EP2270318A1 - Agencement de cylindre pour un moteur à combustion à piston à balayage axial - Google Patents

Agencement de cylindre pour un moteur à combustion à piston à balayage axial Download PDF

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Publication number
EP2270318A1
EP2270318A1 EP09164318A EP09164318A EP2270318A1 EP 2270318 A1 EP2270318 A1 EP 2270318A1 EP 09164318 A EP09164318 A EP 09164318A EP 09164318 A EP09164318 A EP 09164318A EP 2270318 A1 EP2270318 A1 EP 2270318A1
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EP
European Patent Office
Prior art keywords
cylinder
piston
inlet
arrangement according
closing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP09164318A
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German (de)
English (en)
Inventor
Matthias Berchtold
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP09164318A priority Critical patent/EP2270318A1/fr
Publication of EP2270318A1 publication Critical patent/EP2270318A1/fr
Withdrawn legal-status Critical Current

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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
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F01L7/04—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves surrounding working cylinder or piston
    • 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
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/12—Rotary or oscillatory slide valve-gear or valve arrangements specially for two-stroke engines
    • 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

Definitions

  • the invention relates to a cylinder arrangement for a longitudinally purged reciprocating internal combustion engine, in particular for a slow-running longitudinally purged two-stroke large diesel engine according to the preamble of independent claim 1.
  • the piston lubrication is performed by lubricating means in the reciprocating piston or in the cylinder wall, is applied by the lubricating oil on the tread of the cylinder wall, the friction between the piston and the tread and thus the wear of the tread and to minimize the piston rings.
  • the wear of the tread at less than 0.05 mm with a service life of 1000 hours.
  • the lubricant delivery rate is about 1.3 g / kWh and less in such engines and should not least be further reduced for cost reasons as possible, while the wear is to be minimized.
  • a central point is always the difficulty of optimizing the lubricant film on the cylinder surface as locally as possible
  • the CH 613 495 discloses a cylinder apparatus for a reciprocating internal combustion engine, which detects abnormal friction conditions of the piston rings by means of a temperature or vibration sensor to prevent the seizure of piston rings during operation and when such disturbances occur, the amount of lubricating oil discharged from a particular lubrication point is increased.
  • the EP 0 652 426 shows a method in which by cyclically measuring the temperature in the cylinder wall, the occurrence of scuffing or Verschleissfressen is detected on the basis of a characteristic temperature profile and a corresponding damage by an automatic power reduction and / or by increasing the supply of lubricant is counteracted.
  • the lubricant quantity is increased for this cylinder until the detected abnormal operating state disappears again and the quantity of lubricant supplied to this cylinder per unit time again can be reduced.
  • the usually used cylinder liners are generally produced by a well-known casting method, whereby initially a cylinder liner blank is provided.
  • the casting material is suitably enriched with hard materials or the casting and cooling process is influenced in a conventional manner such that during casting and / or cooling of the cylinder liner blank in the cast base material more or less extensive areas of hard phases, the Example may include per se known carbides or other known hard phases, educate or excreted. These hard phases form a more or less irregular distribution or matrix in the cast base material, resulting in an advantageous combination of relatively soft cast base material and hard phases.
  • the relatively soft cast base material ensures, for example, among other things, a certain mechanical elasticity and fatigue strength of the cylinder liner, so that it can withstand the enormous temperature and pressure fluctuation loads in the operating state of the internal combustion engine.
  • the hard phases give the cylinder wall or the running surface of the cylinder a sufficiently high hardness, but not only, against excessive wear due to friction between the piston and the cylinder surface.
  • the different manufacturing processes of this type of cylinder liners and their properties are well known to those skilled in the art and therefore need not be further explained here.
  • An inner wall of the cylinder liner blank which will later form the running surface for the piston on the cylinder wall, is then usually processed in several complex steps.
  • a channel-like coarse structure is created with circumferential channels, which coarse structure extending helically along the cylinder axis in the cylinder wall of the cylinder liner.
  • the cylinder surface can be pre-honed and finish-honed and possibly subjected to a suitable finishing process, so that the tread receives a finer structure.
  • the scavenging ports through which the fresh air is blown, for example, from a turbocharger into the cylinder under a predetermined pressure, per se do not allow uniform formation of the lubricating oil film on the inner surface of the cylinder in the region of the scavenging slots, since the scavenging ports have openings in the cylinder wall of the cylinder and therefore interrupt the lubricating oil film.
  • the negative influence of the scavenging slots on the formation of the lubricating oil film on the running surface of the cylinder is even below and far above, so even outside the cylinder portion in which the scavenging slots are formed, clearly pronounced.
