EP2682572A1 - Système de lubrification - Google Patents

Système de lubrification Download PDF

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Publication number
EP2682572A1
EP2682572A1 EP13171274.7A EP13171274A EP2682572A1 EP 2682572 A1 EP2682572 A1 EP 2682572A1 EP 13171274 A EP13171274 A EP 13171274A EP 2682572 A1 EP2682572 A1 EP 2682572A1
Authority
EP
European Patent Office
Prior art keywords
lubricant
pump
piston
lubricant injection
cylinder
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.)
Granted
Application number
EP13171274.7A
Other languages
German (de)
English (en)
Other versions
EP2682572B1 (fr
Inventor
Reiner Dr. Schulz
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 EP13171274.7A priority Critical patent/EP2682572B1/fr
Publication of EP2682572A1 publication Critical patent/EP2682572A1/fr
Application granted granted Critical
Publication of EP2682572B1 publication Critical patent/EP2682572B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/18—Indicating or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/14—Timed lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/16—Controlling lubricant pressure or quantity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/10—Indicating devices; Other safety devices

Definitions

  • the invention relates to a lubrication system for a piston-cylinder unit according to the preamble of claim 1.
  • the invention further relates to an internal combustion engine, in particular a large engine with a piston-cylinder unit with a lubrication system.
  • Large engines in particular in the design as large diesel engines, which may be designed as two-stroke or four-stroke internal combustion engines are often used as drive units for ships or in stationary operation, e.g. used to drive large generators for generating electrical energy.
  • the large engines usually run for long periods in continuous operation, which places high demands on the reliability and availability. Therefore, for the operator in particular long maintenance intervals, low wear and an economical handling of the operating materials are central criteria.
  • the piston slides along the surface of the wall of the cylinder serving as a running surface, which is usually designed in the form of a cylinder liner, which is also referred to as a cylinder liner.
  • a cylinder or piston lubrication is provided.
  • the piston must slide as smoothly as possible, that is unhindered, in the cylinder, on the other hand, the piston must seal the combustion chamber in the cylinder as well as possible in order to ensure efficient conversion of energy released during the combustion process into mechanical work.
  • a lubricant usually in the form of a lubricating oil
  • a lubricating oil is used to neutralize aggressive combustion products and to prevent corrosion. Because of these many requirements, very high quality and expensive substances are often used as lubricants.
  • Lubricant consumption is the amount of lubricant understood that is no longer available for the actual lubrication task, ie by the lubrication process is consumed, so lost. This loss may be due to the fact that the lubricant is taken up as droplets in the fuel gas or distributed as a lubricant film along the cylinder inner wall. This lubricant can therefore enter the combustion chamber in gaseous form or liquid form, ignite there and be burned, an effect which is undesirable in itself, because it can lead to misfires or deposits in the cylinder interior.
  • a proven lubrication method is the so-called internal lubrication, in which the lubricant is conveyed through the interior of the piston and then applied via one or more lubrication points, which are provided on the surface of the piston, from the piston inner to the piston or on the cylinder surface.
  • Such a method is used, for example, in EP-A-0 903 473 disclosed.
  • an oil collection ring may be provided, as he, for example, from the EP2133520 A1 or from the EP 1 936 245 A1 is known. That is, by means of an oil collection ring can be avoided that lubricant enters the combustion chamber.
  • the sliding surface of the piston in the cylinder interior and lubricant can also be supplied via the cylinder liner itself and are also recorded in the cylinder liner itself in recesses, as for example in the EP 20 50 946 A1 are disclosed.
  • the cylinder lubrication of two-stroke marine diesel engines is carried out by the metered injection of lubricant, the current standard lubrication systems inject only about every tenth revolution due to the constant-volume pump, which is unfavorable for the distribution of the lubricant.
  • the relatively long lines between the pump and injector reduce the dynamics of the system, that is, the amount of time that a metering pulse takes to cover the distance from the pump to the lubricant injector is too long to provide precise control over the injection timing Allow pump.
  • the connecting lines losses due to pipe friction increase, so that by the elasticity of the lubricant by its compressibility in the connecting lines no pulse more detectable at the entrance of the lubricant injection valve.
  • the WO0235068 A1 shows a fluid agent actuated lubricant injection element.
  • a sufficiently high fluid pressure must be available.
  • This fluid fluid pressure is generated according to this embodiment with a mounted on the lubricant injection pump, which is driven by a separate motor. According to this solution, therefore, one pump and one motor are required for each lubricant injection element. Therefore, if a plurality of lubricant injection elements are provided, this solution results in increased maintenance and increased investment costs. Therefore, this solution may be unsuitable for use in multi-cylinder engines, especially in large marine engines.
