinder sleeve piston and therefore piston-ring packing no longer directly with the lower zone of cylinder in suction port cooperate; Wherein fresh air for example is introduced in the cylinder through this suction port with predetermined pressure from turbosupercharger, thereby can form lubricant film fully uniformly at the internal surface of cylinder.Lubricant film can be formed uniformly up to the lower end of cylinder on whole operations surface of cylinder fully, and keeping unit is positioned at the lower end of cylinder.
Therefore, because lubricant film no longer is formed in the suction port zone, but only till the keeping unit, so no longer disturbed by suction port at the lubricant film at cylinder wall place.Got rid of the negative effect of suction port thus, that is, for example through the scavenging slit for the film formed negative effect of lubricant oil.
Therefore, also got rid of suction port and cooperated with the damage of piston ring because these piston rings no longer that kind directly cooperate with suction port.Therefore; Can be not again on the border of the indentation, there of piston ring yet owing to the radially outer working tension of piston ring is pressed against in the suction port; And therefore; Also can be not again be hunted down, thereby through according to cylinder unit of the present invention, scraping or groove mark no longer are damaged at cylinder and/or cylinder wall place at the boundary of scavenging slit.
And because piston-ring packing no longer directly contacts with suction port, so there is not lubricant oil to lose via the scavenging slit, thus lubricant oil remains in the piston-ring packing and further can be used for lubricating.Thus, last, can save a large amount of lubricant oil, lubricated between piston and the cylinder greatly improves, and especially near the lower zone of the cylinder lower dead centre, and vessel space no longer receives the pollution from the lubricant oil of piston-ring packing.
One preferred embodiment in, damper element is set at keeping unit place and/or at cylinder sleeve piston place, receives so that the cylinder sleeve piston is held damping ground, unit.Under serviceability; Piston is along the direction high-speed mobile towards its lower dead centre; Thereby in most of the cases must damper element be set so that the cylinder sleeve piston can too suddenly not slow down through keeping unit, this may cause the badly damaged of piston and cylinder place.
In this regard, the possibility that setting device is set is provided first, thereby the open cross-section of this scavenging air opening can be set according to device of the present invention.That is, be the open cross-section of scavenging air opening or even can set according to another advantage of two-part formula piston of the present invention with changing.Under open mode, for the geometrical shape of given piston, the open cross-section part promptly generally forms through the distance between cylinder sleeve piston and the main piston.
In this regard; This distance also can receive following influence: for example keeping unit changes to the distance of the lower dead centre of piston; Perhaps, for example owing to setting device for example is set at the position of rest change that makes the cylinder sleeve piston between keeping unit and the cylinder sleeve piston with the form of spacer element.For given crank angle, keeping unit and distance cylinder sleeve piston between selected through setting device are big more, and the open cross-section that then is used for the scavenging air between main piston and the cylinder sleeve piston is big more.When keeping unit is selected as when bigger to the distance of lower dead centre, said circumstances is set up naturally.
Aspect this, setting device for example can be hydraulic pressure setting device, pneumatic setting device or electric setting device, and except other aspects, wherein setting device can be set at keeping unit and/or cylinder sleeve piston place.Especially, for example, damper element also can additionally correspondingly be designed to setting device.This means that setting device for example can set the axial position of keeping unit in cylinder.For this purpose, keeping unit for example can be set to be formed on the ring of cylinder internal, and this ring is displaceable through setting device along cylinder axis.Perhaps in different instances, setting device can be the spacer element between cylinder sleeve piston and the keeping unit that is arranged on that the height cocoa changes the ground setting.
Through setting the possibility of the open cross-section that is used for scavenging air with changing; Promptly dispose the possibility of scavenging process neatly; For example for certain load area such as partial load for example zone, motor can be simply through change between main piston and the cylinder sleeve piston open cross-section and simply and optimised very neatly.