  • scavenging slots Another negative side effect of the scavenging slots results from their interaction with the piston rings as they pass through the scavenging slots as they move near bottom dead center. Since the piston rings must have a certain mechanical radial prestress so that they can cooperate more or less sealingly with the cylinder wall, these are not formed as completely closed rings, but the piston rings are rather formed as open rings with a gap, so that a radially to externally directed clamping force is created, which presses the piston ring sealingly against the cylinder wall.
  • the margins at the gap of the piston ring can be partially pressed into the flushing slots due to the radially outward acting tension of the piston ring, whereby they can get caught on the boundaries of the scavenging slots, resulting in dangerous scratches or grooves on the cylinder or on the cylinder wall near the scavenging slots. In the worst case, this can lead to a seizure and destruction of the cylinder and / or the piston, which can lead to dangerous situations especially in a ship on the high seas.
  • the object of the invention is therefore to provide a novel cylinder arrangement for a longitudinally-flushed reciprocating internal combustion engine, in particular for a slow-running two-stroke large diesel engine, which are known from the prior art problems, which are substantially determined in particular by the scavenging slots in the lower region of the known cylinder assembly , avoids.
  • the invention thus relates to a cylinder arrangement for a longitudinally-flushed reciprocating internal combustion engine, in particular for a slow-running longitudinally-flushed two-stroke large diesel engine, comprising a cylinder with a combustion chamber region and an inlet region.
  • a piston along a cylinder axis between a top dead center and a bottom dead center reciprocally installable, wherein on the cylinder a scavenging air inlet for introducing scavenging air is provided in the combustion chamber region.
  • a hollow closure element suitable for receiving the piston is provided in the inlet region of the cylinder so that it can be moved back and forth between the inlet position and a closing position such that the scavenging air inlet is open in the inlet position of the closure element and in the closing position of the closure element Closing element is closed.
  • a suitable for receiving the piston, hollow closure element is provided between an inlet position and a closing position such along the cylinder axis reciprocally disposed and movable that the scavenging air inlet in the inlet position of the closure element is open and in the Closing position of the closure element is closed, the piston is no longer in its movement in the vicinity of the bottom dead center with the scavenging air, in particular so with the scavenging slots in direct contact.
  • the piston always "sees” even during its movement near the bottom dead center a smooth cylinder wall or tread, since the piston is introduced in the vicinity of the bottom dead center in the hollow configured closure element, which in the circumferential direction an inner, closed and forms smooth surface without any radial openings.
  • the lubricating oil film can form completely uniformly from the upper part of the cylinder into the closure element.
  • the lubricating oil film on the cylinder wall is thus no longer interrupted by the air inlet openings, since the lubricating oil film in the region of the air inlet openings is no longer formed on the cylinder wall itself, but on the smooth inner peripheral surface of the closure element.
  • a negative influence of the air inlet openings e.g. a negative influence by the scavenging slots on the formation of the lubricating oil film is therefore excluded below and above the air inlet.
  • a further advantage of the cylinder arrangement according to the invention in a special exemplary embodiment is additionally that the purging air does not constantly bear against the underside of the piston, as is the case with the cylinder arrangements known from the prior art, provided a stuffing box is provided at the bottom of the closure element. through which the piston rod is sealingly passed through the bottom of the closure element.
  • the stuffing box on the closing element closes the underside of the cylinder outwards after introduction of the scavenging air into the combustion chamber, for example against the receiver space, which is supplied with purging air by a turbocharger.
  • a closing element is provided in such a way that the closing element can be displaced from the inlet position into the closing position by the closing element.
  • the closing element may be a compression spring element, preferably a mechanical compression spring element, e.g. be in the form of a compression spring, which may be formed in particular as a spiral spring.
  • compression spring element can also be a pneumatic or hydraulic pressure spring element, in particular an air pressure spring.
  • the closure element When using a compression spring element, the closure element is pushed by the piston in its movement in the direction of bottom dead center against a mechanical pressure of the compression spring element from the closed position to the inlet position, so that a scavenging air is released and scavenging air via a scavenging air into the combustion chamber of the Cylinder can get.
  • the piston continues its movement after passing through the bottom dead center in the direction of top dead center, the closure element is pushed back into the closed position by the compression spring element and the purging air opening is closed again by the closure element.
  • the closing element may also be a tension spring element, wherein the tension spring element may be, for example, a mechanical tension spring element, in particular a tension spring, or else a pneumatic or hydraulic tension spring element, in particular an air tension spring.