  • the maintenance effort must be as low as possible, since the engines must run in continuous operation over the entire journey time of the ship. That is, for redundancy reasons, a plurality of such fluid agent actuated lubricant insert elements would have to be kept redundant in stock. On the other hand, the investment costs should be kept as low as possible.
  • the WO2011116768 A1 shows such a common rail system for the injection of lubricant in a plurality of cylinders of an internal combustion engine.
  • the problem of connecting lines described earlier is solved such that the metering of the lubricant takes place directly in the lubricant element via solenoid-controlled valves.
  • the supply of lubricant can be controlled very accurately, both the time of supply of lubricant to the cylinder, and thus the duration of the supply of lubricant, that is, the amount of lubricant to be supplied to the lubrication point.
  • the magnet-controlled valves to be used for this purpose that the supply of lubricant can be initiated by opening the connection to the lubricant nozzle, but also that the supply of lubricant can be interrupted again.
  • the interruption of the lubricant supply may take a different amount of time until the closing pressure is reached, that is to say the lubricant volume which reaches the lubricating point is greater than that provided by the regulation. It is of course possible to set a pressure-dependent switching behavior of the solenoid-controlled valve, but this means an increased control effort.
  • a further object of the invention is to ensure a precise metering of the lubricant for the lubrication of a sliding surface for a piston along a cylinder inner wall.
  • Another object of the invention is to reduce lubricant consumption.
  • Another object of the invention is to adapt the lubricant requirement to the operating state of the internal combustion engine.
  • the storage element is advantageously located at a short distance from the lubricant injection element, may even be integrated into the lubricant injection element.
  • the storage element contains a defined volume of lubricant. The end of the injection process is thus predetermined by the emptying of the storage element.
  • the solution according to the invention results in a simplification of the metering of lubricant, in particular for a piston-cylinder unit of an internal combustion engine, in particular for a large engine.
  • the volume to be metered per stroke when the storage element is completely filled can be in the range from 0.03 to 0.5 cm 3 , depending on the type of internal combustion engine.
  • the lubrication rate can be in the range of 0.2 to 2.5 g / kWh.
  • the number of injection elements per cylinder can be between 1 and 24, in particular from 4 to 24 be. There can be between 0.3 and 3 injections of lubricant per stroke.
  • the storage element advantageously has a diameter of up to 8 mm when the stroke is 10 mm.
  • an annular space of approximately 3 mm inner diameter and 4 mm outer diameter can be provided. The stroke is then about 5 mm.
  • the sum of the cross sections of the outlet openings serving as injection openings is at most as large as the cross-sectional area of the storage element, in particular at most 1/5 of the cross-sectional area of the storage element, more preferably at most 1/10 of the cross-sectional area of the storage element, depending on the desired exit speed of the lubricant through the Outlet openings and / or the desired atomization.
  • the diameters of each of the openings are in a range of 0.1 to 0.5 mm.
  • the storage element is filled via a connecting line which leads from the pump to the lubricant injection element.
  • a variable lift pump may be used so that the delivery rate may be adjusted to the need for lubricant at each load condition of the internal combustion engine.
  • the lubricant which has been conveyed into the storage element is metered, if appropriate, until the storage element is emptied.
  • the storage element may in particular be designed as an accumulator, for example as a piston accumulator.
  • a throttle element may be disposed between the pump and the lubricant injection element. The storage element is replenished after completion of the lubricant delivery via the throttle element.
  • the throttle element may be designed as an adjustable throttle element to adjust the amount of dosed lubricant to the operating conditions of the internal combustion engine.
  • the throttle element may also be designed as a solenoid valve, or comprise a combination with a multi-way valve for determining the course of the injection process.
  • the storage element includes a chamber for receiving a quantity of lubricant which corresponds to the maximum lubricant requirement at the lubrication point.
  • a plurality of memory elements can be arranged behind one another or next to one another. That means at least two Memory elements may be connected in series with each other or may be connected in parallel with each other.
  • a common storage element may be provided for a plurality of lubricant injection elements.
  • a single or a plurality of lubricant injection elements may be connected to a plurality of storage elements.
  • the storage elements may have chambers that have a different volume and / or the volume of each storage element may be variable.
  • the connecting line may contain at least one throttle element between the pump and the storage element.
  • the throttle element may have at least one adjusting element for changing the flow cross-section. By means of the adjustable throttle element can thus be adjusted, the filling speed of the memory element.
  • the pump may have an adjusting means to change the flow rate per unit time.