In addition; The motor that has according to cylinder unit of the present invention also can be used as " double fuel " motor first; It can can set in the scope of non-constant width like the present amount that in scavenging process, is introduced in the scavenging air in the combustion space with the different fuel operation such as coal gas, heavy oil, diesel oil or other alternative fuel first with changing.
Aspect this, be set in cylinder the discharge orifice advantageous particularly and sentence the exchange of being convenient to lubricant oil.Through discharge orifice, for example, lubricant oil can be from the inside of cylinder to the outside table from cylinder wear away, and also can be processed or be directed into the position of reusing.Alternatively, can also lubricant oil be incorporated in the cylinder via above-mentioned discharge orifice.
Centralising device especially preferably is arranged on main piston and/or cylinder sleeve piston and sentences just main piston with respect to the cylinder sleeve piston pair, thereby in one aspect, main piston can be incorporated in the cylinder sleeve piston with the mode of being close to times without number.And in yet another aspect; Under the assembled state of piston; Main piston and cylinder sleeve piston can cooperate with the mode of being close to usually, so that the combustion space is beginning during scavenging period with respect to the piston subspace and by sealing safely during the compression stage, during the combustion phase and during the expansionary phase.
Aspect this; Centralising device for example can be to be positioned at the inside of cylinder sleeve piston and/or to be positioned at the guide bushing of the outer surface of main piston with the known mode of those of ordinary skill in the art, and perhaps it can also particularly preferably be the cone shape of main piston and/or cylinder sleeve piston.If begin from lower dead centre; Piston is along beginning now towards moving upward of upper dead center; Main piston is himself centering automatically in the cylinder sleeve piston so, and seals the scavenging air slit of cylinder sleeve piston thus, thereby piston can continue its normal function as working piston once more.
The invention still further relates to the piston of the longitudinally scavenged large-scale two-stroke diesel engine that a kind of longitudinally scavenged stroke piston combustion engine that is used to have according to cylinder unit of the present invention especially slowly moves.In this, piston of the present invention can be installed in the cylinder of cylinder unit, can between upper dead center and lower dead centre, move back and forth along cylinder axis.According to the present invention; Piston is two-part formula piston; This two-part formula piston comprises the cylinder sleeve piston with piston ring and can be positioned at the main piston in the cylinder sleeve piston; Thereby under installment state, the cylinder sleeve piston can be held the unit and promote from main piston with respect to cylinder axis near lower dead centre.
Aspect this, damper element especially preferably is arranged on cylinder sleeve piston place.
Through with the down special setting device that is provided with of interior configuration state, the open cross-section of the scavenging slit of cylinder sleeve piston can be set, wherein preferably hydraulic pressure, pneumatic or electric setting device of setting device.This setting device can be arranged on cylinder sleeve piston place and damper element self forms setting device especially especially.
Particularly preferably, centralising device is arranged on main piston and/or cylinder sleeve piston place, is used for making main piston cylinder sleeve piston centering, and wherein centralising device for example can be a guide bushing, or the conical form of main piston or cylinder sleeve piston.
Description of drawings
To describe the present invention in detail with reference to schematic representation below.Shown in the drawings:
Fig. 1 is the longitudinal sectional drawing with known cylinder unit of scavenging slit;
Fig. 2 a is under the closed state schematic representation according to first cylinder unit of the present invention at piston;
Fig. 2 b is the cylinder unit that is in open mode figure below 2a at piston;
Fig. 3 is second mode of execution that has the cylinder unit of discharge orifice and setting device according to of the present invention;
Fig. 4 a is an embodiment according to piston of the present invention;
Fig. 4 b is the embodiment's of Fig. 4 a a stereogram;
Fig. 4 c is the view according to the inside of the cylinder sleeve piston of Fig. 4 a and/or Fig. 4 b.
Embodiment
Fig. 1 show have cylinder sleeve 2 ', the schematic representation of the partly cut-away of the cylinder unit 1 ' of piston 3 ' and supply system of fresh air 400 '.