  • the closure element When using a tension spring element, the closure element is pushed by the piston in its movement in the direction of bottom dead center against a mechanical train of Switzerlandfederelements from the closed position to the inlet position, so that the scavenging air is released and scavenging air through the scavenging air in the combustion chamber of the Cylinder can get. If the piston continues its movement after passing through the bottom dead center in the direction of top dead center, the closure element is pulled back by the tension spring element in the closed position and the scavenging air opening closed by the closure element again.
  • the closing element can be an actively controlled closing element, in particular when the closing element is a pneumatic or hydraulic compression spring element or tension spring element.
  • a hydraulic or pneumatic piston that is to say a closing piston which can be acted upon by a fluid, is suitably in operative connection with the closing element and actively moves the closing element out of the closed position into the inlet position and / or actively out of the inlet position into the closing position.
  • the hydraulic or for example, pneumatic pistons may be connected to a hydraulic or pneumatic control device that appropriately applies a pneumatic or hydraulic fluid, such as air or oil, to the piston so that the pneumatic or hydraulic piston actively brings the closing element into a predeterminable position.
  • different sensors can be provided, for example position sensors for determining the position of the piston, so that the control device can optimally control the closing element in dependence on suitably selected operating parameters.
  • the cylinder with combustion chamber region and inlet region is designed in one piece, wherein the closure element is preferably provided in a cylindrical recess in the inlet region of the cylinder. It can optionally be formed by scavenging slots at the inlet area, which are covered in the closed position by the closure element, so that the piston or the piston ring package does not come into frictional contact with the scavenging slots in its movement towards bottom dead center, because the piston from the closing element taken up and enclosed in the circumferential direction .
  • a guide device for influencing a purge air flow of the purge air (41) may be provided at the inlet region of the cylinder, wherein the guide device may in particular be a controllable guide device, so that the purge air flow can be influenced as a function of a purge air parameter.
  • the scavenging air inlet into the cylinder can be optimized, wherein when using a controllable guide, for example by a suitable rotation of the baffles, preferably depending on certain operating parameters of the internal combustion engine, the scavenging air in the cylinder can be optimally controlled and / or regulated ,
  • Fig. 1 shows in a schematic representation partially in section a cylinder assembly 1 'with cylinder liner 2', piston 3 'and fresh air supply system 400'.
  • the cylinder assembly 1 'of Fig. 1 is a typical arrangement well known for prior art longitudinally scavenged two-stroke large diesel engines.
  • the corresponding reference numerals are provided with an apostrophe, while the reference numerals to features according to the invention cylinder arrangements wear no apostrophe.
  • the arrangement comprises a cylinder 2 ', which is also referred to as a cylinder liner 2', in which a piston 3 'along a cylinder wall of the cylinder 2' is arranged back and forth movable.
  • the piston 3 ' comprises a piston ring packing 31', which is shown here schematically with only two piston rings.
  • the combustion chamber 200 ' which is located in the combustion chamber region 21' of the cylinder 2 ', is delimited at the top by a cylinder cover with an injection nozzle and exhaust valve.
  • the piston 3 ' which reciprocates in the operating state of the large diesel engine between the top dead center OT' and the bottom dead center UT ', via the piston rod 8' with a in Fig. 1 not shown crosshead, from which the reciprocating movement of the piston 3 'is transmitted to the crankshaft, also not shown, of the machine.
  • the piston rod 8 ' is guided through the receiver space 401', which adjoins the inlet area 22 'of the cylinder liner 2' below, and the stuffing box 402 ', which seals the receiver space 401' against the crankshaft space below, so that no fresh air 41 ', symbolized by the arrow 41', which supplies a likewise not shown turbocharger under a high pressure, for example, under a pressure of four bar in the receiver chamber 401 ', from the receiver room 401' in the underlying crankshaft space 9 'can pass.
  • Fig. 1 can be seen and is generally known, is in the receiver chamber 401 'always generated by the turbocharger gas pressure of the fresh air 41', which thus always by design rests on the piston bottom of the piston 3 '.
  • Fig. 2a is a first inventive cylinder arrangement, which is hereinafter referred to in its entirety by the reference numeral 1, schematically shown with compression spring element 6, 61 and closure element 5 in the closed position S.
  • the arrangement comprises in a conventional manner a cylinder 2, which is also referred to as a cylinder liner 2, in particular in the case of two-stroke large diesel engines, in which a piston 3 along a cylinder wall of the cylinder 2 is arranged back and forth movable.
  • the piston 3 usually comprises a piston ring packing with a plurality of piston rings, which is not explicitly shown here for reasons of clarity.
  • the combustion chamber 200 which is located in the combustion chamber region 21 of the cylinder 2, is delimited at the top by a cylinder cover with an injection nozzle and an outlet valve.
  • the piston rod 8 is in ans known manner through the receiver chamber 401, which adjoins the bottom as shown in the inlet portion 22 of the cylinder liner 2, and the stuffing box 402 which seals the receiver chamber 401 against the underlying crankshaft space, so that no fresh air 41, symbolized by the arrow 41, which supplies a turbocharger also not shown under a high pressure, for example, under a pressure of four bar in the receiver chamber 401, from the receiver room 401 can get into the underlying crankshaft space 9.