  • the pump may be designed as a variable-speed gear pump or a piston pump with controllable stroke.
  • the lubricant injector may include the storage element.
  • the storage element has a housing element, an inlet opening for a lubricant which is arranged in the housing element and the storage element which is in fluid-conducting connection with the inlet opening and is arranged in the interior of the housing element.
  • the storage element has a chamber, which is designed to receive lubricant, and an outlet opening, which can be closed by means of a shut-off element.
  • the shut-off element is movable by means of an actuating element such that the outlet opening is releasable for dispensing lubricant.
  • a throttle element may be disposed between the inlet port and the storage element, thereby reducing an amount of lubricant exiting in the short time period between completion of emptying of the accumulator and closure of the solenoid valve to a non-relevant amount.
  • at least one further solenoid valve can be used, to which no special requirements are made with respect to dynamics, since the lubricant supply interrupted long before the start of the injection process and long whose termination can be reopened.
  • the solenoid valve may be extended for injection to a multiway valve or replaced with a multiway valve.
  • the chamber may have a displacement element, so that the volume of the chamber is variable.
  • the lubricant injection element may include a needle valve.
  • An internal combustion engine may include a lubrication system according to any one of the preceding embodiments.
  • the internal combustion engine comprises a piston-cylinder unit, the piston-cylinder unit comprises a cylinder and a piston, wherein the cylinder has a cylinder jacket which delimits a cylinder interior.
  • the cylinder jacket contains at least one lubricant injection element according to one of the preceding embodiments.
  • the method for lubricating a piston-cylinder unit of an internal combustion engine comprises a piston-cylinder unit.
  • a lubrication point of the piston-cylinder unit a lubricant is supplied by means of a lubrication system.
  • the lubrication system includes a pump, a lubricant injector, a connection line between the pump and the lubricant injector for supplying lubricant to the lubricant injector. Between the pump and the lubricant injection element, a storage element is provided in the connection line.
  • the lubricant is conveyed by the pump into the connecting line and into the storage element, from the storage element, the lubricant is conveyed via the lubricant injection element as long as to the lubrication point until the storage element is at least partially emptied.
  • the lubricant injection element has an actuating element, which releases an outlet opening in the housing element of the lubricant injection element, so that lubricant reaches the lubricating point.
  • the lubricant injection element contains a throttle element, which is arranged between the inlet opening and the storage element, so that the storage element is filled up again after at least partial emptying.
  • the time duration of the filling over the delivery rate of the pump can be regulated.
  • FIG. 1 the structure of the proposed lubrication system is shown schematically.
  • a controllable pump for example a variable-speed gear pump or piston pump with controllable stroke, conveys the lubricant into a connecting line 2, to which all lubricant injection elements 6 are connected.
  • the lubricant injection element or elements 6 are arranged on the cylinder wall or the cylinder liner.
  • the delivery pressure is selected as a function of the desired injection quantity of lubricant.
  • the lubricant is conveyed through a throttle element 3 into one or more storage elements 4.
  • the storage element 4 may be designed, for example, as a piston accumulator element or as a pneumatic storage element.
  • the injection process is triggered by a shut-off, such as a solenoid valve 5.
  • a solenoid valve When the solenoid valve is open, the needle valve of the lubricant injection element 6 is opened, so that the lubricant at the lubrication point in the space between the cylinder 20 and piston 11 can flow and from there to the lubrication point on the cylinder inner wall or on the piston ring.
  • the injection process ends when the one or more storage elements 4 are emptied, since the nachfiessende from the supply line 2 amount of lubricant is limited by the throttle element 3.
  • a single solenoid valve may be provided to regulate the supply of lubricant to the lubricant injection elements. That is, the branching of the lubricant line does not occur between the storage element 4 and the two solenoid valves 5, as in Fig. 1 is shown, but following the single solenoid valve. 5
  • the piston-cylinder unit 2 according Fig. 1 comprises a cylinder 20 and a piston 11.
  • the cylinder 20 has a cylinder jacket 17 which has a cylinder interior 18 limited.
  • the piston 11 has a piston skirt surface 35, a piston top side 36 and a piston bottom 37.
  • the piston skirt surface 35, the piston top side 36 and the piston bottom 37 define a piston body 25.
  • the piston body 25 may consist of several parts, for example comprising a piston head 38 and a piston skirt 39.
  • the piston body 25 may be at least partially provided with a cavity 40, through which a coolant can be introduced into the piston body 25.
  • a groove 12 is formed in the piston skirt surface 35, via which a lubricant can be added to the sliding pair of cylinder inner wall and piston ring or can be withdrawn from the surface of the cylinder inner wall.
  • a gap 16 between the piston skirt surface 35 and cylinder shell 17 is formed.