For longitudinally scavenged large-scale two-stroke diesel engine, the cylinder unit 1 ' of Fig. 1 is like the known typical devices of existing technology.In order to distinguish better with known cylinder unit, corresponding reference character all provides single quotation marks, and the reference character that belongs to according to the characteristic of cylinder unit of the present invention does not have single quotation marks.
This device comprises cylinder 2 ', and it also is known as cylinder sleeve 2 ', and wherein piston 3 ' is arranged as movably along the cylinder wall of cylinder 2 ' and moves around.Piston 3 ' comprises piston-ring packing 33 ', only schematically shows this piston-ring packing with two piston rings in this example.
According to view, the firing chamber 200 ' that is present in the combustion space zone 21 ' of cylinder 2 ' is defined through the cylinder head with nozzle and outlet valve at the top.
Piston 3 ' between upper dead center OT ' and lower dead centre UT ', moving back and forth under the serviceability of large-sized diesel motor is connected to unshowned crosshead via piston rod 8 ', piston 3 ' move back and forth the bent axle that is sent to the machine that also is not illustrated via this piston rod 8 '.Piston rod 8 ' is conducted through holding space 401 '; This holding space is located according to view is connected cylinder sleeve 2 ' in the bottom entrance region 22 '; And piston rod is through the filling block 402 ' in seal container space 401 ' is directed with respect to being positioned at following crankshaft space; Therefore not the fresh air 41 ' by arrow 41 ' expression can arrive the crankshaft space 9 ' that not be arranged in the vessel space below from vessel space 401 ', this fresh air also can through unshowned turbosupercharger with 4 pressure feeds that cling to for example in vessel space 401 '.
As visible among Fig. 1 and known usually, the gas pressure of fresh air 41 ' is present in the vessel space 401 ' usually, for this vessel space of reason of constructing therefore always at the piston underside of piston 3 '.
After the combustion process that in combustion space 200 ', begins; When piston 3 ' is positioned at very near near the upper dead center OT ' time; Because the firing pressure that in combustion space 200 ', forms; Piston 3 ' moves along the direction towards lower dead centre UT ', wherein, and when piston face appears at the below of the scavenging air opening 4 ' with scavenging slit 221 '; Scavenging air 41 ' can arrive the combustion space 4 ' from vessel space 401 ' via scavenging slit 4 ', thereby this scavenging air 41 ' can be used for ensuing follow-up combustion process in the combustion space 200 '.
From upper dead center OT ' to lower dead centre UT ' and on the path of returning, piston must have negative effect as in foreword, having described this, so need not to repeat once more at this separately therefore through the scavenging slit 4 ' in the entrance region 22 ' at it.
In Fig. 2 a, schematically show in a simplified manner in the situation of longitudinally scavenged large-scale two-stroke diesel engine according to first cylinder unit of the present invention.The cylinder unit 1 of Fig. 2 a shows the piston that is in closed state.For the sake of clarity, in Fig. 2 a to Fig. 3, be not shown clearly in not crucial parts for understanding large-sized diesel motor of the present invention.
The cylinder unit 1 of Fig. 2 a comprises cylinder 2, and cylinder 2 has combustion space 200 and entrance region 22, can be introduced in the cylinder through the entrance region scavenging air.In this, the entrance region 22 of large-sized diesel motor and/or remaining part can be designed in principle from existing technology known and as described in Fig. 1.
According to the present invention, piston 3 is two-part formula pistons 3, and this two-part formula piston has piston-ring packing 33 and can be positioned on the main piston 31 in the cylinder sleeve piston 32.The keeping unit 5 that is used for cylinder sleeve piston 32 is arranged on cylinder 2 places; So that being held unit 5 near lower dead centre UT, cylinder sleeve piston 32 promotes from main piston 31 with respect to cylinder axis Z; Thereby; Shown in Fig. 2 b, scavenging air 41 can be incorporated into the combustion space 200 from entrance region 22 by the scavenging air opening 320 through cylinder sleeve piston 32.