  • Fig. 1 can also be found in the inventive cylinder assembly 1 in the receiver chamber 401 always the gas pressure of the fresh air 41 generated by the turbocharger, which thus in the example of Fig. 2a always applied to the piston bottom of the piston 3.
  • a hollow closure element 5 suitable for receiving the piston 3, which is arranged so as to be reciprocatable along an axis position Z between an inlet position E and a closing position S such that the scavenging air inlet 4 is in the inlet position E of the closure element 5 is open and is closed in the closed position S of the closure element 5.
  • the piston 3 is still in the combustion chamber region 21 of the cylinder 2 and has not yet reached the closure element 5 in the inlet region 22. Therefore, the closure element 5 is according to Fig. 2a even in the closed position S, in which it is held stable by the compression spring element 6, 61. The scavenging air inlet 4 is therefore still closed.
  • Fig. 2b shows the closure element in its inlet position E, which corresponds to the bottom dead center position UT of the piston.
  • the inlet position E the scavenging air inlet 4 is released so that scavenging air 41 can flow out of the receiver chamber 401 into the combustion chamber 200.
  • the closure element 5 by the closing element 6, 61 in the example of Fig. 2a and 2 B a compression spring is gradually returned to the closed position Fig. 2b pushed back.
  • the Fig. 3 schematically shows a second embodiment of an inventive cylinder assembly with a tension spring element 62.
  • the example of Fig. 3 differs from the one according to Fig. 2a respectively.
  • Fig. 2b merely in that the closure element 5 is returned by means of a closing element 6 in its closed position S back, which is designed as a mechanical tension spring element 62 in the form of a tension spring 62. That is, the tension spring element 62 pulls the closure element 5 from the inlet position E, in which the scavenging air inlet for introducing scavenging air 41 is opened into the combustion chamber 200, back to the closed position S, when the piston 3 from the bottom dead center UT again in the direction of top dead center OT moves.
  • Fig. 3 is the scavenging air 4 only partially opened, because the piston 3 has already passed through the bottom dead center position UT and is already in the direction of OT in the compression stroke.
  • Fig. 4 is a third embodiment with a one-piece cylinder assembly and scavenging slots 221 shown schematically.
  • the closure element 5 is not formed by the lower part of the cylinder 2.
  • the cylinder 2 is designed in one piece, wherein in the inlet region 22 of the cylinder 2 a cylindrical recess 220 formed in the circumferential direction of the cylinder 2 is provided, into which the closure element 5 is fitted such that an inner diameter of the closure element 5 is substantially identical to an inner diameter of the cylinder 2, so that the piston 3 coming from top dead center OT forth can slide smoothly and without impact into the closure element 5 and this can carry on its further path to bottom dead center UT from the closed position S in the inlet position E.
  • scavenging air inlet 4 also known per se scavenging slots 221 may be provided.
  • the scavenging slots 221 are covered by the closure element 5. Since the piston 3 is enclosed by the closure element 5 in the circumferential direction before it passes through the inlet region 22 with the scavenging slots 221, the piston 3 does not come into contact with the cylinder wall interrupted by the scavenging slots 221 in this exemplary embodiment, so that this embodiment too is all above having described advantages of the invention.
  • the scavenging slots 221 can serve to give the scavenging air 41 a suitable flow form in a manner known per se so that the combustion chamber 200 is rinsed better and more effectively by the scavenging air 41.
  • Fig. 4 are provided as closing elements 6 actively controllable, acted upon by a fluid closing piston 63.
  • the closing piston 63 are, for example pneumatically operated with air or hydraulically with oil and are connected in a conventional manner with an external fluid circuit, not shown, with pressure system, which can set the closing piston 63 in response to the position of the closing element 5 below a predetermined pressure, thereby the movement of the closing element 5 between inlet position E and closing position S can be supported, or controlled and / or regulated.
  • pressure system which can set the closing piston 63 in response to the position of the closing element 5 below a predetermined pressure, thereby the movement of the closing element 5 between inlet position E and closing position S can be supported, or controlled and / or regulated.
  • mechanical closing elements 6, 61, 62 could be provided, as for example with reference to FIG Fig. 2a and Fig. 2b respectively.
  • FIG. 5 in a highly schematic representation and in a section perpendicular to the cylinder axis Z in the region of the receiver chamber 401, an exemplary embodiment according to the invention with a guide device 7 for influencing a purging air flow 42 into the combustion chamber 200 is shown.
  • the guide devices 7, which may be adjustable or non-adjustable baffles 7, for example, serve additionally or alternatively to the scavenging slots 221 to give the scavenging air flow 42 of the scavenging air 41 an even more effective flow shape, so that the combustion chamber 200 is even better and more effective Purge air 41 is rinsed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP09164318A 2009-07-01 2009-07-01 Agencement de cylindre pour un moteur à combustion à piston à balayage axial Withdrawn EP2270318A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09164318A EP2270318A1 (fr) 2009-07-01 2009-07-01 Agencement de cylindre pour un moteur à combustion à piston à balayage axial