  • the groove 12 may extend over part of the circumference of the skirt surface 35. In particular, a plurality of such grooves may be provided on the circumference of the piston skirt surface, which is not shown in the drawing.
  • the cylinder 20 has a cylinder jacket 17, which contains a plurality of flushing openings 19.
  • the cylinder 20 has a cylinder head 21 with an inner side 22, to which the cylinder jacket 17 adjoins, wherein from the piston top, the cylinder jacket 17 and the inner side 22 of the cylinder head 21, a combustion chamber 23 is limited.
  • a flushing chamber 24 adjoins the piston bottom 6, wherein the fluid pressure in the interior of the recess 11 is smaller than the pressure in the combustion chamber and smaller than the pressure in the washing chamber 24.
  • a first piston ring 14 and a second piston ring 15 are each arranged on the piston skirt surface 35, so that a piston chamber 14, the piston skirt surface 35 and the cylinder jacket 17 limited space 16 is formed, which includes a groove 12.
  • a plurality of such grooves may be provided parallel to each other on the circumference of the piston skirt surface, which is not shown in the drawing.
  • the piston ring 14 forms a substantially gas-tight connection to the combustion chamber 23.
  • the piston ring 15 has no gas-tight design. It can also be designed as a lubricant wiper ring.
  • Fig. 2 shows a possible characteristic of the lubrication system.
  • the volume is entered on the x-axis and the injection pressure on the y-axis.
  • This characteristic relates to a storage element with two spring elements.
  • the bias voltage and / or the direction of action of a stop the relationship between the injection pressure and the stored volume can be influenced.
  • the pressure range which is between P 0 8 and P n 9
  • only one spring element is stretched.
  • the piston moves to a stop which is a second,
  • a stop For example, coaxially arranged, that is parallel connected spring element entrains.
  • This creates a so-called progressive characteristic which means that as the volume increases, the pressure increases disproportionately.
  • it is also possible to produce a degressive characteristic with two spring elements for example by connecting the spring elements in series and using a stop between the spring elements.
  • a degressive characteristic may be advantageous to keep the pressure change during the injection small.
  • Fig. 3 shows a section through an embodiment of a lubricant injection element 6.
  • the lubricant injection element 6 has a housing member 26 in which an inlet opening 27 is arranged for the lubricant, which passes from the pump via a connecting line to the lubricant injection element 6.
  • the inlet opening 27 is arranged in the housing element 26, which is optionally formed in several parts.
  • a storage element 4 which is in fluid-conducting connection with the inlet opening 27 and is arranged in the interior of the housing element 26, is located in the housing element 26.
  • the storage element 4 has a chamber 28, which is designed to receive lubricant, and an outlet opening 30, which can be closed by means of a shut-off element 31.
  • the shut-off element 31 is movable by means of an actuating element 32 such that the outlet opening 30 can be released for dispensing lubricant.
  • a plurality of outlet openings 30 may be provided.
  • a throttle element 3 is arranged between the inlet opening 27 and the storage element 4.
  • the throttle element 3 is formed as a channel in the housing element, which extends partially annular.
  • the throttle element could also have a different shape than those in Fig. 3 have shown shape.
  • the storage element 4 has a sliding element 29 protruding into the chamber 28, which can be moved back and forth in the chamber 28, so that the volume of the chamber 28 can be changed.
  • the displacement element 29 is by a spring element 33 in his in the Fig. 3 shifted lowest position. In this position, the volume of the chamber 28 is the smallest.
  • the displacement element 29 is at the upper stop, excess lubricant is drawn off via the leakage opening 41 in order to allow rapid movement of the displacement element 29.
  • the lubricant that passes through the leakage opening can be detected by a detection mechanism, so that a leakage of the system can be detected and, if necessary, an alarm can be triggered.
  • the displacement element in the region of the receptacle of the spring element can not be designed as a piston, but a gap between the displacement element and the housing remain, which is not shown in the drawings.
  • the displacement element 29 should not reach the stop, i. do not completely compress the spring 33. The filling process is limited by the equilibrium of forces between the spring element 33 and the displacement element 29 designed as an annular piston.
  • Fig. 4 shows a lubrication system according to a second embodiment, which differs from the embodiment according to Fig. 1 differs in that a second memory element 44 is provided in addition to the memory element 4.
  • the first memory element 4 is arranged in a parallel arrangement to the second memory element 44.
  • both memory elements are filled at the same time.
  • the storage element 4 may be arranged downstream of the storage element 44 in the flow direction. In this case, first the storage element 44 is filled before the filling of the storage element 4 takes place.
  • a separate shut-off such as a solenoid valve should be provided. The arrangement may be advantageous if very different operating conditions must be covered.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP13171274.7A 2012-07-04 2013-06-10 Système de lubrification Not-in-force EP2682572B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP13171274.7A EP2682572B1 (fr) 2012-07-04 2013-06-10 Système de lubrification