The introducing of scavenging air 41 via the scavenging air opening 320 of cylinder sleeve piston 32 has been shown in Fig. 2 b, Fig. 2 b show piston 3 be under the open mode according to cylinder unit 1 of the present invention.
In Fig. 2 b, main piston 31 only moves near lower dead centre UT and opened in 32 minutes from the cylinder sleeve piston thus, and cylinder sleeve piston 32 is landed in keeping unit 5 places, and keeping unit 5 is designed to the retaining ring in cylinder 2 inside.Because cylinder sleeve piston 32 is landed in keeping unit 5 places and main piston 31 separates from cylinder sleeve piston 32; Therefore the scavenging air opening 320 in the cylinder sleeve piston 32 is opened; Thereby formed open cross-section 111, can be via open cross-section 111 scavenging airs like arrow 41 indicated flowing in the combustion space 200.
With reference to Fig. 3, schematically shown at last for second mode of execution of realizing that cylinder unit 1 speech with damper element 10 according to the present invention is correlated with especially, wherein damper element 10 is designed to be the setting device 11 of spacer element form.
In this example; Setting device 11 and/or damper element 10 are hydraulic element; These hydraulic element can be via unshowned hydraulic pipe line can predetermined pressure to stand the hydraulic oil of prearranging quatity; Wherein, in yet another aspect, cylinder sleeve piston 32 damping force during by damping on being set to keeping unit 5 can be set.In yet another aspect, simultaneously or alternatively, the distance between keeping unit 5 and the cylinder sleeve piston 32 can be set, thereby open cross-section 111 and in combustion space 200 supply scavenging air 41 can be complementary with operational condition neatly respectively.
The property set flexibly through the scavenging air supply; Large-scale two-stroke diesel engine of the present invention also can be used as " double fuel " motor first; Can in the scope of non-constant width, can set first owing in scavenging process, be incorporated into the amount of the scavenging air 41 in the combustion space 200 now with changing, be somebody's turn to do " double fuel " motor ability quilt with optional different fuel operation such as coal gas, heavy oil, diesel oil or other fuel.
In addition, in the mode of execution according to Fig. 3, the discharge orifice 12 that is used for the lubricant oil exchange is arranged on cylinder 2 places.Through discharge orifice 12, for example, the lubricant oil surperficial from the operation of cylinder 2 can discharge from the inside of cylinder 2, and can be processed or be directed into reusable position.Alternatively, can also lubricant oil be incorporated in the cylinder 2 via above-mentioned discharge orifice 12.
In addition; According to Fig. 2 a to Fig. 4 c; Be used to make main piston 31 to be arranged on main piston 31 and cylinder sleeve piston 32 places with respect to the centralising device 13 of cylinder sleeve piston 32 centerings; Thereby in yet another aspect, main piston 31 can be incorporated in the cylinder sleeve piston 32 with the mode of being close to (form-fitting) again and again.And; In yet another aspect; Under the assembled state of piston 3; Main piston 31 matches with the mode of being close to cylinder sleeve piston 32 usually, so that combustion space 200 seals with respect to the piston subspace up between the elementary period of scavenging period in compression stage, combustion phase and expansion stage with regard to most of safely.
In this context, centralising device 13 only is set to be as the conical configuration of main piston 31 and at cylinder sleeve piston 32 places in the outer surface of main piston 31 form on corresponding inverted cone surface through the mode of instance.So; If being directed to from lower dead centre UT, the piston that under serviceability, moves upward towards upper dead center begins; Then main piston 31 makes himself centering and close the scavenging air opening 320 of cylinder sleeve piston 32 thus automatically in cylinder sleeve piston 32, thereby piston 3 can continue its normal function as working piston again.