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09164318A EP2270318A1 (fr) 2009-07-01 2009-07-01 Agencement de cylindre pour un moteur à combustion à piston à balayage axial

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EP2270318A1 true EP2270318A1 (fr) 2011-01-05

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EP09164318A Withdrawn EP2270318A1 (fr) 2009-07-01 2009-07-01 Agencement de cylindre pour un moteur à combustion à piston à balayage axial

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH176720A (fr) * 1933-06-12 1935-04-30 Gordon Mackenzie Duncan Moteur à combustion interne du type à deux temps.
CH613495A5 (en) 1976-04-15 1979-09-28 Sulzer Ag Cylinder lubrication device for a piston internal combustion engine
EP0652426A1 (fr) 1993-11-09 1995-05-10 New Sulzer Diesel AG Méthode de reconnaissance des perturbations dans le functionnement d'un moteur à diesel
EP1006271A2 (fr) 1998-12-01 2000-06-07 Wärtsilä NSD Schweiz AG Procédé et dispositif pour la détermination du statut d'une pièce mobile dans le cylindre d'un moteur à combustion interne
EP1188906A1 (fr) * 1999-05-24 2002-03-20 Masaharu Ichikawa Dispositif a soupape d'un moteur
US6513464B1 (en) * 2002-04-03 2003-02-04 BUSCH Frank Two cycle stratified charge gasoline engine
EP1471228A2 (fr) * 2003-04-21 2004-10-27 Mitsubishi Heavy Industries, Ltd. Moteur à combustion interne ayant un dispositif de commande d'une soupape de balayage

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH176720A (fr) * 1933-06-12 1935-04-30 Gordon Mackenzie Duncan Moteur à combustion interne du type à deux temps.
CH613495A5 (en) 1976-04-15 1979-09-28 Sulzer Ag Cylinder lubrication device for a piston internal combustion engine
EP0652426A1 (fr) 1993-11-09 1995-05-10 New Sulzer Diesel AG Méthode de reconnaissance des perturbations dans le functionnement d'un moteur à diesel
EP1006271A2 (fr) 1998-12-01 2000-06-07 Wärtsilä NSD Schweiz AG Procédé et dispositif pour la détermination du statut d'une pièce mobile dans le cylindre d'un moteur à combustion interne
EP1188906A1 (fr) * 1999-05-24 2002-03-20 Masaharu Ichikawa Dispositif a soupape d'un moteur
US6513464B1 (en) * 2002-04-03 2003-02-04 BUSCH Frank Two cycle stratified charge gasoline engine
EP1471228A2 (fr) * 2003-04-21 2004-10-27 Mitsubishi Heavy Industries, Ltd. Moteur à combustion interne ayant un dispositif de commande d'une soupape de balayage

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