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP12174960 2012-07-04
EP13171274.7A EP2682572B1 (fr) 2012-07-04 2013-06-10 Système de lubrification

Publications (2)

Publication Number Publication Date
EP2682572A1 true EP2682572A1 (fr) 2014-01-08
EP2682572B1 EP2682572B1 (fr) 2017-08-09

Family

ID=48539066

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13171274.7A Not-in-force EP2682572B1 (fr) 2012-07-04 2013-06-10 Système de lubrification

Country Status (5)

Country Link
EP (1) EP2682572B1 (fr)
JP (1) JP6635461B2 (fr)
KR (1) KR20140005113A (fr)
CN (1) CN103527282B (fr)
DK (1) DK2682572T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014013038A (ja) * 2012-07-04 2014-01-23 Waertsilae Schweiz Ag 潤滑システム
EP2930414A1 (fr) * 2014-04-11 2015-10-14 Alfa Laval Corporate AB Système de commande de lubrification

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JPH01310115A (ja) * 1988-06-08 1989-12-14 Ishikawajima Harima Heavy Ind Co Ltd 間欠給油式潤滑装置
EP0903473A1 (fr) 1997-09-22 1999-03-24 Wärtsilä NSD Schweiz AG Moteur diesel et méthode de fonctionnement
WO2002035068A1 (fr) 2000-10-24 2002-05-02 Hans Jensen Lubricators A/S Systeme de dosage
EP1936245A1 (fr) 2006-12-18 2008-06-25 Wärtsilä Schweiz AG Piston doté d'un anneau collecteur d'huile
EP2050946A1 (fr) 2007-10-16 2009-04-22 Wärtsilä Schweiz AG Cylindre doté de moyens de réception de lubrifiants
EP2093394A1 (fr) * 2008-02-19 2009-08-26 Wärtsilä Schweiz AG Dispositif destiné au graissage de cylindres
EP2133520A1 (fr) 2009-07-09 2009-12-16 Wärtsilä Schweiz AG Piston pour un cylindre d'un moteur de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour ce piston
EP2253810A1 (fr) 2009-05-20 2010-11-24 Wärtsilä Schweiz AG Piston pour un cylindre d'un moteur diesel de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour un tel piston
WO2011116768A1 (fr) 2010-03-12 2011-09-29 Hans Jensen Lubricators A/S Système de dosage pour huile de lubrification pour gros moteurs diesel et procédé de dosage d'huile de lubrification de cylindre dans des cylindres de gros moteurs diesel
WO2012126473A2 (fr) * 2011-03-18 2012-09-27 Hans Jensen Lubricators A/S Dosage d'huile lubrifiante pour cylindres dans des cylindres de grande taille