With reference to Fig. 4 a; Schematically shown according to another embodiment of the present invention; Wherein in order to understand Fig. 4 b better, the instance of Fig. 4 a illustrates with corresponding view once more, and in Fig. 4 c, can see the more detailed diagram according to the inside of the cylinder sleeve piston 32 of Fig. 4 a and/or Fig. 4 b.
In addition; In mode of execution according to Fig. 4 a to Fig. 4 c; Be used to make main piston 31 to be arranged on main piston 31 and cylinder sleeve piston 32 places with respect to the centralising device of cylinder sleeve piston 32 centerings; Thereby in yet another aspect, main piston 31 can be incorporated in the cylinder sleeve piston 32 usually closely equally in this example.And; In yet another aspect; Under the assembled state of piston 3, main piston 31 cooperates with the mode of being close to cylinder sleeve piston 32 usually, so that the combustion space seals with respect to the piston subspace up between the elementary period of scavenging period in compression stage, combustion phase and expansion stage safely.
In this example, centralising device 13 is set in the outer surface of main piston 31 as the conical configuration of main piston 31 and be the form of the corresponding anti-conical surface of cylinder sleeve piston 32.
In addition, main piston 31 has the first safe antirotation element 1301, has a plurality of first safe antirotation element 1301 in this example and at the second safe antirotation element 1302 of the inner respective numbers of cylinder sleeve piston 32.In this; The first safe antirotation element 1301 and the second safe antirotation element 1302 cooperatively interact under the assembled state of piston 3; So that between elementary period, prevented the rotation of cylinder sleeve piston 32 up to scavenging period safely in compression stage, combustion phase and expansion stage at least against main piston 31.
In addition; Damper element 10 also is arranged on the first safe antirotation element, 1301 places respectively; Damper element is designed to setting device 11; Wherein setting device 11 also can be suitable hydraulic pressure, pneumatic or electric setting device 11 and/or damper element 10, and it can be the spring element that only has displaceable resilient path especially.
Naturally be understood that the mode of execution through case description in the framework of this application only is in order to understand, still to the invention is not restricted to these instances.Especially, said mode of execution can also be by advantageously combination.
Claims (15)
1. cylinder unit that is used for longitudinally scavenged stroke piston combustion engine; Cylinder unit in particular for a kind of longitudinally scavenged large-scale two-stroke diesel engine of slow operation; Said cylinder unit comprises the cylinder (2) of have the combustion space (200) and entrance region (22); The piston (3) that can between upper dead center and lower dead centre (UT), move around along cylinder axis (Z) is installed in said cylinder (2); And wherein locate to be provided with scavenging air inlet (4) so that scavenging air (41) is incorporated in the said combustion space (200) at said cylinder (2); Said cylinder unit is characterised in that: said piston (3) is two-part formula piston (3), and said two-part formula piston (3) comprises the have piston ring cylinder sleeve piston (32) of (33) and the main piston (31) that is arranged in said cylinder sleeve piston (32); And the keeping unit (5) that is used for said cylinder sleeve piston (32) is arranged on said cylinder (2) and locates; Make said cylinder sleeve piston (32) near said lower dead centre (UT), to be promoted from said main piston (31) with respect to said cylinder axis (Z), make said scavenging air (41) to be introduced in the said combustion space (200) from the scavenging air opening (320) of said entrance region (22) through said cylinder sleeve piston (32) by said keeping unit (5).
2. cylinder unit according to claim 1 is wherein located and/or is located to be provided with damper element (10) at said cylinder sleeve piston (32) at said keeping unit (5).
3. cylinder unit according to claim 1 and 2 wherein is provided with setting device (11) so that the open cross-section (111) of said scavenging air opening (320) can be set.
4. cylinder unit according to claim 3, wherein said setting device (11) are hydraulic pressure, pneumatic or electric setting device (11).
5. according to claim 3 or 4 described cylinder units, wherein said setting device (11) is arranged on said keeping unit (5) and locates and/or be arranged on said cylinder sleeve piston (32) and locate, and wherein said damper element (10) forms setting device (11) especially.