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JPH0230914A (ja) * 1988-07-20 1990-02-01 Nippon Denso Co Ltd 潤滑油の注油弁装置
DK98391D0 (da) * 1991-05-24 1991-05-24 Jensens Hans Maskinfabrik Smoeresystem til successive doseringer af olie til smoeresteder i store stempelmaskinecylindre
JP4069306B2 (ja) * 1998-03-27 2008-04-02 株式会社ケーヒン 定流量電磁弁
JP3806398B2 (ja) * 2002-11-28 2006-08-09 三菱重工業株式会社 シリンダ注油装置
DK176934B1 (da) * 2007-05-18 2010-05-31 Hans Jensen Lubricators As Smøreapparat samt fremgangsmåde til dosering af cylindersmøreolie
EP2177720B1 (fr) * 2008-10-16 2014-04-09 Wärtsilä Schweiz AG Grand moteur diesel
EP2196639A1 (fr) * 2008-12-12 2010-06-16 Wärtsilä Schweiz AG Pompe de dosage d'huile de cylindre, système de lubrification de cylindre, et moteur à combustion interne
EP2395208A1 (fr) * 2010-06-11 2011-12-14 Wärtsilä Schweiz AG Grand moteur doté d'un dispositif de lubrification de cylindre et procédé de lubrification d'un cylindre d'un grand moteur
CN103527282B (zh) * 2012-07-04 2017-06-30 瓦锡兰瑞士公司 润滑系统、润滑剂注入元件、内燃发动机以及润滑方法

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3958725A (en) * 1974-10-15 1976-05-25 Auto Research Corporation Metering valve for lubrication injector
JPH01310115A (ja) * 1988-06-08 1989-12-14 Ishikawajima Harima Heavy Ind Co Ltd 間欠給油式潤滑装置
EP0903473A1 (fr) 1997-09-22 1999-03-24 Wärtsilä NSD Schweiz AG Moteur diesel et méthode de fonctionnement
WO2002035068A1 (fr) 2000-10-24 2002-05-02 Hans Jensen Lubricators A/S Systeme de dosage
EP1936245A1 (fr) 2006-12-18 2008-06-25 Wärtsilä Schweiz AG Piston doté d'un anneau collecteur d'huile
EP2050946A1 (fr) 2007-10-16 2009-04-22 Wärtsilä Schweiz AG Cylindre doté de moyens de réception de lubrifiants
EP2093394A1 (fr) * 2008-02-19 2009-08-26 Wärtsilä Schweiz AG Dispositif destiné au graissage de cylindres
EP2253810A1 (fr) 2009-05-20 2010-11-24 Wärtsilä Schweiz AG Piston pour un cylindre d'un moteur diesel de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour un tel piston
EP2133520A1 (fr) 2009-07-09 2009-12-16 Wärtsilä Schweiz AG Piston pour un cylindre d'un moteur de grande cylindrée ainsi que le dispositif et le procédé de lubrification prévu pour ce piston
WO2011116768A1 (fr) 2010-03-12 2011-09-29 Hans Jensen Lubricators A/S Système de dosage pour huile de lubrification pour gros moteurs diesel et procédé de dosage d'huile de lubrification de cylindre dans des cylindres de gros moteurs diesel
WO2012126473A2 (fr) * 2011-03-18 2012-09-27 Hans Jensen Lubricators A/S Dosage d'huile lubrifiante pour cylindres dans des cylindres de grande taille

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014013038A (ja) * 2012-07-04 2014-01-23 Waertsilae Schweiz Ag 潤滑システム
EP2930414A1 (fr) * 2014-04-11 2015-10-14 Alfa Laval Corporate AB Système de commande de lubrification
WO2015155340A1 (fr) * 2014-04-11 2015-10-15 Alfa Laval Corporate Ab Système de commande de lubrification
US10627047B2 (en) 2014-04-11 2020-04-21 Alfa Laval Corporate Ab Lubrication control system

Also Published As

Publication number Publication date
KR20140005113A (ko) 2014-01-14
JP2014013038A (ja) 2014-01-23
DK2682572T3 (da) 2017-11-13
CN103527282A (zh) 2014-01-22
JP6635461B2 (ja) 2020-01-22
CN103527282B (zh) 2017-06-30
EP2682572B1 (fr) 2017-08-09

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