6. according to each described cylinder unit in the aforementioned claim, wherein locate to be provided with the exchange that discharge orifice (12) is used for lubricant oil at said cylinder (2).
7. according to each described cylinder unit in the aforementioned claim, wherein locate and/or locate to be provided with centralising device (13), so that said main piston (31) is with respect to said cylinder sleeve piston (32) centering at said cylinder sleeve piston (32) at said main piston (31).
8. cylinder unit according to claim 7, wherein said centralising device (13) are the taper form of guide bushing or said main piston (31) or the taper form of said cylinder sleeve piston (32).
9. the piston of the longitudinally scavenged large-scale two-stroke diesel engine that especially slowly moves of a longitudinally scavenged stroke piston combustion engine that is used for having according to each described cylinder unit (1) of aforementioned claim; Said piston can be installed in the cylinder (2) of said cylinder unit (1); And can between upper dead center and lower dead centre (UT), move around along cylinder axis (Z); It is characterized in that; Said piston (3) is two-part formula piston (3); Said two-part formula piston (3) comprise have piston ring (33) cylinder sleeve piston (32) and can be positioned at the main piston (31) in the said cylinder sleeve piston (32), thereby under installment state, said cylinder sleeve piston (32) can be held unit (5) and promote from said main piston (31) with respect to said cylinder axis (Z) near said lower dead centre (UT).
10. piston according to claim 9 wherein locates to be provided with damper element (10) at said cylinder sleeve piston (32).
11. according to claim 9 or 10 described pistons, wherein be provided with setting device (11) so that under said installment state the open cross-section (111) of the scavenging air opening (320) of said cylinder sleeve piston (32) can set.
12. piston according to claim 11, wherein said setting device (11) are hydraulic pressure, pneumatic or electric setting device (11).
13. according to claim 11 or 12 described pistons, wherein said setting device (11) is arranged on said cylinder sleeve piston (32) and locates, and wherein said damper element (10) forms setting device (11) especially.
14., wherein locate and/or locate to be provided with centralising device (13), so that said main piston (31) centering in said cylinder sleeve piston (32) at said cylinder sleeve piston (32) at said main piston (31) according to each described piston in the claim 9 to 13.
15. piston according to claim 14, wherein said centralising device (13) are the taper form of guide bushing or said main piston (31) or the taper form of said cylinder sleeve piston (32).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP11159456.0 | 2011-03-23 | ||
| EP11159456 | 2011-03-23 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102691565A true CN102691565A (en) | 2012-09-26 |
Family
ID=45655411
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012100277335A Pending CN102691565A (en) | 2011-03-23 | 2012-02-08 | Cylinder assembly and piston for a longitudinally flushed stroke piston combustion engine |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2503116A1 (en) |
| JP (1) | JP2012202403A (en) |
| KR (1) | KR20120108911A (en) |
| CN (1) | CN102691565A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106014626A (en) * | 2016-07-12 | 2016-10-12 | 魏伯卿 | Multistage sleeve cylinder change device of variable cylinder engine |
| CN112780437A (en) * | 2021-01-19 | 2021-05-11 | 山东交通学院 | Novel cross head type two-stroke direct-current scavenging piston device |
| CN112780438A (en) * | 2021-01-19 | 2021-05-11 | 山东交通学院 | Novel crosshead type two-stroke direct-flow scavenging piston assembly |
| CN112792566A (en) * | 2021-01-19 | 2021-05-14 | 山东交通学院 | Assembling method of novel crosshead type two-stroke direct-current scavenging piston device |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2711530A1 (en) | 2012-09-21 | 2014-03-26 | Wärtsilä Schweiz AG | Piston and cylinder assembly for a longitudinally flushed reciprocating piston combustion engine |
| FR2998007B1 (en) * | 2012-11-09 | 2014-11-14 | Bryan Laumonier | INTEGRATED VALVE PISTON |
| CN204647278U (en) * | 2015-03-17 | 2015-09-16 | 尹建 | The built-in chain type connecting rod of reciprocating piston is without dead point engine piston connecting rod group |
| EP4166766A1 (en) * | 2021-10-15 | 2023-04-19 | Winterthur Gas & Diesel AG | Longitudinally flushed large-scale diesel engine |
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| US1580720A (en) * | 1922-07-31 | 1926-04-13 | John K Gold | Two-cycle engine |
| DE19904004C1 (en) * | 1999-02-02 | 2000-04-20 | Udo Wagener | Two stroke internal combustion engine has pistons with inlet valves mounted in piston crowns |
| WO2004067929A1 (en) * | 2003-01-27 | 2004-08-12 | Tihomir Sic | Two stroke engine with valve distribution system |
| WO2005075801A1 (en) * | 2004-02-10 | 2005-08-18 | Stefan Kanozsay | Highly efficient two-stroke piston combustion engine working without vibrations |
| CN101636560A (en) * | 2007-03-08 | 2010-01-27 | 瓦特西拉芬兰有限公司 | Improved two-stroke engine |
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| JPS577761Y2 (en) * | 1977-03-02 | 1982-02-15 | ||
| JPS63126520U (en) * | 1987-02-10 | 1988-08-18 | ||
| JP2501268B2 (en) * | 1992-04-02 | 1996-05-29 | 株式会社ディーゼルユナイテッド | 2-cycle internal combustion engine |
| US7194989B2 (en) * | 2005-03-03 | 2007-03-27 | Samuel Raymond Hallenbeck | Energy efficient clean burning two-stroke internal combustion engine |
-
2011
- 2011-11-30 JP JP2011261945A patent/JP2012202403A/en not_active Ceased
- 2011-12-28 KR KR1020110144852A patent/KR20120108911A/en not_active Application Discontinuation
-
2012
- 2012-02-07 EP EP12154274A patent/EP2503116A1/en not_active Withdrawn
- 2012-02-08 CN CN2012100277335A patent/CN102691565A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1580720A (en) * | 1922-07-31 | 1926-04-13 | John K Gold | Two-cycle engine |
| DE19904004C1 (en) * | 1999-02-02 | 2000-04-20 | Udo Wagener | Two stroke internal combustion engine has pistons with inlet valves mounted in piston crowns |
| WO2004067929A1 (en) * | 2003-01-27 | 2004-08-12 | Tihomir Sic | Two stroke engine with valve distribution system |
| WO2005075801A1 (en) * | 2004-02-10 | 2005-08-18 | Stefan Kanozsay | Highly efficient two-stroke piston combustion engine working without vibrations |
| CN101636560A (en) * | 2007-03-08 | 2010-01-27 | 瓦特西拉芬兰有限公司 | Improved two-stroke engine |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106014626A (en) * | 2016-07-12 | 2016-10-12 | 魏伯卿 | Multistage sleeve cylinder change device of variable cylinder engine |
| CN112780437A (en) * | 2021-01-19 | 2021-05-11 | 山东交通学院 | Novel cross head type two-stroke direct-current scavenging piston device |
| CN112780438A (en) * | 2021-01-19 | 2021-05-11 | 山东交通学院 | Novel crosshead type two-stroke direct-flow scavenging piston assembly |
| CN112792566A (en) * | 2021-01-19 | 2021-05-14 | 山东交通学院 | Assembling method of novel crosshead type two-stroke direct-current scavenging piston device |
| CN112792566B (en) * | 2021-01-19 | 2022-02-18 | 山东交通学院 | Assembling method of novel crosshead type two-stroke direct-current scavenging piston device |
Also Published As
| Publication number | Publication date |
|---|---|
| KR20120108911A (en) | 2012-10-05 |
| JP2012202403A (en) | 2012-10-22 |
| EP2503116A1 (en) | 2012-09-26 |
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